EP1038147A1 - Echangeur de chaleur a plaques - Google Patents

Echangeur de chaleur a plaques

Info

Publication number
EP1038147A1
EP1038147A1 EP98958933A EP98958933A EP1038147A1 EP 1038147 A1 EP1038147 A1 EP 1038147A1 EP 98958933 A EP98958933 A EP 98958933A EP 98958933 A EP98958933 A EP 98958933A EP 1038147 A1 EP1038147 A1 EP 1038147A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
plate
plates
plate heat
flow
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.)
Granted
Application number
EP98958933A
Other languages
German (de)
English (en)
Other versions
EP1038147B1 (fr
Inventor
Mauri Kontu
Timo PIRILÄ
Tapio HEINIÖ
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.)
Vahterus Oy
Original Assignee
Vahterus Oy
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 Vahterus Oy filed Critical Vahterus Oy
Publication of EP1038147A1 publication Critical patent/EP1038147A1/fr
Application granted granted Critical
Publication of EP1038147B1 publication Critical patent/EP1038147B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • 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
    • F28D9/0012—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 apparatus having an annular form

Definitions

  • the present invention relates to an advantageously welded plate heat exhanger according to the preamble of claim 1, for transferring heat from a heat-supplying medium to a heat-receiving medium, especially between substances in different phase, such as liquid and gas.
  • heat exchangers are divided into heat exchangers with a plate structure and those with a pipe structure.
  • the significant difference concerning both the construction and the heat transfer is that the heat transfer surfaces are mainly pipes in one structure, and plates in the other.
  • a pipe cluster with header and branching parts is usually placed inside a circular mantle. Thanks to the cylindrical shape and the pipes, the structure is well suited as a pressure vessel, and thus pipe heat exchangers have been used in extremely high pressures.
  • a large number of boiler contractions are some kind of pipe heat exchangers. This applies to both fire-tube/corrugated flue boilers and water-tube boilers, the division being based on that on which side of the pipe the pressure prevails.
  • the most significant drawback of the pipe heat exchangers can be considered to lie in the heavy weight when compared to the surface area of the heat transfer surfaces. Due to that, the pipe heat exchangers are usually large in size. Also, when considering the heat transfer and flow characteristics, it is difficult to design and manufacture pipe heat exchangers especially when economical grounds have to be taken into account.
  • a typical plate heat exchanger is composed of rectangular plates which are pressed against each other by means of end plates, which, in turn, are tightened to the ends of the plate stack by means of tension rods or tension screws.
  • the clearances between the plates are closed and sealed with banded sealings on their outer circumference, and sealings are also used at the flow channels.
  • the bearing capacity of sleek plates is poor, they are strengthened with groovings which are usually arranged crosswise in adjacent plates, wherein they also improve the pressure endurance of the structure when the ridges of the grooves are supported to each other.
  • a more important aspect is the significance of the grooves for the heat transfer: the shape of the grooves and their angle with respect to the flows, affect e.g. the heat transfer and pressure losses.
  • a heat-supplying medium flows in every other clearance between the plates, and a heat-receiving medium in the remaining clearances.
  • the flow is conducted in between the plates via holes located in the vicinity of the corners of the plates.
  • Each clearance between the plates always contains two holes with closed rims and two other holes functioning as inlet and outlet channels for the clearance between the plates.
  • the plate heat exchangers are usually composed of relatively thin plates, wherein a small and light structure is obtained. Because the plates can be profiled into a desired shape, it is possible to make the heat transfer properties suitable for the target of use in the best possible way.
  • the greatest weakness in conventional plate heat exchangers are the sealings which restrict the pressure and temperature endurance of the heat exchangers. In several cases the sealings have impaired the possibilities of use also when the heat-supplying or heat-receiving medium has been corrosive.
  • the plate stack is encircled by a mantle, the sides of which are provided with inlet and outlet channels for flows of heat-supplying and heat-receiving medium. Differing from the conventional plate heat exchanger, all flows into the clearances between the plates are directed from outside the plates.
  • the basic problem of the plate heat exchangers i.e. their tightness, is disregarded as a secondary aspect, without providing any solution to that particular problem.
  • the heat exchanger according to the publication is closed by welding, it is possible to attain the same pressure classes as when using a pipe heat exchanger, the heat transfer properties corresponding to the properties of the plate heat exchanger.
  • Finnish patent publication FI 84659 presents a solution which more distinctly shows features typical of both plate heat exchangers and pipe heat exchangers.
  • the circular plates are joined together in pairs by welding them together by the rims of holes which form an inlet and outlet channel.
  • a closed circuit is attained for the flow of one heat transfer medium.
  • the structure is welded and there are only two holes in the plates.
  • the flow of another heat transfer medium is directed to every other clearance between the plates by means of a mantle surrounding the plate stack.
  • sealings are utilized which are primarily used as controllers for the flow.
  • the purpose of this invention is to produce a plate heat exchanger with no sealing problems and with a pressure endurance corresponding to the properties of pipe exchangers, and in which the heat transfer properties can be selected as in a plate heat exchanger.
  • the sealing problems are avoided by welding the joints, and the controllers can be entirely removed between the mantle and the plate stack.
  • the plate heat exchanger according to the invention has an extremely wide range of use, and it can be utilized for heat transfer between media in different phases.
  • the invention is based on the idea that there are holes in the centre of the circular heat exchange plates, which holes form a flow channel for one heat transfer medium, by means of which channel the flow is guided into the clearances between the plates and out of them.
  • the plates are provided with separate holes for inlet and outlet channels. Because the plate stack is a solid piece which is welded together, it can be placed in a detachable manner e.g. in a cylinder which can be opened, from which location the plate stack can be removed for cleaning or repair.
  • the central channel can also function as a support means for the end plates, if it is equipped with a rod, pipe, or the like.
  • the plate heat exchanger according to the invention is characterized in what will be presented in the claims hereinbelow.
  • the welded plate heat exchanger according to the invention is advantageously provided with circular grooved plates, which are joined together in such a way that flow ducts for the heat-supplying medium and heat-receiving medium are formed between the plates.
  • the plate heat exchanger is equipped with channels which are joined to inlet and outlet fittings.
  • the plate stack consisting of relatively thin plates endure pressure
  • its ends are supported with end plates which are connected together with support means, rods, a mantle, or the like.
  • the plates of the plate heat exchanger are joined together in pairs by the outer perimeters of the holes located in the centre of the plates and by the outer perimeters of the plates of the plate pair in question, in such a way that a closed flow duct for one heat transfer medium is formed inside the plate pairs.
  • the plates of the plate pair are provided with at least one hole by which the plate is attached to a corresponding hole in the adjacent plate pair.
  • the plates are provided with two holes in addition to the hole in the centre, the holes forming the inlet and outlet channels for the flow ducts inside the plate pairs.
  • the outer perimeters of the flow ducts formed between the plate pairs are open, and the flow into and out of them takes place via the central channel.
  • the plate stack composed of the plates of the plate heat exchanger is supported between the end plates.
  • the end plates can be fixed to each other with rods, or the like, wherein the outer perimeter of the plate heat exchanger is primarily left open, or the end plates can be joined with a mantle structure whereby the entire outer perimeter can be closed.
  • the central channel can also be provided with a pipe or the like, to support the end plates.
  • the flow of the heat transfer medium enters or leaves the open central channel in the radial direction of the plate.
  • the flow of the second heat transfer medium crosses the flow of the first one, wherein the plate heat exchanger is a cross flow exchanger.
  • the mantle of the plate heat exchanger can be opened at the desired location in order to supply the flow of the heat transfer medium or to discharge it from the plate heat exchanger.
  • the flows are controlled by the mantle located against the plate stack, by a pipe located in the central channel against its walls and by openings on the mantle and in the pipe.
  • the plate heat exchanger is made to function both as a forward flow exchanger and a counter flow exchanger.
  • the cross-sectional area of the flow between the plates is increased by the parallel flow on both sides of the central channel.
  • the flow conditions between the plates can be controlled by changing the angle ⁇ between the ridges of the grooves on the plates placed against each other, wherein by using smaller angles, greater flow quantities are attained for flows of gaseous media through the heat exchanger. Accordingly, the flows of liquid media can be smaller and the angle ⁇ can be wider.
  • the cross-sectional areas of the grooves in the plates variable in size A ⁇ > A2, it is possible to convey greater volume flows on the gas side than on the liquid side.
  • the grooves on the plates of the plate heat exchanger can also be made symmetrically with respect to the centre of the plate. Thus, the flow conditions remain almost equal in the different parts of the plate and in all flow types.
  • the plate heat exchanger according to the invention has a simple stracture. Due to the circular shape, it is possible to automate the manufacturing techniques, e.g. the welding, with relatively low costs. The circular shape also improves pressure endurance. When using a cylindrical outer shell, one end can be arranged to be opened, wherein it is possible to clean the heat transfer surfaces on at least one side. It is possible to incorporate a large heat transfer surface into the small size and light weight.
  • the plate heat exchanger according to the invention can be made of a corrosion resistant material, for example titanium, with moderate costs because, due to the stracture, the material thicknesses of the plates are small.
  • the welded plate heat exchanger according to the invention can be used in a wide variety of ways and in numerous situations.
  • the plate heat exchanger can be used as a cross flow, forward flow and counter flow heat exchanger. Heat transfer between media in different phases and in the same phase is possible.
  • the heat exchanger according to the invention can also be used i.a. as a cooler, an evaporator, a condenser, a boiler, and a waste heat boiler.
  • Fig. 1 shows a plate heat exchanger according to the invention in a crosscut schematical side view, in an embodiment where the plate heat exchanger has an open outer perimeter
  • Fig. 2 shows schematically the position of the superimposed plates of the plate heat exchanger as well as the position of the grooves of the plates in the plate stack
  • Fig. 3 shows a part of the plate stack formed by the plates according to
  • Fig. 4 shows the profiles of the plates of Figs. 2 and 3 in a cross-section
  • Fig. 5 shows a part of the plate stack in which the grooves of the plates are levelled at their bottom
  • Fig. 6 shows the profiles of the plates according to Fig. 5 in a cross- section
  • Fig. 7 shows a schematical side view of the cross-section of a plate heat exchanger according to the invention in an embodiment comprising a mantle and a pipe arranged in the central channel,
  • Fig. 8 shows schematically a cross-cut plate heat exchanger provided with an opened mantle and a central pipe, and functioning on a counter flow principle
  • Fig. 9 shows schematically the plate stack of the plate heat exchanger and the values to be used in calculations
  • Fig. 10 shows a schematical top view of the plate stack of the plate heat exchanger in an embodiment where the plates are grooved symmetrically with respect to their centre.
  • a welded plate heat exchanger 1 is used as a cooler or a heater.
  • the grooves on the plates of the plate heat exchanger are not shown in the figure.
  • plates 2 and 3 form a plate pair 4 which is conjoined for example by welding at the outer perimeters 5.
  • the plate pair 4 is conjoined at the central hole 6 of the plates 2 and 3, along its perimeter 7.
  • the plate pairs 4 are attached together by welding at holes 8 and 9, along their outer perimeters 10 and 11.
  • the plate pairs 4 joined together form a plate stack 12, inside of which a central channel 13 is formed of the central holes 6 of the plates 2, 3.
  • the holes 8 and 9 form the inlet and outlet channels 14 and 15 for one heat transfer medium in the inner flow ducts 16 of the plate stack.
  • the central channel 13 is connected to the flow ducts 17 between the plate pairs 4.
  • the inlet and outlet channels 14 and 15 for the inner flow of the plate stack 12 are connected on at least one end to an inlet fitting 18 and an outlet fitting 19.
  • the flow of the heat transfer medium in this circuit is shown by unbroken arrows 20.
  • the reference number 21 refers to the grooves on the plates 2 and 3, the bottom of the grooves forming a ridge 22 or a level surface 23.
  • Fig. 2 shows the angle ⁇ between the ridges of the superimposed plates 2 and 3.
  • Figs. 3 to 6 illustrate how the cross-sectional areas A ⁇ and A2 formed by the grooves 21 vary in size.
  • a desired proportion is achieved for the cross-sectional areas.
  • the flow volumes of a gaseous medium can be increased by increasing the cross-sectional area of the flow duct 16 or 17.
  • the plates 2 and 3 support each other via supporting points 24, at which the ridges 22 and/or level surfaces 23 of the grooves 21 are placed against each other.
  • the structural strength required, the materials of the plates 2 and 3, and the shape of the grooves 21 set the limits to the proportion between the cross- sectional areas Ai and A2.
  • Fig. 1 shows blowers 38 which are fixed to the end plates 31 and 32 and which generate gas flows illustrated by broken line arrows 39.
  • Figs. 7 and 8 show an embodiment of the plate heat exchanger, in which the flow ducts 16 and 17 of both the heat-supplying and the heat-receiving medium are closed and they can be pressurized.
  • the end plates 31 and 32 are connected together by means of a mantle 41 surrounding the plate stack 12. For maintenance purposes, one of the end plates 31, 32 is attached to the mantle 41 in such a way that it can be easily detached.
  • a pipe 42 or the like is fixed to an opening 43 in the mantle 41, and through which opening the flow 39 of one heat transfer medium is guided to the plate heat exchanger 1 or out of the same.
  • the central channel 13 of the plate stack 12 is provided with a pipe 44 which has an opening 45 for the flow, either into the pipe 44 or out of the same.
  • the grooves 21 and their ridges are in a symmetrical position with respect to the centre.
  • the value of the angle ⁇ is the same everywhere, both in circular flows and in radial flows.
  • the plate heat exchanger 1 can be either open or closed, wherein in the former case it has a primarily open outer perimeter, and in the latter case it is primarily closed with a mantle or the like.
  • the open plate heat exchanger 1 for example as a cooler or a heater, the most advantageous result is achieved by conducting the gas flow 39 to the central channel 13 or out of the same in a forced flow by means of blowers 38 or the like.
  • the flow can also be unidirectional, wherein only one end plate 31, 32 is provided with a hole 33. When the central channel 13 is in vertical position, a free flow of the gas can also be possible.
  • the flow 20 inside the plate stack 12 can be forced or free.
  • the plate heat exchanger according to Fig. 1 functions as a cooler in free circulation.
  • the warm medium flow 20 supplied from above is discharged from below by the effect of gravity. Also, on the basis of phase transitions, a sufficient circulation is attained for example in condensers and evaporators.
  • the best capacity is typically achieved when both flows are forced.
  • the flows of the heat transfer media are passed in the direction of the perimeters of the plates 2 and 3 both in the inner and in the outer flow ducts 16, 17 of the plate stack 12.
  • the inner surface of the mantle 41 abuts the outer perimeters of the plates 2 and 3, which perimeters are welded together, and the outer surface of the pipe 44, located in the central channel 13, abuts the welded perimeters 7 of the holes 6.
  • broader flow ducts are composed, because the grooves 21 are absent therein.
  • the distance from the opening 43 along the inner surface of the mantle 41 to the opening 45 of the pipe 44 located in the central channel 13 is, however, considerably longer than the distance via the centre of the plates 2, 3.
  • the flows on the inner surface of the mantle 41 and on the outer surface of the pipe 44 are minor so that it is not necessary to take them into account, and thus separate flow controllers or sealings are not necessary.
  • the free flow based on gravity may become optional in a closed plate heat exchanger 1 when the construction is used for example as a boiler, wherein the central channel 13 functions as a combustion chamber and the plate stack 12 forms a convection part.
  • the heated water rises from the channel 15 via the flow ducts 16 to the channel 14.
  • the closed plate heat exchanger 1 according to the invention can also be utilized as a waste heat boiler for various purposes of use.
  • the circulation of the liquid can thus be arranged either in free or in forced circulation.
  • the closed plate heat exchanger according to the invention can be especially well used e.g. as an evaporator or a condenser in apparatuses applying the refrigeration technique.
  • Figs. 1 to 10 do not show the structure of the plate heat exchanger 1 according to the invention in which the plate stack is placed inside a spacious mantle 41 and there is no pipe 44 controlling the flow inside the central channel 13.
  • Such a structure is closed and it is well suited e.g. for corrosive conditions in sea water heat exchangers.
  • the parts of the mantle 41 and the end plates 31 and 32 receiving the loads caused by the pressure can be made of constructional steel, and the inner surfaces which are liable to corrosion are coated with corrosion resistant materials.
  • the plate stack 12 containing the welded heat transfer surfaces can be made of titanium which is highly resistant to corrosion. Such a structure can also be used in processing industry and chemical industry, in different types of reactors or the like.
  • a ring-shaped channel is formed between the mantle 41 and the plate stack 12, to which channel a flow is directed from the central channel 13 along the flow ducts 17, or from which a flow is directed to the central channel 13.
  • the plates 2 and 3 of the plate stack 12 can, of course, be joined together with other methods and in a different order as opposed to what has been presented above within the scope of the inventive idea. Besides welding, the joining can be conducted by means of adhesives, by soldering, or with corresponding techniques.

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)

Abstract

L'invention concerne un échangeur (1) de chaleur à plaques constitué d'une pile (12) de plaques comprenant des plaques (2, 3) à rainures, de préférence circulaires, soudées les unes aux autres. Les espaces entre les plaques (2, 3) forment des passages (16, 17) d'écoulement pour un support d'alimentation de chaleur et un support de réception de chaleur. Les plaques (2, 3) comprennent des ouvertures (6, 8, 9) qui forment des canaux (13, 14, 15) d'entrée et de sortie pour les flux (20, 39) des supports de transfert de chaleur. Au moins un des orifices (6) des plaques (2, 3) est placé sensiblement au centre de la plaque (2, 3). L'échangeur (1) de chaleur à plaques fonctionne selon le principe des courants croisés. Lorsque l'échangeur (1) à plaques est équipé d'un manchon partiellement ouvert qui connecte les plaques (31, 32) terminales entre elles, et que le canal (13) central comprend un tube à ouverture partielle permettant de réguler les flux, l'échangeur (1) de chaleur à plaques peut fonctionner à la fois selon le principe des courants croisés et selon le principe du courant avant.
EP98958933A 1997-12-10 1998-12-07 Echangeur de chaleur a plaques Expired - Lifetime EP1038147B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FI974476 1997-12-10
FI974476A FI109148B (fi) 1997-12-10 1997-12-10 Levylämmönvaihdin
PCT/FI1998/000952 WO1999030099A1 (fr) 1997-12-10 1998-12-07 Echangeur de chaleur a plaques

Publications (2)

Publication Number Publication Date
EP1038147A1 true EP1038147A1 (fr) 2000-09-27
EP1038147B1 EP1038147B1 (fr) 2007-04-11

Family

ID=8550096

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98958933A Expired - Lifetime EP1038147B1 (fr) 1997-12-10 1998-12-07 Echangeur de chaleur a plaques

Country Status (7)

Country Link
EP (1) EP1038147B1 (fr)
AU (1) AU1489599A (fr)
DE (1) DE69837557T2 (fr)
DK (1) DK1038147T3 (fr)
ES (1) ES2285790T3 (fr)
FI (1) FI109148B (fr)
WO (1) WO1999030099A1 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10038523C1 (de) * 2000-08-08 2002-06-27 Xcellsis Gmbh Kombiniertes Bauteil aus Wärmeübertrager und Reaktor
US7004237B2 (en) 2001-06-29 2006-02-28 Delaware Capital Formation, Inc. Shell and plate heat exchanger
FI113695B (fi) 2001-10-09 2004-05-31 Vahterus Oy Hitsattu levyrakenteinen lämmönvaihdin
FI118391B (fi) 2001-12-27 2007-10-31 Vahterus Oy Laite pyöreän levylämmönvaihtimen lämmönsiirron parantamiseksi
FI20030527A0 (fi) 2003-04-08 2003-04-08 Vahterus Oy Levylämmönvaihdin ja virtauksen ohjainlevy
SE524883C2 (sv) 2003-12-10 2004-10-19 Swep Int Ab Plattvärmeväxlare
ITBO20040636A1 (it) * 2004-10-15 2005-01-15 Teclab S C R L Recuperatore di calore per la condensazione dei fumi
ITMI20060274A1 (it) 2006-02-15 2007-08-16 Angelo Rigamonti Scambiatore di calore per generatore di aria calda e caldaia
US9285172B2 (en) 2009-04-29 2016-03-15 Westinghouse Electric Company Llc Modular plate and shell heat exchanger
US20120103578A1 (en) 2009-04-29 2012-05-03 Westinghouse Electric Company Llc Modular plate and shell heat exchanger
DE102012003348A1 (de) * 2012-02-21 2013-08-22 Babcock Borsig Steinmüller Gmbh Mikrogasturbinenanlage
CN103175430A (zh) * 2012-06-28 2013-06-26 郑州大学 环形微通道换热板
DK2944912T3 (en) 2014-05-13 2017-03-20 Alfa Laval Corp Ab PLATE HEAT EXCHANGE
DK3372941T3 (da) 2017-03-10 2021-01-11 Alfa Laval Corp Ab Pladepakke, plade og varmeveksleranordning
DE202019104732U1 (de) * 2019-08-29 2019-09-11 levgen Kushch Scheibenförmige Wärmeaustauscherplatte und Scheibenplattenwärmeaustauscher, umfassend eine solche scheibenförmige Wärmeaustauscherplatte
US11662149B2 (en) * 2021-09-03 2023-05-30 B/E Aerospace, Inc. Layered diffuser channel heat exchanger

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US984944A (en) * 1910-06-07 1911-02-21 W A Schnoeblen Lamp-chimney holder.
DE810214C (de) * 1948-10-18 1951-08-06 Rech S Tech Et D Expl S Ind So Kuehlvorrichtung fuer Verbrennungsmotoren
US3424240A (en) * 1966-08-26 1969-01-28 Avco Corp Corrugated stacked-plate heat exchanger
US3385353A (en) * 1967-01-31 1968-05-28 Avco Corp Mounting and support for the stacked sheets of a heat exchanger
US3785435A (en) * 1972-11-15 1974-01-15 Avco Corp Thermal damper for plate type heat exchangers
US3831674A (en) * 1972-11-16 1974-08-27 Avco Corp Plate type heat exchangers
DE3008717A1 (de) * 1980-03-07 1981-09-17 Witzenmann Gmbh Metallschlauch-Fabrik Pforzheim, 7530 Pforzheim Membran-waermetauscher
US4431050A (en) * 1981-10-16 1984-02-14 Avco Corporation Stacked-plate heat exchanger made of identical corrugated plates
US4470454A (en) * 1982-08-19 1984-09-11 Avco Corporation Primary surface for compact heat exchangers
JPS59191888A (ja) * 1983-04-13 1984-10-31 Nippon Denso Co Ltd 熱交換器
US4917181A (en) * 1988-08-04 1990-04-17 Textron Lycoming Segmented annular recuperator and method
US5203832A (en) * 1989-11-17 1993-04-20 Long Manufacturing Ltd. Circumferential flow heat exchanger
US5179999A (en) * 1989-11-17 1993-01-19 Long Manufacturing Ltd. Circumferential flow heat exchanger
DE3938253A1 (de) * 1989-11-17 1991-05-23 Behr Gmbh & Co Oelkuehler fuer eine brennkraftmaschine
US5078209A (en) * 1991-02-06 1992-01-07 Modine Manufacturing Co. Heat exchanger assembly
FI94395B (fi) * 1993-12-20 1995-05-31 Mauri Eino Olavi Kontu Levylämmönsiirrin ja sen valmistusmenetelmä
DE19510847C2 (de) * 1995-03-17 2002-11-21 Michael Rehberg Plattenwärmetauscher

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9930099A1 *

Also Published As

Publication number Publication date
AU1489599A (en) 1999-06-28
DE69837557T2 (de) 2008-01-03
DK1038147T3 (da) 2007-07-16
EP1038147B1 (fr) 2007-04-11
WO1999030099A1 (fr) 1999-06-17
FI974476A (fi) 1999-06-11
FI974476A0 (fi) 1997-12-10
DE69837557D1 (de) 2007-05-24
FI109148B (fi) 2002-05-31
ES2285790T3 (es) 2007-11-16

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