CN213120240U - Heat exchanger - Google Patents

Abstract

The utility model discloses a heat exchanger. The heat exchanger comprises heat exchange fins and a heat exchange tube, wherein the heat exchanger comprises the heat exchange fins and the heat exchange tube; the heat exchange tube is arranged in the tube hole in a penetrating way, and on a reference section formed by a plane where the main surface of the heat exchange fin is located, the shape of the heat exchange tube is consistent with that of the tube hole; the pipe hole is provided with a long axis direction and a short axis direction, and the long axis size of the pipe hole along the long axis direction is larger than the short axis size along the short axis direction; the heat exchange fins comprise windward side contour lines and leeward side contour lines which are arranged at intervals, the long axis direction of each tube hole and the windward side contour lines form an intersection point, and the included angle between the tangent direction of the intersection point and the long axis direction is 70-110 degrees. Through the mode, the long axis direction of the pipe hole is approximately parallel to the wind inlet direction, so that the area of a heat exchange dead zone on the leeward side of the heat exchange pipe and the flow resistance of air are reduced.

Description

Heat exchanger

Technical Field

The utility model relates to an air conditioner technical field, concretely relates to heat exchanger.

Background

At present, in an air conditioning device, a heat exchanger based on heat exchange fins is mostly adopted to realize a heat exchange function. Particularly, the heat exchange tubes are arranged on the plurality of heat exchange fins at intervals in a penetrating mode, the heat exchange tubes serve as flow channels of heat exchange media, gaps among the heat exchange fins serve as airflow channels, and airflow generated by the fan exchanges heat with the heat exchange media in the flowing process of the airflow channels.

At present, a heat exchange tube applied to a heat exchanger is generally a round tube, and a leeward side of the round tube is easy to generate a heat exchange dead zone. And the heat exchange effect of the fin part in the heat exchange dead zone is deteriorated. In addition, the narrow tube spacing between adjacent circular heat exchange tubes results in increased ventilation resistance as the air flow passes through the narrow passages.

SUMMERY OF THE UTILITY MODEL

The utility model provides a heat exchanger to reduce the heat transfer blind spot, strengthen the heat transfer effect, and can reduce the flow resistance of air current.

In order to solve the technical problem, the utility model discloses a technical scheme be: the heat exchanger comprises heat exchange fins and a heat exchange tube, wherein the heat exchange fins are provided with tube holes; the heat exchange tube is arranged in the tube hole in a penetrating way, and on a reference section formed by a plane where the main surface of the heat exchange fin is located, the shape of the heat exchange tube is consistent with that of the tube hole; the pipe hole is provided with a long axis direction and a short axis direction, and the long axis size of the pipe hole along the long axis direction is larger than the short axis size along the short axis direction; the heat exchange fins comprise windward side contour lines and leeward side contour lines which are arranged at intervals, the long axis direction of each tube hole and the windward side contour lines form an intersection point, and the included angle between the tangent direction of the intersection point and the long axis direction is 70-110 degrees.

Through the mode, the included angle between the long axis direction of each pipe hole and the tangential direction of the intersection point formed by the contour line on the windward side is set to be 70-110 degrees, so that the long axis direction of each pipe hole is approximately parallel to the windward direction, and the area of the heat exchange dead zone on the leeward side of the heat exchange pipe and the flow resistance of air are reduced.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings used in the description of the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained without inventive work, wherein:

fig. 1 is a schematic cross-sectional view of an air duct type air conditioner according to an embodiment of the present invention;

fig. 2 is a side view of a heat exchanger fin according to an embodiment of the present invention;

FIG. 3 is a side view of a heat exchange fin according to another embodiment of the present invention;

fig. 4 is a schematic cross-sectional view of a heat exchanger according to an embodiment of the present invention;

fig. 5 is a schematic cross-sectional view of a heat exchanger according to another embodiment of the present invention.

Detailed Description

The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.

Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment can be included in at least one embodiment of the application. The appearances of the phrase in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. It is explicitly and implicitly understood by one skilled in the art that the embodiments described herein can be combined with other embodiments.

Referring to fig. 1 and 2, fig. 1 is a schematic cross-sectional view of an air duct type air conditioner according to an embodiment of the present invention, and fig. 2 is a side view of a heat exchange fin according to an embodiment of the present invention. As shown in fig. 1, the air duct type air conditioner of the present embodiment mainly includes a casing 10, a fan assembly 20, and a heat exchanger 30. The housing 10 forms a receiving chamber 11, and the heat exchanger 30 is disposed in the receiving chamber 11. In the present embodiment, the heat exchanger 30 includes a plurality of heat exchange fins 31 arranged at intervals from each other and heat exchange tubes 32 penetrating the heat exchange fins 31. Since the section shown in fig. 1 is a reference section formed by a plane of the main surfaces of the heat exchange fins 31, only one heat exchange fin 31 is shown in fig. 1, and the remaining heat exchange fins 31 are arranged at intervals from the heat exchange fins 31 shown in fig. 1 in a direction perpendicular to the paper surface on which fig. 1 is drawn. The heat exchange fin 31 is generally formed by press molding from a sheet material, and the main surfaces of the heat exchange fin 31 are two side surfaces which are spaced from each other in the thickness direction of the heat exchange fin 31 and have the largest surface area.

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

Referring to fig. 2, a detailed description will be given of a specific shape of the crescent-shaped heat exchange fin shown in fig. 1 and 2.

In the present embodiment, the heat exchange fin 31 shown in fig. 1 and 2 includes a first side contour 311, a second side contour 312, and two end contours 314 and 315.

In the present application, the contour line refers to a combination of two or more contour lines having a predetermined line type for defining the outline of the heat exchange fin 31. The first side contour line 311 and the second side contour line 312 refer to two contour lines that are spaced apart in the incoming wind direction D3 when the heat exchanging fin 31 is in operation. One of the first side contour line 311 and the second side contour line 312 serves as a windward side contour line, and the other serves as a leeward side contour line. Further, the windward side contour line refers to the side contour line on the side facing the wind direction D3 of the first side contour line 311 and the second side contour line 312, and the leeward side contour line refers to the side contour line on the side facing away from the wind direction D3 of the first side contour line 311 and the second side contour line 312. In the present embodiment, the second side contour line 312 serves as a windward side contour line, and the first side contour line 311 serves as a leeward side contour line. In other embodiments, the first side contour 311 may be used as the windward side contour and the second side contour 312 may be used as the leeward side contour.

End contour lines 314 and 315 refer to contour lines for connecting adjacent ends of the first side contour line 311 and the second side contour line 312. It should be noted that, when the edge of the heat exchange fin 31 is notched due to the process or installation, the contour line of the notch should be understood as being formed by the transition of the contour lines on both sides of the notch. Furthermore, when there is a corner cut at the junction of end contours 314 and 315 with first side contour 311 and/or second side contour 312, the contour lines at the corner cut should be considered part of end contours 314 and 315.

In this embodiment, the second side contour line 312 is curved toward the first side contour line 311, the first side contour line 311 is curved 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 central region of the heat exchange fin 31 to the end regions on both sides of the central region, so that the heat exchange fin 31 is integrally disposed in a moon shape. Generally, the wind field formed by the airflow includes a high flow velocity region in the middle and low flow velocity regions on both sides of the high flow velocity region. The fin width of the heat exchange fin 31 is set to be gradually reduced in the direction from the middle area of the heat exchange fin 31 to the end areas on the two sides of the middle area, so that the high flow velocity area corresponds to the middle area with large fin width, the low flow velocity area corresponds to the end area with small fin width, the heat exchange of the middle area and the end area of the heat exchange fin 31 is more uniform, and the overall heat exchange performance is improved.

It should be noted that the descriptions of "gradually decreasing" and "gradually increasing" mentioned in the present application refer to the overall variation trend, which may be continuous variation or stepwise variation. For example, the above-mentioned "fin width gradually decreases" may include a partial fin width constant region, i.e., stepwise decrease.

In the present application, a reference point is selected on the first side contour 311, the normal (perpendicular to the tangent) of the reference point intersects the second side contour 312 to form an intersection, and the linear distance between the reference point and the intersection is the fin width at the reference point, such as W shown in FIG. 2_maxW1, W2, etc. It should be noted 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.

Further, the length of the line connecting the reference point and the intersection point where the width of the fin is maximum is the peak width W_maxThe 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 noted that when the first side contour 311 and the second side contour 312 have a curved shape, the line l3 where the peak width is located is generally a straight line connecting the vertices of the first side contour 311 and the second side contour 312. When the fin is provided with a plurality of connecting lines with the largest width, the straight line where the connecting line in the middle is located is selected as the straight line l3 where the peak width is located.

In this embodiment, the first side contour 311 and the second side contour 312 are further configured to be translationally coincident. Specifically, when the first side contour line 311 is shifted by the peak width W from the straight line l3 where the peak width is located toward the second side contour line 312_maxRear, first sideThe translation curve 311' formed by the contour lines 311 coincides with at least a partial region of the second side contour line 312. In one embodiment, the length of the overlapped portion of the translation curve 311' and the second side contour line 312 accounts for 90% or more of the total length of the first side contour line 311. The heat exchange fins 31 are generally formed by punching and cutting a sheet material, so that waste materials in the processing process can be reduced, and the production cost is reduced.

Further, the end contour lines 314, 315 comprise straight line segments parallel to the line l3 along which the peak width of the heat exchanger fin 31 is located. The line l3 along which the peak width lies is generally arranged along the length of the sheet during the stamping process, in such a way that the partial regions of the end contour 314, 315 are flush with the edge of the sheet, in order to further reduce scrap.

As shown in fig. 2, the shape characterizing parameters of the heat exchanging fin 31 further include the overall height, the overall width and the opening angle of the side profile. The overall height refers to a projected dimension H1 of the heat exchanging fin 31 on a reference plane P1 perpendicular to a line l3 on which the peak width is located and perpendicular to the main surface of the heat exchanging fin 31. The overall width refers to the projected dimension H2 of the heat exchanger fin 31 on a reference plane P2 that is perpendicular to the major surfaces of the heat exchanger fin and that is a line l3 where the peak width is parallel. The side contour line forms an intersection with a straight line l3 of the peak width, and the opening angle of the side contour line is an angle between a connecting line connecting both ends of the side contour line and the intersection, and for example, in fig. 2, the opening angle of the first side contour line 311 is α 1.

The present application will further optimize the heat exchange fins 31 based on the overall shape of the heat exchange fins 31 described above with reference to the following drawings:

1. side profile flare angle

At overall height H1 and peak width W_maxIn the same case, the opening angle α 1 of the first side contour 311 determines the depth of the heat exchanging fin 31 along the straight line l3 where the peak width is located, i.e., the overall width H2 of the heat exchanging fin 31. If the opening angle α 1 of the first side contour line 311 is too large, the depth of the heat exchange fin 31 is relatively small, 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 relatively lowAnd the deterioration is made. If the opening angle α 1 of the first side contour line 311 is too small, the smoothness of the air flow at the end of the heat exchange fin 31 is insufficient, resulting in deterioration of the heat exchange performance at the end of the heat exchange fin 31.

In order to achieve a balance between the overall heat exchange performance and the smoothness of the end air flow, in the present embodiment, the opening angle α 1 of the first side profile 311 is set to 80 to 135 degrees. Optionally, in a specific embodiment, the opening angle α 1 of the first side contour 311 is further set to 95-120 degrees. In another embodiment, the opening angle α 1 of the first side contour 311 is further set to 100-. Through the mode, the heat exchange fin 31 can have the largest heat exchange area in the minimum space, and the smoothness of the airflow at the tail end can be ensured.

Further, the first side contour 311 has an end tangent angle. Specifically, the end tangent included angle is an included angle α 2 between tangents of two end points of the first side contour line 311. Specifically in fig. 2, the included angle is the tangent of the endpoints S4 and S7. It should be noted that when the end point is located on a straight line segment, the tangent line is the extension of the straight line segment. At overall height H1 and peak width W_maxSimilarly, in the case that the first side contour line 311 and the second side contour line 312 are overlapped in a translation manner, the included angle α 2 of the tangent line at the end of the first side contour line 311 determines the fin width at the end of the heat exchanging fin 31. If the included angle α 2 of the tangent line at the end 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 velocity cannot be realized, and if the included angle α 2 of the tangent line at the end 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, which results in the deterioration of the heat exchange performance at the end of the heat exchange fin 31.

Therefore, in the present embodiment, the included angle α 2 of the end tangent of the first side contour 311 is further set to be 60-120 degrees, and the included angle α 2 of the end tangent of the first side contour 311 is smaller than the opening angle α 1 of the first side contour 311. Further, the ratio of the included angle α 2 of the end tangent of the first side contour 311 to the opening angle α 1 may be set to 0.7-0.85. By the mode, the width of the fin at the tail end of the first side contour line 311 can meet the requirement of matching of the flow velocity of the wind field, and higher heat exchange performance can be guaranteed.

Further, the first side contour line 311 is set to be located in a region defined by a connecting line of the vertex S8 of the end tangent included angle α 2 and both end points S4, S7 of the first side contour line 311 and a connecting line of the vertex S1 of the opening angle α 1 and both end points S4, S7 of the first side contour line 311, and an included angle between the tangent of the first side contour line 311 and a straight line l3 on which the peak width of the heat exchanging fin 31 is located gradually decreases in a direction from the middle region to the end region. The specific line type of the first side contour line 311 may be formed by one or more combinations of an arc line, a straight line segment, an elliptic curve, a circular arc line, a spline curve, a cycloid segment, and the like, and the number of each line may be one or more. In this way, the first side contour line 311 can have a reasonable bending shape, and a reasonable fin width variation rule can be obtained when the first side contour line and the second side contour line 312 are overlapped in a translation mode along the straight line l3 where the peak width is located. It is noted that the first side contour 311 is located within the region including the case where the first side contour 311 coincides with the edge of the region. For example, in FIG. 2, the straight line segments S3-S4, S6-S7 of the first side contour 311 and the connecting lines of the end points S4, S7 and the vertex S8 coincide.

2. Law of fin width variation

As described above, the fin width of the heat exchange fin 31 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 then cooperates with the high flow velocity region and the low flow velocity region of the airflow wind field to improve the overall heat exchange performance of the heat exchange fin 31. However, if the width of the heat exchange fins 31 is too small in the direction from the middle region to the end region, the effect of matching the flow velocity of the wind field cannot be achieved. If the variation range of the fin width of the heat exchange fin 31 is too large, the fin width of the tail end of the heat exchange fin 31 is relatively small, resulting in deterioration of the heat exchange performance of the tail end of the heat exchange fin 31.

Therefore, in the present embodiment, the rule of the change in the fin width of the heat exchange fin 31 in the direction from the middle region to the end region is further performedAnd (6) optimizing. Specifically, the first side contour 311 has a reference point E11 and a reference point E12, a vertical distance from the reference point E11 to a straight line l3 along which the peak width of the heat exchanging fin 31 is located is 25% of the overall height H1 of the heat exchanging fin 31, and a vertical distance from the reference point E12 to a straight line l3 along which the peak width of the heat exchanging fin 31 is located is 45% of the overall height H1 of the heat exchanging fin 31. Fin width W1 at reference point E11 and peak width W of heat exchanger fin 31_maxIs 0.64-0.96, the fin width W2 at reference point E12 and the peak width W of the heat exchanger fin 31_maxIs 0.54-0.80 and the fin width W2 at reference point E12 is less than the fin width W1 at reference point E11.

Alternatively, in one embodiment, the fin width W1 at reference point E11 and the peak width W of the heat exchanger fin 31_maxIs 0.75-0.85, the fin width W2 at reference point E12 and the peak width W of the heat exchanger fin 31_maxThe ratio of (A) to (B) is 0.60-0.70.

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

Optionally, in a specific embodiment, the first side contour 311 has a reference point E13, and the vertical distance from the reference point E13 to the straight line l3 of the peak width of the heat exchanging fin 31 is 35% of the overall height H1 of the heat exchanging fin 31. Fin width W3 at reference point E13 and peak width W of heat exchanger fin 31_maxIs 0.60-0.89, and the fin width W3 at reference point E13 is less than the fin width W1 at reference point E11 and greater than the fin width W2 at reference point E12.

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

By the mode, the fin width change rule of the heat exchange fins 31 can meet the requirement of wind field flow velocity matching, and the tail ends of the heat exchange fins 31 can have high heat exchange performance.

OptionallyIn one embodiment, the peak width W of the heat exchanger fins 31_maxThe perpendicular bisector of (a) forms an intersection point E6 and an intersection point E7 with the first side contour line 311, respectively, and the straight line distance d6 of the intersection point E6 and the intersection point E7, i.e., the sum of the vertical distances from the intersection point E6 and the intersection point E7 to the straight line l3 where the peak width is located. The ratio of the linear distance d6 to the overall height H1 of the heat exchanger fin 31 is 0.46-0.56. The smoothness of the airflow at the ends of the heat exchange fins 31 can be ensured in the above manner.

3. Contour line type

Referring to fig. 2, the first side contour 311 is formed by a linear combination of at least two arcs and at least one straight line sequentially connected in a direction from the central region to the end region 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. Wherein the radii of curvature of the at least two arc segments increase gradually in a direction from the middle region to the end regions.

Specifically, in the present embodiment, the upper half portion of the first side contour 311 on the upper side of the straight line l3 where the peak width is located includes the curved sections S1-S2, the curved sections S2-S3, and the straight line sections S3-S4 which are connected in order in the direction from the middle region to the end region. The lower half of the first side contour 311, which is located on the lower side of the line l3 where the peak width is located, includes the curved sections S1-S5, the curved sections S5-S6, and the straight line sections S6-S7, which are connected in order in the direction from the middle region to the end region. The curvature radius of the arc sections S2-S3 is larger than that of the arc sections S1-S2, and the curvature radius of the arc sections S5-S6 is larger than that of the arc sections S1-S5. It is noted that references to "connected in series" in this application include direct connections or connections that transition through other lines.

Through the manner, the first side contour line 311 has a large bending degree through the sequential connection of the arc sections S1-S2 and the arc sections S2-S3 and the sequential connection of the arc sections S1-S5 and the arc sections S5-S6, the depth of the heat exchange fin 31 along the straight line l3 with the peak width is ensured, and meanwhile, the included angle alpha 2 of the tangent line at the tail end of the first side contour line 311 is not too small through the straight line sections S3-S4 and the straight line sections S6-S7, so that the heat exchange performance of the tail end of the heat exchange fin 31 is ensured.

Further, in the present embodiment, the arc sections S1-S2, the arc sections S2-S3 and the straight line sections S3-S4 on the upper side of the straight line l3 where the peak width is located are axisymmetrically arranged with the arc sections S1-S5, the arc sections S5-S6 and the straight line sections S6-S7 on the lower side of the straight line l3 where the peak width is located, with the straight line l3 where the peak width is located as a symmetry axis. In other embodiments, an asymmetric arrangement may also be employed. Further, in other embodiments, the number of arc segments and straight line segments may be varied as desired and is not limited to the number shown in FIG. 2.

In the present embodiment, the included angle between the tangent of the arc segments S1-S2 and S2-S3, the arc segments S1-S5 and the arc segments S2-S4 and the straight line l3 of the peak width is gradually reduced in the direction from the middle region to the end region, thereby ensuring that the first side contour line 311 is bent away from the second side contour line 312 while facilitating drainage of the condensed water.

Further, the ratio of the curvature radius of the arc sections S1-S2 to the curvature radius of the arc sections S2-S3, the ratio of the curvature radius of the arc sections S1-S5 to the curvature radius of the arc sections S5-S6 are 0.24-0.29, the ratio of the arc length of the arc sections S1-S2 to the arc length of the arc sections S2-S3, and the ratio of the arc length of the arc sections S1-S5 to the arc length of the arc sections S5-S6 are 1.1-1.35, and further the depth of the heat exchange fin 31 and the included angle alpha 2 of the tangent at the tail end are optimized.

Further, the arc sections S1-S2, S2-S3, S1-S5 and S5-S6 are arcs, and the arc sections S1-S2 and S1-S5 are directly connected and arranged in a common circle so as to facilitate the arrangement of pipe holes.

Further, arc segments S2-S3 are directly connected with arc segments S1-S2 and straight line segments S3-S4 and are tangent to arc segments S1-S2 and straight line segments S3-S4 at the connecting point, arc segments S5-S6 are directly connected with arc segments S1-S5 and straight line segments S6-S7 and are tangent to arc segments S1-S5 and straight line segments S6-S7 at the connecting point. Through the mode, the continuity of the first side contour line 311 can be ensured, and the stamping and cutting are facilitated.

Further, the upper half portion of the second side contour line 312 on the upper side of the straight line l3 where the peak width is located includes an arc section S1'-S2', an arc section S2'-S3', and a straight line section S3'-S4' which are connected in order in the direction from the middle region to the end region. The lower half of the second side contour line 312 located on the lower side of the straight line l3 where the peak width is located includes an arc section S1'-S5', an arc section S5'-S6', and a straight line section S6'-S7' which are connected in order in the direction from the middle region to the end region.

After the first side contour line 311 is translated along the straight line l3 where the peak width is located, the arc sections S1-S2, S2-S3, S1-S5, and S5-S6 of the first side contour line 311 can respectively overlap with the arc sections S1' -S2', S2' -S3', S1' -S5', and S5' -S6' on the second side contour line 312, and the straight line sections S3-S4, and S6-S7 ' on the first side contour line can respectively overlap with the straight line sections S3' -S4', and S6' -S7' on the second side contour line at least partially, so that the utilization rate of materials is maximized, the materials are saved, and the production cost is reduced.

Optionally, in a specific embodiment, the straight line segments S3'-S4' and S6'-S7' on the second side contour line respectively form a chamfer with the end contour line of the corresponding side, so that the heat exchanging fin 31 is not prone to being chipped at the position of the corner, the heat exchanging effect is affected, and scratches can be avoided during the assembling process of the heat exchanger 30.

Further, in this embodiment, the reference point E11 is located on the segments S2-S3 of the first side contour line 311, the reference point E12 is located on the segments S3-S4 of the first side contour line 311, the reference point E13 is located on the segments S3-S4 of the first side contour line 311, the intersection point of the straight line of the fin width at the reference point E11 and the second side contour line 312 is located on the segments S1'-S2' of the second side contour line 312, the intersection point of the straight line of the fin width at the reference point E12 and the second side contour line is located on the segments S3'-S4' of the second side contour line 312, and the intersection point of the straight line of the fin width at the reference point E13 and the second side contour line 312 is located on the segments S2'-S3' of the second side contour line 312. By the mode, the fin width change rule of the heat exchange fin 31 meets the requirement, and meanwhile, the depth of the heat exchange fin 31 on the straight line l3 where the peak width is located is ensured.

Further, in the present embodiment, the peak width W of the heat exchange fin 31_maxThe intersection point E6 and the intersection point E7 formed by the perpendicular bisector and the first side contour line 311 are respectively located at the arc sections S2-S3 and S5-S6 of the first side contour line 311, thereby ensuring the smoothness of the airflow at the tail end of the heat exchange fin 31.

Compared with the heat exchange fins 31 of the present embodiment and the heat exchange fins of the comparative example, the flow velocity distribution of the heat exchanger 30 on the side away from the fan 22 is further improved. The heat exchange fins of the comparative example are of a three-segment type, the two sides of the straight line where the peak width is located respectively comprise three-segment type arcs which are sequentially connected in the direction from the middle area to the end area, and the curvature radius of the arcs is gradually increased. Therefore, the opening angle, the tail end tangent included angle and the tail end fin width of the leeward side profile of the heat exchange fin are respectively smaller than those of the embodiment. From the comparison result of the flow velocity distribution, it can be found that the area of the heat exchange fin 31 of the embodiment in the low wind speed area located in the middle area on the side departing from the fan 22 is obviously smaller than that of the heat exchange fin of the comparative example, the uniformity of the flow velocity is obviously improved, and the heat exchange performance is obviously improved.

4. Pipe hole arrangement

Referring to fig. 3, fig. 3 further shows tube holes 316 on the basis of the heat exchange fin 31 shown in fig. 2, so that the heat exchange tubes 32 can be inserted into the heat exchange fin 31.

As shown in fig. 3, the tube holes 316 of the heat exchanging fin 31 are arranged in a row. Specifically, in the present embodiment, each row of pipe 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 a ratio of a shortest distance from the center of each pipe hole 316 in each row of pipe holes 316 to the corresponding arrangement curve to a radius of the pipe hole 316 is less than or equal to 1.5.

Further, the sum of the shortest distances from the centers of the pipe holes 316 in each row of pipe holes 316 to the corresponding arrangement curve is smaller than the sum of the shortest distances from the centers of the pipe holes 316 in each row of pipe holes 316 to other translation curves formed after the first side contour 311 or the second side contour 312 is translated.

Further, the tube holes 316 of different rows are arranged at intervals along an arrangement line formed in parallel with the line l3 on which the peak width of the heat exchange fin 31 is located.

In this way, the direction of each row of tube holes 316 is approximately the same as the direction of the first side contour line 311 or the second side contour line 312, so that the surface space of the heat exchange fins 31 is fully utilized, and the overall heat exchange performance of the heat exchanger 30 is improved. In other embodiments, the apertures 316 may be arranged in other ways.

In the present embodiment, 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 regions in the direction of the interval between the first side contour 311 and the second side contour 312. Specifically, in fig. 3, the number of rows of the tube holes 316 in the middle region is three, and the number of rows of the tube holes 316 in the end regions is two. In other embodiments, the number of rows of the tube holes 316 in the middle region may be four, and the number of rows of the tube holes 316 in the end regions may be two, or the number of rows of the tube holes 316 in the middle region may be three, and the number of rows of the tube holes 316 in the end regions may be one, and 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 regions are not specifically limited in this application.

Further, in the present embodiment, the height H3 of the central region where the number of rows of tube holes 316 is relatively high is set to 25% to 50% of the overall height H1 of the heat exchanging fin 31.

As shown in fig. 3, the boundary between the middle region and the end region is formed by connecting the centers of the pipe holes 316 of the middle region and the pipe holes 316 of the end region that are adjacent to each other in a row of pipe holes 316 near the first side contour 311. Parallel lines parallel to a straight line l3 where the peak width is located are further made along the midpoint of the connecting line of the centers of the pipe holes, and two parallel lines l5 and l6 are further obtained on two sides of the straight line l3 where the peak width is located. The parallel lines l5 and l6 are the dividing lines between the central region and the end regions. The parallel lines l5 and l6 are spaced apart by a distance H3 in a direction perpendicular to the line l3 along which the peak width lies, which is the height of the middle region.

Through the mode, the number of rows of the pipe holes 361 in the middle area is set to be larger than that of the pipe holes 361 in the end area, the height H3 of the middle area and the overall height H1 of the heat exchange fins 31 are set in a reasonable range, and the heat exchange fins 31 can be better matched with a high flow velocity area and a low flow velocity area of a wind field, so that a better heat exchange effect is achieved.

Alternatively, in one embodiment, the height H3 of the central region may be set to 30% -45% of the overall height H1 of the heat exchanger fins 31.

Further with reference to FIG. 2, optionally, in one embodiment, the ratio of the height H3 of the central region to the linear distance d6 of the intersection E6 and the intersection E7 is set to 0.60-0.80, and the ratio of the linear distance d6 of the intersection E6 and the intersection E7 to the overall height H1 of the heat exchanger fin 31 is 0.46-0.56. Through the mode, better heat exchange effect can be realized while the smoothness of the air flow of the heat exchange fins 31 is ensured.

Further, the intersection points E18, E19 of the parallel lines l5 and l6 serving as the boundary lines of the middle region and the end region with the first side contour lines 311 and the intersection points E20, E21 of the second side contour lines 312 are located on the arc segments S2-S3, S5-S6 of the first side contour lines 311 and the arc segments S2'-S3', S5'-S6' of the second side contour lines 312, respectively, and the intersection points E18 of the parallel lines l5 and l6 with the first side contour lines 31 are located on the side of the straight line l3 on which the reference point E11 and the intersection point E6 are located near the peak width. Therefore, the fin area corresponding to the arc sections S1-S2 with relatively large curvature is fully utilized as the middle area of the heat exchange fin 31, and the middle area is ensured to have enough fin width.

Further, in the present embodiment, the fin width of the central 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 pipe holes 316 in the middle area and the end area respectively, D is the distance between the rows of the pipe holes at the tail end, and K1 and K2 are variation coefficients with the value range of 0.8-1.2.

The terminal tube hole row spacing D is defined as the distance between the tube hole 316 closest to the end contour 314 or 315 in the row of tube holes 316 closest to the first side contour 311 and the second side contour 312, and the line drawn through the center E14 of the tube hole 316 and the line drawn from the extension of the first side contour 311 and the second side contour 312 or both is the normal line at the intersection point E15 with respect to the intersection points E15 and E16. When the number of rows of the pipe holes 316 in the end region is 2 or more (2 rows shown in fig. 3), the straight line further intersects the arrangement curve of the pipe holes 316 in the adjacent row or the extension line of the arrangement curve at the intersection point E17. At this time, the distal tube hole row pitch D is a linear distance between the tube hole center E14 of the selected tube hole 316 and the intersection point E17. When the number of rows of tube holes 316 in the end region is 1, the distance D between the rows of terminal tube holes is the linear distance between the intersection points E15 and E16. In this way, it is ensured that each heat exchange tube 32 inserted into the tube hole 316 can exhibit an optimal heat exchange performance.

Optionally, in one embodiment, the ratio of the radius of the tube holes 316 to the terminal tube hole row spacing D is 0.23-0.29, thereby further ensuring that each heat exchange tube 32 exhibits optimal heat exchange performance.

Wherein the center of the tube bore 316 closest to end contour 314, 315 has a shortest distance H4 from the center of end contour 314, 315 to end contour 314, 315 of 0.25 xd to 0.75 xd, where D is the above-described terminal tube bore row spacing.

Further, in this embodiment, the shortest distance H4 from the center of the tube hole 316 closest to the end contour 314, 315 is set to 0.4-0.6 of the end tube hole row spacing D. Through the mode, the heat exchange performance of the heat exchange tube 32 inserted into the tube hole 316 closest to the end contour lines 314 and 315 can be brought into full play, and the heat exchange tube 32 can be prevented from being gouged in the assembling process.

5. Pipe diameter optimization

Referring to fig. 4-5, fig. 4-5 are schematic cross-sectional views of two variations of the heat exchanger 30 described above. The pipe diameter of the heat exchange pipe 32 is optimized in the following aspects with reference to fig. 4-5:

5.1 combination of different pipe diameters

Referring first to fig. 3, in the heat exchanger 30 described above, the cross-sectional shape of the heat exchange tube 32 and the cross-sectional shape of the tube hole 316 are both circular in a reference cross-section formed by a plane of the main surface of the heat exchange fin 31, and the tube hole 316 provided in the heat exchange fin 31 has a substantially uniform tube diameter, so that the heat exchange tube 32 and the heat exchange fin 31 are more tightly connected to facilitate heat transfer.

Because the heat exchange medium in the heat exchange tube 32 can take place the phase transition when evaporating or condensing in the heat exchange tube 32, gaseous phase and liquid phase volume ratio can change gradually, and gaseous phase and liquid phase specific volume differ 20 ~ 30 times for the velocity of flow of heat exchange medium takes place great change in the heat exchange tube 32 of the same pipe diameter before and after the phase transition, and then influences heat transfer and the flow resistance of heat exchange medium in the heat exchange tube 32.

Therefore, in this embodiment, in order to better adapt to the specific volume change and the pressure change of the heat exchange medium during the evaporation or condensation process, it is ensured that the heat exchange medium can be in a state with a high heat exchange coefficient no matter in a liquid state, a two-phase state and a gas state, and the flow resistance can be effectively reduced, so as to improve the heat exchange capacity of the heat exchanger 30 and the energy efficiency of the air conditioner, the combination of the heat exchange tubes 32 with different tube diameters can be used, so that the heat exchange medium sequentially flows through the heat exchange tubes 32 with different tube diameters during the evaporation or condensation.

Because 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, the heat exchange medium gradually evaporates under the action of the airflow, and the volume continuously changes, in this embodiment, the aperture of at least part of the tube hole 316 near the leeward side contour line (first side contour line 311) may be larger than the aperture of at least part of the tube hole 316 near the windward side contour line (second side contour line 312). At this time, because the shape of the heat exchange tube 32 is consistent with the shape of the tube hole 316, the heat exchange tube 32 also generates corresponding changes to better adapt to the specific volume change and the pressure change of the heat exchange medium in the evaporation or condensation process, ensure that the heat exchange medium is in a state with high heat exchange coefficient no matter in a liquid state, a two-phase state and a gas state, and 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.

Specifically, as described above, the heat exchanging fin 31 has the first side contour 311 and the second side contour 312 spaced apart from each other. Wherein, second side contour line 312 sets up in heat transfer fin 31 towards fan 22 one side, as windward side contour line, and first side contour line 311 sets up in heat transfer fin 31 and deviates from fan 22 one side, as leeward side contour line.

Alternatively, in one embodiment, the aperture of the tube hole 316 may be arranged to increase gradually in a direction from the windward side contour to the leeward side contour, i.e., in a direction from the second side contour 312 to the first side contour 311.

For example, in one embodiment, the apertures of the tube holes 316 disposed on the leeward side of the contour may be larger than the apertures of the tube holes 316 disposed on the windward side of the contour.

Specifically, as described above, at least two rows of tube holes 316 are arranged in rows in the heat exchange fin 31 in the direction along the interval between the windward side contour line and the leeward side contour line, each row of tube holes 316 is arranged at intervals along the arrangement curve formed by the first side contour line 311 or the second side contour line 312 after being translated along the line l3 where the peak width is located, and the tube holes 316 in different rows are arranged at intervals along the arrangement line formed in parallel with the line l3 where the peak width of the heat exchange fin 31 is located.

Therefore, in an embodiment, in the pipe holes 316 arranged along the same alignment line, the hole diameter of the pipe hole 316 may be gradually increased in a direction from the second side contour 312 to the first side contour 311.

For example, as shown in fig. 4, in the direction of the interval from the second side contour 312 to the first side contour 311, the number of rows of the tube holes 316 provided in the middle region is three, and the number of rows of the tube holes 316 provided in the end regions at both ends of the middle region is two. The aperture of the row of pipe holes 316 close to the second side contour line 312 is smaller than the aperture of the row of pipe holes 316 close to the first side contour line 311, and the aperture of the row of pipe holes 316 arranged between the two rows of pipe holes 316 may be smaller than or equal to the aperture of the row of pipe holes 316 close to the first side contour line 311, so as to implement the aperture change of the pipe holes 316.

Alternatively, in one embodiment, the aperture of the tube hole 316 may be set to 4-7 mm.

Further, the aperture of the array of pipe holes 316 near the second side contour 312 may be set to be 4mm to 5mm, and the aperture of the array of pipe holes 316 near the first side contour 311 may be set to be 6.35 mm to 7 mm.

Alternatively, in one embodiment, the hole center distance between adjacent tube holes 316 may be set to 12mm to 21 mm. The pitch between adjacent pipe holes 316 refers to a distance between pipe hole centers of two adjacent pipe holes 316. It is thus ensured that each heat exchange tube 32 inserted into the tube hole 316 can exhibit an optimum heat exchange performance. It will be appreciated that the center of the orifice 316 is the center of a circle when the orifice 316 is circular, and the center of the orifice 316 is the center of a geometric center when the orifice 316 is non-circular, such as elliptical or other shapes.

The hole center distances between the adjacent pipe holes 316 may be equal, the hole center distances between the adjacent pipe holes 316 may be different, or the hole center distances between the adjacent pipe holes 316 in a part of the area may be equal, and the hole center distances between the adjacent pipe holes 316 in a part of the area may be different.

Alternatively, in one embodiment, the center-to-center distance d16 of at least some adjacent pipe holes 316 in the row of pipe holes 316 near the second side contour 312 may be smaller than the center-to-center distance d17 of at least some adjacent pipe holes 316 in the row of pipe holes 316 near the first side contour 311 for accommodating larger-diameter heat exchange pipes 32, thereby ensuring that each heat exchange pipe 32 inserted into the pipe holes 316 can exert the best heat exchange performance.

For example, in one embodiment, at least some of the adjacent pipe apertures 316 in the row of pipe apertures 316 near one side of the second side contour 312 may be located at a center-to-center distance d16 of 12mm to 19mm, and the adjacent pipe apertures 316 in the row of pipe apertures 316 near the first side contour 311 may be located at a center-to-center distance d17 of 14mm to 21 mm.

Generally speaking, the wind field that the air current formed is including the high velocity of flow district that is located the middle part region and the low velocity of flow district that is located high velocity of flow district both sides, and the amount of wind in heat transfer fin 31 middle part region is greater than the regional amount of wind of tip, and heat transfer coefficient and the wind speed positive correlation of heat exchanger 30, the heat transfer effect of the heat exchange tube 32 in the middle part region is better, if the middle part region can make the heat transfer performance reduction of heat exchanger 30 air side with the regional pipe diameter that uses the size to equal of tip, and also can lead to the air-out temperature in middle part region and the tip region to differ great.

Further, as described above, the fin width of the heat exchange fin 31 becomes gradually smaller in the direction from the central region of the heat exchange fin 31 to the end regions on both sides of the central region, and therefore, in the present embodiment, in order to enhance the heat exchange performance of the heat exchanger 30, the aperture of at least part of the tube holes 316 of the central region may be set larger than the aperture of at least part of the tube holes 316 of the end regions. By the arrangement mode, the heat exchange tube 32 with a larger tube diameter can be further arranged in the middle area with a larger fin width so as to further increase the heat exchange area in the middle area, enhance the heat exchange performance of the heat exchanger 30, and simultaneously increase the flow resistance of air in the middle area, so that part of air flows to the end area with a small pressure difference; and in the low tip region of air flow velocity, use the heat exchange tube 32 of less pipe diameter, can reduce the flow resistance of air to maintain certain air flow velocity, make heat exchange tube 32 obtain abundant heat transfer, promote heat exchanger 30's whole heat transfer performance.

It is noted that the above-described variation in the aperture diameter of the orifice 316 between the first side contour 312 and the second side contour 312 and from the middle region to the end region may be used alone or in combination. Thus, alternatively, in one embodiment, the apertures 316 in the middle region may be set equal in diameter, the apertures 316 in the end regions may be set equal in diameter, and the apertures 316 in the middle region may be set greater in diameter than the apertures 316 in the end regions. Alternatively, in another embodiment, the apertures of the tube holes 316 may be arranged to decrease gradually in a direction from the middle region to the end regions.

Further, in an embodiment, among the pipe holes 316 arranged along the same alignment curve, the pipe holes 316 may be arranged such that the hole diameters thereof gradually decrease in a direction from the middle region to the end regions.

In summary, one or a combination of the two methods can ensure that the middle area has a large enough 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.

5.2 tubular changes

In the heat exchanger 30 using the circular heat exchange tube 32, when the air current 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. Further, the narrow tube spacing between adjacent circular heat exchange tubes 32 results in increased ventilation resistance as the air flow passes through the narrow passages.

Therefore, as shown in fig. 5, in the present embodiment, the heat exchange tubes 32 are provided as flat tubes. Because the area of the heat transfer blind spot of the lee side of flat pipe is less, and the tube space between the adjacent flat pipes is great, can form great air current way, consequently, can reduce the heat transfer blind spot, reinforcing heat transfer effect to can reduce the flow resistance of air current.

Alternatively, in one embodiment, the tube hole 316 for passing the heat exchange tube 32 may have a major axis direction D8 and a minor axis direction D9, and the major axis dimension D18 of the tube hole 316 in the major axis direction D8 is greater than the minor axis dimension D19 in the minor axis direction D9. At this time, since the shape of the heat exchange pipe 32 is identical to the shape of the pipe hole 316, the heat exchange pipe 32 also needs to be changed accordingly.

Since the angle parameter between the long axis direction D8 and the wind entering direction D10 directly affects the area of the heat exchange dead zone on the leeward side of the heat exchange tube 32 and the flow resistance of air, 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 flow resistance of air, the included angle between the long axis direction D8 and the wind entering direction D10 needs to be set reasonably.

Specifically, in the present embodiment, the long axis direction D8 of the tube hole 316 and the windward side contour line (the second side contour line 312) form an intersection, and by setting the included angle α 5 between the tangential direction of the intersection and the long axis direction D8 to be 70 to 110 degrees, the long axis direction D8 of the tube hole 316 and the windward direction D10 can be better matched, so as to reduce the area of the heat exchange dead zone on the leeward side of the heat exchange tube 32 and the flow resistance of air.

Further, since the second side contour line 312 is curved toward the first side contour line 311, the first side contour line 311 is curved away from the second side contour line 312, and an angle between a tangent of the second side contour line 312, i.e., the windward side contour line, and the straight line l3 of the peak width becomes gradually smaller in a direction from the middle region to the end region, an angle between the long axis direction D8 of the pipe hole 316 and the straight line l3 of the peak width may be set to gradually increase, thereby further better matching with the wind entering direction D10.

Further, the heat exchange tube 32 in the middle region has a good heat exchange effect and a large flow resistance of the heat exchange medium. Therefore, when the heat exchanger is used specifically, the setting modes of the long axis dimension d18 and/or the short axis dimension d19 of the flat tubes can be set differentially by referring to the above-described setting mode of the pipe diameter of the circular heat exchange tube 32, so that the above-described heat exchange effect is enhanced, and the flow resistance of the heat exchange medium in the heat exchange tube 32 is reduced. In the present embodiment, the distance between the centers of the adjacent pipe holes 316 specifically refers to the distance between the geometric centers of the adjacent heat exchange pipes 32.

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, so that the heat exchange effect of the heat exchange tube 32 in the middle region can be stronger than that of the heat exchange tube 32 in the end region by adjusting one or more of the above parameters.

For example, the major axis dimension d18 of at least some of the tube apertures 316 in the central region may be greater than the major axis dimension d18 of at least some of the tube apertures 316 in the end regions, and/or the minor axis dimension d19 of at least some of the tube apertures 316 in the central region may be greater than the minor axis dimension d19 of at least some of the tube apertures 316 in the end regions.

Further, the flow resistance of the heat exchange medium within the heat exchange tube 32 is primarily related to parameters such as the major axis dimension d18 and the minor axis dimension d19 of the heat exchange tube 32, and thus the flow resistance of the heat exchange medium within the heat exchange tube 32 can be reduced by adjusting one or more of the above parameters.

For example, the major axis dimension d18 of at least some of the tube apertures 316 near the leeward side contour may be greater than the major axis dimension d18 of at least some of the tube apertures 316 near the windward side contour, and/or the minor axis dimension d19 of at least some of the tube apertures 316 near the leeward side contour may be greater than the minor axis dimension d19 of at least some of the tube apertures 316 near the windward side contour.

In one embodiment, the arrangement of the orifices 316 follows the arrangement described above. That is, at least two rows of tube holes 316 are arranged on the heat exchange fin 31, the at least two rows of tube holes 316 are arranged at intervals along the interval direction of the second side contour line 312 and the first side contour line 311, each row of tube holes 316 are arranged at intervals along an arrangement curve formed by translating the second side contour line 312 or the first side contour line 311, and the tube holes 316 in different rows are further arranged at intervals along an 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 alignment line, the major axis dimension d18 and/or the minor axis dimension 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 alignment curve, the major axis dimension d18 and/or the minor axis dimension d19 of the tube holes 316 gradually decrease in the direction from the middle region to the end regions.

Alternatively, in one embodiment, as shown in FIG. 5, the heat exchange tube 32 can be provided with a major dimension d18 of 5-12mm and the heat exchange tube 32 can be provided with a minor dimension d19 of 0.8-3 mm.

Alternatively, in one embodiment, the tube spacing between adjacent tube holes 316 may be set to 7mm to 16 mm. It is thus ensured that each heat exchange tube 32 inserted into the tube hole 316 can exhibit an optimum heat exchange performance.

Optionally, in a specific embodiment, a plurality of microchannels arranged at intervals along the long axis direction D8 may be further disposed inside the heat exchange tube 32 to further improve the heat exchange performance of the heat exchange tube 32.

It should be noted that the shape, fin width and arrangement of the tube holes 316 of the heat exchange fins 31 in fig. 4 and 5 can be set in various manners as described above, and will not be described in detail herein.

The above only is the embodiment of the present invention, not limiting the patent scope of the present invention, all the equivalent structures or equivalent processes that are used in the specification and the attached drawings or directly or indirectly applied to other related technical fields are included in the patent protection scope of the present invention.

Claims (10)

1. A heat exchanger, characterized in that the heat exchanger comprises:

the heat exchange fin is provided with a pipe hole; and

the heat exchange tube is arranged in the tube hole in a penetrating mode, the shape of the heat exchange tube is consistent with that of the tube hole on a reference cross section formed by a plane where the main surfaces of the heat exchange fins are located, the tube hole is provided with a long axis direction and a short axis direction, and the size of the long axis of the tube hole along the long axis direction is larger than that of the short axis along the short axis direction;

the heat exchange fins comprise windward side contour lines and leeward side contour lines which are arranged at intervals, the long axis direction of each tube hole and the windward side contour lines form an intersection point, and the included angle between the tangent direction of the intersection point and the long axis direction is 70-110 degrees.

2. The heat exchanger according to claim 1, wherein the windward side contour line is curved in a direction toward the leeward side contour line, the leeward side contour line is curved in a direction away from the windward side contour line, and the fin width of the heat exchange fin is gradually reduced in a direction from a central region of the heat exchange fin to end regions on both sides of the central region, and an included angle between the long axis direction of the tube hole and a straight line on which a peak width of the heat exchange fin is located is gradually increased in a direction from the central region to the end regions.

3. A heat exchanger according to claim 2, wherein the major axis dimension of at least some of the tube apertures in the central region is greater than the major axis dimension of at least some of the tube apertures in the end regions, and/or the minor axis dimension of at least some of the tube apertures in the central region is greater than the minor axis dimension of at least some of the tube apertures in the end regions.

4. The heat exchanger of claim 2, wherein at least a portion of the tube bore proximate the leeward side contour has a major axis dimension that is greater than a major axis dimension of at least a portion of the tube bore proximate the windward side contour, and/or wherein at least a portion of the tube bore proximate the leeward side contour has a minor axis dimension that is greater than a minor axis dimension of at least a portion of the tube bore proximate the windward side contour.

5. The heat exchanger according to claim 2, wherein at least two rows of the tube holes are arranged on the heat exchange fin, the at least two rows of the tube holes are arranged at intervals along the interval direction of the windward side contour line and the leeward side contour line, each row of the tube holes are arranged at intervals along an arrangement curve formed by translation of the windward side contour line or the leeward side contour line, and the tube holes in different rows are further arranged at intervals along an arrangement straight line parallel to a straight line where the peak width of the heat exchange fin is located.

6. The heat exchanger according to claim 5, wherein in the tube holes arranged along the same alignment line, the major axis dimension and/or the minor axis dimension of the tube hole gradually increases in a direction from the windward-side contour line to the leeward-side contour line.

7. A heat exchanger according to claim 5, wherein in the tube bores arranged along the same alignment curve, the major and/or minor axis dimensions of the tube bores decrease progressively in a direction from the central region to the end regions.

8. The heat exchanger as claimed in claim 5, wherein in the direction of the spacing between the windward and leeward side contours, the number of rows of tube holes in the central region is greater than the number of rows of tube holes in the end regions, the height of the central region is 25% -50% of the overall height of the heat exchange fin, the fin width of the central region is K1 xn 1 xD, the fin width of the end regions is K2 xn 2 xD, n1 and n2 are the number of rows of tube holes in the central region and the end regions, respectively, D is the row spacing of tube holes in the end regions, and K1 and K2 are coefficients of variation ranging from 0.8 to 1.2.

9. The heat exchanger according to claim 2, wherein a first reference point and a second reference point are provided on the leeward side contour line, a vertical distance from the first reference point to a straight line on which the peak width is located is 25% of the overall height of the heat exchange fin, a vertical distance from the second reference point to a straight line on which the peak width of the heat exchange fin is located is 45% of the overall height of the heat exchange fin, a ratio of the fin width at the first reference point to the peak width of the heat exchange fin is 0.64-0.96, a 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.

10. The heat exchanger according to claim 2, wherein the field angle of the leeward side contour line is 80 to 135 degrees, the ratio of the included angle of the end tangent of the leeward side contour line to the field angle of the leeward side contour line is 0.7 to 0.85, the leeward side contour line is located in an area defined by a connecting line between the vertex of the included angle of the end tangent of the leeward side contour line and both ends of the leeward side contour line and a connecting line between the vertex of the field angle of the leeward side contour line and both ends of the leeward side contour line, and the included angle between the tangent of the leeward side contour line and a straight line where the peak width of the heat exchange fin is located is gradually reduced in the direction from the middle area to the end area.

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