WO2022174741A1 - 蒸汽换热器 - Google Patents

蒸汽换热器 Download PDF

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Publication number
WO2022174741A1
WO2022174741A1 PCT/CN2022/075432 CN2022075432W WO2022174741A1 WO 2022174741 A1 WO2022174741 A1 WO 2022174741A1 CN 2022075432 W CN2022075432 W CN 2022075432W WO 2022174741 A1 WO2022174741 A1 WO 2022174741A1
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WO
WIPO (PCT)
Prior art keywords
header
heat exchange
steam
composite
pipe
Prior art date
Application number
PCT/CN2022/075432
Other languages
English (en)
French (fr)
Inventor
李永堂
Original Assignee
李永堂
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Filing date
Publication date
Application filed by 李永堂 filed Critical 李永堂
Priority to KR1020237024466A priority Critical patent/KR20230121875A/ko
Priority to GB2311203.0A priority patent/GB2617983A/en
Priority to US18/277,782 priority patent/US20240053102A1/en
Priority to EP22755514.1A priority patent/EP4279849A1/en
Priority to JP2023546522A priority patent/JP2024504846A/ja
Publication of WO2022174741A1 publication Critical patent/WO2022174741A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/08—Auxiliary systems, arrangements, or devices for collecting and removing condensate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/06—Derivation channels, e.g. bypass

Definitions

  • the invention relates to a heat exchange device, in particular to a steam heat exchange device.
  • condensation and heat transfer of steam in the tube (plate) pass There are two forms of condensation and heat transfer of steam in the tube (plate) pass.
  • One is film condensation; the other is bead (drop) condensation.
  • the surface heat transfer coefficient of bead condensation is several times or even an order of magnitude larger than that of film condensation.
  • the steam is condensed in the horizontal tube (plate) pass, which is basically a film condensation.
  • the wall surface is always covered by a layer of liquid film, and the phase change heat (latent heat) released during condensation must pass through the liquid film to transfer to the cooling wall surface. Therefore, the main disadvantage of film condensation is that the thermal resistance during the condensation process is mainly concentrated in the condensate film.
  • it is necessary to reduce the thickness of the liquid film, or to generate turbulence in the flowing medium.
  • the structure of two or more stages of heat exchangers in series is usually used.
  • the Chinese invention patent application with publication number CN104132557A discloses "an intermediate drainage type high-efficiency condensing system", which is provided with at least two-stage heat exchangers, and the rear end of the heat exchange tube of the front-stage heat exchanger is connected with the front-stage lead-out end Header, the front end of the heat exchange tube of the rear heat exchanger is connected with the rear inlet header, and the rear end is connected with the rear outlet header; the front outlet header is connected to the rear inlet header through the pipeline.
  • the front-stage heat exchanger and the back-stage heat exchanger are located in the same box or in different boxes, and the lower end of the box has an air inlet, An axial flow fan is installed on the upper end.
  • the intermediate drainage is implemented at the end of the front-stage heat exchanger, and the gas discharged from the front-stage heat exchanger is introduced into the back-stage heat exchanger, which is conducive to the flow of fluid in the heat exchange pipeline and accelerates the internal flow of the heat exchange pipeline.
  • the discharge of the liquid film greatly increases the heat transfer coefficient.
  • the liquid film Due to the increase of the vapor velocity along the flow direction of the liquid film, the liquid film will be turbulent, and on the other hand, the liquid film will be blown away from the wall surface, thereby increasing the heat transfer coefficient.
  • This type of structure mainly has the following two defects: first, the heat exchange device occupies a large area, and there are many connecting pipes including headers, and the processing complexity is high. The secondary anti-corrosion process increases the difficulty of installation.
  • the effect of this kind of structure is still unsatisfactory, mainly reflected in: the liquid outlet header of the upper stage and the liquid outlet header of the next stage are independent of each other, and there is a certain
  • the pressure drop of the upper stage is a mixture of vapor phase and liquid phase, which is difficult to separate in the flow; They are connected, and their respective liquid outlet pipes are directly discharged. Under the action of pressure drop, part of the foam liquid flows to the next stage steam inlet header. It affects the heat exchange effect of the next stage heat exchanger.
  • the technical problem to be solved by the present invention is to provide a steam heat exchanger, which greatly simplifies the pipeline structure including the header while reducing the thickness of the liquid film and improving the heat exchange efficiency, so as to occupy less space and It is more convenient to process and assemble, so as to overcome the shortcomings of the prior art.
  • the steam heat exchanger is characterized in that it includes a composite header with a liquid discharge pipe, a first-stage steam inlet header and a secondary steam inlet header are arranged above the composite header, and the first-stage steam inlet header has an inlet steam header.
  • Pipes; the composite header and the secondary steam inlet header are communicated through transition pipes; it also includes two groups of heat exchange pipes or heat exchange plates, wherein the inlet and outlet ends of the first group of heat exchange pipes or heat exchange plates are respectively connected to the first level
  • the steam inlet header and the composite header, the inlet and outlet ends of the second group of heat exchange tubes or the heat exchange plates are respectively connected to the secondary steam inlet header and the composite header.
  • the heat exchange tube is a coiled tube or a multi-stage U-shaped tube.
  • the steam heat exchanger further comprises a bypass whose upper end is connected to the lower side of the first-stage steam inlet header, and the lower end is communicated with the composite header, and is used for introducing the liquid phase fluid in the first-stage steam inlet header into the composite header. Tube.
  • bypass pipe is a straight pipe or a pipe with a liquid seal.
  • a liquid accumulator is connected to the discharge pipe, and a balance pipe is connected between the secondary steam inlet header and the liquid accumulator.
  • the steam heat exchanger further comprises an auxiliary drain pipe for connecting the composite header and the drain pipe, and the communication point between the auxiliary drain pipe and the drain pipe is higher than that between the drain pipe and the compound header The connection point is closer to the high pressure end of the composite header.
  • the primary inlet steam header and the secondary inlet steam header are two sections of headers separated by the same header and separated by internal partitions.
  • the most important function of the composite header of the present invention is to balance the pressure difference between the first liquid outlet end and the second liquid outlet end, which greatly improves the vapor-liquid separation effect of the first liquid outlet end.
  • the efficiency of the second set of heat exchangers is improved.
  • the flow velocity of the gas phase in the system is increased, thereby accelerating the discharge of the condensate film, reducing the thickness of the condensate film, and making the The fluid in the system is more likely to form turbulent flow, which improves the heat exchange efficiency.
  • the entire system uses at most three headers, and in particular, one header can be divided into two sections instead of two headers.
  • the device has the outstanding features of compact structure and small footprint, and can complete the anti-corrosion treatment as a whole at one time, reducing the pipeline connection installation and secondary anti-corrosion operation at the user end.
  • the pressure in the first-stage steam inlet header is greater than that in the second-stage steam inlet header.
  • the balance pipe connected with the accumulator is connected to the secondary steam inlet header, which can effectively reduce the internal pressure of the accumulator, which is more conducive to the liquid return of the condensing system, and can effectively reduce the temperature of the medium in the accumulator and reduce the pressure on the accumulator. Cooling workload.
  • the drainage pipe can be connected to the low pressure end of the composite header for discharging the main liquid phase, and the auxiliary drainage pipe can be connected to the high pressure end of the composite header for advance. Part of the liquid phase is discharged to reduce the subsequent (second set of heat exchange tubes or heat exchange plates) load.
  • the condensate and oil in the first-stage steam inlet header are introduced into the composite header in advance through the bypass pipe, thereby effectively reducing the influence of oil film and liquid film, and further improving the replacement efficiency. Thermal efficiency.
  • FIG. 1 is a schematic structural diagram of an embodiment of the present invention.
  • the embodiment of the present invention includes a composite header 1 , and a primary steam inlet header 4 and a secondary inlet steam header 6 are arranged above the composite header 1 .
  • the primary inlet steam header 4 is provided with an inlet steam pipe 3 .
  • the first-stage steam inlet header 4 and the second-stage steam inlet header 6 are two sections of headers separated by the same header and separated by an internal partition 5 .
  • the composite header 1 and the secondary inlet steam header 6 communicate with each other through a transition pipe 7 .
  • It also includes two groups of heat exchange tubes or heat exchange plates, wherein the inlet and outlet ends of the first group of heat exchange tubes or heat exchange plates are respectively connected to the first-stage steam inlet header 4 and the composite header 1, and the second group of heat exchange tubes or heat exchange plates are respectively connected.
  • the inlet and outlet ends of the plates are respectively connected to the secondary steam inlet header 6 and the composite header 1;
  • the heat exchange tube or the heat exchange plate is a heat exchange tube
  • the heat exchange tube is a coiled tube or a multi-stage U-shaped tube.
  • the embodiment of the present invention further includes an upper end
  • the bypass pipe 2 communicates with the lower side and the lower end of the primary steam inlet header 4 and the composite header 1 .
  • the bypass pipe is preferably a straight pipe or a pipe with a liquid seal.
  • Embodiments of the present invention further include an equalization pipe 8 for communicating the secondary inlet steam header 6 and the accumulator 9 .
  • the embodiment of the present invention further includes an auxiliary drain pipe 12 for connecting the composite header 1 and the drain pipe 10 .
  • the communication point between the auxiliary drain pipe 12 and the drain pipe 10 is generally located at the high pressure of the compound header 1 . end,
  • the communication point between the drain pipe 10 and the composite header 1 is generally located at the low pressure end of the composite header 1 .
  • the headers, heat exchange pipes or heat exchange plates and related connecting pipes are all placed in a shell, and the steam in the system is condensed by spraying water or cold air to evaporate and dissipate heat.
  • the high-temperature and high-pressure steam enters from the steam inlet pipe 3 at the left end of the first-stage steam inlet header 4, and exchanges heat with the spray water or cold air in the shell through the first set of heat exchange tubes or heat exchange plates, and enters the composite header 1 after partial condensation.
  • the liquid phase is discharged into the accumulator 9 through the liquid discharge pipe 10 and the auxiliary liquid discharge pipe 12
  • the gas phase enters the second group of heat exchange tubes or heat exchange plates through the transition pipe 7 and the secondary steam inlet header 6, and is sprayed with the shell.
  • water spray or cold air heat exchange it enters the composite header 1 after condensing, and then is discharged into the accumulator 9 through the liquid discharge pipe 10 and the auxiliary liquid discharge pipe 12 .

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

Abstract

本发明是一种蒸汽换热器，它包括复合集管，复合集管的上方设置有一级进汽集管和二级进汽集管，复合集管和二级进汽集管之间通过过渡管相连通；还包括两组换热管或者换热板，其中第一组换热管或者换热板的进出端分别连接一级进汽集管和复合集管，第二组换热管或者换热板的进出端分别连接二级进汽集管和复合集管。本发明提高了第一级换热管内以及换热板（管）程内顺冷凝液流动方向的蒸汽流速，加速了冷凝液膜的排出速度，大大降低了冷凝液膜的厚度，并使其产生湍流，使第一组换热板（管）程内换热效率大幅提高。本发明大幅度简化了包括集管在内的管路结构，减少了换热器组之间的二次管道连接。使其加工组装更筒捷方便。

Description

蒸汽换热器 技术领域
本发明涉及一种热交换装置，具体涉及一种蒸汽换热装置。
 背景技术
蒸汽在管（板）程中冷凝凝结传热有两种形式。一种是膜状冷凝；另一种是珠状（滴状）冷凝。珠状冷凝，其表面传热系数要比膜状冷凝大几倍甚至大一个数量级。蒸汽在水平管（板）程内冷凝，基本属于膜状冷凝。膜状冷凝时，壁面总是被一层液膜覆盖着，凝结时放出的相变热（潜热）必须穿过液膜才能传到冷却壁面上。因此，膜状冷凝的主要缺点，就是冷凝过程中的热阻主要集中在冷凝液膜内。对于膜状冷凝，要想提高其换热系数，就必须减薄液膜厚度，或使流动的介质产生湍流。
对于膜状冷凝换热，为了提高换热系数，加快冷凝，通常采用两级或多级换热器串联的结构形式。比如公开号为CN104132557A的中国发明专利申请公布了“一种中间排液式高效冷凝***”，其至少设置两级换热器，前级换热器的换热管后端连接有前级引出端集管，后级换热器的换热管前端连接有后级进入端集管，后端连接有后级引出端集管；前级引出端集管通过管路与后级进入端集管相连接，用于将前级换热器排出的气体引入后级换热器；前级换热器和后级换热器位于同一箱体内或者分别位于不同箱体内，箱体下端带有进风口、上端安装有轴流风机。在前级换热器末端实施了中间排液，并且将前级换热器排出的气体引入后级换热器中，有利于换热管路内流体的流动，并加速了换热管路内液膜的排出，从而使换热系数大幅上升。由于增加了顺液膜流动方向的蒸气流速，会使液膜产生湍流，另一方面也会使液膜被吹离壁面，从而使换热系数增大。这一类结构主要存在以下两个缺陷：第一、换热装置占地面积大，包括集管在内的连接管路多，加工复杂程度高，在组装过程中还需要再连接管道，有产生二次防腐的工序，增加了安装难度。第二、从中间排液效果看，这类结构效果仍不能令人满意，主要体现在：上一级的出液集管和下一级的出液集管是各自独立的，两者存在一定的压力降，由于上一级的出液集管内是汽相和液相的混合物，在流动当中是很难分离的；另外，由于下一级的进汽集管和上一级的排出集管是相连通的，各自的出液管又是直接排出，在压力降的做用下，导致一部分泡沫液态流到下一级进汽集管。影响到下一级换热器的换热效果。
 技术问题
本发明所要解决的技术问题是，提供一种蒸汽换热器，在减薄液膜厚度、提高换热效率的同时，大幅度简化包括集管在内的管路结构，使占地更少且加工组装更便捷，以克服现有技术存在的不足。
 技术解决方案
本发明的技术方案如下：
蒸汽换热器，其特征在于它包括带有排液管的复合集管，复合集管的上方设置有一级进汽集管和二级进汽集管，一级进汽集管带有进汽管道；复合集管和二级进汽集管之间通过过渡管相连通；还包括两组换热管或者换热板，其中第一组换热管或者换热板的进出端分别连接一级进汽集管和复合集管，第二组换热管或者换热板的进出端分别连接二级进汽集管和复合集管。
优选地，如果所述换热管或者换热板选择换热管，该换热管为盘管或者多级U形管。
优选地，所述蒸汽换热器还包括上端连通一级进汽集管下侧部、下端与复合集管相连通，用于将一级进汽集管内液相流体导入复合集管内的旁通管。
进一步优选地，所述的旁通管为直管或者带有液封的管。
优选地，所述排液管连接有储液器，二级进汽集管和储液器之间连接有平衡管。
优选地，所述蒸汽换热器还包括用于连通复合集管和排液管的辅助排液管，辅助排液管与排液管之间的连通点较排液管与复合集管之间的连通点更靠近复合集管的高压端。
优选地，一级进汽集管和二级进汽集管为同一根集管通过内设隔板隔成的两段集管。
 有益效果
本发明的积极效果在于：
第一、本发明复合集管有一最重要的作用就是均衡第一出液端和第二出液端的压力差，大大提高了一级出液端的汽液分离效果。提高了第二组换热器的效率。另外，由于本发明一级进汽集管与二级进汽集管之间存在压力降，增加了***内气相流动速度，从而加速了冷凝液膜的排出，减薄了冷凝液膜，并使***内流体个更容易形成湍流，提高了换热效率。
第二、整个***最多采用三根集管，特别的，还可以采用一根集管隔成两段代替两根集管。装置具有结构紧凑和占地面积小的突出特点，并且可以整体一次性完成防腐处理，减少了用户端的管道连接安装和二次防腐操作。
第三、一级进汽集管内压力大于与二级进汽集管。与储液器连接的平衡管连接到二级进汽集管能够有效降低储液器内压，更有利于冷凝***回液，并能够有效降低储液器内介质温度，减少针对储液器的降温工作量。
第五、增设辅助排液管的方案中，可以将排液管连接到复合集管的低压端用于排出主要的液相，而将辅助排液管连接到复合集管的高压端用于提前排出部分液相以减少后续（第二组换热管或者换热板）负荷。
第六、增设旁通管的方案中，通过该旁通管将在一级进汽集管中的冷凝液及油分提前导入复合集管，从而有效减轻了油膜和液膜影响，进一步提高了换热效率。
 附图说明
图1是本发明实施例的结构示意图。
 本发明的实施方式
下面结合实施例及其附图进一步说明本发明。
如图1，本发明的实施例包括复合集管1，复合集管1的上方设置有一级进汽集管4和二级进汽集管6。一级进汽集管4带有进汽管道3。作为优化方案，所述的一级进汽集管4和二级进汽集管6为同一根集管通过内设隔板5隔成的两段集管。复合集管1和二级进汽集管6之间通过过渡管7相连通。还包括两组换热管或者换热板，其中第一组换热管或者换热板的进出端分别连接一级进汽集管4和复合集管1，第二组换热管或者换热板的进出端分别连接二级进汽集管6和复合集管1；复合集管1带有排液管10，排液管10通过液封弯管11连接有储液器9。
如果所述换热管或者换热板选择换热管，该换热管为盘管或者多级U形管。
为了将一级进汽集管4内液相流体（主要是冷凝液和油分）导入复合集管1内，以减轻油膜和液膜对换热效率的影响，本发明的实施例进一步地包括上端连通一级进汽集管4下侧部、下端与复合集管1相连通的旁通管2。
所述的旁通管优选为直管或者带有液封的管。
本发明的实施例进一步地包括用于连通二级进汽集管6和储液器9的平衡管8。
本发明的实施例进一步地包括用于连通复合集管1和排液管10的辅助排液管12，辅助排液管12与排液管10之间的连通点一般位于复合集管1的高压端，
排液管10与复合集管1之间的连通点一般位于复合集管1的低压端。
使用时所述集管、换热管或者换热板及相关连接管路均置于一个壳体内，通过喷淋水或者冷风蒸发散热，对***内蒸汽实施冷凝。高温高压蒸汽从一级进汽集管4左端的进汽管道3进入，并经第一组换热管或者换热板与壳体内喷淋水或冷风换热，部分冷凝后进入复合集管1，液相经排液管10以及辅助排液管12排入储液器9，气相经过渡管7及二级进汽集管6进入第二组换热管或者换热板，与壳体内喷淋水或冷风换热，冷凝后进入复合集管1，然后经排液管10以及辅助排液管12排入储液器9。

Claims (7)

  1. 蒸汽换热器，其特征在于它包括带有排液管（10）的复合集管（1），复合集管（1）的上方设置有一级进汽集管（4）和二级进汽集管（6），一级进汽集管（4）带有进汽管道（3）；复合集管（1）和二级进汽集管（6）之间通过过渡管（7）相连通；还包括两组换热管或者换热板，其中第一组换热管或者换热板的进出端分别连接一级进汽集管（4）和复合集管（1），第二组换热管或者换热板的进出端分别连接二级进汽集管（6）和复合集管（1）。
  2. 如权利要求1所述的蒸汽换热器，其特征在于:如果所述换热管或者换热板选择换热管，该换热管为盘管或者多级U形管。
  3. 如权利要求1所述的蒸汽换热器，其特征在于它还包括上端连通一级进汽集管（4）下侧部、下端与复合集管（1）相连通，用于将一级进汽集管（4）内液相流体导入复合集管（1）内的旁通管（2）。
  4. 如权利要求3所述的蒸汽换热器，其特征在于：所述的旁通管（2）为直管或者带有液封的管。
  5. 如权利要求1所述的蒸汽换热器，其特征在于：所述排液管（10）连接有储液器（9），二级进汽集管（6）和储液器（9）之间连接有平衡管（8）。
  6. 如权利要求1所述的蒸汽换热器，其特征在于它还包括用于连通复合集管（1）和排液管（10）的辅助排液管（12），辅助排液管（12）与排液管（10）之间的连通点较排液管（10）与复合集管（1）之间的连通点更靠近复合集管（1）的高压端。
  7. 如权利要求1或2或3或4或5或6所述的蒸汽换热器，其特征在于一级进汽集管（4）和二级进汽集管（6）为同一根集管通过内设隔板（5）隔成的两段集管。
PCT/CN2022/075432 2021-02-22 2022-02-08 蒸汽换热器 WO2022174741A1 (zh)

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