CN212378552U - Heat exchanger - Google Patents

Abstract

The application discloses heat exchanger, it includes: the heat exchange tube comprises a first end part and a second end part which are positioned at two opposite ends of the heat exchange tube in the length direction, the first end part is connected with the first collecting tube, the second end part is connected with the second collecting tube, and the heat exchange tube comprises two side surfaces, a first end surface and a second end surface; the fin includes basal portion and a plurality of heat dissipation tooth, and is a plurality of the heat dissipation tooth is arranged along basal portion length direction, and with one side of the width direction of basal portion is connected, adjacent two be equipped with the breach between the heat dissipation tooth, the heat exchange tube at least part cooperation is in corresponding in the breach, the heat dissipation tooth with the side of heat exchange tube is connected, the width direction of basal portion for the width direction slope setting of heat exchange tube. The heat exchanger of this application is favorable to improving drainage performance.

Description

Heat exchanger

Technical Field

The application relates to the field of heat exchange, in particular to a heat exchanger.

Background

The heat exchanger mainly comprises a heat exchange tube, fins and a collector tube. The two ends of the heat exchange tube are connected with collecting pipes which are used for distributing and collecting refrigerants, the fins are provided with heat exchange tube grooves, the heat exchange tube is inserted into the heat exchange tube grooves of the fins, and the fins are used for enhancing the heat exchange efficiency of the heat exchanger and the air side. The heat exchanger can be applied to an air conditioner or a heat management system, when the air conditioner or the heat management system operates, condensate water is possibly generated on the surface of the fins of the heat exchanger, and if the generated condensate water is not discharged in time, frosting is possibly generated on the fins. Accordingly, the heat exchanger in the related art needs improvement.

SUMMERY OF THE UTILITY MODEL

The application aims at providing a heat exchanger beneficial to draining condensed water.

According to one aspect of the present application, there is provided a heat exchanger comprising: the heat exchange tube comprises a first end part and a second end part which are positioned at two opposite ends of the heat exchange tube in the length direction, the first end part is connected with the first collecting tube, the second end part is connected with the second collecting tube, the heat exchange tube comprises a channel for communicating an inner cavity of the first collecting tube with an inner cavity of the second collecting tube, the heat exchange tube comprises two side surfaces, a first end surface and a second end surface, the first end surface and the second end surface are respectively positioned at two opposite sides of the heat exchange tube in the width direction, the two side surfaces are respectively positioned at two opposite sides of the heat exchange tube in the thickness direction, and the width of the heat exchange tube is larger than the thickness of the heat exchange tube;

the fin comprises a base and a plurality of radiating teeth, the radiating teeth are arranged along the length direction of the base and connected with one side of the width direction of the base, a gap is formed between every two adjacent radiating teeth, at least part of the heat exchange tube is matched in the corresponding gap, the radiating teeth are connected with the side face of the heat exchange tube, and the width direction of the base is inclined relative to the width direction of the heat exchange tube.

The application provides a heat exchanger, the width direction of fin basal portion for the width direction slope of heat exchange tube sets up, is favorable to the discharge of comdenstion water.

Drawings

FIG. 1 is a schematic perspective view of a heat exchanger according to a first embodiment of the present application;

FIG. 2 is an exploded schematic view of a heat exchanger according to a first embodiment of the present application;

FIG. 3 is a front view of the heat exchanger shown in FIG. 1;

FIG. 4 is a schematic perspective view of a first embodiment of the present application with the heat exchange tubes and fins assembled together;

FIG. 5 is a side view of FIG. 4;

FIG. 6 is an enlarged schematic view of the portion circled C in FIG. 5;

FIG. 7 is a cross-sectional view taken along line A-A of FIG. 3;

FIG. 8 is a schematic perspective view of a fin of the first embodiment of the present application from an oblique upward viewing angle;

FIG. 9 is a bottom view of the fin of FIG. 8;

FIG. 10 is an enlarged schematic view of the portion circled A in FIG. 3;

FIG. 11 is an enlarged schematic view of the portion encircled at B in FIG. 4;

FIG. 12 is a schematic view of another fin of the first embodiment of the present application;

FIG. 13 is a schematic view of yet another fin of the first embodiment of the present application;

FIG. 14 is a schematic view of yet another fin of the first embodiment of the present application;

FIG. 15 is a side view of a second embodiment of the present application with an assembled heat exchange tube and fin;

FIG. 16 is an enlarged schematic view of the portion encircled as D in FIG. 15;

FIG. 17 is a side view of a third embodiment of the present application with an assembled heat exchange tube and fin;

FIG. 18 is an enlarged schematic view of the portion of circle E in FIG. 17;

FIG. 19 is a schematic view of a thermal management system according to a first embodiment of the present application.

In the drawings:

100. a heat exchanger;

11. a first header; 12. a second header; 14. an end cap; 15. an interface; 17. an inner cavity;

3. a heat exchange pipe; 31. a channel; 32. a side surface; 33. a first end face; 34. a second end face; a longitudinal direction L3; the width direction W3; the thickness direction T3;

4. a fin; 41. a base; 411. a first substrate surface; 412. a second substrate surface; 413. a first bump structure; 415. a peripheral wall; 416. an opening; 4141. a first flanging; 4142. a first end; 4143. a second end; 4144. a first folded edge; a longitudinal direction L41; the width direction W41; the thickness direction T41; 42. a heat dissipating tooth; 4211. a first connecting edge; 4212. a straight section; 4213. a first stage; 4214. a second stage; 425. chamfering; 4215. a third connecting edge; 4218. second flanging; 4219. third flanging; 4216. a fourth flanging; 422. a notch; 433. a windowing structure; 424. a second connecting edge; 426. a first side; 427. a second face; 428. a second bump structure;

5. a side plate; 51. an abutting portion; 52. a connecting portion; 53. a plane;

6. a thermal management system; 61. a compressor; 62. a first heat exchanger; 63. a second heat exchanger; 64. an expansion valve; 65. and a four-way valve.

Detailed Description

Reference will now be made in detail to the exemplary embodiments, examples of which are illustrated in the accompanying drawings. When the following description refers to the accompanying drawings, like numbers in different drawings represent the same or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present application. Rather, they are merely examples of apparatus and methods consistent with certain aspects of the present application, as detailed in the appended claims.

The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. In the description of the present application, it is to be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the present application and for simplicity in description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed in a particular orientation, and be operated in a particular manner, and are not to be construed as limiting the present application. Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present application, "a plurality" means two or more unless specifically limited otherwise.

In the description of the present application, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.

In this application, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may comprise direct contact of the first and second features, or may comprise contact of the first and second features not directly but through another feature in between. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature. Exemplary embodiments of the present application will be described in detail below with reference to the accompanying drawings. The features of the following examples and embodiments can be supplemented or combined with each other without conflict.

The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. As used in this application and the appended claims, the singular forms "a", "an", and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise.

Exemplary embodiments of the present application will be described in detail below with reference to the accompanying drawings. The features of the following examples and embodiments may be combined with each other without conflict.

When the heat exchanger is used as an evaporator, condensate water is generated on the surface of the heat exchanger, and the condensate water is accumulated on the surface of the fin and cannot be discharged in time, so that the working performance of the heat exchanger is affected.

Fig. 1 is a perspective view of a heat exchanger 100 according to a first embodiment of the present application. Please refer to fig. 1 in conjunction with fig. 2 to 12 as necessary.

The heat exchanger 100 includes a first header 11, a second header 12, a plurality of heat exchange tubes 3, and a plurality of fins 4. The first header 11 and the second header 12 each comprise a circular tube having an inner cavity 17 extending along the length of the tube. The opposite ends of the circular tube body along the length direction are respectively provided with an opening, and the middle part of the circular tube body is provided with a row of insertion ports 15 communicated with the inner cavity 17. In the embodiment shown in fig. 1, the length direction of the first collecting pipe 11 and the length direction of the second collecting pipe 12 are parallel to each other and are respectively connected to the upper and lower sides of the plurality of heat exchange tubes 3, the first collecting pipe 11 is located at the upper side, and the second collecting pipe 12 is located at the lower side. The opening 16 of the first header 11 on the left side and the opening of the second header 12 on the right side are sealed by the end cap 14, and the opening of the first header 11 on the right side and the opening of the second header 12 on the left side are used for inflow and outflow of refrigerant, respectively. In alternative embodiments, the cross-sectional shapes of the tubes of the first header 11 and the second header 12 may be semi-circular, square, or other shapes, and have the function of the inner cavity 17, which is not limited in this application. In other optional embodiments, the refrigerant inlets and the refrigerant outlets of the first collecting pipe 11 and the second collecting pipe 12 are located at the same side, one side of the first collecting pipe 11 and one side of the second collecting pipe 12 are sealed, and the other side of the first collecting pipe 11 and the other side of the second collecting pipe 12 serve as the refrigerant inlet and outlet, which is not limited in this application. In other optional embodiments, due to installation, manufacturing or other reasons, the length direction of the first header 11 and the length direction of the second header 12 form an angle, but are not parallel to each other, and the positions of the first header 11 and the second header 12 are not limited thereto. In other alternative embodiments, the first collecting pipe 11 is located obliquely above the heat exchange tube 3, and the second collecting pipe 12 is located obliquely below the heat exchange tube 3, as long as the first collecting pipe 11 and the second collecting pipe 12 are located at two ends of the heat exchange tube 3 in the length direction, which is not limited in this application. In alternative embodiments, the first header 11 and the second header 12 may also be provided with a plurality of baffles, so as to realize multiple flow paths for the refrigerant flowing through the heat exchanger 100.

As shown in fig. 1 to 4, the length directions L3 of a plurality of heat exchange tubes 3 may be parallel to each other, each heat exchange tube 3 is inserted into the header socket 15 along the length direction L3, the heat exchange tube 3 has a channel 31 (the channel 31 is composed of a plurality of small channels side by side, not shown in the figure) extending along the length direction L3 of the heat exchange tube 3, and the channel 31 communicates the inner cavity 17 of the first header 11 with the inner cavity 17 of the second header 12. As shown in fig. 4, each heat exchange tube 3 comprises two side surfaces 32, a first end surface 33 and a second end surface 34, the first end surface 33 and the second end surface 34 are positioned on two opposite sides of the width direction W3 of the heat exchange tube 3, the two side surfaces 32 are respectively positioned on two opposite sides of the thickness direction T3 of the heat exchange tube 3, and the width of the heat exchange tube 3 is larger than the thickness of the heat exchange tube 3. In the present embodiment, the length direction L3 of the heat exchange tube 3 may be perpendicular to the length direction of the first header 11, and the length direction L3 of the heat exchange tube 3 may be perpendicular to the length direction of the second header 12. In other alternative embodiments, the length directions L3 of the plurality of heat exchange tubes 3 form a small included angle with each other due to manufacturing and the like, and the length directions L3 of the plurality of heat exchange tubes 3 are substantially parallel to each other, and the positions of the heat exchange tubes 3 are not limited thereto. In an alternative embodiment, the first collecting header 11 and the second collecting header 12 are not vertically aligned, and the length direction L3 of the heat exchange tube 3 forms an included angle with the length direction of the first collecting header 11, and/or the length direction L3 of the heat exchange tube 3 and the length of the second collecting header 12, as long as the first collecting header 11 and the second collecting header 12 are respectively located at two opposite ends of the heat exchange tube 3 in the length direction L3, and the position of the heat exchange tube 3 is not limited thereto.

As shown in fig. 1, the plurality of fins 4 are arranged in parallel with each other in the longitudinal direction between the first header 11 and the second header 12. As shown in fig. 9, the fin 4 includes a base 41 and a plurality of heat dissipation teeth 42, the plurality of heat dissipation teeth 42 are arranged along a length direction L41 of the base 41 and connected to one side of a width direction W41 of the base 41, a notch 422 is provided between two adjacent heat dissipation teeth 42, and the heat exchange tubes 3 are at least partially fitted in the corresponding notches 422 of the heat dissipation teeth 42, respectively. In other alternative embodiments, a plurality of fins 4 are arranged in sequence along the length direction L3 of the heat exchange tube 3, the number of the fins 4 is determined according to the actual use situation, and the application is not limited thereto.

The heat exchanger 100 may be applied to a thermal management system 6. As shown in fig. 19, a schematic diagram of a thermal management system 6 is shown, where the thermal management system 6 includes a compressor 61, an expansion valve 64, a first heat exchanger 62, a second heat exchanger 63 and a four-way valve 65. When the heat exchanger 100 is used in this thermal management system 6, it may be used as the first heat exchanger 61 and/or the second heat exchanger 63. Of course, the heat exchanger 100 may also be used in other thermal management systems 6, and the application is not limited thereto. When the heat exchanger 100 is applied to the thermal management system 6, in the present embodiment, as shown in fig. 1 and 3, the length direction of the first header 11 and the length direction of the second header 12 of the heat exchanger 100 may be horizontal, the length direction L3 of the heat exchange tube 3 may be vertical, and the width direction W3 of the heat exchange tube 3 is located on a horizontal plane perpendicular to the direction of gravity. The length directions of the first collecting pipe 11 and the second collecting pipe 12 are horizontal, and the length direction L3 of the heat exchange tube 3 is vertical, which is beneficial to reducing the difficulty of refrigerant distribution in the first collecting pipe 11 and the second collecting pipe 12. Of course, the width direction W3 of the heat exchange tube 3 referred to herein is on a horizontal plane perpendicular to the direction of gravity, including the width direction W3 of the heat exchange tube 3, which is absolutely at a small angle from the width direction W3 of the heat exchange tube 3. In other optional embodiments, the length direction of the first header 11 and the length direction of the second header 12 may be disposed at an angle with respect to the horizontal line, the length direction of the first header 11 and the length direction of the second header 12 may have a height difference in the length direction L3 of the heat exchange tube 3, and the positions of the first header 11 and the second header 12 are not limited thereto.

As shown in fig. 4 to 6, fig. 6 is an enlarged schematic view of a circle C portion of fig. 5, and the first protrusion structure 413 and the opening 416 of the base 41 in the circle C portion are not shown for clarity of description. As shown in fig. 6, the heat dissipation teeth 42 are connected to the side surfaces 32 of the heat exchange tube 3, the width direction W41 of the base 41 is obliquely arranged with respect to the width direction W3 of the heat exchange tube 3, and the width direction W41 of the base 41 forms a first angle α with the width direction of the heat exchange tube 3. It should be understood that the included angle refers to the smallest positive angle formed by the intersection of two straight lines according to the definition of the included angle, so that the first included angle α referred to herein is the smallest positive angle formed by the width direction W41 of the base 41 and the width direction W3 of the heat exchange tube 3. Because the width direction W3 of the heat exchange tube 3 is on the horizontal plane perpendicular to the gravity direction, that is, the width direction W41 of the base 41 forms a certain included angle with the horizontal plane, the condensed water at the base 41 of the fin 4 can be discharged along the inclined plane, thereby enhancing the drainage performance of the fin 4. In the embodiment shown in fig. 5, the air blowing direction C is parallel to the width direction W41 of the base 41, and the air blowing direction C is parallel to the water discharging direction. In alternative embodiments, the air blowing direction C may be opposite to that shown in fig. 5, except that the air blowing direction C is opposite to the water discharge direction, which is less effective than the air blowing direction C shown in fig. 5. In this embodiment, the base 41 is the windward side, the air is contacted at the base 41 first, and the condensed water is discharged as the condensed water when the air is contacted at the base 41 first, which can achieve the effect of delaying the frost formation. In alternative embodiments, the base 41 is on the leeward side, but such that condensation may accumulate on the end of the base 41 away from the heat sink teeth 42 in the width direction W41, the drainage effect is less effective than on the windward side of the base 41. The inventor has found through a lot of experiments that the heat exchanger 100 can have the most balanced heat exchange performance and drainage performance when the value range of the first included angle α is 10 ° to 50 °.

As shown in fig. 4 to 6, the heat dissipation tooth 42 has a first connection edge 4211 connected to the side surface 32 of the heat exchange tube 3, the first connection edge 4211 is obliquely disposed with respect to the width direction W3 of the heat exchange tube 3, and the extension direction of the first connection edge 4211 forms a second angle β with the width direction W3 of the heat exchange tube 3. It should be understood that the included angle refers to a smallest positive angle formed by the intersection of two straight lines according to the definition of the included angle, and therefore, the second included angle β referred to herein is a smallest positive angle formed by the extending direction of the first connecting edge 4211 and the width direction of the heat exchange tube 3. Because the width direction W3 of the heat exchange tube 3 is on the horizontal plane perpendicular to the gravity direction, that is, the width direction W3 of the heat dissipation teeth 42 forms a certain included angle with the horizontal plane, the condensed water formed on the heat dissipation teeth 421 can be discharged along the inclined plane, thereby enhancing the drainage performance of the fins 4. The inventor has found through a lot of experiments that the heat exchanger 100 can have the most balanced heat exchange performance and drainage performance when the numerical range of the second included angle β is 10 ° to 50 °. In the embodiment shown in fig. 4 to 6, the first included angle α is equal to the second included angle β, that is, the width direction W41 of the base portion 41 is parallel to the extending direction of the first connecting edge 4211, or the extending direction of the first connecting edge 4211 coincides with the width direction W41 of the base portion 41; the structure is convenient to manufacture and install.

As shown in fig. 10, the base 41 includes a first base surface 411 and a second base surface 412 which are oppositely arranged in the thickness direction of the base 41, and the first base surface 411 is located above the second base surface 412. As shown in fig. 9 to 11, the base 41 includes a plurality of first protrusion structures 413 protruding from the first base surface 411, the plurality of first protrusion structures 413 are arranged along the length direction L41 of the base 41, and the plurality of protrusion structures 413 are arranged side by side along the length direction L41 of the base 41, which is easier to manufacture. Accordingly, the projection of the first protrusion structure 413 on the first base surface 411 may be an ellipse as shown in fig. 9. The first protrusion structures 413 protrude relative to the first base surface 411, strength of the fins 4 is improved, meanwhile, due to the fact that the width direction W41 of the base 41 is inclined relative to the width direction W3 of the heat exchange tube 3, condensed water accumulated on the first protrusion structures 413 is easier to drain, the condensed water on the protrusion structures 413 can flush the condensed water on the first base surface 411 in a drainage process, and drainage performance of the fins 4 is improved. In alternative embodiments, the projection of the first protrusion structure 413 on the first substrate surface 411 may have a circular shape (as shown in fig. 12), a semicircular shape, and other shapes, which are not limited in this application. In alternative embodiments, the plurality of first protrusion structures 413 are arranged on the base 41 in a staggered manner along the length direction L41 of the base 41, which is not limited in the present application.

As shown in fig. 8, 10 and 11, the base 41 includes a plurality of openings 416, the openings 416 are arranged along a length direction L41 of the base 41, the base 41 further includes a peripheral wall 415 located around the openings, an edge of the peripheral wall 415 includes a first flange 4141 folded from the base 41 toward the base 41 of the adjacent fin 4, the first flange 4141 includes a first end 4142 and a second end 4143, the first end 4142 is connected to the base 41, the second end 4143 is away from the base 41, the second end 4143 includes a first flange 4144 extending along the length direction L41 of the base 41 of the adjacent fin 4, and the first flange 4144 is attached to the first base surface 411 of the adjacent fin 4. The condensed water formed on the base 41 can be drained downward through the openings 416, enhancing the drainage performance of the fins 4. The arrangement of the first burring 4141 achieves the spacing between the adjacent fins 4. The provision of the first turned edge 4144 increases the connecting area of the first turned edge 4141 with the first base surface 411 of the adjacent fin 4, so that the connection between the adjacent two fins 4 is more stable. The shape of the opening 416 may be a trapezoid as shown in fig. 9, and in alternative embodiments, the shape of the opening 416 may be a triangle, a rectangle, a polygon, and the like, which is not limited in this application.

As shown in fig. 1 to 3, the heat exchanger 100 includes two side plates 5, the two side plates 5 and the plurality of heat exchange tubes 3 are arranged along a length direction of the first header 11 and/or a length direction of the second header 12, and the two side plates 5 are respectively located on two opposite sides of the plurality of heat dissipation teeth 3. The heat dissipation teeth 42 are also arranged between the side plate 5 and the adjacent heat exchange tube 3. The provision of the edge plates 5 prevents the fins 4 from being damaged. As shown in fig. 10, the header 5 includes an abutting portion 51 and a connecting portion 52 extending from the abutting portion 5 in the direction of the adjacent heat exchange tube 3.

As shown in fig. 2, the edge plate 5 includes two flat surfaces 53, and the two flat surfaces 53 are located on opposite sides in the thickness direction of the edge plate 5. As shown in fig. 7, two heat dissipating teeth 42 of the plurality of heat dissipating teeth 42 arranged side by side at opposite ends of the base portion 41 in the length direction L41 in the length direction L41 of the base portion 41 respectively have a second connecting edge 424 connected to the flat surface 53 of the edge plate 5; the fin 42 includes two first coupling edges 4211 coupled to the side surfaces 32 of the adjacent two heat exchange tubes 3, respectively, or the fin 42 includes one first coupling edge 4211 coupled to the side surface 32 of the heat exchange tube 3 and one second coupling edge 424 coupled to the flat surface 53 of the edge plate 5. As shown in fig. 7, each heat dissipating tooth 42 comprises a straight section 4212, the straight section 4212 is connected between two first connecting edges 4211 or between the first connecting edge 4211 and the second connecting edge 424, each heat dissipating tooth 42 further comprises a first section 4213 and a second section 4214 which are connected to two ends of the straight section 4212 along the direction of the first connecting edge 4211, the first section 4213 is connected with the base portion 41, and the first section 4213 has a third connecting edge 4215 connected with the first end surface 33 of the heat exchange tube 3; the second segment 4214 extends beyond the side surface 32 of the heat exchange tube 3 along the extension direction of the first connecting edge 4211, and the end of the second segment 4214 away from the straight segment 4212 along the extension direction of the first connecting edge 4211 is provided with a chamfer 425. The second segment 4214 extends beyond the second side 32 of the heat exchange tube 3 along the extension direction of the first connecting edge 4211, so that heat exchange can be enhanced. In alternative embodiments, the heat dissipating teeth 421 may not have the second segment 4214, but the heat exchange performance of the fin 4 is not as good as in the embodiment shown in fig. 7. One end of the second segment 4214, which is far away from the straight segment 4212 in the direction of the first connecting edge 4211, is provided with a chamfer 425, so that the difficulty in assembling the heat exchange tube 3 and the fin 4 in the manufacturing process of the heat exchanger 100 is reduced, and the resistance of the heat exchange tube 3 when the heat exchange tube 3 is transversely inserted into the notch 422 of the fin 4 is smaller.

As shown in fig. 10, the two first connecting edges 4211 of the heat dissipating teeth 42 respectively have a second turned edge 4218 and a third turned edge 4219 extending from the straight section 4212 to the straight section 4212 of the adjacent fin 4. The second turned edge 4218 of the heat dissipation tooth 42 is connected with the straight section 4212 of the adjacent fin 4, the third turned edge 4219 is connected with the straight section 4212 of the adjacent fin 4, and the second turned edge 4218 and the third turned edge 4219 are arranged to realize the distance between the adjacent fins 4. As shown in fig. 8, the second turned-over edge 4218 and the third turned-over edge 4219 are arranged in a staggered manner in the extending direction of the first connecting edge 4211, so that the stability of the fin 4 can be enhanced. In the present embodiment, the length of the second turned edge 4218 in the extending direction of the first connecting edge 4211 is less than half of the length of the first connecting edge 4211, and the length of the third turned edge 4219 in the extending direction of the first connecting edge 4211 is less than half of the length of the first connecting edge 4211, so that the difficulty in assembling the heat exchange tube 3 and the fin 4 during the manufacture of the heat exchanger 100 can be reduced, and the resistance of the heat exchange tube 3 when being inserted into the notch 422 of the fin 4 can be reduced. In alternative other embodiments, the length of the second turned-over edge 4218 in the extending direction of the first connecting edge 4211 is greater than half of the length of the first connecting edge 4211, and/or the length of the third turned-over edge 4219 in the extending direction of the first connecting edge 4211 is greater than half of the length of the first connecting edge 4211, which can enhance the stability of the fin 4, and only the resistance of the heat exchange tube 3 inserted into the notch 422 of the fin 4 is high during the production of the heat exchanger 100.

As shown in fig. 8, the heat dissipating tooth 42 has a fourth turned edge 4216 extending from the straight section 4212 to the straight section 4212 of the adjacent fin 4 at the first connecting edge 4211, and the fourth turned edge 4216 is connected to the side surface 32 of the heat exchange tube 3. The length of the fourth turned-over edge 4216 in the thickness direction of the heat dissipation teeth 42 is smaller than that of the second turned-over edge 4218 in the thickness direction of the heat dissipation teeth 42, and the length of the fourth turned-over edge 4216 in the thickness direction of the heat dissipation teeth 42 is smaller than that of the third turned-over edge 4219 in the thickness direction of the heat dissipation teeth 42. The fourth turned-over edge 4216 increases the connection area of the fin 4 and the heat exchange tube 3, so that the connection of the fin 4 and the heat exchange tube 3 is more stable. The heat exchange tube 3 and the fin 4 may be joined by brazing.

As shown in fig. 11, the heat dissipation teeth 42 include a first surface 426 and a second surface 427 located on opposite sides of the heat dissipation teeth 42 in the thickness direction, and the first surface 426 and the first base surface (411) form a continuous surface. The heat sink teeth 42 include at least one fenestration (433) to facilitate drainage. In other alternative embodiments, the first face 426 of the heat sink tooth 42 may be planar as shown in FIG. 13; when the heat exchanger 100 is used as an evaporator, condensed water is formed on the heat dissipation teeth 42, and when the heat exchanger 100 is used as an evaporator and the temperature reaches the dew point temperature, at least a portion of the condensed water is turned into frost. It is more suitable that the first face 426 of the heat dissipating teeth 42 be planar. In an alternative embodiment, as shown in FIG. 14, the heat dissipating teeth 42 include at least one second raised structure 428 protruding from the first face 426. the second raised structure 428 combines the benefits of increased strength and drainage of the fin 4. Preferably, the surface of the fin 4 is coated with a hydrophobic coating to facilitate drainage.

As shown in fig. 15 and 16, a second embodiment of the present application is different from the first embodiment of the present application in that the extending direction of the first connection edge 4211 of the heat dissipation tooth 42 is parallel to the width direction W3 of the heat exchange tube 3. As shown in fig. 17 and 18, the third embodiment of the present application is different from the first embodiment of the present application in that the first connecting edge 4211 extends at a second angle β with respect to the width direction W3 of the heat exchange tube 3, and the second angle β is larger than the first angle α. It should be understood that the included angle refers to a smallest positive angle formed by the intersection of two straight lines according to the definition of the included angle, and therefore, the second included angle β referred to herein is a smallest positive angle formed by the extending direction of the first connecting edge 4211 and the width direction of the heat exchange tube 3. The second included angle β is larger than the first included angle α, and the drainage performance of the fin 4 is further enhanced.

Although the present application has been described with reference to a preferred embodiment, it should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the application, and all changes, substitutions and alterations that fall within the spirit and scope of the application are to be understood as being covered by the following claims.

Claims (10)

1. A heat exchanger (100), characterized in that the heat exchanger (100) comprises: the heat exchange tube comprises a first collecting pipe (11), a second collecting pipe (12), a plurality of heat exchange tubes (3) and a plurality of fins (4), wherein the heat exchange tubes (3) comprise a first end part and a second end part which are positioned at two opposite ends of the heat exchange tube (3) in the length direction (L3), the first end part is connected with the first collecting pipe (11), the second end part is connected with the second collecting pipe (12), the heat exchange tubes (3) comprise channels (31) for communicating an inner cavity (17) of the first collecting pipe (11) with an inner cavity (17) of the second collecting pipe (12), the heat exchange tubes (3) comprise two side surfaces (32), a first end surface (33) and a second end surface (34), the first end surface (33) and the second end surface (34) are respectively positioned at two opposite sides of the heat exchange tube (3) in the width direction (W3), the two side surfaces (32) are respectively positioned at two opposite sides of the heat exchange tube (3, the width of the heat exchange tube (3) is larger than the thickness of the heat exchange tube (3);

the fin (4) comprises a base (41) and a plurality of heat dissipation teeth (42), the plurality of heat dissipation teeth (42) are arranged along the length direction (L41) of the base (41) and connected with one side of the width direction (W41) of the base (41), a notch (422) is arranged between every two adjacent heat dissipation teeth (42), the heat exchange tube (3) is at least partially matched in the corresponding notch (422), the heat dissipation teeth (42) are connected with the side surface (32) of the heat exchange tube (3), and the width direction (W41) of the base (41) is obliquely arranged relative to the width direction (W3) of the heat exchange tube (3).

2. The heat exchanger (100) of claim 1, wherein the width direction (W41) of the base portion (41) forms a first angle (α) with the width direction (W3) of the heat exchange tube (3), the first angle (α) having a value in the interval 10 ° -50 °.

3. The heat exchanger (100) according to claim 1, wherein the heat dissipation tooth (42) has at least one first connection edge (4211) connected to a side (32) of a heat exchange tube (3), the first connection edge (4211) being arranged obliquely with respect to a width direction (W3) of the heat exchange tube (3).

4. The heat exchanger (100) according to claim 3, wherein the extension direction of the first connecting edge (4211) is parallel to the width direction (W41) of the base portion (41) or the extension direction of the first connecting edge (4211) coincides with the width direction (W41) of the base portion (41).

5. The heat exchanger (100) according to claim 3, wherein the first joint edge (4211) extends in a second angle (β) with the width direction (W3) of the heat exchange tube (3), the second angle (β) having a value in the interval 10 ° -50 °.

6. The heat exchanger (100) according to claim 1, wherein the base (41) comprises a first base surface (411) and a second base surface (412) which are respectively located on both sides of the base (41) in the thickness direction, the base (41) comprises a plurality of first protruding structures (413) protruding from the first base surface (411), and the plurality of first protruding structures (413) are arranged along the length direction (L41) of the base (41).

7. The heat exchanger (100) of claim 6, wherein the base (41) comprises a plurality of openings (416), the openings (416) being arranged along a length direction (L41) of the base (41), the base (41) further comprising a peripheral wall (415) around the openings (416), the base (41) comprising a first flange (4141) extending from an edge of the peripheral wall (415) towards the base (41) of an adjacent fin (4), the first flange (4141) comprising a first end (4142) and a second end (4143), the first end (4142) being connected to the base (41), the second end (4143) being remote from the base (41), the second end (4143) being connected to the first base surface (411) of an adjacent fin (4).

8. The heat exchanger (100) according to claim 6, wherein the heat exchanger (100) comprises two side plates (5), the two side plates (5) and the plurality of heat exchange tubes (3) are arranged along the length direction of the first collecting pipe (11) and/or the length direction of the second collecting pipe (12), and the two side plates (5) are respectively located at two opposite sides of the plurality of heat exchange tubes (3).

9. The heat exchanger (100) according to claim 8, wherein the edge plate (5) includes two flat surfaces (53), the two flat surfaces (53) being located on opposite sides of the thickness direction of the edge plate (5), and among the plurality of heat dissipation teeth (42), two heat dissipation teeth (42) located at opposite ends of the length direction (L41) of the base portion (41) have a second connecting edge (424) connected to the flat surface (53) of the edge plate (5); the heat dissipation tooth (42) comprises two first connecting edges (4211) which are respectively connected with the side surfaces (32) of two adjacent heat exchange tubes (3), or the heat dissipation tooth (42) comprises one first connecting edge (4211) which is connected with the side surfaces (32) of the heat exchange tubes (3) and one second connecting edge (424) which is connected with the plane (53) of the side plate (5);

the heat dissipation tooth (42) comprises a straight section (4212), the straight section (4212) is connected with two first connecting edges (4211) or one first connecting edge (4211) and one second connecting edge (424), the heat dissipation tooth (42) further comprises a first section (4213) and a second section (4214) which are connected with two ends of the straight section (4212) along the extending direction of the first connecting edge (4211), the first section (4213) is connected with the base part (41), and the first section (4213) is provided with a third connecting edge (4215) connected with the first end surface (33) of the heat exchange tube (3);

the second section (4214) extends beyond the side (32) of the heat exchange tube (3) in the direction of extension of the first connecting edge (4211);

the end of the second section (4214) far away from the straight section (4212) along the extension direction of the first connecting edge (4211) is provided with a chamfer (425);

the two first connecting edges (4211) of the heat dissipation teeth (42) are respectively provided with a second flanging (4218) and a third flanging (4219) which extend from the straight section (4212) to the straight section (4212) of the adjacent fin (4), and the second flanging (4218) and the third flanging (4219) are arranged in a staggered mode in the extending direction of the first connecting edges (4211);

the heat dissipation tooth (42) comprises a first face (426) and a second face (427) which are positioned on two opposite sides of the thickness direction of the heat dissipation tooth, the first face (426) and the first base body surface (411) form a continuous surface, and the first face (426) is a plane;

the heat dissipating teeth (42) include at least one second raised structure (428) projecting from the first face (426); the heat dissipating teeth (42) include at least one fenestration (433).

10. The heat exchanger (100) according to any one of claims 1 to 9, wherein the width direction (W3) of the heat exchange tube (3) is located on a horizontal plane perpendicular to the direction of gravity when the heat exchanger (100) is applied to a thermal management system (6).

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