Gas-liquid coplanar refrigerant direct cooling plate

Abstract

The utility model discloses a gas-liquid coplanar refrigerant direct cooling plate. The gas-liquid coplanar refrigerant direct cooling plate specifically comprises a main body structure formed by overlapping and welding an upper aluminum alloy shell plate and a lower aluminum alloy shell plate. A plurality of parallel linear grooves are machined in the inner surface of the upper shell plate, and the upper shell plate is combined with the plane of the lower shell plate to form a multi-channel flow channel structure composed of a plurality of independent heat exchange flow channels. The bottom surface or the top surface of the inner surface of the heat exchange runner is a heat exchange surface; a liquid absorption core layer is compounded on at least the heat exchange surface of the flow channel, and the liquid absorption core layer realizes capillary liquid absorption and liquid storage functions by using a material with capillary liquid absorption and storage functions. The refrigerant direct cooling plate can effectively improve the liquid absorption efficiency and the heat exchange performance of the refrigerant, meanwhile, the flow resistance is reduced, and the stability of the whole system is improved.

Description

TECHNICAL FIELD

[0001] The present application relates to a gas-liquid coplanar refrigerant direct cooling plate, especially suitable for heat dissipation systems in electric vehicles and other high-power energy storage and power battery fields. Specifically, the present application proposes a new type of refrigerant heat exchange plate based on gas-liquid two-phase heat exchange technology, aiming to solve the problem of insufficient heat dissipation efficiency under high heat load in high-power battery systems, especially the adverse effects of gas lock phenomenon on heat exchange efficiency. BACKGROUND

[0002] With the continuous development of new energy technology, electric vehicles have gradually become the market mainstream with their low energy consumption and intelligent operation. Especially in the process of fast charging and discharging of battery systems, the problem of heat redundancy generated by the battery is increasingly prominent. Therefore, an efficient heat dissipation system in electric vehicles and energy storage systems is particularly important. The existing water cooling plate, as the mainstream cooling method, is widely used in battery heat dissipation systems. The water cooling plate uses water or other liquid media to remove heat through convective heat transfer, effectively controlling the working temperature of the battery. However, with the continuous development of battery capacity and fast charging technology, especially in high-load working environments, the heat dissipation effect of traditional water cooling plates gradually tends to saturation, which cannot meet the increasing demand for heat dissipation.

[0003] To solve this problem, liquid cooling plate technology has been widely applied in energy storage and power battery fields. Liquid cooling plates remove heat and effectively control temperature through the circulation of liquid heat exchange medium in the battery module. However, with the progress of battery technology, especially the high requirements of high-power battery systems on thermal management, the heat exchange efficiency of traditional liquid cooling plates gradually reveals its shortcomings. In the application scenario of high-power batteries, liquid cooling plates often have difficulty in maintaining the battery temperature within a safe range due to their limited heat transfer capacity, which not only affects the battery performance and service life, but also may cause safety hazards.

[0004] In order to improve the heat dissipation efficiency, gas-liquid two-phase heat exchange technology has gradually attracted attention. This technology absorbs a large amount of heat through the phase change of refrigerant between liquid and gas, thereby achieving efficient heat exchange. The phase change process of refrigerant can greatly improve the heat exchange efficiency, especially in high-power application scenarios, showing more superior heat dissipation performance. However, gas-liquid two-phase heat exchange technology also faces many challenges in practical application, especially the gas lock phenomenon. In the heat exchange process, the gasification of refrigerant may generate gas lock in the channel, which not only hinders the flow of refrigerant, but also seriously affects the heat exchange efficiency. The existence of gas lock phenomenon makes the existing liquid cooling plate unable to effectively dissipate heat when facing high-power batteries, further exacerbating the instability of battery temperature control, which may cause thermal runaway and other safety risks.

[0005] Therefore, developing a new type of refrigerant heat exchange plate to solve the gas jam phenomenon and improve the heat exchange efficiency has become an urgent task in the current technical field. This not only helps to improve the heat dissipation performance of high-power batteries, but also prolongs the service life of the battery while ensuring its safety. Content of the utility model

[0006] The purpose of the present application is to at least overcome the deficiencies of the prior art, and to provide a gas-liquid coplanar refrigerant direct cooling plate that can effectively improve the liquid absorption efficiency and heat exchange performance of the refrigerant, reduce flow resistance, and improve the stability of the overall system.

[0007] To achieve the above-mentioned purpose, in a first aspect, the present application discloses a gas-liquid coplanar refrigerant direct cooling plate, specifically comprising a main body structure formed by overlapping and welding an upper shell plate and a lower shell plate made of aluminum alloy.

[0008] Among them, the inner surface of the upper shell plate is processed with several parallel straight grooves, and the lower shell plate plane is combined to form a multi-channel flow channel structure composed of several independent heat exchange flow channels; the inner surface of the heat exchange flow channel, the bottom surface or the top surface is the heat exchange surface;

[0009] The flow channel is compounded with a liquid absorption core layer on at least the heat exchange surface, and the liquid absorption core layer uses a material with capillary liquid absorption and storage function to realize the capillary liquid absorption and storage function.

[0010] Further, the thickness of the liquid absorption core layer should be controlled within 1 / 3 of the total height of the flow channel to ensure that the refrigerant can flow uniformly in the flow channel and fully utilize the capillary liquid absorption function of the liquid absorption core, while avoiding excessive resistance to refrigerant flow.

[0011] Further, the width of the liquid absorption core layer is designed to cover at least 1 / 2 of the heat exchange surface in the flow channel to ensure that the refrigerant can be uniformly absorbed by the liquid absorption core and maintain the stability of the flow in the flow channel.

[0012] For some applications, the width of the liquid absorption core can be designed to cover the entire heat exchange surface to further improve the heat exchange efficiency.

[0013] Further, as an optional technical solution, the liquid absorption core layer is a composite structure with multi-stage micro-porous structure of directional capillary effect; the porosity of the liquid absorption core layer changes along the height direction of the flow channel to meet the liquid absorption requirements under different fluid states; the composite structure of the liquid absorption core layer includes three layers. The first layer is a heat-conducting combination layer directly combined with the flow channel base, which is formed by sintering aluminum-copper alloy powder with a particle size of 50-80 μm, and the porosity is 40%-50%. The second layer is a capillary transport layer, which is formed by sintering pure aluminum powder with a particle size of 20-40 μm, and the porosity is increased to 60%-70%. The third layer is a surface functional layer, which is formed by a laser micro-cladding process to form a reticular pore structure with a pore size of 5-15 μm, further enhancing the liquid absorption performance.

[0014] Further, as an optional technical solution, the liquid absorption core layer is an aluminum oxide layer with a thickness of 20 μm to 50 μm, and a micro-groove network with a depth of 2 μm to 5 μm and a width of 10 μm to 20 μm is formed on the surface of the aluminum oxide layer by femtosecond laser processing. The grooves are distributed at an angle of 45° to 60° with respect to the flow channel axis, and nano-silver particles are deposited in the grooves to enhance the capillary wetting performance.

[0015] In some embodiments, as an optional technical solution, the liquid absorption core is a sponge body structure made of high-porosity porous material, with a porosity generally controlled between 50%-80% and a pore size varying between 50 μm to 300 μm to ensure good capillary liquid absorption capacity. The thickness of the sponge body structure is controlled between 20 μm to 100 μm, and the specific thickness design depends on the flow rate of the refrigerant and the required liquid absorption capacity. By optimizing the pore structure, the sponge body structure provides an efficient liquid absorption and transport channel, enabling uniform distribution of the refrigerant in the flow channel and avoiding local overheating or overcooling, thereby improving the cooling efficiency.

[0016] Further, the cross section of the flow channel is in a trapezoidal structure, the bottom surface of the flow channel is a heat exchange surface, the width of the bottom surface is 6 mm to 12 mm, the included angle between the two side slopes and the bottom surface is 75°±2°, and the two side slopes are processed with an array of staggered hemispherical micro-dimple arrays; the diameter of the micro-dimple is 0.3 mm to 0.8 mm, the depth is 0.1 mm to 0.3 mm, the center distance between adjacent dimples is 1.2 mm to 2.5 mm, and the surface of the dimples is chemically polished to form a smooth transition curved surface with Ra≤0.8 μm.

[0017] Further, the two side slopes of the groove are provided with concave positions for disturbance, which causes disturbance of the refrigerant in the heat exchange flow channel, thereby improving the contact efficiency of the refrigerant and the liquid absorption core layer.

[0018] Further, the other side of the flow channel opposite to the heat exchange surface is provided with triangular flow guide fins with a height of 0.5mm to 1.2mm at intervals of 8mm to 15mm, the fin inclination angle is 25° to 35° with the flow direction, and the fin top angle is provided with a rounded corner structure with a corner radius of 0.2mm to 0.5mm.

[0019] Further, the upper shell plate is stamped and formed by a multi-stage progressive die structure, including a pre-forming die, a precision pressing die, and a shaping die three-station processing flow; the stamping pressure of the pre-forming die is controlled at 80MPa to 120MPa, the pressure of the precision pressing die is increased to 150MPa to 200MPa, and a local annealing treatment of 300°C to 400°C is applied in the shaping die stage to eliminate residual stress; the groove edge is also provided with a process compensation area with a width of 0.3mm to 0.6mm, which forms a molten penetration zone with a width of 0.1mm to 0.3mm during the heating process, realizing secondary reinforcement of the flow channel sealing.

[0020] Further, the planar structure of the lower shell plate is provided with a thickness compensation area, and a boss structure with a height of 0.05mm to 0.15mm is arranged at the outer edge of the flow channel projection area. The boss surface is processed with a stress release groove with a depth of 0.02mm to 0.05mm, a groove width of 0.1mm to 0.3mm, and a spacing of 2mm to 5mm, and a zigzag wave shape is adopted to balance the thermal deformation during the welding process.

[0021] Further, the outlet end of the heat exchange flow channel is provided with a tapered flow guide structure with a contraction angle of 8° to 12°, and the outlet cross-sectional area is reduced by 15% to 25% compared with the main body of the flow channel, so as to maintain a stable gas-liquid interface.

[0022] In a second aspect, the application discloses a preparation method of a gas-liquid coplanar refrigerant direct cooling plate, including the following steps:

[0023] Step 1: process the aluminum alloy plate into an upper shell plate and a lower shell plate; process the lower shell plate into a planar structure, and provide a boss structure at the outer edge, and process a stress release groove on the boss surface to relieve thermal deformation during the welding process.

[0024] Step 2: form a plurality of parallel straight grooves on the inner surface of the upper shell plate by multi-stage progressive die stamping. Then process a micro-pit array in the preset area of the lower shell plate matched with the straight grooves, the micro-pit is formed by precise machining or die stamping, the diameter and depth of the micro-pit are controlled according to design requirements, and the surface of the pit is chemically polished to ensure smooth surface and smooth fluid flow; finally, install the flow guide fin in the preset area;

[0025] Step 3: fix and install the liquid absorption core layer at the bottom of the straight groove to ensure firm fixation.

[0026] Step 4: Butt the upper shell plate with the lower shell plate and fix them by welding to form the main structure. During welding, ensure that each area of the flow channel is well sealed.

[0027] Step 1: Perform final inspection and testing on the prepared gas-liquid co-planar refrigerant direct cooling plate to check its size and sealing, ensuring that there is no liquid leakage.

[0028] In summary, the gas-liquid co-planar refrigerant direct cooling plate design has high flexibility, allowing selection of appropriate wick materials and structures according to different working environments and application requirements, and adjusting the thickness and width of the wick as needed. Through these optimized designs, not only the stability of refrigerant flow and heat exchange efficiency are improved, but also the scope of patent protection is expanded, ensuring coverage and protection of multiple technical implementation methods.

[0029] The above-listed benefits are not exhaustive of all advantages. Other potential benefits and detailed technical implementations will be further disclosed in the examples or other description sections of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0030] The specific embodiments will be better understood after reading the following detailed description in conjunction with the accompanying drawings, in which the positions, sizes, and ranges of structures shown in the drawings are sometimes not representative of actual positions, sizes, and ranges. In the drawings:

[0031] Figure 1 is a structural schematic diagram of an embodiment of the present disclosure.

[0032] Figure 2 is a planar structural schematic diagram of an upper shell plate in an embodiment of the present disclosure. DETAILED DESCRIPTION

[0033] The present disclosure will be described below with reference to the accompanying drawings, which show several embodiments of the present disclosure. It should be understood that the present disclosure can be presented in many different ways and is not limited to the embodiments described below; in fact, the embodiments described below are intended to make the disclosure of the present disclosure more complete and fully inform those skilled in the art of the scope of protection of the present disclosure. It should also be understood that the embodiments disclosed herein can be combined in various ways to provide more additional embodiments.

[0034] It should be understood that in all the drawings, the same reference numerals represent the same elements. In the drawings, the sizes of some features can be distorted for the sake of clarity.

[0035] It is to be understood that the language used in the specification has been principally selected for readability and instructional purposes and can not have been selected to delineate or circumscribe the patent rights of the disclosure. That said, all preferences and embodiments discussed in the specification are intended to be combinable... unless otherwise indicated.

[0036] As used in the description of the disclosure and the appended claims, the singular forms "a", "an" and "the" include plural referents unless the context clearly dictates otherwise. As used in the description of the disclosure and the appended claims, the language "including" and / or "comprising" encompasses the terms "consisting essentially of" and / or "consisting of".

[0037] Embodiment:

[0038] The present embodiment relates to the design and manufacture of a gas-liquid coplanar refrigerant direct cooling plate, which includes detailed descriptions of the structural design of the shell plate assembly, the selection and manufacturing process of the wick layer, the optimization of the flow channel system, production process control, and performance verification.

[0039] Referring to the drawings Figure 1 And 2 The main structure of the gas-liquid coplanar refrigerant direct cooling plate is composed of an upper shell plate 1 and a lower shell plate 2, and 6061-T6 aluminum alloy and 5052-H32 aluminum alloy are used as the main materials.

[0040] The inner surface of the upper shell plate 1 is processed with 12 parallel straight grooves 3.

[0041] The straight grooves 3 are designed with an inverted trapezoidal cross-section, with a surface roughness Ra≤0.8μm, and are formed by drawing. These straight grooves 3, in combination with the plane of the lower shell plate 2, form a plurality of independent heat exchange channels 4, with a heat exchange surface provided on the inner surface and a wick layer 5 compounded on the heat exchange surface. The flatness tolerance of the lower shell plate 2 is ≤0.05mm / m 2 The laser deep penetration welding process is used to connect the upper shell plate 1 and the lower shell plate 2, with a weld penetration depth of 1.8-2.2mm, a welding speed of 1.2m / min, and a protective gas of argon with a purity of 99.999%, ensuring the quality and stability of the welding process.

[0042] The cross-section of the straight grooves 3 is trapezoidal, with a bottom width ranging from 6mm to 12mm, and the included angle between the two side slopes of the straight grooves 3 and the bottom is 75°±2°. This design not only optimizes the flow path of the fluid and reduces the flow resistance, but also effectively increases the contact area between the refrigerant and the heat exchange surface, thereby improving the heat exchange efficiency.

[0043] In addition, the two side inclined surfaces inside the straight groove 3 are processed with an array of staggered hemispherical micro-pits, with a diameter of 0.3mm to 0.8mm, a depth of 0.1mm to 0.3mm, and a center distance of 1.2mm to 2.5mm between adjacent pits. The micro-pit surface is chemically polished to ensure a smooth transition surface with Ra≤0.8μm, reducing flow resistance and further improving heat exchange efficiency by increasing surface roughness. These micro-pits not only enhance the stability of the refrigerant flow, but also effectively increase the heat exchange area between the refrigerant and the heat exchange surface, thereby improving the heat exchange efficiency.

[0044] The above design further ensures the superior performance of the refrigerant direct cooling plate in terms of efficient heat exchange and stable refrigerant flow, while considering the production process and structural stability to ensure its reliability and efficiency under various working conditions.

[0045] It should be noted that the refrigerant direct cooling plate of the present embodiment needs to consider the thermal deformation and stability of the gas-liquid interface during welding. The flat structure of the lower shell plate 2 is designed with a thickness compensation area (not shown in the figure), and a 0.05mm to 0.15mm thick boss structure is provided at the outer edge of the flow channel projection area.

[0046] The boss surface is processed with stress release grooves with a depth of 0.02mm to 0.05mm, a width of 0.1mm to 0.3mm, a pitch of 2mm to 5mm, and a zigzag wave shape. The main purpose of this design is to balance the stress caused by thermal deformation during welding, prevent the deformation of the flow channel structure, ensure the accuracy of the flow channel shape and size, and thus ensure the uniform flow of the refrigerant in the flow channel and the stable heat exchange performance.

[0047] In addition, the outlet end of the flow channel is provided with a tapered flow guide structure with a contraction angle of 8° to 12°, so that the area of the outlet cross section of the flow channel is reduced by 15% to 25% compared with the main body of the flow channel. The design of this tapered flow guide structure aims to maintain the stability of the gas-liquid interface by reducing the outlet cross section, reduce the possibility of bubble generation, and ensure that the refrigerant can flow out of the flow channel stably, thereby improving the overall heat exchange efficiency and fluid stability.

[0048] To further improve the sealing of the flow channel, a double-seal design (the corresponding structure is not shown in the figure) can also be used. The first seal uses a fluororubber seal strip with a thickness of 0.3mm and a hardness of Shore A 70±5, and the second seal uses a continuous metallurgical bonding layer formed by laser welding technology. This double-seal design effectively avoids refrigerant leakage and ensures the stability of the structure.

[0049] The liquid absorbing core layer 5 is partially provided with three design schemes of the liquid absorbing core layer 5 according to actual requirements, which are respectively a composite structure of the liquid absorbing core layer 5, an aluminum oxide layer of the liquid absorbing core layer 5 and a sponge structure of the liquid absorbing core layer 5, each of which has different advantages and can meet the requirements of heat exchange efficiency and liquid absorbing capacity under different working conditions.

[0050] Specifically, the liquid absorbing core layer 5 with the composite structure is composed of three layers of different materials: a heat-conducting bonding layer, a capillary transmission layer and a surface functional layer. The heat-conducting bonding layer adopts a vacuum hot-pressing sintering process, uses aluminum-copper alloy powder (Al-3wt%Cu) with a particle size of 65 μm, the sintering temperature is 580℃±10℃, the pressure is 15 MPa, and the holding time is 30 minutes, which ensures the efficiency of heat conduction. The capillary transmission layer is made of pure aluminum powder prepared by plasma rotating electrode atomization, with a sphericity of ≥95%, a porosity of 65±3% after sintering and a permeability of 1.2×10 -12 m 2 , which can effectively transport the liquid in the refrigerant. The surface functional layer is micro-fused by a 532 nm wavelength laser, with a laser power of 80 W, a scanning speed of 200 mm / s and an overlap rate of 40%, forming a gradient pore structure with a pore diameter of 8 μm, which enhances the capillary liquid absorbing performance of the core layer.

[0051] The liquid absorbing core layer 5 with the aluminum oxide layer adopts an anodic aluminum oxide (AAO template) with a pore diameter of 80 nm and a pore depth of 50 μm. By femtosecond laser processing (wavelength 1030 nm, pulse width 350 fs), an interlaced micro-groove is formed, with a groove width of 50 μm, a groove depth of 80 μm and a pitch of 150 μm. These micro-groove structures can improve the liquid absorbing efficiency and enhance the capillary action. Nano-silver deposition adopts a magnetron sputtering process, with a target purity of 99.99%, a sputtering power of 300 W and a sputtering rate of 0.8 nm / s. The thickness of the silver layer is 120 nm, and the contact angle is reduced from 125° to 32°, which greatly improves the wettability of the material.

[0052] The liquid absorbing core layer 5 with the sponge structure is made of polyurethane and graphene composite foam material (porosity 72±5%), with an addition amount of graphene of 1.5wt%. The pore size distribution of the sponge is a bimodal structure, with a main peak pore size of 150 μm, accounting for 65%, and a secondary peak pore size of 50 μm, accounting for 35%. Through a hot-pressing forming process, the temperature is 180℃±5℃, the pressure is 8 MPa, and the holding time is 15 minutes. After demolding, plasma surface treatment (power 500 W, treatment time 5 minutes) is performed to improve the wettability, further improving the capillary liquid absorbing performance of the core layer.

[0053] As a preferred embodiment, the surface of the two side slopes of the heat exchange flow channel 4 is processed with a turbulence concave position 6 with a depth of 0.55 mm, which effectively enhances the contact efficiency of the refrigerant and the liquid absorbing core layer.

[0054] In addition to the above structure, triangular flow guide fins 7 are arranged on the other side of the heat exchange channel 4 opposite the heat exchange surface. The height of the triangular flow guide fins 7 is 1.5 mm, the inclination angle is 30°, the root roundness is R0.3 mm, and the fin spacing density is 6 groups per centimeter. The triangular flow guide fins 7 can effectively guide the flow of refrigerant and improve the heat exchange efficiency.

[0055] In terms of production process, five-station progressive die stamping is adopted for forming, which specifically includes blanking, pre-bending, fine punching flow channel, surface texture processing, and edge cutting processes. The die gap is controlled at 8% of the material thickness, the stamping speed is 30 times / min, and water-based high polymer lubricant is used as the release agent (concentration 8%). During welding, X-ray real-time imaging detection is used with a tube voltage of 160 kV and a current of 5 mA, combined with helium mass spectrometry leak detection with a sensitivity of 1x10 -9 Pa·m 3 / s to ensure the welding quality. The flow channel pressure resistance test uses 3.5 MPa nitrogen pressure for 30 minutes, and the pressure drop should not exceed 0.02 MPa.

[0056] The performance verification results of the embodiment show that under the working condition of a refrigerant flow rate of 2 L / min (R134a, evaporation temperature 25℃), the heat exchange coefficient reaches 5800 W / (m 2 ·K), which is 42% higher than that of the traditional structure. The Washburn method is used to measure the capillary rise speed of the composite structure wick layer, which is 8.2 mm / s, and the effective capillary height is 62 mm. In terms of flow stability, the test results show that the flow fluctuation coefficient is ≤3.5%, and the pressure drop gradient is 0.15 MPa / m, which meets the use requirements.

[0057] Through these detailed designs and manufacturing processes, the application not only achieves the expected target in terms of performance, but also provides a variety of optional wick layer structures for various application scenarios to meet the needs of different cooling systems. The above embodiments provide sufficient details to ensure that those skilled in the art can implement the application based on the provided information without relying on creative labor.

[0058] Although exemplary embodiments of the present disclosure have been described, it will be understood by those skilled in the art that various changes and modifications can be made to the exemplary embodiments of the present disclosure without departing from the spirit and scope of the present disclosure in essence. Therefore, all changes and modifications are included in the protection scope of the present disclosure defined by the claims. The present disclosure is defined by the additional claims, and the equivalents of these claims are also included.

Claims

1. A gas-liquid coplanar coolant direct cooling plate, specifically comprising a main structure formed by the superimposed welding of an upper shell plate and a lower shell plate made of aluminum alloy, characterized in that: the inner surface of the upper shell plate is processed with a plurality of parallel straight grooves, which, in combination with the plane of the lower shell plate, form a multi-channel flow channel structure composed of a plurality of independent heat exchange flow channels; the inner surface of the heat exchange flow channel is a heat exchange surface on the bottom surface or the top surface; the flow channel is compounded with a wick layer on at least the heat exchange surface, and the wick layer utilizes a material with capillary liquid absorption and storage functions to realize capillary liquid absorption and storage functions; the thickness of the wick layer should be controlled within 1 / 3 of the total height of the flow channel; the width of the wick layer is designed to cover at least 1 / 2 of the heat exchange surface in the flow channel; the cross section of the flow channel is in a trapezoidal structure, the bottom surface of the flow channel is a heat exchange surface, the width of the bottom surface is 6mm to 12mm, the included angle between the two side slopes and the bottom surface in the flow channel is 75°±2°, and the two side slopes are processed with an array of staggered hemispherical micro-pits; the diameter of the micro-pits is 0.3mm to 0.8mm, the depth is 0.1mm to 0.3mm, the center distance between adjacent pits is 1.2mm to 2.5mm, the pit surface is chemically polished to form a smooth transition curved surface with Ra≤0.8μm; the two side slopes of the groove are provided with recesses for disturbance, and the refrigerant is disturbed in the heat exchange flow channel through the recesses; the other surface of the flow channel opposite to the heat exchange surface is provided with triangular flow guide fins with a height of 0.5mm to 1.2mm at intervals of 8mm to 15mm, the inclination angle of the fins and the flow direction forms an included angle of 25° to 35°, the top corner of the fin is provided with a rounded corner structure, and the radius of the rounded corner is 0.2mm to 0.5mm; the outlet end of the heat exchange flow channel is provided with a tapered flow guide structure, the contraction angle is 8° to 12°, the outlet cross-sectional area is reduced by 15% to 25% compared with the main body of the flow channel, so as to maintain a stable gas-liquid interface. wherein The wick layer is a composite structure with a multi-stage micropore structure with directional capillary effect; the porosity of the wick layer changes in a gradient along the height direction of the flow channel to meet the liquid absorption requirements under different fluid states; the composite structure of the wick layer includes three layers; the first layer is a heat-conducting combined layer directly combined with the flow channel base, which is formed by sintering aluminum-copper alloy powder with a particle size of 50-80μm, and the porosity is 40%-50%; the second layer is a capillary transport layer formed by sintering pure aluminum powder with a particle size of 20-40μm, and the porosity is increased to 60%-70%; the third layer is a surface functional layer, which forms a reticular pore structure with a pore size of 5-15μm through laser micro-cladding process, further enhancing its liquid absorption performance. The wick layer is an aluminum oxide layer with a thickness of 20μm to 50μm, and a micro-groove network with a depth of 2μm to 5μm and a width of 10μm to 20μm is formed on the surface of the aluminum oxide layer by femtosecond laser processing, and the grooves are distributed at an angle of 45° to 60° with the flow channel axis, and nano-silver particles are deposited in the grooves to enhance the capillary wetting performance. ​ ​ ​ ​ ​ ​ 2. The gas-liquid co-planar coolant direct cooling plate of claim 1, characterized in that: ​ 3. The gas-liquid co-planar coolant direct cooling plate of claim 1, characterized in that: ​ 4. The gas-liquid co-planar coolant direct cooling plate of claim 1, characterized in that: The liquid absorbing core is a sponge structure made of high porosity porous material, the porosity is generally controlled between 50% and 80%, the pore size varies between 50μm and 300μm to ensure good liquid absorbing capacity; the thickness of the sponge structure is controlled between 20μm and 100μm, the specific thickness design depends on the flow rate of the refrigerant and the required liquid absorbing capacity.

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