WO2014048073A1 - 一种多流程板式换热器提高换热效率的方法及产品 - Google Patents

一种多流程板式换热器提高换热效率的方法及产品 Download PDF

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Publication number
WO2014048073A1
WO2014048073A1 PCT/CN2013/001339 CN2013001339W WO2014048073A1 WO 2014048073 A1 WO2014048073 A1 WO 2014048073A1 CN 2013001339 W CN2013001339 W CN 2013001339W WO 2014048073 A1 WO2014048073 A1 WO 2014048073A1
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Prior art keywords
flow
plate
plates
heat exchanger
fluid
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English (en)
French (fr)
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陈建平
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    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling

Definitions

  • the invention relates to a method and a product for improving heat exchange efficiency of a plate heat exchanger, in particular to a method and a product for improving heat exchange efficiency of a multi-flow plate heat exchanger.
  • the plate heat exchanger is assembled by stacking a plurality of thin metal plates with punched corrugations and corner holes, and the adjacent plates are sealed by a spliced seal called a brazed plate heat exchanger or a welded plate heat exchanger.
  • a detachable plate heat exchanger surrounded by gaskets around the adjacent plates and clamped by clamping end plates and clamping bolts.
  • the angular holes of the plates form fluid distribution tubes and collections. Tube, a cold and hot fluid flow path is formed between adjacent plates, and the cold and hot fluids are reasonably separated, so that the cold and hot fluids respectively flow on each side of the thin metal plate with punched corrugations and corner holes.
  • Reverse flow in the channel, heat exchange through thin metal sheets, thin metal sheets are also called heat exchange sheets; plate heat exchangers have high heat exchange efficiency, low heat loss, compact structure, convenient installation, wide application, and low price. , long life and other characteristics.
  • plate heat exchangers have high heat exchange efficiency, low heat loss, compact structure, convenient installation, wide application, and low price. , long life and other characteristics.
  • the fluid flow path is not long enough, the heat transfer between the cold and hot fluids is not enough. It is necessary to increase the length of the fluid flow path by increasing the number of processes. The increase of the number of processes is realized by the flow transition plate.
  • a plate heat exchanger with a process turning plate is called a multi-flow plate heat exchanger. The flow direction of the fluid is opposite to the front and back of the flow transition plate.
  • the flow transition plate is also stamped from the same thin metal plate, the fluid that has been heated or cooled is re-cooled or heated, resulting in each The temperature difference between the inlet and outlet of the fluid is reduced, the heat exchange efficiency of the heat exchanger is reduced, and the waste heat recovery rate is reduced in the waste heat recovery, especially when the number of cold and hot fluid flow paths is small, and the single process is long. .
  • the flow direction of the fluid reverses after passing through the flow transition plate, and the application of the multi-plate heat exchanger is limited in the case where the flow direction of the cold and hot fluid is not desired to be reversed.
  • the first technical problem to be solved by the present invention is to overcome the deficiencies in the prior art, and to provide a fluid that has been heated or cooled on both sides of the flow transition plate of the multi-flow plate heat exchanger to avoid being re-cooled or heated to improve The method of heat exchange efficiency.
  • the technical solution adopted by the present invention is:
  • the fluids on both sides of the process transfer plate are insulated from each other.
  • the method is easy to manufacture, low in cost, simple in structure, reliable in performance, and improves heat exchange efficiency of the multi-flow plate heat exchanger.
  • a second technical problem to be solved by the present invention is to provide a multi-flow plate heat exchanger using the above-described multi-flow plate heat exchanger to improve heat exchange efficiency.
  • the technical solution adopted by the present invention is:
  • the multi-flow plate heat exchanger is composed of a plurality of thin metal sheets with punched corrugations and corner holes stacked with at least one process turning plate, and the adjacent plates are sealed by welding or surrounded by adjacent plates.
  • the gasket is clamped and sealed by the clamping end plate and the clamping bolt to form a flow path of cold and hot fluid, and the flow turning plate is a heat insulating plate.
  • the multi-flow plate heat exchanger is composed of a plurality of thin metal sheets with punched corrugations and corner holes and at least one process turning plate, and the adjacent plates are sealed by a splicing joint or between adjacent plates.
  • the gasket is clamped and sealed by the clamping end plate and the clamping bolt to form a flow path of cold and hot fluid, and the flow turning plate is composed of at least two plates.
  • the multi-flow plate heat exchanger is composed of a plurality of thin metal sheets with punched corrugations and corner holes stacked with at least one process turning plate, and the adjacent plates are sealed by welding or surrounded by adjacent plates.
  • the gasket is clamped and sealed by the clamping end plate and the clamping bolt to form a flow path of cold and hot fluid, and the flow turning plate is composed of at least two heat insulating sheets.
  • multi-flow plate heat exchanger has high heat exchange efficiency and simultaneous production
  • the product has a simple structure, reliable performance and easy production.
  • the third technical problem to be solved by the present invention is: maintaining the fluid flow direction after passing through the flow-folding plate unchanged, meeting the need for heat exchange when vaporization or condensation has a phase change, or heat exchange requiring heat-cooling.
  • the technical solution adopted by the present invention is that the heat-insulating flow turning plate has independent flow paths of cold and hot fluids.
  • the heat insulating sheets constituting the process turning plate have independent flow paths of cold and hot fluid.
  • the beneficial effects of adopting the above technical solution are as follows: the fluid after the flow-folding plate can maintain the flow direction unchanged, and satisfies the need for heat exchange when vaporization or condensation has a phase change or heat exchange requiring hot-cold cooling.
  • a fourth technical problem to be solved by the present invention is to provide a low-cost, easy-to-machine non-metallic flow turning plate, a non-metallic sheet adjacent to the clamping end plate, and a pipe joint for clamping the end plate.
  • the technical solution adopted by the present invention is:
  • the heat-insulating process turning plate is formed by overlapping two non-metallic plates with angular holes in the opposite direction of two fish-shaped non-metal plates.
  • the pipe joint outside the clamping end plate has a flange at one end, and the non-metallic plate with the angular hole and the flange at one end of the pipe joint have a sealing gasket, and the other end of the pipe joint is threaded and Extending out of the corner hole of the clamping end plate, a nut is threadedly connected to the other end of the pipe joint.
  • the non-metal flow turning plate and the non-metal plate adjacent to the clamping end plate not only improve the heat exchange efficiency, but also reduce the heat loss, and have the advantages of simple structure, easy manufacture, and low cost.
  • Advantages of the pipe joints not only have the advantages of simple structure, easy manufacture, low cost, but also reduce the corrosion resistance requirements of the clamping end plates.
  • Figure 1 is a schematic view of a conventional multi-flow plate heat exchanger.
  • Figure 2 is a schematic illustration of a first embodiment of a multi-flow plate heat exchanger.
  • Figure 3 is a schematic illustration of a second embodiment of a multi-flow plate heat exchanger.
  • Figure 4 is a schematic illustration of a third embodiment of a multi-flow plate heat exchanger.
  • Figure 5 is a schematic illustration of a fourth embodiment of a multi-flow plate heat exchanger.
  • Figure 6 is a schematic illustration of a fifth embodiment of a multi-flow plate heat exchanger.
  • Figure 7 is a schematic illustration of a sixth embodiment of a multi-flow plate heat exchanger.
  • Figure 8 is a schematic view of two fishbone-shaped non-metal plates for a multi-flow plate heat exchanger flow transition plate.
  • Figure 9 is a schematic diagram of a multi-flow plate heat exchanger flow transition plate.
  • Figure 10 is a schematic illustration of a seventh embodiment of a multi-flow plate heat exchanger.
  • Figure 11 is a schematic diagram of a multi-flow plate heat exchanger flow transition plate.
  • Figure 12 is a schematic illustration of an eighth embodiment of a multi-flow plate heat exchanger.
  • Figure 13 is a schematic illustration of a ninth embodiment of a multi-flow plate heat exchanger.
  • Figure 14 is a schematic illustration of a tenth embodiment of a multi-flow plate heat exchanger.
  • Figure 15 is a schematic illustration of an eleventh embodiment of a multi-flow plate heat exchanger.
  • Figure 16 is a schematic illustration of a twelfth embodiment of a multi-flow plate heat exchanger.
  • Figure 17 is a schematic illustration of a thirteenth embodiment of a multi-flow plate heat exchanger.
  • FIG. 1 is a schematic view of a conventional multi-flow plate heat exchanger, in which a total of 10 flow paths are shown, which are respectively represented by I-X, wherein I, III, V, VII, and turbulent flow paths are a fluid, and 8 , ⁇ ' respectively represent their progress, Export; II, IV, VI, VID, X flow channel is another fluid, with A' representing its inlet and outlet, respectively, two fluid countercurrent heat exchange; the thin metal plate between the V and VI flow channels is In the flow transition plate 1, the flow direction of the two fluids is changed 180 before and after the flow transition plate 1, that is, the flow directions of the fluids in the IV and VI flow channels are opposite, and the flow directions of the fluids in the V, ⁇ flow channels are opposite, and the flow transition plate
  • the fluid in the V flow path on the left side is heated or cooled by the fluid in the IV flow path
  • the fluid in the VI flow path on the right side of the flow turning plate 1 is cooled or heated by the fluid in the ⁇ flow path, while the fluid
  • the good process turning plate 1 exchanges heat with the fluid in the VI flow path, so that the fluid heated or cooled in the V flow path is re-cooled or heated by the fluid in the VI flow path, eventually leading to the entry of each fluid.
  • the temperature difference at the outlet is reduced, that is, the heat exchange efficiency of the heat exchanger is lowered, for example, in the waste heat recovery system, the waste heat recovery utilization rate is lowered.
  • the fluids in the V and VI flow paths are downstream heat transfer, the heat transfer to the heat transfer through the flow transition plate 1 on both sides of the flow transition plate 1 is long when the single flow is long, especially when the number of fluid flow paths is small. The impact of efficiency is particularly prominent. If the process turning plate 1 is replaced with heat-insulating, the heat exchange between the fluids on both sides of the flow turning plate 1 can be reduced, that is, the heat exchange efficiency of the multi-flow plate heat exchanger is improved.
  • FIG. 2 is a schematic view of a first embodiment of a multi-flow plate heat exchanger, wherein the fluid in the flow passage V and the flow passage VI is a countercurrent heat exchange, and the heat exchange temperature difference is higher than that of the existing multi-flow plate heat exchanger V in FIG.
  • the heat exchange temperature difference between the fluid flow paths of the VI flow path is large, and the heat transfer process turning plate 1 of the existing multi-flow plate heat exchanger is changed into the heat insulation process turning plate 2 made of the heat insulating material, although at this time, the flow
  • the fluid in the channel V and the flow channel VI is countercurrent, but since the flow transition plate 2 is insulated, the heat exchange between the fluids in the V and VI flow channels is significantly reduced, thereby improving the heat exchange efficiency of the heat exchanger, of course.
  • the same process can be achieved by applying or composite heat insulating material layers on both sides of the existing process turning plate 1 to achieve the same effect; at this time, the multi-flow plate heat exchanger is equivalent to two single-flow plate changing
  • the heaters are connected in series, but two clamping end plates and two connecting tubes are omitted.
  • Figure 3 is a schematic view of a second embodiment of a multi-flow plate heat exchanger, two thin metal plates with stamped corrugations and corner holes 3 and 3', respectively, forming a process turning plate, two plates 3 and 3' No fluid between There is, in the same manner as the flow-folding plate 2 in the first embodiment, the flow direction of the two fluids is changed by 180 after passing through the sheets 3 and 3', as long as there is no fluid between the two sheets 3 and 3', that is, Keeping the vacuum or filling with air, it can form an insulated process turning plate, which is equivalent to the process turning plate 2 in the first embodiment, because only the partial regions of the two plates 3 and 3' are corrugated.
  • the two plates 3 and 3' are made of a material with good heat conductivity, it can also reduce the heat exchange between the fluids in the V and VI channels, thereby improving the heat exchange efficiency of the heat exchanger.
  • This solution can be used in brazed or welded plate heat exchangers because non-metallic insulation materials cannot be used in brazed or welded plate heat exchangers; of course in detachable plate heat exchangers
  • the sheets 3 and 3' may also be made of a heat insulating material, or a layer of a composite or composite insulating material applied on both sides, that is, a two-insulated sheet is used to form a flow transition sheet, and one of the first embodiment Compared with the heat-insulated process turning plate 2, it can be further reduced The heat exchange between the fluids on both sides of the process turning plate.
  • the flow direction of the fluid in the flow passage is changed by 180° after passing through the flow transition plate.
  • the flow direction of the fluid in the heat exchanger flow passage is required to remain unchanged, such as evaporation.
  • condensation heat exchange in phase change or heat exchange where hot cooling is required that is, the flow direction of the fluid in the flow passage needs to be changed by 360° after passing through the flow transition plate, which is equivalent to changing the flow direction by two 180 ⁇ .
  • Figure 4 is a schematic view of a third embodiment of a multi-flow plate heat exchanger, two plates having stamped corrugations and angular holes, respectively, plates 4 and 5, the flow direction of each of the two fluids after passing through one plate
  • the flow direction changes 360 Q in total, that is, the flow direction of the two fluids remains unchanged after the two sheets 4 and 5 are formed into the flow transition plate, and the two fluids are independent between the two plates 4 and 5.
  • the flow path, the two sides of the slab or the composite insulation layer, or both are made of insulating material, thereby improving the heat exchange efficiency of the heat exchanger.
  • this can also be understood as a process turning plate, that is, a separate flow path of cold and hot fluid inside, while the side is coated or composite heat insulating material layer or made of heat insulating material and the flow direction is changed before and after a process turning board that insulates fluids from each other; this is equivalent to two single processes and The plate heat exchangers in the direction of fluid flow are connected in series, but two clamping end plates and two connecting pipes are omitted.
  • Figure 5 is a schematic view of a fourth embodiment of a multi-flow plate heat exchanger, which differs from the third embodiment in that: between the plates 4 and 5, there are also plates 6, between the plates 4 and 6, and the plates Between 5 and 6, the flow paths of the two fluids are independent, wherein the plates 4 and 5 are insulated, and the plate 6 can be heat-conducting or heat-insulated.
  • a process turning plate that is, a flow path in which a separate flow path of cold and hot fluid is inside, and a layer of side coating or composite heat insulating material or a fluid made of heat insulating material and before and after the change of flow direction is mutually insulated Turning board
  • Figure 6 is a schematic view of a fifth embodiment of a multi-flow plate heat exchanger, which differs from the fourth embodiment only in the fluid between the plates 4 and 5 and between the plates 5 and 6 in separate flow passages. Type and flow direction of the fluid.
  • Figure 7 is a schematic view of a sixth embodiment of a multi-flow plate heat exchanger, in which a non-metallic insulating material is not suitable for use in a brazed or welded plate heat exchanger, in order to satisfy the flow direction of the fluid in the heat exchanger flow path
  • the plate 4 and the plate 5 in the schematic view of the fifth embodiment of the multi-flow plate heat exchanger can be replaced by a plate group consisting of two thin metal plates with punched corrugations and corner holes, while maintaining the same requirements.
  • the fluids in the flow passages on both sides of the flow turning plate are insulated from each other, that is, the fluid in the flow channels on both sides of the flow turning plate is only adjacent to the adjacent punched corrugations and corner holes.
  • the fluid on one side of the thin metal sheet is exchanged for heat, so that the flow rate of the fluid in the flow channel on both sides of the flow transition plate can be half of the flow rate in the same fluid flow path, that is, the flow rate of the fluid in the V flow path only needs the choke flow path.
  • Half of the flow rate of the inner fluid and the flow rate of the fluid in the VI flow passage only require half of the flow rate of the fluid in the VIA flow passage, and the flow rate of the fluid adjacent to the flow passage adjacent to the clamp end plate can be as long as half the flow rate in the same fluid flow passage, that is,
  • the flow rate of the fluid in the I channel only needs half of the flow rate of the fluid in the III flow channel, and the flow rate of the fluid in the X flow channel only needs half of the flow rate of the fluid in the flow channel.
  • the fluid in the flow channel on both sides of the flow transition plate or the clamping end plate fails to perform sufficient heat exchange to enter the next flow channel or flow out of the heat exchanger, which reduces the heat exchange efficiency of the heat exchanger, especially when the number of cold and hot fluid flow paths is small.
  • Figure 8 is a schematic view of two fishbone-shaped non-metal plates for a multi-flow plate heat exchanger flow transition plate.
  • the two fishbone non-metal plates 11 and 12 are only in opposite directions, and the fishbone shape is combined with the heat exchanger plate.
  • the common chevron punching corrugations correspond.
  • Fig. 9 is a schematic diagram of a multi-flow plate heat exchanger flow turning plate.
  • the multi-flow plate heat exchanger flow turning plate 13 is a flat non-metallic plate with angular holes and no stamping corrugations for pressing the sealing gasket.
  • Figure 10 is a schematic view showing a seventh embodiment of the multi-flow plate heat exchanger, comprising two non-metallic plates 13 having a corner hole and no punched corrugations sandwiched between two oppositely oriented fishbone non-metal plates 11 and 12.
  • the combined multi-flow plate heat exchanger flow transition plate, the thickness of the fishbone non-metal plate 11 and 12 is about half of the corrugation depth of the other angular hole and the punched corrugated thin metal plate 10, and the angular hole has no punched corrugation
  • the thickness of the non-metallic sheet 13-side gasket 8 is larger than the sealing gasket 15 between the two ordinary angular holes and the punched corrugated thin metal sheet 10, and the non-metallic sheet having the corner hole without punching corrugations
  • the seal gasket 9 on the other side has a thickness smaller than that of the gasket 15.
  • the direction of the fishbone non-metallic sheets 11 and 12 is opposite to the direction of the herringbone corrugations of the adjacent angular holes and the punched corrugated thin metal sheets 10, ensuring the fluid in the voids of the fishbone non-metallic sheets and the thin metal sheets.
  • the two angled holes and the stamped corrugated thin metal sheet 10 have the opposite shape of the chevron corrugation, just the opposite direction of the fishbone non-metal sheets 11 and 12, and the fishbone non-metal sheet
  • the opposite direction of 11 and 12 can greatly increase the strength of the combined process transfer plate.
  • the thickness of the non-metallic sheet 13 having the angular punched and unembossed corrugations can be determined according to the strength and thermal conductivity of the material so as to satisfy the strength requirements and minimize the heat exchange of the fluid in the flow passages on both sides of the flow transition plate.
  • the non-metal sheets 11 and 12 do not have a fishbone shape, but adopt a corresponding shape as long as the flow rate and strength requirements are satisfied.
  • FIG. 11 is a schematic diagram of a multi-flow plate heat exchanger flow turning plate
  • the multi-flow plate heat exchanger flow turning plate 14 is a non-metallic plate with an angular hole and no punched corrugation, and a flat surface is arranged on the outer side of the two corner holes. It is used to compress the gasket and the middle portion is convex toward one side.
  • FIG. 12 is a schematic view of an eighth embodiment of a multi-flow plate heat exchanger, which differs from the seventh embodiment in that: an angled hole is sandwiched between two fishbone non-metal sheets 11 and 12 having opposite directions
  • the non-metal plate 14 having no punched corrugation and convex toward the one side constitutes a combined multi-flow plate heat exchanger flow turning plate, and the two fishbone non-metal plates 11 and 12 have the same thickness and other horns.
  • the corrugation depth of the hole and the stamped corrugated thin metal sheet 10 is half, and the protrusion height of the non-metal sheet 14 is equal to the thickness of the fishbone non-metal sheet 11, so that the sealing gasket can directly adopt two ordinary angular holes.
  • sealing the gasket 15 between the corrugated thin metal sheets 10 without having to make two additional molds for producing the gaskets 8, 9.
  • Figure 13 is a schematic view of a ninth embodiment of the multi-flow plate heat exchanger, wherein the flow rate of the fluid in the flow channel adjacent to the clamp end plate 16 is only half of the flow rate in the same fluid flow path, so the eighth implementation is adopted.
  • a pair of fish-bone non-metal sheets 11 and 12 having opposite directions are sandwiched between a non-metallic sheet having a corner hole and no punched corrugations, and a non-metal sheet having a central portion protruding toward one side is placed in a piece.
  • the inner side of the end plate 16 is clamped, and the angle ⁇ in Fig.
  • Figure 14 is a schematic view of a tenth embodiment of the multi-flow plate heat exchanger, and the flow path adjacent to the other clamping end plate 17 can also be the same as in the eighth embodiment, so that the flow rate of the fluid in the flow channel is just The other half of the flow in the same fluid flow path also reduces the energy lost by the heat transfer of the fluid in the flow passage through the clamping end plate 17.
  • Figure 15 is a schematic view showing the eleventh embodiment of the multi-flow plate heat exchanger, comprising a combination of a fishbone non-metal plate 11 or 12 and an angular hole unpunched corrugated flat plate type non-metal plate 13.
  • the plate is placed on the inner side of a clamping end plate 16, and the thickness of the sealing gasket 9 is smaller than the thickness of the sealing gasket 15, so that a fishbone non-metallic plate can be omitted compared with the ninth embodiment. .
  • Figure 16 is a schematic view of a twelfth embodiment of a multi-flow plate heat exchanger, comprising a fishbone-shaped non-metal plate 11 or 12 and a non-metallic metal having an angular hole without punching corrugations and a central portion convex toward one side.
  • the combined plate composed of the plates 14 is placed on the inner side of a clamping end plate 17, and the thickness of the sealing gasket 9 is smaller than the thickness of the sealing gasket 15, so that one sheet can be omitted as compared with the tenth embodiment.
  • Fishbone non-metallic plate Fishbone non-metallic plate.
  • Figure 17 is a schematic view of a thirteenth embodiment of a multi-flow plate heat exchanger having a pipe joint 18 on the outer side of the clamp end plate 17, a flange 19 at one end of the pipe joint 18, and a flange 19 of the pipe joint
  • the gasket 20, the fluid does not come into contact with the clamping end plate 17 when entering or exiting the multi-plate heat exchanger from the pipe joint 18, thereby reducing the corrosion resistance requirement for the clamping end plate 17.
  • a sealing gasket may be added between the nut 21 and the outer side of the clamping end plate 17 to further improve the sealing performance of the pipe joint 18; if the pipe joint 18 is made of plastic, the flange 19 of the pipe joint and the angular hole are
  • the non-metallic sheets 14 can be sealed by glue joint sealing or ultrasonic or hot-melt welding, and the sealing gasket 20 is omitted, which is not shown.
  • the multi-flow plate heat exchangers in the above embodiments are two processes, and the multi-flow plate heat exchangers of more processes can be pushed in the same way.

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

Description

一种多流程板式换热器提高换热效率的方法及产品 技术领域
本发明涉及一种板式换热器提高换热效率的方法及产品， 尤其是多流程板 式换热器提高换热效率的方法及产品。
背景技术
板式换热器由多张有冲压波纹和角孔的薄金属板片相互重叠组装在一起， 相邻板片之间通过悍接密封的称为钎悍式板式换热器或焊接式板式换热器； 相 邻板片之间的四周有密封垫片并由夹紧端板和夹紧螺栓夹紧密封的称为可拆式 板式换热器， 板片的角孔形成流体的分配管和汇集管， 相邻板片之间形成冷、 热流体的流道， 合理地将冷、 热流体分开， 使冷、 热流体分别在每块有冲压波 纹和角孔的薄金属板片两侧的流道中逆向流动， 通过薄金属板片进行热量交换， 薄金属板片也称为换热板片； 板式换热器具有换热效率高、 热损失小、 结构紧 凑、 安装方便、 应用广泛、 价格低廉、 使用寿命长等特点。 在一些特殊场合， 由于流体流道不足够长， 导致冷、 热流体之间换热不够充分， 需要通过增加流 程数量来增加流体流道的长度， 增加流程数量是通过流程转折板来实现的， 有 流程转折板的板式换热器称为多流程板式换热器。 流体的流动方向在流程转折 板的前后相反， 由于流程转折板也是由相同的薄金属板冲压而成的， 因而会出 现已被加热或冷却的流体又被重新冷却或加热的现象， 导致每种流体的进出口 温差减小， 降低了换热器的换热效率， 在余热回收中则降低了余热回收利用率， 特别是当冷、 热流体流道数较少、 单个流程较长时尤为突出。 另外流体在通过 流程转折板后其流动方向发生反向， 在冷、 热流体的流动方向不希望发生反向 的场合也限制了多流程板式换热器的应用。
发明内容 本发明第一个要解决的技术问题是克服现有技术中的不足， 提供一种在多 流程板式换热器的流程转折板两侧已被加热或冷却的流体避免被重新冷却或加 热从而提高换热效率的方法。
为了解决以上技术问题， 本发明所采用的技术方案是：
流程转折板两侧的流体是相互隔热的。
采用上述技术方案的有益效果是： 该方法制作容易、 成本低廉、 结构简单、 性能可靠， 同时提高了多流程板式换热器的换热效率。
本发明第二个要解决的技术问题是： 提供一种应用上述多流程板式换热器 提高换热效率的方法的多流程板式换热器。
为了解决以上技术问题， 本发明所采用的技术方案是：
多流程板式换热器由多张有冲压波纹和角孔的薄金属板片与至少一张流程 转折板叠装， 相邻板片之间通过焊接密封或相邻板片之间的四周有密封垫片并 由夹紧端板和夹紧螺栓夹紧密封， 形成冷、 热流体的流道， 所述的流程转折板 是一张隔热的板片。
多流程板式换热器由多张有冲压波紋和角孔的薄金属板片与至少一张流程 转折板叠装， 相邻板片之间通过悍接密封或相邻板片之间的四周有密封垫片并 由夹紧端板和夹紧螺栓夹紧密封， 形成冷、 热流体的流道， 所述的流程转折板 由至少两张板片组成。
多流程板式换热器由多张有冲压波纹和角孔的薄金属板片与至少一张流程 转折板叠装， 相邻板片之间通过焊接密封或相邻板片之间的四周有密封垫片并 由夹紧端板和夹紧螺栓夹紧密封， 形成冷、 热流体的流道， 所述的流程转折板 由至少两张隔热的板片组成。
采用上述技术方案的有益效果是： 多流程板式换热器换热效率高， 同时产 品结构简单、 性能可靠、 制作容易。
本发明第三个要解决的技术问题是： 保持经过流程转折板后的流体流动方 向不变， 满足蒸发或冷凝有相变时的换热或要求上热下冷的换热等场合的需要。
为了解决以上技术问题， 本发明所采用的技术方案是- 所述的隔热流程转折板内有冷、 热流体各自独立的流道。
组成所述的流程转折板的隔热板片之间有冷、 热流体各自独立的流道。 采用上述技术方案的有益效果是： 经过流程转折板后的流体能维持流动方 向不变， 满足了蒸发或冷凝有相变时的换热或要求上热下冷的换热等场合的需 要。
本发明第四个要解决的技术问题是： 提供一种低成本、 易加工的非金属流 程转折板、 与夹紧端板相邻的非金属板片， 以及夹紧端板的管路接头。
为了解决以上技术问题， 本发明所采用的技术方案是：
所述的隔热流程转折板是由两张方向相反的鱼骨形非金属板片中间夹一张 有角孔的非金属板片重叠而成。
由一张或两张鱼骨形非金属板片和一张有角孔的非金属板片重叠， 并紧贴 所述的夹紧端板。
所述的夹紧端板外侧的管路接头一端有法兰， 所述的有角孔的非金属板片 和管路接头一端的法兰之间有密封垫圈， 管路接头另一端有螺紋并伸出所述的 夹紧端板的角孔外， 有一螺母与管路接头另一端的螺纹连接。
采用上述技术方案的有益效果是： 非金属流程转折板和与夹紧端板相邻的 非金属板片， 不仅提高了换热效率减少了热散失， 而且还有结构简单， 制作容 易， 成本低廉的优点； 管路接头不仅同样具有结构简单， 制作容易， 成本低廉 的优点， 而且同时还降低了对夹紧端板的耐腐蚀性要求。 附图说明
图 1是现有多流程板式换热器的示意图。
图 2是多流程板式换热器第一个实施例的示意图。
图 3是多流程板式换热器第二个实施例的示意图。
图 4是多流程板式换热器第三个实施例的示意图。
图 5是多流程板式换热器第四个实施例的示意图。
图 6是多流程板式换热器第五个实施例的示意图。
图 7是多流程板式换热器第六个实施例的示意图。
图 8是多流程板式换热器流程转折板用的两张鱼骨形非金属板片示意图。 图 9是多流程板式换热器流程转折板示意图。
图 10是多流程板式换热器第七个实施例的示意图。
图 11是多流程板式换热器流程转折板示意图。
图 12是多流程板式换热器第八个实施例的示意图。
图 13是多流程板式换热器第九个实施例的示意图。
图 14是多流程板式换热器第十个实施例的示意图。
图 15是多流程板式换热器第十一个实施例的示意图。
图 16是多流程板式换热器第十二个实施例的示意图。
图 17是多流程板式换热器第十三个实施例的示意图。
图中有箭头的实线代表一种流体， 有箭头的虚线代表另一种流体， 箭头代 表流体的流动方向， 图 1-图 7以及图 10、 图 12省略了夹紧端板。
具体实施方式
下面结合附图对本发明作进一步详细描述。
图 1是现有多流程板式换热器的示意图， 图中一共画出 10个流道， 分别用 I -X表示， 其中 I、 III、 V、 VII、 Κ流道为一种流体， 用8、 Β' 分别代表其进、 出口； II、 IV、 VI、 VID、 X流道为另一种流体， 用 、 A' 分别代表其进、 出口， 两种流体逆流换热； V和 VI流道之间的薄金属板片是流程转折板 1，两种流体的 流动方向在流程转折板 1的前后都改变 180， 即 IV、 VI流道中的流体的流动方 向相反， V、 νπ流道中的流体的流动方向相反， 流程转折板 1左侧的 V流道内 的流体被 IV流道内的流体加热或冷却， 流程转折板 1右侧的 VI流道内的流体被 π流道内的流体冷却或加热， 然而同时 V流道内的流体通过导热良好的流程转 折板 1与 VI流道内的流体进行热量交换， 从而出现 V流道内已被加热或冷却的 流体又被 VI流道内的流体重新冷却或加热的现象， 最终导致每种流体的进、 出 口温差减小， 即降低了换热器的换热效率， 如在余热回收系统中， 则降低了余 热回收利用率。 尽管 V和 VI流道内的流体是顺流换热， 在单个流程较长时， 特 别是当流体流道数较少时， 流程转折板 1两侧流体通过流程转折板 1传递的热 量对换热效率的影响就尤为突出。 如果将流程转折板 1换成可隔热的， 则流程 转折板 1两侧的流体相互之间热量交换可减少， 即提高了多流程板式换热器的 换热效率。
图 2是多流程板式换热器第一个实施例的示意图， 流道 V和流道 VI内的流 体是逆流换热， 其换热温差比图 1中现有多流程板式换热器 V和 VI流道之间流 体的换热温差大， 将现有多流程板式换热器中导热良好的流程转折板 1改换成 由隔热材料制成的隔热流程转折板 2， 虽然此时流道 V和流道 VI内的流体是逆 流， 但由于流程转折板 2是隔热的， V和 VI流道内流体之间的换热量显著降低， 从而提高了换热器的换热效率， 当然在现有的流程转折板 1两侧涂抹或复合隔 热材料层制成隔热流程转折板 2， 也可起到同样的效果； 此时多流程板式换热器 相当于两台单流程板式换热器串联， 但省去了两块夹紧端板和两根连接管。
图 3是多流程板式换热器第二个实施例的示意图， 两张有冲压波紋和角孔 的薄金属板片分别是 3和 3' ， 组成流程转折板， 两张板片 3和 3' 之间无流体 存在，与第一个实施例中的流程转折板 2—样， 两种流体经过板片 3和 3 ' 后流 动方向都改变 180， 只要两张板片 3和 3' 之间无流体存在， 即保持真空或充满 空气， 就可以组成隔热的流程转折板， 也就相当于第一个实施例中的流程转折 板 2， 因为两张板片 3和 3 ' 的冲压波紋之间只有局部区域相互接触， 即使两张 板片 3和 3' 都是由导热良好的材料制成，同样也可以起到减少 V和 VI流道内流 体之间热量交换的效果， 从而提高换热器的换热效率， 这种方案可在钎焊式或 焊接式板式换热器中使用， 因为钎悍式或焊接式板式换热器中无法使用非金属 的隔热材料；当然在可拆式板式换热器中板片 3和 3' 也可以采用隔热材料制成， 或两侧涂抹或复合隔热材料层， 即用两张隔热的板片组成一张流程转折板， 与 第一个实施例中的一张隔热的流程转折板 2相比， 能进一步减少流程转折板两 侧的流体相互之间的热量交换。
在上面第一个、 第二个实施例中， 流道中的流体在经过流程转折板后流动 方向改变 180°， 然而在有些场合需要流体在换热器流道内的流动方向维持不变， 如蒸发或冷凝有相变时的换热或要求上热下冷的换热场合， 即流道中的流体在 经过流程转折板后流动方向需要改变 360°, 相当于流动方向改变两个 180ΰ。
图 4是多流程板式换热器第三个实施例的示意图， 两张有冲压波纹和角孔 的板片， 分别是板片 4和 5, 两种流体每经过一张板片后流动方向都改变 180°, 流动方向一共改变 360Q, 即两种流体在经过两张板片 4和 5组成流程转折板后 流动方向保持不变， 两张板片 4和 5之间有两种流体各自独立的流道， 两张板 片侧面涂抹或复合隔热材料层， 或都由隔热材料制成， 从而提高换热器的换热 效率。 当然这样也可以理解为这是一块流程转折板， 即一块内部有冷、 热流体 各自独立的流道， 同时侧面涂抹或复合隔热材料层或由隔热材料制成的并且流 动方向改变前后的流体之间相互隔热的流程转折板； 此时相当于两台单流程并 且流体流动方向一至的板式换热器串联， 但却省去了两块夹紧端板和两根连接 管。
图 5是多流程板式换热器第四个实施例的示意图， 与第三个实施例不同的 是： 板片 4和 5之间还有板片 6, 板片 4和 6之间、板片 5和 6之间是两种流体 各自独立的流道， 其中板片 4和 5都是隔热的， 板片 6可以是导热的， 也可以 是隔热的， 当然这也可以理解为这是一块流程转折板， 即一块内部有冷、 热流 体各自独立的流道， 同时侧面涂抹或复合隔热材料层或由隔热材料制成的并且 流动方向改变前后的流体之间相互隔热的流程转折板
图 6是多流程板式换热器第五个实施例的示意图， 与第四个实施例不同的 仅仅是： 板片 4和 5之间、 板片 5和 6之间各自独立的流道内的流体种类和流 体的流动方向。
图 7是多流程板式换热器第六个实施例的示意图， 钎焊式或焊接式板式换 热器中不适合使用非金属的隔热材料， 为了满足流体在换热器流道内的流动方 向维持不变的要求， 可将多流程板式换热器第五个实施例的示意图中的板片 4 和板片 5用两张有冲压波紋和角孔的薄金属板片组成的板片组代替， 即用两张 有冲压波紋和角孔的薄金属板片 4和 4' 代替板片 4; 用两张有冲压波紋和角孔 的薄金属板片 5和 5 ' 代替板片 5， 和第二个实施例一样， 两张有冲压波紋和角 孔的薄金属板片之间无流体存在， 即保持真空或充满空气， 就可以组成隔热的 流程转折板。
以上多流程板式换热器实施例中的流程转折板两侧流道内的流体相互之间 是隔热的， 即流程转折板两侧流道内的流体只与相邻的有冲压波纹和角孔的薄 金属板片一侧的流体进行热量交换， 故流程转折板两侧流道内流体的流量只要 是其它同一流体流道内的一半流量即可， 即 V流道内流体的流量只需要 ΠΙ流道 内流体的一半流量、 VI流道内流体的流量只需要 VIA流道内流体的一半流量， 同 样与夹紧端板相邻流道的流体的流量也只要其它同一流体流道内的一半流量即 可， 即 I流道内流体的流量只需要 III流道内的流体的一半流量、 X流道内流体 的流量只需要 νιπ流道内的流体的一半流量， 否则流程转折板两侧流道内的流体 或与夹紧端板相邻流道内的流体未能进行充分换热就进入下一个流道或流出换 热器， 降低了换热器的换热效率， 当冷、 热流体流道数较少时尤为突出。
图 8是多流程板式换热器流程转折板用的两张鱼骨形非金属板片示意图， 这两张鱼骨形非金属板片 11和 12只是方向相反， 鱼骨形是与换热板片常见的 人字形冲压波纹相对应的。
图 9是多流程板式换热器流程转折板示意图， 多流程板式换热器流程转折 板 13是一张有角孔无冲压波纹的平板型非金属板片， 用于压紧密封垫片。
图 10是多流程板式换热器第七个实施例的示意图， 由两张方向相反的鱼骨 形非金属板片 11和 12中间夹一张有角孔无冲压波纹的非金属板片 13组成组合 式多流程板式换热器流程转折板， 鱼骨形非金属板片 11和 12的厚度是其它有 角孔和冲压波紋薄金属板片 10的波紋深度一半左右， 有角孔无冲压波紋的非金 属板片 13—侧的密封垫片 8的厚度大于两张普通的有角孔和冲压波纹薄金属板 片 10之间的密封垫片 15， 而有角孔无冲压波紋的非金属板片 13另一侧的密封 垫片 9的厚度小于密封垫片 15。 鱼骨形非金属板片 11和 12的方向与相邻的有 角孔和冲压波紋薄金属板片 10的人字形波纹方向相反， 保证流体在鱼骨形非金 属板片的空隙和薄金属板片 10的人字形波紋之间流动， 改变图 8中的角度 α则 可改变流体的流量， 使其是同一流体其它流道内的一半流量； 与鱼骨形非金属 板片 11和 12相邻的两张有角孔和冲压波纹薄金属板片 10的人字形波纹方向相 反， 刚好要求鱼骨形非金属板片 11和 12的方向相反， 同时鱼骨形非金属板片 11和 12的方向相反可大大提高组合式流程转折板的强度。有角孔无冲压波紋的 非金属板片 13的厚度可根据材料的强度和导热系数决定， 使其既满足强度要求 又将流程转折板两侧流道内的流体的换热量降到最低。 如果有角孔和冲压波纹 薄金属板片 10的波紋形状不是人字形， 则非金属板片 11和 12不采用鱼骨形， 而采用相对应的形状， 只要满足流量和强度要求即可。
图 11是多流程板式换热器流程转折板示意图， 多流程板式换热器流程转折 板 14是一张有角孔无冲压波纹的非金属板， 其四周及两个角孔外侧是一平面， 用于压紧密封垫片， 并且中部向一侧凸起。
图 12是多流程板式换热器第八个实施例的示意图， 与第七个实施例不同的 是： 由两张方向相反的鱼骨形非金属板片 11和 12中间夹一张有角孔无冲压波 纹并且中部向一侧凸起的非金属板片 14组成组合式多流程板式换热器流程转折 板， 两张鱼骨形非金属板片 11和 12的厚度相等， 并且是其它有角孔和冲压波 纹薄金属板片 10的波紋深度一半， 同时非金属板片 14的凸起高度等于鱼骨形 非金属板片 11的厚度， 这样密封垫片可直接采用两张普通的有角孔和冲压波紋 薄金属板片 10之间的密封垫片 15，而不必另制作两套模具用于生产密封垫片 8、 9。
图 13是多流程板式换热器第九个实施例的示意图， 与夹紧端板 16相邻流 道内的流体的流量只要是其它同一流体流道内的一半流量即可， 故采用第八个 实施例同样的由两张方向相反的鱼骨形非金属板片 11和 12中间夹一张有角孔 无冲压波紋并且中部向一侧凸起的非金属板片 组成的组合式板片置于一块夹 紧端板 16的内侧面， 改变图 8中的角度 α， 使其流道内流体的流量刚好是其它 同一流体流道内的一半流量， 同时非金属板片 14还可以降低其流道内流体通过 夹紧端板 16传热而损失的能量。 图 14是多流程板式换热器第十个实施例的示意图， 与另一块夹紧端板 17 相邻流道也可采用第八个实施例同样的方法， 使其流道内流体的流量刚好是其 它同一流体流道内的一半流量， 同时还可以降低其流道内流体通过夹紧端板 17 传热而损失的能量。
图 15是多流程板式换热器第十一个实施例的示意图， 由一张鱼骨形非金属 板片 11或 12与一张有角孔无冲压波纹平板型非金属板片 13组成的组合式板片 置于一块夹紧端板 16的内侧面， 密封垫片 9的厚度小于密封垫片 15的厚度， 这样和第九个实施例相比可省去一张鱼骨形非金属板片。
图 16是多流程板式换热器第十二个实施例的示意图， 由一张鱼骨形非金属 板片 11或 12与一张有角孔无冲压波纹并且中部向一侧凸起的非金属板片 14组 成的组合式板片置于一块夹紧端板 17的内侧面， 密封垫片 9的厚度小于密封垫 片 15的厚度， 这样和第十个实施例相比同样可省去一张鱼骨形非金属板片。
图 17是多流程板式换热器第十三个实施例的示意图， 夹紧端板 17的外侧 面有管路接头 18， 管路接头 18的一端有法兰 19, 管路接头的法兰 19和有角孔 无冲压波纹的非金属板片 14之间有密封垫圈 20， 管路接头 18伸出夹紧端板 17 外的另一端有螺紋， 螺母 21内有螺紋， 螺母 21通过螺纹压紧密封垫圈 20， 流 体从管路接头 18进出多流程板式换热器时不与夹紧端板 17接触， 从而降低了 对夹紧端板 17的耐腐蚀性要求。 螺母 21和夹紧端板 17外侧之间还可增加一个 密封垫圈， 进一步提高管路接头 18的密封性能； 管路接头 18如采用塑料材质， 则管路接头的法兰 19和有角孔的非金属板片 14之间可通过胶水连接密封或超 声波或热熔焊接密封， 省去密封垫圈 20， 图中未画出。
以上实施例中多流程板式换热器都是两个流程， 更多流程的多流程板式换 热器同理可推。

Claims

权 利 要 求 书
1、 一种多流程板式换热器提高换热效率的方法， 其特征在于： 流程转折板 两侧的流体是相互隔热的。
2、 一种应用权利要求 1提高换热效率的方法的多流程板式换热器， 它由多 张有冲压波紋和角孔的薄金属板片与至少一张流程转折板叠装， 相邻板片之间 通过焊接密封或相邻板片之间的四周有密封垫片并由夹紧端板和夹紧螺栓夹紧 密封， 形成冷、 热流体的流道， 其特征在于： 所述的流程转折板是一张隔热的 板片。
3、 一种应用权利要求 1提高换热效率的方法的多流程板式换热器， 它由多 张有冲压波紋和角孔的薄金属板片与至少一张流程转折板叠装， 相邻板片之间 通过焊接密封或相邻板片之间的四周有密封垫片并由夹紧端板和夹紧螺栓夹紧 密封， 形成冷、 热流体的流道， 其特征在于： 所述的流程转折板由至少两张板 片组成。
4、 一种应用权利要求 1提高换热效率的方法的多流程板式换热器， 它由多 张有冲压波紋和角孔的薄金属板片与至少一张流程转折板叠装， 相邻板片之间 通过焊接密封或相邻板片之间的四周有密封垫片并由夹紧端板和夹紧螺栓夹紧 密封， 形成冷、 热流体的流道， 其特征在于： 所述的流程转折板由至少两张隔 热的板片组成。
5、 根据权利要求 2所述的多流程板式换热器， 其特征在于： 所述的隔热流 程转折板内有冷、 热流体各自独立的流道。
6、 根据权利要求 4所述的多流程板式换热器， 其特征在于： 组成所述的流 程转折板的隔热板片之间有冷、 热流体各自独立的流道。
7、 根据权利要求 2所述的多流程板式换热器， 其特征在于： 所述的隔热流 程转折板是由两张方向相反的鱼骨形非金属板片中间夹一张有角孔的非金属板 片重叠而成。
8、 根据权利要求 2所述的多流程板式换热器， 其特征在于： 由一张或两张 鱼骨形非金属板片和一张有角孔的非金属板片重叠， 并紧贴所述的夹紧端板。
9、 根据权利要求 8所述的多流程板式换热器， 其特征在于： 所述的夹紧端 板外侧的管路接头一端有法兰， 所述的有角孔的非金属板片和管路接头一端的 法兰之间有密封垫圈， 管路接头另一端有螺紋并伸出所述的夹紧端板的角孔外， 有一螺母与管路接头另一端的螺纹连接。
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