EP2541141B1 - Installation mobile de combustion de carburant solide - Google Patents

Installation mobile de combustion de carburant solide Download PDF

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Publication number
EP2541141B1
EP2541141B1 EP12401130.5A EP12401130A EP2541141B1 EP 2541141 B1 EP2541141 B1 EP 2541141B1 EP 12401130 A EP12401130 A EP 12401130A EP 2541141 B1 EP2541141 B1 EP 2541141B1
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EP
European Patent Office
Prior art keywords
heat exchanger
hot
coolant
solid
combustion chamber
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
EP12401130.5A
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German (de)
English (en)
Other versions
EP2541141A2 (fr
EP2541141A3 (fr
Inventor
Johann Landrichinger
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.)
Lasco Heutechnik GmbH
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Lasco Heutechnik GmbH
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Publication date
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Priority to SI201231568T priority Critical patent/SI2541141T1/sl
Publication of EP2541141A2 publication Critical patent/EP2541141A2/fr
Publication of EP2541141A3 publication Critical patent/EP2541141A3/fr
Application granted granted Critical
Publication of EP2541141B1 publication Critical patent/EP2541141B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B10/00—Combustion apparatus characterised by the combination of two or more combustion chambers
    • F23B10/02—Combustion apparatus characterised by the combination of two or more combustion chambers including separate secondary combustion chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B20/00—Combustion apparatus specially adapted for portability or transportability
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B40/00—Combustion apparatus with driven means for feeding fuel into the combustion chamber
    • F23B40/04—Combustion apparatus with driven means for feeding fuel into the combustion chamber the fuel being fed from below through an opening in the fuel-supporting surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B80/00—Combustion apparatus characterised by means creating a distinct flow path for flue gases or for non-combusted gases given off by the fuel
    • F23B80/04—Combustion apparatus characterised by means creating a distinct flow path for flue gases or for non-combusted gases given off by the fuel by means for guiding the flow of flue gases, e.g. baffles
    • 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
    • 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
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • 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
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/06—Portable or mobile, e.g. collapsible
    • 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
    • F24H2230/00—Solid fuel fired boiler
    • 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
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/224—Longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/08—Fluid driving means, e.g. pumps, fans

Definitions

  • the invention relates to a mobile solid fuel combustion system having a combustion chamber, a heat exchanger with a coolant side and a hot gas side, which is connected via a hot gas guide to the combustion chamber, for transferring combustion heat from flue gas to a coolant, a hot gas drive for driving the flue gas through the hot gas side, a Coolant drive for driving the coolant through the coolant side, wherein the coolant is ambient air and the coolant drive comprises an ambient air blower, and a blow-out opening for blowing out heated ambient air as hot air into the environment.
  • Mobile solid fuel firing systems are used, for example, for hay drying or for drying a building or a tent.
  • the solid fuel firing system is driven to the site, parked there and put into operation.
  • solid fuel is burned in the combustion chamber, the heat released being fed to a heat carrier, usually water, which is guided around the combustion chamber to absorb the heat.
  • a heat exchanger transfers the heat to the place of use.
  • the coolant flow in a horizontal cooling flow direction from an ambient air inlet to the exhaust port through the system passes and the coolant drive consists of at least one pressure fan for blowing ambient air into the heat exchanger and a coolant guide from the pressure fan to the discharge opening is drive-free.
  • the invention is based on the consideration that it is important for a mobile use of the solid fuel combustion system that it is carried out as light as possible.
  • the entire solid fuel firing system - in the following also simplified only called firing system - with simple means, such as a forklift, be raised.
  • 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 furnace is expediently a wood-burning plant for operation with, for example, wood chips, in particular a hay drying plant.
  • the firing system is a mobile firing system. It expediently comprises a support frame for lifting and transporting the furnace, which in particular has slots for standardized forks of a forklift.
  • 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.
  • the furnace has a hot side and a cold side.
  • the hot gas guide on the hot side and cold side can thus be divided into a hot side part on the hot side and a cold side part on the cold side.
  • a heat build-up should preferably not spread over immediately.
  • the two sides are - relative to a footprint on which the system is - expediently arranged side by side.
  • the firebox including Feuerungsraumpar and vertical overlying areas of the firing system are expediently arranged completely on the hot side. It is also useful if a heat exchanger inlet is arranged on the hot side.
  • a heat exchanger outlet is expediently arranged on the cold side.
  • the furnace system expediently comprises a gas shield which shields the hot side and the cold side against each other in such a way that at least in the upper half of the firing system a gas transfer, in particular a hot gas transfer, from one side to the other is only possible if the gas, in particular the hot gas, flows through the heat exchanger.
  • a gas transfer in particular a hot gas transfer
  • the cold side for coming out of the combustion chamber, hot flue gases can only be reached after passing through at least a portion of the. Heat exchanger.
  • all electrical components are at least on the hot side in height - meaning a height above a floor on which the system is - arranged below the combustion chamber, for example below a Upper edge of the combustion chamber, in particular below a lower edge of the combustion chamber.
  • a combustion chamber above the combustion chamber is expediently not calculated for the combustion chamber.
  • a fuel funnel at a Unterschubfeuerung is also not calculated to the combustion chamber.
  • all electrical units of the two gas drives and the fuel drive are arranged on the cold side.
  • a solid fuel supply to the combustion chamber is advantageous, a spark arrester and / or an upwardly oriented Kaltzug the heat exchanger.
  • hot flue gases can only be reached via a descent in at least one train of the heat exchanger.
  • the descent is expediently arranged completely on the hot side.
  • the heat exchanger is a stationary heat exchanger with at least one hot train, in which the hot gas stream is oriented vertically downwards, and a cold train, in which the hot gas stream is oriented vertically upwards.
  • the hot train is expediently arranged in the hot gas stream before the cold train.
  • the hot train is advantageously arranged on the hot side and the cold train on the cold side. The boundary between the hot side and the cold side expediently runs through a transition region between hot-drawing and cold-drawing, in particular in a region of a horizontal hot gas duct.
  • the heat exchanger is a corrugated plate heat exchanger in which corrugated sheets form a wall for transferring heat of combustion from the flue gas to the coolant.
  • 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 use of thin stainless steel sheets as a wall for the heat exchanger involves the difficulty that the mechanical stability of thin sheets is lower than of thick pipes. This can be a problem especially with a mobile firing system, as it is exposed to particularly high mechanical stresses that go beyond the usual thermal stress.
  • the firing system must survive a transport and associated jerking and bumping harmless and is exposed to a heavy impact especially in a hard settling at the site.
  • the heat exchanger must be made mechanically very stable in order to reliably prevent cracking or twisting. Due to the shape of the corrugated sheet, a mechanically very stable construction of the heat exchanger can be achieved, which is equal to the high demands of mobile use.
  • the corrugated sheets may have a fully rounded corrugation or an edged corrugation, in particular a polygonal corrugation having a lateral juxtaposition of flat surfaces.
  • the corrugation can have edges up to 90 °.
  • 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.
  • Sweckm make the pairs of corrugated iron are connected to each other at the convex inner surface portions. Such a connection can be achieved by welding.
  • the corrugated sheets of the pair of corrugated sheets may in this case be laid on one another in such a way 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.
  • 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 coolant guide. It can be a good mixing of the outside gas and thus a good heat transfer between hot gas and coolant 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 hot gas duct and the ambient air duct are arranged in countercurrent in the heat exchanger.
  • the cooling air flowing through the overheated area of the heat exchanger can be led out of the firing system immediately, as a result of which good heat emission can be achieved.
  • the firing system comprises, at least on the hot side, an exhaust opening for blowing out heated ambient air as warm air into the environment.
  • the ambient air blower consists of at least one pressure blower for blowing ambient air into the heat exchanger, and a coolant duct is drive-free from the ambient air blower to the blow-off opening. There is thus no aggregate arranged in a possible overheating zone.
  • the firing system at least one exhaust opening for blowing out heated ambient air as hot air into the environment wherein the discharge opening is higher in height above a floor than an ambient air inlet opening, in particular higher than the uppermost ambient air inlet opening. It can be generated a chimney effect, which is a continuous. Air flow generated by the heat exchanger without fan.
  • An ambient air inlet opening is expediently an opening in a housing which encloses the combustion chamber, the hot gas duct including the heat exchanger and the cooling air duct,
  • the highest outlet point of the exhaust opening is higher than 75% of the cooling air volume present in the system. Most of the cooling air can flow out through the chimney effect in the event of a power failure, and only a small amount of air is trapped, which can heat up considerably.
  • the cooling air flow is guided in a horizontal cooling flow direction through the system, with a deviation of up to 30 ° from the exact horizontal is included.
  • the cooling flow direction may be thought of as a straight line from a highest inlet point of the ambient air inlet port to a highest outlet point of the exhaust port, or of one. Centroid of the ambient air inlet opening to a centroid of the exhaust opening.
  • the cooling flow is guided so that it surrounds the entire imaginary line. It achieves a straight air flow that can be designed with low flow resistance.
  • the exhaust opening is a housing opening in a housing around the combustion chamber, the hot gas guide including the heat exchanger and the cooling air duct.
  • the coolant drive has at least one axial fan, in particular from at least one axial fan is formed.
  • An axial fan forms a relatively low flow resistance at standstill and allows even without drive a sufficient air flow through its propeller.
  • the heat exchanger is arranged between an ambient air inlet opening and an exhaust opening for blowing out heated ambient air as warm air into the environment, that the coolant guide is guided to at least 60%, in particular 75% of the distance from the ambient air inlet opening to the exhaust opening through the heat exchanger , As a result, just for larger systems a favorable geometry can be achieved, which enables a low-resistance cooling air flow with a very large heat transfer to the cooling air flow.
  • the solid fuel firing system has a combustion chamber, which is arranged next to the heat exchanger.
  • a large-volume, horizontal cooling air flow can be passed through the heat exchanger with little resistance. It is advantageous in this case if the combustion chamber, expediently including the combustion chamber wall, is concealed by at least one possible, horizontal and infinite, remote view, at least 50%, better 70%, in particular completely from the heat exchanger.
  • the mobile solid fuel firing system 2 will be described below first with reference to the schematic plan Fig. 1 and the two side views from the Figures 2 and 3 explained.
  • the side view of Fig. 2 is simplified, and the representation of some components, such as the cyclone, was omitted to show other underlying elements.
  • the furnace 2 has in this embodiment, a rated power of 750 kW and is mounted in a transport frame 4 with two slots 6 for inserting a fork of a forklift.
  • a mobile solid fuel storage 8 with an analogous frame is placed adjacent to the furnace 2.
  • the respective frames 4 hold all other components of the respective devices 2, 8.
  • the solid fuel storage 8 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 devices 2, 8 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 to transport solid fuel located in the solid fuel storage 8, for example wood chips, to the furnace 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 8 is moved to the place of use and parked next to the furnace 2.
  • the two devices 2, 8 are connected to each other via the terminal 10.
  • a positional adjustment of the two devices 2, 8 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 stored in a contiguous frame and jointly transportable. This solution is particularly advantageous for systems up to 500 kW, since the transport is facilitated and the connection of the two devices 2, 8 together omitted.
  • a burn-back fuse 14 of the solid fuel After passing through a burn-back fuse 14 of the solid fuel passes through another carried out as a Stocker auger conveyor 16 into the combustion chamber 18 in the furnace 2.
  • the combustion chamber 18 is designed for a Unterschubfeuerung, so that the fuel is inserted into the lower end of a hopper 20.
  • the resulting heap of fuel is ignited above, with solid fuel is tracked from below, so that the heap grows from below and burns up.
  • a primary blower 22 For supplying primary combustion air, a primary blower 22 is arranged on the lower edge of the combustion chamber 18 next to the Stocker screw 16.
  • a secondary fan 24 drives secondary combustion air into and around the combustor so that it passes through openings 26 into the combustor 18. The combustion induced by the secondary air takes place predominantly in a combustion chamber 28 above the combustion chamber 18.
  • the resulting during combustion hot flue gases are guided in a hot gas guide 30 in a distribution box 32 of a heat exchanger 34 and there split on a plurality of tubes 36 of the heat exchanger 34.
  • tubes 36 instead of the tubes 36, other gas guide channels of all suitable geometries are generally conceivable.
  • the hot gas guide 30 is in Fig. 4 represented by a similar heat exchanger 40 which is slightly smaller than the heat exchanger 34, but is made the same in many details.
  • the hot flue gases flow through a first train 38 of the heat exchanger 34 and reach a deflection box 42, in which they are deflected by 180 degrees to then reach the tubes 36 of the second train 44 of the heat exchanger 34 and to flow through them.
  • a collecting box 46 the cooled exhaust gases are fed to a spark separator 48, for example a plurality of cyclone separators operated in parallel.
  • the thus purified exhaust gases are led out laterally through a hot gas outlet 50 from the furnace 2.
  • the flue gases are cooled from about 1200 ° C to 150 ° C.
  • the heat released is supplied to ambient air, which is driven in a coolant guide 52 by means of a coolant drive 54 through the heat exchanger 34.
  • the coolant drive 54 consists of two blowers 56 in ambient air inlet openings that push the ambient air through the heat exchanger. A blower for a induced draft is not available.
  • the indicated by flat arrows coolant guide 52 leads the heated ambient air through hot air outlets 58 from the furnace 2 out, which are only openings in the housing of the furnace 2 and do not contain their own drive. The warm air is now available for further use, for example for drying hay.
  • Fig. 4 shows the heat exchanger 40 in a perspective view obliquely from above.
  • the representation of a housing has been omitted, so that the view is free on heat exchanging wall 60 between the hot gas side and the coolant side of the heat exchanger 40.
  • the hot gas guide 30 is guided through the hot gas side of the heat exchanger 34, 40, the coolant guide 52nd through the coolant side of the heat exchanger 34, 40th
  • the furnace 2 has a hot gas drive and the coolant drive 54.
  • the hot gas drive consists of the primary fan 22, the secondary fan 24 and a Saugzuggebläse 62, during operation of the furnace 2 for a continuous negative pressure in the combustion chamber 18 provides.
  • the induced draft fan 62 is located adjacent to the spark separator 48 and above the stocker auger 16 and draws the hot Flue gas from the Ausbrandraum 28 and through the heat exchanger 34, 40 and the spark arrester 48th
  • all electrical components, in particular drives, are arranged either on a cold side 64 of the furnace 2 or below the combustion chamber 18, the funnel 20 not being seen as a combustion chamber 18 for the underfeed firing becomes.
  • the cold side 64 is separated from a hot side 66 of the furnace 2 in that the hot flue gases can spread only on the hot side 66 and can reach the cold side 64 only by virtue of being at least 30% of the regular distance of the hot gas guide 30 in the heat exchanger 34, 40 have to cover. In dargestellen embodiment, it is just over 50%.
  • the heat exchanger 34, 40 is a stationary heat exchanger 34, 40 with at least one vertically downwardly oriented hot train 38 and a vertically upwardly oriented Kaltzug 44.
  • all electrical components of the furnace so aggregates to drive of gases and solid fuel and electrical and electronic, located below the upper edge of the combustion chamber 18, with one exception: the induced draft fan 62 of the hot gas drive.
  • the fan 68 is located at the top of a housing of the furnace 2, below the fan, a thermal insulation 70 in the form of an intermediate plate, suitably provided with an insulating means, wherein the motor 72 of the induced draft fan 62 is disposed below the thermal insulation. It is also positioned outside the hot gas guide 30 so that it does not come into contact with flue gases that remain above the thermal insulation.
  • the fan is expediently a radial fan advantageous to generate a stable negative pressure.
  • the furnace 2 On the hot gas side 66, the furnace 2 is free of a blower.
  • the coolant guide 52 is limited to pressure blower.
  • the coolant guide 52 is also guided so that it rises slightly from the coolant drive 54 at the beginning of the coolant guide 52 to the hot air outlet 58 at the end of the coolant guide 52, so that a low natural chimney effect even with failed drive for a low flow of ambient air through the heat exchanger 34th , 40 provides. As a result, the overheating is reduced slightly.
  • Fig. 5 shows a slight modification of the heat exchanger 40 in detail of the upper header 46a, which in contrast to the Fig. 4 embodiment shown in two box parts 73a, 73b executed divided.
  • the box part 73a is fixedly connected to the hot runner 44, in which about 1000 ° hot flue gases are guided downwards, and the box part 73a is firmly connected to the Kaltzug 38, in which the considerably cooled flue gases are led upwards. Due to the use of ambient air as a coolant it may be in operation In this case, the hot draft can reach up to 1000 ° C, whereas the temperature of the cold draft is up to 800 K lower. Thermal movements of the two box parts 73a, b of up to 2 cm may be the result. To allow this movement tension-free, the two box parts 73a, b are completely separate from each other and only via the two trains 38, 44 connected to each other, so that they are mutually movably mounted.
  • a low-resistance flow is significantly favored by the special construction of the heat exchanger 34, 40 in the form of a corrugated plate heat exchanger, as explained below.
  • the wall 60 of the heat exchanger 34, 40 is made of corrugated sheets, wherein two corrugated sheets 74 form a plate pair 76.
  • a pair of plates is in Fig. 6 illustrated by way of example in perspective.
  • Three such plate pairs 76 of the first train 40 are shown schematically in FIG Fig. 7 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 34, 40 upwards.
  • the top plate 78 thus contains the outer contours of the plate pairs 76 of the two trains 38, 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 sheets 74 of the plate pairs 76 are made of a stainless steel, suitably a stainless steel, and have a wall thickness of 0.5 mm.
  • the thickness of the top plate 78 which is made of structural steel, 5 mm. Accordingly, the plate pairs 76 are welded to a base plate 80 of the heat exchanger 22.
  • 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 superimposed and joined together so that they form a plurality of at least substantially longitudinal chambers in the form of tubes 36.
  • 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 36 is substantially circular, bounded above and below by the two circular segments 86, and laterally deviating somewhat 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 wall 60 flows around very turbulence and thus represents a lower flow resistance than a tube bundle heat exchanger with the same wall surface. Due to the design in stainless steel, the wall 60 can be made very smooth and little roughen by corrosion, so that also the flow resistance remains low, much lower than thicker pipes made of simpler steel.
  • a suction fan in the coolant guide 52 can be dispensed with.
  • Per train 38, 44 is the heat exchanger 34, 40 with several such, as in Fig. 6 provided plate pairs 76 which are positioned vertically side by side. Depending on the size and design of the vertical heat exchanger 34, 40, 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. 7 can be seen - the coolant guide 52 formed.
  • the gas space 92 between the plate pairs 76 here is designed so that it assumes a transverse shape to the longitudinal direction 90 of the tubes 36 and always has substantially the same thickness.
  • the waveguide creates an intensive contact of the coolant gas with the wall 60, so that there is an intense heat transfer from the hot gas to the coolant.

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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)
  • Air Supply (AREA)

Claims (13)

  1. Installation mobile de combustion de carburant solide (2), comprenant une chambre de combustion (18), un échangeur de chaleur (34, 40) avec un côté de réfrigérant et un côté de gaz chaud qui est connecté par le biais d'une conduite de gaz chaud (30) à la chambre de combustion (18) en vue du transfert de la chaleur de combustion sous forme de gaz de fumée à un réfrigérant, un entraînement de gaz chaud pour entraîner le gaz de fumée à travers le côté de gaz chaud, un entraînement de réfrigérant (54) pour entraîner le réfrigérant à travers le côté de réfrigérant, le réfrigérant étant de l'air environnant et l'entraînement de réfrigérant (54) comprenant une soufflante d'air environnant (56), et une ouverture d'évacuation (58) pour évacuer l'air environnant chauffé sous forme d'air chaud dans l'environnement,
    caractérisée en ce que la conduite de réfrigérant (52) s'étend dans une direction d'écoulement de refroidissement horizontale depuis une ouverture d'entrée d'air environnant jusqu'à l'ouverture d'évacuation (58) à travers l'installation, et l'entraînement de réfrigérant (54) est constitué d'au moins une soufflante sous pression (56) pour souffler de l'air environnant dans l'échangeur de chaleur (34, 40) et une conduite de réfrigérant (52) allant de la soufflante sous pression (56) à l'ouverture d'évacuation (58) ne dispose pas d'entraînement.
  2. Installation de combustion de carburant solide (2) selon la revendication 1, caractérisée par sa division en un côté chaud (66) et un côté froid (64) que les gaz de fumée chauds provenant de la chambre de combustion (18) ne peuvent atteindre qu'en passant à travers au moins une partie de l'échangeur de chaleur (34, 40), la chambre de combustion (18) et au moins une section chaude (38) de l'échangeur de chaleur (34, 40) étant disposées du côté chaud (66) et au moins tous les composants électriques qui sont disposés au-dessus de la chambre de combustion (18), étant disposés du côté froid (64).
  3. Installation de combustion de carburant solide (2) selon la revendication 2, caractérisée en ce que tous les groupes électriques des deux entraînements de gaz et d'un entraînement de combustible sont disposés du côté froid (64).
  4. Installation de combustion de carburant solide (2) selon la revendication 2 ou 3, caractérisée en ce que le côté froid (64) ne peut être atteint par les gaz de fumée chauds provenant de la chambre de combustion (18) que par le biais d'une descente dans au moins une section chaude (38) de l'échangeur de chaleur (34, 40).
  5. Installation de combustion de carburant solide (2) selon l'une quelconque des revendications 2 à 4, caractérisée en ce que la section chaude (38) est orientée vers le bas et une section froide (44) de l'échangeur de chaleur (34, 40) est disposée du côté froid (64).
  6. Installation de combustion de carburant solide (2) selon l'une quelconque des revendications précédentes, caractérisée en ce que l'échangeur de chaleur (34, 40) est un échangeur de chaleur fixe (34, 40) avec au moins une section chaude (38) orientée verticalement vers le bas et une section froide (44) orientée verticalement vers le haut.
  7. Installation de combustion de carburant solide (2) selon l'une quelconque des revendications précédentes, caractérisée en ce que l'échangeur de chaleur (34, 40) est un échangeur de chaleur à tôles ondulées, dans lequel les tôles ondulées (74) forment une paroi (60) pour le transfert de la chaleur de combustion du côté de gaz chaud vers le côté de réfrigérant.
  8. Installation de combustion de carburant solide (2) selon l'une quelconque des revendications précédentes, caractérisée en ce que la conduite de gaz chaud (30) et la conduite de réfrigérant (52) sont disposées à contre-courant dans l'échangeur de chaleur (34, 40).
  9. Installation de combustion de carburant solide (2) selon l'une quelconque des revendications précédentes, caractérisée en ce que la conduite de gaz chaud (30) est guidée dans l'échangeur de chaleur (34, 40) au moins pour la majeure partie verticalement et la conduite de réfrigérant (52) est guidée dans l'échangeur de chaleur (34, 40) au moins pour la majeure partie horizontalement.
  10. Installation de combustion de carburant solide (2) selon l'une quelconque des revendications précédentes, caractérisée par au moins une ouverture d'évacuation supplémentaire (58) pour évacuer l'air environnant chauffé sous forme d'air chaud dans l'environnement, l'ouverture d'évacuation supplémentaire (58) étant située à une hauteur au-dessus du sol supérieure à une ouverture d'entrée d'air environnant.
  11. Installation de combustion de carburant solide (2) selon l'une quelconque des revendications précédentes, caractérisée en ce que l'échangeur de chaleur (34, 40) est disposé entre l'ouverture d'entrée d'air environnant et l'ouverture d'évacuation (58) pour l'évacuation de l'air environnant chauffé sous forme d'air chaud dans l'environnement de telle sorte que la conduite de réfrigérant (52) soit guidée sur au moins 60 %, en particulier 75 % de l'étendue depuis l'ouverture d'entrée d'air environnant jusqu'à l'ouverture d'évacuation (58) à travers l'échangeur de chaleur (34, 40).
  12. Installation de combustion de carburant solide (2) selon l'une quelconque des revendications précédentes, caractérisée par une chambre de combustion (18) qui est disposée à côté de l'échangeur de chaleur (34, 40).
  13. Installation de combustion de carburant solide (2) selon l'une quelconque des revendications précédentes, caractérisée en ce que l'échangeur de chaleur (34, 40) présente un caisson collecteur supérieur avec deux parties de caisson supportées de manière déplaçable l'une par rapport à l'autre, une partie de caisson formant un dispositif d'introduction dans une section chaude orientée vers le bas et une partie de caisson formant un dispositif d'évacuation hors d'une section froide de l'échangeur de chaleur (30, 40) orientée vers le haut.
EP12401130.5A 2011-07-01 2012-06-29 Installation mobile de combustion de carburant solide Active EP2541141B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
SI201231568T SI2541141T1 (sl) 2011-07-01 2012-06-29 Mobilna naprava za zgorevanje trdnih goriv

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202011103415U DE202011103415U1 (de) 2011-07-01 2011-07-01 Mobile Festbrennstofffeuerungsanlage

Publications (3)

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EP2541141A2 EP2541141A2 (fr) 2013-01-02
EP2541141A3 EP2541141A3 (fr) 2016-07-20
EP2541141B1 true EP2541141B1 (fr) 2018-12-19

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ID=44658482

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EP (1) EP2541141B1 (fr)
DE (1) DE202011103415U1 (fr)
HU (1) HUE043558T2 (fr)
SI (1) SI2541141T1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3128520A1 (fr) * 2021-10-25 2023-04-28 Axens Paire de plaques d’échangeur de chaleur avec rainures et creux

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AT14471U1 (de) * 2014-03-06 2015-11-15 Lasco Heutechnik Gmbh Feuerungsanlage
AT14470U1 (de) * 2014-03-06 2015-11-15 Lasco Heutechnik Gmbh Feuerungsanlage
AT14473U1 (de) * 2014-03-12 2015-11-15 Lasco Heutechnik Gmbh Mobile Feuerungsanlage
AT14475U1 (de) * 2014-03-12 2015-11-15 Lasco Heutechnik Gmbh Mobile Feuerungsanlage
AT14474U1 (de) * 2014-03-12 2015-11-15 Lasco Heutechnik Gmbh Mobile Feuerungsanlage
DE202014105262U1 (de) * 2014-11-03 2014-11-13 Lasco Heutechnik Gmbh Mobile Festbrennstofffeuerungsanlage
DE202015105427U1 (de) * 2015-10-14 2015-10-21 Lasco Heutechnik Gmbh Mobile Festbrennstofffeuerungsanlage
DE102016120065A1 (de) 2016-10-20 2018-04-26 Lasco Heutechnik Gmbh Mobiler Warmlufterzeuger und Verfahren zu seinem Betrieb

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US1751725A (en) * 1926-01-07 1930-03-25 Walter M Cross Heat exchanger
FR819534A (fr) * 1936-12-07 1937-10-20 Calorifère à air chaud surpressé
DE8223682U1 (de) * 1982-07-31 1982-09-30 Ulbrich, geb. Spilker, Annmemarie, 5470 Andernach Vorrichtung zum Trocknen und Bergen von mähfrischem Gras
FR2553182B1 (fr) * 1983-10-10 1988-05-06 Olivier Calmon Generateur d'air chaud mobile
US20090056705A1 (en) * 2007-08-30 2009-03-05 Suncue Company Ltd Combustion system

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3128520A1 (fr) * 2021-10-25 2023-04-28 Axens Paire de plaques d’échangeur de chaleur avec rainures et creux
WO2023072571A1 (fr) * 2021-10-25 2023-05-04 Axens Paire de plaques d'echangeur de chaleur avec rainures et creux

Also Published As

Publication number Publication date
DE202011103415U1 (de) 2011-08-18
SI2541141T1 (sl) 2019-07-31
EP2541141A2 (fr) 2013-01-02
EP2541141A3 (fr) 2016-07-20
HUE043558T2 (hu) 2019-08-28

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