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WO2010078701A1 - 一种分段式汽液相变换热器的汽液分离方法及换热器 - Google Patents

一种分段式汽液相变换热器的汽液分离方法及换热器 Download PDF

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Publication number
WO2010078701A1
WO2010078701A1 PCT/CN2009/000468 CN2009000468W WO2010078701A1 WO 2010078701 A1 WO2010078701 A1 WO 2010078701A1 CN 2009000468 W CN2009000468 W CN 2009000468W WO 2010078701 A1 WO2010078701 A1 WO 2010078701A1
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WO
WIPO (PCT)
Prior art keywords
liquid
vapor
hole
heat exchanger
auxiliary
Prior art date
Application number
PCT/CN2009/000468
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English (en)
French (fr)
Inventor
彭晓峰
吴迪
王珍
陆规
张易阳
Original Assignee
清华大学
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Publication date
Application filed by 清华大学 filed Critical 清华大学
Publication of WO2010078701A1 publication Critical patent/WO2010078701A1/zh

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Classifications

    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05325—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007—Condensers

Definitions

  • the present invention relates to a vapor-liquid phase shift heat exchanger, and more particularly to a vapor-liquid separation method and a heat exchanger for a segmented vapor-liquid phase shift heat exchanger.
  • Vapor-to-liquidity converters are widely used in energy systems, power engineering, chemical and petrochemical, automotive industries, such as thermal power station air condensers, air conditioning engineering, automotive air conditioning, and evaporation and condensers in chemical processes.
  • the steam flow rate in the pipe is obviously reduced, the condensation effect is drastically degraded, and the heat transfer coefficient is reduced.
  • the single pipe internal process condensation process also leads to complex vapor-liquid two-phase flow, which has a very good system operation stability, flow resistance and system regulation. negative effect.
  • the thermal resistance of the condensing heat transfer in the tube increases, and the temperature of the outer tube wall decreases, resulting in a decrease in the utilization rate of the ribs.
  • the conventional air-cooled condenser satisfies the demand of heat exchange amount by increasing the heat exchange area, but has a large volume and weight, and is high in manufacturing and running costs. There are similar problems with the evaporator.
  • each tube can be in a short tube bead or unstable thin liquid film condensation, Or through the influence of steam on the liquid film to promote the instability and fracture of the liquid film, the formation of membrane-like condensation and bead-like coexistence of the stream-like condensation, enhance the film-like condensation heat transfer effect, and improve the condensation heat transfer coefficient inside the pipe.
  • the headers 2 of the above two patents all use a single drain tube as the liquid leakage and vapor blocking device 30.
  • the thinner drain pipe can better prevent the separated gas in the header from leaking from the drain pipe, but this structure brings the following problems: First, the diameter of the drain pipe is smaller than the diameter of the header, and the flow range of the condensate is compared. Large restrictions, sometimes the problem of poor drainage.
  • a liquid dispensing device consisting of a solid cap 31, a porous core 32 and a drain wall 33 is used (as shown in Figure 3)
  • the upper surface of the dispensing device is a solid cap, The contact surface of the condensate and the liquid separation device in the operation of the condenser is the side surface of the porous medium.
  • the liquid-dispensing driving force of the liquid separation device is mainly the capillary suction force of the porous core body, and the suction force is selected by the porous medium selected.
  • the structural parameters determine that the self-regulating ability is weak. When the amount of condensate is large, there may be a problem of insufficient suction force, which affects the effect of liquid separation. In addition, the structure of the liquid separation device is complicated, and it is scaled up in industrial production. Production and subsequent installation work will bring certain difficulties.
  • an object of the present invention is to provide a vapor-liquid separation method and a heat exchanger for a segmented vapor-liquid phase change heat exchanger capable of performing vapor-liquid separation more efficiently.
  • a vapor-liquid separation method for a segmented vapor-liquid phase change heat exchanger characterized in that it comprises the following contents: 1) at least two sets of heat exchange tubes The ends are respectively provided with a continuous through box, and a plurality of liquid leakage and steam blocking devices which can be embedded in the header are staggered in the two connected boxes, and the two connected boxes are separated into a plurality of liquids which are sequentially connected Space, the liquid leakage and vapor blocking device is provided with at least one equivalent main hole and a plurality of equivalent auxiliary holes; 2) when the liquid in the liquid separation space is small, the liquid film formed at the top of the main hole and the auxiliary hole It can prevent the vapor from entering the liquid separation space of the lower-stage header of the same side; 3) When the accumulated liquid in one of the liquid-dividing spaces accumulates more, under the action of pressure, the liquid will first break through the main hole with larger aperture Outflow, and the smaller diameter auxiliary hole continues to be sealed
  • the main hole has an equivalent diameter of 2 to 5 ram, and the auxiliary hole has an equivalent diameter of less than 2 awake.
  • the flow capacity of the liquid leakage and vapor barrier device is characterized by the porosity S: S Ap /A ⁇ where ⁇ , A, respectively, the ratio of the total flow area of the main hole and the auxiliary hole to the surface area of the liquid leakage blocking device, and the porosity S is
  • the vapor-liquid phase shift heat exchanger system has a circulating flow rate of 20 to 50%.
  • a segmented vapor-to-liquid heat exchanger using the above method characterized in that it comprises at least one set of heat exchange tubes, respectively connected at both ends of the heat exchange tube to a continuous through box, in two
  • a plurality of liquid leakage and vapor blocking devices are staggered in the header, and the two headers are separated into a plurality of liquid separation spaces sequentially connected
  • the liquid separation space is connected to a steam inlet pipe, and the liquid separation space at the bottom of the two ends is connected in parallel with a liquid discharge pipe, and the liquid leakage and steam blocking device is provided with at least one main hole and a plurality of auxiliary holes.
  • the liquid leakage and vapor blocking device is a substrate that can be embedded in the header.
  • the substrate is provided with at least one main hole having an equivalent diameter of 2 to 5 inches and a plurality of auxiliary holes having an equivalent diameter of less than 2 mm.
  • the main hole and the auxiliary hole on the substrate are straight holes of the same upper and lower equivalent diameters, respectively.
  • the main hole and the auxiliary hole on the substrate are respectively a frustum hole, and may also be a variable cross-section through hole.
  • a plurality of auxiliary holes on the substrate intersect the edge of the main hole to form an integral plum-like hole.
  • a plurality of independent auxiliary holes are provided between the unitary plum-shaped holes and the edges of the substrate.
  • a porous dielectric core is disposed in the main hole and the auxiliary hole.
  • the material of the substrate is a metal material.
  • the material of the substrate is a porous dielectric material.
  • the invention adopts the above technical solutions, and has the following advantages: 1.
  • the invention provides a straight-through header box at both ends of a group of heat exchange tubes, and the two boxes are separated into two in the header box by the embedded liquid leakage and gas blocking device. a plurality of liquid separation spaces sequentially connected, at the same time, at least one main hole and a plurality of auxiliary holes are arranged on the substrate of the liquid leakage choke device, so when less condensed liquid is generated in the heat exchange tube upstream of the heat exchanger header, The liquid separated by the header will form a water film on the surface of the main hole and the auxiliary hole to prevent the vapor from flowing out of the main hole and the auxiliary hole; when the liquid amount is slightly increased, the main hole with a larger diameter will first permeate.
  • the liquid is equivalent to the discharge of a single drain pipe in the prior art; when the amount of the separated liquid is large, the pressure of the liquid destroys the liquid film covering the surface of the auxiliary hole, and also leaks from the auxiliary hole, thereby It is equivalent to increasing the drainage of a plurality of drain pipes, which solves the problem that the amount of liquid discharged in the prior art is limited.
  • the present invention has a plurality of holes that can be leaked on the substrate, and the equivalent diameter of the holes can be changed according to design requirements. Therefore, although the equivalent pore diameter of each hole is relatively small, the total leakage amount is larger. Large, especially the setting of different equivalent apertures can automatically adjust the number of leaking apertures according to the change of the amount of liquid, and the structure design is very clever. 3.
  • the equivalent pore diameter can be small, and the smaller equivalent pore size distribution can generate a large surface tension, thereby effectively ensuring the vapor barrier capability of the present invention, and the porous substrate. It also has obvious advantages in solving the problem that the oil in the system blocks the liquid core. 4. Since the porous medium core is disposed in the main hole and the auxiliary hole, even if the flow rate of the condensate is very small, the pore structure of the pore structure can be ensured by the smaller pore structure of the porous medium core, and the present invention Filling the porous dielectric core without changing the pore structure can effectively increase Strong pore surface tension to enhance the ability to block steam.
  • the invention directly embeds the liquid leakage and steam blocking device in the header box, and has advantages in the prior processing, operation stability and post maintenance compared with the prior art, and is suitable for the requirements of industrialized module production. 6.
  • the vapor-liquid separation method of the present invention is applied to a conventional air-cooled vapor-liquid phase change heat exchanger or evaporator, the liquid-liquid separation effect of the heat exchanger can be remarkably improved, and the present invention can be widely applied to energy sources.
  • Systems, power engineering, chemical and petrochemical, automotive industries such as thermal power station air condensers, air conditioning engineering and chemical systems, automotive air conditioning vapor-liquid converters and so on.
  • Figure 1 is a prior art split air condenser
  • Figure 2 is a prior art multi-stage condensing, intermediate liquid air condenser
  • Figure 3 is a schematic view showing the structure of the liquid leakage and vapor barrier device of Figure 2
  • FIG. 4 and FIG. 5 are schematic diagrams showing the arrangement of the liquid leakage and vapor blocking device of the present invention in the left and right side headers.
  • FIG. 6 and FIG. 7 are front and top views of the first embodiment of the present invention.
  • FIG. 8 and FIG. 9 are front and top views of Embodiment 2 of the present invention.
  • FIGS. 10 and 11 are front and top views of a third embodiment of the present invention.
  • FIG. 12 and FIG. 13 are front and top views of a fourth embodiment of the present invention.
  • FIG. 14 and FIG. 15 are front and top views of a fifth embodiment of the present invention.
  • 16 and 17 are front and top views of a sixth embodiment of the present invention.
  • FIG. 18 and FIG. 19 are front and top views of a seventh embodiment of the present invention.
  • 20 and 21 are front and top views of an embodiment 8 of the present invention.
  • Figure 22 is a liquid-discharged air condenser using the method of the present invention.
  • the heat exchanger of the present invention comprises at least one set of heat exchange tubes 1 arranged one above the other, and a vertical connection box 2 for connecting the upper and lower sides of the heat exchange tubes 1 is respectively disposed at the left and right ends of the heat exchange tubes 1.
  • the dry leakage liquid blocking device 10 is disposed at intervals in the two header boxes 2, and the liquid leakage blocking device 10 in the two header boxes 2 is arranged in a staggered manner, so that the two header boxes 2 form a plurality of points which are connected in order.
  • the size of each liquid separation space gradually decreases according to the change of the liquid separation amount.
  • a first inlet box space (left side in the drawing, but not limited thereto) is connected to an inlet pipe 3, and both sides of the header 2
  • the bottom of the bottom is connected in parallel with an outlet pipe 4, and the heat exchange tube 1 is provided with fins 5.
  • the liquid leakage and vapor barrier device 10 of the present invention comprises a substrate 11 embedded in the header 2, and the substrate is provided with at least one main hole having an equivalent diameter of 2 to 5 mm and a plurality of auxiliary holes having an equivalent diameter of less than 2.
  • the following is an embodiment of the liquid leakage and vapor barrier device 10 of the present invention.
  • the liquid leakage and vapor blocking device 10 of the present invention comprises a substrate 11 having the same cross-sectional size as the heat exchanger header 2, and the center of the substrate 11 has a main body having an equivalent diameter of 2 to 5 ram and the same diameter.
  • the holes 12 are evenly arranged around the main holes 12 with a plurality of auxiliary holes 13 having an equivalent diameter of less than 2 mm and the same equivalent diameter.
  • the body flows out from the main hole 12 and the auxiliary hole 13; when the liquid amount is slightly increased, the main hole 12 having a larger hole diameter will first permeate, which is equivalent to the discharge of a single drain pipe in the prior art.
  • the pressure of the liquid destroys the liquid film covering the surface of the auxiliary hole 13, and also oozes out from the auxiliary hole 13, which is equivalent to increasing the drainage of the plurality of drain pipes, and solving There is a problem in the prior art that the amount of liquid discharged is limited.
  • the main hole 12 and the auxiliary hole 13 in this embodiment have a size range similar to that of Embodiment 1, except that the main hole 12 and the auxiliary hole 13 are frustum holes of variable equivalent aperture, equivalent.
  • the aperture can be large above, small below; it can also be small and large, or it can be any variable sectional area.
  • the structure can make a certain amount of condensate can be carried in both the main hole 12 and the auxiliary hole 13.
  • the main hole can ensure the continuity of the liquid discharge when the amount of the condensate is relatively low, and can prevent the steam from passing through; the auxiliary hole 13
  • the condensate in the pores can improve its steam blocking ability, prevent steam from passing through, and can also improve the steam blocking capacity and accelerate the liquid discharge according to the pore shape.
  • the main hole 12 and the auxiliary hole 13 in this embodiment are intersected with each other, and a "Plum" hole-shaped structure is presented.
  • the intersecting plum blossom hole structure can be regarded as an extended structure of the main hole.
  • the flow equivalent diameter is increased, and the condensate flow capacity of the main hole 12 can be effectively enhanced, and the auxiliary hole 13 is simultaneously provided.
  • Intersection with the main orifice 12 enables adhesion of a certain condensate by surface tension when the amount of liquid is relatively small, enhancing the vapor blocking liquid sealing capability of the apparatus.
  • Example 4 As shown in Figs. 12 and 13, the auxiliary hole 13 in this embodiment intersects the main hole 12 to form a "blossom" hole-shaped structure, and an auxiliary hole 13 which does not intersect the main hole 12 is provided.
  • This is a combination of the above structures, which ensures that the liquid leakage and vapor barrier device has an adjustment capability in a larger flow range while the flow area is increased.
  • the function of the above structure is mainly to strengthen the steam blocking capacity and the liquid flow regulating ability of the liquid leakage and vapor blocking device by using a combination of different equivalent pore sizes on the pore structure, and the main hole 12 ensures the basic liquid leakage capacity of the liquid leakage and vapor blocking device, and the auxiliary The hole 13 ensures the liquid flow regulating capability of the liquid leakage and vapor blocking device, and when the liquid amount is small, the steam is blocked by the liquid sealing action.
  • the use of the above-mentioned porous structural substrate 11 directly has an obvious advantage in solving the problem that the heat exchanger system oil blocks the substrate 11 .
  • the porous dielectric core 4 is provided in the main hole 12 and the auxiliary hole 13 provided in the fabricated substrate 11.
  • a smaller pore structure is required to ensure the vapor barrier capability of the pore structure, and the porous dielectric core 4 is filled, without changing the pore structure. Enhance the surface tension of the pores and enhance the resistance to steam.
  • the suction of the porous medium core 4 can also ensure the circulation of the condensate, and achieve the liquid separation under a small refrigerant flow rate.
  • the porous dielectric core 4 is disposed in the aperture of the "Plum" hole-shaped structure in which the main hole and the auxiliary hole intersect, and the structure can be provided on the basis of the characteristics of the above-mentioned Embodiment 3.
  • the steam blocking effect of the device is enhanced.
  • a porous dielectric core 4 is provided in each hole.
  • This structure is a combination of the structures described in the above Embodiment 4, and the flow-receiving area is increased while ensuring that the liquid-leakage and vapor-blocking device has an adjustment capability in a larger flow range, and at the same time, the steam-blocking effect of the device is ensured.
  • this embodiment is similar to Embodiment 1, but a porous dielectric material is used as the substrate 11, and the structure of the main hole 12 and the auxiliary hole 13 is matched, and the porous structure of the porous dielectric material itself ensures the steam blocking capability.
  • the through-hole structure ensures leakage and shunting capability.
  • the liquid leakage and vapor blocking device 10 adopts the same solid material or solid porous medium as the cross section of the header 2 as the substrate 11, generally a metal material, under the premise of ensuring no leakage contact with the header. , other materials can also be used.
  • the substrate is directly embedded in the position determined in the header, and the metal substrate is generally fixed by welding, and the structure is greatly simplified.
  • the pores on the perforated plate may be composed of pores of different equivalent pore sizes and structures.
  • Each pore structure may be a variable-equivalent pore diameter or a same-equivalent pore diameter
  • the porous medium may be a porous medium or a mesh made by sintering powder particles.
  • Example 9 The method of the present invention can be applied to various refrigeration and heating equipment.
  • this embodiment is applied in a liquid-distributing air condenser, and the header 2 equipped with the liquid leakage and vapor blocking device 10 replaces the liquid separation tube and the header in the original liquid-type air condenser.
  • the structure one side of the header 2 is connected to the other side header 2 through the heat exchange tube, and the left and right side headers 2 are interlaced and fixed with a plurality of liquid leakage and vapor blocking devices 10, and the two side headers 2 are separated into left and right sides.
  • the first-stage header 2 is connected to a liquid inlet pipe 3, and the bottom of the two sides of the header box 2 is connected in parallel to a liquid outlet pipe 4, and the heat-exchange pipe 1 is provided with fins 5 .
  • the condensate generated by the heat exchange between the heat exchange tubes 1 is concentrated in the upper part of the liquid leakage blocking device 10 due to gravity in the header 2, and as the condensate accumulates, the condensate will be under the action of gravity. Firstly, it is discharged by the main hole 12 having a larger aperture. The smaller diameter auxiliary hole 13 is sealed by a small amount of liquid film formed by the condensate, effectively preventing the passage of steam, and when the amount of the condensate is relatively large, the leakage resistance is large.
  • the condensate accumulated in the upper portion of the steam device 10 is increased, the thickness of the liquid layer is increased, the pressure head generated by gravity is increased, and the flow capacity of the small-diameter auxiliary hole 13 is activated, which can effectively reduce excessive aggregation of the condensate in the upper portion of the liquid separation device.
  • the flow capacity test of the hole shows that the flow rate of the condensate of the through hole is roughly proportional to the flow area of the through hole at a certain liquid level. Therefore, the flow capacity of the liquid leakage blocking device 10 is characterized by defining the parameter porosity S.
  • p and A are the sum of the flow areas of the respective holes and the surface area of the substrate.
  • the parameter S is determined by the circulating flow of the condenser system, approximately 20 to 50% for this purpose.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Description

一种分段式汽液相变换热器的汽液分离方法及换热器 技术领域
本发明涉及一种汽液相变换热器， 特别是关于一种分段式汽液相变换热 器的汽液分离方法及换热器。
背景技术
汽液相变换热器广泛应用于能源系统、 动力工程、 化工和石油化工、 汽 车工业等行业， 比如火力电站空气冷凝器、 空调工程、 车用空调及化工工艺 中的蒸发和冷凝器等等。
传统空冷式汽液相变换热器多采用蛇形管流程， 依靠空气在管外对流换 热， 工质流体在管内冷凝或蒸发。 管内凝结换热中， 随着冷凝的进行， 壁面 凝结液逐步增加， 随后成膜阻碍了蒸汽与壁面的接触， 是凝结换热的主要热 阻所在。 凝结过程中液膜逐渐增厚， 在以后相当长的管程内为液体逐步增多 的复杂两相流， 热阻逐渐增加， 冷凝效果严重变差； 同时随着蒸汽的凝结， 蒸汽量逐渐降低， 管内蒸汽流速明显下降， 凝结效果急剧退化， 换热系数减 小； 单一管内流程冷凝过程也导致了复杂的汽液两相流， 对系统运行稳定性、 流动阻力和系统的调控等， 都有很不利的影响。 空气侧， 由于管内冷凝换热 热阻增加， 外管壁温度下降， 导致肋片的利用率下降。 为解决上述存在的问 题，传统空气冷却式冷凝器以加大换热面积来满足换热量的需求，但是体积、 重量较大， 且制作和运行成本高。 对于蒸发器来说也有类似的问题。
本申请人在专利号为 ZL200610113304. 4, 名称为 "分液式空气冷凝器" (如图 1所示）， 以及专利申请号为 200710064952. X， 名称为 "多级冷却中 间分液式空气冷凝器" （如图 2所示） 的发明专利中提出了采用多级蒸汽冷 凝、 中间自动汽液分离和排液、 集中聚集冷凝液过冷的技术方案， 从而保证 了各管程都以纯蒸汽进入并被冷却， 有效减小了凝结过程中液膜的厚度和消 除不利的两相流型； 充分利用了短换热管， 使各管程均能处于短管珠状或不 稳定的薄液膜凝结， 或通过蒸汽对液膜的影响作用促进液膜失稳与断裂， 形 成膜状凝结与珠状凝结共存的溪流状凝结， 增强膜状凝结换热效果， 提高管 内凝结换热系数。
上述两专利中的联箱 2都是使用单根排液管作为漏液阻汽装置 30， 这种 较细的排液管可以较好地防止联箱中分离的气体从排液管泄漏， 但是这种结 构又带来以下问题： 首先排液管直径比联箱直径小， 冷凝液流量范围受到较 大的限制， 有时还会出现排液不畅的问题。 尽管在后一项专利中采用了由实 心顶盖 31、 多孔芯体 32和排液管壁面 33组成的分液装置 （如图 3所示）， 但是由于分液装置上表面采用实心顶盖， 冷凝器运行中冷凝液与分液装置接 触面为多孔介质侧表面， 因此分液装置的分液驱动力主要是多孔芯体的毛细 抽吸力， 而抽吸力的大小是由所选用多孔介质的结构参数决定， 自主调节能 力较弱， 当冷凝液量较大时， 可能会存在抽吸力不够的问题， 影响到分液的 效果； 另外分液装置结构比较复杂， 在工业生产中规模化生产以及后续的安 装工作都会带来一定的困难。
发明内容
针对以上问题， 本发明的目的是提供一种能够更有效地进行汽液分离的 分段式汽液相变换热器的汽液分液方法及换热器。
为了实现上述目的， 本实用新型采取以下技术方案： 一种分段式汽液相 变换热器的汽液分离方法， 其特征在于： 其包括以下内容： 1 )在至少一组换 热管的两端分别设置一直通的联箱， 在两所述联箱内交错设置有若干可镶嵌 入所述联箱内的漏液阻汽装置， 将两所述联箱分隔为顺序连通的多个分液空 间， 所述漏液阻汽装置上设置有至少一个当量主孔和若干个当量辅助孔； 2) 当所述分液空间内的积液较少时， 主孔和辅助孔顶部形成的液膜可阻止汽体 进入同侧下一级联箱的分液空间； 3)当一个所述分液空间内的积液积累较多 时， 在压力作用下积液会首先穿破孔径较大的主孔流出， 而直径较小的辅助 孔继续由顶部形成的液膜封住；4)当一个所述分液空间内的积液层厚度增大， 在压力作用下会逐步穿破孔径较小的辅助孔，同时从所述主孔和辅助孔流出。
所述的主孔当量直径为 2〜5ram， 辅助孔当量直径小于 2醒。
所述漏液阻汽装置的流通能力由孔隙率 S表征： S Ap /A^ 其中 ^， A, 分别为主孔和辅助孔总流通面积与漏液阻汽装置表面积的比值， 孔隙率 S为 汽液相变换热器系统循环流量的 20〜50%。
一种应用上述方法的分段式汽液相变换热器， 其特征在于： 它包括至少 一组换热管， 在所述换热管的两端分别连通一直通的联箱， 在两所述联箱内 交错设置有若干漏液阻汽装置， 将两所述联箱分隔为顺序连通的多个分液空 间， 第一级所述分液空间连接一进汽管， 两端最底部的所述分液空间并联连 接一出液管， 漏液阻汽装置上设置有至少一个主孔和若干个辅助孔。
所述漏液阻汽装置为一可镶嵌入所述联箱内的基板， 所述基板上设置有 至少一个当量直径为 2〜5誦的主孔和若干个当量直径小于 2mm的辅助孔。
所述基板上的所述主孔和辅助孔分别为上、 下当量直径相同的直型孔。 所述基板上的主孔和辅助孔分别为锥台孔， 也可以为变截面通孔。
所述基板上的若干辅助孔与所述主孔边缘相交，形成一整体的梅花状孔。 在所述整体的梅花状孔与所述基板的边缘之间设置有若干独立的辅助 孔。
在所述主孔和辅助孔中设置有多孔介质芯。
所述基板的材料为金属材料。
所述基板的材料为多孔介质材料。
本发明由于采取以上技术方案， 其具有以下优点： 1、 本发明在一组换热 管的两端设置直通的联箱， 在联箱中通过嵌入的漏液阻气装置将两联箱分隔 成顺序连通的多个分液空间， 同时在漏液阻气装置的基板上设置至少一个主 孔和若干辅助孔， 因此当换热器联箱上游换热管中产生的冷凝液体较少时， 由联箱分离出来的液体就会在主孔和辅助孔表面形成一层水膜， 阻止汽体从 主孔和辅助孔中流出； 当液量稍增大时， 孔径较大的主孔会首先渗液， 相当 于现有技术中的单根排液管排液； 当分离出来的液量较大时， 液体的压力会 破坏覆盖在辅助孔表面的液膜， 而从辅助孔也渗出， 从而相当于增加了为多 根排液管排液， 解决了现有技术中排液量受到限制的问题。 2、 本发明由于在 基板上设置了多个可以漏液的孔， 且孔的当量直径大小可以根据设计要求有 所变化， 因此每个孔的当量孔径虽然比较小， 但是整体漏液总量较大， 特别 是不同当量孔径孔的设置可以根据积液量的变化， 自动调节漏液孔径的数量， 结构设计非常巧妙。 3、本发明由于在基板上的开孔数量多， 因此当量孔径可 以较小， 较小的当量孔径分布能够产生较大表面张力， 从而有效地保证了本 发明的阻汽能力， 同时多孔的基板在解决系统内机油堵塞分液芯方面也具有 明显的优势。 4、 本发明由于在主孔和辅助孔中设置了多孔介质芯， 因此即使 是冷凝液流量非常小时， 也可以通过多孔介质芯更小的孔隙结构来保证孔结 构的阻汽能力， 本发明在不改变孔结构的条件下填充多孔介质芯， 可有效增 强孔隙表面张力作用， 强化阻汽能力。 同时由于多孔介质芯的抽吸作用也可 以较好的保证冷凝液的流通， 实现小制冷剂流量下的分液功能。 5、本发明将 漏液阻汽装置直接镶嵌在联箱中， 与现有技术相比， 无论从前期加工、 运行 稳定性及后期维护上都具有其优势， 适应于产业化模块生产的要求。 6、 当本 发明的汽液分离方法被应用在传统空冷式汽液相变换热器或蒸发器中时， 可 以显著地改善换热器的漏液汽液分离效果，本发明可以广泛应用于能源系统、 动力工程、 化工和石油化工、 汽车工业等行业， 比如火力电站空气冷凝器、 空调工程及化工系统、 车用空调汽液相变换热器等等。
附图说明
图 1是已有技术的分液式空气冷凝器
图 2是己有技术的多级冷凝、 中间分液的空气冷凝器
图 3是图 2中的漏液阻汽装置的结构示意图
图 4、 图 5是本发明漏液阻汽装置在左、 右两侧联箱中设置示意图 图 6、 图 7是本发明实施例 1的主视和俯视示意图
图 8、 图 9是本发明实施例 2的主视和俯视示意图
图 10、 图 11是本发明实施例 3的主视和俯视示意图
图 12、 图 13是本发明实施例 4的主视和俯视示意图
图 14、 图 15是本发明实施例 5的主视和俯视示意图
图 16、 图 17是本发明实施例 6的主视和俯视示意图
图 18、 图 19是本发明实施例 7的主视和俯视示意图
图 20、 图 21是本发明实施例 8的主视和俯视示意图
图 22是采用本发明方法的分液式空气冷凝器
具体实施方式
下面结合附图和实施例对本发明进行详细的描述。
如图 4所示， 本发明的换热器包括至少一组上下排列的换热管 1， 在换 热管 1的左右两端分别设置一连通换热管 1的上、下直通的联箱 2， 两联箱 2 内分别间隔设置有 干漏液阻汽装置 10， 两联箱 2内的漏液阻汽装置 10的 设置位置呈交错状， 使两联箱 2形成左右顺序连通的多个分液空间， 各分液 空间大小根据分液量的变化呈逐渐递减状。如果本发明的换热器作为冷凝器， 在第一级联箱空间（图中为左侧， 但不限于此）连接一进汽管 3， 两侧联箱 2 的底部并联连接一出液管 4， 换热管 1上设置有翅片 5。本发明的漏液阻汽装 置 10包括镶嵌入联箱 2内的基板 11，基板上设置有至少一个当量直径为 2〜 5mm的主孔和若干个当量直径小于 2讓的辅助孔。 下面是本发明漏液阻汽装 置 10的实施例。
实施例 1 :
如图 6、 图 7所示， 本发明漏液阻汽装置 10包括一与换热器联箱 2横截 面大小相同的基板 11， 基板 11的中心具有一个当量直径为 2〜5ram同孔径的 主孔 12， 围绕主孔 12均匀排布有一圈当量直径小于 2mm同当量孔径的辅助 孔 13。 当换热器 2上游换热管 1中产生的冷凝液体较少时， 由联箱 2分离出 来的液体会在基板 11的主孔 12和辅助孔 13表面形成一层液膜，阻止液体和 汽体从主孔 12和辅助孔 13流出； 当液量稍增大时， 孔径较大的主孔 12会首 先渗液， 相当于现有技术中的单根排液管排液。 当分离出来的液量较大时， 液体的压力会破坏覆盖在辅助孔 13表面的液膜， 而从辅助孔 13中也渗出， 这样就相当于增加为多根排液管排液， 解决了现有技术中排液量受到限制的 问题。
实施例 2:
如图 8、 图 9所示， 本实施例中的主孔 12和辅助孔 13的尺寸范围与实 施例 1类似， 不同的是主孔 12和辅助孔 13是变当量孔径的锥台孔， 当量孔 径可以上面大， 下面小； 也可以上小下大， 还可以是任意的变截面积形式。 这种结构可使得主孔 12和辅助孔 13中都能够承载一定量的冷凝液， 主孔在 冷凝液量相对较低时， 也能保证排液的连续， 可防止蒸汽穿过； 辅助孔 13的 孔隙中有冷凝液可提高其阻汽能力， 防止蒸汽穿过， 也可以依据孔型既能提 高阻汽能力又能加速排液。
实施例 3 :
如图 10、 图 11所示， 本实施例中的主孔 12和辅助孔 13之间是相互相 交的， 呈现 "梅花"孔形结构。 相交的梅花孔形结构可看作是一个主孔的延 展结构， 相比单一主孔 12结构， 其流通当量直径有所增大， 可有效强化主孔 12的冷凝液流通能力， 同时辅助孔 13与主孔 12相交能够在液量相对较小时 通过表面张力粘附一定的冷凝液， 强化了装置的阻汽液封能力。
实施例 4: 如图 12、 图 13所示， 本实施例中的辅助孔 13与主孔 12相交， 形成 "梅 花"孔形结构的同时， 还设置了与主孔 12不相交的辅助孔 13。 这是一种上 述结构的组合， 在流通面积增大的同时， 保证了漏液阻汽装置在更大的流通 范围具有调节能力。
以上结构的功能主要是从孔结构上采用不同当量孔径相组合的方法强化 漏液阻汽装置的阻汽能力和液体流量调节能力，主孔 12保证漏液阻汽装置的 基本漏液能力， 辅助孔 13保证漏液阻汽装置的液体流量调节能力， 在液体量 较小时， 通过液封作用阻隔蒸汽流通。 直接采用上述多孔结构基板 11， 对解 决换热器系统机油堵塞基板 11方面有着明显的优势。
实施例 5:
如图 14、 15所示， 本实施例是在制作的基板 11上设置的主孔 12和辅助 孔 13中设置多孔介质芯 4。 在制冷剂流量较小的换热器中， 由于冷凝液流量 较小， 需要更小的孔隙结构来保证孔结构的阻汽能力， 填充多孔介质芯 4， 可在不改变孔结构的条件下， 增强孔隙表面张力作用， 强化阻汽能力。 同时 多孔介质芯 4的抽吸作用亦可保证冷凝液的流通， 实现小制冷剂流量下的分 液作用。
实施例 6:
如图 16、 17所示， 本实施例是在主孔与辅助孔相交呈现 "梅花"孔形结 构的孔径内设置多孔介质芯 4， 这种结构可以在具备了上述实施例 3特点基 础上， 加强了装置的阻汽效果。
实施例 7:
如图 18、 19所示， 本实施例是在主孔 12与辅助孔 13相交呈现 "梅花" 孔形结构的同时还设置了与主孔不相交的辅助孔 13的情况下，在各孔中设置 了多孔介质芯 4。 这种结构是上述实施例 4所描述的结构组合的情况下， 在 流通面积增大的同时保证了漏液阻汽装置在更大的流通范围具有调节能力， 同时保证了装置的阻汽效果。
实施例 8:
如图 20、 21所示， 本实施例与实施例 1类似， 但是采用多孔介质材料作 为基板 11， 配合主孔 12、 辅助孔 13的结构， 通过多孔介质材料本身的多孔 结构保证阻汽能力， 通孔结构保证漏液分流能力。 上述各实施例中，漏液阻汽装置 10采用与联箱 2横截面相同的固体材料 或固体多孔介质作为基板 11， 一般为金属材料， 在保证与所述联箱无泄漏紧 密接触的前提下， 也可采用其他材料。 基板直接镶嵌在联箱中确定的位置， 对金属材料基板一般采用焊接方式固定，结构大为简化。多孔板上的孔可以采 用不同当量孔径、 结构的孔构成， 各个孔结构可是变当量孔径， 也可以是同 当量孔径， 多孔介质可以采用粉末颗粒烧结制成的多孔介质或丝网等。
实施例 9: 采用本发明方法可以在各种制冷制热设备中应用。
如图 22所示， 本实施例是在分液式空气冷凝器中的应用， 安装有漏液阻 汽装置 10的联箱 2替代了原分液式空气冷凝器中的分液管和联箱结构，一侧 的联箱 2通过换热管连接另一侧联箱 2， 左右两侧联箱 2内交错镶嵌并固定 有多个漏液阻汽装置 10， 将两侧联箱 2分隔成左右顺序连通的多个汽液分离 空间， 第一级联箱 2连接一进液管 3， 最底部的两侧联箱 2底部并联连接一 出液管 4， 换热管 1上设置有翅片 5。
本发明使用时， 通过换热管 1换热产生的冷凝液， 在联箱 2中由于重力 作用汇聚到漏液阻汽装置 10上部， 随着冷凝液的不断积累， 在重力作用下冷 凝液会首先由孔径较大的主孔 12排走， 直径较小的辅助孔 13会由少量的冷 凝液形成的液膜封住， 有效地防止蒸汽通过， 而当冷凝液量比较大， 在漏液 阻汽装置 10上部聚集的冷凝液增多， 液层厚度增大， 重力产生的压头增大， 小直径的辅助孔 13的通流能力被激活，能够有效减少冷凝液在分液装置上部 的过度聚集。 孔的流通能力实验表明， 在一定液位高度条件下， 通孔的冷凝 液流量大致与通孔流通面积成正比， 因此通过定义参数孔隙率 S表征漏液阻 汽装置 10的流通能力，
S = Ap I At
其中 p， A分别为各孔流通面积之和与基板表面积。 参数 S由冷凝器系统循 环流量确定， 大致为此的 20〜50%。
本发明方法还可以用于其它各种制冷制热设备中， 在此不再一一赘述， 任何基于本发明原理和技术方案上的改进和等效变换均不应排除在本发明的 保护范围之外。

Claims

权 利 要 求
1、 一种分段式汽液相变换热器的汽液分离方法， 其特征在于： 其包括以下内 容-
1 )在至少一组换热管的两端分别设置一直通的联箱， 在两所述联箱内交错设 置有若干可镶嵌入所述联箱内的漏液阻汽装置， 将两所述联箱分隔为顺序连通的 多个分液空间， 所述漏液阻汽装置上设置有至少一个当量主孔和若干个当量辅助 孔；
2 )当所述分液空间内的积液较少时， 主孔和辅助孔顶部形成的液膜可阻止汽 体进入同侧下一级联箱的分液空间；
3 )当一个所述分液空间内的积液积累较多时， 在压力作用下积液会首先穿破 孔径较大的主孔流出， 而直径较小的辅助孔继续由顶部形成的液膜封住；
4)当一个所述分液空间内的积液层厚度增大， 在压力作用下会逐步穿破孔径 较小的辅助孔， 同时从所述主孔和辅助孔流出。
2、 如权利要求 1所述的一种分段式汽液相变换热器的汽液分离方法， 其特征 在于： 所述的主孔当量直径为 2〜5mm， 辅助孔当量直径小于 2mm。
3、 如权利要求 1或 2所述的一种分段式汽液相变换热器的汽液分离方法， 其 特征在于： 所述漏液阻汽装置的流通能力由孔隙率 ^表征： 其中^ ^， ^分别为主孔和辅助孔总流通面积与漏液阻汽装置表面积的比值， 孔隙 率 S为汽液相变换热器系统循环流量的 20〜50%。
4、 一种应用如权利要求 1〜3所述方法的分段式汽液相变换热器， 其特征在 于： 它包括至少一组换热管， 在所述换热管的两端分别连通一直通的联箱， 在两 所述联箱内交错设置有若干漏液阻汽装置， 将两所述联箱分隔为顺序连通的多个 分液空间， 第一级所述分液空间连接一进汽管， 两端最底部的所述分液空间并联 连接一出液管， 漏液阻汽装置上设置有至少一个主孔和若干个辅助孔。
5、 如权利要求 4所述的一种分段式汽液相变换热器， 其特征在于： 所述漏液 阻汽装置为一可镶嵌入所述联箱内的基板， 所述基板上设置有至少一个当量直径 为 2~5mm的主孔和若干个当量直径小于 2mm的辅助孔。
6、 如权利要求 5所述的一种分段式汽液相变换热器， 其特征在于： 所述基板 上的所述主孔和辅助孔分别为上、 下当量直径相同的直型孔。
7、 如权利要求 5所述的一种分段式汽液相变换热器， 其特征在于： 所述基板 上的主孔和辅助孔分别为锥台孔和变截面通孔之一。
8、 如权利要求 5或 6或 7所述的一种分段式汽液相变换热器， 其特征在于： 所述基板上的若干辅助孔与所述主孔边缘相交， 形成一整体的梅花状孔。
9、 如权利要求 5或 6或 7所述的一种分段式汽液相变换热器， 其特征在于： 在所述整体的梅花状孔与所述基板的边缘之间设置有若干独立的辅助孔。
10、 如权利要求 8所述的一种分段式汽液相变换热器， 其特征在于： 在所述 整体的梅花状孔与所述基板的边缘之间设置有若干独立的辅助孔。
11、 如权利要求 4〜10所述的一种分段式汽液相变换热器， 其特征在于： 在 所述主孔和辅助孔中设置有多孔介质芯。
12、 如权利要求 5〜11所述的一种分段式汽液相变换热器， 其特征在于： 所 述基板的材料为金属材料。
13、 如权利要求 5〜10所述的一种分段式汽液相变换热器， 其特征在于： 所 述基板的材料为多孔介质材料。
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