Cold Plates, Servers and Server Systems

Abstract

The present invention relates to the field of computer technology, and discloses a cold plate, a server and a server system. The cold plate of the present invention comprises a cold plate body, a cooling liquid cavity is formed in the cold plate body, and a heat exchange plate for connecting a heat source is formed on one side of the cold plate body; a jet structure is arranged in the cooling liquid cavity, and a first cavity and a second cavity are separated in the cooling liquid cavity, and the second cavity is formed between the jet structure and the heat exchange plate, and a jet hole for spraying cooling liquid toward the heat exchange plate is formed on the jet structure; a cooling liquid inlet is connected to the first cavity; a cooling liquid outlet is connected to the second cavity, and the cooling liquid outlets are arranged in pairs and are arranged on both sides of the cold plate body. In the cold plate of the embodiment of the present application, after being sprayed onto the heat exchange plate, the cooling liquid can diffuse to both sides of the cold plate respectively, and flow out through the cooling liquid outlets on both sides of the cold plate respectively, 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.

Description

Technical Field

[0001] The present invention relates to the field of computer technology, and in particular to a cold plate, a server and a server system. Background Art

[0002] The jet cold plate is a highly efficient heat dissipation device, which is mainly used in situations with high heat flux density. It can guide the coolant to spray at high speed through the spray hole, thereby taking away a large amount of heat.

[0003] In the related art, the jet cold plate includes a cold plate body, a jet plate arranged in the liquid cavity of the cold plate body, and a coolant inlet and a coolant outlet respectively arranged on both sides of the cold plate body. The coolant can enter the cold plate body through the coolant inlet and be sprayed onto the heating surface through the jet plate to cool down the heat source. However, the temperature on both sides of this jet cold plate is uneven, which easily causes uneven surface temperature distribution of the heat source (such as a chip). Summary of the invention

[0004] In view of this, the present invention provides a cold plate, a server and a server system to solve the problem in the related art that the temperature on both sides of the cold plate is uneven, resulting in uneven surface temperature distribution of the heat source.

[0005] In a first aspect, the present invention provides a cold plate, comprising:

[0006] A cold plate body, wherein a cooling liquid cavity is formed in the cold plate body, and a heat exchange plate for connecting a heat source is formed on one side of the cold plate body;

[0007] A jet structure is arranged in the cooling liquid cavity, and a first cavity and a second cavity are separated in the cooling liquid cavity, the second cavity is formed between the jet structure and the heat exchange plate, and a jet hole for spraying cooling liquid toward the heat exchange plate is formed on the jet structure;

[0008] A coolant inlet communicated with the first cavity;

[0009] The cooling liquid outlet is communicated with the second cavity, and the cooling liquid outlets are arranged in pairs and are respectively arranged on both sides of the cold plate body.

[0010] Beneficial effect: During use of the cold plate of the embodiment of the present application, the coolant can flow into the coolant cavity through the coolant inlet, and be sprayed onto the heat exchange plate at high speed after passing through the jet plate, forming a very thin velocity boundary layer on the heat exchange plate to generate extremely strong convective heat transfer capacity locally. The local convective heat transfer coefficient is increased by nearly 10 times compared with the skived tooth cold plate, thereby quickly taking away the heat on the heat exchange plate.

[0011] Furthermore, in the embodiment of the present application, the coolant outlets are arranged in pairs and are respectively arranged on both sides of the cold plate body. Therefore, after the coolant is sprayed onto the heat exchange plate, two paths are formed. The two paths of coolant diffuse to the two sides of the cold plate respectively, and take away the heat from the surface of the heat exchange plate in the form of laminar flow, and flow out through the coolant outlets on both sides of the cold plate respectively, 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.

[0012] Furthermore, in the embodiment of the present application, the coolant can be sprayed onto the heat exchange plate and exchange heat with the heat source through the heat exchange plate, thereby preventing the coolant from being sprayed directly onto the heat source, which would increase the difficulty of sealing the heat source and create a risk of leakage.

[0013] In an optional embodiment, the jet structure is arranged in the middle of the cooling liquid cavity and extends along the width direction of the cold plate body. The two ends of the jet structure are respectively close to or abut the inner wall of the cooling liquid cavity, and the cooling liquid outlets are respectively arranged on both sides of the cold plate body along the length direction.

[0014] In an optional embodiment, the cooling liquid inlet is connected to a side of the first cavity away from the heat exchange plate and is located in the middle of the first cavity.

[0015] Beneficial effect: This arrangement helps to provide a more uniform temperature distribution on the surface of the heat source.

[0016] In an optional embodiment, a plurality of jet holes are provided on the jet structure, and the plurality of jet holes are distributed in a rectangular array.

[0017] Beneficial effects: The array distribution of jet holes can significantly improve the heat dissipation performance of the cold plate. The array distribution of jet holes can form multiple strong convection heat exchange areas on the surface of the cold plate, effectively improving the overall temperature uniformity, and also helping to reduce pressure drop and improve energy efficiency.

[0018] In an optional embodiment, the jet structure includes a first wall, the first wall is located on a side of the first cavity close to the heat exchange plate, the plane where the first wall is located is parallel to the plane where the heat exchange plate is located, and the jet holes are formed on the first wall.

[0019] Beneficial effect: Through such an arrangement, it can be ensured that the distances between the multiple jet holes on the jet structure and the heat exchange plate are consistent and all can be at the optimal jet distance, which helps to improve the heat exchange efficiency of the cold plate.

[0020] In an optional embodiment, the jet structure also includes a second wall and a third wall, which are respectively connected to both sides of the first wall along the length direction of the cold plate body, and the distance between the second wall and the third wall gradually increases in the direction away from the heat exchange plate.

[0021] Beneficial effect: Through such an arrangement, when the coolant flows through the coolant inlet toward the jet hole, the second wall and the third wall can 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.

[0022] In an optional embodiment, the jet structure includes a first wall, which is located on a side of the first cavity close to the heat exchange plate, and the first wall protrudes toward the direction close to the heat exchange plate. A first slope and a second slope are respectively formed on both sides of the protruding position of the first wall, and the jet hole is formed on the first slope, the second slope, and at the connection between the first slope and the second slope.

[0023] Beneficial effect: Through such a configuration, the coolant flowing out from the first inclined surface and the second inclined surface can have a certain initial velocity flowing 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, and is beneficial for the coolant after passing through the jet area to carry away the heat on the heat exchange plate in a laminar manner. The fluid ejected from the jet hole between the first inclined surface and the second inclined surface can be sprayed at a high speed in 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.

[0024] On this basis, in the process of the coolant flowing toward the jet hole through the coolant inlet, the first slope and the second slope 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.

[0025] In an optional embodiment, the cold plate further includes a heat exchange protrusion, which is disposed in the second cavity and connected to the heat exchange plate.

[0026] Beneficial effect: 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.

[0027] Therefore, the cold plate of the embodiment of the present application can combine the advantages of the higher local convection heat transfer coefficient of the jet cold plate and the higher heat exchange surface characteristics of the skived cold plate, and can achieve high-efficiency heat exchange for high heat flux heat dissipation scenarios.

[0028] In an optional embodiment, the heat exchange protrusion includes a plurality of first shovel teeth, which are arranged below the jet plate and extend along the length direction of the cold plate body. The plurality of first shovel teeth are arranged on the heat exchange plate at intervals along the width direction of the cold plate.

[0029] Beneficial effect: Through such an arrangement, the first shovel tooth is consistent with the flow direction of the coolant, which can avoid the setting of the heat-conducting protrusion to reduce the flow rate of the coolant, and promote the coolant after passing through the jet area to take away the heat of the shovel tooth in a laminar manner, promote the coolant to be evenly distributed on the heat exchange plate, and then provide a more uniform temperature distribution to the surface of the heat source.

[0030] In an optional embodiment, a side of the jet structure close to the heat exchange plate is transitionally matched with the first shovel tooth.

[0031] Beneficial effect: Through such an arrangement, the contact area between the heat exchange protrusion and the coolant can be increased as much as possible, thereby improving the heat exchange efficiency.

[0032] In an optional embodiment, a flow-through notch is formed on the heat exchange protrusion, and the flow-through notch is arranged at a corresponding position of the jet hole.

[0033] Beneficial effect: The flow gap can facilitate the fluid ejected from the jet hole to diffuse around and reduce the flow resistance of the coolant.

[0034] In an optional embodiment, the heat exchange protrusion further includes second shovel teeth, and the second shovel teeth are arranged on both sides of the first shovel teeth along the length direction of the cold plate body;

[0035] The second shovel teeth are in transitional fit with the inner wall of the cold plate body on a side away from the heat exchange plate; and / or,

[0036] Along the width direction of the cold plate body, the distance between two adjacent first shovel teeth is smaller than the distance between two adjacent second shovel teeth.

[0037] Beneficial effect: By setting it in this way, the height of the second shovel teeth can be set higher to further increase the contact area between the heat exchange protrusion and the coolant, and further improve the heat exchange effect of the cold plate. When the distance between two adjacent first shovel teeth is set to be smaller than the distance between two adjacent second shovel teeth, the first shovel teeth can be set more compactly to increase the contact area between the first shovel teeth and the coolant, thereby improving the heat exchange efficiency of the cold plate, and the second shovel teeth can be set more sparsely, thereby reducing the flow resistance of the coolant in the laminar flow scenario, and promoting the coolant after passing through the jet area to take away the heat on the heat exchange plate in the form of laminar flow.

[0038] In an optional embodiment, the method for processing the heat exchange protrusion includes: first processing a first skiving tooth on the heat exchange plate, and then processing a second skiving tooth on both sides of the first skiving tooth.

[0039] Beneficial effect: Through such an arrangement, it is possible to meet the processing and preparation of skiving teeth with different spacings without developing new tools.

[0040] In an optional embodiment, the cold plate body comprises:

[0041] The area of ​​the jet hole is S2, the number of the jet holes is n1, the area of ​​the coolant inlet is S1, and n1*S2<S1.

[0042] Beneficial effect: Through such an arrangement, it can be ensured that the coolant can be pressurized after passing through the jet hole, and the flow rate at the jet hole is greater than the flow rate at the coolant inlet, thereby ensuring the heat exchange effect of the cold plate.

[0043] In an optional embodiment, the cold plate also includes a water inlet joint, the coolant inlet is formed in the water inlet joint, the water inlet joint includes a first section and a second section, the first section extends along the length direction of the cold plate, the second section is connected between the first section and the jet structure, and the extension direction is perpendicular to the plane where the heat exchange plate is located.

[0044] Beneficial effect: Through such an arrangement, the second section of the water inlet joint extends in a direction perpendicular to the heat exchange plate, so the coolant input at the coolant inlet can flow vertically into the jet plate, so that the jet plate can evenly distribute the coolant.

[0045] In an optional embodiment, the cold plate also includes a water outlet joint, which is connected to the cold plate body, and the coolant outlet is formed in the water outlet joint. The water outlet joint includes a third section and a fourth section. The third section is connected to the cold plate body and extends along the length direction of the cold plate. The fourth section is connected to the third section, and an angle is formed between the extension direction and the plane where the heat exchange plate is located.

[0046] Beneficial effect: Through such an arrangement, the coolant does not need to be turned when flowing into the third section through the coolant outlet, which helps to reduce fluid resistance.

[0047] In an optional embodiment, a mounting port is formed on a side of the cold plate body away from the heat exchange plate, and the jet structure includes:

[0048] The box body is connected to the cold plate body through the installation port, the first cavity is formed in the box body, the coolant inlet is connected to the box body, and the jet hole is formed on the surface of the box body facing the heat exchange plate.

[0049] Beneficial effects:

[0050] With such an arrangement, since the volume of the box body itself is relatively small, the coolant can fill the box body and then be pressurized, and then pass through the jet holes and be sprayed onto the surface of the heat exchange plate in the form of a turbulent flow rate, so as to improve the heat exchange effect of the cold plate.

[0051] In an optional embodiment, the cold plate body is a skived cold plate.

[0052] Beneficial effects:

[0053] The cold plate of the embodiment of the present application does not need to be separately molded. It only needs to open a mounting port on the cold plate body of the skived cold plate and add a jet structure on the mounting port. This not only simplifies the manufacturing process of the cold plate and reduces the research and development cost of the cold plate, but also enables the cold plate of the present application to be replaced with the skived cold plate, so that the liquid cooling system can be suitable for the cold plate of the present application without the need to improve and upgrade the liquid cooling system.

[0054] In a second aspect, the present invention further provides a server, comprising:

[0055] chip;

[0056] As in the cold plate of the first aspect of the present invention, the heat exchange plate of the cold plate is connected to the chip.

[0057] Beneficial effects:

[0058] The server of the second aspect of the embodiment of the present application includes or uses the cold plate of the first aspect of the present application, and thus has its beneficial effect, namely; the heat distribution on both sides of the cold plate is more uniform, thereby providing a more uniform temperature distribution on the surface of the heat source. In addition, since the coolant in the embodiment of the present application can be sprayed on the heat exchange plate and heat is exchanged with the heat source through the heat exchange plate, it is possible to avoid the coolant being sprayed directly on the heat source, which increases the difficulty of sealing the heat source and creates a risk of leakage.

[0059] Therefore, the server of the second aspect of the embodiment of the present application can ensure that the hardware equipment always remains within a normal operating temperature range, thereby improving the computing efficiency of the server.

[0060] In a third aspect, the present invention further provides a server system, comprising:

[0061] The server according to the second aspect of the present invention;

[0062] A cooling unit, a water inlet pipe of the cooling unit is connected to a coolant outlet of a cold plate of the server, and a water return pipe of the cooling unit is connected to a coolant inlet of the cold plate.

[0063] Beneficial effect: The server system of the third aspect of the embodiment of the present application includes or uses the server of the second aspect of the present application, and thus has its beneficial effect, that is, the heat distribution on both sides of the cold plate is more uniform, thereby providing a more uniform temperature distribution on the surface of the heat source. In addition, since in the embodiment of the present application, the coolant can be sprayed on the heat exchange plate and heat is exchanged with the heat source through the heat exchange plate, it is possible to avoid the coolant being sprayed directly on the heat source, which increases the difficulty of sealing the heat source and creates a risk of leakage.

[0064] Therefore, the server system of the third aspect of the embodiment of the present application can ensure that the hardware equipment always remains within a normal operating temperature range, thereby improving the computing efficiency of the server. BRIEF DESCRIPTION OF THE DRAWINGS

[0065] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the related technologies, the drawings required for use in the specific embodiments or the related technical descriptions will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0066] Figure 1 A three-dimensional diagram of a cold plate according to an embodiment of the present invention;

[0067] Figure 2 for Figure 1 An exploded view of the cold plate is shown;

[0068] Figure 3 is a cross-sectional view of a jet structure of a cold plate according to an embodiment of the present invention;

[0069] Figure 4 is a cross-sectional view of a cold plate according to an embodiment of the present invention;

[0070] Figure 5 The skiving teeth of the cold plate according to the embodiment of the present invention are schematically shown;

[0071] Figure 6 for Figure 5 Enlarged view of point A in .

[0072] Description of reference numerals:

[0073] 1. cold plate body; 101. cover plate; 1011. mounting port; 102. heat exchange plate; 1021. heat exchange convex portion; 10211. first shovel tooth; 10212. second shovel tooth; 1022. flow gap;

[0074] 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;

[0075] 3. Coolant inlet;

[0076] 4. Coolant outlet;

[0077] 5. The second cavity;

[0078] 6. Water inlet connector; 601, first section; 602, second section;

[0079] 7. Water outlet joint; 701, third section; 702, fourth section. DETAILED DESCRIPTION

[0080] In order to make the purpose, technical solution and advantages of the embodiments of the present invention clearer, the technical solution in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative work are within the scope of protection of the present invention.

[0081] Currently, the power consumption of a CPU can reach 500 W and 600 W, and the heat flux density is around 9 W / cm². Some CPUs even consume 1000 W of power. Combined with the chip size, the heat flux density of the chip will reach 130 W / cm².

[0082] The traditional air cooling heat removal capacity is 85 W / cm 2 , it can no longer meet the heat dissipation requirements of high heat flux density scenarios, and it is urgent to introduce advanced liquid cooling technology. Research data shows that the jet cold plate has a heat dissipation capacity 1.84 times that of the traditional cold plate. To meet the heat dissipation requirements, the jet cold plate requires a lower water inlet flow rate than the traditional liquid cold plate, which will bring customers a higher server deployment density. If the water inlet flow rate is the same, the jet cold plate can achieve a lower chip core temperature, helping to release the chip computing performance. Research data shows that when the CPU works in the temperature range of 70℃~80℃, its reliability will decrease by 5% for every degree increase in temperature. Although the skived cold plate in use can meet the current chip heat dissipation requirements, the jet cold plate has more advantages in high heat flux density conditions. Since liquid jet impact cooling can produce extremely strong convective heat transfer effects locally, it is considered to be one of the most effective technologies for solving the heat dissipation problem of high heat flux density. Jet impact cooling is the most efficient single-phase heat transfer currently known. Therefore, finding a cooling technology that can solve the heat dissipation problem of high heat flux density is an important guarantee for the further development of CPU and GPU technology and the further improvement of supercomputer performance.

[0083] In the related art, the jet cold plate includes a jet cooling device, a chip assembly and an electronic device. The jet cooling device includes a top cover, a jet plate and at least one support member. The top cover is provided with a receiving cavity and a liquid inlet pipe. The jet plate is received in the receiving cavity and is movably connected to the top cover. The jet plate includes a first surface and a second surface opposite to each other and a jet hole 202 penetrating the first surface and the second surface. At least one support member is fixedly connected to the second surface of the jet plate to support the chip. The cooling medium is ejected to the surface of the chip through the jet plate to cool and dissipate the heat of the chip. When the jet cooling device is installed with the chip, since 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, and can adapt to the tolerance caused by the warping of the chip, so that the supporting surface of at least one support member is against the chip, thereby effectively controlling the jet height between the jet plate and the chip to achieve a better cooling effect. However, this jet plate directly sprays liquid onto the surface of the chip, which causes great sealing difficulty and leakage risk to the assembly of electronic equipment.

[0084] Combine the following Figures 1 to 6 , describing an embodiment of the present invention.

[0085] According to an embodiment of the present invention, on the one hand, Figure 1 As shown, 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 in 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 arranged 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, and a jet hole 202 for spraying coolant toward the heat exchange plate 102 is formed on the jet structure 2. The coolant inlet 3 is connected to the first cavity 201. The coolant outlet 4 is connected to the second cavity 5, and the coolant outlets 4 are arranged in pairs and are arranged on both sides of the cold plate body 1.

[0086] During use of the cold plate of the embodiment of the present application, the coolant can flow into the coolant cavity through the coolant inlet 3, and be sprayed onto the heat exchange plate 102 at high speed after passing through the jet plate, forming a very thin velocity boundary layer on the heat exchange plate 102 to generate extremely strong convective heat transfer capacity locally. The local convective heat transfer coefficient is increased by nearly 10 times compared with the skived tooth cold plate, thereby quickly taking away the heat on the heat exchange plate 102.

[0087] Furthermore, in the embodiment of the present application, the coolant outlets 4 are arranged in pairs and are respectively arranged on both sides of the cold plate body 1. Therefore, after the coolant is sprayed onto the heat exchange plate 102, two paths will be formed. The two paths of coolant will diffuse to both sides of the cold plate respectively, and take away the heat on the surface of the heat exchange plate 102 in the form of laminar flow, and flow out through the coolant outlets 4 on both sides of the cold plate respectively, 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.

[0088] Furthermore, in the embodiment of the present application, the coolant can be sprayed onto the heat exchange plate 102 and exchange heat with the heat source through the heat exchange plate 102, thereby preventing the coolant from being directly sprayed onto the heat source, which would increase the difficulty of sealing the heat source and create a risk of leakage.

[0089] In the related art, the coolant inlet 3 and the coolant outlet 4 are respectively connected to the two sides of the cold plate body 1, so that the coolant with a lower temperature enters from the coolant inlet 3, and the coolant with a higher temperature flows out through the coolant outlet 4 after heat exchange, resulting in a large temperature difference between the two sides of the cold plate, and then causing a temperature difference of about 5°C on both sides of the heat source (such as a chip), which will not only affect the performance of the chip, but may also have an adverse effect on its stability and life.

[0090] The heat exchange plate 102 is made of a heat-conducting material to improve the heat exchange effect of the cold plate on the heat source. The heat-conducting material is preferably, but not limited to, copper, aluminum, stainless steel, graphene-aluminum composite materials, etc. The cold plate body 1 and the jet structure 2 are preferably, but not limited to, made by CNC machine tools, laser processing or 3D printing. The components can be connected by welding.

[0091] It should be noted that in the embodiment of the present application, the number of the cooling liquid outlets 4 is not limited, and one or more cooling liquid outlets 4 may be provided on each side of the cold plate.

[0092] As a convertible implementation, cooling liquid outlets 4 may be provided around the cold plate.

[0093] In one embodiment, the jet structure 2 is arranged in the middle of the cooling liquid cavity and extends along the width direction of the cold plate body 1. The two ends of the jet structure 2 are respectively close to or abut the inner wall of the cooling liquid cavity, and the cooling liquid outlets 4 are respectively arranged on both sides of the cold plate body 1 along the length direction.

[0094] This arrangement helps provide a more uniform temperature distribution on the surface of the heat source.

[0095] As a convertible embodiment, the jet structure 2 is arranged in the middle of the cooling liquid cavity and extends along the length direction of the cold plate body 1. The two ends of the jet structure 2 are respectively close to or abut the inner wall of the cooling liquid cavity, and the cooling liquid outlets 4 are respectively arranged on both sides of the cold plate body 1 along the width direction.

[0096] In one embodiment, a plurality of jet holes 202 are disposed on the jet structure 2, and the plurality of jet holes 202 are distributed in a rectangular array.

[0097] The array distribution of the jet holes 202 can significantly improve the heat dissipation performance of the cold plate. The array distribution of the jet holes 202 can form multiple strong convection heat exchange areas on the surface of the cold plate, effectively improving the overall temperature uniformity, and also helping to reduce pressure drop and improve energy efficiency.

[0098] In one embodiment, the cooling liquid inlet 3 is connected to a side of the first cavity 201 away from the heat exchange plate 102 and is located in the middle of the first cavity 201 .

[0099] By such an arrangement, not only the initial flow direction of the coolant is consistent with the direction of the coolant sprayed at the jet hole 202, thereby avoiding the increase in the flow resistance of the coolant due to the turning of the coolant; but also when the coolant is sprayed onto the heat exchange plate 102 through the jet hole 202, the flow rate and flow velocity of the two coolants are relatively uniform, 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; and the distance between the coolant inlet 3 and each jet hole 202 can be relatively uniform, thereby promoting the uniform dispersion of the coolant to each jet hole 202.

[0100] As a convertible embodiment, the coolant inlet 3 can also be optionally connected to one side of the first cavity 201, but such a setting will cause a certain angle between the initial flow direction of the coolant and the jet direction of the jet hole 202, causing the coolant to need to undergo a certain turn before it can pass through the jet hole 202, resulting in an increase in the flow resistance of the coolant, which can easily cause the flow rate of the coolant at the jet hole 202 to decrease.

[0101] On this basis, 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 is greatly different, resulting in less coolant at some farther jet holes 202, or even no coolant passing through, thereby causing uneven cooling and heating of the heat exchange plate 102.

[0102] In one embodiment, Figure 3 As shown, the jet structure 2 includes a first wall 203 . The first wall 203 is located on a side of the first cavity 201 close to the heat exchange plate 102 . The plane where the first wall 203 is located is parallel to the plane where the heat exchange plate 102 is located. The jet holes 202 are formed on the first wall 203 .

[0103] By such arrangement, it can be ensured that the distances between the plurality of jet holes 202 on the jet structure 2 and the heat exchange plate 102 are consistent and all can be at the optimal jet distance, which helps to improve the heat exchange efficiency of the cold plate.

[0104] In one embodiment, the jet structure 2 also includes a second wall 204 and a third wall 205, and the second wall 204 and the third wall 205 are respectively connected to both sides of the first wall 203 along the length direction of the cold plate body 1, and the distance between the second wall 204 and the third wall 205 gradually increases in the direction away from the heat exchange plate 102.

[0105] By such arrangement, when the coolant flows toward the jet hole 202 through the coolant inlet 3, 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.

[0106] As a convertible implementation method, Figure 2 and Figure 4 As shown, the jet structure 2 includes a first wall 203. The first wall 203 is located on a side of the first cavity 201 close to the heat exchange plate 102, and the first wall 203 protrudes toward 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, 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.

[0107] By such an arrangement, the coolant flowing out from the first inclined surface 206 and the second inclined surface 207 can have a certain initial velocity flowing in the direction of 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, and is beneficial for the coolant after passing through the jet area to carry away the heat on the heat exchange plate 102 in a laminar 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 a high speed in 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.

[0108] On this basis, when the coolant flows toward the jet hole 202 through the coolant inlet 3, the first slope 206 and the second slope 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.

[0109] In the description of this application, it should be understood that the terms "first", "second", etc. are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. In the description of the present invention, the meaning of "plurality" is more than two, unless otherwise clearly and specifically defined.

[0110] As another alternative embodiment, the jet structure 2 includes a first wall 203. The first wall 203 is located on a side of the first cavity 201 close to the heat exchange plate 102, and is a curved cylindrical surface protruding toward the heat exchange plate 102. The jet holes 202 are formed on the arc surface.

[0111] By such arrangement, the coolant sprayed toward the edge of the heat exchange plate 102 can have a larger initial velocity toward the coolant outlet 4, so that the heat distribution in the middle and both sides of the cold plate can be more uniform.

[0112] In one embodiment, the cold plate further includes a heat exchange protrusion 1021. The heat exchange protrusion 1021 is disposed in 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.

[0113] Therefore, the cold plate of the embodiment of the present application can combine the advantages of the higher local convection heat transfer coefficient of the jet cold plate and the higher heat exchange surface characteristics of the skived cold plate, and can achieve high-efficiency heat exchange for high heat flux heat dissipation scenarios.

[0114] In one embodiment, Figure 3 and Figure 5 As shown, the heat exchange protrusion 1021 includes a plurality of first shovel teeth 10211, which are arranged below the jet plate and extend along the length direction of the cold plate body 1. The plurality of first shovel teeth 10211 are arranged on the heat exchange plate 102 at intervals along the width direction of the cold plate.

[0115] Through such an arrangement, the first shovel tooth 10211 is consistent with the flow direction of the coolant, which can avoid the arrangement of the first shovel tooth 10211 reducing the flow rate of the coolant, and promote the coolant after passing through the jet area to take away the heat of the shovel tooth in a laminar manner, promote the coolant to be evenly distributed on the heat exchange plate 102, and then provide a more uniform temperature distribution to the surface of the heat source.

[0116] In one embodiment, a side of the jet structure 2 close to the heat exchange plate 102 is transitionally matched with the first shovel teeth 10211 .

[0117] By such a configuration, the contact area between the heat exchange protrusion 1021 and the coolant can be increased as much as possible, thereby improving the heat exchange efficiency.

[0118] In a preferred embodiment, the gap between the side of the jet structure 2 close to the heat exchange plate 102 and the first shovel teeth 10211 is 0.05 mm≤d2≤0.1 mm.

[0119] When d2 is within the above range, the contact area between the heat exchange protrusion 1021 and the coolant can be guaranteed to the greatest extent, and interference between the heat exchange protrusion 1021 and the jet structure 2 caused by processing errors can be avoided.

[0120] In one embodiment, a flow notch 1022 is formed on the heat exchange protrusion 1021. The flow notch 1022 is arranged at a corresponding position of the jet hole 202. The flow notch 1022 can facilitate the fluid ejected from the jet hole 202 to diffuse around and reduce the flow resistance of the coolant.

[0121] In an optional embodiment, a flow-through notch 1022 is formed on the heat exchange protrusion 1021 , and the flow-through notch 1022 is arranged at a corresponding position of the jet hole 202 .

[0122] The flow gap 1022 can facilitate the fluid ejected from the jet hole 202 to diffuse to the surroundings and reduce the flow resistance of the coolant.

[0123] In one embodiment, the dimension of the flow gap 1022 along the length direction of the cold plate body 1 is w1, 0.3mm≤w1≤1mm. When the dimension of the flow gap 1022 along the length direction of the cold plate body 1 is within the above range, the coolant can be fully diffused around without affecting the heat exchange effect of the heat exchange protrusion 1021.

[0124] In a preferred embodiment, w1=1 mm.

[0125] In an optional embodiment, if Figure 6 As shown, the heat exchange protrusion 1021 further includes second shovel teeth 10212. Along the length direction of the cold plate body 1, the second shovel teeth 10212 are arranged on both sides of the first shovel teeth 10211;

[0126] The second shovel teeth 10212 are in transitional fit with the inner wall of the cold plate body 1 on one side away from the heat exchange plate 102; and / or,

[0127] Along the width direction of the cold plate body 1 , the distance between two adjacent first skiving teeth 10211 is smaller than the distance between two adjacent second skiving teeth 10212 .

[0128] By such a 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 arranged 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, and the second shovel teeth 10212 can be arranged more sparsely, thereby reducing the flow resistance of the coolant in the laminar flow scenario, and promoting the coolant after passing through the jet area to take away the heat on the heat exchange plate 102 in the form of laminar flow.

[0129] In a preferred embodiment, the gap between the second shovel teeth 10212 and the inner wall of the cold plate body 1 on the side away from the heat exchange plate 102 and the second shovel teeth 10212 is 0.05 mm≤d3≤0.1 mm.

[0130] When d3 is within the above range, the contact area between the heat exchange protrusion 1021 and the coolant can be maximized, and interference between the heat exchange protrusion 1021 and the inner wall of the cold plate body 1 due to processing errors can be avoided.

[0131] In an optional embodiment, the processing method of the heat exchange protrusion 1021 includes: first processing the first scraping teeth 10211 on the heat exchange plate 102 , and then processing the second scraping teeth 10212 on both sides of the first scraping teeth 10211 .

[0132] Through such an arrangement, the processing and preparation of skiving teeth with different spacings can be met without developing new tools.

[0133] In one embodiment, the distance between the jet hole 202 and the heat exchange plate 102 is d1, 1.5mm≤d1≤1.6mm. The above distance is the optimal jet distance obtained after multiple tests. When the distance between the jet hole 202 and the heat exchange plate 102 is within the above range, the cold plate can have an excellent heat exchange effect.

[0134] In one embodiment, the area of ​​the jet hole 202 is S2, the number of the jet holes 202 is n1, the area of ​​the coolant inlet 3 is S1, and n1*S2<S1.

[0135] By such arrangement, it can be ensured that the coolant can be pressurized after passing through the jet hole 202, and the flow rate at the jet hole 202 is greater than the flow rate at the coolant inlet 3, thereby ensuring the heat exchange effect of the cold plate.

[0136] Assuming that the coolant flow rate at the coolant inlet is 0.4 LPM, S1 is the cross-sectional area at the coolant inlet 3, the water inlet flow rate can be calculated by the following formula:

[0137] Q1= ·S2= πR²;

[0138] =Q1 / n1·π(D2 / 2)²;

[0139] In the formula, represents the flow rate of the coolant at the jet hole 202, is the coolant flow rate at the coolant inlet 3, n1 is the number of the jet holes 202, D2 is the diameter of the jet holes 202, and Q1 is the water inlet flow rate in LPM.

[0140] The following table lists the jet hole 202 velocity at a fixed water inlet flow rate for different jet hole 202 diameters and jet hole 202 numbers:

[0141]

[0142] The horizontal column data in the table is the number of the jet holes 202, the vertical column data in the table is the aperture of the jet holes 202, and the data in the table is the flow rate of the coolant at the jet holes 202 under the corresponding aperture and number of the jet holes 202. It can be seen from the table that under the combination of aperture and number of some jet holes 202, the flow rate of the coolant cannot meet the use requirements. Therefore, the above calculation method can be used to guide the development and design of the jet plate.

[0143] In one embodiment, the cold plate further includes a water inlet joint 6. The coolant inlet 3 is formed in the water inlet joint 6, and the water inlet joint 6 includes a first section 601 and a second section 602, wherein the first section 601 extends along the length direction of the cold plate, and the second section 602 is connected between the first section 601 and the jet structure 2, and the extension direction is perpendicular to the plane where the heat exchange plate 102 is located.

[0144] By such arrangement, the second section 602 of the water inlet joint 6 extends in a direction perpendicular to the heat exchange plate 102, so the coolant input at the coolant inlet 3 can flow vertically into the jet plate, so that the jet plate can evenly distribute the coolant.

[0145] The cold plate also includes a water outlet joint 7, which is connected to the cold plate body 1. The coolant outlet 4 is formed in the water outlet joint 7. The water outlet joint 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 direction of the cold plate. The fourth section 702 is connected to the third section 701, and an angle is formed between the extension direction and the plane where the heat exchange plate 102 is located.

[0146] With such an arrangement, the coolant does not need to be turned when flowing into the third section 701 through the coolant outlet 4, which helps to reduce fluid resistance.

[0147] In one embodiment, a mounting port 1011 is formed on a side of the cold plate body 1 facing away from the heat exchange plate 102, and the jet structure 2 includes a box body. The box body is connected to the cold plate body 1 through the mounting port 1011, the first cavity 201 is formed in the box body, the coolant inlet 3 is connected to the box body, and the jet hole 202 is formed on the surface of the box body facing the heat exchange plate 102.

[0148] By such arrangement, since the volume of the box body itself is small, the coolant can fill the box body and then be pressurized, and then pass through the jet hole 202 and be sprayed onto the surface of the heat exchange plate 102 in the form of turbulent flow, so as to improve the heat exchange effect of the cold plate.

[0149] In a preferred embodiment, the cold plate body 1 is a skived cold plate. Therefore, the cold plate of the embodiment of the present application does not need to be separately molded. It is only necessary to open an installation port 1011 on the cold plate body 1 of the skived cold plate, and add a jet structure 2 on the installation port 1011. This not only simplifies the manufacturing process of the cold plate and reduces the research and development cost of the cold plate, but also enables the cold plate of the present application to be replaced with the skived cold plate, so that the liquid cooling system can be suitable for the cold plate of the present application without improving and upgrading the liquid cooling system.

[0150] In a preferred embodiment, the box body itself is strip-shaped and extends along the width direction of the cold plate body 1. Through such an arrangement, the coolant can fill the box body and then be pressurized to pass through the jet plate at a higher flow rate and impact the heat exchange surface.

[0151] As a convertible implementation, the jet plate can also be arranged to cover the entire heat exchange plate 102, and the jet holes 202 are all located on the jet plate. However, such an arrangement will cause the fluid to enter a larger space, increase the cross-sectional area of ​​the fluid, and reduce the flow rate of the fluid. Therefore, in this process, the coolant will lose part of its flow rate, which will affect the heat exchange efficiency of the cold plate.

[0152] On this basis, when the area of ​​the jet plate is large, the jet holes 202 at the edge of the jet plate can often only receive less coolant, or even no coolant passes through, resulting in the chip corresponding to this part of the heat exchange plate 102 cannot obtain sufficient heat exchange, which easily causes uneven heat exchange efficiency.

[0153] As a convertible embodiment, the jet plate is a plate-like structure and is arranged 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.

[0154] In one embodiment, the cold plate body 1 includes a cover plate 101. The cover plate 101 is placed on the heat exchange plate 102, and a cooling liquid cavity is formed between the cover plate 101 and the heat exchange plate 102. The cover plate 101 and the heat exchange plate 102 are preferably connected by welding, but not limited thereto. As a convertible embodiment, the cold plate body 1 can also be made by 3D printing.

[0155] Next, a set of formulas are provided for characterizing the convective heat transfer effect of the cold plate of the embodiment of the present application.

[0156] ………(1)

[0157] ……… (2)

[0158] Re1=ρvD1 / u……… (3)

[0159] ………(4)

[0160] ………(5)

[0161] Re2=ρvD2 / u……… (6)

[0162] Q2=h·S1·ΔT…………………………(7)

[0163] Formula (1) is the calculation formula for the Nusselt number in turbulent scenarios;

[0164] In the formula, Nu1 is the Nusselt number in the turbulent scenario;

[0165] Re1 is the Reynolds number in the turbulent scene; Pr is the Prandtl number; D2 is the diameter of the jet hole 202, in mm; d1 is the distance between the jet hole 202 and the heat exchange plate 102, in mm; λ is the thermal conductivity;

[0166] Formula (2) is the calculation formula for the local convection heat transfer coefficient in turbulent scenarios;

[0167] In the formula, h1 is the convective heat transfer coefficient in the turbulent scenario.

[0168] Formula (3) is used to calculate the Reynolds number in a turbulent flow scenario, where v represents the average flow velocity of the coolant at the jet hole 202, D1 represents the diameter of the jet hole 202, in mm; u represents the kinematic viscosity; ρ represents the density of the coolant;

[0169] Formula (4) is the calculation formula for the Nusselt number in laminar flow scenarios;

[0170] In the formula, Nu2 is the Nusselt number in laminar flow scenario; Re2 is the Reynolds number in laminar flow scenario; Pr is the Prandtl number; D2 is the gap between the shovel teeth, in mm; λ is the thermal conductivity;

[0171] Formula (5) is the calculation formula for the local convection heat transfer coefficient under laminar flow conditions;

[0172] In the formula, h2 is the convective heat transfer coefficient under laminar flow scenario.

[0173] Formula (6) is used to calculate the Reynolds number in a laminar flow scenario, where v represents the average flow velocity of the coolant at the jet hole 202, D2 represents the gap between the shovel teeth, in units of mm; u represents the kinematic viscosity; and ρ represents the density of the coolant.

[0174] Formula (7) is the calculation formula for convective heat conduction, where Q2 is the chip power consumption, S1 is the convective heat transfer area, ΔT is the temperature difference between the center temperature of the chip surface and the water inlet temperature, and h is the convective heat transfer coefficient.

[0175] According to formula (7), under certain conditions of power consumption, convection heat transfer area and water inlet temperature, if the local convection heat transfer coefficient is increased, the center temperature of the chip surface will be reduced, achieving a good heat dissipation effect.

[0176] According to an embodiment of the present invention, on the other hand, a server is provided, comprising a chip and a cold plate according to the first aspect of the embodiment of the present application. The heat exchange plate 102 of the cold plate is connected to the chip.

[0177] The server of the second aspect of the embodiment of the present application includes or uses the cold plate of the first aspect of the present application, and thus has its beneficial effect, namely; the heat distribution on both sides of the cold plate is more uniform, thereby providing a more uniform temperature distribution on the surface of the heat source. In addition, since the coolant can be sprayed on the heat exchange plate 102 in the embodiment of the present application, and heat is exchanged with the heat source through the heat exchange plate 102, it is possible to avoid the coolant being sprayed directly on the heat source, which increases the difficulty of sealing the heat source and creates a risk of leakage.

[0178] Therefore, the server of the second aspect of the embodiment of the present application can ensure that the hardware equipment always remains within a normal operating temperature range, thereby improving the computing efficiency of the server.

[0179] According to an embodiment of the present invention, on the other hand, a server system is provided, comprising the server and cooling unit provided in the second aspect of the embodiment of the present application. The water inlet pipe of the cooling unit is connected to the coolant outlet 4 of the cold plate of the server, and the water return pipe of the cooling unit is connected to the coolant inlet 3 of the cold plate.

[0180] The cooling unit drives the coolant circulation inside the server and removes the heat generated during the operation of the server. The cooling unit (CDU, Cooling Distribution Unit) is a device used to cool the server, responsible for transferring the cooling medium (usually water) from the central cooling device to the cooling unit in the server rack.

[0181] The server system of the third aspect of the embodiment of the present application includes or uses the server of the second aspect of the present application, and thus has its beneficial effect, that is, the heat distribution on both sides of the cold plate is more uniform, thereby providing a more uniform temperature distribution on the surface of the heat source. In addition, since in the embodiment of the present application, the coolant can be sprayed on the heat exchange plate 102 and heat is exchanged with the heat source through the heat exchange plate 102, it is possible to avoid the coolant being sprayed directly on the heat source, which increases the difficulty of sealing the heat source and creates a risk of leakage.

[0182] Therefore, the server system of the third aspect of the embodiment of the present application can ensure that the hardware equipment always remains within a normal operating temperature range, thereby improving the computing efficiency of the server.

[0183] In summary, the cold plate of the first aspect, the server of the second aspect, and the server system of the third aspect of the present invention have the following advantages:

[0184] 1. Although the skived cold plate in use can meet the current chip cooling needs, the jet cold plate can produce extremely strong convective heat transfer effects locally. Jet impact cooling is the most efficient single-phase heat transfer known so far. It is considered to be one of the most effective technologies for solving high heat flux density cooling scenarios, and has great potential for future application prospects. This invention technology broadens the company's advanced liquid cooling technology layout and forms a technical reserve to cope with the harsh high heat flux density cooling scenarios in the future.

[0185] 2. This invention can meet the heat dissipation requirements of chips. Compared with traditional liquid cooling plates, the jet cooling plate requires a lower water inlet flow rate, which will bring customers a higher server deployment density. If the inlet flow rate is the same, the jet cooling plate can achieve a lower chip core temperature, help release the chip computing performance, and delay the chip life.

[0186] 3. The present invention proposes a single-phase cooling liquid cold plate for high heat flux density heat dissipation scenarios, an array jet cold plate to indirectly dissipate heat for the chip, an array jet cooling device and an enhanced heat exchange structure are combined with each other, and the combined jet cooling improves the local convection heat transfer coefficient and the shovel tooth structure enhances the excellent characteristics of the heat exchange surface area.

[0187] 4. A calculation method for the relationship between the aperture and number of the jet hole 202 and the flow rate of the coolant at the jet hole 202 is proposed to guide the development and design of the liquid cooling plate.

[0188] The above is only a preferred embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any technician in the field can easily make changes or variations within the technical scope disclosed in the present invention, and such changes or variations should be included in the protection scope of the present invention. Therefore, the protection scope of the present invention shall be based on the protection scope of the claims. As long as there is no structural conflict, the various technical features mentioned in each embodiment can be combined in any way. The present invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions that fall within the scope of the claims.

Claims

1. A cold plate, characterized in that: include: A cold plate body (1), wherein a cooling liquid cavity is formed in the cold plate body (1), and a heat exchange plate (102) for connecting to a heat source is formed on one side of the cold plate body (1); A jet structure (2) is arranged in the cooling liquid cavity, and is divided into a first cavity (201) and a second cavity (5) in the cooling liquid cavity, wherein the second cavity (5) is formed between the jet structure (2) and the heat exchange plate (102), and a jet hole (202) is formed on the jet structure (2) for spraying cooling liquid toward the heat exchange plate (102); A cooling liquid inlet (3) connected to the first cavity (201); A cooling liquid outlet (4) is connected to the second cavity (5), and the cooling liquid outlets (4) are arranged in pairs and are arranged on both sides of the cold plate body (1); The jet structure (2) is arranged in the middle of the cooling liquid cavity and extends along the width direction of the cold plate body (1); two ends of the jet structure (2) are respectively close to or abut against the inner wall of the cooling liquid cavity; and the cooling liquid outlets (4) are respectively arranged on both sides of the cold plate body (1) along the length direction; The jet structure (2) comprises: a box body, the first cavity (201) is formed in the box body, the coolant inlet (3) is connected to the box body, the jet hole (202) is formed on the surface of the box body facing the heat exchange plate (102), and the box body itself is in a strip shape; The heat exchange protrusion (1021) comprises a plurality of first shovel teeth (10211), wherein the first shovel teeth (10211) are arranged below the jet structure and extend along the length direction of the cold plate body (1), and the plurality of first shovel teeth (10211) are arranged on the heat exchange plate (102) at intervals along the width direction of the cold plate; A flow notch (1022) is formed on the heat exchange protrusion (1021), and the flow notch (1022) is arranged at a corresponding position of the jet hole (202); A side of the jet structure (2) close to the heat exchange plate (102) is transitionally matched with the first shovel tooth (10211); The heat exchange protrusion (1021) further comprises second shovel teeth (10212), and along the length direction of the cold plate body (1), the second shovel teeth (10212) are arranged on both sides of the first shovel teeth (10211); The second shovel teeth (10212) are transitionally matched with the inner wall of a side of the cold plate body (1) away from the heat exchange plate (102); Along the width direction of the cold plate body (1), the distance between two adjacent first shovel teeth (10211) is smaller than the distance between two adjacent second shovel teeth (10212).

2. The cold plate according to claim 1, characterized in that The cooling liquid inlet (3) is connected to a 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.

3. The cold plate according to claim 1 or 2, characterized in that: The jet structure (2) comprises a first wall (203), the first wall (203) being located on a side of the first cavity (201) close to the heat exchange plate (102), the plane where the first wall (203) is located being parallel to the plane where the heat exchange plate (102) is located, and the jet hole (202) is formed on the first wall (203).

4. The cold plate according to claim 3, characterized in that The jet structure (2) further comprises a second wall (204) and a third wall (205), wherein the second wall (204) and the third wall (205) are respectively connected to two sides of the first wall (203) along the length direction of the cold plate body (1), and the distance between the second wall (204) and the third wall (205) gradually increases in a direction away from the heat exchange plate (102).

5. The cold plate according to claim 3, characterized in that The jet structure (2) comprises a first wall (203), the first wall (203) being located on a side of the first cavity (201) close to the heat exchange plate (102), the first wall (203) protruding in a direction close to the heat exchange plate (102), a first inclined surface (206) and a second inclined surface (207) being formed on both sides of the protruding position of the first wall (203), respectively, and the jet hole (202) being formed on the first inclined surface (206), the second inclined surface (207), and a connection between the first inclined surface (206) and the second inclined surface (207).

6. The cold plate according to claim 1 or 2, characterized in that: It also comprises a heat exchange protrusion (1021), wherein the heat exchange protrusion (1021) is arranged in the second cavity (5) and connected to the heat exchange plate (102).

7. The cold plate according to claim 1, characterized in that The processing method of the heat exchange protrusion (1021) comprises: firstly processing a first scraping tooth (10211) on the heat exchange plate (102), and then processing the second scraping teeth (10212) on both sides of the first scraping tooth (10211).

8. The cold plate according to claim 1 or 2, characterized in that: The cold plate body (1) comprises: The area of ​​the jet hole (202) is S2, the number of the jet holes (202) is n1, the area of ​​the coolant inlet (3) is S1, and n1*S2<S1.

9. The cold plate according to any one of claims 1 to 3, characterized in that A mounting opening (1011) is formed on a side of the cold plate body (1) facing away from the heat exchange plate (102), and the box body is connected to the cold plate body (1) through the mounting opening (1011).

10. The cold plate according to claim 1 or 2, characterized in that: The cold plate body (1) is a skived cold plate.

11. The cold plate according to claim 1 or 2, characterized in that: The cold plate further comprises a water inlet joint (6), the coolant inlet (3) being formed in the water inlet joint (6), the water inlet joint (6) comprising a first section (601) and a second section (602), the first section (601) extending along the length direction of the cold plate, the second section (602) being connected between the first section (601) and the jet structure (2), and extending in a direction perpendicular to the plane where the heat exchange plate (102) is located; and / or, The cold plate further comprises a water outlet joint (7), the water outlet joint (7) being connected to the cold plate body (1), the coolant outlet (4) being formed in the water outlet joint (7), the water outlet joint (7) comprising a third section (701) and a fourth section (702), the third section (701) being connected to the cold plate body (1) and extending along the length direction of the cold plate, the fourth section (702) being connected to the third section (701), and the extension direction forming an angle with the plane where the heat exchange plate (102) is located.

12. A server, characterized in that: include: chip; The cold plate according to any one of claims 1 to 11, wherein the heat exchange plate (102) of the cold plate is connected to the chip.

13. A server system, characterized in that: include: The server according to claim 12; A cooling unit, wherein a water inlet pipe of the cooling unit is connected to a cooling liquid outlet (4) of a cold plate of the server, and a water return pipe of the cooling unit is connected to a cooling liquid inlet (3) of the cold plate.

Images