CN213811914U - Heat exchange fin, heat exchanger and air conditioning device - Google Patents

Heat exchange fin, heat exchanger and air conditioning device Download PDF

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Publication number
CN213811914U
CN213811914U CN202020979267.0U CN202020979267U CN213811914U CN 213811914 U CN213811914 U CN 213811914U CN 202020979267 U CN202020979267 U CN 202020979267U CN 213811914 U CN213811914 U CN 213811914U
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heat exchange
fin
side contour
line
exchange fin
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周柏松
李运志
罗彬�
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Midea Group Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
Guangdong Midea HVAC Equipment Co Ltd
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Midea Group Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
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Abstract

The utility model discloses a heat transfer fin, heat exchanger and air conditioning equipment. The heat exchange fin comprises a first side contour line and a second side contour line which are spaced from each other, the second side contour line is arranged in a bending mode towards the first side contour line, the first side contour line is arranged in a bending mode towards the direction deviating from the second side contour line, the width of the heat exchange fin is gradually reduced in the direction from the middle area of the heat exchange fin to the end area of the two sides of the middle area, and the opening angle of the first side contour line is 80-135 degrees. By the mode, the heat exchange fins can be effectively balanced in two aspects of heat exchange area and tail end airflow smoothness.

Description

Heat exchange fin, heat exchanger and air conditioning device
Technical Field
The utility model relates to an air conditioning technology field, concretely relates to heat transfer fin, heat exchanger and air conditioning equipment.
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.
Therefore, the optimization of the heat exchange fins is an important factor for improving the overall performance of the air conditioner.
SUMMERY OF THE UTILITY MODEL
The utility model provides a heat transfer fin, heat exchanger and air conditioning equipment to optimize through the side profile opening angle to heat transfer fin, make heat transfer fin realize effectual balance in heat transfer area and terminal air current smooth and easy degree two aspects.
In order to solve the technical problem, the utility model discloses a technical scheme be: the heat exchange fin comprises a first side contour line and a second side contour line which are spaced from each other, the second side contour line is arranged in a bending mode towards the first side contour line, the first side contour line is arranged in a bending mode towards the direction deviating from the second side contour line, the width of the heat exchange fin is gradually reduced in the direction from the middle area of the heat exchange fin to the end area of the two sides of the middle area, and the opening angle of the first side contour line is 80-135 degrees.
In this way, the flare angle of the first side contour line is optimized, so that the situation that the depth of the heat exchange fin is insufficient due to the overlarge flare angle of the first side contour line is avoided, meanwhile, the situation that the tail end airflow is unsmooth due to the overlarge flare angle of the first side contour line is avoided, and further the heat exchange fin realizes effective balance in two aspects of heat exchange area and tail end airflow smoothness.
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 side view of a heat exchange fin according to another embodiment of the present invention;
fig. 5 is a partial perspective view of a heat exchange fin according to an embodiment of the present invention;
FIG. 6 is a schematic view of a portion of the enlarged structure of FIG. 4;
fig. 7 is a partial perspective view of a heat exchange fin according to another embodiment of the present invention;
fig. 8 is a partial top view of another embodiment according to 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. 2maxW1, 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 WmaxThe 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 312maxThen, the translation curve 311' formed by the first side contour 311 and the second side contourAt least partial areas of the lines 312 coincide. 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 WmaxIn 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, and further, the area of the main surface of the heat exchange fin 31 is relatively small, and the overall heat exchange performance of the heat exchange fin 31 is deteriorated. If the opening angle α 1 of the first side contour line 311 is too smallThe smoothness of the air flow at the ends of the heat exchange fins 31 is insufficient, resulting in deterioration of the heat exchange performance at the ends of the heat exchange fins 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 WmaxSimilarly, 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 variation in fin width of the heat exchange fin 31 in the direction from the middle region to the end region is further optimized. Specifically, the first side contour 311 hasReference point E11 and reference point E12, wherein the vertical distance from the reference point E11 to the straight line l3 of the peak width of the heat exchange fin 31 is 25% of the overall height H1 of the heat exchange fin 31, and the vertical distance from the reference point E12 to the straight line l3 of the peak width of the heat exchange fin 31 is 45% of the overall height H1 of the heat exchange fin 31. Fin width W1 at reference point E11 and peak width W of heat exchanger fin 31maxIs 0.64-0.96, the fin width W2 at reference point E12 and the peak width W of the heat exchanger fin 31maxIs 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 31maxIs 0.75-0.85, the fin width W2 at reference point E12 and the peak width W of the heat exchanger fin 31maxThe 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 31maxIs 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.
Alternatively, in one embodiment, the peaks of the heat exchanger fins 31Width of value WmaxThe 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 the present embodiment, the reference point E11 is located on the arc sections S2-S3 of the first side contour line 311, the reference point E12 is located on the straight line sections S3-S4 of the first side contour line 311, the reference point E13 is located on the straight line sections 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 arc sections 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 straight line sections 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 arc sections 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 31maxThe 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.
Comparing the heat exchange fins 31 of the present embodiment with 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. Surface structure
Referring to fig. 4, fig. 4 further shows various surface structures on the basis of the heat exchange fin 31 shown in fig. 3, and the surface structure of the heat exchange fin 31 is optimized in the following aspects:
5.1. heat transfer enhancement structure
As shown in fig. 4, in the present embodiment, the heat exchange fin 31 is provided with a plurality of heat transfer enhancing structures, specifically, a plurality of bridge piece sets 317, each bridge piece set 317 includes at least one bridge piece 3171, and each bridge piece 3171 has a specific shape as shown in fig. 5, and includes two side walls 3171a that are arranged in a bent manner with respect to the heat exchange fin 31 and are opposite to each other, and a top wall 3171b that is bridged between the two side walls 3171 a. Each of the bridge pieces 3171 serves as a heat transfer enhancing unit. The main function of the bridge piece set 317 is to destroy the flow boundary layer, improve the heat transfer coefficient of the air side of the heat exchange fin 31, and further realize heat transfer enhancement.
As described above, the fin width of the heat exchange fin 31 of the present embodiment 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 further the number of rows of the tube holes 316 in the central region is larger than the number of rows of the tube holes 316 in the end regions. When the heat exchange fins 31 are combined with the heat exchange tubes 32 to form the heat exchanger 30, the heat exchange capacity of the middle regions of the heat exchange fins 31 is greater than that of the end regions of the heat exchange fins 31.
Therefore, in this embodiment, the heat transfer enhancing capability of the bridge plate set 317 in the end region is set to be greater than the heat transfer enhancing capability of the bridge plate set 317 in the middle region, so as to improve the heat exchange uniformity of the middle region and the end region of the heat exchange fin 31, and further improve the overall heat exchange performance of the heat exchanger 30.
Specifically, the heat transfer enhancing capacity of the bridge piece set 317 is related to the number, height, width and other parameters of the arrangement of the bridge pieces 3171 per unit area, so that the heat transfer enhancing capacity of the bridge piece set 317 in the end region can be greater than that of the bridge piece set 317 in the middle region by differentiating one or more of the above parameters of the bridge pieces 3171 in the middle region and the end regions.
Alternatively, the number of the arrangement of the bridge pieces 3171 per unit area in the end region is set to be greater than the number of the arrangement of the bridge pieces 3171 per unit area in the middle region, so that the heat transfer enhancing capability of the bridge piece group 317 in the end region is greater than that of the bridge piece group 317 in the middle region. In the present application, the number of arrangement per unit area refers to a ratio of the number of the bridge pieces 3171 in the middle region or the end regions to the area of the middle region or the end regions.
For example, as shown in FIG. 4, the number of bridge pieces 3171 in at least some of the bridge piece sets 317 in the end regions is set greater than the number of bridge pieces 3171 in at least some of the bridge piece sets 317 in the middle regions, thereby providing a greater heat transfer enhancement capability for the bridge piece sets 317 in the end regions than for the bridge piece sets 317 in the middle regions. Specifically, in fig. 4, the number of the bridge pieces 3171 in the bridge piece group 317 in the end region is three or four, and the number of the bridge pieces 3171 in the bridge piece group 317 disposed in the middle region is two or three. Of course, in other embodiments, the number of the bridge pieces 3171 in the bridge piece set 317 may be set according to practical situations, and the application is not limited in particular.
Further, in the present embodiment, the second side contour line 312 is taken as the windward side contour line, and the first side contour line 311 is taken as the leeward side contour line. The air current is at the in-process of following the transmission of second side outline line 312 to first side outline line 311, and the velocity of flow constantly descends to constantly carry out the heat transfer with heat transfer fin 31, lead to the difference in temperature between air current and the heat transfer fin 31 to diminish gradually, and then make heat transfer fin 31 be less than the heat transfer ability in the region that is close to second side outline line 312 in the heat transfer ability of the region that is close to first side outline line 311. Therefore, the heat transfer enhancing capability of the bridge piece set 317 near the second side contour line 312 can be further set to be smaller than that of the bridge piece set 317 near the first side contour line 311, so as to improve the uniformity of heat exchange between the first side contour line 311 and the second side contour line 312 of the heat exchange fin 31. Specifically, the number of bridge pieces 3171 in at least a portion of the set of bridge pieces 317 adjacent to the first side contour 311 may be set greater than the number of bridge pieces 3171 in at least a portion of the set of bridge pieces 317 adjacent to the second side contour 312. For example, in fig. 4, in the central region of the heat exchange fin 31, the number of the bridges 3171 in the bridge group 317 adjacent to the second side contour line 312 is two, and the number of the bridges 3171 in the bridge group 317 adjacent to the first side contour line 311 is three. Of course, in other embodiments, the second side contour 312 may be used as the leeward side contour, and the first side contour 311 may be used as the windward side contour. At this time, the specific arrangement of the bridge piece set 317 also needs to be adjusted accordingly.
Further, during the cooling process, when the airflow passes through the surfaces of the heat exchange fins 31, the water vapor in the airflow may be condensed when meeting the cold, and condensed water is generated. The condensed water flows down along the heat exchange fins 31 by gravity, and the amount of water gradually increases in the flow direction. Therefore, in this embodiment, the drainage capacity of the bridge set 317 in the lower end region can be further set to be greater than the drainage capacity of the bridge set 317 in the upper end region, so as to reduce the drainage difficulty of the lower end of the heat exchange fin 31, so that the drainage is smoother, and the heat exchange effect of the lower end of the heat exchange fin 31 is further improved.
Specifically, the drainage capacity of the bridge piece group 317 is also related to various parameters such as the number of arranged bridge pieces 3171 per unit area, the height, and the width, and therefore, the drainage capacity of the bridge piece group 317 in the lower end region can be made larger than the drainage capacity of the bridge piece group 317 in the upper end region by differentiating one or more of the above parameters of the bridge pieces 3171 in the upper end region and the lower end region.
Alternatively, the number of arrangement per unit area of the bridge pieces 3171 in the lower end region is set smaller than the number of arrangement per unit area of the bridge pieces 3171 in the upper end region, so that the drainage capacity of the bridge piece group 317 in the lower end region is greater than that of the bridge piece group 317 in the upper end region.
For example, as shown in fig. 4, the number of the bridge pieces 3171 in at least a part of the bridge piece group 317 in the lower end region is set smaller than the number of the bridge pieces 3171 in at least a part of the bridge piece group 317 in the upper end region, so that the drainage capacity of the bridge piece group 317 in the lower end region is greater than that of the bridge piece group 317 in the upper end region. Specifically, in fig. 4, the number of the bridge pieces 3171 in the bridge piece group 317 in the upper end portion region is four, and the number of the bridge pieces 3171 in the bridge piece group 317 in the lower end portion region is three. Of course, in other embodiments, the number of the bridge pieces 3171 in the bridge piece set 317 may be set according to practical situations, and the application is not limited in particular. In other embodiments, the set of fins 317 may be replaced by other heat transfer enhancing structures, such as vortex generators, louvers, and other various other raised structures relative to the heat exchange fins 31, as described below.
5.2. Heat insulation structure
In this embodiment, the number of rows of the tube holes 316 on the heat exchange fin 31 is at least two, specifically, the central area is 3 rows, and the end area is 2 rows.
The heat exchanging fin 31 is further provided with a plurality of rows of heat insulating structures 318, 319 in rows, and each row of heat insulating structures 318, 319 is arranged between two adjacent rows of tube holes 316. The primary function of the row thermal spacers 318, 319 is to prevent cross-talk between heat exchange tubes 32 inserted into adjacent two rows of tube holes 316.
As described above, the fin width of the heat exchange fin 31 of the present embodiment 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 further the number of rows of the tube holes 316 in the central region is larger than the number of rows of the tube holes 316 in the end regions. When the heat exchange fin 31 is combined with the heat exchange tube 32 to form the heat exchanger 30, the wind resistance of the middle region of the heat exchange fin 31 is greater than that of the end regions of the heat exchange fin 31.
Therefore, in the present embodiment, setting the wind resistance of the row thermal insulation structure 318 in the middle area to be smaller than the wind resistance of the row thermal insulation structure 319 in the end area can balance the wind resistance in the middle area and the wind resistance in the end area, and improve the overall heat exchange performance of the heat exchange fin 31.
Specifically, the windage of the row thermal structures 318, 319 is primarily related to the height, width, etc. of the row thermal structures 318, 319, and thus the windage of the row thermal structures 318 in the middle region may be made less than the windage of the row thermal structures 319 in the end regions by adjusting one or more of the above parameters.
For example, the height of the row spacing thermal structures 318 in the central region may be set to be less than the height of the row spacing thermal structures 319 in the end regions, and/or the width of the row spacing thermal structures 318 in the central region may be set to be less than the width of the row spacing thermal structures 319 in the end regions.
In this embodiment, the row spacing thermal structures 318 in the middle region are slits and the row spacing thermal structures 319 in the end regions are louvers, the specific configuration of which is shown in FIG. 5. The louver is a strip-shaped area which is mainly formed by cutting the heat exchange fins 31 and is turned over relative to the heat exchange fins 31.
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, the middle region is curved to a greater extent and has a slope varying in a reverse direction, so that the flow rate of the condensed water in the middle region is relatively slow, and the flow rate of the condensed water in the middle region can be increased by setting the heat insulating structure 318 in the middle region as a slit. Furthermore, by providing the row spacing thermal structures 319 in the end regions as louvers, an additional turbulating effect may be provided, thereby enhancing heat transfer in the end regions.
In other embodiments, the rows of thermally-spaced structures 318, 319 in the middle and end regions may both be provided as louvers, or both as slits, and the embodiments of the present application are not particularly limited.
Further, in order to improve the smoothness of water drainage, the water drainage capacity of the thermal structure 319 at the lower end region may be set to be greater than the water drainage capacity of the thermal structure 319 at the upper end region, so that water drainage is smoother, and the heat exchange effect of the lower end region of the heat exchange fin 31 may be improved.
Specifically, since the height and width of the row spacing thermal structures 319 may affect the drainage capacity, in the present embodiment, the height of the row spacing thermal structures 319 in the lower end region is set to be smaller than the height of the row spacing thermal structures 319 in the upper end region, and/or the width of the row spacing thermal structures 319 in the lower end region is set to be smaller than the width of the row spacing thermal structures 319 in the upper end region, to enhance the drainage capacity in the lower end region.
Further, as described above, in the present embodiment, the second side contour line 312 is taken as the windward side contour line, and the first side contour line 311 is taken as the leeward side contour line. The heat exchange fins 31 have a heat exchange capacity in the region near the first side contour 311 lower than that in the region near the second side contour 312. Therefore, the row pitch of the row spaced thermal structures 318 or 319 is set to gradually increase in the direction from the second side contour line 312 to the first side contour line 311. In this way, the heat exchange efficiency of the heat exchange tube 32 near the leeward side can be enhanced.
In the present application, when the number of rows of the tube holes 316 in the heat exchange fin 31 is two in the direction from the second side contour 312 to the first side contour 311, the row pitch of the row spacing thermal structure 318 or 319 refers to the spacing distance between the row spacing thermal structure 318 or 319 and the adjacent first side contour 311 and second side contour 312. When the number of rows of tube holes 316 in the heat exchange fin 31 is at least three, the row pitch of the row spacing thermal structure 318 or 319 further includes the spacing distance between two adjacent rows of the row spacing thermal structure 318 or 319.
For example, as shown in fig. 4, in the present embodiment, in the middle area of the heat exchanging fin 31, the number of rows of the tube holes 316 is three, and the row pitch of the row spacing thermal structures 318 includes a distance d9 between the row spacing thermal structures 318 close to the second side contour line 312 and the second side contour line 312, a spacing distance d10 between the two rows of row spacing thermal structures 318, and a spacing distance d11 between the row spacing thermal structures 318 close to the first side contour line 311 and the first side contour line 312, respectively, wherein d9< d10< d 11. In the end regions of the heat exchanger fins 31, the rows of tube holes 316 are in two rows, and the row pitch of the row spacing thermal structures 319 includes a spacing distance d12 between the row spacing thermal structures 319 and the second side contour 312 and a distance d13 between the row spacing thermal structures 319 and the first side contour 311, respectively, wherein d12< d 13. Further, the second side contour line 312 is taken as a leeward side contour line, and the first side contour line 311 is taken as a windward side contour line. At this point, the row spacing of the row spacer thermal structures 318 or 319 would need to be adjusted accordingly.
Further, as shown in fig. 4, the heat exchange fin 31 is further provided with a row internal insulation structure 320, and the row internal insulation structure 320 is arranged between two tube holes 316 which are located at the middle region and the end region and adjacent to each other in the row of tube holes 316 close to the second side contour 312. By arranging the inner heat-insulating discharge structure 320 at the junction of the middle region and the end region, mutual heat transfer between the adjacent heat exchange tubes 32 of the middle region and the end region can be avoided, and the overall heat exchange performance of the heat exchanger 30 can be improved.
5.3. End reinforcing rib
Further, as shown in fig. 4, the heat exchanging fin 31 is provided with an end reinforcing rib 321, and the end reinforcing rib 321 is arranged between the tube hole 316 close to the end contour 314 or 315 and the end contour 314 or 315, so as to enhance the strength of the end of the heat exchanging fin 31 and avoid the occurrence of curling.
Further, in the present embodiment, the end reinforcing ribs 321 are arranged in an elongated shape, and the length direction of the end reinforcing ribs 321 is arranged in the radial direction of the pipe hole 316 near the end contour 314 or 315 and directed to the point of the end contour 314 or 315 where the distance from the center of the pipe hole 316 near the end contour 314 or 315 is the largest.
Specifically, in the present embodiment, the pore 316 closest to end contour 314 or 315 is the pore 316 adjacent to end contour 314 or 315 and second side contour 312, and the point at which the distance from the pore 316 is the greatest is the corner cut between end contour 314 or 315 and second side contour 312. The elongated end ribs 321 extend in a direction along a line connecting the center of the tube hole 316 and the cut angle to reinforce the strength of the end portion located farthest from the tube hole 316.
The end reinforcing ribs 321 may be integrally formed with the heat exchange fin 31, and the end reinforcing ribs 321 may be formed on the surface of the heat exchange fin 31 by stamping, so as to simplify the connection manner of the end reinforcing ribs 321.
Optionally, the protruding direction of the end reinforcing rib 321 relative to the heat exchange fin 31 may be the same as the protruding direction of the heat transfer enhancing structure and the heat insulating structure relative to the heat exchange fin 31, so as to improve the production efficiency of the heat exchange fin through one-step punch forming.
Further, in one embodiment, the end reinforcing ribs 321 have a width of 0.3 to 1.5mm and a length of 2mm to 10 mm. In other specific embodiments, the width of the end reinforcing rib 321 may be 0.3mm, 0.5mm, 0.8mm, 1mm, 1.25mm, 1.5mm, etc., and the length may be 2mm, 2.5mm, 3mm, 3.5mm, 4mm, 4.5mm, 5mm, 5.5mm, 6mm, 6.5mm, 7mm, 7.5mm, 8mm, 8.5mm, 9mm, 9.5mm, 10mm, etc., and the end reinforcing rib may be flexibly set according to the distance between the tube hole 316 and the end contour lines 314 and 315 and the thickness of the heat exchange fin 31, which is not particularly limited in the present application.
5.4. Vortex generator
As further shown in fig. 4-8, the heat exchange fin 31 is further provided with a vortex generator, and the vortex generator is configured to enable an airflow flowing from the windward side of the heat exchange tube 32 to form a vortex under the action of the vortex generator, so as to reduce the area of the wake area of the leeward side of the heat exchange tube 32.
Specifically, as the air flows through the heat exchange tubes 32, separation occurs on the leeward side of the heat exchange tubes 32, forming a larger wake zone, which has poor heat transfer properties.
Therefore, in the present embodiment, one or at least two vortex generators may be symmetrically disposed on the periphery of the heat exchange tube 32 along the air flowing direction, so as to suppress the separation of air on the leeward side of the heat exchange tube 32, reduce the area of the wake region, and improve the heat transfer performance on the leeward side of the heat exchange tube 32, thereby improving the overall heat transfer performance of the heat exchanger 30.
Alternatively, in a specific embodiment, the vortex generator is a convex hull 322 integrally formed with the heat exchanging fin 31 and protruding relative to the heat exchanging fin 31, and the specific shape of the convex hull 322 is as shown in fig. 5-6. When the airflow flows through the surface of the convex hull 322, horseshoe-shaped vortex, transverse vortex, longitudinal vortex, mixed vortex and even complex secondary vortex are formed, so that the local nussel number (Nu) at the downstream of the convex hull 322 is strengthened, and the heat exchange of the downstream heat exchange fin 31 is strengthened. The presence of the convex hulls 322 improves the degree of synergy of velocity and temperature gradient, so that under the same Reynolds number, the heat exchange fins 31 with the convex hulls 322 have a synergy angle lower than that of the flat sheets without the convex hulls 322 and a heat exchange coefficient higher than that of the flat sheets, so as to improve the heat transfer performance of the leeward side of the heat exchange tubes 32, thereby improving the overall heat transfer performance of the heat exchanger 30.
Optionally, in a specific embodiment, the convex hull 322 may be formed by stamping, and the protruding direction of the convex hull 322 relative to the surface of the heat exchange fin 31 may be set to be the same as the protruding direction of the heat transfer enhancing structure, the heat insulation structure, and the end reinforcing ribs 320 relative to the surface of the heat exchange fin 31, so as to form the above structure on the heat exchange fin 31 at the same time by one-time stamping forming, thereby greatly simplifying the production process of the heat exchange fin 31 and improving the production efficiency of the heat exchange fin 31.
Alternatively, in a specific embodiment, the protruding direction of the convex hull 322 with respect to the surface of the heat exchange fin 31 may be set to be different from the protruding direction of the above structure.
Optionally, in a specific embodiment, a part of the convex hulls 322 may be arranged to protrude towards one side of the heat exchange fin 31, and another part of the convex hulls 322 may be arranged to protrude towards the other side of the heat exchange fin 31, so that the heat exchange enhancement effects at two sides of the heat exchange fin 31 are the same.
Optionally, in a specific embodiment, the convex hulls 322 may also be formed on the surface of the heat exchange fin 31 by using other production process manners, which are not specifically limited in this application.
Further, when the convex hull 322 is disposed on the windward side of the heat exchange tube 32, the improvement of the heat exchange enhancement effect of the convex hull 322 on the heat exchange fins 31 is significantly weaker than that on the leeward side of the heat exchange tube 32, and the pressure drop level on the windward side is larger than that on the leeward side. Therefore, in the present embodiment, as shown in fig. 6, the convex hull 322 is disposed on the leeward side of the heat exchange tube 32. Moreover, the convex hull 322 is further disposed in a fan-shaped area which takes the center of the pipe hole 316 as a vertex and faces the leeward side of the heat exchange pipe 32, and two side edges of the fan-shaped area and the wind inlet direction D4 of the heat exchange pipe 32 form an included angle of 45 degrees respectively, so as to improve the heat exchange effect of the leeward side of the heat exchange pipe 32 and improve the overall heat exchange performance of the heat exchanger 30.
Specifically, in an embodiment, the wind inlet direction D4 of the heat exchange tube 32 may be a horizontal direction, and the fan-shaped area is an area on the upper and lower sides forming an angle of 45 degrees with the horizontal direction. In other embodiments, the wind direction D4 of the heat exchange tube 32 may also be inclined from the horizontal direction.
Further, in an embodiment, when the heat exchange pipe 32 is a circular pipe, the ratio of the distance between the convex hull 322 and the heat exchange pipe 32 to the diameter of the heat exchange pipe 32 may be set to 0.3-1.0.
Further, the convex hull 322 is one of the heat transfer enhancing structures, when the fluid flows through the convex hull 322, horseshoe-shaped vortices are formed in the front half part of the convex hull 322, and transverse vortices are formed in the rear half part of the convex hull 322, so that the convex hull 322 generates a large shape resistance while increasing the heat exchange, and the pressure drop of the fluid is increased. Therefore, in specific use, the number of the convex hulls 322 arranged on the periphery of each heat exchange pipe 32 can be one or more than two. At this time, all the convex hulls 322 on the periphery of each heat exchange tube 32 can be used as a heat transfer enhancing structure, and each convex hull 322 can be used as a heat transfer enhancing unit, and the differentiation arrangement is performed with reference to the above description. For example, the number, height, etc. of the convex hulls 322 arranged on the heat exchange fins 31 in unit area are set differently to achieve the above-described effects of uniform heat exchange and accelerating the flow of the condensed water.
Alternatively, in a specific embodiment, the number of the convex hulls 322 at the rear side of each heat exchange tube 32 may be set to 2 to 6, and the height of the convex hulls 322 may be set to 0.8 to 1.2 mm.
Further, since the heat transfer coefficient of the convex hull 322 is also related to the shape of the convex hull 322, the heat transfer coefficient of the convex hull 322 can be further improved by changing the shape of the convex hull 322.
Alternatively, in one embodiment, the projection of the convex hull 322 on the heat exchanging fin 31 is provided in an elliptical shape, a rectangular shape, or a raceway shape. That is, the projection of the convex hull 322 on the heat exchanging fin 31 has a major axis direction D5 and a minor axis direction D6 perpendicular to the major axis direction D5, and the major axis dimension D14 of the projection of the convex hull 322 in the major axis direction D5 is larger than the minor axis dimension D15 in the minor axis direction D6.
At this point, the heat transfer coefficient and drag coefficient of the convex hull 322 are related to the ratio of the major axis dimension d14 and the minor axis dimension d15 of the convex hull 322. As the major axis dimension d14 of the convex hull 322 increases, the resistance to flow and the knoop number (Nu) decreases, and the velocity becomes less synergistic with the temperature gradient. The opposite is true when the minor axis dimension d15 is increased. This is because an increase in the major axis dimension d14 of the convex hull 322 causes the shape of the convex hull 322 to more closely approximate the streamlined drag reducing shape, with less turbulence resulting in reduced heat transfer and drag, and an increase in the minor axis dimension d15 resulting in the opposite effect.
Thus, in one embodiment, the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hull 322 may be set between 1.2 and 1.6 to optimize the heat transfer coefficient and drag coefficient of the convex hull 322.
Further, the angle between the long axis direction D5 of the convex hull 322 and the wind inlet direction D4 is large, which results in a significant increase in flow resistance and a significant increase in airflow pressure drop. Therefore, in an embodiment, the included angle between the long axis direction D5 of the convex hull 322 and the wind inlet direction D4 of the heat exchange pipe 32 can be further set to be less than or equal to 10 degrees, so as to reduce the air flow resistance and reduce the air pressure drop.
For example, the long axis direction D5 of the convex hull 322 may be set to coincide with the incoming wind direction D4, i.e., the angle between the two is 0 degrees. Alternatively, the included angle between the major axis direction D5 and the wind direction D4 may be set to 1 degree, 2 degrees, 3 degrees, 4 degrees, 5 degrees, 6 degrees, 7 degrees, 8 degrees, 9 degrees, 10 degrees, or the like.
In addition, the shape of the convex hull 322 may also be set according to needs, for example, the projection of the convex hull 322 on the heat exchange fin 31 may be set to be a circle, a drop (large curvature radius near the windward side), a regular or irregular polygon, and the like, and the present application is not limited specifically.
Optionally, in a specific embodiment, the ratio of the long axis dimension d14 of the convex hull 322 to the diameter of the heat exchange tube 32 may be set to 0.2-0.6, so as to improve the turbulence effect of the convex hull 322 on the periphery of the heat exchange tube 32.
Further, since the number of the convex hulls 322 disposed at the periphery of each heat exchange tube 32 and the ratio of the long axis dimension d14 to the short axis dimension d15 of the convex hulls 322 can affect the heat transfer coefficient and the drag coefficient of the convex hulls 322, the number of the convex hulls 322 disposed at the periphery of the same heat exchange tube 32 and the ratio of the long axis dimension d14 to the short axis dimension d15 of the convex hulls 322 can be coupled to balance the heat transfer coefficient and the drag coefficient of the convex hulls 322. Specifically, the number of convex hulls 322 is set to be inversely related to the ratio of the major axis dimension d14 to the minor axis dimension d 15. That is, when the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hull 322 is designed to be larger, the number of convex hulls 322 can be reduced appropriately; similarly, when the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hull 322 is designed to be small, the number of convex hulls 322 can be increased appropriately.
Alternatively, in a specific embodiment, as shown in fig. 7-8, the vortex generator may also be a flap 323 integrally formed with the heat exchange fin 31 and folded over with respect to the heat exchange fin 31, the flap 323 having a specific shape as shown in fig. 7. The flap 323 serves to guide the air flow along the gap between the flap 323 and the heat exchange tube 32 toward the leeward side of the heat exchange tube 32, thereby forming a vortex.
Optionally, in a specific embodiment, the folded piece 323 may be formed by stamping, and the folding direction of the folded piece 323 relative to the surface of the heat exchange fin 31 may be set to be the same as the protruding direction of the heat transfer enhancing structure, the heat insulating structure, and the end reinforcing rib 320 relative to the surface of the heat exchange fin 31, so that the structures are formed at the same time by one-step stamping forming, thereby greatly simplifying the production process of the heat exchange fin 31 and improving the production efficiency of the heat exchange fin 31.
In a specific embodiment, the folding direction of the folding piece 323 relative to the surface of the heat exchange fin 31 can be set to be different from the protruding direction of other surface structures. Alternatively, other manufacturing methods may be adopted to form the folding pieces 323 on the surface of the heat exchanging fin 31, which is not limited in this application.
As shown in fig. 8, the flap 323 is connected to the heat exchange fin 31 by a connection line 324, and the connection line 324 is disposed around the tube hole 316 to guide air flow when the air flows through the heat exchange tube 32, thereby suppressing separation of air on the leeward side of the heat exchange tube 32 and reducing the area of a wake region.
Further, the higher the height of the flap 323, the greater the wind resistance provided by the flap 323. Therefore, the height of the flap 323 relative to the main surface of the heat exchange fin 31 can be set gradually larger in the direction from the windward side to the leeward side of the heat exchange tube 32 to reduce the wind resistance near the windward side while enhancing the turbulent flow effect of the flap 323.
Optionally, in one embodiment, the flap 323 is folded over an area defined by the connecting line 324 and a cut line 325 on a side of the connecting line 324 facing away from the tube aperture 316.
Specifically, as shown in fig. 8, the cut line 325 includes a first cut line 3251 and a second cut line 3252, wherein one end of the first cut line 3251 is connected to an end of the connection line 324 near the windward side of the heat exchange tube 32, the other end of the first cut line 3251 is connected to another end of the connection line 324 near the leeward side of the heat exchange tube 32 by the second cut line 3252, and the first cut line 3251 and the connection line 324 are separated from each other in a direction from the windward side to the leeward side of the heat exchange tube 32, so that the height of the flap 323 gradually increases in a direction from the windward side to the leeward side of the heat exchange tube 32 after the flap 323 is folded over the heat exchange fin 31.
In other embodiments, the shape of the flap 323 can also take other shapes, such as a triangle, a regular or irregular polygon, and the height of the flap 323 can also be set constant or have other variations.
Further, since the flap 323 disposed on the windward side of the heat exchange tube 32 may cause the pressure drop level on the windward side to be increased, in an embodiment, an angle α 3 between a connecting line between an end point of the connecting line 324 of the flap 323 and the heat exchange fin 31 near the windward side of the heat exchange tube 32 and the center of the tube hole 316 and the windward direction D7 of the heat exchange tube 32 may be set to be 90-110 degrees, so as to reduce the resistance of the windward side of the flap 323 and reduce the pressure drop level. Further, the included angle α 4 between the connecting line between the two end points of the connecting line 324 between the flap 323 and the heat exchange fin 31 and the center of the tube hole 316 can be set to 47-56 degrees.
Further, in an embodiment, the connecting line 324 between the folding piece 323 and the heat exchange fin 31 may be configured as an arc, the tube hole 316 is configured as a circular hole, and the circle center of the arc where the connecting line 324 is located coincides with the circle center of the tube hole 316, so that the folding piece 323 and the heat exchange tube 32 are approximately arranged at equal intervals, and further the turbulence effect of the folding piece 323 on the leeward side of the heat exchange tube 32 is improved.
Optionally, in a specific embodiment, the ratio of the radius R2 of the connecting line 324 between the flap 323 and the heat exchanging fin 31 to the radius R1 of the tube hole 316 is 1.19-1.34, so as to further enhance the turbulent flow effect.
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 (12)

1. The utility model provides a heat transfer fin, its characterized in that, heat transfer fin includes spaced first side profile line and second side profile line each other, second side profile line is towards the crooked setting of direction of first side profile line, first side profile line deviates from the crooked setting of direction of second side profile line, heat transfer fin's fin width is following heat transfer fin's middle part is regional to diminish gradually in the direction of the tip region of the regional both sides in middle part, wherein the field angle of first side profile line is 80-135 degrees.
2. The heat exchange fin of claim 1, wherein the opening angle of the first side contour is 95-120 degrees.
3. The heat exchange fin according to claim 1, wherein the included angle of the end tangent of the first side contour line is 60-120 degrees, and the included angle of the end tangent of the first side contour line is smaller than the opening angle of the first side contour line.
4. The heat exchange fin according to claim 1, wherein the ratio of the included angle of the end tangent of the first side contour to the opening angle of the first side contour is 0.7-0.85.
5. The heat exchange fin according to claim 4, wherein the first side contour line is located in an area defined by a connecting line between a vertex of an included angle of a tangent line at the end of the first side contour line and end points at two ends of the first side contour line and a connecting line between a vertex of an opening angle of the first side contour line and end points at two ends of the first side contour line, and an included angle between the tangent line of the first side contour line and a straight line where a peak width of the heat exchange fin is located is gradually reduced in a direction from the middle area to the end area.
6. The heat exchange fin according to claim 5, wherein a first reference point and a second reference point are provided on the first side profile line, the vertical distance from the first reference point to a straight line on which the peak width of the heat exchange fin is located is 25% of the overall height of the heat exchange fin, the 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, the ratio of the fin width at the first reference point to the peak width of the heat exchange fin is 0.64-0.96, the 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.
7. The heat exchange fin of claim 5, wherein the heat exchange fin has tube holes arranged in rows, 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 in the direction of the spacing between the first and second side contours, wherein the fin width in the central region is K1 xn 1 xd, the fin width in 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 terminal tube hole row spacing in the end regions of the heat exchange fin, and K1 and K2 are coefficients of variation ranging from 0.8 to 1.2.
8. The heat exchange fin according to claim 7, further comprising a plurality of heat transfer enhancing structures disposed thereon, wherein the heat transfer enhancing structures in the end regions have a heat transfer enhancing capacity greater than that of the heat transfer enhancing structures in the central region, the end regions include an upper end region on an upper side of the central region and a lower end region on a lower side of the central region, and wherein the heat transfer enhancing structures in the lower end region have a drainage capacity greater than that of the heat transfer enhancing structures in the upper end region.
9. The heat exchange fin according to claim 7, wherein the number of rows of tube holes is at least two, the at least two rows of tube holes are arranged at intervals along the interval direction of the first side contour line and the second side contour line, wherein a plurality of rows of spaced thermal structures are further arranged on the heat exchange fin in rows, each row of spaced thermal structures is arranged between two adjacent rows of the tube holes, and wherein the wind resistance of the row of spaced thermal structures in the middle region is smaller than the wind resistance of the row of spaced thermal structures in the end regions.
10. The heat exchange fin according to claim 7, further comprising a vortex generator disposed on the heat exchange fin, wherein the vortex generator is used for reducing the area of a wake region on the leeward side of the heat exchange tube inserted into the tube hole, and the vortex generator is a flap integrally formed with the heat exchange fin and folded over with respect to the heat exchange fin, or a convex hull integrally formed with the heat exchange fin and protruding with respect to the heat exchange fin.
11. A heat exchanger, characterized in that the heat exchanger comprises a heat exchange tube and a heat exchange fin as recited in any one of claims 1 to 10, the heat exchange tube being disposed through the heat exchange fin.
12. An air conditioning apparatus, characterized in that it comprises a heat exchanger according to claim 11.
CN202020979267.0U 2020-06-01 2020-06-01 Heat exchange fin, heat exchanger and air conditioning device Active CN213811914U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202020979267.0U CN213811914U (en) 2020-06-01 2020-06-01 Heat exchange fin, heat exchanger and air conditioning device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202020979267.0U CN213811914U (en) 2020-06-01 2020-06-01 Heat exchange fin, heat exchanger and air conditioning device

Publications (1)

Publication Number Publication Date
CN213811914U true CN213811914U (en) 2021-07-27

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Family Applications (1)

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Country Status (1)

Country Link
CN (1) CN213811914U (en)

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