EP1938037A1 - Echangeur de chaleur a plaques et procede de construction d'un echangeur de chaleur a plaques resistant a la pression - Google Patents

Echangeur de chaleur a plaques et procede de construction d'un echangeur de chaleur a plaques resistant a la pression

Info

Publication number
EP1938037A1
EP1938037A1 EP06807966A EP06807966A EP1938037A1 EP 1938037 A1 EP1938037 A1 EP 1938037A1 EP 06807966 A EP06807966 A EP 06807966A EP 06807966 A EP06807966 A EP 06807966A EP 1938037 A1 EP1938037 A1 EP 1938037A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
plate
plates
pairs
plate pairs
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.)
Withdrawn
Application number
EP06807966A
Other languages
German (de)
English (en)
Inventor
Mauri Olavi Kontu
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 EP1938037A1 publication Critical patent/EP1938037A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F28D9/0012—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
    • 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
    • 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
    • F28D9/0043—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 plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • 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
    • F28F2240/00—Spacing means

Definitions

  • the object of the invention is a plate heat exchanger and a method for constructing a pressure-proof plate heat exchanger according to the preambles of the independent claims presented below.
  • a corrugated heat exchanger plate refers to a plate, which has been folded in several places so as to corrugate or the plate has otherwise been provided with corrugations, i.e. grooves and recesses.
  • the heat exchanger plates are typically designed so that when they are fastened to each other flow ducts of specific size and form are formed inside the stack of plates and between the plate pairs.
  • the heat transfer properties of a heat exchanger can be controlled with the corrugation of heat exchanger plates, i.e. by shaping the recesses and bulges in a plate.
  • the heat exchanger and its parts are often designed for a specific use situation.
  • the flow rate and properties, such as temperature, density and pressure, of heat transfer media have a substantial influence on the dimensioning of a plate heat exchanger and on the choice of an optimal plate profile.
  • Different corrugations of plates and angles between the corrugations of a plate pair need to be designed for different use conditions. In other words, different heat exchanger plates are needed for different applications.
  • the plate heat exchanger and method according to the invention are characterised by what is presented in the characterising parts of the enclosed independent claims.
  • the embodiments and advantages mentioned in this text are in suitable parts applicable to both a plate heat exchanger and a method according to the invention, even if this is not always specifically mentioned.
  • a typical plate heat exchanger according to the invention comprises several corrugated heat exchanger plates. According to the invention:
  • each heat exchanger plate has at least two openings
  • the openings in question of the heat exchanger plates are positioned facing each other so that they form an inlet and outlet channel for at least one heat transfer medium
  • a typical method according to the invention for building a high-pressure resistant plate heat exchanger has at least following steps:
  • each heat exchanger plate has at least two openings, are fastened to each other in pairs as plate pairs,
  • an inlet and outlet channel for at least one heat transfer medium is formed by arranging the openings of the heat exchanger plates facing each other,
  • Contact surfaces refer in this context to ridges, which are in contact with each other, of the protrusions of the corrugated heat exchanger plates.
  • the ridges of the heat exchanger plates placed towards each other are typically arranged to intersect each other, whereby contact surfaces are formed at the intersections of the ridges.
  • two heat exchanger plates which form a plate pair, are firmly fastened to each other by soldering or welding at at least substantially all contact surfaces.
  • two adjacent plate pairs are, not soldered or welded together, at least not at substantially all contact surfaces.
  • a great advantage of the invention is that by means of it the heat exchanger can easily be made self-supportive, in other words, ends, which bind the stack of plates, can be left out. This is the fact especially, if the heat transfer medium flowing between plate pairs is not under high pressure.
  • a great advantage of the invention is that by means of it the production processes of various heat exchangers can be made simpler and more inexpensive. Heat exchangers often need channel systems of different size for a different heat transfer medium. Typically, for example the density of the steam to be condensed by a vacuum condenser is very low, whereby its volume in relation to the mass flow and effect of the steam is large.
  • a problem that can occur in an ordinary plate heat exchanger is the narrowness of the plate gaps provided for steam, which narrowness limits the effect of the condenser.
  • One solution is to manufacture plate types, which have a wider profile. That requires, however, the manufacture of expensive pressing tools.
  • one and the same plate profile can be used in all heat exchangers.
  • the gap between the plate pairs can be adjusted so that a necessary flow cross- section is achieved on the steam side.
  • same kind of plates can be used for several different heat exchangers with the aid of the invention, this redounds substantial cost-benefit to the manufacturers of heat exchangers.
  • the gap between two adjacent plate pairs is left at least mainly free. This means that adjacent plate pairs are not particularly fastened to each other. This enables the heat transfer medium passing between the plate pairs to flow as free as possible.
  • a suitable distance between two adjacent plate pairs is 1-10 mm, or 1- 5 mm.
  • each heat exchanger plate has two openings. Typically, one opening is thus arranged as an inflow channel for the heat exchanger medium passing inside the plate pairs and the second opening is arranged as an outflow channel of the same heat exchanger medium.
  • the stack of plates is thus typically arranged inside the housing, and the second heat exchanger medium is arranged to flow in the housing, outside the plate pairs, i.e. between the plate pairs.
  • the heat exchanger plates can also have e.g. four openings, one for the inflow and outflow channel of each heat exchanger medium. Applications obtainable by different number of openings are not a specific aim of this invention and are thus not explained more broadly.
  • the adjacent plate pairs are fastened to each other at the openings for the heat exchanger medium in the plate pairs.
  • space between two adjacent plate pairs is accomplished by fitting pieces, made of e.g. suitable metal, arranged between the plate pairs.
  • the thickness of the fitting pieces is arranged to correspond the desired space and they are fastened or mounted between the plate pairs when assembling the heat exchanger. With the aid of the fitting pieces it is easy to arrange the spaces between the plate pairs exactly to the desired size.
  • the fitting pieces are arranged at the edges of the openings for the heat exchanger medium in the plate pairs.
  • the plates and the fitting pieces are easy to weld together at this same point.
  • the fitting piece is a ring surrounding said opening and placed between two plate pairs. This ring can thus form a sort of duct between the openings of the adjacent plate pairs.
  • the fastening of a ring-like fitting piece to the adjacent plate pairs is easy to carry out in a leak-proof manner. The welding is easy, if the plate pairs are welded together at the inner surface of the fitting piece.
  • the edge of at least one heat exchanger plate is bent as a collar for a distance away from the plate pair towards the next plate pair.
  • the next plate pair is fastened to said collar either from it's own corresponding collar or from another suitable point.
  • the distance between the plate pairs can be determined by adjusting the length of the collar.
  • said collar is formed at the edge of the opening for the flow medium formed in the heat exchanger plate.
  • the collar can act as a sort of duct between the openings of adjacent plate pairs.
  • two adjacent plate pairs are provided with collars pointing to each other, which collars are welded together.
  • the collars can act as a longer duct than before between the openings of adjacent plate pairs.
  • the collars to be placed towards each other have slightly different diameters, the collars can be fastened to each other within each other. This kind of connection is easily made firm.
  • the distance between the plate pairs can be adjusted by changing the length, for which the collars are within each other, i.e. the overlapping length of the collars.
  • the stack of plates is placed in a housing with high-pressure resistance between ends supporting the stack.
  • a pressure resistant channel network also for the heat exchanger medium flowing between the plate pairs.
  • the heat exchanger medium of a heat exchanger is a liquid inside the plate pairs and a gas or a steam between the plate pairs.
  • the effective heat exchange of gas or steam often requires rather big spaces between the plates.
  • the pressure of the gas or steam is not especially high, for example only a little higher than the normal air pressure, and thus it does not direct great force to the stack of plates.
  • the spaces between the plate pairs i.e. the distance between the adjacent plate pairs, is easy to arrange suitable for gases or steam.
  • Figure 1 shows the connection of two heat exchanger plates as a plate pair.
  • Figure 2 shows a partial cut-through of a stack of plates according to the invention in its radial direction.
  • Figure 3 shows a possible arrangement according to the invention at the central opening of the stack of plates,
  • Figure 4 shows another possible arrangement according to the invention at the central opening of the stack of plates,
  • Figure 5 shows a flue gas heat recovery device according to the invention
  • Figure 6 shows a vacuum condenser according to the invention as a sectional view seen from the side
  • Figure 7 shows a vacuum condenser of Figure 6 as seen from the end.
  • FIG 1 it is schematically shown, how two round heat exchanger plates 1 and 1' can be connected as a plate pair 2 according to the invention.
  • a plate pair 2 according to the invention is formed in a manner known per se by welding or soldering two corrugated heat exchanger plates 1 , 1' together. Because of the corrugated form of the plates 1 , 1', i.e. the protrusions 22, 22', i.e. ribs, placed towards each other, and the grooves between them, a channel network for the heat exchanger medium is formed inside the stack of plates 2.
  • the plates have three round openings. The opening 3 formed in the middle of the plates acts as an inflow or outflow channel for the heat exchanger medium flowing outside the plate pairs.
  • the openings 4 formed in the edges of the plates 1 act as inflow or outflow channels for the heat exchanger medium flowing inside the plate pairs.
  • the openings 3 and 4 face each other.
  • the plates 1 , 1' and openings 3 and 4 can also have shapes other than round.
  • Figure 2 shows a cross-section of a stack of plates 11 formed of four plate pairs 2.
  • the connection areas which have been connected by welding or soldering at the protrusions 22 and 22' placed towards each other of two plates 1 and 1 ' of a plate pair, are indicated by numeral 5.
  • space 6 between the plates connected together i.e. the plate pair 2
  • the plate pairs according to the invention are dimensioned to resist a pressure of at least 20 bars.
  • Space 7 between two plate pairs is left at least mainly free, i.e. the plate pairs 2 are not fastened to each other in the area shown in Figure 2.
  • the stack of plates 11 can be supported at its end by an end 8 indicated by a dashed line.
  • the stack of plates 11 can be placed inside the housing 10 indicated by a dashed line.
  • the plates 1 and 1' connected firmly to each other according to the invention make the structure self-supportive, i.e. the stack of plates 11 does not require pressure-supporting structures, such as ends 8, when the space 7 between the plate pairs is non-pressurized or the pressure therein is low.
  • the housing 10 can be supportive and high-pressure-proof. If the heat exchanger medium flowing in the space 7 between the plate pairs also has to be at high pressure, ends 8 and the housing 10 can be arranged as a pressure vessel, which can be dimensioned to resist even very high pressure, for example 100 bars. The pressure resistances of heat exchangers can of course be adjusted to be suitable for each case.
  • Figure 3 shows as an enlarged scale, how the size of the free space 7 between the plate pairs 2 can be arranged changeable with the fitting pieces 12 according to the invention.
  • the ring of a suitable thickness arranged around the edge of the opening 4 formed in the stack of plates acts as a fitting piece 12.
  • the adjacent plates 1 , 1' of two different stacks of plates are welded to the ring 12 and to each other at the ring 12 by a welding 13. The welding 13 is thus made at the edge of the opening 4.
  • Figure 4 shows another embodiment of the invention presenting, how a changeable space 7 between the plate pairs can be accomplished.
  • plates 1 , 1' of the plate pairs are bent at the edges of the openings 4 towards the adjacent plate pair 2.
  • the edge of the plate 1 is bent as a collar 14 and the edge of the plate V in bent as a collar 14'.
  • the length hi of the collars 14 and 14' and the overlapping length h2 between them space 7 between the plate pairs 2 is obtained as desired.
  • the length hi of the collar is typically between 1 — 5 mm.
  • the overlapping length h2 is typically between 3 — 5 mm.
  • the collars 14 and 14' are fastened to each other at the edge of the opening 4 by a welding 13. Different dimensions can of course be sized to be suitable for each case.
  • FIG. 5 shows a flue gas heat recovery device 15.
  • the self-supporting stack of plates 11 can be placed to the end of the flue gas channel 16, in which case the heat exchanger is formed from the stack of plates 11 and no housing structure is needed.
  • the travel direction of flue gases is illustrated by arrows 17 and 17'.
  • the travel directions of the liquid, e.g. water, cooling the flue gases are illustrated by arrows 18 and 18'.
  • the flue gases are directed from the flue gas channel 16 to the central opening 3 and from there further to the spaces between the plate pairs 2, i.e. to spaces 7 shown in Figures 3 and 4. From spaces 7 the flue gases are directed out from the outer edge of the stack of plates 11 in a manner shown by arrows 17'.
  • the water to be heated is directed according to arrow 18 into the inlet fitting 19 for water and into the stack of plates 11 via the opening 4. It is shown in Figures 3 and 4, how water is directed from the opening 4 inside the plate pairs 2. Via the channel network 6 of the plate pairs the water travels to the opening 4' and further via the outlet fitting 19', according to arrow 18', out from the stack of plates 11. Openings 3 and 4 are closed at the upper end 20 of the heat recovery device.
  • the flue gas pressure is typically only a little higher than the normal air pressure and it does not direct great forces to the stack of plates 11.
  • the pressure of the liquid side, i.e. the pressure prevailing inside the plate pairs 2 can be for example 5 — 20 bar, for example 10 bar.
  • the spaces between plates on the flue gas side i.e. the size of spaces 7 remaining between the plate pairs 2
  • the size of spaces 7 can be arranged considerably bigger than the size of the liquid channel network 6 inside the plate pairs.
  • FIG 6 and 7 show a vacuum condenser 21 according to an embodiment of the invention.
  • the steam to be condensed is directed according to arrow 17 into the inlet fitting 17 arranged to the upper edge of the condenser and further inside the vessel formed by the housing 10 and ends 8.
  • the condensed water is directed away from the stack of plates 11 and further according to arrow 17' via the outlet fitting 16' out from the vacuum condenser 21.
  • the water, which is warming up, is directed according to arrow 18 to the inlet fitting 19 for water and further into the stack of plates 11 via the opening 4.
  • Figures show only some preferred exemplary embodiments according to the invention. Figures do not separately show matters that are irrelevant in view of the main idea of the invention, known as such or obvious as such for a man skilled in the art. It is apparent to a man skilled in the art that the invention is not limited exclusively to the examples described above, but that the invention can vary within the scope of the claims presented below. The dependent claims present some possible embodiments of the invention, and they are not to be considered to restrict the scope of protection of the invention as such.

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 de chaleur à plaques (15, 21) et un procédé de construction d'un échangeur de chaleur à plaques (15, 21) résistant à la pression. L'échangeur de chaleur à plaques selon l'invention comporte une pile de plaques dotée de plusieurs paires de plaques (2) formées de deux plaques ondulées d'échangeur de chaleur (1, 1 '). Les plaques d'échangeur de chaleur (1, 1 ') qui forment une paire de plaques (2) sont fermement reliées l'une à l'autre en les soudant l'une à l'autre au niveau de leurs surfaces de contact (5).
EP06807966A 2005-10-20 2006-10-19 Echangeur de chaleur a plaques et procede de construction d'un echangeur de chaleur a plaques resistant a la pression Withdrawn EP1938037A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20051056A FI20051056L (fi) 2005-10-20 2005-10-20 Levylämmönsiirrin ja menetelmä painetta kestävän levylämmönsiirtimen rakentamiseksi
PCT/FI2006/000338 WO2007045719A1 (fr) 2005-10-20 2006-10-19 Echangeur de chaleur a plaques et procede de construction d'un echangeur de chaleur a plaques resistant a la pression

Publications (1)

Publication Number Publication Date
EP1938037A1 true EP1938037A1 (fr) 2008-07-02

Family

ID=35185195

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06807966A Withdrawn EP1938037A1 (fr) 2005-10-20 2006-10-19 Echangeur de chaleur a plaques et procede de construction d'un echangeur de chaleur a plaques resistant a la pression

Country Status (3)

Country Link
EP (1) EP1938037A1 (fr)
FI (1) FI20051056L (fr)
WO (1) WO2007045719A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI20095267A (fi) * 2009-03-13 2010-09-14 Mauri Kontu Levylämmönsiirrin ja menetelmä levylämmönsiirtimen paineenkestävyyden parantamiseksi
JP5747335B2 (ja) * 2011-01-11 2015-07-15 国立大学法人 東京大学 熱機関用熱交換装置
EP2527775A1 (fr) * 2011-05-25 2012-11-28 Alfa Laval Corporate AB Plaque d'échangeur thermique pour échangeur thermique de type plaque et enveloppe
JP7182395B2 (ja) * 2018-08-09 2022-12-02 リンナイ株式会社 熱交換器
DE202019104732U1 (de) * 2019-08-29 2019-09-11 levgen Kushch Scheibenförmige Wärmeaustauscherplatte und Scheibenplattenwärmeaustauscher, umfassend eine solche scheibenförmige Wärmeaustauscherplatte

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997039301A1 (fr) * 1996-04-16 1997-10-23 Alfa Laval Ab Echangeur de chaleur a plaques

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1928146A1 (de) * 1968-06-06 1969-12-11 Delaney Gallay Ltd Waermeaustauscher
JP3359946B2 (ja) * 1993-03-04 2002-12-24 東京ラヂエーター製造株式会社 積層型熱交換器
DE4307503C2 (de) * 1993-03-10 1995-01-19 Mtu Friedrichshafen Gmbh Wärmetauscher, insbesondere Ladeluftkühler einer Brennkraftmaschine
DE4307504C1 (de) * 1993-03-10 1994-09-22 Mtu Friedrichshafen Gmbh Wärmetauscher, insbesondere Ladeluftkühler einer Brennkraftmaschine
DE59701152D1 (de) * 1996-05-24 2000-03-30 Alenko Ag Zuerich Wärmetauscher und Vorrichtung zum Durchführen eines Kreisprozesses
FI118391B (fi) * 2001-12-27 2007-10-31 Vahterus Oy Laite pyöreän levylämmönvaihtimen lämmönsiirron parantamiseksi

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997039301A1 (fr) * 1996-04-16 1997-10-23 Alfa Laval Ab Echangeur de chaleur a plaques

Also Published As

Publication number Publication date
WO2007045719B1 (fr) 2007-06-07
FI20051056A0 (fi) 2005-10-20
FI20051056L (fi) 2007-04-21
WO2007045719A1 (fr) 2007-04-26

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