Heat exchange device and air conditioning system

Abstract

The invention relates to the technical field of refrigeration, in particular to a heat exchange device and an air conditioning system. The heat exchange device comprises a shell assembly, a refrigerant assembly and a partition assembly, an air inlet and an air outlet are formed in the shell assembly, an airflow cavity arranged in the first direction is formed in the shell assembly and communicates with the air inlet and the air outlet, and the first direction is the direction from the air inlet to the air outlet; the refrigerant assembly comprises a plurality of refrigerant pipelines arranged in the airflow cavity in a penetrating mode, the separation assembly is arranged in the airflow cavity and divides the airflow cavity into at least two airflow channels which are separated from each other, the refrigerant pipelines are arranged in each airflow channel, and the number of the refrigerant pipelines in any two airflow channels is different. According to the heat exchange device in the embodiment, the airflow cavity is divided into the multiple independent airflow channels through the separation assemblies, disordered flowing of airflow in the heat exchange device is avoided, and therefore the contact efficiency of the airflow and the refrigerant pipeline is improved.

Description

Technical Field

[0001] The present invention relates to the field of refrigeration technology, and in particular to a heat exchange device and an air conditioning system. Background Art

[0002] The main function of the heat exchanger is to exchange heat with cooling water or cold liquid when high-temperature gas enters through the air inlet, thereby reducing the gas temperature and ensuring the normal operation of the system. However, existing heat exchangers usually adopt a unified cooling method, which cannot meet the different temperature regulation requirements of different parts. Due to the cross-arrangement of the airflow and cooling water inside the heat exchanger, the heat exchange efficiency is relatively high, but in response to the needs of complex systems, when different sections require different cooling efficiencies, the conventional heat exchanger design can no longer effectively meet the segmented cooling requirements. In addition, the problem of heat exchange capacity distribution after segmentation and the difficulty of adjusting the flow rate are relatively large, and the existing heat exchangers still have design deficiencies in this regard. Summary of the invention

[0003] The purpose of the present invention is to at least solve the problem that the existing heat exchange device cannot achieve segmented cooling. This purpose is achieved through the following technical solutions:

[0004] A first aspect of the present invention provides a heat exchange device, comprising:

[0005] A shell component, wherein an air inlet and an air outlet are provided on the shell component, and an air flow cavity arranged along a first direction is provided inside the shell component, and the air flow cavity is respectively connected with the air inlet and the air outlet, and the first direction is the direction from the air inlet to the air outlet;

[0006] A refrigerant assembly, the refrigerant assembly comprising a plurality of refrigerant pipes passing through the airflow cavity;

[0007] A partition component is arranged in the airflow cavity, and the partition component divides the airflow cavity into at least two airflow channels isolated from each other. Each of the airflow channels is respectively connected to the air inlet and the air outlet. Each of the airflow channels is provided with the refrigerant channel, and the number of the refrigerant pipelines in any two of the airflow channels is different.

[0008] According to the heat exchange device of the present invention, the high-temperature gas enters the shell component from the air inlet and enters the airflow cavity along the first direction. Then, the airflow in the airflow cavity is divided into at least two independent airflow channels by the partition component and enters different airflow channels. Different airflow channels are provided with different numbers of refrigerant pipes. The airflow cavity is divided into a plurality of independent airflow channels by the partition component, so that the airflow can flow in a directional manner along a preset path. The segmented airflow channel layout avoids the disordered flow of the airflow in the heat exchanger, reduces the generation of vortices and dead zones, thereby improving the contact efficiency between the airflow and the refrigerant pipe, so that the airflow can fully flow through the refrigerant pipe, improves the heat exchange efficiency per unit time, and achieves the effect of rapid cooling. In addition, by dividing the airflow channel into a plurality of independent parts, the gas can be cooled more evenly in each channel. In a conventional heat exchange device, due to the uneven cooling effect of the cooling fluid at different positions, insufficient heat exchange or overcooling may occur in some areas. The present invention effectively reduces the temperature difference deviation through segmented cooling, so that the gas temperature in each airflow channel is more uniform, the temperature gradient of the refrigerant is fully utilized, and the overall heat exchange efficiency is improved.

[0009] In addition, the heat exchange device according to the present invention may also have the following additional technical features:

[0010] In some embodiments of the present invention, the heat exchange device also includes a first air distributor disposed inside the shell assembly, the first air distributor is connected to the shell assembly in a detachable manner, and the first air distributor is disposed between the air inlet and the air flow chamber, and the first air distributor is used to separately adjust the gas flow entering each of the air flow channels.

[0011] In some embodiments of the present invention, the heat exchange device also includes a second air separator disposed inside the shell assembly, the second air separator is connected to the shell assembly in a detachable manner, and along the first direction, the second air separator is arranged opposite to the first air separator, the second air separator is disposed between the air outlet and the airflow chamber, and the second air separator is used to stabilize the air pressure of each of the airflow channels.

[0012] In some embodiments of the present invention, both the first gas separation member and the second gas separation member are gas separation plates, and at least two gas separation areas are arranged on the gas separation plate, and each gas separation area corresponds to one gas flow channel;

[0013] Wherein, a plurality of gas separation holes are opened on the gas separation zone, and the opening area on each gas separation zone is different from the opening area on another gas separation zone.

[0014] In some embodiments of the present invention, the heat exchange device includes a heat exchange part, which is connected to one of the air flow channels, and the heat exchange part is used to transport the air flow after heat exchange with the refrigerant pipeline to the heat exchange component for heat exchange.

[0015] In some embodiments of the present invention, the heat exchange part includes a heat exchange inlet and a heat exchange outlet arranged on the shell assembly, and the heat exchange device also includes a middle partition, and the middle partition is arranged in at least one of the air flow channels, and the middle partition divides the air flow channel into a first area and a second area isolated from each other, the first area is respectively connected to the heat exchange inlet and the air inlet, and the second area is respectively connected to the heat exchange outlet and the air outlet.

[0016] In some embodiments of the present invention, the housing assembly comprises an air inlet end cover and an air outlet end cover arranged opposite to each other along the first direction, the air inlet is arranged on the air inlet end cover, and the air outlet is arranged on the air outlet end cover;

[0017] Wherein, the axial direction of the air inlet is perpendicular to the first direction, and the axial direction of the air outlet is parallel to the first direction.

[0018] In some embodiments of the present invention, the air inlet and the air outlet are spaced apart along a direction perpendicular to the first direction.

[0019] In some embodiments of the present invention, the air intake end cover is provided with an air intake cavity and a first flow stabilizing cavity which are connected to each other. The air intake cavity is located on one side of the air intake end cover and is connected to the air inlet. The cross-sectional area of ​​the first flow stabilizing cavity gradually decreases in a direction away from the air intake cavity.

[0020] And / or, the outlet end cover is provided with an outlet cavity and a second flow stabilizing cavity which are connected, the outlet cavity is located on one side of the outlet end cover and is connected to the outlet, and the cross-sectional area of ​​the second flow stabilizing cavity gradually decreases in the direction away from the outlet cavity.

[0021] In some embodiments of the present invention, the shell assembly also includes a first end cover and a second end cover arranged relative to each other in a direction perpendicular to the first direction, the first end cover is provided with a refrigerant inlet and a refrigerant outlet, the refrigerant assembly includes a first support plate and a second support plate, the first end cover and the first support plate together form a first chamber and a second chamber, the first chamber is connected to the refrigerant inlet, the second chamber is connected to the refrigerant outlet, the second end cover and the second support plate together form a guide channel, and the guide channel is used to guide the refrigerant entering from the first chamber to the second chamber.

[0022] In some embodiments of the present invention, the refrigerant pipeline is arranged along a second direction, and the second direction and the first direction are perpendicular to each other.

[0023] In some embodiments of the present invention, the partition assembly includes at least one partition plate, and the partition plate is disposed in the airflow cavity. At least one of the partition plates divides the airflow cavity into at least two airflow channels isolated from each other.

[0024] A second aspect of the present invention provides an air conditioning system, which includes the above-mentioned heat exchange device. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Various other advantages and benefits will become apparent to those of ordinary skill in the art by reading the detailed description of the preferred embodiments below. The accompanying drawings are only for the purpose of illustrating the preferred embodiments and are not to be considered as limiting the present invention. Moreover, the same reference numerals are used throughout the accompanying drawings to represent the same components. In the accompanying drawings:

[0026] Figure 1 The structure diagram of the heat exchange device according to the embodiment of the present invention is schematically shown;

[0027] Figure 2 The exploded structure diagram of the heat exchange device according to the embodiment of the present invention is schematically shown;

[0028] Figure 3 Schematically showing a first perspective view of a heat exchange device according to an embodiment of the present invention;

[0029] Figure 4 Shows Figure 3 Sectional view of the AA plane;

[0030] Figure 5 Shows Figure 3 Sectional view of the middle BB plane;

[0031] Figure 6 The structure diagram of the gas distribution plate according to the embodiment of the present invention is schematically shown;

[0032] Figure 7 The first part of the heat exchange device according to the embodiment of the present invention is schematically shown;

[0033] Figure 8 The second part of the heat exchange device according to the embodiment of the present invention is schematically shown;

[0034] Fig. 9 The schematic diagram of the structure of the partition plate according to the embodiment of the present invention is schematically shown;

[0035] Fig.10 Schematically showing a first perspective view of a separator plate according to an embodiment of the present invention;

[0036] Fig.11 A schematic diagram of the structure of a first support plate according to an embodiment of the present invention is shown;

[0037] Fig.12 Schematically showing a first perspective view of a first support plate according to an embodiment of the present invention;

[0038] Fig.13 The schematic diagram of the structure of the bottom plate according to the embodiment of the present invention is shown schematically;

[0039] Fig.14 Schematically showing a first perspective view of a base plate according to an embodiment of the present invention;

[0040] Fig.15 Schematically showing a second perspective view of a heat exchange device according to an embodiment of the present invention;

[0041] Fig.16 Shows Fig.15 Sectional view of the middle CC plane;

[0042] Fig.17 The working flow chart of the heat exchange device according to the embodiment of the present invention is schematically shown.

[0043] The reference numerals are as follows:

[0044] 100. Heat exchange device;

[0045] 10. Shell assembly; 101. Air inlet; 102. Air outlet; 103. Refrigerant inlet; 104. Refrigerant outlet; 105. Heat exchange inlet; 106. Heat exchange outlet; 107. Air flow cavity; 1071. First area; 1072. Second area; 1073. Third area;

[0046] 11. Inlet end cover; 111. Inlet cavity; 112. First flow stabilizing cavity; 12. Outlet end cover; 121. Outlet cavity; 122. Second flow stabilizing cavity; 13. First end cover; 131. First chamber; 132. Second chamber; 14. Second end cover; 141. Flow guide channel; 15. Upper cover plate; 16. Base; 17. Mounting bracket; 18. Bottom plate;

[0047] 20. refrigerant assembly; 21. first support plate; 22. refrigerant pipeline; 23. second support plate;

[0048] 30. First gas distribution component; 301. First gas distribution area; 302. Second gas distribution area; 303. Gas distribution hole; 31. Second gas distribution component;

[0049] 40. partition plate; 50. middle partition plate;

[0050] 60. Water collecting part; 61. First water collecting tank; 62. Second water collecting tank; 63. Third water collecting tank; 64. Fourth water collecting tank; 65. Connecting pipe; 66. Drainage outlet. DETAILED DESCRIPTION

[0051] The exemplary embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. Although the exemplary embodiments of the present disclosure are shown in the accompanying drawings, it should be understood that the present disclosure can be implemented in various forms and should not be limited by the embodiments described herein. On the contrary, these embodiments are provided in order to enable a more thorough understanding of the present disclosure and to fully convey the scope of the present disclosure to those skilled in the art.

[0052] It should be understood that the terms used herein are only for the purpose of describing specific example embodiments and are not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms "one", "an" and "said" as used herein may also be meant to include plural forms. The terms "include", "comprise", "contain", and "have" are inclusive, and therefore specify the existence of stated features, steps, operations, elements and / or parts, but do not exclude the existence or addition of one or more other features, steps, operations, elements, parts, and / or combinations thereof. The method steps, processes, and operations described herein are not interpreted as necessarily requiring them to be performed in the specific order described or illustrated, unless the execution order is clearly indicated. It should also be understood that additional or alternative steps may be used.

[0053] Although the terms first, second, third, etc. can be used in the text to describe multiple elements, components, regions, layers and / or sections, these elements, components, regions, layers and / or sections should not be limited by these terms. These terms can only be used to distinguish an element, component, region, layer or section from another region, layer or section. Unless the context clearly indicates, terms such as "first", "second" and other numerical terms do not imply order or sequence when used in the text. Therefore, the first element, component, region, layer or section discussed below can be referred to as the second element, component, region, layer or section without departing from the teaching of the example embodiments.

[0054] For ease of description, spatial relative terms may be used herein to describe the relationship of one element or feature relative to another element or feature as shown in the figure, such as "inside", "outside", "inner side", "outer side", "below", "below", "above", "above", etc. Such spatial relative terms are intended to include different orientations of the device in use or operation in addition to the orientation depicted in the figure. For example, if the device in the figure is turned over, then the elements described as "below other elements or features" or "below other elements or features" will subsequently be oriented as "above other elements or features" or "above other elements or features". Therefore, the example term "below..." can include both above and below orientations.

[0055] like Figures 1 to 16 As shown, according to an embodiment of the present invention, a heat exchange device 100 is proposed, including a shell component 10, a refrigerant component 20 and a partition component, wherein the shell component 10 is provided with an air inlet 101 and an air outlet 102, and the shell component 10 is provided with an air flow cavity 107 arranged along a first direction, and the air flow cavity 107 is respectively connected with the air inlet 101 and the air outlet 102, and the first direction is the direction from the air inlet 101 to the air outlet 102, and the refrigerant component 20 includes a plurality of refrigerant pipes 22 passing through the air flow cavity 107, and the partition component is arranged in the air flow cavity 107, and the partition component divides the air flow cavity 107 into at least two mutually isolated air flow channels, each of which is respectively connected with the air inlet 101 and the air outlet 102, and the air flow channel guides the air flow from the air inlet to the air outlet. A refrigerant pipe 22 is arranged in each air flow channel, and the number of refrigerant pipes 22 in any two air flow channels is different.

[0056] According to the heat exchange device 100 of this embodiment, the high-temperature gas enters the shell component 10 from the air inlet 101 and enters the airflow cavity 107 along the first direction. Then, the airflow in the airflow cavity 107 is affected by the partition component and is divided into at least two independent airflow channels and enters different airflow channels. Different airflow channels are provided with different numbers of refrigerant pipes 22. The airflow cavity 107 is divided into a plurality of independent airflow channels by the partition component, so that the airflow can flow in a directional manner along a preset path. This segmented airflow channel layout avoids the disordered flow of the airflow in the heat exchanger, reduces the generation of vortices and dead zones, thereby improving the contact efficiency between the airflow and the refrigerant pipe 22, so that the airflow can fully flow through the refrigerant pipe 22, improves the heat exchange efficiency per unit time, and achieves a rapid cooling effect. In addition, by dividing the airflow channel into a plurality of independent parts, the gas can be cooled more evenly in each channel. In the conventional heat exchange device 100, due to the uneven cooling effect of the cooling fluid at different positions, insufficient heat exchange or overcooling may occur in some areas. The present invention effectively reduces the temperature difference deviation through segmented cooling, making the gas temperature in each air flow channel more uniform, fully utilizing the temperature gradient of the refrigerant, and improving the overall heat exchange efficiency.

[0057] It is understandable that if Fig.17 As shown, arrow a1 indicates high-temperature airflow entering the airflow chamber 107; arrow a2 indicates high-temperature airflow flowing out of the airflow chamber 107 after heat exchange; arrow b1 indicates refrigerant liquid entering the refrigerant pipe 22; arrow b2 indicates refrigerant liquid flowing out of the refrigerant pipe 22; a3 indicates airflow going to the heat exchange component after partial cooling; a4 indicates airflow returning from the heat exchange component after heat exchange.

[0058] It is understandable that the refrigerant liquid may be Freon.

[0059] It is understandable that if 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).

[0060] In some embodiments, the refrigerant pipe 22 is arranged along the second direction, and the second direction is perpendicular to the first direction, which means that the arrangement direction of the refrigerant pipe 22 is perpendicular to the flow direction of the airflow channel, and such a design is conducive to increasing the contact area between the airflow and the refrigerant. When the airflow passes through the refrigerant pipe 22, the vertical design of the gas flow direction and the direction of the refrigerant pipe 22 allows the gas to contact the surface of the refrigerant pipe 22 to the greatest extent, and increasing the contact area can enhance the effect of convective heat exchange and improve the heat exchange efficiency. At the same time, the refrigerant pipe 22 is penetrated along the second direction, so that when the airflow flows through the airflow cavity 107, it will perform multiple heat exchanges with the refrigerant in the vertical direction, and this multi-point contact method can disperse heat more evenly. Since the directions of gas flow and refrigerant flow are perpendicular to each other, the gas can fully flow in the gap of the refrigerant pipe 22, and it is not easy to form a local hot spot with a large temperature gradient, thereby ensuring the uniformity of the internal temperature of the heat exchange device 100. In addition, when the refrigerant pipe 22 is arranged along the second direction, the gas flow does not have to bypass the refrigerant pipe 22 for complex path adjustment, but directly intersects with it, which can reduce the turning and disturbance of the airflow during the flow process, thereby reducing the airflow resistance and pressure loss, making the operation of the entire heat exchange device 100 more stable. After reducing the airflow resistance, the energy efficiency ratio of the system can be improved, and a higher heat exchange effect can be achieved at the same power. Finally, the design of the refrigerant pipe 22 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 with the design in which the refrigerant pipe 22 is parallel to the airflow channel, this vertical intersection method allows the heat exchange device 100 to occupy a smaller space with the same heat exchange area.

[0061] It can be understood that the shell assembly 10 includes a first end cover 13 and a second end cover 14 arranged opposite to each other along the second direction, and a refrigerant inlet 103 and a refrigerant outlet 104 are provided on the first end cover 13. The refrigerant assembly 20 includes a first support plate 21 and a second support plate 23. The first end cover 13 and the first support plate 21 together form a first chamber 131 and a second chamber 132, and the second end cover 14 and the second support plate 23 together form a guide 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 part of the refrigerant pipe 22, and the second chamber 132 is connected to the first port and the refrigerant outlet 104 of another part of the refrigerant pipe 22. The guide channel 141 is connected to the second ports of all the refrigerant pipes 22, and the guide 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 part of the refrigerant pipe 22, absorbing most of the heat of the high-temperature gas in the airflow chamber 107. At this time, the temperature of the refrigerant rises, but it still has cooling capacity. Through the drainage channel, the refrigerant re-enters another part 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 enable the refrigerant to make more full use of its own cooling capacity and improve the overall cooling effect. At the same time, the refrigerant undergoes secondary heat exchange in another part of the refrigerant pipe 22, absorbing residual heat and realizing the gradual distribution and utilization of heat, ensuring that the refrigerant can be fully utilized in each heat exchange stage, avoiding the direct waste of the refrigerant's cooling capacity after the initial heat exchange, and making the system's heat management more efficient and reasonable.

[0062] It is understandable that the shell assembly 10 also includes an air inlet cover 11 and an air outlet cover 12 arranged relatively along the first direction, the air inlet 101 is arranged on the air inlet cover 11, and the air outlet 102 is arranged on the air outlet cover 12, wherein the axial direction of the air inlet 101 is perpendicular to the first direction, and the axial direction of the air outlet 102 is parallel to the first direction. After entering the air inlet cover 11, the airflow diffuses in the vertical direction, so that the airflow begins to be evenly distributed before entering the airflow cavity 107. This design helps to slow down the flow rate before the airflow enters the airflow cavity 107, avoiding the flow turbulence caused by the airflow directly entering the airflow cavity 107. By performing preliminary diffusion and distribution in the air inlet cover 11, the airflow is more stable when entering the airflow cavity 107, reducing the turbulence of the airflow and the pressure loss caused by it. This enables the airflow to maintain a higher efficiency when exchanging heat with the refrigerant pipe 22 later. The axial direction of the gas outlet 102 is parallel to the first direction, so that the gas can flow smoothly to the outlet along the first direction after passing through the refrigerant pipe 22 in the gas flow cavity 107. This parallel flow design helps to maintain the flow direction of the gas flow in the gas flow cavity 107 and avoid the gas flow from changing direction suddenly at the outlet. By reducing the change in direction, the generation of turbulence and eddy current is reduced, thereby reducing the energy loss in the gas flow and improving the operating efficiency of the entire heat exchange device 100.

[0063] Specifically, along the second direction, the air inlet 101 and the air outlet 102 are spaced apart, which means that the air inlet 101 and the air outlet 102 are not located in the same horizontal plane, but have a certain distance along the second direction. First, the air inlet 101 and the air outlet 102 are spaced apart along the second direction, forcing the airflow to flow through a larger area in the airflow cavity 107, so that it can be more evenly distributed in the entire heat exchange area. This uniform airflow distribution helps to avoid the problem of insufficient heat exchange in some areas due to concentrated airflow, and overcooling in other areas due to slow airflow velocity, thereby reducing uneven cooling and ensuring the uniformity of the outlet gas temperature. Secondly, the airflow has a longer flow path in the airflow cavity 107, and the spacing design of the air inlet 101 and the air outlet 102 enables the airflow to flow smoothly, reducing the generation of turbulence. Reduced turbulence means a decrease in flow resistance, which not only helps to reduce the energy loss when the airflow passes through the heat exchange device 100, but also reduces pressure loss. This design of reducing turbulence and pressure loss enables the heat exchange device 100 to handle more gas flow at the same energy consumption, thereby improving the energy efficiency ratio of the system. In addition, when the air flow passes through the refrigerant pipe 22, condensate may be generated due to cooling. The spacing design of the air inlet 101 and the air outlet 102 in the second direction allows the condensate to have a sufficient flow distance in the air flow cavity 107, which is conducive to the discharge of the condensate along the air flow direction. This design reduces the accumulation of condensate inside the air flow cavity 107, helps to prevent the problem of reduced heat exchange efficiency caused by the accumulation of condensate, thereby reducing the maintenance frequency of the heat exchange device 100 and extending the service life of the heat exchange device 100. Finally, since the air inlet 101 and the air outlet 102 are spaced apart, the air flow needs to pass a certain distance after entering the air flow cavity 107 and flow to the air outlet 102 along a longer path. This design makes the air flow in the cavity more stable, avoiding turbulence and vibration caused by the air inlet and outlet being too close. Reducing the turbulence and vibration of the airflow can significantly reduce the noise generated by the heat exchange device 100 during operation, improve the operating comfort of the heat exchange device 100, and is particularly suitable for applications that require a low-noise environment.

[0064] Furthermore, the air inlet end cover 11 is provided with an air inlet cavity 111 and a first flow stabilizing cavity 112 which are connected. The air inlet cavity 111 is located on one side of the air inlet end cover 11 and is connected to the air inlet port 101 for receiving external airflow. The first flow stabilizing cavity 112 is located in the direction away from the air inlet cavity 111 and is connected to the air inlet cavity 111. Along the direction away from the air inlet cavity 111, the cross-sectional area of ​​the first flow stabilizing cavity 112 gradually decreases, that is, the shape of the first flow stabilizing cavity 112 is similar to a gradually narrowing channel. This gradually narrowing design helps to effectively guide and stabilize the airflow before the airflow enters the airflow cavity 107, so that the airflow is smoother when entering the airflow cavity 107. At the same time, the air outlet end cover 12 is provided with an air outlet cavity 121 and a second flow stabilizing cavity 122 which are connected. The air outlet cavity 121 is located on one side of the air outlet end cover 12 and is connected to the air outlet port 102 for discharging the gas after heat exchange. The second flow stabilization chamber 122 is located in the direction away from the outlet chamber 121 and is connected to the outlet chamber 121. Along the direction away from the outlet chamber 121, the cross-sectional area of ​​the second flow stabilization chamber 122 gradually decreases, similar to a gradually narrowing outlet channel. This design can adjust the flow rate before the airflow is discharged, so that the airflow is more stable when it is discharged from the airflow chamber 107. Therefore, when the gas flows into the first flow stabilization chamber 112, the design of gradually decreasing cross-sectional area can gradually smooth the high-speed incoming airflow, reduce the turbulence caused by the sudden deceleration of the airflow or the corner, thereby improving the stability of the airflow. Similarly, when the gas flows through the second flow stabilization chamber 122 and is ready to be discharged, this design can smooth the gas discharge process, avoid the turbulence generated when the airflow is discharged from the heat exchange device 100, and make the airflow leave the device more evenly, reducing the disturbance to the downstream equipment.

[0065] It can be understood that the shell assembly 10 also includes a bottom plate 18 and an upper cover plate 15, which are arranged relative to each other in a direction perpendicular to the third direction (the third direction is respectively perpendicular to the first direction and the second direction), and the bottom plate 18, the upper cover plate 15, the first end cover 13, the second end cover 14, the air inlet end cover 11 and the air outlet end cover 12 are surrounded by six components to form an airflow cavity 107. The bottom plate 18 and the upper cover plate 15 are arranged relative to each other in a direction perpendicular to the third direction, that is, the two are respectively located at the upper and lower sides of the airflow cavity 107. The bottom plate 18, the upper cover plate 15, the first end cover 13, the second end cover 14, the air inlet end cover 11 and the air outlet end cover 12 are combined to form a closed airflow cavity 107. In the airflow cavity 107, the high-temperature gas enters from the air inlet end cover 11, and performs heat exchange with the refrigerant pipe 22 inside, and is finally discharged from the air outlet end cover 12.

[0066] Specifically, a base 16 is provided at the lower part of the bottom plate 18, and the base 16 is used to support the entire shell assembly 10. The base 16 is tightly connected to the bottom plate 18 and provides a stable foundation, so that the entire heat exchange device 100 can be firmly fixed on the ground or other supporting platforms during installation. A mounting bracket 17 is provided at the upper part of the upper cover plate 15, and the mounting bracket 17 is used to fix the heat exchange device 100 with an external supporting structure (such as a bracket of an air conditioning system), thereby sharing the gravity borne by the base 16. The base 16 of the bottom plate 18 provides a stable support point, so that the entire shell assembly 10 is not easy to tilt or move during installation, and the overall stability of the heat exchange device 100 is effectively improved. At the same time, the mounting bracket 17 transmits part of the gravity to the external supporting structure through the connection with the upper cover plate 15, reducing the weight directly borne by the base 16. In this way, the deformation problem of the bottom plate 18 or the base 16 caused by the weight of the shell assembly 10 being concentrated on the base 16 can be avoided, and the structural stability of the heat exchange device 100 during long-term operation can be ensured.

[0067] In some embodiments, the heat exchange device 100 further includes a heat exchange part, which is connected to an air flow channel, and the heat exchange part is used to transport the airflow after heat exchange with the refrigerant pipe 22 to the heat exchange part for heat exchange. The heat exchange part guides the airflow that has been preliminarily cooled by the refrigerant pipe 22 to the heat exchange part, and the cooled airflow can directly contact the surface or internal flow channel of the heat exchange part, thereby quickly absorbing the heat of the heat exchange part to achieve an efficient cooling effect. The connection between the heat exchange part and the air flow channel enables the airflow to be distributed to the components that need to be cooled as needed during the cooling process, avoiding the situation where the cooling airflow circulates ineffectively or dissipates heat in the air flow chamber 107. At the same time, this flexible adjustment capability enables the heat exchange device 100 to quickly adapt to changing cooling needs when dealing with different working conditions, thereby achieving efficient temperature management.

[0068] It can be understood that there are multiple airflow channels, each of which is connected to a heat exchange part, and each of which exchanges heat with a heat-exchanged component.

[0069] Specifically, a heat exchange unit and an air flow channel are used as an example for explanation. The heat exchange unit 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 air flow channel through the heat exchange inlet 105. After the heat exchange pipe exchanges heat with the heat exchange element, the airflow returns to the air flow channel from the heat exchange outlet 106. The heat exchange device 100 includes a middle partition 50. The middle partition 50 is provided in at least one air flow channel. The middle partition 50 blocks the air flow channel along a first direction. The middle partition 50 divides the air flow channel into a first area 1071 connected to the air inlet 101 and a second area 1072 connected to the air outlet 102. The first area 1071 and the second area 1072 are isolated from each other. The heat exchange inlet 105 is connected to the first area 1071, and the heat exchange outlet 106 is connected to the second area 1072. The high-temperature gas enters the first area 1071 from the air inlet 101, enters the heat exchange pipe through the heat exchange inlet 105, and exchanges heat with the heat exchange parts in the heat exchange pipe. The temperature of the airflow drops during the heat exchange process. The airflow after heat exchange enters the second area 1072 from the heat exchange outlet 106. In the second area 1072, the airflow is cooled again through the refrigerant pipe 22, and finally discharged from the air outlet 102 after cooling. The setting of the middle partition 50 divides the airflow channel into two areas, so that the airflow must pass through the heat exchange part for heat exchange before entering the second area 1072. This ensures that the airflow can fully utilize its cooling capacity before being discharged and perform multiple heat exchanges with the heat exchange parts. The reasonable connection path between the heat exchange part and the airflow channel allows the heat of the high-temperature gas to be effectively transferred multiple times before entering the air outlet 102, which helps to reduce the temperature of the heat exchange parts more quickly and significantly improve the cooling efficiency.

[0070] It is understandable that the number of refrigerant pipes 22 in the first area 1071 is greater than the number of refrigerant pipes 22 in the second area 1072. The first area 1071 plays the main role of heat exchange. After cooling the high-temperature airflow, it is transported from the heat exchange inlet 105 to the heat exchange pipe, and then returns to the second area 1072 from the heat exchange outlet 106. The refrigerant pipes 22 in the second area 1072 undertake a small part of the heat exchange function and exchange the heat generated by the heat exchange component. Due to the large number of refrigerant pipes 22 in the first area 1071, it undertakes the main heat exchange task. After entering the first area 1071, the high-temperature airflow undergoes large-scale heat exchange through a large number of refrigerant pipes 22, rapidly reducing the temperature of the airflow. The first area 1071 has a strong heat exchange capacity, so that the main heat of the high-temperature gas is initially released here, thereby achieving rapid cooling. The number of refrigerant pipes 22 in the second area 1072 is relatively small, and it undertakes a small part of the heat exchange task. After the initial cooling in the first area 1071, the airflow goes to the heat exchange part, and the temperature is higher than that of the airflow in the first area 1071. At this time, it enters the second area 1072 for heat exchange and adjusts the remaining heat. Through this staged cooling process, the cooling capacity of the refrigerant can be more efficiently utilized to achieve gradual cooling. At the same time, the asymmetric design of the number of refrigerant pipes 22 in the first area 1071 and the second area 1072 enables the heat exchange device 100 to be adjusted according to different working conditions. For example, when the heat exchange part generates a large amount of heat, the flow rate of the refrigerant pipe 22 in the first area 1071 can be appropriately adjusted to increase the initial heat exchange intensity while retaining the adjustment capacity of the second area 1072. This flexibility enables the heat exchange device 100 to quickly respond to different cooling needs by adjusting the refrigerant flow and heat exchange path when facing various load changes, thereby adapting to a variety of application scenarios.

[0071] In some embodiments, the partition assembly includes at least one partition plate 40, which is arranged in the airflow cavity 107 along the second direction. At least one partition plate 40 divides the airflow cavity 107 into at least two airflow channels that are isolated from each other and arranged along the first direction, and the airflow channels are respectively connected to the air inlet 101 and the air outlet 102. The partition plate 40 adopts a flat plate structure to divide the airflow cavity 107 into two airflow channels arranged along the first direction. The number of partition plates 40 can be multiple, and the airflow cavity 107 is divided into multiple airflow channels. The partition plate 40 divides the airflow cavity 107 into multiple airflow channels, so that the airflow in each channel can 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 to improve the overall heat exchange efficiency, especially when a large volume of airflow needs to be processed, the cooling capacity can be significantly improved through the multi-channel structure, and the cooling time can be shortened.

[0072] In some embodiments, the heat exchange device 100 also includes a first gas distributor 30 disposed inside the shell assembly 10, wherein the first gas distributor 30 is connected to the shell assembly 10 in a detachable manner, and the first gas distributor 30 is disposed between the air inlet 101 and the air flow chamber 107, and the first gas distributor 30 is used to adjust the gas flow entering each air flow channel respectively. The use of the first gas distributor 30 allows the air flow to be accurately distributed according to the cooling requirements of each air flow channel when entering the air flow chamber 107. By adjusting the gas flow entering each air flow channel, the heat exchange between the air flow and the refrigerant can be made more efficient. For example, when the temperature of the heat exchange component to be exchanged at a certain air flow channel is high, the gas flow of the channel can be increased by the first gas distributor 30 to increase the cooling intensity. On the contrary, in other channels with lower temperatures, the gas flow can be appropriately reduced to avoid unnecessary energy consumption. Since the first gas distributor 30 can independently adjust the gas flow of each air flow channel, the difference in cooling effect of each channel caused by uneven gas flow can be effectively avoided. This design can ensure that when the entire heat exchange device 100 operates in multiple channels in parallel, the airflow distribution in each airflow channel is more balanced, avoiding the problem of excessive flow rate in some channels due to excessive gas flow, or the problem of reduced heat exchange effect due to insufficient gas flow.

[0073] Furthermore, the heat exchange device 100 also includes a second gas separator 31 disposed inside the shell assembly 10. The second gas separator 31 is connected to the shell assembly 10 in a detachable manner. Along the first direction, the second gas separator 31 is arranged opposite to the first gas separator 30 and the structure can be the same. The second gas separator 31 is disposed between the gas outlet 102 and the gas flow chamber 107. The second gas separator 31 is used to stabilize the air pressure of each gas flow channel. The second gas separator 31 is disposed between the gas outlet 102 and the gas flow chamber 107, and is used to adjust the airflow in each gas flow channel to ensure that the air pressure of each gas flow channel remains stable before the gas is discharged from the gas flow chamber 107, and to control the flow resistance of different gas flow channels at the gas outlet 102, so that the gas flow of each gas flow channel is balanced, and to prevent pressure fluctuations caused by uneven gas flow. The first gas separator 30 and the second gas separator 31 are respectively located at the two ends of the gas inlet 101 and the gas outlet 102. By adjusting the airflow entering and exiting the gas flow chamber 107, the airflow in the entire gas flow chamber 107 can be adjusted in both directions. This two-way adjustment can balance the pressure distribution in the airflow channel, ensuring that the airflow maintains a stable speed and flow rate when flowing through the entire airflow channel, and effectively avoiding eddies, turbulence and airflow oscillations caused by uneven airflow.

[0074] Specifically, the first gas separation member 30 and the second gas separation member 31 are both gas separation plates, and at least two gas separation areas are arranged on the gas separation plate, and at least two gas separation areas are arranged one by one with at least two air flow channels, that is, each gas separation area is specifically used to control the air flow of the corresponding air flow channel, wherein a plurality of gas separation holes 303 are provided on the gas separation area, and the plurality of gas separation holes 303 on each gas separation area can have different apertures, quantities, or arrangements. However, there is a difference between the sum of the opening areas of the plurality of gas separation holes 303 on each gas separation area and the sum of the opening areas of the plurality of gas separation holes 303 on another gas separation area, which means that the total opening area of ​​the gas separation holes 303 on each gas separation area can be designed according to the cooling requirements to adapt to the air flow requirements of different air flow channels. The sum of the opening areas of the plurality of gas separation holes 303 on each gas separation area has a difference with other gas separation areas, so that different air flow channels can receive different amounts of gas flow. By adjusting the number and aperture of the gas separation holes 303, the air resistance entering the corresponding air flow channel can be changed. For example, reducing the aperture or number of a certain air distribution zone can increase the air resistance of the air distribution zone, thereby reducing the flow rate of airflow entering the channel; increasing the aperture or number of another air distribution zone can reduce the air resistance and increase the airflow. By setting the air distribution zone and the adjustable area of ​​the air distribution holes 303 on the air distribution plate, precise control of the gas flow of each air flow channel can be achieved. Different air flow channels can receive different air flow rates, thereby ensuring that the heat exchange between the air flow and the refrigerant is more matched. This precise airflow distribution helps to increase the air flow to improve the cooling effect when the high-temperature heat exchange parts require greater cooling intensity, while reducing the air flow in lower temperature areas to avoid overcooling and improve the overall heat exchange efficiency.

[0075] It is understandable that, since the air distribution plate is a detachable structure, when the heat exchange device 100 needs to adjust the airflow distribution, it can be achieved by replacing the air distribution plate, without the need for complex disassembly or modification of the heat exchange device 100. In this way, the time and labor costs can be greatly reduced during the maintenance and upgrade of the heat exchange device 100. This design flexibility makes the heat exchange device 100 more adaptable in different usage scenarios, and can be quickly iterated and upgraded according to different cooling requirements, realizing a variety of heat exchange solutions, and realizing rapid iteration of the heat exchange device 100.

[0076] Specifically, the two air distributors are connected to the air inlet cover 11 and the air outlet cover 12, respectively, to adjust the flow rate of the airflow entering and exiting the airflow channel. Each air distributor is fixed to the air inlet cover 11 or the air outlet cover 12 by bolts or screws. The position of the bolt hole matches the preset screw hole on the air inlet cover 11 or the air outlet cover 12, ensuring that the air distributor is tightly fixed after installation and will not loosen or shift due to the pressure of the airflow.

[0077] In some specific embodiments, the partition assembly includes a partition plate 40, which divides the airflow cavity 107 into two upper and lower airflow channels. A middle partition plate 50 is provided in the upper airflow channel, which divides the upper airflow channel into a first area 1071 and a second area 1072. The first area 1071 is connected to the air inlet 101, and the second area 1072 is connected to the air outlet 102. The middle partition plate 50 is not provided in the lower airflow channel, and the interior of the lower airflow channel is the third area 1073. For the convenience of description, the multiple refrigerant pipes 22 located in the third area 1073 are called the first core body, the multiple refrigerant pipes 22 located in the second area 1072 are called the third core body, and the multiple refrigerant pipes 22 located in the first area 1071 are called the second core body. The first core body and the second core body are multi-flow, and the third core body is a single-flow. Specifically, the refrigerant liquid enters the first chamber 131 from the refrigerant inlet 103, and then a portion of the refrigerant liquid enters the third core from the first chamber 131, and another portion of the refrigerant liquid enters a portion of the first core from the first chamber 131. The refrigerant liquid from the third core is guided to the second core from the guide channel 141 of the second end cover 14, and finally, the refrigerant liquid flows out from the first core and the second core to the second chamber 132, and finally flows out from the refrigerant outlet 104.

[0078] Furthermore, the gas distribution plate includes a first gas distribution area 301 and a second gas distribution area 302 . The first gas distribution area 301 is connected to the first region 1071 or the second region 1072 , and the second gas distribution area 302 is connected to the third region 1073 .

[0079] In some embodiments, the heat exchange device further includes a water collecting portion 60, which includes at least two interconnected water collecting structures and a drain port 66 disposed inside the shell assembly 10, and a water collecting structure is disposed on the inner wall of each air flow channel. Since each water collecting structure is disposed on the inner wall of its own air flow cavity 107, segmented condensed water collection can be achieved, and the condensed water generated by the refrigerant pipe 22 in each air flow channel is introduced into the water collecting structure, and then guided to the drain port 66 through the interconnected structures. In this way, even in the case of a large amount of condensed water, it can be ensured that the water flow does not overflow, and the retention phenomenon is effectively reduced.

[0080] It is understandable that during the operation of the heat exchange device 100, when the airflow flows from the air inlet 101 to the air outlet 102, a relatively high-speed airflow is formed in the airflow chamber 107. In this process, due to the difference in airflow speed and path, pressure differences are formed at different positions of the airflow chamber 107. Generally, the pressure near the air inlet 101 and the air outlet 102 are different, wherein the pressure near the air outlet 102 is generally lower, while the pressure near the air inlet 101 is higher.

[0081] Specifically, the water collection structure includes a first water collection tank 61, and the first water collection tank 61 is arranged at one end of the air flow channel connected to the air outlet 102 along the second direction. The first water collection tank 61 is arranged at one end of the air flow channel connected to the air outlet 102. Due to the pressure difference between the two ends of the air flow cavity 107, the condensed water will naturally flow from the area with higher pressure to the area with lower pressure. In this design, the condensed water will be affected by the pressure difference. After dripping from the surface of the refrigerant pipe 22, it will gradually flow along the inner wall of the air flow cavity 107 or the guide structure of the water collection tank to the end with lower pressure (usually a position close to the air outlet 102, that is, the area where the first water collection tank 61 is located). Such an arrangement can make full use of the condensed water driven by the pressure difference during the cooling process, and concentrate the condensed water to a position close to the air outlet 102 for collection. By rationally utilizing the flow characteristics of the air flow, the accumulation of condensed water in other positions of the air flow channel can be reduced, thereby avoiding the phenomenon of internal water accumulation and keeping the air flow channel unobstructed.

[0082] Specifically, in order to facilitate the first water collection tank 61 to collect condensed water, the water collection structure also includes a second water collection tank 62, which is arranged along the first direction and is connected to the first water collection tank 61. The second water collection tank 62 can collect condensed water in the area where the air flow channel is longer, and guide the collected condensed water into the first water collection tank 61. Through multi-point collection and centralized guidance, it is possible to avoid condensed water from being retained in the air flow channel for a long time, effectively reduce the phenomenon of condensed water gathering on the surface of the air flow channel, and prevent the occurrence of corrosion and mildew problems. At the same time, the arrangement direction of the second water collection tank 62 is consistent with the air flow direction, which means that the condensed water can flow forward along the path of the second water collection tank 62 under the impetus of the air flow, so as to enter the first water collection tank 61 more smoothly, thereby improving the overall condensed water collection efficiency.

[0083] Specifically, the water collection structure includes a third water collection trough 63. There is a connecting edge between the middle partition 50 and the air flow channel in the above embodiment. The third water collection trough 63 is along the edge. The third water collection trough 63 is arranged in the first area 1071 and is connected to the second water collection trough 62. The third water collection trough 63 is arranged along the connecting edge between the middle partition 50 and the air flow channel, so that it can effectively collect condensed water in the edge area. By utilizing the position characteristics of the edge, the third water collection trough 63 can capture the condensed water in time when it drips from the middle partition 50 and the edge of the air flow channel, preventing the condensed water from freely scattering in the air flow chamber 107, and ensuring the orderliness of the condensed water flow path. The third water collection trough 63 is connected to the second water collection trough 62, so that the condensed water can be gradually collected in the multi-stage water collection structure. By setting up a third water collection tank 63 in the first area 1071, the collection range of condensed water can be further expanded, so that the condensed water generated at different positions of the refrigerant pipe 22 can be effectively collected and introduced into the first water collection tank 61 through the second water collection tank 62 for discharge, thereby improving the efficiency of the overall condensed water management system.

[0084] Furthermore, there are two second water collecting tanks 62, which are arranged on both sides of the first area 1071, one of which is the connecting edge between the partition plate 40 and the first support plate 21, and the other is the connecting edge between the partition plate 40 and the second support plate 23. When condensed water is concentrated, if there is only a water collecting tank on one side, there may be too much water accumulation on one side, affecting the drainage speed and efficiency. By arranging the second water collecting tanks 62 on both sides of the first area 1071, the distribution of condensed water on both sides can be balanced to avoid the adverse effects of water accumulation on one side. In this way, the condensed water can flow evenly to the water collecting tanks on both sides, reducing the risk of local overload during drainage, thereby improving the drainage stability of the system.

[0085] Furthermore, the water collection structure includes a plurality of fourth water collection grooves 64 arranged along the first direction, the plurality of fourth water collection grooves 64 are opened on the inner wall of the air flow channel and are located in the first area 1071, and the plurality of fourth water collection grooves 64 are connected to the third water collection groove 63. The reason why a plurality of fourth water collection grooves 64 are arranged in the first area 1071 is that a large number of refrigerant pipes 22 are arranged in the first area 1071, and the first area 1071 is directly connected to the air inlet 101. When the refrigerant pipes 22 exchange heat with the high-temperature gas in this area, a large amount of condensate will be generated due to the rapid drop in temperature. The plurality of fourth water collection grooves 64 are arranged along the inner wall of the air flow channel, and can capture and collect the condensate in time where it is just formed, so as to prevent the condensate from accumulating too much in the first area 1071, and ensure that the condensate can be quickly guided to the drainage channel.

[0086] In some embodiments, the middle partition 50 is curved. The curved design of the middle partition 50 can make the airflow more uniform and stable when flowing inside the heat exchange device 100. The curved structure can reduce the turbulence of the airflow near the surface of the middle partition 50, thereby maintaining a smooth flow in the airflow channel. When the stability of the airflow is improved, it helps to enhance the heat exchange efficiency between the refrigerant pipe 22 and the airflow, thereby further improving the overall performance of the heat exchange device 100. At the same time, the middle partition 50 is designed to be curved, so that the condensate can flow more naturally along the curve to both sides when flowing on its surface. The curved structure can guide the condensate to flow downward along a predetermined flow path, thereby avoiding the condensate from being retained in a flat area. Such a design allows the condensate to quickly gather in the area where the sump is provided, thereby improving the drainage efficiency.

[0087] Specifically, the bottom plate 18 is located at the bottom side of the partition plate 40, and the bottom plate 18 and the upper cover plate 15 are respectively arranged on opposite sides of the partition plate 40. Part of the water collection structure is arranged on the bottom plate 18, and a drain port 66 is arranged at the bottom of the bottom plate 18. Through gravity, the condensed water is drained to the drain port 66 and discharged. Furthermore, a second water collection tank 62 is arranged on both sides of the bottom plate 18, and a first water collection tank 61 is arranged at one end of the bottom plate 18 connected to the exhaust port. The water collection structure on the bottom plate 18 is combined and connected with the partition plate 40 and other water collection tanks to form a multi-stage condensate collection and discharge system. The condensate is first preliminarily collected in the water collection structure around the partition plate 40 and the refrigerant pipe 22, and then flows to the water collection structure on the bottom plate 18 through gravity, and is finally introduced into the drain port 66. This multi-stage coordinated collection method can ensure that the condensate flows smoothly during the entire drainage process, and will not cause overflow due to insufficient water collection capacity at a certain point, thereby improving the stability of the drainage system.

[0088] It is understandable that a valve is provided at the drain port 66 , and when the heat exchange device 100 is in a non-operating state, the valve is opened to allow the condensed water at the drain port 66 to be discharged.

[0089] In some embodiments, the water collecting part 60 includes a connecting pipe 65, which is arranged 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 a connecting pipe 65, and the connecting pipe 65 is used to connect two adjacent water collecting structures. For example, the first water collecting tank 61 on the partition plate 40 and the first water collecting 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 collecting tank to the lower water collecting tank, and reduce the residence time of condensate in each water collecting structure. In this way, excessive accumulation of condensate in a certain water collecting tank can be prevented, and the risk of corrosion and mildew caused by long-term residence of condensate can be reduced, thereby protecting the internal components of the heat exchange device 100 and extending the life of the heat exchange device 100.

[0090] It can be understood that the second water collecting tank 62 or the fourth water collecting tank 64 has a certain slope along the gravity direction, and the side close to the air inlet 101 is higher than the side close to the air outlet 102. The water collecting tank is set with a slope along the gravity direction, so that the condensate can flow naturally downward with the help of gravity when flowing in the tank. Such a design can reduce the retention time of the condensate in the water collecting tank, avoid the accumulation of water caused by the stagnation of the condensate, thereby significantly improving the drainage efficiency, so that the condensate can be guided to the drain more quickly. The first water collecting tank 61 and the third water collecting tank 63 have a certain slope along the second direction, and the side close to the drain 66 is higher than the side away from the drain 66. The first water collecting tank 61 and the third water collecting tank 63 have a slope along the second direction, so that the condensate can flow naturally to the drain 66 in the tank with the help of gravity. Such a design can ensure that the condensate flows quickly in the water collecting tank toward the drain, reduce the retention time of the condensate in the water collecting tank, and thus greatly improve the drainage efficiency.

[0091] The above is only a preferred specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any changes or substitutions that can be easily thought of by a person skilled in the art within the technical scope disclosed by the present invention should be included in the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.

Claims

1. A heat exchange device, characterized in that: include: A shell component, wherein an air inlet and an air outlet are provided on the shell component, and an air flow cavity arranged along a first direction is provided inside the shell component, and the air flow cavity is respectively connected with the air inlet and the air outlet, and the first direction is the direction from the air inlet to the air outlet; A refrigerant assembly, the refrigerant assembly comprising a plurality of refrigerant pipes passing through the airflow cavity; A partition component is arranged in the airflow cavity, and the partition component divides the airflow cavity into at least two airflow channels isolated from each other. Each of the airflow channels is respectively connected to the air inlet and the air outlet. Each of the airflow channels is provided with the refrigerant channel, and the number of the refrigerant pipelines in any two of the airflow channels is different.

2. The heat exchange device according to claim 1, characterized in that: The heat exchange device also includes a first air distributor arranged inside the shell assembly, the first air distributor is connected to the shell assembly in a detachable manner, and the first air distributor is arranged between the air inlet and the air flow chamber, and the first air distributor is used to separately adjust the gas flow entering each of the air flow channels.

3. The heat exchange device according to claim 2, characterized in that: The heat exchange device also includes a second air separator arranged inside the shell assembly, the second air separator is connected to the shell assembly in a detachable manner, and along the first direction, the second air separator is arranged opposite to the first air separator, the second air separator is arranged between the air outlet and the airflow cavity, and the second air separator is used to stabilize the air pressure of each of the airflow channels.

4. The heat exchange device according to claim 3, characterized in that: The first gas separation member and the second gas separation member are both gas separation plates, and at least two gas separation areas are arranged on the gas separation plate, and each gas separation area corresponds to one gas flow channel; Wherein, a plurality of gas separation holes are opened on the gas separation zone, and the opening area on each gas separation zone is different from the opening area on another gas separation zone.

5. The heat exchange device according to claim 1, characterized in that: The heat exchange device includes a heat exchange part, which is connected to one of the air flow channels. The heat exchange part is used to transport the air flow after heat exchange with the refrigerant pipeline to the heat exchange component for heat exchange.

6. The heat exchange device according to claim 5, characterized in that: The heat exchange part includes a heat exchange inlet and a heat exchange outlet arranged on the shell assembly, and the heat exchange device also includes a middle partition. The middle partition is arranged in at least one of the air flow channels, and the middle partition divides the air flow channel into a first area and a second area isolated from each other, the first area is respectively connected to the heat exchange inlet and the air inlet, and the second area is respectively connected to the heat exchange outlet and the air outlet.

7. The heat exchange device according to claim 1, characterized in that: The housing assembly comprises an air inlet end cover and an air outlet end cover which are arranged opposite to each other along the first direction, the air inlet is arranged on the air inlet end cover, and the air outlet is arranged on the air outlet end cover; Wherein, the axial direction of the air inlet is perpendicular to the first direction, and the axial direction of the air outlet is parallel to the first direction.

8. The heat exchange device according to claim 7, characterized in that: Along a direction perpendicular to the first direction, the air inlet and the air outlet are arranged at intervals.

9. The heat exchange device according to claim 8, characterized in that: The air intake end cover is provided with an air intake cavity and a first flow stabilizing cavity which are connected to each other. The air intake cavity is located on one side of the air intake end cover and is connected to the air inlet. The cross-sectional area of ​​the first flow stabilizing cavity gradually decreases in the direction away from the air intake cavity. And / or, the outlet end cover is provided with an outlet cavity and a second flow stabilizing cavity which are connected, the outlet cavity is located on one side of the outlet end cover and is connected to the outlet, and the cross-sectional area of ​​the second flow stabilizing cavity gradually decreases in the direction away from the outlet cavity.

10. The heat exchange device according to claim 1, characterized in that: The shell assembly also includes a first end cover and a second end cover arranged opposite to each other in a direction perpendicular to the first direction, and a refrigerant inlet and a refrigerant outlet are provided on the first end cover. The refrigerant assembly includes a first support plate and a second support plate. The first end cover and the first support plate together form a first chamber and a second chamber. The first chamber is connected to the refrigerant inlet, and the second chamber is connected to the refrigerant outlet. The second end cover and the second support plate together form a guide channel, and the guide channel is used to guide the refrigerant entering from the first chamber to the second chamber.

11. The heat exchange device according to any one of claims 1 to 10, characterized in that: The refrigerant pipeline is arranged along a second direction, and the second direction and the first direction are perpendicular to each other.

12. The heat exchange device according to any one of claims 1 to 10, characterized in that: The partition assembly includes at least one partition plate, which is arranged in the airflow cavity. At least one partition plate divides the airflow cavity into at least two airflow channels isolated from each other.

13. An air conditioning system, characterized in that: The air conditioning system comprises the heat exchange device according to any one of claims 1 to 12.

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