Liquid cooling plate and cooling system

Abstract

The application provides a liquid cooling plate and a cooling system, and relates to the technical field of electronic equipment. The liquid cooling plate comprises an inlet and outlet plate, a jet plate and a heat exchange plate arranged in the order of a stack along the thickness direction of the liquid cooling plate. The inlet and outlet plate is provided with an inlet and an outlet. The jet plate and the inlet and outlet plate form a first cavity. The first cavity is in communication with the inlet and the outlet. The jet plate and the heat exchange plate form a second cavity. The jet plate is further provided with a shunt channel. The shunt channel is provided with a plurality of jet holes. The jet holes are in communication with the first cavity and the second cavity. At least one of the surfaces of the inlet and outlet plate and the jet plate is provided with a hydrophobic coating. The liquid cooling plate provided by the application can help to solve the problem of low cooling liquid flow efficiency in the existing liquid cooling plate.

Description

Technical Field

[0001] This application relates to the field of electronic equipment technology, and in particular to a liquid cooling plate and cooling system. Background Technology

[0002] With the rapid development of the server industry, server power demands continue to rise. Traditional air cooling can no longer meet these high heat dissipation requirements. Liquid cooling technology, on the other hand, offers significantly better cooling performance than air cooling and has become a key solution for heat dissipation in high-power servers.

[0003] Liquid cooling plates in related technologies generally adopt a microchannel flow channel design, which increases the heat exchange area by reducing the flow channel size to enhance heat dissipation.

[0004] However, the microchannels in the liquid cooling plates of related technologies have increased viscous resistance due to their small hydraulic diameter, which in turn leads to lower coolant flow efficiency. Utility Model Content

[0005] This application provides a liquid cooling plate and a cooling system, which helps to solve the problem of low coolant flow efficiency in existing liquid cooling plates.

[0006] In a first aspect, this application provides a liquid cooling plate, comprising: an inlet / outlet water plate, a jetting plate, and a heat exchange plate arranged sequentially along the thickness direction of the liquid cooling plate, wherein the inlet / outlet water plate is provided with an inlet and an outlet water outlet, a first cavity is formed between the jetting plate and the inlet / outlet water plate, the first cavity is respectively connected to the inlet water outlet and the outlet water outlet, and a second cavity is formed between the jetting plate and the heat exchange plate; the jetting plate is also provided with a flow distribution channel, the flow distribution channel is provided with a plurality of jetting holes, the jetting holes are respectively connected to the first cavity and the second cavity; at least one of the inlet / outlet water plate and the jetting plate is provided with a hydrophobic coating on its surface.

[0007] This design, through the flow distribution channels and multi-jet hole design of the jet plate, uniformly sprays the coolant from the first chamber to the second chamber. It replaces traditional long-distance microchannel flow with short-path impact heat exchange. Combined with the hydrophobic coating on the inlet / outlet plates or the jet plate surface, it reduces solid-liquid interface frictional resistance, significantly reducing fluid viscosity losses and pump power consumption. The jet impact achieves full-coverage heat dissipation on the heat exchange plate surface, eliminating localized high-temperature zones and improving temperature distribution uniformity. Simultaneously, the layered plate stacking design maintains manufacturing feasibility and ease of maintenance, comprehensively improving heat dissipation efficiency.

[0008] Optionally, in the liquid cooling plate described above, a partition is provided in the first cavity, which divides the first cavity into a first sub-cavity and a second sub-cavity. The first sub-cavity corresponds to and is connected to the water inlet, and the second sub-cavity corresponds to and is connected to the water outlet.

[0009] This design, by dividing the first chamber into a first sub-chamber connected to the inlet and a second sub-chamber connected to the outlet, allows the coolant to be vertically sprayed from the first sub-chamber through jet holes into the second chamber for heat exchange, and then flow back into the second sub-chamber through the jet holes, forming a unidirectional, efficient circulation path. This design eliminates the ineffective bypass flow caused by turbulent coolant flow in traditional open chambers, ensuring that the coolant fully participates in impact heat exchange through the jet holes.

[0010] Optionally, in the liquid cooling plate described above, there are multiple flow channels, all of which are located in the first sub-cavity. The multiple flow channels are arranged along the length direction of the jet plate, each flow channel extends along the width direction of the jet plate, and multiple jet holes in each flow channel are distributed along the extension direction of the flow channel.

[0011] This configuration, with multiple distribution channels arranged in an orderly fashion along the length of the jet plate and each channel extending along its width, combined with multiple jet holes within the channels, enables multi-level and wide-range distribution of the coolant flowing into the first sub-cavity from the inlet. This allows the coolant to be sprayed vertically and densely into the second cavity at a uniform pressure and flow rate through the jet holes, ensuring that every area of ​​the heat exchange plate surface receives efficient and stable impact heat transfer, greatly improving the comprehensiveness and uniformity of heat dissipation. Simultaneously, the orderly distribution of distribution channels and jet holes effectively prevents the formation of eddies or ineffective flow of the coolant within the first cavity, further optimizing the coolant flow path, reducing energy loss, and improving coolant flow efficiency while lowering the pump power consumption required for system operation, significantly enhancing the heat dissipation performance and energy efficiency ratio of the liquid cooling plate.

[0012] Optionally, in the liquid cooling plate described above, the flow distribution channel includes a first sub-channel and a second sub-channel connected along the width direction of the jet plate. The first sub-channel includes a first end facing the second sub-channel and a second end away from the second sub-channel. In the direction from the second end toward the first end, the width of the first sub-channel gradually decreases or increases. The first sub-channel and the second sub-channel are symmetrically distributed about the centerline of the flow distribution channel along the width direction of the jet plate.

[0013] This design, by symmetrically distributing a first and second sub-channel with gradually varying widths, effectively regulates the coolant flow rate and pressure using the gradually decreasing width of the first sub-channel. As the width decreases, the coolant flow rate is accelerated, enhancing the jet impact force and improving heat exchange efficiency. Conversely, as the width increases, the coolant flow rate is reduced, preventing energy loss due to excessive velocity. Simultaneously, the symmetrical structure ensures uniform force on the coolant during distribution, allowing it to be symmetrically and stably sprayed into the second cavity through the jet holes along the width of the jet plate. This effectively avoids uneven coolant distribution leading to localized differences in heat dissipation efficiency, further improving the uniformity of temperature distribution on the heat exchange plate surface, reducing localized hot spots, and helping to balance the fluid pressure inside the liquid cooling plate, thus enhancing the overall heat dissipation performance and operational stability of the liquid cooling plate.

[0014] Optionally, in the liquid cooling plate described above, the surface of the heat exchange plate is provided with a hydrophilic coating.

[0015] This design, by applying a hydrophilic coating to the heat exchanger plate surface, leverages the strong wetting properties of the hydrophilic coating on the coolant to significantly reduce the contact angle between the coolant and the heat exchanger plate surface. This promotes the rapid and uniform spread of coolant impacted by the jet onto the heat exchanger plate surface, forming a large-area, thin liquid film covering layer. This significantly increases the effective heat exchange area between the coolant and the heat exchanger plate, enhancing heat transfer efficiency. Simultaneously, the hydrophilic coating effectively inhibits localized agglomeration or gas-liquid separation of the coolant on the heat exchanger plate surface, avoiding localized increases in thermal resistance and hot spots caused by uneven liquid film distribution, further improving the uniformity of temperature distribution on the heat exchanger plate surface. Furthermore, the synergistic effect of the hydrophilic surface and the jet impact enhances the residence time and flow stability of the coolant on the heat exchanger plate surface, allowing heat to be transferred more efficiently from the heat exchanger plate to the coolant, thus improving the overall heat dissipation performance and reliability of the liquid cooling plate.

[0016] Optionally, in the liquid cooling plate as described above, a flow guide cover is provided on the side of the inlet / outlet plate facing the first cavity. The flow guide cover covers the multiple flow distribution channels and has through holes that connect the water inlet and the first cavity.

[0017] This design, by installing a guide plate covering the distribution channels on the side of the inlet / outlet water plate facing the first cavity, and opening a through hole on it connecting the inlet to the first cavity, can create a directional flow of coolant flowing in from the inlet. This allows the coolant to enter the first cavity evenly and stably through the through hole, and under the guidance of the guide plate, it is orderly distributed to each distribution channel, avoiding fluid impact turbulence or uneven flow caused by the inlet directly connecting to the cavity. The covering design of the guide plate can effectively regulate the flow path of the coolant in the first cavity, reduce eddy current losses and pressure fluctuations during the distribution process, ensure that each distribution channel obtains a balanced flow and stable pressure, and then achieve uniform jet impact on the surface of the heat exchange plate through the jet holes.

[0018] Optionally, in the liquid cooling plate described above, the through hole extends along the length direction of the jet plate, and the through hole includes a first hole end and a second hole end along the length direction of the jet plate. In the direction from the first hole end to the second hole end, the width of the through hole gradually increases or decreases.

[0019] This design, by extending the through-holes along the length of the jet plate and featuring a gradually changing width, allows for the regulation of coolant flow rate and pressure. When the through-hole width gradually increases from the first end to the second, it effectively reduces coolant flow rate and increases static pressure, ensuring sufficient jet energy for the distal jet holes and preventing flow attenuation due to path differences. Conversely, when the width gradually decreases, it accelerates fluid flow to enhance the impact force of the near-end jet, balancing jet intensity across different areas. This gradual design compensates for differences in fluid resistance along the length of the jet plate, ensuring uniform coolant distribution along the through-hole length to each distribution channel and eliminating heat dissipation blind spots or localized overshoot caused by uneven pressure between the inlet and distal ends.

[0020] Optionally, in the liquid cooling plate described above, the top of the heat exchange plate is provided with a plurality of flow guiding channels, the extension direction of the flow guiding channels is parallel to the extension direction of the flow distribution channels, and the plurality of flow guiding channels are arranged side by side in the length direction of the heat exchange plate.

[0021] This configuration, by incorporating multiple guide channels parallel to the extension direction of the distribution channels at the top of the heat exchange plate and arranged side-by-side along the plate's length, effectively guides the coolant sprayed from the jet orifices onto the plate surface. This ensures the coolant flows orderly in a predetermined direction under the constraint of the guide channels, effectively preventing flow dead zones and energy loss caused by disordered diffusion on the heat exchange plate surface. The parallel distribution of the guide channels and distribution channels works in synergy to ensure uniform coolant coverage across the width and length of the heat exchange plate, significantly improving the uniformity of fluid distribution after jet impact, thereby eliminating localized heat dissipation blind spots and reducing surface temperature gradients.

[0022] Optionally, in the liquid cooling plate described above, each of the flow channels is provided with multiple turbulence structures, and the multiple turbulence structures are distributed at intervals in the extension direction of the flow channel.

[0023] This design, by distributing multiple turbulence structures at intervals along the flow channel, creates periodic disturbances to the coolant flowing along the channel, effectively disrupting the fluid boundary layer and enhancing turbulence. This significantly improves the convective heat transfer coefficient between the coolant and the heat exchange plate. The presence of these turbulence structures forces the coolant to generate local eddies and velocity gradients as it flows, increasing the contact frequency and mixing efficiency between fluid particles and the heat exchange plate surface. This allows for the rapid removal of more heat, reducing the adverse effects of boundary layer thermal resistance on heat dissipation. The spaced distribution design ensures effective turbulence while avoiding the problem of drastically increased flow resistance caused by overly dense turbulence structures, ensuring that the coolant maintains a reasonable flow velocity and pressure drop characteristics within the flow channel.

[0024] Secondly, this application provides a cooling system, comprising: the aforementioned liquid cooling plate, which is used for thermally conductive contact with the object to be cooled; a liquid supply module, which is used to provide coolant to the liquid cooling plate; and a liquid supply pipe, which connects the liquid supply module and the liquid cooling plate, the liquid supply pipe comprising: a supply port and a return port, the supply port being connected to a water inlet, the return port being connected to a water outlet, and the inner wall of the liquid supply pipe being provided with a hydrophobic coating.

[0025] This configuration integrates the aforementioned liquid cooling plate, liquid supply module, and liquid supply pipe with a hydrophobic coating on its inner wall, forming a highly efficient and synergistic closed-loop heat dissipation system. The jet impact structure of the liquid cooling plate and the flow guiding design of the heat exchange plate achieve high-intensity and uniform heat exchange on the heat source surface. The liquid supply module provides stable coolant circulation power to the liquid cooling plate through the liquid supply pipe. The hydrophobic coating on the inner wall of the liquid supply pipe, together with the hydrophobic coatings on the inlet and outlet plates and the jet plate of the liquid cooling plate, forms a synergistic effect of drag reduction throughout the flow channel. This significantly reduces the viscous resistance of the coolant flowing in the pipes and within the plates, reduces pump power consumption, and improves fluid circulation efficiency. It significantly improves heat dissipation uniformity and energy efficiency ratio, effectively solving the heat dissipation problems caused by high flow resistance and uneven heat exchange in traditional liquid cooling systems.

[0026] The liquid-cooled plate and cooling system provided in this application, through the diversion channel and multi-jet hole design of the jet plate, uniformly sprays the coolant from the first chamber to the second chamber. This replaces traditional long-distance microchannel flow with short-path impact heat exchange. Combined with the hydrophobic coating on the surface of the inlet / outlet plates or jet plate, it reduces the frictional resistance at the solid-liquid interface, significantly reducing fluid viscosity loss and pump power consumption. The jet impact achieves full-coverage heat dissipation on the heat exchange plate surface, eliminating localized high-temperature zones and improving temperature distribution uniformity. Simultaneously, the layered plate stacking design maintains processing feasibility and ease of maintenance, comprehensively improving heat dissipation efficiency. Attached Figure Description

[0027] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application.

[0028] Figure 1 Schematic diagram of the liquid cooling plate provided in this application Figure 1 ;

[0029] Figure 2 Schematic diagram of the liquid cooling plate provided in this application Figure 2 ;

[0030] Figure 3 Exploded view of the liquid cooling plate provided in this application;

[0031] Figure 4 A partial structural diagram of the liquid cooling plate provided in this application. Figure 1 ;

[0032] Figure 5 A partial structural diagram of the liquid cooling plate provided in this application. Figure 2 ;

[0033] Figure 6 A schematic diagram of the liquid supply pipe provided in this application.

[0034] Explanation of reference numerals in the attached figures:

[0035] 1: Liquid cooling plate; 2: Liquid supply pipe; 201: Liquid supply port; 202: Liquid return port;

[0036] 10: Inlet / outlet plate; 11: Inlet; 12: Outlet; 13: Flow guide cover; 131: Through hole;

[0037] 20: Jet plate; 21: First cavity; 211: Separator; 212: First sub-cavity; 213: Second sub-cavity; 22: Second cavity; 23: Diversion channel; 231: Jet hole; 232: First sub-channel; 233: Second sub-channel;

[0038] 30: Heat exchange plate; 31: Flow guide channel.

[0039] The accompanying drawings illustrate specific embodiments of this application, which will be described in more detail below. These drawings and descriptions are not intended to limit the scope of the concept in any way, but rather to illustrate the concept of this application to those skilled in the art through reference to particular embodiments. Detailed Implementation

[0040] Exemplary embodiments will now be described in detail, examples of which are illustrated in the accompanying drawings. When the following description relates to the drawings, unless otherwise indicated, the same numbers in different drawings denote the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this application. Rather, they are merely examples of apparatuses and methods consistent with some aspects of this application as detailed in the appended claims.

[0041] Liquid cooling plates in related technologies generally employ a microchannel flow design, which increases the heat exchange area by reducing the flow channel size to enhance heat dissipation. However, the microchannels in these liquid cooling plates suffer from increased viscous resistance due to their small hydraulic diameter, resulting in lower coolant flow efficiency.

[0042] To address the aforementioned technical problems, this application provides a liquid cooling plate and cooling system. Through the diversion channel and multi-jet hole design of the jet plate, coolant is uniformly sprayed from the first chamber to the second chamber, replacing traditional long-distance microchannel flow with short-path impact heat exchange. Combined with a hydrophobic coating on the inlet / outlet plates or the jet plate surface, the solid-liquid interface frictional resistance is reduced, significantly decreasing fluid viscosity loss and pump power consumption. The jet impact achieves full-coverage heat dissipation on the heat exchange plate surface, eliminating localized high-temperature zones and improving temperature distribution uniformity. Simultaneously, the layered plate stacking design maintains processing feasibility and maintenance convenience, comprehensively improving heat dissipation efficiency.

[0043] The technical solution of this application and how the technical solution of this application solves the above-mentioned technical problems are described in detail below with specific embodiments. These specific embodiments can be combined with each other, and the same or similar concepts or processes may not be described again in some embodiments. The embodiments of this application will now be described with reference to the accompanying drawings.

[0044] refer to Figure 1-6 This application provides a liquid cooling plate 1, including an inlet / outlet water plate 10, a jet plate 20, and a heat exchange plate 30. The inlet / outlet water plate 10, the jet plate 20, and the heat exchange plate 30 can be stacked sequentially along the thickness direction of the liquid cooling plate 1. The inlet / outlet water plate 10 is provided with an inlet 11 and an outlet 12, responsible for guiding the coolant into and out of the liquid cooling plate 1. A first cavity 21 is formed between the jet plate 20 and the inlet / outlet water plate 10. The first cavity 21 communicates with the inlet 11 and the outlet 12, respectively. A second cavity 22 is formed between the jet plate 20 and the heat exchange plate 30.

[0045] Furthermore, the jet plate 20 is also provided with a flow distribution channel 23. Multiple jet holes 231 can be provided within the flow distribution channel 23. The jet holes 231 penetrate the flow distribution channel 23, so that the jet holes 231 are respectively connected to the first cavity 21 and the second cavity 22. Thus, the first cavity 21 serves as a distribution and return space for the coolant, connecting the inlet 11 and the outlet 12, and is used to evenly distribute the coolant to the second cavity 22 via the flow distribution channel 23 and the jet holes 231, and collect the return liquid. The second cavity 22 serves as a jet impact heat exchange zone, allowing the coolant to be sprayed onto the surface of the heat exchange plate 30 through the jet holes 231, enhancing heat exchange through impact flow.

[0046] To reduce the flow resistance of the coolant, a hydrophobic coating is applied to the surface of the inlet / outlet water plate 10. Alternatively, a hydrophobic coating is applied to the surface of the jet plate 20. Or, both the inlet / outlet water plate 10 and the jet plate 20 may have hydrophobic coatings. Optionally, the hydrophobic coating can be obtained by anodizing. Anodizing, as a mature metal surface treatment process, has the advantages of simple operation and controllable process, and can form a well-structured nanoscale rough morphology on the substrate surface. Laser etching technology can also precisely construct micro / nano composite structures, providing a basic roughness for the superhydrophobic surface. Based on this, by modifying the rough surface with low surface energy materials (such as n-octyltriethoxysilane ethanol solution), functionalized surfaces with stable superhydrophobic properties can be efficiently constructed, achieving directional control of the material's hydrophobic properties.

[0047] Understandably, through the design of the flow distribution channel 23 and multiple jet holes 231 of the jet plate 20, the coolant is uniformly sprayed from the first chamber 21 to the second chamber 22, replacing the traditional long-distance microchannel flow with short-path impact heat exchange. Combined with the hydrophobic coating on the surface of the inlet / outlet water plate 10 or the jet plate 20, the frictional resistance at the solid-liquid interface is reduced, significantly reducing fluid viscosity loss and pump power consumption. The jet impact achieves full-coverage heat dissipation on the surface of the heat exchange plate 30, eliminating local high-temperature areas and improving temperature distribution uniformity. At the same time, the layered plate stacking design maintains processing feasibility and maintenance convenience, comprehensively improving heat dissipation efficiency.

[0048] In one possible implementation, a partition 211 is further provided within the first cavity 21. The partition 211 divides the first cavity 21 into a first sub-cavity 212 and a second sub-cavity 213. The first sub-cavity 212 corresponds to and communicates with the inlet 11, and the second sub-cavity 213 corresponds to and communicates with the outlet 12. Preferably, the volume of the first sub-cavity 212 is larger than the volume of the second sub-cavity 213. The partition 211 can be a plate-like or block-like structure adapted to the cavity. The partition 211 can be made of metal or plastic. The larger first sub-cavity 212 can serve as a "pressure stabilizing cavity" on the inlet side, effectively buffering the impact of the coolant flowing in at high speed through the inlet 11, reducing the fluid velocity and balancing the pressure inside the cavity, so that the coolant forms a stable and uniform pressure field before entering the diversion channel 23 of the jet plate 20. The smaller second sub-cavity 213 serves as a "collecting cavity" on the outlet side, which can collect the coolant that returns through the jet orifice 231 after heat exchange. By reducing the cavity volume, the flow rate of the returning fluid is increased, and the residence time of the fluid in the cavity is reduced. In addition, the edges of the separator 211 are usually designed with streamlined transitions (such as rounded chamfers), which can reduce boundary layer separation when the fluid turns, thereby reducing flow resistance.

[0049] Understandably, by dividing the first cavity 21 into a first sub-cavity 212 connected to the inlet 11 and a second sub-cavity 213 connected to the outlet 12, the coolant is vertically sprayed from the first sub-cavity 212 through the jet orifice 231 into the second cavity 22 for heat exchange, and then flows back to the second sub-cavity 213 through the jet orifice 231, forming a unidirectional, efficient circulation path. This design eliminates the ineffective bypass flow caused by the turbulent coolant flow in traditional open cavities, ensuring that the coolant fully participates in impact heat exchange through the jet orifice 231.

[0050] In one possible implementation, there can be multiple diversion channels 23. All multiple diversion channels 23 are disposed within the first sub-cavity 212. The multiple diversion channels 23 are arranged along the length direction of the jet plate 20. Furthermore, each diversion channel 23 extends along the width direction of the jet plate 20, and multiple jet holes 231 within each diversion channel 23 can be distributed along the extending direction of the diversion channel 23. Preferably, the surface of the diversion channel 23 is provided with a hydrophobic coating.

[0051] The spacing between adjacent diversion channels 23 can be adapted to the size of the jet plate 20 and the heat source distribution area of ​​the heat exchange plate 30 to ensure that there are no blind spots in the jet coverage area. Each diversion channel 23 extends along the width direction of the jet plate 20, and its cross-sectional shape can be rectangular, trapezoidal, rhomboid, or arc-shaped, etc. For example, the cross-sectional shape of the diversion channel 23 can be rhomboid.

[0052] Understandably, multiple diversion channels 23 are arranged in an orderly manner along the length of the jet plate 20, and each channel extends along its width. Combined with multiple jet holes 231 within the channels, this allows for multi-level and wide-range diversion of the coolant flowing from the inlet 11 into the first sub-cavity 212. This ensures that the coolant is sprayed vertically and densely into the second cavity 22 at a uniform pressure and flow rate through the jet holes 231, guaranteeing efficient and stable impact heat transfer across every area of ​​the heat exchange plate 30 surface, significantly improving the comprehensiveness and uniformity of heat dissipation. Simultaneously, the orderly distributed diversion channels 23 and jet holes 231 effectively prevent the coolant from forming eddies or ineffective flow within the first cavity 21, further optimizing the coolant flow path, reducing energy loss, and improving coolant flow efficiency while lowering the pump power consumption required for system operation, significantly enhancing the heat dissipation performance and energy efficiency ratio of the liquid cooling plate 1.

[0053] In one possible implementation, the diversion channel 23 includes a first sub-channel 232 and a second sub-channel 233. The first sub-channel 232 and the second sub-channel 233 may be connected in the width direction of the jet plate 20. The first sub-channel 232 includes a first end and a second end. The first end of the first sub-channel 232 is disposed facing the second sub-channel 233, and the second end of the first sub-channel 232 is disposed away from the second sub-channel 233. Further, the width of the first sub-channel 232 gradually decreases in the direction from the second end to the first end. Alternatively, the width of the first sub-channel 232 gradually increases in the direction from the second end to the first end. The first sub-channel 232 and the second sub-channel 233 may be symmetrically distributed about the centerline of the jet plate 20 in the width direction of the diversion channel 23 to form a rhomboid or near-rhomboid diversion channel 23.

[0054] Furthermore, multiple jet holes 231 can be provided in the first sub-channel 232 and the second sub-channel 233. The diameters of the multiple jet holes 231 in the first sub-channel 232 decrease synchronously along the direction of decreasing width of the first sub-channel 232. Alternatively, the diameters of the multiple jet holes 231 in the first sub-channel 232 increase synchronously along the direction of increasing width of the first sub-channel 232. Similarly, the diameters of the multiple jet holes 231 in the first and second sub-channels decrease synchronously along the direction of decreasing width of the second sub-channel 233. Alternatively, the diameters of the multiple jet holes 231 in the second sub-channel 233 increase synchronously along the direction of increasing width of the second sub-channel 233.

[0055] Understandably, by designing the diversion channel 23 as a symmetrically distributed first sub-channel 232 and second sub-channel 233 with gradually changing widths, the gradually changing width of the first sub-channel 232 can effectively regulate the coolant flow rate and pressure. When the width gradually decreases, the coolant flow rate is accelerated, enhancing the jet impact force of the jet orifice 231 and improving heat exchange efficiency. When the width gradually increases, the coolant flow rate is reduced, avoiding energy loss due to excessive flow rate. Simultaneously, the symmetrical structural design ensures uniform force on the coolant during diversion, allowing it to be sprayed symmetrically and stably through the jet orifice 231 into the second cavity 22 along the width direction of the jet plate 20. This effectively avoids localized differences in heat dissipation efficiency caused by uneven coolant diversion, further improving the uniformity of surface temperature distribution on the heat exchange plate 30, reducing localized hot spots, and the symmetrical structure helps balance the fluid pressure inside the liquid cooling plate 1, improving the overall heat dissipation performance and operational stability of the liquid cooling plate 1.

[0056] In one possible implementation, a hydrophilic coating is provided on the surface of the heat exchange plate 30. Optionally, the hydrophilic coating can be an inorganic oxide, such as silica, titanium dioxide, or alumina, which enhances wettability by forming hydrogen bonds with the coolant through surface hydroxyl groups. The hydrophilic coating can also be a hydrophilic polymer, such as polyvinyl alcohol, polyethylene glycol, or polyacrylic acid, which enhances affinity with the coolant through polar groups (such as hydroxyl and carboxyl groups) on the molecular chain. The hydrophilic coating can also be a composite coating, such as a silica-titanium dioxide composite film or a polymer-nanoparticle hybrid coating, which balances high wettability and mechanical strength. The hydrophilic coating can be bonded to the surface of the heat exchange plate 30 by methods such as sol-gel method, magnetron sputtering, electrochemical deposition, or spraying.

[0057] Understandably, by applying a hydrophilic coating to the surface of the heat exchange plate 30, the strong wetting property of the hydrophilic coating on the coolant can significantly reduce the contact angle between the coolant and the surface of the heat exchange plate 30. This promotes the rapid and uniform spread of the coolant impacted by the jet onto the surface of the heat exchange plate 30, forming a large-area, thin-film liquid film covering layer. This significantly increases the effective heat exchange area between the coolant and the heat exchange plate 30, enhancing heat transfer efficiency. Simultaneously, the hydrophilic coating effectively inhibits the formation of localized agglomeration or gas-liquid separation of the coolant on the surface of the heat exchange plate 30, avoiding localized increases in thermal resistance and hot spots caused by uneven liquid film distribution, further improving the uniformity of temperature distribution on the surface of the heat exchange plate 30. Furthermore, the synergistic effect of the hydrophilic surface and the jet impact enhances the residence time and flow stability of the coolant on the surface of the heat exchange plate 30, allowing heat to be transferred more efficiently from the heat exchange plate 30 to the coolant, thus improving the overall heat dissipation performance and reliability of the liquid cooling plate 1.

[0058] In one possible implementation, a flow guide cover 13 is provided on the inlet / outlet water plate 10. Specifically, the flow guide cover 13 is located on the side of the inlet / outlet water plate 10 facing the first cavity 21. The flow guide cover 13 can cover multiple diversion channels 23. A through hole 131 is provided on the flow guide cover 13, which connects the water inlet 11 and the first cavity 21. Optionally, the flow guide cover 13 can be a flat plate structure adapted to the inlet / outlet water plate 10. The material of the flow guide cover 13 can be the same as that of the inlet / outlet water plate 10 to ensure a matching coefficient of thermal expansion and avoid deformation or cracking due to temperature changes. The flow guide cover 13 can be welded to the inlet / outlet water plate 10, bolted to it, or integrally formed.

[0059] It is understandable that by providing a guide plate 13 covering the flow distribution channel 23 on the side of the inlet / outlet plate 10 facing the first cavity 21, and opening a through hole 131 on it connecting the inlet 11 and the first cavity 21, a directional flow effect can be formed on the coolant flowing in from the inlet 11. This allows the coolant to enter the first cavity 21 evenly and stably through the through hole 131, and under the guidance of the guide plate 13, it is orderly distributed to each flow distribution channel 23, avoiding fluid impact turbulence or uneven flow caused by the inlet 11 directly connecting to the cavity. The covering design of the guide plate 13 can effectively regulate the flow path of the coolant in the first cavity 21, reduce eddy current loss and pressure fluctuation during the flow distribution process, ensure that each flow distribution channel 23 obtains a balanced flow and stable pressure, and then achieve uniform jet impact on the surface of the heat exchange plate 30 through the jet hole 231.

[0060] In one possible implementation, the through-hole 131 of the flow guide plate 13 can extend along the length direction of the jet plate 20. Optionally, the shape of the through-hole 131 can be rhomboid. The through-hole 131 of the flow guide plate 13 can include a first end and a second end. The first end and the second end can be distributed along the length direction of the jet plate 20. Further, the width of the through-hole 131 gradually increases or decreases in the direction from the first end to the second end. Optionally, the surface of the flow guide plate 13 can be provided with a hydrophobic coating. An arc-shaped flow guide wall can also be provided on the inlet side of the through-hole 131 to reduce coolant flow separation.

[0061] Understandably, by extending the through-hole 131 along the length of the jet plate 20 and designing a gradually changing width structure, the flow rate and pressure of the coolant can be controlled. When the width of the through-hole 131 gradually increases from the first end to the second end, it effectively reduces the coolant flow rate and increases the static pressure, ensuring that the distal jet hole 231 receives sufficient jet energy and avoiding flow attenuation due to path differences. When the width gradually decreases, it accelerates fluid flow to enhance the near-end jet impact force and balance the jet intensity in different areas. This gradual design can compensate for the fluid resistance differences along the length of the jet plate 20, ensuring that the coolant is evenly distributed to each distribution channel 23 along the length of the through-hole 131, eliminating heat dissipation blind spots or local overrush caused by uneven pressure between the inlet and distal ends.

[0062] In one possible implementation, a plurality of flow guiding channels 31 are provided on the top of the heat exchange plate 30. The flow guiding channels 31 extend along the width direction of the heat exchange plate 30. Alternatively, the extension direction of the flow guiding channels 31 is parallel to the extension direction of the flow distribution channel 23. The plurality of flow guiding channels 31 are arranged side by side along the length direction of the heat exchange plate 30. The spacing of the flow guiding channels 31 can be determined according to actual needs, and this application does not impose any limitations.

[0063] It is understandable that by setting multiple guide channels 31 parallel to the extension direction of the diversion channel 23 on the top of the heat exchange plate 30 and distributing them side by side along the length of the heat exchange plate 30, the coolant sprayed onto the surface of the heat exchange plate 30 by the jet orifice 231 can be guided in a directional manner. This allows the coolant to flow orderly in a preset direction under the constraint of the guide channels 31, effectively avoiding flow dead zones and energy loss caused by disordered diffusion of fluid on the surface of the heat exchange plate 30. The parallel distribution of the guide channels 31 and the diversion channel 23 forms a spatial synergy, ensuring that the coolant is uniformly covered in the width and length directions of the heat exchange plate 30, significantly improving the uniformity of fluid distribution after jet impact, thereby eliminating local heat dissipation blind spots and reducing the surface temperature gradient.

[0064] In one possible implementation, each flow channel 31 is provided with multiple flow-disrupting structures. These structures are spaced apart along the extension direction of the flow channel 31. Optionally, the flow-disrupting structures can be metal fins, such as straight fins, corrugated fins, or louvered fins. Alternatively, the flow-disrupting structures can be metal cylinders. Or, they can be biomimetic fish fin structures. The distribution density of the flow-disrupting structures can be determined according to actual needs, and this application does not impose any limitations.

[0065] Understandably, by distributing multiple turbulence structures at intervals along the flow channel 31, periodic disturbances can be created to the coolant flowing along the channel 31, effectively disrupting the fluid boundary layer and enhancing turbulence, thereby significantly improving the convective heat transfer coefficient between the coolant and the heat exchange plate 30. The presence of the turbulence structures forces the coolant to generate local eddies and velocity gradients as it flows, increasing the contact frequency and mixing efficiency between fluid particles and the surface of the heat exchange plate 30, thus rapidly removing more heat and reducing the adverse effects of boundary layer thermal resistance on heat dissipation. The interval distribution design ensures the turbulence effect while avoiding the problem of a sharp increase in flow resistance caused by excessively dense turbulence structures, ensuring that the coolant maintains a reasonable flow velocity and pressure drop characteristics within the flow channel 31.

[0066] Furthermore, this application provides a cooling system, including the aforementioned liquid cooling plate 1, liquid supply module, and liquid supply pipe 2. The liquid cooling plate 1 is used for thermally conductive contact with the object to be cooled to dissipate heat from the object. The liquid supply module is used to supply coolant to the liquid cooling plate 1. The liquid supply pipe 2 can connect the liquid supply module and the liquid cooling plate 1. The liquid supply pipe 2 includes a supply port 201 and a return port 202. The supply port 201 is connected to the water inlet 11, and the return port 202 is connected to the water outlet 12. The inner wall of the liquid supply pipe 2 is provided with a hydrophobic coating.

[0067] Furthermore, the liquid supply module includes a storage tank, a circulation pump, and a temperature control unit, and is connected to the inlet 11 and outlet 12 of the liquid cooling plate 1 via a liquid supply pipe 2. A hydrophobic coating is provided on the inner wall of the liquid supply pipe 2 to reduce flow resistance. The circulation pump drives the coolant to flow through the liquid cooling plate 1, and after heat exchange by impacting the heat exchange plate 30 through the jet holes 231, it flows back to the storage tank.

[0068] Understandably, the cooling system integrates the aforementioned liquid cooling plate 1, the liquid supply module, and the liquid supply pipe 2 with a hydrophobic coating on its inner wall to form a highly efficient and synergistic closed-loop heat dissipation system. The jet impact structure of the liquid cooling plate 1 and the flow guiding design of the heat exchange plate 30 achieve high-intensity and uniform heat exchange on the heat source surface. The liquid supply module provides stable coolant circulation power to the liquid cooling plate 1 through the liquid supply pipe 2. The hydrophobic coating on the inner wall of the liquid supply pipe 2, together with the hydrophobic coatings on the inlet and outlet plates 10 and the jet plate 20 of the liquid cooling plate 1, forms a synergistic effect of drag reduction throughout the flow path, significantly reducing the viscous resistance of the coolant flowing in the pipes and within the plates, reducing pump power consumption and improving fluid circulation efficiency. This significantly improves heat dissipation uniformity and energy efficiency ratio, effectively solving the heat dissipation problem caused by high flow resistance and uneven heat exchange in traditional liquid cooling systems.

[0069] The various embodiments or implementation methods described in this specification are presented in a progressive manner. Each embodiment focuses on the differences from other embodiments, and the same or similar parts between the embodiments can be referred to each other.

[0070] It should be noted that the terms "one embodiment," "embodiment," "exemplary embodiment," "some embodiments," etc., mentioned in the specification indicate that the described embodiment may include a specific feature, structure, or characteristic, but not every embodiment necessarily includes that specific feature, structure, or characteristic. Furthermore, such phrases do not necessarily refer to the same embodiment. Moreover, when a specific feature, structure, or characteristic is described in connection with an embodiment, implementing such a feature, structure, or characteristic in conjunction with other embodiments, whether explicitly described or not, is within the knowledge scope of those skilled in the art.

[0071] Generally speaking, terms should be understood at least in part by their use in context. For example, at least in part by context, the term "one or more" as used in the text can be used to describe any feature, structure, or characteristic of the singular meaning, or a combination of features, structures, or characteristics of the plural meaning. Similarly, at least in part by context, terms such as "a" or "the" can also be understood to convey either singular or plural usage.

[0072] It should be readily understood that the terms “on,” “above,” and “on top of” in this disclosure should be interpreted in the broadest possible sense, such that “on” means not only “directly on something” but also “on something” with an intermediate feature or layer therebetween, and that “above” or “on top of” means not only “on top of something” but also “on top of something” without an intermediate feature or layer therebetween (i.e., directly on something).

[0073] Furthermore, for ease of explanation, spatially relative terms such as "below," "below," "under," "above," and "above" may be used to describe the relationship of one element or feature relative to other elements or features as shown in the figures. Spatially relative terms are intended to encompass different orientations of the device in use or operation other than those shown in the figures. The device may have other orientations (rotated 90 degrees or in other orientations), and the spatially relative descriptive terms used herein may be interpreted accordingly.

[0074] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application.

Claims

1. A liquid cold plate (1) characterized by, include: The inlet and outlet water plates (10), jet plate (20) and heat exchange plate (30) are arranged in sequence along the thickness direction of the liquid cooling plate (1), wherein the inlet and outlet water plates (10) are provided with an inlet (11) and an outlet (12). A first cavity (21) is formed between the jet plate (20) and the inlet / outlet plate (10), and the first cavity (21) is connected to the inlet (11) and the outlet (12) respectively. A second cavity (22) is formed between the jet plate (20) and the heat exchange plate (30). The jet plate (20) is also provided with a diversion channel (23), and the diversion channel (23) is provided with a plurality of jet holes (231), which are respectively connected to the first cavity (21) and the second cavity (22); At least one of the inlet / outlet water plate (10) and the jet plate (20) has a hydrophobic coating on its surface.

2. The liquid cold plate (1) according to claim 1, characterized in that, The first cavity (21) is provided with a partition (211), which divides the first cavity (21) into a first sub-cavity (212) and a second sub-cavity (213). The first sub-cavity (212) corresponds to and is connected to the water inlet (11), and the second sub-cavity (213) corresponds to and is connected to the water outlet (12).

3. The liquid cold plate (1) of claim 2, characterized in that, There are multiple diversion channels (23), all of which are located in the first sub-cavity (212). The multiple diversion channels (23) are arranged along the length direction of the jet plate (20), and each diversion channel (23) extends along the width direction of the jet plate (20). Multiple jet holes (231) in each diversion channel (23) are distributed along the extension direction of the diversion channel (23).

4. The liquid cold plate (1) of claim 3, characterized in that, The diversion channel (23) includes a first sub-channel (232) and a second sub-channel (233) connected along the width direction of the jet plate (20). The first sub-channel (232) includes a first end facing the second sub-channel (233) and a second end away from the second sub-channel (233), and the width of the first sub-channel (232) gradually decreases or increases in the direction from the second end toward the first end; The first sub-channel (232) and the second sub-channel (233) are symmetrically distributed about the center line of the width direction of the jet plate (20) with respect to the diversion channel (23).

5. The liquid cooling plate (1) according to claim 1, characterized in that, The heat exchange plate (30) has a hydrophilic coating on its surface.

6. The liquid cooling plate (1) according to claim 2, characterized in that, The inlet / outlet plate (10) is provided with a flow guide cover (13) on the side facing the first cavity (21). The flow guide cover (13) covers the multiple diversion channels (23). The flow guide cover (13) has a through hole (131) which connects the inlet (11) and the first cavity (21).

7. The liquid cooling plate (1) according to claim 6, characterized in that, The through hole (131) extends along the length direction of the jet plate (20). The through hole (131) includes a first hole end and a second hole end along the length direction of the jet plate (20). In the direction from the first hole end toward the second hole end, the width of the through hole (131) gradually increases or decreases.

8. The liquid cooling plate (1) according to claim 1, characterized in that, The top of the heat exchange plate (30) is provided with a plurality of flow guiding channels (31), the extension direction of the flow guiding channels (31) is parallel to the extension direction of the flow diversion channel (23), and the plurality of flow guiding channels (31) are arranged side by side in the length direction of the heat exchange plate (30).

9. The liquid cooling plate (1) according to claim 8, characterized in that, Each of the flow channels (31) is provided with a plurality of turbulence structures, which are spaced apart in the extension direction of the flow channels (31).

10. A cooling system, characterized in that, include: The liquid cooling plate (1) according to any one of claims 1-9, wherein the liquid cooling plate (1) is used for thermally conductive contact with the object to be cooled; A liquid supply module is used to supply coolant to the liquid cooling plate (1); Liquid supply pipe (2), the liquid supply pipe (2) connects the liquid supply module and the liquid cooling plate (1), the liquid supply pipe (2) includes: The liquid supply port (201) and the liquid return port (202) are connected to the water inlet (11) and the liquid return port (202) is connected to the water outlet (12). The inner wall of the liquid supply pipe (2) is provided with a hydrophobic coating.

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