A high-flux heat spreader

Abstract

The application relates to the technical field of heat exchange, and discloses a high-flux heat dissipation plate which comprises a shell, an end cover fixed at one end of the shell, an intermediate plate, a plurality of arrayed flow guide blocks arranged at the upper and lower ends of the intermediate plate which is movably inserted into the shell, and a plurality of wave-shaped channels parallel to the water inlet and outlet direction formed in the gaps between the flow guide blocks. The curved surface structure of the wave-shaped channels is used for reflecting and mixing the cooling liquid, so that the cooling liquid can fully absorb the heat transferred by the shell and avoid forming a local overheating area. A flow guide mechanism is arranged in the rectangular frame, the flow guide mechanism uniformly guides the cooling liquid into the wave-shaped channels, and the cooling liquid can uniformly flow in the shell along the set direction. The application can construct a heat dissipation plate structure which is uniform in distribution, intense in mixing and efficient in flow, and the heat dissipation plate structure is excellent in single index, and remarkable overall balance is achieved among the heat dissipation performance, temperature uniformity, system energy efficiency and dynamic response speed.

Description

Technical Field

[0001] This invention relates to the field of heat exchange technology, specifically a high-throughput heat dissipation plate. Background Technology

[0002] The core contradiction facing current liquid cooling technology lies in the inherent defects of traditional solutions that are difficult to reconcile in terms of key performance indicators. For example, although serpentine channel liquid cooling plates can ensure cooling coverage by increasing the flow path, their physical structure leads to a systemic bottleneck. The long and winding single flow channel generates extremely high flow resistance, making the system dependent on high-power, high-head water pumps. More importantly, its first-in-first-out series flow mode inevitably leads to the coolant being continuously heated during the flow process, resulting in a significant frictional temperature rise effect and uneven temperature distribution on the surface of the cold plate (cold at the inlet and hot at the outlet). In high heat flux density applications, this can easily form harmful local hot spots, and its large fluid heat capacity leads to a slow thermal response. While the parallel DC channel, as an alternative, significantly reduces flow resistance due to its straight flow path, it shifts the problem to the flow distribution stage. Its flow distribution relies entirely on the flow resistance matching of each branch, which can easily lead to severe uneven flow distribution. Some channels may even experience flow stagnation, forming cooling dead zones, and the heat dissipation uniformity will deteriorate. Therefore, the existing technology is always trapped in the dilemma of high flow resistance and uneven flow, and cannot achieve a synergistic breakthrough in system energy efficiency (low flow resistance), heat dissipation uniformity, and the ability to cope with high heat flux density.

[0003] To solve the above-mentioned technical problems, it is urgent to construct a heat dissipation plate structure that is uniformly distributed, vigorously mixed, and has high flow efficiency, thereby solving the technical problems of high flow resistance and uneven flow in existing technologies. Summary of the Invention

[0004] Technical problems to be solved

[0005] To address the shortcomings of existing technologies, this invention provides a high-throughput heat dissipation plate that solves the dilemma of high flow resistance and uneven flow in existing technologies, which cannot achieve a synergistic breakthrough in system energy efficiency, heat dissipation uniformity, and the ability to cope with high heat flux density.

[0006] Technical solution

[0007] To achieve the above objectives, the present invention provides the following technical solution: a high-throughput heat dissipation plate, comprising a housing and an end cap fixed to one end of the housing, and further comprising:

[0008] The intermediate plate is movably inserted into the housing and has multiple arrayed guide blocks at both the upper and lower ends. The gaps between the multiple guide blocks form multiple wave-shaped channels parallel to the inlet and outlet directions. The curved structure of the wave-shaped channels reflects and mixes the coolant, allowing the coolant to fully absorb the heat transferred from the housing and avoid the formation of local overheating areas.

[0009] A rectangular frame is provided with a flow guiding mechanism, which uniformly guides the coolant into multiple wavy channels, so that the coolant can flow evenly in the shell along a set direction.

[0010] The rectangular frame is fixed to one side of the end cap, and two water inlet pipes are fixedly connected to one side of the end cap. Two drain pipes are fixedly connected to one side of the housing.

[0011] As a further description of the above technical solution, the intermediate plate is inserted into the housing and divides the interior of the housing into two DC channels, upper and lower. The sidewalls of the intermediate plate are arrayed with multiple baffles. The multiple baffles are distributed in the wave-shaped channel and form multiple sets of transversely arranged turbulence arrays with the guide blocks. A crossflow zone is formed between two adjacent sets of turbulence arrays, so that the coolant continuously and alternately passes through multiple turbulence arrays and crossflow zone to reflect and mix the coolant. The end of the baffle and guide block away from the intermediate plate is in contact with the inner wall of the housing.

[0012] As a further description of the above technical solution, the guide block is provided with an outwardly convex arc-shaped part and two inwardly concave parts on opposite sides. The two inwardly concave parts are symmetrically distributed on both sides of the arc-shaped part, so that the sidewall of the guide block forms a symmetrical polyhedral structure. The arc-shaped part and the inwardly concave parts have the same curvature, so that the arrayed guide blocks form a wave-shaped channel.

[0013] As a further description of the above technical solution, the structure of the baffle is one of a cylinder, a rhombus, an elliptical cylinder, and a C-shaped plate, wherein the side wall of the baffle is provided with a load reduction hole, and the center line of the load reduction hole is perpendicular to the crossflow zone.

[0014] As a further description of the above technical solution, the flow guiding mechanism includes two V-shaped rubber plates symmetrically fixed within a rectangular frame. The bends of the two V-shaped rubber plates form a flow guiding channel. One end of the intermediate plate is fixedly connected to a flow guiding plate. One side of the flow guiding plate is fixedly connected to one end of the two V-shaped rubber plates. The side wall of the flow guiding plate is provided with multiple evenly distributed flow guiding holes, and the flow guiding holes correspond to the positions of the wavy channel. When the flow guiding plate is sleeved inside the housing, the gap is less than 0.3-0.5 mm.

[0015] As a further description of the above technical solution, multiple support strips matching the V-shaped rubber plate structure are fixedly connected to both opposite sides of the rectangular frame. One end of each of the multiple support strips is fixedly connected to one end of the guide plate. A gap of 2-4mm is reserved between the support strips and the V-shaped rubber plate, so that the V-shaped rubber plate deforms under the pressure of the coolant, thereby changing the flow rate of the guide channel.

[0016] As a further description of the above technical solution, one end of the housing is provided with an outward flange, the end cap is fixedly connected to the outward flange by bolts, and a rubber frame is provided between the end cap and the outward flange. The rectangular frame is inserted into the housing and is fitted with multiple sealing rings.

[0017] As a further description of the above technical solution, a positioning plate is fixedly connected to one end of the intermediate plate, and a plurality of evenly distributed drainage holes are opened on the side wall of the positioning plate. The drainage holes correspond to the positions of the wave-shaped channel. A plurality of curved plates are fixedly connected to one side of the positioning plate, and a plurality of drainage outlets are opened on the side wall of the curved plates. Guide rails are fixedly connected to opposite sides inside the housing. The edge of the intermediate plate is engaged in the guide rail. A through groove that cooperates with the guide rail is opened on the edge of the positioning plate.

[0018] As a further description of the above technical solution, a guide strip is fixedly connected to one side of the guide plate, and one end of the guide strip is provided with two guide surfaces that guide the coolant into the drain hole. A diversion channel is formed between the guide surfaces and the V-shaped rubber plate.

[0019] As a further description of the above technical solution, a conduit is fixedly connected between each of the two inlet pipes and the two outlet pipes, and a liquid pressure sensor is installed on the wall of the conduit.

[0020] Beneficial effects

[0021] Compared with the prior art, the present invention provides a high-throughput heat dissipation plate with the following beneficial effects:

[0022] 1. This technical solution adopts an inlet diversion design, which can form a flow from passive adaptation to active control. By designing an active diversion structure at the inlet, this technical solution physically limits the single incoming flow to "laminar flow" or a highly ordered "strip flow", realizing active control of flow distribution. It ensures from the source that the heat exchange area in the radiator can obtain a preset and uniform coolant supply, reducing the probability of local overheating caused by uneven distribution.

[0023] 2. This technical solution also designs a double-layer three-dimensional turbulence array. The turbulence array creates a three-dimensional network of fluid agitators. The staggered guide blocks on the upper and lower sides of the central plate not only disrupt the flow boundary layer in the horizontal direction and greatly enhance the convective heat transfer coefficient, but also induce strong secondary flow and vortex, so that the temperature of the coolant itself is rapidly homogenized in the flow channel.

[0024] 3. This technical solution is powered by DC cooling, which improves the flow path from "high resistance long path" to "low resistance parallel". Under the premise of ensuring uniformity and high efficiency, the advantages of DC flow channel can be perfectly brought into play. It abandons the long path and sharp bends that must be endured in the pursuit of coverage by serpentine channel, and improves it into a short and direct parallel path. This greatly reduces the flow resistance in the heat sink, reduces the power consumption of the system pump, and increases the flow rate of coolant so that the cold plate can respond to changes in heat load faster. The use of short flow path makes the overall pressure drop more controllable and predictable, and facilitates matching design with system pump. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the structure of a high-throughput heat dissipation plate proposed in this invention;

[0026] Figure 2 The present invention proposes a high-throughput heat dissipation plate. Figure 1 A partial sectional view;

[0027] Figure 3 The present invention proposes a high-throughput heat dissipation plate. Figure 1 Overall sectional view;

[0028] Figure 4 This is a schematic diagram of the structure of the middle end cover, rectangular tube and central plate of a high-throughput heat dissipation plate proposed in this invention;

[0029] Figure 5 This is a side view of the end cap, rectangular tube, and center plate of a high-throughput heat dissipation plate proposed in this invention.

[0030] Figure 6 This invention proposes a high-throughput heat dissipation plate. Figure 5 Cross-sectional view of the middle end cap, rectangular tube, and center plate;

[0031] Figure 7 This is a schematic diagram of the shell structure in a high-throughput heat dissipation plate proposed in this invention;

[0032] Figure 8 The present invention proposes a high-throughput heat dissipation plate. Figure 4 Top view;

[0033] Figure 9 This is a schematic diagram of the structure of multiple blocks in a high-throughput heat dissipation plate proposed in this invention;

[0034] Figure 10 The present invention proposes a high-throughput heat dissipation plate. Figure 9 Top view;

[0035] Figure 11 This is a comparison of simulation predictions for cooling the cell surface using a conventional liquid cooling plate and a patented solution in the experimental examples of this invention.

[0036] Figure 12 This is a comparison chart of the simulated predicted surface temperatures of a conventional liquid cooling plate and a patented liquid cooling plate in the experimental examples of this invention.

[0037] Figure 13 This is a comparison chart of the simulation predictions of the inlet and outlet pressure drops of the conventional liquid cooling plate and the patented liquid cooling plate in the experimental examples of this invention.

[0038] In the diagram: 1. Housing; 2. Outward flange; 3. End cap; 4. Inlet pipe; 5. Drain pipe; 6. Guide pipe; 7. Liquid pressure sensor; 8. Intermediate plate; 9. Guide rail; 10. Positioning plate; 11. Drain hole; 12. Stop block; 13. Flow guide block; 14. Bend plate; 15. Load reduction hole; 16. Through groove; 17. Sealing ring; 18. Rectangular frame; 19. V-shaped rubber plate; 20. Flow guide hole; 21. Flow guide plate; 22. Support strip; 23. Rubber frame; 24. Flow guide strip; 25. Diversion channel; 26. Flow guide channel; 27. Crossflow area; 28. Turbulence array; 29. ​​Concave part; 30. Arc-shaped part. Detailed Implementation

[0039] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0040] Example:

[0041] Currently, for heat dissipation of energy storage devices, such as large computing centers and energy storage batteries, liquid cooling plates are typically installed between the batteries to achieve efficient heat dissipation of the battery pack. Inside the liquid cooling plate, a serpentine channel is used to extend the flow path of the liquid and increase the flow time of the coolant in the liquid cooling plate, thereby increasing the heat exchange coverage and achieving uniform heat dissipation. However, the fundamental drawback of the traditional serpentine channel lies in its inherent structural design. For example, the long path and continuous sharp bends (serpentine channel or continuous S-shaped channel) used to pursue heat dissipation path coverage inevitably lead to extremely high flow resistance inside the liquid cooling plate, which in turn requires the configuration of a high-power water pump, resulting in high system energy consumption and high noise. Furthermore, due to the fixed flow resistance and flow rate, the pressure difference between the inlet and outlet is large, which can easily cause the liquid cooling plate to expand and deform under pressure. At the same time, the "first-in, first-out" single-channel unidirectional flow pattern of the coolant will form a significant temperature gradient along the flow path (low temperature at the inlet and high temperature at the outlet). Even if turbulence columns are set in the channel, it cannot change the problem of the local heat dissipation efficiency being reduced due to the increase in coolant temperature at the outlet. Moreover, adding turbulence columns in the curved and narrow channel will undoubtedly further increase the flow resistance and reduce the flow velocity. In addition, the long fluid path and large heat capacity result in a slow thermal response speed, which is difficult to meet the heat dissipation requirements of modern equipment under transient high heat loads. Therefore, this technical solution designs a heat dissipation plate with high heat dissipation performance, excellent temperature uniformity, low pump power consumption requirements, and fast dynamic response.

[0042] The core innovation of this technical solution lies in its high-throughput, direct-flow internal channel, which reduces the flow path length of the coolant. This low-resistance, high-velocity cooling method improves the dynamic response speed of heat dissipation. Furthermore, by designing an active flow-diverting structure at the inlet and a double-layered three-dimensional turbulent column array inside the radiator, it overturns the traditional passive flow mode that relies on a single long path. This achieves uniform flow distribution at the source and three-dimensional turbulent mixing, which not only significantly reduces flow resistance but also fundamentally solves the problem of uneven flow distribution inside the heat sink. Thus, it simultaneously achieves integrated optimization of high heat dissipation performance, excellent temperature uniformity, low pump power consumption, and rapid dynamic response. The specific technology of this high-throughput heat sink is as follows:

[0043] Please see the appendix Figures 1-10 The heat sink includes a housing 1 and an end cap 3 fixed to one end of the housing 1. The housing 1 has a box-like structure with a thickness of 1-1.5 cm, and a special airflow guiding component is designed at one end of the end cap 3, such as... Figure 3 As shown, the housing 1 and the flow guiding assembly form a "drawer" structure. The end cap 3 is sealed to the housing 1 by bolts and related seals. Both the inlet and outlet ends are equipped with two inlet and outlet pipes, forming a dual-inlet and dual-outlet effect to reduce flow resistance. In addition, the drawer structure design allows for easy removal of the flow guiding assembly later for thorough cleaning of internal scale.

[0044] An intermediate plate 8 is also designed inside the housing 1. The intermediate plate 8 is movably inserted into the housing 1 and has multiple arrayed guide blocks 13 at both its upper and lower ends. The gaps between the multiple guide blocks 13 form multiple wave-shaped channels parallel to the inlet and outlet directions. Each guide block 13 has a convex arc-shaped part 30 and two concave parts 29 on opposite sides. The two concave parts 29 are symmetrically distributed on both sides of the arc-shaped part 30, so that the sidewalls of the guide blocks 13 form a symmetrical polyhedral structure, specifically a hexahedral structure with an arc surface, such as... Figure 9 As shown, the guide block 13 has two "points" and two "protrusions". The two "points" can divert the coolant, and the two "protrusions" form a wave structure. Therefore, when the coolant flows, the arc-shaped part 30 of the protrusion can reflect the water flow, thus creating a natural mixing effect in the wave-shaped channel. The arc-shaped part 30 and the concave part 29 have the same curvature, so that the arrayed guide blocks 13 form a wave-shaped channel. The curved structure of the wave-shaped channel reflects and mixes the coolant to fully absorb the heat transferred by the shell 1, avoiding the formation of local overheating areas. In order to further homogenize the coolant flow, baffles can be used in the wave-shaped channel for secondary reflection and diversion. Therefore, the structure of the baffle 12 can be used for secondary reflection and diversion, and at the same time, the cooling flow rate can be limited to ensure that the coolant has enough time to absorb heat. The structure of the baffle 12 used in this technical solution is not unique. It can be one of the following: cylindrical, rhomboid, elliptical column, and C-shaped plate. The specific configuration is as follows. Figures 9-10 As shown, the side wall of the baffle 12 is provided with a load reduction hole 15. Since the core of this technical solution is to increase the flow rate, and to exchange the cooling effect and the speed of response to temperature changes for high flow rate and uniformity, when the coolant impacts the baffle 12, the coolant passing through the load reduction hole 15 can form a water column and enter the crossflow zone 27. The center line of the load reduction hole 15 is perpendicular to the crossflow zone 27, which will cause the coolant to be further impacted and mixed in the crossflow zone 27.

[0045] In existing technologies, coolant crystallization and deposition are unavoidable phenomena, resulting from the coupling of multiple factors including chemistry, physics, and fluid dynamics. The fundamental internal cause lies in the coolant's own chemical properties, such as phase change crystallization occurring below the freezing point, or salting out due to evaporation and concentration of additives or incompatible reactions. Key external factors include localized low-temperature points or stagnant zones with insufficient flow velocity. The former induces supercooling and supersaturation precipitation, while the latter, due to insufficient fluid shear force, fails to flush away microcrystal nuclei and particles, providing a breeding ground for deposition. Furthermore, impurities from coolant oxidation and degradation, as well as incompatible reaction products, also become deposition sources. Currently, the solution is to replace the coolant, but existing scale deposits remain trapped in the radiator's internal channels and cannot be drained.

[0046] In summary, unlike existing technologies with serpentine or loop-shaped channels, this technical solution utilizes a high-velocity, strong-turbulence direct-flow channel design to fundamentally eliminate stagnant areas, enhance flushing effects, and improve temperature uniformity. This effectively inhibits scale buildup. Combined with a high-quality coolant formula and rigorous system maintenance, the probability of crystallization and blockage inside the radiator will be greatly reduced.

[0047] Secondly, in this technical solution, the intermediate plate 8 is directly inserted into the housing 1, dividing the interior of the housing 1 into two DC channels, upper and lower. Even if a blockage occurs with a small probability, causing one DC channel to become blocked and the flow rate to decrease or stop, the other DC channel can continue to circulate coolant, maintaining a certain heat dissipation effect. The side wall of the intermediate plate 8 is arrayed with multiple baffles 12, which are distributed in the wave-shaped channel and form multiple sets of transversely arranged turbulence arrays 28 with the guide blocks 13. A crossflow zone 27 is formed between two adjacent sets of turbulence arrays 28, allowing the coolant to continuously and alternately pass through multiple turbulence arrays 28 and crossflow zone 27 to reflect and mix the coolant. The end of the baffle 12 and the guide block 13 away from the intermediate plate 8 is in contact with the inner wall of the housing 1. At this time, the high temperature on the blocked side can also be conducted through the coolant, baffle 12 and guide block 13, and the heat can still be discharged through the coolant flowing on the other side.

[0048] In addition, the liquid pressure sensor 7 can detect or periodically collect the pressure difference between the inlet and outlet ends. When maintenance is required, the "detachable" structure of this technical solution can be used to remove the bolts and directly pull out the end cover 3 along with the intermediate plate 8, so that the baffle 12 and the guide block 13 are completely exposed outside the housing 1. In this way, the baffle 12, the guide block 13 and the inside of the housing 1 can be cleaned quickly and thoroughly without replacing the radiator assembly.

[0049] like Figure 10 As shown, when the coolant flows through the turbulence array 28, the structure of the baffle 12 and the guide block 13 can reflect and guide the coolant. After reflection and guidance, the coolant enters a crossflow zone 27 without obstructions. After mixing, it enters the next turbulence array 28 for reflection and guidance. This process is repeated until the coolant passes through the last turbulence array 28 and is discharged. This achieves repeated reflection and guidance, making the flow distribution inside the heat sink uniform, and simultaneously achieving high heat dissipation performance and excellent temperature uniformity.

[0050] It should be noted that, with Figure 9For example, the longitudinal gap of the guide block 13 array is defined as a wavy channel, and the transverse gap is defined as a crossflow zone 27. In this way, the wavy channel and the crossflow zone 27 can form multiple intersections, so that the coolant forms turbulence when passing through the intersection. A further design is to arrange the baffles 12 in an array in the wavy channel, which further limits the space in the wavy channel and allows the coolant to travel in a smaller curvature path. While ensuring the uniformity of flow, the flow rate is also taken into account.

[0051] A rectangular frame 18 is provided between the housing 1 and the end cap 3. The rectangular frame 18 is fixed to one side of the end cap 3. One end of the housing 1 is provided with an outward flange 2. The end cap 3 is fixedly connected to the outward flange 2 by bolts. A rubber frame 23 is provided between the end cap 3 and the outward flange 2. The rectangular frame 18 is inserted into the housing 1 and multiple sealing rings 17 are embedded. The design of the rubber frame 23 and the sealing rings 17 provides good sealing between the end cap 3 and the housing 1. A flow guiding mechanism is provided inside the rectangular frame 18. The flow guiding mechanism guides the coolant evenly into multiple wave-shaped channels, so that the coolant can flow evenly in the housing 1 in a set direction. Two water inlet pipes 4 are fixedly connected to one side of the end cap 3, and two drain pipes 5 are fixedly connected to one side of the housing 1. A conduit 6 is fixedly connected between the two water inlet pipes 4 and the two drain pipes 5. A liquid pressure sensor 7 is installed on the wall of the conduit 6. The designed liquid pressure sensor 7 can monitor the pressure difference between the water inlet and the water outlet in real time. When the pressure difference exceeds the threshold, it indicates that the internal channel is blocked.

[0052] As one of the key aspects of this technical solution, the function of the flow guiding mechanism is to fundamentally solve the problem of uneven flow distribution inside the heat sink by evenly distributing the coolant flow from the source.

[0053] For detailed technical solutions, please refer to [link / reference]. Figure 5 and Figure 6 The flow guiding mechanism includes two V-shaped rubber plates 19 symmetrically fixed within a rectangular frame 18. The bends of the two V-shaped rubber plates 19 form a flow guiding channel 26. The flow guiding channel 26 allows the water discharged from the two inlet pipes 4 to be diverted through the narrow channel, so that the form of the coolant is physically defined as "laminar flow" or a highly ordered "ribbon flow". One end of the intermediate plate 8 is fixedly connected to a flow guiding plate 21. One side of the flow guiding plate 21 is fixedly connected to one end of the two V-shaped rubber plates 19. The side wall of the flow guiding plate 21 has multiple evenly distributed flow guiding holes 20, and the flow guiding holes 20 correspond to the positions of the wavy channel. When the flow guiding plate 21 is fitted into the housing 1, the gap is less than 0.3-0.5 mm. When the pressure of the coolant is high, the elastically deformable V-shaped rubber plates 19 can deform under the action of water pressure.

[0054] Multiple support bars 22, matching the structure of the V-shaped rubber plate 19, are fixedly connected to opposite sides of the rectangular frame 18. One end of each support bar 22 is fixedly connected to one end of the guide plate 21. The support bars 22 are mainly used to limit the deformation of the V-shaped rubber plate 19 and connect the intermediate plate 8, making it easy to remove the intermediate plate 8 during maintenance and cleaning. A 2-4mm gap is reserved between the support bars 22 and the V-shaped rubber plate 19, so that the V-shaped rubber plate 19 deforms under the pressure of the coolant, increasing the flow area of ​​the guide channel 26, thereby increasing the flow rate and changing the flow volume of the guide channel 26.

[0055] A positioning plate 10 is fixedly connected to one end of the intermediate plate 8. The side wall of the positioning plate 10 has multiple evenly distributed drain holes 11. The drain holes 11 correspond to the positions of the wave-shaped channels. The fixed number and fixed position of the drain holes can allow the coolant to be discharged separately according to the set position, so as to avoid affecting the stability of the internal coolant flow when discharged uniformly. Therefore, a design of dispersed entry and dispersed discharge is adopted to make the flow rate of coolant in the flow area inside the shell 1 uniform. A number of bent plates 14 are fixedly connected to one side of the positioning plate 10, and the side wall of the bent plates 14 has multiple drain ports. Guide rails 9 are fixedly connected to opposite sides inside the shell 1. The edge of the intermediate plate 8 is engaged in the guide rail 9. The edge of the positioning plate 10 has a through groove 16 that matches the guide rail 9. A guide strip 24 is fixedly connected to one side of the guide plate 21. One end of the guide strip 24 is provided with two guide surfaces that guide the coolant into the drain hole 11. A flow-dividing channel 25 is formed between the guide surface and the V-shaped rubber plate 19. When the coolant, which is limited to "laminar flow" or highly ordered "ribbon flow", is divided into two streams and discharged to the upper and lower sides of the middle plate 8 respectively, the coolant can flow at a similar flow rate in the upper and lower channels.

[0056] This technical solution, by adopting an inlet diversion design, can form a coolant flow that shifts from passive adaptation to active control. Traditional cold plate flow distribution relies on the pressure balance within the inlet manifold, which is a passive adaptation to the width of the internal water flow channel. However, this technical solution, by designing an active diversion structure at the inlet, physically limits the single incoming flow to "laminar flow" or a highly ordered "strip flow," thus achieving active control over the flow distribution. This ensures from the source that the heat exchange area within the plate receives a preset, uniform coolant supply, reducing the probability of local overheating (hot spots) caused by uneven distribution. This is also the first element in achieving excellent temperature uniformity.

[0057] Secondly, the design of this technical solution can form a double-layer three-dimensional turbulence array. This represents an improvement over the traditional serpentine channel's "two-dimensional extension" heat exchange scheme, which uses a direct-flow "three-dimensional stirring" method. Traditional serpentine channels only increase contact time by extending the two-dimensional path, while this technical solution's double-layer three-dimensional turbulence array creates a three-dimensional network of "fluid agitators." The staggered guide blocks 13 on the surface of the central plate 8 not only disrupt the flow boundary layer in the horizontal direction and greatly enhance the convective heat transfer coefficient, but also induce strong secondary flows and vortices. This full-space three-dimensional turbulent mixing allows the coolant's temperature to be rapidly homogenized within the flow channel, resolving the often contradictory goals of "enhanced heat transfer" and "improved temperature uniformity," thereby achieving the ultimate goal of efficient and uniform heat dissipation.

[0058] Finally, and most importantly, this invention utilizes direct-flow cooling to improve the flow path from a "high-resistance, long path" to a "low-resistance, parallel path." With the above two innovations ensuring "uniformity" and "efficiency," the advantages of the direct-flow channel are fully realized. It eliminates the lengthy paths and sharp bends inherent in serpentine channels that must be tolerated to achieve coverage, replacing them with short and direct parallel paths. This significantly reduces flow resistance within the heatsink (pressure loss primarily comes from turbulence columns rather than lengthy bends), drastically reducing system pump power consumption and easily increasing coolant flow rate. This allows the cold plate to respond faster to changes in heat load. Simultaneously, the short flow path makes the overall coolant pressure more controllable and predictable, facilitating matching design with the system pump. Ultimately, it combines the inherent advantages of direct-flow cooling—"low flow resistance, fast response"—with the capabilities of "high temperature uniformity, strong heat exchange," forming a high-throughput heatsink structure.

[0059] Experimental example:

[0060] To verify the technical effectiveness of the novel liquid-cooled plate structure described in this invention, this experimental example employs a combination of computer simulation prediction and prototype testing. Under identical heat load and cooling conditions, it is compared with a traditional S-shaped channel liquid-cooled plate. For detailed comparison results, please refer to [link / reference needed]. Figures 11-13 ;

[0061] I. Comparison Objects and Test Conditions:

[0062] Example: The liquid cooling plate with fractal branching and gradient cross-section features provided by the present invention;

[0063] Comparative example: Traditional S-shaped channel liquid cooling plate;

[0064] Standardized testing conditions:

[0065] Thermal load: Simulates a battery module consisting of 52 cells, with each cell generating 12W of heat, and the total system heat generation power is 624W.

[0066] Cooling system:

[0067] Cooling medium: 50% ethylene glycol aqueous solution (by volume).

[0068] Coolant inlet temperature: 18℃ (constant).

[0069] Coolant volumetric flow rate: 6.25 L / min.

[0070] Performance goals:

[0071] The temperature rise (ΔT) of the liquid cooling plate itself is ≤ 3℃.

[0072] The system flow resistance voltage drop (ΔP) ≤ 10 kPa.

[0073] II. Comparative Analysis of Computer Simulations

[0074] Three-dimensional conjugate heat transfer simulation was performed using a computational fluid dynamics (CFD) model that had been verified for mesh independence and benchmarked.

[0075] The simulation results are compared in the table below:

[0076]

[0077] Preliminary simulation results show that the proposed solution exhibits significant advantages in terms of synergistic optimization in terms of heat dissipation capacity, temperature uniformity, and low flow resistance.

[0078] III. Actual Verification of the Prototype

[0079] To confirm the engineering validity of the simulation results, a 1:1 prototype was fabricated based on the technical solution of this invention, and standardized field tests were conducted.

[0080] 1. Testing Platform and Methods:

[0081] Prototype: A liquid-cooled plate prototype manufactured strictly according to the design drawings of this invention.

[0082] Thermal simulation: 52 precision thin-film heating elements with a nominal power of 12W are attached to the corresponding positions of the liquid cooling plate to simulate a uniform heat source with a total power of 624W.

[0083] Measurement system:

[0084] Temperature: The temperature of key points on the surface of the liquid cooling plate and the simulated battery cell was measured using 24 calibrated T-type thermocouples (accuracy ±0.5℃).

[0085] Pressure: High-precision differential pressure sensors (accuracy ±0.1% FS) are installed at the inlet and outlet of the liquid cooling plate to directly measure the pressure drop (ΔP).

[0086] Control: The inlet coolant temperature is maintained at (18.0±0.5)℃ by a constant temperature liquid chiller, and the flow rate is controlled at (6.25±0.10) L / min by a mass flow meter.

[0087] Procedure: After the system reaches thermal steady state (temperature change at all measuring points ≤0.1℃ within 10 minutes), record the data.

[0088] 2. Measured data and comparison:

[0089] Key results of actual measurement of the prototype of this invention:

[0090] The pressure drop across the liquid cooling plate is ΔP = 2.58 kPa.

[0091] The simulated maximum surface temperature of the battery cell is T(max) = 23.92℃;

[0092] The highest surface temperature of the liquid cooling plate is T_plate_max = 19.05℃ (corresponding to a temperature rise ΔT = 1.05℃).

[0093] Comparative analysis with simulation predictions:

[0094]

[0095] Experimental findings: The measured data closely match the simulation predictions, with the deviation rate of key indicators all less than 7%, fully verifying the reliability of the simulation model. The experimental results clearly show that the prototype of this invention fully achieves the excellent performance predicted by the simulation in actual operation, and the pressure drop (2.58 kPa) and temperature rise (1.05℃) are significantly better than the preset design targets (ΔP≤10kPa, ΔT≤3℃).

[0096] This experimental example, through a complete technical verification chain of "simulation-guided design - actual measurement verification," confirms that the liquid-cooled plate structure of this invention achieves the following technical effects compared to existing conventional solutions:

[0097] 1. This technical solution can effectively resolve the inherent contradiction between "enhanced heat transfer (requiring complex flow channels)" and "reduced flow resistance (requiring simple flow channels)" in high heat density heat dissipation. By adopting a high-throughput heat dissipation channel structure design and internal turbulence components, multiple mixed flow fields can be formed internally while ensuring flow rate. This significantly improves heat dissipation uniformity (temperature difference reduced by 32.4%) while reducing system flow resistance by about 51.5%, thus achieving a significant synergistic effect.

[0098] 2. This invention provides an efficient, reliable and energy-saving technical solution for the thermal management of high-power battery systems. It enables the battery system to operate in a healthy environment with lower cell operating temperature and a more uniform temperature field, which helps to extend the battery cycle life. At the same time, the liquid cooling plate has a lower system voltage drop, which can significantly reduce the energy consumption of the cooling system.

[0099] It should be noted that the term "comprising" or any other variation thereof is 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 limitation, 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.

[0100] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A high-throughput heat dissipation plate, comprising a housing (1) and an end cap (3) fixed to one end of the housing (1), characterized in that, Also includes: The intermediate plate (8) is movably inserted into the housing (1) and has multiple arrayed guide blocks (13) at both the upper and lower ends. The gaps between the multiple guide blocks (13) form multiple wave-shaped channels parallel to the water inlet and outlet directions. The curved structure of the wave-shaped channels reflects and mixes the coolant to fully absorb the heat transferred by the housing (1) and avoids the formation of local overheating areas. A rectangular frame (18) is provided with a flow guiding mechanism. The flow guiding mechanism includes two V-shaped rubber plates (19) symmetrically fixed inside the rectangular frame (18). The bending points of the two V-shaped rubber plates (19) form a flow guiding channel (26). One end of the intermediate plate (8) is fixedly connected to a flow guiding plate (21). One side of the flow guiding plate (21) is fixedly connected to one end of the two V-shaped rubber plates (19). The side wall of the flow guiding plate (21) is provided with a plurality of evenly distributed flow guiding holes (20), and the flow guiding holes (20) correspond to the positions of the wave-shaped channel. When the flow guiding plate (21) is sleeved inside the housing (1), the gap is less than 0.3-0.5 mm. One end of the intermediate plate (8) is fixedly connected to a positioning plate (10). The side wall of the positioning plate (10) is provided with a plurality of evenly distributed drainage holes (11). The drainage holes (11) correspond to the positions of the wave-shaped channels. One side of the positioning plate (10) is fixedly connected to a plurality of curved plates (14), and the side wall of the curved plates (14) is provided with a plurality of drainage outlets. The opposite sides of the housing (1) are fixedly connected to guide rails (9). The edge of the intermediate plate (8) is engaged in the guide rails (9). The edge of the positioning plate (10) is provided with a through groove (16) that cooperates with the guide rails (9). The flow guiding mechanism evenly guides the coolant into multiple wave-shaped channels, so that the coolant can flow evenly in the shell (1) along a set direction. The rectangular frame (18) is fixed to one side of the end cap (3), and two water inlet pipes (4) are fixedly connected to one side of the end cap (3), and two drain pipes (5) are fixedly connected to one side of the housing (1).

2. The high-throughput heat dissipation plate according to claim 1, characterized in that: The intermediate plate (8) is inserted into the housing (1) and divides the interior of the housing (1) into two DC channels, upper and lower. The side wall of the intermediate plate (8) is arranged with multiple baffles (12). The multiple baffles (12) are distributed in the wave-shaped channel and form multiple sets of transversely arranged turbulence arrays (28) with the flow guide block (13). A crossflow zone (27) is formed between two adjacent sets of turbulence arrays (28), so that the coolant continuously and alternately passes through multiple turbulence arrays (28) and crossflow zone (27) to reflect and mix the coolant. The end of the baffle (12) and the flow guide block (13) away from the intermediate plate (8) is in contact with the inner wall of the housing (1).

3. The high-throughput heat dissipation plate according to claim 1, characterized in that: The guide block (13) has an outwardly convex arc-shaped part (30) and two inwardly concave parts (29) on opposite sides. The two inwardly concave parts (29) are symmetrically distributed on both sides of the arc-shaped part (30), so that the side wall of the guide block (13) forms a symmetrical polyhedral structure. The arc-shaped part (30) and the inwardly concave parts (29) have the same curvature, so that the arrayed guide blocks (13) form a wave-shaped channel.

4. A high-throughput heat dissipation plate according to claim 2, characterized in that: The structure of the baffle (12) is one of a cylinder, a rhombus, an elliptical cylinder and a C-shaped plate, wherein the side wall of the baffle (12) is provided with a load reduction hole (15), and the center line of the load reduction hole (15) is perpendicular to the crossflow zone (27).

5. A high-throughput heat dissipation plate according to claim 1, characterized in that: Multiple support strips (22) matching the structure of the V-shaped rubber plate (19) are fixedly connected to the opposite sides of the rectangular frame (18). One end of each of the multiple support strips (22) is fixedly connected to one end of the guide plate (21). A gap of 2-4mm is reserved between the support strips (22) and the V-shaped rubber plate (19) so that the V-shaped rubber plate (19) deforms under the pressure of the coolant, thereby changing the flow rate of the guide channel (26).

6. A high-throughput heat dissipation plate according to claim 1, characterized in that: One end of the housing (1) is provided with an outward flange (2), the end cap (3) is fixedly connected to the outward flange (2) by bolts, and a rubber frame (23) is provided between the end cap (3) and the outward flange (2). The rectangular frame (18) is inserted into the housing (1) and is fitted with multiple sealing rings (17).

7. A high-throughput heat dissipation plate according to claim 1, characterized in that: A guide strip (24) is fixedly connected to one side of the guide plate (21). One end of the guide strip (24) is provided with two guide surfaces that guide the coolant into the drain hole (11). A diversion channel (25) is formed between the guide surface and the V-shaped rubber plate (19).

8. A high-throughput heat dissipation plate according to claim 1, characterized in that: A conduit (6) is fixedly connected between the two water inlet pipes (4) and the two water outlet pipes (5), and a liquid pressure sensor (7) is installed on the wall of the conduit (6).

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