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 flow guide part, the first flat part is provided with a plurality of through holes formed in the first direction at intervals, and the refrigerant pipe is arranged in the through holes in a penetrating mode and penetrates through the first flow guide part in the axial direction of the through holes. The first flat part and the second flat part are arranged at intervals in the second direction, the second direction intersects with the axial direction of the through hole and the first direction, and the first flow guide part is arranged between the first flat part and the second flat part. The first flow guide part is obliquely arranged relative to the first flat part and the second flat part, and in the direction from the first flat part to the second flat part, the height difference formed between the first flow guide part and the second flat part in the axial direction is gradually reduced. 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, while 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, the outdoor heat exchange fins will have frost formation, which makes it difficult for air flow to circulate the main surface of the heat exchange fins, resulting in deterioration of heat exchange. Therefore, it is necessary to perform defrosting operation 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 an urgent technical problem to be solved. 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 flow guide 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 arranged spaced apart along a second direction. There is a gap between the first flat portion and the second flat portion along the axial direction of the through holes. The first flow guide portion is arranged between the first flat portion and the second flat portion. The first flow guide portion is arranged inclined with respect to the first flat portion and the second flat portion, and in the direction from the first flat portion to the second flat portion, the height difference between the first flow guide portion and the second flat portion along the axial direction gradually decreases. The second direction intersects the axial direction of the through holes and the first direction.

[0005] The beneficial effects of the embodiments of this application are as follows: This application provides a heat exchange device, which includes heat exchange plates and refrigerant pipes. The heat exchange plates include a first flat portion, a second flat portion, and a first flow guide portion. The first flat portion and the second flat portion are spaced apart along the axial direction and connected by a first flow guide portion that is inclined relative to the first flat portion and the second flat portion, thereby setting the main surfaces of the first flat portion and the second flat portion in a gradient shape along the axial direction. The first guide portion is connected between the first flat portion and the second flat portion, so that the main surface of the first guide portion can serve as a guide slope between the main surfaces of the first flat portion and the second flat portion. This makes the main surfaces of the heat exchange plates on the first and second sides stepped, so that the water molecule aggregates on the main surfaces of the first and second sides of the heat exchange plates have two flow modes, thereby effectively improving the drainage efficiency of the heat exchange plates and thus effectively improving the defrosting efficiency of the heat exchange device. Attached Figure Description

[0006] Figure 1 This is a three-dimensional structural schematic diagram of the first embodiment of the heat exchanger of this application;

[0007] Figure 2 This is a three-dimensional structural schematic diagram of the second embodiment of the heat exchanger of this application;

[0008] Figure 3 This is a three-dimensional structural schematic diagram of the third embodiment of the heat exchanger of this application;

[0009] Figure 4 yes Figure 1 The diagram shows a front view of the heat exchanger plate on the first side along the axial direction x3.

[0010] Figure 5 yes Figure 2 The diagram shows a front view of the heat exchanger plate on the first side along the axial direction x3.

[0011] Figure 6 yes Figure 3 The diagram shows a front view of the heat exchanger plate on the first side along the axial direction x3.

[0012] Figure 7 yes Figure 1 The diagram shows a side view of the heat exchanger structure viewed along the first direction x1.

[0013] Figure 8 yes Figure 2 The diagram shows a side view of the heat exchanger structure viewed along the first direction x1.

[0014] Figure 9 yes Figure 3 The diagram shows a side view of the heat exchanger structure viewed along the first direction x1.

[0015] Figure 10 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section; Figure 4 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section;

[0016] Figure 11 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section; Figure 5 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section;

[0017] Figure 12 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section; Figure 6 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section;

[0018] Figure 13 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section; Figure 6 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section;

[0019] Figure 14 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section; Figure 2 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section;

[0020] Figure 15 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section; Figure 3 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section;

[0021] Figure 16a is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section; Figure 2 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section;

[0022] Figure 16b is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section; Figure 2 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section;

[0023] Figure 16c is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section; Figure 2 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section;

[0024] Figure 16d is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section; Figure 2 is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section;

[0025] Figure 17a is a partial cross-sectional view of the heat exchange sheet shown in FIG. 1, taken along the reference plane P2 as a cross section;

[0026] Figure 17b is Figure 2 The test result schematic diagram of the main surface of the first side LB1 and the second side LB2 of the heat exchange sheet shown in the figure to the water molecule cluster flow guiding effect when the minimum value of the fourth dimension of the second flat part along the second direction is set to 2.5mm;

[0027] Figure 17c is Figure 2 The test result schematic diagram of the main surface of the first side LB1 and the second side LB2 of the heat exchange sheet shown in the figure to the water molecule cluster flow guiding effect when the minimum value of the fourth dimension of the second flat part along the second direction is set to 1.5mm;

[0028] Figure 18 is the effect schematic diagram of the contact angle of the water molecule cluster 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 the hydrophilic material;

[0030] Figure 20 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 the hydrophobic material. 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 skilled 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 optionally also includes steps or units not listed, or optionally also includes other steps or units inherent to these processes, methods, products or devices.

[0033] As Figure 1 , Figure 2 and Figure 3As shown, 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 sheet 1, and a plurality of refrigerant pipes. The heat exchange sheet 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 circulate refrigerant fluid, and can directly contact with 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 sheet 1. Based on this, the refrigerant pipe cooperates with the heat exchange sheet 1, and the heat exchange sheet 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 sheet 1 to realize heat exchange with the heat exchange sheet 1, and then indirectly realizes heat exchange with the heat exchange gas in the environment through the main surfaces of the heat exchange sheet 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 sheet 1 and the refrigerant pipe, so as to realize the effect of accelerating the heat exchange efficiency of the heat exchange sheet 1 and the refrigerant pipe and the heat exchange gas, thereby improving the heat exchange efficiency of the heat exchange device.

[0034] As shown in some embodiments, Figure 1 , Figure 2 and Figure 3 , the through holes 40 are arranged in the heat exchange sheet 1 along the first direction x1, and the gas conveying mechanism is arranged to output the heat exchange gas towards the heat exchange sheet 1 and the refrigerant pipe along the second direction x2, or the gas conveying mechanism is arranged to drive the heat exchange gas in the environment to flow towards 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 parallel to the axis z1 of the through hole 40, the first direction x1 is the interval direction of the plurality of through holes 40 on the heat exchange sheet 1, and the second direction x2 is the direction intersecting with the first direction x1 and the axial direction x3, respectively. In some embodiments herein, 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 comprises 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 hole 40, and the refrigerant pipes are 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 pipes.

[0036] When the refrigerant temperature in the refrigerant pipe is higher than the ambient temperature, heat in the refrigerant is transferred through the refrigerant pipe to heat exchanger 1, and then transferred to the external environment through the main surfaces of heat exchanger 1 (the two main surfaces on both sides of heat exchanger 1 along the axial direction x3), thus achieving heat exchange between the refrigerant and the external environment. When the refrigerant temperature in the refrigerant pipe is lower than the ambient temperature, heat from the external environment is transferred through heat exchanger 1 to the refrigerant pipe and then to the refrigerant, thus achieving heat exchange between the refrigerant and the external environment. Heat exchanger 1 mainly performs heat exchange through its main surfaces; therefore, during defrosting, water droplets or water films, etc., aggregates of water molecules 80 (such as...) Figure 16a , Figure 16b , Figure 16c , Figure 16d , Figure 17a , Figure 17b and Figure 17c (As shown) mainly exists on the two main surfaces of heat exchange plate 1, and the drainage efficiency of the main surface of heat exchange plate 1 directly affects the defrosting efficiency of heat exchange plate 1.

[0037] like Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 and Figure 6 As shown, in some embodiments, the heat exchange plate 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 and the first direction x1 of the through hole 40, and the first flat portion 10 and the second flat portion 20 are spaced apart along the second direction x2. The intermediate connecting portion 30 connects the second flat portion 20 and the first flat portion 10. In this way, the main surface of the heat exchange plate 1 is divided along the second direction x2 into multiple parts 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, a cylindrical portion 50 is provided on the first flat portion 10 along the edge of the through hole 40. The cylindrical portion 50 protrudes along the axial direction x3 toward one side of the first flat portion 10. Specifically, as shown... Figure 7 , Figure 8 as well as Figure 9 As shown, the cylindrical portion 50 protrudes from the first flat portion 10 along the axial direction x3 toward the first side LB1 of the heat exchange plate 1. The cylindrical portion serves as an extension of the through hole 40, which increases the contact area between the refrigerant pipe and the heat exchange plate 1, thereby improving the heat exchange efficiency between the refrigerant pipe and the heat exchange plate 1.

[0039] Of course, in some embodiments, the second flat portion 20 can also be arranged on both sides of the first flat portion 10 along the second direction x2, and the corresponding intermediate connecting portion 30 can also be arranged on both sides of the second flat portion 20 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 arranged opposite to each other along the axial direction x3, wherein the first side LB1 of the heat exchange fin 1 is defined as a side on which the cylindrical portion 50 is arranged protruding 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 a side opposite to 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 relative 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 parallel to the direction of gravity, and the second direction x2 is parallel to the horizontal plane. In this way, the water molecule collection 80 on the heat exchange fin 1 can be guided to flow along the first flat portion 10, the second flat portion 20, and the intermediate connecting portion 30, respectively, under the action of gravity, and flow out of the main surface of the heat exchange fin 1, thereby effectively improving the 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. In this way, the heat exchange efficiency of the heat exchange fin 1 can be effectively improved, and the flow direction of the heat exchange gas can be made 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, such an arrangement can also reduce the flow resistance of the water molecule collection 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 collection 80 condensed on the main surface of the heat exchange fin 1 is 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 guiding effect. The three parts of the water molecule collection 80 can regularly flow 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 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, the second flat portion 20 is a continuous flat sheet structure along the entire length of the heat exchange plate 1 along the first direction x1. That is, the second flat portion 20 is a continuously extending flat sheet structure along the first direction x1, and no blocking structures, such as grooves, channels, or protrusions, are provided in the section of the heat exchange plate 1 along the first direction x1 to divide the second flat portion 20 into two or more discontinuous parts. This makes the main surface of the second flat portion 20 a continuous main surface extending along the first direction x1, thereby 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 along the entire length of the heat exchange plate 1 along the first direction x1. That is, the first flat portion 10 is a continuously extending flat sheet structure along the first direction x1, and no blocking structures, such as grooves, channels, or protrusions, are provided in the section of the heat exchange plate 1 along the first direction x1, dividing the first flat portion 10 into two or more discontinuous parts along the first direction x1. 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 the intermediate connecting portion 30 extends in a continuous wavy shape along the first direction x1. Specifically, the intermediate connecting portion 30 is a continuous structure along the entire length range of the heat exchange plate 1 along the first direction x1, that is, the intermediate connecting portion 30 extends continuously along the first direction x1. No blocking structures, such as grooves, channels, protrusions, etc., are provided in the section of the heat exchange plate 1 along the first direction x1 to divide the intermediate connecting portion 30 into two or more discontinuous parts along the first direction x1. Furthermore, while the intermediate connecting portion 30 is configured to extend continuously along the first direction x1, it is also configured to extend periodically 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, that is, to extend in a wavy shape. The wavy shape of the intermediate connecting portion 30 can effectively improve the drainage efficiency of the intermediate connecting portion 30.

[0048] It should be noted that the reference plane P1 is the plane that passes through the axis z1 of the through hole 40 and is set 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, for example, the reference plane P2 or a reference plane parallel to the reference plane P2, at least one of the fifth dimension L2 of the first flat portion 10 along the second direction x2 and the fourth dimension L1 of the second flat portion 20 along the second direction x2 is greater than the dimension of the intermediate connecting portion 30 along the second direction x2, in other words, at least one of the fifth dimension L2 of the first flat portion 10 along the second direction x2 and the fourth dimension L1 of the second flat portion 20 along the second direction x2 is greater than the dimension of the intermediate connecting portion 30 along the second direction x2 in at least a partial section along the first direction x1 of the heat exchange fin.

[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. When a normal projection is made to 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, and it can be understood that the height difference between the first guide portion 301 and the first flat portion 10 along the axial direction x3 gradually increases in the direction from the first flat portion 10 to the intermediate connecting portion 30, or the height difference between the first guide portion 301 and the first flat portion 10 along the axial direction x3 gradually decreases in the direction from the intermediate connecting portion 30 to the first flat portion 10. Figure 4 , Figure 5 , Figure 6 , Figure 7 , Figure 8 and 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. When a normal projection is made to 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, and it can be understood that the height difference between the first guide portion 301 and the second flat portion 20 along the axial direction x3 gradually increases in the direction from the second flat portion 20 to the first flat portion 10, or the height difference between the first guide portion 301 and the second flat portion 20 along the axial direction x3 gradually decreases in the direction from the first flat portion 10 to the second flat portion 20.

[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 protrudingly 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 and Figure 12 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 protrudingly 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.

[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 second 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 act 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 within a cross-section perpendicular to the tangent of the third edge 101, the main surface of the second guide portion 302 and the main surface of the first flat portion 10 both have interconnected cross-sectional lines on the first side LB1 or the second side LB2. The included 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. The included angle 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 complementary acute and obtuse angles. In this embodiment of the application, Figure 12 The included angle J4 is the acute angle between the cross-sectional lines of the main surface of the second guide portion 302 on the second side LB2 and the main surface of the first flat portion 10. It should be understood that, in the embodiments of this application, the heat exchange plate 1 is a plate structure with uniform thickness, and the included angles between the cross-sectional lines of the main surface of the second guide portion 302 on the first side LB1 and the second side LB2 and the main surface of the first flat portion 10 are equal.

[0074] It should be noted that the third edge 101 has multiple tangents along its length direction. The reference plane P2 is a reference plane perpendicular to one of the tangents of the third edge 101. In any embodiment of this paper, the positional relationship between the first guide portion 301 and the first flat portion 10 is illustrated by taking the angle J4 between the first guide portion 301 and the first flat portion 10 in the reference plane P2 as an example.

[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, it will increase the wind resistance of the heat exchange plate 1; if the height difference H4 is too low, it will affect the flow of 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 makes the height difference H4 setting more reasonable, allowing the water molecule aggregate 80 to flow better in the channel-like structure, thereby improving the drainage efficiency of the first flat portion 10 and effectively reducing the wind resistance of the heat exchange plate 1, thus 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 parallel and coplanar.

[0076] like Figure 15As shown, in some embodiments, the first spacing portion 303 has a height difference H7 with the first flat portion 10 along the axial direction x3, wherein in the present 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 the present embodiment, the height difference H7 of the first spacing portion 303 with the first flat portion 10 along the axial direction x3 is equal to the height difference H4 between the second guide portion 302 and the first flat portion 10 along the axial direction x3. The first spacing portion 303 comprises an overlapping region 305 which overlaps with the cylindrical portion 50 when viewed along the second direction x2, and at least within the overlapping region 305, the height difference H7 of the first spacing portion 303 with the first flat portion 10 along the axial direction x3 is less than the height difference H3 of the cylindrical portion 50 with the first flat portion 10 along the axial direction x3. In this way, the blocking of the cylindrical portion 50 by the overlapping region 305 can be effectively reduced without affecting the function of the first spacing portion 303 too much, thereby reducing the wind resistance on the circumferential side of the cylindrical portion 50, so that the heat exchange gas can flow smoothly along the second direction x2 through the circumferential side of the cylindrical portion 50, thereby effectively improving the heat exchange efficiency of the cold pipe. In some embodiments, the height difference H3 is also the first dimension of the cylindrical portion 50 along the axial direction x3.

[0077] For example, as shown in FIG. 1, the first spacing portion 303 comprises a first spacing portion 303a and a second spacing portion 303b, and the first spacing portion 303a and the second spacing portion 303b are arranged along the first direction x1. Figure 15 As shown, in some embodiments, along the first direction x1, the height difference H7 of each region of the first spacing portion 303 with the first flat portion 10 can be set to be unequal, and the height difference H7 of the first spacing portion 303 in the overlapping region 305 with the first flat portion 10 is less than the height difference H7 of the first spacing portion 303 in other regions with the first flat portion 10, and the height difference H7 of the first spacing portion 303 in the overlapping region 305 with the first flat portion 10 is less 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 spacing portion 303 with the first flat portion 10 can also be set to be equal, and the height difference H7 of each region of the first spacing portion 303 with the first flat portion 10 is less than the height difference H3.

[0078] For example, as shown in FIG. 1, the first spacing portion 303 comprises a first spacing portion 303a and a second spacing portion 303b, and the first spacing portion 303a and the second spacing portion 303b are arranged along the first direction x1. Figure 15 As shown, in some embodiments, the minimum value of the height difference H7 of the first spacing portion 303 with the first flat portion 10 along the axial direction x3 is located within the overlapping region 305, in other words, the lowest point G of the first spacing portion 303 relative to the first flat portion 10 along the axial direction x3 is located within the overlapping region 305, and the first spacing portion 303 has a height difference between the highest point of the first spacing portion 303 along the axial direction x3 (i.e. the highest point of the first spacing portion 303 relative to the first flat portion 10 along the axial direction x3) and the lowest point G of the first spacing portion 303 along the axial direction x3 (i.e. the lowest point of the first spacing portion 303 relative to the first flat portion 10 along the axial direction x3), and the height difference is less than one third of the height difference H3.

[0079] For example, as shown in FIG. 1, the first spacing portion 303 comprises a first spacing portion 303a and a second spacing portion 303b, and the first spacing portion 303a and the second spacing portion 303b are arranged along the first direction x1. Figure 15As 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.

[0080] 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 a first direction x1, and two portions of the second flat part 20 are arranged on both sides of the first flat part 10 along a second direction x2. Correspondingly, two portions of the first interval part 303 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 a first direction x1, and two portions of the second flat part 20 are arranged on both sides of the first flat part 10 along a second direction x2. Correspondingly, two portions of the first interval part 303 are arranged on both sides of the first flat part 10 along the second direction x2.

[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 a first direction x1, and two portions of the second flat part 20 are arranged on both sides of the first flat part 10 along a second direction x2. Correspondingly, two portions of the first interval part 303 are arranged on both sides of the first flat part 10 along the second direction x2. Figure 4 to Figure 12 As shown in FIG. 1, in some embodiments, the heat exchange sheet 1 further comprises a second flow guide part 60, wherein the second flow guide part 60 is connected with the second flat part 20, and the second flow guide part 60 is located on the side of the second flat part 20 away from the first flow guide part 60 along the second direction x2, in other words, the second flow guide part 60 is connected with the second edge 202, and the second edge 202 is a common connecting edge between the second flow guide part 60 and the second flat part 20. Wherein, the second flow guide part 60 is arranged obliquely relative to the second flat part 20.

[0082]

[0083] ​​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.

[0084] 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.

[0085] In addition, 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.

[0086] It can be understood that in the cross section perpendicular to the tangent 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 included angle J3 marked in the figure is the acute angle between the cross-sectional lines of the main surface of the second flow guide portion 60 and the main surface of the second flat portion 20 on the second side LB2. It should be understood that, in the embodiments of this application, the heat exchange plate 1 is a plate structure with uniform thickness, and the included angles between the cross-sectional lines of the main surface of the second flow guide portion 60 and the main surface of the second flat portion 20 on the first side LB1 and the second side LB2 are equal.

[0087] It should be noted that the second edge 202 has multiple tangents along its length direction. 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 positional relationship between the second guide portion 60 and the second flat portion 20 is illustrated by taking the included angle J3 between the second guide portion 60 and the second flat portion 20 in the reference plane P2 as an example.

[0088] like Figure 11 and Figure 12 As shown, in some embodiments, the tilt direction of the second guide portion 60 relative to the first flat portion 10 is consistent with the tilt direction of the first guide portion 301 relative to the first flat portion 10. In other words, the tilt direction of the second guide portion 60 relative to the second flat portion 20 is inconsistent with the tilt direction of the first guide portion 301 relative to the second flat portion 20. More specifically, the first guide portion 301 protrudes towards the second side LB2 along the axial direction x3 relative to the first flat portion 10, and the second guide portion 60 protrudes towards 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 the same as the inclination direction of the first guide portion 301 relative to the first flat portion 10, and their inclination directions are both relative to the first flat portion 10 and towards the second side LB2. The first guide portion 301 protrudes towards the first side LB1 along the axial direction x3 relative to the second flat portion 20, and the second guide portion 60 protrudes towards 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 not the same as 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 also 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.

[0089] like Figure 11In 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, respectively, so that the projection of the first guide portion 301, the second guide portion 60, and the second flat portion 20 along the second direction x2 does not overlap with the projection of the cylindrical portion 5 along the second direction x2, thereby effectively reducing the obstruction of the first guide portion 301, the second guide portion 60, and the second flat portion 20 to the cylindrical portion 50, reducing the wind resistance on the circumferential side of the cylindrical portion 50, so that the heat exchange gas can smoothly flow along the second direction x2 through the circumferential side of the cylindrical portion 50, thereby effectively improving the heat exchange efficiency of the cold aisle tube. Moreover, the first flat portion 10 and the second flat portion 20 are arranged in parallel, and the first dimension (i.e., the height difference H3) of the cylindrical portion 50 along the axial direction x3 is greater than the sum of the second dimension (i.e., the height difference H1) of the first guide portion 301 along the axial direction x3 and the third dimension H2 of the second guide portion 60 along the axial direction x3.

[0090] As shown in Figure 10 In some embodiments, the inclination direction of the second 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 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 is arranged protruding along the axial direction x3 toward the second side LB2 relative to the first flat portion 10, and the second guide portion 60 is arranged protruding along the axial direction x3 toward the first side LB1 relative to the first flat portion 10, so that the inclination direction of the second 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 is arranged protruding along the axial direction x3 toward the first side LB1 relative to the second flat portion 20, and the second guide portion 60 is arranged protruding along the axial direction x3 toward the first side LB1 relative to the second flat portion 20, so that 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 the inclination direction of both is arranged toward the second side LB2 relative to the second flat portion 20. In this way, on the first side LB2, a channel-like structure extending along the first direction x1 can also be formed between the main surface of the first guide portion 301, the main surface of the second guide portion 60, 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 fin 1.

[0091] As shown in Figure 4 , Figure 5 and Figure 6 In at least a part of the section of the heat exchange fin 1 along the first direction x1 (also referred to as the gradual section of the heat exchange fin 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 arranged to gradually change along the first direction x1.

[0092] It is to be noted that the fifth 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 fourth 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.

[0093] 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 fourth 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.

[0094] 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.

[0095] The dimension L0 of the flat portion 70 along the second direction x2 is set to gradually change along the first direction x1. This can be understood as the dimension L0 of the flat portion 70 along the second direction x2 being 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. 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 flat portion 70 include at least one tapering region or a widening region along the first direction x1. The width dimension of the flat portion 70 will change along the dimension L0 of the flat portion 70 along the second direction x2. Therefore, 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 width dimension of the flat portion 70 gradually changes along the first direction x1, thereby making the main surface of the flat portion 70 have a gradually changing shape such as gradually narrowing, gradually widening, gradually narrowing then widening, gradually widening then narrowing, periodically gradually narrowing then widening, or periodically widening then narrowing. Thus, within the narrowing or widening region, the main surface of the flat portion 70 includes a narrowing plane region with a smaller width and a widening plane region with a larger width. The water molecule aggregate 80 located in the narrowing plane region experiences greater capillary action and is guided to the widening plane region under capillary action, thereby achieving the effect of water molecule aggregate 80 converging in the widening plane region. When the water molecule aggregate in the widening plane region accumulates to a certain mass, the water molecule aggregate 80 will accelerate and continue to flow 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, and effectively improving the defrosting efficiency of the heat exchange device.

[0096] Therefore, in at least a portion of the heat exchange plate 1 along the first direction x1 (also known as the gradual section of the heat exchange plate 1), the size L0 of the flat portion 70 along the second direction x2 is set to gradually change along the first direction x1, which enables the flat portion 70 to have 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.

[0097] like Figure 16a , Figure 16b , Figure 16c and Figure 16d As shown, the minimum value Lmin of the fourth dimension L1 of the second flat portion 20 along the second direction x2 is set to be less than or equal to 3mm. For example, the minimum value Lmin of the fourth dimension L1 can be an actual value less than or equal to 3mm, such as 3mm, 2.5mm, 2mm, 1.5mm or 1mm. This can effectively improve the aggregation effect of the water molecule aggregate 80 on the main surface of the flat portion 70 in the constricted plane area, thereby improving the drainage efficiency of the heat exchange plate 1 during the defrosting process and effectively improving the defrosting efficiency of the heat exchange device.

[0098] Specifically, as shown in Figure 16a and Figure 16b When the minimum value Lmin of the fourth dimension L1 is large, for example, the minimum value Lmin is greater than 3mm, the second flat portion 20 has a poor effect of gathering water molecule clusters 80 in the vicinity of the position where the fourth dimension L1 along the second direction x2 is located (i.e., the main surface of the second flat portion 20 is in the narrow plane area), the effect of gravity on the water molecule clusters 80 in the narrow plane area is greater than the effect of capillary force, so that the narrow plane area of the main surface of the second flat portion 20 cannot play a role in gathering the water molecule clusters 80, and the water molecule clusters 80 in each area along the second direction x2 flow along the first direction x1 under the action of gravity respectively and individually, so that the second flat portion 20 has a poor effect of guiding water flow.

[0099] As shown in Figure 16c and Figure 16d When the minimum value Lmin of the fourth dimension L1 along the second direction x2 of the second flat portion 20 is set to 1.5mm, the main surface of the second flat portion 20 has a good effect of gathering water molecule clusters 80 in the narrow plane area, the effect of capillary gravity on the water molecule clusters 80 in the narrow plane area of the main surface of the second flat portion 20 is less than the effect of capillary force, so that the narrow plane area of the main surface of the second flat portion 20 plays a role in gathering the water molecule clusters 80, and the water molecule clusters 80 in each area along the second direction x2 will be gathered under the action of capillary force towards the direction of the resultant force of capillary force, as shown in Figure 16c on the first side LB1, the water molecule clusters 80 on the second flat portion 20 are gathered under the action of capillary force towards the first guide portion 301 and guided 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 clusters 80 located on the main surface of the second flat portion 20 can be guided along the first direction x1 with 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 clusters 80 on the second flat portion 20 are gathered under the action of capillary force towards the second guide portion 60 and guided 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 clusters 80 located on the main surface of the second flat portion 20 can be guided along the first direction x1 with 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.

[0100] As shown in Figure 17a , Figure 17b and Figure 17c inFigure 17a The heat exchange fin structure shown in Figure 17b and Figure 17c is completely different from the structure of Figure 17a The heat exchange fin shown in Figure 17b is a conventional flat fin structure, Figure 17c and Figure 2 The heat exchange fin shown in Figure 17b Two different embodiments of the heat exchange fin 1 are shown in Figure 17c In the first embodiment, the minimum value of the fourth dimension L1 of the second flat portion 20 along the second direction x2 is set to 2.5 mm, and in the second embodiment, the minimum value of the fourth dimension L1 of the second flat portion 20 along the second direction x2 is set to 1.5 mm. The test results obtained under the same environmental conditions and the same time show that Figure 17a The heat exchange fin shown in Figure 17b and Figure 17c has a much poorer drainage efficiency than the heat exchange fin shown in Figure 17c The heat exchange fin shown in Figure 17b has a better drainage efficiency than the heat exchange fin shown in Therefore, setting the fourth dimension L1 of the second flat portion 20 along the second direction x2 to gradually change along the first direction x1, and the minimum value of the fourth dimension L1 being less than or equal to 3 mm, 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.

[0101] Optionally, the minimum value Lmin of the fourth dimension L1 of the second flat portion 20 along the second direction x2 is set to be greater than or equal to 1 mm, that is, in the embodiments of the present application, the minimum value Lmin of the fourth dimension L1 is not less than 1 mm. Such a setting can ensure that the capillary action of the water molecule assembly 80 flowing to the necked flat area is not too large, so that the width dimension of the necked flat area meets the convergence effect of the water molecule assembly 80 while not affecting the flowability of the water molecule assembly 80 along the first direction x1.

[0102] It should be noted that in some embodiments, within a certain section along the first direction x1, the flat portion 70 is provided with a groove, a through hole 40 or a flow dividing portion 103, etc. The dividing portion separates the major surface of the flat portion 70 into multiple discontinuous surfaces along the second direction x2, for example, Figure 6 In the embodiments, the minimum value of the fifth dimension L2 of the first flat portion 10 is provided with a flow dividing portion 103, which separates the first flat portion 10 into two flow dividing areas arranged along the second direction x2. The major surface of the first flat portion 10 includes two parts arranged along the second direction x2, i.e., the major surfaces of the two flow dividing areas. For another example, Figure 4 , Figure 5 and Figure 6In the shown embodiment, the first flat portion 10 is provided with a through hole 40 at the position of the maximum value of the fifth dimension L2 of the first flat portion 10 in the second direction x2, and the through hole 40 separates the first flat portion 10 into two portions discontinuous in the second direction x2 and arranged in the second direction x2.

[0103] In some embodiments, in the gradual change section of the heat exchange fin 1, the ratio of the maximum value of the fourth dimension L1 of the second flat portion 20 in the second direction x2 to the minimum value of the fourth dimension L1 is greater than or equal to 3 and less than or equal to 20, so that the gradual change trend of the main surface of the second flat portion 20 is more obvious, so that the capillary action on the water molecule assembly 80 of the narrow flat section is significantly greater than the capillary action on the water molecule assembly 80 of the wide flat section, and the effect of the narrow flat section draining to the wide flat section is more obvious, thereby effectively improving the drainage efficiency of the heat exchange fin 1 in the defrosting process, thereby effectively improving the defrosting efficiency of the heat exchange device.

[0104] As shown in Figure 4 , Figure 5 and Figure 6 , in some embodiments, in the gradual change section of the heat exchange fin 1, the fifth dimension L2 of the first flat portion 10 in the second direction x2 and the fourth dimension L1 of the second flat portion 20 in the second direction x2 are gradually changed in the first direction x1, so that the drainage efficiency of the heat exchange fin 1 can be effectively improved, thereby effectively improving the defrosting efficiency of the heat exchange device.

[0105] For example, as shown in Figure 4 and Figure 6 , between the two adjacent reference planes P2, the fifth dimension L2 of the first flat portion 10 in the second direction x2 is gradually changed in the first direction x1 by first decreasing and then increasing, and the fourth dimension L1 of the second flat portion 20 in the second direction x2 is gradually changed in the first direction x1 by first increasing and then decreasing.

[0106] For example, as shown in Figure 4 , Figure 5 and Figure 6 , the second flat portion 20 includes a first edge 201 and a second edge 202, wherein the first edge 201 is curved in the first direction x1, so that the fourth dimension L1 of the second flat portion 20 in the second direction x2 is gradually changed in the first direction x1 at least in the gradual change section of the heat exchange fin 1. Specifically, as shown in Figure 4 , Figure 5 and Figure 6 , between the two adjacent reference planes P2, the second edge 202 is arranged in a straight line in the first direction x1, and the first edge 201 is arranged in a curved shape by first gradually approaching the second edge 202 and then gradually moving away from the second edge 202, so that the fourth dimension L1 of the second flat portion 20 in the second direction x2 is arranged in the first direction x1 by first decreasing and then increasing.

[0107] 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, so that the fifth dimension L2 of the first flat portion 10 along the second direction x2 is arranged to gradually change along the first direction x1 at least within the gradual change section of the heat exchange fin 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, the two third edges 101 are symmetrically arranged with respect to the reference plane P1, and the two third edges 101 are not connected to each other. Between the 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 along the first direction x1 along the second direction x2, so that the fifth 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 parts of third edges 101 respectively located on two sides of the reference plane P1, and the two parts of third edges 101 are symmetrically arranged with respect to the reference plane P1. Between the two adjacent reference planes P2, the two parts of third edges 101 are arranged to be curved along the first direction x1, and the two parts of third edges 101 are arranged to gradually approach and then gradually move away along the first direction x1 along the second direction x2, so that the fifth 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.

[0108] As shown in Figure 4 , Figure 5 and Figure 6 , in some embodiments, the dimension 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, 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.

[0109] Specifically, as shown in Figure 4 , Figure 5 and Figure 6 , in the entire section of the length range of the heat exchange fin 1 along the first direction x1, the fifth dimension L2 of the first flat portion 10 along the second direction x2 and the fourth dimension L1 of the second flat portion 20 along the second direction x2 are both arranged to be continuously and periodically gradually changed 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.

[0110] As shown in Figure 4 ,Figure 5 and Figure 6 As shown, in some embodiments, the fifth dimension L2 of the first flat portion 10 along the second direction x2 and the fourth dimension L1 of the second flat portion 20 along the second direction x2 are arranged in a staggered manner along the first direction x1. Specifically, the minimum value of the fourth dimension L1 of the second flat portion 20 along the second direction x2 is flush with the center of the through hole 40, the maximum value of the fourth dimension L1 of the second flat portion 20 along the second direction x2 is located between two through holes 40, the minimum value of the fifth dimension L2 of the first flat portion 10 along the second direction x2 is located between two adjacent through holes 40, and the maximum value of the fifth dimension L2 of the first flat portion 10 along the second direction x2 is flush with the center of the through hole 40, thus making the fourth dimension L1 of the second flat portion 20 along the second direction x2... The minimum value of dimension L1 is offset from the minimum value of the fifth dimension L2 of the first flat portion 10 along the second direction x2, and the maximum value of the fourth dimension L1 of the second flat portion 20 along the second direction x2 is offset from the maximum value of the fifth dimension L2 of the first flat portion 10 along the second direction x2. This results in the fifth dimension L2 of the first flat portion 10 along the second direction x2 and the fourth dimension L1 of the second flat portion 20 along the second direction x2 being offset along the first direction x1. Based on this, the space utilization rate of the heat exchange plate 1 can be effectively improved.

[0111] like Figure 6 and Figure 9As shown, in some embodiments, the first flat portion 10 is provided with a shunt portion 103 at the position of the minimum value of the fifth dimension L2 of the first flat portion 10 along the second direction x2, specifically, the shunt portion 103 penetrates a reference plane at the position of the minimum value of the fifth 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 shunt portion 103 separates the first flat portion 10 into at least two shunt zones arranged at intervals along the second direction x2. Specifically, on the first side LB1, the shunt portion 103 is recessed relative to the first flat portion 10 along the axial direction x3, that is, in a groove shape, and the shunt portion 103 can have a recessed flow guiding effect on the two shunt zones, so as to accelerate the flow speed of the water molecule assembly 80 at the position of the minimum value of the fifth 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 fifth 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 fifth 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 shunt portion 103 is protruded relative to the first flat portion 10 along the axial direction x3, and the shunt portion 103 can divide the position of the minimum value of the dimension L2 of the first flat portion 10 along the second direction x2 into two smaller shunt zones, so that on the second side LB2, the water molecule assembly 80 at the position of the minimum value of the fifth 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 fifth dimension L2 along the second direction x2 is greater than 2.5 mm.

[0112] In some embodiments, the minimum value of the dimension of the two shunt zones along the second direction x2 is greater than or equal to 1 mm and less than or equal to 3 mm, and in this way, the convergence effect of the shunt zones on the water molecule assembly 80 can be effectively improved while ensuring the flowability of the water molecule assembly 80 flowing on the shunt zones along the first direction x1.

[0113] In some embodiments, the ratio of the first extension dimension of the shunt portion 103 along the first direction x1 to the second extension dimension of the shunt portion 103 along the second direction x2 is greater than 5, and in this way, the forming difficulty of the shunt portion 103 can be reduced, thereby improving the processing convenience of the heat exchange fin 1.

[0114] In some embodiments, as Figure 18 , Figure 19 and Figure 20As shown, the surface material of the heat exchange fin 1 is arranged such that the contact angle θ of the heat exchange fin 1 with water is less than 90 degrees. Specifically, the surface of the heat exchange fin 1, i.e. the main surface of the heat exchange fin 1, is of a material such that the contact angle θ of the main surface with water is less than 90 degrees, so as to effectively improve the water drainage efficiency of the main surface of the heat exchange fin 1.

[0115] Specifically, as Figure 18 As shown, the contact angle θ refers to the tangent line of the gas-liquid interface made at the intersection of the gas, liquid (e.g. the water molecule assembly 80 in the embodiments of the present application) and solid, and the angle between the tangent line on the liquid side and the solid-liquid interface line is a measure of the degree of wetting. The contact angle θ of a liquid on the surface of a solid material, e.g. the contact angle θ of the water molecule assembly 80 in the embodiments of the present application on the main surface of the heat exchange fin 1, is an important parameter for measuring the wetting performance of the liquid on the surface of the material. Through the measurement of the contact angle θ, much information about the interaction of the solid-liquid and solid-gas interfaces of the surface of the material can be obtained. The contact angle θ measurement technology can not only be used to characterize the surface performance of the material, but also has important applications in the fields of petroleum industry, flotation industry, medical materials, chip industry, low surface energy non-toxic antifouling materials, ink, cosmetics, pesticides, printing and dyeing, papermaking, fabric finishing, detergents, spraying, sewage treatment, etc. If the contact angle θ < 90°, the surface of the solid is hydrophilic, i.e. the liquid is easy to wet the solid, and the smaller the angle, the better the wettability; if the contact angle θ > 90°, the surface of the solid is hydrophobic, i.e. the liquid is not easy to wet the solid. In the water soaking comparison and consistency comparison experiments of the hydrophilic heat exchange fin 1 and the hydrophobic heat exchange fin 1 respectively, it is found through experiments that the water molecule assembly 80 condensed on the main surface of all the hydrophobic heat exchange fins 1 forms larger water droplets visible to the naked eye and adheres to the main surface of the hydrophobic heat exchange fin 1, while the water molecule assembly 80 on the main surface of the hydrophilic heat exchange fin 1 is in the form of a film and does not significantly adhere to the surface in the form of water droplets.

[0116] As 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.

[0117] In some embodiments, the heat exchange fin 1 is formed by an integrated molding process, such as a stamping process.

[0118] 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.

[0119] 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 by, The heat exchange sheet comprises a first flat portion, a second flat portion and a first flow guide portion, the first flat portion is provided with a plurality of through holes spaced in a first direction, a refrigerant pipe is arranged in the through hole, the first flat portion and the second flat portion are arranged in a second direction, the first flat portion and the second flat portion are spaced in an axial direction of the through hole, the first flow guide portion is connected between the first flat portion and the second flat portion, the first flow guide portion is arranged obliquely relative to the first flat portion and the second flat portion, and in a direction from the first flat portion to the second flat portion, the height difference between the first flow guide portion and the second flat portion in the axial direction decreases gradually.

2. The heat exchange device according to claim 1, wherein The heat exchange sheet comprises a second flow guide portion, the second flow guide portion is connected with the second flat portion, and in the second direction, the second flow guide portion is located on a side of the second flat portion away from the first flow guide portion, and the second flow guide portion is arranged obliquely relative to the second flat portion.

3. The heat exchange device according to claim 2, wherein The oblique direction of the second flow guide portion relative to the first flat portion is consistent with the oblique direction of the first flow guide portion relative to the first flat portion.

4. The heat exchange device according to claim 3, wherein The included angle between the second flow guide portion and the second flat portion is greater than or equal to 15° and less than or equal to 45°.

5. The heat exchange device according to claim 3, wherein The first flat portion comprises a cylindrical portion arranged along the hole edge of the through hole, and the second flat portion and the cylindrical portion are respectively located on two sides of the first flat portion in the axial direction.

6. The heat exchange device according to claim 5, wherein In the axial direction, the first size of the cylindrical portion is greater than the sum of the second size of the first flow guide portion and the third size of the second flow guide portion.

7. The heat exchange device according to claim 3 or 4, characterized by The included angle between the first flow guide portion and the second flat portion is greater than or equal to 15° and less than or equal to 45°.

8. The heat exchange device according to claim 1, wherein The first flat portion and the second flat portion are arranged in parallel.

9. The heat exchange device according to claim 1, wherein The second flat portion continuously extends in the first direction.

10. The heat exchange device of claim 1, wherein The first flat portion, the second flat portion and the first flow guide portion are symmetrically arranged with respect to a first reference plane, wherein the first reference plane passes through the axis of the through hole and is parallel to the first direction.

11. The heat exchange device according to claim 1, wherein On one side of the first reference plane, at least part of the second flat portion in the fourth size in the second direction changes in the first direction in the form of first gradually increasing and then gradually decreasing or first gradually decreasing and then gradually increasing, wherein the first reference plane passes through the axis of the through hole and is parallel to the first direction.

12. The heat exchange device according to claim 11, wherein In the first direction, the position where the minimum value of the fourth size is located is flush with the axis of the through hole.

13. The heat exchange device of claim 12, wherein, The first flat portion continuously extends in the first direction, and at least part of the first flat portion in the fifth size in the second direction changes in the first direction in the form of first gradually increasing and then gradually decreasing or first gradually decreasing and then gradually increasing.

14. The heat exchange device according to claim 13, wherein In the first direction, the position where the minimum value of the fifth size is located is located between two adjacent through holes.

15. The heat exchange device of claim 8, wherein, The first flat portion includes a plurality of sub-flat portions spaced apart along the first direction, and the through hole is arranged in the sub-flat portion. The first flow guide portion includes a plurality of sub-flow guide portions, and each sub-flow guide portion is arranged around the outer periphery of the corresponding sub-flat portion.

16. The heat exchange device of claim 15, wherein The sub-flat portion is arranged in a circular ring, and the maximum distance of the connecting edge of the sub-flow guide portion and the second flat portion in the first direction is greater than the maximum distance in the second direction.

17. The heat exchange device of claim 16, wherein In the first direction, the connecting edge is arranged in a sharp corner shape protruding away from the sub-flat portion.

18. A heat exchange device according to any one of claims 1-6 or 8-17, characterised in that The heat exchange device includes a gas conveying mechanism arranged to output heat exchange gas along the second direction towards the heat exchange sheet and the refrigerant pipe.

19. A heat exchange device according to any one of claims 1-6 or 8-17, characterised in that The surface material of the heat exchange sheet is arranged such that the contact angle between the heat exchange sheet and water is less than 90 degrees.

20. The heat exchange device according to any one of claims 1-6 or 8-17, characterized in that The heat exchange device includes a plurality of heat exchange sheets arranged along the axial direction, and the refrigerant pipe is sequentially arranged in 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.

21. An air conditioning device characterized by comprising: The heat exchange device includes any one of claims 1-6, 7, 8-17, 18, 19, or 20.

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