Heat exchange device and air conditioning device

Abstract

The utility model provides a heat exchange device and an air conditioning device.The heat exchange device comprises a heat exchange piece and a refrigerant pipe, the heat exchange piece comprises a first flat part, a second flat part and a first interval part, the first flat part is provided with a plurality of through holes spaced in the first direction, and the refrigerant pipe penetrates through the through holes; the first flat part and the second flat part are respectively connected to two opposite sides of the first spacing part along the second direction, and the second flat part and the first flat part continuously extend along the first direction; the first interval part extends in a continuous wavy shape in the first direction; the second direction intersects with the axial direction of the through hole and the first direction. In this way, the defrosting efficiency of the heat exchange device can be effectively improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of heat exchange devices, in particular to a heat exchange device and an air conditioning device. BACKGROUND

[0002] During operation, the indoor heat exchange device of an air conditioning device or the like has high-temperature refrigerant inside, which releases heat to the indoor environment. Meanwhile, the outdoor heat exchange device has low-temperature refrigerant inside, which absorbs heat from the outdoor environment. When the outdoor air is low in temperature and high in humidity, water vapor in the air is prone to condensing on the heat exchange fins of the heat exchange device to form condensed water. If the temperature of the heat exchange fins is lower than the freezing point of water, the condensed water will further freeze into frost or ice. Therefore, when the air conditioning device is in heating operation, frost will form on the outdoor heat exchange fins, which makes it difficult for air to flow over the main surfaces of the heat exchange fins, resulting in poor heat exchange. Therefore, it is necessary to perform defrosting on the heat exchange fins of the outdoor heat exchange device. The existing defrosting technology mainly uses reverse circulation of a heat pump system to achieve the purpose of defrosting.

[0003] The length of the defrosting process of the heat exchange device is of great reference significance for evaluating the performance and comfort of the heat pump system. How to accelerate the drainage of frost or condensed water (water molecule aggregates) and shorten the entire drainage process to improve the defrosting efficiency of the heat exchange device is a technical problem that needs to be solved urgently. CONTENT OF THE INVENTION

[0004] To solve the above technical problems, the technical scheme adopted by the present application is as follows: The present application provides a heat exchange device, which comprises heat exchange fins and a refrigerant pipe. The heat exchange fins comprise a first flat portion, a second flat portion, and a first spacing portion. The first flat portion is provided with a plurality of through holes spaced apart along a first direction, and the refrigerant pipe is arranged in the through holes. The first flat portion and the second flat portion are respectively connected to opposite sides of the first spacing portion along a second direction, and the second flat portion and the first flat portion continuously extend along the first direction. The first spacing portion extends in a continuous wave shape along the first direction. The second direction intersects the axial direction of the through holes and the first direction.

[0005] The heat exchange device provided by the present application has the following beneficial effects: The heat exchange device comprises heat exchange fins, which comprise a first flat portion, a second flat portion, and a first spacing portion. The first flat portion and the second flat portion are respectively connected to opposite sides of the first spacing portion. In this way, the main surface of the heat exchange fins is divided into three smaller surface regions. This can effectively reduce the unit area of the water film, so that the water film is more easily dried, thereby effectively improving the defrosting efficiency of the heat exchange device. BRIEF DESCRIPTION OF DRAWINGS

[0006] Figure 1 is a three-dimensional structure schematic view of the first embodiment of the heat exchange fins of the present application;

[0007] Figure 2 is a three-dimensional structural schematic view of a second embodiment of the heat exchange sheet of the present application;

[0008] Figure 3 is a three-dimensional structural schematic view of a third embodiment of the heat exchange sheet of the present application;

[0009] Figure 4 is a three-dimensional structural schematic view of a fourth embodiment of the heat exchange sheet of the present application; Figure 1 is a front structural schematic view of the heat exchange sheet shown in FIG. 1 along a first side thereof in an axial direction x3;

[0010] Figure 5 is a front structural schematic view of the heat exchange sheet shown in FIG. 2 along a first side thereof in an axial direction x3; Figure 2

[0011] Figure 6 is a front structural schematic view of the heat exchange sheet shown in FIG. 3 along a first side thereof in an axial direction x3; Figure 3

[0012] Figure 7 is a side structural schematic view of the heat exchange sheet shown in FIG. 4 as viewed along a first direction x1; Figure 1

[0013] Figure 8 is a side structural schematic view of the heat exchange sheet shown in FIG. 5 as viewed along a first direction x1; Figure 2

[0014] Figure 9 is a side structural schematic view of the heat exchange sheet shown in FIG. 6 as viewed along a first direction x1; Figure 3

[0015] Figure 10 is a partial cross-sectional schematic view of the heat exchange sheet shown in FIG. 7 with a reference plane P2 as a cross section; Figure 4

[0016] Figure 11 is a partial cross-sectional schematic view of the heat exchange sheet shown in FIG. 8 with a reference plane P2 as a cross section; Figure 5

[0017] Figure 12 is a partial cross-sectional schematic view of the heat exchange sheet shown in FIG. 9 with a reference plane P2 as a cross section; Figure 6

[0018] Figure 13 is another partial cross-sectional schematic view of the heat exchange sheet shown in FIG. 10 with a reference plane P2 as a cross section; Figure 6

[0019] Figure 14 is a partial front structural schematic view of the heat exchange sheet shown in FIG. 11 along a first side thereof in an axial direction x3; Figure 2

[0020] Figure 15 is a partial front structural schematic view of the heat exchange sheet shown in FIG. 12 along a first side thereof in an axial direction x3;​​​​​​​​​​Figure 3 Partial side view structure schematic diagram of the heat exchange sheet shown in the second direction x2;

[0021] Figure 16a is Figure 2 Schematic diagram of the flow guiding effect of the main surface of the first side LB1 of the heat exchange sheet shown in the second flat part along the minimum value of the third dimension in the second direction is greater than 3mm;

[0022] Figure 16b is Figure 2 Schematic diagram of the flow guiding effect of the main surface of the second side LB2 of the heat exchange sheet shown in the second flat part along the minimum value of the third dimension in the second direction is greater than 3mm;

[0023] Figure 16c is Figure 2 Schematic diagram of the flow guiding effect of the main surface of the first side LB1 of the heat exchange sheet shown in the second flat part along the minimum value of the third dimension in the second direction is 1.5mm;

[0024] Figure 16d is Figure 2 Schematic diagram of the flow guiding effect of the main surface of the second side LB2 of the heat exchange sheet shown in the second flat part along the minimum value of the third dimension in the second direction is 1.5mm;

[0025] Figure 17a is the test result schematic diagram of the flow guiding effect of the main surface of the first side LB1 and the second side LB2 of the heat exchange sheet of the conventional flat sheet structure;

[0026] Figure 17b is Figure 2 Schematic diagram of the test result of the flow guiding effect of the main surface of the first side LB1 and the second side LB2 of the heat exchange sheet shown in the second flat part along the minimum value of the third dimension in the second direction is 2.5mm;

[0027] Figure 17c is Figure 2 Schematic diagram of the test result of the flow guiding effect of the main surface of the first side LB1 and the second side LB2 of the heat exchange sheet shown in the second flat part along the minimum value of the third dimension in the second direction is 1.5mm;

[0028] Figure 18 is the effect schematic diagram of the contact angle of the water molecule collection on the main surface of the heat exchange sheet of any embodiment of the present application;

[0029] Figure 19 is the defrosting experiment process schematic diagram of the heat exchange device when the main surface material of the heat exchange sheet of the present application is a hydrophilic material;

[0030] Figure 20 is the main surface material of the heat exchange fin of the present application is a hydrophobic material, the defrosting experiment process of the heat exchange device is shown. DETAILED DESCRIPTION

[0031] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative labor fall within the scope of protection of the present application.

[0032] The terms "first", "second" in the present application are only for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. In the description of the present application, the meaning of "multiple" is at least two, for example, two, three, etc., unless otherwise explicitly specified. In addition, the terms "include" and "have" and any variations thereof are intended to cover exclusive inclusion. For example, a process, method, system, product or device including a series of steps or units is not limited to the listed steps or units, but can optionally include steps or units not listed, or can optionally include other steps or units inherent to the process, method, product or device.

[0033] As shown in Figure 1 , Figure 2 and Figure 3 , the present application provides a heat exchange device, which is applied to a heat exchange device of an air conditioning device, such as an air conditioner, etc. The heat exchange device comprises a gas conveying mechanism, a heat exchange fin 1 and a plurality of refrigerant pipes. The heat exchange fin 1 is provided with a plurality of through holes 40, and each refrigerant pipe is arranged in a corresponding through hole 40. The refrigerant pipe is used to flow the refrigerant fluid, and the refrigerant pipe can directly contact with the heat exchange gas in the environment, so as to realize heat exchange with the heat exchange gas in the environment. Moreover, the refrigerant pipe is arranged in the through hole 40 to contact with the heat exchange fin 1. Based on this, the refrigerant pipe cooperates with the heat exchange fin 1, and the heat exchange fin 1 can increase the contact area of the refrigerant pipe and the heat exchange gas in the environment, so as to realize the effect of improving the heat exchange efficiency of the heat exchange device. Specifically, the refrigerant pipe cooperates with the heat exchange fin 1 to contact with the heat exchange fin 1, so as to exchange heat with the heat exchange fin 1, and then indirectly exchange heat with the heat exchange gas in the environment through the main surfaces of the heat exchange fin 1 on both sides of the axial direction x3. The gas conveying mechanism is a mechanism for outputting or driving the heat exchange gas in the environment to flow towards the heat exchange fin 1 and the refrigerant pipe, so as to achieve the effect of accelerating the heat exchange efficiency of the heat exchange fin 1 and the refrigerant pipe with the heat exchange gas, thereby improving the heat exchange efficiency of the heat exchange device.

[0034] As shown in Figure 1 , Figure 2 andFigure 3 In some embodiments, the through holes 40 are arranged in the heat exchange sheet 1 along a first direction x1, and the gas delivery mechanism is configured to output the heat exchange gas to the heat exchange sheet 1 and the refrigerant pipe along a second direction x2 perpendicular to the axial direction x3 of the through holes 40 and the first direction x1, or the gas delivery mechanism is configured to drive the heat exchange gas in the environment to flow to the heat exchange sheet 1 and the refrigerant pipe along the second direction x2. It should be noted that the first direction x1, the second direction x2 and the axial direction x3 are all reference directions defined by the structure of the heat exchange sheet 1, the axial direction x3 is a direction parallel to the axis z1 of the through hole 40, the first direction x1 is the spacing direction of the plurality of through holes 40 on the heat exchange sheet 1, and the second direction x2 is a direction intersecting the first direction x1 and the axial direction x3, respectively. In some embodiments, the second direction x2 can be perpendicular to the first direction x1 and the axial direction x3, respectively.

[0035] In some embodiments, the heat exchange device includes a plurality of heat exchange sheets 1, wherein the heat exchange sheets 1 are arranged side by side and spaced apart along the axial direction x3 of the through holes 40, and the refrigerant pipe is sequentially arranged in the plurality of through holes 40 along the axial direction x3, so as to improve the heat dissipation efficiency of the refrigerant pipe.

[0036] When the temperature of the refrigerant in the refrigerant pipe is higher than the temperature of the external environment, the heat in the refrigerant is transferred to the heat exchange sheet 1 through the refrigerant pipe, and then transferred to the external environment through the main surface of the heat exchange sheet 1 (the two main surfaces on both sides of the heat exchange sheet 1 along the axial direction x3), so as to realize the external exchange between the refrigerant and the external environment. When the temperature of the refrigerant in the refrigerant pipe is lower than the temperature of the external environment, the heat in the external environment is transferred to the refrigerant pipe through the heat exchange sheet 1 and then to the refrigerant, so as to realize the heat exchange between the refrigerant and the external environment. The heat exchange sheet 1 mainly exchanges heat through the main surface, so in the defrosting process, the water molecule assembly 80 (such as Figure 16a 、 Figure 16b 、 Figure 16c 、 Figure 16d 、 Figure 17a 、 Figure 17b and Figure 17c The drainage efficiency of the main surface of the heat exchange sheet 1 directly affects the defrosting efficiency of the heat exchange sheet 1.

[0037] As shown in Figure 1 、 Figure 2 、 Figure 3 、 Figure 4 、 Figure 5 and Figure 6As shown, in some embodiments, the heat exchange fin 1 includes a first flat portion 10, an intermediate connecting portion 30, and a second flat portion 20. The second flat portion 20 is disposed on at least one side of the first flat portion 10 along a second direction x2 perpendicular to the axial direction x3 of the through hole 40 and the first direction x1. The first flat portion 10 and the second flat portion 20 are spaced apart along the second direction x2, and the intermediate connecting portion 30 connects between the second flat portion 20 and the first flat portion 10. In this way, the main surface of the heat exchange fin 1 is divided along the second direction x2 into multiple portions located in different spatial planes, namely the main surface of the first flat portion 10, the main surface of the intermediate connecting portion 30, and the main surface of the second flat portion 20.

[0038] like Figure 1 、 Figure 2 、 Figure 3 、 Figure 4 、 Figure 5 and Figure 6 As shown, the first flat portion 10 is provided with a cylindrical portion 50 arranged along the hole edge of the through hole 40, and the cylindrical portion 50 is protruded toward one side of the first flat portion 10 along the axial direction x3. Specifically, as shown in FIG. Figure 7 、 Figure 8 as well as Figure 9 As shown, the cylindrical portion 50 is protruded toward the first side LB1 of the heat exchange plate 1 along the axial direction x3 relative to the first flat portion 10, wherein the cylindrical portion serves as an extension structure of the through hole 40, which can increase the contact area between the refrigerant tube and the heat exchange plate 1, thereby improving the heat exchange efficiency between the refrigerant tube and the heat exchange plate 1.

[0039] Of course, in some embodiments, the second flat portion 20 and the corresponding intermediate connecting portion 30 may also be provided on both sides of the first flat portion 10 along the second direction x2.

[0040] It should be noted that the heat exchange fin 1 includes a first side LB1 and a second side LB2, which are disposed opposite each other along the axial direction x3. The first side LB1 of the heat exchange fin 1 is defined as the side of the cylindrical portion 50 that protrudes relative to the first flat portion 10 along the axial direction x3, and the second side LB2 of the heat exchange fin 1 is defined as the side opposite the first side LB1 along the axial direction x3. In some embodiments, the main surface of the first side LB1 of the heat exchange fin 1 is referred to as the front surface of the heat exchange fin 1, and the main surface of the second side LB2 of the heat exchange fin 1 is referred to as the back surface of the heat exchange fin 1.

[0041] In the embodiments of the present application, the first flat portion 10, the second flat portion 20 and the intermediate connecting portion 30 all extend along the first direction x1, which can be arranged to be inclined to the horizontal plane, specifically, the first direction x1 can be arranged to be perpendicular to the horizontal plane, that is, the first direction x1 is arranged to be parallel to the direction of gravity, and the second direction x2 is parallel to the horizontal plane, so that the water molecule clusters 80 on the heat exchange fin 1 can be guided along the first flat portion 10, the second flat portion 20 and the intermediate connecting portion 30 under the action of gravity, and flow out of the main surface of the heat exchange fin 1, thereby effectively improving the water drainage efficiency of the heat exchange fin 1, and further effectively improving the defrosting efficiency of the heat exchange device. Moreover, in some embodiments, the heat exchange gas flows along the second direction x2 towards the heat exchange fin 1 and the refrigerant pipe, so that the heat exchange efficiency of the heat exchange fin 1 can be effectively improved, and the flow direction of the heat exchange gas is also perpendicular to the direction of gravity. In the defrosting process of the heat exchange device, if the heat exchange gas is needed to assist defrosting, the above arrangement can also reduce the flow resistance of the heat exchange gas to the water molecule clusters 80 flowing along the first direction x1, thereby increasing the defrosting efficiency of the heat exchange device.

[0042] In the defrosting process, the water molecule clusters 80 condensed on the main surface of the heat exchange fin 1 are divided into three parts located on the main surface of the first flat portion 10, the main surface of the intermediate connecting portion 30 and the main surface of the second flat portion 20, respectively. On the one hand, the main surface of the first flat portion 10, the main surface of the intermediate connecting portion 30 and the main surface of the second flat portion 20 have a flow guiding effect, and the three parts of water molecule clusters 80 can flow regularly along the first direction x1 on the main surface of the first flat portion 10, the main surface of the intermediate connecting portion 30 and the main surface of the second flat portion 20, respectively, and flow out of the main surface of the heat exchange fin 1, thereby effectively improving the water drainage efficiency of the heat exchange fin 1, and further effectively improving the defrosting efficiency of the heat exchange device.

[0043] In another aspect, the main surface of the heat exchange sheet 1 is divided into three smaller surface regions located in different spatial planes, which can increase the number of regions with larger local capillary forces on the main surface of the heat exchange sheet 1, so that the main surface of the heat exchange sheet 1 can have a local gathering effect on the water molecule assembly 80 attached to the main surface of the heat exchange sheet 1 through the action of capillary force. In some embodiments, the first direction x1 can be arranged parallel to the direction of gravity, so that the local gathering effect of the main surface of the heat exchange sheet 1 on the water molecule assembly 80 can effectively increase the gravity of the water molecule assembly 80, thereby accelerating the flow of the water molecule assembly 80 along the first direction x1, thereby effectively improving the defrosting efficiency of the heat exchange device. Specifically, during the defrosting process, the water molecule assembly 80 is usually in the form of a water film attached to the main surface of the heat exchange sheet 1, and the main surface of the heat exchange sheet 1 is divided into three smaller surface regions located in different spatial planes, which increases the local curvature of the main surface of the heat exchange sheet 1, thereby increasing the number of regions with larger local capillary forces on the main surface of the heat exchange sheet 1, such as the region where the main surface of the first flat portion 10 and the main surface of the intermediate connecting portion 30 are connected, and the region where the main surface of the intermediate connecting portion 30 and the main surface of the second flat portion 20 are connected. Under the action of capillary force, the water molecule assembly 80 attached to the main surface of the heat exchange sheet 1 in the form of a water film will be torn and gathered into water droplets with larger gravity in the regions with larger capillary forces, thereby accelerating the shedding and effectively improving the defrosting efficiency of the heat exchange device. Moreover, after most of the water molecule assembly 80 is gathered into water droplets or water flow under the action of capillary force in the above-mentioned manner and separates from the surface of the heat exchange sheet 1 in the form of water droplets or water flow, a small part of the water molecule assembly 80 will continue to be attached to the main surface of the heat exchange sheet 1 in the form of a very thin water film due to the action of inertial force, viscous force and tension force of the main surface of the heat exchange sheet 1 on the water molecule assembly 80. Due to the action of capillary force, the water molecule assembly 80 attached to the main surface of the heat exchange sheet 1 in the form of a water film will be torn and gathered into water droplets or water flow with a smaller contact area with the main surface of the heat exchange sheet 1, which can effectively reduce the area and weight of the water film remaining on the main surface of the heat exchange sheet 1 due to the action of inertial force, viscous force and tension force, thereby effectively reducing the defrosting energy required during the defrosting process. Under the same defrosting energy, the heat exchange sheet 1 of the present application can effectively improve the defrosting efficiency of the heat exchange device compared with the existing heat exchange sheet.

[0044] It should be noted that in the embodiments of the present application, the first flat portion 10 and the second flat portion 20 are both flat sheet structures, specifically, the surface of the flat sheet structure includes a main surface with a proportion greater than or equal to 80% or more.

[0045] As Figure 4 , Figure 5 and Figure 6As shown, in some embodiments, the second flat portion 20 extends continuously along the first direction x1. Specifically, along the entire length of the heat exchange fin 1 along the first direction x1, the second flat portion 20 is a continuous flat sheet structure. That is, the second flat portion 20 is a flat sheet structure that extends continuously along the first direction x1. No interrupting structures, such as grooves, channels, or protrusions, are provided along the length of the heat exchange fin 1 along the first direction x1, dividing the second flat portion 20 into two or more discontinuous sections along the first direction x1. This ensures that the main surface of the second flat portion 20 extends continuously along the first direction x1, effectively improving the drainage efficiency of the second flat portion 20 along the first direction x1.

[0046] like Figure 4 and Figure 6 As shown, in some embodiments, the first flat portion 10 extends continuously along the first direction x1. Specifically, the first flat portion 10 is a continuous flat sheet structure throughout the entire length of the heat exchange fin 1 along the first direction x1. That is, the first flat portion 10 is a flat sheet structure that extends continuously along the first direction x1. No interrupting structures, such as grooves, channels, or protrusions, are provided along the heat exchange fin 1 along the first direction x1, dividing the first flat portion 10 into two or more discontinuous sections. This effectively improves the drainage efficiency of the first flat portion 10 along the first direction x1.

[0047] like Figure 4 and Figure 6 As shown, in some embodiments, the intermediate connecting portion 30 extends continuously along the first direction x1 and extends in a continuous, wavy pattern along the first direction x1. Specifically, the intermediate connecting portion 30 is a continuous structure throughout the entire length of the heat exchange fin 1 along the first direction x1. In other words, the intermediate connecting portion 30 extends continuously along the first direction x1. No interrupting structures, such as grooves, channels, or protrusions, are provided along the length of the heat exchange fin 1 along the first direction x1 to divide the intermediate connecting portion 30 into two or more discontinuous sections along the first direction x1. Furthermore, while the intermediate connecting portion 30 extends continuously along the first direction x1, it also extends in a periodic pattern along the second direction x2, first gradually approaching the reference plane P1 and then gradually moving away from the reference plane P1, or first gradually moving away from the reference plane P1 and then gradually approaching the reference plane P1. This wavy pattern effectively improves the drainage efficiency of the intermediate connecting portion 30.

[0048] It should be noted that the reference plane P1 is a plane passing through the axis z1 of the through hole 40 and parallel to the first direction x1.

[0049] like Figure 4 、 Figure 5and Figure 6 As shown in FIG. 1, in at least one reference plane perpendicular to the first direction x1, such as the reference plane P2 or a reference plane parallel to the reference plane P2, at least one of the first dimension L2 of the first flat portion 10 along the second direction x2 and the third dimension L1 of the second flat portion 20 along the second direction x2 is greater than the second dimension of the intermediate connecting portion 30 along the second direction x2, in other words, at least one of the first dimension L2 of the first flat portion 10 along the second direction x2 and the third dimension L1 of the second flat portion 20 along the second direction x2 is greater than the second dimension of the intermediate connecting portion 30 along the second direction x2 in at least a partial section along the first direction x1.

[0050] As shown in FIG. 1, the first flat portion 10 includes a first edge 101, the intermediate connecting portion 30 includes a first guide portion 301 connected to the first edge 101, and the first guide portion 301 is obliquely arranged relative to the first flat portion 10. In orthographic projection onto a projection plane perpendicular to the axial direction x3, the projection of the first guide portion 301 is spaced apart from the projection of the first flat portion 10 along the second direction x2. It can be understood that, in the direction from the first flat portion 10 to the intermediate connecting portion 30, the height difference between the first guide portion 301 and the first flat portion 10 along the axial direction x3 increases, or in the direction from the intermediate connecting portion 30 to the first flat portion 10, the height difference between the first guide portion 301 and the first flat portion 10 along the axial direction x3 decreases. Figure 4 Figure 5 Figure 6 Figure 7 Figure 8 Figure 9 As shown in FIG. 1, the second flat portion 20 includes a first edge 201, the intermediate connecting portion 30 includes a first guide portion 301 connected to the first edge 201, and the first guide portion 301 is obliquely arranged relative to the second flat portion 20. In orthographic projection onto a projection plane perpendicular to the axial direction x3, the projection of the first guide portion 301 is spaced apart from the projection of the second flat portion 20 along the second direction x2. It can be understood that, in the direction from the second flat portion 20 to the first flat portion 10, the height difference between the first guide portion 301 and the second flat portion 20 along the axial direction x3 increases, or in the direction from the first flat portion 10 to the second flat portion 20, the height difference between the first guide portion 301 and the second flat portion 20 along the axial direction x3 decreases.

[0051] More specifically, as shown in FIG. 1, the oblique arrangement of the first guide portion 301 relative to the second flat portion 20 can be understood as the first guide portion 301 being convexly arranged relative to the second flat portion 20 along the axial direction x3 of the through hole 40 towards the first side LB1, and the positional relationship between the first guide portion 301 and the second flat portion 20 is between perpendicular and parallel. Figure 10 Figure 11 Figure 12

[0052] The first guide portion 301 can play a role of assisting the flow of the water molecule assembly 80 on the major surface of the second flat portion 20, thereby accelerating the drainage efficiency of the second flat portion 20. More specifically, on the first side LB1, the major surface of the first guide portion 301 and the major surface of the second flat portion 20 form a channel-like structure extending along the first direction x1, thereby effectively improving the drainage efficiency of the second flat portion 20, and further effectively improving the drainage efficiency of the heat exchange fin 1.

[0053] ​​​​​​​​The included angle J1 between the first guide portion 301 and the second flat portion 20 is greater than or equal to 15° and less than or equal to 45°. The included angle between the first guide portion 301 and the second flat portion 20 directly affects the curvature of the channel-like structure. The greater the included angle J1 between the first guide portion 301 and the second flat portion 20, the greater the curvature of the channel-like structure, and the better the flow of the water molecule cluster 80 in the channel-like structure. However, the greater the included angle J1 between the first guide portion 301 and the second flat portion 20, the greater the resistance of the first guide portion 301 to the heat exchange gas blown along the second direction x2 to the heat exchange fin 1 and the refrigerant pipe, that is, the greater the included angle between the first guide portion 301 and the second guide portion 302, the greater the wind resistance of the heat exchange fin 1, which affects the heat exchange efficiency of the heat exchange device. Therefore, the included angle J1 between the first guide portion 301 and the second flat portion 20 is set to be between 15° and 45°, for example, 15°, 30°, 40°, or 45°, and the like. In this way, the included angle J1 between the first guide portion 301 and the second flat portion 20 is reasonable, the flow of the water molecule cluster 80 in the channel-like structure is better, the drainage efficiency of the second flat portion 20 is improved, and the wind resistance of the heat exchange fin 1 is effectively reduced, thereby ensuring the heat exchange efficiency of the heat exchange device.

[0054] In addition, the included angle J1 between the first guide portion 301 and the second flat portion 20 is greater than or equal to 15° and less than or equal to 45°, which effectively reduces the difficulty of forming the first guide portion 301, thereby effectively improving the processing convenience of the heat exchange fin 1.

[0055] It can be understood that in the cross section perpendicular to the tangent of the first edge 201, the main surface of the first guide portion 301 and the main surface of the second flat portion 20 are connected to each other in the first side LB1 or the second side LB2. The included angle J1 between the first guide portion 301 and the second flat portion 20 is the acute angle formed between the cross section lines of the main surface of the first guide portion 301 and the main surface of the second flat portion 20 in the first side LB1 or the second side LB2. The included angle formed between the cross section lines of the main surface of the first guide portion 301 and the main surface of the second flat portion 20 includes complementary acute angles and obtuse angles. In the embodiments of the present application, Figure 10 Figure 11 and Figure 12 The included angle J1 marked in the above-mentioned embodiments is the acute angle between the cross section lines of the main surface of the first guide portion 301 and the main surface of the second flat portion 20 in the second side LB2. It should be understood that in the embodiments of the present application, the heat exchange fin 1 is a plate structure with uniform thickness, and the included angles between the cross section lines of the main surface of the first guide portion 301 and the main surface of the second flat portion 20 in the first side LB1 and the second side LB2 are equal to each other.

[0056] ​It is to be noted that the first edge 201 has a plurality of tangent lines along its length direction, and the reference plane P2 is a reference plane perpendicular to one of the tangent lines of the first edge 201. In any embodiment herein, the positional relationship between the first guide portion 301 and the second flat portion 20 is exemplarily described by the included angle J1 between the first guide portion 301 and the second flat portion 20 in the reference plane P2.

[0057] As shown in Figure 10 , Figure 11 and Figure 13 , in some embodiments, the maximum value of the height difference H1 between the first guide portion 301 and the second flat portion 20 along the axial direction x3 is less than or equal to 0.7 mm. If the height difference H1 is too high, it will increase the air resistance of the heat exchange fin 1, and if the height difference H1 is too low, it will affect the flowability of the water molecule assembly 80 in the channel-like structure. Therefore, the maximum value of the height difference H1 is set to be less than or equal to 0.7 mm, which can make the height difference H1 more reasonable, make the flowability of the water molecule assembly 80 in the channel-like structure better, improve the drainage efficiency of the second flat portion 20, and effectively reduce the air resistance of the heat exchange fin 1, thereby ensuring the heat exchange efficiency of the heat exchange device. It is to be noted that, in some embodiments, the height difference H1 is the dimension of the first guide portion 301 along the axial direction x3.

[0058] As shown in Figure 10 and Figure 11 , in some embodiments, the first flat portion 10 and the second flat portion 20 are spaced apart along the axial direction x3, the first guide portion 301 is connected between the first flat portion 10 and the second flat portion 20, and the first guide portion 301 is also inclinedly arranged relative to the second flat portion 20. In other words, in the embodiments of the present application, the first flat portion 10 and the second flat portion 20 are connected through the first guide portion 301, and in the direction from the first flat portion 10 to the second flat portion 20, the height difference between the first guide portion 301 and the second flat portion 20 along the axial direction x3 gradually decreases. The spacing between the first flat portion 10 and the second flat portion 20 is the maximum value of the height difference H1 of the first guide portion 301. The inclined arrangement of the first guide portion 301 relative to the first flat portion 10 can be understood as that the first guide portion 301 is protrudingly arranged relative to the first flat portion 10 along the axial direction x3 of the through hole 40 towards the second side LB2, and the positional relationship between the first guide portion 301 and the first flat portion 10 is between perpendicular and parallel.

[0059] Thus, on one hand, the first guide part 301 plays an auxiliary guiding role for the first flat part 10 and the second flat part 20 respectively, thereby effectively improving the drainage efficiency of the first flat part 10 and the second flat part 20. More specifically, on the second side LB2, a channel-like structure extending along the first direction x1 is formed between the main surface of the first guide part 301 and the main surface of the first flat part 10, and on the first side LB1, a channel-like structure extending along the first direction x1 can also be formed between the main surface of the first guide part 301 and the main surface of the second flat part 20, thereby effectively improving the drainage efficiency of the first flat part 10 and the second flat part 20, and further effectively improving the drainage efficiency of the heat exchange sheet 1.

[0060] On the other hand, the main surface of the first flat part 10 and the main surface of the second flat part 20 are arranged in a gradient manner along the axial direction x3, and the first guide part 301 is connected between the first flat part 10 and the second flat part 20, so that the main surface of the first guide part 301 can serve as a guide slope between the main surface of the first flat part 10 and the main surface of the second flat part 20, thereby making the main surface of the heat exchange sheet 1 on the first side LB1 and the second side LB2 arranged in a stepped manner, and further making the water molecule assembly 80 on the main surface of the heat exchange sheet 1 on the first side LB1 and the second side LB2 have two flow modes, thereby effectively improving the drainage efficiency of the heat exchange sheet 1. More specifically, on the first side LB1, the water molecule assembly 80 flows along the first direction x1 on the main surface of the first guide part 301, the main surface of the first flat part 10 and the main surface of the second flat part 20 respectively, and a part of the water molecule assembly 80 on the main surface of the first flat part 10 can also be shunted along the main surface of the first guide part 301 to the main surface of the second flat part 20, thereby reducing the water storage amount on the main surface of the first flat part 10, while also enabling more water molecule assembly 80 to converge on the second flat part 20, and further enabling the flow speed of the water molecule assembly 80 on the second flat part 20 to be accelerated, so as to effectively improve the drainage efficiency of the heat exchange sheet 1. On the second side LB2, the water molecule assembly 80 flows along the first direction x1 on the main surface of the first guide part 301, the main surface of the first flat part 10 and the main surface of the second flat part 20 respectively, and a part of the water molecule assembly 80 on the main surface of the second flat part 20 can also be shunted along the main surface of the first guide part 301 to the main surface of the first flat part 10, thereby reducing the water storage amount on the main surface of the second flat part 20, while also enabling more water molecule assembly 80 to converge on the first flat part 10, and further enabling the flow speed of the water molecule assembly 80 on the first flat part 10 to be accelerated, so as to effectively improve the drainage efficiency of the heat exchange sheet 1.

[0061] As Figure 10 and Figure 11As shown, in some embodiments, the first flat portion 10 is arranged in parallel with the second flat portion 20, and thus the included angle J2 between the first flat portion 10 and the first guide portion 301 is equal to the included angle J1 between the second flat portion 20 and the first guide portion 301. It can be understood that, in the cross section perpendicular to the tangent of the third edge 101, there are cross section lines connected to each other between the main surface of the first guide portion 301 and the main surface of the first flat portion 10 at the first side LB1 or the second side LB2, and the included angle J2 between the first guide portion 301 and the first flat portion 10 is the acute angle formed between the cross section lines of the main surface of the first guide portion 301 and the main surface of the first flat portion 10 at the first side LB1 or the second side LB2, wherein the included angle formed between the cross section lines of the main surface of the first guide portion 301 and the main surface of the first flat portion 10 includes complementary acute angles and obtuse angles. In the embodiments of the present application, Figure 10 and Figure 11 The labeled included angle J1 is the acute angle between the cross section lines of the main surface of the first guide portion 301 and the main surface of the first flat portion 10 at the second side LB2. It should be understood that, in the embodiments of the present application, the heat exchange sheet 1 is a plate structure with uniform thickness, and the included angles between the cross section lines of the main surface of the first guide portion 301 and the main surface of the first flat portion 10 at the first side LB1 and the second side LB2 are equal to each other.

[0062] It should be noted that the third edge 101 has a plurality of tangents along its length direction, wherein the reference plane P2 is a reference plane perpendicular to one of the tangents of the third edge 101, and in any embodiment herein, the positional relationship between the first guide portion 301 and the first flat portion 10 is exemplarily described by the included angle J2 between the first guide portion 301 and the first flat portion 10 in the reference plane P2.

[0063] As Figure 5 and Figure 8As shown, in some embodiments, the heat exchange sheet 1 is a symmetric structure symmetrically arranged with respect to the reference plane P1, and the first flat portion 10 is located in the middle of the heat exchange sheet 1 along the second direction x2, the first flat portion 10, the second flat portion 20 and the first guide portion 301 are symmetrically arranged with respect to the reference plane P1, wherein the first flat portion 10 includes a plurality of sub-flat portions 102 arranged along the first direction x1, the first guide portion 301 includes a plurality of sub-guide portions 304 arranged along the first direction x1, and therefore the two parts of the second flat portion 20 located on both sides of the first flat portion 10 along the second direction x2 can be connected between adjacent two sub-flat portions 102, so that the two parts of the second flat portion 20 form a continuous second flat portion 20 as a whole. In the present embodiment, the first guide portion 301 includes a plurality of sub-guide portions 304 arranged along the first direction x1, each sub-guide portion 304 is arranged around the corresponding first flat portion 10, wherein the sub-guide portion 304 includes two parts symmetrically arranged with respect to the reference plane P1 along the second direction x2, and the two parts of the sub-guide portion 304 are connected between adjacent two sub-flat portions 102, so that the two parts of the sub-guide portion 304 form a continuous sub-guide portion 304. In this way, on the first side LB1, the sub-flat portions 102 and the sub-guide portions 304 are arranged protruding along the axial direction x3 with respect to the second flat portion 20, and the part of the water molecule clusters 80 on the sub-flat portions 102 can be guided to flow to the second flat portion 20 along the first direction x1 and the second direction x2 through the sub-guide portions 304, thereby effectively improving the drainage efficiency of the first flat portion 10 and the second flat portion 20. On the second side LB2, the sub-flat portions 102 and the sub-guide portions 304 are arranged recessed along the axial direction x3 with respect to the second flat portion 20, and the part of the water molecule clusters 80 on the second flat portion 20 can be guided to flow to the sub-flat portions 102 along the second direction x2 through the sub-guide portions 304, thereby effectively improving the drainage efficiency of the first flat portion 10. It should be noted that the spatial structural features between the sub-guide portions 304 and the second flat portion 20 and the first flat portion 10 are similar to the spatial structural features between the first guide portion 301 and the second flat portion 20 and the first flat portion 10 described above, which will not be described in detail here.

[0064] As Figure 5 and Figure 14As shown, in some embodiments, the sub-flat portion 102 is arranged in a circular ring, and the sub-guide portion 304 is connected with the second flat portion 20, so that the sub-guide portion 304 and the second flat portion 20 have a common connecting edge, which is also referred to as the first edge 201 in the above-mentioned embodiments. Correspondingly, the sub-flat portion 102 is connected with the first flat portion 10, so that the sub-guide portion 304 and the first flat portion 10 have another common connecting edge, which is also referred to as the third edge 101 in some embodiments, wherein the sub-flat portion 102 is arranged in a circular ring, so that the third edge 101 is arranged in a circular shape. The maximum size L3 (in some embodiments, the maximum size L3 is also referred to as the maximum distance of the first edge 201 in the first direction x1) of the graphic profile formed by the first edge 201 in the first direction x1 is greater than the maximum size L4 (in some embodiments, the maximum size L4 is also referred to as the maximum distance of the first edge 201 in the second direction x2) in the second direction x2. Specifically, the graphic profile formed by the first edge 201 is arranged in an elliptical shape, wherein the position of the maximum size L4 of the graphic profile in the second direction x2 is flush with the center of the through hole 40, that is, the position of the maximum size L4 of the graphic profile in the second direction x2 is located in the reference plane P2, wherein the reference plane P2 is perpendicular to the first direction x1 and passes through the axis z1 of the through hole 40. The position of the maximum size L3 of the graphic profile formed by the first edge 201 in the first direction x1 is located in the reference plane P1. Thus, on one side of the reference plane P1, the size of the sub-guide portion 304 in the second direction x2 is gradually changed from decreasing to increasing along the first direction x1. Based on this, the capillary force of the sub-guide portion 304 in the area with smaller size in the second direction x2 is greater than that in the area with larger size, and the area with smaller size of the sub-guide portion 304 can serve as a collection transition port of the water molecule assembly 80. The water molecule assembly 80 can be gathered on the area with smaller size of the sub-guide portion 304 by the action of capillary force, and flow to the area with larger size of the sub-guide portion 304 along the first direction x1, thereby increasing the gravity of the water molecule assembly 80, and further realizing the effect of accelerating the flow speed of the water molecule assembly 80, thereby effectively improving the guiding effect of the sub-guide portion 304 on the water molecule assembly 80.

[0065] As Figure 5 and Figure 14As shown in some embodiments, in the first direction x1, the first edge 201 is arranged in a sharp corner shape protruding away from the sub-flat portion 102, so that the end of the first edge 201 away from the sub-flat portion 102 has a smaller force, such as tension, viscous force, etc., on the water molecule cluster 80, so that the water molecule cluster 80 on the sub-guide portion 304 is more easily guided to the second flat portion 20. In some embodiments, the first guide portion 301 in this embodiment is also referred to as a first flow guide portion. The sub-guide portion 304 is also referred to as a sub-flow guide portion.

[0066] As shown in some embodiments, in the first direction x1, the first edge 201 is arranged in a sharp corner shape protruding away from the sub-flat portion 102, so that the end of the first edge 201 away from the sub-flat portion 102 has a smaller force, such as tension, viscous force, etc., on the water molecule cluster 80, so that the water molecule cluster 80 on the sub-guide portion 304 is more easily guided to the second flat portion 20. In some embodiments, the first guide portion 301 in this embodiment is also referred to as a first flow guide portion. The sub-guide portion 304 is also referred to as a sub-flow guide portion. Figure 4 Figure 7 As shown in some embodiments, the heat exchange sheet 1 is a symmetrical structure arranged symmetrically with respect to the reference plane P1, the first flat portion 10, the second flat portion 20, and the first guide portion 301 are all arranged symmetrically with respect to the reference plane P1, wherein the first flat portion 10 is a flat sheet structure continuously extending in the first direction x1, and the two parts of the second flat portion 20 are arranged on both sides of the first flat portion 10 in the second direction x2. Correspondingly, the first guide portion 301 is spaced on both sides of the first flat portion 10 in the second direction x2 by the first flat portion 10, and the two parts of the first guide portion 301 are arranged in the second direction x2. In some embodiments, the first guide portion 301 in this embodiment is also referred to as a first flow guide portion.

[0067] As shown in some embodiments, the heat exchange sheet 1 is a symmetrical structure arranged symmetrically with respect to the reference plane P1, the first flat portion 10, the second flat portion 20, and the first guide portion 301 are all arranged symmetrically with respect to the reference plane P1, wherein the first flat portion 10 is a flat sheet structure continuously extending in the first direction x1, and the two parts of the second flat portion 20 are arranged on both sides of the first flat portion 10 in the second direction x2. Correspondingly, the first guide portion 301 is spaced on both sides of the first flat portion 10 in the second direction x2 by the first flat portion 10, and the two parts of the first guide portion 301 are arranged in the second direction x2. In some embodiments, the first guide portion 301 in this embodiment is also referred to as a first flow guide portion. Figure 6 Figure 9 As shown in some embodiments, the intermediate connecting portion 30 further includes a second guide portion 302 connected between the side of the first guide portion 301 away from the second flat portion 20 and the first flat portion 10, and the second guide portion 302 is arranged obliquely with respect to the first flat portion 10. Figure 12 Specifically, in this embodiment, the intermediate connecting portion 30 includes the first guide portion 301 and the second guide portion 302 connected between the side of the first guide portion 301 away from the second flat portion 20 and the first flat portion 10, and the first guide portion 301 and the second guide portion 302 together form a first spacing portion 303 arranged protruding or recessed towards the same side of the first flat portion 10 and the second flat portion 20 in the axial direction x3.

[0068] Figure 4 The second guide portion 302 is arranged obliquely with respect to the first flat portion 10, which can be understood as the second guide portion 302 being arranged protruding towards the first side LB1 in the axial direction x3 of the through hole 40, and the positional relationship between the second guide portion 302 and the first flat portion 10 is between perpendicular and parallel. Figure 5

[0069]

[0070] ​​​​​The first guide portion 301 is connected with the second guide portion away from the first flat portion 10 at one end thereof to form a first spacing portion 303 on the first side LB1 of the heat exchange fin 1 along the axial direction x3 of the through hole 40, the first spacing portion 303 is arranged protruding along the axial direction x3 relative to the first flat portion 10 and the second flat portion 20, and the first spacing portion 303 is arranged tapering along the direction in which it protrudes, the water molecule assembly 80 on the main surface of the first spacing portion 303 can converge towards the first flat portion 10 and the second flat portion 20 respectively, so as to effectively improve the water drainage efficiency of the first flat portion 10 and the second flat portion 20. On the second side LB2, the first spacing portion 303 is arranged recessed along the axial direction x3 relative to the first flat portion 10 and the second flat portion 20, so that the first spacing portion 303 guides a part of the water molecule assembly 80 coming to the first flat portion 10 and the second flat portion 20, thereby achieving the effect of accelerating the water drainage efficiency.

[0071] The second guide portion 302 can play a role in assisting the water molecule assembly 80 on the main surface of the first flat portion 10 to flow, thereby accelerating the water drainage efficiency of the first flat portion 10. More specifically, on the first side LB1, a channel-like structure extending along the first direction x1 is formed between the main surface of the second guide portion 302 and the main surface of the first flat portion 10, thereby effectively improving the water drainage efficiency of the first flat portion 10, and further effectively improving the water drainage efficiency of the heat exchange fin 1.

[0072] The included angle J4 between the second guide portion 302 and the first flat portion 10 is greater than or equal to 15° and less than or equal to 45°. The included angle J4 between the second guide portion 302 and the first flat portion 10 directly affects the curvature of the channel-like structure, wherein the greater the included angle J4 between the second guide portion 302 and the first flat portion 10, the greater the curvature of the channel-like structure, and the better the flow of the water molecule assembly 80 in the channel-like structure, but at the same time, the greater the included angle J4 between the second guide portion 302 and the first flat portion 10, the greater the resistance of the second guide portion 302 to the heat exchange gas blown along the second direction x2 to the heat exchange fin 1 and the coolant pipe (i.e., the greater the included angle between the second guide portion 302 and the second guide portion 302, the greater the wind resistance of the heat exchange fin 1), affecting the heat exchange efficiency of the heat exchange device. Therefore, the included angle between the second guide portion 302 and the first flat portion 10 is set to be between 15° and 45°, for example, 15°, 30°, 40° or 45°, and the like. Thus, the included angle between the second guide portion 302 and the first flat portion 10 is reasonable, the flow of the water molecule assembly 80 in the channel-like structure is better, the water drainage efficiency of the first flat portion 10 is improved, and the wind resistance of the heat exchange fin 1 is effectively reduced, thereby ensuring the heat exchange efficiency of the heat exchange fin 1.

[0073] As Figure 6 , Figure 9 and Figure 12As shown, in this embodiment, it can be understood that, in a cross section perpendicular to the tangent line of the third edge 101, the main surface of the second guide portion 302 and the main surface of the first flat portion 10 have mutually connected cross-sectional lines on the first side LB1 or the second side LB2, and the angle J4 between the first guide portion 301 and the first flat portion 10 is the acute angle formed between the cross-sectional lines of the main surface of the second guide portion 302 and the main surface of the first flat portion 10 on the first side LB1 or the second side LB2, wherein the angle formed between the cross-sectional lines of the main surface of the second guide portion 302 and the main surface of the first flat portion 10 includes a complementary acute angle and an obtuse angle. In this embodiment of the application, Figure 12 The angle J4 is the acute angle between the main surface of the second guide portion 302 on the second side LB2 and the cross-sectional line of the main surface of the first flat portion 10. It should be understood that in this embodiment of the present application, the heat exchange fin 1 is a plate structure with uniform thickness, and the angles between the main surface of the second guide portion 302 on the first side LB1 and the cross-sectional line of the main surface of the first flat portion 10 on the second side LB2 are equal.

[0074] It should be noted that there are multiple tangents along the length of the third edge 101, wherein the reference plane P2 is a reference plane perpendicular to one of the tangents of the third edge 101. In any embodiment of this document, the positional relationship between the first guide portion 301 and the first flat portion 10 is exemplified by the angle J4 between the first guide portion 301 and the first flat portion 10 within the reference plane P2.

[0075] like Figure 13 As shown, in some embodiments, the maximum value of the height difference H4 between the second guide portion 302 and the first flat portion 10 along the axial direction x3 is less than or equal to 0.7 mm. If the height difference H4 is too high, the wind resistance of the heat exchange plate 1 will increase. If the height difference H4 is too low, it will affect the fluidity of the water molecule aggregate 80 in the channel-like structure. Therefore, setting the maximum value of the height difference H4 to less than or equal to 0.7 mm can make the height difference H4 setting more reasonable, so that the fluidity of the water molecule aggregate 80 in the channel-like structure is better, thereby improving the drainage efficiency of the first flat portion 10 and effectively reducing the wind resistance of the heat exchange plate 1, thereby ensuring the heat exchange efficiency of the heat exchange plate 1. It should be noted that, in Figure 13 In the embodiment, the first flat portion 10 and the second flat portion 20 are arranged parallel and coplanar.

[0076] like Figure 15As shown, in some embodiments, the first spacer portion 303 has a height difference H7 with the first flat portion 10 along the axial direction x3, wherein, in this embodiment, the height difference H7 is determined by the height difference H4 between the second guide portion 302 and the first flat portion 10 along the axial direction x3. In other words, in this embodiment, the height difference H7 between the first spacer portion 303 and the first flat portion 10 is the height difference H4 between the second guide portion 302 and the first flat portion 10 along the axial direction x3.

[0077] The first spacer 303 includes an overlapping region 305 that overlaps with the cylindrical portion 50 when viewed along the second direction x2. At least within the overlapping region 305, the height difference H7 between the first spacer 303 and the first flat portion 10 along the axial direction x3 is less than the height difference H3 between the cylindrical portion 50 and the first flat portion 10 along the axial direction x3. This effectively reduces the obstruction of the cylindrical portion 50 by the overlapping region 305 without significantly affecting the function of the first spacer 303, thereby reducing wind resistance around the cylindrical portion 50. This allows heat exchange gas to flow smoothly around the cylindrical portion 50 along the second direction x2, thereby effectively improving the heat exchange efficiency of the cold gate pipe. In some embodiments, the height difference H3 is also the dimension of the cylindrical portion 50 along the axial direction x3.

[0078] For example, Figure 15 As shown, in some embodiments, along the first direction x1, the height difference H7 of each region of the first spacer 303 relative to the first flat portion 10 can be set to be unequal. The height difference H7 of the first spacer 303 relative to the first flat portion 10 in the overlapping region 305 is smaller than the height difference H7 of the first spacer 303 relative to the first flat portion 10 in other regions. The height difference H7 of the first spacer 303 relative to the first flat portion 10 in the overlapping region 305 is smaller than the height difference H3. Of course, in other embodiments, along the first direction x1, the height difference H7 of each region of the first spacer 303 relative to the first flat portion 10 can also be set to be equal, and the height difference H7 of each region of the first spacer 303 relative to the first flat portion 10 is smaller than the height difference H3.

[0079] like Figure 15 As shown, in some embodiments, the minimum value of the height difference H7 between the first spacer 303 and the first flat portion 10 along the axial direction x3 is located within the overlapping area 305. In other words, the lowest point G of the first spacer 303 relative to the first flat portion 10 along the axial direction x3 is located within the overlapping area 305, and there is a height difference between the highest point of the first spacer 303 along the axial direction x3 (that is, the highest point of the first spacer 303 along the axial direction x3 relative to the first flat portion 10) and the lowest point G (that is, the lowest point of the first spacer 303 along the axial direction x3 relative to the first flat portion 10), and the height difference is less than one third of the height difference H3.

[0080] Specifically, ifFigure 15 As shown, the height difference between the highest point and the lowest point G of the first interval part 303 along the axial direction x3 can be understood as the difference between the height difference H6 of the highest point of the first interval part 303 along the axial direction x3 relative to the first flat part 10 and the height difference H5 of the lowest point G of the first interval part 303 along the axial direction x3 relative to the first flat part 10, and the difference is less than one third of the height difference H3, so as to ensure the heat dissipation efficiency of the heat exchange sheet 1 while effectively improving the drainage efficiency of the heat exchange sheet 1. It should be noted that the height difference H7 is defined as the height difference of the first interval part 303 along the axial direction x3 relative to the first flat part 10, the height difference H6 is defined as the height difference of the highest point of the first interval part 303 along the axial direction x3 relative to the first flat part 10, and the height difference H5 is defined as the height difference of the lowest point G of the first interval part 303 along the axial direction x3 relative to the first flat part 10.

[0081] As shown in FIG. 1, in some embodiments, the heat exchange sheet 1 is a symmetric structure symmetrically arranged with respect to a reference plane P1, and the first flat part 10, the second flat part 20, and the first interval part 303 are symmetrically arranged with respect to the reference plane P1. The first flat part 10 is a flat sheet structure continuously extending along the first direction x1, and the two parts of the second flat part 20 are arranged on both sides of the first flat part 10 along the second direction x2. Figure 6 Figure 9 As shown in FIG. 1, in some embodiments, the heat exchange sheet 1 is a symmetric structure symmetrically arranged with respect to a reference plane P1, and the first flat part 10, the second flat part 20, and the first interval part 303 are symmetrically arranged with respect to the reference plane P1. The first flat part 10 is a flat sheet structure continuously extending along the first direction x1, and the two parts of the second flat part 20 are arranged on both sides of the first flat part 10 along the second direction x2.

[0082] As shown in FIG. 1, in some embodiments, the heat exchange sheet 1 is a symmetric structure symmetrically arranged with respect to a reference plane P1, and the first flat part 10, the second flat part 20, and the first interval part 303 are symmetrically arranged with respect to the reference plane P1. The first flat part 10 is a flat sheet structure continuously extending along the first direction x1, and the two parts of the second flat part 20 are arranged on both sides of the first flat part 10 along the second direction x2. Figure 4 to Figure 12 Specifically, the inclined arrangement of the second flow guide part 60 relative to the second flat part 20 can be understood as the protruding arrangement of the second flow guide part 60 along the axial direction x3 of the through hole 40 towards one side of the second flat part 20, and the positional relationship between the second flow guide part 60 and the second flat part 20 is between perpendicular and parallel.

[0083]

[0084] ​​The second flow guide part 60 can play a role of assisting the water molecule collection 80 on the main surface of the second flat part 20 to flow, thereby accelerating the drainage efficiency of the second flat part 20. More specifically, along one side of the axial direction x3 of the through hole 40, the main surface of the second flow guide part 60 and the main surface of the second flat part 20 form a channel-like structure extending along the first direction x1, thereby effectively improving the drainage efficiency of the second flat part 20, and further effectively improving the drainage efficiency of the heat exchange fin 1.

[0085] The included angle J3 between the second flow guide part 60 and the second flat part 20 is greater than or equal to 15° and less than or equal to 45°. The included angle between the second flow guide part 60 and the second flat part 20 will directly affect the curvature of the channel-like structure, wherein the greater the included angle J3 between the second flow guide part 60 and the second flat part 20, the greater the curvature of the channel-like structure, and the better the flowability of the water molecule collection 80 in the channel-like structure, but at the same time, the greater the included angle between the second flow guide part 60 and the second flat part 20, the greater the resistance of the second flow guide part 60 to the heat exchange gas blown along the second direction x2 to the heat exchange fin 1 and the refrigerant pipe (that is, the greater the included angle between the second flow guide part 60 and the second guide part 302, the greater the wind resistance of the heat exchange fin 1), which affects the heat exchange efficiency of the heat exchange device. Therefore, the included angle J3 between the second flow guide part 60 and the second flat part 20 is set to be between 15° and 45°, for example, 15°, 30°, 40° or 45°, and the like. Thus, the included angle J3 between the second flow guide part 60 and the second flat part 20 is reasonable, the flowability of the water molecule collection 80 in the channel-like structure is better, the drainage efficiency of the second flat part 20 is improved, and at the same time, the wind resistance of the heat exchange fin 1 is effectively reduced, thereby ensuring the heat exchange efficiency of the heat exchange device.

[0086] Moreover, the included angle J3 between the second flow guide part 60 and the second flat part 20 is greater than or equal to 15° and less than or equal to 45°, which effectively reduces the forming difficulty of the second flow guide part 60, and further effectively improves the processing convenience of the heat exchange fin 1.

[0087] It can be understood that in the cross section perpendicular to the tangent line of the second edge 202, the main surface of the second flow guide part 60 and the main surface of the second flat part 20 exist cross section lines connected to each other at the first side LB1 or the second side LB2, and the included angle J3 between the second flow guide part 60 and the second flat part 20 is the acute angle formed between the cross section lines of the main surface of the second flow guide part 60 and the main surface of the second flat part 20 at the first side LB1 or the second side LB2, wherein the included angle formed between the cross section lines of the main surface of the second flow guide part 60 and the main surface of the second flat part 20 includes complementary acute angles and obtuse angles. In the embodiments of the present application, Figure 10 、 Figure 11 and Figure 12The angle J3 indicated in the figure is the acute angle between the main surface of the second air guide portion 60 and the cross-sectional line of the main surface of the second flat portion 20 on the second side LB2. It should be understood that in the embodiment of the present application, the heat exchange fin 1 is a plate structure with uniform thickness, and the angles between the main surface of the second air guide portion 60 and the cross-sectional line of the main surface of the second flat portion 20 on the first side LB1 and the second side LB2 are equal.

[0088] It should be noted that there are multiple tangents along the length of the second edge 202, wherein the reference plane P2 is a reference plane perpendicular to one of the tangents of the second edge 202. In any embodiment of this document, the angle J3 between the second guide portion 60 and the second flat portion 20 within the reference plane P2 is used to exemplify the positional relationship between the second guide portion 60 and the second flat portion 20.

[0089] like Figure 11 and Figure 12 As shown, in some embodiments, the inclination direction of the second guide portion 60 relative to the first flat portion 10 is consistent with the inclination direction of the first guide portion 301 relative to the first flat portion 10. In other words, the inclination direction of the second guide portion 60 relative to the second flat portion 20 is inconsistent with the inclination direction of the first guide portion 301 relative to the second flat portion 20. More specifically, the first guide portion 301 protrudes toward the second side LB2 along the axial direction x3 relative to the first flat portion 10, and the second guide portion 60 protrudes toward the second side LB2 along the axial direction x3 relative to the first flat portion 10. Therefore, the inclination direction of the second guide portion 60 relative to the first flat portion 10 is consistent with the inclination direction of the first guide portion 301 relative to the first flat portion 10, and their inclination directions are both set toward the second side LB2 relative to the first flat portion 10. The first guide portion 301 protrudes toward the first side LB1 along the axial direction x3 relative to the second flat portion 20, and the second guide portion 60 protrudes toward the second side LB2 along the axial direction x3 relative to the second flat portion 20. Therefore, the inclination direction of the second guide portion 60 relative to the second flat portion 20 is inconsistent with the inclination direction of the first guide portion 301 relative to the second flat portion 20. Thus, on the second side LB2 , a channel-like structure extending along the first direction x1 can be formed between the main surface of the first guide portion 301 and the main surface of the second flat portion 20 , thereby effectively improving the drainage efficiency of the second flat portion 20 and further effectively improving the drainage efficiency of the heat exchange plate 1 .

[0090] like Figure 11As shown, in some embodiments, the second flat portion 20 and the cylindrical portion 50 are located on opposite sides of the first flat portion 10 along the axial direction x3. This allows the projections of the first guide portion 301, the second flow guide portion 60, and the second flat portion 20 along at least the second direction x2 to not overlap with the projection of the circular portion 5 along the second direction x2. This effectively reduces the obstruction of the cylindrical portion 50 by the first guide portion 301, the second flow guide portion 60, and the second flat portion 20, thereby reducing wind resistance around the cylindrical portion 50. This allows the heat exchange gas to flow smoothly around the cylindrical portion 50 along the second direction x2, thereby effectively improving the heat exchange efficiency of the cold gate pipe. Furthermore, the first flat portion 10 and the second flat portion 20 are arranged parallel to each other, and the dimension of the cylindrical portion 50 along the axial direction x3 (i.e., the height difference H3) is greater than the sum of the dimension of the first guide portion 301 along the axial direction x3 (i.e., the height difference H1) and the dimension H2 of the second flow guide portion 60 along the axial direction x3.

[0091] like Figure 10 As shown, in some embodiments, the inclination direction of the second air guide portion 60 relative to the first flat portion 10 is inconsistent with the inclination direction of the first guide portion 301 relative to the first flat portion 10. In other words, the inclination direction of the second air guide portion 60 relative to the second flat portion 20 is consistent with the inclination direction of the first guide portion 301 relative to the second flat portion 20. More specifically, the first guide portion 301 protrudes toward the second side LB2 along the axial direction x3 relative to the first flat portion 10, and the second air guide portion 60 protrudes toward the first side LB1 along the axial direction x3 relative to the first flat portion 10. Therefore, the inclination direction of the second air guide portion 60 relative to the first flat portion 10 is inconsistent with the inclination direction of the first guide portion 301 relative to the first flat portion 10. The first guide portion 301 protrudes relative to the second flat portion 20 along the axial direction x3 toward the first side LB1, and the second guide portion 60 protrudes relative to the second flat portion 20 along the axial direction x3 toward the first side LB1. Therefore, the inclination direction of the second guide portion 60 relative to the second flat portion 20 is consistent with the inclination direction of the first guide portion 301 relative to the second flat portion 20, and both inclination directions are arranged toward the second side LB2 relative to the second flat portion 20. Thus, on the first side LB2, a channel-like structure extending along the first direction x1 is formed between the main surfaces of the first guide portion 301, the second guide portion 60, and the second flat portion 20, thereby effectively improving the drainage efficiency of the second flat portion 20 and, by extension, the heat exchange fin 1.

[0092] like Figure 4 、 Figure 5 and Figure 6 As shown, in at least a portion of the heat exchange plate 1 along the first direction x1 (also called the gradual change section of the heat exchange plate 1 ), the size of at least one of the first flat portion 10 and the second flat portion 20 along the second direction x2 is configured to gradually change along the first direction x1.

[0093] It is to be noted that the first dimension L2 of the first flat portion 10 along the second direction x2 can be understood as the interval distance between the third edges 101 located on both sides of the reference plane PI along the second direction x2. The third dimension LI of the second flat portion 20 along the second direction x2 can be understood as the distance between the first edge 201 and the second edge 202 located on the same side of the reference plane PI along the second direction x2.

[0094] In some embodiments, the first flat portion 10 and the second flat portion 20 are arranged in parallel (i.e. the main surface of the first flat portion 10 and the main surface of the second flat portion 20 are parallel to each other), and the first flat portion 10 and the second flat portion 20 are both parallel to the second direction x2. The third dimension LI of the second flat portion 20 is defined as the dimension of the second flat portion 20 parallel to the main surface and perpendicular to the first direction xi. In other embodiments, the first flat portion 10 and the second flat portion 20 can also be arranged at a certain angle.

[0095] It is to be noted that, in this document, if not otherwise specified, the flat portion 70 refers to any one of the first flat portion 10 and the second flat portion 20.

[0096] The dimension L0 of the flat portion 70 along the second direction x2 is set to gradually change along the first direction x1. It can be understood that the dimension L0 of the flat portion 70 along the second direction x2 is set to gradually increase, gradually decrease, first gradually increase and then gradually decrease, first gradually decrease and then gradually increase, periodically first gradually decrease and then gradually increase, or periodically first gradually increase and then gradually decrease, etc. along the first direction x1. Therefore, the dimension L0 of the flat portion 70 along the second direction x2 is set to gradually change along the first direction x1, which can make the flat portion 70 include at least one tapered area or a gradually widened area along the first direction x1. The width dimension of the flat portion 70 will change along with the dimension L0 of the flat portion 70 along the second direction x2. Therefore, setting the dimension L0 of the flat portion 70 along the second direction x2 to gradually change along the first direction x1 can make the width dimension of the flat portion 70 gradually change along the first direction x1, so that the main surface of the flat portion 70 is gradually configured such as gradually shrinking, gradually widening, first gradually shrinking and then gradually widening, first gradually widening and then gradually shrinking, periodically first gradually shrinking and then gradually widening, or periodically first gradually widening and then gradually shrinking. In this way, in the gradually shrinking area or the gradually widening area, the main surface of the flat portion 70 includes a shrinking plane area with a smaller width dimension and a wide-opening plane area with a larger width dimension. The water molecule aggregate 80 located in the shrinking plane area is subjected to a larger capillary action and is guided to the wide-opening plane area under the capillary action, thereby achieving the effect of the water molecule aggregate 80 converging in the wide-opening plane area. When the water aggregate in the wide-opening plane area converges to a certain mass, the water molecule aggregate 80 will accelerate to continue flowing along the first direction x1 under the action of gravity, thereby effectively improving the drainage efficiency of the heat exchange plate 1 during the defrosting process, so as to effectively improve the defrosting efficiency of the heat exchange device.

[0097] Therefore, in at least a partial section of the heat exchange plate 1 along the first direction x1 (also called the gradient section of the heat exchange plate 1), the dimension L0 of the flat portion 70 along the second direction x2 is set to gradually change along the first direction x1, so that the flat portion 70 has a better guiding effect on the water molecule aggregate 80 along the first direction x1, thereby effectively improving the drainage efficiency of the heat exchange plate 1, and further effectively improving the defrosting efficiency of the heat exchange device.

[0098] like Figure 16a 、 Figure 16b 、 Figure 16c and Figure 16d As shown, the minimum value Lmin of the third dimension L1 of the second flat portion 20 along the second direction x2 is set to be less than or equal to 3 mm. For example, the minimum value Lmin of the third dimension L1 can be an actual value less than or equal to 3 mm, such as 3 mm, 2.5 mm, 2 mm, 1.5 mm or 1 mm. This can effectively improve the convergence effect of the main surface of the second flat portion 20 on the water molecule aggregate 80 in the shrinkage plane area, thereby improving the drainage efficiency of the heat exchange plate 1 during the defrosting process, thereby effectively improving the defrosting efficiency of the heat exchange device.

[0099] Specifically, as shown in Figure 16a and Figure 16b When the minimum value Lmin of the third dimension L1 is large, for example, the minimum value Lmin is greater than 3mm, the area near the position where the minimum value Lmin of the third dimension L1 of the second flat portion 20 along the second direction x2 is located (i.e., the main surface of the second flat portion 20 is in the narrow plane area) is poor in the effect of converging the water molecule assembly 80, the water molecule assembly 80 in the narrow plane area is subjected to the effect of gravity greater than that of the capillary force, so that the narrow plane area cannot play a role in converging the water molecule assembly 80, and the water molecule assembly 80 in each area along the second direction x2 flows along the first direction x1 under the action of gravity respectively and individually, so that the second flat portion 20 is poor in the effect of guiding flow.

[0100] As shown in Figure 16c and Figure 16d When the minimum value Lmin of the third dimension L1 of the second flat portion 20 along the second direction x2 is set to 1.5mm, the main surface of the second flat portion 20 is in the narrow plane area and has a good effect of converging the water molecule assembly 80, the water molecule assembly 80 in the narrow plane area of the main surface of the second flat portion 20 is subjected to the effect of capillary gravity smaller than that of the capillary force, so that the narrow plane area of the main surface of the second flat portion 20 plays a role in converging the water molecule assembly 80, and the water molecule assembly 80 in each area along the second direction x2 converges towards the direction of the resultant force of the capillary force under the action of the capillary force, as shown in Figure 16c , on the first side LB1, the water molecule assembly 80 on the second flat portion 20 converges towards the first guide portion 301 under the action of the capillary force and flows along the first direction x1 to the wide plane area of the main surface of the second flat portion 20, so that the water molecule assembly 80 on the main surface of the second flat portion 20 can flow along the first direction x1 at a greater gravitational acceleration, thereby effectively accelerating the drainage efficiency of the second flat portion 20, and further effectively improving the drainage efficiency of the heat exchange fin 1 during defrosting, so as to effectively improve the defrosting efficiency of the heat exchange device. As shown in Figure 16d , on the second side LB2, the water molecule assembly 80 on the second flat portion 20 converges towards the second guide portion 60 under the action of the capillary force and flows along the first direction x1 to the wide plane area of the main surface of the second flat portion 20, so that the water molecule assembly 80 on the main surface of the second flat portion 20 can flow along the first direction x1 at a greater gravitational acceleration, thereby effectively accelerating the drainage efficiency of the second flat portion 20, and further effectively improving the drainage efficiency of the heat exchange fin 1 during defrosting, so as to effectively improve the defrosting efficiency of the heat exchange device.

[0101] As shown in Figure 17a , Figure 17b and Figure 17cAs shown in Figure 17a The heat exchange fin structure shown in Figure 17b and Figure 17c is completely different from the structure shown in Figure 17a The heat exchange fin shown in Figure 17b and Figure 17c is Figure 2 Two different embodiments of the heat exchange fin 1 shown in Figure 17b , the minimum value of the third dimension L1 of the second flat portion 20 along the second direction x2 is set to 2.5mm, in Figure 17c , the minimum value of the third dimension L1 of the second flat portion 20 along the second direction x2 is set to 1.5mm. The test results obtained under the same environmental conditions and the same time show that Figure 17a The drainage efficiency of the heat exchange fin shown in Figure 17b and Figure 17c is far worse than that of the heat exchange fin shown in Figure 17c The drainage efficiency of the heat exchange fin shown in Figure 17b is better than that of the heat exchange fin shown in Thus, setting the dimension of at least one of the first flat portion 10 and the second flat portion 20 along the second direction x2 to gradually change along the first direction x1, and the minimum value of the dimension (such as the first dimension L2 and / or the third dimension L1) being less than or equal to 3mm, can effectively improve the drainage efficiency of the heat exchange fin 1 during defrosting, thereby effectively improving the defrosting efficiency of the heat exchange device.

[0102] Figure 4 , Figure 5 and Figure 6 As shown in some embodiments, in the gradient section of the heat exchange fin 1, the first dimension L2 of the first flat portion 10 along the second direction x2 and the third dimension L1 of the second flat portion 20 along the second direction x2 are both set to gradually change along the first direction x1, which can effectively improve the drainage efficiency of the heat exchange fin 1, thereby effectively improving the defrosting efficiency of the heat exchange device.

[0103] For example, as shown in Figure 4 and Figure 6 , between the two adjacent reference planes P2, the first dimension L2 of the first flat portion 10 along the second direction x2 is set to gradually decrease first and then gradually increase along the first direction x1, and the third dimension L1 of the second flat portion 20 along the second direction x2 is set to gradually increase first and then gradually decrease along the first direction x1.

[0104] For example, as shown in Figure 4 , Figure 5 and Figure 6As shown, the second flat portion 20 comprises a first edge 201 and a second edge 202, wherein the first edge 201 is arranged to be curved along the first direction x1, such that the third dimension L1 of the second flat portion 20 along the second direction x2 is gradually varied along the first direction x1 at least within the gradual change section of the heat exchange sheet 1. Specifically, as shown in Figure 4 , Figure 5 and Figure 6 between two adjacent reference planes P2, the second edge 202 is arranged to be straight along the first direction x1, and the first edge 201 is arranged to be curved such that it gradually approaches the second edge 202 and then gradually moves away from the second edge 202, such that the third dimension L1 of the second flat portion 20 along the second direction x2 is arranged to gradually decrease and then gradually increase along the first direction x1.

[0105] For example, as shown in Figure 4 and Figure 6 the first flat portion 10 comprises a third edge 101, wherein the third edge 101 is arranged to be curved along the first direction x1, such that the first dimension L2 of the first flat portion 10 along the second direction x2 is gradually varied along the first direction x1 at least within the gradual change section of the heat exchange sheet 1. Specifically, as shown in Figure 4 and Figure 6 the first flat portion 10 comprises two third edges 101 respectively located on two sides of the reference plane P1, and the two third edges 101 are symmetrically arranged with respect to the reference plane P1 and are not connected to each other. Between two adjacent reference planes P2, the third edges 101 are arranged to be curved along the first direction x1, and the two third edges 101 are arranged to gradually approach and then gradually move away from each other along the first direction x1 along the second direction x2, such that the first dimension L2 of the first flat portion 10 along the second direction x2 is arranged to gradually increase and then gradually decrease along the first direction x1. As shown in Figure 5 in some embodiments, the first flat portion 10 comprises a third edge 101, wherein the third edge 101 comprises two portions of the third edge 101 respectively located on two sides of the reference plane P1, and the two portions of the third edge 101 are symmetrically arranged with respect to the reference plane P1. Between two adjacent reference planes P2, the two portions of the third edge 101 are arranged to be curved along the first direction x1, and the two portions of the third edge 101 are arranged to gradually approach and then gradually move away from each other along the first direction x1 along the second direction x2, such that the first dimension L2 of the first flat portion 10 along the second direction x2 is arranged to gradually increase and then gradually decrease along the first direction x1.

[0106] As shown in Figure 4 , Figure 5 and Figure 6As shown, in some embodiments, the size L0 of the flat portion 70 along the second direction x2 is arranged to be continuously and periodically gradually changed along the first direction x1. Specifically, the size L0 of the flat portion 70 along the second direction x2 is arranged to be continuously and periodically gradually changed from gradually decreasing to gradually increasing or from gradually increasing to gradually decreasing along the first direction x1 throughout the length range of the heat exchange fin 1 along the first direction x1, which can effectively improve the drainage efficiency of the heat exchange fin 1 during defrosting, thereby effectively improving the defrosting efficiency of the heat exchange device.

[0107] Specifically, as shown in Figs. 1 to 3, Figure 4 , Figure 5 and Figure 6 , the first size L2 of the first flat portion 10 along the second direction x2 and the third size L1 of the second flat portion 20 along the second direction x2 are arranged to be continuously and periodically gradually changed along the first direction x1 throughout the length range of the heat exchange fin 1 along the first direction x1, which can effectively improve the drainage efficiency of the heat exchange fin 1, thereby effectively improving the defrosting efficiency of the heat exchange device.

[0108] As shown in Figs. 1 to 3, Figure 4 , Figure 5 and Figure 6 , in some embodiments, the first size L2 of the first flat portion 10 along the second direction x2 and the third size L1 of the second flat portion 20 along the second direction x2 are arranged to be staggered along the first direction x1. Specifically, the position where the minimum value of the third size L1 of the second flat portion 20 along the second direction x2 is located is flush with the center of the through hole 40, the position where the maximum value of the third size L1 of the second flat portion 20 along the second direction x2 is located is between two through holes 40, the position where the minimum value of the first size L2 of the first flat portion 10 along the second direction x2 is located is between two adjacent through holes 40, and the position where the maximum value of the first size L2 of the first flat portion 10 along the second direction x2 is located is flush with the center of the through hole 40, so that the position where the minimum value of the third size L1 of the second flat portion 20 along the second direction x2 is located is staggered with the position where the minimum value of the first size L2 of the first flat portion 10 along the second direction x2 is located, and the position where the maximum value of the third size L1 of the second flat portion 20 along the second direction x2 is located is staggered with the position where the maximum value of the first size L2 of the first flat portion 10 along the second direction x2 is located, so that the first size L2 of the first flat portion 10 along the second direction x2 and the third size L1 of the second flat portion 20 along the second direction x2 are arranged to be staggered along the first direction x1, which can effectively improve the space utilization of the heat exchange fin 1.

[0109] As shown in Figs. 1 to 3, Figure 6 and Figure 9As shown, in some embodiments, the first flat portion 10 is provided with a flow distribution portion 103 at the position of the minimum value of the first dimension L2 of the first flat portion 10 along the second direction x2, specifically, the flow distribution portion 103 penetrates a reference plane of the minimum value of the first dimension L2 of the first flat portion 10 along the second direction x2 along the first direction x1, and the reference plane is the reference plane P2. Wherein, the flow distribution portion 103 separates the first flat portion 10 into at least two flow distribution zones arranged along the second direction x2. Specifically, on the first side LB1, the flow distribution portion 103 is recessed relative to the first flat portion 10 along the axial direction x3, that is, in a groove shape, the flow distribution portion 103 can have a recessed flow guiding effect on the two flow distribution zones, so as to accelerate the flow speed of the water molecule assembly 80 at the position of the minimum value of the first dimension L2 of the first flat portion 10 along the second direction x2, so that the water molecule assembly 80 at the position of the minimum value of the first dimension L2 of the first flat portion 10 along the second direction x2 can flow faster to the position of the maximum value of the first dimension L2 of the first flat portion 10 along the second direction x2, thereby effectively improving the drainage efficiency of the first flat portion 10. On the second side LB2, the first spacing portion 303 is recessed relative to the first flat portion 10, and the flow distribution portion 103 is protruded relative to the first flat portion 10 along the axial direction x3, the flow distribution portion 103 can divide the position of the minimum value of the first dimension L2 of the first flat portion 10 along the second direction x2 into two flow distribution zones with smaller dimensions, so that on the second side LB2, the water molecule assembly 80 at the position of the minimum value of the first dimension L2 of the first flat portion 10 along the second direction x2 is more prone to converge towards the first spacing portion 303, thereby effectively improving the drainage efficiency of the first flat portion 10 and the first spacing portion 303. In this embodiment, the dimension of the first flat portion 10 at the position of the minimum value of the first dimension L2 along the second direction x2 is greater than 2.5 mm.

[0110] In some embodiments, the minimum value of the fourth dimension of the two flow distribution zones along the second direction x2 is greater than or equal to 1 mm and less than or equal to 3 mm, so that the flow distribution zones can effectively improve the convergence effect of the water molecule assembly 80 while ensuring the flowability of the water molecule assembly 80 flowing on the flow distribution zones along the first direction x1.

[0111] In some embodiments, the ratio of the first extension dimension of the flow distribution portion 103 along the first direction x1 to the second extension dimension of the flow distribution portion 103 along the second direction x2 is greater than 5, so as to reduce the forming difficulty of the flow distribution portion 103, thereby improving the processing convenience of the heat exchange fin 1.

[0112] In some embodiments, as shown in FIG. 1B, the heat exchange fin 1 further comprises a second flat portion 20 arranged along the first direction x1 and arranged on the first flat portion 10, and the second flat portion 20 is provided with a second flow distribution portion 203. Figure 18 , Figure 19 and Figure 20As shown, the surface material of the heat exchanger fin 1 is configured such that the contact angle θ between the heat exchanger fin 1 and water is less than 90 degrees. Specifically, the surface of the heat exchanger fin 1 is also the main surface of the heat exchanger fin 1. The material of the main surface of the heat exchanger fin 1 is configured such that the contact angle θ between the heat exchanger fin 1 and water is less than 90 degrees. This can effectively improve the drainage efficiency of the main surface of the heat exchanger fin 1.

[0113] Specifically, if Figure 18 As shown, the contact angle θ refers to the tangent of the gas-liquid interface at the intersection of gas, liquid (such as the water molecule aggregate 80 in the embodiment of the present application), and solid. The angle between this tangent on the liquid side and the solid-liquid boundary line is a measure of the degree of wettability. The contact angle θ of a liquid on the surface of a solid material, such as the contact angle θ of the water molecule aggregate 80 on the main surface of the heat exchange plate 1 in the embodiment of the present application, is an important parameter for measuring the wettability of the liquid on the surface of the material. By measuring the contact angle θ, a lot of information about the interaction between the solid-liquid and solid-gas interfaces on the surface of the material can be obtained. The contact angle θ measurement technology can not only be used for the common characterization of the surface properties of materials, but also has important applications in the fields of petroleum industry, flotation industry, pharmaceutical materials, chip industry, low surface energy non-toxic anti-fouling materials, inks, cosmetics, pesticides, printing and dyeing, papermaking, textile finishing, detergents, spraying, sewage treatment, etc. If the contact angle θ is less than 90°, the solid surface is hydrophilic, meaning liquids wet the solid more easily. A smaller contact angle indicates better wettability. If the contact angle θ is greater than 90°, the solid surface is hydrophobic, meaning liquids do not wet the solid easily. Water soaking and consistency comparison experiments were conducted on hydrophilic and hydrophobic heat exchanger sheets 1, respectively. The experiments revealed that all water molecule aggregates 80 condensed on the main surfaces of the hydrophobic heat exchanger sheets 1 formed large, visible droplets attached to the main surfaces of the hydrophobic heat exchanger sheets 1. In contrast, the water molecule aggregates 80 on the main surfaces of the hydrophilic heat exchanger sheets 1 formed a film-like structure, with no visible droplets attached to the surface.

[0114] like Figure 18 and Figure 19As shown, in the embodiment of the present application, the heat exchange device comprises a plurality of heat exchange fins 1 arranged along the axial direction x3 at intervals, wherein the interval distance j1 between each heat exchange fin 1 is greater than or equal to 1.3 mm, for example, the interval distance j1 can be 1.3 mm or other actual values greater than or equal to 1.3 mm. The hydrophilic heat exchange fin 1 and the hydrophobic heat exchange fin 1 are defrosted and drained respectively. Through experiments, it is found that when the hydrophilic heat exchange fin 1 is defrosted, the thickness of the water droplets condensed by the water molecule assembly 80 is less than the interval distance j1 between the heat exchange fins 1, so that the water molecule assembly 80 on the main surface of the heat exchange fin 1 can be discharged in the form of a film. For the hydrophobic heat exchange fin 1, the thickness of the water droplets formed by the water molecule assembly 80 is greater than the interval distance j1 between the heat exchange fins 1, and finally a water bridge is formed. Once the water bridge is formed, it will be subjected to a great capillary force, which will hinder the discharge of the water molecule assembly 80. Therefore, the material of the main surface of the heat exchange fin 1 is set to a material with a contact angle θ with water less than 90 degrees, so that the main surface of the heat exchange fin 1 is hydrophilic. Compared with the hydrophobic heat exchange fin 1, the hydrophilic heat exchange fin 1 can effectively reduce the capillary force of the water molecule assembly 80 between two heat exchange fins 1, thereby effectively improving the drainage efficiency of the heat exchange device.

[0115] In some embodiments, the heat exchange fin 1 is formed by an integrated molding process, such as a stamping process.

[0116] It is worth noting that the drawings herein are only used to show the structural relationship and connection relationship of the utility model product of the present application, and do not limit the specific structure size of the utility model product of the present application.

[0117] The above is only an embodiment of the present application, and does not limit the patent scope of the present application, and any equivalent structure or equivalent process transformation using the contents of the present application specification and drawings, or direct or indirect application in other related technical fields, are also included in the patent protection scope of the present application.

Claims

1. A heat exchange device, characterized in that: The heat exchanger comprises a heat exchange plate and a refrigerant tube, wherein the heat exchange plate comprises a first flat portion, a second flat portion, and a first spacer portion, wherein the first flat portion is provided with a plurality of through holes spaced apart along a first direction, and the refrigerant tube is passed through the through holes; the first flat portion and the second flat portion are respectively connected to opposite sides of the first spacer portion along a second direction, and the second flat portion and the first flat portion extend continuously along the first direction; and the first spacer portion extends in a continuous wave shape along the first direction; The second direction intersects with the axial direction of the through hole and the first direction respectively.

2. The heat exchange device according to claim 1, characterized in that: The first spacing portion is convex or concave along the axial direction.

3. The heat exchange device according to claim 1, characterized in that In at least one first reference plane perpendicular to the first direction, a first dimension of the first flat portion along the second direction is greater than a second dimension of the first spacer along the second direction; and / or a third dimension of the second flat portion along the second direction is greater than the second dimension.

4. The heat exchange device according to claim 1, characterized in that In at least a partial section of the heat exchange plate along the first direction, a size of at least one of the first flat portion, the second flat portion, and the first spacer in the second direction is configured to first increase and then decrease or first decrease and then increase along the first direction.

5. The heat exchange device according to claim 4, characterized in that: In at least a portion of the heat exchange fin along the first direction, a first dimension of the first flat portion in the second direction is configured to first gradually increase and then gradually decrease, and a third dimension of the second flat portion in the second direction is configured to first gradually decrease and then gradually increase; or A first dimension of the first flat portion in the second direction is configured to first gradually decrease and then gradually increase, and a third dimension of the second flat portion in the second direction is configured to first gradually increase and then gradually decrease.

6. The heat exchange device according to claim 5, characterized in that: Between two adjacent second reference planes, the first dimension is set to first decrease and then increase, and the third dimension is set to first increase and then decrease, wherein the second reference plane passes through the axis of the through hole and is set perpendicular to the first direction.

7. The heat exchange device according to claim 6, characterized in that: Between two adjacent through holes, the first flat portion is provided with a diversion portion protruding or recessed relative to the first flat portion, and the diversion portion is used to separate the first flat portion into two diversion areas located on both sides of the diversion portion along the second direction.

8. The heat exchange device according to claim 7, characterized in that: The diverter portion passes through a third reference plane where the minimum value of the first dimension is located along the first direction, and the third reference plane is arranged parallel to the second reference plane.

9. The heat exchange device according to claim 7, characterized in that: The diverter portion includes a first extension parallel to the first direction and a second extension parallel to the second direction, and a ratio of a maximum value of the first extension to a maximum value of the second extension is greater than 5.

10. The heat exchange device according to claim 7, characterized in that: A minimum value of a fourth dimension of the two diversion areas along the second direction is greater than or equal to 1 mm and less than or equal to 3 mm.

11. The heat exchange device according to claim 2, characterized in that: The first flat portion is provided with a cylindrical portion arranged along the edge of the through hole, the first spacer portion and the cylindrical portion are protruded toward the same side of the first flat portion and the second flat portion, the first spacer portion includes an overlapping area overlapping with the cylindrical portion when viewed along the second direction, and at least in the overlapping area, a first height difference between the first spacer portion and the first flat portion along the axial direction is smaller than a second height difference between the cylindrical portion and the first flat portion along the axial direction.

12. The heat exchange device according to claim 11, characterized in that: The minimum value of the first height difference is located in the overlapping area. A third height difference exists between the highest point and the lowest point of the first spacer along the axial direction. The third height difference is less than one third of the second height difference.

13. The heat exchange device according to claim 2, characterized in that: The first spacer is arranged in a tapered shape along its protruding direction.

14. The heat exchange device according to any one of claims 1 to 13, characterized in that: The heat exchange device includes a gas delivery mechanism configured to deliver heat exchange gas toward the heat exchange fins and the refrigerant pipe along the second direction.

15. The heat exchange device according to any one of claims 1 to 13, characterized in that: The surface material of the heat exchange plate is configured so that the contact angle between the heat exchange plate and water is less than 90 degrees.

16. The heat exchange device according to any one of claims 1 to 13, characterized in that: The heat exchange device includes a plurality of heat exchange fins, which are spaced apart along the axial direction. The refrigerant pipe is sequentially passed through the plurality of through holes along the axial direction, and the outer surface of the refrigerant pipe is in contact with the hole wall of the through hole.

17. An air conditioning device, characterized in that: A heat exchange device comprising any one of claims 1-13, 14, 15 or 16.

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