Heat exchangers and heating and ventilation devices

Abstract

The utility model provides a kind of heat exchanger and heating and ventilation equipment, heat exchanger includes multiple first fin units, multiple second fin units and multiple heat exchange tube assemblies, heat exchange tube assembly includes first heat exchange tube and second heat exchange tube, the flow area of first heat exchange tube is greater than the flow area of second heat exchange tube. Condensate produced when heat exchanger works can be discharged through the windward part of first fin unit and the leeward part of second fin unit, improve the drainage performance of heat exchanger. The first fin unit of larger heat load and more condensate generation located windward side is installed with the first heat exchange tube of larger flow area, the second fin unit of smaller heat load and less condensate generation located leeward part is installed with the second heat exchange tube of smaller flow area, so that the structure design of fin assembly is optimized by zoning in combination with temperature distribution and heat exchange characteristics of air side, so that the distribution of heat exchange tube is matched with temperature field and heat exchange characteristics, reduce the redundancy of fin, improve the efficiency and utilization of overall fin.

Description

Technical Field

[0001] This utility model relates to the field of heat exchanger technology, and in particular to a heat exchanger and HVAC equipment. Background Technology

[0002] This section provides only background information relevant to this disclosure and is not necessarily prior art.

[0003] The fin drainage path design of existing heat exchangers is unreasonable, especially under condensation conditions, which can easily cause condensate to accumulate and stagnate, reducing heat exchange efficiency. Furthermore, it is prone to freezing in low-temperature environments, affecting the stable operation of the system.

[0004] In addition, the utilization rate of the fins is low and the heat exchange enhancement is insufficient: the existing fin design does not take into account the temperature distribution and heat exchange characteristics of the air side for zonal optimization, resulting in fin redundancy in some areas and insufficient enhancement in other areas. The overall fin heat exchange efficiency and utilization rate are not high, which limits the further improvement of heat exchanger performance. Utility Model Content

[0005] The purpose of this invention is to at least solve the technical problems of low fin redundancy utilization and low heat exchange efficiency in existing heat exchangers. This purpose is achieved through the following technical solution:

[0006] The first aspect of this utility model provides a heat exchanger, comprising:

[0007] A plurality of first fin units are spaced apart along a first direction. Each first fin unit includes a plurality of first fins connected sequentially along a second direction. The positions of the plurality of first fins of adjacent first fin units along the first direction correspond to each other in the second direction. Each first fin includes a windward portion and a first connecting portion arranged along a third direction. The first direction, the second direction, and the third direction are perpendicular to each other. In the same first fin unit, a first installation space is formed between the two first connecting portions of two adjacent first fins.

[0008] A plurality of second fin units are spaced apart along the first direction. Each second fin unit includes a plurality of second fins connected sequentially along the second direction. The positions of the plurality of second fins of adjacent second fin units along the first direction are corresponding in the second direction. Each second fin includes a second connecting portion and a leeward portion arranged along the third direction. In the same second fin unit, a second mounting space is formed between the two second connecting portions of two adjacent second fins.

[0009] A plurality of heat exchange tube assemblies are spaced apart along the second direction. Each heat exchange tube assembly includes a first heat exchange tube and a second heat exchange tube. The flow area of ​​the first heat exchange tube is larger than that of the second heat exchange tube. The first heat exchange tube extends along the first direction and passes through a plurality of first installation spaces arranged along the first direction. The second heat exchange tube extends along the first direction and passes through a plurality of second installation spaces arranged along the first direction.

[0010] The heat exchanger proposed in the first aspect of this utility model has a first heat exchange tube installed in a first installation space and a second heat exchange tube installed in a second installation space. One side of the first installation space has a windward section, and one side of the second installation space has a leeward section. Condensate generated during heat exchanger operation can be discharged through the windward and leeward sections, improving the heat exchanger's drainage performance. Furthermore, the first heat exchange tube with a larger flow area is installed on the windward side, where the heat load is higher and more condensate is generated, while the second heat exchange tube with a smaller flow area is installed on the leeward side, where the heat load is lower and less condensate is generated. This allows the fin assembly structure design to be optimized by zone based on the air-side temperature distribution and heat exchange characteristics. The first heat exchanger, with a higher flow rate, exchanges heat on the windward side where the heat exchange capacity is strong, while the second heat exchange tube, with a lower flow rate, exchanges heat on the leeward side where the heat exchange capacity is weaker. This ensures that the distribution of heat exchange tubes matches the temperature field and heat exchange characteristics, reducing fin redundancy and improving the overall fin efficiency and utilization rate.

[0011] In addition, the heat exchanger according to this utility model may also have the following additional technical features:

[0012] In some embodiments of this utility model, along the second direction, the length of the windward portion is greater than the length of the leeward portion;

[0013] And / or, along the second direction, the length of the first mounting space is greater than the length of the second mounting space.

[0014] In some embodiments of this utility model, the plurality of first fin units are located upstream of the plurality of second fin units in the airflow direction, and the windward portion, the first connecting portion, the second connecting portion and the leeward portion are arranged sequentially along the airflow direction;

[0015] Alternatively, the plurality of first fin units are located upstream of the plurality of second fin units in the airflow direction, and the windward portion, the first connecting portion, the leeward portion and the second connecting portion are arranged sequentially along the airflow direction.

[0016] In some embodiments of this utility model, the first fin is a flat fin;

[0017] And / or, the second fin is a flat fin.

[0018] In some embodiments of this utility model, at least one of the first connecting portion and the second connecting portion is provided with a heat exchange enhancement structure.

[0019] In some embodiments of this utility model, the heat exchange enhancement structure is a corrugated structure.

[0020] In some embodiments of this utility model, both the first connecting part and the second connecting part are provided with heat exchange enhancement structures;

[0021] The length of the corrugated structure along the third direction is W. W The length of the corrugated structure along the second direction is L. e Among them, W w =L e ;

[0022] And / or, the length of the corrugated structure along the first direction is h. w Along the first direction, the distance between two adjacent first fins is p. f1 The spacing between two adjacent second fins is p f2 Where 0.3≤h w / p f1 ≤0.8, 0.3≤h w / p f2 ≤0.8;

[0023] And / or, along the third direction, the length of the first installation space is t. w1 And the length of the second installation space is t w2 Along the second direction, the distance between two adjacent first installation spaces is p. t1 And the distance between two adjacent second installation spaces is p t2 The length of the corrugated structure along the second direction is L. w , where 0.5≤L w / (p t1 -t w1 )<1, 0.5≤L w / (p t2 -t w2 )<1.

[0024] In some embodiments of this utility model, the heat exchange enhancement structure is a bridge-type structure.

[0025] In some embodiments of this utility model, both the first connecting part and the second connecting part are provided with heat exchange enhancement structures;

[0026] Along the first direction, the length of the bridge structure is h.s Along the first direction, the distance between two adjacent first fins is p. f1 The spacing between two adjacent second fins is p f2 Where 0.3≤h s / p f1 ≤0.8, 0.3≤h s / p f2 ≤0.8;

[0027] And / or, the number N of the bridge structures s , 2≤N s ≤15;

[0028] And / or, the number of the bridge structures is multiple, the multiple bridge structures are arranged along the third direction, and the length of each bridge structure along the third direction is equal;

[0029] And / or, the sum of the lengths of all the bridge structures along the second direction is L. s Along the third direction, the length of the first installation space is t. w1 And the length of the second installation space is t w2 Along the second direction, the distance between two adjacent first installation spaces is p. t1 And the distance between two adjacent second installation spaces is p t2 , where 0.5≤L s / (p t1 -t w1 )<1, 0.5≤L s / (p t2 -t w2 )<1.

[0030] In some embodiments of this utility model, the heat exchange enhancement structure is a louvered structure.

[0031] In some embodiments of this utility model, both the first connecting part and the second connecting part are provided with heat exchange enhancement structures;

[0032] The louvered structure includes multiple air vents arranged along the third direction, each air vent having an air guide vane, and the number of air vents is N1, where 2≤N l ≤15;

[0033] And / or, the louvered structure includes a plurality of air vents arranged along the third direction, each air vent having an air guide vane, the plurality of air guide vanes being arranged in parallel, and the spacing between two adjacent air guide vanes along the third direction being p. f The length of the air guide vane along the air guide direction of the air guide opening is w, and sinα≤pf / w≤3sinα, where α is the angle between the air guide vane and the third direction, 20°≤α≤35°;

[0034] And / or, along the second direction, the length of the first installation space is t w1 The distance between two adjacent first installation spaces is p t1 The length of the second installation space is t w2 The distance between two adjacent second installation spaces is p t2 The length of the air guide vane along the second direction is l d , 0.5≤l d / (p t1 -t w1 ) < 1, and 0.5 ≤ l d / (p t2 -t w2 ) < 1.

[0035] In some embodiments of this utility model, along the third direction, the minimum distance from the heat exchange enhancement structure to the end of the windward portion away from the first connecting portion is l1, and the length of the first fin is L1.

[0036] 0.2≤l1 / L1≤0.5, the maximum distance from the heat exchange enhancement structure to the end of the windward portion away from the first connecting portion is l2, 0.5≤l2 / L1≤1.0;

[0037] And / or, along the third direction, the minimum distance from the heat exchange enhancement structure to the end of the leeward portion away from the second connecting portion is l3, the length of the second fin is L2, 0.2≤l3 / L2≤0.5, and the maximum distance from the heat exchange enhancement structure to the end of the leeward portion away from the first connecting portion is l4, 0.5≤l4 / L2≤1.0.

[0038] In some embodiments of this utility model, along the first direction, the spacing between two adjacent second fin units is greater than or equal to the spacing between two adjacent first fin units.

[0039] In some embodiments of this utility model, the length of the windward portion along the third direction is e1, 6mm≤e1≤12mm, the length of the leeward portion along the third direction is e2, 0.2≤e2 / e1≤1, the length of the first fin along the third direction is L1, and the length of the second fin along the third direction is L2, 0<e1 / L1≤0.5, 0<e2 / L2≤0.5.

[0040] In some embodiments of this utility model, the first fin unit is provided with a water guiding structure, which is sequentially disposed on a plurality of the windward portions arranged along the second direction in the same first fin unit, and is used to discharge the condensate on the windward portions to the outside of the fin assembly.

[0041] In some embodiments of this utility model, the first heat exchange tube and the second heat exchange tube of each heat exchange tube assembly are separately arranged;

[0042] Alternatively, the heat exchange tube assembly may further include a connecting structure, through which a portion of the sidewall of the first heat exchange tube of the same heat exchange tube assembly is connected to a portion of the sidewall of the second heat exchange tube.

[0043] In some embodiments of this utility model, the heat exchanger further includes:

[0044] The first manifold is connected to one end of all the first heat exchange tubes and one end of all the second heat exchange tubes.

[0045] The second manifold is connected to the other ends of all the first heat exchange tubes and all the other ends of the second heat exchange tubes.

[0046] In some embodiments of this utility model, the heat exchanger further includes a third manifold and a fourth manifold. In the same heat exchange tube assembly, one end of the first heat exchange tube is connected to the third manifold, the other end of the first heat exchange tube is connected to one end of the second heat exchange tube, and the other end of the second heat exchange tube is connected to the fourth manifold.

[0047] The second aspect of this utility model provides a heating and ventilation device, including the microchannel heat exchanger proposed in the second aspect of this utility model.

[0048] The heat exchanger for HVAC equipment proposed in the second aspect of this utility model has a strong drainage capacity, a compact structure, and high heat exchange efficiency. The heat exchanger has a first heat exchange tube installed in a first installation space and a second heat exchange tube installed in a second installation space. One side of the first installation space has a windward section, and one side of the second installation space has a leeward section. Condensate generated during heat exchanger operation can be discharged through the windward and leeward sections, improving the drainage performance of the heat exchanger. Furthermore, the first heat exchange tube with a larger flow area is installed on the windward side, where the heat load is higher and more condensate is generated, while the second heat exchange tube with a smaller flow area is installed on the leeward side, where the heat load is lower and less condensate is generated. This allows the structural design of the fin assembly to be optimized by zone based on the temperature distribution and heat exchange characteristics of the air side. The first heat exchanger, with a higher flow rate, exchanges heat on the windward side where the heat exchange capacity is strong, while the second heat exchange tube, with a lower flow rate, exchanges heat on the leeward side where the heat exchange capacity is weaker. This ensures that the distribution of the heat exchange tubes matches the temperature field and heat exchange characteristics, reducing fin redundancy and improving the overall efficiency and utilization rate of the fins. Attached Figure Description

[0049] Various other advantages and benefits will become apparent to those skilled in the art upon reading the following detailed description of preferred embodiments. The accompanying drawings are for illustrative purposes only and are not intended to limit the scope of the invention. Furthermore, the same reference numerals denote the same parts throughout the drawings. In the drawings:

[0050] Figure 1 A schematic diagram of the structure of a heat exchanger (single row of plugs, with inlet and outlet on both sides) according to an embodiment of the present invention is shown.

[0051] Figure 2 A schematic diagram of the structure of a heat exchanger (single row of plugs, single side inlet and outlet) according to an embodiment of the present invention is shown.

[0052] Figure 3 A schematic diagram of the structure of a heat exchanger (double-row side-insertion) according to an embodiment of the present invention is shown.

[0053] Figure 4 A schematic diagram of the structure of a heat exchanger (double row plug-in) according to an embodiment of the present invention is shown.

[0054] Figure 5 The schematic diagram shows the structure of the first fin and the second fin (double-row side insertion, flat plate heat exchange enhancement zone) according to an embodiment of the present invention.

[0055] Figure 6 The schematic diagram shows the structure of the first fin and the second fin (double row interlocking, flat plate heat exchange enhancement zone) according to an embodiment of the present invention.

[0056] Figure 7 The schematic diagram shows the structure of the first fin and the second fin (single row of interlocking, flat plate heat exchange enhancement zone) according to an embodiment of the present invention.

[0057] Figure 8 A schematic diagram of the structure of the first fin (flat-plate heat exchange enhancement zone) according to an embodiment of the present invention is shown.

[0058] Figure 9 A schematic diagram of the structure of the second fin (flat-plate heat exchange enhancement zone) according to an embodiment of the present invention is shown.

[0059] Figure 10 The schematic diagram shows the structure of the first fin and the second fin (double-row side insertion, corrugated heat transfer enhancement zone) according to an embodiment of the present invention.

[0060] Figure 11 The schematic diagram shows the structure of the first fin and the second fin (double row interlocking, corrugated heat transfer enhancement zone) according to an embodiment of the present invention.

[0061] Figure 12 The schematic diagram shows the structure of the first fin and the second fin (single row interlocking, corrugated heat transfer enhancement zone) according to an embodiment of the present invention.

[0062] Figure 13 A schematic diagram of the structure of the first fin (corrugated heat transfer enhancement zone) according to an embodiment of the present invention is shown.

[0063] Figure 14 The schematic diagram shows the structure of the first fin and the second fin (double-row side insertion, bridge-type heat exchange enhancement zone) according to an embodiment of the present invention.

[0064] Figure 15 The schematic diagram shows the structure of the first fin and the second fin (double row interlocking, bridge-type heat transfer enhancement zone) according to an embodiment of the present invention.

[0065] Figure 16 The schematic diagram shows the structure of the first and second fins (single row of interlocking, bridge-type heat transfer enhancement zone) according to an embodiment of the present invention.

[0066] Figure 17 A schematic cross-sectional view of the first fin (bridge-shaped heat exchange enhancement zone) according to an embodiment of the present invention is shown.

[0067] Figure 18The schematic diagram shows the structure of the first fin and the second fin (double-row side insertion, louver-type heat exchange enhancement zone) according to an embodiment of the present invention.

[0068] Figure 19 The schematic diagram shows the structure of the first fin and the second fin (double row interlocking, louver-type heat exchange enhancement zone) according to an embodiment of the present invention.

[0069] Figure 20 The schematic diagram shows the structure of the first and second fins (single row of interlocking, louver-type heat exchange enhancement zone) according to an embodiment of the present invention.

[0070] Figure 21 A schematic cross-sectional view of the first fin (louver-type heat exchange enhancement zone) according to an embodiment of the present invention is shown.

[0071] The markings in the attached diagram are as follows:

[0072] 100. Heat exchanger;

[0073] 10. First fin unit; 11. First fin; 111. Windward section; 112. First connecting section; 113. First mounting space;

[0074] 20. Second fin unit; 21. Second fin; 211. Leeward portion; 212. Second connecting portion; 213. Second mounting space;

[0075] 30. Heat exchange enhancement structure; 31. Corrugated structure; 32. Bridge-type structure; 33. Louver-type structure; 331. Air guide; 332. Air guide vane;

[0076] 40. First heat exchange tube; 41. Second heat exchange tube; 42. First manifold; 43. Second manifold; 44. Third manifold; 45. Fourth manifold; 46. Connection structure;

[0077] The X direction is the first direction;

[0078] Y-axis is a third-party direction;

[0079] The Z direction is the second direction. Detailed Implementation

[0080] Exemplary embodiments of the present disclosure will now be described in more detail with reference to the accompanying drawings. While exemplary embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.

[0081] It should be understood that the terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “described” as used herein may also include the plural forms. The terms “comprising,” “including,” “containing,” and “having” are inclusive and therefore indicate the presence of the stated features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not construed as requiring them to be performed in a particular order described or illustrated unless the order of performance is explicitly indicated. It should also be understood that additional or alternative steps may be used.

[0082] Although terms such as first, second, third, etc., may be used in this document to describe multiple elements, components, regions, layers, and / or segments, these elements, components, regions, layers, and / or segments should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or segment from another. Unless the context clearly indicates otherwise, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence. Therefore, the first element, component, region, layer, or segment discussed below may be referred to as the second element, component, region, layer, or segment without departing from the teachings of the exemplary embodiments.

[0083] For ease of description, spatial relative terms may be used in the text to describe the relationship of one element or feature relative to another element or feature, as shown in the figure. These relative terms include, for example, "inside," "outside," "middle," "outer," "below," "below," "above," "over," etc. Such spatial relative terms are intended to include different orientations of the device in use or operation, other than those depicted in the figure. For example, if the device in the figure is flipped, an element described as "below other elements or features" or "below other elements or features" would subsequently be oriented as "above other elements or features" or "above other elements or features." Therefore, the example term "below" can include both upper and lower orientations. The device may be otherwise oriented (rotated 90 degrees or in other directions), and the spatial relative descriptors used in the text will be interpreted accordingly.

[0084] like Figures 1 to 21 As shown, the first aspect of this utility model provides a heat exchanger 100, comprising:

[0085] A plurality of first fin units 10 are spaced apart along a first direction. Each first fin unit 10 includes a plurality of first fins 11 connected sequentially along a second direction. The positions of the plurality of first fins 11 of adjacent first fin units 10 along the first direction correspond to each other in the second direction. Each first fin 11 includes a windward portion 111 and a first connecting portion 112 arranged along a third direction. The first direction, the second direction, and the third direction are perpendicular to each other. A first mounting space 113 is formed between the two first connecting portions 112 of two adjacent first fins 11.

[0086] A plurality of second fin units 20 are spaced apart along a first direction. Each second fin unit 20 includes a plurality of second fins 21 connected sequentially along a second direction. The positions of the plurality of second fins 21 of adjacent second fin units 20 along the first direction are corresponding in the second direction. Each second fin 21 includes a second connecting portion 212 and a leeward portion 211 arranged along a third direction. A second mounting space 213 is formed between the two second connecting portions 212 of two adjacent second fins 21.

[0087] A plurality of heat exchange tube assemblies are spaced apart along a second direction. Each heat exchange tube assembly includes a first heat exchange tube 40 and a second heat exchange tube 41. The flow area of ​​the first heat exchange tube 40 is larger than that of the second heat exchange tube 41. The first heat exchange tube 40 extends along a first direction and passes through a plurality of first installation spaces 113 arranged along the first direction. The second heat exchange tube 41 extends along the first direction and passes through a plurality of second installation spaces 213 arranged along the first direction.

[0088] As can be seen, the heat exchanger 100 proposed in the first aspect of this utility model has a first heat exchange tube 40 installed in a first installation space 113 and a second heat exchange tube 41 installed in a second installation space 213. A windward part 111 is provided on one side of the first installation space 113 and a leeward part 211 is provided on one side of the second installation space 213. The condensate generated when the heat exchanger 100 is working can be discharged through the windward part 111 and the leeward part 211, thereby improving the drainage performance of the heat exchanger 100. Furthermore, a first heat exchange tube 40 with a larger flow area is installed on the windward side where the heat load is higher and more condensate is generated, while a second heat exchange tube 41 with a smaller flow area is installed on the leeward side 211 where the heat load is lower and less condensate is generated. This allows the structural design of the fin assembly to be optimized by partitioning the temperature distribution and heat exchange characteristics of the air side. The first heat exchanger 100 with a larger flow rate is used for heat exchange on the windward side where the heat exchange capacity is strong, while the second heat exchange tube 41 with a smaller flow rate is used for heat exchange on the leeward side where the heat exchange capacity is weaker. This ensures that the distribution of the heat exchange tubes matches the temperature field and heat exchange characteristics, reducing fin redundancy and improving the overall efficiency and utilization rate of the fins.

[0089] In addition, the heat exchanger 100 of this utility model can be a microchannel heat exchanger 100 or other types of heat exchangers 100, and the type of heat exchanger 100 is not further limited here.

[0090] like Figures 1 to 21 As shown, in some embodiments of this utility model, along the second direction, the length of the windward portion 111 is greater than the length of the leeward portion 211;

[0091] And / or, along the second direction, the length of the first mounting space 113 is greater than the length of the second mounting space 213.

[0092] It is evident that by making the length of the windward portion 111 in the second direction greater than the length of the leeward portion 211, the windward portion 111, which generates more condensate, can improve its drainage efficiency, and the contact area between the windward portion 111, which has a higher heat load, and the air can be increased, thereby improving its heat exchange efficiency. Furthermore, with the spacing between adjacent first fins 11 in the second direction being equal to the spacing between adjacent second fins 21 in the second direction, the length of the first mounting space 113 in the second direction is set to be greater than the length of the second mounting space 213. This allows the first mounting space 113 to accommodate the installation of a thicker first heat exchange tube 40, while the second mounting space 213 accommodates a thinner second heat exchange tube 41.

[0093] In some embodiments of this utility model, a plurality of first fin units 10 are located upstream of a plurality of second fin units 20 in the airflow direction, and along the airflow direction, the windward portion 111, the first connecting portion 112, the second connecting portion 212 and the leeward portion 211 are arranged sequentially.

[0094] Alternatively, multiple first fin units 10 are located upstream of multiple second fin units 20 in the airflow direction, and along the airflow direction, the windward portion 111, the first connecting portion 112, the leeward portion 211, and the second connecting portion 212 are arranged sequentially.

[0095] As can be seen, the first fin unit 10 and the second fin unit 20 can be connected to the heat exchange tube assembly by interlocking or inserting on the same side, thereby improving the assembly flexibility of the fin assembly.

[0096] For example, in the first fin unit 10 and the second fin unit 20 corresponding to each other along the second direction, the windward portion 111, the first connecting portion 112, the second connecting portion 212 and the leeward portion 211 are arranged sequentially along the third direction, that is, along the direction from windward to leeward. The windward portion 111 and the first connecting portion 112 are arranged sequentially and connected to each other, and the second connecting portion 212 and the leeward portion 211 are arranged sequentially and connected to each other, so that heat exchange tube assemblies can be assembled between the first fin unit 10 and the second fin unit 20 to realize plug-in assembly. Furthermore, in the first fin unit 10 and the second fin unit 20 corresponding to each other along the second direction, the windward portion 111, the first connecting portion 112, the leeward portion 211 and the second connecting portion 212 are arranged sequentially along the third direction, that is, along the direction from windward to leeward, the windward portion 111 and the first connecting portion 112 are arranged sequentially and connected to each other, and the leeward portion 211 and the second connecting portion 212 are arranged sequentially and connected to each other, so that the leeward side of the first fin unit 10 and the leeward side of the second fin unit 20 can be equipped with heat exchange tube assemblies, so that the first heat exchange tube 40 and the second heat exchange tube 41 of the heat exchange tube assembly are assembled on the same side of the first fin unit 10 and the second fin unit 20, that is, on the leeward side.

[0097] like Figures 5 to 9 As shown, in some embodiments of this utility model, the first fin 11 is a flat fin;

[0098] And / or, the second fin 21 is a flat fin.

[0099] It is evident that the first fin 11 and the second fin 21 are set as flat fins to save costs.

[0100] In some embodiments of this utility model, both the first connecting part 112 and the second connecting part 212 are provided with heat exchange enhancement structures 30.

[0101] It can be seen that a heat exchange enhancement structure 30 can be provided on the first connecting portion 112 and the second connecting portion 212 to enhance the heat exchange capacity of the first fin 11 near the first connecting portion 112 of the first heat exchange tube 40, improve ventilation efficiency, and thus improve heat exchange efficiency. Furthermore, the heat exchange capacity of the second fin 21 near the second connecting portion 212 of the first heat exchange tube 40 is enhanced to improve ventilation efficiency and thus improve heat exchange efficiency.

[0102] For example, the heat exchange enhancement structure 30 can be a corrugated structure 31, a bridge-shaped structure 32, or a louver structure. That is, the corrugated structure 31 is stamped out on the first fin 11 and the second fin 21, or the bridge-shaped structure 32 and the louver structure are cut and bent out, so as to increase the heat dissipation area of ​​the first fin 11 and the second fin 21, thereby improving the heat dissipation capacity of the first fin 11 and the second fin 21. The bridge-shaped structure 32 and the louver structure can connect the two sides of the first fin 11 and the second fin 21, so that air on one side can pass through the first fin 11 and the second fin 21 and carry away the heat of the first fin 11 and the second fin 21.

[0103] like Figures 10 to 13 As shown, in some embodiments of this utility model, the heat exchange enhancement structure 30 is a corrugated structure 31. The corrugated structure 31 increases the heat dissipation area of ​​the first fin 11 and the second fin 21, thereby improving the heat dissipation capacity of the first fin 11 and the second fin 21.

[0104] like Figures 10 to 13 As shown, in some embodiments of this utility model, the length of the corrugated structure 31 along the third direction is W. W， The length of the corrugated structure 31 along the second direction is L e Among them, W w =L e ;

[0105] And / or, the length of the corrugated structure 31 along the first direction is h. w Along the first direction, the distance between two adjacent first fins 11 is p. f1 The distance between two adjacent second fins 21 is p f2 Where 0.3≤h w / p f1 ≤0.8, 0.3≤h w / p f2 ≤0.8;

[0106] And / or, along a third direction, the length of the first installation space 113 is t w1 And the length of the second installation space 213 is t w2 Along the second direction, the distance between two adjacent first installation spaces 113 is p. t1 And the distance between two adjacent second installation spaces 213 is p t2 The length of the corrugated structure 31 along the second direction is L. w , where 0.5≤L w / (p t1 -t w1 )<1, 0.5≤L w / (p t2 -t w2 )<1.

[0107] As can be seen, the corrugated structure 31 of this utility model has a triangular cross-section along the second direction. It includes two triangular plates spaced apart along the second direction and a V-shaped plate disposed between the two triangular plates. By reasonably setting the length, width and height of the corrugated structure 31, as well as the dimensions of the corrugated structure 31 relative to the first installation space 113 and the second installation space 213, that is, the dimensions of the corrugated structure 31 relative to the first heat exchange tube 40 located in the first installation space 113 and the dimensions of the corrugated structure 31 relative to the second heat exchange tube 41 located in the second installation space 213, the structural strength and heat exchange efficiency of the corrugated structure 31 are improved.

[0108] like Figures 14 to 17 As shown, in some embodiments of this utility model, the heat exchange enhancement structure 30 is a bridge-type structure 32, which enables the two sides of the first fin 11 and the second fin 21 to be connected through the opening of the bridge-type structure 32, so that air on one side can pass through the first fin 11 and the second fin 21, and carry away the heat of the first fin 11 and the second fin 21, thereby improving the heat exchange efficiency of the first fin 11 and the second fin 21.

[0109] like Figures 14 to 17 As shown, in some embodiments of this utility model, the length of the bridge structure 32 along the first direction is h. s Along the first direction, the distance between two adjacent first fins 11 is p. f1 The distance between two adjacent second fins 21 is p f2 Where 0.3≤h s / p f1 ≤0.8, 0.3≤h s / p f2 ≤0.8;

[0110] And / or, the number N of bridge-type structures 32 s , 2≤N s ≤15;

[0111] And / or, the number of bridge structures 32 is multiple, the multiple bridge structures 32 are arranged along a third direction, and the length of each bridge structure 32 along the third direction is equal;

[0112] And / or, the sum of the lengths of all bridge structures 32 along the second direction is L. s Along the third direction, the length of the first installation space 113 is t. w1 And the length of the second installation space 213 is t w2 Along the second direction, the distance between two adjacent first installation spaces 113 is p. t1 And the distance between two adjacent second installation spaces 213 is p t2 , where 0.5≤Ls / (p t1 -t w1 )<1, 0.5≤L s / (p t2 -t w2 )<1.

[0113] As can be seen, the bridge structure 32 of this utility model includes a bridge plate and two side plates connected on both sides. Two adjacent bridge structures 32 are located on opposite sides of the thickness direction of the first fin 11 or the second fin 21, and are staggered. Airflow on one side of the first fin 11 can pass through the opening formed by the bridge structure 32 to the other side of the first fin 11, and airflow on both sides of the second fin 21 can also pass through the bridge structure 32. Furthermore, by reasonably setting the starting and ending regions of the bridge structure 32, and the height h of the bridge structure 32... s This makes the position and height of the bridge structure 32 more reasonable, improving the heat dissipation effect of the fin assembly. Regarding the number of bridge structures 32, based on N of the number of bridge structures 32... s Analysis shows that a higher number of bridge structures 32 results in better heat exchange performance, but also a greater pressure drop. Therefore, the required number of bridge structures 32 is determined based on overall needs. The width W of the bridge structure 32... s The length of the heat exchange reinforcement zone and the number of bridges are determined by the length L of the bridge structure 32. s Analysis shows that the longer the bridge structure 32 is, the better the heat transfer performance, but the greater the pressure drop. Therefore, it is necessary to combine the surface temperature distribution of the fins and reasonably change the length of the bridge structure 32 so that the bridging length can just break the temperature boundary.

[0114] like Figures 18 to 21 As shown, in some embodiments of this utility model, the heat exchange enhancement structure 30 is a louvered structure 33. This allows the two sides of the first fin 11 and the second fin 21 to communicate through the opening of the louvered structure 33, so that air from one side can pass through the first fin 11 and the second fin 21, carrying away the heat from the first fin 11 and the second fin 21, thereby improving the heat exchange efficiency of the first fin 11 and the second fin 21.

[0115] In some embodiments of this utility model, the louvered structure 33 includes a plurality of air guides 331 arranged along a third direction, each air guide being provided with an air guide vane 332, and the number of air guides 331 is N1, wherein 2≤N l ≤15;

[0116] And / or, the angle between the air guide vane 332 and the third direction is α, 20°≤α≤35°;

[0117] And / or, the louvered structure 33 includes a plurality of air vents 331 arranged along a third direction, each air vent 331 having an air guide slab 332, the plurality of air guide slabs 332 being arranged in parallel, and the spacing between two adjacent air guide slabs 332 along the third direction being p. f The length of the air guide vane 332 along the air guide direction of the air guide 331 is w, and sinα≤p f / w≤3sinα;

[0118] And / or, along the first direction, the length of the installation space is t w The distance between two adjacent installation spaces is p t The length of the air guide vane 332 along the third direction is l, and the third direction is perpendicular to the first and second directions, 0.5≤l / (p t -t w ) < 1.

[0119] As can be seen from the analysis of the opening angle α of the air guide 33120, the larger the opening angle α, the better the heat exchange performance. However, when the opening angle reaches the critical value α0, further increasing the angle has little effect on improving heat exchange performance, while the pressure drop increases rapidly, which is detrimental to heat exchange efficiency. Therefore, an opening angle of 20°≤α≤35° is the optimal choice. Furthermore, based on the analysis of the opening width w of the air guide 33120, the larger the opening width w, the better the heat exchange performance. However, according to the fin spacing p... f Considering that an excessively large window width w leads to increased pressure drop, which is detrimental to heat exchange efficiency, the fin spacing p is also considered. f Given the window opening angle w, choose sinα≤p f / w≤3sinα. In addition, according to the analysis of the window opening length l, l refers to l1 or l2. The longer the window opening length l, the better the heat exchange performance, but the greater the pressure drop, which is detrimental to the heat exchange efficiency. Therefore, it is necessary to combine the temperature distribution on the fin surface and reasonably change the window opening length so that the window opening length can just break the temperature boundary optimally.

[0120] In some embodiments of this utility model, along the first direction, the distance between two adjacent second fin units 20 is greater than or equal to the distance between two adjacent first fin units 10.

[0121] It can be seen that by making the first fin unit 10 arranged more densely on the windward side, the first fin unit 10 can take advantage of the uneven distribution of heat load on the air side. On the windward side with strong heat exchange capacity and high heat load, the first fin unit 10 is arranged more densely, while on the leeward side with weak heat exchange capacity and low heat load, the second fin unit 20 is arranged more sparsely. This makes the fin arrangement of the heat exchanger 100 match the air heat load, thereby improving the heat exchange efficiency of the heat exchanger 100.

[0122] For example, the spacing between the first fin unit 10 and the second fin unit 20 can be set to be between 1 mm and 3 mm, and the spacing of the first fin unit 10 is smaller.

[0123] In addition, in some heat exchangers 100 that are often used in low-temperature conditions, the second fin unit 20 can be arranged more densely and the first fin unit 10 can be arranged more sparsely, so that the first fin unit 10 on the windward side will be less frosted, thus affecting the heat exchange efficiency of the heat exchanger 100.

[0124] In some embodiments of this utility model, the length of the windward portion 111 along a third direction is e1, where 6mm≤e1≤12mm;

[0125] And / or, the length of the leeward portion 211 along the third direction is e2, 0.2≤e2 / e1≤1;

[0126] And / or, the length of the first fin 11 along the third direction is L1, the length of the second fin 21 along the third direction is L2, 0 < e1 / L1 ≤ 0.5, 0 < e2 / L2 ≤ 0.5.

[0127] It can be seen that by setting the length of the windward portion 111 along a third direction and the length relationship between the leeward portion 211 and the windward portion 111, the lengths of the windward portion 111 and the leeward portion 211 are matched with the heat load, and the strength and installation reliability of the first fin 11 and the second fin 21 are guaranteed. This makes the length of the windward portion 111 on the windward side of the high heat load greater than the length of the leeward portion 211 on the leeward side of the low heat load area, thereby increasing the contact area between the windward portion 111 and the air, improving the heat exchange efficiency of the windward portion 111, and increasing the size of the windward portion 111 with more condensate to improve the drainage capacity of the windward portion 111, thereby improving the heat exchange efficiency and drainage efficiency of the fin assembly.

[0128] In addition, under special working conditions with low ambient temperature, the windward part 111 and the leeward part 211 can be designed in reverse, that is, the size constraints of the windward part 111 and the leeward part 211 can be interchanged.

[0129] In some embodiments of this utility model, the minimum distance between the heat exchange enhancement structure 30 and the end of the windward portion 111 that is away from the first connecting portion 112 is l1, 0.2≤l1 / L1≤0.5, and the maximum distance between the heat exchange enhancement structure 30 and the end of the windward portion 111 that is away from the first connecting portion 112 is l2, 0.5≤l2 / L1≤1.0.

[0130] And / or, the minimum distance from the end of the heat exchange enhancement structure 30 to the leeward part 211 away from the second connecting part 212 is l3, 0.2≤l3 / L2≤0.5, and the maximum distance from the end of the heat exchange enhancement structure 30 to the end of the leeward part 211 away from the first connecting part 112 is l4, 0.5≤l4 / L2≤1.0.

[0131] As can be seen from the analysis of the position of the heat exchange enhancement structure 30, setting the heat exchange enhancement structure 30 at the above position results in high heat transfer coefficients and fin efficiency of the first fin 11 and the second fin 21, and has little impact on the pressure drop of the first fin 11 and the second fin 21.

[0132] In some embodiments of this utility model, the first fin unit 10 is provided with a water guiding structure. The water guiding structure is sequentially provided on a plurality of windward portions 111 arranged along the second direction in the same first fin unit 10, and is used to discharge the condensate on the windward portions 111 to the outside of the fin assembly.

[0133] It can be seen that grooves or ribbed water guiding structures can be provided on the first fin unit 10 and / or the second fin unit 20 to guide the condensate on the first fin unit 10 and / or the second fin unit 20, thereby improving the drainage capacity of the first fin unit 10 and / or the second fin unit 20 and thus improving the heat exchange efficiency of the first fin unit 10 and / or the second fin unit 20.

[0134] For example, a groove can be provided on the outer surface of the windward portion 111 of the first fin unit 10. The groove can extend generally along the second direction, in a straight or inclined direction, and pass sequentially through a plurality of windward portions 111 arranged along the second direction. Condensate on the first fin unit 10 can be collected and discharged through the groove, improving drainage efficiency. Ribs can also be welded or pressed onto the outer surface of the windward portion 111 of the first fin unit 10. The ribs can extend generally along the second direction, in a straight or inclined direction. Condensate on the first fin unit 10 can be discharged along the ribs, improving drainage efficiency.

[0135] like Figures 1 to 21 As shown, in some embodiments of this utility model, the first heat exchange tube 40 and the second heat exchange tube 41 of each heat exchange tube assembly are separately arranged.

[0136] Alternatively, the heat exchanger assembly may also include a connection structure, through which a portion of the sidewall of the first heat exchanger tube 40 of the same heat exchanger assembly is connected to a portion of the sidewall of the second heat exchanger tube 41.

[0137] As can be seen, a composite heat exchange tube assembly can be used, in which the first heat exchange tube 40 and the second heat exchange tube 41 are welded together or formed into one piece through a connecting structure, so that the relative positions of the first heat exchange tube 40 and the second heat exchange tube 41 can remain unchanged, which facilitates the assembly of the heat exchange tube assembly.

[0138] For example, the first heat exchange tube 40 and the second heat exchange tube 41 are arranged parallel and spaced apart in the second direction and connected by a connecting structure. The connecting structure can be a strip structure or a support structure, which is connected to the first heat exchange tube 40 and the second heat exchange tube 41 respectively by welding on both sides along the second direction, or is integrally formed.

[0139] like Figures 1 to 2 As shown, in some embodiments of this utility model, the heat exchanger 100 further includes:

[0140] The first manifold 42 is connected to one end of all the first heat exchange tubes 40 and one end of all the second heat exchange tubes 41.

[0141] The other ends of all the first heat exchange tubes 40 and all the second heat exchange tubes 41 are connected to the second manifold 43.

[0142] For example, the heat exchange tube assembly, the first finned unit 10, and the second finned unit 20 can be assembled in an asymmetrical single-row interlocking configuration. During heat exchange, the high-temperature refrigerant enters from the first manifold 42 and is distributed to multiple heat exchange tube assemblies. In the same heat exchange tube assembly, the first heat exchange tube 40, with a larger flow area, handles more refrigerant heat exchange, while the second heat exchange tube 41, with a smaller flow area, handles less refrigerant heat exchange. The first heat exchange tube 40 is located on the windward side, and the second heat exchange tube 41 is located on the leeward side. After the refrigerant is cooled by heat exchange with the air through the heat exchange tube assembly, it flows out of the heat exchanger 100 through the second manifold 43.

[0143] like Figures 3 to 4 As shown, in some embodiments of the present invention, the heat exchanger 100 further includes a third manifold 44 and a fourth manifold 45. In the same heat exchange tube assembly, one end of the first heat exchange tube 40 is connected to the third manifold 44, the other end of the first heat exchange tube 40 is connected to one end of the second heat exchange tube 41, and the other end of the second heat exchange tube 41 is connected to the second manifold 43.

[0144] For example, the heat exchange tube assembly, the first finned unit 10, and the second finned unit 20 can be assembled in an asymmetrical double-row plug-in type or a double-row side-plug-in type. During heat exchange, the high-temperature refrigerant enters from the first manifold 42 and is distributed to multiple first heat exchange tubes 40. After exchanging heat with the air through multiple first finned units 10 on the windward side, it flows to the second heat exchange tube 41 and continues to exchange heat through the second finned unit 20 on the leeward side. In the same heat exchange tube assembly, the first heat exchange tube 40 with a larger flow area on the windward side undertakes more heat exchange efficiency, while the second heat exchange tube 41 with a smaller flow area on the leeward side undertakes less heat exchange efficiency. Finally, the refrigerant is cooled down by exchanging heat with the air through the second heat exchange tube 41 and flows out of the heat exchanger 100 through the second manifold 43.

[0145] The second aspect of this utility model provides a heating, ventilation and air conditioning device, including the microchannel heat exchanger 100 proposed in the first aspect of this utility model.

[0146] As can be seen, the HVAC equipment proposed in the second aspect of this utility model has a heat exchanger 100 with strong drainage capacity, compact structure and high heat exchange efficiency. The heat exchanger 100 has a first heat exchange tube 40 installed in a first installation space 113 and a second heat exchange tube 41 installed in a second installation space 213. A windward part 111 is provided on one side of the first installation space 113 and a leeward part 211 is provided on one side of the second installation space 213. When the heat exchanger 100 is working, the condensate generated can be discharged through the windward part 111 and the leeward part 211, thereby improving the drainage performance of the heat exchanger 100. Furthermore, a first heat exchange tube 40 with a larger flow area is installed on the windward side where the heat load is higher and more condensate is generated, while a second heat exchange tube 41 with a smaller flow area is installed on the leeward side 211 where the heat load is lower and less condensate is generated. This allows the structural design of the fin assembly to be optimized by partitioning the temperature distribution and heat exchange characteristics of the air side. The first heat exchanger 100 with a larger flow rate is used for heat exchange on the windward side where the heat exchange capacity is strong, while the second heat exchange tube 41 with a smaller flow rate is used for heat exchange on the leeward side where the heat exchange capacity is weaker. This ensures that the distribution of the heat exchange tubes matches the temperature field and heat exchange characteristics, reducing fin redundancy and improving the overall efficiency and utilization rate of the fins.

[0147] The above are merely preferred embodiments of this utility model, but the scope of protection of this utility model is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this utility model should be included within the scope of protection of this utility model. Therefore, the scope of protection of this utility model should be determined by the scope of the claims.

Claims

1. A heat exchanger, characterized by, include: A plurality of first fin units are spaced apart along a first direction. Each first fin unit includes a plurality of first fins connected sequentially along a second direction. The positions of the plurality of first fins of adjacent first fin units along the first direction correspond to each other in the second direction. Each first fin includes a windward portion and a first connecting portion arranged along a third direction. The first direction, the second direction, and the third direction are perpendicular to each other. In the same first fin unit, a first installation space is formed between the two first connecting portions of two adjacent first fins. A plurality of second fin units are spaced apart along the first direction. Each second fin unit includes a plurality of second fins connected sequentially along the second direction. The positions of the plurality of second fins of adjacent second fin units along the first direction are corresponding in the second direction. Each second fin includes a second connecting portion and a leeward portion arranged along the third direction. In the same second fin unit, a second mounting space is formed between the two second connecting portions of two adjacent second fins. A plurality of heat exchange tube assemblies are spaced apart along the second direction. Each heat exchange tube assembly includes a first heat exchange tube and a second heat exchange tube. The flow area of ​​the first heat exchange tube is larger than that of the second heat exchange tube. The first heat exchange tube extends along the first direction and passes through a plurality of first installation spaces arranged along the first direction. The second heat exchange tube extends along the first direction and passes through a plurality of second installation spaces arranged along the first direction.

2. The heat exchanger of claim 1, wherein Along the second direction, the length of the windward portion is greater than the length of the leeward portion; And / or, along the second direction, the length of the first mounting space is greater than the length of the second mounting space.

3. The heat exchanger of claim 1, wherein The plurality of first fin units are located upstream of the plurality of second fin units in the airflow direction, and the windward portion, the first connecting portion, the second connecting portion and the leeward portion are arranged sequentially along the airflow direction; Alternatively, the plurality of first fin units are located upstream of the plurality of second fin units in the airflow direction, and the windward portion, the first connecting portion, the leeward portion and the second connecting portion are arranged sequentially along the airflow direction.

4. The heat exchanger of claim 1, wherein The first fin is a flat fin; And / or, the second fin is a flat fin.

5. The heat exchanger of claim 1, wherein At least one of the first connecting portion and the second connecting portion is provided with a heat exchange enhancement structure.

6. The heat exchanger of claim 5, wherein The heat exchange enhancement structure is a corrugated structure.

7. The heat exchanger of claim 6, wherein Both the first connecting part and the second connecting part are provided with heat exchange enhancement structures; a length of the corrugation structure along the third direction is W W , a length of the corrugation structure along the second direction is L e , and W w =L e ; And / or, the length of the corrugated structure along the first direction is h. w Along the first direction, the distance between two adjacent first fins is p. f1 The spacing between two adjacent second fins is p f2 Where 0.3≤h w / p f1 ≤0.8, 0.3≤h w / p f2 ≤0.8; And / or, along the third direction, the length of the first installation space is t. w1 And the length of the second installation space is t w2 Along the second direction, the distance between two adjacent first installation spaces is p. t1 And the distance between two adjacent second installation spaces is p t2 The length of the corrugated structure along the second direction is L. w , where 0.5≤L w / (p t1 -t w1 )<1, 0.5≤L w / (p t2 -t w2 )<1.

8. The heat exchanger of claim 5, wherein The heat exchange enhancement structure is a bridge-type structure.

9. The heat exchanger of claim 8, wherein, Both the first connecting part and the second connecting part are provided with heat exchange enhancement structures; Along the first direction, the length of the bridge structure is h. s Along the first direction, the distance between two adjacent first fins is p. f1 The spacing between two adjacent second fins is p f2 Where 0.3≤h s / p f1 ≤0.8, 0.3≤h s / p f2 ≤0.8; and / or the number N of the bridge type structures s , 2 ≤ N s ≤ 15; And / or, the number of the bridge structures is multiple, the multiple bridge structures are arranged along the third direction, and the length of each bridge structure along the third direction is equal; And / or, the sum of the lengths of all the bridge structures along the second direction is L. s Along the third direction, the length of the first installation space is t. w1 And the length of the second installation space is t w2 Along the second direction, the distance between two adjacent first installation spaces is p. t1 And the distance between two adjacent second installation spaces is p t2 , where 0.5≤L s / (p t1 -t w1 )<1, 0.5≤L s / (p t2 -t w2 )<1.

10. The heat exchanger of claim 5, wherein, The heat exchange enhancement structure is a louvered structure.

11. The heat exchanger of claim 10, wherein Both the first connecting part and the second connecting part are provided with heat exchange enhancement structures; The louver type structure comprises a plurality of air guide openings arranged along the third direction, each of the air guide openings is provided with an air guide sheet, and the number of the air guide openings is N1, wherein 2≤N l ≤15. And / or, the louvered structure includes a plurality of air vents arranged along the third direction, each air vent having an air guide vane, the plurality of air guide vanes being arranged in parallel, and the spacing between two adjacent air guide vanes along the third direction being p. f The length of the air guide vane along the air guide direction of the air guide opening is w, and sinα≤p f / w≤3sinα, where α is the angle between the air guide vane and the third direction, and 20°≤α≤35°; And / or, along the second direction, the length of the first installation space is t w1 The distance between two adjacent first installation spaces is p t1 The length of the second installation space is t w2 The distance between two adjacent second installation spaces is p t2 The length of the air guide vane along the second direction is l d , 0.5≤l d / (p t1 -t w1 ) < 1, and 0.5 ≤ l d / (p t2 -t w2 ) < 1.

12. The heat exchanger of claim 5, wherein, Along the third direction, the minimum distance from the heat exchange enhancement structure to the end of the windward portion away from the first connecting portion is l1, the length of the first fin is L1, 0.2≤l1 / L1≤0.5, and the maximum distance from the heat exchange enhancement structure to the end of the windward portion away from the first connecting portion is l2, 0.5≤l2 / L1≤1.

0. And / or, along the third direction, the minimum distance from the heat exchange enhancement structure to the end of the leeward portion away from the second connecting portion is l3, the length of the second fin is L2, 0.2≤l3 / L2≤0.5, and the maximum distance from the heat exchange enhancement structure to the end of the leeward portion away from the first connecting portion is l4, 0.5≤l4 / L2≤1.

0.

13. The heat exchanger according to any one of claims 1 to 12, characterized in that Along the first direction, the spacing between two adjacent second fin units is greater than or equal to the spacing between two adjacent first fin units.

14. The heat exchanger according to any one of claims 1 to 12, characterized in that The length of the windward portion along the third direction is e1, 6mm≤e1≤12mm; the length of the leeward portion along the third direction is e2, 0.2≤e2 / e1≤1; the length of the first fin along the third direction is L1; the length of the second fin along the third direction is L2, 0<e1 / L1≤0.5, 0<e2 / L2≤0.

5.

15. The heat exchanger according to any one of claims 1 to 12, characterized in that The first fin unit is provided with a water guiding structure, which is sequentially provided on a plurality of the windward portions arranged along the second direction in the same first fin unit, and is used to discharge the condensate on the windward portions to the outside of the first fin unit.

16. The heat exchanger according to any one of claims 1 to 12, characterized in that The first heat exchange tube and the second heat exchange tube of each heat exchange tube assembly are separately provided; Alternatively, the heat exchange tube assembly may further include a connecting structure, through which a portion of the sidewall of the first heat exchange tube of the same heat exchange tube assembly is connected to a portion of the sidewall of the second heat exchange tube.

17. The heat exchanger according to any one of claims 1 to 12, characterized in that, The heat exchanger also includes: The first manifold is connected to one end of all the first heat exchange tubes and one end of all the second heat exchange tubes. The second manifold is connected to the other ends of all the first heat exchange tubes and all the other ends of the second heat exchange tubes.

18. The heat exchanger according to any one of claims 1 to 12, characterized in that The heat exchanger also includes a third manifold and a fourth manifold. In the same heat exchange tube assembly, one end of the first heat exchange tube is connected to the third manifold, the other end of the first heat exchange tube is connected to one end of the second heat exchange tube, and the other end of the second heat exchange tube is connected to the fourth manifold.

19. A heating and ventilation device, characterized in that Includes the heat exchanger according to any one of claims 1 to 18.

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