Cold plate, server, and server system

Abstract

The present application relates to the technical field of computers, and discloses a cold plate, a server, and a server system. The cold plate of the present application comprises: a cold plate body, a cooling liquid cavity being formed in the cold plate body, and a heat exchange plate configured to be connected to a heat source being formed on one side of the cold plate body; a jet structure arranged in the cooling liquid cavity and partitioning the interior of the cooling liquid cavity into a first cavity and a second cavity, the second cavity being formed between the jet structure and the heat exchange plate, and jet holes for spraying cooling liquid toward the heat exchange plate being formed in the jet structure; a cooling liquid inlet communicated with the first cavity; and cooling liquid outlets communicated with the second cavity, the cooling liquid outlets being arranged in pairs and respectively formed in two sides of the cold plate body. In the cold plate of embodiments of the present application, after being sprayed onto the heat exchange plate, the cooling liquid can diffuse to the two sides of the cold plate, and flow out through the cooling liquid outlets in the two sides of the cold plate, such that the heat distribution on the two sides of the cold plate is more uniform, thereby providing a more uniform temperature distribution on the surface of the heat source.

Description

Cold plates, servers and server systems

[0001] Cross-references to related applications

[0002] This application claims priority to Chinese Patent Application No. 202410919146.X, filed on July 10, 2024, entitled "Cold Plate, Server and Server System", the entire contents of which are incorporated herein by reference. Technical Field

[0003] This application relates to the field of computer technology, specifically to a cold plate, a server, and a server system. Background Technology

[0004] A jet cooling plate is a highly efficient heat dissipation device, mainly used in applications with high heat flux density. It guides coolant to be sprayed at high speed through injection holes, thereby removing a large amount of heat.

[0005] In related technologies, a jet cooling plate includes a main body, a jet plate disposed within a liquid cavity of the main body, and coolant inlets and outlets respectively disposed on both sides of the main body. Coolant can enter the main body through the coolant inlets and be sprayed onto the heat-generating surface through the jet plate to cool the heat source. However, the temperature on both sides of this jet cooling plate is uneven, which can easily cause uneven surface temperature distribution of the heat source (e.g., a processor). Summary of the Invention

[0006] In view of this, this application provides a cold plate, a server, and a server system to solve the problem in the related art where the temperature on both sides of the cold plate is uneven, resulting in uneven surface temperature distribution of the heat source.

[0007] In a first aspect, this application provides a cold plate, comprising:

[0008] The main body of the cold plate has a coolant cavity formed inside it, and a heat exchange plate for connecting a heat source is formed on one side of the main body of the cold plate.

[0009] A jet structure is disposed in the coolant cavity and is divided into a first cavity and a second cavity in the coolant cavity. The second cavity is formed between the jet structure and the heat exchange plate. The jet structure has jet holes for spraying coolant toward the heat exchange plate.

[0010] The coolant inlet is connected to the first chamber.

[0011] The coolant outlet is connected to the second cavity. The coolant outlets are arranged in pairs and located on both sides of the main body of the cold plate.

[0012] Beneficial effects: In the use of the cold plate of this application embodiment, the coolant can flow into the coolant cavity through the coolant inlet and be sprayed at high speed onto the heat exchange plate after passing through the jet plate, forming a very thin velocity boundary layer on the heat exchange plate, so as to generate extremely strong convective heat transfer capacity locally. The local convective heat transfer coefficient is nearly 10 times higher than that of the toothed cold plate, thereby quickly removing the heat on the heat exchange plate.

[0013] Furthermore, in this embodiment, the coolant outlets are arranged in pairs and located on both sides of the cold plate body. Therefore, after the coolant is sprayed onto the heat exchange plate, it will form two paths. The two paths of coolant will diffuse to both sides of the cold plate and carry away the heat on the surface of the heat exchange plate in the form of laminar flow. They will then flow out through the coolant outlets on both sides of the cold plate, so that the heat distribution on both sides of the cold plate is more uniform, thereby providing a more uniform temperature distribution to the surface of the heat source.

[0014] Furthermore, in this embodiment, the coolant can be sprayed onto the heat exchange plate and exchange heat with the heat source through the heat exchange plate. This avoids the coolant being sprayed directly onto the heat source, which would increase the difficulty of sealing the heat source and create a risk of leakage.

[0015] In one optional embodiment, the jet structure is disposed in the middle of the coolant cavity and extends along the width direction of the cold plate body. The two ends of the jet structure are close to or abut against the inner wall of the coolant cavity, and the coolant outlets are respectively disposed on both sides of the cold plate body along the length direction.

[0016] In one alternative embodiment, the coolant inlet is connected to the side of the first cavity away from the heat exchange plate and is located in the middle of the first cavity.

[0017] Beneficial effect: This setup helps to provide a more uniform temperature distribution on the surface of the heat source.

[0018] In one alternative embodiment, the jet structure is provided with multiple jet holes, which are distributed in a rectangular array.

[0019] Beneficial effects: The arrayed distribution of jet holes can significantly improve the heat dissipation performance of the cold plate. The arrayed jet holes can form multiple strong convection heat transfer zones on the surface of the cold plate, effectively improving the overall temperature uniformity, and also helping to reduce pressure drop and improve energy efficiency ratio.

[0020] In one alternative embodiment, the jet structure includes a first wall located on the side of the first cavity near the heat exchange plate, the plane of the first wall being parallel to the plane of the heat exchange plate, and jet holes being formed on the first wall.

[0021] Beneficial effects: This configuration ensures that the distance between the multiple jet holes on the jet structure and the heat exchange plate is consistent and that they are all at the optimal jet distance, which helps to improve the heat exchange efficiency of the cold plate.

[0022] In one alternative embodiment, the jet structure further includes a second wall and a third wall, which are respectively connected to both sides of the first wall along the length of the cold plate body, and the distance between the second wall and the third wall gradually increases along the direction away from the heat exchange plate.

[0023] Beneficial effects: With this configuration, as the coolant flows from the coolant inlet toward the jet hole, the second and third walls can converge the coolant and help increase the flow rate of the coolant at the jet hole, thereby improving the heat exchange effect of the cold plate.

[0024] In one alternative embodiment, the jet structure includes a first wall located on the side of the first cavity near the heat exchange plate. The first wall protrudes in the direction of approaching the heat exchange plate. A first inclined surface and a second inclined surface are formed on both sides of the protruding part of the first wall, and jet holes are formed on the first inclined surface, the second inclined surface, and the connection between the first inclined surface and the second inclined surface.

[0025] Beneficial effects: With this configuration, the coolant flowing out from the first and second inclined surfaces can have a certain initial velocity in the direction of the coolant outlet, which helps to expand the area where the fluid is in a turbulent state, thereby improving the heat exchange efficiency of the cold plate. It also helps the coolant after passing through the jet area to carry away the heat on the heat exchange plate in a laminar flow manner. The fluid ejected from the jet hole between the first and second inclined surfaces can be sprayed at high speed onto the middle position of the heat exchange plate, and the flow state of the coolant in the middle position of the heat exchange plate is turbulent, which can ensure that the heat distribution in the middle and both sides of the cold plate is more uniform.

[0026] Based on this, as the coolant flows from the coolant inlet toward the jet hole, the first and second inclined surfaces can also converge the coolant and help increase the flow rate of the coolant at the jet hole, thereby helping to improve the heat exchange effect of the cold plate.

[0027] In one alternative embodiment, the cold plate further includes a heat exchange protrusion disposed within the second cavity and connected to the heat exchange plate.

[0028] Beneficial effects: The heat exchange protrusion can increase the contact area between the heat exchange plate and the coolant, thereby improving the heat exchange efficiency of the cold plate.

[0029] Therefore, the cold plate in this embodiment combines the advantages of the high local convection heat transfer coefficient of the jet cold plate and the high heat transfer surface characteristics of the toothed cold plate, and can achieve high-efficiency heat exchange for high heat flux heat dissipation scenarios.

[0030] In one optional embodiment, the heat exchange protrusion includes a plurality of first shovel teeth, which are disposed below the jet plate and extend along the length direction of the cold plate body. The plurality of first shovel teeth are spaced apart on the heat exchange plate along the width direction of the cold plate.

[0031] Beneficial effects: With this configuration, the first spade tooth is aligned with the flow direction of the coolant, which avoids the cooling velocity being reduced by the heat-conducting protrusion. It also promotes the coolant to carry away the heat from the spade tooth in a laminar flow manner after passing through the jet zone, thus promoting the uniform distribution of the coolant on the heat exchange plate and providing a more uniform temperature distribution to the surface of the heat source.

[0032] In one alternative implementation, the side of the jet structure closest to the heat exchange plate transitions into the first shovel tooth.

[0033] Beneficial effect: By setting it up in this way, the contact area between the heat exchange protrusion and the coolant can be increased as much as possible, thereby improving the heat exchange efficiency.

[0034] In one alternative embodiment, a flow passage notch is formed on the heat exchange protrusion, and the flow passage notch is located at the corresponding position of the jet hole.

[0035] Beneficial effects: The flow notch facilitates the diffusion of fluid ejected from the jet orifice in all directions and reduces the flow resistance of the coolant.

[0036] In one optional embodiment, the heat exchange protrusion further includes a second shovel tooth, which is disposed on both sides of the first shovel tooth along the length direction of the cold plate body.

[0037] The second shovel tooth transitions into the inner wall of the cold plate body on the side furthest from the heat exchange plate; and / or,

[0038] Along the width direction of the cold plate body, the distance between two adjacent first shovel teeth is less than the distance between two adjacent second shovel teeth.

[0039] Beneficial effects: This configuration allows for a higher height of the second shovel teeth, further increasing the contact area between the heat exchange protrusion and the coolant, and enhancing the heat exchange efficiency of the cold plate. When the distance between two adjacent first shovel teeth is set smaller than the distance between two adjacent second shovel teeth, the first shovel teeth can be arranged more compactly to increase the contact area between them and the coolant, thereby improving the heat exchange efficiency of the cold plate. The second shovel teeth can be arranged more sparsely to reduce the flow resistance of the coolant in laminar flow scenarios and promote the coolant to carry away heat from the heat exchange plate in a laminar flow manner after passing through the jet zone.

[0040] In one optional embodiment, the processing method of the heat exchange protrusion includes: firstly processing a first shovel tooth on the heat exchange plate, and then processing a second shovel tooth on both sides of the first shovel tooth.

[0041] Beneficial effect: With this setup, it is possible to meet the machining requirements of shovel teeth with different spacing without developing new cutting tools.

[0042] In one alternative embodiment, the cold plate body includes:

[0043] The area of ​​the jet orifice is S2, the number of jet orifices is n1, the area of ​​the coolant inlet is S1, and n1*S2<S1.

[0044] Beneficial effects: This configuration ensures that the coolant is pressurized after passing through the jet holes, and the flow velocity at the jet holes is greater than that at the coolant inlet, thus ensuring the heat exchange effect of the cold plate.

[0045] In one alternative embodiment, the cold plate further includes a water inlet connector, in which a coolant inlet is formed. The water inlet connector includes a first section and a second section. The first section extends along the length of the cold plate, and the second section connects the first section and the jet structure, with the extension direction perpendicular to the plane of the heat exchange plate.

[0046] Beneficial effect: With this configuration, the second section of the water inlet connector extends in a direction perpendicular to the heat exchange plate, so that the coolant input at the coolant inlet can flow vertically into the jet plate, allowing the jet plate to distribute the coolant evenly.

[0047] In one alternative embodiment, the cold plate further includes a water outlet connector connected to the cold plate body, and a coolant outlet is formed inside the water outlet connector. The water outlet connector includes a third section and a fourth section. The third section is connected to the cold plate body and extends along the length of the cold plate. The fourth section is connected to the third section, and its extension direction forms an angle with the plane where the heat exchange plate is located.

[0048] Beneficial effect: With this configuration, the coolant does not need to be turned as it flows into the third stage through the coolant outlet, which helps to reduce fluid resistance.

[0049] In one alternative embodiment, a mounting port is formed on the side of the cold plate body facing away from the heat exchange plate, and the jet structure includes:

[0050] The housing is connected to the main body of the cold plate through the mounting port. The first cavity is formed inside the housing. The coolant inlet is connected to the housing. The jet hole is formed on the surface of the housing facing the heat exchange plate. Beneficial effects:

[0051] With this configuration, due to the small size of the housing, the coolant can fill the housing, be pressurized, and then sprayed onto the surface of the heat exchange plate in a turbulent flow after passing through the jet holes, thereby improving the heat exchange effect of the cold plate.

[0052] In one alternative implementation, the cold plate body is a toothed cold plate.

[0053] Beneficial effects:

[0054] The cold plate in this embodiment does not require separate mold making. It is only necessary to open an installation port on the cold plate body of the toothed cold plate and add a jet structure to the installation port. This not only simplifies the manufacturing process of the cold plate and reduces the R&D cost of the cold plate, but also makes the cold plate of this application replaceable with the toothed cold plate. This allows the liquid cooling system to be used with the cold plate of this application without the need to improve or upgrade the liquid cooling system.

[0055] Secondly, this application also provides a server, comprising:

[0056] processor;

[0057] As described in the first aspect of this application, the cold plate has a heat exchange plate connected to the processor.

[0058] Beneficial effects:

[0059] The server in the second aspect of this application includes or uses the cold plate of the first aspect of this application, thus having the beneficial effect that the heat distribution on both sides of the cold plate is more uniform, thereby providing a more uniform temperature distribution to the surface of the heat source. Furthermore, in this embodiment, the coolant can be sprayed onto the heat exchange plate and exchange heat with the heat source through the heat exchange plate, thus avoiding the direct spraying of coolant onto the heat source, which would increase the difficulty of sealing the heat source and create a risk of leakage.

[0060] Therefore, the server in the second aspect of this application can ensure that the hardware device is always kept within the normal operating temperature range, thereby improving the server's computing efficiency.

[0061] Thirdly, this application also provides a server system, including:

[0062] The server as described in the second aspect of this application;

[0063] The cooling unit has its inlet pipe connected to the coolant outlet of the server's cold plate, and its return pipe connected to the coolant inlet of the cold plate.

[0064] Beneficial Effects: The server system of the third aspect of this application includes or uses the server of the second aspect of this application, and therefore has the beneficial effect of providing a more uniform heat distribution on both sides of the cold plate, thereby providing a more uniform temperature distribution to the surface of the heat source. Furthermore, in this embodiment, the coolant can be sprayed onto the heat exchange plate and exchange heat with the heat source through the heat exchange plate, thus avoiding the direct spraying of coolant onto the heat source, which would increase the difficulty of sealing the heat source and create a risk of leakage.

[0065] Therefore, the server system of the third aspect of this application can ensure that the hardware device is always kept within the normal operating temperature range, thereby improving the server's computing efficiency. Attached Figure Description

[0066] To more clearly illustrate the technical solutions in the specific embodiments or related technologies of this application, the drawings used in the description of the specific embodiments or related technologies will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0067] Figure 1 is a perspective view of a cold plate according to an embodiment of this application;

[0068] Figure 2 is an exploded view of the cold plate shown in Figure 1;

[0069] Figure 3 is a cross-sectional view of the jet structure of the cold plate in an embodiment of this application;

[0070] Figure 4 is a cross-sectional view of the cold plate according to an embodiment of this application;

[0071] Figure 5 schematically shows the spade teeth of the cold plate in an embodiment of this application;

[0072] Figure 6 is an enlarged view of point A in Figure 5.

[0073] Explanation of reference numerals in the attached drawings: 1. Cold plate body; 101. Cover plate; 1011. Mounting port; 102. Heat exchange plate; 1021. Heat exchange protrusion; 10211. First shovel tooth; 10212. Second shovel tooth; 1022. Flow notch; 2. Jet structure; 201. First cavity; 202. Jet hole; 203. First wall; 204. Second wall; 205. Third wall; 206. First inclined surface; 207. Second inclined surface; 3. Coolant inlet; 4. Coolant outlet; 5. Second cavity; 6. Water inlet connector; 601. First section; 602. Second section; 7. Water outlet connector; 701. Third section; 702. Fourth section. Detailed Implementation

[0074] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, 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 some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0075] Currently, central processing units (CPUs) can consume 500W and 600W, with a heat flux density of 9W / cm³. 2 Around 1000W, some central processing units even consume up to 1000W. Combined with the processor size, the processor's heat flux density will reach 130W / cm2.

[0076] Traditional air-cooled systems have a heat dissipation capacity of 85W / cm². 2 The existing liquid cooling technology is no longer sufficient to meet the heat dissipation requirements of high heat flux density scenarios, necessitating the introduction of advanced liquid cooling technology. Research data shows that jet cooling plates have 1.84 times the heat dissipation capacity of traditional liquid cooling plates. Compared to traditional liquid cooling plates, jet cooling plates require lower inlet flow rates to meet heat dissipation needs, allowing for higher server deployment density. With the same inlet flow rate, jet cooling plates can achieve lower processor core temperatures, contributing to improved processor computing performance. Research data indicates that when a CPU operates within the 70℃~80℃ temperature range, its reliability decreases by 5% for every degree Celsius increase in temperature. While the currently used toothed liquid cooling plates can meet the current processor heat dissipation requirements, jet cooling plates are more advantageous for high heat flux density conditions. Because liquid jet impact cooling can generate extremely strong convective heat transfer effects locally, it is considered one of the most effective technologies for solving high heat flux density heat dissipation problems. Jet impact cooling is currently the most efficient single-phase heat transfer method known. Therefore, finding a cooling technology that can solve the high heat flux density heat dissipation problem is a crucial guarantee for the further development of central processing unit and graphics processing unit technologies and the further improvement of supercomputer performance.

[0077] In related technologies, jet cooling plates include jet cooling devices, processor assemblies, and electronic devices. The jet cooling device includes a top cover, a jet plate, and at least one support member. The top cover has a receiving cavity and a liquid inlet pipe. The jet plate is housed within the receiving cavity and is movably connected to the top cover. The jet plate includes a first surface and a second surface facing away from each other, and jet holes 202 penetrating the first and second surfaces. At least one support member is fixed to the second surface of the jet plate to support the processor. Cooling medium is jetted onto the surface of the processor through the jet plate to cool and dissipate heat. When the jet cooling device is installed with the processor, because the jet plate is movably connected to the top cover, while the top cover is fixedly connected to the substrate, the jet plate has a degree of freedom of movement relative to the top cover, which can accommodate the tolerances caused by processor warping. This allows the supporting surface of at least one support member to abut against the processor, thereby effectively controlling the jet height between the jet plate and the processor to achieve a better cooling effect. However, this type of jet plate directly sprays liquid onto the surface of the processor, which poses significant sealing difficulties and leakage risks during the assembly of electronic devices.

[0078] The embodiments of this application are described below with reference to Figures 1 to 6.

[0079] According to an embodiment of this application, as shown in FIG1, a cold plate is provided, including a cold plate body 1, a jet structure 2, a coolant inlet 3, and a coolant outlet 4. A coolant cavity is formed within the cold plate body 1, and a heat exchange plate 102 for connecting a heat source is formed on one side of the cold plate body 1. The jet structure 2 is disposed within the coolant cavity and divides the coolant cavity into a first cavity 201 and a second cavity 5. The second cavity 5 is formed between the jet structure 2 and the heat exchange plate 102. The jet structure 2 has jet holes 202 formed on it for spraying coolant toward the heat exchange plate 102. The coolant inlet 3 communicates with the first cavity 201. The coolant outlet 4 communicates with the second cavity 5, and the coolant outlets 4 are arranged in pairs, located on opposite sides of the cold plate body 1.

[0080] In the use of the cold plate of this embodiment, the coolant can flow into the coolant chamber through the coolant inlet 3 and be sprayed at high speed onto the heat exchange plate 102 after passing through the jet plate, forming a very thin velocity boundary layer on the heat exchange plate 102, so as to generate extremely strong convective heat transfer capacity locally. The local convective heat transfer coefficient is nearly 10 times higher than that of the toothed cold plate, thereby quickly removing the heat on the heat exchange plate 102.

[0081] Furthermore, in this embodiment, the coolant outlets 4 are arranged in pairs and respectively located on both sides of the cold plate body 1. Therefore, after the coolant is sprayed onto the heat exchange plate 102, it will form two paths. The two paths of coolant will diffuse to both sides of the cold plate and carry away the heat on the surface of the heat exchange plate 102 in the form of laminar flow. They will then flow out through the coolant outlets 4 on both sides of the cold plate, so that the heat distribution on both sides of the cold plate is more uniform, thereby providing a more uniform temperature distribution to the surface of the heat source.

[0082] Furthermore, in this embodiment, the coolant can be sprayed onto the heat exchange plate 102 and exchange heat with the heat source through the heat exchange plate 102. Therefore, it can avoid the coolant being sprayed directly onto the heat source, which would increase the difficulty of sealing the heat source and create a risk of leakage.

[0083] In related technologies, the coolant inlet 3 and the coolant outlet 4 are respectively connected to both sides of the cold plate body 1. This allows the coolant with a lower temperature to enter through the coolant inlet 3, and the coolant with a higher temperature to flow out through the coolant outlet 4 after heat exchange. This results in a large temperature difference between the two sides of the cold plate, which in turn causes a temperature difference of about 5°C between the two sides of the heat source (such as the processor). This not only affects the performance of the processor, but may also have an adverse effect on its stability and lifespan.

[0084] The heat exchange plate 102 is made of a thermally conductive material to improve the heat exchange effect of the cold plate on the heat source. The thermally conductive material is preferably, but not limited to, copper, aluminum, stainless steel, graphene-aluminum composite material, etc. The cold plate body 1 and the jet structure 2 are preferably, but not limited to, manufactured by CNC machine tools, laser processing, or 3D printing. The components can be connected by welding.

[0085] It should be noted that, in this embodiment of the application, the number of coolant outlets 4 is not limited, and one or more coolant outlets 4 may be provided on each side of the cold plate.

[0086] As an alternative implementation method, coolant outlets 4 can be provided on all four sides of the cold plate.

[0087] In one embodiment, the jet structure 2 is disposed in the middle of the coolant cavity and extends along the width direction of the cold plate body 1. The two ends of the jet structure 2 are close to or abut against the inner wall of the coolant cavity, and the coolant outlets 4 are respectively disposed on both sides of the cold plate body 1 along the length direction.

[0088] This setup helps to provide a more uniform temperature distribution on the surface of the heat source.

[0089] As a variable implementation, the jet structure 2 is disposed in the middle of the coolant cavity and extends along the length direction of the cold plate body 1. The two ends of the jet structure 2 are close to or abut against the inner wall of the coolant cavity, and the coolant outlets 4 are respectively disposed on both sides of the cold plate body 1 along the width direction.

[0090] In one embodiment, the jet structure 2 is provided with a plurality of jet holes 202, which are distributed in a rectangular array.

[0091] The arrayed distribution of jet holes 202 can significantly improve the heat dissipation performance of the cold plate. The arrayed jet holes 202 can form multiple strong convection heat transfer zones on the surface of the cold plate, effectively improving the overall temperature uniformity, and also helping to reduce pressure drop and improve energy efficiency ratio.

[0092] In one embodiment, the coolant inlet 3 is connected to the side of the first cavity 201 away from the heat exchange plate 102 and is located in the middle of the first cavity 201.

[0093] This configuration not only ensures that the initial flow direction of the coolant is consistent with the direction of the coolant sprayed at the jet holes 202, avoiding increased flow resistance caused by the coolant changing direction; it also ensures that when the coolant is sprayed onto the heat exchange plate 102 through the jet holes 202, the flow rate and velocity of the two coolants are relatively uniform, resulting in a more uniform heat distribution on both sides of the cold plate, and thus providing a more uniform temperature distribution to the surface of the heat source; it also ensures that the distance between the coolant inlet 3 and each jet hole 202 is relatively uniform, promoting the uniform dispersion of coolant to each jet hole 202.

[0094] As an alternative implementation, the coolant inlet 3 can also be connected to one side of the first cavity 201. However, this arrangement will cause a certain angle between the initial flow direction of the coolant and the jet direction of the jet hole 202, which will cause the coolant to need to turn to pass through the jet hole 202, thereby increasing the flow resistance of the coolant and easily causing the flow rate of the coolant at the jet hole 202 to decrease.

[0095] Based on this, when the coolant inlet 3 is connected to one side of the first cavity 201, the distance between the coolant inlet 3 and each jet hole 202 varies greatly, resulting in less coolant at some of the farther jet holes 202, or even no coolant passing through, which in turn causes uneven heating and cooling of the heat exchange plate 102.

[0096] In one embodiment, as shown in FIG3, the jet structure 2 includes a first wall 203. The first wall 203 is located on the side of the first cavity 201 near the heat exchange plate 102, and the plane of the first wall 203 is parallel to the plane of the heat exchange plate 102. The jet hole 202 is formed on the first wall 203.

[0097] This configuration ensures that the distance between the multiple jet holes 202 on the jet structure 2 and the heat exchange plate 102 is consistent and that they are all at the optimal jet distance, which helps to improve the heat exchange efficiency of the cold plate.

[0098] In one embodiment, the jet structure 2 further includes a second wall 204 and a third wall 205, which are respectively connected to the two sides of the first wall 203 along the length direction of the cold plate body 1. The distance between the second wall 204 and the third wall 205 gradually increases along the direction away from the heat exchange plate 102.

[0099] With this configuration, as the coolant flows through the coolant inlet 3 toward the jet hole 202, the second wall 204 and the third wall 205 can converge the coolant and help increase the flow rate of the coolant at the jet hole 202, thereby helping to improve the heat exchange effect of the cold plate.

[0100] As a possible implementation, as shown in Figures 2 and 4, the jet structure 2 includes a first wall 203. The first wall 203 is located on the side of the first cavity 201 near the heat exchange plate 102. The first wall 203 protrudes in the direction of approaching the heat exchange plate 102. A first inclined surface 206 and a second inclined surface 207 are formed on both sides of the protruding part of the first wall 203, respectively. The jet hole 202 is formed on the first inclined surface 206, the second inclined surface 207, and the connection between the first inclined surface 206 and the second inclined surface 207.

[0101] With this configuration, the coolant flowing out from the first inclined surface 206 and the second inclined surface 207 can have a certain initial velocity flowing towards the coolant outlet 4, which helps to expand the area where the fluid is in a turbulent state, thereby improving the heat exchange efficiency of the cold plate. It also helps the coolant after passing through the jet area to carry away the heat on the heat exchange plate 102 in a laminar flow manner. The fluid ejected from the jet hole 202 between the first inclined surface 206 and the second inclined surface 207 can be sprayed at high speed onto the middle position of the heat exchange plate 102, and the flow state of the coolant in the middle position of the heat exchange plate 102 is turbulent, which can ensure that the heat distribution in the middle and both sides of the cold plate is more uniform.

[0102] Based on this, as the coolant flows through the coolant inlet 3 toward the jet hole 202, the first inclined surface 206 and the second inclined surface 207 can also converge the coolant and help increase the flow rate of the coolant at the jet hole 202, thereby helping to improve the heat exchange effect of the cold plate.

[0103] In the description of this application, it should be understood that the terms "first," "second," etc., 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. In the description of this application, "a plurality of" means two or more, unless otherwise explicitly defined.

[0104] As another alternative implementation, the jet structure 2 includes a first wall 203. The first wall 203 is located on the side of the first cavity 201 near the heat exchange plate 102. The first wall 203 is cylindrical and protrudes in the direction of approaching the heat exchange plate 102. The jet hole 202 is formed on the arc surface.

[0105] With this configuration, the coolant sprayed toward the edge of the heat exchange plate 102 can have a larger initial velocity toward the coolant outlet 4, which can make the heat distribution in the middle and sides of the cold plate more uniform.

[0106] In one embodiment, the cold plate further includes a heat exchange protrusion 1021. The heat exchange protrusion 1021 is disposed within the second cavity 5 and connected to the heat exchange plate 102. The heat exchange protrusion 1021 can increase the contact area between the heat exchange plate 102 and the coolant, thereby improving the heat exchange efficiency of the cold plate.

[0107] Therefore, the cold plate in this embodiment combines the advantages of the high local convection heat transfer coefficient of the jet cold plate and the high heat transfer surface characteristics of the toothed cold plate, and can achieve high-efficiency heat exchange for high heat flux heat dissipation scenarios.

[0108] In one embodiment, as shown in Figures 3 and 5, the heat exchange protrusion 1021 includes a plurality of first shovel teeth 10211, which are disposed below the jet plate and extend along the length direction of the cold plate body 1. The plurality of first shovel teeth 10211 are spaced apart on the heat exchange plate 102 along the width direction of the cold plate.

[0109] With this configuration, the first shovel tooth 10211 is aligned with the flow direction of the coolant, which avoids reducing the flow rate of the coolant and promotes the coolant to carry away the heat of the shovel tooth in a laminar flow manner after passing through the jet zone. This promotes the uniform distribution of the coolant on the heat exchange plate 102, thereby providing a more uniform temperature distribution to the surface of the heat source.

[0110] In one embodiment, the side of the jet structure 2 near the heat exchange plate 102 transitions into the first shovel tooth 10211.

[0111] This configuration maximizes the contact area between the heat exchange protrusion 1021 and the coolant, thereby improving heat exchange efficiency.

[0112] In a preferred embodiment, the gap between the side of the jet structure 2 near the heat exchange plate 102 and the first shovel tooth 10211 is 0.05mm≤d2≤0.1mm.

[0113] When d2 is within the above range, it can maximize the contact area between the heat exchange protrusion 1021 and the coolant, and avoid interference between the heat exchange protrusion 1021 and the jet structure 2 due to processing errors.

[0114] In one embodiment, a flow notch 1022 is formed on the heat exchange protrusion 1021. The flow notch 1022 is located at a corresponding position of the jet hole 202. The flow notch 1022 facilitates the diffusion of fluid ejected from the jet hole 202 in all directions and reduces the flow resistance of the coolant.

[0115] In one alternative embodiment, a flow passage notch 1022 is formed on the heat exchange protrusion 1021, and the flow passage notch 1022 is disposed at the corresponding position of the jet hole 202.

[0116] The flow notch 1022 facilitates the diffusion of fluid ejected from the jet orifice 202 in all directions and reduces the flow resistance of the coolant.

[0117] In one embodiment, the dimension of the flow notch 1022 along the length of the cold plate body 1 is w1, where 0.3mm≤w1≤1mm. When the dimension of the flow notch 1022 along the length of the cold plate body 1 is within the above range, it can promote the coolant to diffuse sufficiently in all directions without affecting the heat exchange effect of the heat exchange protrusion 1021.

[0118] In a preferred embodiment, w1 = 1 mm.

[0119] In an optional embodiment, as shown in FIG6, the heat exchange protrusion 1021 further includes a second shovel tooth 10212, which is disposed on both sides of the first shovel tooth 10211 along the length direction of the cold plate body 1.

[0120] The second shovel tooth 10212 transitionally fits with the inner wall of the cold plate body 1 on the side away from the heat exchange plate 102; and / or,

[0121] Along the width direction of the cold plate body 1, the distance between two adjacent first shovel teeth 10211 is less than the distance between two adjacent second shovel teeth 10212.

[0122] With this configuration, the height of the second shovel teeth 10212 can be set higher to further increase the contact area between the heat exchange protrusion 1021 and the coolant, and further improve the heat exchange effect of the cold plate. When the distance between two adjacent first shovel teeth 10211 is set to be smaller than the distance between two adjacent second shovel teeth 10212, the first shovel teeth 10211 can be set more compactly to increase the contact area between the first shovel teeth 10211 and the coolant, thereby improving the heat exchange efficiency of the cold plate. The second shovel teeth 10212 can be set more sparsely to reduce the flow resistance of the coolant in laminar flow scenarios and promote the coolant after passing through the jet zone to carry away the heat on the heat exchange plate 102 in a laminar flow form.

[0123] In a preferred embodiment, the gap between the second shovel tooth 10212 and the inner wall of the side of the cold plate body 1 away from the heat exchange plate 102 is 0.05mm≤d3≤0.1mm.

[0124] When d3 is within the above range, it can maximize the contact area between the heat exchange protrusion 1021 and the coolant, and avoid interference between the heat exchange protrusion 1021 and the inner wall of the cold plate body 1 due to processing errors.

[0125] In one optional embodiment, the processing method of the heat exchange protrusion 1021 includes: firstly processing a first shovel tooth 10211 on the heat exchange plate 102, and then processing a second shovel tooth 10212 on both sides of the first shovel tooth 10211.

[0126] This setup allows for the fabrication of shovel teeth with varying spacing without the need to develop new cutting tools.

[0127] In one embodiment, the distance between the jet hole 202 and the heat exchange plate 102 is d1, where 1.5mm ≤ d1 ≤ 1.6mm. This distance is the optimal jet distance obtained through multiple experiments. When the distance between the jet hole 202 and the heat exchange plate 102 is within the above range, the cold plate can be guaranteed to have excellent heat exchange performance.

[0128] In one embodiment, the area of ​​the jet orifice 202 is S2, the number of jet orifices 202 is n1, the area of ​​the coolant inlet 3 is S1, and n1*S2<S1.

[0129] This configuration ensures that the coolant is pressurized after passing through the jet hole 202, and the flow velocity at the jet hole 202 is greater than the flow velocity at the coolant inlet 3, thereby ensuring the heat exchange effect of the cold plate.

[0130] Assuming the coolant flow rate at the coolant inlet is 0.4 LPM, and S1 is the cross-sectional area at coolant inlet 3, the inlet velocity can be calculated using the following formula: Q1 = V in ·S2=V in ·πR 2 V jet =Q1 / n1·π(D2 / 2)2;

[0131] In the formula, V jet V represents the flow rate of the coolant at jet orifice 202. in The value is the coolant flow rate at coolant inlet 3, n1 is the number of jet holes 202, D2 is the diameter of jet holes 202, and Q1 is the inlet water flow rate in LPM.

[0132] The table below lists the jet orifice 202 velocities for different jet orifice 202 diameters and numbers at a fixed inlet flow rate:

[0133] The horizontal columns in the table represent the number of jet holes 202, and the vertical columns represent the diameter of the jet holes 202. The data in the table also represent the flow rate of the coolant at the jet holes 202 under the corresponding diameter and number of jet holes 202. As can be seen from the table, the flow rate of the coolant cannot meet the usage requirements under some combinations of the diameter and number of jet holes 202. Therefore, the above calculation method can be used to guide the development and design of jet plates.

[0134] In one embodiment, the cold plate further includes a water inlet connector 6. A coolant inlet 3 is formed within the water inlet connector 6, which includes a first section 601 and a second section 602. The first section 601 extends along the length of the cold plate, and the second section 602 connects the first section 601 and the jet structure 2, with its extension direction perpendicular to the plane of the heat exchange plate 102.

[0135] With this configuration, the second section 602 of the water inlet connector 6 extends in a direction perpendicular to the heat exchange plate 102, so that the coolant input at the coolant inlet 3 can flow vertically into the jet plate, so that the jet plate can distribute the coolant evenly.

[0136] The cold plate also includes a water outlet connector 7, which is connected to the cold plate body 1. A coolant outlet 4 is formed in the water outlet connector 7. The water outlet connector 7 includes a third section 701 and a fourth section 702. The third section 701 is connected to the cold plate body 1 and extends along the length of the cold plate. The fourth section 702 is connected to the third section 701 and its extension direction forms an angle with the plane where the heat exchange plate 102 is located.

[0137] With this configuration, the coolant does not need to be turned as it flows from coolant outlet 4 into the third section 701, which helps to reduce fluid resistance.

[0138] In one embodiment, a mounting port 1011 is formed on the side of the cold plate body 1 facing away from the heat exchange plate 102, and the jet structure 2 includes a housing. The housing is connected to the cold plate body 1 through the mounting port 1011, a first cavity 201 is formed in the housing, a coolant inlet 3 is connected to the housing, and a jet hole 202 is formed on the surface of the housing facing the heat exchange plate 102.

[0139] With this configuration, since the box itself is small in size, the coolant can fill the box, be pressurized, and then spray onto the surface of the heat exchange plate 102 in a turbulent flow after passing through the jet hole 202, thereby improving the heat exchange effect of the cold plate.

[0140] In a preferred embodiment, the cold plate body 1 is a toothed cold plate. Therefore, the cold plate of this application embodiment does not need to be molded separately. It is only necessary to open the mounting port 1011 on the cold plate body 1 of the toothed cold plate and add the jet structure 2 on the mounting port 1011. This not only simplifies the manufacturing process of the cold plate and reduces the R&D cost of the cold plate, but also makes the cold plate of this application replaceable with the toothed cold plate. This allows the liquid cooling system to be used with the cold plate of this application without the need to improve or upgrade the liquid cooling system.

[0141] In a preferred embodiment, the box itself is strip-shaped and extends along the width direction of the cold plate body 1. With this arrangement, the coolant can fill the box and then be pressurized, passing through the jet plate at a large flow rate and impacting the heat exchange surface.

[0142] As an alternative implementation, the jet plate can also be configured to cover the entire heat exchange plate 102, with all jet holes 202 located on the jet plate. However, this configuration results in the fluid entering a larger space, increasing the cross-sectional area of ​​the fluid and decreasing its flow velocity. Consequently, the coolant will lose some of its flow velocity during this process, affecting the heat exchange efficiency of the cold plate.

[0143] Based on this, when the area of ​​the jet plate is large, the jet holes 202 at the edge of the jet plate can often only receive a small amount of coolant, or even no coolant at all, which results in the processor corresponding to this part of the heat exchange plate 102 not receiving sufficient heat exchange, and easily causing uneven heat exchange efficiency.

[0144] As a variable implementation, the jet plate has a plate-like structure and is disposed inside the cold plate body 1. A first cavity 201 is formed between the side of the jet plate away from the heat exchange plate 102 and the cold plate body 1, and a second cavity 5 is formed between the side of the jet plate close to the heat exchange plate 102 and the cold plate body 1.

[0145] In one embodiment, the cold plate body 1 includes a cover plate 101. The cover plate 101 covers the heat exchange plate 102, forming a coolant cavity between the cover plate 101 and the heat exchange plate 102. The cover plate 101 and the heat exchange plate 102 are preferably, but not limited to, connected by welding. As an alternative implementation, the cold plate body 1 may also be made by 3D printing.

[0146] The following set of formulas is provided to characterize the convective heat transfer effect of the cold plate in the embodiments of this application. Re1=ρvD1 / u……… (3) Re2=ρvD2 / u………… (6) Q2=h·S1·ΔT………………………………(7)

[0147] Formula (1) is the formula for calculating the Nusselt number in a turbulent scenario;

[0148] In the formula, Nu1 is the Nusselt number in the turbulent scenario;

[0149] Re1 is the Reynolds number in turbulent conditions; Pr is the Prandtl number; D2 is the diameter of the jet orifice 202 in mm; d1 is the distance between the jet orifice 202 and the heat exchange plate 102 in mm; λ is the thermal conductivity.

[0150] Formula (2) is the formula for calculating the local convective heat transfer coefficient in turbulent scenarios;

[0151] In the formula, h1 represents the convective heat transfer coefficient in the turbulent scenario.

[0152] Formula (3) is used to calculate the Reynolds number in turbulent scenarios. In the formula, v represents the average flow velocity of the coolant at the jet orifice 202, D1 represents the diameter of the jet orifice 202 in mm, u represents the kinematic viscosity, and ρ represents the density of the coolant.

[0153] Formula (4) is the formula for calculating the Nusselt number in a laminar flow scenario;

[0154] In the formula, Nu2 is the Nusselt number in laminar flow; Re2 is the Reynolds number in laminar flow; Pr is the Prandtl number; D2 is the gap between the shovel teeth in mm; and λ is the thermal conductivity.

[0155] Formula (5) is the formula for calculating the local convective heat transfer coefficient under laminar flow conditions;

[0156] In the formula, h2 is the convective heat transfer coefficient in a laminar flow scenario.

[0157] Formula (6) is used to calculate the Reynolds number in a laminar flow scenario. In the formula, v represents the average flow velocity of the coolant at the jet orifice 202, D2 is the gap between the shovel teeth in mm; u represents the kinematic viscosity; and ρ represents the density of the coolant.

[0158] Formula (7) is the formula for calculating convective heat transfer. In the formula, Q2 is the processor power consumption, S1 is the convective heat transfer area, ΔT is the temperature difference between the center temperature of the processor surface and the water temperature, and h is the convective heat transfer coefficient.

[0159] According to formula (7), under the condition that the power consumption, convection heat transfer area and inlet temperature are constant, increasing the local convection heat transfer coefficient will reduce the center temperature of the processor surface and achieve a good heat dissipation effect.

[0160] According to an embodiment of this application, another aspect provides a server including a processor and a cold plate according to a first aspect of the embodiments of this application. The heat exchange plate 102 of the cold plate is connected to the processor.

[0161] The server in the second aspect of this application includes or uses the cold plate of the first aspect of this application, thus having the beneficial effect that the heat distribution on both sides of the cold plate is more uniform, thereby providing a more uniform temperature distribution to the surface of the heat source. Furthermore, in this embodiment, the coolant can be sprayed onto the heat exchange plate 102 and exchange heat with the heat source through the heat exchange plate 102, thus avoiding the direct spraying of coolant onto the heat source, which would increase the difficulty of sealing the heat source and create a risk of leakage.

[0162] Therefore, the server in the second aspect of this application can ensure that the hardware device is always kept within the normal operating temperature range, thereby improving the server's computing efficiency.

[0163] According to an embodiment of this application, another aspect provides a server system including the server and cooling unit provided in the second aspect of the present application. The inlet pipe of the cooling unit is connected to the coolant outlet 4 of the server's cold plate, and the return pipe of the cooling unit is connected to the coolant inlet 3 of the cold plate.

[0164] Cooling units circulate the coolant inside the server, carrying away the heat generated during server operation. A cooling distribution unit (CDU) is a device used to cool servers, responsible for transferring the cooling medium (usually water) from the central cooling system to the cooling units within the server rack.

[0165] The server system of the third aspect of this application includes or uses the server of the second aspect of this application, and therefore has the beneficial effect that the heat distribution on both sides of the cold plate is more uniform, thereby providing a more uniform temperature distribution to the surface of the heat source. Furthermore, in this embodiment, the coolant can be sprayed onto the heat exchange plate 102 and exchange heat with the heat source through the heat exchange plate 102, thus avoiding the direct spraying of coolant onto the heat source, which would increase the difficulty of sealing the heat source and create a risk of leakage.

[0166] Therefore, the server system of the third aspect of this application can ensure that the hardware device is always kept within the normal operating temperature range, thereby improving the server's computing efficiency.

[0167] In summary, the cold plate of the first aspect, the server of the second aspect, and the server system of the third aspect of this application have the following advantages:

[0168] 1. Although the existing toothed cold plate can meet the current heat dissipation requirements of processors, the jet cold plate can generate a very strong convective heat transfer effect in a localized area. Jet impact cooling is the most efficient single-phase heat transfer technology known to date. It is considered to be one of the most effective technologies for solving high heat flux density heat dissipation scenarios and has great potential for future applications. This invention technology broadens the company's advanced liquid cooling technology layout and forms a technology reserve to cope with the harsh high heat flux density heat dissipation scenarios in the future.

[0169] 2. This invention, while meeting processor cooling requirements, requires a lower inlet flow rate compared to traditional liquid cooling plates, allowing for higher server deployment density. With the same inlet flow rate, the jet cooling plate can achieve a lower processor core temperature, contributing to improved processor performance and extending processor lifespan.

[0170] 3. This application proposes a single-phase liquid cooling plate for high heat flux density heat dissipation scenarios, an array jet cooling plate for indirect heat dissipation of the processor, and an array jet cooling device and an enhanced heat exchange structure combined to combine the advantages of jet cooling to improve the local convective heat transfer coefficient and the toothed structure to enhance the heat transfer surface area.

[0171] 4. A calculation method is proposed to determine the relationship between the aperture and number of nozzles of the jet orifice 202 and the flow velocity of the coolant at the jet orifice 202, which can guide the development and design of liquid cooling plates.

[0172] The above are merely preferred embodiments of this application, but the scope of protection of this application is not limited thereto. Any person skilled in the art can easily make changes or modifications within the technical scope disclosed in this application, and such changes or modifications should be covered within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims. As long as there is no structural conflict, the various technical features mentioned in the various embodiments can be combined in any way. This application is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A cold-rolled steel plate, characterized in that, include: A cold plate body (1) has a cooling liquid cavity formed inside it, and a heat exchange plate (102) for connecting a heat source is formed on one side of the cold plate body (1). A jet structure (2) is disposed in the coolant cavity and a first cavity (201) and a second cavity (5) are separated in the coolant cavity. The second cavity (5) is formed between the jet structure (2) and the heat exchange plate (102). The jet structure (2) has a jet hole (202) for spraying coolant toward the heat exchange plate (102). The coolant inlet (3) is connected to the first cavity (201); The coolant outlet (4) is connected to the second cavity (5). The coolant outlets (4) are arranged in pairs and are located on both sides of the cold plate body (1).

2. The cold-rolled plate according to claim 1, characterized in that, The jet structure (2) is located in the middle of the coolant cavity and extends along the width direction of the cold plate body (1). The two ends of the jet structure (2) are close to or abut against the inner wall of the coolant cavity, and the coolant outlets (4) are located on both sides of the cold plate body (1) along the length direction.

3. The cold-rolled plate according to claim 2, characterized in that, The coolant inlet (3) is connected to the side of the first cavity (201) away from the heat exchange plate (102) and is located in the middle of the first cavity (201); and / or, The jet structure (2) is provided with a plurality of jet holes (202), and the plurality of jet holes (202) are distributed in a rectangular array.

4. The cold-rolled plate according to any one of claims 1 to 3, characterized in that, The jet structure (2) includes a first wall (203), which is located on the side of the first cavity (201) close to the heat exchange plate (102). The plane of the first wall (203) is parallel to the plane of the heat exchange plate (102), and the jet hole (202) is formed on the first wall (203).

5. The cold-rolled plate according to claim 4, characterized in that, The jet structure (2) further includes a second wall (204) and a third wall (205), which are respectively connected to the first wall (203) on both sides along the length of the cold plate body (1). The distance between the second wall (204) and the third wall (205) gradually increases along the direction away from the heat exchange plate (102).

6. The cold-rolled plate according to claim 4, characterized in that, The jet structure (2) includes a first wall (203), which is located on the side of the first cavity (201) close to the heat exchange plate (102). The first wall (203) protrudes in the direction close to the heat exchange plate (102). A first inclined surface (206) and a second inclined surface (207) are formed on both sides of the protruding position of the first wall (203). The jet hole (202) is formed at the first inclined surface (206), the second inclined surface (207), and the connection between the first inclined surface (206) and the second inclined surface (207).

7. The cold-rolled plate according to any one of claims 1 to 3, characterized in that, It also includes a heat exchange protrusion (1021), which is disposed in the second cavity (5) and connected to the heat exchange plate (102).

8. The cold-rolled plate according to claim 7, characterized in that, The heat exchange protrusion (1021) includes a plurality of first shovel teeth (10211), which are disposed below the jet structure and extend along the length direction of the cold plate body (1). The plurality of first shovel teeth (10211) are spaced apart on the heat exchange plate (102) along the width direction of the cold plate.

9. The cold plate according to claim 8, characterized in that, The jet structure (2) is in transition fit with the first shovel tooth (10211) on the side near the heat exchange plate (102).

10. The cold plate according to claim 7, characterized in that, A flow passage notch (1022) is formed on the heat exchange protrusion (1021), and the flow passage notch (1022) is located at the corresponding position of the jet hole (202).

11. The cold plate according to claim 8, characterized in that, The heat exchange protrusion (1021) further includes a second shovel tooth (10212), which is disposed on both sides of the first shovel tooth (10211) along the length direction of the cold plate body (1); The second shovel tooth (10212) transitionally engages with the inner wall of the cold plate body (1) on the side away from the heat exchange plate (102); and / or, Along the width direction of the cold plate body (1), the distance between two adjacent first shovel teeth (10211) is less than the distance between two adjacent second shovel teeth (10212).

12. The cold-rolled plate according to claim 11, characterized in that, The processing method of the heat exchange protrusion (1021) includes: firstly processing a first shovel tooth (10211) on the heat exchange plate (102), and then processing a second shovel tooth (10212) on both sides of the first shovel tooth (10211).

13. The cold-rolled plate according to any one of claims 1 to 3, characterized in that, The main body of the cold plate (1) includes: The area of ​​the jet hole (202) is S2, the number of jet holes (202) is n1, the area of ​​the coolant inlet (3) is S1, and n1*S2<S1.

14. The cold-rolled plate according to any one of claims 1 to 3, characterized in that, The cold plate body (1) has an installation port (1011) on the side away from the heat exchange plate (102), and the jet structure (2) includes: The housing is connected to the cold plate body (1) through the mounting port (1011), the first cavity (201) is formed in the housing, the coolant inlet (3) is connected to the housing, and the jet hole (202) is formed on the surface of the housing facing the heat exchange plate (102).

15. The cold-rolled plate according to any one of claims 1 to 3, characterized in that, The main body of the cold plate (1) is a toothed cold plate.

16. The cold-rolled plate according to any one of claims 1 to 3, characterized in that, The cold plate also includes a water inlet connector (6), and the coolant inlet (3) is formed within the water inlet connector (6). The water inlet connector (6) includes a first section (601) and a second section (602). The first section (601) extends along the length of the cold plate, and the second section (602) connects the first section (601) and the jet structure (2), and its extension direction is perpendicular to the plane of the heat exchange plate (102); and / or, The cold plate also includes a water outlet connector (7), which is connected to the cold plate body (1). The coolant outlet (4) is formed in the water outlet connector (7). The water outlet connector (7) includes a third section (701) and a fourth section (702). The third section (701) is connected to the cold plate body (1) and extends along the length of the cold plate. The fourth section (702) is connected to the third section (701) and its extension direction forms an angle with the plane where the heat exchange plate (102) is located.

17. The cold-rolled plate according to claim 1, characterized in that, The jet structure (2) is located in the middle of the coolant cavity and extends along the length of the cold plate body (1). The two ends of the jet structure (2) are close to or abut against the inner wall of the coolant cavity. The coolant outlets (4) are located on both sides of the cold plate body (1) along the width direction.

18. The cold-rolled plate according to any one of claims 1 to 3, characterized in that, The jet structure (2) includes a first wall (203) located on the side of the first cavity (201) close to the heat exchange plate (102). The first wall (203) is cylindrical and protrudes toward the heat exchange plate (102). The jet hole (202) is formed on the arc surface.

19. A server, characterized in that, include: processor; The cold plate as described in any one of claims 1 to 18, wherein the heat exchange plate (102) of the cold plate is connected to the processor.

20. A server system, characterized in that, include: The server as described in claim 19; The cooling unit has an inlet pipe connected to the coolant outlet (4) of the server's cold plate and a return pipe connected to the coolant inlet (3) of the cold plate.

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