Multi-section integrated fin for heat exchanger

Abstract

The invention discloses a multi-section integrated fin for a heat exchanger, and belongs to the technical field of air conditioning devices. The technical problems that in the prior art, a traditional V-shaped heat exchanger is poor in drainage and waste in heat exchange efficiency, the wind field of a centrifugal fan is uneven, the heat exchanger cannot be completely matched with the wind field, the wind field collaboration of the heat exchanger is poor, and the production efficiency is low are solved. A fin body is of an integrated structure, pipe holes allowing heat exchange pipes to penetrate through conveniently are distributed in the fin body, and the fin body is divided into an upper section area, a middle section area and a lower section area from top to bottom. The outer edge line OCL of the fin is formed by connecting a plurality of line segments and comprises a fin body main line segment, edge sealing line segments L7 and L9, a leeward side with the overall trend of the outer edge of the left side of the fin bending leftwards and a windward side with the overall trend of the outer edge of the right side of the fin bending leftwards. The connecting line of the midpoint of the L2 and the midpoint of the L5 is a fin reference line ROC1, and the number of holes located in the upper portion fin and the number of holes located in the lower portion fin of the fin reference line ROC1 are different.

Description

Technical Field

[0001] The invention relates to the technical field of air conditioning devices, and in particular to a multi-section integrated fin for a heat exchanger. Background Art

[0002] The traditional V-type heat exchanger adopts a two-piece hot-joint splicing solution, and the splicing place is sealed with a sealing strip, which has problems such as poor drainage and waste of heat exchange efficiency. The wind field of the centrifugal fan is uneven, the heat exchanger cannot fully adapt to the wind field, and the heat exchanger wind field coordination is poor. The production efficiency of splicing two independent sub-assemblies is low and cannot reach the production efficiency of an integrated heat exchanger.

[0003] The existing V-shaped heat exchanger fins cannot be processed in one piece, the process is complicated and the sealing strip affects some heat exchange performance. The one-piece fin is a symmetrical design and cannot perfectly match the wind farm heat exchange. The existing technical solution has a high proportion of three-row heat exchangers, and the overall wind resistance and heat exchange synergy are poor, which cannot achieve a balance between heat exchange efficiency and cost.

[0004] In evaporation conditions, due to the high proportion of the three rows in the middle of the arc and the wind-guiding effect of the fins, the condensate in the upper part is not drained well, resulting in increased wind resistance and a decrease in the heat transfer coefficient, affecting the wet condition capacity. Summary of the invention

[0005] In view of the shortcomings and deficiencies in the prior art, the present invention provides a multi-section integrated fin for a heat exchanger that adopts a three-row tube hole area with fewer holes in the middle and a vertical design, combined with the sheet-type wind rectification effect, to achieve rapid discharge of condensed water under evaporation conditions, solve current industry shortcomings, improve evaporation heat exchange efficiency and reduce wind resistance.

[0006] To achieve the above objectives, the present invention is implemented through the following technical solutions: The multi-section integrated fin for a heat exchanger provided by the present invention has an integrated structure, the fin body is provided with tube holes for heat exchange tubes to pass through, and the fin body is divided into three sections from top to bottom: an upper section, a middle section, and a lower section;

[0007] The fin outer edge line OCL is composed of a plurality of line segments, including sheet body main line segments L1, L2, L3, L4, L5, L6 and edge banding line segments L7, L9, and the main line segments and edge banding line segments are connected in a clockwise order: L1-L7-L4-L5-L6-L9-L3-L2; the leeward side of the left outer edge of the fin, where the overall trend is to bend to the left, is composed of the sheet body main line segments L1, L2, and L3 main line segments to form the left outer edge of the fin; the windward side of the right outer edge of the fin, where the overall trend is also to bend to the left, is composed of the sheet body main line segments L4, L5, and L6 main line segments to form the right outer edge of the fin;

[0008] Among them, L1 and L2 intersect at point P1, L2 and L3 intersect at point P2, L4 and L5 intersect at point P3, and L5 and L6 intersect at point P4; the fin area between P1, P2, P3 and P4 is the middle area, the fin area above the line connecting P1 and P3 is the upper area, and the fin area below the line connecting P2 and P4 is the lower area;

[0009] The line connecting the midpoint of the main line segment L2 of the fin body and the midpoint of L5 is the fin reference line ROC1, and the number of holes on the upper and lower parts of the fin located on the fin reference line ROC1 is different.

[0010] Preferably, the upper and lower ends of the right outer edge of the fin are chamfered structures respectively, the edge sealing lines L8 and L10 are the edge sealing sections of the upper and lower chamfered structures respectively, L7-L8 constitute the upper edge sealing, and L10-L9 constitute the lower edge sealing.

[0011] Preferably, the length ratio of L1 to L4 is 1.189±10%; the length ratio of L3 to L6 is 1.159±10%;

[0012] The length ratio of the main line segments L2 and L1 is 0.529±10%, the length ratio of L2 and L3 is 0.457±10%; the length ratio of L2 and L5 is 1.

[0013] Preferably, the direction from left to right along the reference line ROC1 is the first reference direction, the angle α1 between L1 and the reference line ROC1 along the first reference direction is 40-45°, and the ratio of the angle between L4 and the reference line ROC1 along the first reference direction to the angle between L1 and the reference line ROC1 along the first reference direction is 1;

[0014] The angle α2 between L2 and the reference line ROC1 along the first reference direction is 85-95°, and the ratio of the angle between L5 and the reference line ROC1 along the first reference direction to the angle between L2 and the reference line ROC1 along the first reference direction is 1;

[0015] The angle α3 between L3 and the reference line ROC1 along the first reference direction is 40-45°, and the ratio of the angle between L6 and the reference line ROC1 along the first reference direction to the angle between L3 and the reference line ROC1 along the first reference direction is 1;

[0016] The extension lines of the main line segments L1 and L3 on the left outer edge of the fin intersect on the reference line ROC1, and the angle α4 between the extension lines is 80-90°.

[0017] Preferably, L5 is set using the vertical reference line ROC1, and the drainage low resistance ratio H2 / H is 0.25-0.3, wherein H2 is the height of the middle area and H is the overall height of the fin body.

[0018] Preferably, the distance between the left outer edge and the right outer edge of the fin is the width W of the fin, the maximum value Wmax of the width W is between L2 and L5, the minimum value Wmin of the width W is between L1 and L4 or between L3 and L6, and Wmin=(0.667±10%)Wmax;

[0019] The height H1 of the upper section area is 33.89% of the overall height H of the fin ± 10% deviation, the height H2 of the middle section area is 26.82% of the overall height H of the fin ± 10% deviation, and the height H3 of the lower section area is 39.29% of the overall height H of the fin ± 10% deviation;

[0020] The ratio of the overall fin height H to the width Wmax is 3.987±10%.

[0021] Preferably, each row of tube holes on each section of the fin body is distributed at intervals, the tube row line formed by connecting the centers of each row of tube holes in the upper section in sequence is parallel to L1 or L4, the tube row line formed by connecting the centers of each row of tube holes in the middle section in sequence is parallel to L2 or L5, and the tube row line formed by connecting the centers of each row of tube holes in the lower section in sequence is parallel to L3 or L6.

[0022] Preferably, the tube holes on each section of the fin body are arranged in 2 or 3 rows;

[0023] The pores in the upper region are located above ROC1 and are arranged in two rows, the pores in the middle region pass through ROC1 and are arranged in three rows, and the pores in the lower region are located below ROC1 and are arranged in two rows.

[0024] Preferably, the ratio of the distance D1 between the tube hole on the tube arrangement line and the nearest main line segment to the tube hole diameter D in the upper section is 1.1 to 1.7.

[0025] The ratio of the distance D2 between the tube hole on the tube arrangement line and the nearest main line segment to the tube hole diameter D in the middle section is in the range of 1.2 to 1.6.

[0026] The ratio of the distance D3 between the tube hole on the tube arrangement line and the nearest main line segment in the lower section area and the diameter D of the tube hole is in the range of 1.2 to 1.6.

[0027] Preferably, the ratio of the center distance D4 of the two rows of tube holes in the upper section and the lower section to the tube hole diameter D is 2.82±10%.

[0028] The ratio of the distance D5 between the centers of each row of pores in the middle section to the pore diameter D is 2.78±10%;

[0029] The ratio of the shortest distance D6 from the center of the tube hole closest to the edge sealing line segment to the edge line of the edge sealing line segment to the diameter D of the tube hole is in the range of 1.25 to 1.55.

[0030] Preferably, the tube holes on the fin body adopt two tube spacings, namely D7 and D8, D7 is 16-18mm, D8 is 13-15mm, wherein the tube spacing of the three rows of tube holes in the middle section adopts the D7 tube spacing; the tube spacing of the two rows of tube holes in the upper section and the lower section adopts the D8 design,

[0031] Among them, near the bottom area of ​​the water receiving tray, a tube hole is set to facilitate the oblique insertion of the heat exchange copper tube, and the hole spacing is D7;

[0032] The ratio of the shortest distance D6 from the center of the tube hole closest to the edge sealing line segment to the edge line of the edge sealing line segment to the tube hole diameter D is in the range of 1.28 to 1.55.

[0033] The present invention provides a multi-section integrated fin for a heat exchanger. The fin has the following beneficial effects:

[0034] The multi-stage integrated fins for heat exchangers of the present invention can improve production efficiency and adapt to the heat exchange wind field with uneven heat exchange of the duct machine, and the overall performance is better. The heat exchanger is asymmetrically designed with different numbers of upper and lower holes, which better adapts to the differences in wind fields and realizes the performance of field synergy.

[0035] The innovative use of the three-row area in the middle and its vertical design, combined with the sheet-type wind rectification effect, achieves the rapid discharge of condensed water in the evaporation condition, solves the current shortcomings of the industry, improves the evaporation heat exchange efficiency and reduces wind resistance. Among them, the three-row tube hole area in the middle section matches the area with the maximum wind speed. Under the premise of ensuring the same number of holes, the overall double-row tube hole design is adopted to improve the maximum heat exchange efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] Figure 1 It is a structural schematic diagram of the multi-section integrated fin of the present invention;

[0037] Figure 2 This is a schematic diagram of the tube hole distribution structure on the multi-stage integrated fin of the present invention;

[0038] Figure 3 It is a schematic diagram of the distribution of tube holes and corresponding dimension marking structure of the multi-stage integrated fin of the present invention;

[0039] Figure 4 This is a schematic diagram of the manufacturing structure of the multi-section integrated fin of the present invention formed by direct punching and cutting of sheet material;

[0040] Figure 5 It is a structural schematic diagram of the multi-section integrated fin of the present invention according to the usage state.

[0041] In the figure: fin outer edge line OCL; along the reference line ROC1; sheet main line segments L1, L2, L3, L4, L5, L6 and edge banding line segments L7, L8, L9, L10; L1 and L2 intersect at point P1, L2 and L3 intersect at point P2, L4 and L5 intersect at point P3, L5 and L6 intersect at point P4. DETAILED DESCRIPTION

[0042] The technical solutions in the embodiments of the present invention will be described clearly and completely below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments.

[0043] See also Figure 1-Figure 5 , the present invention provides a technical solution:

[0044] like Figure 1-Figure 2 As shown, the multi-section integrated fin for a heat exchanger provided by the present invention has an integrated structure of the fin body, the fin body is provided with tube holes for the heat exchange tubes to pass through, and the fin body is divided into three areas from top to bottom, namely, an upper area, a middle area, and a lower area.

[0045] 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 of the sheet body and the edge sealing line segments L7 and L9. The upper and lower ends of the right outer edge of the fin are chamfered structures respectively. The edge sealing lines L8 and L10 are the edge sealing sections of the upper and lower chamfered structures respectively. L7-L8 constitute the upper edge sealing, and L10-L9 constitute the lower edge sealing.

[0046] The clockwise connection sequence of the main line segments and the edge banding line segments is: L1-L7-L8-L4-L5-L6-L10-L9-L3-L2; the leeward side where the overall trend of the left outer edge of the fin is bent to the left is composed of the main line segments L1, L2, and L3 of the sheet body; the windward side where the overall trend of the right outer edge of the fin is also bent to the left is composed of the main line segments L4, L5, and L6 of the sheet body; L4, L5, and L6 constitute the inner drainage curve. The contours of the inner side L4-L5-L6 and the outer side L1-L2-L3 of the multi-segment one body are completely matched and defined as a continuous curve, which can realize seamless connection of the front and rear fins, and no waste in the middle continuous processing.

[0047] L1 and L2 intersect at point P1, L2 and L3 intersect at point P2, L4 and L5 intersect at point P3, and L5 and L6 intersect at point P4; the fin area between P1, P2, P3 and P4 is the middle area, the fin area above the line connecting P1 and P3 is the upper area, and the fin area below the line connecting P2 and P4 is the lower area.

[0048] The line connecting the midpoint of the main line segment L2 of the fin body and the midpoint of L5 is the fin reference line ROC1. The number of holes on the upper and lower parts of the fins located on the fin reference line ROC1 is different. The heat exchanger is designed asymmetrically. This fin structure design can correspond to uneven heat exchange wind fields, better adapt to wind field differences, significantly improve the heat exchange performance of the heat exchanger, and achieve field synergy performance.

[0049] like Figure 2 As shown, according to the relationship between the number of rows of the tube holes through which the heat exchange tube passes and the first reference line ROC1, the fin body is divided into three sections: the upper section, the middle section, and the lower section. The tube holes G in each section of the fin body are arranged in 2 or 3 rows; the tube holes in the upper section are located above ROC1 and arranged in 2 rows, the tube holes in the middle section pass through ROC1 and are arranged in 3 rows, and the tube holes in the lower section are located below ROC1 and are arranged in 2 rows. The tube hole distribution of this structural design corresponds to the wind field flow rate. The flow rate in the middle section is large, and more tube rows are set, while the flow rate in the upper and lower sections is small, and fewer tube rows are set.

[0050] like Figure 1 As shown, the multi-section integrated fin for heat exchanger provided by the present invention has a length ratio of main line segment L1 to L4 of 1.189±10%; a length ratio of L3 to L6 of 1.159±10%; a length ratio of main line segment L2 to L1 of 0.529±10%, a length ratio of L2 to L3 of 0.457±10%; and a length ratio of L2 to L5 of 1. When manufacturing the fin with this structural design, it can be formed by direct stamping and cutting of sheet material, which significantly reduces waste during processing and reduces production costs.

[0051] The direction from left to right along the reference line ROC1 is the first reference direction, the angle α1 between L1 and the reference line ROC1 along the first reference direction is 40-45°, and the ratio of the angle between L4 and the reference line ROC1 along the first reference direction to the angle between L1 and the reference line ROC1 along the first reference direction is 1.

[0052] The angle α2 between L2 and the reference line ROC1 along the first reference direction is 85-95°, and the ratio of the angle between L5 and the reference line ROC1 along the first reference direction to the angle between L2 and the reference line ROC1 along the first reference direction is 1. The angle α3 between L3 and the reference line ROC1 along the first reference direction is 40-45°, and the ratio of the angle between L6 and the reference line ROC1 along the first reference direction to the angle between L3 and the reference line ROC1 along the first reference direction is 1.

[0053] The extension lines of the main line segments L1 and L3 on the left outer edge of the fin of the present invention intersect on the reference line ROC1, and the angle α4 between the extension lines is 80-90°. This angle design can balance the fin area and airflow smoothness.

[0054] The distance between the left outer edge and the right outer edge of the fin is the width W of the fin. The maximum value Wmax of the width W is between L2 and L5, and the minimum value Wmin of the width W is between L1 and L4 or between L3 and L6. Wmin=(0.667±10%)Wmax.

[0055] L5 corresponds to the three-row tube hole heat exchanger area. L5 is set with the vertical reference line ROC1, and the drainage low resistance ratio H2 / H is 0.25-0.3. This design is conducive to the rapid discharge of condensed water in the evaporation condition under the premise of fin rectification of uneven wind field, reducing wind resistance and improving heat transfer coefficient.

[0056] Among them, H2 is the height of the middle area, and H is the overall height of the fin body. The height H1 of the upper area is 33.89% ± 10% of the overall height H of the fin, the height H2 of the middle area is 26.82% ± 10% of the overall height H of the fin, and the height H3 of the lower area is 39.29% ± 10% of the overall height H of the fin; the ratio of the overall height H of the fin to the width Wmax is 3.987 ± 10%, H1 = 0.669L1 ± 10%. The wind field with a larger flow rate corresponds to the middle area, and the wind field with a smaller flow rate corresponds to the upper and lower areas. The upper and lower heat exchange lengths and areas are different, matching the wind field heat exchange synergy, making the heat exchange more uniform and improving performance.

[0057] Each row of tube holes on each section of the fin body is distributed at intervals. The tube row line formed by connecting the centers of each row of tube holes in the upper section is parallel to L1 or L4, the tube row line formed by connecting the centers of each row of tube holes in the middle section is parallel to L2 or L5, and the tube row line formed by connecting the centers of each row of tube holes in the lower section is parallel to L3 or L6.

[0058] In the upper area, the ratio of the distance D1 of the pipe hole on the pipe arrangement line from the nearest main line segment to the pipe hole diameter D is 1.1-1.7, the ratio of the distance D2 of the pipe hole on the pipe arrangement line from the nearest main line segment to the pipe hole diameter D in the middle area ranges from 1.2 to 1.6, and the ratio of the distance D3 of the pipe hole on the pipe arrangement line from the nearest main line segment to the pipe hole diameter D in the lower area ranges from 1.2 to 1.6.

[0059] The ratio of the center distance D4 of the two rows of tube holes in the upper and lower sections to the tube hole diameter D is 2.82±10%, and the ratio of the center distance D5 of each row of tube holes in the middle section to the tube hole diameter D is 2.78±10%. Among them, the ratio of the shortest distance D6 from the center of the tube hole closest to the edge sealing line segment to the edge line of the edge sealing line segment to the tube hole diameter D is in the range of 1.25 to 1.55.

[0060] The tube holes on the fin body adopt two kinds of tube spacing, namely D7 and D8, D7 is 16-18mm, and D8 is 13-15mm. Among them, the tube spacing of the three rows of tube holes in the middle area adopts D7 tube spacing, which is conducive to the best field synergistic heat exchange of the three rows of wind resistance and drainage. The tube spacing of the upper and lower sections of the upper two rows of tube holes adopts D8 design, which is conducive to the best field synergistic heat exchange with the fin width. Among them, near the bottom area of ​​the water tray, tube holes are set for the oblique insertion of heat exchange copper tubes. The hole spacing is D7, which is conducive to the rapid discharge of the bottom water and the improvement of the heat transfer coefficient, while making full use of the fin area.

[0061] The ratio of the shortest distance D6 from the center of the tube hole closest to the edge sealing line segment to the edge line of the edge sealing line segment to the tube hole diameter D is in the range of 1.28 to 1.55.

[0062] like Figure 5 As shown, an enhanced heat exchange design of opening bridges or opening windows is adopted between adjacent copper tubes on the fin body. The number and shape of the opening windows and opening bridges are classified and designed according to parameters such as wind field heat exchange and drainage resistance, and 2-4 types are preferred.

[0063] like Figure 3 As shown, T1, T2, T3 and T4 are virtual tangent lines between adjacent rows, which play a role in process processing and increase the heat transfer coefficient between adjacent rows. Among them, the T1-T2-T3 shape corresponds to the L1-L2-L3 profile, plays the role of optimal heat resistance transfer, and is designed as a heat resistance curve.

[0064] In summary, the multi-stage integrated fin structure for the heat exchanger of the present invention is ingenious and has low manufacturing cost. The multi-stage integrated fin can significantly improve production efficiency and adapt to the heat exchange wind field with uneven heat exchange of the duct machine, and the overall performance is better.

[0065] Among them, the innovative use of three rows of tube holes in the middle area and its vertical design matches the area with the maximum wind speed. Under the premise of ensuring the same number of holes, the overall double-row tube hole design is adopted to improve the maximum heat exchange efficiency. The heat exchanger is asymmetrically designed with different numbers of holes in the upper and lower parts to better adapt to the differences in wind fields and achieve field synergy performance. Combined with the sheet-type wind rectification effect, the rapid discharge of condensed water in evaporation conditions is achieved, solving the current shortcomings of the industry, significantly improving the evaporation heat exchange efficiency and reducing wind resistance.

[0066] The above are merely embodiments of the present invention. For example, an enhanced heat exchange design with open bridges or windows is adopted between adjacent copper tubes on the fin body. The number and shape of the windows and bridges are classified and designed according to parameters such as wind field heat exchange and drainage resistance. The multi-section integrated fins for heat exchangers of the present invention can be realized.

[0067] The above description is only a preferred specific implementation manner of the present invention, but the protection scope of the present invention is not limited thereto. Any technician familiar with the technical field can make equivalent replacements or changes according to the technical scheme and inventive concept of the present invention within the technical scope disclosed by the present invention, which should be covered by the protection scope of the present invention.

Claims

1. A multi-stage integrated fin for a heat exchanger, characterized in that: The fin body is an integrated structure, and the fin body is provided with tube holes for the heat exchange tubes to pass through. The fin body is divided into three areas from top to bottom: an upper area, a middle area, and a lower area; The fin outer edge line OCL is composed of a plurality of line segments, including sheet body main line segments L1, L2, L3, L4, L5, L6 and edge banding line segments L7, L9, and the main line segments and edge banding line segments are connected in a clockwise order: L1-L7-L4-L5-L6-L9-L3-L2; the leeward side of the left outer edge of the fin, where the overall trend is to bend to the left, is composed of the sheet body main line segments L1, L2, and L3 main line segments to form the left outer edge of the fin; the windward side of the right outer edge of the fin, where the overall trend is also to bend to the left, is composed of the sheet body main line segments L4, L5, and L6 main line segments to form the right outer edge of the fin; Among them, L1 and L2 intersect at point P1, L2 and L3 intersect at point P2, L4 and L5 intersect at point P3, and L5 and L6 intersect at point P4; the fin area between P1, P2, P3 and P4 is the middle area, the fin area above the line connecting P1 and P3 is the upper area, and the fin area below the line connecting P2 and P4 is the lower area; The line connecting the midpoint of the main line segment L2 of the fin body and the midpoint of L5 is the fin reference line ROC1, and the number of holes on the upper and lower parts of the fin located on the fin reference line ROC1 is different.

2. The multi-section integrated fin for a heat exchanger according to claim 1, characterized in that: The upper and lower ends of the right outer edge of the fin are chamfered structures respectively, and the edge sealing lines L8 and L10 are the edge sealing sections of the upper and lower chamfered structures respectively, L7-L8 constitute the upper edge sealing, and L10-L9 constitute the lower edge sealing.

3. The multi-section integrated fin for a heat exchanger according to claim 2, characterized in that: The length ratio of L1 to L4 is 1.189±10%; the length ratio of L3 to L6 is 1.159±10%; The length ratio of the main line segments L2 to L1 is 0.529±10%, the length ratio of L2 to L3 is 0.457±10%; the length ratio of L2 to L5 is 1.

4. The multi-section integrated fin for a heat exchanger according to claim 1, characterized in that: The direction from left to right along the reference line ROC1 is the first reference direction, the angle α1 between L1 and the reference line ROC1 along the first reference direction is 40-45°, and the ratio of the angle between L4 and the reference line ROC1 along the first reference direction to the angle between L1 and the reference line ROC1 along the first reference direction is 1; The angle α2 between L2 and the reference line ROC1 along the first reference direction is 85-95°, and the ratio of the angle between L5 and the reference line ROC1 along the first reference direction to the angle between L2 and the reference line ROC1 along the first reference direction is 1; The angle α3 between L3 and the reference line ROC1 along the first reference direction is 40-45°, and the ratio of the angle between L6 and the reference line ROC1 along the first reference direction to the angle between L3 and the reference line ROC1 along the first reference direction is 1; The extension lines of the main line segments L1 and L3 on the left outer edge of the fin intersect on the reference line ROC1, and the angle α4 between the extension lines is 80-90°.

5. According to the multi-stage integrated fin for heat exchanger of claim 4, L5 is set by vertical reference line ROC1, and the drainage low resistance ratio H2 / H is 0.25-0.3, wherein, H2 is the height of the middle area, and H is the overall height of the fin body.

6. The multi-section integrated fin for a heat exchanger according to claim 1, characterized in that: The distance between the left outer edge and the right outer edge of the fin is the width W of the fin, the maximum value Wmax of the width W is between L2 and L5, the minimum value Wmin of the width W is between L1 and L4 or between L3 and L6, Wmin = (0.667 ± 10%) Wmax; The height H1 of the upper section area is 33.89% of the overall height H of the fin ± 10% deviation, the height H2 of the middle section area is 26.82% of the overall height H of the fin ± 10% deviation, and the height H3 of the lower section area is 39.29% of the overall height H of the fin ± 10% deviation; The ratio of the overall fin height H to the width Wmax is 3.987±10%.

7. The multi-section integrated fin for a heat exchanger according to claim 1, characterized in that: Each row of tube holes on each section of the fin body is distributed at intervals, the tube row line formed by connecting the centers of each row of tube holes in the upper section is parallel to L1 or L4, the tube row line formed by connecting the centers of each row of tube holes in the middle section is parallel to L2 or L5, and the tube row line formed by connecting the centers of each row of tube holes in the lower section is parallel to L3 or L6.

8. The multi-section integrated fin for a heat exchanger according to claim 7, characterized in that: The tube holes on each section of the fin body are arranged in 2 or 3 rows; The pores in the upper section are located above ROC1 and are arranged in two rows, the pores in the middle section pass through ROC1 and are arranged in three rows, and the pores in the lower section are located below ROC1 and are arranged in two rows.

9. The multi-section integrated fin for a heat exchanger according to claim 8, characterized in that: The ratio of the distance D1 between the tube hole on the tube arrangement line and the nearest main line segment to the tube hole diameter D in the upper section is 1.1 to 1.

7. The ratio of the distance D2 between the tube hole on the tube arrangement line and the nearest main line segment to the tube hole diameter D in the middle section is in the range of 1.2 to 1.

6. The ratio of the distance D3 between the tube hole on the tube arrangement line and the nearest main line segment in the lower section area and the diameter D of the tube hole is in the range of 1.2 to 1.

6.

10. The multi-section integrated fin for a heat exchanger according to claim 8, characterized in that: The ratio of the center distance D4 of the two rows of tube holes in the upper section and the lower section to the tube hole diameter D is 2.82±10%, The ratio of the distance D5 between the centers of each row of pores in the middle section to the pore diameter D is 2.78±10%; The ratio of the shortest distance D6 from the center of the tube hole closest to the edge sealing line segment to the edge line of the edge sealing line segment to the diameter D of the tube hole is in the range of 1.25 to 1.

55.

11. The multi-section integrated fin for a heat exchanger according to claim 8, characterized in that: The tube holes on the fin body adopt two tube spacings, namely D7 and D8, D7 is 16-18mm, D8 is 13-15mm, wherein the tube spacing of the three rows of tube holes in the middle section adopts the D7 tube spacing; the tube spacing of the two rows of tube holes in the upper section and the lower section adopts the D8 design, Among them, near the bottom area of ​​the water receiving tray, a tube hole is set to facilitate the oblique insertion of the heat exchange copper tube, and the hole spacing is D7; The ratio of the shortest distance D6 from the center of the tube hole closest to the edge sealing line segment to the edge line of the edge sealing line segment to the tube hole diameter D is in the range of 1.28 to 1.55.

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