EP0487931B1 - Echangeur de chaleur à plaques - Google Patents

Echangeur de chaleur à plaques Download PDF

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Publication number
EP0487931B1
EP0487931B1 EP91118684A EP91118684A EP0487931B1 EP 0487931 B1 EP0487931 B1 EP 0487931B1 EP 91118684 A EP91118684 A EP 91118684A EP 91118684 A EP91118684 A EP 91118684A EP 0487931 B1 EP0487931 B1 EP 0487931B1
Authority
EP
European Patent Office
Prior art keywords
plates
heat exchanger
seal
plate heat
medium
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.)
Revoked
Application number
EP91118684A
Other languages
German (de)
English (en)
Other versions
EP0487931A1 (fr
Inventor
Ulrich Dipl.-Ing. Stirnkorb (Fh)
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.)
Schmidt Bretten GmbH
Original Assignee
Schmidt Bretten GmbH
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6419148&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0487931(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Schmidt Bretten GmbH filed Critical Schmidt Bretten GmbH
Publication of EP0487931A1 publication Critical patent/EP0487931A1/fr
Application granted granted Critical
Publication of EP0487931B1 publication Critical patent/EP0487931B1/fr
Anticipated expiration legal-status Critical
Revoked 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
    • 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
    • F28F3/10—Arrangements for sealing the margins

Definitions

  • the invention relates to a plate heat exchanger with a plurality of substantially rectangular plates that are aligned with one another and provided with embossing with a profiling, which are alternately rotated by 180 ° with respect to one another, with the profiling of adjacent plates facing one another being at least partially releasably tensioned to form a stack, the Form plates between themselves alternately for a first and a substantially parallel second medium through a seal arranged between them along their circumference flow spaces, which are aligned with each other, formed by openings arranged in the corner regions of the plates with the respective inflow and outflow openings Medium can be loaded, the seal between the mutually detachable plates being designed as a releasable peripheral seal, which is formed at least over part of its longitudinal extent as an at least two-row multiple seal det.
  • the relatively thin-walled and often also mutually identical plates are held together in a frame and stretched into a stack between thicker end plates, a so-called frame plate and a so-called cover plate, the end plate and / or cover plate containing the connections for the media which along the Plate stacks are guided over channels, which are formed by the above-mentioned perforations of the plates in connection with a corresponding design of the seals.
  • the seals can at least partially consist of profiles fastened between adjacent plates by welding, soldering, gluing or the like, while a releasable peripheral seal made of at least partially elastic material is used in the mutually detachable plates.
  • the flow spaces formed between the plates are pressurized by the first and second medium.
  • the possible amount of such pressurization is limited by the resilience of the peripheral seals, which are at least partially made of elastic material. It is true that the stack of plates can be strongly pressed together by a corresponding high prestress between the frame and cover plate. Here, too, however, there is a limit if the material of the peripheral seals is pressed too much and thus squeezed.
  • a plate heat exchanger of the type mentioned is known from GB-A-2 141 814.
  • the seal is designed as a multiple seal, this consists in cross section of a hard, load-bearing part and a soft, sealing part, which are integrally connected to one another to form a sealing cord, that is to say represent a uniform circumferential seal.
  • a sealing cord that is to say represent a uniform circumferential seal.
  • the object of the invention is therefore to modify or supplement a plate heat exchanger of the type mentioned in a simple manner in such a way that it opposes one the previous much higher pressure resistance by the media allowed with a comparatively moderate increase in the cost price.
  • This object is achieved on the basis of a plate heat exchanger of the type mentioned at the outset in that the multiple seal is formed from sealing profiles arranged at a spacing from one another while leaving a gap free of sealing material, and in that the gap forms a sealed channel.
  • This measure according to the invention has the effect of creating a narrow channel sealed on both sides between adjacent profiles of the peripheral seals.
  • an intermediate pressure can build up in the channel, which on the one hand can be carried without leakage by the seal facing away from the media, while providing a support and counter-pressure effect for the seal facing the media.
  • the media pressure is gradually reduced to ambient pressure, usually atmospheric pressure, with each of the sealing profiles parallel to one another only having to bear part of the difference between media pressure and ambient pressure.
  • the multiple seal can in each case between the flow space and the openings of the assigned plate can be provided which, without connection to the flow space, only serve to transfer media to the flow spaces adjacent to the flow space.
  • This usually existing sealing zone is one of the critical, if not the critical, sealing zone between two adjacent plates, since the plate on the side facing away from the seal generally has no support for the sealing zone with respect to the adjacent plate, because there the opening must be based on the opening mentioned
  • Adjacent flow space are loaded with the assigned medium or disposed of by this medium. Due to this lack of support, the seal there cannot be pre-stressed as much as the other parts of the circumferential seal, so that there is a leakage at high media pressures.
  • the entire peripheral seal is designed as a multiple seal. This now gives the possibility of a considerable increase in the applicable media pressures.
  • the profiles of the peripheral seals are inserted in sealing grooves embossed from the plates, the depth of which corresponds to part of the height of the respective sealing profile.
  • the plate profile protrudes with an elevation, which does not have to be continuous over the circumference, into the channel formed in each case between adjacent sealing profiles in order to support the sealing profiles with respect to the channel.
  • adjacent profiles of the multiple seal are integrally connected to one another at individual, mutually spaced locations by bridges made of the material of the peripheral seal and extending transversely to their longitudinal extension. This results in a significant relief, particularly with regard to the handling of the multiple seal when it is installed in the sealing grooves.
  • the height of the bridges is reduced in comparison with that of the sealing profiles in such a way that a channel extending in the longitudinal direction thereof is formed between the sealing profiles of the multiple seal. This ensures pressure equalization over the entire length of the channel, so that different pressures cannot build up on both sides of a bridge.
  • the height of the plate profiling existing between two adjacent sealing grooves is reduced at the points having the bridge. This prevents the bridges from being too thin-walled.
  • the plates have bores in the region of the channels formed between adjacent profiles of the peripheral seal, through which the sealing channels can be charged with a third medium which is under pressure, the amount of pressure being between that of the first and second Medium on the one hand and the environment of the plate heat exchanger on the other.
  • This design enables the channels formed between the circumferential seals to be charged with a barrier medium, for example a liquid or a gas, which prevents quantities of the first or second medium from getting into the channels at all.
  • a barrier medium for example a liquid or a gas
  • this leakage material can be easily washed away immediately by the third medium.
  • the height of the excess pressure of the third medium is approximately midway between that of the first and second medium on the one hand and that of the surroundings of the plate heat exchanger on the other.
  • openings 4, 3, 4, 5 can be seen in the four corners, via which the two media involved in the heat exchange are guided in a manner known per se in a stack of a plate heat exchanger.
  • the plate 1 has recesses 6, 7 which are open to the outside. Via these recesses, the plate 1 can be placed on guide rods of a frame which, in a known manner, has a frame plate and a cover plate, between which the stack of plates 1 can be clamped.
  • the plate 1 has a profile 8, over which the adjacent plates lie against one another in such a way that flow spaces are formed between adjacent plates, through which the first and second medium can move forward.
  • the flow spaces are delimited from the outside by a circumferential seal 10, which in the case of FIG. 1 is designed and guided such that the medium flowing over the visible side of the plate 1 can move between the openings 2 and 3.
  • the openings 4, 5 are sealed off from this medium by a circulation 11, 12 and by an upstream connection 13, 14 of the seal 10.
  • the peripheral seal 10 is now, as shown in Fig. 1, designed as a double seal by a media-facing sealing profile 15 and a media-facing sealing profile 16 are guided parallel to each other such that a channel 17 is formed between these two sealing profiles.
  • this design has the effect that the pressure existing in the interior of the flow spaces is gradually reduced towards the surroundings of the plate heat exchanger, so that the flow spaces are subjected to very high media pressures can, without a leakage can occur to the outside as a result.
  • the inner sealing profile 15 and the outer sealing profile 16 are connected to one another several times by bridges 18 along the course of the circumferential seal in order in this way to facilitate the assembly of the seal on the plate 1.
  • FIG. 2 shows two plates 19 of the type described with reference to FIG. 1 in an exploded view as they finally come to lie on one another in the plate stack.
  • Fig. 2 shows that the two identical plates are rotated against each other by 180 °. This results in the fact that, starting from the flow channels 20, 21, 22, 23 formed by the openings in the plates, the flow space formed between the two plates shown can be fed via the flow channels 20, 21, while that in front of the front plate 19 and the rear plate Plate 19 located flow space is fed via the flow channels 22, 23.
  • the plates 19 shown in FIG. 2 show bores 24 of the plate material arranged between the inner sealing profile 15 and the outer sealing profile 16, via which adjacent channels 17 are connected to one another in the stacking direction of the plates.
  • this gives the possibility of loading the channels 17 with a third medium in order to build up the differential pressure between the two sealing profiles via this third medium, with a flushing process being carried out at the same time a possible leakage can take place via the inner sealing profile 15.
  • FIG. 3 shows the two plates 19 according to FIG. 2 in a rear view, from which the embossing of grooves 25, 26 into which the sealing profiles 15, 16 are inserted can be seen.
  • Fig. 4 shows an enlarged view of a section perpendicular to the plane of the heat exchanger plates 1, 19 in the region of the peripheral seal. It can be seen here how the seals are connected to one another at individual points by bridges 18.
  • the bridges have a reduced height compared to the sealing profiles 15, 16 in order to allow channels 17 to run continuously over the entire sealing circumference. So that the bridges 18 do not have to be made too thin, the height of the plate profiling 27 located between the sealing profiles 15, 16 is also reduced in the region of the bridges 18.
  • FIG. 5 shows the overall perspective view of a plate heat exchanger, mainly in an exploded view.
  • This shows the plates 19, which are stacked rotated by 180 ° relative to one another, a frame plate 30 and a cover plate 31, as well as the stand 32, from which rods 33, 34 go to the frame plate 30, which the plates 19 pass through their recesses 6 guide and adjust each other.
  • the rods 33, 34 are fixed by screws 45, 46 in receiving bores 47, 48 of the frame and cover plate.
  • the frame and cover plates form connection openings 35 to 38, the openings 2 to 5 of the plates correspond and thereby connect the channels 20 to 23 (Fig. 2 and 3) to the outside.
  • tie rods are used in recesses 51, 52 of the frame and cover plate for the mutual bracing of these plates and thus the package of heat exchanger plates arranged therebetween.

Landscapes

  • 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)
  • Separation By Low-Temperature Treatments (AREA)
  • Fuel Cell (AREA)

Claims (10)

  1. Echangeur de chaleur à plaques comprenant une pluralité de plaques (1, 19) sensiblement rectangulaires, alignées les unes sur les autres et munies d'un relief (8) par emboutissage, qui sont serrées en une pile, de façon au moins partiellement démontable, retournées de 180° les unes par rapport aux autres en alternance, dans lesquelles les reliefs (8) des plaques adjacentes (1, 19) dirigés l'un vers l'autre sont en contact, les plaques (1, 19) formant entre elles, alternativement pour un premier milieu et pour un deuxième milieu qui circule à peu près parallèlement au premier, des chambres d'écoulement entourées d'un joint d'étanchéité (10) interposé entre les plaques le long de leur périphérie, et qui peuvent être chargées de leurs milieux respectifs à travers des ouvertures d'arrivée et de départ alignées les unes sur les autres formées par des perçages (2, 3, 4, 5) disposés dans les régions d'angles des plaques (1, 19), l'étanchéité entre les plaques séparables les unes des autres étant établie par un joint périphérique démontable (10) qui est formé d'un joint multiple à au moins deux files sur au moins une partie de son extension longitudinale,
    caractérisé
    en ce que le joint multiple est composé de profilés de joint (15, 16) disposés à un certain écartement l'un de l'autre, en ménageant un espace intermédiaire exempt de matière de joint, et en ce que l'espace intermédiaire forme un conduit (17) hermétiquement fermé.
  2. Echangeur de chaleur à plaques selon la revendication 1,
    caractérisé
    en ce que le joint multiple (13, 14) est prévu entre la chambre d'écoulement et les perçages (4, 5) de la plaque (1) correspondante, qui servent exclusivement au transfert du milieu vers les chambres d'écoulement adjacentes à la chambre d'écoulement considérée, sans communication avec celle-ci.
  3. Echangeur de chaleur à plaques selon la revendication 1,
    caractérisé
    en ce que le joint périphérique (10) est constitué en totalité par un joint multiple.
  4. Echangeur de chaleur à plaques selon une des revendications 1 à 3,
    caractérisé
    en ce que les profilés du joint périphérique (15, 16) sont encastrés dans des rainures de joints (25, 26) embouties dans les plaques (1, 19) et dont la profondeur correspond à une partie de la hauteur du profilé de joint correspondant.
  5. Echangeur de chaleur à plaques selon une des revendications précédentes
    caractérisé
    en ce que les profilés adjacents (15, 16) du joint multiple (10) soient réunis entre eux en une seule pièce, en des points distincts espacés les uns des autres, par des ponts (18) s'étendant transversalement à leur extension longitudinale, formés de la matière du joint périphérique.
  6. Echangeur de chaleur à plaques selon la revendication 5,
    caractérisé
    en ce que la hauteur des ponts (18) est réduite, comparativement à celle des profilés de joint (15, 16), de manière qu'il se forme entre les profilés d'un joint multiple (10) un conduit (17) qui est continu sur toute son extension longitudinale.
  7. Echangeur de chaleur à plaques selon la revendication 5 ou 6,
    caractérisé
    en ce que le relief (27) des plaques qui est compris entre deux rainures de joint adjacents (25, 26) est réduit en hauteur aux endroits qui présentent les ponts.
  8. Echangeur de chaleur à plaques selon une des revendications précédentes,
    caractérisé
    en ce que, dans la région des conduits (17) formés entre les profilés adjacents du joint périphérique (15, 16), les plaques (19) présentent des perçages (24) à travers lesquels les conduits de joint peuvent être chargés d'un troisième milieu qui est sous surpression, le niveau de la surpression se trouvant entre celui des premier et deuxième milieux, d'une part, et celui de l'environnement de l'échangeur de chaleur à plaques, d'autre part.
  9. Echangeur de chaleur à plaques selon la revendication 8,
    caractérisé
    en ce que le niveau de la surpression du troisième milieu est à peu près au milieu entre celui des premier et deuxième milieux, d'une part, et celle de l'environnement de l'échangeur de chaleur à plaques, d'autre part.
  10. Echangeur de chaleur à plaques selon la revendication 8 ou 9, dans lequel les plaques sont serrées en une pile, de façon démontable, disposées dans un châssis et guidées dans un alignement entre une plaque de base et une plaque de couvercle du châssis,
    caractérisé
    en ce que la plaque d'armature (30) et/ou la plaque de couvercle (31) présentent des communications de raccordement correspondant aux conduits (17) servant à acheminer et éventuellement évacuer le troisième milieu.
EP91118684A 1990-11-29 1991-11-02 Echangeur de chaleur à plaques Revoked EP0487931B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4037969A DE4037969A1 (de) 1990-11-29 1990-11-29 Plattenwaermeaustauscher
DE4037969 1990-11-29

Publications (2)

Publication Number Publication Date
EP0487931A1 EP0487931A1 (fr) 1992-06-03
EP0487931B1 true EP0487931B1 (fr) 1995-03-01

Family

ID=6419148

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91118684A Revoked EP0487931B1 (fr) 1990-11-29 1991-11-02 Echangeur de chaleur à plaques

Country Status (6)

Country Link
US (1) US5193612A (fr)
EP (1) EP0487931B1 (fr)
JP (1) JPH04273994A (fr)
AT (1) ATE119270T1 (fr)
DE (2) DE4037969A1 (fr)
DK (1) DK0487931T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10029999A1 (de) * 2000-06-17 2002-01-03 Otto Thermotech Gmbh Plattenwärmeübertrager der gedichteten Bauart
CN103673696A (zh) * 2013-12-26 2014-03-26 上海艾克森集团有限公司 一种改进的半焊板式热交换器

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DE10035939A1 (de) * 2000-07-21 2002-02-07 Bosch Gmbh Robert Vorrichtung zur Wärmeübertragung
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FR2910607B1 (fr) 2006-12-21 2009-02-06 Alfa Laval Vicard Soc Par Acti Echangeur thermique a plaques
WO2011013950A2 (fr) * 2009-07-27 2011-02-03 한국델파이주식회사 Echangeur de chaleur à plaques
US9596785B2 (en) * 2010-03-22 2017-03-14 Pratt & Whitney Canada Corp. Heat exchanger
SE535209C2 (sv) * 2010-06-15 2012-05-22 Alfa Laval Corp Ab Korrosionsbeständig plattvärmeväxlare med tantalhaltig beläggning
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EP2757339B1 (fr) * 2011-09-14 2018-05-02 Hisaka Works, Ltd. Échangeur de chaleur à plaques
DE102014014070A1 (de) * 2014-09-29 2016-03-31 Forschungszentrum Jülich GmbH Vorrichtung zum geregelten Wärmeübergang auf und von einem Bauteil
CN106017159B (zh) * 2015-04-29 2018-08-14 青岛中正周和科技发展有限公司 一种铜合金板式换热器
JP6911469B2 (ja) * 2017-03-31 2021-07-28 株式会社Ihi 熱処理装置
US10876794B2 (en) * 2017-06-12 2020-12-29 Ingersoll-Rand Industrial U.S., Inc. Gasketed plate and shell heat exchanger
CN109141095A (zh) * 2018-09-30 2019-01-04 浙江华立智能装备股份有限公司 一种密封性好的板式换热器
DK180145B1 (en) * 2018-11-27 2020-06-25 Danfoss As Intellectual Property Plate heat exchanger
CN110779360A (zh) * 2019-10-30 2020-02-11 广西华银铝业有限公司 一种方便在线酸洗的换热器
CN111412783B (zh) * 2020-03-30 2021-03-12 浙江大学 一种动力电池板式换热器装配处理装置
WO2023042919A1 (fr) * 2021-09-17 2023-03-23 株式会社ティラド Échangeur de chaleur

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10029999A1 (de) * 2000-06-17 2002-01-03 Otto Thermotech Gmbh Plattenwärmeübertrager der gedichteten Bauart
CN103673696A (zh) * 2013-12-26 2014-03-26 上海艾克森集团有限公司 一种改进的半焊板式热交换器

Also Published As

Publication number Publication date
DK0487931T3 (da) 1995-05-22
US5193612A (en) 1993-03-16
EP0487931A1 (fr) 1992-06-03
JPH04273994A (ja) 1992-09-30
DE4037969A1 (de) 1992-06-04
ATE119270T1 (de) 1995-03-15
DE59104777D1 (de) 1995-04-06

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