EP3044531B1 - Echangeur de chaleur à plaques à haute pression - Google Patents

Echangeur de chaleur à plaques à haute pression Download PDF

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Publication number
EP3044531B1
EP3044531B1 EP14761863.1A EP14761863A EP3044531B1 EP 3044531 B1 EP3044531 B1 EP 3044531B1 EP 14761863 A EP14761863 A EP 14761863A EP 3044531 B1 EP3044531 B1 EP 3044531B1
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EP
European Patent Office
Prior art keywords
plate
heat exchanger
plates
opening
exchanger according
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.)
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Application number
EP14761863.1A
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German (de)
English (en)
Other versions
EP3044531A1 (fr
Inventor
Dirk Kux
Markus Lentz
Bernd Müller
Gerd Abker
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.)
Kelvion PHE GmbH
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Kelvion PHE GmbH
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Publication date
Application filed by Kelvion PHE GmbH filed Critical Kelvion PHE GmbH
Priority to EP14761863.1A priority Critical patent/EP3044531B1/fr
Publication of EP3044531A1 publication Critical patent/EP3044531A1/fr
Application granted granted Critical
Publication of EP3044531B1 publication Critical patent/EP3044531B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F28D9/0006—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 plate-like or laminated conduits being enclosed within a pressure vessel
    • 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
    • F28D9/0037—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 conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • 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
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • 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
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • 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
    • F28F9/007—Auxiliary supports for elements
    • F28F9/0075—Supports for plates or plate assemblies
    • 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
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/106—Particular pattern of flow of the heat exchange media with cross flow

Definitions

  • the invention relates to a high-pressure plate heat exchanger with an angular plate pack, which is arranged in a pressure space provided by a housing, the plate pack being formed from a plurality of individual plates connected to one another to form a plate stack, the plate pack having first and second channels through which media can flow arranged in a cross flow and tubular for the first medium between individual plates connected to form a pair of plates and for the second medium wavy between pairs of plates connected to form a stack of plates, the tubular channels being formed parallel to the longitudinal edges of the individual plates and the individual plates along their longitudinal edges to plate pairs and the plate pairs are connected to one another to form a plate stack along their edges running transversely to the longitudinal edges of the individual plates (14), the tube side for the first medium un d the shaft side serve as the pressure side for the second medium, the housing having flange covers that are connected to the tube side of the plate assembly and are at least partially spherical.
  • the high pressure plate heat exchanger has a plate pack.
  • the plate package has, for example, first and second channels through which media can flow and which are arranged in a cross-flow or, in the case of multiple paths, in a cross-counter-flow.
  • the first channel provided for the first medium is tubular between individual plates connected to form a plate pair and the second channel provided for the second medium is designed in a wave-shaped manner between plate pairs connected to a plate stack.
  • a plate pack of the type described above is from DE 43 43 399 A1 known.
  • a plate heat exchanger is disclosed here with channels through which cross-flow flows, which for one medium are formed in a wave shape between individual plates connected to form a pair of plates and for the other medium in a tubular shape between the plate pairs joined together to form a plate stack.
  • the individual plates for channel formation are equipped with several parallel rows of cams or embossed support structures aligned in the direction of flow of the one medium, which are offset from one another in the longitudinal direction from row to row.
  • Other embodiments of plate packs are also known.
  • plate heat exchangers are therefore known in which a plate pack is arranged in a pressure chamber provided by a housing, which housing is closed at the end by convexly curved flange covers, for example from the U.S. 5,755,280 .
  • connection piece significantly extends the plate heat exchanger so that the design of the plate heat exchanger cannot fall below a certain minimum size from the start.
  • free corners of the rectangular plate pack are not suitable for high differential pressures.
  • connection pieces have to be connected precisely to both the plate pack and the flange cover, which brings with it the risk that leaks or predetermined breaking points arise during the assembly of the plate heat exchanger.
  • the invention provides a high pressure plate heat exchanger proposed according to claim 1.
  • At least one of the flange covers has an opening of angular design for receiving the plate assembly. Opening means an opening, a recess and / or the like. In the flange cover. The opening enables a fluid-technical connection between the interior of the housing and the environment. The opening is formed in a convexly curved region of the flange cover.
  • the opening is square. This includes, for example, a rectangular, in particular square, opening.
  • the angular shape of the opening relates to the clear dimensions of the opening, provided that the opening is viewed from the front.
  • the angular shape corresponds to the (imaginary) base area of a segment cut out of the flange cover.
  • angular within the meaning of the invention also includes a shape that deviates from a mathematically angular shape, i.e. a shape which is rounded in the corner areas, for example for manufacturing reasons. It is crucial that the opening is not circular.
  • the edge of the opening does not lie in a plane according to the angular design of the opening, but has a three-dimensional course.
  • the edge is curved, for example, starting from the corners of the square.
  • the invention is based, inter alia, on the knowledge that in a convexly curved flange cover other opening shapes than circular openings (see U.S. 5,755,280 ) can be introduced, ie in particular those opening geometries in which the edge of the opening does not run in a single, common plane.
  • the opening in the flange cover is designed to correspond to the geometric configuration of the plate pack. In the case of a square plate pack, the opening is also square, for example.
  • the opening is at least so large that the plate package, in particular a connecting flange of the plate package, can be received therein.
  • the embodiment according to the invention has the advantage that the plate pack can basically be fastened directly to the flange cover. It the connection pieces known from the prior art, which have to be interposed between the flange cover and the plate pack in such a way that these parts are spaced from one another in the longitudinal direction of the heat exchanger or the plate pack, are dispensed with.
  • the end of a plate assembly can be arranged directly in the area of a flange cover, so that the heat exchanger can be made significantly more compact overall. This allows the installation of a high-pressure plate heat exchanger according to the invention even where the heat exchangers known from the prior art cannot be used due to their installation dimensions or design.
  • the high-pressure plate heat exchanger according to the invention can thus be used more flexibly.
  • the configuration according to the invention also has the advantage that the high-pressure plate heat exchanger is overall more stable and operationally reliable.
  • the time-consuming calibration of the connection pieces and the associated potential for errors are overcome, since the plate pack in the invention can basically simply be inserted into the opening in the flange cover. The position of the plate pack is thus firmly predetermined by the opening itself, so that no measurement, adjustment work and / or the like are required.
  • the inventive design synergistically combines the advantages of plate heat exchangers in high pressure applications on the one hand with the advantages of convexly curved flange covers in high pressure applications on the other hand, without having to use fault-prone and space-consuming connectors.
  • the plate pack is inserted into the opening with a frame interposed.
  • the frame can enclose the plate pack in particular at the end.
  • the frame can be welded to the plate pack.
  • the frame can serve to hold the individual plates of the plate pack together, in particular as a supplement.
  • the frame enables a further simplified assembly of the high pressure plate heat exchanger according to the invention.
  • the panel package is held together monolithically by the frame. When inserted into the opening of the flange cover, displacement or tilting of individual panels is prevented.
  • the frame is angular, in particular in correspondence with the opening in the flange cover on the one hand and the geometric design of the plate assembly on the other hand.
  • the external dimensions of the frame are selected in such a way that they essentially correspond to the internal dimensions of the opening in the flange cover.
  • the frame in turn has an opening in which the plate pack can be at least partially received.
  • the inside dimensions of this opening essentially correspond to the outside dimensions of the plate assembly, in particular a connection contour of the plate assembly.
  • the depth of the frame is designed such that the frame is in contact with the flange cover over the entire edge of the opening.
  • the depth of the frame extends in the longitudinal direction of the housing or the plate assembly.
  • the edge of the opening does not lie in a plane, but rather has a three-dimensional profile.
  • the depth of the frame is now selected such that the points of the edge of the opening which are furthest from one another in the longitudinal direction are in contact with the frame in each case.
  • the frame can be connected to the flange cover all the way round, so that no leaks remain.
  • At least one end of the plate pack opens directly into the opening of the flange cover. This means that the end of the plate pack extends in the longitudinal direction of the housing at least to such an extent that it intersects an imaginary plane through the opening in the flange cover. This makes the heat exchanger even more compact.
  • the plate pack can basically have any structure. According to the invention, however, the plate package has first and second channels through which media can flow, which are arranged in a cross flow and are tubular for the first medium between individual plates connected to form a plate pair and in a wave shape for the second medium between plate pairs connected to a plate stack, wherein the tubular channels formed parallel to the longitudinal edges of the individual plates and the individual plates along their longitudinal edges to form pairs of plates and the pairs of plates to form one with each other along their edges extending transversely to the longitudinal edges of the individual plates
  • Plate stacks are connected, the tube side serving for the first medium and the shaft side as a pressure side for the second medium.
  • the pressurized second medium is to be guided on the shaft side of the plate pack.
  • the tube side of the plate pack carries the first, lower pressure medium.
  • the tubular channels forming the tube side extend transversely to the longitudinal direction of the individual plates forming the plate pack. Due to the manufacturing process, the transverse extension of an individual plate is limited by the width of the embossing tool, whereas a quasi-endless, that is to say arbitrarily selectable extension in the longitudinal direction is possible.
  • the embodiment according to the invention provides a remedy here.
  • a plate embossing rotated by 90 degrees is proposed so that the tube side, ie the tubes, run in the longitudinal direction of the plate.
  • the ducts for the first medium which are tubular between individual plates connected to form a pair of plates, are formed parallel to the longitudinal edges of the individual plates.
  • the result of this is that the flow-related connection of several plate heat exchangers one behind the other can be dispensed with, since the individual plates can be designed in the desired length with the result that the pipe-side flow channels are dimensioned for the high-pressure application.
  • the configuration according to the invention is therefore particularly suitable for high-pressure applications without the risk of performance losses due to pressure drop on the pipe side.
  • the pressure holding plates or the package side walls can remain as they are designed only for the lower pressure on the pipe side.
  • plate heat exchangers are comparatively unstable in terms of pressure.
  • the individual plates are only connected at the edge, if the application of pressure is too high, the individual plates may bulge and / or the connection points existing between the individual plates may tear.
  • the construction according to the invention proves to be advantageous in this regard, as that pressure holding plates or package side walls can only be used with reference to the comparatively low pressure on the pipe side, i.e. of the first medium are to be designed, which means that they can be used unchanged in their design compared to the prior art, and this with simultaneous suitability for high pressure application in the sense of the invention.
  • the housing providing the pressure space is preferably spherical and / or circular with reference to at least one cross-section, deviating from the rectangular shape of the plate assembly, to accommodate the pressures prevailing during operation.
  • the invention also provides that the housing has flange covers on the tube side of the plate assembly which are at least partially spherical.
  • a housing providing a pressure chamber which separates the shaft side to the outside, that is to say from the surrounding atmosphere by a cylindrical jacket and from the tube side by a spherical jacket, which as a result prevents the housing-side stress peaks in the transition area from the shaft side to the tube side .
  • the configuration according to the invention makes it possible for the first time to use plate heat exchangers in the high pressure range, namely at working pressures with regard to the second medium of over 50 bar, preferably over 60 bar, even more preferably over 100 bar, up to 120 bar.
  • Previously known constructions do not allow such printing applications. Rather, the working range of previously known designs ends at a pressure of approx. 20 bar, possibly approx. 30 bar. Pressures of more than 30 bar, let alone 60 bar and more, are not possible with the previously known embodiments.
  • the pressure range of more than 120 bar possible with the embodiment according to the invention is surprising, without being restricted by differential pressures, since the thickness of the exchanger plates used on the one hand and the housing wall thickness on the other hand are comparatively thin. In this respect, the wide range of applications for pressure of the high-pressure plate heat exchanger according to the invention results as a synergy effect from the individual features explained above.
  • connecting wedges are arranged in the corner areas of the stack of panels between two adjacent pairs of panels. These connecting wedges are preferably connected to one another in a form-fitting manner by welding to the adjacent pairs of plates.
  • the connection wedges serve two purposes. On the one hand, the entire plate pack construction is stabilized. On the other hand, the connection wedges serve to separate the flow-technical separation of the shaft and tube side.
  • the individual plates provide embossed sections.
  • the individual plates are provided with several parallel rows of embossed sections running in the longitudinal direction, and embossed sections of adjacent rows are aligned offset from one another in the longitudinal direction.
  • embossed sections of adjacent rows are aligned offset from one another in the longitudinal direction.
  • the invention is in contrast to State of the art provided to design a more closely pressed embossed image.
  • This embossing pattern which is narrower than in the prior art, leads to an improved support of the individual plates among one another and thus to a reinforcement of the entire plate package, which proves to be particularly favorable in the case of high pressure application.
  • the plate package has spaces extending transversely to the longitudinal direction of the plate package, in particular of the individual plates.
  • Empty space means that the plate package or the individual plate is not provided with embossed sections and / or the like at this point. Rather, it is a continuously essentially flat area.
  • the void preferably extends over at least 80%, particularly preferably at least 90% of the width of the plate package, in particular an individual plate.
  • the gaps serve to enable individual panels of the panel package to be connected to one another, specifically at a point remote from the edges spaced apart in the longitudinal direction of an individual panel.
  • the voids can, for example, extend in the middle of a single plate. The spaces thus subdivide individual panels into sub-areas.
  • both individual plates with voids can be connected to one another in the area of the voids, for example welded.
  • This configuration has the advantage that, compared to a connection exclusively in the edge areas, the stability of the entire plate package can be significantly improved.
  • the voids can also serve to form flow barriers. For example, a tubular channel extending through the plate assembly can be interrupted by empty spaces. As a result, it can be achieved, for example, that one and the same continuous single plate can be flowed through alternately, in particular alternately in a cross-flow, thus a multiple flow is achieved, which increases the efficiency of the plate heat exchanger.
  • FIG Figure 1 shows a high pressure plate heat exchanger 1 according to the invention in a side view.
  • This has a housing 2, which - like the sectional view according to Figure 2 can be seen - provides a pressure chamber 3.
  • a plate pack 4 is arranged within the pressure chamber 3, which for a better overview is shown in FIG Figure 2 is only shown schematically.
  • the plate pack 4 is formed from individual plates 14. Two individual plates 14 together form a plate pair 15 and several plate pairs 15 coupled to one another represent a plate stack 16.
  • the plate pack 4 shown here consists of a plate stack 16 which has four plate pairs 15 which are arranged between two individual plates 14 serving as cover plates.
  • the individual plates 14 are each designed identically and are connected in mirror image to one another to form a plate pair 15. This connection is preferably made in a materially bonded manner by welding, specifically along the longitudinal edges 17.
  • tubular plates 14 are formed between the individual plates 14, which each form a pair of plates 15 formed first channels K1, specifically for a medium M1 participating in the heat exchange in the intended use.
  • the second medium M2 is the high pressure medium which is under pressure.
  • the pair of plates 4 can also have a different structure.
  • each individual plate 14 is provided with several parallel rows of embossed sections 21 running in the direction of the longitudinal edges 17. These embossed sections 21 of adjacent rows are offset from one another in the longitudinal direction, as a result of which flat supports between embossed sections 21 following one another in a row result between individual plates 14 resting on one another.
  • Connection wedges 20 are arranged between the individual plates 14 of adjacent plate pairs 15 in the corner regions 19 of a plate assembly 4. These connecting wedges 20 separate, on the one hand, the shaft side from the pipe side in the inlet and outlet area of the media M1 and M2 and, on the other hand, serve to stabilize the design of the plate assembly 4 as a whole.
  • the housing 2 is formed from an annular section 7 and two flange covers 8 and 9.
  • the flange covers 8 and 9 each provide an opening 10 for the pipe side, which are designed to correspond to the geometric configuration of the plate assembly 4 and are used to receive the plate assembly 4.
  • the flange covers are at least partially spherical, preferably in the manner of a dished bottom, with which the housing 2 adjoins the plate stack 4 on the shaft side in a spherical design.
  • Fig. 7 shows an embodiment of a flange cover 8 according to the invention in detail.
  • the plate pack 4 is square.
  • the opening 10 in the flange cover 8 is also square, with reference to the clear dimensions.
  • the opening 10 is delimited by the edge 23 of the flange cover 8.
  • the edge 23 has a three-dimensional course, the side edges extending from the corners the opening 10 starting to arch towards the tip of the flange cover 8. The corners themselves are slightly rounded.
  • a frame 22 is inserted into the opening 10. This is designed in accordance with the geometric configuration of the flange cover 8 or the plate assembly 4.
  • the frame 22 receives the plate pack 4 or a connecting contour of the plate pack 4.
  • the plate pack 4 is held together in an improved manner.
  • the plate pack 4 and the frame 22 can be connected to one another, in particular welded.
  • the plate package 4 can then be handled together with the frame 22 as a unit. In this way, the plate pack 4 can be inserted into the opening 10 in the flange cover 8 in a particularly simple manner.
  • connection between the frame 22 and the plate pack 4 can be made in a simple manner using the connecting wedges 20 described above.
  • the connecting wedges 20 By means of the connecting wedges 20, the individual plates 14 or the plate pairs 15 are connected to one another in a pressure-resistant and solid manner.
  • the frame 22 can be attached, in particular welded, to the connecting wedges 20.
  • the frame 22 can be designed in one piece, for example as a milled part, or in multiple parts, the individual parts preferably being welded to one another in the case of multiple parts.
  • the respective flange covers 8 and 9 are equipped with a flange 11, which in turn carries a respective flange plate 12 connected thereto by means of screws 13.
  • the flange plates 12 are equipped with connecting pieces 5 for the first medium, that is to say the low-pressure medium.
  • the side with tubular channels for medium M1 also with spherical bottoms, can be welded directly to the flange covers 8 and 9.
  • the plate pack 4 is in fluidic communication with the second medium, that is to say the high-pressure medium, via connecting pieces 6.
  • the pressurized second medium M2 is used in accordance with the in Figure 2
  • the arrows drawn in are introduced into the plate pack 4 on the shaft side and, after flowing through the plate pack 4, exits the high-pressure plate heat exchanger 1 again via the connection piece 6 provided for this purpose.
  • the fluid introduced flows into the pressure chamber 3 provided by the housing 2, so that on the plate package 4 acts an external pressure identical to the internal pressure, whereby the plate package 4 or the individual plates 14 of the plate package 4 are depressurized overall, or are only loaded with the lower pressure of the first medium M1 in the case of one-sided load with the first medium M1 of the low-pressure side .
  • the medium flows at a lower pressure, that is, the first medium, in accordance with the arrows Figure 2 via the tube side of the plate pack 4.
  • Both the tube and the shaft side can be operated in multiple ways. In this case, deflections are provided on the tube side between the plate pack 4 and the housing, or deflections are provided on the shaft side in the plate pack 4 and between the plate pack 4 and the housing.
  • the multi-way circuit enables cross-countercurrent operation.
  • the pipe-side channels K1 are determined in their geometric dimensions, inter alia, by the distance between the embossed sections 21 formed offset from one another in adjacent rows. This distance A is in Figure 6 drawn in as an example.
  • Fig. 8 shows an embodiment of a single plate 24 according to the invention with a vacancy 25.
  • the vacancy 25 extends transversely to the longitudinal direction of the individual plate 24.
  • the vacancy 25 extends essentially over the entire width of the individual plate 24. If two individual plates 24 are arranged on top of one another, their vacancies are located 25 in contact with each other. The two individual plates 24 can then be connected to one another, in particular welded, in the region of the voids 25.
  • This has two advantages. On the one hand, the stability of the plate pair formed in this way and thus also the stability of a plate pack 4 formed with such individual plates is significantly increased. This is particularly advantageous in the case of high-pressure applications and in particular in the case of comparatively long, continuous individual plates 24.
  • the plates of a plate heat exchanger can, under certain circumstances, be pushed apart as a result of the fluid pressure, which impairs the function of the heat exchanger since the intended flow paths are no longer maintained.
  • the vacancy 25 has a further advantage. In this way, one and the same individual plate 24 can be subdivided in the longitudinal direction of the same into areas which are fluidically separated from one another. This allows one and the same Single plate 24 can be acted upon with fluid in alternating cross-countercurrent.
  • the corresponding flow paths of a first medium M3 and a second medium M4 are shown in Fig. 8 shown.

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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)

Claims (11)

  1. Echangeur thermique à plaques et à haute pression comprenant un paquet de plaques (4) rectangulaire, qui est disposé dans une chambre de pression (3) fournie par un boîtier (2), le paquet de plaques (4) étant formé par une pluralité de plaques individuelles (14) reliées les unes aux autres pour former une pile de plaques (16), le paquet de plaques (4) comprenant des premiers et deuxièmes canaux (K1, K2) pouvant être traversés par des médias (M1, M2), les canaux (K1, K2) étant disposés en courant croisé et étant formés pour le premier médium (M1) par des tubes entre des plaques individuelles (14), qui sont reliées l'une à l'autre pour former une paire de plaques (15), et pour le deuxième médium sous forme d'ondes entre des paires de plaques (15), qui sont reliées l'une à l'autre pour former une pile de plaques (16), les canaux tubulaires (K1) s'étendant dans la direction longitudinale parallèlement aux bords longitudinaux (17) des plaques individuelles (14) et les plaques individuelles (14) étant reliées les unes aux autres le long de leurs bords longitudinaux (17) pour former des paires de plaques (15) et les paires de plaques (15) étant reliées les unes aux autres le long de leurs bords (18), qui s'étendent transversalement aux bords longitudinaux (17) des plaques individuelles (14) pour former une pile de plaques, le côté de tubes servant de côté de pression pour le premier médium (M1) et le côté d'ondes servant de côté de pression pour le deuxième médium (M2), et le boîtier (2) comprenant des couvercles de bride (8, 9), qui se raccordent au côté de tubes du paquet de plaques (4) et qui sont au moins partiellement en forme sphérique, caractérisé en ce qu'au moins un des couvercles de bride (8, 9) comprend une ouverture (10) anguleuse pour recevoir le paquet de plaques (4), un bord du couvercle de bride (8, 9), qui forme l'ouverture (10), s'étendant de manière courbée à partir des coins de l'ouverture (10), le paquet de plaques (4) étant directement fixé au couvercle de bride (8, 9), au moins une extrémité du paquet de plaques (4) débouchant directement dans l'ouverture du couvercle de bride (8, 9).
  2. Echangeur thermique selon la revendication 1, caractérisé en ce que le paquet de plaques (4) est inséré dans l'ouverture avec interposition d'un cadre (22).
  3. Echangeur thermique selon la revendication 2, caractérisé en ce que la profondeur du cadre est configurée de sorte que le cadre est en contact avec le couvercle de bride (8, 9) sur le bord entier de l'ouverture.
  4. Echangeur thermique selon l'une des revendications précédentes, caractérisé en ce que les couvercles de bride (8, 9) sont chacun configurés comme des fonds torosphériques.
  5. Echangeur thermique selon l'une des revendications précédentes, caractérisé en ce que le paquet de plaques (4) disposé à l'intérieur du boîtier (2) est entouré d'une pression de support.
  6. Echangeur thermique selon l'une des revendications précédentes, caractérisé en ce que des cales de raccordement (20) sont disposées entre deux paires de plaques (15) adjacentes dans les zones de coin (19) de la pile de plaques (16).
  7. Echangeur thermique selon la revendication 6, caractérisé en ce que les plaques individuelles (14) comprennent une épaisseur de plaque comprise entre 1,2 mm et 2,0 mm, de préférence entre 1,3 mm et 1,8 mm, de préférence plus particulière de 1,5 mm.
  8. Echangeur thermique selon l'une des revendications 6 ou 7, caractérisé en ce que les plaques individuelles (14) sont munies de plusieurs rangs parallèles de sections d'embossage (21), qui s'étendent dans la direction longitudinale, les sections d'embossage (21) des rangs adjacents étant décalés l'une par rapport à l'autre dans la direction longitudinale.
  9. Echangeur thermique selon l'une des revendications 6 à 8, caractérisé en ce que sur le côté des ondes le paquet de plaques (4) est ouvert vers la chambre de pression (3) fournie par le boîtier (2).
  10. Echangeur thermique selon l'une des revendications précédentes, caractérisé en ce que le paquet de plaques (4) comprend des espaces vides (25), qui s'étendent transversalement par rapport à la direction longitudinale du paquet de plaques (4), notamment des plaques individuelles (14).
  11. Echangeur thermique selon la revendication 10, caractérisé en ce qu'un espace vide s'étend sur au moins 80 % de la largeur du paquet de plaques (4), notamment d'une plaque individuelle (14).
EP14761863.1A 2013-09-10 2014-09-10 Echangeur de chaleur à plaques à haute pression Active EP3044531B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14761863.1A EP3044531B1 (fr) 2013-09-10 2014-09-10 Echangeur de chaleur à plaques à haute pression

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP13183684.3A EP2846121B1 (fr) 2013-09-10 2013-09-10 Echangeur de chaleur à plaques à haute pression
EP14761863.1A EP3044531B1 (fr) 2013-09-10 2014-09-10 Echangeur de chaleur à plaques à haute pression
PCT/EP2014/069267 WO2015036423A1 (fr) 2013-09-10 2014-09-10 Échangeur de chaleur à plaques à haute pression

Publications (2)

Publication Number Publication Date
EP3044531A1 EP3044531A1 (fr) 2016-07-20
EP3044531B1 true EP3044531B1 (fr) 2020-09-09

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Application Number Title Priority Date Filing Date
EP13183684.3A Not-in-force EP2846121B1 (fr) 2013-09-10 2013-09-10 Echangeur de chaleur à plaques à haute pression
EP14761863.1A Active EP3044531B1 (fr) 2013-09-10 2014-09-10 Echangeur de chaleur à plaques à haute pression

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP13183684.3A Not-in-force EP2846121B1 (fr) 2013-09-10 2013-09-10 Echangeur de chaleur à plaques à haute pression

Country Status (5)

Country Link
US (1) US10228191B2 (fr)
EP (2) EP2846121B1 (fr)
KR (1) KR20160055158A (fr)
RU (1) RU2654293C2 (fr)
WO (1) WO2015036423A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3179190A1 (fr) * 2015-12-11 2017-06-14 Alfa Laval Corporate AB Échangeur thermique à plaque
JP2020523546A (ja) * 2017-06-11 2020-08-06 リヴニ，ツヴィ 分割されたマニホールド管を有するプレートおよびシェル熱交換システム
EP3561433B1 (fr) * 2018-04-27 2021-12-15 Valeo Autosystemy SP. Z.O.O. Ensemble échangeur thermique
EP3561427B1 (fr) * 2018-04-27 2021-12-15 Valeo Autosystemy SP. Z.O.O. Ensemble échangeur thermique

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US2620169A (en) * 1948-06-23 1952-12-02 English Electric Co Ltd Plate type heat exchanger
GB1233584A (fr) * 1967-08-22 1971-05-26
DE1601215B2 (de) * 1967-11-03 1971-11-18 Linde Ag, 6200 Wiesbaden Plattenwaermetauscher insbesondere als spaltgaskuehler
DE2453961A1 (de) * 1974-11-14 1976-05-20 Daimler Benz Ag Rekuperativer waermeaustauscher
GB2120768B (en) * 1982-05-24 1985-09-11 Dvt Buro Fur Anwendung Deutsch Apparatus for the desalination of sea water
DE3618225A1 (de) * 1986-05-30 1987-12-03 Funke Waerme Apparate Kg Waermeaustauscher
FI79409C (fi) * 1987-07-13 1989-12-11 Pentti Raunio Foerfarande foer konstruering av en vaermevaexlare jaemte enligt foerfarandet konstruerad vaermevaexlare.
DE3918189A1 (de) * 1989-06-03 1990-12-06 Wendelin Dipl Ing Einmueller Waermeaustauscher
DE4343399C2 (de) 1993-12-18 1995-12-14 Balcke Duerr Ag Plattenwärmetauscher
FR2733823B1 (fr) * 1995-05-04 1997-08-01 Packinox Sa Echangeur thermique a plaques
DE19620543C2 (de) * 1996-04-19 2003-11-27 Apv Thermotech Gmbh Hybrid-Plattenwärmetauscher
FR2779812B1 (fr) * 1998-06-12 2000-10-06 Soc Et Et De Const Aero Navale Echangeur de chaleur du type a carter creux renfermant notamment un grand nombre de premieres voies d'ecoulement d'un premier fluide et parcouru par un second fluide en contact d'echange thermique avec ces voies
DE19944426C2 (de) * 1999-09-16 2003-01-09 Balcke Duerr Energietech Gmbh Plattenwärmetauscher und Verdampfer
RU2206851C1 (ru) * 2001-12-27 2003-06-20 Худяков Алексей Иванович Кожухопластинчатый теплообменник (варианты)
SE529808C2 (sv) * 2006-04-06 2007-11-27 Alfa Laval Corp Ab Plattvärmeväxlare
WO2010142306A1 (fr) * 2009-06-10 2010-12-16 Gea Ecoflex Gmbh Procédé pour faire fonctionner un échangeur de chaleur à plaques et système de condenseur avec échangeur de chaleur à plaques
FI20095707A0 (fi) * 2009-06-24 2009-06-24 Vahterus Oy Levylämmönsiirrin ja menetelmä levylämmönsiirtimen levypakan tukemiseksi
FI20106394A0 (fi) * 2010-12-31 2010-12-31 Vahterus Oy Levylämmönsiirrin ja menetelmä sen valmistamiseksi
DE202011005693U1 (de) * 2011-04-28 2011-09-26 Behr Gmbh & Co. Kg Schichtwärmeübertager

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Also Published As

Publication number Publication date
EP2846121A1 (fr) 2015-03-11
EP2846121B1 (fr) 2017-12-27
RU2016110584A (ru) 2017-09-28
EP3044531A1 (fr) 2016-07-20
US10228191B2 (en) 2019-03-12
RU2654293C2 (ru) 2018-05-17
WO2015036423A1 (fr) 2015-03-19
KR20160055158A (ko) 2016-05-17
RU2016110584A3 (fr) 2018-03-07
US20160223266A1 (en) 2016-08-04

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