WO1998048230A1 - Cross- and counterflow plate heat exchanger wherein the ports are provided with flanged, joined rims around part of their periphery - Google Patents

Cross- and counterflow plate heat exchanger wherein the ports are provided with flanged, joined rims around part of their periphery Download PDF

Info

Publication number
WO1998048230A1
WO1998048230A1 PCT/SE1998/000717 SE9800717W WO9848230A1 WO 1998048230 A1 WO1998048230 A1 WO 1998048230A1 SE 9800717 W SE9800717 W SE 9800717W WO 9848230 A1 WO9848230 A1 WO 9848230A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat
flow
side wall
absorbing medium
plates
Prior art date
Application number
PCT/SE1998/000717
Other languages
French (fr)
Swedish (sv)
Inventor
Erik Hedman
Original Assignee
Volvo Lastvagnar Ab
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 Volvo Lastvagnar Ab filed Critical Volvo Lastvagnar Ab
Priority to JP54559998A priority Critical patent/JP2002501604A/en
Priority to EP98917925A priority patent/EP0977972A1/en
Priority to AU70956/98A priority patent/AU7095698A/en
Priority to BR9808959-5A priority patent/BR9808959A/en
Publication of WO1998048230A1 publication Critical patent/WO1998048230A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0037—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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

Definitions

  • Cross- and counter flow plate heat exchanger wherein he ports are provided with flanged, joined rims around part of their periphery.
  • the present invention relates to an arrangement in a plate heat exchanger according to the pre-characterising clause of claim 1.
  • recuperator is already known from the E-C Parsons Government/Industry Meeting 2 Summary on "Development, Fabrication and Application of a Primary Surface Gas Turbine Recuperator” held in Washington, D.C. on 20-23 May 1985.
  • the flow channels which have cross-flow and counter- flow sections, connect here via the inlet and exhaust ports with separate manifolds arranged outside the actual set of heat exchanger plates and welded to the set of heat exchanger plates.
  • Integrating manifolds into the plates by providing the plates with openings with splayed flanges placed around the edge of the openings is already known from DE-A-29 23 944.
  • the said flanges telescope into one another to form the walls of the manifolds and indentations in the flanges form inlet and outlet ports of the said manifolds.
  • the object here was to produce a design that is resistant to mechanical stresses and easy to manufacture. No method of controlling the flow into and out of the manifolds is disclosed in the publication.
  • the object of the present invention is to produce an improved plate heat exchanger of the type described in the pre-characterising clause of claim 1. This is achieved by the combination of characteristic features described in the characterising part of claim 1. Advantageous embodiments will be seen from the subordinate clauses.
  • figure 1 is a perspective view of a plate heat exchanger according to the invention.
  • Figures 2 and 3 show sections through the heat exchanger plates in two different positions, marked in figure 1.
  • Figure 4 shows a perspective view of an alternative embodiment of a plate heat exchanger according to the invention.
  • FIG 1 generally denotes a plate heat exchanger according to the invention, preferably a recuperator, with flow channels arranged between the plates.
  • every other channel is designed to receive the flow of a heat-emitting medium, in this case exhaust gases from a gas turbine.
  • the direction of flow for these is indicated in figure 1 by an arrow 2 and the person skilled in the art will appreciate that in order to control the exhaust gas flow a surrounding casing with connections for the inlet and outlet exhaust gas flows is required.
  • the remainder of the flow channels are designed to accommodate the flow of a heat-absorbing medium, in this case compressed air from the gas turbine compressor.
  • the inlet flow from the latter to the recuperator is indicated by an arrow 3 and the outlet flow by an arrow 4.
  • the flow 3 of heat-absorbing medium in the recuperator 1 passes via a manifold 8, which connects with the manifold 8 via inlet ports in each flow channel for the heat- absorbing medium. There is a corresponding connection via outlet ports in each flow channel to a manifold 9 for the flow 4 of heat-absorbing medium out of the recuperator.
  • the inlet ports are connected to section 6 of the through- flow channels, whereas the outlet ports are connected to section 7 of the through- flow channels.
  • an opening 9' In the plates from which the recuperator is constructed, an opening 9', with side wall 10 running around the edge 9" of the opening 9', is made in one section on two opposing sides a, b.
  • the said side wall is inclined somewhat inwards towards the opening 9'.
  • an interruption 10' In a section of the side wall 10 adjoining the section 7 there is an interruption 10'.
  • the side walls 10 With the side walls of the plates telescoped in one another as shown in figure 2 and joined pressure-tightly to one another, for example by soldering, the side walls 10 form the walls of the manifold 9 and the interruptions 10' form the outlet ports 10", which connect the manifold 9 to the through-flow channels for the heat-absorbing medium.
  • the said through- flow channels are denoted by 11, whilst the flow of the heat-absorbing medium is indicated by arrows 4'.
  • the through- flow channels for the heat-emitting medium are correspondingly indicated by 12.
  • the interruption 10' is preferably formed in the side wall 10 of each plate in such a way that, as shown diagrammatically in figure 3, the side wall section 10'" corresponding to the interruption 10' is bent so that it forms an angle x with the plane of the plates.
  • the side wall section 10'" is thereby made to form a guide for the flow of heat-absorbing medium through the inlet and outlet ports 10".
  • Figure 4 shows that the outer walls of the manifolds, as well as the short sides of the recuperator in an alternative embodiment, are bent outwards.
  • the splayed form gives increased strength, which improves the service life of the recuperator.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

The invention relates to an arrangement in a plate heat exchanger (1). Between the plates are flow channels, every other one of which is designed to receive the flow of a heat-emitting medium and every second one of which a heat-absorbing medium. The flow channels for one of the media, preferably the heat-absorbing medium, are connected in parallel via inlet and outlet ports to manifolds for the said medium. In one section on two opposing sides an opening (9') with a side wall (10) running round the edge (9'') of the opening and inclined somewhat inwards is made in the plates. The said side wall has an interruption (10') so that, with the side walls (10) of the plates telescoped in one another and connected pressure-tightly with one another by a joining process the side walls (10) form walls of the manifolds (8, 9) and the side wall interruptions (10') form inlet and outlet ports (10'') between the manifolds (8, 9) and the flow channels.

Description

Cross- and counter flow plate heat exchanger wherein he ports are provided with flanged, joined rims around part of their periphery.
The present invention relates to an arrangement in a plate heat exchanger according to the pre-characterising clause of claim 1.
A recuperator is already known from the E-C Parsons Government/Industry Meeting 2 Summary on "Development, Fabrication and Application of a Primary Surface Gas Turbine Recuperator" held in Washington, D.C. on 20-23 May 1985. The flow channels, which have cross-flow and counter- flow sections, connect here via the inlet and exhaust ports with separate manifolds arranged outside the actual set of heat exchanger plates and welded to the set of heat exchanger plates.
Integrating manifolds into the plates by providing the plates with openings with splayed flanges placed around the edge of the openings is already known from DE-A-29 23 944. When the said plates are joined together into a set of plates, the said flanges telescope into one another to form the walls of the manifolds and indentations in the flanges form inlet and outlet ports of the said manifolds. The object here was to produce a design that is resistant to mechanical stresses and easy to manufacture. No method of controlling the flow into and out of the manifolds is disclosed in the publication.
The object of the present invention is to produce an improved plate heat exchanger of the type described in the pre-characterising clause of claim 1. This is achieved by the combination of characteristic features described in the characterising part of claim 1. Advantageous embodiments will be seen from the subordinate clauses.
The invention will now be explained in more detail below with reference to the attached drawings in which figure 1 is a perspective view of a plate heat exchanger according to the invention. Figures 2 and 3 show sections through the heat exchanger plates in two different positions, marked in figure 1. Figure 4 shows a perspective view of an alternative embodiment of a plate heat exchanger according to the invention.
In figure 1, 1 generally denotes a plate heat exchanger according to the invention, preferably a recuperator, with flow channels arranged between the plates. Of the said channels every other channel is designed to receive the flow of a heat-emitting medium, in this case exhaust gases from a gas turbine. The direction of flow for these is indicated in figure 1 by an arrow 2 and the person skilled in the art will appreciate that in order to control the exhaust gas flow a surrounding casing with connections for the inlet and outlet exhaust gas flows is required. The remainder of the flow channels are designed to accommodate the flow of a heat-absorbing medium, in this case compressed air from the gas turbine compressor. The inlet flow from the latter to the recuperator is indicated by an arrow 3 and the outlet flow by an arrow 4.
In order to achieve high efficiency in the transfer of thermal energy from the heat- emitting medium to the heat-absorbing medium the flows will, of course, essentially be in opposite directions. This is the case in a section of the through-flow channels for the heat-absorbing medium, denoted by 5. 6 and 7 respectively indicate sections of the said through-flow channels in which the flows are not in opposite directions, but crossing one another.
The flow 3 of heat-absorbing medium in the recuperator 1 passes via a manifold 8, which connects with the manifold 8 via inlet ports in each flow channel for the heat- absorbing medium. There is a corresponding connection via outlet ports in each flow channel to a manifold 9 for the flow 4 of heat-absorbing medium out of the recuperator. As will be explained in more detail below, the inlet ports are connected to section 6 of the through- flow channels, whereas the outlet ports are connected to section 7 of the through- flow channels.
With reference to figures 2 and 3, which show sections A- A and B-B respectively of the recuperator in figure 1, the arrangement of the inlet and outlet ports and the manifolds 8, 9 will now be described in more detail. Since the conditions are analogous in the two manifolds, reference will only be made to the construction in connection with the manifold 9 and the said partial sections A-A and B-B illustrated in figures 2 and 3 respectively.
In the plates from which the recuperator is constructed, an opening 9', with side wall 10 running around the edge 9" of the opening 9', is made in one section on two opposing sides a, b. The said side wall is inclined somewhat inwards towards the opening 9'. In a section of the side wall 10 adjoining the section 7 there is an interruption 10'. With the side walls of the plates telescoped in one another as shown in figure 2 and joined pressure-tightly to one another, for example by soldering, the side walls 10 form the walls of the manifold 9 and the interruptions 10' form the outlet ports 10", which connect the manifold 9 to the through-flow channels for the heat-absorbing medium. In figures 2 and 3 the said through- flow channels are denoted by 11, whilst the flow of the heat-absorbing medium is indicated by arrows 4'. The through- flow channels for the heat-emitting medium are correspondingly indicated by 12.
The interruption 10' is preferably formed in the side wall 10 of each plate in such a way that, as shown diagrammatically in figure 3, the side wall section 10'" corresponding to the interruption 10' is bent so that it forms an angle x with the plane of the plates. The side wall section 10'" is thereby made to form a guide for the flow of heat-absorbing medium through the inlet and outlet ports 10".
Figure 4 shows that the outer walls of the manifolds, as well as the short sides of the recuperator in an alternative embodiment, are bent outwards. The splayed form gives increased strength, which improves the service life of the recuperator.
By arranging the manifolds 8, 9, inlet and outlet ports and the sections 5, 6 and 7 of media flows in opposite directions to one another or crossing one another according to the invention, a compact construction is thus achieved whilst making the recuperator highly efficient and easy to manufacture.

Claims

Claims
1. Arrangement in a plate heat exchanger (1), preferably a so-called recuperator, with flow channels (11, 12) arranged between the plates of the heat exchanger, of which every other channel is designed to receive the flow of a heat-emitting medium and every second channel the flow of a heat-absorbing medium in a predetermined direction, characterised by a combination of the following: for the heat-absorbing medium an opening (9'), with a side wall (10) running round the edge (9") of the opening and somewhat inclined towards the opening (9') is made in the plates in one section on two opposing sides (a,b), the said side wall having an interruption (10') so that with the side walls (10) of the plates telescoped in one another and connected pressure-tightly to one another by a joining process the side walls (10) form walls for two manifolds (8,9) incorporated into the heat exchanger and the side wall interruptions (10') form inlet and outlet ports (10") between the manifolds (8,9) and the flow channels (11,12) for the heat- absorbing medium,
a raised pattern in the plates forms three areas (5,6,7), a central area (5) in which the raised pattern causes the heat-absorbing medium to flow in essentially the opposite direction to the direction of flow of the heat-emitting medium and on both sides of the central area (5) an area (6 and 7) adjoining the inlet and outlet ports (10") respectively in which the direction of flow of the heat-absorbing medium is essentially across the direction of flow of the heat-absorbing medium
the inlet ports are designed to direct the flow of medium into the adjoining area.
2. Arrangement according to claim 1, characterised in that the interruption (10') in the side wall (10) of each plate is formed by bending a corresponding section (10'") of the side wall (10) so that it forms an angle (a) with the plate and at the same time constitutes a guide for the flow of heat-absorbing medium through the inlet and outlet ports (10").
3. Arrangement according to claim 1, characterised in that the edge (9") of the opening (9') facing the said opposite side and the said side are bent into a curve.
PCT/SE1998/000717 1997-04-22 1998-04-21 Cross- and counterflow plate heat exchanger wherein the ports are provided with flanged, joined rims around part of their periphery WO1998048230A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP54559998A JP2002501604A (en) 1997-04-22 1998-04-21 Cross-flow and countercurrent plate heat exchangers with each port having a flanged joining rim around its perimeter
EP98917925A EP0977972A1 (en) 1997-04-22 1998-04-21 Cross- and counterflow plate heat exchanger wherein the ports are provided with flanged, joined rims around part of their periphery
AU70956/98A AU7095698A (en) 1997-04-22 1998-04-21 Cross- and counterflow plate heat exchanger wherein the ports are provided with flanged, joined rims around part of their periphery
BR9808959-5A BR9808959A (en) 1997-04-22 1998-04-21 Arrangement on a plate heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE9701489-8 1997-04-22
SE9701489A SE511072C2 (en) 1997-04-22 1997-04-22 Cross and countercurrent plate heat exchangers where the gate edges are provided with joined flanges around part of the periphery

Publications (1)

Publication Number Publication Date
WO1998048230A1 true WO1998048230A1 (en) 1998-10-29

Family

ID=20406660

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1998/000717 WO1998048230A1 (en) 1997-04-22 1998-04-21 Cross- and counterflow plate heat exchanger wherein the ports are provided with flanged, joined rims around part of their periphery

Country Status (7)

Country Link
EP (1) EP0977972A1 (en)
JP (1) JP2002501604A (en)
KR (1) KR20010020122A (en)
AU (1) AU7095698A (en)
BR (1) BR9808959A (en)
SE (1) SE511072C2 (en)
WO (1) WO1998048230A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1365582A1 (en) 1998-03-04 2003-11-26 United Video Properties, Inc. Program guide system with targeted advertising
WO2005098334A1 (en) * 2004-04-08 2005-10-20 Swep International Ab A plate heat exchanger
US10094284B2 (en) 2014-08-22 2018-10-09 Mohawk Innovative Technology, Inc. High effectiveness low pressure drop heat exchanger

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CZ300999B6 (en) * 2007-09-27 2009-10-07 2 V V S. R. O. Counter-current recuperative heat exchanger

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE127970C1 (en) * 1950-01-01
GB1048122A (en) * 1966-08-12 1966-11-09 Nicholson Terence Peter Improvements in and relating to plate type heat exchangers
GB1062529A (en) * 1965-02-17 1967-03-22 Rosenblads Patenter Ab Heat exchangers of the plate type
US3460611A (en) * 1967-10-06 1969-08-12 Gen Motors Corp Heat exchanger of plate fin modules
US3759323A (en) * 1971-11-18 1973-09-18 Caterpillar Tractor Co C-flow stacked plate heat exchanger
DE2312456A1 (en) * 1972-03-28 1973-10-04 Brayton Cycle Improvement Ass GAS-COOLED PLATE-RIB HEAT EXCHANGER
US3805889A (en) * 1973-05-04 1974-04-23 United Aircraft Prod Plate type heat exchanger
DE2923944A1 (en) * 1978-06-14 1980-03-13 Piemontese Radiatori PLATE HEAT EXCHANGER
GB2107845A (en) * 1981-10-16 1983-05-05 Schmidt W Gmbh & Co Plate heat exchanger
GB2171507A (en) * 1985-02-27 1986-08-28 Trade & Industry The Secretary Counterflow heat exchangers
SE449399B (en) * 1978-10-26 1987-04-27 Garrett Corp DEVICE FOR AMPLIFYING THERMAL EXCHANGE WITH THIN PLATE AND HIGH PRESSURE AS WELL AS ASTADCOMMA REINFORCEMENT FOR COLLECTION PIPE SECTIONS BY CONTROLLER
DE3824073A1 (en) * 1988-07-15 1990-02-08 Laengerer & Reich Kuehler Oil cooler
DE4029096A1 (en) * 1989-09-14 1991-03-28 Susono Light Metal Co Modular heat exchanger block with flattened tubes - gripped between complementary edge recesses in transverse terminal plate components
EP0622600A1 (en) * 1993-04-24 1994-11-02 Knecht Filterwerke Gmbh Flat plate oil cooler assembly

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE127970C1 (en) * 1950-01-01
GB1062529A (en) * 1965-02-17 1967-03-22 Rosenblads Patenter Ab Heat exchangers of the plate type
GB1048122A (en) * 1966-08-12 1966-11-09 Nicholson Terence Peter Improvements in and relating to plate type heat exchangers
US3460611A (en) * 1967-10-06 1969-08-12 Gen Motors Corp Heat exchanger of plate fin modules
US3759323A (en) * 1971-11-18 1973-09-18 Caterpillar Tractor Co C-flow stacked plate heat exchanger
DE2312456A1 (en) * 1972-03-28 1973-10-04 Brayton Cycle Improvement Ass GAS-COOLED PLATE-RIB HEAT EXCHANGER
US3805889A (en) * 1973-05-04 1974-04-23 United Aircraft Prod Plate type heat exchanger
DE2923944A1 (en) * 1978-06-14 1980-03-13 Piemontese Radiatori PLATE HEAT EXCHANGER
SE449399B (en) * 1978-10-26 1987-04-27 Garrett Corp DEVICE FOR AMPLIFYING THERMAL EXCHANGE WITH THIN PLATE AND HIGH PRESSURE AS WELL AS ASTADCOMMA REINFORCEMENT FOR COLLECTION PIPE SECTIONS BY CONTROLLER
GB2107845A (en) * 1981-10-16 1983-05-05 Schmidt W Gmbh & Co Plate heat exchanger
GB2171507A (en) * 1985-02-27 1986-08-28 Trade & Industry The Secretary Counterflow heat exchangers
DE3824073A1 (en) * 1988-07-15 1990-02-08 Laengerer & Reich Kuehler Oil cooler
DE4029096A1 (en) * 1989-09-14 1991-03-28 Susono Light Metal Co Modular heat exchanger block with flattened tubes - gripped between complementary edge recesses in transverse terminal plate components
EP0622600A1 (en) * 1993-04-24 1994-11-02 Knecht Filterwerke Gmbh Flat plate oil cooler assembly

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1365582A1 (en) 1998-03-04 2003-11-26 United Video Properties, Inc. Program guide system with targeted advertising
WO2005098334A1 (en) * 2004-04-08 2005-10-20 Swep International Ab A plate heat exchanger
JP2007532852A (en) * 2004-04-08 2007-11-15 スウェップ インターナショナル アクティエボラーグ Plate heat exchanger
US9091494B2 (en) 2004-04-08 2015-07-28 Swep International Ab Plate heat exchanger
US10094284B2 (en) 2014-08-22 2018-10-09 Mohawk Innovative Technology, Inc. High effectiveness low pressure drop heat exchanger

Also Published As

Publication number Publication date
EP0977972A1 (en) 2000-02-09
SE9701489D0 (en) 1997-04-22
AU7095698A (en) 1998-11-13
JP2002501604A (en) 2002-01-15
SE511072C2 (en) 1999-08-02
KR20010020122A (en) 2001-03-15
BR9808959A (en) 2000-08-01
SE9701489L (en) 1998-10-23

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