Uniform temperature plate round hole heat pipe heat conduction structure and reinforced reflux method

Abstract

This invention relates to a heat conduction structure for a heat pipe with circular holes in a vapor chamber and a method for enhancing reflux, belonging to the technical field of vapor chambers. It includes a vapor chamber body with a cavity within it. The cavity is circular, and multiple raised strips are evenly arranged on its inner circumference. These raised strips, in conjunction with the cavity wall, form multiple capillary grooves distributed around the inner circumference. By utilizing the absence of sharp corners in the circular cavity, localized stress concentration caused by vapor pressure is avoided, significantly improving pressure resistance and deformation resistance, ensuring the long-term reliability of the vapor chamber under high heat loads. The raised strips are evenly arranged along the circumference, forming capillary grooves without dead corners in conjunction with the arc-shaped cavity wall, completely solving the problem of weakened capillary force and poor working fluid flow in the corner areas of square cavities. Under the same projected area, the circumference-to-area ratio of the circular cavity is superior to that of a rectangle, increasing the inner surface area and significantly improving heat exchange efficiency.

Description

Technical Field

[0001] This invention belongs to the field of heat spreader technology, specifically relating to a heat conduction structure of a heat spreader with a circular hole heat pipe and a method for enhancing reflux. Background Technology

[0002] Currently, a vapor chamber typically consists of a vapor chamber body with a square cavity inside. To enhance the capillary reflux capability of the working fluid and improve heat transfer efficiency, parallel ridges of the same height are usually provided on the inner walls of the upper and lower sides of the square cavity. These ridges cooperate with the straight wall surface of the square cavity to form multiple capillary channel structures extending along the length of the cavity. The main purpose of this design is to use the capillary structure formed by the ridges and the cavity wall to drive the working fluid to circulate efficiently between the evaporation end and the condensation end, thereby achieving rapid heat diffusion.

[0003] However, the aforementioned design based on a square cavity structure has some inherent limitations. First, when subjected to internal steam pressure, the sharp corners of the square cavity are prone to stress concentration, which limits the overall pressure resistance and deformation resistance of the cavity structure. This, in turn, affects the long-term reliability and maximum operating temperature limit of the heat spreader under high heat loads or extreme temperature conditions. Second, the capillary channel structure inside the square cavity, composed of straight walls and convex ribs, often has an undesirable channel distribution and morphology in the corner areas, which may lead to weakened capillary forces or impaired working fluid flow. While the overall heat exchange efficiency has been further improved, the geometric characteristics of the square cavity itself may also limit the optimization of the effective heat exchange area under the same projected area. Therefore, how to design a new type of heat spreader cavity structure to significantly improve its pressure resistance, temperature load capacity and heat exchange efficiency, especially to overcome the stress concentration at the corners of the square cavity, optimize the uniformity of capillary distribution and maximize the effective heat exchange area, so as to meet the heat dissipation requirements of higher power density electronic devices, has become an urgent technical problem to be solved. To address this, a heat spreader circular hole heat pipe thermal conduction structure and enhanced reflux method are proposed. Summary of the Invention

[0004] To address the problems of insufficient pressure resistance, uneven capillary distribution, and limited effective heat exchange area caused by stress concentration in existing square cavity heat exchange plates, this invention provides a heat conduction structure with circular hole heat pipes in the heat exchange plate and a method to enhance reflux.

[0005] The objective of this invention can be achieved through the following technical solutions:

[0006] A heat pipe heat conduction structure with a heat spreader and a circular hole includes a heat spreader body. A cavity is provided inside the heat spreader body. The cavity is circular. A plurality of raised strips are uniformly arranged on the inner circumference of the circular cavity. The raised strips cooperate with the cavity wall of the circular cavity to form a plurality of capillary grooves distributed around the inner circumference of the cavity.

[0007] As a further embodiment of the present invention, the overall thickness of the heat exchange plate body is 5.5mm–6.5mm, and the length of the heat exchange plate body is 100mm–103mm.

[0008] As a further aspect of the present invention, the equivalent circle diameter of the capillary groove formed by the convex strip is 4.3mm–4.7mm.

[0009] As a further embodiment of the present invention, the distance between the centers of two adjacent circular cavities is 5.0mm–5.5mm.

[0010] As a further embodiment of the present invention, the number of the circular cavities is 18–20, and the circular cavities are arranged linearly and uniformly along the length of the heat equalization plate body.

[0011] As a further embodiment of the present invention, the number of the protrusions is 19–21, and the width of the protrusions is greater than the width of the capillary groove.

[0012] A method for enhancing reflux using a heat pipe with a circular hole in a vapor chamber includes the following steps:

[0013] S1: Divide the heat spreader body into an evaporation zone, a transition zone, and a condensation zone along its length. A first depth groove is opened on the surface of the convex strip in the evaporation zone in a direction perpendicular to the axis of the circular cavity. Then, an auxiliary groove communicating with the first depth groove is opened on the bottom wall of the capillary groove. A second depth groove is opened on the bottom wall of the capillary groove and the surface of the convex strip in the transition zone to form a continuous wavy flow channel. A third depth groove is opened on the bottom wall of the capillary groove in the condensation zone in a direction parallel to the axis of the circular cavity.

[0014] S2: An external heat source is applied to the evaporation zone, so that heat is conducted to the working fluid through the cavity wall, promoting the working fluid to be heated and vaporized;

[0015] S3: Enhanced steam phase change, controlling the directional flow of vaporized propellant through the steam space to the condensation zone, while simultaneously releasing latent heat of vaporization;

[0016] S4: Reflux trigger in the condensation zone, guiding the liquefied chemical substance to reflux into the evaporation zone along the bottom wall groove of the capillary tank in the condensation zone;

[0017] S5: Using capillary pressure and gravity, the liquid working fluid is driven back to the evaporation zone to complete the cycle.

[0018] As a further aspect of the present invention, the trench depth in step S1 satisfies the following: first depth trench > second depth trench > third depth trench.

[0019] As a further aspect of the present invention, in step S3, the directional flow of steam is accelerated through the wavy flow channel in the transition zone, and the steam flow direction is consistent with the angle between the channel and the groove.

[0020] As a further embodiment of the present invention, in step S4, the reflux in the condensation zone is guided by a third-depth trench, and the reflux direction is connected to the auxiliary trench in the evaporation zone.

[0021] The beneficial effects of this invention are:

[0022] The circular cavity structure design completely eliminates sharp corners, avoiding localized stress concentration caused by steam pressure, significantly improving pressure resistance and deformation resistance, and ensuring long-term reliable operation of the heat spreader under high heat loads. The raised strips are evenly arranged along the circumference, forming a capillary groove structure without dead corners in conjunction with the arc-shaped cavity wall, completely solving the problem of weakened capillary force in the corner areas of the square cavity, achieving uniform wetting of the working fluid throughout and eliminating flow dead zones. With the same projected area, the inner surface area of ​​the circular cavity is significantly increased, effectively improving heat exchange efficiency. Precise parameter design ensures that the overall thickness and length match the heat source size, and the cavity spacing is precisely controlled. The number of heat distribution raised strips and the size of the capillary grooves are optimized in tandem to maintain the optimal groove-to-wall area ratio, ensuring no dead corners in the working fluid coverage and significantly enhancing the heat flux density carrying capacity.

[0023] The zoned trench enhanced reflux method involves creating deep trenches in the evaporation zone to enhance capillary suction; a wave-like flow channel in the transition zone to directionally accelerate steam flow; and parallel trenches in the condensation zone to guide rapid reflux of the working fluid, forming a closed-loop, low-resistance path. The steam flow direction and trench morphology work in synergy, with the reflux path connecting to auxiliary trenches in the evaporation zone, achieving a significant increase in working fluid circulation speed. Ultimately, while eliminating stress concentration, this method simultaneously achieves a synergistic effect of enhanced pressure resistance, reduced thermal resistance, and improved temperature uniformity. Under the same power conditions, the chip temperature is significantly lower than that of the traditional square-hole structure, and its lifespan is greatly extended after extreme temperature shock verification. Attached Figure Description

[0024] To facilitate understanding by those skilled in the art, the present invention will be further described below with reference to the accompanying drawings.

[0025] Figure 1 This is a schematic diagram of the overall structure of the heat-conducting structure of the heat spreader plate with circular holes in the present invention.

[0026] Figure 2 This is a dimensional diagram of the heat-conducting structure of the heat pipe with circular holes in the heat spreader of the present invention.

[0027] Figure 3 This is a flowchart of the heat pipe enhanced reflux method for a heat spreader with a circular hole in a heat pipe according to the present invention.

[0028] Legend: 1. Heat spreader body; 2. Circular cavity; 3. Raised strip; 4. Capillary groove. Detailed Implementation

[0029] To further illustrate the technical means and effects of the present invention in achieving its intended purpose, the following detailed description of the specific implementation methods, structures, features, and effects of the present invention, in conjunction with the accompanying drawings and preferred embodiments, is provided.

[0030] refer to Figures 1-3 This embodiment provides a heat conduction structure for a heat pipe with a circular hole in a heat spreader, including a heat spreader body 1. A cavity is provided inside the heat spreader body 1. The cavity is a circular cavity 2. A plurality of protrusions 3 are uniformly arranged on the inner circumference of the circular cavity 2. The protrusions 3 cooperate with the cavity wall of the circular cavity 2 to form a plurality of capillary grooves 4 distributed around the inner circumference of the cavity.

[0031] It should be noted that by eliminating sharp corners through circular shapes, stress concentration is eliminated, and the pressure resistance and deformation resistance are improved, allowing the heat spreader to withstand higher temperatures and heat loads. The raised strips 3 are evenly arranged along the circumference and cooperate with the arc-shaped cavity wall to form capillary grooves 4 without dead corners, ensuring uniform wetting of the working fluid throughout the entire area and avoiding flow dead corners. Under the same projected area, the circular cavity 2 has a larger inner surface area than the square cavity because the ratio of the circumference to the area of ​​a circle is better than that of a rectangle, which meets the requirement of maximizing the effective heat exchange area. In addition, in actual tests, under the same power and environment, the chip temperature of the circular hole structure is lower than that of the square hole structure.

[0032] Current vapor chambers typically consist of a vapor chamber body 1, which has a square cavity machined inside. To enhance the capillary reflux capability of the working fluid and improve heat transfer efficiency, parallel ribs 3 of the same height are usually provided on the inner walls of the upper and lower sides of the square cavity. These ribs 3 cooperate with the straight wall surface of the square cavity to form multiple capillary grooves 4 extending along the length of the cavity. The main purpose of this design is to use the capillary structure formed by the ribs 3 and the cavity wall to drive the working fluid to circulate efficiently between the evaporation and condensation ends, thereby achieving rapid heat diffusion. However, the above-mentioned design based on the square cavity structure has some inherent limitations. First, the square cavity... When the body is subjected to internal steam pressure, stress concentration is prone to occur in its sharp corner areas, which limits the overall pressure resistance and deformation resistance of the cavity structure. This, in turn, affects the long-term working reliability and maximum load-bearing temperature limit of the heat spreader under high heat load or extreme temperature conditions. Secondly, the capillary groove structure consisting of straight walls and convex strips 3 inside the square cavity is often not ideal in terms of channel distribution and shape in the corner areas of the cavity. This may lead to local weakening of capillary force or poor flow of working fluid, which limits the further improvement of overall heat exchange efficiency. In addition, the geometric characteristics of the square cavity itself may also limit the optimization of effective heat exchange area under the same projected area.

[0033] To address the aforementioned issues, this embodiment utilizes a circular cavity 2 without sharp corners to avoid localized stress concentration caused by steam pressure, significantly improving pressure resistance and deformation resistance, and ensuring the long-term reliability of the heat spreader under high heat loads. The raised strips 3 are evenly arranged along the circumference, forming capillary grooves 4 without dead angles in conjunction with the arc-shaped cavity wall, completely solving the problem of weakened capillary force and poor working fluid flow in the corner areas of the square cavity, achieving uniform wetting and efficient working fluid circulation throughout the entire area. Under the same projected area, the circumference-to-area ratio of the circular cavity 2 is superior to that of the rectangle, increasing the inner surface area and significantly improving heat exchange efficiency.

[0034] Following the above embodiments, in one embodiment, the overall thickness of the heat spreader body 1 is 5.5mm–6.5mm, the length of the heat spreader body 1 is 100mm–103mm, and the center-to-center distance between two adjacent circular cavities 2 is 5.0mm–5.5mm. The overall thickness of the heat spreader body 1 is selected to be 6mm, the length of the heat spreader body 1 is selected to be 101.8mm, and the center-to-center distance is selected to be 5.25mm. This ensures that the cavity wall thickness is sufficient to disperse the steam pressure, while the spacing precisely matches the heat source size to avoid heat accumulation. Figure 2 As shown, the 6mm wall thickness ensures that the cavity can disperse steam pressure, avoid stress concentration caused by thin walls, and improve pressure resistance; the 5.25mm center-to-center spacing precisely corresponds to the size of the heat source, avoiding heat accumulation due to too small a spacing or incomplete heat coverage due to too large a spacing; the 101.8mm length is linked to the spacing to achieve uniform arrangement of the cavity in a limited space.

[0035] To better balance the working fluid reflux efficiency and heat flux density, in one embodiment, the equivalent circular diameter of the capillary groove 4 formed by the protrusion 3 is 4.3mm–4.7mm; here, an equivalent circular diameter of 4.5mm is selected. The number of circular cavities 2 is 18–20, and the circular cavities 2 are linearly and uniformly arranged along the length of the heat spreader body 1. The number of circular cavities 2 is limited by the length of the heat spreader body 1. Under the length limitation of the heat spreader body 1, if the number of circular cavities 2 is less than 18, the heat distribution of the cavities will be uneven; if the number of circular cavities 2 is greater than 20, the machining of the cavities will exceed the tolerance. 18-20 cavities make the projected area of ​​a single cavity ≈ 5.5mm², which is the optimal solution for heat flux density. Here, we take 19 circular cavities 2 as an example. Figure 2 As shown. A 4.5mm diameter balances capillary force (too small increases flow resistance) and working fluid coverage (too large weakens capillary driving force). With 19 cavities and a length of 101.8mm, a single cavity projected area of ​​approximately 5.5mm² is achieved, reaching the optimal heat flux density. Furthermore, the number of protrusions 3 is 19–21, and the width of protrusions 3 is greater than the width of capillary grooves 4. Here, 20 protrusions 3 are selected. Figure 2 As shown, if the diameter of the capillary groove 4 is too small, the flow resistance will increase; if it is too large, the capillary force will be weakened. The number of protrusions 3 needs to be matched to maintain the working fluid coverage without dead corners.

[0036] Furthermore, it should be noted that exceeding any of the above parameters will disrupt the balance. For example, increasing the thickness to 7mm requires a simultaneous increase in the spacing, which will disrupt the center-to-center spacing of the circular cavity 2 (5.0mm–5.5mm). Otherwise, stress concentration will occur. Alternatively, reducing the number of protrusions 3 to 18 requires a reduction in the groove diameter, which conflicts with the equivalent circular diameter of 4.3mm–4.7mm. Otherwise, capillary force will be insufficient. Only by using the following... Figure 2 Only by implementing the scale shown can we simultaneously achieve the synergistic effects of improved pressure resistance, reduced thermal resistance, and measured temperature reduction, while eliminating stress concentration.

[0037] A method for enhancing reflux using a heat pipe with a circular hole in a vapor chamber includes the following steps:

[0038] S1: Divide the heat spreader body 1 into an evaporation zone, a transition zone, and a condensation zone along its length. A first depth groove is opened on the surface of the convex strip 3 in the evaporation zone along a direction perpendicular to the axis of the circular cavity 2. Then, an auxiliary groove communicating with the first depth groove is opened on the bottom wall of the capillary groove 4. A second depth groove is opened on the bottom wall of the capillary groove 4 and the surface of the convex strip 3 in the transition zone to form a continuous wavy flow channel. A third depth groove is opened on the bottom wall of the capillary groove 4 in the condensation zone along a direction parallel to the axis of the circular cavity 2.

[0039] The first deep groove is perpendicular to the axis, increasing the surface area of ​​the convex strip 3 and promoting the vaporization of the working fluid. The auxiliary groove provides additional capillary force on the bottom wall of the capillary groove 4, ensuring rapid evaporation of the working fluid and the formation of a steam flow. The transition zone has a wavy flow channel. The second deep groove creates a continuous path, guiding the steam to move directionally from the evaporation zone to the condensation zone and reducing flow resistance. The third deep groove is parallel to the axis, forming a straight reflux channel in the condensation zone, which facilitates the return of the liquefied fluid to the evaporation zone. By controlling the depth and direction of the grooves, the decoupling of steam flow and liquid reflux is achieved, with the aim of maximizing the release of latent heat of vaporization and reflux rate.

[0040] S2: An external heat source is applied to the evaporation zone, allowing heat to be conducted to the working fluid through the cavity wall, promoting the vaporization of the working fluid. By applying an external heat source to the evaporation zone, heat can be effectively conducted to the working fluid through the cavity wall. This method not only ensures uniform heating of the working fluid but also promotes the vaporization of the working fluid in the evaporation zone, thereby improving the heat transfer efficiency.

[0041] S3: Steam phase change enhancement controls the directional flow of vaporized propellant through the steam space to the condensation zone, simultaneously releasing latent heat of vaporization. Steam phase change enhancement controls the flow of vaporized propellant in the steam space, directing it to the condensation zone. In this way, the steam releases latent heat of vaporization simultaneously during the flow, which helps to improve the thermal energy conversion efficiency and reduce energy loss during the flow process.

[0042] S4: Reflux triggering in the condensation zone guides the liquefied propellant back to the evaporation zone along the bottom wall grooves of capillary channel 4. This ensures the liquefied propellant returns to the evaporation zone quickly and efficiently. This reflux mechanism not only helps maintain stable vaporization of the working propellant in the evaporation zone but also reduces energy loss during the reflux process, thereby improving overall heat transfer efficiency. S5: Utilizing capillary pressure and gravity, the liquid working propellant returns to the evaporation zone to complete the cycle. Through the combined action of capillary pressure and gravity, the liquid working propellant effectively returns to the evaporation zone, achieving circulation of the working propellant within the vapor chamber. This process ensures continuous and stable system operation. Firstly, it improves thermal efficiency and reduces energy waste. Secondly, it helps maintain temperature balance in the evaporation, transition, and condensation zones, ensuring stable performance of the entire vapor chamber. This circulation method reduces system maintenance costs and improves the service life and reliability of the vapor chamber.

[0043] It is worth mentioning that in a vapor chamber, the working fluid filled inside the vapor chamber needs to achieve efficient heat transfer during evaporation and condensation. If the capillary structure design is inappropriate, the flow path of the working fluid may not be clear or efficient enough, leading to a decrease in heat transfer efficiency. In addition, low reflux efficiency means that the working fluid cannot quickly return to the evaporation zone, thus affecting the overall heat dissipation performance. To address this, in S1, the vapor chamber body 1 is divided along its length into an evaporation zone, a transition zone, and a condensation zone, and grooves are cut for each zone: a first-depth groove perpendicular to the axis of the circular cavity 2 is opened on the surface of the convex strip 3, and an auxiliary groove is opened on the bottom wall of the capillary groove 4; a second-depth groove is opened on the bottom wall of the capillary groove 4 and the surface of the convex strip 3, forming a continuous, wave-shaped flow channel; a third-depth groove is opened on the bottom wall of the capillary groove 4 along a direction parallel to the axis of the circular cavity 2. This partitioned grooving is based on the inherent defects of working fluid flow in the background technology: in traditional methods... The working fluid tends to diffuse randomly after vaporization in the evaporation zone, resulting in low steam flow efficiency. Meanwhile, the liquid return in the condensation zone lacks a guiding path, causing a return delay. By using directional grooves and the depth differences of the grooves mentioned below, a directional flow channel is created in step S1. The evaporation zone grooves enhance capillary force to drive initial vaporization, the transition zone's wavy flow channel guides steam acceleration, and the condensation zone grooves optimize the liquid return path. In short, by creating grooves of different depths in the evaporation, transition, and condensation zones, directional flow channels are formed, achieving effective control of the working fluid flow. The evaporation zone grooves enhance capillary force, contributing to the initial vaporization drive; the transition zone's wavy flow channel accelerates steam flow; and the condensation zone grooves optimize the liquid return path, reducing return delay. These designs make the flow of the working fluid in the vapor chamber more orderly and efficient, thereby improving the vapor chamber's heat dissipation performance.

[0044] The flow conflict caused by uniform depth mainly occurs in the evaporation, transition, and condensation zones. When the trench depths in these three zones are consistent, the capillary evaporation force in the evaporation zone may be insufficient because the maximum depth is required to enhance evaporation efficiency. Simultaneously, steam acceleration in the transition zone is hindered because its depth is insufficient to ensure smooth flow. Liquid reflux in the condensation zone is also affected because its excessive depth is unfavorable for preferential liquid reflux. This uniform depth makes it impossible to effectively control the phase change process in different zones, leading to a conflict in flow requirements between the evaporation and condensation zones: the evaporation zone needs more steam generation, while the condensation zone needs more liquid reflux. To address this issue, in one embodiment, the trench depths in step S1 satisfy the following order: first depth trench > second depth trench > third depth trench. The evaporation zone requires the maximum depth to enhance capillary evaporation force; the transition zone requires the next deepest depth to ensure steam acceleration without hindering flow; the condensation zone has the minimum depth for preferential liquid reflux. The phase change process is controlled through depth differences, with the evaporation zone prioritizing vaporization and the condensation zone prioritizing condensation.

[0045] In heat exchange systems, steam, as the heat transfer medium, has a significant impact on heat exchange efficiency due to its flow state. The steam flow path may exhibit inconsistent flow direction and velocity due to channel shape, size, or the characteristics of the steam itself. When steam enters the condensation zone, if its flow is not uniform and directional, it will cause steam to accumulate in localized areas while remaining relatively sparse in others. This uneven distribution prevents the timely and effective release of latent heat in some areas, leading to a decrease in heat exchange efficiency and potentially causing localized overheating or undercooling, affecting the stable operation of the entire system. To avoid uneven latent heat release caused by dispersed steam flow, in one embodiment, the directional steam flow in step S3 is accelerated through a corrugated channel in the transition zone, with the steam flow direction aligned with the angle between the channel and the groove. This alignment of the steam flow direction with the groove angle, and the acceleration via the corrugated channel, stems from the optimization of fluid dynamics in the transition zone. The corrugated channel reduces flow resistance, ensuring high-speed directional steam flow from the evaporation zone to the condensation zone, avoiding disorderly diffusion.

[0046] Furthermore, discontinuities or obstacles exist in the working fluid flow channel between the condensation zone and the evaporation zone, preventing the liquefied fluid from smoothly returning to the evaporation zone. When the liquefied fluid in the condensation zone needs to flow back to the evaporation zone, if the return path is obstructed due to design or structural defects, such as insufficient trench depth or incomplete connection, the return path will be broken. This break will hinder the continuous flow of liquid, leading to untimely replenishment of the working fluid and causing delays. Such obstruction or delay will reduce the thermal efficiency of the system and may affect the overall performance of the equipment. To avoid delays in working fluid replenishment caused by broken return paths, in one embodiment, the condensation zone return in step S4 is guided by a third-depth trench, and the return direction is connected to the auxiliary trench in the evaporation zone. The third-depth trench in the condensation zone is connected to the auxiliary trench in the evaporation zone. Based on the requirement for continuity of the liquid capillary return path, a closed-loop return channel is created to drive the liquefied fluid to return to the evaporation zone efficiently.

[0047] The working principle and workflow of this invention:

[0048] By replacing the traditional square cavity with multiple circular cavities 2 inside the heat spreader body 1, the circular cavity 2 has evenly distributed ridges 3 on its arc-shaped inner wall. The ridges 3 cooperate with the cavity wall to form a capillary groove 4 around the inner wall without dead corners. This design completely eliminates stress concentration at sharp corners and significantly improves pressure resistance. The circumferentially distributed capillary groove 4 ensures uniform wetting of the working fluid throughout the entire area and avoids dead corners in flow. Under the same projected area, the inner surface area of ​​the circular cavity 2 is increased, and the heat exchange efficiency is improved. Then, the heat spreader body 1 is divided into an evaporation zone, a transition zone, and a condensation zone along its length. A first depth groove is opened on the surface of the ridges 3 in the evaporation zone in a direction perpendicular to the axis of the circular cavity 2. Then, an auxiliary groove connected to the first depth groove is opened on the bottom wall of the capillary groove 4. A second depth groove is opened on the bottom wall of the capillary groove 4 and the surface of the ridges 3 in the transition zone to form a continuous wave-shaped flow channel. A third depth groove is opened on the bottom wall of the capillary groove 4 in the condensation zone in a direction parallel to the axis of the circular cavity 2.

[0049] When an external heat source acts on the evaporation zone, the heat is conducted to the working fluid through the cavity wall, and the working fluid is heated and vaporized in the evaporation zone. This process enhances the capillary suction force through the first deep groove vertically opened on the surface of the evaporation zone protrusion 3 and the auxiliary groove connected to the bottom wall of the capillary groove 4, which greatly accelerates the vaporization efficiency. In the directional steam flow stage, the generated steam enters the transition zone and is guided by the wave-shaped flow channel to flow directionally and accelerate towards the condensation zone. The steam flow direction is consistent with the angle between the grooves, which reduces turbulence loss and releases the latent heat of vaporization simultaneously and efficiently. Condensation and reflux stage: After the steam is liquefied into working fluid in the condensation zone, it flows back in a straight line along the third depth groove parallel to the axis of the cavity. This shallow groove preferentially guides the liquid flow, and the reflux path is connected to the auxiliary groove in the evaporation zone, forming a closed-loop low-resistance channel. Combined with the capillary pressure and gravity, the liquefied fluid returns to the evaporation zone efficiently to complete the cycle. The depth difference of the partitioned grooves realizes vaporization and reflux, while the groove direction design ensures that the directional acceleration of steam and the preferential reflux path of liquid are separated, ultimately achieving the combined effects of high-speed circulation of working fluid, significant reduction of thermal resistance and improvement of temperature uniformity.

[0050] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention in any way. Although the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art can make some modifications or alterations to the above-disclosed technical content to create equivalent embodiments without departing from the scope of the present invention. Any simple modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present invention without departing from the scope of the present invention shall still fall within the scope of the present invention.

Claims

1. A method for enhancing reflux using a heat pipe with a circular hole in a heat spreader, characterized in that, The system includes a heat spreader body, within which a cavity is provided. The cavity is circular, and multiple raised ribs are evenly distributed on its inner circumference. These raised ribs cooperate with the cavity wall to form multiple capillary grooves distributed around the inner circumference. Includes the following steps: S1: Divide the heat spreader body into an evaporation zone, a transition zone and a condensation zone along its length. A first depth groove is opened on the surface of the convex strip in the evaporation zone in a direction perpendicular to the axis of the circular cavity. Then, an auxiliary groove communicating with the first depth groove is opened on the bottom wall of the capillary groove. A second depth groove is opened on the bottom wall of the capillary groove and the surface of the convex strip in the transition zone to form a continuous wave-shaped flow channel. A third depth groove is opened on the bottom wall of the capillary groove in the condensation zone in a direction parallel to the axis of the circular cavity. S2: An external heat source is applied to the evaporation zone, so that heat is conducted to the working fluid through the cavity wall, promoting the working fluid to be heated and vaporized; S3: Enhanced steam phase change, controlling the directional flow of vaporized propellant through the steam space to the condensation zone, while simultaneously releasing latent heat of vaporization; S4: Reflux trigger in the condensation zone, guiding the liquefied chemical substance to reflux into the evaporation zone along the bottom wall groove of the capillary tank in the condensation zone; S5: Using capillary pressure and gravity, the liquid working fluid is driven back to the evaporation zone to complete the cycle; The trench depth in step S1 satisfies the following conditions: first depth trench > second depth trench > third depth trench; in step S3, the directional flow of steam is accelerated through the wavy flow channel in the transition zone, and the steam flow direction is consistent with the angle between the trench and the flow direction; in step S4, the reflux in the condensation zone is guided by the third depth trench, and the reflux direction is connected to the auxiliary trench in the evaporation zone.

2. The method for enhancing reflux using a heat pipe with a circular hole in a heat spreader according to claim 1, characterized in that, The overall thickness of the heat exchange plate body is 5.5mm–6.5mm, and the length of the heat exchange plate body is 100mm–103mm.

3. The method for enhancing reflux using a heat pipe with a circular hole in a heat spreader according to claim 1, characterized in that, The equivalent circle diameter of the capillary groove formed by the convex strip is 4.3mm–4.7mm.

4. The method for enhancing reflux using a heat pipe with a circular hole in a heat spreader according to claim 1, characterized in that, The distance between the centers of two adjacent circular cavities is 5.0mm–5.5mm.

5. The method for enhancing reflux using a heat pipe with a circular hole in a heat spreader according to claim 1, characterized in that, The number of circular cavities is 18–20, and the circular cavities are arranged linearly and uniformly along the length of the heat equalization plate body.

6. The method for enhancing reflux using a heat pipe with a circular hole in a heat spreader according to claim 1, characterized in that, The number of the protrusions is 19–21, and the width of the protrusions is greater than the width of the capillary groove.

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