EP0499883A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP0499883A1
EP0499883A1 EP92101884A EP92101884A EP0499883A1 EP 0499883 A1 EP0499883 A1 EP 0499883A1 EP 92101884 A EP92101884 A EP 92101884A EP 92101884 A EP92101884 A EP 92101884A EP 0499883 A1 EP0499883 A1 EP 0499883A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
space
sheet
wall
profiled sheet
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
EP92101884A
Other languages
German (de)
English (en)
Other versions
EP0499883B1 (fr
Inventor
Karl May
Hartmut Herm
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.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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 Siemens AG, Siemens Corp filed Critical Siemens AG
Publication of EP0499883A1 publication Critical patent/EP0499883A1/fr
Application granted granted Critical
Publication of EP0499883B1 publication Critical patent/EP0499883B1/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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F28D21/0005—Recuperative heat exchangers the heat being recuperated from exhaust gases for domestic or space-heating systems
    • F28D21/0008—Air heaters
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits

Definitions

  • the invention relates to a heat exchanger with a primary space for a primary medium and a secondary space for a secondary medium, which are separated from one another by a gas-tight, heat-conducting wall.
  • a heat exchanger is used to transfer thermal energy from a hot primary medium to a cold secondary medium.
  • the two media should not be mixed.
  • Various types of such a heat exchanger are known.
  • One of these embodiments provides a container in which a plurality of pipelines connected in parallel are arranged. Webs are arranged as spacers between adjacent tubes.
  • the parallel tubes are part of a secondary circuit that is passed gas-tight through the container wall.
  • the interior of the tubes forms the secondary space through which the heat-absorbing secondary medium flows.
  • the remaining interior of the container is part of a primary circuit. It forms the primary space through which a hot primary medium is conducted.
  • Such a heat exchanger can also be used in a smoldering furnace according to EP-PS 0 302 310. Thermal energy from hot flue gas is fed to the contents of a pyrolysis drum via a secondary medium.
  • the pipes carrying the secondary medium must consist of material that is resistant to high temperatures. Then the pipes may have to be covered with a refractory mass. To do this, the pipes must be provided with metal pins, between which a refractory ceramic mass is then held.
  • Heat exchangers in which the secondary space is formed by parallel pipes can be produced with great effort and high costs.
  • the pipes required are very expensive.
  • the connection of the pipes by means of webs requires complex and expensive welding work.
  • the invention has for its object to provide a heat exchanger that can be assembled quickly with simple, inexpensive means and which still works reliably.
  • possible different thermal expansions of different components of the heat exchanger should not result in material stresses or even destruction, e.g. of welds.
  • the secondary space is delimited by the wall and by an outer casing sheet spaced from this wall and in that the secondary space is divided into an inner and an outer sheet by a profiled sheet arranged between the wall and the outer casing sheet Subspace.
  • the arrangement of the profiled sheet forms tube-like channels which serve as a secondary space.
  • the heat exchanger according to the invention therefore only requires inexpensive profiled sheet metal for its manufacture, as well as cheaper non-profiled sheet for the outer cladding sheet.
  • parallel channels for the secondary medium are constructed according to the invention, the effect of which corresponds to the expensive parallel tubes connected by webs. This is true, although the channels are often not delimited from one another.
  • the arrangement of the profiled sheet in the space between the wall and the outer cladding sheet forms two partial spaces, each of which is divided into parallel channels by the profiled sheet.
  • the channels of the inner sub-space are directly delimited by the wall that separates the secondary space from the primary space. Therefore, the secondary medium flowing in the inner subspace is first heated. This heated secondary medium can then give off thermal energy via the profiled sheet to the secondary medium in the outer subspace.
  • the profiled sheet is arranged in the direction of the flow of the primary medium and profiled in a plane perpendicular to the direction of flow of the primary medium.
  • the secondary medium can then be rectified through the inner channels or can flow in countercurrent to the primary medium ensures good heat transfer through the heat-conducting wall between the primary space and the secondary space.
  • the profiled sheet is arranged, for example, so that it alternately touches the wall that delimits the primary space and the outer cladding sheet, thereby forming subspaces and the outer cladding sheet is held at the same distance from the wall.
  • the profiled sheet can be clamped. Welded connections are advantageously not required.
  • the advantage is achieved that the wall, the profiled plate and the outer jacket plate assume a fixed position in relation to one another in the radial direction or perpendicular to the direction of flow, while they are freely displaceable in the direction of the axis of the heat exchanger or in the direction of flow as a result of thermal expansions.
  • the profiled sheet is only attached to its upper section and hangs down freely between the wall and the outer cladding sheet. This has the advantage that different thermal expansion of the jacket sheet, the wall and the profiled sheet can have no effect on the rest of the construction. Different thermal expansions of rigidly connected components could lead to bending or even cracks.
  • the two subspaces of the secondary space are on one end, e.g. connected to each other at the foot of the heat exchanger.
  • the outer part On the other end, e.g. at the head end of the heat exchanger, the outer part is connected to a feed line and the inner part is connected to a discharge line.
  • the secondary medium allows the secondary medium to be guided through the secondary space, the secondary medium first in the outer partial space, e.g. in its channels, flows, then is deflected and then in the inner subspace, e.g. in its channels, flows back in the opposite direction.
  • the outer sub-space is connected to a supply line for the supply of the secondary medium.
  • the inner part of the room is connected to a drain to discharge the secondary medium.
  • the advantage is achieved that the same secondary medium is passed twice through the secondary space.
  • the opposite direction of the secondary medium achieved the advantage that the warmer medium flowing in the inner subspace can preheat the cooler medium flowing in the outer subspace via the profiled sheet.
  • the outer jacket plate on one end of the heat exchanger is gas-tightly connected to the wall of the primary space by a floor, and the profiled sheet ends at a distance from the floor.
  • the subspaces of the secondary space are connected to one another and a gas stream can advantageously be conducted around the end of the profiled sheet.
  • the gas passes from one subspace to the other, for example from the outer to the inner subspace. However, it is ensured that no gas escapes from the secondary space.
  • the floor mentioned is, for example, elastic. This has the advantage that stresses due to different thermal expansions of the wall and the outer jacket sheet are compensated. Thermal expansion of the profiled sheet metal cannot lead to stress, since it ends at a distance from the floor and only needs to be fastened in its upper part.
  • the head end of the heat exchanger for example the outer partial space of the secondary space is closed by a sealing plate extending between the outer jacket plate and the profiled plate.
  • a second collecting duct which is open to the inner partial space and is connected to a discharge line, is arranged on the end face of the closure plate.
  • a first collecting duct which is open to the outer part space, is arranged on the other side of the closure plate. This first collecting duct is connected to a feed line.
  • This construction ensures that the secondary medium in the area of an end face of the heat exchanger only reaches the outer part of the secondary space.
  • a distribution of the secondary medium to lower part spaces formed by the profiled sheet metal is ensured by the first collecting duct.
  • This first collecting duct connects all the outer lower part spaces with each other. The secondary medium can thus get from the supply line via the first collecting duct into each individual outer lower part space. Since no further path is possible through the sealing plate, the secondary medium flows in the same direction between the profiled plate and the outer jacket plate.
  • the direction of flow of the secondary medium is reversed on the floor, which connects the wall of the primary room to the outer casing sheet. It flows around the end of the profiled sheet and then flows between the profiled sheet and the wall of the primary space to the second collecting duct.
  • the inner lower part spaces of the secondary space are connected to one another by the second collecting duct. As a result, the secondary medium arriving from all inner lower part spaces is collected and can then be discharged via the drain.
  • the first collecting duct is placed on the outer surface of the casing plate, the outer casing plate having an opening continuously towards the first collecting duct.
  • This embodiment ensures that all outer lower part spaces are also connected to one another by the first collecting duct when the profiled sheet metal touches the jacket sheet.
  • the profiled sheet is only attached to its upper part hanging. It can be connected to the wall of the primary space via the second collecting duct. This provides a simple and effective construction and, since it is suspended like a curtain, the profiled sheet can expand downwards without tension or even cracks occurring in the material.
  • the profiled sheet has, for example, an angular profile.
  • the profile can be rectangular or trapezoidal. It can then lie flat against the outer jacket sheet and / or against the wall of the primary space.
  • the profile can also be triangular.
  • the profiled sheet can be a corrugated sheet with a round, in particular sinusoidal, profile.
  • a corrugated sheet is commercially available in the required form.
  • the advantage is achieved that the costs for the heat exchanger can be further reduced. This is due to the fact that corrugated iron can be purchased at a low price, which is significantly lower than the price of pipes.
  • the profiled sheet and / or the cladding sheet and / or other parts of the secondary space are made of steel, for example.
  • inexpensive steel is sufficient, since in the heat exchanger according to the invention the profiled sheet and the jacket sheet do not come into contact with the hot primary medium.
  • the hot primary medium only hits the wall of the primary room. While in a known embodiment with tubes and webs all parts come into contact with the hot primary medium and must therefore be made of heat-resistant material, the profiled sheet and the jacket sheet can consist of a simpler, less expensive steel in the heat exchanger according to the invention. This has the advantage that largely any commercially available corrugated sheet can be used. Only the wall of the primary room has to consist of high temperatures, eg 800 ° C resistant material.
  • the wall between the primary space and the secondary space can, for example, be pinned on its side facing the primary space and covered with a refractory ceramic material. This ensures that corrosion of the wall by hot primary medium containing pollutants is excluded.
  • the arrangement of the pins on the wall can be done by automatic welding, since a flat or only slightly curved surface must be pinned.
  • the primary medium is a hot flue gas
  • the secondary medium is a heating gas
  • the thermal energy of the hot flue gas can be used via the heating gas for heating or preheating a substance.
  • the primary medium is a hot flue gas from a combustion chamber of a smoldering furnace according to EP 0 302 310 and the secondary medium is a heating gas for heating a pyrolysis reactor of a smoldering furnace.
  • a heat exchanger according to the invention can therefore be usefully used in a smoldering-burning plant known as such. By working reliably and with simple means quickly, inexpensively and reliably The heat exchanger to be built can direct heat energy from the very hot flue gas into the pyrolysis reactor for preheating the material to be smoldered there.
  • a heat exchanger which can be operated with simple, commercially available and inexpensive means, e.g. Corrugated iron, is quick to set up and works reliably. In particular, its function cannot be impaired by thermal expansion of its material.
  • the heat exchanger 1 consists of a primary space 2 in which a hot primary medium, for example hot flue gas R, flows, and a secondary space 3 in which a heat-absorbing secondary medium, for example heating gas H for a pyrolysis reactor, flows.
  • the primary space 2 and the secondary space 3 are separated from one another by a wall 4.
  • this wall 4 forms a tube with a round cross section.
  • any other cross section is also possible.
  • the secondary space 3 is delimited by an outer cladding sheet 5 in addition to the wall 4.
  • the secondary space 3 therefore forms an annular space around the primary space 2.
  • the secondary space 3 is divided by a profiled sheet 6 into an inner partial space 3a and an outer partial space 3b.
  • the profiled sheet 6 can be a self-contained corrugated sheet, which alternately touches the wall 4 and the outer jacket sheet 5 in a sinusoidally curved manner.
  • the inner sub-space 3a and the outer sub-space 3b of the secondary space 3 are each subdivided into subspaces and the profiled one Sheet 6 serves as a spacer for the wall 4 and the outer jacket sheet 5.
  • An exchange of heating gas H may be possible between the respective lower part spaces, since the profiled sheet 6 is not gas-tightly connected to the wall 4 and the outer jacket sheet 5.
  • the two sub-rooms 3a and 3b are connected to one another on one end of the heat exchanger 1, in FIG. 1 on the lower end, and are closed off from the outside. This connection is provided by a floor 7.
  • the profiled sheet 6 ends at a distance above the floor 7. The heating gas H can therefore reach the inner partial space 3a or vice versa via this distance from the outer partial space 3b.
  • a feed line 8 is provided for feeding heating gas H into the secondary space 3. This opens into a first collecting duct 9 which surrounds the heat exchanger 1.
  • the first collecting duct 9 is open to the outer part space 3b.
  • the outer partial space 3b above the first collecting duct 9 is closed by a closure plate 10 arranged between the outer jacket plate 5 and the profiled plate 6. This ensures that the supplied heating gas H is always conducted downward in the outer subspace 3b.
  • the heating gas H is distributed through the first collecting duct 9 to the lower part spaces of the outer part space 3b. Between the bottom 7 and the lower end of the profiled sheet 6, the flow direction of the heating gas H is reversed and the heating gas H passes from the outer part space 3b into the inner part space 3a. There it flows upwards according to FIG. 1.
  • the second collecting duct 11 receives the heating gas H, which first flows from top to bottom in the outer subspace 3b and then from bottom to top in the inner subspace 3a.
  • a discharge line 12 for the heating gas H is connected to the second collecting duct 11.
  • the profiled sheet 6 is mechanically connected to the wall 4 by the second collecting duct 11.
  • the outer jacket plate 5 is connected to the profiled plate 6 by the first collecting duct 9 and the closure plate 10.
  • the closure plate 10 can also be connected directly to the second collecting duct 11 instead of the profiled plate 6 or even be part of the second collecting duct 11.
  • the hot primary medium flows in the primary space, for example flue gas R, the temperature of which can be above 800 ° C.
  • the primary space 2 like the secondary space 3, is connected to supply lines and discharge lines, not shown in FIG.
  • the wall 4 of the primary space 2 consists of a heat-resistant material. For example, it is pinned and covered with a refractory ceramic mass 14. All other parts of the heat exchanger 1 can consist of an inexpensive sheet, since they only come into contact with the cooler secondary medium, the heating gas H.
  • the heating gas H has, for example, the temperature 250 ° C. in the feed line 8 and the temperature 600 ° C. in the discharge line 12.
  • FIG. 2 shows a radial section through the secondary space 3 of the heat exchanger 1 according to FIG. 1.
  • the wall 4 of the primary space 2 is provided with pins 13 on the side of the primary space 2 and coated with a refractory ceramic mass 14.
  • the pins 13 enable the ceramic mass 14 to adhere well.
  • the secondary space 3 is delimited by the wall 4 and the outer jacket plate 5.
  • the profiled sheet 6 Through the profiled sheet 6, its profiling Is not visible in the sectional view of Figure 2, the secondary space 3 is divided into an inner part space 3a and an outer part space 3b.
  • the profiled sheet 6 is struck directly on the wall 4, directly on the outer jacket sheet 5 or at any location in between.
  • the profiled sheet 6 is profiled in a plane perpendicular to the plane of the drawing and perpendicular to the wall 4, the profile covering the entire width of the secondary space 3.
  • the profile of the profiled sheet 6 can be an angular profile or a round, for example sinusoidal profile, but also any other type of profile.
  • the outer jacket plate 5 is connected to the wall 4 by a base 7. This bottom 7 can be box-shaped. The bottom 7 can also be elastic to compensate for different thermal expansions.
  • the profiled sheet 6 ends in the secondary space 3 at a distance above the floor 7.
  • the outer partial space 3b is closed at the top by a closing plate 10. Below the closure plate 10, the outer sub-space 3b is connected to a feed line 8.
  • a first collecting duct 9 can be located between the feed line 8 and the outer partial space 3b. This connects the individual sub-spaces of the outer sub-space 3b formed by the profiling of the profiled sheet 6.
  • the inner compartment 3a is connected to a drain 12.
  • a second collecting duct 11 can be interposed, which first collects the secondary medium emerging from the sub-compartments of the inner sub-compartment 3a.
  • the profiled sheet 6 is exclusively attached to the second collecting duct 11. It hangs similarly to a curtain in the secondary space 3.
  • thermal expansions of the profiled sheet 6 can have no effects on other components of the heat exchanger 1.
  • the first collecting duct 9 and the outer jacket plate 5 are held on the profiled plate 6 via the closing plate 10.
  • the Primary medium in particular flue gas R
  • the secondary medium in particular heating gas H
  • the advantage is achieved that only inexpensive material such as corrugated sheet is required to build the secondary space 3 instead of expensive pipes and that thermal expansion of the components of the heat exchanger 1 remain without affecting its stability.

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  • 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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Power Steering Mechanism (AREA)
  • Gasification And Melting Of Waste (AREA)
EP92101884A 1991-02-18 1992-02-05 Echangeur de chaleur Expired - Lifetime EP0499883B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4104959 1991-02-18
DE4104959A DE4104959A1 (de) 1991-02-18 1991-02-18 Waermetauscher

Publications (2)

Publication Number Publication Date
EP0499883A1 true EP0499883A1 (fr) 1992-08-26
EP0499883B1 EP0499883B1 (fr) 1994-04-20

Family

ID=6425279

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92101884A Expired - Lifetime EP0499883B1 (fr) 1991-02-18 1992-02-05 Echangeur de chaleur

Country Status (11)

Country Link
US (1) US5215144A (fr)
EP (1) EP0499883B1 (fr)
JP (1) JPH0579777A (fr)
AT (1) ATE104762T1 (fr)
CZ (1) CZ283100B6 (fr)
DE (2) DE4104959A1 (fr)
DK (1) DK0499883T3 (fr)
ES (1) ES2051603T3 (fr)
HU (1) HU215992B (fr)
PL (1) PL293465A1 (fr)
RU (1) RU2070700C1 (fr)

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Publication number Priority date Publication date Assignee Title
US5466603A (en) * 1994-02-15 1995-11-14 Meehan; Brian W. Temperature regulated hybridization chamber
SE507479C2 (sv) * 1995-11-17 1998-06-08 Flygt Ab Itt Kylanordning för en omrörare
US5684346A (en) * 1995-11-17 1997-11-04 Itt Flygt Ab Cooling device
DE19617916B4 (de) 1996-05-03 2007-02-01 Airbus Deutschland Gmbh Verdampfer zum Verdampfen eines tiefkalten flüssigen Mediums
US6438936B1 (en) 2000-05-16 2002-08-27 Elliott Energy Systems, Inc. Recuperator for use with turbine/turbo-alternator
DE10129099A1 (de) * 2001-06-16 2002-12-19 Ballard Power Systems Katalytische Beschichtung von strukturierten Wärmetauscherblechen
FR2872264B1 (fr) * 2004-06-29 2007-03-09 Solvay Sa Sa Belge Recipient a double paroi et procede pour le fabriquer
EP1657156A1 (fr) * 2004-11-16 2006-05-17 Saab Ab Un appareil d'entrée d'air pour un moteur d'avion
US20080128345A1 (en) * 2006-11-30 2008-06-05 Sotiriades Aleko D Unified Oil Filter and Cooler
US20150083366A1 (en) * 2011-03-11 2015-03-26 Janis Zakis Multi-surface heat exchange with vacuum capability and magnetic scrapers
KR101475398B1 (ko) * 2013-04-25 2014-12-22 주식회사 두발 보일러 열교환용 혼합관
US9897398B2 (en) 2013-05-07 2018-02-20 United Technologies Corporation Extreme environment heat exchanger
GB201513415D0 (en) * 2015-07-30 2015-09-16 Senior Uk Ltd Finned coaxial cooler
US10995998B2 (en) * 2015-07-30 2021-05-04 Senior Uk Limited Finned coaxial cooler
US11988147B2 (en) * 2022-07-07 2024-05-21 General Electric Company Heat exchanger for a hydrogen fuel delivery system

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DE814159C (de) * 1949-07-08 1951-09-20 Otto H Dr-Ing E H Hartmann Waermeaustauscher
FR1210108A (fr) * 1957-08-30 1960-03-07 Air Exchangers Ltd Foyer et échangeur pour le chauffage des gaz
DE1401851A1 (de) * 1960-02-08 1968-10-24 Brown Fintube Company In einen Rauchgaszug einhaengbarer Rekuperativ-Waermeaustauscher
GB2065861A (en) * 1979-12-14 1981-07-01 Aerco Int Inc Countercurrent heat exchanger with a dimpled membrane

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DE839806C (de) * 1949-08-02 1952-05-26 Otto H Dr-Ing E H Hartmann Sternfoermiges Faltenrohr als Einsatzrohr fuer Waermeaustauscher
US2641451A (en) * 1950-11-04 1953-06-09 Edward W Kaiser Heat exchanger
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EP0083379A1 (fr) * 1981-12-31 1983-07-13 Emil Kress Echangeur de chaleur
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Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE814159C (de) * 1949-07-08 1951-09-20 Otto H Dr-Ing E H Hartmann Waermeaustauscher
FR1210108A (fr) * 1957-08-30 1960-03-07 Air Exchangers Ltd Foyer et échangeur pour le chauffage des gaz
DE1401851A1 (de) * 1960-02-08 1968-10-24 Brown Fintube Company In einen Rauchgaszug einhaengbarer Rekuperativ-Waermeaustauscher
GB2065861A (en) * 1979-12-14 1981-07-01 Aerco Int Inc Countercurrent heat exchanger with a dimpled membrane

Also Published As

Publication number Publication date
PL293465A1 (en) 1992-08-24
RU2070700C1 (ru) 1996-12-20
DE59200120D1 (de) 1994-05-26
CS46092A3 (en) 1992-11-18
HU215992B (hu) 1999-03-29
US5215144A (en) 1993-06-01
CZ283100B6 (cs) 1998-01-14
HU9200468D0 (en) 1992-04-28
ATE104762T1 (de) 1994-05-15
ES2051603T3 (es) 1994-06-16
JPH0579777A (ja) 1993-03-30
DE4104959A1 (de) 1992-08-20
DK0499883T3 (da) 1994-09-12
EP0499883B1 (fr) 1994-04-20
HUT61096A (en) 1992-11-30

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