Liquid cooling plate and bidirectional inverter

Abstract

The utility model discloses a liquid cooling plate and a bidirectional inverter. The liquid cooling plate provided by the utility model comprises a shell and a turbulent flow assembly. A runner is arranged in the shell and comprises an inlet, an outlet and a first heat exchange area, and the first heat exchange area is located between the inlet and the outlet. The turbulent flow assembly is arranged in the first heat exchange area and comprises a first cylinder, a second cylinder and a first water drop column, and the conical end of the first water drop column is located on the upstream of the arc-shaped end of the first water drop column in the flowing direction of cooling liquid in the first heat exchange area. According to the liquid cooling plate provided by the embodiment of the utility model, the first circular cylinder and the second circular cylinder are respectively arranged at the inlet and the outlet of the first heat exchange area, and the circular turbulent flow assembly has a smaller turbulent flow effect and smaller resistance compared with a water-drop-shaped turbulent flow assembly, so that the inlet and the discharge of cooling liquid are not influenced while the turbulent flow function is considered, and the service life of the liquid cooling plate is prolonged. And the cooling liquid can smoothly enter and be discharged out of the first heat exchange area with the turbulent flow assembly.

Description

Technical Field

[0001] This utility model relates to the field of heat dissipation in energy storage systems, specifically to a liquid cooling plate and a bidirectional inverter. Background Technology

[0002] Liquid cooling plates indirectly transfer heat from heat-generating devices to cooling liquid enclosed in a circulating pipeline, with the cooling liquid carrying away the heat. With continuous advancements in science and technology, various devices are becoming smaller while their performance and power consumption are increasing, thus requiring stronger heat dissipation capabilities. Traditional cooling systems have limited heat dissipation capacity. By designing a flow-turbulence structure within the internal channels of the liquid cooling plate, better heat dissipation can be achieved with lower energy consumption. However, this structure suffers from a problem: due to excessive resistance at the inlet and outlet of the turbulence structure area, the coolant cannot smoothly enter and exit the area containing the turbulence structure. Utility Model Content

[0003] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a liquid cooling plate that allows coolant to smoothly enter and exit the region with a turbulence structure within the flow channel.

[0004] According to a first aspect of the present invention, a liquid-cooled plate includes a housing and a flow-dispersing assembly. A flow channel is provided within the housing for the flow of coolant. The flow channel includes an inlet, an outlet, and a first heat exchange zone, the first heat exchange zone being located between the inlet and the outlet. The flow-dispersing assembly is disposed within the first heat exchange zone and includes a first cylinder, a second cylinder, and a first water droplet column. The first cylinder is disposed at one end of the first heat exchange zone near the inlet, the second cylinder is disposed at one end of the first heat exchange zone near the outlet, and the first water droplet column is disposed between the first cylinder and the second cylinder, along the flow direction of the coolant within the first heat exchange zone, with the conical end of the first water droplet column located upstream of its arcuate end.

[0005] The liquid cooling plate according to the first aspect of the present invention has at least the following beneficial effects: the liquid cooling plate of the present invention provides a first circular cylinder and a second circular cylinder at the inlet and outlet of the first heat exchange zone, respectively. The circular turbulence component has a smaller turbulence effect and less resistance than the teardrop-shaped turbulence component. While taking into account the turbulence function, it does not affect the entry and exit of the coolant, so that the coolant can smoothly enter and exit the first heat exchange zone with the turbulence component.

[0006] According to some embodiments of the present invention, the turbulence component further includes a second water droplet column, the cross-sectional dimension of the second water droplet column being larger than that of the first water droplet column, the first heat exchange zone including a plurality of interconnected sub-zones, the second water droplet column being provided at the connection of adjacent sub-zones, and the conical end of the second water droplet column being located upstream of the arc-shaped end of the second water droplet column.

[0007] According to some embodiments of the present invention, the first heat exchange zone further includes a transition zone, which is located between the two sub-zones, and the second water droplet column is disposed in the transition zone. The width of the transition zone is smaller than the width of the sub-zones on both sides.

[0008] According to some embodiments of the present invention, the flow channel further includes a second heat exchange zone and a third heat exchange zone. The second heat exchange zone connects the first heat exchange zone and the third heat exchange zone. The third heat exchange zone connects the second heat exchange zone and the outlet. The second heat exchange zone is serpentine and the third heat exchange zone is serpentine.

[0009] According to some embodiments of the present invention, the second heat exchange zone and the third heat exchange zone are respectively located on both sides of the first heat exchange zone.

[0010] According to some embodiments of the present invention, there are multiple first cylinders, second cylinders, and first water droplet columns arranged along a first direction. The first cylinders, first water droplet columns, and second cylinders are distributed at intervals along a second direction. Along the second direction, adjacent first cylinders and first water droplet columns are staggered, adjacent second cylinders and first water droplet columns are staggered, and adjacent first water droplet columns are also staggered.

[0011] According to some embodiments of this utility model, the shell is made of aluminum alloy.

[0012] The bidirectional inverter according to a second aspect of the present invention includes a liquid-cooled plate as described in any one of the first aspect embodiments, and further includes a load, the load being mounted on the outer surface of the liquid-cooled plate, and the load and the flow channel undergoing heat transfer through the outer surface of the liquid-cooled plate.

[0013] According to the bidirectional inverter of the second aspect of the present invention, it has at least the following beneficial effects: the liquid cooling plate is provided with a first circular cylinder and a second circular cylinder at the inlet and outlet of the first heat exchange zone, respectively. The circular turbulence component has a smaller turbulence effect and less resistance than the teardrop-shaped turbulence component. While taking into account the turbulence function, it does not affect the entry and exit of the coolant, so that the coolant can smoothly enter and exit the first heat exchange zone with the turbulence component. When the bidirectional inverter using the liquid cooling plate injects coolant into the liquid cooling plate, the flow of coolant can also be made smoother, improving the coolant flow effect and circulation efficiency.

[0014] According to some embodiments of this utility model, the flow channel further includes a second heat exchange zone and a third heat exchange zone, wherein the path of the second heat exchange zone is serpentine, and the path of the third heat exchange zone is serpentine. The load includes a first load, a second load, and a third load, wherein the first load is thermally connected to the first heat exchange zone, the second load is thermally connected to the second heat exchange zone, and the third load is thermally connected to the third heat exchange zone.

[0015] According to some embodiments of the present invention, the power of the first load is greater than the power of the second load, and the power of the first load is greater than the power of the third load.

[0016] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0017] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0018] Figure 1 This is a first perspective view of a bidirectional inverter in one embodiment of the present invention;

[0019] Figure 2 This is an exploded view of a bidirectional inverter in one embodiment of the present invention;

[0020] Figure 3 This is a top view of the bottom shell of the liquid cooling plate in one embodiment of the present invention;

[0021] Figure 4 for Figure 3 Enlarged view of region A in the middle;

[0022] Figure 5 for Figure 4 Enlarged view of region B in the middle;

[0023] Figure 6 This is a second perspective view of a bidirectional inverter in one embodiment of the present invention.

[0024] Reference numerals: bidirectional inverter 100, liquid cooling plate 101, inlet 102, outlet 103, load 104, housing 201, flow channel 202, bottom shell 203, cover plate 204, first heat exchange zone 301, second heat exchange zone 302, third heat exchange zone 303, turbulence component 304, fourth heat exchange zone 305, first cylinder 401, second cylinder 402, first water droplet column 403, second water droplet column 404, sub-zone 405, transition zone 406, first load 601, second load 602, third load 603, fourth load 604. Detailed Implementation

[0025] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0026] In the description of this utility model, it should be understood that the directional descriptions, such as up, down, front, back, left, right, etc., indicate the directional or positional relationship based on the directional or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0027] In the description of this utility model, "several" means one or more, "multiple" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. The use of "first" and "second" in the description is merely for distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0028] In the description of this utility model, unless otherwise explicitly defined, terms such as "setting," "installation," and "connection" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this utility model in conjunction with the specific content of the technical solution.

[0029] In the description of this utility model, the terms "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this utility model. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0030] Turbulence refers to altering the flow state of a fluid to create instability, such as turbulence or eddies, thereby increasing energy loss and resistance. Near a solid surface, a low-velocity, low-turbulence fluid layer forms, hindering heat transfer from the bulk fluid to the solid surface. Turbulence disrupts this boundary layer, allowing for more thorough contact between the fluid and the fixed surface, thus improving heat transfer efficiency. Furthermore, turbulence generates more vortices and turbulence during flow, enhancing internal mixing and disturbance, resulting in more uniform and efficient heat transfer. Therefore, incorporating a turbulence component 304 into the flow channel 202 of the liquid-cooled plate 101 can effectively improve heat transfer efficiency.

[0031] Under this premise, according to the research paper "Study on the heat transfer performance of cold plates with different turbulence structures" in the Journal of Chemical Industry and Engineering, Vol. 74, No. 4, 2023, it can be seen that different shapes of turbulence columns have different turbulence effects. Among them, the teardrop-shaped turbulence column has the best turbulence effect and therefore the best heat transfer performance, followed by the circular column. Furthermore, teardrop turbulence columns with different length-to-width ratios, different sizes and densities will also have different turbulence and heat transfer performance.

[0032] refer to Figures 1 to 4 According to a first aspect embodiment of the present invention, the liquid cooling plate 101 includes a housing 201 and a flow-disrupting assembly 304. A flow channel 202 is provided inside the housing 201 for circulating coolant. The flow channel 202 includes an inlet 102, an outlet 103, and a first heat exchange zone 301, which is located between the inlet 102 and the outlet 103. The turbulence-disrupting component 304 is disposed within the first heat exchange zone 301. The turbulence-disrupting component 304 includes a first cylinder 401, a second cylinder 402, and a first water droplet column 403. The first cylinder 401 is disposed at one end of the first heat exchange zone 301 near the inlet 102, the second cylinder 402 is disposed at one end of the first heat exchange zone 301 near the outlet 103, and the first water droplet column 403 is disposed between the first cylinder 401 and the second cylinder 402. Along the flow direction of the coolant within the first heat exchange zone 301, the conical end of the first water droplet column 403 is located upstream of the arc-shaped end of the first water droplet column 403. Thus, in this embodiment of the present invention, the liquid cooling plate 101 is provided with a circular first cylinder 401 and a second cylinder 402 at the inlet and outlet 103 of the first heat exchange zone 301, respectively. The circular turbulence component 304 has a smaller turbulence effect and less resistance compared to the teardrop shape. While taking into account the turbulence function, it does not affect the entry and exit of the coolant, so that the coolant can smoothly enter and exit the first heat exchange zone 301 with the turbulence component 304.

[0033] It should be noted that the reference Figure 4 and Figure 5In some embodiments of this utility model, the first cylinder 401, the second cylinder 402, the first water droplet column 403, and the second water droplet column 404 refer to Figure 4 From a top-down perspective, the turbulence column is circular or teardrop-shaped, and the turbulence component 304 extends along this perspective and one end is connected to the bottom wall of the flow channel 202.

[0034] It should be noted that in some embodiments of this utility model, the coolant used is pure water, but propylene glycol, cooling oil, or other components can also be used.

[0035] It should be noted that the reference Figure 2 In some embodiments of this utility model, the housing 201 is a split design, including a bottom shell 203 and a cover plate 204. This design facilitates the processing of the internal flow channel 202 of the housing 201.

[0036] refer to Figure 4 and Figure 5 In some embodiments of this utility model, the turbulence component 304 further includes a second water droplet column 404, the cross-sectional dimension of which is larger than that of the first water droplet column 403. The first heat exchange zone 301 includes a plurality of interconnected sub-zones 405, and a second water droplet column 404 is provided at the connection point of adjacent sub-zones 405. The conical end of the second water droplet column 404 is located upstream of the arc-shaped end of the second water droplet column 404. Figure 5 As shown, the size of the second water droplet column 404 is larger than that of the first water droplet column 403. Therefore, the density of the second water droplet column 404 can be arranged in the same area, and the turbulence effect is also lower. Therefore, placing the second water droplet column 404 at the connection between the two sub-sections 405 can play a role in diverting the coolant. Specifically, since the conical end of the second water droplet column 404 is located upstream of the arc end, when the coolant flows to the vicinity of the second water droplet column 404, it will be diverted to both sides by the conical end. Therefore, the coolant can flow evenly to the left and right sides of the next sub-section 405, so that the next sub-section 405 can better turbulentize the coolant and improve the heat transfer performance of the coolant in the sub-section 405, thereby improving the heat exchange effect of the liquid cooling plate 101.

[0037] refer to Figure 4 and Figure 5 In some embodiments of this utility model, the first heat exchange zone 301 further includes a transition zone 406, which is located between two sub-zones 405. A second water droplet column 404 is disposed in the transition zone 406, and the width of the transition zone 406 is smaller than the width of the two sub-zones 405. Reducing the width of the transition zone 406 can reduce the unnecessary flow channel 202 area, improve the heat exchange efficiency of the flow channel 202, and improve the flow efficiency of the coolant in the non-heat exchange zone. Preferably, as shown... Figure 5As shown, the width of the transition zone 406 is set to accommodate only the conical end of a single second water droplet column 404, thereby maximizing the diversion effect of the second water droplet column 404.

[0038] It should be noted that in some embodiments of this utility model, the transition zone 406 is also provided with a certain inclination, and the transition zone 406 is inclined from both ends toward the middle along the flow direction of the coolant. This design can further improve the guiding effect of the transition zone 406 and improve the liquid flow efficiency.

[0039] refer to Figure 3 In some embodiments of this utility model, the flow channel 202 further includes a second heat exchange zone 302 and a third heat exchange zone 303. The second heat exchange zone 302 is connected to the first heat exchange zone 301 and the third heat exchange zone 303. The third heat exchange zone 303 is connected to the second heat exchange zone 302 and the outlet 103. The second heat exchange zone 302 is serpentine and the third heat exchange zone 303 is serpentine. The second heat exchange zone 302 and the third heat exchange zone 303 allow the liquid cooling plate 101 to simultaneously meet the heat exchange requirements of multiple loads 104. Different loads 104 can be thermally connected to different heat exchange zones. A serpentine shape increases the heat exchange area and improves the heat exchange effect. The specific heat exchange capacity can be adjusted by changing the shape of the serpentine pattern. Specifically, while keeping the total area constant, reducing the width of the serpentine pattern and increasing its bending frequency, while minimizing the gaps between bends, can effectively improve the heat exchange capacity. Increasing the overall area of ​​the second heat exchange zone 302 and the third heat exchange zone 303 also allows them to meet the heat exchange requirements of loads 104 of different sizes. The second heat exchange zone 302 and the third heat exchange zone 303 can also be configured in other shapes, such as multi-layered interlocking rings.

[0040] It should be noted that the reference Figure 3 In some embodiments of this utility model, in addition to the second heat exchange zone 302 and the third heat exchange zone 303, other heat exchange zones such as... can also be provided. Figure 3 The fourth heat exchange zone 305 shown is linear and is located between the first heat exchange zone 301 and the inlet 102. It can meet the requirements of the load 104 with a small cooling demand and further improve the overall heat exchange efficiency of the liquid cooling plate 101.

[0041] refer to Figure 3In some embodiments of this invention, the second heat exchange zone 302 and the third heat exchange zone 303 are located on opposite sides of the first heat exchange zone 301. This arrangement increases the distance between the second heat exchange zone 302 and the third heat exchange zone 303, allowing the coolant to flow through a longer flow channel 202 after heat exchange and temperature rise in the second heat exchange zone 302 before entering the third heat exchange zone 303, thus improving the flow effect of the coolant in the third heat exchange zone 303. Furthermore, this design allows the inlet 102 and outlet 103 to be located on the same side of the liquid cooling plate 101, facilitating the connection between the liquid cooling plate 101 and external liquid cooling pipes, as well as the circulation of the coolant.

[0042] refer to Figure 4 and Figure 5 In some embodiments of this utility model, multiple first cylinders 401, second cylinders 402, and first water droplet columns 403 are arranged along a first direction. The first cylinders 401, first water droplet columns 403, and second cylinders 402 are distributed at intervals along a second direction. Along the second direction, adjacent first cylinders 401 and first water droplet columns 403 are staggered, adjacent second cylinders 402 and first water droplet columns 403 are staggered, and adjacent first water droplet columns 403 are also staggered. This staggered distribution allows the coolant to flow along the second direction. After entering from the area of ​​the first cylinder 401, the positions of the first water droplet columns 403 and second cylinders 402 in each layer are not consistent with the previous layer, which can reduce the downstream flow of coolant, improve the turbulence effect on the coolant, and thus improve the heat exchange effect of the liquid cooling plate 101.

[0043] It should be noted that the reference Figure 5 As can be seen from the dashed line portion of the conical end of the first water droplet column 403, in some embodiments of this utility model, along the second direction, the extension directions of the inclined surfaces of the conical ends of adjacent first water droplets do not coincide. This design, based on the staggered positions, can further reduce the downstream flow of coolant and improve the turbulence effect and heat exchange effect.

[0044] It should be noted that the reference Figure 4 and Figure 5 In some embodiments of this utility model, a small number of second water droplet columns 404 and circular columns are also provided in the middle part and at the end of the sub-partition 405. This design is adjusted according to the actual size of the sub-partition 405 and the transition zone 406. If there is not enough space in the edge area, some circular columns or second water droplet columns 404 are provided to make the turbulence component 304 in the first heat exchange zone 301 as saturated as possible and improve the turbulence effect.

[0045] In some embodiments of this invention, the housing 201 is made of aluminum alloy. Aluminum alloy has a high thermal conductivity, enabling rapid heat transfer to the required location, achieving rapid heat dissipation and uniform distribution. Furthermore, aluminum alloy is a lightweight material, which, as a thermal conductor, reduces the overall weight of the liquid cooling plate 101, improving the user experience. Aluminum alloy also has good corrosion resistance and machinability, facilitating the fabrication of flow channels 202 of different shapes, and can adapt to different types of coolants, making it versatile and adaptable. In some embodiments of this invention, materials such as copper alloy may also be used.

[0046] refer to Figure 1 and Figure 6 According to a second aspect embodiment of the present invention, the bidirectional inverter 100 includes a liquid-cooled plate 101 as described in any of the first aspect embodiments, and also includes a load 104. The load 104 is mounted on the outer surface of the liquid-cooled plate 101, and the load 104 and the flow channel 202 transfer heat through the outer surface of the liquid-cooled plate 101. The liquid-cooled plate 101 has a first circular cylinder 401 and a second circular cylinder 402 respectively provided at the inlet and outlet 103 of the first heat exchange zone 301. The circular turbulence-disrupting component 304 has a smaller turbulence effect and lower resistance than the teardrop-shaped turbulence-disrupting component. While taking into account the turbulence-disrupting function, it does not affect the entry and exit of the coolant, allowing the coolant to smoothly enter and exit the first heat exchange zone 301 with the turbulence-disrupting component 304. When the bidirectional inverter 100 using the liquid-cooled plate 101 injects coolant into the liquid-cooled plate 101, the flow of the coolant is also smoother, improving the coolant flow effect and circulation efficiency.

[0047] refer to Figure 1 , Figure 2 and Figure 6 In some embodiments of this utility model, the flow channel 202 further includes a second heat exchange zone 302 and a third heat exchange zone 303. The path of the second heat exchange zone 302 is serpentine, and the path of the third heat exchange zone 303 is serpentine. The load 104 includes a first load 601, a second load 602, and a third load 603. The first load 601 is thermally connected to the first heat exchange zone 301, the second load 602 is thermally connected to the second heat exchange zone 302, and the third load 603 is thermally connected to the third heat exchange zone 303. This design allows the first heat exchange zone 301, the second heat exchange zone 302, and the third heat exchange zone 303 to perform heat exchange treatment on the first load 601, the second load 602, and the third load 603, respectively, so that the liquid cooling plate 101 can simultaneously cool and reduce the temperature of different loads 104 in the bidirectional inverter 100, thus meeting the heat exchange requirements.

[0048] It should be noted that the reference Figure 3 and Figure 6In some embodiments of this utility model, the flow channel 202 is further provided with a fourth heat exchange zone 305, and the bidirectional inverter 100 is further provided with a fourth load 604 that is thermally connected to the fourth heat exchange zone 305, so that the liquid cooling plate 101 can further meet the heat exchange requirements of more types of loads 104.

[0049] It should be noted that in some embodiments of this utility model, thermal grease is also provided between the load 104 and the outer surface of the housing 201. The thermal grease has high thermal conductivity and electrical insulation, which can further improve the thermal conductivity between the load 104 and the housing 201, thereby improving the cooling and heat exchange effect of the coolant in the flow channel 202 on the load 104.

[0050] In some embodiments of this invention, the power of the first load 601 is greater than the power of the second load 602, and the power of the first load 601 is greater than the power of the third load 603. Since the first heat exchange zone 301 is equipped with a turbulence-inducing component 304, its turbulence and heat transfer performance are optimal. Therefore, placing the first load 601 with the highest power in the first heat exchange zone 301 can maximize the fulfillment of heat exchange requirements. The second heat exchange zone 302 and the third heat exchange zone 303 can be equipped with loads 602 and 603 with relatively lower power and lower heat exchange requirements compared to the first load 601.

[0051] It should be noted that in some embodiments of this utility model, the power of the fourth load 604 is lower than that of the second load 602 and the third load 603, and its cooling requirement is also the lowest. Therefore, it is designed to be thermally connected to the shorter fourth heat exchange zone 305.

[0052] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present invention. Furthermore, the embodiments of the present invention and the features thereof can be combined with each other unless otherwise specified.

Claims

1. A liquid-cooled plate, characterized in that, include: A housing, wherein a flow channel is provided inside the housing for circulating coolant, the flow channel including an inlet, an outlet and a first heat exchange zone, the first heat exchange zone being located between the inlet and the outlet; A flow-disrupting component is disposed within the first heat exchange zone. The flow-disrupting component includes a first cylinder, a second cylinder, and a first water droplet column. The first cylinder is disposed at one end of the first heat exchange zone near the inlet, the second cylinder is disposed at one end of the first heat exchange zone near the outlet, and the first water droplet column is disposed between the first cylinder and the second cylinder, along the flow direction of the coolant within the first heat exchange zone. The conical end of the first water droplet column is located upstream of the arc-shaped end of the first water droplet column.

2. The liquid cooling plate according to claim 1, characterized in that, The turbulence-inducing component further includes a second water droplet column, the cross-sectional dimension of which is larger than that of the first water droplet column. The first heat exchange zone includes multiple interconnected sub-zones, and the second water droplet column is provided at the connection point of adjacent sub-zones. The conical end of the second water droplet column is located upstream of the arc-shaped end of the second water droplet column.

3. The liquid cooling plate according to claim 2, characterized in that, The first heat exchange zone further includes a transition zone located between the two sub-zones, and the second water droplet column is disposed in the transition zone. The width of the transition zone is smaller than the width of the sub-zones on both sides.

4. The liquid cooling plate according to claim 1, characterized in that, The flow channel further includes a second heat exchange zone and a third heat exchange zone. The second heat exchange zone connects the first heat exchange zone and the third heat exchange zone. The third heat exchange zone connects the second heat exchange zone and the outlet. The second heat exchange zone is serpentine, and the third heat exchange zone is serpentine.

5. The liquid cooling plate according to claim 4, characterized in that, The second heat exchange zone and the third heat exchange zone are located on both sides of the first heat exchange zone.

6. The liquid cooling plate according to claim 1, characterized in that, The first cylinder, the second cylinder, and the first water droplet are arranged in multiples along the first direction. The first cylinder, the first water droplet, and the second cylinder are distributed at intervals along the second direction. Along the second direction, adjacent first cylinders and first water droplets are distributed alternately, adjacent second cylinders and first water droplets are distributed alternately, and adjacent first water droplets are also distributed alternately.

7. The liquid cooling plate according to claim 1, characterized in that, The shell is made of aluminum alloy.

8. A bidirectional inverter, characterized in that, include: Liquid cooling plate as described in any one of claims 1-7; The load is mounted on the outer surface of the liquid cooling plate, and the load and the flow channel exchange heat through the outer surface of the liquid cooling plate.

9. The bidirectional inverter according to claim 8, characterized in that, The flow channel further includes a second heat exchange zone and a third heat exchange zone, the path of the second heat exchange zone is serpentine, and the path of the third heat exchange zone is serpentine; The load includes a first load, a second load, and a third load. The first load is thermally connected to the first heat exchange zone, the second load is thermally connected to the second heat exchange zone, and the third load is thermally connected to the third heat exchange zone.

10. The bidirectional inverter according to claim 9, characterized in that, The power of the first load is greater than the power of the second load, and the power of the first load is greater than the power of the third load.

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