Heat exchange apparatus and air conditioning apparatus

Abstract

The present application provides a heat exchange apparatus and an air conditioning apparatus. The heat exchange apparatus comprises a heat exchange member and refrigerant pipes. The heat exchange member comprises a first flat portion, a second flat portion, and a first spacing portion. The first flat portion is provided with a plurality of through holes spaced apart in a first direction, and each refrigerant pipe penetrates through a through hole. The first flat portion and the second flat portion are respectively connected to two opposite sides of the first spacing portion in a second direction. The second flat portion and the first flat portion continuously extend in the first direction. The first spacing portion extends in a continuous wave shape in the first direction. The second direction intersects with both the axis of each through hole and the first direction. In this way, the defrosting efficiency of the heat exchange apparatus can be effectively improved.

Description

Heat exchanger and air conditioning unit

[0001] This application claims priority to Chinese Patent Application No. 202422616746.7, filed on October 28, 2024, entitled “Heat Exchanger and Air Conditioning Device”, which is incorporated herein by reference in its entirety.

[0002] This application also claims priority to Chinese Patent Application No. 202411518564.4, filed on October 28, 2024, entitled “Heat Exchanger and Air Conditioning Device”, which is incorporated herein by reference in its entirety. [Technical Field]

[0003] This application relates to the field of heat exchanger technology, and in particular to a heat exchanger and an air conditioning device. [Background Technology]

[0004] In air conditioning systems such as air conditioners, the refrigerant inside the indoor heat exchanger is at a high temperature, dissipating heat into the room, while the refrigerant inside the outdoor heat exchanger is at a low temperature, absorbing heat from the outside. When the outdoor air is cold and humid, water vapor in the air easily condenses on the heat exchange fins, forming condensate. If the temperature of the heat exchange fins is below the freezing point of water, this condensate will further condense into frost or ice. Therefore, when the air conditioning system is in heating mode, frost will form on the outdoor heat exchange fins, making it difficult for airflow to circulate across the surface of the fins and causing heat exchange to deteriorate. Therefore, it is necessary to defrost the outdoor heat exchange fins. Current defrosting technology mainly uses a heat pump system with reverse circulation to achieve this purpose.

[0005] The duration of the defrosting process in a heat exchanger is a crucial factor in evaluating the performance and comfort of a heat pump system. Improving the defrosting efficiency of the heat exchanger by accelerating the drainage of defrost or condensate (a collection of water molecules) and shortening the overall drainage process is a pressing technical challenge. [Summary of the Invention]

[0006] To solve the above-mentioned technical problems, the technical solution adopted in this application is 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 spacer portion. The first flat portion is provided with a plurality of through holes spaced apart along a first direction, and the refrigerant pipes pass through the through holes. The first flat portion and the second flat portion are respectively connected to opposite sides of the first spacer portion along a second direction. The second flat portion and the first flat portion extend continuously along the first direction. The first spacer portion extends continuously in a wavy shape along the first direction. The second direction intersects the axial direction of the through holes and the first direction, respectively.

[0007] The beneficial effects of the embodiments of this application are as follows: This application provides a heat exchange device, wherein the heat exchange device includes a heat exchange plate, the heat exchange plate includes a first flat portion, a second flat portion and a first spacer portion, the first flat portion and the second flat portion are respectively connected to opposite sides of the first spacer portion, so that the main surface of the heat exchange plate is divided into three smaller surface areas, which can effectively reduce the unit area of ​​the water film, thereby making the water film easier to dry, and thus effectively improving the defrosting efficiency of the heat exchange device. [Attached Image Description]

[0008] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0009] Figure 1 is a three-dimensional structural schematic diagram of the first embodiment of the heat exchanger of this application;

[0010] Figure 2 is a three-dimensional structural schematic diagram of the second embodiment of the heat exchanger of this application;

[0011] Figure 3 is a three-dimensional structural schematic diagram of the third embodiment of the heat exchanger of this application;

[0012] Figure 4 is a front view of the first side of the heat exchange plate shown in Figure 1 along the axial direction x3.

[0013] Figure 5 is a front view of the first side of the heat exchange plate shown in Figure 2 along the axial direction x3.

[0014] Figure 6 is a front view of the first side of the heat exchange plate shown in Figure 3 along the axial direction x3.

[0015] Figure 7 is a side view of the heat exchanger shown in Figure 1 along the first direction x1.

[0016] Figure 8 is a side view of the heat exchanger shown in Figure 2 along the first direction x1.

[0017] Figure 9 is a side view of the heat exchanger shown in Figure 3, viewed along the first direction x1.

[0018] Figure 10 is a partial cross-sectional schematic diagram of the heat exchanger plate shown in Figure 4 with reference plane P2 as the cross section;

[0019] Figure 11 is a partial cross-sectional schematic diagram of the heat exchanger plate shown in Figure 5 with reference plane P2 as the cross section;

[0020] Figure 12 is a partial cross-sectional schematic diagram of the heat exchanger plate shown in Figure 6 with reference plane P2 as the cross section;

[0021] Figure 13 is another partial cross-sectional schematic diagram of the heat exchange plate shown in Figure 6 with reference plane P2 as the cross section;

[0022] Figure 14 is a partial front view of the first side of the heat exchange plate shown in Figure 2 along the axial direction x3;

[0023] Figure 15 is a partial side view of the heat exchanger shown in Figure 3, viewed along the second direction x2.

[0024] Figure 16a is a schematic diagram of the guiding effect of the main surface of the first side LB1 on the water molecule aggregate when the minimum value of the third dimension of the second flat part along the second direction of the heat exchange plate shown in Figure 2 is set to be greater than 3 mm.

[0025] Figure 16b is a schematic diagram of the guiding effect of the main surface of the second side LB2 of the heat exchange plate shown in Figure 2 on the water molecule aggregate when the minimum value of the third dimension along the second direction of the second flat part is set to be greater than 3 mm.

[0026] Figure 16c is a schematic diagram of the guiding effect of the main surface of the first side LB1 on the water molecule aggregate when the minimum value of the third dimension of the second flat part along the second direction of the heat exchange plate shown in Figure 2 is set to 1.5 mm.

[0027] Figure 16d is a schematic diagram of the guiding effect of the main surface of the second side LB2 of the heat exchange plate shown in Figure 2 on the water molecule aggregate when the minimum value of the third dimension along the second direction of the second flat part is set to 1.5 mm.

[0028] Figure 17a is a schematic diagram of the test results of the main surfaces of the first side LB1 and the second side LB2 of a conventional flat plate heat exchanger on the flow guiding effect on water molecule aggregates.

[0029] Figure 17b is a schematic diagram of the test results of the main surfaces of the first side LB1 and the second side LB2 of the heat exchange plate shown in Figure 2, when the minimum value of the third dimension along the second direction of the second flat part is set to 2.5 mm, for the water molecule aggregate guiding effect.

[0030] Figure 17c is a schematic diagram of the test results of the main surfaces of the first side LB1 and the second side LB2 of the heat exchange plate shown in Figure 2, when the minimum value of the third dimension along the second direction of the second flat part is set to 1.5 mm, for the water molecule aggregate guiding effect.

[0031] Figure 18 is a schematic diagram showing the effect of the contact angle of the main surface of the heat exchange plate of the water molecule aggregate in any embodiment of this application;

[0032] Figure 19 is a schematic diagram of the defrosting experiment of the heat exchange device when the main surface material of the heat exchange plate of this application is a hydrophilic material;

[0033] Figure 20 is a schematic diagram of the defrosting experiment of the heat exchange device when the main surface material of the heat exchange plate of this application is a hydrophobic material.

Detailed Implementation Methods

[0034] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0035] The terms "first" and "second" in this application are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise expressly specified. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover exclusive inclusion. For example, a process, method, system, product, or apparatus that includes a series of steps or units is not limited to the steps or units listed, but may optionally include steps or units not listed, or may optionally include other steps or units inherent to such processes, methods, products, or apparatus.

[0036] As shown in Figures 1, 2, and 3, this application provides a heat exchange device applied to air conditioning devices, such as air conditioners. The heat exchange device includes a gas delivery mechanism, heat exchange plates 1, and multiple refrigerant pipes. Each heat exchange plate 1 has multiple through holes 40, and each refrigerant pipe passes through a corresponding through hole 40. The refrigerant pipes are used to circulate refrigerant fluid and can directly contact the heat exchange gas in the environment, thereby achieving heat exchange with the gas. Furthermore, the refrigerant pipes also pass through the through holes 40 to contact the heat exchange plates 1. Based on this, the refrigerant pipes and heat exchange plates 1 cooperate, increasing the contact area between the refrigerant pipes and the heat exchange gas in the environment, thus improving the heat exchange efficiency of the heat exchange device. Specifically, the refrigerant pipes cooperate and contact the heat exchange plates 1, thereby exchanging heat with the heat exchange plates 1, and indirectly exchanging heat with the heat exchange gas in the environment through the main surfaces of the heat exchange plates 1 on both sides along the axial direction x3. The gas delivery mechanism is used to output or drive the heat exchange gas in the environment to flow toward the heat exchange plate 1 and the refrigerant pipe, so as to accelerate the heat exchange efficiency between the heat exchange plate 1, the refrigerant pipe and the heat exchange gas, thereby improving the heat exchange efficiency of the heat exchange device.

[0037] As shown in Figures 1, 2, and 3, in some embodiments, through holes 40 are spaced apart along a first direction x1 on the heat exchange plate 1. The gas delivery mechanism is configured to output heat exchange gas towards the heat exchange plate 1 and the refrigerant pipe along an axial direction x3 perpendicular to the through holes 40 and a second direction x2 perpendicular to the first direction x1. Alternatively, the gas delivery mechanism is configured to drive heat exchange gas in the environment to flow towards the heat exchange plate 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 plate 1. The axial direction x3 is a direction parallel to the axis z1 of the through holes 40. The first direction x1 is the spacing direction of the multiple through holes 40 on the heat exchange plate 1. The second direction x2 is a direction that intersects the first direction x1 and the axial direction x3 respectively. In some embodiments described herein, the second direction x2 may intersect the first direction x1 and the axial direction x3 perpendicularly.

[0038] In some embodiments, the heat exchange device includes a plurality of heat exchange plates 1, wherein the heat exchange plates 1 are arranged side by side at intervals along the axial direction x3 of the through holes 40, and the refrigerant pipes are sequentially inserted through the plurality of through holes 40 along the axial direction x3, thereby improving the heat dissipation efficiency of the refrigerant pipes.

[0039] When the refrigerant temperature in the refrigerant pipe is higher than the ambient temperature, heat in the refrigerant is transferred to heat exchanger 1 through the refrigerant pipe, and then transferred to the external environment through the main surfaces of heat exchanger 1 (the two main surfaces of heat exchanger 1 on both sides along the axial direction x3), thus realizing 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 to the refrigerant pipe through heat exchanger 1 and then to the refrigerant, thus realizing heat exchange between the refrigerant and the external environment. Heat exchanger 1 mainly exchanges heat through its main surfaces. Therefore, during the defrosting process, water droplets or water films and other water molecule aggregates 80 (as shown in Figures 16a, 16b, 16c, 16d, 17a, 17b, and 17c) mainly exist on the two main surfaces of heat exchanger 1. The drainage efficiency of the main surfaces of heat exchanger 1 directly affects the defrosting efficiency of heat exchanger 1.

[0040] As shown in Figures 1, 2, 3, 4, 5, and 6, 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.

[0041] As shown in Figures 1, 2, 3, 4, 5 and 6, 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 in Figures 7, 8 and 9, the cylindrical portion 50 protrudes along the axial direction x3 toward the first side LB1 of the heat exchange plate 1 relative to the first flat portion 10. The cylindrical portion, as an extension of the through hole 40, can increase 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.

[0042] Of course, in some embodiments, the first flat portion 10 may also have a second flat portion 20 and a corresponding intermediate connecting portion 30 on both sides along the second direction x2.

[0043] It should be noted that the heat exchange plate 1 includes a first side LB1 and a second side LB2 disposed opposite to each other along the axial direction x3. The first side LB1 of the heat exchange plate 1 is defined as the side of the cylindrical portion 50 that protrudes relative to the first flat portion 10 along the axial direction x3, and the second side LB2 of the heat exchange plate 1 is defined as the 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 plate 1 is referred to as the front side of the heat exchange plate 1, and the main surface of the second side LB2 of the heat exchange plate 1 is referred to as the back side of the heat exchange plate 1.

[0044] In this embodiment, the first flat portion 10, the second flat portion 20, and the intermediate connecting portion 30 all extend along the first direction x1. The first direction x1 can be set to be inclined relative to the horizontal plane. Specifically, the first direction x1 can be set to be perpendicular to the horizontal plane, that is, the first direction x1 is parallel to the direction of gravity. The second direction x2 is parallel to the horizontal plane. This allows the water molecule aggregate 80 on the heat exchange plate 1 to be guided along the first flat portion 10, the second flat portion 20, and the intermediate connecting portion 30 under the action of gravity, and flow out of the main surface of the heat exchange plate 1, thereby effectively improving the drainage efficiency of the heat exchange plate 1, and thus effectively improving the defrosting efficiency of the heat exchange device. Furthermore, in some embodiments, the heat exchange gas flows along the second direction x2 toward the heat exchange plate 1 and the refrigerant pipe. This can effectively improve the heat exchange efficiency of the heat exchange plate 1, and also make the flow direction of the heat exchange gas perpendicular to the direction of gravity. During the defrosting process of the heat exchange device, if heat exchange gas is required to assist defrosting, this setting can also reduce the flow resistance of the heat exchange gas to the water molecule aggregate 80 flowing along the first direction x1, thereby increasing the defrosting efficiency of the heat exchange device.

[0045] During the defrosting process, the water molecule aggregate 80 condensed on the main surface of the heat exchange plate 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. On the one hand, the main surfaces of the first flat portion 10, the intermediate connecting portion 30, and the second flat portion 20 have a guiding effect. These three parts of water molecule aggregate 80 can flow regularly along the first direction x1 on the main surfaces of the first flat portion 10, the intermediate connecting portion 30, and the second flat portion 20, respectively, and be discharged from the main surface of the heat exchange plate 1, thereby effectively improving the drainage efficiency of the heat exchange plate 1, and thus effectively improving the defrosting efficiency of the heat exchange device.

[0046] On the other hand, the main surface of the heat exchanger 1 is divided into three smaller surface regions located in different spatial planes. This increases the number of regions with greater local capillary forces on the main surface of the heat exchanger 1. This allows the main surface of the heat exchanger 1 to exert a local aggregation effect on the water molecule aggregates 80 adhering to its surface through capillary action. In some embodiments, the first direction x1 can be set parallel to the direction of gravity. In this way, the local aggregation effect of the main surface of the heat exchanger 1 on the water molecule aggregates 80 can effectively increase the gravity of the water molecule aggregates 80, thereby accelerating the flow of the water molecule aggregates 80 along the first direction x1 and effectively improving the defrosting efficiency of the heat exchange device. Specifically, during the defrosting process, the water molecule aggregates 80 typically adhere to the main surface of the heat exchanger plate 1 in the form of a water film, dividing the main surface of the heat exchanger plate 1 into three smaller surface regions located in different spatial planes. This increases the local curvature of the main surface of the heat exchanger plate 1, resulting in multiple areas with strong local capillary forces on the main surface of the heat exchanger plate 1. For example, the area where the main surface of the first flat portion 10 and the main surface of the intermediate connecting portion 30 are connected, and the area 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 forces, the water molecule aggregates 80 adhering to the main surface of the heat exchanger plate 1 in the form of a water film are torn apart and converge towards the areas with strong capillary forces, forming water droplets with greater gravity, thereby accelerating their detachment and effectively improving the defrosting efficiency of the heat exchange device. Furthermore, most of the water molecule aggregates 80 converge into water droplets or streams under the action of capillary force in the above manner, and after detaching from the surface of the heat exchange plate 1 in the form of water droplets or streams, the remaining small portion continues to adhere to the main surface of the heat exchange plate 1 in a very thin water film structure due to the inertial force, viscosity force and tension of the water molecule aggregates 80 on the main surface of the heat exchange plate 1. Due to the action of capillary force, the water molecule aggregates 80 in the form of water film attached to the main surface of the heat exchange plate 1 are torn apart and converge into water droplets or streams with a smaller contact area with the main surface of the heat exchange plate 1. In this way, the area and weight of the water film remaining on the main surface of the heat exchange plate 1 due to the action of inertial force, viscosity force and tension can be effectively reduced, thereby effectively reducing the defrosting energy required for the defrosting process. Under the same defrosting energy, the heat exchange plate 1 of this application can effectively improve the defrosting efficiency of the heat exchange device compared with the existing heat exchange plates.

[0047] It should be noted that in the embodiments of this 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 that accounts for more than 80% or more, and the main surface is a flat plane.

[0048] As shown in Figures 4, 5, and 6, 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 along the length 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 continuously extending main surface along the first direction x1, thereby effectively improving the drainage efficiency of the second flat portion 20 along the first direction x1.

[0049] As shown in Figures 4 and 6, 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.

[0050] As shown in Figures 4 and 6, 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, wavy extension. The wavy arrangement of the intermediate connecting portion 30 can effectively improve the drainage efficiency of the intermediate connecting portion 30.

[0051] 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.

[0052] As shown in Figures 4, 5, and 6, in at least one reference plane perpendicular to the first direction x1, such as reference plane P2 or a reference plane parallel to reference plane P2, at least one of the first dimension L2 of the first flat portion 10 along the second direction x2 and the third dimension L1 of the second flat portion 20 along the second direction x2 is greater than the second dimension of the intermediate connecting portion 30 along the second direction x2. In other words, in at least a portion of the heat exchange plate along the first direction x1, at least one of the first dimension L2 of the first flat portion 10 along the second direction x2 and the third dimension L1 of the second flat portion 20 along the second direction x2 is greater than the second dimension of the intermediate connecting portion 30 along the second direction x2.

[0053] As shown in Figures 4, 5, 6, 7, 8, and 9, the second flat portion 20 includes a first edge 201, and the intermediate connecting portion 30 includes a first guide portion 301 connected to the first edge 201, with the first guide portion 301 inclined relative to the second flat portion 20. Projecting orthographically onto a projection plane perpendicular to the axial direction x3, the projections of the first guide portion 301 and the second flat portion 20 are spaced apart along a second direction x2. This can be understood as follows: from the second flat portion 20 to the first flat portion 10, the height difference between the first guide portion 301 and the second flat portion 20 along the axial direction x3 gradually increases; or 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.

[0054] More specifically, as shown in Figures 10, 11 and 12, the first guide portion 301 being inclined relative to the second flat portion 20 can be understood as the first guide portion 301 being protruding towards the first side LB1 along the axial direction x3 of the through hole 40 relative to the second flat portion 20, and the positional relationship between the first guide portion 301 and the second flat portion 20 being between perpendicular and parallel.

[0055] The first guide section 301 assists in guiding the water molecule aggregate 80 on the main surface of the second flat section 20, thereby accelerating the drainage efficiency of the second flat section 20. 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 first guide section 301 and the main surface of the second flat section 20, thereby effectively improving the drainage efficiency of the second flat section 20, and further effectively improving the drainage efficiency of the heat exchange plate 1.

[0056] The included angle J1 between the first guide section 301 and the second flat section 20 is greater than or equal to 15° and less than or equal to 45°. The included angle between the first guide section 301 and the second flat section 20 directly affects the curvature of the channel-like structure. The larger the included angle J1 between the first guide section 301 and the second flat section 20, the greater the curvature of the channel-like structure, which also makes the water molecule aggregate 80 flow better in the channel-like structure. However, at the same time, the larger the included angle J1 between the first guide section 301 and the second flat section 20, the greater the resistance of the first guide section 301 to the heat exchange gas blown towards the heat exchange plate 1 and the refrigerant pipe along the second direction x2 (that is, the larger the included angle between the first guide section 301 and the second guide section 302, the greater the wind resistance of the heat exchange plate 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 between 15° and 45°, for example, specific angle values ​​such as 15°, 30°, 40° or 45°. This makes the included angle J1 between the first guide portion 301 and the second flat portion 20 more reasonable, so that the water molecule aggregate 80 has better fluidity in the channel-like structure. This improves the drainage efficiency of the second flat portion 20 and also effectively reduces the wind resistance of the heat exchange plate 1, thereby ensuring the heat exchange efficiency of the heat exchange device.

[0057] Furthermore, 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 molding difficulty of the first guide portion 301 and thus effectively improves the processing convenience of the heat exchange plate 1.

[0058] It is understood that within a 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 both have interconnected cross-sectional lines on either 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-sectional lines of the main surfaces of the first guide portion 301 and the second flat portion 20 on either the first side LB1 or the second side LB2. The included angle between the cross-sectional lines of the main surfaces of the first guide portion 301 and the second flat portion 20 includes complementary acute and obtuse angles. In the embodiments of this application, the included angle J1 marked in Figures 10, 11, and 12 is the acute angle between the cross-sectional lines of the main surfaces of the first guide portion 301 and 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 angle between the cross-sectional lines of the main surface of the first guide portion 301 and the main surface of the second flat portion 20 on the first side LB1 and the second side LB2 is equal to that between them.

[0059] It should be noted that the first edge 201 has multiple tangents along its length direction. The reference plane P2 is a reference plane perpendicular to one of the tangents of the first edge 201. In any embodiment of this document, the positional relationship between the first guide portion 301 and the second flat portion 20 is illustrated by taking the angle J1 between the first guide portion 301 and the second flat portion 20 in the reference plane P2 as an example.

[0060] As shown in Figures 10, 11, and 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 plate 1; if the height difference H1 is too low, it will affect the flow of the water molecule aggregate 80 in the channel-like structure. Therefore, setting the maximum value of the height difference H1 to less than or equal to 0.7 mm makes the height difference H1 setting more reasonable, allowing the water molecule aggregate 80 to flow better in the channel-like structure. This improves the drainage efficiency of the second flat portion 20 while effectively reducing the air resistance of the heat exchange plate 1, thereby ensuring the heat exchange efficiency of the heat exchange device. It should be noted that in some embodiments, the height difference H1 is also the dimension of the first guide portion 301 along the axial direction x3.

[0061] As shown in Figures 10 and 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 inclined relative to the second flat portion 20. In other words, in the embodiments of this application, the first flat portion 10 and the second flat portion 20 are connected by the first guide portion 301, and the height difference between the first guide portion 301 and the second flat portion 20 gradually decreases along the axial direction x3 from the first flat portion 10 to the second flat portion 20. The distance between the first flat portion 10 and the second flat portion 20 is also 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 the first guide portion 301 protruding towards the second side LB2 along the axial direction x3 of the through hole 40 relative to the first flat portion 10, and the positional relationship between the first guide portion 301 and the first flat portion 10 is between perpendicular and parallel.

[0062] Thus, on the one hand, the first guide portion 301 plays an auxiliary guiding role for the first flat portion 10 and the second flat portion 20 respectively, thereby effectively improving the drainage efficiency of the first flat portion 10 and the second flat portion 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 portion 301 and the main surface of the first flat portion 10. 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 portion 301 and the main surface of the second flat portion 20, thereby effectively improving the drainage efficiency of the first flat portion 10 and the second flat portion 20, and thus effectively improving the drainage efficiency of the heat exchange plate 1.

[0063] On the other hand, the main surfaces of the first flat portion 10 and the second flat portion 20 are arranged in a gradient along the axial direction x3. The first guide portion 301 is connected between the first flat portion 10 and the second flat portion 20, so that the main surface of the first guide portion 301 can serve as a guide slope between the main surfaces of the first flat portion 10 and the second flat portion 20. This makes the main surfaces of the heat exchange plate 1 on the first side LB1 and the second side LB2 arranged in a stepped manner, thereby making the water molecule aggregate 80 have two flow modes on the main surfaces of the heat exchange plate 1 on the first side LB1 and the second side LB2, thus effectively improving the drainage efficiency of the heat exchange plate 1. More specifically, on the first side LB1, water molecule aggregates 80 flow along the first direction x1 on the main surface of the first guide portion 301, the main surface of the first flat portion 10, and the main surface of the second flat portion 20. Furthermore, a portion of the water molecule aggregates 80 on the main surface of the first flat portion 10 can also be diverted along the main surface of the first guide portion 301 to the main surface of the second flat portion 20. This reduces the amount of water stored on the main surface of the first flat portion 10 while allowing more water molecule aggregates 80 to converge on the second flat portion 20, thereby accelerating the flow rate of the water molecule aggregates 80 on the second flat portion 20 and effectively improving the drainage efficiency of the heat exchange plate 1. On the second side LB2, water molecule aggregates 80 flow along the first direction x1 on the main surface of the first guide portion 301, the main surface of the first flat portion 10, and the main surface of the second flat portion 20. Furthermore, a portion of the water molecule aggregates 80 on the main surface of the second flat portion 20 can also be diverted along the main surface of the first guide portion 301 to the main surface of the first flat portion 10. This reduces the amount of water stored on the main surface of the second flat portion 20 while allowing more water molecule aggregates 80 to converge on the first flat portion 10, thereby accelerating the flow rate of the water molecule aggregates 80 on the first flat portion 10 and effectively improving the drainage efficiency of the heat exchange plate 1.

[0064] As shown in Figures 10 and 11, in some embodiments, the first flat portion 10 and the second flat portion 20 are arranged parallel to each other, such that the included angle J2 between the first flat portion 10 and the first guide portion 301 and the included angle J1 between the second flat portion 20 and the first guide portion 301 are equal. It is understood that in a cross-section perpendicular to the tangent of the third edge 101, the main surfaces of the first guide portion 301 and the first flat portion 10 have interconnected cross-sectional lines on either the first side LB1 or the second side LB2. The included angle J2 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 surfaces of the first guide portion 301 and the first flat portion 10 on either the first side LB1 or the second side LB2. The included angle between the cross-sectional lines of the main surfaces of the first guide portion 301 and the first flat portion 10 includes complementary acute and obtuse angles. In this embodiment, the included angle J1 marked in Figures 10 and 11 is the acute angle between the cross-sectional lines of the main surface of the first guide portion 301 on the second side LB2 and the main surface of the first flat portion 10. It should be understood that in this embodiment, 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 first guide portion 301 on the first side LB1 and the main surface of the first flat portion 10 on the second side LB2 are equal.

[0065] 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 document, the positional relationship between the first guide portion 301 and the first flat portion 10 is illustrated by taking the angle J2 between the first guide portion 301 and the first flat portion 10 in the reference plane P2 as an example.

[0066] As shown in Figures 5 and 8, in some embodiments, the heat exchange plate 1 is a symmetrical 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 plate 1 along the second direction x2. The first flat portion 10, the second flat portion 20, and the first guide portion 301 are all symmetrically arranged with respect to the reference plane P1. The first flat portion 10 includes a plurality of sub-flat portions 102 spaced apart along the first direction x1, and the first guide portion 301 includes sub-guide portions 304 spaced apart along the first direction x1. 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 two adjacent 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 this embodiment, the first guiding section 301 includes a plurality of sub-guiding sections 304 spaced apart along a first direction x1. Each sub-guiding section 304 is arranged around a corresponding first flat section 10. Each sub-guiding section 304 includes two parts symmetrically arranged with respect to a reference plane P1 along a second direction x2. The two parts of the sub-guiding section 304 are connected between adjacent sub-flat sections 102 so that the two parts of the sub-guiding section 304 form a continuous sub-guiding section 304. Thus, on the first side LB1, the sub-flat section 102 and the sub-guiding section 304 protrude relative to the second flat section 20 along an axial direction x3. A portion of the water molecule aggregates 80 on the sub-flat section 102 can flow through the sub-guiding section 304 along both the first direction x1 and the second direction x2 to the second flat section 20, thereby effectively improving the drainage efficiency of the first flat section 10 and the second flat section 20. On the second side LB2, the sub-flat portion 102 and the sub-guiding portion 304 are recessed relative to the second flat portion 20 along the axial direction x3. A portion of the water molecule aggregates 80 on the second flat portion 20 can converge to the sub-flat portion 102 along the second direction x2 via the guidance of the sub-guiding portion 304, thereby accelerating the flow-guiding capacity of the sub-flat portion 102 along the first direction x1 and effectively improving the drainage efficiency of the first flat portion 10. It should be noted that the spatial structural features between the sub-guiding portion 304 and the second flat portion 20 and the first flat portion 10 are similar to the spatial structural features between the first guiding portion 301 and the second flat portion 20 and the first flat portion 10 described above, and will not be elaborated upon here.

[0067] As shown in Figures 5 and 14, in some embodiments, the sub-flat portion 102 is arranged in a ring shape. The sub-guide portion 304 is connected to the second flat portion 20, thus the sub-guide portion 304 and the second flat portion 20 share a common connecting edge. In the above embodiments, this connecting edge is also referred to as the first edge 201. Correspondingly, the sub-flat portion 102 is connected to the first flat portion 10, thus the sub-guide portion 304 and the first flat portion 10 share another common connecting edge. In some embodiments, this is also referred to as the third edge 101. Since the sub-flat portion 102 is arranged in a ring shape, the third edge 101 is circular. The maximum dimension L3 of the graphic outline enclosed by the first edge 201 in the first direction x1 (in some embodiments, the maximum dimension L3 is also referred to as the maximum distance of the first edge 201 in the first direction x1) is greater than the maximum dimension L4 in the second direction x2 (in some embodiments, the maximum dimension L4 is also referred to as the maximum distance of the first edge 201 in the second direction x2). Specifically, the graphic outline enclosed by the first edge 201 is elliptical in shape, wherein the position of the maximum dimension L4 of the graphic outline in the second direction x2 is flush with the center of the through hole 40, that is, the position of the maximum dimension L4 of the graphic outline in the second direction x2 is located within 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, and the position of the maximum dimension L3 of the graphic outline enclosed by the first edge 201 in the first direction x1 is... The sub-guide section 304 is positioned within the reference plane P1. On one side of the reference plane P1, the size of the sub-guide section 304 along the second direction x2 is gradually changed, decreasing in size and then widening along the first direction x1. Based on this, the capillary force of the sub-guide section 304 is greater in the smaller area along the second direction x2 than in the larger area. The smaller area of ​​the sub-guide section 304 along the second direction x2 can serve as a converging transition point for the water molecule aggregate 80. The water molecule aggregate 80 can converge in the smaller area of ​​the sub-guide section 304 along the second direction x2 due to capillary force and flow along the first direction x1 to the larger area of ​​the sub-guide section 304, thereby increasing the gravity of the water molecule aggregate 80 and accelerating its flow speed. This effectively enhances the guiding effect of the sub-guide section 304 on the water molecule aggregate 80.

[0068] As shown in Figures 5 and 14, in some embodiments, in the first direction x1, the first edge 201 is provided in the shape of a pointed protrusion of the back ion flat portion 102. This makes the force exerted by the end of the back ion flat portion 102 of the first edge 201 on the water molecule aggregate 80, such as tension or viscosity, smaller, making it easier for the water molecule aggregate 80 on the sub-guide portion 304 to flow to the second flat portion 20. In some embodiments, the first guide portion 301 in this embodiment is also referred to as the first flow guide portion. The sub-guide portion 304 is also referred to as the sub-flow guide portion.

[0069] As shown in Figures 4 and 7, in some embodiments, the heat exchange plate 1 is a symmetrical structure arranged symmetrically with respect to a reference plane P1. The first flat portion 10, the second flat portion 20, and the first guiding portion 301 are all symmetrically arranged with respect to the reference plane P1. The first flat portion 10 is a flat sheet structure that extends continuously along a first direction x1, and two portions of the second flat portion 20 are spaced apart on both sides of the first flat portion 10 along a second direction x2. Correspondingly, the first guiding portion 301 has two portions of the first guiding portion 301 spaced apart on both sides of the first flat portion 10 along the second direction x2, and these two portions of the first guiding portion 301 are spaced apart along the second direction x2. In some embodiments, the first guiding portion 301 in this embodiment is also referred to as the first flow guiding portion.

[0070] As shown in Figures 6, 9 and 12, in some embodiments, the intermediate connecting portion 30 further includes a second guiding portion 302 connected between the side of the first guiding portion 301 away from the second flat portion 20 and the first flat portion 10, and the second guiding portion 302 is inclined relative to the first flat portion 10.

[0071] Specifically, unlike the embodiments shown in Figures 4 and 5, in this embodiment, the intermediate connecting portion 30 includes a first guiding portion 301 and a second guiding portion 302 connected between the side of the first guiding portion 301 away from the second flat portion 20 and the first flat portion 10. The first guiding portion 301 and the second guiding portion 302 together form a first spacer portion 303 that protrudes or is recessed along the axial direction x3 toward the same side of the first flat portion 10 and the second flat portion 20.

[0072] The second guide portion 302 is inclined relative to the first flat portion 10. This can be understood as the second guide portion 302 protruding towards the first side LB1 along 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 vertical and parallel.

[0073] One end of the first guide portion 301 facing away from the second flat portion 20 is connected to one end of the second guide portion facing away from the first flat portion 10 to form a first spacer portion 303. On the first side LB1 of the heat exchange plate 1 along the axial direction x3 of the through hole 40, the first spacer portion 303 protrudes relative to the first flat portion 10 and the second flat portion 20 along the axial direction x3, and the first spacer portion 303 is gradually tapered along its protruding direction. The water molecule aggregates 80 on the main surface of the first spacer portion 303 can converge toward the first flat portion 10 and the second flat portion 20 respectively, thus effectively improving the drainage efficiency of the first flat portion 10 and the second flat portion 20. On the second side LB2, the first spacer portion 303 is recessed relative to the first flat portion 10 and the second flat portion 20 along the axial direction x3. In this way, the first spacer portion 303 guides a portion of the water molecule aggregates 80 from the first flat portion 10 and the second flat portion 20, thereby achieving the effect of accelerating drainage efficiency.

[0074] The second guide portion 302 assists in guiding the water molecule aggregate 80 on the main surface of the first flat portion 10, thereby accelerating the 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 drainage efficiency of the first flat portion 10, and further effectively improving the drainage efficiency of the heat exchange plate 1.

[0075] The angle J4 between the second guide section 302 and the first flat section 10 is greater than or equal to 15° and less than or equal to 45°. The angle J4 between the second guide section 302 and the first flat section 10 directly affects the curvature of the channel-like structure. The larger the angle J4 between the second guide section 302 and the first flat section 10, the greater the curvature of the channel-like structure, which also makes the water molecule aggregate 80 flow better in the channel-like structure. However, at the same time, the larger the angle J4 between the second guide section 302 and the first flat section 10, the greater the resistance of the second guide section 302 to the heat exchange gas blown towards the heat exchange plate 1 and the refrigerant pipe along the second direction x2 (that is, the larger the angle between the two second guide sections 302, the greater the wind resistance of the heat exchange plate 1), which affects 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 between 15° and 45°, for example, specific angle values ​​such as 15°, 30°, 40° or 45°. This makes the included angle between the second guide portion 302 and the first flat portion 10 more reasonable, so that the water molecule aggregate 80 has better flow in the channel-like structure. This improves the drainage efficiency of the first flat portion 10 and also effectively reduces the wind resistance of the heat exchange plate 1, thereby ensuring the heat exchange efficiency of the heat exchange plate 1.

[0076] As shown in Figures 6, 9, and 12, 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 have interconnected cross-sectional lines on either 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 either 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, the included angle J4 marked in Figure 12 is the acute 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 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 angle 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 is equal to each other.

[0077] 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.

[0078] As shown in Figure 13, 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. This improves the drainage efficiency of the first flat portion 10 while effectively reducing the wind resistance of the heat exchange plate 1, thereby ensuring the heat exchange efficiency of the heat exchange plate 1. It should be noted that in the embodiment of Figure 13, the first flat portion 10 and the second flat portion 20 are parallel and coplanar.

[0079] As shown in Figure 15, in some embodiments, the first spacing portion 303 has a height difference H7 with the first flat portion 10 along the axial direction x3. In this embodiment, the height difference H7 is determined by the height difference H4 between the second guide portion 302 and the first flat portion 10 along the axial direction x3. In other words, in this embodiment, the height difference H7 between the first spacing portion 303 and the first flat portion 10 is the same as the height difference H4 between the second guide portion 302 and the first flat portion 10 along the axial direction x3.

[0080] The first spacer 303 includes an overlapping region 305 that overlaps with the cylindrical portion 50 when viewed along the second direction x2. At least within the overlapping region 305, the height difference H7 between the first spacer 303 and the first flat portion 10 along the axial direction x3 is less than the height difference H3 between the cylindrical portion 50 and the first flat portion 10 along the axial direction x3. This effectively reduces the obstruction of the overlapping region 305 on the cylindrical portion 50 without significantly affecting the function of the first spacer 303, thereby reducing the wind resistance around the cylindrical portion 50 and allowing the heat exchange gas to flow smoothly along the second direction x2 through the periphery of the cylindrical portion 50, thus effectively improving the heat exchange efficiency of the cooling tube. In some embodiments, the height difference H3 is also the dimension of the cylindrical portion 50 along the axial direction x3.

[0081] For example, as shown in FIG15, in some embodiments, along the first direction x1, the height difference H7 of each region of the first spacing portion 303 relative to the first flat portion 10 can be set to be unequal. The height difference H7 of the first spacing portion 303 relative to the first flat portion 10 in the overlapping region 305 is less than the height difference H7 of the first spacing portion 303 relative to the first flat portion 10 in other regions, and the height difference H7 of the first spacing portion 303 relative to the first flat portion 10 in the overlapping region 305 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 relative to the first flat portion 10 can also be set to be equal, and the height difference H7 of each region of the first spacing portion 303 relative to the first flat portion 10 is less than the height difference H3.

[0082] As shown in Figure 15, in some embodiments, the minimum value of the height difference H7 between the first spacing portion 303 and 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 along the axial direction x3 relative to the first flat portion 10 is located within the overlapping region 305. There is a height difference between the highest point of the first spacing portion 303 along the axial direction x3 (that is, the highest point of the first spacing portion 303 along the axial direction x3 relative to the first flat portion 10) and the lowest point G (that is, the lowest point of the first spacing portion 303 along the axial direction x3 relative to the first flat portion 10), and this height difference is less than one-third of the height difference H3.

[0083] Specifically, as shown in Figure 15, the height difference between the highest point and the lowest point G of the first interval portion 303 along the axial x3 can be understood as the difference between the height difference H6 of the highest point of the first interval portion 303 along the axial x3 relative to the first flat portion 10 and the height difference H5 of the lowest point G of the first interval portion 303 along the axial x3 relative to the first flat portion 10. This difference is less than one-third of the height difference H3, thus ensuring the heat dissipation efficiency of the heat exchange plate 1 while effectively improving the drainage efficiency of the heat exchange plate 1. It should be noted that the height difference H7 is defined as the general term for the height difference of the first interval portion 303 along the axial x3 relative to the first flat portion 10, the height difference H6 is defined as the height difference of the highest point of the first interval portion 303 along the axial x3 relative to the first flat portion 10, and the height difference H5 is defined as the height difference of the lowest point G of the first interval portion 303 along the axial x3 relative to the first flat portion 10.

[0084] As shown in Figures 6 and 9, in some embodiments, the heat exchange plate 1 is a symmetrical structure arranged symmetrically with respect to a reference plane P1. The first flat portion 10, the second flat portion 20, and the first spacer portion 303 are all symmetrically arranged with respect to the reference plane P1. The first flat portion 10 is a flat sheet structure that extends continuously along a first direction x1. Two portions of the second flat portion 20 are spaced apart on both sides of the first flat portion 10 along a second direction x2. Correspondingly, two portions of the first spacer portion 303 are spaced apart on both sides of the first flat portion 10 along the second direction x2.

[0085] As shown in Figures 4 to 12, in some embodiments, the heat exchange plate 1 further includes a second flow guide 60, wherein the second flow guide 60 is connected to the second flat portion 20 and, along the second direction x2, the second flow guide 60 is located on the side of the second flat portion 20 away from the first flow guide; in other words, the second flow guide 60 is connected to a second edge 202, which is a common connecting edge between the second flow guide 60 and the second flat portion 20. The second flow guide 60 is inclined relative to the second flat portion 20.

[0086] Specifically, the second guide portion 60 being inclined relative to the second flat portion 20 can be understood as the second guide portion 60 protruding towards one side of the second flat portion 20 along the axial direction x3 of the through hole 40, and the positional relationship between the second guide portion 60 and the second flat portion 20 being between vertical and parallel.

[0087] The second guide section 60 assists in guiding the water molecule aggregate 80 on the main surface of the second flat section 20, thereby accelerating the drainage efficiency of the second flat section 20. More specifically, along one side of the axial direction x3 of the through hole 40, a channel-like structure extending in the first direction x1 is formed between the main surface of the second guide section 60 and the main surface of the second flat section 20, thereby effectively improving the drainage efficiency of the second flat section 20, and thus effectively improving the drainage efficiency of the heat exchange plate 1.

[0088] The angle J3 between the second guide section 60 and the second flat section 20 is greater than or equal to 15° and less than or equal to 45°. The angle between the second guide section 60 and the second flat section 20 directly affects the curvature of the channel-like structure. The larger the angle J3 between the second guide section 60 and the second flat section 20, the greater the curvature of the channel-like structure, which also makes the water molecule aggregate 80 flow better in the channel-like structure. However, at the same time, the larger the angle between the second guide section 60 and the second flat section 20, the greater the resistance of the second guide section 60 to the heat exchange gas blown towards the heat exchange plate 1 and the refrigerant pipe along the second direction x2 (that is, the larger the angle between the second guide section 60 and the second guide section 302, the greater the wind resistance of the heat exchange plate 1), thus affecting the heat exchange efficiency of the heat exchange device. Therefore, the included angle J3 between the second guide section 60 and the second flat section 20 is set between 15° and 45°, for example, specific angle values ​​such as 15°, 30°, 40° or 45°. This makes the included angle J3 between the second guide section 60 and the second flat section 20 more reasonable, so that the water molecule aggregate 80 has better flow in the channel-like structure. This improves the drainage efficiency of the second flat section 20 and also effectively reduces the wind resistance of the heat exchange plate 1, thereby ensuring the heat exchange efficiency of the heat exchange device.

[0089] Furthermore, the included angle J3 between the second guide portion 60 and the second flat portion 20 is greater than or equal to 15° and less than or equal to 45°, which effectively reduces the molding difficulty of the second guide portion 60 and thus effectively improves the processing convenience of the heat exchange plate 1.

[0090] It is understood that within a cross-section perpendicular to the tangent of the second edge 202, the main surface of the second guide portion 60 and the main surface of the second flat portion 20 have interconnected cross-sectional lines on either the first side LB1 or the second side LB2. The included angle J3 between the second guide portion 60 and the second flat portion 20 is the acute angle formed between the cross-sectional lines of the main surface of the second guide portion 60 and the main surface of the second flat portion 20 on either the first side LB1 or the second side LB2. This included angles include complementary acute and obtuse angles. In this embodiment, the included angle J3 shown in Figures 10, 11, and 12 is the acute angle between the cross-sectional lines of the main surface of the second guide portion 60 and the main surface of the second flat portion 20 on the second side LB2. It should be understood that in this embodiment, 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 60 and the main surface of the second flat portion 20 on the first side LB1 and the second side LB2 are equal.

[0091] 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.

[0092] As shown in Figures 11 and 12, in some embodiments, the inclination direction of the second guide portion 60 relative to the first flat portion 10 is consistent with the inclination direction of the first guide portion 301 relative to the first flat portion 10. In other words, the inclination direction of the second guide portion 60 relative to the second flat portion 20 is inconsistent with the inclination direction of the first guide portion 301 relative to the second flat portion 20. More specifically, the first guide portion 301 protrudes 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.

[0093] As shown in Figure 11, in some embodiments, the second flat portion 20 and the cylindrical portion 50 are located on opposite sides of the first flat portion 10 along the axial direction x3. This ensures that the projections of the first guide portion 301, the second guide portion 60, and the second flat portion 20 along the second direction x2 do not overlap with the projection of the cylindrical portion 5 along the second direction x2. This effectively reduces the obstruction of the cylindrical portion 50 by the first guide portion 301, the second guide portion 60, and the second flat portion 20, thereby reducing the wind resistance around the cylindrical portion 50. This allows the heat exchange gas to flow smoothly along the second direction x2 through the periphery of the cylindrical portion 50, effectively improving the heat exchange efficiency of the cooling tube. Furthermore, the first flat portion 10 and the second flat portion 20 are arranged parallel to each other, and the dimension of the cylindrical portion 50 along the axial direction x3 (i.e., the height difference H3) is greater than the sum of the dimension of the first guide portion 301 along the axial direction x3 (i.e., the height difference H1) and the dimension H2 of the second guide portion 60 along the axial direction x3.

[0094] 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 not the same as 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 the same as the inclination direction of the first guide portion 301 relative to the second flat portion 20. More specifically, the first guide portion 301 protrudes axially x3 toward the second side LB2 relative to the first flat portion 10, and the second guide portion 60 protrudes axially x3 toward the first side LB1 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 not the same as the inclination direction of the first guide portion 301 relative to the first flat portion 10. The first guide portion 301 protrudes axially x3 toward the first side LB1 relative to the second flat portion 20, and the second flow guide portion 60 protrudes axially x3 toward the first side LB1 relative to the second flat portion 20. Therefore, the inclination direction of the second flow 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 their inclination directions are both relative to the second flat portion 20 toward the second side LB2. 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 flow 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 thus effectively improving the drainage efficiency of the heat exchange plate 1.

[0095] As shown in Figures 4, 5 and 6, in at least a portion of the heat exchange plate 1 along the first direction x1 (also referred to as the gradual section of the heat exchange plate 1), at least one of the first flat portion 10 and the second flat portion 20 is configured to gradually change in size along the second direction x2 along the first direction x1.

[0096] It should be noted that the first dimension L2 of the first flat portion 10 along the second direction x2 can be understood as the distance between the third edges 101 located on both sides of the reference plane P1 along the second direction x2. The third dimension L1 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 P1 along the second direction x2.

[0097] In some embodiments, the first flat portion 10 and the second flat portion 20 are arranged parallel to each other (that is, 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 both the first flat portion 10 and the second flat portion 20 are parallel to the second direction x2. The third dimension L1 of the second flat portion 20 is defined as the dimension by which the second flat portion 20 is parallel to its main surface and perpendicular to the first direction x1. In other embodiments, the first flat portion 10 and the second flat portion 20 may also be arranged at a certain angle.

[0098] It should be noted that, unless otherwise specified, in this document, the flat portion 70 refers to either the first flat portion 10 or the second flat portion 20.

[0099] 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.

[0100] 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.

[0101] As shown in Figures 16a, 16b, 16c and 16d, the minimum value Lmin of the third dimension L1 of the second flat portion 20 along the second direction x2 is set to be less than or equal to 3mm. For example, the minimum value Lmin of the third 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 water molecule aggregate 80 on the main surface of the second flat portion 20 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.

[0102] Specifically, as shown in Figures 16a and 16b, when the minimum value Lmin of the third dimension L1 is large, for example, when the minimum value Lmin is greater than 3 mm, the area near the location of the minimum value Lmin of the third dimension L1 along the second direction x2 of the second flat portion 20 (that is, the main surface of the second flat portion 20 in the constricted plane area) has a poor aggregation effect on the water molecule aggregate 80. The gravitational effect on the water molecule aggregate 80 in the constricted plane area is greater than the capillary effect. Thus, the constricted plane area cannot play a aggregation role on the water molecule aggregate 80. The water molecule aggregate 80 in each area along the second direction x2 flows separately along the first direction x1 under the action of gravity, resulting in a poor guiding effect of the second flat portion 20.

[0103] As shown in Figures 16c and 16d, when the minimum value Lmin of the third dimension L1 of the second flat portion 20 along the second direction x2 is set to 1.5mm, the main surface of the second flat portion 20 has a better aggregation effect on the water molecule aggregate 80 in the constricted plane region. The capillary gravity effect on the water molecule aggregate 80 in the constricted plane region of the main surface of the second flat portion 20 is less than the capillary force effect. Thus, the constricted plane region of the main surface of the second flat portion 20 plays a aggregation role on the water molecule aggregate 80, and the water molecule aggregates 80 in each region along the second direction x2 will converge towards the water molecule aggregate 80 under the action of capillary force. As shown in Figure 16c, the resultant force of capillary forces converges on the first side LB1. The water molecule aggregate 80 on the second flat portion 20 converges towards the first guiding portion 301 under the action of capillary force and flows along the first direction x1 to the wide-mouthed plane area of ​​the main surface of the second flat portion 20. This allows the water molecule aggregate 80 located on the main surface of the second flat portion 20 to flow along the first direction x with greater gravitational acceleration, thereby effectively accelerating the drainage efficiency of the second flat portion 20 and thus effectively improving the drainage efficiency of the heat exchange plate 1 during the defrosting process, thereby effectively improving the defrosting efficiency of the heat exchange device. As shown in Figure 16d, on the second side LB2, the water molecule aggregate 80 on the second flat portion 20 converges towards the second guide portion 60 under the action of capillary force and is guided along the first direction x1 to the wide-mouth plane area of ​​the main surface of the second flat portion 20. This allows the water molecule aggregate 80 on the main surface of the second flat portion 20 to be guided along the first direction x1 with greater gravitational acceleration, thereby effectively accelerating the drainage efficiency of the second flat portion 20 and thus effectively improving the drainage efficiency of the heat exchange plate 1 during the defrosting process, thereby effectively improving the defrosting efficiency of the heat exchange device.

[0104] As shown in Figures 17a, 17b, and 17c, the heat exchanger structure in Figure 17a is completely different from that in Figures 17b and 17c. The heat exchanger in Figure 17a is a conventional flat plate structure, while the heat exchangers in Figures 17b and 17c are two different embodiments of the heat exchanger 1 shown in Figure 2. In Figure 17b, the minimum value of the third dimension L1 of the second flat portion 20 along the second direction x2 is set to 2.5 mm; in Figure 17c, the minimum value of the third dimension L1 of the second flat portion 20 along the second direction x2 is set to 1.5 mm. Test results obtained under the same environmental conditions and for the same time show that the drainage efficiency of the heat exchanger shown in Figure 17a is significantly worse than that shown in Figures 17b and 17c. Furthermore, the drainage efficiency of the heat exchanger shown in Figure 17c is better than that of the heat exchanger shown in Figure 17b. Therefore, by setting the size of at least one of the first flat portion 10 and the second flat portion 20 along the second direction x2 to gradually change along the first direction x1, and the minimum value of this size (e.g., the first size L2 and / or the third size L1) is less than or equal to 3 mm, the drainage efficiency of the heat exchange plate 1 during the defrosting process can be effectively improved, thereby effectively improving the defrosting efficiency of the heat exchange device.

[0105] As shown in Figures 4, 5 and 6, in some embodiments, within the gradient section of the heat exchange plate 1, the first dimension L2 of the first flat portion 10 along the second direction x2 and the third dimension L1 of the second flat portion 20 along the second direction x2 are both set to gradually change along the first direction x1. This can effectively improve the drainage efficiency of the heat exchange plate 1, thereby effectively improving the defrosting efficiency of the heat exchange device.

[0106] For example, as shown in Figures 4 and 6, between two adjacent reference planes P2, the first flat portion 10 has a first dimension L2 along the second direction x2 that gradually decreases and then increases along the first direction x1, and the second flat portion 20 has a third dimension L1 along the second direction x2 that gradually increases and then decreases along the first direction x1.

[0107] For example, as shown in Figures 4, 5, and 6, the second flat portion 20 includes a first edge 201 and a second edge 202. The first edge 201 is curved along a first direction x1, such that the third dimension L1 of the second flat portion 20 along the second direction x2 gradually changes along the first direction x1, at least within the gradient section of the heat exchange plate 1. Specifically, as shown in Figures 4, 5, and 6, between two adjacent reference planes P2, the second edge 202 is straight along the first direction x1. The first edge 201 is curved, first gradually approaching the second edge 202 and then gradually moving away from it, such that the third dimension L1 of the second flat portion 20 along the second direction x2 gradually decreases and then increases along the first direction x1.

[0108] For example, as shown in Figures 4 and 6, the first flat portion 10 includes a third edge 101, wherein the third edge 101 is curved along the first direction x1. This configuration causes the first dimension L2 of the first flat portion 10 along the second direction x2 to gradually change along the first direction x1, at least within the gradient section of the heat exchange plate 1. Specifically, as shown in Figures 4 and 6, the first flat portion 10 includes two third edges 101 located on either side of a reference plane P1. The two third edges 101 are symmetrically arranged with respect to the reference plane P1 and are not connected to each other. Between two adjacent reference planes P2, the third edges 101 are curved along the first direction x1, and the two third edges 101 are arranged along the second direction x2 to gradually approach and then gradually move away from each other along the first direction x1. This configuration causes the first dimension L2 of the first flat portion 10 along the second direction x2 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 includes a third edge 101, wherein the third edge 101 includes two portions of the third edge 101 located on both sides of the reference plane P1, and the two portions of the third edge 101 are symmetrically arranged with respect to the reference plane P1. Between two adjacent reference planes P2, the two portions of the third edge 101 are configured to be curved along a first direction x1, and the two portions of the third edge 101 are configured along a second direction x2 to gradually approach each other and then gradually move away from each other along the first direction x1. This configuration causes the first dimension L2 of the first flat portion 10 along the second direction x2 to gradually increase and then gradually decrease along the first direction x1.

[0109] As shown in Figures 4, 5, and 6, in some embodiments, the dimension L0 of the flat portion 70 along the second direction x2 is arranged to change continuously and periodically along the first direction x1. Specifically, throughout the entire length range of the heat exchange plate 1 along the first direction x1, the dimension L0 of the flat portion 70 along the second direction x2 is arranged to change continuously and periodically, either gradually decreasing and then gradually increasing or gradually increasing and then gradually decreasing. This effectively improves the drainage efficiency of the heat exchange plate 1 during the defrosting process, thereby effectively improving the defrosting efficiency of the heat exchange device.

[0110] Specifically, as shown in Figures 4, 5 and 6, in the entire length range of the heat exchange plate 1 along the first direction x1, the first dimension L2 of the first flat portion 10 along the second direction x2 and the third dimension L1 of the second flat portion 20 along the second direction x2 are both set to change continuously and periodically along the first direction x1. This can effectively improve the drainage efficiency of the heat exchange plate 1, and thus effectively improve the defrosting efficiency of the heat exchange device.

[0111] As shown in Figures 4, 5, and 6, in some embodiments, the first dimension L2 of the first flat portion 10 along the second direction x2 and the third dimension L1 of the second flat portion 20 along the second direction x2 are arranged in a staggered manner along the first direction x1. Specifically, the minimum value of the third 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 third 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 first 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 first dimension L2 of the first flat portion 10 along the second direction x2 is flush with the center of the through hole 40. This makes the third dimension L1 of the second flat portion 20 along the second direction x2... The minimum value of L1 is offset from the minimum value of the first dimension L2 of the first flat portion 10 along the second direction x2, and the maximum value of the third dimension L1 of the second flat portion 20 along the second direction x2 is offset from the maximum value of the first dimension L2 of the first flat portion 10 along the second direction x2. This results in the first dimension L2 of the first flat portion 10 along the second direction x2 and the third dimension L1 of the second flat portion 20 along the second direction x2 being offset along the first direction x1. Based on this, the space utilization rate of the heat exchange plate 1 can be effectively improved.

[0112] As shown in Figures 6 and 9, in some embodiments, a diversion section 103 is provided at the location of the minimum value of the first dimension L2 of the first flat portion 10 along the second direction x2. Specifically, the diversion section 103 passes through the reference plane where the minimum value of the first dimension L2 of the first flat portion 10 along the second direction x2 is located, along the first direction x1. This reference plane is the same as the reference plane P2. The diversion section 103 divides the first flat portion 10 into at least two diversion zones spaced apart along the second direction x2. Specifically, on the first side LB1, the diversion section 103 is recessed relative to the first flat section 10 along the axial direction x3, that is, in the shape of a groove. The diversion section 103 can play a concave guiding effect on the two diversion areas, thereby accelerating the flow speed of the water molecule aggregate 80 at the position where the first dimension L2 of the first flat section 10 along the second direction x2 is the minimum value. This allows the water molecule aggregate 80 at the position where the first dimension L2 of the first flat section 10 along the second direction x2 is the minimum value to flow to the position where the first dimension L2 of the first flat section 10 along the second direction x2 is the maximum value more quickly, thereby effectively improving the drainage efficiency of the first flat section 10. On the second side LB2, the first spacer portion 303 is recessed relative to the first flat portion 10, and the diversion portion 103 protrudes relative to the first flat portion 10 along the axial direction x3. The diversion portion 103 can divide the position where the minimum value of the first dimension L2 of the first flat portion 10 along the second direction x2 is located into two smaller diversion zones. Thus, on the second side LB2, the water molecule aggregate 80 at the position where the minimum value of the first dimension L2 of the first flat portion 10 along the second direction x2 is located is more likely to converge towards the first spacer portion 303, thereby effectively improving the drainage efficiency of the first flat portion 10 and the first spacer portion 303. In this embodiment, the dimension of the first flat portion 10 at the position where the minimum value of the first dimension L2 along the second direction x2 is located is greater than 2.5 mm.

[0113] In some embodiments, the minimum value of the fourth dimension of the two diversion zones along the second direction x2 is greater than or equal to 1 mm and less than or equal to 3 mm. This setting can effectively improve the aggregation effect of the diversion zones on the water molecule aggregate 80, while also ensuring the fluidity of the water molecule aggregate 80 when it flows along the first direction x1 in the diversion zones.

[0114] In some embodiments, the ratio of the first extension dimension of the diversion section 103 along the first direction x1 to the second extension dimension of the diversion section 103 along the second direction x2 is greater than 5, which can reduce the molding difficulty of the diversion section 103 and thus improve the processing convenience of the heat exchange plate 1.

[0115] In some embodiments, as shown in Figures 18, 19, and 20, the surface material of the heat exchange plate 1 is configured such that the contact angle θ between the heat exchange plate 1 and the water is less than 90 degrees. Specifically, the surface of the heat exchange plate 1 is also known as the main surface of the heat exchange plate 1, wherein the material of the main surface of the heat exchange plate 1 is such that its contact angle θ with the water is less than 90 degrees, thereby effectively improving the drainage efficiency of the main surface of the heat exchange plate 1.

[0116] Specifically, as shown in Figure 18, the contact angle θ refers to the tangent line drawn at the gas-liquid interface at the intersection of the gas, liquid (e.g., the water molecule aggregate 80 in this embodiment), and solid phases. This tangent line forms the angle between the liquid side and the solid-liquid interface line, and is a measure of the degree of wetting. The contact angle θ of a liquid on a solid material surface, such as the contact angle θ of the water molecule aggregate 80 on the main surface of the heat exchange plate 1 in this embodiment, is an important parameter for measuring the wetting performance of the liquid on the material surface. Measuring the contact angle θ provides much information about the interactions between the solid-liquid and solid-gas interfaces on the material surface. The contact angle θ measurement technique can not only be used for common characterization of material surface properties, but also has important applications in the petroleum industry, flotation industry, pharmaceutical materials, chip industry, low surface energy non-toxic antifouling materials, inks, cosmetics, pesticides, printing and dyeing, papermaking, textile finishing, detergents, spraying, and wastewater treatment. If the contact angle θ < 90°, the solid surface is hydrophilic, meaning the liquid easily wets the solid; the smaller the angle, the better the wettability. If the contact angle θ > 90°, the solid surface is hydrophobic, meaning the liquid does not easily wet the solid. In water immersion comparison and consistency comparison experiments on hydrophilic and hydrophobic heat exchanger plates 1, it was found that the water molecule aggregates 80 condensed on the main surface of all hydrophobic heat exchanger plates 1 formed large, visible water droplets attached to the main surface, while the water molecule aggregates 80 on the main surface of the hydrophilic heat exchanger plate 1 formed a film, without obvious water droplet morphology.

[0117] As shown in Figures 18 and 19, in this embodiment of the application, the heat exchange device includes a plurality of heat exchange plates 1 spaced apart along the axial direction x3, wherein the spacing j1 between each heat exchange plate 1 is greater than or equal to 1.3 mm. For example, this spacing j1 can typically be an actual value greater than or equal to 1.3 mm. Defrosting and drainage were performed on both hydrophilic and hydrophobic heat exchange plates 1. Experiments showed that when the hydrophilic heat exchange plate 1 defrosted, the thickness of the water droplets formed by the water molecule aggregates 80 was less than the spacing j1 between the heat exchange plates 1, thus allowing the water molecule aggregates 80 on the main surface of the heat exchange plate 1 to be discharged in a film-like manner. However, for the hydrophobic heat exchange plate 1, the thickness of the water droplets formed by the water molecule aggregates 80 was greater than the spacing j1 between the heat exchange plates 1, eventually forming water bridges. Once formed, these water bridges are subject to significant capillary forces, hindering the discharge of the water molecule aggregates 80. Therefore, the material of the main surface of the heat exchange plate 1 is set such that its contact angle θ with water is less than 90 degrees. This makes the main surface of the heat exchange plate 1 hydrophilic. Compared with the hydrophobic heat exchange plate 1, the hydrophilic heat exchange plate 1 can effectively reduce the capillary force of the water molecule aggregate 80 between the two heat exchange plates 1, thereby effectively improving the drainage efficiency of the heat exchange device.

[0118] In some embodiments, the heat exchange plate 1 is formed by a one-piece molding process, such as stamping.

[0119] It is worth noting that the accompanying drawings are only for illustrating the structural and connection relationships of the product of this utility model, and do not limit the specific structural dimensions of the product of this utility model.

[0120] The above are merely embodiments of this utility model and do not limit the patent scope of this utility model. Any equivalent structural or procedural transformations made based on the description and drawings of this utility model, or direct or indirect applications in other related technical fields, are similarly included within the patent protection scope of this utility model.

Claims

1. A heat exchange device, wherein, The device includes heat exchange plates and refrigerant pipes. The heat exchange plates include a first flat portion, a second flat portion, and a first spacer portion. The first flat portion is provided with a plurality of through holes spaced apart along a first direction, and the refrigerant pipes pass through the through holes. The first flat portion and the second flat portion are respectively connected to opposite sides of the first spacer portion along a second direction. The second flat portion and the first flat portion extend continuously along the first direction. The first spacer portion extends continuously in a wavy shape along the first direction. The second direction intersects both the axial direction of the through hole and the first direction.

2. The heat exchange device according to claim 1, wherein, The first spacer portion is provided to protrude or be recessed along the axial direction.

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

4. The heat exchange device according to claim 1, wherein, In at least a portion of the heat exchange plate along the first direction, at least one of the first flat portion, the second flat portion, and the first spaced portion has its dimensions in the second direction arranged to gradually increase and then decrease or gradually decrease and then increase along the first direction.

5. The heat exchange device according to claim 4, wherein, In at least a portion of the heat exchange plate along the first direction, the first flat portion is configured to gradually increase and then decrease in a first dimension in the second direction, and the second flat portion is configured to gradually decrease and then increase in a third dimension in the second direction. or The first flat portion has a first dimension in the second direction that is first gradually decreasing and then gradually increasing, and the second flat portion has a third dimension in the second direction that is first gradually increasing and then gradually decreasing.

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

7. The heat exchange device according to claim 6, wherein, Between two adjacent through holes, the first flat portion is provided with a diversion portion that protrudes or is recessed relative to the first flat portion. The diversion portion is used to divide the first flat portion into two diversion zones located on both sides of the diversion portion along the second direction.

8. The heat exchange device according to claim 7, wherein, The diversion section passes through the third reference plane where the minimum value of the first dimension is located along the first direction, and the third reference plane is arranged parallel to the second reference plane.

9. The heat exchange device according to claim 7, wherein, The diversion section includes a first extension dimension parallel to the first direction and a second extension dimension parallel to the second direction, wherein the ratio of the maximum value of the first extension dimension to the maximum value of the second extension dimension is greater than 5.

10. The heat exchange device according to claim 7, wherein, The minimum value of the fourth dimension of the two diversion zones along the second direction is greater than or equal to 1 mm and less than or equal to 3 mm.

11. The heat exchange device according to claim 2, wherein, The first flat portion is provided with a cylindrical portion disposed along the edge of the through hole. The first spacer portion and the cylindrical portion protrude toward the same side of the first flat portion and the second flat portion. The first spacer portion includes an overlapping area that overlaps with the cylindrical portion when viewed along the second direction. At least in the overlapping area, the first height difference between the first spacer portion and the first flat portion along the axial direction is less than the second height difference between the cylindrical portion and the first flat portion along the axial direction.

12. The heat exchange device according to claim 11, wherein, The minimum value of the first height difference is located within the overlapping area, and there is a third height difference between the highest and lowest points of the first interval along the axial direction, the third height difference being less than one-third of the second height difference.

13. The heat exchange device according to claim 2, wherein, The first spacer is provided in a tapering shape along its protruding direction.

14. The heat exchange device according to any one of claims 1-13, wherein, The heat exchange device includes a gas delivery mechanism, which is configured to deliver heat exchange gas along the second direction toward the heat exchange plates and the refrigerant pipe.

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

16. The heat exchange device according to any one of claims 1-13, wherein, The heat exchange device includes a plurality of heat exchange plates, which are spaced apart along the axial direction. The refrigerant pipes are sequentially inserted into the plurality of through holes along the axial direction, and the outer surface of the refrigerant pipes is in contact with the hole wall of the through holes.

17. An air conditioning device, wherein, Includes the heat exchange device as described in any one of claims 1-13, 14, 15 or 16.

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