EP0737296B1 - Echangeur de chaleur a plaques - Google Patents

Echangeur de chaleur a plaques Download PDF

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Publication number
EP0737296B1
EP0737296B1 EP95905679A EP95905679A EP0737296B1 EP 0737296 B1 EP0737296 B1 EP 0737296B1 EP 95905679 A EP95905679 A EP 95905679A EP 95905679 A EP95905679 A EP 95905679A EP 0737296 B1 EP0737296 B1 EP 0737296B1
Authority
EP
European Patent Office
Prior art keywords
plates
lines
facets
heat exchanger
bumps
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.)
Expired - Lifetime
Application number
EP95905679A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0737296A1 (fr
Inventor
Bernard Thonon
Roland Vidil
Claude Roussel
Jean-Michel Grillot
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.)
Vicarb SA
Commissariat a lEnergie Atomique et aux Energies Alternatives CEA
Original Assignee
Vicarb SA
Commissariat a lEnergie Atomique CEA
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 Vicarb SA, Commissariat a lEnergie Atomique CEA filed Critical Vicarb SA
Publication of EP0737296A1 publication Critical patent/EP0737296A1/fr
Application granted granted Critical
Publication of EP0737296B1 publication Critical patent/EP0737296B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F28F3/02—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
    • F28F3/083—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning capable of being taken apart
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the invention relates to a plate heat exchanger, formed by a stack of corrugated plates delimiting channels of variable section.
  • corrugations The general function of the corrugations is to disturb the flow of fluids in order to increase the heat transfers through the plates, but they have the drawback of making the pressure drops much greater than with flat plates.
  • FR-A-2 648 220 a particular form of corrugated plate was described which made it possible to reduce the volume of the dead zones or of recirculation, where the fluid stagnates appreciably, which is one of the main causes of losses of heat exchange efficiency and fouling of the plates if the fluid is loaded with particles, because these then settle much more easily.
  • the plates of this prior invention had facets alternately of two different lengths and were joined together so that the corrugations of the consecutive plates formed angles preferably close to 180 °, that is to say that, in each channel , the long facets were oriented substantially in the same direction, which corresponded to the direction of flow of the fluid in the canal: the short facets therefore faced the fluid and, thanks to their steeper slope, deviated it strongly towards the long facets on the other plate delimiting the channel.
  • the fluid current licked the long facets over a large part of their surface and the recirculation zones, which form behind the undulations which restrict the channel, to know before long facets, were reduced accordingly. We therefore obtained better heat exchange performance and also easier flow.
  • the corrugations composed of a long facet and a short facet have, with identical pitch (the pitch designating the width of the corrugation), a lesser height than the corrugations of a conventional corrugated sheet, composed of two similar facets.
  • the channels have a smaller average section.
  • it is desired not to reduce this section which requires the use of plates of similar shape but with larger undulations and not larger.
  • the corrugation lines are then spaced apart and the number of points of contact of the plates between them smaller, which reduces the mechanical resistance of the stack.
  • the present invention can be viewed as an improvement on the previous invention, since it offers substantially equivalent advantages with regard to the heat exchange performance and the weakness of the fouling of the walls of the plates, but also losses of significantly lower load by reducing movements vortex, while involving the same number of points of contact between plates as ordinary corrugated plates.
  • the invention also lends itself to similar flows of fluids in both directions, which makes it possible to freely choose flows with parallel currents as well as with countercurrents.
  • the invention relates in its most general form to a heat exchanger composed of corrugated plates and joined together to delimit channels, the plates being similar, composed of facets joined by bottom and top lines, the plates being joined together at contact points; the plates are alternately turned over and joined either by their top lines or by their bottom lines; it is characterized in that the facets include bumps near the top lines and hollows near the bottom lines.
  • hollows and bumps be discontinuous along the facets, the bumps being located near the contact points, which allows them to play the role of reduction of volume of the channel only in the places where the dead or stagnant zones are most likely to form.
  • the bumps are much less useful elsewhere.
  • a simple construction is one whose facets include alternating hollows and bumps.
  • FIG. 1 A common type of plate heat exchanger is shown in FIG. 1. It is formed by a superposition of rectangular plates 1, carrying four holes 2 at the corners, a smooth groove 3 peripheral and corrugations 4 on the rest of their surface.
  • the plates can be manufactured by various means, by stamping, machining or molding, and in the real heat exchanger they are supported one on the other by their corrugations 4. Joints not shown are then compressed between the grooves 3 and maintain the seal. The stack is maintained by clamping.
  • the circulation of fluids is against the current, but it could be otherwise.
  • the corrugations 4 are in the form of chevrons but could be rectilinear. Fluids are generally liquids in existing embodiments, but this is not mandatory, and there may also be changes in state. The invention can be applied to all these categories of exchangers as well as to still different kinds of exchangers.
  • the corrugations 4 of the plates 1 can be broken down into top lines 10 alternating with bottom lines 11, the lines 10 and 11 all being parallel to each other and separating facets 12 contiguous.
  • the facets 12 have an uneven surface, that is to say that they are not straight over most of their length as in conventional corrugated sheets, but have bumps 13 and recesses 14.
  • the observation reference is located in the channel 6 above the plate 1, and the top lines 10 are above the bottom lines 11; the bumps 13 are convex reliefs and the hollows 14 are concave reliefs in this channel 6.
  • Holes and bumps 14 and 13 are produced without difficulty with the corrugations 4, for example by stamping with special dies, without any particular operation.
  • the hollows 14 and the bumps 13 do not extend over the entire length of the corrugations 4 but are, on the contrary, discontinuous and that the bumps 13 extend near the apex lines 10, about half the length of the corrugations 4, and at places close to the contact points 15 of the neighboring plate 1; more precisely, the bumps 13 of the adjacent facets 12 extend on either side of the adjoining top line 10 so as to surround the contact points 15 in pairs.
  • the recesses 14 are adjacent to the bottom lines 11 and s '' each extend between two consecutive bumps 13 of the facet 12 to which they belong (hollow 14 and bumps 13 therefore alternate along each of the facets 12), in such a way that they form a more or less uninterrupted series along each bottom lines 11, alternately on the two facets 12 which border it.
  • the average direction of the flow of the fluid in the channel 6 is vertical (according to the representation of this figure 3) and the angle ⁇ of the corrugations 4 with this direction is 60 °.
  • the other plate 1 delimiting the channel 6 will be similar but placed after having been turned over, so that the plates 1 will join by their apex lines 10 (FIGS. 4 and 5), their corrugations 4 being crossed and making angles of 60 °.
  • each pair of plates 1 which will be joined either by their respective top lines 10, or by their bottom lines 11. Whether the direction of flow is ascending or descending, the characteristics of the flow are identical because the shape of the channels 6 is symmetrical.
  • the bumps 13 form areas where the section of the channel 6 is very small around the contact points 15, where the fluid would have tended to stagnate, but that the bumps 13 do not contribute to obstruct the flow to other places in the canals 6.
  • the points of contact 16 with the other adjacent plate 1, located in the center of the diamonds formed by four points of contact 15 neighbors, will be surrounded by two pairs of hollows 14 of the two plates 1 concerned, but which can be seen as bumps 13 in the neighboring channel 6 that these two plates 1 delimit. It can therefore be seen that all of the channels 6 will have the same shape.
  • recesses 17 can be produced on the crown lines 10 at the contact points 15, between the bumps 13. These recesses allow on the one hand to precisely position the plates and on the other hand to better profile the flow around the corrugation.
  • the dimension of these recesses 17 is approximately 0.5 mm deep (between 0.3 mm and 1 mm), and their shape allows the interlocking of the contact points 15 of the upper plate. Their realization is done in the same way as the rest of the plate, without additional cost.
  • the recesses 17 are established on a plate 1 of two; the top lines 10 of the other plates 1 remain straight.
  • Bumps could also be made at the bottom lines 11, at the location of the contact points 16, of some of the plates 1 to also facilitate the interlocking of the plates 1 by these bottom lines 11.
  • One embodiment actually tested included plates with corrugations 4 whose angle ⁇ with respect to the flow was equal to 60 °, plates 1 whose pitch p (FIGS. 2 and 3) was 13 mm and the height e ( figure 2) of 3.9 mm, for heights or maximum depths of 0.8 mm and diameters of 3 to 4 mm for the bumps 13 and the hollows 14.
  • the channels 6 were 0.4 m long and 0.14 m wide.
  • the flow rate was 6 to 40 m 3 per hour in each channel 6.
  • the plates 1 according to the invention produced a pressure (or pressure) loss of 30 to 50% less than a conventional corrugated plate, that is to say devoid of bumps 13 and hollows 14.
  • the heat exchange coefficients were close, with deviations of less than 5%.
  • the plates were formed by stamping stainless steel sheets 0.6 mm thick.
  • the invention can be applied to all fields of activity where this type of exchanger already finds use, and in particular the chemical, para-chemical, petroleum, climatic, agro-food, energy producing and metallurgical industries.

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)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Separation By Low-Temperature Treatments (AREA)
EP95905679A 1993-12-29 1994-12-28 Echangeur de chaleur a plaques Expired - Lifetime EP0737296B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9315816A FR2714456B1 (fr) 1993-12-29 1993-12-29 Echangeur de chaleur à plaques améliorées.
FR9315816 1993-12-29
PCT/FR1994/001545 WO1995018348A1 (fr) 1993-12-29 1994-12-28 Echangeur de chaleur a plaques ameliorees

Publications (2)

Publication Number Publication Date
EP0737296A1 EP0737296A1 (fr) 1996-10-16
EP0737296B1 true EP0737296B1 (fr) 1997-08-06

Family

ID=9454534

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95905679A Expired - Lifetime EP0737296B1 (fr) 1993-12-29 1994-12-28 Echangeur de chaleur a plaques

Country Status (10)

Country Link
US (1) US5806584A (da)
EP (1) EP0737296B1 (da)
JP (1) JP3618350B2 (da)
DE (1) DE69404868T2 (da)
DK (1) DK0737296T3 (da)
ES (1) ES2107911T3 (da)
FR (1) FR2714456B1 (da)
GR (1) GR3025251T3 (da)
NO (1) NO305920B1 (da)
WO (1) WO1995018348A1 (da)

Families Citing this family (20)

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Publication number Priority date Publication date Assignee Title
IT1306959B1 (it) * 1999-01-15 2001-10-11 Antonio Gigola Procedimento e pressa per l'ottenimento di pannelli oscuranti eumidificanti,in particolare per allevamenti avicoli o serre,e pannello
DE19963373A1 (de) * 1999-12-28 2001-07-12 Abb Alstom Power Ch Ag Vorrichtung zur Kühlung einer, einen Strömungskanal umgebenden Strömungskanalwand mit wenigstens einem Rippenzug
DE10218912A1 (de) 2002-04-27 2003-11-06 Modine Mfg Co Gewellter Wärmetauschkörper
US7011904B2 (en) * 2002-07-30 2006-03-14 General Electric Company Fluid passages for power generation equipment
DE10249724B4 (de) * 2002-10-25 2005-03-17 Bayer Industry Services Gmbh & Co. Ohg Hochleistungs-Temperierkanäle
DE10333177A1 (de) * 2003-07-22 2005-02-24 Modine Manufacturing Co., Racine Strömungskanal für einen Wärmeaustauscher
US6976531B2 (en) * 2003-10-22 2005-12-20 Dana Canada Corporation Heat exchanger, method of forming a sleeve which may be used in the heat exchanger, and a sleeve formed by the method
FR2876179B1 (fr) * 2004-10-04 2007-02-16 Alfa Laval Vicarb Sa Echangeur de chaleur a plaques specifiques
CZ300999B6 (cs) * 2007-09-27 2009-10-07 2 V V S. R. O. Protiproudý rekuperacní výmeník
PL2202476T3 (pl) 2008-12-29 2016-09-30 Sposób wytwarzania spawanego płytowego wymiennika ciepła
JP5733900B2 (ja) * 2010-02-26 2015-06-10 三菱電機株式会社 プレート式熱交換器の製造方法及びプレート式熱交換器
SE534918C2 (sv) 2010-06-24 2012-02-14 Alfa Laval Corp Ab Värmeväxlarplatta och plattvärmeväxlare
EP2591303B9 (en) * 2010-07-08 2016-02-10 SWEP International AB A plate heat exchanger
US9933214B2 (en) 2011-11-30 2018-04-03 Mitsubishi Electric Corporation Plate heat exchanger and refrigeration cycle apparatus including the same
US9724746B2 (en) * 2013-03-14 2017-08-08 Pratt & Whitney Canada Corp. Aerodynamically active stiffening feature for gas turbine recuperator
JP2016114300A (ja) * 2014-12-15 2016-06-23 フタバ産業株式会社 熱交換器
EP3225947A1 (en) 2016-03-30 2017-10-04 Alfa Laval Corporate AB Heat transfer plate and plate heat exchanger comprising a plurality of such heat transfer plates
US10578367B2 (en) 2016-11-28 2020-03-03 Carrier Corporation Plate heat exchanger with alternating symmetrical and asymmetrical plates
JP6742504B2 (ja) * 2017-03-07 2020-08-19 株式会社Ihi 航空機用放熱器
PL73432Y1 (pl) * 2019-01-04 2024-04-22 Secespol Spolka Z Ograniczona Odpowiedzialnoscia Płyta grzewcza z powierzchnią wymiany ciepła płytowego wymiennika ciepła

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US2550339A (en) * 1948-08-03 1951-04-24 York Corp Plate type heat exchanger
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Also Published As

Publication number Publication date
NO962758D0 (no) 1996-06-28
DE69404868T2 (de) 1998-02-12
DK0737296T3 (da) 1998-02-23
DE69404868D1 (de) 1997-09-11
US5806584A (en) 1998-09-15
FR2714456A1 (fr) 1995-06-30
JPH09511565A (ja) 1997-11-18
ES2107911T3 (es) 1997-12-01
JP3618350B2 (ja) 2005-02-09
WO1995018348A1 (fr) 1995-07-06
GR3025251T3 (en) 1998-02-27
FR2714456B1 (fr) 1996-01-12
NO962758L (no) 1996-06-28
NO305920B1 (no) 1999-08-16
EP0737296A1 (fr) 1996-10-16

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