Cold plate type liquid cooling heat dissipation device with cooling liquid inlet and outlet on same side

Abstract

The invention discloses a cold plate type liquid cooling heat dissipation device with a cooling liquid inlet and a cooling liquid outlet on the same side. The cold plate type liquid cooling heat dissipation device comprises a cold plate cavity and a liquid cooling heat dissipation flow guide structure arranged in the cavity. The cooling liquid inlet and the cooling liquid outlet are located on the same side of the cold plate cavity, compact layout of flow channels is achieved through the design of opposite arrangement, and a stable circulating flow path is formed. According to the multi-area liquid cooling heat dissipation flow guide structure, a plurality of irregular-shaped flow guide rib columns are arranged in a staggered mode, two main heat dissipation paths similar to a C shape and a mirror image C shape and a plurality of branch flow paths are formed, and sufficient fluid disturbance and heat exchange are provided. The transition flow guide rib columns arranged at the corners enable cooling liquid to steer smoothly in the flowing process, and turbulent flow and rapid flow velocity change are avoided. According to the structural design, the cooling liquid is uniformly distributed, the heat dissipation efficiency is improved, the local overheating risk is reduced, the efficient heat dissipation performance of the device is ensured, the device is particularly suitable for heat management requirements of various high-power-density electronic equipment, and the device has the advantages of being compact in structure, high in heat dissipation efficiency, stable in flowing and the like.

Description

Technical Field

[0001] The present invention belongs to the field of liquid cooling and heat dissipation of electronic components, and relates to the cooling technology of high power density components in electronic control systems. Specifically, the present invention is a cold plate type liquid cooling and heat dissipation device with a coolant inlet and outlet on the same side. Through the guide rib column structure and multi-channel design in its inner cavity, the flow efficiency and heat exchange effect of the coolant are effectively improved to meet the efficient heat dissipation needs of compact electronic equipment. Background Art

[0002] In modern aviation and industrial fields, the application of multi-electric engines and distributed electronic control systems is becoming more and more widespread. The multi-electric engine is based on a non-contact magnetic bearing supporting the engine rotor and an internal integrated starter / generator installed on the engine shaft, and is equipped with a distributed electronic control system to provide electric drive for the engine and various aircraft systems. Compared with traditional mechanical transmission systems, multi-electric engines can eliminate contact rolling bearings, lubrication systems, and mechanical (hydraulic, pneumatic) actuation systems, thereby greatly reducing the weight of the engine system, reducing mechanical complexity, improving reliability and maintainability, and reducing costs.

[0003] In multi-electric engine systems, due to space and size limitations, distributed electronic control systems mostly use compact, fast-running, high-power-density electronic components, which generate a lot of heat under high load conditions. How to reasonably and effectively dissipate the heat of these high-power devices to improve their reliability is a difficult problem. Existing studies have shown that the main reason for the failure of about 55% of electronic equipment is that a large amount of heat is generated during operation, causing the temperature of the components and the surrounding environment to be too high. Generally speaking, every time the temperature of an electronic component rises by 10°C, its reliability will be reduced by 50%.

[0004] However, as the functions of electronic control systems become more and more complex, the packaging becomes more and more compact, and the heat dissipation channels become more and more crowded, the unit heat generation of the equipment increases sharply, the heat flux density increases rapidly, and the heat cannot be dissipated in time within the same period of time, resulting in the temperature of electronic components rising, the life and stability decreasing, and the failure rate greatly increasing. The heat generated by the internal components of the closed electronic controller / driver when working is mainly transferred to the bottom plate of the box by heat conduction, and then the heat is dissipated to the external environment through the radiator to achieve the purpose of cooling. As electronic equipment gradually develops towards compactness and miniaturization, the difficulty of heat dissipation is further increased. Therefore, how to ensure that electronic equipment can operate efficiently, long-term, and stably poses a huge challenge to the thermal design of electronic equipment.

[0005] In response to this demand, the current mainstream heat dissipation methods are mainly divided into two categories: air cooling and liquid cooling. The traditional air cooling method relies on air flow to take away heat, but it is difficult to meet the demand due to its low cooling efficiency and uneven heat dissipation. In contrast, the liquid cooling method uses the higher specific heat capacity and thermal conductivity of the liquid during the flow process to take away the heat. However, the traditional liquid cooling heat dissipation structure usually adopts a fixed and regular flow channel structure, with a single fluid flow path and large fluid resistance, resulting in low cooling efficiency, large pressure loss, and large energy dissipation. Because the regular flow channel limits the fluid disturbance, the flow path of the coolant in the flow channel is difficult to fully cover all heat sources, resulting in a decrease in local heat dissipation efficiency and uneven overall system temperature. At the same time, the fluid resistance of the liquid cooling system is large, which causes the coolant flow rate to decrease and the pressure loss to increase, affecting the further improvement of the cooling efficiency.

[0006] In summary, the existing electronic control systems have the characteristics of compact size and high power density, which makes the heat dissipation design more difficult. The traditional air cooling method cannot meet the needs, and the existing liquid cooling heat dissipation structure also has obvious defects in fluid resistance, pressure loss and cooling efficiency. Therefore, how to design a liquid cooling heat dissipation device with high heat exchange efficiency, low fluid resistance and compact structure to meet the efficient heat dissipation needs of multi-electric distributed electronic control systems is a technical problem that needs to be solved urgently. Summary of the invention

[0007] (I) Purpose of the invention

[0008] In view of the defects and shortcomings of the existing liquid cooling heat dissipation devices, such as low cooling efficiency, large fluid resistance, high pressure loss, and uneven heat dissipation, in order to solve at least one of the above and other technical problems in the prior art, the present invention aims to provide a cold plate type liquid cooling heat dissipation device with the coolant inlet and outlet on the same side, by setting an irregular shaped guide rib column structure in the cold plate to form a main heat dissipation channel and several branches that are approximately "C" shaped and mirror "C" shaped, so as to realize a complex flow path of the coolant. This structural design not only increases the contact area between the coolant and the heat source, but also reduces the fluid resistance and evens out the fluid pressure distribution by strengthening the fluid disturbance, thereby effectively improving the overall heat exchange efficiency, improving the cooling performance, and realizing efficient heat dissipation of high power density electronic components in a limited space.

[0009] (II) Technical solution

[0010] In order to achieve the purpose of the invention and solve the technical problems, the present invention adopts the following technical solutions:

[0011] A cold plate type liquid cooling heat dissipation device with a coolant inlet and outlet on the same side is used to achieve efficient heat dissipation of high power density electronic components, and at least includes a cold plate cavity and a liquid cooling heat dissipation guide structure arranged in the cold plate cavity. Specifically:

[0012] The cold plate cavity includes two cover plates arranged opposite to each other in the thickness direction and surrounding side walls connecting the two cover plates to form a closed cavity, at least one of the two cover plates is made of a high thermal conductivity material, and high power density electronic components are distributed on the outer wall surface thereof for conducting heat to the inside of the cold plate cavity;

[0013] A cooling liquid inlet and a cooling liquid outlet are provided on one side wall in the length or width direction of the cold plate cavity, and the cooling liquid inlet and the cooling liquid outlet are arranged at both ends in the length or width direction of the side wall in a relative arrangement, so that the cooling liquid enters from one side of the cold plate cavity, and is discharged from the same side after completing the internal circulation under the guidance of its liquid cooling heat dissipation guide structure, so as to realize the circulation of the cooling liquid in the cold plate cavity;

[0014] The heat dissipation guide structure includes a plurality of guide ribs discretely distributed in the cold plate cavity, each of the guide ribs is made of a high thermal conductivity material and is a columnar structure with an irregular cross-section, and the upper and lower ends thereof are respectively abutted and connected to the inner wall surfaces of the two cover plates, and the space between the guide ribs is formed as a coolant flow channel for guiding the coolant to circulate in the cold plate cavity;

[0015] And wherein, a plurality of discretely distributed guide ribs are roughly staggered and arranged in an S shape in the cold plate cavity, so that the coolant flow channel is spatially formed into two main heat dissipation flow paths, one approximately in a C shape and the other approximately in a mirror image C shape, and a plurality of branch heat dissipation flow paths formed by the constraints of adjacent guide ribs, and the plurality of branch heat dissipation flow paths are connected to the two main heat dissipation flow paths, and the coolant flows through a multi-channel complex path formed by the two main heat dissipation flow paths and the plurality of branch heat dissipation flow paths, forming a wide contact surface with the heat conductive cover plate of the cold plate cavity, thereby achieving uniform heat exchange and enhancing the heat exchange efficiency of the coolant.

[0016] (III) Technical Effect

[0017] Compared with the prior art, the cold plate type liquid cooling heat dissipation device with the coolant inlet and outlet on the same side of the present invention has the following beneficial and significant technical effects:

[0018] (1) The present invention achieves compactness of structure and optimization of flow channel layout by arranging the coolant inlet and outlet on the same side of the cold plate cavity. The coolant inlet and outlet are arranged at relative positions on the same side wall, so that the coolant can form a complete circulation path in the flow channel, avoiding the problems of complex coolant flow path and uneven heat dissipation in traditional designs. This design makes the coolant flow more smoothly, significantly reduces energy loss in the flow path, improves the circulation efficiency of the coolant, and thus enhances the heat dissipation performance. It is particularly suitable for electronic control systems with limited space, such as distributed electronic control systems of multiple electric engines, and effectively solves the problem of poor heat dissipation effect of traditional heat dissipation structures in limited space.

[0019] (2) The present invention adopts a staggered guide rib structure in multiple regions, and realizes the improvement of fluid disturbance and heat exchange efficiency by designing two main heat dissipation paths of approximate C shape and mirror image C shape and multiple branch heat dissipation paths. The different arrangement and spacing distribution of the guide ribs in the first region, the second region and the third region enable the coolant to maintain a uniform flow rate in each region, avoiding local heat accumulation. The design of the main flow path of approximate C shape and mirror image C shape not only enhances the flow stability of the coolant, but also ensures sufficient disturbance of the coolant in the flow channel, effectively increases the contact area between the coolant and the inner wall of the cold plate cavity, thereby realizing efficient heat exchange.

[0020] (3) The cross-sectional shape, arrangement position and spacing from the side wall of the guide ribs in the present invention are optimized to ensure that the coolant has a suitable flow rate and direction when flowing through different areas. The arrangement structure and width design of the guide ribs ensure that the coolant is fully disturbed in each area, so that the coolant can be evenly distributed and the local fluid resistance can be reduced, thereby achieving a more efficient heat dissipation effect. By setting the guide rib design with an irregular cross section, the turbulence effect of the coolant is further enhanced.

[0021] (5) The coolant flow channel design of the present invention reduces the overall structural volume and improves the stability of the structure, which is suitable for the heat dissipation requirements of high-power density electronic components. The design of the coolant flow channel reduces the overall volume of the cold plate while maintaining the heat dissipation effect through reasonable space utilization, providing a more compact heat dissipation solution for electronic equipment and increasing the available space of the equipment. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The accompanying drawings constituting a part of the present invention are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. The embodiments of the present invention are described in detail below in conjunction with the accompanying drawings, wherein:

[0023] Figure 1It is a structural schematic diagram of a cold plate type liquid cooling heat dissipation device on the same side of the coolant inlet and outlet of the present invention.

[0024] Figure 2 Schematic diagram of the position distribution of the guide ribs and the flow channel composition in an embodiment of the present invention.

[0025] Figure 3 It is a velocity distribution diagram of CFD calculation of a liquid cooling heat sink according to an embodiment of the present invention.

[0026] Figure 4 It is a pressure distribution diagram of CFD calculation of a liquid cooling heat sink according to an embodiment of the present invention.

[0027] Figure 5 It is a temperature distribution diagram of the middle section of the cold plate calculated by CFD for the liquid cooling heat sink of the present invention.

[0028] Figure 6 It is a cold plate surface temperature distribution diagram calculated by CFD for a liquid cooling heat sink according to the present invention.

[0029] Description of reference numerals:

[0030] Cold plate cavity 100, cover plate 101, inlet side wall 102, coolant inlet 103, coolant outlet 104, inlet opposite side wall 105, first length side wall 106, second length side wall 107, liquid cooling heat dissipation guide structure 200, guide rib 201, coolant flow channel 202, approximately C-shaped main heat dissipation flow path 203, mirror image C-shaped main heat dissipation flow path 204, branch heat dissipation flow path 205, guide ribs 1-37, first area I, second area II, third area III. DETAILED DESCRIPTION

[0031] In order to make the purpose, technical scheme and advantages of the implementation of the present invention clearer, the technical scheme in the embodiment of the present invention will be described in more detail below in conjunction with the drawings in the embodiment of the present invention. The described embodiments are part of the embodiments of the present invention, rather than all of the embodiments. The embodiments described below with reference to the drawings are exemplary and are intended to be used to explain the present invention, and should not be understood as limiting the present invention. Based on the embodiments in the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention.

[0032] The present invention aims to provide a cold plate type liquid cooling device with the coolant inlet and outlet on the same side, by setting an irregular shaped guide rib column structure in the cold plate to form a main heat dissipation channel and several branches that are approximately C-shaped and mirror C-shaped, so as to realize a complex flow path of the coolant. This structural design not only increases the contact area between the coolant and the heat source, but also reduces the fluid resistance and evens out the fluid pressure distribution by strengthening the fluid disturbance, thereby effectively improving the overall heat exchange efficiency, improving the cooling performance, and realizing efficient heat dissipation of high power density electronic components in a limited space.

[0033] As a specific example, Figure 1 , 2 As shown, the cold plate type liquid cooling heat dissipation device provided by the embodiment of the present invention on the same side of the coolant inlet and outlet is mainly composed of a cold plate cavity 100 and a liquid cooling heat dissipation guide structure 200 arranged in the cold plate cavity 100. Among them, the cold plate cavity 100 includes two cover plates 101 arranged opposite to each other in the thickness direction and surrounding side walls (102, 105-107, etc.) connecting the two cover plates and forming a closed cavity. Specifically, the surrounding side walls of the cold plate cavity 100 include an inlet side wall 102, an inlet opposite side wall 105, a first length side wall 106 and a second length side wall 107, and the two cover plates 101 are respectively arranged at the upper and lower sides of the cold plate cavity. At least one of the two cover plates 101 is made of a high thermal conductivity material (preferably made of a high thermal conductivity material with a thermal conductivity coefficient of not less than 150W / m·K, and preferably made of copper, aluminum or its alloy material), and high power density electronic components are distributed on the outer wall surface thereof to conduct heat to the inside of the cold plate cavity 100. A cooling liquid inlet 103 and a cooling liquid outlet 104 are provided on a side wall (for example, the inlet side wall 102) in the length or width direction of the cold plate cavity 100, and the cooling liquid inlet 103 and the cooling liquid outlet 104 are arranged at both ends of the length or width direction of the side wall in a relative arrangement, so that the cooling liquid enters from one side of the cold plate cavity 100, and is discharged from the same side after completing the internal circulation under the guidance of the liquid-cooled heat dissipation guide structure 200, thereby realizing the circulation of the cooling liquid in the cold plate cavity 100.

[0034] The heat dissipation guide structure 200 includes a plurality of guide ribs 201 discretely distributed in the cold plate cavity 100, each guide rib 201 is made of a high thermal conductivity material (preferably a high thermal conductivity material with a thermal conductivity coefficient of not less than 150 W / m·K, and a surface roughness Ra of not more than 1.6 μm), and is structurally a columnar structure with an irregular cross-section, and its upper and lower ends are respectively connected to the inner wall surfaces of the two cover plates 101, and the space between each guide rib 201 forms a coolant flow channel 202 for guiding the coolant to circulate inside the cold plate cavity 100. And wherein, a plurality of discretely distributed guide ribs 201 are arranged roughly in an S-shape in an alternating manner in the cold plate cavity 100, so that the coolant flow channel 202 is spatially formed into two main heat dissipation flow paths 203 and 204, one approximately in a C-shape and the other approximately in a mirror-image C-shape, and a plurality of branch heat dissipation flow paths 205 constrained by adjacent guide ribs 201, and the plurality of branch heat dissipation flow paths 205 connect the two main heat dissipation flow paths 203 and 204, and the coolant flows through a multi-channel complex path formed by the two main heat dissipation flow paths 203 and 204 and the plurality of branch heat dissipation flow paths 205, forming a wide contact surface with the heat conductive cover plate 101 of the cold plate cavity 100, thereby achieving uniform heat exchange and enhancing the heat exchange efficiency of the coolant.

[0035] In the cold plate type liquid cooling heat sink of the present invention, the coolant inlet and outlet are located on the same side of the heat sink. The coolant inlet and outlet are arranged on the same side wall, which reduces the overall structural volume of the device and contributes to the compact design of the fluid flow path. The central axes of the inlet and outlet are parallel and coplanar, so that the coolant is evenly distributed in the cavity, avoiding the occurrence of local overheating and further improving the heat dissipation performance.

[0036] Preferably, the coolant inlet 103 and the coolant outlet 104 are arranged on the inlet side wall 102 extending in the width direction of the cold plate cavity 100, and are arranged at both ends of the width side wall 102 in a relative arrangement, and the central axes of the coolant inlet 103 and the coolant outlet 104 both extend in the length direction, and the central axes of the two are parallel to each other and coplanar with the horizontal center plane of the cold plate cavity 100, so as to optimize the coolant flow path and ensure that the coolant can be evenly distributed throughout the cold plate cavity 100.

[0037] In the cold plate type liquid cooling heat dissipation device of the present invention, Figure 1 As shown, the heat dissipation guide structure 200 is mainly composed of two main heat dissipation paths of approximately C shape and mirror image C shape formed by staggered arrangement of a plurality of irregular shaped guide ribs 201 and a plurality of branches. Specifically, the guide ribs 201 are staggered in an S shape in the cold plate cavity 100, and are roughly divided into three areas according to their arrangement, such as Figure 2 As shown:

[0038] The guide ribs 1 to 14, 37 in the first region I are arranged along the length direction of the cold plate cavity 100, from a position close to the inlet side wall 102 to a position close to the inlet opposite side wall 105, and the space between them and the first length side wall 106 forms the first part of the mirror image C-shaped main heat dissipation flow path, and the first length side wall 106 is located outside the coolant inlet 103 in the width direction and extends in the length direction;

[0039] The guide ribs 24 to 33 in the second region II are arranged along the length direction of the cold plate cavity 100 from a position close to the inlet opposite side wall 105 to a position close to the inlet side wall 102, and the space between the guide ribs 24 to 33 and the second length side wall 107 forms a first part of a substantially C-shaped main heat dissipation flow path, and the second length side wall 107 is located outside the coolant outlet 104 in the width direction and extends in the length direction;

[0040] The guide ribs 15 to 23 in the third region III are arranged from the tail guide rib 14 in the first region I to the tail guide rib 24 in the second region II, and the spaces between the guide ribs 1 to 14 and 37 in the first region I form the second part of the mirrored C-shaped main heat dissipation flow path, and the spaces between the guide ribs 24 to 33 in the second region II form the second part of the approximate C-shaped main heat dissipation flow path.

[0041] Preferably, the middle position of the approximately C-shaped flow channel is connected to the cold plate outlet, and one end of the mirror image C shape is connected to the inlet. Specifically, the first part and the second part of the approximately C-shaped main heat dissipation flow path 203 converge at the vertex position thereof, and are connected to the coolant outlet 104 through the flow path, and one end of the first part of the mirror image C-shaped main heat dissipation flow path 204 is directly connected to the coolant inlet 103, so that after the coolant enters the cold plate cavity 100, it first flows along the first part of the mirror image C-shaped main heat dissipation flow path 204 and each branch heat dissipation flow path 205 connected thereto, and then flows through the second part of the mirror image C-shaped main heat dissipation flow path 204 and each branch heat dissipation flow path 205 connected thereto, and is divided to the first part and the second part of the approximately C-shaped main heat dissipation flow path 203, and finally converges at the vertex position of the approximately C-shaped main heat dissipation flow path 203 and is discharged, forming a flow path with a relatively small overall flow resistance.

[0042] Further preferably, in the first region I, the guide ribs 1, 37 at the head end are arranged adjacent to the inlet side wall 102, and there is a first spacing between the guide ribs 14 at the tail end and the opposite side wall 105 of the inlet, and the first spacing is several times the average width of the branch heat dissipation flow path 205, and each of the guide ribs 1 to 14, 37 in the region is located on the inner side of the coolant inlet 103 in the width direction and is arranged relative to the first length side wall 106, and there is a second spacing between each of the guide ribs 1 to 14, 37 and the first length side wall 106, and the second spacing is several times the average width of the branch heat dissipation flow path 205, and gradually increases from the inlet side wall 102 along the length direction, forming a spacing distribution from narrow to wide, and the second spacing is comparable in size to the first spacing.

[0043] For the second region II, the guide rib 33 at the head end is arranged near the side wall 105 opposite to the inlet, and there is a third spacing between the guide rib 24 at the tail end and the inlet side wall 102, and the third spacing is several times the average width of the branch heat dissipation flow path 205, and each guide rib (24~33) in this region is located on the inner side of the coolant outlet 104 in the width direction and is arranged relative to the second length side wall 107, and there is a fourth spacing between each guide rib (24~33) and the second length side wall 107, and the fourth spacing is several times the average width of the branch heat dissipation flow path 205, and the fourth spacing is equivalent to the third spacing.

[0044] In the third region III, for the second part of the mirror image C-shaped main heat dissipation flow path, its width gradually decreases along the flow direction to form a main flow path width distribution from wide to narrow, thereby controlling the coolant flow rate and increasing the fluid disturbance to enhance the heat exchange effect. For the second part of the approximately C-shaped main heat dissipation flow path, its flow path width gradually increases along the flow direction to form a main flow path width distribution from narrow to wide, so as to slow down the coolant flow rate and allow it to have a longer residence time before the outlet to fully contact the wall.

[0045] In addition, preferably, a first transition guide rib 34 is provided at the corner between the inlet opposite side wall 105 and the first length side wall 106, and a second transition guide rib 35 is provided at the corner between the inlet opposite side wall 105 and the second length side wall 107, which are used to guide the coolant to turn smoothly at the corner to avoid turbulence or a sharp change in flow rate of the coolant here, thereby maintaining the stability of the flow; a third transition guide rib 36 is provided on the inlet side wall 102, which is opposite to the outlet of the second part of the approximately C-shaped main heat dissipation flow path, and is used to control the direction and speed of the coolant flow, ensure that the coolant is smoothly guided to the coolant outlet 104, and at the same time enhance the heat exchange effect with the outlet flow path.

[0046] Preferably, the cross-section of the guide rib 201 is irregularly shaped, and generally includes a first type of guide rib and a second type of guide rib, wherein the cross-section of the first type of guide rib is approximately elliptical, and the cross-section of the second type of guide rib is long strip-shaped, and the staggered arrangement of the first type of guide rib and the second type of guide rib forms a coolant flow channel 202 with different flow channel widths, thereby realizing local regulation of the coolant flow rate and improving the heat exchange efficiency.

[0047] Preferably, the branch heat dissipation flow path 205 includes a Y-shaped branch flow channel, a herringbone branch flow channel and a parallel branch flow channel, wherein the Y-shaped branch flow channel is formed by setting an approximately elliptical guide rib column 6 between two long strip guide rib columns 5 and 7, the herringbone branch flow channel is formed by three approximately elliptical guide rib columns 8, 9, and 10 of equivalent size, and the parallel branch flow channel is formed by two parallel long strip guide rib columns. Uniform distribution of coolant is achieved through the combination of various forms of branch flow channels.

[0048] Specifically, if Figure 2 As shown, in the first region I, the approximately elliptical flow guide ribs 1 and 2 are arranged up and down, located at the inlet, and form a branch with the cold plate inlet. Ribs 3 and 4 are arranged up and down, located on the right side of ribs 1 and ribs 2, forming another branch. The approximately elliptical rib 6 is placed between the long strip ribs 5 and ribs 7 to form a Y-shaped branch flow channel. The approximately elliptical ribs 8, ribs 9, and ribs 10 are distributed in a "pin" shape. Ribs 1 to 14 and the bottom wall of the heat sink form half of the mirror image C-shaped main channel. Similarly, the space between ribs 15 to ribs 23 in the third region III and ribs 24 to ribs 33 in the second region II forms the other half of the mirror image C-shaped main channel. Ribs 24 to ribs 33 in the second region II and the top wall of the heat sink (i.e., the second length side wall 107) form half of the C-shaped main channel. The space between the ribs 1 to 14 in the first region I and the ribs 15 to 23 in the third region III forms the other half of the C-shaped main flow channel.

[0049] Example 2

[0050] As a further specific example, the cold plate liquid cooling device provided by the present invention adopts an optimized flow channel design to improve the cooling effect of high power density electronic components. The cold plate liquid cooling device of this embodiment has a length of 204mm, a width of 100mm, a thickness of 7mm, a width of 6mm for the inlet and outlet pipes, a fluid cooling medium of water, a cooling fluid temperature of 20°C, a cold plate inlet flow rate of 2m / s, and a heat flux of 100W / cm 2 After CFD calculation, the cold plate has high heat exchange efficiency, small fluid resistance and uniform pressure distribution, which proves that the cold plate achieves high heat exchange efficiency and uniform pressure distribution under small fluid resistance.

[0051] In the specific implementation process, Figure 3 The CFD calculation results of the coolant velocity distribution in the cold plate are shown. Figure 3 It can be seen that the coolant flows along the approximately C-shaped and mirror-image C-shaped main heat dissipation flow paths inside the cold plate cavity. Due to the staggered layout design of the main flow path and the branch flow path, the coolant forms a complex flow path when flowing through the space between the guide ribs, thereby enhancing the fluid disturbance while ensuring the stability of the coolant flow rate. The flow velocity distribution diagram shows that after the coolant enters the main channel, the flow velocity gradually stabilizes, avoiding the phenomenon of excessively fast or slow local flow velocities, which helps to improve the heat exchange efficiency.

[0052] Figure 4 The pressure distribution in the cold plate cavity is shown. As can be seen from the figure, the pressure distribution of the coolant in the entire flow channel is uniform, and the transition guide ribs 34 and 35 at the corners effectively guide the flow of the coolant, avoiding turbulence at the corners and reducing the pressure drop of the fluid. In addition, the coolant maintains a stable pressure distribution when flowing through each area, further reducing the fluid resistance of the coolant inside the cold plate, so that the cooling system can achieve efficient cooling effect at a lower pressure.

[0053] From the temperature field distribution (such as Figure 5 As shown in the figure, when the coolant flows through the cavity, it evenly absorbs the heat generated by the cold plate wall. In the two parts of the approximate C-shaped and mirror C-shaped flow paths, the temperature distribution is relatively uniform, and there is no significant local temperature rise phenomenon, indicating that the coolant can effectively remove the heat generated by high-power density electronic components. This uniform temperature distribution further verifies the advantages of the flow channel structure design provided by the present invention in terms of heat exchange efficiency.

[0054] Figure 6 The figure shows the temperature distribution on the cold plate surface. As can be seen from the figure, the temperature distribution on the cold plate surface is relatively uniform, indicating that the coolant can effectively remove the heat from the surface when flowing through the cold plate. Especially in the high heat flux area, the coolant achieves efficient heat dissipation through complex flow paths and staggered guide ribs, further improving the overall cooling performance of the cold plate.

[0055] In general, the cold plate type liquid cooling device of the present invention achieves efficient heat exchange while maintaining low fluid resistance and uniform pressure distribution through optimized flow channel design, making the flow of coolant in the cold plate cavity more stable and uniform. This design not only improves the cooling efficiency, but also effectively reduces the temperature rise problem caused by insufficient heat dissipation of high power density electronic components during operation, thereby extending the service life of the electronic components.

[0056] Through the above embodiments, the purpose of the present invention is fully and effectively achieved. Those skilled in the art can understand that the present invention includes but is not limited to the contents described in the drawings and the above specific embodiments. Although the present invention has been described with respect to the most practical and preferred embodiments currently considered, it should be understood that the present invention is not limited to the disclosed embodiments, and any modification that does not deviate from the functional and structural principles of the present invention will be included in the scope of the claims.

Claims

1. A cold plate type liquid cooling heat dissipation device with a cooling liquid inlet and outlet on the same side, comprising at least a cold plate cavity and a liquid cooling heat dissipation guide structure arranged in the cold plate cavity, characterized in that: The cold plate cavity includes two cover plates arranged opposite to each other in the thickness direction and surrounding side walls connecting the two cover plates to form a closed cavity, at least one of the two cover plates is made of a high thermal conductivity material, and high power density electronic components are distributed on the outer wall surface thereof for conducting heat to the inside of the cold plate cavity; A cooling liquid inlet and a cooling liquid outlet are provided on one side wall in the length or width direction of the cold plate cavity, and the cooling liquid inlet and the cooling liquid outlet are arranged at both ends in the length or width direction of the side wall in a relative arrangement, so that the cooling liquid enters from one side of the cold plate cavity, and is discharged from the same side after completing the internal circulation under the guidance of its liquid cooling heat dissipation guide structure, so as to realize the circulation of the cooling liquid in the cold plate cavity; The heat dissipation guide structure includes a plurality of guide ribs discretely distributed in the cold plate cavity, each of the guide ribs is made of a high thermal conductivity material and is a columnar structure with an irregular cross-section, and the upper and lower ends thereof are respectively abutted and connected to the inner wall surfaces of the two cover plates, and the space between the guide ribs is formed as a coolant flow channel for guiding the coolant to circulate in the cold plate cavity; And wherein, a plurality of discretely distributed guide ribs are roughly staggered and arranged in an S shape in the cold plate cavity, so that the coolant flow channel is spatially formed into two main heat dissipation flow paths, one approximately in a C shape and the other approximately in a mirror image C shape, and a plurality of branch heat dissipation flow paths formed by the constraints of adjacent guide ribs, and the plurality of branch heat dissipation flow paths are connected to the two main heat dissipation flow paths, and the coolant flows through a multi-channel complex path formed by the two main heat dissipation flow paths and the plurality of branch heat dissipation flow paths, forming a wide contact surface with the heat conductive cover plate of the cold plate cavity, thereby achieving uniform heat exchange and enhancing the heat exchange efficiency of the coolant.

2. The cold plate type liquid cooling heat dissipation device with the coolant inlet and outlet on the same side as claim 1, characterized in that: The coolant inlet and the coolant outlet are arranged on a side wall of the cold plate cavity extending in the width direction, and are arranged at both ends of the width side wall in a relatively arranged manner, and the central axes of the coolant inlet and the coolant outlet both extend in the length direction, and the central axes of the two are parallel to each other and coplanar with the horizontal center plane of the cold plate cavity, so as to optimize the coolant flow path and ensure that the coolant can be evenly distributed throughout the cold plate cavity.

3. The cold plate type liquid cooling heat dissipation device with the coolant inlet and outlet on the same side as claim 1, characterized in that: The guide ribs are arranged in an S-shape in a staggered manner in the cold plate cavity, and are roughly divided into three areas according to their arrangement, wherein: The guide ribs in the first region I are arranged along the length direction of the cold plate cavity, from a position close to the inlet side wall to a position close to the opposite side wall of the inlet, and the space between the guide ribs and the first length side wall forms a first part of a mirror image C-shaped main heat dissipation flow path, and the first length side wall is located outside the coolant inlet in the width direction and extends in the length direction; The guide ribs in the second region II are arranged along the length direction of the cold plate cavity from a position close to the side wall opposite to the inlet to a position close to the side wall of the inlet, and the space between the guide ribs and the second length side wall forms a first part of a substantially C-shaped main heat dissipation flow path, and the second length side wall is located outside the coolant outlet in the width direction and extends in the length direction; The guide ribs in the third area III are arranged from the tail guide ribs in the first area I to the tail guide ribs in the second area II, and the space between them and the guide ribs in the first area I forms the second part of the mirrored C-shaped main heat dissipation flow path, and the space between them and the guide ribs in the second area II forms the second part of the approximate C-shaped main heat dissipation flow path.

4. The cold plate type liquid cooling heat dissipation device with the coolant inlet and outlet on the same side as claim 3, characterized in that: The first part and the second part of the approximately C-shaped main heat dissipation flow path converge at the vertex position thereof and are connected to the coolant outlet. One end of the first part of the mirror image C-shaped main heat dissipation flow path is directly connected to the coolant inlet, so that after the coolant enters the cold plate cavity, it first flows along the first part of the mirror image C-shaped main heat dissipation flow path and the branch heat dissipation flow paths connected thereto, then flows through the second part of the mirror image C-shaped main heat dissipation flow path and the branch heat dissipation flow paths connected thereto, and is diverted to the first part and the second part of the approximately C-shaped main heat dissipation flow path, and finally converges at the vertex position of the approximately C-shaped main heat dissipation flow path and is discharged, forming a flow path with a relatively small overall flow resistance.

5. The cold plate type liquid cooling heat dissipation device with the coolant inlet and outlet on the same side as claim 3 or 4, characterized in that: In the first region I, the guide ribs at the head end are arranged close to the inlet side wall, and there is a first spacing between the guide ribs at the tail end and the opposite side wall of the inlet, and the first spacing is several times the average width of the branch heat dissipation flow path, and each guide rib in the region is located on the inner side of the coolant inlet in the width direction and is arranged relative to the first length side wall, and there is a second spacing between each guide rib and the first length side wall, and the second spacing is several times the average width of the branch heat dissipation flow path, and gradually increases from the inlet side wall along the length direction, forming a spacing distribution from narrow to wide, and the second spacing is comparable to the first spacing.

6. The cold plate type liquid cooling and heat dissipation device with the coolant inlet and outlet on the same side as claim 3 or 4, characterized in that: In the second region II, the guide ribs at the head end are arranged near the side wall opposite to the inlet, and there is a third spacing between the guide ribs at the tail end and the side wall of the inlet, and the third spacing is several times the average width of the branch heat dissipation flow path, and each guide rib in this region is located on the inner side of the coolant outlet in the width direction and is arranged relative to the second length side wall, and there is a fourth spacing between each guide rib and the second length side wall, and the fourth spacing is several times the average width of the branch heat dissipation flow path, and the fourth spacing is comparable to the third spacing.

7. The cold plate type liquid cooling heat dissipation device with the coolant inlet and outlet on the same side as claim 3 or 4, characterized in that: In the third region III, for the second part of the mirror image C-shaped main heat dissipation flow path, its width gradually decreases along the flow direction to form a main flow path width distribution from wide to narrow, thereby controlling the coolant flow rate and increasing the fluid disturbance to enhance the heat exchange effect. For the second part of the approximately C-shaped main heat dissipation flow path, its flow path width gradually increases along the flow direction to form a main flow path width distribution from narrow to wide, so as to slow down the coolant flow rate and allow it to have a longer residence time before the outlet to fully contact the wall.

8. The cold plate type liquid cooling heat dissipation device with the coolant inlet and outlet on the same side as claim 3 or 4, characterized in that: A first transition guide rib is provided at the corner between the inlet opposite side wall and the first length side wall, and a second transition guide rib is provided at the corner between the inlet opposite side wall and the second length side wall, which are used to guide the coolant to turn smoothly at the corner to avoid turbulence or a sharp change in flow rate of the coolant here, thereby maintaining the stability of the flow; a third transition guide rib is provided on the inlet side wall, which is directly opposite to the outlet of the second part of the approximately C-shaped main heat dissipation flow path, and is used to control the direction and speed of the coolant flow to ensure that the coolant is smoothly guided to the coolant outlet.

9. The cold plate type liquid cooling and heat dissipation device with the coolant inlet and outlet on the same side as claim 1, characterized in that: The cross-section of the guide ribs is irregular in shape, and generally includes a first type of guide ribs and a second type of guide ribs, wherein the cross-section of the first type of guide ribs is approximately elliptical, and the cross-section of the second type of guide ribs is long strip-shaped, and the staggered arrangement of the first type of guide ribs and the second type of guide ribs forms coolant flow channels with different flow channel widths, thereby realizing local regulation of the coolant flow rate and improving the heat exchange efficiency.

10. The cold plate type liquid cooling and heat dissipation device with the coolant inlet and outlet on the same side as claim 1, characterized in that: The branch heat dissipation flow path includes a Y-shaped branch flow channel, a herringbone branch flow channel and a parallel branch flow channel, wherein the Y-shaped branch flow channel is formed by setting an approximately elliptical guide rib column between two long strip guide rib columns, the herringbone branch flow channel is formed by three approximately elliptical guide rib columns of equivalent size, and the parallel branch flow channel is formed by two parallel long strip guide rib columns. Uniform distribution of coolant is achieved through the combination of various forms of branch flow channels.

Images