EP2541141A2 - Mobile solid-fuel combustion device - Google Patents

Abstract

The mobile solid fuel combustion system (2) comprises a combustion chamber (18), a heat exchanger with a coolant side and a hot gas side, which are connected with the combustion chamber by a hot gas guide for transferring combustion heat from flue gas to the coolant. A hot gas drive is provided for driving the flue gas through the hot gas side. A coolant drive is provided for driving the coolant through the coolant side.

Description

The invention relates to a mobile solid fuel combustion system with 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 furnace heat from flue gas to a coolant, a hot gas drive for driving the flue gas through the hot gas side and a Coolant drive for driving the coolant through the coolant side.

Mobile solid fuel firing systems are used, for example, for hay drying or for drying a building or a tent. For this purpose, the solid fuel firing system is driven to the site, parked there and put into operation. For 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.

It is an object of the present invention to provide a solid fuel firing system which is particularly suitable for mobile operation.

This object is achieved by a solid fuel combustion system of the aforementioned type, in which according to the invention the coolant is ambient air and the coolant drive comprises an ambient air blower.

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. Thus, the entire solid fuel firing system - in the following also simplified only called firing system - with simple means, such as a forklift, be raised. In this regard, 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.

If the water is replaced as coolant by ambient air, although the weight of the water can be saved, but the heat exchanger must be made considerably larger, since a heat transfer from flue gas to air requires about three times larger transmission surfaces per transmission power, as a heat transfer from flue gas to water , However, large metallic transfer surfaces are heavy on weight, so that the advantage of the replaced water is erased to a significant extent again.

However, if a very large volume flow of warm air is required, then the disadvantage of a large heat exchanger can be compensated again. Because to produce a very large volume flow, a large heat exchanger is advantageous because it can be dispensed with high pressures or speeds in the cooling air flow. In these special applications, the use of ambient air as a coolant is thus advantageous.

The furnace is expediently a wood-burning plant for operation with, for example, wood chips, in particular a hay drying plant. Next is the furnace 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.

If flue gas is used as the hot gas flowing from the combustion chamber into the heat exchanger, the heat exchanger is exposed to extreme thermal loads. 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 problematic is a power failure, since then fails the drive to Hindustreiben the ambient air as a coolant through the heat exchanger and the cooling air flow collapses or is significantly reduced. Since the combustion still produces a strong heat for a while, which is no longer sufficiently dissipated can occur in the heat exchanger and above him a heat accumulation with temperatures above 1,200 ° C.

To avoid damage, it is therefore advantageous if the furnace has a hot side and a cold side. Here, expediently, the hot gas guide on the hot side and cold side. The hot gas path can thus be divided into a hot side part on the hot side and a cold side part on the cold side. 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 Feuerungsraumwände and vertical overlying areas of the firing system are expediently arranged completely on the hot side. It is also useful if a heat exchanger on the hot side is arranged. 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. Advantageously, the cold side for coming out of the combustion chamber, hot flue gases can be reached only after passing through at least a portion of the heat exchanger.

In particular, the combustion chamber and at least one hot draft of the heat exchanger on the hot side and at least those electrical components which are arranged in their height above the combustion chamber, arranged on the cold side. Further advantageously, 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 an 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.

In particular, all electrical units of the two gas drives and the fuel drive are arranged on the cold side. 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.

To avoid damage, it is also advantageous if the cold side for coming out of the combustion chamber, 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. In the event of a heat accumulation in the system caused by a power failure, the extremely heated air in the heat exchanger must first travel downwards in order to exit the heat exchanger. Here it is cooled, so that even a subsequent way in the heat exchanger up the hot air is not able to draw very strong through the heat exchanger. The way down therefore represents a heat blockage. This provides the advantage that no extremely overheated air exits the furnace, which could cause damage to the environment or even ignition of objects in the environment.

An advantageous embodiment of the invention provides that 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 advantageously 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.

It is particularly advantageous if 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. By using sheets As a 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, however, 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. Thus, 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. In this respect, 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 °.

In an advantageous embodiment of the invention, the corrugated sheets are 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. In this way, a corrugated sheet pair can form a number of tubes, at least form a part of the inner gas guide, so that the inner gas guide passes through the tubes thus formed.

Conveniently, the corrugated plate pairs 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 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.

It is further proposed that 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 achieved a good mixing of the outside gas and thus a good heat transfer between hot gas and coolant. Advantageously, 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.

In order to achieve a significant residual cooling of the superheated gas in the heat exchanger after a power failure, is it is advantageous if 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.

In order to maintain a discharge of hot air from the overheating zone, it is advantageous if the furnace has, at least on the hot side, an exhaust opening for blowing out heated ambient air as warm air into the environment.

Further, it is advantageous if the ambient air blower consists of at least one pressure blower for blowing ambient air into the heat exchanger and a coolant flow from the ambient air blower to the blow-out is free of drive. There is thus no aggregate arranged in a possible overheating zone.

In order to maintain a cooling air flow through the heat exchanger even when all fans are, it is advantageous if the firing system has at least one exhaust opening for blowing out heated ambient air as hot air into the environment, the exhaust opening is higher in height above a floor as an ambient air inlet opening, in particular higher than the uppermost ambient air inlet opening. It can be generated a chimney effect, which generates a continuous flow of air through 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,

Advantageously, 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 advantageously 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 from a centroid of the ambient air inlet port to a centroid of the exhaust port. Conveniently, 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.

In order to ensure a good flow of cooling air, even in the event of a power failure, it is also advantageous if the center of gravity of an exhaust opening lies above the middle of the overall height of a housing enclosing the combustion chamber, the hot gas duct including the heat exchanger and the cooling air duct.

Advantageously, 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.

Also maintaining a cooling air flow in case of power failure, it is conducive if 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.

It is also proposed that 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.

With the same advantage, 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 previously given description of advantageous embodiments of the invention contains numerous features, which are given in the individual subclaims partially summarized in several. However, those skilled in the art will conveniently consider these features individually and summarize them to meaningful further combinations. The same applies to the features of each embodiment of the following description of the figures, which are considered explicitly isolated and can be combined with the heat exchanger according to the invention.

Fig. 1

eine schematische Draufsicht auf eine mobile Festbrennstofffeuerungsanlage,

Fig. 2

eine schematische Seitenansicht auf die Festbrennstofffeuerungsanlage aus Fig. 1,

Fig. 3

eine schematische Seitenansicht von der anderen Seite auf einen Wärmetauscher der Festbrennstofffeuerungsanlage aus Fig. 1,

Fig. 4

einen ähnlichen Wärmetauscher für eine Festbrennstofffeuerungsanlage in einer perspektivischen Ansicht von oben,

Fig. 5

einen weiteren Wärmetauscher mit einem geteilten oberen Verteilerkasten,

Fig. 6

eine perspektivische Ansicht auf ein Wellblechplattenpaar des Wärmetauschers und

Fig. 7

eine schematische Schnittdarstellung durch drei Wellblechplattenpaare des Wärmetauschers.

Show it:

Fig. 1

a schematic plan view of a mobile solid fuel burning plant,

Fig. 2

a schematic side view of the solid fuel burning plant Fig. 1 .

Fig. 3

a schematic side view of the other side of a heat exchanger of the solid fuel burning plant Fig. 1 .

Fig. 4

a similar heat exchanger for a solid fuel burning plant in a perspective view from above,

Fig. 5

another heat exchanger with a split upper distribution box,

Fig. 6

a perspective view of a corrugated plate pair of the heat exchanger and

Fig. 7

a schematic sectional view through three corrugated metal plate pairs of 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. For this purpose, 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.

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. Subsequently, 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. Now 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. During operation of the furnace 2, the solid fuel is conveyed via the conveyor 12 and the connection 10 to the furnace 2.

In an alternative embodiment, 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.

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.

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. 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. Via 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.

In the heat exchanger 34, 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 direction indicated by area 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. For better explanation, 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

To move the two gases through the heat exchanger 34, 40, 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

In the event of a power failure, all electrical components of the furnace 2 are out of service. The fire in the combustion chamber 18 continues to burn and initially continues to generate much heat. This leads to a strong heat accumulation in the region of the Ausbrandraums 28, the distribution box 32 and the first train 38, wherein a heating of the materials of these components over 1200 ° C is possible.

In order to avoid destruction of components of the furnace 2 in this case too, 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. The descent brakes with the associated cooling a natural train through the heat exchanger 34, 40 when the hot gas drive fails, so that the overheating is essentially limited to the hot side 66.

In the illustrated embodiment, all electrical components of the furnace 2, 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. However, it is split to protect it. While 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.

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. Such 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. At its top end, 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. For stable support of the plate pairs 76, 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.

Out Fig. 7 It can be seen that the coolant guide 52 is guided very accurately. This results in an advantage of a corrugated iron heat exchanger 34, 40 compared to a tube bundle heat exchanger: The cooling gas must cover a defined path along the wall 60, which can not be achieved in tubular heat exchangers, since the cooling gas can flow around the tubes 36 on both sides.

In addition, 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.

Due to the good flow through the heat exchanger 34, 40, a natural current is maintained even in case of failure of the drive sufficiently. In addition, 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.

LIST OF REFERENCE NUMBERS

2

Festbrennstofffeuerungsanlage

4

transport frame

6

insertion

8th

Solid fuel storage

10

connection

12

discharge unit

14

Burn-back protection

16

funding

18

combustion chamber

20

funnel

22

primary blower

24

secondary fan

26

opening

28

burn-out

30

Hot gas management

32

distribution box

34

heat exchangers

36

pipe

38

train

40

heat exchangers

42

deflection box

44

train

46

collection box

48

Funkenabtrenner

50

hot gas outlet

52

Coolant circulation

54

Coolant drive

56

fan

58

Hot air outlet

60

wall

62

induced draft fan

64

cold side

66

hot side

68

fan

70

insulation

72

engine

73

box part

74

corrugated iron

76

pair of plates

78

headstock

80

footplate

82

longitudinal edge

84

tube

86

segment

88

segment

90

longitudinal direction

92

headspace

Claims (15)

Mobile solid fuel firing system (2) having a combustion chamber (18), a heat exchanger (34, 40) with a coolant side and a hot gas side, which is connected via a hot gas guide (30) to the combustion chamber (18), for transferring combustion heat from flue gas to a Coolant, a hot gas drive for driving the flue gas through the hot gas side and a coolant drive (54) for driving the coolant through the coolant side,
characterized in that the coolant is ambient air and the coolant drive (54) comprises an ambient air blower (56). Solid fuel combustion system (2) according to claim 1, characterized by its division into a hot side (66) and a cold side (64), for hot flue gases coming from the combustion chamber (18) only by passing through at least a part of the heat exchanger (34, 40 ), wherein the combustion chamber (18) and at least one hot strip (38) of the heat exchanger (34, 40) on the hot side (66) and at least all those electrical components which are arranged above the combustion chamber (18) on the cold side (64) are arranged. Solid fuel combustion system (2) according to claim 2, characterized in that all electrical units of the two gas drives and the fuel drive on the cold side (64) are arranged. Solid fuel burning plant (2) according to claim 2 or 3, characterized in that the cold side (64) coming from the combustion chamber (18), hot flue gases only via a descent in at least one hot train (38) of the heat exchanger (34, 40) can be reached. Solid fuel burning plant (2) according to one of claims 2 to 4,
characterized in that the hot train (38) is oriented downwards and a cold train (44) of the heat exchanger (34, 40) on the cold side (64) is arranged. Solid fuel burning plant (2) according to one of the preceding claims,
characterized in that 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 directed cold train (44). Solid fuel burning plant (2) according to one of the preceding claims,
characterized in that the heat exchanger (34, 40) is a corrugated iron heat exchanger, wherein the corrugated sheets (74) form a wall (60) for transmitting heat of combustion from the hot gas side to the coolant side. Solid fuel burning plant (2) according to one of the preceding claims,
characterized in that the hot gas guide (30) and the coolant guide (52) in the heat exchanger (34, 40) are arranged in countercurrent. Solid fuel burning plant (2) according to one of the preceding claims,
characterized in that the coolant guide (52) extends in a horizontal cooling flow direction through the system. Solid fuel burning plant (2) according to one of the preceding claims,
characterized in that the hot gas guide (30) in the heat exchanger (34, 40) at least for the most part vertically and the coolant guide (52) in the heat exchanger (34, 40) are guided at least for the most part horizontally. Solid fuel burning plant (2) according to one of the preceding claims,
characterized by at least one blow-off opening (58) for blowing out heated ambient air as hot air into the environment, the coolant drive (54) consisting of at least one pressure blower (56) for blowing ambient air into the heat exchanger (34, 40) and a coolant guide (52 ) from the pressure fan (56) to the exhaust port (58) is drive-free. Solid fuel burning plant (2) according to one of the preceding claims,
characterized by at least one exhaust opening (58) for blowing heated ambient air as warm air into the environment, the discharge opening (58) being higher in height above a floor than an ambient air inlet opening. Solid fuel burning plant (2) according to one of the preceding claims,
characterized in that the heat exchanger (34, 40) between an ambient air inlet opening and an exhaust opening (58) for blowing heated ambient air is arranged as hot air into the environment that the coolant guide (52) to at least 60%, in particular 75% of the route from the ambient air inlet opening to the exhaust opening (58) through the heat exchanger (34, 40) is guided. Solid fuel burning plant (2) according to one of the preceding claims,
characterized by a combustion chamber (18) disposed adjacent to the heat exchanger (34, 40). Solid fuel burning plant (2) according to one of the preceding claims,
characterized in that the heat exchanger (34, 40) comprises an upper header with two movably mounted box parts, wherein a box part an initiator in a downward hot train and a box part a discharge from an upward Kaltzug the heat exchanger (34, 40 ).

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