Heat exchange fin, heat exchanger and air conditioning device

Abstract

The present invention discloses a heat exchange fin, a heat exchanger and an air conditioning device. The heat exchange fin includes a first side contour line and a second side contour line spaced apart from each other. The first side contour line includes a first reference point and a second reference point, the vertical distance from the first reference point to the straight line where the peak width of the heat exchange fin is located is 25% of the overall height of the heat exchange fin, the ratio of the fin width at the first reference point to the peak width of the heat exchange fin is 0.64-0.96, the vertical distance from the second reference point to the straight line where the peak width of the heat exchange fin is located is 45% of the overall height of the heat exchange fin, the ratio of the fin width at the second reference point to the peak width of the heat exchange fin is 0.54-0.80, and the fin width at the second reference point is smaller than the fin width at the first reference point. Through the above method, the heat exchange fin can meet the wind field flow rate coordination requirements while ensuring that the end of the heat exchange fin has a higher heat exchange performance.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioning, and in particular to a heat exchange fin, a heat exchanger and an air conditioning device. Background Art

[0002] At present, in air conditioning devices, heat exchangers based on heat exchange fins are mostly used to achieve heat exchange functions. Specifically, heat exchange tubes are inserted into a plurality of heat exchange fins arranged at intervals, and the heat exchange tubes are used as flow channels for the heat exchange medium, and the gaps between the heat exchange fins are used as air flow channels, so that the airflow generated by the fan exchanges heat with the heat exchange medium during the flow of the air flow channel.

[0003] Therefore, the optimization of heat exchange fins is an important factor in improving the overall performance of air-conditioning devices. Summary of the invention

[0004] The present invention provides a heat exchange fin, a heat exchanger and an air conditioning device, which improve the heat exchange performance of the heat exchange fin by optimizing the variation rule of the fin width of the heat exchange fin.

[0005] In order to solve the above technical problems, a technical solution adopted by the present invention is: to provide a heat exchange fin, which includes a first side contour line and a second side contour line, and the first side contour line and the second side contour line are spaced from each other. The second side contour line is bent in the direction toward the first side contour line, and the first side contour line is bent in the direction away from the second side contour line, and the fin width of the heat exchange fin gradually decreases from the middle area of ​​the heat exchange fin to the end areas on both sides of the middle area. The first side contour line includes a first reference point and a second reference point, and the vertical distance from the first reference point to the straight line where the peak width of the heat exchange fin is located is 25% of the overall height of the heat exchange fin, and the ratio of the fin width at the first reference point to the peak width of the heat exchange fin is 0.64-0.96. The vertical distance from the second reference point to the straight line where the peak width of the heat exchange fin is located is 45% of the overall height of the heat exchange fin, and the ratio of the fin width at the second reference point to the peak width of the heat exchange fin is 0.54-0.80, and the fin width at the second reference point is smaller than the fin width at the first reference point.

[0006] By optimizing the variation rule of the fin width of the heat exchange fins in the above manner, the heat exchange fins can meet the flow rate matching requirements of the wind field while ensuring that the ends of the heat exchange fins have higher heat exchange performance. BRIEF DESCRIPTION OF THE DRAWINGS

[0007] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings required for describing the embodiments are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative work, among which:

[0008] Figure 1 is a cross-sectional schematic diagram of a duct-type air conditioning device according to an embodiment of the present invention;

[0009] Figure 2 is a side view of a heat exchange fin according to an embodiment of the present invention;

[0010] Figure 3a and 3b It is a flow velocity distribution diagram of a duct type air conditioner using a diffuser plate arrangement method according to an embodiment of the present invention and a flow velocity distribution comparison diagram of a comparative example;

[0011] Figure 4a and 4b 1. is a flow velocity distribution diagram of a duct type air conditioner using a heat exchange fin according to an embodiment of the present invention and a flow velocity distribution comparison diagram of a comparative example;

[0012] Figure 5 is a side view of a heat exchange fin according to another embodiment of the present invention;

[0013] Figure 6 is a side view of a heat exchange fin according to another embodiment of the present invention;

[0014] Figure 7 is a partial structural stereogram of a heat exchange fin according to an embodiment of the present invention;

[0015] Figure 8 yes Figure 6 Schematic diagram of the local enlarged structure in;

[0016] Fig. 9 is a partial structural stereogram of a heat exchange fin according to another embodiment of the present invention;

[0017] Fig.10 is a partial top view according to another embodiment of the present invention;

[0018] Fig.11 is a cross-sectional schematic diagram of a heat exchanger according to an embodiment of the present invention;

[0019] Fig.12 is a schematic cross-sectional view of a heat exchanger according to another embodiment of the present invention;

[0020] Fig.13 is a schematic diagram of a three-dimensional structure of a heat exchanger and an auxiliary matching mechanism according to an embodiment of the present invention;

[0021] Fig.14 is a side view of a sheet metal edge plate according to an embodiment of the present invention;

[0022] Fig.15 yes Fig.14 Schematic diagram of the three-dimensional structure of the sheet metal edge plate;

[0023] Fig.16 yes Fig.15 Schematic diagram of the cross-sectional structure of the sheet metal edge plate in FIG.

[0024] Fig.17 is a schematic diagram of a three-dimensional structure of a plastic side plate according to an embodiment of the present invention;

[0025] Fig.18 yes Fig.17 A schematic diagram of a three-dimensional structure of a plastic side plate and a U-shaped pipe section arranged in a coordinated manner;

[0026] Fig.19 yes Fig.17 A schematic diagram of a three-dimensional structure of another arrangement of the plastic side panels and the U-shaped pipe sections shown;

[0027] Fig. 20 yes Fig.17 A partial cross-sectional view of the plastic side plate and the U-shaped pipe section shown. DETAILED DESCRIPTION

[0028] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0029] Reference to "embodiments" herein means that a particular feature, structure, or characteristic described in conjunction with the embodiments may be included in at least one embodiment of the present application. The appearance of the phrase in various locations in the specification does not necessarily refer to the same embodiment, nor is it an independent or alternative embodiment that is mutually exclusive with other embodiments. It is explicitly and implicitly understood by those skilled in the art that the embodiments described herein may be combined with other embodiments.

[0030] See also Figure 1 and Figure 2 , Figure 1 is a cross-sectional schematic diagram of a duct-type air conditioning device in an embodiment of the present application, Figure 2 FIG. 1 is a side view of a heat exchange fin according to an embodiment of the present invention. Figure 1As shown, the duct type air conditioning device of this embodiment mainly includes a housing 10, a fan assembly 20 and a heat exchanger 30. The housing 10 forms a receiving chamber 11, and the heat exchanger 30 is arranged in the receiving chamber 11. In this embodiment, the heat exchanger 30 includes a plurality of heat exchange fins 31 arranged at intervals from each other and a heat exchange tube 32 passing through the heat exchange fins 31. Figure 1 The cross section shown is a reference cross section formed by the plane where the main surface of the heat exchange fin 31 is located. Figure 1 Only one heat exchange fin 31 is shown, and the remaining heat exchange fins 31 are arranged along Figure 1 The vertical direction of the paper Figure 1 The heat exchange fins 31 are arranged at intervals. The heat exchange fins 31 are generally formed by stamping a sheet of material, and the main surfaces of the heat exchange fins 31 are the two side surfaces which are arranged at intervals along the thickness direction of the heat exchange fins 31 and have the largest surface area.

[0031] The fan assembly 20 includes a volute 21 and a fan 22 disposed in the volute 21. The airflow generated by the fan 20 flows into the accommodating chamber 11 through the air outlet 211 of the volute 21 under the action of the volute 21, and blows on the heat exchanger 30. The heat exchange medium flowing in the heat exchange tube 32 exchanges heat with the airflow flowing through the heat exchanger 30 through the heat exchange tube 32 and the heat exchange fins 31, and then cools or heats the airflow flowing through the heat exchanger 30 as needed. The airflow after heat exchange in the heat exchanger 30 further flows out through the air outlet 101 of the housing 10.

[0032] The present application further optimizes the following aspects based on the overall structure of the duct type air conditioning device described above:

[0033] 1. Snail case air outlet angle

[0034] In this embodiment, the fan 22 and the heat exchange fin 31 are spaced apart along the direction D1. The volute 21 includes a first diffuser plate 212 and a second diffuser plate 213, and the first diffuser plate 212 and the second diffuser plate 213 are spaced apart along the direction D2. The direction D2 is perpendicular to the direction D1 and parallel to the main surface of the heat exchange fin 31. Further, in the direction from the fan 22 to the heat exchange fin 31, the first diffuser plate 212 is inclined toward the direction of the second diffuser plate 213, and the second diffuser plate 213 is inclined away from the first diffuser plate 212.

[0035] It is worth noting that in the normal installation and use state of the duct type air conditioner of the present application, the direction D1 is generally the horizontal direction, the direction D2 is generally the vertical direction (i.e., the gravity direction), and the first diffuser plate 212 is located on the upper side of the second diffuser plate 213. The relative positional relationships such as "upper", "lower", "front", and "rear" mentioned in the present application are also the relative positional relationships of the duct type air conditioner in the normal installation and use state.

[0036] The first diffuser plate 212 and the second diffuser plate 213 are used to guide the airflow generated by the fan 22 to flow into the accommodating chamber 11 through the air outlet 211 of the volute 21, and to convert the velocity energy of the airflow into pressure energy through the shape change of the flow channel between the first diffuser plate 212 and the second diffuser plate 213, thereby increasing the airflow pressure at the air outlet 211. Therefore, the angle parameters of the first diffuser plate 212 and the second diffuser plate 213 directly affect the uniformity of the velocity distribution of the airflow flowing through the heat exchange fins 31.

[0037] Therefore, in this embodiment, in order to obtain better uniformity of flow velocity distribution, on the reference cross section formed by the plane where the main surface of the heat exchange fin 31 is located, the angle β1 between the first diffuser plate 212 and the direction D1 is set to 6-9 degrees, and the angle β2 between the second diffuser plate 213 and the direction D1 is set to 20-24 degrees. In a specific embodiment, the angle β1 is set to 6-8 degrees, and β2 is set to 21-23 degrees. It is worth noting that, unless otherwise specified, the numerical ranges mentioned in this application include end values.

[0038] Further reading Figure 3a and 3b The flow velocity distribution diagram of this embodiment and the flow velocity distribution diagram of the comparative example are shown. Figure 3a and Figure 3b When the angles β1 and β2 between the first diffuser plate 212 and the second diffuser plate 213 and the direction D1 are set in different ways, the airflow generated by the fan 22 flows through Figure 1 The flow velocity distribution diagram after the same heat exchanger 30 is shown. The Y axis in the figure represents the wind speed, and the X axis represents the leeward side contour line of the heat exchange fin 31 ( Figure 2 Different lines represent different sampling points from the middle area to the end area on the first side contour line 311 in the figure, and different lines represent different sampling points from one end to the other end of the heat exchanger 30 along the spacing direction of the heat exchange fins 31.

[0039] further, Figure 3a Using the angle setting method of this embodiment, the specific angle β1 is 7 degrees and the angle β2 is 22 degrees. Figure 3b Using other angle settings, the specific angle β1 is 5 degrees and the angle β2 is 19 degrees. Figure 3a and Figure 3b The comparison results show that Figure 3b The wind speed flowing through the heat exchange fin 31 changes significantly more when the wind speed changes from the middle area to the end area. Figure 3a Therefore, the uniformity of the airflow velocity in the angle setting method of this embodiment is significantly higher than that in other angle setting methods.

[0040] It is worth noting that when the first diffuser plate 212 or the second diffuser plate 213 is a flat plate or the main part is a flat plate, the angles β1 and β2 between it and the direction D1 are the angles between the extension line of the straight line segment formed by the flat plate part of the first diffuser plate 212 or the second diffuser plate 213 on the above reference section and the direction D1. When the first diffuser plate 212 or the second diffuser plate 213 is an arc-shaped plate or the main part is an arc-shaped plate, the angles β1 and β2 between it and the direction D1 are the angles between the connecting line of the two ends of the overall line formed by the first diffuser plate 212 or the second diffuser plate 213 on the above reference section and the direction D1.

[0041] Further, when the ratio of the length of the straight line segment corresponding to the flat plate in the overall line formed by the first diffuser plate 212 or the second diffuser plate 213 on the above-mentioned reference section to the total length of the overall line is greater than or equal to 60%, the main part of the first diffuser plate 212 or the second diffuser plate 213 is considered to be a flat plate; when the ratio of the length of the straight line segment corresponding to the flat plate to the total length of the overall line is less than 60%, the main part of the first diffuser plate 212 or the second diffuser plate 213 is considered to be an arc-shaped plate.

[0042] See also Figure 1 The airflow flowing out of the air outlet 211 of the volute 21 is mainly divided into three flow rate zones before reaching the heat exchanger 30: zone A, zone B, and zone C. Zone A is the direct blowing mainstream zone, zone B is the mainstream diffusion zone, and zone C is the dynamic pressure conversion static pressure and inherent static pressure diffusion zone. The flow rates of zones A and B are relatively large, and the flow rate of zone C is small.

[0043] Further integration Figure 2 The heat exchange fin 31 has a first side contour line 311 and a second side contour line 312 spaced apart from each other. The second side contour line 312 is arranged on the side of the heat exchange fin 31 facing the fan 22 as the windward side contour line, and the first side contour line 311 is arranged on the side of the heat exchange fin 31 facing away from the fan 22 as the leeward side contour line.

[0044] like Figure 1As shown, in this embodiment, the extension line of the first diffuser plate 212 intersects with the second side contour line 312 to form an intersection E1, and the extension line of the second diffuser plate 213 intersects with the second side contour line 312 to form an intersection E2. There is a vertical distance d1 from the intersection E1 to the reference line l1 which is parallel to the uppermost end of the heat exchange fin 31 and in the direction D1, and there is a vertical distance d2 from the intersection E2 to the reference line l2 which is parallel to the lowermost end of the heat exchange fin 31 and in the direction D1. The ratio of the sum d1+d2 of the vertical distance d1 and the vertical distance d2 to the height L2 of the heat exchange fin 31 along the direction D2 is 0.26-0.35. Referring to the above description, when the first diffuser plate 212 or the second diffuser plate 213 is a flat plate or the main body is a flat plate, its extension line is the extension line of the straight line segment formed by the flat plate portion of the first diffuser plate 212 or the second diffuser plate 213 on the above reference section. When the first diffuser plate 212 or the second diffuser plate 213 is an arc-shaped plate or the main body is an arc-shaped plate, its extension line is the extension line of the line connecting the two ends of the overall line formed by the first diffuser plate 212 or the second diffuser plate 213 on the above reference section.

[0045] Through the above-mentioned method, the direct blowing mainstream area A and the mainstream diffusion area B can cover the heat exchange fins 31 at the same time, so that the heat exchange of the heat exchange fins 31 is more uniform.

[0046] Furthermore, since the slow diffusion of the airflow to both sides is similar when the airflow flows in the closed channel, the vertical distance d1 and the vertical distance d2 can be set to be approximately equal. Specifically, the ratio of the vertical distance d1 to the height L2 of the heat exchange fin 31 along the direction D2 is set to 0.13-0.175, and the ratio of the vertical distance d2 to the height L2 of the heat exchange fin 31 along the direction D2 is set to 0.13-0.175, so that the mainstream diffusion and spreading areas B on both sides of the direct blowing mainstream area A can cover the heat exchange fin 31, further improving the heat exchange uniformity of the heat exchange fin 31.

[0047] Furthermore, in the present embodiment, the second side contour line 312 is bent in the direction toward the first side contour line 311, and the first side contour line 311 is bent in the direction away from the second side contour line 312. The ratio of the straight-line distance d3 between the projections of the intersection point E1 and the intersection point E2 on the reference line l1 or l2 to the width L4 of the heat exchange fin along the direction D1 is less than or equal to 0.2, thereby enabling the mainstream diffusion zone B on both sides of the direct blowing mainstream zone A to more comprehensively cover the heat exchange fin 31.

[0048] 2. Overall size

[0049] See also Figure 1In a duct-type air conditioner, if the heat exchanger 30 is too close to the air outlet 211 of the volute 21, the direct blowing area of ​​the airflow is small, the local flow velocity flowing through the heat exchanger 30 is large, the heat exchange is insufficient, and the noise is large. If the heat exchanger 30 is too far from the air outlet 211 of the volute 21, the airflow enters the relatively large space of the accommodating chamber 11 from the relatively small space of the volute 21, and the airflow will collide with each other in the accommodating chamber 11, causing large local losses. At the same time, it leads to an increase in the size of the whole machine, which is not conducive to the integrated design of the air conditioner and the home, and the cost is high.

[0050] Therefore, in this embodiment, in order to achieve a balance between heat exchange performance and overall size, the duct-type air conditioner is further configured to satisfy the following formula on a reference cross section formed by a plane where the main surface of the heat exchange fin 31 is located:

[0051] L2 = ξ × (L1 + L3 × tgθ);

[0052] Among them, θ is the angle between the first diffuser plate 212 and the second diffuser plate 213, tg is the tangent trigonometric function, L1 is the height of the air outlet 211 of the volute 21 along the direction D2, L2 is the height of the heat exchange fin 31 along the direction D2, L3 is the distance between the end of the heat exchange fin 31 close to the air outlet 211 and the air outlet 211 along the direction D1, and ξ is a preset coefficient of 1.3-1.6.

[0053] Combined with the above description, for different plate shapes, the angle between the first diffuser plate 212 and the second diffuser plate 213 and the direction D1 is defined by the extension line and / or the line connecting the two ends of the first diffuser plate 212 and the second diffuser plate 213. Therefore, in this embodiment, the angle θ between the first diffuser plate 212 and the second diffuser plate 213 refers to the angle between the above-mentioned extension line and / or the line connecting the two ends of the first diffuser plate 212 and the second diffuser plate 213. Specifically, the angle θ between the first diffuser plate 212 and the second diffuser plate 213 is the difference between the angle β1 between the first diffuser plate 212 and the direction D1 and the angle β2 between the second diffuser plate 213 and the direction D1, that is, θ=β2-β1. The height L1 of the air outlet 211 of the volute 21 along the direction D2 specifically refers to the distance between the two side edges of the air outlet 211 of the volute 21 along the direction D2.

[0054] By the above method, the heat exchange performance and the size of the whole unit of the duct type air conditioner can be effectively balanced. Under the same air volume, the air flow through the heat exchanger 30 is more uniform, with better heat exchange effect and lower noise. Under the same noise, the duct type air conditioner can have a larger air volume to meet the air conditioning of a larger space. At the same time, the duct type air conditioner has a smaller volume, meeting the needs of a wider range of home air conditioning integration.

[0055] Optionally, in a specific embodiment, the angle θ between the first diffuser plate 212 and the second diffuser plate 213 is set to 10-20 degrees, thereby optimizing the coverage area of ​​the direct blowing mainstream area A on the heat exchange fins 31 .

[0056] Optionally, in a specific embodiment, the ratio between L1 and L2 is set to 0.4 to 0.6, and ξ is set to 1.4-1.5, thereby improving the smoothness of air outlet at the upper and lower ends of the duct air conditioning device and improving the heat exchange effect at the end of the heat exchange fin 31.

[0057] Optionally, in a specific embodiment, the height L2 of the heat exchange fin 31 along the direction D2 is 150-190 mm, the height L1 of the air outlet 211 of the volute 21 along the direction D2 is set to 80-100 mm, and the distance L3 between the end of the heat exchange fin 31 close to the air outlet 211 and the air outlet 211 along the direction D1 is further calculated according to the above formula, thereby achieving a balance between the heat exchange performance and the size of the whole machine.

[0058] 3. Condensation interference

[0059] Further integration Figure 2 , the fin width of the heat exchange fin 31 gradually decreases in the direction from the middle area to the end area of ​​the heat exchange fin 31. The heat exchange fin 31 has a straight line l3 where the peak width is located. In the present embodiment, the straight line l3 where the peak width is located is arranged along the direction D1. In other embodiments, the straight line l3 where the peak width is located can be inclined relative to the direction D1, and the angle between the two is less than or equal to 10 degrees. The heat exchange fin 31 further has an overall height H1 and an overall width H2. When the straight line l3 where the peak width of the heat exchange fin 31 is arranged along the direction D1, the height L2 of the heat exchange fin 31 along the direction D2 is the overall height H1 of the heat exchange fin 31, and the width L4 of the heat exchange fin 31 along the direction D1 is the overall width H2 of the heat exchange fin 31. When the straight line l3 where the peak width of the heat exchange fin 31 is located is set at an angle to the direction D1, the height L2 of the heat exchange fin 31 along the direction D2 and the width along the direction D1 are the projections of the overall height H1 and the overall width H2 of the heat exchange fin 31 in the directions D2 and D1, and can be obtained according to trigonometric calculations.

[0060] During the cooling process of the duct air conditioner, when the airflow passes through the surface of the heat exchange fin 31, the water vapor in the airflow will condense when it encounters cold, generating condensed water. The condensed water flows down along the heat exchange fin 31 under the action of gravity, and more condensed water accumulates in the lower half of the heat exchange fin 31, causing the wind resistance of the lower half of the heat exchange fin 31 to be greater than that of the upper half, thereby causing uneven heat exchange of the heat exchange fin 31.

[0061] Therefore, in order to improve the heat exchange uniformity between the lower and upper parts of the heat exchange fin 31, on the reference cross-section formed by the plane where the main surface of the heat exchange fin 31 is located, the intersection E3 formed by the bisector l4 of the angle θ between the first diffuser plate 212 and the second diffuser plate 213 and the straight line l3 where the peak width of the heat exchange fin 31 is located is set to be located on the side of the heat exchange fin 31 close to the fan 22, and the intersection E4 formed by the bisector l3 and the second side contour line 312 of the heat exchange fin 31 is located below the straight line l3 where the peak width is located.

[0062] Since the two sides of the angle bisector l3 of the angle between the first diffuser plate 212 and the second diffuser plate 213 correspond to the maximum flow velocity area of ​​the airflow, through the above method, the lower half of the heat exchange fin 31 can be purged with a higher speed airflow to overcome the wind resistance of the condensed water, thereby making the heat exchange effect of the entire heat exchange fin 31 more uniform. In addition, since the airflow direction that purges the lower half of the heat exchange fin 31 has a certain component along the direction D2, it can provide additional acceleration force for the condensed water on the basis of gravity, thereby accelerating the flow of the condensed water.

[0063] Optionally, in a specific embodiment, the ratio of the vertical distance d4 from the intersection E4 to the straight line l3 where the peak width is located to the overall height H1 of the heat exchange fin 31 is set to 0.02-0.06, thereby avoiding the reverse unevenness of the heat exchange performance between the lower and upper parts of the heat exchange fin 31 caused by excessive flow rate of the airflow blowing the lower part of the heat exchange fin 31.

[0064] Optionally, in a specific embodiment, the angle β3 between the angle bisector l4 and the straight line l3 where the peak width is located is set to 10-16 degrees, thereby achieving a balance between heat exchange performance and condensation water acceleration.

[0065] Optionally, in a specific embodiment, based on the above setting range of the angle β3, the straight line distance d5 between the intersection point E5 formed by the straight line l3 where the peak width is located and the second side contour line 312 and the intersection point E3 is further calculated as max The ratio is set to 0.45-0.61.

[0066] Further integration Figure 2Optionally, in a specific embodiment, the second side contour line 312 includes arc segments S1'-S2', S1'-S5', arc segments S2'-S3', S5'-S6' and straight segments S3'-S4', S6'-S7', which are sequentially connected in the direction from the middle area to the end area on both sides of the straight line l3 where the peak width is located, wherein the curvature radius of the arc segments S2'-S3', S5'-S6' is greater than the curvature radius of the arc segments S1'-S2', S1'-S5', and the intersection E4 is located on the arc segment S1'-S5' below the straight line l3 where the peak width is located. By any one or combination of the above two methods, it can be ensured that the maximum flow velocity area on both sides of the angle bisector l4 fully acts on the middle area of ​​the heat exchange fin 31, thereby improving the heat exchange effect.

[0067] It is worth noting that the peak width W of the heat exchange fin 31 mentioned above is max , the straight line l3 where the peak width is located, the overall height H1, the overall width H2 and other shape characterization parameters of the heat exchange fin 31 mentioned later will be combined below Figure 2 Describe in detail.

[0068] 4. Heat exchanger air outlet angle

[0069] like Figure 1 As shown, the duct-type air conditioning device of this embodiment further includes a first collector plate 41 and a second collector plate 51 , and the first collector plate 41 and the second collector plate 51 are respectively arranged above and below the heat exchange fins 31 along the direction D2 .

[0070] In this embodiment, the second conduit plate 51 is formed by a portion of the water receiving tray 50 close to the air outlet 101 of the housing 10. In other embodiments, the second conduit plate 51 may also be provided as an independent element independent of the water receiving tray 50. The first conduit plate 41 and the second conduit plate 51 are used to converge the airflow passing through the heat exchange fins 31 and guide it to the air outlet 101 of the housing 10. In the duct type air conditioning device of this embodiment, the space between the first conduit plate 41 and the second conduit plate 51 and the first side contour line 311 determines the air outlet smoothness and converging effect of the heat exchanger 30.

[0071] Therefore, in order to achieve a balance between air outlet smoothness and confluence effect, on the reference section formed by the plane where the main surface of the heat exchange fin 31 is located, the perpendicular bisector of the peak width Wmax of the heat exchange fin 31 forms intersections E6 and E7 with the first side contour line 311, and further forms intersections E8 and E9 with the first confluence plate 41 and the second confluence plate 51.

[0072] An included angle β4 between a tangent line at the intersection point E6 and a tangent line at an adjacent intersection point E8 is 27-37 degrees, and an included angle β5 between a tangent line at the intersection point E7 and a tangent line at an adjacent intersection point E9 is 36-46 degrees.

[0073] By the above method, the convergence angle of the air outlet side of the heat exchanger 30 defined by the first convergence plate 41 and the second convergence plate 51 can be moderate, which can not only make the air outlet of the heat exchanger 30 smooth, thereby improving the heat exchange effect at the end of the heat exchange fin 31, but also have a good convergence effect. In addition, by further setting the difference between the angle β4 and the angle β5, and in combination with the angle β3 described above, the balance of the air outlet smoothness of the upper and lower parts of the heat exchange fin 31 can be further ensured.

[0074] Optionally, in a specific embodiment, the intersection E6 and the intersection E7 have a straight line distance d6, that is, the sum of the vertical distances from the intersection E6 and the intersection E7 to the straight line l3 where the peak width is located, and the ratio of the straight line distance d6 to the overall height H1 of the heat exchange fin 31 is 0.46-0.56.

[0075] Optionally, in a specific embodiment, the second side contour line 312 is bent toward the first side contour line 311, and the first side contour line 311 is bent away from the second side contour line 312. The ratio of the straight-line distance d7 between the intersection point E8 and the upper end point of the first side contour line 311 along the straight line l3 where the peak width is located to the peak width Wmax is 0.92-1.13, and the ratio of the straight-line distance d8 between the intersection point E9 and the lower end point of the first side contour line 311 along the straight line l3 where the peak width is located to the peak width Wmax is 0.93-1.14. Further, the straight-line distance d7 and the straight-line distance d8 can be set to be approximately equal, for example, the ratio of the straight-line distance d7 and the straight-line distance d8 can be set to 0.9-1.1.

[0076] Further integration Figure 2 Optionally, in a specific embodiment, the first side contour line 311 includes arc segments S1-S2, S1-S5, arc segments S2-S3, S5-S6 and straight line segments S3-S4, S6-S7 that are sequentially connected in the direction from the middle area to the end area on both sides of the straight line l3 where the peak width is located, wherein the curvature radius of the arc segments S2-S3 and S5-S6 is greater than the curvature radius of the arc segments S1-S2 and S1-S5. The intersection point E6 and the intersection point E7 are located on the arc segments S2-S3 and S5-S6.

[0077] One or a combination of the above three methods can ensure that there is enough space between the first collector plate 41 and the second collector plate 51 and the first side contour line 311, thereby further ensuring smooth air flow of the heat exchanger 30.

[0078] Optionally, in a specific embodiment, the ratio of the sum of the angle β4 and the angle β5 to the opening angle α1 of the first side contour line 311 is 0.58-0.79, thereby ensuring the smoothness of the air outlet of the heat exchanger 30 while ensuring that the heat exchange fins 31 have sufficient depth along the direction D1, thereby improving the heat exchange efficiency of the heat exchange fins 31.

[0079] Further, the water receiving tray 50 includes two water receiving grooves 53 and 54 separated by a support portion 52. The heat exchange fin 31 is supported on the support portion 52, and the projection of the lower end point of the first side contour line 311 along the direction D2 falls into the water receiving groove 53, while the projection of the lower end point of the second side contour line 312 along the direction D2 falls into the water receiving groove 54, and then the water receiving grooves 53 and 54 are used to receive the condensed water falling along the first side contour line 311 and the second side contour line 312 respectively. Since the first side contour line 311 is located on the leeward side compared to the second side contour line 312, there is more condensed water along the first side contour line 311. Therefore, in a specific embodiment, along the direction D1, the width of the water receiving groove 53 is greater than the width of the water receiving groove 54. In the above manner, it is possible to avoid excessive accumulation of condensed water in the water receiving groove 53, and at the same time, avoid the airflow from blowing out the condensed water in the water receiving groove 53.

[0080] It should be further explained that the four optimization schemes for the overall structure of the duct air conditioner described above can be used alone or in combination, and the heat exchange fins 31 used are not limited to Figure 1 and Figure 2 The moon-shaped heat exchange fins shown may also be V-shaped or straight-strip heat exchange fins.

[0081] See also Figure 2 , the following will Figure 1 and Figure 2 The specific shape of the crescent-shaped heat exchange fin shown is described in detail.

[0082] In this embodiment, Figure 1 and Figure 2 The heat exchange fin 31 shown includes a first side contour line 311 , a second side contour line 312 , and two end contour lines 314 and 315 .

[0083] In the present application, a contour line refers to a combination of two or more contour lines with a predetermined line type used to define the outer contour of the heat exchange fin 31. The first side contour line 311 and the second side contour line 312 refer to two contour lines spaced apart along the incoming wind direction D3 when the heat exchange fin 31 is working. One of the first side contour line 311 and the second side contour line 312 is used as a windward side contour line, and the other is used as a leeward side contour line. Further, the windward side contour line refers to the side contour line of the first side contour line 311 and the second side contour line 312 facing the incoming wind direction D3, and the leeward side contour line refers to the side contour line of the first side contour line 311 and the second side contour line 312 facing away from the incoming wind direction D3. In this embodiment, the second side contour line 312 is used as the windward side contour line, and the first side contour line 311 is used as the leeward side contour line. In other embodiments, the first side contour line 311 can be used as the windward side contour line, and the second side contour line 312 can be used as the leeward side contour line.

[0084] The end contour lines 314 and 315 refer to contour lines used to connect the adjacent ends of the first side contour line 311 and the second side contour line 312. It is worth noting that when a notch is formed at the edge of the heat exchange fin 31 due to process or installation requirements, the contour line at the notch should be understood as a transition formed by the contour lines on both sides of the notch. In addition, when there is a cut angle at the connection between the end contour lines 314 and 315 and the first side contour line 311 and / or the second side contour line 312, the contour line at the cut angle should be regarded as a part of the end contour lines 314 and 315.

[0085] In this embodiment, the second side contour line 312 is bent in the direction toward the first side contour line 311, the first side contour line 311 is bent in the direction away from the second side contour line 312, and the fin width of the heat exchange fin 31 gradually decreases in the direction from the middle area of ​​the heat exchange fin 31 to the end areas on both sides of the middle area, so that the heat exchange fin 31 is set in a crescent shape as a whole. Generally speaking, the wind field formed by the airflow includes a high velocity area located in the middle and low velocity areas located on both sides of the high velocity area. By setting the fin width of the heat exchange fin 31 to gradually decrease in the direction from the middle area of ​​the heat exchange fin 31 to the end areas on both sides of the middle area, the high velocity area corresponds to the middle area with a larger fin width, and the low velocity area corresponds to the end area with a smaller fin width, the heat exchange in the middle area and the end area of ​​the heat exchange fin 31 can be made more uniform, thereby improving the overall heat exchange performance.

[0086] It is worth noting that the descriptions such as "gradually decreasing" and "gradually increasing" mentioned in this application refer to the overall change trend, which can be a continuous change or a segmented change. For example, the "fin width gradually decreases" mentioned above can include a portion of the fin width constant area, that is, a segmented decrease.

[0087] In the present application, a reference point is selected on the first side contour line 311, and the normal line (perpendicular line of the tangent line) of the reference point intersects with the second side contour line 312 to form an intersection point. The straight-line distance between the reference point and the intersection point is the fin width at the reference point, for example Figure 2 W shown in max , W1, W2, etc. It is worth noting that when the line type of the contour line where the reference point is located is a straight line, the normal line of the reference point is the perpendicular line of the straight line.

[0088] Furthermore, the length of the line connecting the reference point and the intersection point at the maximum fin width is the peak width W. max , the straight line where the line connecting the reference point and the intersection point is located is the straight line l3 where the peak width is located. It is worth noting that when the first side contour line 311 and the second side contour line 312 are curved, the straight line l3 where the peak width is located is generally the straight line where the line connecting the vertices of the first side contour line 311 and the second side contour line 312 is located. When there are multiple lines with the largest fin width, the straight line where the line in the middle is located is selected as the straight line l3 where the peak width is located.

[0089] In this embodiment, the first side contour line 311 and the second side contour line 312 are further arranged to overlap in translation. Specifically, when the first side contour line 311 is translated along the straight line l3 where the peak width is located toward the second side contour line 312 by the peak width W max After that, the translation curve 311' formed by the first side contour line 311 overlaps with at least a portion of the second side contour line 312. In a specific embodiment, the length of the overlapping portion of the translation curve 311' and the second side contour line 312 accounts for more than or equal to 90% of the total length of the first side contour line 311. The heat exchange fin 31 is generally formed by stamping and cutting a sheet of material. The above method can reduce waste during the processing and reduce production costs.

[0090] Furthermore, the end contour lines 314 and 315 include straight line segments parallel to the straight line l3 where the peak width of the heat exchange fin 31 is located. During the stamping process, the straight line l3 where the peak width is located is generally set along the length direction of the sheet. In this way, a portion of the end contour lines 314 and 315 can be flush with the edge of the sheet to further reduce waste.

[0091] like Figure 2As shown, the shape characterization parameters of the heat exchange fin 31 also include the overall height, the overall width and the side profile angle. The overall height refers to the projected dimension H1 of the heat exchange fin 31 on a reference plane P1 that is perpendicular to the straight line l3 where the peak width is located and perpendicular to the main surface of the heat exchange fin 31. The overall width refers to the projected dimension H2 of the heat exchange fin 31 on a reference plane P2 that is parallel to the straight line l3 where the peak width is located and perpendicular to the main surface of the heat exchange fin. The side profile forms an intersection with the straight line l3 where the peak width is located. The side profile angle refers to the angle between the two ends of the side profile and the line connecting the intersection, for example, Figure 2 In FIG. 3 , the opening angle of the first side contour line 311 is α1.

[0092] In combination with the subsequent drawings, the present application will further optimize the heat exchange fins 31 in the following aspects based on the overall shape of the heat exchange fins 31 described above:

[0093] 1. Side profile angle

[0094] The overall height H1 and peak width W max Under the same conditions, the opening angle α1 of the first side contour line 311 determines the depth of the heat exchange fin 31 along the straight line l3 where the peak width is located, that is, the overall width H2 of the heat exchange fin 31. If the opening angle α1 of the first side contour line 311 is too large, the depth of the heat exchange fin 31 is relatively small, and then the area of ​​the main surface of the heat exchange fin 31 is relatively small, and the overall heat exchange performance of the heat exchange fin 31 is deteriorated. If the opening angle α1 of the first side contour line 311 is too small, the airflow smoothness at the end of the heat exchange fin 31 is insufficient, resulting in poor heat exchange performance at the end of the heat exchange fin 31.

[0095] In order to achieve a balance between the overall heat exchange performance and the smoothness of the airflow at the end, in this embodiment, the opening angle α1 of the first side contour line 311 is set to 80-135 degrees. Optionally, in a specific embodiment, the opening angle α1 of the first side contour line 311 is further set to 95-120 degrees. In another specific embodiment, the opening angle α1 of the first side contour line 311 is further set to 100-110 degrees. In the above manner, not only can the heat exchange fins 31 have the largest heat exchange area in the smallest space, but also the smoothness of the airflow at the end can be ensured.

[0096] Furthermore, the first side contour line 311 also has an end tangent angle. Specifically, the end tangent angle refers to the angle α2 between the tangents of the two end points of the first side contour line 311. Figure 2 In , is the angle between the tangents of endpoints S4 and S7. It is worth noting that when the end point is located on a straight line segment, its tangent is the extension of the straight line segment. maxWhen the first side contour line 311 and the second side contour line 312 are the same and the first side contour line 311 and the second side contour line 312 are translated and overlapped, the end tangent angle α2 of the first side contour line 311 determines the fin width at the end of the heat exchange fin 31. If the end tangent angle α2 of the first side contour line 311 is too large, the fin width at the end of the heat exchange fin 31 is relatively large, and the effect of matching with the wind field flow rate cannot be achieved. If the end tangent angle α2 of the first side contour line 311 is too small, the fin width at the end of the heat exchange fin 31 is relatively small, resulting in poor heat exchange performance at the end of the heat exchange fin 31.

[0097] Therefore, in this embodiment, the end tangent angle α2 of the first side contour line 311 is further set to 60-120 degrees, and the end tangent angle α2 of the first side contour line 311 is smaller than the opening angle α1 of the first side contour line 311. Further, the ratio of the end tangent angle α2 of the first side contour line 311 to the opening angle α1 can be set to 0.7-0.85. In the above manner, the fin width at the end of the first side contour line 311 can meet the wind field flow rate matching requirements and ensure high heat exchange performance.

[0098] Further, the first side contour line 311 is set to be located in the area defined by the line connecting the vertex S8 of the end tangent angle α2 and the two end points S4 and S7 of the first side contour line 311 and the line connecting the vertex S1 of the opening angle α1 and the two end points S4 and S7 of the first side contour line 311, and the angle between the tangent of the first side contour line 311 and the straight line l3 where the peak width of the heat exchange fin 31 is located gradually decreases in the direction from the middle area to the end area. Among them, the specific line type of the first side contour line 311 can be formed by one or more combinations of arcs, straight line segments, elliptical curves, circular arcs, spline curves, cycloid segments, etc., and the number of each type of line can be one or more. In the above manner, the first side contour line 311 can have a reasonable bending shape, and a reasonable fin width change law can be obtained when it is translated and overlapped with the second side contour line 312 along the straight line l3 where the peak width is located. It is worth noting that the first side contour line 311 being located within the above region includes the situation where the first side contour line 311 coincides with the edge of the above region. Figure 2 In the figure, the straight line segments S3-S4, S6-S7 of the first side contour line 311 coincide with the line connecting the end points S4, S7 and the vertex S8.

[0099] 2. Variation of fin width

[0100] As described above, the fin width of the heat exchange fin 31 gradually decreases in the direction from the middle area of ​​the heat exchange fin 31 to the end areas on both sides of the middle area, thereby cooperating with the high velocity area and the low velocity area of ​​the air flow wind field to improve the overall heat exchange performance of the heat exchange fin 31. However, in the direction from the middle area to the end area, if the change range of the fin width of the heat exchange fin 31 is too small, the effect of coordinating with the wind field flow rate cannot be achieved. If the change range of the fin width of the heat exchange fin 31 is too large, the fin width at the end of the heat exchange fin 31 is relatively small, resulting in poor heat exchange performance at the end of the heat exchange fin 31.

[0101] Therefore, in this embodiment, the variation rule of the fin width of the heat exchange fin 31 in the direction from the middle area to the end area is further optimized. Specifically, there are reference points E11 and E12 on the first side contour line 311. The vertical distance from the reference point E11 to the straight line l3 where the peak width of the heat exchange fin 31 is located is 25% of the overall height H1 of the heat exchange fin 31, and the vertical distance from the reference point E12 to the straight line l3 where the peak width of the heat exchange fin 31 is located is 45% of the overall height H1 of the heat exchange fin 31. The fin width W1 at the reference point E11 is equal to the peak width W1 of the heat exchange fin 31. max The ratio of the fin width W2 at the reference point E12 to the peak width W of the heat exchange fin 31 is 0.64-0.96. max The ratio is 0.54-0.80, and the fin width W2 at the reference point E12 is smaller than the fin width W1 at the reference point E11.

[0102] Optionally, in a specific embodiment, the fin width W1 at the reference point E11 is equal to the peak width W of the heat exchange fin 31. max The ratio of the fin width W2 at the reference point E12 to the peak width W of the heat exchange fin 31 is 0.75-0.85. max The ratio is 0.60-0.70.

[0103] Optionally, in a specific embodiment, the ratio of the fin width W2 at the reference point E12 to the fin width W1 at the reference point E11 is 0.70-0.90.

[0104] Optionally, in a specific embodiment, there is a reference point E13 on the first side contour line 311, and the vertical distance from the reference point E13 to the straight line l3 where the peak width of the heat exchange fin 31 is located is 35% of the overall height H1 of the heat exchange fin 31. The fin width W3 at the reference point E13 is equal to the peak width W of the heat exchange fin 31. max The ratio is 0.60-0.89, and the fin width W3 at the reference point E13 is smaller than the fin width W1 at the reference point E11, and larger than the fin width W2 at the reference point E12.

[0105] Optionally, in a specific embodiment, the ratio of the fin width W3 at the reference point E13 to the fin width W1 at the reference point E11 is 0.85-0.95, and the ratio of the fin width W2 at the reference point E12 to the fin width W3 at the reference point E13 is 0.85-0.95.

[0106] Through the above-mentioned method, the variation rule of the fin width of the heat exchange fin 31 can not only meet the wind field flow velocity matching requirements, but also ensure that the end of the heat exchange fin 31 has a higher heat exchange performance.

[0107] Optionally, in a specific embodiment, the peak width W of the heat exchange fin 31 is max The perpendicular midline of the heat exchange fin 31 forms intersections E6 and E7 with the first side contour line 311, and the straight-line distance d6 between the intersections E6 and E7 is the sum of the vertical distances from the intersections E6 and E7 to the straight line l3 where the peak width is located. The ratio of the straight-line distance d6 to the overall height H1 of the heat exchange fin 31 is 0.46-0.56. The above method can ensure the smoothness of the airflow at the end of the heat exchange fin 31.

[0108] 3. Contour line type

[0109] See also Figure 2 The first side contour line 311 adopts a line type combination of at least two arc segments and at least one straight line segment sequentially connected in the direction from the middle area to the end area of ​​the heat exchange fin 31 on both sides of the straight line l3 where the peak width of the heat exchange fin 31 is located. The curvature radius of the at least two arc segments gradually increases in the direction from the middle area to the end area.

[0110] Specifically, in this embodiment, the upper half of the first side contour line 311 located on the upper side of the straight line l3 where the peak width is located includes arc segments S1-S2, arc segments S2-S3 and straight line segments S3-S4 that are sequentially connected in the direction from the middle area to the end area. The lower half of the first side contour line 311 located on the lower side of the straight line l3 where the peak width is located includes arc segments S1-S5, arc segments S5-S6 and straight line segments S6-S7 that are sequentially connected in the direction from the middle area to the end area. Among them, the radius of curvature of the arc segment S2-S3 is greater than the radius of curvature of the arc segment S1-S2, and the radius of curvature of the arc segment S5-S6 is greater than the radius of curvature of the arc segment S1-S5. It is worth noting that the "sequential connection" mentioned in this application includes direct connection or transition connection through other lines.

[0111] Through the above-mentioned method, by sequentially connecting arc segments S1-S2 and arc segments S2-S3 and sequentially connecting arc segments S1-S5 and arc segments S5-S6, the first side contour line 311 has a greater degree of curvature, ensuring the depth of the heat exchange fin 31 along the straight line l3 where the peak width is located. At the same time, through the straight line segments S3-S4 and the straight line segments S6-S7, the end tangent angle α2 of the first side contour line 311 will not be too small, ensuring the heat exchange performance of the end of the heat exchange fin 31.

[0112] Further, in this embodiment, the arc segments S1-S2, arc segments S2-S3 and straight line segments S3-S4 on the upper side of the straight line l3 where the peak width is located and the arc segments S1-S5, arc segments S5-S6 and straight line segments S6-S7 on the lower side of the straight line l3 where the peak width is located are arranged symmetrically with the straight line l3 where the peak width is located as the axis of symmetry. In other embodiments, an asymmetrical arrangement may also be adopted. In addition, in other embodiments, the number of arc segments and straight line segments may be changed as needed, and is not limited to Figure 2 The quantity shown in .

[0113] In this embodiment, in the direction from the middle area to the end area, the angles between the tangents of arc segment S1-S2 and arc segment S2-S3, arc segment S1-S5 and arc segment S2-S4 and the straight line l3 where the peak width is located gradually decreases, thereby ensuring that the first side contour line 311 bends in a direction away from the second side contour line 312, while facilitating the discharge of condensed water.

[0114] Furthermore, the ratio of the radius of curvature of arc segment S1-S2 to the radius of curvature of arc segment S2-S3 and the ratio of the radius of curvature of arc segment S1-S5 to the radius of curvature of arc segment S5-S6 are 0.24-0.29, and the ratio of the arc length of arc segment S1-S2 to the arc length of arc segment S2-S3 and the ratio of the arc length of arc segment S1-S5 to the arc length of arc segment S5-S6 are 1.1-1.35, thereby optimizing the depth and the end tangent angle α2 of the heat exchange fin 31.

[0115] Furthermore, the arc segments S1-S2, S2-S3, S1-S5, and S5-S6 are circular arcs, and the arc segments S1-S2 and S1-S5 are directly connected and arranged in a circle to facilitate the arrangement of the tube holes.

[0116] Furthermore, arc segment S2-S3 is directly connected to arc segment S1-S2 and straight line segment S3-S4, and is tangent to arc segment S1-S2 and straight line segment S3-S4 at the connection point, and arc segment S5-S6 is directly connected to arc segment S1-S5 and straight line segment S6-S7, and is tangent to arc segment S1-S5 and straight line segment S6-S7 at the connection point. In the above manner, the continuity of the first side contour line 311 can be ensured, which is convenient for punching and cutting.

[0117] Further, the upper half of the second side contour line 312 located above the straight line l3 where the peak width is located includes arc segments S1'-S2', arc segments S2'-S3' and straight line segments S3'-S4' that are sequentially connected in the direction from the middle area to the end area. The lower half of the second side contour line 312 located below the straight line l3 where the peak width is located includes arc segments S1'-S5', arc segments S5'-S6' and straight line segments S6'-S7' that are sequentially connected in the direction from the middle area to the end area.

[0118] After the first side contour line 311 is translated along the straight line l3 where the peak width is located, the arc segments S1-S2, S2-S3, S1-S5, S5-S6 of the first side contour line 311 can respectively coincide with the arc segments S1'-S2', S2'-S3', S1'-S5', S5'-S6' on the second side contour line 312, and the straight line segments S3-S4, S6-S7 on the first side contour line can respectively coincide at least partially with the straight line segments S3'-S4', S6'-S7' on the second side contour line, so as to maximize the utilization of materials, thereby saving materials and reducing production costs.

[0119] Optionally, in a specific embodiment, the straight line segments S3'-S4' and S6'-S7' on the second side contour line respectively form a cut angle with the end contour line of the corresponding side, so that the heat exchange fins 31 are not prone to flipping at the corners, which affects the heat exchange effect, and can also avoid scratches during the assembly process of the heat exchanger 30.

[0120] Further, in this embodiment, the reference point E11 is located on the arc segment S2-S3 of the first side contour line 311, the reference point E12 is located on the straight line segment S3-S4 of the first side contour line 311, the reference point E13 is located on the straight line segment S3-S4 of the first side contour line 311, the intersection of the straight line where the fin width at the reference point E11 and the second side contour line 312 is located on the arc segment S1'-S2' of the second side contour line 312, the intersection of the straight line where the fin width at the reference point E12 and the second side contour line is located on the straight line segment S3'-S4' of the second side contour line 312, and the intersection of the straight line where the fin width at the reference point E13 and the second side contour line 312 is located on the arc segment S2'-S3' of the second side contour line 312. In the above manner, while the fin width variation law of the heat exchange fin 31 meets the above requirements, the depth of the heat exchange fin 31 on the straight line l3 where the peak width is located is ensured.

[0121] Furthermore, in this embodiment, the peak width W of the heat exchange fin 31 is maxThe intersection points E6 and E7 formed by the mid-perpendicular line and the first side contour line 311 are respectively located in the arc segments S2 - S3 and S5 - S6 of the first side contour line 311 , thereby ensuring the smoothness of the airflow at the end of the heat exchange fin 31 .

[0122] Further reading Figure 4a and 4b The flow velocity distribution diagram of this embodiment and the flow velocity distribution diagram of the comparative example are shown. Figure 4a and Figure 4b The flow velocity distribution diagrams are respectively shown when the heat exchange fins 31 of this embodiment and the heat exchange fins of the comparative example are used, after the heat exchanger 30 is away from the fan 22. Figure 4a The heat exchange fins 31 of this embodiment are used. Figure 4b The comparative heat exchange fin adopts a three-arc type, and includes three arcs connected in sequence from the middle area to the end area on both sides of the straight line where the peak width is located, and the curvature radius of the arc gradually increases. Therefore, the opening angle of the leeward side profile of the comparative heat exchange fin, the end tangent angle, and the end fin width are respectively smaller than those of the present embodiment. Figure 4a and Figure 4b From the comparison results, it can be found that the area of ​​the low wind speed zone in the middle area of ​​the heat exchange fin 31 of this embodiment away from the fan 22 is significantly smaller than that of the heat exchange fin of the comparative example, the flow velocity uniformity is significantly improved, and the heat exchange performance is significantly improved.

[0123] 4. Hole arrangement

[0124] See also Figure 5 , Figure 5 exist Figure 2 The heat exchange fin 31 shown further has tube holes 316 , so that the heat exchange tubes 32 can be passed through the heat exchange fin 31 .

[0125] like Figure 5 As shown, the tube holes 316 on the heat exchange fins 31 are arranged in rows. Specifically, in this embodiment, each row of tube holes 316 is arranged at intervals along an arrangement curve formed by translating the first side contour line 311 or the second side contour line 312 along the straight line l3 where the peak width is located, and the ratio of the shortest distance from the center of each tube hole 316 in each row of tube holes 316 to the corresponding arrangement curve to the radius of the tube hole 316 is less than or equal to 1.5.

[0126] Furthermore, the sum of the shortest distances from the center of each tube hole 316 in each row of tube holes 316 to the corresponding arrangement curve is less than the sum of the shortest distances from the center of each tube hole 316 in each row of tube holes 316 to other translation curves formed after translation of the first side contour line 311 or the second side contour line 312.

[0127] Furthermore, the tube holes 316 of different rows are arranged at intervals along an arrangement straight line parallel to the straight line l3 where the peak width of the heat exchange fins 31 is located.

[0128] By the above method, the direction of each row of tube holes 316 is substantially the same as the direction of the first side contour line 311 or the second side contour line 312, so as to fully utilize the surface space of the heat exchange fins 31 and improve the overall heat exchange performance of the heat exchanger 30. In other embodiments, the tube holes 316 may also be arranged in other ways.

[0129] In this embodiment, in the spacing direction between the first side contour line 311 and the second side contour line 312, the number of rows of the tube holes 316 in the middle region is greater than the number of rows of the tube holes 316 in the end region. Figure 5 In the embodiment, the number of rows of the tube holes 316 in the middle region is three rows, and the number of rows of the tube holes 316 in the end region is two rows. In other embodiments, the number of rows of the tube holes 316 in the middle region can be four rows, and the number of rows of the tube holes 316 in the end region can be two rows, or the number of rows of the tube holes 316 in the middle region can be three rows, and the number of rows of the tube holes 316 in the end region can be one row. The present application does not specifically limit the number of rows of the tube holes 316 in the middle region and the number of rows of the tube holes 316 in the end region.

[0130] Furthermore, in this embodiment, the height H3 of the middle region where the number of rows of the tube holes 316 is relatively high is set to 25%-50% of the overall height H1 of the heat exchange fin 31 .

[0131] like Figure 5 As shown, the boundary line between the middle area and the end area is to take the tube holes 316 in the middle area and the tube holes 316 in the end area that are adjacent to each other in a row of tube holes 316 close to the first side contour line 311, and connect the centers of the tube holes of the two. Further, a parallel line parallel to the straight line l3 where the peak width is located is drawn along the midpoint of the line connecting the centers of the tube holes, and then two parallel lines l5 and l6 are obtained on both sides of the straight line l3 where the peak width is located. The parallel lines l5 and l6 are the boundary lines between the middle area and the end area. The distance H3 between the parallel lines l5 and l6 in the direction perpendicular to the straight line l3 where the peak width is located is the height of the middle area.

[0132] Through the above method, the number of rows of tube holes 361 in the middle area is set to be greater than the number of rows of tube holes 361 in the end area, and the height H3 of the middle area and the overall height H1 of the heat exchange fins 31 are set within a reasonable range, which can enable the heat exchange fins 31 to better match the high flow velocity area and the low flow velocity area of ​​the wind field to achieve a better heat exchange effect.

[0133] Optionally, in a specific embodiment, the height H3 of the middle region may be set to 30%-45% of the overall height H1 of the heat exchange fin 31 .

[0134] Further integration Figure 2 Optionally, in a specific embodiment, the ratio of the height H3 of the middle area to the straight-line distance d6 between the intersection E6 and the intersection E7 is set to 0.60-0.80, and the ratio of the straight-line distance d6 between the intersection E6 and the intersection E7 to the overall height H1 of the heat exchange fin 31 is 0.46-0.56. In the above manner, while ensuring the smoothness of the airflow of the heat exchange fin 31, a better heat exchange effect can be achieved.

[0135] Furthermore, the intersection points E18, E19 of the parallel lines l5 and l6 used as the dividing lines between the middle area and the end area with the first side contour line 311 and the intersection points E20, E21 of the second side contour line 312 are respectively located on the arc segments S2-S3, S5-S6 of the first side contour line 311 and the arc segments S2'-S3', S5'-S6' of the second side contour line 312, and the intersection point E18 of the parallel lines l5 and l6 with the first side contour line 31 is located on the side of the reference point E11 and the intersection point E6 close to the straight line l3 where the peak width is located. In this way, the fin area corresponding to the arc segment S1-S2 with a relatively large curvature is fully utilized as the middle area of ​​the heat exchange fin 31, ensuring that the middle area has sufficient fin width.

[0136] Further, in this embodiment, the fin width of the middle region is set to K1×n1×D, and the fin width of the end region is set to K2×n2×D, wherein n1 and n2 are the number of rows of tube holes 316 in the middle region and the end region, respectively, D is the distance between the end tube holes, and K1 and K2 are coefficients of variation, ranging from 0.8 to 1.2.

[0137] The end tube hole row spacing D refers to selecting the tube hole 316 closest to the end contour line 314 or 315 in a row of tube holes 316 close to the first side contour line 311, and drawing a straight line through the center E14 of the tube hole 316. The straight line and the first side contour line 311 and the second side contour line 312 or the extension of the two are compared with the intersection points E15 and E16, and the straight line is the normal line at the intersection point E15. When the number of rows of tube holes 316 in the end area is 2 or more ( Figure 5The straight line further intersects with the arrangement curve of an adjacent row of tube holes 316 or the extension of the arrangement curve at the intersection E17. At this time, the end tube hole row spacing D is the straight line distance between the tube hole center E14 of the selected tube hole 316 and the intersection E17. When the number of tube holes 316 rows in the end area is 1 row, the end tube hole row spacing D is the straight line distance between the intersections E15 and E16. The above method can ensure that each heat exchange tube 32 inserted into the tube hole 316 can exert the best heat exchange performance.

[0138] Optionally, in a specific embodiment, the ratio of the radius of the tube hole 316 to the distance D between the end tube hole rows is 0.23-0.29, thereby further ensuring that each heat exchange tube 32 can exert the best heat exchange performance.

[0139] The shortest distance H4 from the center of the tube hole 316 closest to the end contour lines 314, 315 to the end contour lines 314, 315 is 0.25×D-0.75×D, where D is the above-mentioned end tube hole row spacing.

[0140] Furthermore, in this embodiment, the shortest distance H4 from the center of the tube hole 316 closest to the end contour lines 314, 315 to the end contour lines 314, 315 is set to 0.4-0.6 of the end tube hole row spacing D. In this way, not only is it easy to fully exert the heat exchange performance of the heat exchange tube 32 inserted into the tube hole 316 closest to the end contour lines 314, 315, but it can also avoid damaging the heat exchange tube 32 during the assembly process.

[0141] 5. Surface structure

[0142] See also Figure 6 , Figure 6 exist Figure 5 The heat exchange fin 31 shown in the figure further shows a variety of surface structures. The surface structure of the heat exchange fin 31 will be optimized in the following aspects:

[0143] 5.1. Heat transfer enhancement structure

[0144] like Figure 6 As shown, in this embodiment, a plurality of heat transfer enhancement structures are provided on the heat exchange fin 31, and are specifically bridge plate groups 317. Each bridge plate group 317 includes at least one bridge plate 3171. The specific shape of the bridge plate 3171 is as follows: Figure 7 As shown, it includes two side walls 3171a bent relative to the heat exchange fins 31 and opposite to each other, and a top wall 3171b bridging the two side walls 3171a. Each bridge fin 3171 serves as a heat transfer enhancement unit. The main function of the bridge fin group 317 is to destroy the flow boundary layer, improve the heat transfer coefficient on the air side of the heat exchange fins 31, and thus achieve heat transfer enhancement.

[0145] As described above, the fin width of the heat exchange fin 31 of the present embodiment gradually decreases in the direction from the middle region of the heat exchange fin 31 to the end regions on both sides of the middle region, and further, the number of rows of tube holes 316 in the middle region is greater than the number of rows of tube holes 316 in the end regions. When the heat exchange fin 31 and the heat exchange tube 32 are combined to form the heat exchanger 30, the heat exchange capacity of the middle region of the heat exchange fin 31 is greater than the heat exchange capacity of the end regions of the heat exchange fin 31.

[0146] Therefore, in this embodiment, the heat transfer enhancement capability of the bridge plate group 317 in the end area is set to be greater than the heat transfer enhancement capability of the bridge plate group 317 in the middle area, thereby improving the heat transfer uniformity in the middle area and the end area of ​​the heat exchange fin 31, and further improving the overall heat exchange performance of the heat exchanger 30.

[0147] Specifically, the heat transfer enhancement capability of the bridge plate group 317 is related to many parameters such as the number of bridge plates 3171 arranged per unit area, height, and width. Therefore, by differentially setting one or more of the above parameters of the bridge plates 3171 in the middle area and the end area, the heat transfer enhancement capability of the bridge plate group 317 in the end area can be greater than the heat transfer enhancement capability of the bridge plate group 317 in the middle area.

[0148] Optionally, the number of bridge pieces 3171 arranged per unit area in the end region is set to be greater than the number of bridge pieces 3171 arranged per unit area in the middle region, so that the heat transfer enhancement capability of the bridge piece group 317 in the end region is greater than the heat transfer enhancement capability of the bridge piece group 317 in the middle region. In the present application, the number of bridge pieces 3171 arranged per unit area refers to the ratio of the number of bridge pieces 3171 in the middle region or the end region to the area of ​​the middle region or the end region.

[0149] For example, Figure 6 As shown, the number of bridge fins 3171 in at least part of the bridge fin group 317 in the end region is set to be greater than the number of bridge fins 3171 in at least part of the bridge fin group 317 in the middle region, thereby making the heat transfer enhancement capability of the bridge fin group 317 in the end region greater than the heat transfer enhancement capability of the bridge fin group 317 in the middle region. Figure 6 In the embodiment, the number of bridge pieces 3171 in the bridge piece group 317 in the end region is three or four, and the number of bridge pieces 3171 in the bridge piece group 317 in the middle region is two or three. Of course, in other embodiments, the number of bridge pieces 3171 in the bridge piece group 317 can be set according to actual conditions, and this application does not make specific limitations.

[0150] Further, in this embodiment, the second side contour line 312 is used as the windward side contour line, and the first side contour line 311 is used as the leeward side contour line. In the process of airflow being transmitted from the second side contour line 312 to the first side contour line 311, the flow velocity is continuously reduced, and heat is continuously exchanged with the heat exchange fins 31, resulting in a gradual decrease in the temperature difference between the airflow and the heat exchange fins 31, thereby making the heat exchange capacity of the heat exchange fins 31 in the area close to the first side contour line 311 lower than the heat exchange capacity in the area close to the second side contour line 312. Therefore, the heat transfer enhancement capacity of the bridge plate group 317 close to the second side contour line 312 can be further set to be smaller than the heat transfer enhancement capacity of the bridge plate group 317 close to the first side contour line 311, thereby improving the heat exchange uniformity of the heat exchange fins 31 between the first side contour line 311 and the second side contour line 312. Specifically, the number of bridge pieces 3171 in at least a portion of the bridge piece group 317 near the first side contour line 311 may be set to be greater than the number of bridge pieces 3171 in at least a portion of the bridge piece group 317 near the second side contour line 312. Figure 6 In the middle area of ​​the heat exchange fin 31, the number of bridge fins 3171 in the bridge fin group 317 close to the second side contour line 312 is two, and the number of bridge fins 3171 in the bridge fin group 317 close to the first side contour line 311 is three. Of course, in other embodiments, the second side contour line 312 can also be used as the leeward side contour line, and the first side contour line 311 can be used as the windward side contour line. In this case, the specific arrangement of the bridge fin group 317 also needs to be adjusted accordingly.

[0151] Furthermore, during the refrigeration process, when the airflow flows through the surface of the heat exchange fin 31, the water vapor in the airflow will condense when it encounters cold, generating condensed water. The condensed water flows downward along the heat exchange fin 31 under the action of gravity, and the amount of water will gradually increase along the flow direction. Therefore, in this embodiment, the drainage capacity of the bridge plate group 317 in the lower end region can be further set to be greater than the drainage capacity of the bridge plate group 317 in the upper end region, so as to reduce the drainage difficulty of the lower end of the heat exchange fin 31, make the drainage smoother, and thus improve the heat exchange effect of the lower end of the heat exchange fin 31.

[0152] Specifically, the drainage capacity of the bridge plate group 317 is also related to many parameters such as the number of bridge plates 3171 arranged per unit area, height and width. Therefore, by differentially setting one or more of the above parameters of the bridge plates 3171 in the upper end area and the lower end area, the drainage capacity of the bridge plate group 317 in the lower end area can be greater than the drainage capacity of the bridge plate group 317 in the upper end area.

[0153] Optionally, the number of bridge pieces 3171 arranged per unit area in the lower end region is set to be smaller than the number of bridge pieces 3171 arranged per unit area in the upper end region, thereby making the drainage capacity of the bridge piece group 317 in the lower end region greater than the drainage capacity of the bridge piece group 317 in the upper end region.

[0154] For example, Figure 6 As shown, the number of bridge pieces 3171 in at least part of the bridge piece group 317 in the lower end region is set to be smaller than the number of bridge pieces 3171 in at least part of the bridge piece group 317 in the upper end region, thereby making the drainage capacity of the bridge piece group 317 in the lower end region greater than the drainage capacity of the bridge piece group 317 in the upper end region. Figure 6 In the embodiment, the number of bridge fins 3171 in the bridge fin group 317 in the upper end region is four, and the number of bridge fins 3171 in the bridge fin group 317 in the lower end region is three. Of course, in other embodiments, the number of bridge fins 3171 in the bridge fin group 317 can be set according to actual conditions, and this application does not make specific limitations. In other embodiments, the bridge fin group 317 can be replaced by other heat transfer enhancement structures, such as the vortex generator, louver, and other various structures protruding relative to the heat exchange fins 31 described below.

[0155] 5.2. Thermal insulation structure

[0156] In this embodiment, the number of rows of the tube holes 316 on the heat exchange fins 31 is at least two rows, specifically, three rows in the middle area and two rows in the end area.

[0157] The heat exchange fins 31 are further provided with a plurality of row heat insulation structures 318, 319 in a row, and each row of heat insulation structures 318, 319 is provided between two adjacent rows of tube holes 316. The main function of the row heat insulation structures 318, 319 is to prevent the heat exchange tubes 32 inserted into two adjacent rows of tube holes 316 from being heated in series with each other.

[0158] As described above, the fin width of the heat exchange fin 31 of the present embodiment gradually decreases in the direction from the middle region of the heat exchange fin 31 to the end regions on both sides of the middle region, and further, the number of rows of tube holes 316 in the middle region is greater than the number of rows of tube holes 316 in the end regions. When the heat exchange fin 31 and the heat exchange tube 32 are combined to form the heat exchanger 30, the wind resistance in the middle region of the heat exchange fin 31 is greater than the wind resistance in the end regions of the heat exchange fin 31.

[0159] Therefore, in this embodiment, the wind resistance of the row insulation structure 318 in the middle area is set to be smaller than the wind resistance of the row insulation structure 319 in the end area, which can balance the wind resistance in the middle area and the end area and improve the overall heat exchange performance of the heat exchange fins 31.

[0160] Specifically, the wind resistance of the row insulation structures 318 and 319 is mainly related to parameters such as the height and width of the row insulation structures 318 and 319. Therefore, by adjusting one or more of the above parameters, the wind resistance of the row insulation structure 318 in the middle area can be made smaller than the wind resistance of the row insulation structure 319 in the end area.

[0161] For example, the height of the row of thermal insulation structures 318 in the middle region can be set to be smaller than the height of the row of thermal insulation structures 319 in the end region, and / or the width of the row of thermal insulation structures 318 in the middle region can be set to be smaller than the width of the row of thermal insulation structures 319 in the end region.

[0162] In this embodiment, the row insulation structure 318 in the middle area is a slit, and the row insulation structure 319 in the end area is a louver. The specific structure of the louver is as follows: Figure 7 The shutter is mainly formed by cutting the heat exchange fins 31 and is a strip area folded relative to the heat exchange fins 31 .

[0163] Furthermore, since the second side contour line 312 is bent toward the direction of the first side contour line 311, and the first side contour line 311 is bent away from the second side contour line 312, the curvature of the middle area is relatively large and there is a process of reverse change of the slope, so the flow rate of the condensed water in the middle area is relatively slow, and the condensed water flow rate in the middle area can be increased by setting the row insulation structure 318 in the middle area as a slit. In addition, by setting the row insulation structure 319 in the end area as a louver, an additional turbulence effect can be provided, thereby enhancing the heat transfer in the end area.

[0164] In other embodiments, the rows of heat-insulating structures 318 and 319 in the middle area and the end area may both be configured as shutters, or both be configured as slits, which is not specifically limited in the embodiments of the present application.

[0165] Furthermore, in order to improve the smoothness of drainage, the drainage capacity of the row insulation structure 319 in the lower end area can be set to be greater than the drainage capacity of the row insulation structure 319 in the upper end area, so that the drainage is smoother and the heat exchange effect of the lower end area of ​​the heat exchange fin 31 can be improved.

[0166] Specifically, since the height and width of the row insulation structure 319 will affect the drainage capacity, in this embodiment, the height of the row insulation structure 319 in the lower end region is set to be smaller than the height of the row insulation structure 319 in the upper end region, and\or the width of the row insulation structure 319 in the lower end region is set to be smaller than the width of the row insulation structure 319 in the upper end region, so as to enhance the drainage capacity in the lower end region.

[0167] Further, as described above, in this embodiment, the second side profile line 312 is used as the windward side profile line, and the first side profile line 311 is used as the leeward side profile line. The heat transfer capacity of the heat transfer fins 31 near the first side profile line 311 is lower than that in the region near the second side profile line 312. Therefore, in the direction from the second side profile line 312 to the first side profile line 311, the row spacing of the row insulation structure 318 or 319 is set to gradually increase. In this way, the heat transfer efficiency of the heat transfer tubes 32 near the leeward side can be enhanced.

[0168] In this application, in the direction from the second side profile line 312 to the first side profile line 311, when the number of rows of the tube holes 316 on the heat transfer fins 31 is two rows, the row spacing of the row insulation structure 318 or 319 refers to the spacing distance between the row insulation structure 318 or 319 and the adjacent first side profile line 311 and second side profile line 312. When the number of rows of the tube holes 316 on the heat transfer fins 31 is at least three rows, the row spacing of the row insulation structure 318 or 319 further includes the spacing distance between two adjacent row insulation structures 318 or 319.

[0169] For example, as Figure 6 shown, in this embodiment, in the middle region of the heat transfer fins 31, the number of rows of the tube holes 316 is three rows. The row spacing of the row insulation structure 318 respectively includes the distance d9 between the row insulation structure 318 near the second side profile line 312 and the second side profile line 312, the spacing distance d10 between two row insulation structures 318, and the spacing distance d11 between the row insulation structure 318 near the first side profile line 311 and the first side profile line 312, where d9 < d10 < d11. In the end region of the heat transfer fins 31, the number of rows of the tube holes 316 is two rows. The row spacing of the row insulation structure 319 respectively includes the spacing distance d12 between the row insulation structure 319 and the second side profile line 312, and the distance d13 between the row insulation structure 319 and the first side profile line 311, where d12 < d13. Further, the second side profile line 312 is used as the leeward side profile line, and the first side profile line 311 is used as the windward side profile line. At this time, the row spacing of the row insulation structure 318 or 319 needs to be adjusted accordingly.

[0170] Further, as Figure 6As shown, the heat exchange fin 31 is further provided with an inner-row heat insulation structure 320, which is provided between two tube holes 316 located in the middle region and in the end region and adjacent to each other in a row of tube holes 316 close to the second side contour line 312. By providing the inner-row heat insulation structure 320 at the junction of the middle region and the end region, the mutual heat exchange between adjacent heat exchange tubes 32 in the middle region and the end region can be avoided, thereby improving the overall heat exchange performance of the heat exchanger 30.

[0171] 5.3. End reinforcement

[0172] Furthermore, if Figure 6 As shown, the heat exchange fin 31 is provided with an end reinforcement rib 321, which is arranged between the tube hole 316 close to the end contour line 314 or 315 and the end contour line 314 or 315 to enhance the strength of the end of the heat exchange fin 31 and avoid curling.

[0173] Furthermore, in this embodiment, the end reinforcement rib 321 is arranged in a long strip shape, and the length direction of the end reinforcement rib 321 is arranged along the radial direction of the tube hole 316 close to the end contour line 314 or 315, and points to the position point where the distance between the end contour line 314 or 315 and the center of the tube hole 316 close to the end contour line 314 or 315 is the largest.

[0174] Specifically, in this embodiment, the tube hole 316 closest to the end contour line 314 or 315 is the tube hole 316 adjacent to the end contour line 314 or 315 and the second side contour line 312, and the position point with the greatest distance from the tube hole 316 is the position of the cut angle between the end contour line 314 or 315 and the second side contour line 312. The extending direction of the long strip end reinforcing rib 321 is arranged along the direction of the line connecting the center of the tube hole 316 and the cut angle, so as to enhance the strength of the end farthest from the tube hole 316.

[0175] The end reinforcement rib 321 can be set as an integral structure with the heat exchange fin 31 , and the end reinforcement rib 321 can be formed on the surface of the heat exchange fin 31 by stamping to simplify the connection method of the end reinforcement rib 321 .

[0176] Optionally, the protruding direction of the end reinforcement rib 321 relative to the heat exchange fin 31 can be set to be the same as the protruding direction of the above-mentioned heat transfer enhancement structure and heat insulation structure relative to the heat exchange fin 31, so as to improve the production efficiency of the heat exchange fin through one-time stamping.

[0177] Further, in a specific embodiment, the width of the end reinforcement rib 321 is 0.3-1.5mm, and the length is 2mm-10mm. In other specific embodiments, the width of the end reinforcement rib 321 can be 0.3mm, 0.5mm, 0.8mm, 1mm, 1.25mm, and 1.5mm, etc., and the length can be 2mm, 2.5mm, 3mm, 3.5mm, 4mm, 4.5mm, 5mm, 5.5mm, 6mm, 6.5mm, 7mm, 7.5mm, 8mm, 8.5mm, 9mm, 9.5mm, and 10mm, etc., which can be flexibly set according to the distance between the tube hole 316 and the end contour lines 314 and 315 and the thickness of the heat exchange fin 31, and the present application does not make specific restrictions.

[0178] 5.4. Vortex generator

[0179] Further combined with 6- Fig.10 As shown, a vortex generator is also provided on the heat exchange fin 31, and the vortex generator is used to form a vortex in the airflow flowing in from the windward side of the heat exchange tube 32 under the action of the vortex generator, thereby reducing the area of ​​the wake zone on the leeward side of the heat exchange tube 32.

[0180] Specifically, when the air flows through the heat exchange tube 32, separation will occur on the leeward side of the heat exchange tube 32 to form a larger wake area, and the heat transfer performance of the wake area is poor.

[0181] Therefore, in this embodiment, one or at least two vortex generators can be arranged on the periphery of the heat exchange tube 32 along the air flow direction to suppress the separation of air on the leeward side of the heat exchange tube 32, reduce the area of ​​the wake region, and improve the heat transfer performance on the leeward side of the heat exchange tube 32, thereby improving the overall heat transfer performance of the heat exchanger 30.

[0182] Optionally, in a specific embodiment, the vortex generator is a convex hump 322 integrally formed with the heat exchange fin 31 and protruding relative to the heat exchange fin 31. The specific shape of the convex hump 322 is as follows: Figure 7-8 As shown. When the airflow flows over the surface of the convex hull 322, horseshoe vortices, transverse vortices, longitudinal vortices, mixed vortices, and even complex secondary vortices are formed, so that the local Nusselt number (Nu) downstream of the convex hull 322 is enhanced, which promotes the heat transfer enhancement of the downstream heat exchange fins 31. The existence of the convex hull 322 improves the coordination degree of the velocity and temperature gradient, so that under the same Reynolds number (Reynolds number), the coordination angle of the heat exchange fin 31 with the convex hull 322 is lower than that of the flat sheet without the convex hull 322, and the heat transfer coefficient is higher than that of the flat sheet, so as to improve the heat transfer performance of the leeward side of the heat exchange tube 32, thereby improving the overall heat transfer performance of the heat exchanger 30.

[0183] Optionally, in a specific embodiment, the bulge 322 can be formed by stamping, and the protruding direction of the bulge 322 relative to the surface of the heat exchange fin 31 can be set to be the same as the protruding direction of the heat transfer enhancement structure, the heat insulation structure and the end reinforcement rib 320 relative to the surface of the heat exchange fin 31, so as to facilitate the simultaneous formation of the above-mentioned structures located on the heat exchange fin 31 by one-time stamping, thereby greatly simplifying the production process of the heat exchange fin 31 and improving the production efficiency of the heat exchange fin 31.

[0184] Optionally, in a specific embodiment, the protruding direction of the convex bump 322 relative to the surface of the heat exchange fin 31 may be set to be different from the protruding direction of the above structure.

[0185] Optionally, in a specific embodiment, a portion of the convex bumps 322 may be configured to protrude toward one side of the heat exchange fin 31 , and another portion of the convex bumps 322 may be configured to protrude toward the other side of the heat exchange fin 31 , so that the heat exchange enhancement effects on both sides of the heat exchange fin 31 are consistent.

[0186] Optionally, in a specific embodiment, other production processes may be used to form the convex bumps 322 on the surface of the heat exchange fins 31, which is not specifically limited in the present application.

[0187] Furthermore, when the convex hump 322 is arranged on the windward side of the heat exchange tube 32, the heat exchange enhancement effect of the convex hump 322 on the heat exchange fin 31 is significantly weaker than that when the convex hump 322 is arranged on the leeward side of the heat exchange tube 32, and the pressure drop level on the windward side is greater than that on the leeward side. Figure 8 As shown, the convex hump 322 is arranged on the leeward side of the heat exchange tube 32. Furthermore, the convex hump 322 is further arranged in a fan-shaped area with the center of the tube hole 316 as the vertex and facing the leeward side of the heat exchange tube 32, and the angles between the two sides of the fan-shaped area and the air inlet direction D4 of the heat exchange tube 32 are 45 degrees respectively, so as to improve the heat exchange effect on the leeward side of the heat exchange tube 32 and improve the overall heat exchange performance of the heat exchanger 30.

[0188] Specifically, in one embodiment, the air inlet direction D4 of the heat exchange tube 32 may be horizontal, and the fan-shaped area is an area on the upper and lower sides with an angle of 45 degrees with the horizontal direction. In other embodiments, the air inlet direction D4 of the heat exchange tube 32 may also have an angle with the horizontal direction.

[0189] Furthermore, in a specific embodiment, when the heat exchange tube 32 is a circular tube, the ratio of the distance between the convex hump 322 and the heat exchange tube 32 to the diameter of the heat exchange tube 32 can be set to 0.3-1.0.

[0190] Furthermore, the convex hump 322 is a kind of the above-mentioned heat transfer enhancement structure. When the fluid flows through the convex hump 322, a horseshoe-shaped vortex is formed in the front half of the convex hump 322, and a transverse vortex is formed in the rear half of the convex hump 322. The convex hump 322 will generate a large shape resistance while increasing the heat exchange, so that the pressure drop of the fluid is increased. Therefore, in specific use, the number of convex hump 322 arranged on the periphery of each heat exchange tube 32 can be one or more than two. At this time, all the convex hump 322 on the periphery of each heat exchange tube 32 can be used as a heat transfer enhancement structure, and each convex hump 322 can be used as a heat transfer enhancement unit, and differentiated settings can be made with reference to the contents described above. For example, the number of convex hump 322 per unit area on the heat exchange fin 31, the height, etc. are differentiated to achieve the effects of uniform heat exchange and accelerated condensate flow described above.

[0191] Optionally, in a specific embodiment, the number of the convex bumps 322 on the rear side of each heat exchange tube 32 can be set to 2-6, and the height of the convex bumps 322 can be set to 0.8-1.2 mm.

[0192] Furthermore, since the heat transfer coefficient of the convex hump 322 is also related to the shape of the convex hump 322 , the heat transfer coefficient of the convex hump 322 can be further improved by changing the shape of the convex hump 322 .

[0193] Optionally, in a specific embodiment, the projection of the convex hull 322 on the heat exchange fin 31 is set to be elliptical, rectangular or racetrack-shaped. That is, the projection of the convex hull 322 on the heat exchange fin 31 has a long axis direction D5 and a short axis direction D6 perpendicular to the long axis direction D5, and the long axis dimension d14 of the projection of the convex hull 322 along the long axis direction D5 is greater than the short axis dimension d15 along the short axis direction D6.

[0194] At this time, the heat transfer coefficient and resistance coefficient of the convex hull 322 are related to the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hull 322. As the major axis dimension d14 of the convex hull 322 increases, the flow resistance and the Nusselt number (Nu) decrease, and the coordination of the velocity and temperature gradient deteriorates. When the minor axis dimension d15 increases, the situation is just the opposite. This is because the increase in the major axis dimension d14 of the convex hull 322 will make the shape of the convex hull 322 closer to a streamlined drag reduction shape, reduce disturbances, and reduce both heat transfer and resistance, while the increase in the minor axis dimension d15 leads to the opposite effect.

[0195] Therefore, in a specific implementation, the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hump 322 may be set between 1.2 and 1.6 to optimize the heat transfer coefficient and the resistance coefficient of the convex hump 322 .

[0196] Furthermore, since the angle between the long axis direction D5 of the convex hump 322 and the air inlet direction D4 is relatively large, the flow resistance is significantly increased, and the air flow pressure drop is significantly increased. Therefore, in a specific embodiment, the angle between the long axis direction D5 of the convex hump 322 and the air inlet direction D4 of the heat exchange tube 32 can be further set to be less than or equal to 10 degrees to reduce the air flow resistance and reduce the air pressure drop.

[0197] For example, the long axis direction D5 of the convex hull 322 may be set to be consistent with the wind inlet direction D4, that is, the angle between the two is 0 degrees. Alternatively, the angle between the long axis direction D5 and the wind inlet direction D4 may be set to 1 degree, 2 degrees, 3 degrees, 4 degrees, 5 degrees, 6 degrees, 7 degrees, 8 degrees, 9 degrees or 10 degrees, etc.

[0198] In addition, the shape of the convex hump 322 can also be set as needed. For example, the projection of the convex hump 322 on the heat exchange fin 31 can be set to a circle, a teardrop shape (with a larger radius of curvature close to the windward side), a regular or irregular polygon, etc. This application does not make specific limitations.

[0199] Optionally, in a specific embodiment, the ratio of the major axis dimension d14 of the convex hump 322 to the diameter of the heat exchange tube 32 can be set to 0.2-0.6 to enhance the flow disturbance effect of the convex hump 322 on the periphery of the heat exchange tube 32 .

[0200] Furthermore, since the number of convex hulls 322 arranged on the periphery of each heat exchange tube 32 and the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hull 322 can affect the heat transfer coefficient and the resistance coefficient of the convex hull 322, the number of convex hulls 322 located on the periphery of the same heat exchange tube 32 and the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hull 322 can also be coupled to balance the heat transfer coefficient and the resistance coefficient of the convex hull 322. Specifically, the number of convex hulls 322 is set to be negatively correlated with the ratio of the major axis dimension d14 to the minor axis dimension d15. That is, when the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hull 322 is designed to be larger, the number of convex hulls 322 can be appropriately reduced; similarly, when the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hull 322 is designed to be relatively small, the number of convex hulls 322 can be appropriately increased.

[0201] Optionally, in a specific embodiment, if Figure 9-10 As shown, the vortex generator can also be a folded piece 323 integrally formed with the heat exchange fin 31 and folded relative to the heat exchange fin 31. The specific shape of the folded piece 323 is as follows: Fig. 9 The folded sheet 323 is used to guide the airflow to flow along the gap between the folded sheet 323 and the heat exchange tube 32 toward the leeward side of the heat exchange tube 32, thereby forming a vortex.

[0202] Optionally, in a specific embodiment, the folding tab 323 can be formed by stamping, and the folding direction of the folding tab 323 relative to the surface of the heat exchange fin 31 can be set to be the same as the protruding direction of the heat transfer enhancement structure, the heat insulation structure and the end reinforcement rib 320 relative to the surface of the heat exchange fin 31, so as to form the above structures at the same time by one stamping forming, thereby greatly simplifying the production process of the heat exchange fin 31 and improving the production efficiency of the heat exchange fin 31.

[0203] In a specific embodiment, the folding direction of the folded piece 323 relative to the surface of the heat exchange fin 31 can be set to be different from the protruding direction of other surface structures. Alternatively, the folded piece 323 can be formed on the surface of the heat exchange fin 31 by other production processes, which are not specifically limited in this application.

[0204] like Fig.10 As shown, the fold 323 is connected to the heat exchange fin 31 through a connecting line 324, and the connecting line 324 is arranged around the tube hole 316 to guide the air when the air flows through the heat exchange tube 32, inhibit the separation of the air on the leeward side of the heat exchange tube 32, and reduce the area of ​​the wake region.

[0205] Furthermore, since the height of the folded piece 323 is higher, the wind resistance caused by the folded piece 323 is greater. Therefore, the height of the folded piece 323 relative to the main surface of the heat exchange fin 31 can be set to gradually increase in the direction from the windward side to the leeward side of the heat exchange tube 32, so as to reduce the wind resistance close to the windward side and enhance the turbulence effect of the folded piece 323.

[0206] Optionally, in a specific embodiment, the folding piece 323 is formed by folding an area defined by a connecting line 324 and a cutting line 325 located on a side of the connecting line 324 away from the tube hole 316 .

[0207] Specifically, if Fig.10 As shown, the cutting line 325 includes a first cutting line 3251 and a second cutting line 3252, wherein one end of the first cutting line 3251 is connected to the end point of the connecting line 324 close to the windward side of the heat exchange tube 32, and the other end of the first cutting line 3251 is connected to the other end point of the connecting line 324 close to the leeward side of the heat exchange tube 32 through the second cutting line 3252. The first cutting line 3251 and the connecting line 324 are separated from each other in the direction from the windward side to the leeward side of the heat exchange tube 32, so that the height of the folding piece 323 gradually increases in the direction from the windward side to the leeward side of the heat exchange tube 32 after the folding piece 323 is folded relative to the heat exchange fin 31.

[0208] In other embodiments, the shape of the folding piece 323 may also be other shapes, such as a triangle, a regular or irregular polygon, and the height of the folding piece 323 may also be set to be constant or have other variations.

[0209] Furthermore, since the folded sheet 323 is arranged on the windward side of the heat exchange tube 32, the pressure drop level on the windward side will be increased. Therefore, in a specific embodiment, the angle α3 between the connecting line 324 of the folded sheet 323 and the heat exchange fin 31 close to the windward side of the heat exchange tube 32 and the center of the tube hole 316 and the wind inlet direction D7 of the heat exchange tube 32 can be set to 90-110 degrees, so as to reduce the resistance on the windward side of the folded sheet 323 and reduce the pressure drop level. Furthermore, the angle α4 between the connecting line 324 of the folded sheet 323 and the heat exchange fin 31 and the center of the tube hole 316 can be set to 47-56 degrees.

[0210] Furthermore, in a specific embodiment, the connecting line 324 between the fold 323 and the heat exchange fin 31 can be set as an arc, the tube hole 316 can be set as a circular hole, and the center of the arc where the connecting line 324 is located coincides with the center of the tube hole 316, so that the fold 323 and the heat exchange tube 32 are arranged at approximately equal intervals, thereby enhancing the turbulence effect of the fold 323 on the leeward side of the heat exchange tube 32.

[0211] Optionally, in a specific embodiment, the ratio of the radius R2 of the connection line 324 between the fold 323 and the heat exchange fin 31 to the radius R1 of the tube hole 316 is 1.19-1.34, so as to further enhance the turbulence effect.

[0212] 6. Pipe diameter optimization

[0213] See also Figure 11-12 , Figure 11-12 The cross-sectional schematic diagrams of the two deformations of the heat exchanger 30 described above are shown below. Figure 11-12 The diameter of the heat exchange tube 32 is optimized in the following aspects:

[0214] 6.1 Combinations of different pipe diameters

[0215] See first Figure 5 In the heat exchanger 30 described above, on the reference cross-section formed by the plane where the main surface of the heat exchange fin 31 is located, the cross-sectional shape of the heat exchange tube 32 and the cross-sectional shape of the tube hole 316 are both circular, and the tube diameters of the tube holes 316 arranged on the heat exchange fin 31 are basically the same, so that the heat exchange tube 32 and the heat exchange fin 31 are more closely connected to facilitate heat transfer.

[0216] Since the heat exchange medium in the heat exchange tube 32 will undergo a phase change when evaporating or condensing in the heat exchange tube 32, the volume ratio of the gas phase and the liquid phase will gradually change. The volume ratio of the gas phase and the liquid phase differs by 20 to 30 times, which causes a significant change in the flow rate of the heat exchange medium in the heat exchange tube 32 of the same diameter before and after the phase change, thereby affecting the heat exchange and flow resistance of the heat exchange medium in the heat exchange tube 32.

[0217] Therefore, in this embodiment, in order to better adapt to the specific volume change and pressure change of the heat exchange medium during the evaporation or condensation process, ensure that the heat exchange medium can be in a state with a high heat transfer coefficient regardless of whether it is in a liquid, two-phase state or a gaseous state, and can effectively reduce the flow resistance, thereby improving the heat exchange capacity of the heat exchanger 30 and the energy efficiency of the air conditioner, a combination of heat exchange tubes 32 with different diameters can be used, so that the heat exchange medium flows through these heat exchange tubes 32 with different diameters in sequence when evaporating or condensing.

[0218] When the heat exchange medium in the heat exchange tube 32 flows in the heat exchange tube 32, the heat exchange tube 32 near the windward side first contacts the airflow, and the heat exchange medium gradually evaporates under the action of the airflow, and the volume changes continuously. Therefore, in this embodiment, the aperture of at least part of the tube holes 316 near the leeward side contour line (the first side contour line 311) can be set to be larger than the aperture of at least part of the tube holes 316 near the windward side contour line (the second side contour line 312). At this time, since the shape of the heat exchange tube 32 is consistent with the shape of the tube holes 316, the heat exchange tube 32 also undergoes corresponding changes to better adapt to the specific volume change and pressure change of the heat exchange medium during evaporation or condensation, ensuring that the heat exchange medium can be in a state with a high heat exchange coefficient regardless of being in a liquid state, a two-phase state, or a gaseous state, and can effectively reduce the flow resistance of the heat exchange medium, thereby improving the heat exchange capacity of the heat exchanger 30 and the energy efficiency of the air conditioner.

[0219] Specifically, as described above, the heat exchange fin 31 has a first side contour line 311 and a second side contour line 312 spaced apart from each other. The second side contour line 312 is arranged on the side of the heat exchange fin 31 facing the fan 22 as a windward side contour line, and the first side contour line 311 is arranged on the side of the heat exchange fin 31 facing away from the fan 22 as a leeward side contour line.

[0220] Optionally, in a specific embodiment, the diameter of the tube hole 316 may be set to gradually increase in the direction from the windward side contour line to the leeward side contour line, that is, in the direction from the second side contour line 312 to the first side contour line 311 .

[0221] For example, in a specific embodiment, the diameter of the tube hole 316 disposed on the side close to the leeward side contour line may be larger than the diameter of the tube hole 316 disposed on the side close to the windward side contour line.

[0222] Specifically, as described above, the heat exchange fin 31 is provided with at least two rows of tube holes 316 in the spacing direction along the windward side contour line and the leeward side contour line, and each row of tube holes 316 is arranged at intervals along an arrangement curve formed by translating the first side contour line 311 or the second side contour line 312 along the straight line l3 where the peak width is located, and different rows of tube holes 316 are arranged at intervals along an arrangement straight line formed parallel to the straight line l3 where the peak width of the heat exchange fin 31 is located.

[0223] Therefore, in a specific embodiment, in the tube holes 316 arranged along the same straight line, the diameters of the tube holes 316 may be arranged to gradually increase in a direction from the second side contour line 312 to the first side contour line 311 .

[0224] For example, Fig.11 As shown, in the spacing direction from the second side contour line 312 to the first side contour line 311, the number of rows of the tube holes 316 arranged in the middle area is three rows, and the number of rows of the tube holes 316 arranged in the end areas at both ends of the middle area is two rows. Among them, the aperture of the tube holes 316 in a row close to the second side contour line 312 is smaller than the aperture of the tube holes 316 in a row close to the first side contour line 311, and the aperture of the tube holes 316 in a row between the two rows can be smaller than or equal to the aperture of the tube holes 316 in a row close to the first side contour line 311, so as to achieve the change of the aperture of the tube holes 316.

[0225] Optionally, in a specific embodiment, the diameter of the tube hole 316 can be set to 4-7 mm.

[0226] Furthermore, the diameter of the tube holes 316 in a row close to the second side contour line 312 may be set to 4 mm-5 mm, and the diameter of the tube holes 316 in a row close to the first side contour line 311 may be set to 6.35-7 mm.

[0227] Optionally, in a specific embodiment, the hole center distance between adjacent tube holes 316 can be set to 12mm-21mm. The hole center distance between adjacent tube holes 316 refers to the distance between the tube hole centers of two adjacent tube holes 316. This ensures that each heat exchange tube 32 inserted into the tube hole 316 can exert the best heat exchange performance. It can be understood that when the shape of the tube hole 316 is circular, the tube hole center of the tube hole 316 is the center of the circle, and when the shape of the tube hole 316 is non-circular, such as an ellipse or other shapes, the tube hole center of the tube hole 316 is the geometric center.

[0228] The hole center distances between adjacent tube holes 316 may be equal or unequal, or the hole center distances between adjacent tube holes 316 in some areas may be equal or unequal.

[0229] Optionally, in a specific embodiment, the hole center distance d16 of at least some adjacent tube holes 316 in a row of tube holes 316 close to the second side contour line 312 can be set to be smaller than the hole center distance d17 of at least some adjacent tube holes 316 in a row of tube holes 316 close to the first side contour line 311, so as to adapt to the heat exchange tubes 32 with larger tube diameters, thereby ensuring that each heat exchange tube 32 inserted into the tube holes 316 can exert the best heat exchange performance.

[0230] For example, in a specific embodiment, the hole center distance d16 of at least some adjacent tube holes 316 in a row of tube holes 316 close to the second side contour line 312 can be set to 12 mm-19 mm, and the hole center distance d17 between adjacent tube holes 316 in a row of tube holes 316 close to the first side contour line 311 can be set to 14 mm-21 mm.

[0231] Generally speaking, the wind field formed by the airflow includes a high flow velocity zone located in the middle area and low flow velocity zones located on both sides of the high flow velocity zone, and the air volume in the middle area of ​​the heat exchange fin 31 is greater than the air volume in the end area, and the heat transfer coefficient of the heat exchanger 30 is positively correlated with the wind speed. The heat exchange effect of the heat exchange tube 32 in the middle area is better. If the middle area and the end area use pipes of equal diameter, the heat exchange performance of the air side of the heat exchanger 30 will be reduced, and it will also cause a large difference in the outlet air temperature between the middle area and the end area.

[0232] Further, as described above, the fin width of the heat exchange fin 31 gradually decreases in the direction from the middle area of ​​the heat exchange fin 31 to the end areas on both sides of the middle area. Therefore, in this embodiment, in order to improve the heat exchange performance of the heat exchanger 30, the aperture of at least part of the tube holes 316 in the middle area can be set to be larger than the aperture of at least part of the tube holes 316 in the end areas. Through this arrangement, a heat exchange tube 32 with a larger tube diameter can be further arranged in the middle area with a larger fin width to further increase the heat exchange area in the middle area and enhance the heat exchange performance of the heat exchanger 30. At the same time, the flow resistance of the air in the middle area can also be increased, so that part of the air flows to the end areas with a small pressure difference. In the end areas with low air flow rate, the use of heat exchange tubes 32 with smaller tube diameters can reduce the flow resistance of the air, so as to maintain a certain air flow rate, so that the heat exchange tubes 32 can be fully exchanged, and the overall heat exchange performance of the heat exchanger 30 can be improved.

[0233] It is worth noting that the variation rule of the aperture of the pores 316 between the first side contour line 312 and the second side contour line 312 and the variation rule from the middle region to the end region described above can be used alone or in combination. Therefore, optionally, in a specific embodiment, the apertures of the pores 316 in the middle region can be set to be equal, the apertures of the pores 316 in the end regions can be set to be equal, and the apertures of the pores 316 in the middle region can be set to be larger than the apertures of the pores 316 in the end regions. Alternatively, in another specific embodiment, the aperture of the pores 316 can be set to gradually decrease in the direction from the middle region to the end region.

[0234] Further, in a specific embodiment, in the tube holes 316 arranged along the same arrangement curve, the diameter of the tube holes 316 can be set to gradually decrease in the direction from the middle area to the end area.

[0235] In summary, adopting one or a combination of the above two methods can ensure that the middle area has a sufficiently large heat exchange area and can effectively reduce the flow resistance of the heat exchange medium, thereby improving the heat exchange capacity of the heat exchanger 30.

[0236] 6.2 Tube shape changes

[0237] In the heat exchanger 30 using the circular heat exchange tube 32, when the air flows through the heat exchange tube 32, a heat exchange dead zone is easily generated on the leeward side of the circular heat exchange tube 32, and the heat exchange effect of the heat exchange fins 31 in the heat exchange dead zone is poor. In addition, the tube spacing between adjacent circular heat exchange tubes 32 is narrow, and when the air flows through a narrow passage, the ventilation resistance will increase.

[0238] Therefore, Fig.12 As shown, in this embodiment, the heat exchange tube 32 is configured as a flat tube. Since the heat exchange dead zone on the leeward side of the flat tube is small and the tube spacing between adjacent flat tubes is large, a larger airflow path can be formed, thereby reducing the heat exchange dead zone, enhancing the heat exchange effect, and reducing the flow resistance of the airflow.

[0239] Optionally, in a specific embodiment, the tube hole 316 for passing the heat exchange tube 32 may have a long axis direction D8 and a short axis direction D9, and the long axis dimension d18 of the tube hole 316 along the long axis direction D8 is greater than the short axis dimension d19 along the short axis direction D9. At this time, since the shape of the heat exchange tube 32 is consistent with the shape of the tube hole 316, the heat exchange tube 32 also needs to be changed accordingly.

[0240] Since the angle parameter between the major axis direction D8 and the air inlet direction D10 directly affects the area of ​​the heat exchange dead zone on the leeward side of the heat exchange tube 32 and the air flow resistance, in this embodiment, in order to reduce the area of ​​the heat exchange dead zone on the leeward side of the heat exchange tube 32 and the air flow resistance, it is necessary to reasonably set the angle between the major axis direction D8 and the air inlet direction D10.

[0241] Specifically, in this embodiment, the long axis direction D8 of the tube hole 316 forms an intersection with the windward side contour line (the second side contour line 312), and by setting the angle α5 between the tangent direction of the intersection and the long axis direction D8 to 70-110 degrees, the long axis direction D8 of the tube hole 316 can be better matched with the wind inlet direction D10 to reduce the area of ​​the heat exchange dead zone on the leeward side of the heat exchange tube 32 and the air flow resistance.

[0242] Furthermore, since the second side contour line 312 is bent in the direction toward the first side contour line 311, and the first side contour line 311 is bent in the direction away from the second side contour line 312, in the direction from the middle area to the end area, the angle between the tangent of the second side contour line 312, i.e., the windward side contour line, and the straight line l3 where the peak width is located gradually decreases. Therefore, the angle between the long axis direction D8 of the tube hole 316 and the straight line l3 where the peak width is located can be set to gradually increase, thereby further better matching with the wind inlet direction D10.

[0243] Furthermore, the heat exchange effect of the heat exchange tube 32 in the middle area is good and the flow resistance of the heat exchange medium is large. Therefore, in specific use, the setting method of the major axis dimension d18 and / or the minor axis dimension d19 of the flat tube can be set differently with reference to the setting method of the tube diameter of the circular heat exchange tube 32 described above, so as to achieve the above-described enhanced heat exchange effect and reduce the flow resistance of the heat exchange medium in the heat exchange tube 32. In this embodiment, the hole center distance of adjacent tube holes 316 specifically refers to the distance between the geometric centers of adjacent heat exchange tubes 32.

[0244] Specifically, the heat exchange effect of the heat exchange tube 32 is mainly related to parameters such as the major axis dimension d18 and the minor axis dimension d19 of the heat exchange tube 32. Therefore, by adjusting one or more of the above parameters, the heat exchange effect of the heat exchange tube 32 in the middle area can be stronger than the heat exchange effect of the heat exchange tube 32 in the end area.

[0245] For example, the major axis dimension d18 of at least part of the tube holes 316 in the middle area can be set to be larger than the major axis dimension d18 of at least part of the tube holes 316 in the end area, and / or the minor axis dimension d19 of at least part of the tube holes 316 in the middle area can be set to be larger than the minor axis dimension d19 of at least part of the tube holes 316 in the end area.

[0246] Furthermore, the flow resistance of the heat exchange medium in the heat exchange tube 32 is mainly related to parameters such as the major axis dimension d18 and the minor axis dimension d19 of the heat exchange tube 32. Therefore, the flow resistance of the heat exchange medium in the heat exchange tube 32 can be reduced by adjusting one or more of the above parameters.

[0247] For example, the major axis dimension d18 of at least part of the tube holes 316 near the leeward side contour line can be set to be larger than the major axis dimension d18 of at least part of the tube holes 316 near the windward side contour line, and / or the minor axis dimension d19 of at least part of the tube holes 316 near the leeward side contour line can be set to be larger than the minor axis dimension d19 of at least part of the tube holes 316 near the windward side contour line.

[0248] In a specific embodiment, the arrangement of the tube holes 316 follows the arrangement described above. That is, at least two rows of tube holes 316 are arranged on the heat exchange fin 31, and the at least two rows of tube holes 316 are arranged at intervals from each other along the spacing direction of the second side contour line 312 and the first side contour line 311. Each row of tube holes 316 is arranged at intervals along the arrangement curve formed by translating the second side contour line 312 or the first side contour line 311, and different rows of tube holes 316 are further arranged at intervals along the arrangement straight line parallel to the straight line where the peak width of the heat exchange fin 31 is located. At this time, in the tube holes 316 arranged along the same arrangement straight line, the major axis size d18 and / or the minor axis size d19 of the tube holes 316 gradually increase in the direction from the second side contour line 312 to the first side contour line 311, and in the tube holes 316 arranged along the same arrangement curve, the major axis size d18 and / or the minor axis size d19 of the tube holes 316 gradually decrease in the direction from the middle area to the end area.

[0249] Optionally, in a specific embodiment, Fig.12 As shown, the major axis dimension d18 of the heat exchange tube 32 can be set to 5-12 mm, and the minor axis dimension d19 of the heat exchange tube 32 can be set to 0.8 mm-3 mm.

[0250] Optionally, in a specific embodiment, the tube spacing between adjacent tube holes 316 can be set to 7 mm-16 mm, thereby ensuring that each heat exchange tube 32 inserted into the tube hole 316 can exert the best heat exchange performance.

[0251] Optionally, in a specific embodiment, a plurality of microchannels spaced apart along the long axis direction D8 may be provided inside the heat exchange tube 32 to further improve the heat exchange performance of the heat exchange tube 32 .

[0252] It is worth noting that in Fig.11 and 12 The shape of the heat exchange fins 31, the fin width and the arrangement of the tube holes 316 can be set with reference to the various methods described above, and will not be repeated here.

[0253] 7. Auxiliary cooperation mechanism

[0254] This application will be combined with Figure 13-20 The auxiliary cooperation mechanism of the heat exchanger 30 is further optimized.

[0255] In this embodiment, sheet metal side plates 60 and plastic side plates 70 are respectively provided at both ends of the heat exchanger 30, and are specifically arranged on the outer side of the heat exchange fins 31 at the outermost ends of the heat exchanger 30 in a direction perpendicular to the main surface of the heat exchange fins 31, so as to fix the heat exchanger 30 on the shell 10 of the duct air conditioning device through the sheet metal side plates 60 and the plastic side plates 70.

[0256] Optionally, in a specific embodiment, the heat exchange tube 32 includes a linear tube segment 326 passing through a plurality of heat exchange fins 31 and a U-shaped tube segment 327 connected to adjacent ends of different linear tube segments 326. The linear tube segment 326 is used to support and fix the plurality of heat exchange fins 31, and the U-shaped tube segment 327 is connected to adjacent ends of the linear tube segment 326 to facilitate the reflux of the heat exchange medium.

[0257] Furthermore, the heat exchanger 30 has a welding end and a non-welding end. At the non-welding end, the U-shaped pipe section 327 and the linear pipe section 326 are integrally formed. At the welding end, the U-shaped pipe section 327 and the linear pipe section 326 are connected by welding. The plastic side panel 70 is arranged at the non-welding end, and the sheet metal side panel 60 is arranged at the welding end.

[0258] 7.1. Side panel bracket

[0259] See also Figure 13-16 The sheet metal side plate 60 is fixed to the housing 10 through the side plate bracket 80. The sheet metal side plate 60 includes a sheet metal side plate body 62, and the side plate bracket 80 includes a support plate 82. The support plate 82 is overlapped with the sheet metal side plate 60 and locked to each other through a locking mechanism 90.

[0260] Optionally, in a specific embodiment, the sheet metal side plate body 62 has substantially the same shape as the heat exchange fin 31, and the sheet metal side plate body 62 is stacked with the heat exchange fin 31 in a direction perpendicular to the main surface of the heat exchange fin 31, and is located at the outermost side of the heat exchange fin 31. A avoidance hole 64 coaxial with the tube hole 316 is provided on the sheet metal side plate body 62 at a position corresponding to the tube hole 316 on the heat exchange fin 31, and the heat exchange tube 32 is passed through the avoidance hole 64 and the tube hole 316 to fix the plurality of heat exchange fins 31 and the sheet metal side plate body 62. The support plate 82 is overlapped with the sheet metal side plate body 62 in a direction perpendicular to the main surface of the heat exchange fin 31, and the support plate 82 and the sheet metal side plate body 62 are assembled and fixed by a locking mechanism 90.

[0261] Specifically, in a specific embodiment, a first fixing hole 84 may be provided on the support plate 82, and a second fixing hole 66 may be provided on the sheet metal edge plate body 62, the first fixing hole 84 and the second fixing hole 66 are provided overlappingly, and the locking mechanism 90 is a fastener inserted into the first fixing hole 84 and the second fixing hole 66. The locking mechanism 90 may be, for example, a bolt and a nut that cooperate with each other, so as to fix the support plate 82 and the sheet metal edge plate body 62 through a threaded fixing structure. Alternatively, the locking mechanism 90 may also be a rivet, so as to fix the support plate 82 and the sheet metal edge plate body 62 through riveting.

[0262] In some other implementations, the support plate 82 and the sheet metal edge plate body 62 may be fixedly connected by snap-fitting or other methods, which is not specifically limited in the embodiments of the present application.

[0263] In order to ensure the connection strength and connection stability between the support plate 82 and the sheet metal edge plate body 62, the number of locking mechanisms 90 is usually three or more. A large number of locking mechanisms 90 will make installation and removal inconvenient and affect the installation efficiency of the heat exchanger 30. In addition, when the heat exchange tube 32 passing through the heat exchange fin 31 is deformed, the presence of the locking mechanism 90 will interfere with the operating space of the repair tool, making it inconvenient to repair the heat exchange tube 32.

[0264] Therefore, in this embodiment, the side panel bracket 80 further includes a sink 86 arranged on the support plate 82, and the sheet metal side panel 60 further includes a lug 68 arranged on the sheet metal side panel body 62. When the support plate 82 and the sheet metal side panel body 62 are overlapped, the lug 68 is inserted into the sink 86.

[0265] Specifically, when fixing the side plate bracket 80 and the sheet metal side plate 60, the lug 68 can be inserted into the sink 86 first, and the support plate 82 and the sheet metal side plate body 62 can be positioned so that the first fixing hole 84 on the support plate 82 and the second fixing hole 66 on the sheet metal side plate body 62 overlap, and then the locking mechanism 90 is inserted into the first fixing hole 84 and the second fixing hole 66 to fix the support plate 82 and the sheet metal side plate body 62. In the above manner, the number of locking mechanisms 90 can be reduced, which can improve the assembly efficiency of the heat exchanger 30 on the one hand, and avoid interference with the repair tools on the other hand, so as to facilitate the repair of the heat exchange tube 32.

[0266] In other embodiments, the countersunk platform 86 and the lug 68 may also be replaced by other forms of first stop positions and second stop positions. It is only necessary to ensure that when the support plate 82 and the sheet metal edge plate body 62 are overlapped, one of the first stop position and the second stop position is inserted into the other, and then cooperates with the locking mechanism 90 to achieve relative fixation of the sheet metal edge plate 60 and the edge plate bracket 80.

[0267] Optionally, in a specific embodiment, the sink 86 is recessed toward the side of the support plate 82 close to the sheet metal side plate body 62, and the sink 86 has a notch 862, which is located on the side edge of the support plate 82 close to the sheet metal side plate body 62, and the lug 68 is located on the side edge of the sheet metal side plate body 62 close to the support plate 82. When the support plate 82 and the sheet metal side plate body 62 are overlapped, the lug 68 can be inserted into the sink 86 along the notch 862. The locking mechanism 90 fixes the sheet metal side plate body 62 to the side of the support plate 82 facing the heat exchange fins 31, and the lug 68 on the sheet metal side plate body 62 abuts against the side of the support plate 82 away from the heat exchange fins 31, thereby forming a limiting effect on the opposite sides of the support plate 82 to fix the support plate 82.

[0268] It can be understood that in another specific embodiment, the lug 68 and the sinker 86 can be set in reverse, that is, the lug 68 is set on the edge of the side of the support plate 82 facing the sheet metal edge plate body 62, and the sinker 86 is set on the sheet metal edge plate body 62, and is recessed on the side of the sheet metal edge plate body 62 close to the support plate 82, wherein the fixing method of the lug 68 and the sinker 86 can refer to the description of the above embodiment and will not be repeated here.

[0269] Optionally, in a specific embodiment, the number of locking mechanisms 90 can be two, and the two locking mechanisms 90 connect the opposite ends of the sheet metal edge plate body 62 and the support plate 82. The number of the mutually matching sink 86 and lug 68 can be one, and the sink 86 and lug 68 are respectively arranged in the middle area of ​​the support plate 82 and the sheet metal edge plate body 62, so that the support plate 82 and the sheet metal edge plate body 62 are evenly stressed.

[0270] Alternatively, in another specific embodiment, the number of locking mechanisms 90 can be set to one as needed, and the number of mutually cooperating countersunk platforms 86 and lugs 68 can be set to two. The two mutually cooperating countersunk platforms 86 and lugs 68 are respectively arranged at the opposite ends of the sheet metal edge plate main body 62 and the support plate 82, which can also simplify the installation complexity of the heat exchanger 30 and improve production efficiency.

[0271] Alternatively, in other specific embodiments, the locking mechanism 90 and the number and setting positions of the mutually cooperating countersunk platforms 86 and lugs 68 can be reasonably set according to the properties and sizes of the support plate 82 and the sheet metal edge plate body 62 to fix the support plate 82 and the sheet metal edge plate body 62, and this application does not make specific limitations.

[0272] Optionally, in a specific embodiment, when the outer shape of the heat exchange fin 31 is a crescent shape, the shape of the edge of the support plate 82 close to the sheet metal edge plate body 62 can be set to match the shape of the side contour line of the heat exchange fin 31, so as to avoid the heat exchange tube 32 passing through the heat exchange fin 31. At this time, the lug 68 can be set corresponding to the middle area of ​​the heat exchange fin 31, and the shape of the lug 68 can be set to a triangle, so as to match the edge shape of the support plate 82.

[0273] Alternatively, in a specific embodiment, when the heat exchange fin 31 is V-shaped or straight-strip-shaped, the lug 68 of other shapes may be provided specifically according to the shape of the edge of the support plate 82 , which is not specifically limited in the embodiment of the present invention.

[0274] Optionally, in a specific embodiment, the side plate bracket 80 and the sheet metal side plate 60 can be made of metal or alloy materials by stamping to improve the structural strength of the side plate bracket 80 and the sheet metal side plate 60 and improve the production efficiency of the heat exchanger 30. The sheet metal side plate 60 can also be replaced by other forms of side plates made of other heat-resistant materials.

[0275] Furthermore, in a specific embodiment, the lug 68 and the sheet metal edge plate body 62 are coplanar and of equal thickness, and the recessed depth of the sink 86 relative to the support plate 82 is equal to the thickness of the sheet metal edge plate body 62 and the lug 68, so as to simplify the manufacturing process of the sheet metal edge plate body 62, improve the manufacturing efficiency of the sheet metal edge plate body 62, and make the surface of the lug 68 away from the support plate 82 flush with the surface of the support plate 82, so as to facilitate the installation of the heat exchanger 30.

[0276] Furthermore, in order to improve the stability of the side plate bracket 80 and the sheet metal side plate 60 , the overlapping area of ​​the side plate bracket 80 and the sheet metal side plate 60 may be increased to provide auxiliary support for the support plate 82 .

[0277] For example, the sheet metal edge plate body 62 and the support plate 82 can be arranged to at least partially overlap in the edge area between the locking mechanism 90 and the sinker 86 and the lug 68 to support the edge of the support plate 82. On the one hand, the stability of the support plate 82 can be improved, and on the other hand, the edge of the support plate 82 can be prevented from being deformed by external force.

[0278] Optionally, in a specific embodiment, the edge of one side of the support plate 82 close to the sheet metal side plate body 62 is arranged in a wavy curve, so that the heat exchange tube 32 close to the support plate 82 is located in the trough area of ​​the wavy curve, and the peak area of ​​the wavy curve is embedded between adjacent heat exchange tubes 32. In this way, on the one hand, the overlapping area of ​​the sheet metal side plate body 62 and the support plate 82 can be maximized, and on the other hand, the support plate 82 can be used to provide auxiliary support for the heat exchange tube 32 to prevent the heat exchange tube 32 from being deformed or skewed to affect assembly.

[0279] Furthermore, in a specific embodiment, the side panel bracket 80 also includes a fixed flange 88, which is arranged on the other side edge of the support plate 82 away from the sheet metal side plate body 62 and is folded relative to the support plate 82. The fixed flange 88 is used to fix the side panel bracket 80 on the shell 10 of the duct type air-conditioning device.

[0280] 7.2. Plastic side panels

[0281] At present, when fixing the heat exchanger 30 in the duct air conditioner, a slot 72 is usually provided on the plastic side plate 70 corresponding to each U-shaped pipe segment 327, and the U-shaped pipe segment 327 is inserted into the slot 72 to support the heat exchange tube 32 and prevent the heat exchange tube 32 from being deformed. When the connection mode between the U-shaped pipe segment 327 and the linear pipe segment 326 (i.e., the arrangement mode of the U-shaped pipe segment 327) changes, different slots 72 need to be used to adapt to the U-shaped pipe segment 327, resulting in the need to manufacture different plastic side plates 70 for different arrangements of the U-shaped pipe segments 327, resulting in low versatility of the plastic side plates 70.

[0282] Therefore, if Figure 17-19 As shown, in this embodiment, the slots 72 are configured to be adaptable to at least two different arrangements of the U-shaped tube segments 327, so that when the arrangement of the U-shaped tube segments 327 changes, the same plastic side panels 70 can be used to support the heat exchange tubes 32, thereby improving the versatility of the plastic side panels 70, thereby facilitating large-scale production of the plastic side panels 70 to reduce production costs.

[0283] Furthermore, in order to prevent the heat exchange tube 32 from detaching from the plastic side plate 70, in a specific embodiment, a snap-fit ​​portion 74 can be provided in the slot 72 so that after the U-shaped tube segment 327 is inserted into the slot 72, it can be snap-fitted to the U-shaped tube segment 327, thereby snapping and fixing the U-shaped tube segment 327.

[0284] The number of the buckle parts 74 in the slot 72 that can adapt to different arrangements of the U-shaped tube segments 327 can be at least two, and each buckle part 74 corresponds to a different arrangement, and then after the U-shaped tube segments 327 are arranged in the corresponding arrangement and inserted into the slot 72, the U-shaped tube segments 327 are buckled and fixed. In this way, when the arrangement of the heat exchange tube 32 is changed, at least one of the buckle parts 74 provided in the slot 72 can be buckled with the heat exchange tube 32 to prevent the plastic side plate 70 from being separated from the heat exchange tube 32.

[0285] Optionally, in a specific embodiment, the slot 72 is configured to simultaneously receive at least two U-shaped tube segments 327, and the at least two U-shaped tube segments 327 have at least two different arrangements, wherein in different arrangements, the spacing directions of the at least two U-shaped tube segments 327 are different.

[0286] For example, in one specific embodiment, at least part of the slots 72 can simultaneously receive at least two U-shaped tube segments 327 , and the at least two U-shaped tube segments 327 have two different arrangements, namely, a first arrangement and a second arrangement.

[0287] Specifically, in Fig.18 In the embodiment shown, the number of heat exchange tubes 32 located in the same slot 72 is two, and the two U-shaped tube sections 327 are arranged at intervals along the direction D11. Fig.19 In the illustrated embodiment, the number of heat exchange tubes 32 located in the same slot 72 is two, and the two U-shaped tube sections 327 are arranged at intervals along the direction D12, wherein the direction D11 and the direction D12 are arranged perpendicular to each other.

[0288] Optionally, in a specific embodiment, the direction D11 may be set as the air inlet direction of the heat exchanger 30 , and the direction D12 may be set to be perpendicular to the air inlet direction of the heat exchanger 30 .

[0289] Alternatively, in another specific embodiment, the direction D11 and the direction D12 may be arranged to intersect each other. Alternatively, in another specific embodiment, at least two U-shaped tube segments 327 may be arranged in three or more arrangements, and more arrangements may be achieved by changing the inclination angle between the spacing direction of the U-shaped tube segments 327 in each arrangement and the direction D11.

[0290] Optionally, in a specific embodiment, in a cross section perpendicular to the insertion direction of the U-shaped pipe section 327 relative to the slot 72, the slot 72 is arranged in a parallelogram, the direction D11 is the spacing direction of the two opposite sides of the parallelogram, and the direction D12 is the spacing direction of the other two opposite sides of the parallelogram. In the above manner, when the U-shaped pipe section 327 is inserted into the slot 72 in different arrangements, the side walls of the slot 72 can fit tightly against the heat exchange tube 32, so as to enhance the support effect on the heat exchange tube 32 and prevent the heat exchange tube 32 from being deformed.

[0291] Furthermore, in a specific embodiment, the plastic side plate 70 may include a plastic side plate body 76 and a slot side plate 78 integrally formed with the plastic side plate body 76, and the slot side plate 78 surrounds the slot 72. In this way, on the one hand, the height of the slot side plate 78 can be extended to increase the contact area between the slot 72 and the heat exchange tube 32, thereby enhancing the abutting force on the heat exchange tube 32, and on the other hand, the thickness of the plastic side plate body 76 can be reduced to save the use of materials and reduce costs.

[0292] Optionally, in one embodiment, an elastic cantilever 71 is further formed on the slot side plate 78, and a buckle portion 74 is arranged on the elastic cantilever 71. When the heat exchange tube 32 is inserted into the slot 72, the abutment force of the heat exchange tube 32 on the buckle portion 74 can drive the elastic cantilever 71 to deform, so that the heat exchange tube 32 can enter the slot 72. After the heat exchange tube 32 enters the slot 72, the elastic reset force of the elastic cantilever 71 will drive the buckle portion 74 to reset so as to be engaged with the heat exchange tube 32.

[0293] In one specific embodiment, a first cutout 73 is provided on the slot side panel 78 along the insertion direction of the U-shaped tube section 327 relative to the slot 72, and a second cutout 75 is further provided on the slot side panel 78 or the plastic side panel body 76 along the circumference of the slot side panel 78. The first cutout 73 and the second cutout 75 are connected, thereby forming an elastic cantilever 71 on the slot side panel 78.

[0294] Optionally, the first cutout 73 may be disposed at a position adjacent to the buckle portion 74 along the circumference of the slot side plate 78 to extend the force arm at the position of the buckle portion 74 as much as possible, so as to facilitate deformation of the heat exchange tube 32 when it abuts against the elastic cantilever 71 .

[0295] The above descriptions are merely embodiments of the present invention and are not intended to limit the patent scope of the present invention. Any equivalent structure or equivalent process transformation made using the contents of the present invention specification and drawings, or directly or indirectly applied in other related technical fields, are also included in the patent protection scope of the present invention.

Claims

1. A heat exchange fin, characterized in that: The heat exchange fins include: side profile; The side contour line and the straight line where the peak width of the heat exchange fin is located form an intersection, the opening angle of the side contour line refers to the angle between the two ends of the side contour line and the line connecting the intersection; the end tangent angle of the side contour line refers to the angle between the tangents of the two end points of the side contour line; The side contour line includes a first side contour line and a second side contour line; the first side contour line and the second side contour line are spaced from each other, the second side contour line is bent in a direction toward the first side contour line, the first side contour line is bent in a direction away from the second side contour line, the first side contour line and the second side contour line are arranged to overlap in translation, and the length of the overlapping portion accounts for a proportion of the total length of the first side contour line greater than or equal to 90%; a reference point is selected on the first side contour line, the normal of the reference point intersects with the second side contour line and forms an intersection, the straight-line distance between the reference point and the intersection is the fin width at the reference point, and the length of the line connecting the reference point and the intersection at the maximum fin width is the peak width of the heat exchange fin; the overall height of the heat exchange fin refers to the projection size of the heat exchange fin on a reference plane perpendicular to the straight line where the peak width is located and perpendicular to the main surface of the heat exchange fin; the opening angle of the first side contour line is 95-120 degrees, and the ratio of the end tangent angle of the first side contour line to the opening angle is 0.7-0.85; Wherein, the fin width of the heat exchange fin gradually decreases from the middle area of ​​the heat exchange fin to the end areas on both sides of the middle area, and the first side contour line includes: a first reference point, wherein the vertical distance from the first reference point to the straight line where the peak width of the heat exchange fin is located is 25% of the overall height of the heat exchange fin, and the ratio of the fin width at the first reference point to the peak width of the heat exchange fin is 0.64-0.96; and a second reference point, the vertical distance from the second reference point to the straight line where the peak width of the heat exchange fin is located is 45% of the overall height of the heat exchange fin, the ratio of the fin width at the second reference point to the peak width of the heat exchange fin is 0.54-0.80, and the fin width at the second reference point is smaller than the fin width at the first reference point; and A third reference point, a vertical distance from the third reference point to the straight line where the peak width of the heat exchange fin is located is 35% of the overall height of the heat exchange fin, a ratio of the fin width at the third reference point to the peak width of the heat exchange fin is 0.60-0.89, and the fin width at the third reference point is smaller than the fin width at the first reference point, and larger than the fin width at the second reference point.

2. The heat exchange fin according to claim 1, characterized in that: The first side contour line includes the following on both sides of the straight line where the peak width of the heat exchange fin is located: The first arc segment; The second arc segment; and a first straight line segment, wherein the first arc segment, the second arc segment and the first straight line segment are sequentially connected in a direction from the middle region to the end region; The second side contour line includes on both sides of the straight line where the peak width of the heat exchange fin is located: The third arc segment; The fourth arc; and a second straight line segment, the third arc segment, the fourth arc segment and the second straight line segment are connected in sequence from the middle region to the end region, Among them, when the first side contour line is translated along the straight line where the peak width is located, the first arc segment and the second arc segment can overlap with the third arc segment and the fourth arc segment respectively, the first straight line segment and the second straight line segment can at least partially overlap, the first reference point is located on the second arc segment, the second reference point and the third reference point are located on the first straight line segment, the intersection point of the straight line where the fin width at the first reference point and the second side contour line is located on the third arc segment, the intersection point of the straight line where the fin width at the second reference point and the second side contour line is located on the second straight line segment, and the intersection point of the straight line where the fin width at the third reference point and the second side contour line is located on the fourth arc segment.

3. The heat exchange fin according to claim 2, characterized in that: The two intersection points formed by the perpendicular bisector of the line connecting the reference point and the intersection point at the maximum fin width and the first side contour line are respectively located on the second arc segment of the first side contour line, and the ratio of the straight-line distance between the two intersection points to the overall height of the heat exchange fin is 0.46-0.

56.

4. The heat exchange fin according to claim 1, characterized in that: The heat exchange fins are provided with tube holes in rows. In the spacing direction between the first side contour line and the second side contour line, the number of rows of the tube holes in the middle area is greater than the number of rows of the tube holes in the end area. The height of the middle area is 25%-50% of the overall height of the heat exchange fins.

5. The heat exchange fin according to claim 4, characterized in that: The fin width in the middle area is K1×n1×D, and the fin width in the end area is K2×n2×D, n1 and n2 are the number of rows of the tube holes in the middle area and the end area respectively, D is the end tube hole row spacing of the heat exchange fin, K1 and K2 are variation coefficients, and the value range is 0.8-1.

2.

6. The heat exchange fin according to claim 4, characterized in that: The heat exchange fin is further provided with a plurality of heat transfer enhancement structures, wherein the heat transfer enhancement capacity of the heat transfer enhancement structure in the end region is greater than the heat transfer enhancement capacity of the heat transfer enhancement structure in the middle region; the end region includes: an upper end region located above the middle region; and The lower end region is located at the lower side of the middle region, wherein the drainage capacity of the heat transfer enhancement structure in the lower end region is greater than the drainage capacity of the heat transfer enhancement structure in the upper end region.

7. The heat exchange fin according to claim 4, characterized in that: The number of rows of the tube holes is at least two, and the at least two rows of tube holes are spaced apart from each other along the spacing direction of the first side contour line and the second side contour line, wherein a plurality of row insulation structures are further arranged in rows on the heat exchange fins, and each row of the row insulation structures is arranged between two adjacent rows of the tube holes, wherein the wind resistance of the row insulation structures in the middle area is smaller than the wind resistance of the row insulation structures in the end areas.

8. The heat exchange fin according to claim 4, characterized in that: A vortex generator is further provided on the heat exchange fin, and the vortex generator is used to reduce the area of ​​the wake zone on the leeward side of the heat exchange tube inserted into the tube hole. The vortex generator is a folded piece that is integrally formed with the heat exchange fin and folded relative to the heat exchange fin, or is a convex hump that is integrally formed with the heat exchange fin and protrudes relative to the heat exchange fin.

9. A heat exchanger, characterized in that: The heat exchanger comprises a heat exchange tube and a heat exchange fin according to any one of claims 1 to 8, and the heat exchange tube is passed through the heat exchange fin.

10. An air conditioning device, characterized in that: The air conditioning device includes the heat exchanger according to claim 9.

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