WO2020103194A1 - 一种具有梯度润湿结构的平板热管 - Google Patents

一种具有梯度润湿结构的平板热管

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Publication number
WO2020103194A1
WO2020103194A1 PCT/CN2018/119423 CN2018119423W WO2020103194A1 WO 2020103194 A1 WO2020103194 A1 WO 2020103194A1 CN 2018119423 W CN2018119423 W CN 2018119423W WO 2020103194 A1 WO2020103194 A1 WO 2020103194A1
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WO
WIPO (PCT)
Prior art keywords
plate
bottom plate
heat pipe
top plate
flat
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2018/119423
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English (en)
French (fr)
Inventor
齐宝金
魏进家
王雅
于婷
崔晨乙
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Xian Jiaotong University
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Xian Jiaotong University
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Publication date
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Publication of WO2020103194A1 publication Critical patent/WO2020103194A1/zh
Priority to US17/326,367 priority Critical patent/US11913727B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0233—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes the conduits having a particular shape, e.g. non-circular cross-section, annular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure
    • F28D15/043—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure forming loops, e.g. capillary pumped loops
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure
    • F28D15/046—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure characterised by the material or the construction of the capillary structure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/003—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by using permeable mass, perforated or porous materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2245/00—Coatings; Surface treatments
    • F28F2245/02—Coatings; Surface treatments hydrophilic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2245/00—Coatings; Surface treatments
    • F28F2245/04—Coatings; Surface treatments hydrophobic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/18—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes sintered
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/06—Fastening; Joining by welding

Definitions

  • the invention belongs to the technical field of electronic component heat dissipation devices, and relates to a flat plate heat pipe with a gradient wetting structure.
  • the flat plate heat pipe is a highly efficient phase change heat transfer equipment improved on the basis of the traditional heat pipe. It has the advantages of simple structure, good temperature uniformity and high heat transfer efficiency. It is mainly composed of shell, liquid absorbing core, working medium, etc.
  • the working principle is similar to the working principle of ordinary heat pipe, using the phase change latent heat of working medium to take the heat of electronic components.
  • phase change of the evaporation surface takes away the heat of the heat source, and the heat of the condensation surface is taken away by other heat dissipation methods outside the flat heat pipe.
  • flat heat pipes upgrade one-dimensional heat transfer to two-dimensional, with better temperature uniformity.
  • the existing flat heat pipes mainly rely on the capillary force provided by the liquid wick to promote the backflow of the working medium, and because the condensation surface of the evaporation surface is covered with the liquid wick, the porous structure of the liquid wick has a large thermal resistance, which increases the entire heat pipe Heat transfer thermal resistance.
  • the sintered wick structure itself requires energy consumption, and the sintering quality is difficult to guarantee.
  • the object of the present invention is to provide a flat heat pipe with a gradient wetting structure.
  • the flat heat pipe has a reasonable structure design, and uses surface tension and capillary force to guide and accelerate the working fluid recirculation speed. Reduce the coverage of the wick, reduce the heat transfer resistance and improve the overall heat transfer capacity.
  • the invention discloses a flat plate heat pipe with a gradient wetting structure, which comprises a bottom plate, a top plate and a support plate between the bottom plate and the top plate. There are two support plates. The bottom plate, the top plate and the support plates on both sides are connected to form a sealed cavity body;
  • the inner surface of the bottom plate is processed with micron-level radial stripes, showing a wetting gradient that changes uniformly from the center to the circumference. It is used to transport liquid and collect condensate to the center of the center without a pump.
  • a radial structure with super-hydrophilic and super-hydrophobic intervals arranged on the inner surface of the top plate is used to transport the condensate to the surrounding wall;
  • a liquid absorbing core is provided on the inner side of the support plate, which is used to transfer liquid from the edge of the top plate to the edge of the bottom plate.
  • the liquid-absorbent core is sintered on the inside of the support plate with powder, and has a porous structure; the upper and lower ends of the liquid-absorbent core are respectively connected to the top plate and the bottom plate.
  • it further includes a plurality of support columns disposed between the bottom plate and the top plate, and the upper and lower two of the support columns are respectively connected to the top plate and the bottom plate.
  • the bottom plate, the top plate and the support plate are connected by welding and sealing.
  • the area of the superhydrophobic region is larger than the area of the superhydrophilic region; further, the surface area ratio of the superhydrophilic region and the superhydrophobic region is 1: 5.
  • the height of the micron-level radial stripes raised on the inner surface of the bottom plate and the distance between adjacent micron-level radial stripes satisfy the Cassie-Baxter state in which droplets can be held up to ensure the surface.
  • the micron-level radial stripes on the inner surface of the bottom plate are prepared by photolithography
  • the present invention has the following beneficial effects:
  • the bottom plate is the evaporation surface of the flat heat pipe, and the inner surface is processed with micron-level radial stripes, and the droplets can present the wetting model of Cassie-Baxter on this surface. Therefore, it has a uniformly changing wetting gradient, and the wettability gradually increases from the outer side to the inner side of the circumference.
  • This structure has the function of directionally transporting liquid and collecting condensate without a pump, which is beneficial to concentrate the condensate returning to the heat source. Speed up the replenishment rate of the working fluid on the evaporation surface.
  • the inner surface of the top plate is processed with a radial pattern structure of super-affinity and hydrophobic phases.
  • the super-hydrophobic area increases the condensation nucleation area, and all are droplet-shaped condensation, reducing the heat transfer resistance and greatly enhancing the heat transfer efficiency
  • the super-hydrophilic zone has the ability to transport condensate to the surrounding pipe wall, speeding up the circulation speed of the working medium.
  • the flat heat pipe of the present invention reduces the sintering of the liquid-absorbing core by processing and modifying the top plate and the bottom plate, and strengthens the evaporation and condensation speed on the premise of ensuring the working fluid reflux speed, reduces the heat transfer thermal resistance, and improves the evaporation area And the heat transfer performance of the condensation area, thereby improving the heat transfer capacity of the entire flat heat pipe.
  • a plurality of supporting columns with both ends in contact with the bottom plate and the top plate are evenly arranged in the closed cavity of the flat plate heat pipe to prevent the surface of the flat plate heat pipe from being deformed.
  • the preparation method of the surface structure of the bottom plate is a photolithography method, and the radial microscopic strip protrusions on the surface are prepared by the photolithography method.
  • the raised micron-level strips need to be high enough, and the spacing between the strips needs to be small enough to hold up the droplets, while also ensuring the surface's hydrophobicity.
  • FIG. 1 is a front sectional view of a flat heat pipe with a gradient wetting structure of the present invention
  • Figure 2-1 is a top view of the bottom plate of the flat heat pipe with a gradient wetting structure of the present invention
  • Figure 2-2 is a side view of the structure of the transportation area of the bottom plate
  • FIG. 3 is a top view of a top plate of a flat heat pipe with a gradient wetting structure of the present invention
  • Figure 4-1 is a schematic diagram of the Cassie model of the mechanism of the gradient wetting structure on the bottom surface
  • Figure 4-2 is a schematic diagram of the model of the proportion of solids on the surface of the bottom plate
  • Figure 4-3 is a schematic diagram of the principle of droplet movement direction
  • Figure 5-1 is a model diagram of water droplets on the wedge-shaped super-hydrophilic trajectory
  • Figure 5-2 is a mechanical model diagram of the force situation during the spontaneous motion of water droplets.
  • the flat heat pipe with a gradient wetting structure of the present invention includes a bottom plate 11, a top plate 12, and a support plate 13 between the top plate and the bottom plate.
  • the bottom plate 11, the top plate 12, and the support plate 13 are formed in a sealed connection Sealed cavity; the inner surface of the bottom plate 11 as the evaporation surface of the flat heat pipe is processed with micron-level radial stripes, showing a uniformly varying wetting gradient.
  • the structure has the function of transporting liquid and collecting condensate without pump orientation; as a flat plate
  • the inner surface of the top plate 12 of the condensing surface of the heat pipe is processed with a radial pattern of super-affinity and hydrophobic phases.
  • the structure has the ability to transport condensate to the surrounding pipe wall.
  • a liquid wick 14 is placed inside the support plate 13.
  • the liquid-absorbent core 14 has a porous structure, and is sintered on the inner side of the support plate 13 by a sintering method; the upper and lower ends of the liquid-absorbent core 14 are respectively connected to the top plate 12 and the bottom plate 11.
  • it further includes a plurality of support posts 15 disposed between the bottom plate 11 and the top plate 12, and the upper and lower two of the support posts 15 are connected to the top plate 12 and the bottom plate 11, respectively.
  • the invention is a flat heat pipe suitable for heat dissipation of electronic devices.
  • the bottom plate 11 is the evaporation surface of the flat heat pipe, as shown in Figure 2-1 and Figure 2-2, the inner surface of which is processed with convex micron-level radial strips, micron-level
  • the height of the radial bands and the distance between adjacent micron-level radial bands are sufficient to hold the droplets to ensure the Cassie-Baxter state of the surface, so the droplets present the Cassie-Baxter wetting model on the surface.
  • the structure With a uniformly changing wetting gradient, the wettability gradually increases from the outer side to the inner side of the circumference, so the structure has the function of pump-free directional transport of liquid and concentrated condensate, which is conducive to the concentration of reflux condensate at the heat source. Speed up the replenishment rate of the working fluid on the evaporation surface.
  • the inner surface of the top plate is processed with a radial structure with super-hydrophilic and super-hydrophobic phases.
  • the super-hydrophobic area increases the condensation nucleation area, and all are droplet-shaped condensation, reducing the heat transfer resistance and heat transfer efficiency It is greatly enhanced, and the super-hydrophilic zone has the ability to transport condensate to the outside under the action of surface tension, accelerating the circulation speed of the working medium.
  • This flat heat pipe reduces the sintering of the liquid-absorbing core by processing and modifying the top plate and bottom plate, and strengthens the evaporation and condensation speed on the premise of ensuring the reflux rate of the working medium, reduces the heat transfer heat resistance, and improves the evaporation area and the condensation area. Heat transfer performance, thereby improving the heat transfer capacity of the entire flat heat pipe.
  • the area of the superhydrophobic area is larger than the area of the superhydrophilic area; the surface area ratio of the superhydrophilic area and the superhydrophobic area is 1: 5.
  • f 1 is the ratio of the surface occupied by the solid, ⁇ 0 is the intrinsic contact angle, and ⁇ is the apparent contact angle;
  • ⁇ (l) arccos [r (1 + cos ⁇ 0 ) / l-1];
  • FIG. 5-1 The model of water droplets on the wedge-shaped super-hydrophilic trajectory is shown in Figure 5-1.
  • a single water droplet can be divided into a liquid convex part and a liquid front end during transmission.
  • the force situation is simplified to the mechanical model shown in Figure 5-2.
  • the difference of the Laplace force ⁇ P in the x direction of the water droplet is proportional to ⁇ LG / r (x), where ⁇ LG is the interfacial tension between water and air, r (x) is the radius of curvature of the water droplet, and can be pressed Formula estimate:
  • w (x) is the width of the superhydrophilic locus
  • ⁇ (x) is the contact angle of the water droplet
  • a is the initial width of the wedge-shaped superhydrophilic locus. Therefore, the difference ⁇ P of the Laplace force can be based on the following formula:
  • F x is proportional to tan ( ⁇ / 2) and inversely proportional to sin [ ⁇ (x)].
  • the flat heat pipe with a gradient wetting structure of the present invention is processed with a micron-level radial strip on the inner surface of the bottom plate as the evaporation surface of the flat heat pipe, showing a uniformly changing wetting gradient, and the structure has a centripetal center
  • the inner surface of the top plate as the condensation surface of the flat heat pipe is processed with a radial pattern of super affinity and hydrophobic phases.
  • the structure has the ability to transport condensate to the outside; inside the support plate A liquid-absorbing core structure is provided.
  • This flat heat pipe has the function of transporting liquid without pumping and collecting condensate reflux by micro-nano processing on the evaporation surface; patterned super-affinity and hydrophobic processing on the condensing surface, driving the condensate to migrate to the surrounding pipe wall direction, Accelerate the condensate return flow rate, at the same time, because the liquid wick structure on the upper and lower surfaces is omitted, the thermal resistance is reduced, the evaporation and condensation speed is strengthened, the heat exchange performance of the evaporation area and the condensation area is improved, and thus the entire flat heat pipe is improved. Heat exchange performance. Since the backflow driving of the working medium depends on the difference of the wetting gradient and the capillary force, the flat heat pipe of the present invention can better reflect the advantages of its excellent heat transfer performance under the condition of microgravity.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Chemical & Material Sciences (AREA)
  • Dispersion Chemistry (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

一种具有梯度润湿结构的平板热管，包括底板（11）、顶板（12）和位于底板（11）与顶板（12）之间的支撑板（13），底板（11）、顶板（12）及两侧支撑板（13）连接构成密封腔体；在底板（11）的内表面加工有微米级放射状条带，呈现由圆心到圆周均匀变化的润湿梯度；在顶板（12）的内表面加工有超亲水、超疏水间隔设置的放射状结构，用于向四周管壁方向运输冷凝液；在支撑板（13）内侧设有吸液芯（14）。通过对蒸发面进行微纳加工，使其具有无泵定向运输液体且汇集回流冷凝液的功能；对冷凝面进行图案化超亲、疏水加工，驱动冷凝液向四周管壁方向迁移，加快冷凝液回流速度，省去了上下表面的吸液芯结构，减小了热阻，强化了蒸发冷凝速度，提高了蒸发区和冷凝区的换热性能，从而提高了整个平板热管的换热性能。

Description

一种具有梯度润湿结构的平板热管 技术领域
本发明属于电子元器件散热装置技术领域，涉及一种具有梯度润湿结构的平板热管。
背景技术
随着电子技术的快速发展，电子元器件逐渐向小型化、高速高频化、高集成化发展，功能越来越复杂，散热热流密度越来越高，造成电子设备的故障率增加。因此实现电子元器件的高效散热，保证电子元器件的可靠性是目前的技术难点和研究热点。
平板热管是在传统热管的基础上经过改进而成的高效相变传热设备，具有结构简单，均温性好，传热高效的优点。它主要由外壳、吸液芯、工质等组成，工作原理与普通热管工作原理类似，利用工质的相变潜热带走电子元件的热量。当热量由热源通过平板热管的蒸发区时，低真空度密闭空腔内的工质液体沸腾气化，气体由于压差作用被压向冷凝区，在冷凝面气体遇冷凝结放热，在毛细力的作用下沿着吸液芯重新回流到蒸发区，蒸发面工质相变带走热源的热量，而冷凝面的热量由平板热管外部其他散热方式带走。与普通热管相比较，平板热管将一维传热升级为二维，有更好的均温性。
然而现有平板热管主要依靠吸液芯提供的毛细力来推动工质回流，且由于蒸发面冷凝面上都覆有吸液芯，多孔结构的吸液芯热阻较大，增加了整个热管的传热热阻。此外，烧结吸液芯结构本身需要耗能，并且烧结质量难以保证。
发明内容
为了克服上述现有技术的缺点，本发明的目的在于提供一种具有梯度润湿结构的平板热管，该平板热管结构设计合理，利用表面张力、毛细力共同作用引导 并加快工质回流速度，同时减少吸液芯的覆盖面，减少传热热阻从而提高整体换热能力。
为了达到上述目的，本发明采用以下技术方案予以实现：
本发明公开了一种具有梯度润湿结构的平板热管，包括底板、顶板和位于底板与顶板之间的支撑板，所述支撑板有两个，底板、顶板及两侧支撑板连接构成密封腔体；
在底板的内表面加工有微米级放射状条带，呈现由圆心到圆周均匀变化的润湿梯度，用于向圆心处无泵定向运输液体及汇集冷凝液；
在顶板的内表面加工有超亲水、超疏水间隔设置的放射状结构，用于向四周管壁方向运输冷凝液；
在支撑板内侧设有吸液芯，用于将液体从顶板边缘转移到底板边缘。
优选地，吸液芯利用粉末烧结于支撑板内侧，具有多孔结构；吸液芯的上、下两端分别与顶板和底板相连。
优选地，还包括设置在底板和顶板之间的若干根支撑柱，支撑柱的上、下两分别与顶板和底板相连。
进一步优选地，若干根支撑柱在底板和顶板之间均匀分布。
优选地，底板、顶板和支撑板之间采用焊接密封相连。
优选地，顶板内表面的放射状结构中，超疏水区的面积大于超亲水区的面积；进一步地，超亲水区和超疏水区的表面积比为1：5。
优选地，底板内表面上凸起的微米级放射状条带的高度以及相邻的微米级放射状条带之间的距离，满足能够将液滴托起以保证表面的Cassie-Baxter状态。
优选地，底板内表面的微米级放射状条带采用光刻法制备
与现有技术相比，本发明具有以下有益效果：
本发明的具有梯度润湿结构的平板热管，一方面，底板为平板热管蒸发面， 其内表面加工有微米级的放射状条带，液滴在该表面上能够呈现Cassie-Baxter的润湿模型，因而具有均匀变化的润湿梯度，且从圆周外侧至内侧，润湿性逐渐增大，该结构具有无泵定向运输液体与汇集冷凝液的功能，有利于将回流的冷凝液集中在热源处，加快蒸发面上工质的补给速率。另一方面，顶板内表面加工有超亲、疏水相间的放射状图案结构，超疏水区增加了冷凝成核区，且均为滴状凝结，减小了传热热阻，传热效率极大增强，而超亲水区在表面张力的作用下具有向四周管壁方向运输冷凝液的能力，加快工质的循环速度。可见，本发明的平板热管通过对顶板、底板进行加工改性，减少了吸液芯的烧结，保证工质回流速度的前提下强化了蒸发冷凝速度，减少了传热热阻，提高了蒸发区和冷凝区的传热性能，从而提升了整个平板热管的换热能力。
进一步地，平板热管密闭空腔内均匀布置若干个两端分别与底板、顶板相接触的支撑柱，用来防止平板热管表面发生变形。
进一步地，以硅基为例，底板表面结构的制备方法为光刻法，利用光刻法制备出表面的放射状微米级条带凸起。特别地，为了保证表面稳定的Cassie-Baxter状态，凸起的微米级条带需要足够高，条带之间的间距需要足够小能将液滴托起，同时也需要保证表面的疏水性。
附图说明
图1为本发明的具有梯度润湿结构平板热管的主视剖面图；
图2-1为本发明的具有梯度润湿结构平板热管的底板的俯视图；
图2-2为底板的运输区具备结构侧视图；
图3为本发明的具有梯度润湿结构平板热管的顶板的俯视图；
图4-1为底板表面梯度润湿结构的机理Cassie模型示意图；
图4-2为底板表面的固体所占比模型示意图；
图4-3为液滴运动方向原理示意图；
图5-1为水滴在楔形超亲水轨迹上的模型图；
图5-2为水滴自发运动过程中的受力情况力学模型图。
其中：11为底板；12为顶板；13为支撑板；14为吸液芯；15为支撑柱。
具体实施方式
为了使本技术领域的人员更好地理解本发明方案，下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本发明一部分的实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都应当属于本发明保护的范围。
需要说明的是，本发明的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本发明的实施例能够以除了在这里图示或描述的那些以外的顺序实施。此外，术语“包括”和“具有”以及他们的任何变形，意图在于覆盖不排他的包含，例如，包含了一系列步骤或单元的过程、方法、系统、产品或设备不必限于清楚地列出的那些步骤或单元，而是可包括没有清楚地列出的或对于这些过程、方法、产品或设备固有的其它步骤或单元。
下面结合附图对本发明做进一步详细描述：
如图1所示，本发明的具有梯度润湿结构的平板热管，包括底板11、顶板12、位于顶板与底板之间的支撑板13，所述底板11、顶板12、支撑板13密封连接形成密封腔体；作为平板热管蒸发面的底板11内表面加工有微米级的放射状条带，呈现出均匀变化的润湿梯度，所述结构具有无泵定向运输液体与汇集冷凝液的功能；作为平板热管冷凝面的顶板12内表面加工有超亲、疏水相间的放射状图案，所述结构具有向四周管壁方向运输冷凝液的能力。
所述支撑板13内侧置有吸液芯14。吸液芯14为多孔结构，采用烧结法烧结于支撑板13的内侧；吸液芯14的上、下两端分别与顶板12和底板11相连。
优选地，还包括设置在底板11和顶板12之间的若干根支撑柱15，支撑柱15的上、下两分别与顶板12和底板11相连。
更进一步优选地，若干根支撑柱15在底板11和顶板12之间均匀分布。底板11、顶板12和支撑板13之间采用焊接密封相连。
本发明是适用于电子器件散热的平板热管，底板11为平板热管蒸发面，如图2-1和图2-2所示，其内表面加工有凸起的微米级的放射状条带，微米级放射状条带的高度以及相邻的微米级放射状条带之间的距离，满足能够将液滴托起以保证表面Cassie-Baxter状态，因此液滴在该表面上呈现Cassie-Baxter的润湿模型，具有均匀变化的润湿梯度，从圆周外侧至内侧，润湿性逐渐增大，因此所述结构具有无泵定向运输液体与集中冷凝液的功能，有利于将回流的冷凝液集中在热源处，加快蒸发面上工质的补给速率。
如图3所示，顶板内表面加工有超亲水、超疏水相间的放射状结构，超疏水区增加了冷凝成核区，且均为滴状凝结，减小了传热热阻，传热效率极大增强，而超亲水区在表面张力的作用下具有向外侧运输冷凝液的能力，加快工质的循环速度。此平板热管通过对顶板、底板进行加工改性，减少了吸液芯的烧结，保证工质回流速度的前提下强化了蒸发冷凝速度，减少了传热热阻，提高了蒸发区和冷凝区的传热性能，从而提升了整个平板热管的换热能力。
优选地，顶板12内表面的放射状结构中，超疏水区的面积大于超亲水区的面积；超亲水区和超疏水区的表面积比为1：5。
下面结合底板表面梯度润湿结构的机理说明本发明对底板的改性设计优势。
如图4-1所示的Cassie模型，Cassie-Baxter方程：cosθ＝f 1cosθ 0-(1-f 1)；
其中，f 1是固体所占表面比，θ 0是本征接触角，θ是表观接触角；
如图4-2所示，表面的固体所占比可写为：
Figure PCTCN2018119423-appb-000001
Figure PCTCN2018119423-appb-000002
θ(l)＝arccos[r(1+cosθ 0)/l-1]；
θ∈,cosθ为单调递减函数，当l减小时，cosθ增大，θ减小。l越小，表面更趋于亲水。
如图4-3所示：θ B＜θ A，液滴运动方向为A→B，因此，液滴向中间汇集。
下面结合顶板液滴运输机理说明本发明对顶板的改性设计优势。
水滴在楔形超亲水轨迹上的模型如图5-1所示，单个水滴在传输过程中可分为液体凸起部分和液体前端，在拉普拉斯力的作用下水滴自发运动过程中的受力情况简化为图5-2所示的力学模型。水滴x方向的拉普拉斯力之差ΔP与γ LG/r(x)成正比，其中γ LG为水与空气之间的界面张力，r(x)是水滴的曲率半径，并可按下式估算：
Figure PCTCN2018119423-appb-000003
Figure PCTCN2018119423-appb-000004
式中，w(x)是超亲水轨迹的宽度，θ(x)是水滴的接触角，a是楔形结构超亲水轨迹的初始宽度。因此，拉普拉斯力之差ΔP可根据下式：
Figure PCTCN2018119423-appb-000005
水滴在x方向的合力为F x＝ΔP·S x其中S x为x方向的横截面积，假设横截面积为圆形截面的一部分，那么S x正比于πr 2(x)。
Figure PCTCN2018119423-appb-000006
F x与tan(α/2)成正比，与sin[θ(x)]成反比。
综上所述，本发明的具有梯度润湿结构的平板热管，作为平板热管蒸发面的底板内表面加工有微米级的放射状条带，呈现出均匀变化的润湿梯度，所述结构具有向圆心处无泵定向运输液体与集中冷凝液的功能；作为平板热管冷凝面的顶板内表面加工有超亲、疏水相间的放射状图案，所述结构具有向外侧运输冷凝液的能力；所述支撑板内部置有吸液芯结构。此平板热管通过对蒸发面进行微纳加工，使其具有无泵定向运输液体且汇集回流冷凝液的功能；对冷凝面进行图案化超亲、疏水加工，驱动冷凝液向四周管壁方向迁移，加快冷凝液回流速度，同时由于省去了上下表面的吸液芯结构，减小了热阻，强化了蒸发冷凝速度，提高了蒸发区和冷凝区的换热性能，从而提高了整个平板热管的换热性能。由于工质的回流驱动依靠润湿梯度的差异与毛细力，因而本发明的平板热管在微重力情况下更能体现其优良传热性能的优势。
以上内容仅为说明本发明的技术思想，不能以此限定本发明的保护范围，凡是按照本发明提出的技术思想，在技术方案基础上所做的任何改动，均落入本发明权利要求书的保护范围之内。

Claims (9)

  1. 一种具有梯度润湿结构的平板热管，其特征在于，包括底板(11)、顶板(12)和位于底板(11)与顶板(12)之间的支撑板(13)，所述支撑板(13)有两个，底板(11)、顶板(12)及两侧支撑板(13)连接构成密封腔体；
    在底板(11)的内表面加工有微米级放射状条带，呈现由圆心到圆周均匀变化的润湿梯度，用于向圆心处无泵定向运输液体及汇集冷凝液；
    在顶板(12)的内表面加工有超亲水、超疏水间隔设置的放射状结构，用于向四周管壁方向运输冷凝液；
    在支撑板(13)内侧设有吸液芯(14)。
  2. 根据权利要求1所述的具有梯度润湿结构的平板热管，其特征在于，吸液芯(14)为多孔结构，采用烧结法烧结于支撑板(13)的内侧；吸液芯(14)的上、下两端分别与顶板(12)和底板(11)相连。
  3. 根据权利要求1所述的具有梯度润湿结构的平板热管，其特征在于，还包括设置在底板(11)和顶板(12)之间的若干根支撑柱(15)，支撑柱(15)的上、下两分别与顶板(12)和底板(11)相连。
  4. 根据权利要求3所述的具有梯度润湿结构的平板热管，其特征在于，若干根支撑柱(15)在底板(11)和顶板(12)之间均匀分布。
  5. 根据权利要求1所述的具有梯度润湿结构的平板热管，其特征在于，底板(11)、顶板(12)和支撑板(13)之间采用焊接密封相连。
  6. 根据权利要求1所述的具有梯度润湿结构的平板热管，其特征在于，顶板(12)内表面的放射状结构中，超疏水区的面积大于超亲水区的面积。
  7. 根据权利要求6所述的具有梯度润湿结构的平板热管，其特征在于，超亲水区和超疏水区的表面积比为1：5。
  8. 根据权利要求1所述的具有梯度润湿结构的平板热管，其特征在于，底板(11)内表面上凸起的微米级放射状条带的高度以及相邻的微米级放射状条带 之间的距离，满足能够将液滴托起以保证表面Cassie-Baxter状态。
  9. 根据权利要求1或8所述的具有梯度润湿结构的平板热管，其特征在于，底板(11)内表面的微米级放射状条带采用光刻法制备。
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