Gas-liquid coplanar refrigerant direct cooling plate and preparation method

Abstract

The invention discloses a gas-liquid coplanar refrigerant direct cooling plate and a preparation method. The gas-liquid coplanar refrigerant direct cooling plate specifically comprises a main body structure formed by overlapping and welding an aluminum alloy upper shell plate and a lower 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 and a preparation method thereof, which is particularly 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, which aims to solve the problem of insufficient heat dissipation efficiency under high heat load in high-power battery systems, especially the adverse effects of gas plugging on heat exchange efficiency. Background Art

[0002] With the continuous development of new energy technologies, electric vehicles have gradually become the mainstream of the market with their low energy consumption and intelligent operation. Especially in the rapid charging and discharging process of the battery system, the problem of heat redundancy generated by the battery has become increasingly prominent. Therefore, an efficient heat dissipation system in electric vehicles and energy storage systems is particularly important. As a mainstream cooling method, the existing water-cooled plate is widely used in battery cooling systems. The water-cooled plate uses water or other liquid media to remove heat by convection heat transfer, which effectively controls the operating 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-cooled plates has gradually become saturated and cannot meet the increasing heat dissipation needs.

[0003] To address this problem, liquid cooling plate technology has been widely used in the fields of energy storage and power batteries. Liquid cooling plates remove heat and effectively control temperature by circulating liquid heat exchange media in battery modules. However, with the advancement of battery technology, especially the high requirements for thermal management in high-power battery systems, the heat exchange efficiency of traditional liquid cooling plates has gradually exposed its shortcomings. In the application scenarios of high-power batteries, liquid cooling plates often have difficulty keeping the battery temperature within a safe range due to their limited heat transfer capabilities. This not only affects battery performance and service life, but may also pose safety risks.

[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 the refrigerant between liquid and gas, thereby achieving efficient heat exchange. The phase change process of the 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 applications, especially the gas plug phenomenon. During the heat exchange process, the gasification of the refrigerant may generate gas plugs in the channel, which not only hinders the flow of the refrigerant, but also seriously affects the heat exchange efficiency. The existence of the gas plug phenomenon makes it impossible for the existing liquid cooling plate to effectively dissipate heat when facing high-power batteries, further aggravating the instability of battery temperature control, and may cause safety risks such as thermal runaway.

[0005] Therefore, developing a new type of refrigerant heat exchange plate to solve the gas plug phenomenon and improve the heat exchange efficiency has become an urgent task in the current technical field. This will not only help improve the heat dissipation performance of high-power batteries, but also ensure the safety of the battery while extending its service life. Summary of the invention

[0006] The purpose of the present application is to overcome at least one of the shortcomings of the prior art and to provide a gas-liquid coplanar refrigerant direct cooling plate, which can effectively improve the refrigerant's liquid absorption efficiency and heat exchange performance, while reducing flow resistance and improving the stability of the overall system.

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

[0008] Among them, the inner surface of the upper shell plate is processed with a plurality of parallel linear grooves, which are 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; in 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 absorbing core layer on at least the heat exchange surface, and the liquid absorbing core layer uses a material with capillary liquid absorbing and liquid storing functions to realize capillary liquid absorbing and liquid storing functions.

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

[0011] Furthermore, the width of the liquid absorbent 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 adsorbed by the liquid absorbent core in the flow channel and maintain flow stability.

[0012] For some applications, the width of the wick can be designed to cover the entire heat transfer surface, further improving the heat transfer efficiency.

[0013] Furthermore, as an optional technical solution, the absorbent core layer is a composite structure with a multi-level microporous structure with a directional capillary effect; the porosity of the absorbent core changes gradually along the height direction of the flow channel to meet the absorption requirements under different fluid states; the composite structure of the absorbent core layer includes three layers. The first layer is a thermally conductive bonding layer directly bonded to the flow channel matrix, which is formed by sintering aluminum-copper alloy powder with a particle size of 50-80μm and a porosity of 40%-50%. The second layer is a capillary transmission layer, which is 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 is formed by a laser micro-cladding process to form a mesh pore structure with a pore size of 5-15μm, further enhancing its absorption performance.

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

[0015] In some embodiments, as an optional technical solution, the absorbent core is a sponge structure made of a porous material with high porosity. The porosity is generally controlled between 50% and 80%, and the pore size varies between 50 μm and 300 μm to ensure good capillary absorption capacity. The thickness of the sponge structure is controlled between 20 μm and 100 μm, and the specific thickness design depends on the flow rate of the refrigerant and the required absorption capacity. The sponge structure provides an efficient liquid adsorption and transmission channel by optimizing the pore structure, so that the refrigerant can be evenly distributed in the flow channel, avoiding local overheating or overcooling, and improving the cooling efficiency.

[0016] Furthermore, the cross-section of the flow channel is a trapezoidal structure, and the bottom surface of the flow channel is a heat exchange surface. The width of the bottom surface is 6mm to 12mm, and the angle between the inclined surfaces on both sides of the flow channel and the bottom surface is 75°±2°. The surfaces of the inclined surfaces on both sides 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, and the surface of the pits is chemically polished to form a smooth transition surface with Ra≤0.8μm.

[0017] Furthermore, the inclined surfaces on both sides of the groove are provided with concave positions for flow disturbance, and the refrigerant is disturbed in the heat exchange flow channel through the concave positions, thereby improving the contact efficiency between the refrigerant and the liquid absorbent core layer.

[0018] Furthermore, on the other side of the flow channel opposite to the heat exchange surface, triangular guide fins with a height of 0.5mm to 1.2mm are arranged at intervals of 8mm to 15mm, the inclination angle of the fins is 25° to 35° with the flow direction, and the top corners of the fins are provided with a chamfered structure with a fillet radius of 0.2mm to 0.5mm.

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

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

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

[0022] In a second aspect, the present application discloses a method for preparing a gas-liquid coplanar refrigerant direct cooling plate, comprising 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 plane structure, and provide a boss structure on the outer edge, and process a stress relief groove on the surface of the boss to alleviate thermal deformation during welding.

[0024] Step 2: A number of parallel linear grooves are formed on the inner surface of the upper shell plate by multi-stage progressive die stamping. Then, a micro-pit array is processed in a preset area of ​​the lower shell plate that matches the linear grooves. The micro-pits are formed by precision machining or die stamping. The diameter and depth of the micro-pits are controlled according to the design requirements, and the surface of the pits is chemically polished to ensure that the surface is smooth and the fluid flows smoothly. Finally, the guide fins are fixed in the preset area;

[0025] Step 3: Install the absorbent core layer on the bottom of the linear groove to ensure that it is firmly fixed.

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

[0027] Step 1: Final inspection and testing: Inspect the size and sealing of the prepared gas-liquid coplanar refrigerant direct cooling plate to ensure there is no leakage.

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

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

[0030] After reading the following detailed description in conjunction with the accompanying drawings, you will better understand the various aspects of the present disclosure. The positions, sizes, and ranges of various structures shown in the accompanying drawings sometimes do not represent the actual positions, sizes, and ranges. In the accompanying drawings:

[0031] Figure 1 It is a structural schematic diagram of an embodiment disclosed in this application.

[0032] Figure 2 It is a schematic diagram of the planar structure of an upper shell plate in an embodiment disclosed in the present application. DETAILED DESCRIPTION

[0033] The present disclosure will be described below with reference to the accompanying drawings, wherein the accompanying drawings illustrate several embodiments of the present disclosure. However, it should be understood that the present disclosure can be presented in a variety of 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 illustrate the scope of protection of the present disclosure to those skilled in the art. 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 the same reference numerals represent the same elements throughout the drawings. In the drawings, the dimensions of certain features may be distorted for clarity.

[0035] It should be understood that the terms used in the specification are only used to describe specific embodiments and are not intended to limit the present disclosure. All terms (including technical terms and scientific terms) used in the specification have the meanings commonly understood by those skilled in the art unless otherwise defined. For the sake of brevity and / or clarity, the techniques, methods and equipment known to ordinary technicians in the relevant fields may not be discussed in detail, but where appropriate, the techniques, methods and equipment should be considered as part of the authorization specification.

[0036] The singular forms "a", "said" and "the" used in the specification include plural forms unless clearly indicated. The terms "include", "comprise" and "contain" used in the specification indicate the presence of the claimed features, but do not exclude the presence of one or more other features. The term "and / or" used in the specification includes any and all combinations of one or more of the relevant listed items.

[0037] Example:

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

[0039] See attached Figure 1 and 2 The main structure of the gas-liquid coplanar refrigerant direct cooling plate consists of an upper shell plate 1 and a lower shell plate 2, and uses 6061-T6 aluminum alloy and 5052-H32 aluminum alloy as the main materials.

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

[0041] The linear grooves 3 are designed with an inverted trapezoidal cross section, with a surface roughness of Ra ≤ 0.8 μm, and are formed by drawing. After these linear grooves 3 are combined with the plane of the lower shell plate 2, multiple independent heat exchange channels 4 are formed, and a heat exchange surface is set on the inner surface, and a liquid absorbing core layer 5 is compounded on the heat exchange surface. The flatness tolerance of the lower shell plate 2 is ≤ 0.05 mm / m 2 , it is connected to the upper shell plate 1 by laser deep melting welding process, the weld penetration is 1.8-2.2mm, the welding speed is 1.2m / min, and the shielding gas is argon with a purity of 99.999%, which ensures the quality and stability of the welding process.

[0042] The cross section of the linear groove 3 is a trapezoidal structure, the bottom width ranges from 6mm to 12mm, and the angle between the two side slopes of the linear groove 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 inclined surfaces on both sides of the linear groove 3 are processed with staggered hemispherical micro-pit arrays, the diameter of these micro-pits is 0.3mm to 0.8mm, the depth is 0.1mm to 0.3mm, and the center distance between adjacent pits is 1.2mm to 2.5mm. The surface of the micro-pits is chemically polished to ensure that the surface forms a smooth transition surface with Ra≤0.8μm to reduce flow resistance and further improve the heat exchange effect by enhancing the 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 this refrigerant direct cooling plate in terms of efficient heat exchange and refrigerant flow stability. At the same time, taking into account the production process and structural stability, it ensures its reliability and efficiency under various working conditions.

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

[0046] The surface of the boss is processed with stress relief grooves with a depth of 0.02mm to 0.05mm. The width of these grooves is 0.1mm to 0.3mm, the spacing is 2mm to 5mm, and they have a zigzag wavy shape. The main purpose of this design is to balance the stress caused by thermal deformation during the welding process, prevent the flow channel structure from deforming, and ensure the accuracy of the flow channel shape and size, thereby ensuring the uniform flow of the refrigerant in the flow channel and stable heat exchange performance.

[0047] In addition, the outlet end of the flow channel is provided with a tapered guide structure, and the contraction angle is designed to be 8° to 12°, so that the area of ​​the flow channel outlet cross section is reduced by 15% to 25% compared with the flow channel body. The design of this tapered guide structure is 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] In order to further improve the sealing performance of the flow channel, a double-channel sealing design can be used in the specific structure (the corresponding structure is not shown in the figure). The first seal uses a fluororubber sealing 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-channel sealing design effectively avoids refrigerant leakage and ensures the stability of the structure.

[0049] As for the absorbent core layer 5, according to actual needs, this embodiment provides three design schemes for the absorbent core layer 5, namely, a composite structure absorbent core layer 5, an alumina layer absorbent core layer 5 and a sponge structure absorbent core layer 5. Each scheme has different advantages and can meet the requirements of heat exchange efficiency and liquid adsorption capacity under different working conditions.

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

[0051] The liquid absorption core layer 5 of the alumina layer adopts anodized aluminum (AAO template) with a pore size of 80nm and a pore depth of 50μm. Through femtosecond laser processing (wavelength 1030nm, pulse width 350fs), staggered micro grooves are formed with a groove width of 50μm, a groove depth of 80μm, and a spacing of 150μm. These micro groove structures can improve the liquid absorption efficiency and enhance the capillary action. Nano silver deposition adopts magnetron sputtering technology, with a target purity of 99.99%, a sputtering power of 300W, a sputtering rate of 0.8nm / s, a silver layer thickness of 120nm, and a contact angle reduced from the original 125° to 32°, which greatly improves the wettability of the material.

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

[0053] Preferably, the surfaces of the inclined surfaces on both sides of the heat exchange channel 4 are processed with flow disturbance recesses 6 with a depth of 0.55 mm, which effectively enhances the contact efficiency between the refrigerant and the liquid absorbent core layer.

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

[0055] In terms of production process, a five-station progressive die is used for stamping, including blanking, pre-bending, fine stamping of runners, surface texture processing and trimming. The mold gap is controlled at 8% of the material thickness, the stamping speed is 30 times / min, and a water-based polymer lubricant is used as a release agent (concentration 8%). During welding, an X-ray real-time imaging detection tube voltage of 160kV and a current of 5mA are used, and a helium mass spectrometer leak detection with a sensitivity of 1×10 -9 Pa·m 3 / s to ensure welding quality. The flow channel pressure test uses 3.5MPa nitrogen to maintain pressure for 30 minutes, and the pressure drop shall not exceed 0.02MPa.

[0056] The performance verification results of this embodiment show that the heat transfer coefficient reaches 5800W / (m 2 ·K), which is 42% higher than the traditional structure. The capillary rise rate of the composite structure absorbent core layer measured by the Washburn method is 8.2mm / s, and the effective capillary height is 62mm. In terms of flow stability, the test results show that the flow fluctuation coefficient is ≤3.5%, and the pressure drop gradient is 0.15MPa / m, which meets the use requirements.

[0057] Through these detailed designs and manufacturing processes, the present invention not only achieves the expected goals in terms of performance, but also provides a variety of optional liquid-absorbing core 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 present invention based on the information provided without relying on creative work.

[0058] Although the exemplary embodiments of the present disclosure have been described, it should 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 scope of protection of the present disclosure as defined by the claims. The present disclosure is defined by the appended claims, and the equivalents of these claims are also included.

Claims

1. A gas-liquid coplanar refrigerant direct cooling plate, specifically comprising a main structure formed by superimposing and welding an aluminum alloy upper shell plate and a lower shell plate, characterized in that: in, The inner surface of the upper shell plate is processed with a plurality of parallel linear grooves, which are 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; in the inner surface of the heat exchange flow channel, the bottom surface or the top surface is the heat exchange surface; The flow channel is compounded with a liquid absorbing core layer on at least the heat exchange surface, and the liquid absorbing core layer uses a material with capillary liquid absorbing and liquid storing functions to realize capillary liquid absorbing and liquid storing functions; The thickness of the liquid-absorbing core layer should be controlled within 1 / 3 of the total height of the flow channel; The width of the liquid-absorbing core 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 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 angle between the inclined surfaces on both sides of the flow channel and the bottom surface is 75°±2°, and the surfaces of the inclined surfaces on both sides are processed with staggered hemispherical micro-pit arrays; 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, and the pit surface is chemically polished to form a smooth transition surface with Ra≤0.8μm; The inclined surfaces on both sides of the groove are provided with concave positions for flow disturbance, through which the refrigerant is disturbed in the heat exchange flow channel; On the other side of the flow channel opposite to the heat exchange surface, triangular guide fins with a height of 0.5mm to 1.2mm are arranged at intervals of 8mm to 15mm, the inclination angle of the fins is 25° to 35° with the flow direction, and the top corners of the fins are provided with a rounded structure with a fillet radius of 0.2mm to 0.5mm; The liquid outlet end of the heat exchange flow channel is provided with a tapered flow guide structure with a contraction angle of 8° to 12°. The outlet cross-sectional area is reduced by 15% to 25% compared with the flow channel body to maintain a stable gas-liquid interface.

2. A gas-liquid coplanar refrigerant direct cooling plate as claimed in claim 1, characterized in that: The absorbent core layer is a composite structure with a multi-level microporous structure with a directional capillary effect; the porosity of the absorbent core changes gradually along the height direction of the flow channel to meet the absorption requirements under different fluid states; the composite structure of the absorbent core layer includes three layers; the first layer is a thermal conductive bonding layer directly bonded to the flow channel substrate, which is formed by sintering aluminum-copper alloy powder with a particle size of 50-80μm and a porosity of 40%-50%; the second layer is a capillary transmission layer, which is 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 is formed by a laser micro-cladding process to form a mesh pore structure with a pore size of 5-15μm, further enhancing its absorption performance.

3. A gas-liquid coplanar refrigerant direct cooling plate as claimed in claim 1, characterized in that: The liquid-absorbing core layer is an aluminum oxide layer with a thickness of 20 μm to 50 μm. The surface of the aluminum oxide layer is processed by femtosecond laser to form a micro-groove network with a depth of 2 μm to 5 μm and a width of 10 μm to 20 μm. The groove direction is cross-distributed at 45° to 60° with the flow channel axis, and nano-silver particles are deposited in the groove to enhance the capillary wetting performance.

4. A gas-liquid coplanar refrigerant direct cooling plate as claimed in claim 1, characterized in that: The absorbent core is a sponge structure made of porous material with high porosity. The porosity is generally controlled between 50% and 80%, and the pore size varies between 50μm and 300μm to ensure good capillary absorption capacity; the thickness of the sponge structure is controlled between 20μm and 100μm, and the specific thickness design depends on the flow rate of the refrigerant and the required absorption capacity.

5. A method for preparing a gas-liquid coplanar refrigerant direct cooling plate, applied to the gas-liquid coplanar refrigerant direct cooling plate as claimed in any one of claims 1 to 5, characterized in that: The following steps are involved: Step 1: Process the aluminum alloy plate into an upper shell plate and a lower shell plate; process the lower shell plate into a plane structure, and provide a boss structure on the outer edge, and process a stress relief groove on the surface of the boss to relieve thermal deformation during welding; Step 2: A plurality of parallel linear grooves are formed on the inner surface of the upper shell plate by multi-stage progressive die stamping; then a micro-pit array is processed in a preset area of ​​the lower shell plate that matches the linear grooves. The micro-pits are formed by precision machining or die stamping. The diameter and depth of the micro-pits are controlled according to the design requirements, and the surface of the pits is chemically polished to ensure that the surface is smooth and the fluid flows smoothly; finally, the guide fins are fixedly installed in the preset area; Step 3: Fix the absorbent core layer to the bottom of the linear groove to ensure that it is firmly fixed; Step 4: Butt the upper shell plate and the lower shell plate together and fix them by welding to form the main structure; When welding, ensure that all areas of the flow channel are well sealed; Step 1: Final inspection and testing: Inspect the size and sealing of the prepared gas-liquid coplanar refrigerant direct cooling plate to ensure there is no leakage.

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