EP3957940A1 - Module d'échangeur de chaleur à plaque à contre-courant et échangeur de chaleur à plaque à contre-courant - Google Patents

Module d'échangeur de chaleur à plaque à contre-courant et échangeur de chaleur à plaque à contre-courant Download PDF

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Publication number
EP3957940A1
EP3957940A1 EP21151998.8A EP21151998A EP3957940A1 EP 3957940 A1 EP3957940 A1 EP 3957940A1 EP 21151998 A EP21151998 A EP 21151998A EP 3957940 A1 EP3957940 A1 EP 3957940A1
Authority
EP
European Patent Office
Prior art keywords
plate
heat exchanger
plate heat
individual
countercurrent
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP21151998.8A
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German (de)
English (en)
Inventor
Olivier Brasseur
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP3957940A1 publication Critical patent/EP3957940A1/fr
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/082—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys
    • 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
    • F28D9/0062—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 spaced plates with inserted elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/14—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by endowing the walls of conduits with zones of different degrees of conduction of heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/082—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys
    • F28F21/083—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys from stainless steel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/005—Arrangements for preventing direct contact between different heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/06—Fastening; Joining by welding

Definitions

  • the invention relates to a countercurrent plate heat exchanger module with individual plates which are joined together to form a plate stack, with a flow channel for a first gaseous medium or for a second gaseous medium being formed alternately between two adjacent individual plates in the height direction of the plate stack, with Plate stack is arranged at least one spacer, the individual plates each having different materials in the longitudinal direction. Furthermore, the invention relates to a countercurrent plate heat exchanger.
  • Plate heat exchangers are well known per se from the prior art, so that separate printed evidence is not required at this point. It is therefore only an example of the DE 1 501 586 A1 referenced, which discloses a heat exchanger in which corrugated plates can be laminated by means of edge spacer strips.
  • a composite of alternating panels and a flat back panel incorporates spacer strips between edge portions of the panels. The spacer strips are straight and run the full length of both sides of the two panels. Where lateral inlet and outlet ports are provided, the spacer strips are in the shape of an "L".
  • Plate heat exchangers which can be operated in cross flow are known. Furthermore, plate heat exchangers are known which can be operated in counterflow.
  • Cross-flow plate heat exchangers have the advantage that they can be designed so that they can be adapted comparatively well to individual requirements.
  • the plate sizes and the plate spacing can be made variable. On the one hand, this can influence the material temperature of the heat exchanger, which has advantages over corrosion.
  • particle-laden gases can also flow comparatively easily through a heat exchanger with a comparatively large plate spacing.
  • cross-flow plate heat exchangers are different in terms of their efficiency limited efficiency. Furthermore, such heat exchangers can no longer be operated effectively with comparatively large volume flows.
  • Countercurrent plate heat exchangers have a comparatively good level of efficiency and can process comparatively large volume flows effectively. However, due to their construction, they cannot be adapted to individual requirements. Instead, they are basically only built and offered in standardized versions. It therefore happens regularly that the customer has to order counterflow plate heat exchangers whose maximum output is not required or which do not optimally utilize the available installation space.
  • the invention is therefore based on the object of specifying a heat exchanger which is improved over the prior art in terms of its individualizability and its efficiency, and this at the same time as reduced production costs.
  • the invention proposes a countercurrent plate heat exchanger module of the type mentioned at the beginning, which is characterized in that the individual plates each have a first plate section made of a first material and a second plate section made of a second material, the second plate section corresponding to the first plate section downstream in the flow direction of a medium condensing upon cooling, and wherein the second plate portion is formed of a corrosion-resistant stainless steel.
  • the invention proposes a countercurrent plate heat exchanger with at least one countercurrent plate heat exchanger module according to the invention.
  • the individual plates are arranged at a distance from one another by the spacers.
  • “height direction” denotes the direction in which the individual panels are stacked one on top of the other to form the panel stack.
  • the distance between the Individual panels can basically be freely selected by means of the spacers.
  • the size of the spacers can also be freely selected.
  • the counterflow plate heat exchanger module and thus also the counterflow plate heat exchanger can be individualized with regard to the required output by adjusting the plate spacing using the spacers. A high level of efficiency is also achieved due to countercurrent operation.
  • the counterflow plate heat exchanger according to the invention can basically be adapted to any high volume flows due to its modular configuration from counterflow plate heat exchanger modules according to the invention. The lower the volume flow to be processed, the fewer modules are required, and the higher the volume flow, the more modules the heat exchanger according to the invention can be constructed from. It is also possible to retrofit existing countercurrent plate heat exchangers according to the invention with additional modules.
  • the distance between two adjacent individual panels can be adjusted using the spacers.
  • a distance between 5 mm and 30 mm can preferably be set.
  • each individual plate with the exception of the two outermost individual plates, has a directly adjacent individual plate on each of its flat sides.
  • the aforementioned individual plates therefore delimit a flow channel for the first medium on one of their two flat sides and a flow channel for the second medium on the other of the two sides. It is preferably provided that at least some of the individual panels, in particular all the individual panels apart from the two outermost individual panels, are at a different distance from their two respective adjacent individual panels. In this respect, the flow channels for the first medium have a different flow cross section than the flow channels for the second medium.
  • the individual plates, which form flow channels between them for the first medium at a distance of between 5 mm and 30 mm from one another. It is also preferred to arrange the individual plates, which form flow channels between them for the second medium, at a distance of between 5 mm and 30 mm from one another.
  • the individual plates are preferably rectangular.
  • the individual panels have two opposite short sides and two opposite long sides.
  • the individual panels are aligned in the panel stack so that the long sides and the short sides parallel to each other.
  • the individual plates each have a first plate section made of a first material and a second plate section made of a second material.
  • the second plate section is arranged downstream of the first plate section in the direction of flow of a medium that condenses on cooling.
  • this second plate section consists of a corrosion-resistant high-grade steel.
  • one of the two media is one that condenses when cooled.
  • This can be water vapor, for example.
  • other gaseous media such as flue gases, can also lead to the formation of condensate as a result of cooling, which then condenses on the individual plates.
  • such a condensate does not form when the medium enters the countercurrent plate heat exchanger module, but only after it has covered a certain flow path within the module.
  • the flow path can be functionally subdivided into a non-condensation area on the one hand and a condensation area on the other.
  • the individual plates have a first plate section made of a first material and a second plate section made of a second material.
  • the first plate section lying outside of the condensation area does not need to be made of corrosion-resistant high-grade steel because no condensate is formed in this area. This creates the possibility of choosing a material for the first plate section that is much cheaper than corrosion-resistant stainless steel. As a result, considerable material costs can be saved, which makes production cheaper and therefore more economical.
  • the result of the configuration according to the invention is that only the area of an individual plate is made of corrosion-resistant high-grade steel in which a condensate forms when used as intended.
  • the area in front of this area in the direction of flow can be made of a less expensive material compared to corrosion-resistant stainless steel, since no condensate forms in this area, which is why a corrosion-resistant design is not required in this area.
  • the second plate section is formed from a high-alloy high-grade steel, preferably an austenitic high-grade steel, in particular alloyed 1.4539 or higher.
  • the corrosion-resistant stainless steel is preferably a high-alloy stainless steel.
  • This can preferably be an austenitic high-grade steel, for example a high-grade steel of type 1.4539.
  • Such stainless steel stands out its high resistance to corrosion and is therefore suitable as a material for the second plate section.
  • the first plate section is formed from a low-alloy stainless steel, preferably of the 1.4301 type.
  • a high-grade steel is comparatively inexpensive, in particular in comparison to a high-alloy high-grade steel such as is used to form the second plate section.
  • significantly reduced manufacturing costs can be achieved in comparison to forming the entire individual plate from a high-alloy stainless steel.
  • Both the low-alloy stainless steel of the first plate section and the high-alloy stainless steel of the second plate section can be processed using conventional methods and devices, in particular welded to one another.
  • the two plate sections are connected to one another without any protrusions, preferably welded to one another.
  • the projection-free connection of the two plate sections ensures that no unwanted pressure losses occur when the connection area between the first plate section and the second plate section is overflowed.
  • the projection-free connection is achieved in a simple way by welding the two plate sections together. This can be done with laser welding, for example.
  • the two plate sections are placed face to face and then welded together. If necessary, the connection area between the first and second panel sections can then be reworked, for example by grinding, so that a level, projection-free transition between the first panel section and the second panel section is ensured.
  • the first panel section has an extent in the longitudinal direction of the individual panel of 30% to 70%, preferably 50% of the total longitudinal extent of the individual panel.
  • the longitudinal extension of a plate section depends primarily on the subsequent application, ie the media to be routed through the heat exchanger. There is at When selecting the longitudinal extent of the first plate section, it is particularly important to ensure that no condensate is formed in this area when used as intended.
  • the length of the first panel section can be chosen to be 50% of the total length of an individual panel. In this case, the first plate section and the second plate section are therefore of the same length.
  • the first plate section can also be selected to be shorter or longer. What is decisive is that such an extension ratio in the longitudinal direction of the first plate section and the second plate section is selected such that condensate formation takes place exclusively in the second plate section.
  • the extent of the first plate section should be selected to be as long as possible, so that maximum cost savings are achieved.
  • the individual plates are designed without embossing, particularly in the area of the flow channels. This simplifies the manufacturing process, since complex embossing and the associated embossing machines can be dispensed with.
  • the spacers also make it possible to use not only completely embossing-free individual plates, but even completely flat individual plates. Individual plates with normalized standard sizes are preferably used, which are then immediately ready for use in order to be assembled into a plate stack.
  • the individual panels can be formed with variable dimensions. This allows the counterflow plate heat exchanger to be further individualized. It is provided in particular that the individual plates have a thickness of between 0.8 mm and 6 mm, preferably between 1 mm and 3 mm. As a result, resistance to corrosion and mechanical stability of the heat exchanger can be adjusted. It is also provided that the individual panels have a width of between 1000 mm and 2000 mm. This is particularly advantageous compared to countercurrent plate heat exchangers known from the prior art, since their width is fixed.
  • the individual plates can be of any length.
  • the individual panels have a length of 1 m to 10 m, preferably 1 m to 4 m, more preferably 2 m to 3.5 m, particularly preferably 3 m, exhibit.
  • Heat exchangers with modules constructed from individual plates with the same width are preferred. However, heat exchangers with modules can also be built from plates with different widths. As a result, the heat exchanger is more flexibly adapted to the given installation space. This depends on the individual requirements for the heat exchanger according to the invention.
  • At least one spacer is designed as an elongate, rectangular profile. It can be designed in the form of a rectangular frame.
  • the spacers are preferably arranged in the edge regions of the long sides of the respective individual panels.
  • Two spacers are preferably arranged in each case between two adjacent individual plates.
  • the two spacers are arranged in edge regions of the individual panels that run opposite one another. They run parallel to each other along the long sides of the individual panels.
  • the areas running between the short sides of adjacent individual plates, which are arranged one above the other in the height direction of the plate stack, are open. In particular, they are designed without spacers. In this way, inlets and outlets of the flow channels for the first and the second medium can be formed on the short sides.
  • the respective opening of the inlets and outlets can be adapted to the individual requirements such as pressure loss, accessibility and the like, in particular with regard to flow cross section and position.
  • the cross section of a spacer designed as a profile is essentially rectangular.
  • the training as a full profile is preferred.
  • the spacers are preferably connected to the individual plates in a gas-tight manner. The spacers therefore close the flow channels laterally in a gas-tight manner. The spacers form the respective side walls of the flow channels.
  • the spacer is L-shaped in plan view. With the intended arrangement between the individual panels, it thus forms part of a frame.
  • the frame part extends in this case along the long side of the Individual plates and extends at least a part of the short side of the individual plates. This improves the mechanical stability in particular.
  • the L-shaped spacer is preferably formed from two spacers which are connected to one another at right angles, preferably welded, and are rectangular in plan view.
  • At least one spacer is designed as a separate component.
  • spacers are preferably designed as separate components.
  • the spacer(s) is/are preferably welded to the individual plates.
  • the connecting surfaces are welded to the individual plates.
  • a spacer, in particular a single spacer, which is formed as a separate component is arranged only between the, in particular each, short side of adjacent individual panels.
  • spacers made of different materials to be precise in accordance with the materials used for the plate sections of a single plate.
  • the material used for spacers in the region of the second plate section is preferably the material from which the second plate section is also formed.
  • the spacers in the area of the first plate sections are formed from the material of the first plate sections. A further reduction in the production costs can also be achieved in this way.
  • At least one spacer is formed in one piece with at least one of the individual plates.
  • the spacer is preferably formed by bending an edge section of the single plate.
  • the free end of the spacer is materially connected, preferably welded, to an immediately adjacent further individual plate to form the plate stack.
  • a weld seam is saved in an advantageous manner. This leads to a reduction in production costs and to an improvement in the mechanical stability, in particular with regard to corrosion, of the plate heat exchanger.
  • the spacer is preferably formed in that a corresponding edge section of two adjacent individual panels is bent over in the direction of the other edge section in each case. The bent edge section of one individual panel is connected to one another, in particular welded, to an edge section of the other individual panel.
  • a spacer only between the, in particular each, long side of adjacent individual panels arranged, which is formed by bending.
  • a single panel consists of two panel sections made of different materials. Accordingly, the plate sections are first produced and then connected to one another to form a single plate. Then the edge of the individual plate is bent to form the spacers, with the result that not only plate sections made of different materials but also spacers made of corresponding materials are created.
  • additional spacers in particular in the form of knobs, are arranged between individual plates.
  • the additional spacers serve to ensure constant plate spacing over at least part of the flow channel.
  • the spacers arranged in the edge area are already sufficient for this. If, however, comparatively large dimensioned individual plates are used, it can be advantageous to provide the aforementioned additional spacers.
  • the additional spacers, in particular the knobs are preferably welded onto at least one of the individual plates. As a result, the individual plates can nevertheless be designed completely free of embossing, as is preferably provided.
  • a nub field is preferably formed by a plurality of nubs arranged at regular intervals from one another and distributed over the flow channel.
  • the field of knobs advantageously contributes to an improvement in the dimensional stability of the heat exchanger.
  • the height of the nubs can be adjusted to the desired distance between the individual panels.
  • the nubs are preferably formed from the same material as the plate section that carries the nubs. Accordingly, nubs for a second plate section are preferably formed from a high-alloy stainless steel, whereas nubs for a first plate section are made from a low-alloy stainless steel.
  • At least one reinforcement element is arranged between two individual plates. It is preferably arranged in the flow channel along at least one of the long sides.
  • the reinforcement element preferably extends from one of the individual plates to the immediately adjacent individual plate. It is preferably integrally connected at one end to the first individual plate, in particular welded. On the other end, the reinforcement element is preferably bonded to the second individual plate, especially welded.
  • the reinforcement element is preferably formed from a weldable material, in particular metal, preferably steel.
  • the reinforcing element is designed with a comb-like contour based on the model of a “comb”. It has an elongate web and prongs extending away from this web at an angle, in particular a right angle.
  • the web is arranged in such a way that it extends parallel to the long sides of the individual panels. Its side facing away from the tines is connected, in particular welded, to the first individual plate. In contrast, the free ends of the prongs are connected, in particular welded, to the second individual plate.
  • a reinforcement element is preferably made of the material of the plate section to which the reinforcement element is connected. Preferably, a reinforcing member is divided into two sections corresponding to the plate design, which sections are welded to each other.
  • the sections of the connecting element consist of the same materials from which the panel sections of the individual panel are also formed, with which the connecting element is connected in the final assembled state. This material configuration also serves on the one hand for improved protection against corrosion and on the other hand for reducing production costs.
  • the reinforcement element can extend over the entire length of the flow channel or only over a section with a certain length.
  • the length of the section can be freely selected.
  • the reinforcement element preferably extends over the entire length of the flow channel.
  • the long sides of the counterflow plate heat exchanger are provided with a cover.
  • the cover covers the connection points, in particular weld seams, between the spacer and the individual plates. On the one hand, this serves to protect the weld seams from corrosion. On the other hand, this creates an additional diffusion barrier, which prevents the media from escaping over the long sides of the countercurrent plate heat exchanger escape.
  • the cover is preferably formed by a sheet metal, in particular sheet steel.
  • the cover is preferably integrally connected, in particular welded, to individual plates and/or spacers.
  • the counterflow plate heat exchanger has at least one counterflow plate heat exchanger module according to the invention. This can be sufficient for simple applications, since the modules themselves can be customized by selecting the dimensioning of the individual panels and the selection of the panel spacing.
  • the countercurrent plate heat exchanger according to the invention has a plurality of countercurrent plate heat exchanger modules.
  • the modules are arranged one above the other and/or next to one another in such a way that the long sides of the individual panels run parallel to one another.
  • the individual countercurrent plate heat exchanger modules have different dimensions, in particular with regard to the thickness of the individual plates, the width of the individual plates, the length of the individual plates and/or the distances between the individual plates.
  • the heat exchanger according to the invention can be adapted even further to the spatial and procedural conditions, as a result of which the available installation space can be used in an optimized manner.
  • figure 1 shows a countercurrent plate heat exchanger module 1. This has a plate stack 3 assembled from individual plates 2.
  • FIG. 1 shows a countercurrent plate heat exchanger module 1. This has a plate stack 3 assembled from individual plates 2.
  • Adjacent individual plates 2 are each arranged at a distance from one another with the interposition of two spacers 4, 5 and with the formation of flow channels for a first medium and for a second medium.
  • the first medium flows through the respective flow channel in flow direction A.
  • the second medium flows through that flow channel in flow direction B, which is formed between the flow channels for the first medium.
  • the plate stack 3 carries separating elements 6 in the area of the short sides of the individual plates 2.
  • One separating element 6, 7 is arranged on the opposite short sides of the plate stack 3.
  • the separating elements 6, 7 extend over the entire height of the plate stack 3 in the stacking direction in order to keep the two media separate from one another.
  • a separating element 6, 7 divides a short side of the plate stack 3 into an inflow section 8 and an outflow section 9 for the second medium and an inflow section 10 and an outflow section 11 for the first medium.
  • two inlet openings 12 for the flow channels of the second medium are formed in the inflow section 8 delimited by the separating element 6 .
  • the flow channel for the first medium which runs between the flow channels for the second medium, is sealed gas-tight in the area 13 between the two inlet openings 9 .
  • an outlet opening 14 for the flow channel of the first medium is formed in the outflow section 11 delimited by the separating element 6 .
  • the flow channels for the second medium which run spaced apart from one another with the interposition of the flow channel for the first medium, are each closed in a gas-tight manner in the region 15 adjoining the outlet opening 14 .
  • the inflow/outflow sections 10 , 9 delimited by the separating element 7 are formed corresponding to the inflow/outflow sections 8 , 11 . This means that the first and second medium can flow through the flow channels via the two inlet openings and outlet opening thus created, but mixing of the first and second medium is ruled out.
  • the spacers 4, 5 form the side walls of the respective flow channels.
  • the spacers 4, 5 are designed here as solid profiles with a rectangular cross section. When viewed from above, the solid profiles are essentially L-shaped. The two sides of the profile are each welded to one of the adjacent individual panels 2 .
  • the individual plates 2 are completely free of embossing and are designed with a completely flat surface. As a result, the flow properties within the plate stack 3 are improved.
  • the possibility of forming the individual plates 2 in this way is only made possible by the spacers 4, 5 according to the invention, which ensure the necessary mechanical stability of the plate stack 3 even without embossing.
  • the individual plates are arranged equidistantly from one another with a spacing of 6 mm. They have a thickness of 1 mm. Furthermore, the individual plates are designed with a width of 1000 mm and a length of 2 m.
  • FIG. 2 shows a schematic plan view of a single panel 2 according to the invention.
  • This has two panel sections, namely a first panel section 16 and a second panel section 17, which are arranged one after the other in the longitudinal direction 18.
  • the second plate section 17 is connected downstream of the first plate section 16 in the direction of flow 20 of a medium that condenses as it cools. In the intended operating case, the medium therefore first passes through the first plate section 16 in the direction of flow 20 before it reaches the second plate section 17 .
  • the two plate sections 16 and 17 are each made of different materials.
  • the second plate section 17 is formed from a corrosion-resistant high-grade steel, for example an austenitic high-grade steel.
  • a stainless steel with the type designation 1.4539 can be used.
  • the first plate section 16 is formed from a low-alloy high-grade steel, for example a high-grade steel with the type designation 1.4301.
  • the low-alloy stainless steel of the first plate section 16 is much cheaper than the high-alloy stainless steel of the second plate section 17, so that the single plate 2 is much more economical to produce overall, in contrast to a single plate 2 that is made entirely of high-alloy stainless steel.
  • the second plate section 17 has a longitudinal extension in the longitudinal direction 18, which corresponds to the later condensation area in the intended use. Accordingly, high-alloy stainless steel is only used in the area of the individual plate 2 in which condensation occurs in the intended use case. The area in which no condensate formation takes place in the intended use corresponds to the first plate section, which is why this does not have to be made of high-alloy stainless steel.
  • the two plate sections 16 and 17 are connected to one another without any projections, for example by means of welding.
  • a weld seam 19 therefore extends between the two plate sections 16 and 17.
  • the two plate sections 16 and 17 must first be formed. These are then placed face to face and connected to one another by welding. Post-processing can then take place, for example by grinding, so that overall an individual plate 2 with a flat surface design is produced. Undesirable flow losses in the transition area between the first plate section 16 and the second plate section 17 are thus advantageously avoided.

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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)
EP21151998.8A 2019-09-02 2021-01-18 Module d'échangeur de chaleur à plaque à contre-courant et échangeur de chaleur à plaque à contre-courant Pending EP3957940A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202019104813.1U DE202019104813U1 (de) 2019-09-02 2019-09-02 Gegenstromplattenwärmetauscher-Modul und Gegenstromplattenwärmetauscher
DE102020120708.5A DE102020120708A1 (de) 2019-09-02 2020-08-05 Gegenstromplattenwärmetauscher-Modul und Gegenstromplattenwärmetauscher

Publications (1)

Publication Number Publication Date
EP3957940A1 true EP3957940A1 (fr) 2022-02-23

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EP21151998.8A Pending EP3957940A1 (fr) 2019-09-02 2021-01-18 Module d'échangeur de chaleur à plaque à contre-courant et échangeur de chaleur à plaque à contre-courant

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EP (1) EP3957940A1 (fr)
DE (2) DE202019104813U1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202022100245U1 (de) 2022-01-18 2023-04-20 Olivier Brasseur Plattenwärmetauscher

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DE102020120708A1 (de) 2021-03-04
DE202019104813U1 (de) 2019-09-10

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