A multi-section integrated air conditioner heat exchanger fin with three fields of synergistic heat exchange enhancement

Abstract

The application discloses a kind of multi-section integrated air conditioner heat exchanger fin of three field synergistic enhanced heat exchange, belong to air conditioner heat exchanger technical field, fin body is integrated structure, from top to bottom is divided into upper section, middle section, lower section area, outer edge is connected by multiple main line sections and edge line sections in order and is formed, left side is leeward side, right side is windward side, both sides are bent to left as a whole;Three section area hole row quantity is consistent, the number of lower section pipe hole is more than upper section, upper section matches four bridges, middle section matches long two bridges, and lower section matches three bridges.Fin middle section width is maximum, upper and lower end narrow, heat insulation cut is arranged between pipe row, upper and lower end of edge is chamfer structure.This fin adapts to air pipe machine uneven wind field, can improve unit space heat exchange capacity under the premise of not increasing shell size, satisfying wind resistance requirement, strengthens three field synergistic heat exchange effect, speeds up condensate water discharge, heat exchange efficiency is significantly improved, and production efficiency is high.

Description

Technical Field

[0001] This invention belongs to the field of air conditioning heat exchanger technology, specifically relating to a multi-segment integrated enhanced heat exchange fin that is adapted to the V-type centrifugal fan of ducted air conditioners and realizes the synergy of the air field, temperature field and pressure field. Background Technology

[0002] Traditional V-type heat exchangers are assembled by splicing two fins on the left and right sides. The splicing gap is sealed by a sealing strip. During operation, condensate tends to accumulate at the sealing strip, resulting in poor drainage and the formation of a water film that increases the heat exchange resistance. At the same time, the centrifugal fan has a high wind speed in the middle and a low wind speed in the upper and lower sections. The symmetrical spliced ​​fins cannot match the uneven air field, resulting in poor air field coordination. A large amount of heat exchange area cannot be fully utilized, and there is a significant waste of heat exchange efficiency. The two-piece split structure requires two sets of stamping dies and two assembly processes, resulting in low production efficiency and high manufacturing costs.

[0003] Existing internal improvements to integrated fins only optimize the outline and hole layout, and are mostly symmetrical structural designs, which cannot perfectly match the heat exchange of the wind field. They lack graded differentiated bridging and turbulence structures and complete sets of bridge body quantitative parameters, and can only achieve a 15% heat exchange improvement, which cannot further explore the heat exchange upper limit within the limited shell space. The uniform design of various bridging structures results in insufficient heat exchange in high wind speed areas and excessive wind resistance in low wind speed areas, which cannot match the gradient wind speed. There is no dedicated vertical double-bridge flow guiding structure, and the problem of condensate retention cannot be completely solved.

[0004] In summary, the existing technology lacks a set of three-field synergistic integrated fins that integrate multi-segment integrated asymmetric contours, three-segment zone gradient differential bridging, unified single hole spacing compatible with tube insertion, row-interval thermal shaving, and a complete set of quantitative coupling parameters. It cannot simultaneously solve multiple industry pain points such as poor drainage, poor wind field adaptability, low heat transfer coefficient, complex processing, and limited overall casing size. Summary of the Invention

[0005] To address the shortcomings of existing V-type heat exchangers, such as poor drainage due to spliced ​​structures, poor airflow matching of integrated fins, single enhanced heat exchange structure, inability to balance air resistance and heat exchange, complex processing molds, and condensate retention, this paper proposes a multi-segment integrated air conditioning heat exchanger fin design that enhances heat exchange through three-field synergy. This design utilizes an asymmetric multi-segment integrated profile, differentiated multi-level bridging to match gradient airflow in three zones, a unified single-hole spacing structure, inter-row zoned insulation with virtual cutting, and complete simulation optimization of quantitative parameters to achieve synergistic matching of the airflow, temperature, and pressure fields. This improves the heat exchanger's heat exchange capacity, reduces airflow resistance, accelerates condensate drainage, simplifies stamping molds, and increases production efficiency without increasing the size of the air conditioning casing.

[0006] To achieve the above objectives, the present invention provides a multi-segment integrated air conditioning heat exchanger fin with three-field synergistic enhanced heat exchange. The fin body is an integrated structure, and the fin body is provided with tube holes to facilitate the passage of heat exchange tubes. The fin body is divided into an upper section, a middle section, and a lower section from top to bottom. The outer edge line OCL of the fin is composed of multiple line segments, including the main line segments L1, L2, L3, L4, L5, and L6 of the fin body and the sealing line segments L7 and L9. The clockwise connection order of the main line segments and the sealing line segments is: L1-L7-L4-L5-L6-L9-L3-L2. The leeward side of the left outer edge of the fin, which has an overall trend of curving to the left, is formed by the main line segments L1, L2, and L3 of the fin body. The windward side of the right outer edge of the fin, which also has an overall trend of curving to the left, is formed by the main line segments L4, L5, and L6 of the fin body.

[0007] Where L2 has two endpoints P1 and P2, and L5 has two endpoints P3 and P4, and the line connecting endpoints P1 and P3 is L... 13 The line connecting P2 and P4 is L. 24 L2, L 13 L5, L 24 The fin region between them is the middle section region, L 13 The finned area mentioned above is the upper section region, L 24 The finned area below is the lower section region;

[0008] Multiple holes are arranged sequentially along the length of the fin body to form a hole row. The number of hole rows in the upper section, middle section and lower section are the same, and the number of holes in the lower section is greater than the number of holes in the upper section.

[0009] A reinforced heat exchange bridging structure is formed by stamping along the length of the fin body and between the tube holes in each region. The upper section has four bridges, the lower section has three bridges, and the middle section has long double bridges.

[0010] Preferably, the four bridges include a first bridge located in the middle, of the same size and symmetrically distributed, and second bridges of the same size and symmetrically arranged on both sides of the first bridge. The height 'a' of the first bridge and the second bridge is 0.5-0.8 mm. The rear bridge side length 'd' of the second bridge is equal to 1.65-1.76 times the inner diameter of the heat exchange tube, and the width 'e' is equal to 0.18-0.24 times the inner diameter of the heat exchange tube. The rear bridge side length 'g' of the first bridge is equal to 0.55-0.75 times 'd'. The width 'h' of the first bridge is equal to the width 'e' of the second bridge. The opening angle 'c' of the first bridge is 23-29°, the opening angle 'b' of the second bridge is 18-26°, and the bridge spacing 'f' between the first bridge and the second bridge is equal to 0.24-0.32 times the inner diameter of the heat exchange tube.

[0011] Preferably, the three bridges include a third bridge located in the middle, and a fourth bridge distributed on both sides of the third bridge, which are of the same size and arranged symmetrically. The rear bridge side length j of the fourth bridge is 1.62-1.78 times the inner diameter of the heat exchange tube, the front bridge side length K is 1.16-1.32 times the diameter of the heat exchange tube, the width N is equal to 0.32-0.53 times the inner diameter of the heat exchange tube, and the angle M is 52-67°. The rear bridge side length L of the third bridge is equal to 0.76-0.92 times the dimension K, and the bridge spacing P between the third bridge and the fourth bridge is equal to 0.35-0.45 times the inner diameter of the heat exchange tube.

[0012] Preferably, the long double bridge includes two fifth bridges of the same size and arranged symmetrically. The width R of the fifth bridge is 0.32-0.42 times the inner diameter of the heat exchange tube, the side length Q of the rear bridge is 2.02-2.25 times the inner diameter of the heat exchange tube, the side length U of the front bridge is 0.79-0.88 times Q, the opening angle S is 63-71°, the opening angle V is 24-35°, and the bridge spacing T between the two fifth bridges is equal to the width R, which is 0.95-1.05cm.

[0013] Preferably, the distance between the left and right outer edges of the fin is the width W of the fin, and the maximum value of the width W is W0. max Located between L2 and L5, with a minimum width W. min Located between L1 and L4 or between L3 and L6, W min = (0.79 ± 10%) W max。

[0014] Preferably, the overall height H and width W of the fins are... max The ratio is 3.3 ± 5%.

[0015] Preferably, the height H1 of the upper section is 35% ± 10% of the overall fin height H, the height H2 of the middle section is 22% ± 10% of the overall fin height H, and the height H3 of the lower section is 42% ± 10% of the overall fin height H.

[0016] Preferably, the upper, middle, and lower sections of the copper tubes are provided with inter-row tangent lines. The inter-row tangent line adjacent to the leeward side is a leeward side heat insulation tangent line, and the inter-row tangent line adjacent to the windward side is a windward side heat insulation tangent line, which is used to block the lateral heat conduction of adjacent copper tubes.

[0017] Preferably, the upper, middle, and lower sections of the heat exchange main body of the fin adopt a unified basic hole spacing D1, where D1 is 3 to 4 times the pipe hole diameter D. The transverse and longitudinal hole spacings of the middle section are both equal to D1. Based on the square uniform pipe hole grid structure, the same type of span hairpin heat exchange copper tube can be arranged either upright or obliquely, adapting to various refrigerant diversion paths such as N-type, S-type, and Z-type. Only one set of punching molds is needed to complete the processing of the entire fin, reducing the specifications of copper tube materials and improving the overall production efficiency of the heat exchanger.

[0018] Preferably, the upper and lower ends of the outer right edge of the fin are chamfered structures, and the sealing lines L8 and L10 are the sealing sections of the upper and lower chamfered structures, respectively. L7-L8 constitute the upper sealing edge, and L10-L9 constitute the lower sealing edge.

[0019] The present invention has the following beneficial effects:

[0020] One-piece stamping eliminates the traditional two-piece splicing and sealing strip, completely eliminating the problems of water accumulation and heat exchange attenuation at the splicing point. A single set of molds completes the molding, improving production efficiency and reducing mold costs.

[0021] The asymmetrical three-section profile and the maximum width of the middle section force the high-speed airflow in the middle to be evenly distributed to the upper and lower sections, matching the naturally uneven wind field of the centrifugal fan to achieve wind field synergy;

[0022] Three-section zoned differentiated bridge design: four bridges in the high wind speed zone enhance airflow turbulence and improve the heat transfer coefficient; three bridges in the medium and low wind speed zones control wind resistance; and two vertical long bridges in the middle section take into account both heat transfer and rapid drainage, achieving synergistic coupling of the wind field, temperature field, and pressure field; after multi-feature coupling, the heat transfer capacity is increased by 20% under the same shell size, which is better than the 15% improvement of the existing contour optimization scheme alone.

[0023] The unified single-hole spacing design is compatible with both straight and oblique copper tube flow paths, and can adapt to different flow distribution requirements without changing the mold; the precise hole spacing and edge distance parameters balance the heat exchange area and the strength of the fin structure.

[0024] The inter-row partition insulation and partial cutting block the lateral heat conduction of copper tubes, amplifying the heat exchange temperature difference and further improving heat exchange efficiency;

[0025] The complete set of quantitative bridge body and contour geometry parameters have been optimized through simulation and experimental iterations to form a standardized industrial solution that can be mass-produced and adapted to the compact chassis of duct air conditioners, increasing cooling and heating loads without increasing the size of the unit casing. Attached Figure Description

[0026] Figure 1 This is a schematic diagram of the structure of the multi-segment integrated fin of the present invention;

[0027] Figure 2 This is a schematic diagram of the tangent line of the multi-segment integrated fin of the present invention;

[0028] Figure 3 This is a schematic diagram showing the corresponding dimensions of the multi-segment integrated fin four-bridge design of the present invention;

[0029] Figure 4 This is a schematic diagram of the structure of the first and second bridges of the multi-segment integrated finned bridge of the present invention.

[0030] Figure 5 This is a schematic diagram showing the corresponding dimensions of the three bridges in this invention;

[0031] Figure 6 This is a schematic diagram showing the corresponding dimensions of the two bridges in this invention.

[0032] In the diagram: outer edge line OCL of the fin; main line segments L1, L2, L3, L4, L5, L6 of the fin body; edge sealing line segments L7, L8, L9, L10; two endpoints P1, P2 of L2; two endpoints P3, P4 of L5; inter-row virtual tangent lines G1, G2, G3, G4, G5, G6; first bridge 1; second bridge 2; third bridge 3; fourth bridge 4; fifth bridge 5. Detailed Implementation

[0033] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0034] Please see Figures 1-2 This invention provides a technical solution: a multi-segment integrated air conditioning heat exchanger fin with three-field synergistic enhanced heat exchange. The fin body is an integrated structure, and the fin body is provided with tube holes to facilitate the passage of heat exchange tubes. The fin body is divided into an upper section, a middle section, and a lower section from top to bottom. In this embodiment, the fin is formed by stamping as a whole piece, without splicing seams or sealing strips, which solves the problems of poor drainage and heat exchange efficiency loss at the splicing point from the root. The one-piece molding only requires one set of stamping molds, saving multiple processes such as segmented stamping, splicing assembly, and glue sealing, which significantly simplifies the production process and reduces manufacturing costs.

[0035] The outer edge line (OCL) of the fin is composed of multiple line segments, including the main body segments L1, L2, L3, L4, L5, and L6, and the sealing line segments L7 and L9. The main body segments and the sealing line segments are connected in a clockwise order as follows: L1-L7-L4-L5-L6-L9-L3-L2. The leeward side, where the outer edge of the left fin curves to the left, is formed by the main body segments L1, L2, and L3. The windward side, where the outer edge of the right fin curves to the left, is formed by the main body segments L4, L5, and L6.

[0036] Where L2 has two endpoints P1 and P2, and L5 has two endpoints P3 and P4, and the line connecting endpoints P1 and P3 is L... 13 The line connecting P2 and P4 is L. 24 L2, L 13 L5, L 24 The fin region between them is the middle section region, L 13 The finned area mentioned above is the upper section region, L 24 The finned area below is the lower section region;

[0037] In this ducted centrifugal fan, the wind speed is highest in the middle and lower in the upper and lower areas. In this embodiment, the middle section of the fins is enclosed by L2 and L5 to form the widest area, corresponding to the high-speed airflow zone of the fan. More heat exchange tube holes can be arranged to increase the core heat exchange area. The upper and lower sections narrow to match the low-speed airflow. The outer edges on both sides bend to the left to form a regular V-shaped guide surface, which can guide the airflow to diffuse evenly to the upper and lower sections, avoiding the problem of concentrated airflow in the middle and insufficient airflow at the top and bottom. This achieves initial airflow coordination and makes full use of the limited space inside the casing of the whole machine. The heat exchange capacity can be increased without increasing the size of the casing. By dividing the fins into three independent functional zones according to the fan speed gradient through two dividing lines L13 and L24, the upper section is high-speed, the middle section is the highest-speed, and the lower section is medium-low-speed. The arrangement of pipe holes and turbulence bridging can be designed separately for the airflow velocity and condensate volume of each section. Instead of using a uniform single structure for all fins, it can achieve differentiated design for heat exchange enhancement, wind resistance control, and rapid drainage in each section, providing a zonal structural basis for the collaborative design of the three fields.

[0038] Multiple perforations are arranged sequentially along the length of the fin body to form a perforation row. The number of perforations is the same in the upper, middle, and lower sections. In this embodiment, the attached diagram shows three perforation rows, and the number of perforations in the lower section is greater than that in the upper section. The lower section is closer to the unit's water receiving pan, has a longer airflow path, and a greater heat exchange demand, so more perforations are arranged to increase the heat exchange area in the lower section. The upper section has a high airflow velocity but a relatively small total air volume, so fewer perforations are used to avoid excessively increasing air resistance. Maintaining the same number of perforations in all three sections ensures a regular stamping grid and a universal mold. The asymmetrical layout of multiple perforations in the lower section perfectly matches the difference in airflow between the upper and lower parts of the fan, balances the heat exchange load of the entire plate, eliminates local heat exchange bottlenecks, and significantly improves the overall heat exchange uniformity.

[0039] The heat exchange-enhancing bridging structure is formed by stamping along the length of the fin body and between the pipe holes in each region. The upper section has four bridges, the lower section has three bridges, and the middle section has long double bridges. The upper section, being a high-speed airflow area, employs a four-bridge multi-turbulence structure to tear the boundary layer multiple times, enhance airflow turbulence, and significantly improve the heat transfer coefficient in this area, fully utilizing the heat transfer potential of the high-speed airflow. The lower section, with its lower airflow velocity, uses a simpler three-bridge structure to ensure basic turbulence-enhanced heat transfer while reducing airflow friction resistance, avoiding excessive overall airflow resistance and increased fan power consumption. The middle section, the core heat exchange area with the highest overall airflow velocity and largest condensate production, uses a vertically arranged long double bridge: on the one hand, the long-sized turbulence structure maximizes turbulent heat transfer; on the other hand, the vertical bridge body forms a vertical flow channel, allowing condensate to slide vertically and quickly down the bridge wall under evaporation conditions, preventing water film thermal resistance from accumulating between the pipe holes in the middle section, simultaneously achieving high-intensity heat transfer and efficient drainage. By matching three types of open-bridge zones, high wind speed enhances heat exchange, low wind speed controls wind resistance, and the core area takes into account both heat exchange and drainage, balancing the three major indicators of heat transfer coefficient, air-side pressure drop, and condensation drainage, the synergy of the wind field, temperature field, and pressure field is achieved, and the heat exchange capacity is significantly improved compared with traditional integrated fins under the same shell size.

[0040] As a preferred embodiment of this practice, refer to Figure 3 , 4 The four bridges include a first bridge 1 located in the middle, with the same size and symmetrically distributed, and a second bridge 2 located on both sides of the first bridge 1, with the same size and symmetrically arranged. The height a of the first bridge 1 and the second bridge 2 is 0.5-0.8 mm. The rear bridge side length d of the second bridge 2 is equal to 1.65-1.76 times the inner diameter of the heat exchange tube, and the width e is equal to 0.18-0.24 times the inner diameter of the heat exchange tube. The rear bridge side length g of the first bridge 1 is equal to 0.55-0.75 times the dimension d. The width h of the first bridge 1 is equal to the width e of the second bridge. The opening angle c of the first bridge 1 is 23-29°, the opening angle b of the second bridge 2 is 18-26°, and the bridge spacing f between the first bridge 1 and the second bridge 2 is equal to 0.24-0.32 times the inner diameter of the heat exchange tube. For example: bridge height = 0.46 × fin spacing = 0.598 mm (0.44 to 0.48 times the midpoint of the range); rear bridge side length d = 1.7 × copper tube inner diameter = 10.54 mm, bridge width e = 0.21d = 1.302 mm; middle bridge width g = 0.65d = 6.85 mm; outer opening angle b = 22°, middle opening angle c = 26°; bridge spacing f = 0.28d = 1.74 mm.

[0041] As a preferred embodiment of this practice, refer to Figure 5The three bridges include the third bridge 3 located in the middle, and the fourth bridge 4, which are of the same size and symmetrically arranged on both sides of the third bridge 3. The rear bridge side length j of the fourth bridge 4 is 1.62-1.78 times the inner diameter of the heat exchange tube, the front bridge side length K is 1.16-1.32 times the diameter of the heat exchange tube, the width N is equal to 0.32-0.53 times the inner diameter of the heat exchange tube, and the angle M is 52-67°. The rear bridge side length L of the third bridge 3 is equal to 0.76-0.92 times the size K, and the bridge spacing P between the third bridge 3 and the fourth bridge 4 is equal to 0.35-0.45 times the inner diameter of the heat exchange tube. For example: bridge height = 0.40 × fin spacing = 0.52 mm; rear axle j = 1.7d = 10.54 mm, front axle k = 1.22d = 7.56 mm; bridge width N = 0.4d = 2.48 mm; opening angle M = 60°; L = 0.82k = 6.20 mm.

[0042] As a preferred embodiment of this practice, refer to Figure 6 The long two-bridge system comprises two identical and symmetrically arranged fifth bridges 5. The width R of each fifth bridge 5 is 0.32-0.42 times the inner diameter of the heat exchange tubes, the side length Q of the rear bridge is 2.02-2.25 times the inner diameter of the heat exchange tubes, and the side length U of the front bridge is 0.79-0.88 times Q. The fin angle S is 63-71°, and the opening angle V is 24-35°. The bridge spacing T between the two fifth bridges 5 is equal to the width R, and is 0.95-1.05cm. For example: bridge height = 0.54 × fin spacing = 0.702mm; rear bridge Q = 2.1d = 13.02mm, bridge width R = 0.36d = 2.23mm; fin angle S = 67°, opening angle V = 28°; R / T = 1; front bridge U = 0.84Q = 10.94mm; arranged vertically along the ROC, with condensate falling vertically along the bridge walls.

[0043] In a preferred embodiment of this invention, the distance between the left outer edge and the right outer edge of the fin is the width W of the fin, and the maximum value of the width W is W0. max Located between L2 and L5, with a minimum width W. min Located between L1 and L4 or between L3 and L6, W min = (0.79 ± 10%) W max。 The width of the middle section is greater than that of the upper and lower sections, which forces the high-speed airflow in the middle to move upwards and downwards, thus homogenizing the airflow field. The width dimension has been optimized to improve the utilization rate of the heat exchange area without increasing wind resistance.

[0044] In a preferred embodiment of this invention, the overall height H and width W of the fins are... max The aspect ratio is 3.3 ± 5%. It features a golden aspect ratio, is compatible with standard ducted air conditioning units, and can be installed without increasing the size of the enclosure.

[0045] In a preferred embodiment of this invention, the height H1 of the upper section is 35% ± 10% of the overall fin height H, the height H2 of the middle section is 22% ± 10% of the overall fin height H, and the height H3 of the lower section is 42% ± 10% of the overall fin height H. The lower section has the highest height and the most ducts, allowing it to receive high-speed airflow and thus maximizing heat exchange capacity.

[0046] In a preferred embodiment of this invention, the number of holes in the upper, middle, and lower regions is three or four.

[0047] In a preferred embodiment of this invention, dummy tangent lines are provided between the rows of holes in the upper, middle, and lower regions. The dummy tangent lines adjacent to the leeward side are leeward side heat insulation dummy tangents, and the dummy tangent lines adjacent to the windward side are windward side heat insulation dummy tangents. For example... Figure 2 As shown, G1, G3, G5 and G2, G4, G6 are inter-row tangent lines, which increase the heat transfer coefficient between adjacent rows. The shapes of G1, G3, and G5 correspond to the outer contours of G2, G4, and G6, achieving optimal heat transfer resistance and serving as part of the heat resistance curve design. G1-G3-G5 is the leeward side insulation tangent, and G2-G4-G6 is the windward side insulation tangent.

[0048] As a preferred embodiment of this invention, the upper, middle, and lower sections of the heat exchange main body of the fin adopt a unified basic hole spacing D1, where D1 is 3 to 4 times the tube hole diameter D. The transverse and longitudinal hole spacings of the middle section are both equal to D1. Based on the square uniform tube hole grid structure, the same type of span hairpin heat exchange copper tube can be arranged either upright or obliquely, adapting to various refrigerant diversion paths such as N-type, S-type, and Z-type. Only one set of punching molds is needed to complete the processing of the entire fin, reducing the specifications of copper tube materials and improving the overall production efficiency of the heat exchanger.

[0049] In a preferred embodiment of this invention, the upper and lower ends of the outer right edge of the fin are chamfered structures, and the sealing lines L8 and L10 are the sealing sections of the upper and lower chamfered structures, respectively. L7-L8 constitute the upper sealing edge, and L10-L9 constitute the lower sealing edge.

[0050] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A multi-segment integrated air conditioning heat exchanger fin with three-field synergistic enhanced heat exchange, wherein the fin body is an integrated structure, and the fin body is provided with tube holes to facilitate the passage of heat exchange tubes. The fin body is divided into an upper section, a middle section, and a lower section from top to bottom. The outer edge line OCL of the fin is composed of multiple line segments, including the main line segments L1, L2, L3, L4, L5, L6 and the sealing line segments L7, L9. The main line segments and the sealing line segments are connected in a clockwise order as follows: L1-L7-L4-L5-L6-L9-L3-L2. The leeward side of the left outer edge of the fin, which has an overall trend of curving to the left, is formed by the main line segments L1, L2, and L3. The windward side of the right outer edge of the fin, which also has an overall trend of curving to the left, is formed by the main line segments L4, L5, and L6. in, The two endpoints of L2 are P1 and P2, and the two endpoints of L5 are P3 and P4. The line connecting endpoints P1 and P3 is L. 13 The line connecting P2 and P4 is L. 24 L2, L 13 L5, L 24 The fin region between them is the middle section region, L 13 The finned area mentioned above is the upper section region, L 24 The finned area below is the lower section region; The feature is that multiple tube holes are arranged sequentially along the length of the fin body to form a hole row, the number of hole rows in the upper section, middle section and lower section are the same, and the number of tube holes in the lower section is greater than the number of tube holes in the upper section; a heat exchange strengthening bridging structure is formed by stamping between the tube holes in each section along the length of the fin body, wherein the upper section is provided with four bridges, the lower section with three bridges, and the middle section with long double bridges.

2. The multi-segment integrated air conditioning heat exchanger fins with three-field synergistic enhanced heat exchange as described in claim 1, characterized in that, The four bridges include a first bridge located in the middle, of the same size and symmetrically distributed, and second bridges of the same size and symmetrically arranged on both sides of the first bridge. The height 'a' of the first and second bridges is 0.5-0.8 mm. The rear bridge side length 'd' of the second bridge is equal to 1.65-1.76 times the inner diameter of the heat exchange tube, and the width 'e' is equal to 0.18-0.24 times the inner diameter of the heat exchange tube. The rear bridge side length 'g' of the first bridge is equal to 0.55-0.75 times 'd'. The width 'h' of the first bridge is equal to the width 'e' of the second bridge. The opening angle 'c' of the first bridge is 23-29°, and the opening angle 'b' of the second bridge is 18-26°. The bridge spacing 'f' between the first and second bridges is equal to 0.24-0.32 times the inner diameter of the heat exchange tube.

3. The multi-segment integrated air conditioning heat exchanger fins with three-field synergistic enhanced heat exchange as described in claim 1, characterized in that, The three bridges include a third bridge in the middle and a fourth bridge of the same size and symmetrically arranged on both sides of the third bridge. The rear bridge side length j of the fourth bridge is 1.62-1.78 times the inner diameter of the heat exchange tube, the front bridge side length K is 1.16-1.32 times the diameter of the heat exchange tube, the width N is equal to 0.32-0.53 times the inner diameter of the heat exchange tube, and the angle M is 52-67°. The rear bridge side length L of the third bridge is equal to 0.76-0.92 times the size K. The bridge spacing P between the third bridge and the fourth bridge is equal to 0.35-0.45 times the inner diameter of the heat exchange tube.

4. The multi-segment integrated air conditioning heat exchanger fins with three-field synergistic enhanced heat exchange as described in claim 1, characterized in that, The second long bridge includes two fifth bridges of the same size and arranged symmetrically. The width R of the fifth bridge is 0.32-0.42 times the inner diameter of the heat exchange tube, the side length Q of the rear bridge is 2.02-2.25 times the inner diameter of the heat exchange tube, the side length U of the front bridge is 0.79-0.88 times Q, the opening angle S is 63-71°, the opening angle V is 24-35°, and the bridge spacing T between the two fifth bridges is equal to the width R, which is 0.95-1.05cm.

5. The multi-segment integrated air conditioning heat exchanger fins with three-field synergistic enhanced heat transfer as described in any one of claims 1-4, characterized in that, The distance between the outer left edge and the outer right edge of the fin is the width W of the fin, and the maximum value of the width W is W0. max Located between L2 and L5, with a minimum width W. min Located between L1 and L4 or between L3 and L6, W min = (0.79 ± 10%) W max。 6. The multi-segment integrated air conditioning heat exchanger fins with three-field synergistic enhanced heat exchange as described in claim 5, characterized in that, The overall height H and width W of the fins max The ratio is 3.3 ± 5%.

7. The multi-segment integrated air conditioning heat exchanger fins with three-field synergistic enhanced heat exchange as described in claim 6, characterized in that, The height H1 of the upper section is 35% ± 10% of the overall fin height H, the height H2 of the middle section is 22% ± 10% of the overall fin height H, and the height H3 of the lower section is 42% ± 10% of the overall fin height H.

8. The multi-segment integrated air conditioning heat exchanger fins with three-field synergistic enhanced heat exchange as described in claim 1, characterized in that, The upper, middle, and lower sections of the copper tubes are provided with inter-row tangent lines. The inter-row tangent line adjacent to the leeward side is a leeward side heat insulation tangent line, and the inter-row tangent line adjacent to the windward side is a windward side heat insulation tangent line, which is used to block the lateral heat conduction of adjacent copper tubes.

9. The multi-segment integrated air conditioning heat exchanger fins with three-field synergistic enhanced heat exchange as described in claim 1, characterized in that, The upper, middle, and lower sections of the heat exchange main area of ​​the fins adopt a unified basic hole spacing D1, where D1 is 3 to 4 times the pipe hole diameter D. The transverse and longitudinal hole spacings of the middle section are both equal to D1. Based on the square uniform pipe hole grid structure, the same type of span hairpin heat exchange copper tube can be arranged either upright or obliquely, adapting to various refrigerant diversion paths such as N-type, S-type, and Z-type.

10. The multi-segment integrated air conditioning heat exchanger fins with three-field synergistic enhanced heat exchange as described in claim 1, characterized in that, The upper and lower ends of the outer right edge of the fin are chamfered structures. The sealing lines L8 and L10 are the sealing sections of the upper and lower chamfered structures, respectively. L7-L8 constitute the upper sealing edge, and L10-L9 constitute the lower sealing edge.

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