Heat exchange device and air conditioning system

Abstract

This invention relates to the field of refrigeration technology, and more particularly to a heat exchange device and an air conditioning system. The heat exchange device includes a shell assembly, a refrigerant assembly, and a water collection assembly. The shell assembly has an air inlet and an air outlet. Inside the shell assembly is an airflow chamber arranged along a first direction, which is connected to both the air inlet and the air outlet. The first direction is from the air inlet to the air outlet. The refrigerant assembly includes multiple refrigerant pipes passing through the airflow chamber. The water collection assembly includes a water collection structure and a drain outlet. The water collection structure is located on the inner wall of the airflow chamber and is used to collect condensate generated by the multiple refrigerant pipes and transport it to the drain outlet, which discharges the condensate. According to this embodiment, the heat exchange device has a water collection structure on the inner wall of the airflow chamber, which can effectively collect condensate generated during the cooling process of the refrigerant pipes, causing moisture to remain inside the airflow chamber, thereby improving the overall drainage efficiency of the heat exchange device.

Description

Technical Field

[0001] This invention relates to the field of refrigeration technology, and more particularly to a heat exchange device and an air conditioning system. Background Technology

[0002] The working principle of an intercooler in an air compressor is to cool the compressed air or gas between stages in a multi-stage compressor, thereby reducing its temperature and decreasing the temperature of the air entering the next stage compressor, thus improving compression efficiency. This cooling process directly affects the overall operating efficiency of the air compressor. Traditional intercoolers typically use a fan to cool the motor and the compressed air separately. To improve system reliability, segmented intercoolers have emerged in recent years, which direct a portion of the cooled compressed air to the motor for further cooling, and then return it for secondary cooling.

[0003] However, during the high-temperature, high-pressure air cooling process, a large amount of condensate is often generated, especially below the dew point temperature. If this condensate cannot be drained in time, it will accumulate inside the heat exchange core, leading to problems such as core corrosion and mold growth. This is particularly true for segmented intercoolers with relatively complex structures, where the upper and lower layers create relatively enclosed cooling zones, making condensate drainage even more difficult. This drainage problem not only affects the intercooler's cooling efficiency but also shortens its service life. Summary of the Invention

[0004] The objective of this invention is to at least solve the problem of how to improve the drainage efficiency of heat exchange devices. This objective is achieved through the following technical solution:

[0005] A first aspect of the present invention provides a heat exchange device comprising:

[0006] A housing assembly having an air inlet and an air outlet, and an airflow cavity arranged along a first direction inside the housing assembly, the airflow cavity being connected to the air inlet and the air outlet respectively, the first direction being the direction from the air inlet to the air outlet;

[0007] A refrigerant assembly, the refrigerant assembly including multiple refrigerant pipes passing through the airflow cavity;

[0008] A water collection assembly is provided inside the housing assembly and includes a connected water collection structure and a drain outlet. The water collection structure is provided on the inner wall of the airflow cavity. The water collection structure is used to collect condensate generated by multiple refrigerant pipes and transport it to the drain outlet. The drain outlet is used to discharge the condensate.

[0009] According to the heat exchange device of the present invention, a water collection structure is provided on the inner wall of the airflow chamber. During the cooling of compressed air by the refrigerant pipe, the moisture in the air condenses due to the temperature drop, forming condensate. This condensate drips down the surface of the refrigerant pipe or flows to the inner wall of the airflow chamber. The condensate adhering to the inner wall of the airflow chamber is blown by the airflow and flows to the water collection structure. The water collection structure collects the condensate and discharges it from the heat exchange device through the drain port. This water collection structure, located on the inner wall of the airflow chamber, effectively collects the condensate generated during the cooling process of the refrigerant pipe, preventing condensate from dripping directly into the airflow chamber and causing moisture retention inside the airflow chamber, thereby improving the overall drainage efficiency of the heat exchange device. Furthermore, by collecting and discharging the condensate through the water collection structure, long-term accumulation of condensate on the inner wall of the airflow chamber and the surface of the refrigerant pipe can be avoided, preventing corrosion and mold growth of the refrigerant pipe caused by condensate retention, and extending the service life of the heat exchange device.

[0010] In addition, the heat exchange device according to the present invention may also have the following additional technical features:

[0011] In some embodiments of the present invention, the heat exchange device further includes a partition, which is disposed in the airflow cavity and divides the airflow cavity into at least two mutually isolated airflow channels, each of the airflow channels being connected to the air inlet and the air outlet respectively.

[0012] The water collection assembly includes at least two interconnected water collection structures, and each of the airflow channels has a water collection structure on its inner wall.

[0013] In some embodiments of the present invention, the water collection structure includes a first water collection tank, which is disposed at one end of the airflow channel that is connected to the air outlet and is arranged along a second direction, the second direction being perpendicular to the first direction.

[0014] In some embodiments of the present invention, the water collection structure further includes a second water collection trough disposed on the inner wall of the airflow channel along the first direction, the second water collection trough being connected to the first water collection trough.

[0015] In some embodiments of the present invention, the heat exchange device further includes a heat exchange section and a partition plate. The heat exchange section includes a heat exchange inlet and a heat exchange outlet disposed on the housing assembly. The partition plate is disposed in at least one of the airflow channels. The partition plate divides the airflow channel into a first region and a second region that are isolated from each other. The first region is connected to the heat exchange inlet and the air inlet, respectively. The second region is connected to the heat exchange outlet and the air outlet, respectively.

[0016] In some embodiments of the present invention, the water collection structure further includes a third water collection tank, which is disposed along the edge connecting the central partition and the airflow channel, and is located in the first area and communicates with the second water collection tank.

[0017] In some embodiments of the present invention, the water collection structure further includes multiple fourth water collection troughs arranged along a first direction, the multiple fourth water collection troughs being formed on the inner wall of the airflow channel and located in the first region, and the multiple fourth water collection troughs being respectively connected to the third water collection trough.

[0018] In some embodiments of the present invention, the partition plate is curved.

[0019] In some embodiments of the present invention, the partition includes at least one partition plate disposed within the airflow cavity, the airflow channel is formed by the partition plate, and the water collection structure is provided on the partition plate.

[0020] In some embodiments of the present invention, the housing assembly includes a bottom plate disposed on the bottom side of the partition plate, and the bottom plate is provided with the water collection structure and the drain outlet.

[0021] In some embodiments of the present invention, the refrigerant assembly includes a first support plate and a second support plate disposed within the housing assembly, and the water collection assembly includes a connecting pipe disposed on the first support plate and / or the second support plate, wherein the water collection structure on the partition plate is connected to the water collection structure on the bottom plate through the connecting pipe.

[0022] A second aspect of the present invention provides an air conditioning system comprising the heat exchange device as described above. Attached Figure Description

[0023] Various other advantages and benefits will become apparent to those skilled in the art upon reading the following detailed description of preferred embodiments. The accompanying drawings are for illustrative purposes only and are not intended to limit the invention. Furthermore, the same reference numerals denote the same parts throughout the drawings. In the drawings:

[0024] Figure 1 A schematic diagram of the structure of a heat exchange device according to an embodiment of the present invention is shown.

[0025] Figure 2 An exploded structural diagram of a heat exchange device according to an embodiment of the present invention is shown schematically.

[0026] Figure 3 A schematic diagram of the first part of the structure of a heat exchange device according to an embodiment of the present invention is shown.

[0027] Figure 4 A schematic diagram of the second part of the heat exchange device according to an embodiment of the present invention is shown.

[0028] Figure 5 A schematic diagram of the structure of a partition plate according to an embodiment of the present invention is shown.

[0029] Figure 6 A first-view view of a partition plate according to an embodiment of the present invention is shown schematically;

[0030] Figure 7 A schematic diagram of the structure of the first support plate according to an embodiment of the present invention is shown.

[0031] Figure 8 A first-view view of a first support plate according to an embodiment of the present invention is shown schematically;

[0032] Figure 9 A schematic diagram of the structure of the base plate according to an embodiment of the present invention is shown.

[0033] Figure 10 A first-view view of the base plate according to an embodiment of the present invention is schematically shown;

[0034] Figure 11 A second perspective view of a heat exchange device according to an embodiment of the present invention is shown schematically;

[0035] Figure 12 It shows Figure 11 A sectional view of the C-plane;

[0036] Figure 13 A first-view view of a heat exchange device according to an embodiment of the present invention is shown schematically;

[0037] Figure 14 It shows Figure 13 A cross-sectional view of the AA plane;

[0038] Figure 15 It shows Figure 13 A cross-sectional view of the BB plane;

[0039] Figure 16 A schematic diagram of the structure of the air distribution plate according to an embodiment of the present invention is shown.

[0040] Figure 17 A schematic diagram illustrating the operation of a heat exchange apparatus according to an embodiment of the present invention is shown.

[0041] The attached figures are labeled as follows:

[0042] 100. Heat exchange device;

[0043] 10. Shell assembly; 101. Air inlet; 102. Air outlet; 103. Refrigerant inlet; 104. Refrigerant outlet; 105. Heat exchanger inlet; 106. Heat exchanger outlet; 107. Airflow chamber; 1071. First zone; 1072. Second zone; 1073. Third zone;

[0044] 11. Inlet end cap; 111. Inlet chamber; 112. First flow stabilizing chamber; 12. Outlet end cap; 121. Outlet chamber; 122. Second flow stabilizing chamber; 13. First end cap; 131. First chamber; 132. Second chamber; 14. Second end cap; 141. Flow guide channel; 15. Top cover plate; 16. Base; 17. Mounting bracket; 18. Base plate;

[0045] 20. Refrigerant assembly; 21. First support plate; 22. Refrigerant pipe; 23. Second support plate;

[0046] 30. First air distribution component; 301. First air distribution zone; 302. Second air distribution zone; 303. Air distribution hole; 31. Second air distribution component;

[0047] 40. Divider; 50. Middle partition;

[0048] 60. Water collection assembly; 61. First water collection tank; 62. Second water collection tank; 63. Third water collection tank; 64. Fourth water collection tank; 65. Connecting pipe; 66. Drain outlet. Detailed Implementation

[0049] Exemplary embodiments of the present disclosure will now be described in more detail with reference to the accompanying drawings. While exemplary embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.

[0050] It should be understood that the terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “described” as used herein may also include the plural forms. The terms “comprising,” “including,” “containing,” and “having” are inclusive and therefore indicate the presence of the stated features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not construed as requiring them to be performed in a particular order described or illustrated unless the order of performance is explicitly indicated. It should also be understood that additional or alternative steps may be used.

[0051] Although terms such as first, second, third, etc., may be used in this document to describe multiple elements, components, regions, layers, and / or segments, these elements, components, regions, layers, and / or segments should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or segment from another. Unless the context clearly indicates otherwise, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence. Therefore, the first element, component, region, layer, or segment discussed below may be referred to as the second element, component, region, layer, or segment without departing from the teachings of the exemplary embodiments.

[0052] For ease of description, spatial relative terms may be used in the text to describe the relationship of one element or feature relative to another element or feature, as shown in the figure. These relative terms include, for example, "inside," "outside," "middle," "outer," "below," "below," "above," "over," etc. Such spatial relative terms are intended to include different orientations of the device in use or operation, other than those depicted in the figure. For example, if the device in the figure is flipped, an element described as "below other elements or features" or "below other elements or features" would subsequently be oriented "above other elements or features" or "above other elements or features." Therefore, the example term "below" can include both upper and lower orientations.

[0053] like Figures 1 to 16 As shown, according to an embodiment of the present invention, a heat exchange device 100 is provided, including a housing assembly 10, a refrigerant assembly 20, and a water collection assembly 60. The housing assembly 10 is provided with an air inlet 101 and an air outlet 102. The interior of the housing assembly 10 is provided with an airflow cavity 107 arranged along a first direction. The airflow cavity 107 is connected to the air inlet 101 and the air outlet 102 respectively. The first direction is the direction from the air inlet 101 to the air outlet 102. The refrigerant assembly 20 includes multiple refrigerant pipes 22 passing through the airflow cavity 107. The water collection assembly 60 includes a water collection structure and a drain outlet 66. The water collection structure is provided on the inner wall of the airflow cavity 107. The water collection structure is used to collect the condensate generated by the multiple refrigerant pipes 22 and discharge it through the drain outlet 66.

[0054] According to the heat exchange device 100 of this embodiment, a water collection structure is provided on the inner wall of the airflow chamber 107. The airflow chamber 107 is arranged along a first direction. During the cooling of compressed air by the refrigerant pipe 22, the moisture in the air will condense due to the temperature drop, forming condensate. This condensate will drip down or flow along the surface of the refrigerant pipe 22 to the inner wall of the airflow chamber 107. The condensate adhering to the inner wall of the airflow chamber 107 is blown by the airflow and flows to the water collection structure. After collecting the condensate, the water collection structure discharges it from the heat exchange device 100 through the drain port 66. The water collection structure is provided on the inner wall of the airflow chamber 107, which can effectively collect the condensate generated during the cooling process of the refrigerant pipe 22, and prevent the condensate from dripping directly into the airflow chamber 107, causing moisture to remain inside the airflow chamber 107, thereby improving the overall drainage efficiency of the heat exchange device 100. Furthermore, by collecting the condensate through the water collection structure and discharging it from the drain outlet 66, the long-term accumulation of condensate on the inner wall of the airflow cavity 107 and the surface of the refrigerant pipe 22 can be avoided, thus preventing corrosion and mold growth of the refrigerant pipe 22 caused by condensate retention and extending the service life of the heat exchange device 100.

[0055] It is understandable that, such as Figure 17 As shown, arrow a1 indicates that the high-temperature airflow enters the airflow chamber 107; arrow a2 indicates that the high-temperature airflow after heat exchange flows out of the airflow chamber 107; arrow b1 indicates that the refrigerant liquid enters the refrigerant pipe 22; arrow b2 indicates that the refrigerant liquid flows out of the refrigerant pipe 22; a3 indicates that the airflow after partial cooling goes to the heat exchange component; a4 indicates the airflow returning from the heat exchange component.

[0056] Understandably, the refrigerant can be Freon.

[0057] It is understandable that, such as Figure 2 As shown, the x-direction is the first direction (airflow direction), the y-direction is the second direction (perpendicular to the airflow direction), and the z-direction is the third direction (gravity direction).

[0058] In some embodiments, the refrigerant pipe 22 is arranged along a second direction, which is perpendicular to the first direction. This means that the arrangement direction of the refrigerant pipe 22 is perpendicular to the flow direction of the airflow channel. This design helps to increase the contact area between the airflow and the refrigerant. When the airflow passes through the refrigerant pipe 22, the perpendicularity of the gas flow direction to the direction of the refrigerant pipe 22 allows the gas to have maximum contact with the surface of the refrigerant pipe 22. Increasing the contact area enhances the convective heat transfer effect and improves the heat exchange efficiency. At the same time, the refrigerant pipe 22 is arranged along the second direction, so that the airflow will have multiple heat exchanges with the refrigerant in the vertical direction when it flows through the airflow cavity 107. This multi-point contact method can distribute heat more evenly. Since the gas flow and the refrigerant flow are perpendicular to each other, the gas can flow fully in the gaps of the refrigerant pipe 22, making it less likely to form local hot spots with large temperature gradients, thus ensuring the uniformity of the internal temperature of the heat exchange device 100. Furthermore, when the refrigerant pipe 22 is arranged along the second direction, the gas flow does not need to bypass the refrigerant pipe 22 through complex path adjustments, but directly intersects with it. This reduces the turning and disturbance of the airflow during the flow process, thereby reducing airflow resistance and pressure loss, making the operation of the entire heat exchange device 100 more stable. Reducing airflow resistance improves the system's energy efficiency ratio, achieving a higher heat exchange effect at the same power. Finally, the design of the refrigerant pipe 22 being perpendicular to the airflow direction allows the refrigerant pipe 22 to be tightly arranged between the airflow channels, reducing the overall length and volume of the device. Compared to a design where the refrigerant pipe 22 is parallel to the airflow channels, this perpendicular intersection allows the heat exchange device 100 to occupy less space with the same heat exchange area. The refrigerant pipe 22 being arranged along the second direction also helps the airflow blow the condensate formed on the refrigerant pipe 22 onto the inner wall of the airflow chamber 107.

[0059] like Figure 2As shown, it can be understood that the housing assembly 10 includes a first end cap 13 and a second end cap 14 disposed opposite to each other along the second direction. The first end cap 13 is provided with a refrigerant inlet 103 and a refrigerant outlet 104. The refrigerant assembly 20 includes a first support plate 21 and a second support plate 23. The first end cap 13 and the first support plate 21 enclose a first chamber 131 and a second chamber 132. The second end cap 14 and the second support plate 23 enclose a flow guiding channel 141. The refrigerant pipe 22 has a first port and a second port. The first chamber 131 is connected to the first port and the refrigerant inlet 103 of a portion of the refrigerant pipe 22. The second chamber 132 is connected to the first port and the refrigerant outlet 104 of another portion of the refrigerant pipe 22. The flow guiding channel 141 is connected to the second port of all the refrigerant pipes 22. The flow guiding channel 141 is used to guide the refrigerant entering from the first chamber 131 to the second chamber 132. After entering the first chamber 131, the refrigerant undergoes initial heat exchange through a portion of the refrigerant pipe 22, absorbing most of the heat from the high-temperature gas in the airflow chamber 107. At this point, the refrigerant temperature rises, but it still retains its cooling capacity. Through the drainage channel, the refrigerant re-enters another portion of the refrigerant pipe 22 for secondary heat exchange, further reducing the temperature of the high-temperature gas in the airflow chamber 107. Multiple heat exchanges allow the refrigerant to utilize its cooling capacity more fully, improving the overall cooling effect. Simultaneously, the refrigerant undergoes secondary heat exchange in another portion of the refrigerant pipe 22, absorbing residual heat, achieving gradual heat distribution and utilization. This ensures that the refrigerant is fully utilized at each heat exchange stage, preventing the cooling capacity from being directly wasted after the initial heat exchange, making the system's heat management more efficient and rational.

[0060] Understandably, the housing assembly 10 also includes an inlet end cap 11 and an outlet end cap 12 disposed opposite to each other along a first direction. An inlet 101 is located on the inlet end cap 11, and an outlet 102 is located on the outlet end cap 12. The axial direction of the inlet 101 is perpendicular to the first direction, and the axial direction of the outlet 102 is parallel to the first direction. After entering the inlet end cap 11, the airflow diffuses vertically, ensuring a uniform distribution before entering the airflow chamber 107. This design helps to slow the flow velocity before the airflow enters the airflow chamber 107, preventing turbulence caused by direct entry into the airflow chamber 107. Through initial diffusion and distribution within the inlet end cap 11, the airflow becomes smoother upon entering the airflow chamber 107, reducing turbulence and the resulting pressure loss. This allows the airflow to maintain higher efficiency during subsequent heat exchange with the refrigerant pipe 22. The axial direction of the outlet 102 is parallel to the first direction, allowing the gas to flow smoothly towards the outlet along the first direction after passing through the refrigerant pipe 22 in the airflow chamber 107. This parallel flow design helps maintain the flow direction of the airflow within the airflow chamber 107, preventing abrupt changes in airflow direction at the outlet. By reducing changes in direction, the generation of turbulence and eddies is reduced, thereby reducing energy loss in the airflow and improving the overall operating efficiency of the heat exchanger 100.

[0061] Specifically, along the second direction, the air inlet 101 and the air outlet 102 are spaced apart, meaning that the air inlet 101 and the air outlet 102 are not located on the same horizontal plane, but are separated by a certain distance along the second direction. First, the spaced arrangement of the air inlet 101 and the air outlet 102 along the second direction forces the airflow to flow over a larger area within the airflow cavity 107, thus allowing for a more uniform distribution throughout the heat exchange area. This uniform airflow distribution helps avoid insufficient heat exchange in some areas due to concentrated airflow, and overcooling in other areas due to excessively slow airflow velocity, thereby reducing uneven cooling and ensuring the uniformity of the outlet gas temperature. Second, the airflow has a longer flow path within the airflow cavity 107, and the spaced design of the air inlet 101 and the air outlet 102 allows for smooth airflow, reducing turbulence. Reduced turbulence means lower flow resistance, which not only helps reduce energy loss when the airflow passes through the heat exchange device 100, but also reduces pressure loss. This design, which reduces turbulence and pressure loss, allows the heat exchanger 100 to handle a larger gas flow rate with the same energy consumption, thereby improving the system's energy efficiency ratio. Additionally, when the airflow passes through the refrigerant pipe 22, condensate may be generated due to cooling. The spacing between the inlet 101 and outlet 102 in the second direction ensures sufficient flow distance for the condensate within the airflow chamber 107, facilitating its discharge along the airflow direction. This design reduces condensate accumulation within the airflow chamber 107, helping to prevent a decrease in heat exchange efficiency due to condensate buildup, thus reducing the maintenance frequency of the heat exchanger 100 and extending its service life. Finally, because the inlet 101 and outlet 102 are spaced apart, the airflow, after entering the airflow chamber 107, needs to travel a certain distance along a longer path to the outlet 102. This design makes the airflow within the chamber smoother, avoiding turbulence and vibration caused by the inlet and outlet being too close together. Reducing airflow turbulence and vibration can significantly reduce the noise generated by the heat exchanger 100 during operation, improve the operating comfort of the heat exchanger 100, and is especially suitable for applications requiring a low-noise environment.

[0062] Furthermore, the air inlet end cap 11 has an interconnected air inlet chamber 111 and a first flow stabilizing chamber 112 inside. The air inlet chamber 111 is located on one side of the air inlet end cap 11 and is connected to the air inlet 101, used to receive external airflow. The first flow stabilizing chamber 112 is located in the opposite direction of the air inlet chamber 111 and is connected to the air inlet chamber 111. Along the direction opposite to the air inlet chamber 111, the cross-sectional area of ​​the first flow stabilizing chamber 112 gradually decreases, that is, the shape of the first flow stabilizing chamber 112 is similar to a gradually narrowing channel. This gradually narrowing design helps to effectively guide and stabilize the airflow before it enters the airflow chamber 107, making the airflow smoother when entering the airflow chamber 107. At the same time, the air outlet end cap 12 has an interconnected air outlet chamber 121 and a second flow stabilizing chamber 122 inside. The air outlet chamber 121 is located on one side of the air outlet end cap 12 and is connected to the air outlet 102, used to discharge the heat-exchanged gas. The second flow stabilizing chamber 122 is located in the opposite direction to the outlet chamber 121 and is connected to it. Along the direction opposite to the outlet chamber 121, the cross-sectional area of ​​the second flow stabilizing chamber 122 gradually decreases, resembling a gradually narrowing outlet channel. This design allows for flow velocity adjustment before the airflow is discharged, making the airflow more stable when it exits the airflow chamber 107. Therefore, when gas flows into the first flow stabilizing chamber 112, the gradually decreasing cross-sectional area gradually smooths the high-speed incoming airflow, reducing turbulence caused by sudden deceleration or cornering of the airflow, thereby improving airflow stability. Similarly, when gas flows through the second flow stabilizing chamber 122 to prepare for discharge, this design smooths the gas discharge process, avoiding turbulence generated when the airflow exits the heat exchanger 100, allowing the airflow to leave the device more evenly, and reducing disturbance to downstream equipment.

[0063] It is understood that the housing assembly 10 also includes a base plate 18 and an upper cover plate 15. The base plate 18 and upper cover plate 15 are positioned opposite each other along a third direction perpendicular to the third direction (the third direction is perpendicular to both the first and second directions). The six components—base plate 18, upper cover plate 15, first end cap 13, second end cap 14, air inlet end cap 11, and air outlet end cap 12—enclose an airflow cavity 107. The base plate 18 and upper cover plate 15 are positioned opposite each other along a third direction perpendicular to the third direction, i.e., they are located on the upper and lower sides of the airflow cavity 107, respectively. The base plate 18, upper cover plate 15, first end cap 13, second end cap 14, air inlet end cap 11, and air outlet end cap 12, combined, enclose a closed airflow cavity 107. In the airflow cavity 107, high-temperature gas enters from the air inlet end cap 11, exchanges heat with the refrigerant pipe 22 inside, and finally exits from the air outlet end cap 12.

[0064] Specifically, the lower part of the base plate 18 is provided with a base 16, which supports the entire shell assembly 10. The base 16 is tightly connected to the base plate 18 and provides a stable foundation, allowing the entire heat exchange device 100 to be firmly fixed to the ground or other supporting platform during installation. The upper part of the top cover plate 15 is provided with a mounting bracket 17, which is used to fix the heat exchange device 100 to an external support structure (such as the bracket of an air conditioning system), thereby distributing the weight borne by the base 16. The base 16 of the base plate 18 provides a stable support point, making it difficult for the entire shell assembly 10 to tilt or move during installation, effectively improving the overall stability of the heat exchange device 100. At the same time, the mounting bracket 17, through its connection with the top cover plate 15, transfers part of the weight to the external support structure, reducing the weight directly borne by the base 16. This avoids the deformation of the base plate 18 or the base 16 caused by the weight of the shell assembly 10 being concentrated on the base 16, ensuring the structural stability of the heat exchange device 100 during long-term operation.

[0065] In some embodiments, the heat exchange device 100 further includes a heat exchange section connected to an airflow channel. The heat exchange section is used to deliver the airflow, after heat exchange with the refrigerant pipe 22, to the component to be heat-exchanged. The heat exchange section guides the airflow, which has been preliminarily cooled by the refrigerant pipe 22, to the component to be heat-exchanged. The cooled airflow can directly contact the surface or internal flow channels of the component, thereby rapidly absorbing heat from the component and achieving a highly efficient cooling effect. The connection between the heat exchange section and the airflow channel allows the airflow to be distributed as needed to the components requiring cooling during the cooling process, avoiding ineffective circulation or heat dissipation of the cooling airflow in the airflow chamber 107. Simultaneously, this flexible adjustment capability allows the heat exchange device 100 to quickly adapt to changing cooling demands under different operating conditions, achieving efficient temperature management.

[0066] It is understandable that there are multiple airflow channels, each of which is connected to a heat exchange section, and each heat exchange section exchanges heat with a component to be heat exchanged.

[0067] Specifically, taking a heat exchange section and an airflow channel as an example, the heat exchange section includes a heat exchange inlet 105, a heat exchange outlet 106, and a heat exchange pipe. The heat exchange inlet 105, the heat exchange pipe, and the heat exchange outlet 106 are connected in sequence. The airflow enters the heat exchange pipe from the airflow channel through the heat exchange inlet 105. After the heat exchange pipe exchanges heat with the component to be heat-exchanged, the airflow returns to the airflow channel from the heat exchange outlet 106. The heat exchange device 100 includes a partition plate 50. At least one airflow channel is provided with a partition plate 50. The partition plate 50 blocks the airflow channel along a first direction. The partition plate 50 divides the airflow channel into a first region 1071 connected to the air inlet 101 and a second region 1072 connected to the air outlet 102. The first region 1071 and the second region 1072 are isolated from each other. The heat exchange inlet 105 is connected to the first region 1071, and the heat exchange outlet 106 is connected to the second region 1072. High-temperature gas enters the first region 1071 through inlet 101, passes through heat exchange inlet 105 into the heat exchange pipe, and exchanges heat with the components to be heat-exchanged in the heat exchange pipe. The airflow temperature decreases during the heat exchange process. The heat-exchanged airflow then enters the second region 1072 through heat exchange outlet 106. In the second region 1072, the airflow is cooled again by passing through refrigerant pipe 22, and finally exits from outlet 102 after cooling is complete. The partition 50 divides the airflow channel into two regions, ensuring that the airflow must undergo heat exchange before entering the second region 1072. This ensures that the airflow fully utilizes its cooling capacity and undergoes multiple heat exchanges with the components before exiting. The optimized connection path between the heat exchange section and the airflow channel allows the high-temperature gas to effectively transfer heat multiple times before entering outlet 102, helping to reduce the temperature of the components more quickly and significantly improving cooling efficiency.

[0068] Understandably, the number of refrigerant pipes 22 in the first zone 1071 is greater than that in the second zone 1072. The first zone 1071 plays a primary role in heat exchange, cooling the high-temperature airflow and then transporting it from the heat exchange inlet 105 to the heat exchange pipes, before returning to the second zone 1072 from the heat exchange outlet 106. The refrigerant pipes 22 in the second zone 1072 perform a smaller portion of the heat exchange, transferring heat generated by the heat exchange components. Because the first zone 1071 has a larger number of refrigerant pipes 22, it undertakes the main heat exchange task. After entering the first zone 1071, the high-temperature airflow undergoes large-scale heat exchange through the numerous refrigerant pipes 22, rapidly reducing the airflow temperature. The strong heat exchange capacity of the first zone 1071 allows for the initial release of the main heat of the high-temperature gas, thus achieving rapid cooling. The second zone 1072 has a relatively smaller number of refrigerant pipes 22, undertaking a smaller portion of the heat exchange task. After initial cooling in the first zone 1071, the airflow reaches the heat exchange component, where its temperature is higher than that of the airflow in the first zone 1071. Then, it enters the second zone 1072 for heat exchange, regulating the remaining heat. This staged cooling process allows for more efficient utilization of the refrigerant's cooling capacity, achieving gradual temperature reduction. Furthermore, the asymmetrical design of the number of refrigerant pipes 22 in the first and second zones 1071 allows the heat exchange device 100 to be adjusted according to different operating conditions. For example, when the heat exchange component generates significant heat, the flow rate of the refrigerant pipe 22 in the first zone 1071 can be appropriately adjusted to increase the initial heat exchange intensity, while retaining the adjustment capability of the second zone 1072. This flexibility allows the heat exchange device 100 to quickly respond to different cooling demands by adjusting the refrigerant flow rate and heat exchange path in the face of various load changes, thus adapting to diverse application scenarios.

[0069] In some embodiments, the partition includes at least one partition plate 40 with a water collection structure. The partition plate 40 is disposed within the airflow cavity 107, dividing the airflow cavity 107 into at least two mutually isolated airflow channels arranged along a first direction (i.e., the airflow channels are formed by the partition plate 40). These airflow channels are respectively connected to the air inlet 101 and the air outlet 102. The partition plate 40 has a flat plate structure, dividing the airflow cavity 107 into two airflow channels arranged along the first direction. Multiple partition plates 40 can be used to divide the airflow cavity 107 into multiple airflow channels. The partition plates 40 divide the airflow cavity 107 into multiple airflow channels, allowing the airflow in each channel to flow independently and exchange heat with the corresponding refrigerant pipe 22. Since the airflow channels do not interfere with each other, multi-channel parallel heat exchange can be achieved in the same heat exchange device 100. This parallel heat exchange method helps improve the overall heat exchange efficiency, especially when dealing with large volumes of airflow, significantly improving cooling capacity and shortening cooling time through the multi-channel structure.

[0070] like Figure 3 and Figure 4 As shown, the water collection assembly 60 includes at least two interconnected water collection structures, with one structure located on the inner wall of each airflow channel. Since each water collection structure is located on the inner wall of its respective airflow chamber 107, segmented condensate collection is achieved. Condensate generated in the refrigerant pipes 22 within each airflow channel is guided to the water collection structure and then, through the interconnected structures, to the overall drainage area. This ensures that even with a large volume of condensate, water flow does not overflow, effectively reducing stagnation.

[0071] Understandably, during the operation of the heat exchanger 100, as the airflow moves from the inlet 101 to the outlet 102, a high-velocity airflow is formed within the airflow chamber 107. During this process, due to the differences in airflow velocity and path, pressure differences will form at different locations within the airflow chamber 107. Typically, the pressure near the inlet 101 and the outlet 102 is different, with the pressure near the outlet 102 generally being lower, while the pressure near the inlet 101 is higher.

[0072] like Figure 5 , Figure 6 , Figure 9 and Figure 10 As shown, specifically, the water collection structure includes a first water collection tank 61, which is located along the second direction at the end where the airflow channel connects to the air outlet 102. Because of the pressure difference between the two ends of the airflow cavity 107, condensate naturally flows from the area of ​​higher pressure to the area of ​​lower pressure. In this design, condensate, under the influence of the pressure difference, drips from the surface of the refrigerant pipe 22 and gradually flows along the inner wall of the airflow cavity 107 or the guiding structure of the water collection tank towards the end with lower pressure (usually near the air outlet 102, i.e., the area where the first water collection tank 61 is located). This arrangement fully utilizes the pressure difference driving the condensate during cooling, concentrating and guiding it to a location near the air outlet 102 for collection. By rationally utilizing the flow characteristics of the airflow, the accumulation of condensate in other parts of the airflow channel can be reduced, thereby avoiding internal water accumulation and maintaining the unobstructed flow of the airflow channel.

[0073] Specifically, to facilitate the collection of condensate in the first water collection tank 61, the water collection structure also includes a second water collection tank 62. The second water collection tank 62 is arranged along the first direction and is connected to the first water collection tank 61. The second water collection tank 62 can collect condensate in areas with longer airflow channels and guide the collected condensate into the first water collection tank 61. Through multi-point collection and centralized guidance, condensate can be prevented from remaining in the airflow channel for a long time, effectively reducing the accumulation of condensate on the surface of the airflow channel and preventing corrosion and mold problems. At the same time, the arrangement direction of the second water collection tank 62 is consistent with the airflow direction, which means that the condensate can flow forward along the path of the second water collection tank 62 under the propulsion of the airflow, thus entering the first water collection tank 61 more smoothly and improving the overall condensate collection efficiency.

[0074] Specifically, the water collection structure includes a third water collection tank 63. In the above embodiment, the partition plate 50 and the airflow channel have a connecting edge. The third water collection tank 63 is located along this edge, within the first region 1071, and is connected to the second water collection tank 62. The third water collection tank 63 is positioned along the connecting edge between the partition plate 50 and the airflow channel, enabling it to effectively collect condensate within this edge area. By utilizing the positional characteristics of the edge, the third water collection tank 63 can promptly capture condensate dripping from the edge of the partition plate 50 and the airflow channel, preventing condensate from freely scattering within the airflow cavity 107 and ensuring the orderly flow path of the condensate. The third water collection tank 63 is connected to the second water collection tank 62, allowing condensate to gradually collect within the multi-stage water collection structure. By setting up a third water collection tank 63 in the first area 1071, the collection range of condensate can be further expanded, so that condensate generated at different locations in the refrigerant pipe 22 can be effectively collected and discharged into the first water collection tank 61 through the second water collection tank 62, thereby improving the efficiency of the overall condensate management system.

[0075] Furthermore, there are two second water collection tanks 62, located on both sides of the first region 1071. One side is the connecting edge between the partition plate 40 and the first support plate 21, and the other side is the connecting edge between the partition plate 40 and the second support plate 23. When condensate is generated, if there is only one water collection tank, excessive water accumulation on one side may occur, affecting the drainage speed and efficiency. By setting second water collection tanks 62 on both sides of the first region 1071, the distribution of condensate on both sides can be balanced, avoiding the adverse effects of water accumulation on one side. This allows condensate to flow evenly to the water collection tanks on both sides, reducing the risk of local overload during drainage and thus improving the drainage stability of the system.

[0076] Furthermore, the water collection structure includes multiple fourth water collection tanks 64 arranged along the first direction. These fourth water collection tanks 64 are mounted on the inner wall of the airflow channel and located within the first region 1071. These fourth water collection tanks 64 are connected to the third water collection tank 63. The reason for having multiple fourth water collection tanks 64 within the first region 1071 is that a large number of refrigerant pipes 22 are arranged within the first region 1071, and the first region 1071 is directly connected to the air inlet 101. When the refrigerant pipes 22 exchange heat with the high-temperature gas in this region, a large amount of condensate will be generated due to the rapid temperature drop. The multiple fourth water collection tanks 64, arranged along the inner wall of the airflow channel, can promptly capture and collect the condensate where it first forms, preventing excessive accumulation of condensate within the first region 1071 and ensuring that the condensate is quickly guided to the drainage channel.

[0077] In some embodiments, the partition 50 is curved. The curved design of the partition 50 allows for more uniform and stable airflow within the heat exchanger 100. The curved structure reduces turbulence near the surface of the partition 50, thus maintaining smooth flow within the airflow channel. Improved airflow stability enhances the heat exchange efficiency between the refrigerant pipe 22 and the airflow, further improving the overall performance of the heat exchanger 100. Simultaneously, the curved design of the partition 50 allows condensate to flow more naturally along the curved surface. The curved structure guides the condensate downwards along a predetermined flow path, preventing condensate from stagnating in flat areas. This design allows condensate to quickly collect in an area with a collection tank, improving drainage efficiency.

[0078] Specifically, the base plate 18 is located on the bottom side of the partition plate 40, and the base plate 18 and the top cover plate 15 are respectively located on opposite sides of the partition plate 40. The base plate 18 has a water collection structure, and a drain outlet 66 is located at the bottom of the base plate 18. Condensate is guided to the drain outlet 66 and discharged by gravity. Furthermore, second water collection troughs 62 are provided on both sides of the base plate 18, and a first water collection trough 61 is provided at the end of the base plate 18 that connects to the vent. The water collection structure on the base plate 18, combined with and connected to the partition plate 40 and other water collection troughs, forms a multi-stage condensate collection and discharge system. The condensate is first initially collected in the water collection structure around the partition plate 40 and the refrigerant pipe 22, then flows to the water collection structure on the base plate 18 by gravity, and is finally guided to the drain outlet 66. This multi-stage coordinated collection method ensures smooth flow of condensate throughout the drainage process, preventing overflow due to insufficient water collection capacity at any point, thereby improving the stability of the drainage system.

[0079] It is understandable that a valve is provided at the drain outlet 66. When the heat exchange device 100 is not in operation, the valve is opened to allow the condensate at the drain outlet 66 to be discharged.

[0080] like Figure 8 and Figure 9 As shown, in some embodiments, the water collection assembly 60 includes a connecting pipe 65, which is disposed on the first support plate 21, or on the second support plate 23, or both the first support plate 21 and the second support plate 23 are provided with connecting pipes 65. The connecting pipe 65 is used to connect two adjacent water collection structures. For example, the first water collection tank 61 on the partition plate 40 and the first water collection tank 61 on the bottom plate 18 are connected by the connecting pipe 65. The design of the connecting pipe 65 can accelerate the flow of condensate from the upper water collection tank to the lower water collection tank, reducing the residence time of condensate in each water collection structure. This can prevent excessive accumulation of condensate in a certain water collection tank, reduce the risk of corrosion and mold growth caused by long-term residence of condensate, thereby protecting the internal components of the heat exchange device 100 and extending the service life of the heat exchange device 100.

[0081] It is understandable that the second water collection tank 62 or the fourth water collection tank 64 has a certain slope along the direction of gravity, with the side closer to the air inlet 101 being higher than the side closer to the air outlet 102. The slope along the direction of gravity allows the condensate to flow naturally downwards within the tank. This design reduces the residence time of the condensate in the tank, preventing water accumulation due to condensate stagnation, thus significantly improving drainage efficiency and allowing the condensate to be guided to the drain outlet more quickly. The first water collection tank 61 and the third water collection tank 63 also have a certain slope along the second direction, with the side closer to the drain outlet 66 being higher than the side farther from the drain outlet 66. The slope along the second direction allows the condensate to flow naturally towards the drain outlet 66 within the tank under the influence of gravity. This design ensures that the condensate flows rapidly towards the drain outlet within the tank, reducing the residence time of the condensate and thus significantly improving drainage efficiency.

[0082] In some embodiments, the heat exchange device 100 further includes a first gas distributor 30 disposed within the housing assembly 10. The first gas distributor 30 is detachably connected to the housing assembly 10 and is located between the air inlet 101 and the airflow chamber 107. The first gas distributor 30 is used to adjust the gas flow rate entering each airflow channel. The use of the first gas distributor 30 allows for precise distribution of airflow according to the cooling requirements of each airflow channel when entering the airflow chamber 107. By adjusting the gas flow rate entering each airflow channel, the heat exchange between the airflow and the refrigerant can be made more efficient. For example, when the temperature of the heat exchange component in a certain airflow channel is high, the gas flow rate in that channel can be increased through the first gas distributor 30 to increase the cooling intensity. Conversely, in other channels with lower temperatures, the gas flow rate can be appropriately reduced to avoid unnecessary energy consumption. Since the first gas distributor 30 can independently adjust the gas flow rate of each airflow channel, it can effectively avoid differences in cooling effects between channels caused by uneven gas flow. This design ensures that when the entire heat exchanger 100 operates in parallel with multiple channels, the airflow distribution in each airflow channel is more balanced, avoiding problems such as excessive flow velocity in some channels due to excessive gas flow or reduced heat exchange effect due to insufficient gas flow.

[0083] Furthermore, the heat exchange device 100 also includes a second gas distributor 31 disposed within the housing assembly 10. The second gas distributor 31 is detachably connected to the housing assembly 10. Along the first direction, the second gas distributor 31 is arranged opposite to the first gas distributor 30 and has the same structure. The second gas distributor 31 is disposed between the outlet 102 and the airflow chamber 107, and is used to stabilize the air pressure in each airflow channel. The second gas distributor 31, disposed between the outlet 102 and the airflow chamber 107, is used to regulate the airflow in each airflow channel, ensuring that the air pressure in each airflow channel remains stable before the gas is discharged from the airflow chamber 107, controlling the flow resistance of different airflow channels at the outlet 102, so that the gas flow rate in each airflow channel is balanced, and preventing pressure fluctuations caused by uneven airflow. The first gas distributor 30 and the second gas distributor 31 are located at the inlet 101 and the outlet 102, respectively. By regulating the airflow entering and exiting the airflow chamber 107, the airflow in the entire airflow chamber 107 can be bidirectionally regulated. This bidirectional regulation can balance the pressure distribution within the airflow channel, ensuring that the airflow maintains a stable speed and flow rate as it flows through the entire airflow channel, effectively avoiding eddies, turbulence, and airflow oscillations caused by uneven airflow.

[0084] Specifically, both the first air distribution component 30 and the second air distribution component 31 are air distribution plates. Each air distribution plate has at least two air distribution zones, each connected to an airflow channel. Each air distribution zone is specifically designed to control the airflow of its corresponding airflow channel. Each air distribution zone has multiple air distribution holes 303, which can have different diameters, numbers, or arrangements. However, there is a difference between the opening area of ​​one air distribution zone and the opening area of ​​another, meaning that the total opening area of ​​the air distribution holes 303 in each air distribution zone can be designed according to cooling requirements to accommodate the airflow needs of different airflow channels. The difference in opening area between each air distribution zone and other air distribution zones allows different airflow channels to receive different amounts of gas flow. By adjusting the number and diameter of the air distribution holes 303, the air resistance entering the corresponding airflow channel can be changed. For example, reducing the orifice diameter or number of orifices in a certain air distribution zone can increase the air resistance of that zone, thereby reducing the flow rate entering that channel; conversely, increasing the orifice diameter or number of orifices in another air distribution zone can reduce air resistance and increase air flow. By setting air distribution zones and adjusting the area of ​​the air distribution holes 303 on the air distribution plate, precise control of the gas flow rate in each airflow channel can be achieved. Different airflow channels can receive different air flow rates, thus ensuring a better match between the airflow and the refrigerant's heat exchange. This precise airflow distribution helps to increase the air flow rate to improve the cooling effect when the high-temperature heat exchange component requires greater cooling intensity, while reducing the air flow rate in lower temperature areas avoids overcooling and improves overall heat exchange efficiency.

[0085] Understandably, since the air distribution plate is a detachable structure, the heat exchanger 100 can be adjusted by replacing the air distribution plate when needed, without requiring complex disassembly or modification of the heat exchanger 100. This significantly reduces time and labor costs during the maintenance and upgrade of the heat exchanger 100. This design flexibility makes the heat exchanger 100 more adaptable to different application scenarios, allowing for rapid iteration and upgrades based on varying cooling requirements, resulting in diverse heat exchange solutions and enabling rapid iteration of the heat exchanger 100.

[0086] Specifically, two air distribution plates are connected to the inlet end cap 11 and the outlet end cap 12 respectively, and are used to regulate the flow rate of air entering and exiting the airflow channel. Each air distribution plate is fixed to the inlet end cap 11 or the outlet end cap 12 by bolts or screws. The position of the bolt holes matches the preset screw holes on the inlet end cap 11 or the outlet end cap 12 to ensure that the air distribution plate is tightly fixed after installation and will not loosen or shift due to airflow pressure.

[0087] In some specific embodiments, the partition includes a partition plate 40 that divides the airflow chamber 107 into upper and lower airflow channels. A middle partition plate 50 is provided in the upper airflow channel, dividing it into a first region 1071 and a second region 1072 that are isolated from each other. The first region 1071 is connected to the air inlet 101, and the second region 1072 is connected to the air outlet 102. The lower airflow channel does not have a middle partition plate 50; the interior of the lower airflow channel is the third region 1073. For ease of description, the multiple refrigerant pipes 22 located in the third region 1073 are referred to as the first core, the multiple refrigerant pipes 22 located in the second region 1072 are referred to as the third core, and the multiple refrigerant pipes 22 located in the first region 1071 are referred to as the second core. The first and second cores are multi-flow, while the third core is single-flow. Specifically, refrigerant enters the first chamber 131 through refrigerant inlet 103, then a portion of the refrigerant enters the third core from the first chamber 131, while another portion enters part of the first core from the first chamber 131. The refrigerant exiting the third core is guided to the second core through the guide channel 141 of the second end cap 14. Finally, the refrigerant flows out from the first and second cores into the second chamber 132, and finally exits through refrigerant outlet 104.

[0088] Furthermore, the air distribution plate includes a first air distribution zone 301 and a second air distribution zone 302. The first air distribution zone 301 is connected to either the first region 1071 or the second region 1072, and the second air distribution zone 302 is connected to the third region 1073.

[0089] This embodiment also provides an air conditioning system, which includes the heat exchange device 100 described above.

[0090] The above description is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A heat exchange device, characterized in that, include: A housing assembly having an air inlet and an air outlet, and an airflow cavity arranged along a first direction inside the housing assembly, the airflow cavity being connected to the air inlet and the air outlet respectively, the first direction being the direction from the air inlet to the air outlet; A refrigerant assembly, the refrigerant assembly including multiple refrigerant pipes passing through the airflow cavity; A water collection assembly is provided inside the housing assembly and includes a connected water collection structure and a drain outlet. The water collection structure is provided on the inner wall of the airflow cavity. The water collection structure is used to collect condensate generated by multiple refrigerant pipes and transport it to the drain outlet. The drain outlet is used to discharge the condensate.

2. The heat exchange device according to claim 1, characterized in that, The heat exchange device further includes a partition, which is disposed in the airflow cavity and divides the airflow cavity into at least two mutually isolated airflow channels. Each airflow channel is connected to the air inlet and the air outlet, respectively. The water collection assembly includes at least two interconnected water collection structures, and each of the airflow channels has a water collection structure on its inner wall.

3. The heat exchange device according to claim 2, characterized in that, The water collection structure includes a first water collection tank, which is located at one end of the airflow channel that is connected to the air outlet and is arranged along a second direction, which is perpendicular to the first direction.

4. The heat exchange device according to claim 3, characterized in that, The water collection structure further includes a second water collection trough disposed on the inner wall of the airflow channel along the first direction, and the second water collection trough is connected to the first water collection trough.

5. The heat exchange device according to claim 4, characterized in that, The heat exchange device further includes a heat exchange section and a partition plate. The heat exchange section includes a heat exchange inlet and a heat exchange outlet disposed on the housing assembly. The partition plate is disposed in at least one of the airflow channels. The partition plate divides the airflow channel into a first region and a second region that are isolated from each other. The first region is connected to the heat exchange inlet and the air inlet, respectively. The second region is connected to the heat exchange outlet and the air outlet, respectively.

6. The heat exchange device according to claim 5, characterized in that, The water collection structure also includes a third water collection tank, which is arranged along the edge connecting the middle partition and the airflow channel. The third water collection tank is located in the first area and is connected to the second water collection tank.

7. The heat exchange device according to claim 6, characterized in that, The water collection structure also includes multiple fourth water collection troughs arranged along the first direction. The multiple fourth water collection troughs are opened on the inner wall of the airflow channel and located in the first area. The multiple fourth water collection troughs are respectively connected to the third water collection trough.

8. The heat exchange device according to claim 5, characterized in that, The partition plate is curved.

9. The heat exchange device according to claim 2, characterized in that, The partition includes at least one partition plate disposed within the airflow cavity, the airflow channel is formed by the partition plate, and the water collection structure is provided on the partition plate.

10. The heat exchange device according to claim 9, characterized in that, The housing assembly includes a base plate disposed on the bottom side of the partition plate, and the base plate is provided with the water collection structure and the drain outlet.

11. The heat exchange device according to claim 10, characterized in that, The refrigerant assembly includes a first support plate and a second support plate disposed within the housing assembly. The water collection assembly includes a connecting pipe disposed on the first support plate and / or the second support plate. The water collection structure on the partition plate is connected to the water collection structure on the bottom plate through the connecting pipe.

12. An air conditioning system, characterized in that, The air conditioning system includes a heat exchange device as described in any one of claims 1 to 11.

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