AI server side liquid cooling structure, server side power supply and liquid cooling structure and equipment

Abstract

The invention relates to an AI server side liquid cooling structure, a server side power supply and liquid cooling structure and equipment, and relates to the technical field of servers, the structure comprises a bottom plate and a heat exchange plate, the bottom plate is installed at the bottom of an AI server case, the lower plate surface of the heat exchange plate is attached to the surface of the bottom plate, and the upper plate surface of the heat exchange plate is attached to the bottom of the case. A spiral flow channel is formed between the bottom plate and the heat exchange plate and comprises an inner rotational flow channel and an outer rotational flow channel which communicate with each other and are arranged in a staggered mode in the thickness direction of the bottom plate, the inner rotational flow channel spirally extends from outside to inside, the outer rotational flow channel spirally extends from inside to outside, and a concentric-square-shaped circulation path is formed. The inner rotational flow channel is provided with an inflow section extending in the long edge direction, and the outer rotational flow channel is provided with an outflow section extending in the wide edge direction. A straight flow channel is further formed in the bottom plate and communicates with the inflow section and an external pipeline, the outflow section is connected with the straight flow channel through a communicating groove, a turbulent flow heat exchange piece is arranged in the communicating groove, a heat exchange cavity in the turbulent flow heat exchange piece is used for guiding a refrigerant to flow back and forth, and efficient heat exchange and flow stability improvement are achieved.

Description

Technical Field

[0001] This application relates to the field of server technology, and in particular to an AI server-side liquid cooling structure, a server-side power supply and liquid cooling structure and device. Background Technology

[0002] Currently, an AI server (Artificial Intelligence Server) is a high-performance computing device specifically designed to run artificial intelligence (AI) algorithms and models. Unlike ordinary business servers (such as website or database servers), AI servers are designed to meet the needs of massive data processing and high-intensity parallel computing. Therefore, AI servers have high requirements for heat dissipation during operation and need to be equipped with liquid cooling structures to reduce operating temperature.

[0003] However, the liquid cooling structure on existing AI servers is limited by the length and arrangement of its internal flow channels, which can easily lead to overheating in the terminal area. This can cause significant temperature differences in certain parts of the AI ​​server, affecting its operating efficiency and lifespan. Summary of the Invention

[0004] This application provides an AI server-side liquid cooling structure, a server-side power supply and liquid cooling structure and device, to at least partially solve the above-mentioned technical problems.

[0005] To achieve the above objectives, according to the first aspect of this application, an AI server-side liquid cooling structure is provided, comprising: all the technical features of claim 1.

[0006] Optionally, a base plate and a heat exchange plate are provided. The base plate is configured to be installed at the bottom of the AI ​​server chassis, and the heat exchange plate is configured such that the lower plate surface is attached to the surface of the base plate and the upper plate surface is attached to the bottom of the AI ​​server chassis. A spiral flow channel is provided between the base plate and the heat exchange plate. The spiral flow channel includes an inner spiral flow channel and an outer spiral flow channel that are connected. The inner spiral flow channel extends spirally from the outside to the inside along a loop path, and the outer spiral flow channel extends spirally from the inside to the outside along a loop path. The inner spiral flow channel and the outer spiral flow channel are arranged alternately layer by layer along the thickness of the base plate. The inner swirling channel has an inflow section that extends along the long side of the bottom plate. The outer swirling channel has an outflow section whose length direction is consistent with the width direction of the bottom plate and perpendicular to the length direction of the inflow section. The outflow section extends from the side close to the inflow section to the side away from the inflow section and connects to the outside. A direct current channel is also provided between the base plate and the heat exchange plate. The direct current channels are parallel and spaced apart on one side of the outflow section. One end of the direct current channel is connected to the initial part of the inflow section, and the other end is connected to the external pipe. The outflow section and the DC channel are connected by a plurality of connecting slots that are perpendicular to each other and spaced apart. Each connecting slot is embedded with a turbulence heat exchanger. The turbulence heat exchanger extends from the inside of the connecting slot into the outflow section. Along the length direction perpendicular to the outflow section, the maximum length of the portion of the turbulence heat exchanger located in the outflow section is a, and the width of the outflow section is b, where 1 / 3b≤a≤1 / 2b. The turbulence heat exchanger has a heat exchange cavity. The first end opening of the heat exchange cavity is connected to the direct current channel, and the second end opening of the heat exchange cavity is located on the outer wall of the turbulence heat exchanger upstream of the outflow section.

[0007] Optionally, the wall surface of the turbulence heat exchanger facing the upstream end of the outflow section is a heat exchange surface, and the heat exchange surface is configured to contact the coolant flowing in the outflow section so that the coolant in the heat exchange chamber and the coolant in the outflow section can achieve partial heat exchange.

[0008] Optionally, the wall surface of the turbulence heat exchanger facing away from the upstream end of the outflow section is a reinforcing surface, the thickness of the reinforcing surface is greater than the thickness of the heat exchange surface, and a force transmission beam is provided in the heat exchange cavity, one end of the force transmission beam is connected to the heat exchange surface and the other end is connected to the reinforcing surface.

[0009] Optionally, the heat exchange surface is an arc surface, and the heat exchange surface is concave towards the upstream end side away from the outflow section; And / or, the reinforcing surface is an arc surface, and the reinforcing surface is recessed toward the upstream end side away from the outflow section, and the second end opening of the heat exchange cavity is opened at the trough of the reinforcing surface.

[0010] Optionally, the cross-sectional shape of the force transmission beam is an equilateral triangle, and one of the apexes of the equilateral triangle is directly opposite the first end opening of the heat exchange cavity.

[0011] Optionally, along the flow direction of the coolant in the outflow section, the second end opening of the heat exchange chamber is inclined toward the side away from the direct flow path.

[0012] Optionally, the width of the second end opening of the heat exchange chamber gradually decreases along the flow direction of the coolant in the outflow section.

[0013] Optionally, a plurality of guide plates are provided on the inner wall of the DC channel on the side away from the connecting groove, and one guide plate corresponds to one connecting groove; The guide plate is an arc-shaped plate, and one end of the guide plate extends arc-shaped towards the side close to the connecting groove, so as to guide part of the coolant flowing in the direct current channel to the second end opening of the heat exchange cavity.

[0014] According to a second aspect of this application, a server-side power supply and liquid cooling structure is provided, including the AI ​​server-side liquid cooling structure described in the first aspect, and further including an AI server chassis, wherein the AI ​​server chassis is disposed on the surface of the heat exchange plate.

[0015] According to a third aspect of this application, an AI server device is also provided, including the AI ​​server-side liquid cooling structure described in the first aspect, or the server-side power supply and liquid cooling structure described in the second aspect.

[0016] In summary, this application includes at least one of the following beneficial technical effects: 1. By incorporating a multi-stage fluid guiding and heat exchange system, including heat exchange chambers, direct-flow channels, outflow sections, and connecting channels, within the liquid cooling structure of the AI ​​server, a smooth, stable, and efficient flow path for the coolant is created within the structure. The heat exchange chambers and direct-flow channels utilize various structural elements, such as inclined openings, equilateral triangular force-transfer beams, and arc-shaped heat exchange surfaces, to generate appropriate turbulence in necessary areas during coolant flow, thereby enhancing heat exchange efficiency. Simultaneously, the gradual design limiting the channel size and flow direction angle helps reduce fluid resistance and improve heat exchange uniformity. Under the high heat load environment of AI servers, this structure can, to a certain extent, improve cooling performance and thermal management efficiency, alleviate uneven heat distribution, and extend the lifespan of the AI ​​server. 2. By introducing a combination of designs including arc-shaped guide vanes, inclined openings, and a tapering structure, a flow guiding mechanism is established between the heat exchange cavity and the direct-flow channel. This allows for a controllable fluid distribution pattern as the refrigerant enters and exits the heat exchange cavity. The arc-shaped profile of the guide vanes guides some of the refrigerant into the heat exchange area and maintains smooth flow, preventing local backflow and turbulence. The inclined arrangement and gradually decreasing opening width improve the continuity of the fluid transition. This structure makes the refrigerant flow more stable during the heat exchange process, resulting in more efficient heat transfer. Overall, it improves the heat exchange balance and structural reliability of the liquid cooling system, meeting the heat dissipation requirements of AI servers operating at high power for extended periods. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] To gain a more complete understanding of this application and its beneficial effects, the following description will be provided in conjunction with the accompanying drawings, wherein the same reference numerals in the following description denote the same parts.

[0019] Figure 1This is a cross-sectional view showing the arrangement of the AI ​​server-side liquid cooling structure and the AI ​​server chassis provided in the embodiments of this application; Figure 2 This is an internal cross-sectional view of the AI ​​server-side liquid cooling structure provided in the embodiments of this application; Figure 3 yes Figure 2 An enlarged schematic diagram of part A in the middle; Figure 4 This is a diagram showing the orientation of the force transmission beam within the heat exchanger in an embodiment of this application.

[0020] Explanation of reference numerals in the attached figures: 1. Base plate; 2. Heat exchange plate; 3. Spiral flow channel; 31. Inner spiral flow channel; 311. Inlet section; 32. Outer spiral flow channel; 321. Outlet section; 4. Direct current channel; 5. Connecting slot; 6. Turbulent heat exchanger; 61. Heat exchange cavity; 611. First end opening; 612. Second end opening; 62. Heat exchange surface; 63. Reinforcing surface; 7. Force transmission beam; 8. Deflector plate; 9. AI server chassis. Detailed Implementation

[0021] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the protection scope of this application.

[0022] This application provides a liquid cooling structure for an AI server. Please refer to [link / reference]. Figure 1 , Figure 2 and Figure 3 The liquid cooling structure of the AI ​​server includes a base plate 1 and a heat exchange plate 2. The base plate 1 is installed at the bottom of the AI ​​server chassis 9 and is used to support the main structure of the liquid cooling system. The lower surface of the heat exchange plate 2 is in close contact with the surface of the base plate 1 and the upper surface is in close contact with the bottom of the AI ​​server chassis 9, thereby forming a closed fluid channel space between the base plate 1 and the heat exchange plate 2.

[0023] For example, the fluid channel space formed between the base plate 1 and the heat exchange plate 2 is a spiral channel 3. The spiral channel 3 includes an inner spiral channel 31 and an outer spiral channel 32 that are connected. The inner spiral channel 31 extends spirally from the outside to the inside along a loop path, and the outer spiral channel 32 extends spirally from the inside to the outside along a loop path. The two are arranged in an alternating layer in the thickness direction of the base plate 1, so that the refrigerant presents a flow path with alternating hot and cold distribution during the flow process.

[0024] It is understandable that such staggered arrangement can create a relatively balanced temperature distribution area at the bottom of the AI ​​server chassis 9, giving the liquid cooling structure better temperature uniformity, which helps to reduce the temperature difference between different areas of the chassis and improve heat dissipation stability.

[0025] In some implementations, combined Figure 1 , Figure 2 and Figure 3 Both the base plate 1 and the heat exchange plate 2 have rectangular shapes. The inflow section 311 of the inner swirling channel 31 extends along the long side of the base plate 1, while the outflow section 321 of the outer swirling channel 32 extends along the wide side of the base plate 1 and is perpendicular to the inflow section 311. The outflow section 321 extends from the side closest to the inflow section 311 to the side furthest from the inflow section 311 and connects to a pipe to the outside. This directional arrangement allows the refrigerant to enter from one side and distribute evenly along the long side, then flow from the inside to the outside via a spiral path and exit along the wide side, resulting in a more uniform flow path for the refrigerant throughout the flow field and reducing stagnant areas at the ends of the channels.

[0026] For example, a direct current channel 4 is also provided between the base plate 1 and the heat exchange plate 2. The direct current channel 4 is parallel and spaced on one side of the outflow section 321. One end of the direct current channel 4 is connected to the initial part of the inflow section 311, and the other end is connected to an external pipe. It can be understood that this structure allows a portion of the refrigerant entering the inflow section 311 to directly enter the direct current channel 4, so that the direct current channel 4 and the inflow section 311 form a partially parallel flow relationship. This results in a lower temperature of the refrigerant in the direct current channel 4, and it can subsequently form a local temperature balance with the outflow section 321, thus having the function of regulating the temperature distribution of the flow field.

[0027] For example, multiple connecting slots 5 are perpendicularly and spaced apart between the outflow section 321 and the direct current channel 4. Each connecting slot 5 is embedded with a turbulence-inducing heat exchanger 6, which extends from the inside of the connecting slot 5 into the outflow section 321. Its maximum length in the direction perpendicular to the length of the outflow section 321 is 'a', and the width of the outflow section 321 is 'b', where 'a' and 'b' satisfy: 1 / 3b ≤ a ≤ 1 / 2b. It can be understood that this length design allows the turbulence-inducing heat exchanger 6 to penetrate deep into the outflow section 321 to turbulent the main current without obstructing the refrigerant flow path.

[0028] For example, the turbulent heat exchanger 6 has a heat exchange cavity 61. The first end opening 611 of the heat exchange cavity 61 is connected to the direct current channel 4, and the second end opening 612 is located on the upstream outer wall of the turbulent heat exchanger 6 away from the outflow section 321. When the refrigerant flows in the direct current channel 4, it can flow into the interior of the turbulent heat exchanger 6 through the heat exchange cavity 61, and then be introduced into the outflow section 321 through the second end opening 612. This allows the refrigerant to be injected into the relatively high-temperature region of the outflow section 321 at a lower temperature, which is beneficial to reducing the average temperature of the outflow section 321. At the same time, since the turbulent heat exchanger 6 extends from the direct current channel 4 into the outflow section 321, it forms local flow disturbances in the outflow section 321. When the refrigerant flows around the turbulent heat exchanger 6, a turbulent zone is formed, which destroys the low thermal conductivity gas film layer originally attached to the channel wall, thereby enhancing the heat exchange capacity between the liquid and the heat exchange wall.

[0029] Based on this, through the above structural combination, the flow state of the refrigerant in the liquid cooling system changes from a single mainstream circulation to a combined mainstream and tributary circulation mode. The alternating hot and cold layout of the inner swirling channel 31 and the outer swirling channel 32 creates a temperature compensation effect in the longitudinal direction of the liquid cooling path. The connection structure between the direct current channel 4 and the outflow section 321 creates a temperature equalization effect in the transverse direction of the refrigerant. The turbulent heat exchanger 6 introduces turbulent flow into the local flow field, further improving heat transfer performance. The overall structure improves the heat distribution in the bottom liquid cooling area of ​​the AI ​​server chassis 9 to a certain extent, reducing the temperature difference between different areas, increasing the utilization rate of the coolant, and improving the efficiency of heat exchange. It also helps to extend the stable operating time of electronic components in the AI ​​server chassis 9. This liquid cooling structure is suitable for high-density AI computing environments and plays a positive role in improving the reliability of AI server operation and the energy efficiency of the cooling system.

[0030] In some implementations, refer to Figure 1 , Figure 2 and Figure 3 The wall surface of the turbulent heat exchanger 6 facing the upstream end of the outflow section 321 is a heat exchange surface 62. The heat exchange surface 62 is configured to contact the coolant flowing in the outflow section 321 so that the coolant in the heat exchange chamber 61 and the coolant in the outflow section 321 can achieve partial heat exchange.

[0031] It can be understood that the wall surface of the turbulent heat exchanger 6 facing the upstream end of the outlet section 321 is the heat exchange surface 62. This heat exchange surface 62 is directly exposed in the fluid channel of the outlet section 321 and comes into contact with the coolant flowing in the outlet section 321. The heat exchange surface 62 is made of a heat exchange material with excellent thermal conductivity, such as copper, aluminum, or a high thermal conductivity composite material, to improve the heat exchange efficiency between it and the coolant. The orientation of the heat exchange surface 62 is the upstream end region of the outlet section 321, so that the refrigerant flowing from the upstream end to the downstream end in the outlet section 321 first comes into contact with the heat exchange surface 62 when it flows through this region, thereby forming turbulence in the contact area. Because the heat exchange surface 62 has a certain convex curvature or surface microstructure, when the refrigerant flows through, the fluid boundary layer will be disturbed, the velocity gradient of the refrigerant will change, and the originally relatively stable laminar flow will be transformed into local turbulence. This turbulent state promotes a more uniform temperature field for the refrigerant and enhances the heat exchange between the refrigerant and the heat exchange surface 62, resulting in a more effective convective heat transfer mode inside the outflow section 321.

[0032] Meanwhile, behind the heat exchange surface 62 is the heat exchange cavity 61. The coolant temperature in the heat exchange cavity 61 is relatively low. When the heat exchange surface 62 comes into contact with the relatively high-temperature refrigerant in the outflow section 321, heat is conducted along the heat exchange surface 62 to the heat exchange cavity 61, thus establishing a heat exchange path between the refrigerants on both sides of the heat exchange surface 62. Since the refrigerant in the heat exchange cavity 61 comes from the direct current channel 4, its temperature is lower than that of the mainstream refrigerant in the outflow section 321, thus forming a temperature gradient in the contact area, making the heat exchange surface 62 act as an intermediary for heat transfer. Through this structural arrangement, some of the refrigerant in the outflow section 321 exchanges heat with the low-temperature refrigerant in the heat exchange cavity 61 before mixing with the refrigerant flowing out from the second end opening 612, causing the overall temperature of the refrigerant in the outflow section 321 to gradually decrease during the flow process. This local heat exchange effect can reduce the temperature difference between the upstream and downstream of the outflow section 321, making the temperature distribution of the entire liquid cooling system more uniform, thereby helping to reduce the local overheating area at the bottom of the AI ​​server chassis 9.

[0033] Furthermore, since the heat exchange surface 62 directly faces the main flow path of the outflow section 321, the resulting turbulence improves the flow state of the refrigerant to a certain extent, making the fluid velocity distribution more uniform and preventing stagnation zones at structural turning points. The direct contact between the heat exchange surface 62 and the refrigerant in the outflow section 321 allows for simultaneous momentum and heat exchange along the flow path, thus forming a composite convective heat transfer process. Through this structure, the AI ​​server-side liquid cooling structure exhibits good overall heat exchange balance, high coolant utilization, and a more direct and efficient heat conduction path. This reduces the temperature gradient in the outflow section 321 to a certain extent, positively impacting the thermal stability of the AI ​​server under high computing power operating conditions.

[0034] For example, the wall surface of the turbulence heat exchanger 6 facing away from the upstream end of the outflow section 321 is a reinforced surface 63. The thickness of the reinforced surface 63 is greater than the thickness of the heat exchange surface 62. A force transmission beam 7 is provided in the heat exchange cavity 61. One end of the force transmission beam 7 is connected to the heat exchange surface 62 and the other end is connected to the reinforced surface 63.

[0035] It is understandable that the heat exchange surface 62 is designed to be relatively thin because it needs to be in direct contact with the refrigerant and exchange heat, so as to reduce thermal resistance and enhance thermal conductivity. The reinforcing surface 63 is located on the back of the turbulent heat exchanger 6. A force transmission beam 7 is provided inside the heat exchange cavity 61. One end of the force transmission beam 7 is connected to the heat exchange surface 62 and the other end is connected to the reinforcing surface 63.

[0036] For example, the force transmission beam 7 can be an integrally formed structure or a metal embedded structure, and its cross-sectional shape can be rectangular, circular, triangular or other irregular cross-sections with reinforcing ribs, in order to form a rigid support path inside.

[0037] It is understandable that when the refrigerant in the outflow section 321 flows from the upstream end to the downstream end, a certain impact force is generated on the heat exchange surface 62 when the refrigerant flows over the surface of the turbulent heat exchanger 6. Since the thickness of the heat exchange surface 62 is relatively small, if there is a lack of structural support, it is prone to local vibration or deformation, thus affecting the heat exchange stability. The presence of the force transmission beam 7 allows the impact force on the heat exchange surface 62 to be transmitted to the reinforcing surface 63 along the force transmission path. Due to its larger thickness and higher rigidity, the reinforcing surface 63 can share and absorb some of the fluid impact energy, thereby keeping the heat exchange surface 62 in a stable and flat state under the action of fluid impact. This force transmission path effectively reduces the local stress concentration phenomenon of the heat exchange surface 62, which to a certain extent helps to extend the service life of the heat exchange surface 62 and maintain its good heat exchange performance.

[0038] Furthermore, the connection between the force transmission beam 7 and the reinforcing surface 63 creates a three-dimensional stress system within the turbulent heat exchanger 6. The dynamic pressure exerted by the refrigerant on the heat exchange surface 62 is transmitted to the reinforcing surface 63 via the force transmission beam 7, and then dispersed to the overall frame through the structural rigidity of the reinforcing surface 63, resulting in a more uniform stress distribution within the heat exchanger. The thickness difference between the reinforcing surface 63 and the heat exchange surface 62 not only enhances the overall structural resistance to deformation but also reduces the vibration amplitude of the heat exchange surface 62 caused by refrigerant impact, making the flow of coolant within the outflow section 321 more stable and beneficial for maintaining heat exchange efficiency and structural reliability. This design shows promising application prospects in the high-intensity cooling cycle environment of AI servers, providing stable heat exchange conditions and higher mechanical durability for liquid cooling systems.

[0039] In some implementations, combined with Figure 2 , Figure 3 and Figure 4The cross-sectional shape of the force-transmitting beam 7 is an equilateral triangle, with one apex of the equilateral triangle facing the first end opening 611 of the heat exchange cavity 61. It can be understood that the force-transmitting beam 7 is located inside the heat exchange cavity 61, with one end connected to the heat exchange surface 62 and the other end connected to the reinforcing surface 63. It is used to transmit fluid impact force and support the structure of the heat exchange surface 62 during refrigerant flow. Because the cross-section of the force-transmitting beam 7 is an equilateral triangle, when the refrigerant enters the heat exchange cavity 61 from the first end opening 611, the apex faces the inflow direction, allowing the refrigerant to smoothly flow to both sides of the force-transmitting beam 7. The fluid flow around the beam is relatively smooth, and no significant flow separation zone is generated at the front end of the force-transmitting beam 7. This can reduce flow resistance to a certain extent and maintain the continuity and stability of the refrigerant flow within the heat exchange cavity 61.

[0040] Furthermore, multiple force transmission beams 7 can be installed to improve the force transmission effect.

[0041] It is worth noting that since the heat exchange cavity 61 mainly serves as an intermediary for heat exchange in the liquid cooling system, and the primary function of the refrigerant inside is to absorb or release heat rather than generate turbulence, the equilateral triangular structure of the force transmission beam 7 is beneficial in reducing flow disturbance. The geometric arrangement with the tip facing the inlet gives the force transmission beam 7 good flow guiding characteristics while transmitting load. The flow obstruction area around the refrigerant is relatively small, resulting in a more uniform flow velocity distribution. Because there is a certain angle between the two sides of the triangular cross-section and the fluid flow direction, a stable boundary layer can be formed on both sides when the refrigerant flows through, preventing the turbulent zone from forming prematurely in the heat exchange cavity 61, thereby reducing pressure drop. This structural design results in lower fluid resistance and a more stable flow field inside the heat exchange cavity 61, which is beneficial for the refrigerant to maintain a continuous heat transfer path within the cavity. At the same time, it takes into account both structural strength and smooth flow, enabling the liquid cooling structure to maintain high thermal conductivity while having good flow efficiency.

[0042] In some implementations, combined Figure 2 , Figure 3 The heat exchange surface 62 is an arc surface, and the heat exchange surface 62 is concave towards the upstream end side away from the outflow section 321. In some implementations, combined Figure 2 , Figure 3 The reinforcing surface 63 is an arc surface, and the reinforcing surface 63 is concave towards the upstream end side away from the outflow section 321. The second end opening 612 of the heat exchange cavity 61 is opened at the trough of the reinforcing surface 63.

[0043] It is understood that the heat exchange surface 62 has an arc-shaped structure, with its arc contour concave towards the upstream end away from the outlet section 321. This creates a local velocity gradient on the inner wall of the arc surface, causing secondary turbulence in the refrigerant and increasing the contact path between the refrigerant and the heat exchange surface 62 per unit length, thus enhancing heat exchange efficiency. Simultaneously, the reinforcing surface 63 also has an arc-shaped structure, with a protrusion on the outer side facing downstream and a concave shape on the inner side. The second end opening 612 is located at the trough of this reinforcing surface 63. Through this arrangement, as the refrigerant flows from the first opening to the second end opening 612, it can gradually transition along the curvature direction of the inner wall of the arc surface. The direction of fluid inertia matches the shape of the reinforcing surface 63, thereby reducing turbulence at the outlet and allowing the refrigerant to enter the outlet section 321 more smoothly. The spatial flow path formed by the heat exchange surface 62 and the reinforcing surface 63 takes into account both heat exchange efficiency and flow stability in its structure, and has the effect of improving heat exchange performance within a limited installation space.

[0044] In some implementations, combined Figure 2 , Figure 3 Along the flow direction of the coolant in the outflow section 321, the second end opening 612 of the heat exchange chamber 61 is inclined toward the side away from the direct flow channel 4.

[0045] For example, along the flow direction of the coolant in the outflow section 321, the width of the second end opening 612 of the heat exchange chamber 61 gradually decreases.

[0046] It is understandable that, along the flow direction of the coolant in the outflow section 321, the second end opening 612 of the heat exchange cavity 61 is inclined towards the side away from the direct current channel 4. This ensures that the flow direction of the coolant, as it enters the heat exchange cavity 61 from the direct current channel 4 and flows towards the outflow section 321, matches the opening angle, creating a smooth velocity transition at the flow turning point. This structurally reduces fluid separation at the edge, allowing the refrigerant to maintain high flow stability when entering the second end opening 612. Furthermore, the second end opening 612 of the heat exchange cavity 61 gradually narrows along the coolant flow direction, forming a converging structure. This causes the refrigerant flow velocity within the cavity to gradually increase at the outlet, creating a pressure gradient in the inlet region of the outflow section 321. Under the influence of this gradient, the refrigerant flows smoothly into the outflow section 321, reducing backflow or localized eddies between the heat exchange cavity 61 and the outflow section 321. By combining the inclined arrangement with the gradually narrowing width design, the connection between the heat exchange cavity 61 and the outflow section 321 has higher flow matching, which is beneficial to improving the flow continuity and flow guiding efficiency of the refrigerant in the entire heat exchange path, thereby enhancing the heat exchange capacity of the heat exchange cavity 61 while maintaining stable flow.

[0047] In some implementations, combined with Figure 2 , Figure 3Multiple guide plates 8 are provided on the inner wall of the DC channel 4 away from the connecting groove 5, with one guide plate 8 corresponding to one connecting groove 5; further, the guide plate 8 is an arc-shaped plate, and one end of the guide plate 8 extends arc-shaped towards the side close to the connecting groove 5, so as to guide part of the coolant flowing in the DC channel 4 to flow to the second end opening 612 of the heat exchange chamber 61.

[0048] It is understandable that the guide plate 8 adopts an arc-shaped structure, with one end extending in an arc towards the direction close to the connecting groove 5. This guides the flow direction of the coolant flowing through the direct current channel 4 when it encounters the guide plate 8. Some of the coolant is deflected along the arc surface of the guide plate 8 and flows towards the second end opening 612 of the heat exchange chamber 61. The arc-shaped guide plate 8 generates a gradually changing guiding angle along the flow path, causing the fluid to form a smoother flow distribution trend in the area close to the connecting groove 5, reducing turbulence and backflow caused by sudden changes in flow direction inside the direct current channel 4. Through the arc-shaped design of the guide plate 8, the refrigerant can be guided to form a regular flow distribution in the heat exchange area to a certain extent, promoting a more uniform entry of the refrigerant into each heat exchange chamber 61, thereby improving the flow balance and heat exchange stability inside the liquid cooling structure.

[0049] Secondly, this application also provides a server-side power supply and liquid cooling structure, including the AI ​​server-side liquid cooling structure of the first aspect, and also includes an AI server chassis 9, which is disposed on the surface of the heat exchange plate 2.

[0050] Thirdly, this application also provides an AI server device, including the AI ​​server-side liquid cooling structure of the first aspect, or the server-side power supply and liquid cooling structure of the second aspect.

[0051] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0052] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions of other embodiments.

[0053] The embodiments, implementation methods, and related technical features of this application can be combined and substituted for each other without conflict.

[0054] The above are merely preferred embodiments of this application and are not intended to limit this application in any way. Any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of this application without departing from the scope of the technical solution of this application shall still fall within the scope of the technical solution of this application.

Claims

1. An AI server-side liquid cooling structure, characterized by, The application relates to a heat exchange plate (2) and a bottom plate (1) which are arranged on the bottom of an AI server case (9), wherein a spiral flow channel (3) is arranged between the bottom plate (1) and the heat exchange plate (2), the spiral flow channel (3) comprises an inner spiral flow channel (31) and an outer spiral flow channel (32) which are connected to each other, the inner spiral flow channel (31) extends spirally along a meandering path from outside to inside, the outer spiral flow channel (32) extends spirally along a meandering path from inside to outside, and the inner spiral flow channel (31) and the outer spiral flow channel (32) are staggered along the thickness direction of the bottom plate (1). The inner spiral flow channel (31) has an inflow section (311) which extends along the long side direction of the bottom plate (1), the outer spiral flow channel (32) has an outflow section (321) which is perpendicular to the length direction of the inflow section (311) and coincides with the width direction of the bottom plate (1), and the outflow section (321) extends from the side close to the inflow section (311) to the side far away from the inflow section (311) and is connected to a pipeline outside. A straight flow channel (4) is further arranged between the bottom plate (1) and the heat exchange plate (2), the straight flow channel (4) is parallel to and spaced from one side of the outflow section (321), one end of the straight flow channel (4) is connected to the initial part of the inflow section (311), and the other end of the straight flow channel (4) is connected to the pipeline outside. A plurality of communication grooves (5) are vertically and spacedly connected between the outflow section (321) and the straight flow channel (4), each communication groove (5) is embedded with a turbulence heat exchange element (6), the turbulence heat exchange element (6) extends from the inner part of the communication groove (5) to the outflow section (321), is perpendicular to the length direction of the outflow section (321), the maximum length of the part of the turbulence heat exchange element (6) in the outflow section (321) is a, the width of the outflow section (321) is b, and 1 / 3b<=a<=1 / 2b. The turbulence heat exchange element (6) has a heat exchange cavity (61), the first end opening (611) of the heat exchange cavity (61) is connected to the straight flow channel (4), and the second end opening (612) of the heat exchange cavity (61) is located on the outer wall of the turbulence heat exchange element (6) which is away from the upstream of the outflow section (321). 2.The AI server-side liquid cooling structure according to claim 1, characterized in that, The wall surface of the turbulence heat exchange element (6) which is towards the upstream end of the outflow section (321) is a heat exchange surface (62), the heat exchange surface (62) is arranged to be in contact with the cooling liquid flowing in the outflow section (321), so that the cooling liquid in the heat exchange cavity (61) and the cooling liquid in the outflow section (321) realize partial heat exchange. 3.The AI server-side liquid cooling structure of claim 2, characterized in that, The wall surface of the spoiler heat exchange element (6) away from the upstream end of the outflow section (321) is a reinforced surface (63), the thickness of the reinforced surface (63) is greater than the thickness of the heat exchange surface (62), the heat exchange cavity (61) is provided with a force transmission beam (7), one end of the force transmission beam (7) is connected to the heat exchange surface (62), and the other end is connected to the reinforced surface (63). 4.The AI server-side liquid cooling structure of claim 3, characterized in that, The heat exchange surface (62) is a curved surface, and the heat exchange surface (62) is recessed towards the side away from the upstream end of the outflow section (321); And / or, the reinforced surface (63) is a curved surface, and the reinforced surface (63) is recessed towards the side away from the upstream end of the outflow section (321), and the second end opening (612) of the heat exchange cavity (61) is arranged at the trough of the reinforced surface (63). 5.The AI server-side liquid cooling structure of claim 3, wherein, The cross-sectional shape of the force transmission beam (7) is an equilateral triangle, and one of the sharp ends of the equilateral triangle is opposite the first end opening (611) of the heat exchange cavity (61). 6.The AI server-side liquid cooling structure of claim 3, wherein, Along the flow direction of the cooling liquid in the outflow section (321), the second end opening (612) of the heat exchange cavity (61) is arranged inclined towards the side away from the straight flow channel (4). 7.The AI server-side liquid cooling structure according to claim 6, characterized in that, Along the flow direction of the cooling liquid in the outflow section (321), the width of the second end opening (612) of the heat exchange cavity (61) gradually decreases. 8.The AI server-side liquid cooling structure according to any one of claims 2 to 7, characterized in that, A plurality of guide plates (8) are arranged on the inner wall of the side of the straight flow channel (4) away from the communication groove (5), one of the guide plates (8) corresponds to one of the communication grooves (5); The guide plate (8) is an arc plate, and one end of the guide plate (8) extends arc-shaped towards the side close to the communication groove (5), so as to guide part of the cooling liquid flowing in the straight flow channel (4) to flow to the second end opening (612) of the heat exchange cavity (61).

9. A server-side power supply and liquid cooling structure, characterized by, The AI server side liquid cooling structure of any one of claims 1 to 8 further comprises an AI server case (9), and the AI server case (9) is arranged on the plate surface of the heat exchange plate (2).

10. An AI server device, comprising: The server side power supply and liquid cooling structure of claim 9, or the AI server side liquid cooling structure of any one of claims 1 to 8.

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