Liquid cooling heat dissipation cold plate assembly and preparation process thereof

Abstract

The present application relates to a kind of liquid cooling heat dissipation cold plate assembly and its preparation process.The assembly includes bottom plate, top plate and corrugated core plate, and the core plate separates chamber into alternately arranged positive and negative trapezoidal flow channels.The side wall array of flow channel has flow guide fin and associated avoidance hole, the root of flow guide fin is located upstream, and the overhanging part extends to the center of flow channel and covers the avoidance hole.In preparation, the initial state of fin is formed by overall stamping, and then the end of flow guide fin is flattened by punch.The jet flow is generated by using flow guide fin to guide fluid, the laminar boundary layer is destroyed, and the cold is replenished across the lane by using negative pressure effect through avoidance hole, while maintaining low flow resistance, the heat dissipation efficiency and uniformity are improved.In addition, the welding configuration of corrugated core plate and cover bottom plate significantly enhances the structural stiffness of cold plate.

Description

Technical Field

[0001] This invention relates to the field of liquid cooling heat dissipation plate technology, specifically to a liquid cooling heat dissipation plate assembly and its manufacturing process. Background Technology

[0002] As high-performance computing (HPC), artificial intelligence servers, high-power semiconductor devices, and new energy vehicle power battery systems develop towards ultra-high power density and high integration, higher requirements are placed on the heat dissipation efficiency and structural strength of liquid cooling heat dissipation cold plate components. The core challenge in improving the overall performance of liquid cooling plates lies in how to achieve a high convective heat transfer coefficient, excellent surface temperature consistency, and robust structural mechanical strength under the conditions of limited space size and limited system pumping power consumption.

[0003] In existing heat dissipation channel designs, the cooling medium flow path inside the liquid cooling plate is typically a regular rectangular cross-section channel. While this design offers some manufacturing convenience, the effective heat exchange area between the channel and the base plate is significantly limited by the channel's projected width because its sidewalls are perpendicular to the heat exchange base plate. Furthermore, structural ribs of a certain thickness must be maintained between adjacent channels to support the cover plate and withstand the static pressure of the coolant. These ribs occupy a large amount of usable space on the inner surface of the base plate, resulting in a low direct wetting ratio between the cooling medium and the main heat dissipation surface, thus limiting the overall heat diffusion capacity of the cooling plate.

[0004] Secondly, in traditional flat-flow channels with uniform cross-sections, the coolant easily forms a stable laminar boundary layer in the near-wall region during circulation. This boundary layer, characterized by an extremely low-velocity fluid film, not only exhibits significant thermal resistance but also hinders the radial transfer of heat from the base plate to the main flow area in the center of the channel, forming a heat transfer shield. Although existing technologies can induce turbulence to some extent by adding turbulence-inducing columns or bends in the flow channel, this often results in increased system flow resistance, leading to excessive pumping power consumption. Furthermore, complex internal components can easily create dead zones, increasing the risk of localized heat accumulation and scaling failure.

[0005] Furthermore, adjacent flow channels of liquid cooling plates are typically completely isolated in physical structure, with the cooling medium flowing only along its predetermined longitudinal path. This prevents adaptive compensation and dynamic exchange of fluid mass and energy in the lateral dimension. This isolated flow field structure leads to a sharp temperature gradient on the surface of the cooling plate when facing non-uniformly distributed heat sources, making it difficult to meet the temperature uniformity requirements of modern high-precision electronic equipment. Summary of the Invention

[0006] The purpose of this invention is to provide a liquid-cooled heat dissipation cold plate assembly to solve the technical problems of existing cold plate assemblies failing to meet overall heat diffusion requirements and having a laminar boundary layer forming a heat transfer shield, thus resulting in low heat dissipation efficiency; the purpose of this invention is also to provide a manufacturing process for the liquid-cooled heat dissipation cold plate assembly.

[0007] The technical solution of the liquid-cooled heat dissipation plate assembly of the present invention is as follows:

[0008] A liquid-cooled heat dissipation plate assembly includes:

[0009] A metal base plate and a sealed top plate together form a closed fluid chamber;

[0010] A corrugated core plate is built into the fluid chamber. The corrugated core plate has alternating crests and troughs, and inclined sidewalls connecting the crests and troughs. The troughs are connected to the metal base plate, and the crests are connected to the sealing top plate, so as to divide the fluid chamber into several parallel fluid channels. The fluid channels include a first channel with a wide bottom and a narrow top, and a second channel with a narrow bottom and a wide top, which are arranged alternately along the direction perpendicular to the fluid flow.

[0011] Multiple flow guiding units are arranged at intervals on the inclined sidewall of at least one side of the first flow channel, including flow guiding vanes and clearance holes opened on the inclined sidewall, the clearance holes connecting to adjacent fluid channels.

[0012] The guide vane includes a root integrally connected to the inclined sidewall, and an overhang located downstream of the root and extending toward the bottom center of the fluid channel along the flow direction of the fluid. The overhang forms a local contraction throat between the overhang and the inclined sidewall on the opposite side. The flow area of ​​the local contraction throat is smaller than the average flow area of ​​the first flow channel. The overhang covers the clearance hole in the radial projection direction of the fluid channel so as to utilize the local instantaneous dynamic pressure rise and static pressure drop generated when the fluid flows through the local contraction throat to adsorb the cooling medium in the second flow channel into the first flow channel through the clearance hole.

[0013] Furthermore, a wedge-shaped compression gap is formed between the tail end of the overhang of the guide vane and the metal base plate, so as to form a guide surface pointing towards the metal base plate at the tail end of the guide vane.

[0014] Furthermore, the guide vane is integrally formed by stamping and bending a portion of the inclined sidewall, and the clearance hole is formed by the forming hole formed on the portion of the sidewall after being stamped.

[0015] Furthermore, the cross-section of the first flow channel is trapezoidal, and the second flow channel is an inverted trapezoidal.

[0016] Furthermore, the height at which the guide vanes fold up within the fluid channel is 15%-30% of the width of the fluid channel at that location.

[0017] Furthermore, the guide vanes are distributed on the inclined sidewalls on both sides of the first flow channel, and the guide vanes on both sides are alternately staggered along the fluid flow direction.

[0018] The preparation process includes the following steps:

[0019] (1) Precast corrugated core plate: The metal sheet is processed into a corrugated structure with continuous undulation;

[0020] (2) Stamping guide vanes: The pre-made corrugated core plate is placed in the mold, and the inclined side wall is stamped by the cutter head to form the initial outline and clearance hole of the guide vanes, and the guide vanes are pushed into the fluid channel to form a preset angle.

[0021] (3) Angle torsion forming: By applying a torsional torque to the overhang of the guide vane, one side edge of the tail end of the guide vane is twisted and deformed downwards to form a downward-facing flow guide surface towards the bottom edge of the fluid channel.

[0022] (4) Encapsulation and welding: The formed corrugated core plate, metal base plate and sealing top plate are stacked and welded together.

[0023] Furthermore, in steps (2) and (3), a combined cutting head is used for stamping. The combined cutting head is pressed down along the first direction to implement step (2). Then, the secondary punch in the combined cutting head moves independently along the second direction to implement step (3).

[0024] Furthermore, in steps (2) and (3), the mold includes a lower mold with a support protrusion that enters the external gap of the fluid channel to support the inclined sidewall during the stamping process. The lower mold also has a follower head that is floatingly supported on the lower mold. In step (2), the follower head is fixed in the lower mold, and in step (3), a portion of the follower head floats and moves downward following the secondary punch.

[0025] The beneficial effects of this application are as follows: Compared with the prior art, the liquid-cooled heat dissipation cold plate assembly of this invention, by configuring the corrugated core plate with an alternating distribution of the first and second flow channels, reduces the ineffective heat exchange space occupied by the solid structural ribs between adjacent flow channels compared to the rectangular flow channels with vertical sidewalls in the prior art. The wide bottom edge of the first flow channel directly adheres to the metal base plate, significantly increasing the wetting ratio of the cooling medium on the main heat exchange surface. This makes the heat diffusion path from the heat source through the metal base plate to the interior of the flow channel shorter and more efficient, effectively solving the defect of insufficient heat diffusion capacity caused by the structural limitations of traditional rectangular flow channels.

[0026] Simultaneously, flow field interference is achieved using guide vanes arrayed on the inclined sidewall of the first flow channel. When the coolant flows along the first flow channel and contacts the root of the guide vanes, guided by the overhang, the fluid that was originally flowing close to the sidewall is forced to change its momentum direction and dive and accumulate towards the central region at the bottom of the flow channel. This process generates a strong jet, causing the high-speed fluid to directly impact the inner heat exchange surface of the metal base plate, disrupting the stability of the laminar boundary layer, thereby eliminating the heat transfer shield formed by the low-speed fluid film, increasing the local convective heat transfer coefficient, and effectively improving heat dissipation efficiency.

[0027] Furthermore, when the fluid in the first flow channel is guided by the guide vanes to accelerate and converge towards the center, a momentary local negative pressure gradient is generated in the area of ​​the clearance hole, which is radially shielded by the overhang. Since the flow pressure in the adjacent second flow channel is relatively stable and the temperature is lower, this local negative pressure generates a suction effect, inducing the low-temperature cooling medium in the second flow channel to surge into the first flow channel through the clearance hole. This lateral coolant supply and the mainstream flow field in the first flow channel result in a strong momentum collision and energy exchange, achieving not only adaptive heat compensation in the lateral dimension but also effectively suppressing the temperature gradient on the surface of the cold plate, achieving excellent temperature uniformity, solving the heat dissipation imbalance problem caused by isolated flow channels in existing technologies, and further improving heat dissipation efficiency. Attached Figure Description

[0028] Figure 1 This is a schematic diagram of a specific embodiment of the liquid-cooled heat dissipation plate assembly of the present invention;

[0029] Figure 2 for Figure 1 Center view;

[0030] Figure 3 for Figure 2 Enlarged view of a portion of point A in the middle;

[0031] Figure 4 for Figure 2 Schematic diagram of the structure of the corrugated core board;

[0032] Figure 5 for Figure 4 Enlarged view of a portion of point B in the middle;

[0033] Figure 6 A schematic diagram of the stamping structure of the mold and the combined cutter head in the manufacturing process of this invention;

[0034] Figure 7 for Figure 6 A diagram showing the state of the air guide vane formed by stamping;

[0035] Figure 8 for Figure 7 Diagram showing the state of the twist at the tail end of the central guide vane;

[0036] Figure 9 for Figure 8 Side view.

[0037] In the diagram: 1-Metal base plate; 2-Sealed top plate; 3-Corrugated core plate; 31-Crest; 32-Trough; 33-Inclined sidewall; 4-First flow channel; 5-Second flow channel; 6-Guide vane; 61-Root; 62-Overhang; 63-Tail end; 7-Avoidance hole; 8-Combined cutter head; 81-Secondary punch; 9-Lower die; 91-Follower head; 92-Elastic element. Detailed Implementation

[0038] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only for explaining the invention and are not intended to limit the invention; that is, the described embodiments are merely some embodiments of the invention, and not all embodiments. The components of the embodiments of the invention described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0039] Therefore, the following detailed description of the embodiments of the invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the invention without inventive effort are within the scope of protection of the invention.

[0040] It should be noted that relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0041] The features and performance of the present invention will be further described in detail below with reference to embodiments.

[0042] Specific embodiments of the liquid-cooled heat dissipation plate assembly of the present invention are as follows: Figures 1 to 5As shown, the cold plate assembly includes a metal base plate 1 serving as the main heat exchange interface, a sealing top plate 2 disposed opposite to it, and a metal corrugated core plate 3 clamped and welded between the metal base plate 1 and the sealing top plate 2.

[0043] The metal base plate 1 and the sealing top plate 2 form a fluid chamber with a sealed periphery, open ends, and high pressure resistance by enclosing each other at the edges. In this embodiment, the metal base plate 1, the sealing top plate 2, and the corrugated core plate 3 are all made of aluminum alloy (such as 3003 aluminum alloy or 6061 aluminum alloy) with high thermal conductivity and good brazing performance, or oxygen-free copper material under extremely high heat dissipation requirements.

[0044] The thickness of the metal base plate 1 can be set according to the mechanical load requirements of the electronic device. Its outer surface is processed into a contact surface with extremely high flatness, which is used to achieve heat conduction with the power chip or battery cell surface through the thermal interface material. The corrugated core plate 3, through its continuous undulating structural characteristics, constructs multiple parallel flow channel spaces in the closed fluid cavity.

[0045] The corrugated core plate 3 has alternating peaks 31 and troughs 32, and inclined sidewalls 33 connecting the peaks 31 and troughs 32. In this embodiment, the troughs 32 are firmly connected to the inner heat exchange surface of the metal base plate 1 by vacuum brazing, while the peaks 31 are also connected to the inner surface of the sealing top plate 2 by brazing.

[0046] This connection method divides the fluid chamber into several parallel fluid channels extending axially. To overcome the limitations of traditional rectangular channels in terms of heat exchange area, the fluid channels in this embodiment include a first channel 4 and a second channel 5 arranged alternately in sequence perpendicular to the fluid flow direction. The cross-section of the first channel 4 is a trapezoidal shape that is wider at the bottom and narrower at the top, and its wide bottom surface directly constitutes the effective heat exchange area on the metal base plate 1. Correspondingly, the cross-section of the second channel 5 is an inverted trapezoidal shape that is narrower at the bottom and wider at the top, and its contact area with the metal base plate 1 is extremely small.

[0047] Under actual operating conditions, because the first flow channel 4 has an effective wetting perimeter that far exceeds that of traditional rectangular flow channels, the cooling medium can achieve more thorough contact with the metal base plate 1, which is subjected to the most intense heating. This reduces the overall thermal resistance of the cold plate and improves the heat diffusion capability. Compared to the first flow channel 4, the second flow channel 5 does not directly contact the base plate and is subjected to relatively less heating. Therefore, the cooling medium inside it always maintains a lower energy level (cold water), which can meet the needs of subsequent cross-channel make-up cooling to achieve the purpose of mixing hot and cold fluids.

[0048] In this embodiment, a flow guiding unit is designed on the inclined sidewall 33 of the corrugated core plate 3. Multiple flow guiding units are arranged at intervals on both sides of the inclined sidewall 33 of the first flow channel 4. Each flow guiding unit consists of a flow guiding vane 6 with specific spatial orientation and an avoidance hole 7 associated with the sidewall.

[0049] The guide vane 6 is integrally formed from a portion of the base material of the inclined sidewall 33 through stamping and bending. It includes an integral root 61 that remains continuous with the inclined sidewall 33, and an overhang 62 extending into the central region of the flow channel. In this embodiment, the root 61 of the guide vane 6 is located upstream, while the overhang 62 is located downstream, forming a guide surface that gradually tapers into the flow channel from front to back. The folding angle of the overhang 62 relative to the sidewall plane is set to approximately between 15 and 45 degrees, preferably 30 degrees, which allows the fluid to generate a smooth momentum deflection when it contacts the vane.

[0050] The tail end 63 of the overhang 62 undergoes secondary mechanical shaping to form a wedge-shaped extrusion gap with the metal base plate 1, thereby creating a guiding curved surface pointing towards the metal base plate 1 at the end edge of the tail end 63 of the guide vane 6. When the fluid converges towards the center along the overhang 62 and enters the wedge-shaped extrusion gap between the tail end 63 and the metal base plate 1, the momentum of the fluid in the direction perpendicular to the metal base plate 1 is converted into extrusion static pressure towards the surface of the metal base plate 1 due to the restriction of the end edge. At the instant this part of the fluid leaves the tail end 63, it is entrained by the low-pressure area behind the tail end 63, generating a velocity component pointing towards the surface of the metal base plate 1, forming a high-speed scouring flow running closely against the metal base plate 1, thereby forcibly stripping the laminar thermal boundary layer on the surface of the metal base plate 1.

[0051] Furthermore, the height at which the guide vane 6 flips up in the flow channel (i.e., the normal height of the tail end 63 of the overhang 62 from the sidewall) is 15% to 30% of the width of the flow channel at that location. If the proportion is less than 15%, the agitation effect of the vane on the boundary layer is insufficient to penetrate the laminar sublayer; if the proportion exceeds 30%, it will cause severe throttling in the mainstream region of the flow channel center, inducing uncontrollable pressure drop losses.

[0052] Correspondingly, the clearance hole 7 is formed by a naturally formed hole left by the inclined sidewall 33 after the flow guide vane 6 is formed by stamping. The clearance hole 7 is located downstream of the root 61, and because the overhang 62 of the flow guide vane 6 is deflected toward the inner center, the overhang 62 can effectively shield the clearance hole 7 in the radial projection direction.

[0053] When the cooling medium flows at high speed along the longitudinal direction of the first flow channel 4 under the driving force of the pump pressure, the fluid near the side wall first contacts the root 61 of the guide vane 6 and accelerates towards the center of the flow channel along the inner surface of the micro-wing.

[0054] During this process, because the overhang 62 of the guide vane 6 has a guiding angle pointing towards the base plate, the fluid is forced to form a directional diving jet the instant it leaves the vane. This jet directly impacts the high-temperature boundary layer on the metal base plate 1 vertically or obliquely, generating a strong stagnation heat transfer effect, which rapidly strips away the heat that was originally trapped on the surface of the base plate and entrains it into the main fluid.

[0055] At the same time, those skilled in the art should understand that in the macroscopic channel where the first channel 4 and the second channel 5 are connected in parallel, although the first channel 4 has a high friction coefficient due to the presence of the guide vane 6, at the microscopic flow field level, multiple asymmetric local contraction throats are formed between the overhang 62 of the guide vane 6 and the inner wall of the channel.

[0056] When the fluid flows through the local contraction throat defined by the overhang 62, the fluid contracts, causing the characteristic flow velocity in this local area to be significantly higher than the average flow velocity at the inlet of the first flow channel 4. The increase in kinetic energy is inevitably accompanied by a decrease in static pressure energy. Through the design position of the overhang 62 and the overlapping of the shielding hole 7, the local instantaneous static pressure at the shielding hole 7 is lower than the average static pressure of the adjacent second flow channel 5. This local pressure difference constitutes the power source to overcome the local resistance of the cross-channel flow and realizes cold energy compensation.

[0057] When the fluid flows through the guide vane 6, which contracts towards the center, a sudden increase in flow velocity creates a momentary local negative pressure zone at the obstructed clearance hole 7 on the back side of the guide vane 6. Since the flow velocity in the adjacent second flow channel 5 is relatively stable and the pressure energy is relatively high, driven by this negative pressure gradient, the low-temperature cooling medium in the second flow channel 5 will automatically and spontaneously flow across the clearance hole 7 into the first flow channel 4.

[0058] In addition, in order to form alternating S-shaped vortex bands in the first flow channel and enhance the lateral mixing of the fluid, the guide vanes 6 are alternately staggered on the side walls of both sides of the first flow channel 4.

[0059] The introduction of this lateral coolant works synergistically with the longitudinal spiral vortex generated by the guide vanes 6 within the first flow channel 4, significantly disrupting the stability of the flow field and generating a wider range of three-dimensional turbulence. In this way, not only is the excess cold energy within the second flow channel 5 utilized, but also the extreme mixing of hot and cold fluids achieves exceptionally good temperature uniformity on the surface of the cold plate, solving the temperature gradient problem caused by traditional isolated flow channels.

[0060] In other embodiments, in order to balance the flow resistance, the guide vanes are not continuously arranged on the sidewall, but are only concentrated in the first 30% of the flow channel in each turbulence cycle. The turbulence generated in the initial stage can realize self-sustaining vortex heat transfer in the subsequent 70% length, thereby significantly improving the heat dissipation limit while keeping the total pressure drop of the system within a reasonable range.

[0061] In other embodiments, the tail end of the guide vane may be replaced by a guide surface with a specific curvature or a multi-level stepped surface to adapt to the thermal boundary layer stripping requirements under different flow rate conditions.

[0062] In other embodiments, the integrally formed guide vanes and associated clearance holes formed by stamping and bending can be replaced by separately implanted turbulence components or three-dimensional microstructures processed by precision etching, in order to achieve finer control of the flow field on a smaller scale.

[0063] In other embodiments, the trapezoidal or inverted trapezoidal cross-section flow channel can also be replaced by a sinusoidal, semi-circular, or triangular cross-section flow channel, thereby optimizing the pressure loss along the flow path under different cooling medium viscosities.

[0064] In other embodiments, the guide vanes may be replaced by a mirror-symmetric arrangement or a non-periodic array with variable pitch characteristics to suppress flow-induced vibrations at specific flow velocities and enhance local turbulence intensity.

[0065] Examples of the manufacturing process of the cold plate assembly involved in this invention, such as... Figures 6 to 9 As shown, the main steps include:

[0066] In step (1), the flat metal strip is processed into a corrugated structure with alternating positive and negative trapezoidal cross sections by precision rolling or continuous bending process, forming the blank of the corrugated core plate 3.

[0067] Subsequently, the core stamping process begins. In steps (2) and (3), a combined cutter head 8 with two-stage independent displacement is used for processing. The combined cutter head 8 is mounted on a high-speed press, while the lower die 9 is configured with a support protrusion that enters the flow channel gap of the corrugated core plate 3. To prevent the thin-walled sidewall from becoming unstable and collapsing during the stamping process, the lower die 9 is also equipped with a follower head 91, which is floatingly mounted on the top edge of the lower die 9 via an elastic element 92.

[0068] In step (2), the combined cutter head 8 is pressed down along the first direction. The edge of the cutter head first cuts out the wing profile on the inclined sidewall 33, and then pushes it into the flow channel as the stroke progresses. At this time, a preset flip angle is formed between the guide wing 6 and the sidewall. During this stage, the follower head 91 in the lower die 9 remains stationary and cooperates with the lower die forming cavity wall to provide rigid support.

[0069] In step (3), the secondary punch 81 in the combined cutter head 8 is driven by the internal slider mechanism and independently moves further along the second direction. The secondary punch 81 acts precisely on the tail end 63 of the guide vane 6. At this time, the position of the follower head 9 corresponding to the projection area of ​​the secondary punch 81 moves down synchronously after being pressed, thereby forming a local forming cavity. The secondary punch 81 presses the tail end 63 of the guide vane 6 into the forming cavity. By applying a torsional torque to the overhang 62 of the guide vane 6, one side edge of the tail end 63 of the guide vane 6 is twisted and deformed downwards to form a downward-facing flow-guiding surface facing the bottom edge of the fluid channel. Through this combined torsion and shaping action, during the torsion process, due to the forced directional displacement of one side of the guide vane 6 by the secondary punch 81, while the other side and the root are geometrically constrained by the sidewall base material, shear stress is generated inside the guide vane 6 and lattice slip is induced, thereby achieving the transition from the inclined plane to the spatial torsional curved surface without destroying the continuity of the material.

[0070] In step (4), the corrugated core plate 3, metal base plate 1, and sealing top plate 2 with the above-mentioned microstructure are precisely stacked and positioned. The assembly is then sent into a vacuum brazing furnace, where the joints are joined together at a controlled temperature close to the melting point of the materials to obtain a liquid cooling plate.

[0071] In other embodiments, the secondary displacement shaping process implemented by the combined cutting head can also be replaced by multi-station molds in separate processes.

[0072] In other embodiments, the lower mold structure with supporting protrusions and follower heads can also be replaced by a flexible mold with hydraulic compensation function or a combination fixture with multi-degree-of-freedom adjustment capability to ensure the stability of sidewall support during the processing of corrugated core plates of different thicknesses.

[0073] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. The scope of patent protection of the present invention shall be determined by the claims. Similarly, any equivalent structural changes made based on the description and drawings of the present invention shall also be included within the scope of protection of the present invention.

Claims

1. A liquid-cooled heat dissipation plate assembly, characterized in that, include: A metal base plate and a sealed top plate together form a closed fluid chamber; A corrugated core plate is built into the fluid chamber. The corrugated core plate has alternating crests and troughs, and inclined sidewalls connecting the crests and troughs. The troughs are connected to the metal base plate, and the crests are connected to the sealing top plate, so as to divide the fluid chamber into several parallel fluid channels. The fluid channels include a first channel with a wide bottom and a narrow top, and a second channel with a narrow bottom and a wide top, which are arranged alternately along the direction perpendicular to the fluid flow. Multiple flow guiding units are arranged at intervals on the inclined sidewall of at least one side of the first flow channel, including flow guiding vanes and clearance holes opened on the inclined sidewall, the clearance holes connecting to adjacent fluid channels. The guide vane includes a root integrally connected to the inclined sidewall, and an overhang located downstream of the root and extending toward the bottom center of the fluid channel along the flow direction of the fluid. The overhang forms a local contraction throat between the overhang and the inclined sidewall on the opposite side. The flow area of ​​the local contraction throat is smaller than the average flow area of ​​the first flow channel. The overhang covers the clearance hole in the radial projection direction of the fluid channel so as to utilize the local instantaneous dynamic pressure rise and static pressure drop generated when the fluid flows through the local contraction throat to adsorb the cooling medium in the second flow channel into the first flow channel through the clearance hole.

2. The liquid-cooled heat dissipation plate assembly according to claim 1, characterized in that, A wedge-shaped compression gap is formed between the tail end of the overhang of the guide vane and the metal base plate, so as to form a guide surface pointing towards the metal base plate at the tail end of the guide vane.

3. The liquid-cooled heat dissipation plate assembly according to claim 2, characterized in that, The guide vane is integrally formed by stamping and bending a portion of the inclined sidewall, and the clearance hole is formed by the forming hole formed on the portion of the sidewall after being stamped.

4. The liquid-cooled heat dissipation plate assembly according to any one of claims 1-3, characterized in that, The first flow channel has a trapezoidal cross-section, and the second flow channel has an inverted trapezoidal cross-section.

5. The liquid-cooled heat dissipation plate assembly according to any one of claims 1-3, characterized in that, The height at which the guide vanes fold up within the fluid channel is 15%-30% of the width of the fluid channel at that location.

6. The liquid-cooled heat dissipation plate assembly according to any one of claims 1-3, characterized in that, The guide vanes are distributed on the inclined sidewalls on both sides of the first flow channel, and the guide vanes on both sides are alternately staggered along the fluid flow direction.

7. A manufacturing process for preparing the liquid-cooled heat dissipation cold plate assembly as described in any one of claims 1-6, characterized in that, Includes the following steps: (1) Precast corrugated core plate: The metal sheet is processed into a corrugated structure with continuous undulation; (2) Stamping guide vanes: The pre-made corrugated core plate is placed in the mold, and the inclined side wall is stamped by the cutter head to form the initial outline and clearance hole of the guide vanes, and the guide vanes are pushed into the fluid channel to form a preset angle. (3) Angle torsion forming: By applying a torsional torque to the overhang of the guide vane, one side edge of the tail end of the guide vane is twisted and deformed downwards to form a downward-facing flow guide surface towards the bottom edge of the fluid channel. (4) Encapsulation and welding: The formed corrugated core plate, metal base plate and sealing top plate are stacked and welded together.

8. The preparation process according to claim 7, characterized in that, In steps (2) and (3), a combined cutting head is used for stamping. The combined cutting head is pressed down along the first direction to implement step (2). Then, the secondary punch in the combined cutting head moves independently along the second direction to implement step (3).

9. The preparation process according to claim 8, characterized in that, In steps (2) and (3), the mold includes a lower mold with a support protrusion that enters the external gap of the fluid channel to support the inclined sidewall during the stamping process. The lower mold also has a follower head that is floatingly supported on the lower mold. In step (2), the follower head is fixed in the lower mold, and in step (3), a portion of the follower head floats and moves downward following the secondary punch.

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