Hybrid rectification-discontinuous liquid cooling plate based on field synergy principle

Abstract

The invention discloses a mixed type rectification-discontinuous liquid cooling plate based on a field synergy principle, and belongs to the technical field of liquid cooling heat dissipation, the mixed type rectification-discontinuous liquid cooling plate comprises a liquid cooling plate main body, the inlet end of the liquid cooling plate main body is provided with a rectangular splitter for rectifying incoming flow, and eddy current and bias current are eliminated; a central main channel of the liquid cooling plate main body adopts a discontinuous fin with a flow guide strip, a gap of the discontinuous fin is communicated with secondary flow channels on two sides, a low-pressure area is formed at the gap to entrain low-speed fluid to generate transverse secondary flow, and'peak clipping and valley filling 'type redistribution of flow is realized; inclined flow guide strips are continuously arranged on the surfaces of all the fins, and heat exchange is continuously enhanced and resistance increase is inhibited by utilizing a three-field synergy principle; smooth series connection between the multiple stages of cold plates is achieved through the fillet transition flow guide pipes. The mixed rectification-discontinuous liquid cooling plate has low voltage drop, high uniform temperature and high reliability, is simple in structure, and is easy for batch manufacturing and multi-stage expansion.

Description

Technical Field

[0001] This invention belongs to the field of liquid cooling technology, specifically relating to a hybrid rectifier-intermittent liquid cooling plate based on the principle of field synergy. Background Technology

[0002] With the large-scale application of wide-bandgap semiconductor devices such as SiC / GaN, the power density of equipment such as motor controllers and server power supplies continues to rise, leading to a sharp increase in heat flux per unit area. Traditional air cooling or aluminum extruded heat sinks, due to their limited heat transfer limits, can no longer meet the temperature control requirements of next-generation electronic devices. Liquid cooling plates, with their high-efficiency heat transfer capabilities, are gradually becoming the mainstream solution.

[0003] There are two main types of liquid cooling plate flow channels: 1. The S-shaped continuous bend flow channel enhances heat transfer by extending the flow path.

[0004] 2. Parallel multi-branch flow channels can shorten the flow rate and reduce pressure drop.

[0005] 3. To further improve heat exchange performance, the industry generally adds fins or micro-ribs to the flow channel.

[0006] However, existing liquid cooling plates have four common problems: 1. While S-shaped continuous bend flow channels can extend the heat exchange path and improve heat dissipation capacity, they also bring excessive friction and local resistance, resulting in high pump power requirements. On the other hand, parallel multi-branch flow channels significantly reduce pressure drop, but due to the shortened flow path and manifold effect, the heat exchange area is compressed, making it easy for areas with insufficient heat exchange to appear. How to achieve a balance between "low pressure drop" and "high uniform temperature" is a key challenge in flow channel topology design.

[0007] 2. In a parallel multi-branch cooling plate, the fluid tends to flow along the central channel, which is closest to the inlet and has the lowest resistance, resulting in excess flow in the central region and insufficient flow in the side branches. This imbalance in distribution, characterized by "insufficient peak shaving and insufficient valley filling," not only wastes cooling resources but also causes the temperature of peripheral power devices to exceed the limit, severely restricting the overall thermal reliability of the system.

[0008] 3. Conventional fins only aim to increase the heat transfer area, failing to fully utilize the synergistic theory of the "velocity field-temperature gradient field-pressure gradient field". This results in an exponential increase in resistance while the heat transfer coefficient increases. In high heat flux density scenarios, the rapid increase in resistance and pump work not only weakens the system's energy efficiency but also limits the engineering implementation of heat dissipation solutions.

[0009] 4. The lack of a flow-rectifying structure at the fin inlet causes eddies and flow deviations in the coolant as it enters the liquid-cooled plate manifold due to sudden changes in flow velocity, cross-sectional expansion, and geometric asymmetry. This results in significant flow differences in downstream branch channels. This non-uniformity can directly lead to insufficient cooling in some branches, excessive local temperature rise, and the formation of unacceptable hot spots.

[0010] Therefore, how to achieve uniform flow distribution while reducing pressure drop, and maximize the local heat transfer coefficient of the fins based on the field synergy principle, has become a technical bottleneck that high power density liquid cooling plates urgently need to overcome. Summary of the Invention

[0011] Based on the problems existing in the above-mentioned background technology, the present invention proposes a hybrid rectifier-intermittent liquid cooling plate based on the field cooperation principle, which solves the problem that existing liquid cooling plates cannot achieve uniform flow distribution while reducing pressure drop.

[0012] The embodiments of the present invention are implemented as follows: The present invention provides a hybrid rectifier-intermittent liquid cooling plate based on the field cooperation principle, which includes at least one liquid cooling plate body. The liquid cooling plate body is provided with a coolant inlet pipe and a coolant outlet pipe along the coolant flow direction. The liquid cooling plate body is provided with multiple rectangular flow dividers and multiple fins. The multiple rectangular flow dividers are inclined near the coolant inlet pipe and uniformly divide the coolant into several sub-jet streams. The multiple fins are arranged along the coolant flow direction. The several sub-jet streams flow through the multiple fins for heat exchange and then flow out through the coolant outlet pipe.

[0013] Furthermore, the axes of the coolant inlet pipe and the coolant outlet pipe coincide with the center line of the liquid cooling plate body. The middle position of the liquid cooling plate body is the central main channel, and the two sides of the central main channel are secondary flow channels.

[0014] Furthermore, multiple guide strips are obliquely arranged on both sides of each fin, and the multiple guide strips are arranged along the length direction of the fin; the multiple guide strips on both sides of each fin are alternately distributed, and the middle part of each guide strip is a semi-circular protrusion.

[0015] Furthermore, the height of the central protrusion of each guide bar is 1.5mm to 2.5mm, and the inclination angle of each guide bar is the acute angle between the guide bar and the length direction of the fin. The inclination angle of the guide bar ranges from 55° to 75°.

[0016] Furthermore, the multiple fins are evenly spaced along the coolant flow direction, with the spacing between adjacent fins being 1.8mm to 3.2mm.

[0017] Furthermore, the coolant inlet pipe is connected to the liquid cooling plate body through the liquid cooling plate inlet manifold. One end of the liquid cooling plate inlet manifold is a round opening, and the other end is a rectangular opening. The round opening of the liquid cooling plate inlet manifold is fixedly connected to the coolant inlet pipe, and the rectangular opening of the liquid cooling plate inlet manifold is fixedly connected to the liquid cooling plate body. The length of the leading edge of the multiple rectangular diverter plates is less than the length of the rectangular opening.

[0018] Furthermore, the coolant outlet pipe is connected to the liquid cooling plate body through the liquid cooling plate outlet manifold. One end of the liquid cooling plate outlet manifold is a round opening, and the other end is a rectangular opening. The round opening of the liquid cooling plate outlet manifold is fixedly connected to the coolant outlet pipe, and the rectangular opening of the liquid cooling plate outlet manifold is fixedly connected to the liquid cooling plate body.

[0019] Furthermore, the multiple fins within the central main channel are all intermittent fins, which are segmented and cut off along the coolant flow direction to form several gaps.

[0020] Furthermore, there are multiple liquid cooling plate bodies, with the first liquid cooling plate body having a coolant inlet pipe and the last liquid cooling plate body having a coolant outlet pipe. The multiple liquid cooling plate bodies in the middle are connected by guide pipes to form a multi-stage continuous heat dissipation system.

[0021] The basic principle of the hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle in this invention is as follows: after the coolant enters the main body of the liquid cooling plate from the coolant inlet pipe, it goes through the following 7 stages to complete rectification, flow equalization, enhanced heat transfer and multi-stage circulation.

[0022] 1. Wall-attached circulation formation stage: The coolant enters the liquid-cooled plate inlet manifold from the coolant inlet pipe in a vertical jet state. It first impacts the wall of the liquid-cooled plate inlet manifold, and after being blocked by the wall, it quickly spreads outward, forming a wall-attached circulation along the wall of the liquid-cooled plate inlet manifold. During the wall-attaching process, the local flow velocity is rapidly reduced by the wall friction, and some of the initial turbulent kinetic energy is dissipated, effectively weakening the large-scale vortex brought by the inlet jet.

[0023] 2. Frontal Impact Stage with Rectangular Diverter Plates: After traveling a certain distance along the wall, the circulating flow encounters multiple inclined rectangular diverter plates head-on. The leading edges of the rectangular diverter plates uniformly split the circulating flow into several jets. Each jet continues to advance within the gradually expanding channel formed by the rectangular diverter plates and the liquid-cooled plate walls. The channel cross-section gradually expands, the fluid velocity further decreases, the static pressure gradually increases, and the flow direction is forcibly adjusted to be parallel to the downstream channel axis.

[0024] 3. Sub-jet Rectification Stage: The sub-jet continues to diffuse within the gradually expanding channel formed by the trailing edge of the rectangular splitter and the wall of the liquid-cooled plate. Due to the continuous expansion of the channel cross-section, the fluid velocity gradient decreases, turbulent pulsations are further suppressed, and the velocity differences between the sub-jet streams are quickly smoothed out, forming a uniform low-velocity laminar or weakly turbulent state, providing uniform inlet conditions for subsequent entry into the finned area. After being rectified by multiple rectangular splitters, the uniform fluid layer then smoothly transitions to the subsequent finned area, completing the entire inlet rectification process.

[0025] 4. Low-Pressure Zone Formation Stage: After being rectified by the coolant inlet pipe and rectangular flow dividers, the coolant enters the narrow main heat exchange channel, which is composed of multiple fins and the liquid-cooled plate wall, at a relatively uniform speed. At this point, except for the slightly higher flow rate at the central main channel, the flow rates in the other branches have become consistent, and the overall distribution is relatively uniform. The fins at the central main channel are replaced with intermittent fins, which are segmented along the flow direction to form several gaps. The two sides of the gaps are directly connected to the secondary flow channels. The sudden expansion of the cross-section at the gaps causes a sharp drop in local static pressure, forming a significant low-pressure zone.

[0026] 5. Formation and Mixing of Lateral Secondary Flow: Due to the presence of the low-pressure zone at the gap, the coolant with relatively low flow velocity in the secondary flow channels on both sides is rapidly drawn into the mainstream, generating a strong lateral secondary flow. This lateral flow passes through the gap in a direction approximately perpendicular to the mainstream, and mixes violently with the high-speed fluid in the center, redistributing the excess momentum originally concentrated in the middle flow channel to the adjacent branches, forming a "peak shaving and valley filling" type flow rebalancing.

[0027] 6. Enhanced Heat Transfer through Guide Strip Synergy: The guide strips extend continuously at an angle along the surfaces of both continuous and discontinuous fins, starting from the coolant inlet pipe. Their angle of inclination forms a fixed angle of attack with the mainstream direction, causing the fluid close to the fin wall to be periodically cut, lifted, and reattached behind each guide strip, forming dense transverse secondary vortices. These secondary vortices continuously pull the high-speed core fluid towards the wall while simultaneously drawing the high-temperature fluid from the wall towards the mainstream, continuously thinning the thermal boundary layer and increasing turbulence intensity. This ensures that the velocity vector and temperature gradient vector maintain a high degree of synergy throughout the entire heat transfer channel. When the coolant passes through the gaps in the discontinuous fins, the transverse secondary flow and the secondary vortices induced by the guide strips superimpose, further promoting the mixing of hot and cold fluids. This ensures that the flow after redistribution maintains a high convective heat transfer coefficient, suppresses local thermal resistance growth, and achieves efficient heat dissipation throughout the entire process.

[0028] 7. Multi-stage series continuous heat dissipation: After the coolant smoothly leaves the first cold plate by bending along the continuous rounded corners of the guide tube, there is no sudden contraction or separation, and it maintains the flow close to the wall. Then it directly enters the inlet manifold of the next cold plate, and once again impacts the rectangular splitter vanes for rectification. It flows through the fins and intermittent fins to complete field-coordinated heat exchange and flow redistribution, and then turns through the guide tube to enter the subsequent cold plates. This cycle continues until it finally flows out through the coolant outlet pipe, realizing multi-stage series continuous heat dissipation.

[0029] Compared with existing liquid cooling plates, the advantages of this invention are: This invention provides a hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle. By incorporating rectangular flow dividers and fins, it adjusts the turbulent incoming flow into a uniform initial field with a highly consistent velocity-temperature gradient. The liquid cooling plate's main body features a central main channel and secondary flow channels. By expanding the flow area and reducing bends, it maintains full coverage heat transfer over the heating zone while lowering the overall pressure drop. Optimized flow guides are introduced on the fin surfaces to increase the field synergy angle through local flow guidance, significantly improving the heat transfer coefficient while controlling resistance growth for the same pump power. The fins in the central main channel are intermittent, with several notches that couple with the secondary flow channels on both sides of the liquid cooling plate. These notches induce lateral secondary flow, achieving a "peak-shaving and valley-filling" flow redistribution and fundamentally eliminating local hot spots. This hybrid rectifier-intermittent liquid cooling plate, with its integrated structure, simultaneously achieves three major goals: homogenized inlet flow field, low-resistance and high-efficiency heat transfer throughout the entire process, and uniform temperature across the entire domain. This provides highly reliable and low-energy-consumption heat dissipation for next-generation high-power-density power electronic devices. Attached Figure Description

[0030] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly described below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort. The above and other objects, features, and advantages of the present invention will become clearer through the accompanying drawings. The same reference numerals indicate the same parts in all the drawings. The drawings are not intentionally drawn to scale to actual dimensions; the focus is on illustrating the main points of the invention.

[0031] Figure 1 This is a schematic diagram of the planar structure of a hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle.

[0032] Figure 2 This is a three-dimensional structural diagram of a hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle.

[0033] Figure 3 This is a three-dimensional structural diagram of the guide strip.

[0034] Figure 4 This is a side view of the guide strip structure.

[0035] The components are as follows: 1. Liquid cooling plate body; 2. Coolant inlet pipe; 3. Coolant outlet pipe; 4. Rectangular flow divider; 5. Fins; 6. Central main channel; 7. Guide strips; 8. Liquid cooling plate inlet manifold; 9. Liquid cooling plate outlet manifold; 10. Intermittent fins; 11. Guide pipes. Detailed Implementation

[0036] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The components of the embodiments of the present invention described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0037] Therefore, the following detailed description of the embodiments of the invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the invention without inventive effort are within the scope of protection of the invention.

[0038] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0039] Furthermore, the terms "first," "second," etc., are used only to distinguish descriptions and should not be interpreted as indicating or implying relative importance.

[0040] Please refer to Figures 1-2 As shown, this invention provides a hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle, comprising four liquid cooling plate bodies 1, which are horizontally spaced and evenly arranged. The rightmost liquid cooling plate body 1 is provided with a coolant inlet pipe 2 and a liquid cooling plate inlet manifold 8, while the leftmost liquid cooling plate body 1 is provided with a liquid cooling plate outlet manifold 9 and a coolant outlet pipe 3. The four liquid cooling plate bodies 1 are connected by a flow guide pipe 11 with rounded corners, which can eliminate flow separation caused by sharp bends. The hybrid rectifier-intermittent liquid cooling plate with its wide-narrow-wide hybrid channel reduces bends and friction resistance, resulting in a significantly lower overall pressure drop compared to the traditional S-shaped channel, thus reducing pump power requirements.

[0041] Specifically, as a specific design of the liquid-cooled plate inlet manifold 8 and the liquid-cooled plate outlet manifold 9, the coolant inlet pipe 2 is connected to the liquid-cooled plate body 1 through the liquid-cooled plate inlet manifold 8. One end of the liquid-cooled plate inlet manifold 8 is a round opening and the other end is a rectangular opening. The round opening of the liquid-cooled plate inlet manifold 8 is fixedly connected to the coolant inlet pipe 2, and the rectangular opening of the liquid-cooled plate inlet manifold 8 is fixedly connected to the liquid-cooled plate body 1. The length of the leading edge of the multiple rectangular diverter plates 4 is less than the length of the rectangular opening.

[0042] The coolant outlet pipe 3 is connected to the liquid cooling plate body 1 through the liquid cooling plate outlet manifold 9. One end of the liquid cooling plate outlet manifold 9 is a round opening and the other end is a rectangular opening. The round opening of the liquid cooling plate outlet manifold 9 is fixedly connected to the coolant outlet pipe, and the rectangular opening of the liquid cooling plate outlet manifold 9 is fixedly connected to the liquid cooling plate body 1.

[0043] As a specific arrangement within each liquid-cooled plate body 1, the axes of the coolant inlet pipe 2 and the coolant outlet pipe 3 coincide with the centerline of the liquid-cooled plate body 1. The central main channel 6 is located in the middle of the liquid-cooled plate body 1, and secondary flow channels are located on both sides of the central main channel 6. Multiple rectangular flow dividers 4 and multiple fins 5 are arranged inside the liquid-cooled plate body 1. The rectangular flow dividers 4 are inclined and close to the coolant inlet pipe 2, evenly dividing the coolant into several sub-jet streams. The multiple fins 5 are arranged along the coolant flow direction. After heat exchange, the sub-jet streams flow from the multiple fins 5 to the next liquid-cooled plate body 1.

[0044] Preferred, but not limited to, such as Figure 3 and Figure 4 As shown, each of the fins 5 has multiple guide strips 7 inclinedly arranged on both sides of its surface. The guide strips 7 continuously induce transverse secondary vortices, enhance boundary layer disturbances, maintain a high degree of coordination between the velocity field and the temperature gradient field, significantly improve the heat transfer coefficient, and can bear higher heat loads under the same pump power.

[0045] Multiple guide strips 7 are arranged along the length of the fin 5; the multiple guide strips 7 on both sides of each fin 5 are alternately distributed, and the center of each guide strip 7 is a semi-circular protrusion. The height of the protrusion at the center of each guide strip 7 is... h The thickness is 1.5mm to 2.5mm, and the height of the central protrusion is [not specified]. h Boundary layer can be continuously disrupted in the 1.5~2.5mm range. h At very low temperatures, vortex dynamics are weak. h Excessive height exacerbates blockage; the optimal height is 2.0mm.

[0046] The tilt angle of each guide bar 7 is the acute angle between the guide bar 7 and the length direction of the fin 5. θ The value ranges from 55° to 75°. (Tilting angle) θ Within the range of 55° to 75°, the field coordination angle can be reduced and heat transfer enhanced, but θ <55° Insufficient synergy θ >75° resistance surges; the optimal balance point is 65°.

[0047] The multiple fins 5 are evenly spaced along the coolant flow direction, with the spacing between adjacent fins 5 being... δ With a diameter of 1.8mm to 3.2mm, it can balance flow rate and heat exchange area. δToo small a value can lead to reflow, while too large a value can result in a thickened thermal boundary layer; the optimal compromise is 2.5 mm.

[0048] Therefore, all three parameters are limited to 55°≤ θ ≤75°, 1.8mm≤ δ ≤3.2mm, 1.5mm≤ h Within a coupling median range of ≤2.5mm, the optimal balance between enhanced heat transfer and resistance control can be achieved; among which θ =65° δ =2.5mm h The combination with a diameter of 2.0 mm was verified as the globally optimal geometric configuration.

[0049] Preferably, but not limited to, all the fins 5 within the central main channel 6 are intermittent fins 10. These intermittent fins 10 are segmented and cut off along the coolant flow direction, forming several gaps. The function of the intermittent fins 10 is to couple with multiple rectangular diverter plates 4, reducing the peak flow rate in the central flow area and shifting it to both sides. This significantly reduces the flow rate difference between each branch, making the surface temperature distribution of the liquid cooling plate body 1 more uniform and effectively eliminating local hot spots.

[0050] In this invention, the coolant of the hybrid rectifier-intermittent liquid cooling plate, based on the field synergy principle, enters the liquid cooling plate body 1 from the coolant inlet pipe 2 and sequentially undergoes the following 7 stages to complete rectification, flow equalization, enhanced heat transfer and multi-stage circulation.

[0051] 1. Wall-attached circulation formation stage: The coolant enters the liquid-cooled plate inlet manifold 8 from the coolant inlet pipe 2 in a vertical jet state. It first impacts the wall of the liquid-cooled plate inlet manifold 8, and after being blocked by the wall, it quickly spreads outward, forming a wall-attached circulation along the wall of the liquid-cooled plate inlet manifold 8. During the wall-attaching process, the local flow velocity is rapidly reduced by the wall friction, and some of the initial turbulent kinetic energy is dissipated, effectively weakening the large-scale vortex brought by the inlet jet.

[0052] 2. Frontal Impact Stage with Rectangular Diverter Plate 4: After traveling a certain distance along the wall, the circulating flow encounters the multiple inclined rectangular diverter plates 4 head-on. The leading edges of the rectangular diverter plates 4 uniformly split the circulating flow into several jets. Each jet continues to advance within the gradually expanding channel formed by the sides of the rectangular diverter plates 4 and the liquid-cooled plate wall. The channel cross-section gradually expands, the fluid velocity further decreases, the static pressure gradually increases, and the flow direction is forcibly adjusted to be parallel to the downstream channel axis.

[0053] 3. Sub-jet Rectification Stage: The sub-jet continues to diffuse within the gradually expanding channel formed by the trailing edge of the rectangular splitter plate 4 and the wall of the liquid-cooled plate. Due to the continuous expansion of the channel cross-section, the fluid velocity gradient decreases, turbulent pulsations are further suppressed, and the velocity differences between the sub-jet streams are quickly smoothed out, forming a uniform low-velocity laminar or weakly turbulent state, providing uniform inlet conditions for subsequent entry into the finned 5 region. After being rectified by multiple rectangular splitter plates 4, the uniform fluid layer then smoothly transitions to the subsequent region equipped with fins 5, completing the entire inlet rectification process.

[0054] 4. Low-pressure zone formation stage: After being rectified by the coolant inlet pipe 2 and the rectangular flow divider 4, the coolant enters the narrow main heat exchange channel, which is composed of multiple fins and the liquid-cooled plate wall, at a basically uniform speed. At this time, except for the slightly higher flow rate at the central main channel 6, the flow rates of the other branches have become consistent, and the overall distribution is relatively uniform. The fins 5 at the central main channel 6 are replaced with intermittent fins 10. These intermittent fins 10 are segmented and cut off along the flow direction, forming several gaps. The two sides of the gaps are directly connected to the secondary flow channels. The sudden expansion of the cross-section at the gaps causes a sharp drop in local static pressure, forming a significant low-pressure zone.

[0055] 5. Formation and Mixing of Lateral Secondary Flow: Due to the presence of the low-pressure zone at the gap, the coolant with relatively low flow velocity in the secondary flow channels on both sides is rapidly drawn into the mainstream, generating a strong lateral secondary flow. This lateral flow passes through the gap in a direction approximately perpendicular to the mainstream, and mixes violently with the high-speed fluid in the center, redistributing the excess momentum originally concentrated in the middle flow channel to the adjacent branches, forming a "peak shaving and valley filling" type flow rebalancing.

[0056] 6. Enhanced heat transfer through the synergistic effect of the guide strips 7: The guide strips 7 extend continuously and obliquely along the surfaces of the continuous fins 5 and the intermittent fins 10, starting from the coolant inlet pipe 2. The oblique direction forms a fixed angle of attack with the mainstream direction, causing the fluid close to the wall of the fins 5 to be periodically cut, lifted, and reattached behind each guide strip 7 at its leading edge, forming dense transverse secondary vortices. These secondary vortices continuously pull the core high-speed fluid toward the wall, while simultaneously drawing the high-temperature fluid on the wall toward the mainstream, continuously thinning the thermal boundary layer and increasing the turbulence intensity. This ensures that the velocity vector and temperature gradient vector maintain a high degree of field synergy throughout the entire heat transfer channel. When the coolant passes through the gaps in the intermittent fins 10, the transverse secondary flow and the secondary vortices induced by the guide strips 7 superimpose, further promoting the mixing of hot and cold fluids. This ensures that the liquid flow after flow redistribution still maintains a high convective heat transfer coefficient, suppresses the increase of local thermal resistance, and achieves efficient heat dissipation throughout the entire process.

[0057] 7. Multi-stage series continuous heat dissipation: After the coolant smoothly leaves the first cold plate by bending along the continuous rounded corners of the guide pipe 11, there is no sudden contraction or separation, and it maintains the flow close to the wall. Then it directly enters the inlet manifold of the next cold plate, and once again hits the rectangular splitter plate 4 for rectification. It flows through the fins 5 and the intermittent fins 10 to complete the field-coordinated heat exchange and flow redistribution. Then it turns through the guide pipe 11 to enter the subsequent cold plates. This cycle continues until it finally flows out through the coolant outlet pipe 3, realizing multi-stage series continuous heat dissipation.

[0058] In summary, this invention provides a hybrid rectifying-intermittent liquid cooling plate based on the field synergy principle. By setting rectangular flow dividers 4 and fins 5, the turbulent incoming flow is adjusted into a uniform initial field with a consistent velocity-temperature gradient direction. The liquid cooling plate body 1 is internally constructed with a central main channel 6 and secondary flow channels. By expanding the flow area and reducing bends, the overall pressure drop is reduced while maintaining full coverage heat exchange of the heating zone. Optimized flow guides 7 are introduced on the surface of the fins 5 to increase the field synergy angle by guiding local flow, achieving a significant increase in heat transfer coefficient while controlling resistance growth under the same pump power. The fins 5 in the central main channel 6 are intermittent fins 10. The intermittent fins 10 have several notches and are coupled with the secondary flow channels on both sides of the liquid cooling plate body 1. The intermittent notches induce transverse secondary flow, achieving a "peak shaving and valley filling" flow redistribution, fundamentally eliminating local hot spots. The hybrid rectifier-intermittent liquid cooling plate achieves three major goals simultaneously with its integrated structure: uniform inlet flow field, low-resistance and high-efficiency heat exchange throughout the entire process, and uniform temperature across the entire range. This provides highly reliable and low-energy-consumption heat dissipation for the next generation of high-power-density power electronic devices.

[0059] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle, characterized in that, It includes at least one liquid-cooled plate body, on which a coolant inlet pipe and a coolant outlet pipe are arranged along the coolant flow direction; the liquid-cooled plate body is provided with multiple rectangular diverter plates and multiple fins, the multiple rectangular diverter plates are inclined near the coolant inlet pipe and evenly split the coolant into several sub-jet streams, the multiple fins are arranged along the coolant flow direction, and the several sub-jet streams flow through the multiple fins for heat exchange and then flow out through the coolant outlet pipe.

2. The hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle according to claim 1, characterized in that, The axes of the coolant inlet pipe and the coolant outlet pipe coincide with the center line of the liquid cooling plate body. The middle position of the liquid cooling plate body is the central main channel, and the two sides of the central main channel are secondary flow channels.

3. The hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle according to claim 1, characterized in that, Multiple guide strips are obliquely arranged on both sides of each fin, and the multiple guide strips are arranged along the length of the fin; the multiple guide strips on both sides of each fin are alternately distributed, and the middle of each guide strip is a semi-circular protrusion.

4. The hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle according to claim 3, characterized in that, The height of the central protrusion of each guide bar is 1.5mm to 2.5mm, and the tilt angle of each guide bar is the acute angle between the guide bar and the length direction of the fin. The value range of the tilt angle of the guide bar is 55° to 75°.

5. The hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle according to claim 4, characterized in that, The multiple fins are evenly spaced along the coolant flow direction, with a spacing of 1.8mm to 3.2mm between adjacent fins.

6. The hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle according to claim 1, characterized in that, The coolant inlet pipe is connected to the liquid cooling plate body through the liquid cooling plate inlet manifold. One end of the liquid cooling plate inlet manifold is a round opening and the other end is a rectangular opening. The round opening of the liquid cooling plate inlet manifold is fixedly connected to the coolant inlet pipe, and the rectangular opening of the liquid cooling plate inlet manifold is fixedly connected to the liquid cooling plate body. The length of the leading edge of the multiple rectangular diverter plates is less than the length of the rectangular opening.

7. The hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle according to claim 6, characterized in that, The coolant outlet pipe is connected to the liquid cooling plate body through the liquid cooling plate outlet manifold. One end of the liquid cooling plate outlet manifold is round and the other end is rectangular. The round end of the liquid cooling plate outlet manifold is fixedly connected to the coolant outlet pipe, and the rectangular end of the liquid cooling plate outlet manifold is fixedly connected to the liquid cooling plate body.

8. The hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle according to claim 2, characterized in that, The multiple fins within the central main channel are all intermittent fins, which are segmented and cut along the coolant flow direction to form several gaps.

9. The hybrid rectifier-intermittent liquid cooling plate based on the field synergy principle according to any one of claims 1 to 8, characterized in that, The liquid cooling plate body is a plurality of such bodies. The first liquid cooling plate body is provided with the coolant inlet pipe, the last liquid cooling plate body is provided with the coolant outlet pipe, and the plurality of liquid cooling plate bodies in the middle are connected by a guide pipe.

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