EP2684001B1 - Échangeur de chaleur pour installation mobile de foyer à combustible solide - Google Patents

Échangeur de chaleur pour installation mobile de foyer à combustible solide Download PDF

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Publication number
EP2684001B1
EP2684001B1 EP12714834.4A EP12714834A EP2684001B1 EP 2684001 B1 EP2684001 B1 EP 2684001B1 EP 12714834 A EP12714834 A EP 12714834A EP 2684001 B1 EP2684001 B1 EP 2684001B1
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EP
European Patent Office
Prior art keywords
gas
tubes
plant according
heat exchanger
corrugated sheets
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.)
Active
Application number
EP12714834.4A
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German (de)
English (en)
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EP2684001A1 (fr
Inventor
Johannes LANDRICHINGER
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Lasco Heutechnik GmbH
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Lasco Heutechnik GmbH
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Publication of EP2684001A1 publication Critical patent/EP2684001A1/fr
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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H3/00—Air heaters
    • F24H3/02—Air heaters with forced circulation
    • F24H3/06—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators
    • F24H3/08—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by tubes
    • F24H3/088—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by tubes using solid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H3/00—Air heaters
    • F24H3/02—Air heaters with forced circulation
    • F24H3/06—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators
    • F24H3/10—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by plates
    • F24H3/107—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by plates using solid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/0052—Details for air heaters
    • F24H9/0057—Guiding means
    • F24H9/0063—Guiding means in air channels
    • 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
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • 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
    • F28D9/0025—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 being formed by zig-zag bend plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/04—Reinforcing means for conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/30—Safety or protection arrangements; Arrangements for preventing malfunction for preventing vibrations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/06—Fastening; Joining by welding
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/12—Fastening; Joining by methods involving deformation of the elements

Definitions

  • the invention relates to a mobile wood combustion system with a heat exchanger according to the preamble of claim 1.
  • FR 2 553 182 discloses such a wood combustion plant.
  • Mobile solid fuel firing systems are used to generate large amounts of heat for a limited period of time in one location. Possible applications are, for example, the generation of heat for drying hay, the heating of a building or a large tent or the short-term provision of heat for industrial processes. For this purpose, the solid fuel firing system is driven to the site, parked there and put into operation.
  • a solid fuel container may be connected via a fuel delivery mechanism to a combustor of the solid fuel firing system.
  • the solid fuel is burned in the combustion chamber, wherein the heat released to a heat transfer medium, usually water, is fed, which is guided around the combustion chamber for receiving the heat.
  • a heat exchanger transfers the heat to the place of use.
  • the wall comprises a plurality of interconnected corrugated sheets extending between the two gas passages.
  • the invention is based on the consideration that it is important for mobile use of the solid fuel combustion system that it is as light as possible.
  • a conventional heat transfer from the combustion chamber or the flue gas to water is disadvantageous because here the water must be carried as a heat transfer in the furnace and thus contributes to its weight.
  • the heat exchanger has a hot gas connection and a cooling gas connection, so that the heat is transferred directly from the hot gas to the cooling gas.
  • the wall for heat transfer should therefore be made of a very heat-resistant and chemically resistant steel in order to avoid a strong oxidation of the wall.
  • Particularly suitable materials are very expensive.
  • a cost-saving measure is to provide cheaper materials in a thicker wall thickness. These too satisfy the requirement of sufficient Longevity.
  • a thicker wall entails the considerable disadvantage of high weight when used in the mobile solid fuel firing system.
  • the invention is based on the further consideration that noble steels are much cheaper available in sheets than in tube form.
  • the use of sheet metal as the wall of the heat exchanger can therefore be used in a cost-effective framework on noble steels, whereby a thin design of the wall and thus a weight-saving design of the heat exchanger is possible.
  • the disadvantage of higher costs is therefore offset by the advantage of weight savings, which is of considerable importance in mobile solid fuel burning systems.
  • a large heat transfer area per weight can be achieved with metal sheets, so that a corrugated metal heat exchanger with the same transfer capacity and wall thickness is lighter than a tube bundle heat exchanger.
  • the furnace is expediently a wood combustion plant for use with, for example, wood chips.
  • the hot gas connection can serve as a flue gas connection, through which the hot flue gas produced in the combustion chamber of the combustion system is guided.
  • the cooling gas connection may be an ambient air connection through which ambient air is introduced for cooling the wall.
  • the corrugated sheets may have flat surfaces or be executed purely with curved surfaces. They may be curved, wavy or edged, e.g. with trapezoidal wave, rectangular wave, triangular wave or other edged shape. Even rounded edges are possible and advantageous.
  • the outer gas guide is expediently designed so that the outer gas flow guided in it flows around the inner gas guide.
  • the internal gas guide is suitably arranged to shield the internal gas carried therein from the environment, at least until it reaches a predetermined state, e.g. has cooled sufficiently. Further, it is advantageous if the outer gas guide is applied at least predominantly transversely to the inner gas guide. As a result, a uniform cooling of the inner gas guide can be achieved.
  • the heat exchanger according to the invention is particularly suitable for use in a mobile solid fuel firing system, but its use is not limited to a mobile firing system, since its advantages can also be used in stationary furnaces.
  • the corrugated sheets are each connected in pairs in such a way that convex inner surface portions of the corrugated sheets each pairwise and concave inner surface portions of the corrugated sheets face each pair.
  • a pair of corrugated sheets may form a number of tubes forming at least part of the inner gas guide so that the inner gas guide passes through the tubes thus formed.
  • the corrugated plate pairs are connected to each other at the convex inner surface portions.
  • a connection can be achieved by welding, e.g. with a roll seam welding process.
  • the corrugated sheets of the pair of corrugated sheets can in this case be laid on one another such that the convex inner surface portions touch each other in a straight line so that a good directional guidance is created within the inner gas guide.
  • the concave inner surface sections in pairs form a tube. This also makes it possible to achieve a particularly good flow guidance in the internal gas guidance.
  • corrugated sheets are expediently placed on one another in such a way that the tubes are formed in such a way that their inner spaces are substantially separated from one another in the region of their parallel course, at least by the sheets resting one on top of the other. This also allows a particularly good flow guidance of the inner gas guide can be achieved.
  • the inner gas duct runs as a hot gas duct through the tubes.
  • the tubes are advantageously connected to the hot gas connection so that flows through this flowing hot gas and through the tubes.
  • the Internal gas guide may be a flue gas duct and the outer gas duct may be an ambient air duct.
  • a further advantageous embodiment of the invention provides that in each case two pairs of plates are arranged to each other such that they form between them a wavy flow area as part of the outer gas guide. It can be a good mixing of the externally guided gas and thus a good heat transfer between hot gas and cold gas can be achieved.
  • several tubes are formed between pairs of plates, wherein the wave-shaped throughflow region can be traversed perpendicularly to the longitudinal direction of the tubes, in particular can flow through in a wave-like manner.
  • a compact design of the heat exchanger can be achieved if between two pairs of sheets a third pair of sheets is arranged such that convex outer surface portions of the third pair of sheets come to lie between concave outer surface portions of the two surrounding pairs.
  • the problem may arise that at least one of the gas guides from the gas guide section is short, which is not conducive to good heat transfer.
  • This problem can be solved if the corrugated sheets form a plurality of parallel tubes and the outer gas guide crosses at least some of the tubes on the outside, is deflected in their direction and these tubes crosses a second outside. Through this deflection, a long contact of external and internal flow over the wall formed and so on good heat transfer can be achieved.
  • the crossing is expediently carried out at an angle of at least 70 degrees, in particular of at least 80 degrees.
  • the corrugated sheets form a plurality of parallel tubes and the outer gas guide is guided by means of at least two baffles S-shaped through the corrugated sheets, so that it extends transversely and parallel to the tubes.
  • This also allows a long combination of inner and outer gas guide formed and a good heat transfer can be achieved.
  • a parallel or transverse guide to the tube longitudinal direction understood, with a transverse guide is understood at an angle of at least 70 degrees, suitably at least 80 degrees and in particular perpendicular to the tube longitudinal direction.
  • the corrugated sheets form a plurality of parallel inner tubes, which are divided into two groups, each having a plurality of separate outer gas channels, between which a mixing section is arranged, in which open the outer gas channels.
  • this mixing section expediently also the baffles, whereby a simple and stable construction of both the baffles and the heat exchanger is achievable.
  • the inner gas guide is guided successively through the two groups of the inner tubes, which are arranged in particular parallel to one another. This allows a long gas flow in a confined space can be achieved.
  • Cool outer gas initially encounters relatively cool inner gas and later hotter outer gas meets hotter inner gas, whereby the heat content of already cooled hot gas is still effectively used to preheat the cooling gas.
  • the corrugated sheets each have at least one end of a collar. This can be used advantageously for fastening the corrugated sheets to each other - directly or indirectly.
  • the attachment to each other may be via a retaining means, e.g. a head plate, a fullblech or the like.
  • the attachment can be done by welding, bolting, gluing, riveting or other methods.
  • the corrugated sheets are formed at least one end to a collar, the collar is thus formed from the corrugated metal.
  • the corrugated sheet can be bent to the collar. It is also possible to first make the collar and then introduce the corrugation in the corrugated sheet.
  • the collars are arranged transversely to the orientation of the waves. Under cross will be understood in the following an angle between 70 ° and 110 °.
  • the orientation of the waves is parallel to the troughs or mountains.
  • the holding means is a sheet transverse orientation of the shafts, and the collar are aligned flat parallel to the sheet.
  • the collar can be easily and reliably attached to the holding means.
  • the collars are expediently applied flat to the holding means, directly or indirectly via one or more intermediate layers.
  • a particularly strong attachment can be achieved when the collars are clamped between the holding means and a counter-element arranged between the corrugated sheets.
  • the clamping is advantageously carried out by screwing or riveting.
  • the counter element extends in particular between the corrugated sheets. For this, it can be tortuous in waveform.
  • the invention is directed to a solid fuel combustion system with a combustion chamber, a heat exchanger as described above and a combustion chamber connecting the combustion chamber with the inner gas connection flue gas guide. It can thereby be a thermally and mechanically stable unit, combined with a low weight, formed within the solid fuel burning plant.
  • the solid fuel firing system includes an ambient air inlet, a warm air outlet, an ambient air channel connecting the ambient air inlet to the outer gas port of the heat exchanger, and a hot air duct connecting an outer gas outlet of the heat exchanger to the hot air outlet.
  • Ambient air can be brought into a heat contact with flue gas directly in the heat exchanger, whereby a good and effective heating of ambient air can be generated even in a high volume, which is particularly suitable for heating large rooms or large volumes of product.
  • the invention is directed to a mobile hay drying plant with a transportable frame in which a solid fuel burning plant is arranged as described above.
  • the frame further comprises a solid fuel container, whereby a delivery of solid fuel to a combustion chamber of the furnace can be kept simple.
  • Fig. 1 shows a mobile solid fuel combustion system 2 - hereinafter also simplified only referred to as combustion plant 2 - with a rated power of 250 kW and a solid fuel storage 4 in a schematic representation.
  • the solid fuel storage 4 is mobile, so carried portable.
  • both the solid fuel storage 4 and the furnace 2 each with only one indicated schematically Means of transport 6, 8 provided, by means of which the two elements 2, 4 can each be raised, for example by a forklift.
  • the transport means 6, 8 comprise a stable frame which holds the remaining components of the respective element 2, 4.
  • the solid fuel storage 4 is connected via a connection 10 with the furnace 2, which contains a joint or other angle compensation means, so that any unevenness in the installation of the two elements 2, 4 can be compensated.
  • the connection 10 is additionally provided with a height compensation means for adapting a discharge unit 12.
  • the discharge unit 12 is, for example, a screw conveyor and serves for transporting solid fuel located in the solid fuel storage 4, for example wood chips, to the firing installation 2.
  • the furnace 2 To operate the furnace 2, this is driven to its place of use, for example, on a truck and parked there on a floor.
  • the solid fuel storage 4 is also driven to the site and parked next to the furnace 2. Subsequently, the two elements 2, 4 are connected to each other via the terminal 10. A positional adjustment of the two elements 2, 4 to each other is usually not necessary because the terminal 10 sufficiently compensates for unevenness of the soil.
  • the solid fuel such as wood chips, pellets or other suitable solid fuel, can be filled into the solid fuel storage 4, for example with a wheel loader.
  • the solid fuel is conveyed via the conveyor 12 and the connection 10 to the furnace 2.
  • the furnace 2 and the solid fuel storage 4 are in a contiguous Frame stored and transportable together. This solution is particularly advantageous for systems up to 500 kW, since the transport is facilitated and the connection of the two elements 2, 4 together.
  • the solid fuel After passing through a burn back 14 the solid fuel passes through another carried out as a Stocker auger conveyor 16 into the combustion chamber 18 in the furnace 2. There, the solid fuel is ignited and burned over time to ash. The resulting during combustion hot flue gases are fed to a first heat exchanger 20. There, they are cooled from about 1200 ° C to below 1000 ° C: The thus cooled flue gases are then fed to a second heat exchanger 22 and cooled there to about 150 ° C. By the two heat exchangers 20, 22 ambient air is blown to cool them. This is heated in the heat exchangers 20, 22 and is now available for further use, for example for drying hay.
  • the exhaust gases cooled in the heat exchangers 20, 22 are fed to a spark separator 24, for example a cyclone separator. Larger systems may provide multiple cyclone separators that operate in parallel. Deposited ash is collected in an ash container 26 and the purified waste gases are led up out of the furnace 2.
  • Fig. 2 shows the large heat exchanger 22 in a perspective view obliquely from above.
  • the representation of the largest part of a housing 28 has been dispensed with, so that the view becomes free on the heat exchanging wall 30 between an inner gas guide 32 and an outer gas guide 34, which in Fig. 2 are indicated by thin or thick arrows.
  • the heat exchanger 22 is a corrugated iron heat exchanger, the wall 30 of corrugated metal sheets is manufactured and which is described in more detail below.
  • the heat exchanger 22 includes a flue gas inlet 36, which is designed in the embodiment shown as a distribution box for distributing the hot gas to many tubes.
  • a flue gas inlet 36 Into the flue gas inlet 36 are sucked through connections 38 to the upstream small heat exchanger 20 heated to between 900 degrees Celsius and 1000 ° C flue gases, as indicated by the first and down arrow of the inner gas guide 32.
  • the hot flue gases pass through a first train 40, reach therefrom a deflection space 42, are deflected there by 180 degrees up again, pass through the second train 44 and from there reach a collection box 46.
  • the cooled hot gases leave the heat exchanger 22 by a hot gas discharge 48, through which they are routed to the spark separator 24..
  • accumulated ash is fed through an ash removal 50 to the ash container 26.
  • the outer gas guide 34 extends in an S-shape around the wall 30 of the two trains 40, 44, as in FIG Fig. 3 is shown.
  • Fig. 3 shows the two trains 40, 44 with the indicated housing 28 and the outer gas guide 34.
  • air is admitted through an ambient air inlet 54 with a blower 60.
  • a cooling gas connection 58 the ambient air is guided in an ambient air guide 62 to the heat exchanger 22, ie to the wall 30 of the second train 44.
  • the housing 28, the wall 30 and two deflection means 64, 66 form the outer gas guide 34 and thus give the air flow of the ambient air the heat exchanger 22 ago.
  • the ambient air is passed as cooling air first around the wall 30 of the second train 44, then around the wall 30 of the first train 40, then around the wall 30 of the second train 44 and finally around the wall 30 of the first train 40 and leaves the heat exchanger 22 as hot air in a hot air duct 68. It enters the hot air duct 68 through the first heat exchanger 20 and is blown out through the hot air outlet 72 of the furnace 2.
  • the deflection means 64, 66 are designed in the form of intermediate plates, wherein each intermediate plate is guided around all plate pairs 76 of only one train 40, 44.
  • the intermediate plates serve to guide the ambient air or the outer gas in an S-arc through the heat exchanger 22.
  • Fig. 4 shows the wall 30 of the two trains 40, 44, which are designed in the form of many corrugated sheets 74.
  • Two plate plates 76 forming corrugated sheets 74 are in Fig. 5 illustrated by way of example in perspective.
  • Three such plate pairs 76 of the first train 40 are shown schematically in FIG Fig. 6 shown in a sectional view.
  • the corrugated sheets 74 are welded into a head plate 78, which closes the wall 30 of the heat exchanger 22 upwards.
  • the top plate 78 thus contains the outer contours of the plate pairs 76 of the two trains 40, 44 corresponding openings into which the plate pairs 76 are inserted. With one fillet weld each, the corrugated sheets 74 or plate pairs 76 are welded to the top plate 78.
  • the corrugated sheet 74 of the plate pairs 76 is made of a stainless steel, suitably a stainless steel, and has a wall thickness of 0.5 mm.
  • the thickness of the top plate 78 which is made of structural steel, 5 mm. Also possible is stainless steel, which then thinner can be executed. Accordingly, the plate pairs 76 are welded to a base plate 80 of the heat exchanger 22.
  • the two deflection means 64, 66 which are also manufactured as sheets, with the corresponding openings for the passage of the plate pairs 76, can be welded in the same way, with a cohesive stapling of the deflecting plates 64, 66 on the plate pairs 76 already sufficient.
  • the plate pairs 76 consist of two corrugated sheets 74 which are welded together at their two longitudinal edges 82.
  • the corrugated sheets 74 are deep-drawn stainless steel sheets, which are placed on top of each other and joined together to form a plurality of at least substantially longitudinal chambers in the form of tubes 84.
  • the corrugation of the corrugated sheets 74 consists per wave phase essentially of two approximately 110 degree wide arcuate segments 86, 88, which form an S-shaped wave phase.
  • the cross section of the longitudinal chambers or tubes 84 is substantially circular, bounded above and below by the two circular segments 86, and laterally deviating slightly from the circular arc shape, wherein a circle with the radius of 20 mm can be placed in the cross section, with the two arcuate segments 86 coincides.
  • the segments 88 touch each other in their central axis, which is parallel to the longitudinal axis of the tubes 84 and plate pairs 76. Due to the juxtaposition of the segments 88, the interior space of the tubes 84 is at least substantially separated from one another in regions of the parallel course. Opposite the segments 88 are convex inner surface portions which are joined together by welding. The outer segments 86 form concave inner surface portions that face each other in pairs and that form the major boundary of the tubes 84.
  • the middle plate pair 76 is arranged between the two plate pairs 76 shown outside such that convex outer surface portions of the segments 86 of the middle plate pair 76 come to rest between concave outer surface portions of the segments 88 of the two surrounding plate pairs 76.
  • the contacting segments 88 need not be continuous or not welded together. To promote the stability of the plate pairs 76, however, it is beneficial if the segments 88 are each partially welded along their central axis, wherein a welding between 10% and 50% of the total length of the central axis, advantageously distributed over many small welding distances, is conducive.
  • Per train 40, 44 is the heat exchanger 22 with several such, as in Fig. 5 provided plate pairs 76 which are positioned vertically side by side. Depending on the size and design of the vertical heat exchanger 22, the corrugated sheets 74 and plate pairs 76 can be welded in any number at both ends of the tubes 84 in the top and bottom plates 78, 80. Between the plate pairs 76 is thereby - as in Fig. 6 can be seen - the outer gas guide 34 is formed. The gas space 92 between the plate pairs 76 here is designed so that it assumes a waveform transverse to the longitudinal direction 90 of the tubes 84 and always has substantially the same thickness. The waveguide creates an intensive contact of the cooling gas with the wall 30, so that an intense heat transfer from the inner gas to the outer gas takes place.
  • the thickness of the gas space 92 or the spacing of the plate pairs 76 from each other it is important to ensure that the distance is not greater than half the radius of the tubes 84, otherwise the cooling air or the external gas must not extend the waves and there is a risk the cooling air forms air cushions in the bulges of the waves and the cooling air flows straight through between the plate pairs 76 without complete passage through the waves and comes only into limited contact with the plate pairs 76 or the wall 30.
  • the guidance of the gases can - depending on the application - be completely reversed, so that hot gas between the plate pairs 76 in the outer gas guide 34 and cooling gas in the tubes 84 is guided in the inner gas guide.
  • corrugated sheet metal as the wall 30 between the outer gas guide 34 and the inner gas guide 32 can be dispensed with tubes of a tube bundle heat exchanger.
  • the foot plate 80 is in Fig. 7 shown in a perspective view, so that the openings 94 in the base plate 80 for connection with the plate pairs 76 are visible.
  • the deflection means 64 is in a plan view in Fig. 8 shown. Also there, the openings 94 are visible.
  • the deflection means 66 is formed analogously to the deflection means 64, but the openings are shorter by one wave phase than the openings 94 of the deflection means 64.
  • the pairs of plates 76 of the heat exchanger 22 are divided into two groups: the plate pairs 76 of the first train 40 and the plate pairs 76 of the second train 44. As seen in FIG Fig. 4 As can be seen, the plate pairs 76 of the first train 40 are spaced from those of the second train by an area 96 without plates. This area 96 serves to facilitate the introduction of flue gas into the heat exchanger 22, since the introduction into the distribution box and the discharge through the collection box 46 is spatially separated and one or two baffles are arranged in the region 46, which thus do not cut tube openings.
  • the region 96 has yet another advantage: Especially in the upper region of the two trains 40, 44 there is a considerable difference in temperature of the walls 30 of the two trains 40, 44. While the wall 30 of the first train 40 is at about 800 ° C. in the upper area , The temperature of the wall in the upper part of the second train 44 is only about 200 ° C. Therefore, there is a different temperature expansion, due to the thermal expansion of the corrugated sheet material, in the two trains 40, 44 instead. By arranging as separate plate pairs 76 in the trains 40, 44 temperature stresses in the material of the corrugated sheets 74 can be kept low.
  • the arrangement of the outer gas guide 34 is such that it runs in a countercurrent flow to the inner gas guide 32. Namely, the outer gas guide 34 is arranged to first flow around the wall 30 of the cooler second train, and finally to the hottest area of the first train 40. In this way, efficient utilization of the heat of the flue gas is achieved. In the first heat exchanger 20, the hot air is reheated again.
  • Fig. 9 shows an alternative outer gas guide 98.
  • the air to be heated flows first on the entire length of the second train 44 in this, is then not deflected below but laterally of the two trains 40, 44 by about 180 degrees and then flows through the wall 30 of the first train 40. In this way, a countercurrent flow to the internal gas guide 32 is achieved.
  • Such an outer gas guide 98 is particularly suitable for very high volume flows of air to be heated, since in each case the entire train 40, 44 can be used forstructuregasumströmung in only one direction.
  • FIG Fig. 10 An alternative plate pair 100 of two corrugated sheets 74 is shown in FIG Fig. 10 shown.
  • the two corrugated sheets 74 are not connected in antiphase, as in the in Fig. 5 shown example of the plate pair 76, but in-phase and are thus everywhere parallel to each other. It arises between corrugated sheets 74, a single longitudinal channel 102 which extends over the entire width of the corrugated sheets 74. Laterally, the two corrugated sheets 74 are welded again, so that the inner gas channel is closed on both sides and is only open at the front and rear, as out Fig. 11 can be seen.
  • Fig. 11 shows the plate pair 100 in a perspective view obliquely from above.
  • the two corrugated sheets 74 are interconnected along their sides by means of two strip-shaped connector sheets. Also, a folded edge of the two corrugated sheets 74 to each other or one of the corrugated sheets 74 to the other is possible, so that the connector plates omitted.
  • Fig. 12 an alternative to the longitudinal edge 82 longitudinal edge 104 is shown. At least one of the two corrugated sheets 74 is bent around the other along the longitudinal edge 104, so that a rounded flow edge is formed.
  • the two corrugated sheets 74 are provided on one longitudinal side with a wider unwoven sheet surface.
  • the two identically shaped corrugated sheets 74 are placed on each other to produce a pair of plates 76 so that each of the corrugated sheets 64 projects beyond the other on one longitudinal side with the non-corrugated area.
  • the two corrugated sheets 74 welded to two parallel welds 106 which extend along the entire longitudinal edge 104.
  • a part of the flat portion of the protruding corrugated sheet 74 is folded 180 degrees, as in FIG Fig. 12 is shown.
  • the resulting laminated core of three sheet metal layers with a third weld 108 is completely welded through, also along the entire longitudinal edge 104 and in particular directly to the sheet edge, so that the wave sheets 74 are sealed at the edge sealed together and, for example, run no pickling between the sheets 74 can.
  • This longitudinal edge 104 has two advantages. First, it forms a very secure composite of the corrugated sheets 74, which remains gas-tight even under extreme mechanical and thermal stress. The mechanical load is absorbed not only by the welds 106, 108, but also by supporting the corrugated sheets 74 to each other. A leakage of hot flue gases can be safely avoided. Second, the longitudinal edge 104 forms a rounded leading edge. If the outside gases flow very quickly into the heat exchanger 22, a sharp longitudinal edge 82 can lead to vibrations and thus to an undesirable noise. By the round longitudinal edge 104 flapping and swinging is avoided.
  • FIG. 13 An alternative heat exchanger 110 is in Fig. 13 shown. It is the same except for the following details, as the heat exchanger 22: Especially at large firing capacities, a non-deflected outer gas guide 112 may be advantageous in order to be able to blow very large volumes of air per time through the heat exchanger 110.
  • the deflection means 64, 66 can be omitted, so that the outer gas guide 112 is guided in a straight line through the heat exchanger 110, by all trains 40, 44th
  • the heat exchangers 22, 110 are stationary heat exchangers, the inner gas guide 32 runs vertically through the trains 40, 44. Also possible is the use of corrugated metal pairs 76, 100 in a horizontal heat exchanger in which the inner gas duct runs horizontally through the trains. Also oblique arrangements are conceivable.
  • the connection between the corrugated sheets 74 and the top plate 78 and / or the foot plate 80 is in Fig. 14 shown.
  • the corrugated sheets 74 are brought with their upper or lower edge directly to the top plate 78 and foot plate 80 and welded thereto. In this way, the plate pairs 76 are very firmly connected.
  • another holding means may be used, wherein the top plate 78 and the foot plate 80 may also be referred to as holding means
  • FIG. 15 An alternative connection between the holding means, eg head plate 78 or foot plate 80, and the corrugated sheets 74 is in Fig. 15 shown.
  • the corrugated sheets 74 are passed through the holding means.
  • Collar 114 and holding means lie flat one above the other and are firmly connected to each other, for example a weld, as in Fig. 15 is shown.
  • a sealing means between collar 114 and retaining means may be arranged, for example a sealing layer.
  • Fig. 16 In contrast to Fig. 15 shows Fig. 16 a rounded transition between collar 114 and the fuselage of the corresponding corrugated sheet 74. This allows a hot gas flow turbulence and thus low noise and low pressure loss are performed.
  • the width 116 of the rounded region in the collar direction is at least 10% of the greatest width 118 of a gas tube between the wave plates 74, in particular at least 20%. The rounding can be performed on all embodiments shown.
  • FIG. 17 Another embodiment of an attachment of the collar 114 on the fastening means is in Fig. 17 shown.
  • the collar 114 of two corrugated sheets 74, which form a plate pair 76, are designed to overlap.
  • the overlap guides a fastener, such as a screw or rivet, and connects to the retaining means, eg, the top plate 78 or the foot plate 80.
  • the overlap allows the use of a central fixture instead of two fixtures side by side, as in FIG Fig. 18 is shown.
  • a sealing paper 120 is placed in each case for sealing the hot gas duct against the cold gas guide or the environment.
  • sealing paper 120 and holding means 78 each air is drawn. This is only for better illustration.
  • the elements are directly adjacent to each other.
  • Fig. 18 shows narrower collars 114 that do not overlap each other.
  • the collar 114 are clamped between the holding means and in each case a counter-element 122, as well as the sealant 120 between collar 114 and holding means, eg head plate 78 or base plate 80.
  • the counter element 122 is a plate arranged between the plate pairs 76, advantageously in the thickness of Holding means, eg 5 mm. It is in serpentine in this embodiment, as in Fig. 19 you can see.
  • bolts 124 are secured to mating member 122, e.g. welded, suitably carry thread.
  • mating member 122 e.g. welded
  • the jamming can be achieved by a screw connection, e.g. can be achieved with a mother 128.
  • riveting is possible, so that instead of the bolts 124 rivets are guided by the holding means and the counter-element 122.
  • the combination of plate pairs 76 with molded collar 114 from Fig. 18 and the counter elements 122 is in Fig. 19 shown in a plan view.
  • the holding element and the sealing paper 120 are omitted in the illustration for the sake of clarity, so that the view falls directly on the collar 114 and the underlying counter-elements 122.
  • the bolts 124 are inserted through holes in the collar.
  • the counter-elements 122 wind each serpentine between adjacent plate pairs 76, except for the outer counter-elements, which have only one adjacent plate pair 76.
  • Fig. 20 is the arrangement off Fig. 19 with the retaining means, in this case the head plate 78, shown.
  • Through holes 126 in the top plate 78 can be seen from above into the tubes of the plate pairs 76.
  • the bolts 124 are also inserted through the retaining means and bolted to the nuts 128, so that the collars 114 are clamped between the retaining means and the counter-element 122.

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

Claims (15)

  1. Centrale à bois mobile avec un échangeur thermique (22) avec un raccord de gaz chaud (38) et une conduite de gaz intérieur (32), un raccord de gaz de refroidissement (58) et une conduite de gaz extérieur (34) et une paroi (30) qui sépare les deux conduites de gaz (32, 34) et qui conduit la chaleur pour réaliser un transfert de chaleur du gaz chaud au gaz plus froid, une chambre de combustion, une conduite de gaz de fumée qui relie la chambre de combustion (18) au raccord de gaz chaud (38), une entrée d'air ambiant (54), une sortie d'air chaud (72), une conduite d'air ambiant (62) qui relie l'entrée d'air ambiant (54) au raccord de gaz de refroidissement (58) de l'échangeur thermique (22) et une conduite d'air chaud (68) qui relie une sortie de gaz extérieur de l'échangeur thermique (22) à la sortie d'air chaud (72), caractérisée en ce que la paroi (30) comprend plusieurs tôles ondulées reliées l'une à l'autre (74) entre lesquelles passent les deux conduites de gaz (32, 34).
  2. Centrale à bois mobile selon la revendication 1, caractérisée en ce que les tôles ondulées (74) sont reliées respectivement par paires l'une à l'autre de telle manière que des sections de surface intérieure convexes s'opposent respectivement par paires et que des sections de surface intérieure concaves s'opposent respectivement par paires.
  3. Centrale à bois mobile selon la revendication 2, caractérisée en ce que les sections de surface intérieure concaves forment respectivement par paires un tuyau (84).
  4. Centrale à bois mobile selon l'une des revendications 2 ou 3, caractérisée en ce que respectivement deux paires de plaques (76) sont placées l'une par rapport à l'autre de telle manière qu'elles forment entre elles une chambre de gaz ondulée (92) comme partie de la conduite de gaz extérieur.
  5. Centrale à bois mobile selon la revendication 4, caractérisée en ce que plusieurs tuyaux sont formés entre des paires de plaques et que la chambre de gaz (92) peut être traversée perpendiculairement au sens longitudinal des tuyaux (84).
  6. Centrale à bois mobile selon l'une des revendications 2 à 5, caractérisée en ce qu'une troisième paire de tôles ondulées (76) est placée entre deux paires de tôles ondulées (76) de telle manière que des sections de surface extérieure convexes de la troisième paire de tôles ondulées (76) viennent se situer entre des sections de surface extérieure concaves des deux paires de tôles ondulées qui entourent (76).
  7. Centrale à bois mobile selon l'une des revendications précédentes, caractérisée en ce que les tôles ondulées (74) forment une multitude de tuyaux parallèles (84) et la conduite de gaz extérieur (34) croise au moins quelques-uns des tuyaux (84) à l'extérieur, sa direction est renversée et elle croise ces tuyaux (84) une seconde fois à l'extérieur.
  8. Centrale à bois mobile selon l'une des revendications précédentes, caractérisée en ce que les tôles ondulées (74) forment une multitude de tuyaux parallèles (84) et la conduite de gaz extérieur (34) est guidée à l'aide d'au moins deux tôles de déviation (64, 66) en forme de S à travers les tôles ondulées (74) si bien qu'elle passe transversalement et parallèlement aux tuyaux (84).
  9. Centrale à bois mobile selon l'une des revendications précédentes, caractérisée en ce que les tôles ondulées (74) forment une multitude de tuyaux parallèles intérieurs (84) qui sont répartis en deux groupes avec respectivement plusieurs canaux de gaz extérieur séparés l'un de l'autre entre lesquels une section de mélange (96) est placée dans laquelle les canaux de gaz extérieur aboutissent.
  10. Centrale à bois mobile selon la revendication 9, caractérisée en ce que la conduite de gaz intérieur (32) est guidée à travers les deux groupes de tuyaux intérieurs (84) l'un après l'autre.
  11. Centrale à bois mobile selon l'une des revendications précédentes, caractérisée en ce que la conduite de gaz extérieur (34) passe dans une conduite à contre-courant vers la conduite de gaz intérieur (32).
  12. Centrale à bois mobile selon l'une des revendications précédentes, caractérisée en ce que les tôles ondulées (74) sont moulées respectivement à au moins une extrémité en un collet (114) qui est placé transversalement par rapport à l'orientation des ondulations et les tôles ondulées (74) sont fixées respectivement à ce collet (114) à un moyen de retenue pour retenir plusieurs tôles ondulées (74).
  13. Centrale à bois mobile selon la revendication 12, caractérisée en ce que le moyen de retenue est une tôle transversalement par rapport à l'orientation des ondulations et les collets (114) sont orientés en étant étendus en surface parallèlement à la tôle.
  14. Centrale à bois mobile selon la revendication 12 ou 13, caractérisée en ce que les collets (114) sont coincés entre le moyen de retenue et un élément antagoniste (122) placé entre les tôles ondulées (74).
  15. Installation mobile de séchage du foin avec un cadre transportable (6, 8) dans lequel une centrale à bois selon l'une des revendications précédentes, et en particulier un conteneur de combustible solide (4), est placée.
EP12714834.4A 2011-03-08 2012-03-08 Échangeur de chaleur pour installation mobile de foyer à combustible solide Active EP2684001B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102011013284 2011-03-08
DE202011103414U DE202011103414U1 (de) 2011-03-08 2011-07-01 Wärmetauscher für eine mobile Festbrennstofffeuerungsanlage
PCT/IB2012/000440 WO2012120369A1 (fr) 2011-03-08 2012-03-08 Échangeur de chaleur pour installation mobile de foyer à combustible solide

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EP2684001B1 true EP2684001B1 (fr) 2017-01-11

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AT (1) AT12584U1 (fr)
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WO2023006132A1 (fr) * 2021-07-28 2023-02-02 Vysoká Škola Báňská - Technická Univerzita Ostrava Échangeur de chaleur à plaques

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WO2015090578A1 (fr) * 2013-12-18 2015-06-25 Mobil In Time Ag Appareil mobile de chauffage à air pour combustibles solides
AT14469U1 (de) * 2014-03-12 2015-11-15 Lasco Heutechnik Gmbh Mobile Feuerungsanlage
DE202014008158U1 (de) * 2014-10-15 2014-10-30 Lasco Heutechnik Gmbh Mobilie Festbrennstofffeuerungsanlage
DE202014105262U1 (de) * 2014-11-03 2014-11-13 Lasco Heutechnik Gmbh Mobile Festbrennstofffeuerungsanlage
JP7035187B2 (ja) * 2018-06-27 2022-03-14 株式会社Welcon 熱輸送デバイスおよびその製造方法
WO2020143891A1 (fr) * 2019-01-08 2020-07-16 Machachou Abderrahim Méthode de développement de la climatisation centrale, la production d'air chaud, et d'eau chaude

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WO2023006132A1 (fr) * 2021-07-28 2023-02-02 Vysoká Škola Báňská - Technická Univerzita Ostrava Échangeur de chaleur à plaques

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WO2012120369A1 (fr) 2012-09-13
EP2684001A1 (fr) 2014-01-15
DE202011103414U1 (de) 2011-12-19
AT12584U1 (de) 2012-08-15

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