• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
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    • 专利摘要:
    The invention relates to a heat exchanger (22) for a mobile solid fuel firing system (2) having a hot gas connection (38) and an inner gas guide (32), a cooling gas connection (58) and an outer gas guide (34) and one separating the two gas guides (32, 34) A defined gas conduction and a low weight of the heat exchanger can be achieved if the wall (30) comprises a plurality of interconnected corrugated sheets (74) between which two gas ducts (30). 32, 34).
    公开号:AT12584U1
    申请号:TGM375/2011U
    申请日:2011-07-01
    公开日:2012-08-15
    发明作者:
    申请人:Lasco Heutechnik Gmbh；
    IPC主号:
    专利说明:

    Austrian Patent Office AT12 584U1 2012-08-15
    Description: The invention relates to a heat exchanger for a mobile solid fuel combustion system with a hot gas connection and an inner gas guide, a cooling gas connection and an outer gas guide and a wall separating the two guides and heat conducting wall for producing a heat transfer from the hot to the colder gas.
    Mobile solid fuel firing systems are used to generate large quantities of heat for a limited period of time in one place. 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 supply of heat for industrial processes. For this purpose, the solid fuel firing system is driven to the site, parked there and put into operation.
    For operation, a solid fuel tank may be connected via a fuel delivery mechanism to a combustion chamber of the solid fuel burning plant. 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.
    It is an object of the present invention to provide a heat exchanger which is particularly suitable for use in a mobile solid fuel burning plant.
    This object is achieved by the heat exchanger of the type mentioned, in which according to the invention, 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 a mobile use of solid fuel burning system that it is carried out as light as possible. Thus, the entire solid fuel firing system - in the following simplified also called firing plant - 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.
    Significantly weight-saving, it is when the heat from the hot flue gas is delivered directly to the cooling gas, which is now available for further use, for example, for hay drying or tent heating available. Accordingly, 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.
    Is used as hot gas flue 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 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. However, 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, as 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. In addition, 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 shell-and-tube heat exchanger.
    However, the use of stainless steel sheets as a wall for the heat exchanger involves the difficulty that the mechanical stability of thin sheets is less than of thick pipes. This can be a problem especially in a mobile firing system, as they are exposed to particularly high mechanical stresses that go beyond the usual thermal stress. Thus, the firing system must survive a transport and associated jerks and bumps without damage 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. Therefore, a weight-saving, mechanically stable and sufficiently inexpensive heat exchanger can be provided by means of the invention.
    The furnace is suitably a wood-burning plant for operation 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 outer gas guide is expediently designed so that the guided in their outer gas flow flows around the inner gas flow. 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.
    In an advantageous embodiment of the invention, the corrugated sheets are each connected in pairs such 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 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.
    Conveniently, the pairs of corrugated sheets are connected to each other at the convex inner surface portions. Such 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.
    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.
    Conveniently, the corrugated sheets are placed one above the other, that the tubes are formed so that their interiors in the region of their parallel course, at least by juxtaposition of the sheets are substantially separated from each other. This also allows a particularly good flow guidance of the inner gas guide can be achieved.
    Advantageously, the inner gas duct runs as a hot gas duct through the tubes. For this purpose, the tubes are advantageously connected to the hot gas connection so that flows through this flowing hot gas through the tubes. The inner gas guide may be a flue gas guide and the outer gas guide may be an ambient air guide. However, it is also possible to supply the hot gas of the outer gas guide and the cooling gas of the inner gas guide.
    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.
    Advantageously, a plurality of tubes are formed between pairs of plates, wherein the wave-shaped flow area can be flowed through perpendicular to the longitudinal direction of the tubes, in particular is wavy flowed through.
    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 rest between concave outer surface portions of the two surrounding pairs.
    In particular, in a crossing flow arrangement of the inner gas guide and outer gas guide, the problem may arise that at least one of the gas guides from the gas guide section is short, which is not beneficial to a 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. By this deflection, a long contact of the outer and inner flow can be formed over the wall and thus a 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.
    Further, it is advantageous if 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. Under parallel and transverse to the tubes is 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.
    A uniform heat transfer between the two gas ducts, it is also beneficial if the corrugated sheets form a plurality of parallel inner tubes, which are divided into two groups, each with a plurality of separate outer gas channels, between which a mixing section is arranged, in which the outer gas channels lead. In this mixing section expediently also the baffles, whereby a simple and stable construction of both the baffles and the heat exchanger is achievable.
    Next expedient, the inner gas guide is guided successively through the two groups of the inner tubes, which are arranged in particular parallel to each other. This allows a long gas flow in a confined space can be achieved.
    Good heat utilization of the hot gas can be further assisted if the outer gas guide runs in a countercurrent flow to the inner gas guide. 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.
    In addition, the invention is directed to a solid fuel burning plant with a combustion chamber, a heat exchanger as described above and a combustion chamber connecting the internal gas connection flue gas duct. It can thereby be a thermally and mechanically stable unit, combined with a low weight, formed within the solid fuel burning plant.
    Particularly good air heating can be achieved when the solid fuel firing system comprises an ambient air inlet, a warm air outlet, an ambient air duct 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.
    Further, 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. In particular, 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.
    The previously given description of advantageous embodiments of the invention contains numerous features that 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. 2 Fig. 3 Fig. 4 Fig. 6 Fig. 6 is a schematic representation of a mobile and air-cooled solid fuel burning plant with a heat exchanger for heating air in a schematic representation, the heat exchanger in a perspective view from above, the heat exchanger in a schematic side view, a plan view of a top plate of the heat exchanger, a perspective view of a corrugated plate pair of the heat exchanger, a schematic sectional view through three Fig. 7 is a perspective view of a foot plate of the heat exchanger, Fig. 8 is a plan view of a baffle of the heat exchanger, Fig. 9 is a schematic view of an air guide through the heat exchanger, [0041 10 shows an alternative pair of corrugated sheets in a plan view, FIG. 11 shows the pair of corrugated sheets of FIG. 10 in FIG a perspective view, Fig. 12 is a welded connection of the corrugated metal sheets on the longitudinal edge of the corrugated metal plate pair in a sectional view, and Fig. 13 shows an alternative heat exchanger with a rectilinear external gas guide.
    Fig. 1 shows a mobile solid fuel burning plant 2 - hereinafter also simplified only referred to as furnace 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. For this purpose, both the solid fuel storage 4 and the furnace 2 are each provided with a transport means 6, 8 indicated only schematically, by means of which the two elements 2, 4 can each be raised, for example by Austrian patent office AT12 584U1 2012-08-15 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. 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 for transporting solid fuel located in the solid fuel storage 4, for example wood chips, to the firing installation 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. 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 coherent framework 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 elements 2, 4 together.
    After passing through a burn-back fuse 14 of the solid fuel passes through another carried out as Stockerschnee 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 ^ 0 to under 1000 ^ 0. 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. For better explanation, 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 are indicated in FIG. 2 by thin or thick arrows. The heat exchanger 22 is a corrugated plate heat exchanger whose wall 30 is made of corrugated sheets and which is described in more detail below.
    The heat exchanger 22 comprises a flue gas inlet 36, which is designed in the embodiment shown as a distribution box for distributing the hot gas to many tubes. 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, from there reach a deflection space 42, where they are redirected upwards by 180 degrees, pass through the second train 44 and from there reach a collecting box 46. Then leave the Austrian Patent Office AT12 584U1 2012- 08-15 the cooled hot gases, the heat exchanger 22 through a hot gas discharge 48, through which they are passed to the spark separator 24. In the deflection space 42 accumulated ash is fed through an ash removal 50 to the ash container 26.
    While the inner gas guide 32 extend U-shaped through the two trains 40, 44 of the heat exchanger 22, the outer gas guide 34 extends in an S-shape around the wall 30 of the two trains 40, 44, as shown in Fig. 3.
    Fig. 3 shows the two trains 40, 44 with the indicated housing 28 and the outer gas guide 34. During operation of the solid fuel combustion system 2, air is admitted through an ambient air inlet 54 with a fan 60. By 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 before. 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 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 shown in FIG. 5 by way of example in perspective. Three such pairs of plates 76 of the first train 40 are shown schematically in Fig. 6 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 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. For stable support of the plate pairs 76, the thickness of the top plate 78, which is made of structural steel, 5 mm. Also possible is stainless steel, which can then be made thinner. 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 contact each other in their central axis, which is parallel to the longitudinal axis of the tubes 84 and plate pairs 76. As a result of the juxtaposition of the segments of the European Patent Office, the interior 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.
    From Fig. 6 it can be seen that the outer gas guide 34 is guided very accurately. This results in an advantage of a corrugated iron heat exchanger 22 compared to a tubular heat exchanger: The outer gas or cooling gas must cover a defined path along the wall 30, which can not be achieved in tubular heat exchangers, since the outer gas can flow around the tubes on both sides.
    Since a gas tightness of the tubes 84 against each other is not necessary, since the same hot flue gas flows through all the tubes 84, 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 of the heat exchanger 22 is provided with a plurality of such, as shown in Fig. 5, pairs of plates 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. As a result, as shown in FIG. 6, the outer gas guide 34 is formed between the plate pairs 76. 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.
    With regard to the thickness of the gas space 92 and the spacing of the plate pairs 76 from each other, it should be ensured that the distance is not greater than half the radius of the tubes 84, otherwise the cooling air or the outer gas, the waves must not extend and the There is a risk that 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 completely passing 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.
    By the S-shaped outer gas guide 34 this crosses the tubes 84 of the second train 44 and some of the tubes 84 of the first train 40, is then deflected by 180 degrees, so also runs a little way parallel to the tubes 84 of the first train 40, to then intersect some tubes 84 of the first train 40 and some tubes 84 of the second train 44, is in turn deflected by about 180 degrees, thus running parallel to some of the tubes 84 of the second train 44, then other tubes 84 of the second Train 44 and all tubes 84 of the first train 40 to cross.
    By using 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. This has the advantage of a much wider choice of materials, since sheets are available in a significantly larger material variation than pipes. It is possible to resort to materials of higher quality than would be possible with pipes, for example a steel which is resistant to oxidation under high heat, a very heat-resistant steel or a metal with a preferred coefficient of thermal expansion. Accordingly, the wall thickness of the corrugated sheets 74 may be smaller than would be necessary for pipes, so that the heat exchanger 22 can be made easy to build and save weight. This is particularly advantageous in the case of a mobile solid fuel firing installation 2, since every weight saving there facilitates transport.
    The foot plate 80 is shown in a perspective view in FIG. 7 so that the openings 94 in the foot plate 80 are visible for connection to the plate pairs 76. The deflection means 64 is shown in a plan view in Fig. 8. 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 plate pairs 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 can be seen from Fig. 4, the plate pairs 76 of the first train 40 are of those of the second train is spaced by a region 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 dividing plates are arranged in the area 46, which thus do not intersect tube openings.
    The region 96 has yet another advantage: straight in the upper region of the two trains 40, 44 there is a significant difference in temperature of the walls 30 of the two trains 40, 44. While the wall 30 of the first train 40 in the upper area at about 800 Ό is, 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 counterflow 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 inner 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 for Außengasumströmung in only one direction.
    An alternative plate pair 100 of two corrugated sheets 74 is shown in FIG. The two corrugated sheets 74 are not connected in opposite phase, as in the example shown in Fig. 5 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 shown in FIG. 11 can be seen. Fig. 11 shows the plate pair 100 in a perspective view obliquely from above.
    It is also possible that the two corrugated sheets 74 are joined together 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 shows an alternative longitudinal edge 104 to the longitudinal edge 82. 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.
    For the production of this longitudinal edge 104, the two corrugated sheets 74 are provided on one longitudinal side with a wider non-corrugated sheet metal 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. Then, the two corrugated sheets 74 are welded to two parallel welds 106 that extend along the entire longitudinal edge 104. Subsequently, a part of the planar portion of the protruding corrugated sheet 74 is folded 180 degrees, as shown in FIG. 12. Subsequently, the resulting laminated core of three sheet metal layers with a third weld 108 is completely welded through, also along the entire longitudinal edge 104th
    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.
    An alternative heat exchanger 110 is shown in FIG. 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 exchanger 22, 110 are stationary heat exchanger, the inner gas guide 32 extends perpendicularly 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.
    REFERENCE LIST 2 Solid fuel firing system 4 Solid fuel storage 6 Transport means 8 Transport means 10 Connection 12 Delivery unit 14 Back fire protection 16 Delivery means 18 Combustion chamber 20 Heat exchanger 22 Heat exchanger 24 Spark arrestor 26 Ash container 9/18 Austrian Patent Office AT12 584U1 2012-08-15 28 Housing 30 Wall 32 Internal gas guide 34 Outside gas guide 36 Flue gas inlet 38 Hot gas connection 40 Pull 42 Diverter 44 Pull 46 Collecting box 48 Hot gas discharge 50 Ash removal 54 Ambient air inlet 56 Opening 58 Cooling gas connection 60 Blower 62 Ambient air flow 64 Diverter 66 Diverter 68 Warm air duct 70 Blower 72 Warm air outlet 74 Corrugated sheet 76 Plate pair 78 Top plate 80 Base plate 82 Longitudinal edge 84 Tube 86 Segment 88 Segment 90 Longitudinal direction 92 gas space 94 opening 96 mixing area 98 outside gas guide 100 plate pair 102 inner gas chamber 104 longitudinal edge 106 weld seam 108 weld seam 110 heat exchanger 112 external gas guide 10/18
    权利要求:
    Claims (17)
    [1]
    Austrian Patent Office AT12 584U1 2012-08-15 Claims 1. A heat exchanger (22) for a mobile solid fuel firing installation (2) with a hot gas connection (38) and an internal gas duct (32), a cooling gas connection (58) and an external gas duct (34) and one two gas guides (32, 34) separating and heat-conducting wall (30) for producing a heat transfer from the hot to the colder gas, characterized in that the wall (30) comprises a plurality of interconnected corrugated sheets (74), between which two gas ducts (32, 34).
    [2]
    Second heat exchanger (22) according to claim 1, characterized in that the corrugated sheets (74) are each connected in pairs such that convex inner surface portions each pairwise and concave inner surface portions are in pairs opposite each other.
    [3]
    3. Heat exchanger (22) according to claim 2, characterized in that the pairs of corrugated sheets (76) are connected to each other at the convex inner surface portions.
    [4]
    4. Heat exchanger (22) according to claim 2 or 3, characterized in that concave inner surface portions in pairs form a tube (84).
    [5]
    5. Heat exchanger (22) according to claim 4, characterized in that the tubes (84) are formed such that their interiors in the region of their parallel course at least by juxtaposition of the corrugated sheets (74) are substantially separated from each other.
    [6]
    6. Heat exchanger (22) according to claim 4 or 5, characterized in that the inner gas guide (32) extends as a hot gas guide through the tubes (84).
    [7]
    7. Heat exchanger (22) according to any one of claims 2 to 6, characterized in that in each case two pairs of plates (76) are arranged to each other such that they form between them a wave-shaped gas space (92) as part of the outer gas guide.
    [8]
    8. Heat exchanger (22) according to claim 7, characterized in that between pairs of plates a plurality of tubes are formed and the gas space (92) perpendicular to the longitudinal direction of the tubes (84) can be flowed through.
    [9]
    9. The heat exchanger (22) according to any one of claims 2 to 8, characterized in that between two pairs of corrugated sheets (76) a third pair of corrugated sheets (76) is arranged such that convex outer surface portions of the third corrugated plate pair (76) between concave outer surface portions of the two surrounding pairs of corrugated iron (76) come to rest.
    [10]
    10. The heat exchanger (22) according to any one of the preceding claims, characterized in that the corrugated sheets (74) form a plurality of parallel tubes (84), and the outer gas guide (34) at least some of the tubes (84) outside crosses, in their direction is deflected and these tubes (84) crosses a second time outside.
    [11]
    11. The heat exchanger (22) according to any one of the preceding claims, characterized in that the corrugated sheets (74) form a plurality of parallel tubes (84), and the outer gas guide (34) by means of at least two baffles (64, 66) S-shaped is passed through the corrugated sheets (74) so that it extends transversely and parallel to the tubes (84).
    [12]
    12. The heat exchanger (22) according to any one of the preceding claims, characterized in that the corrugated sheets (74) form a plurality of parallel inner tubes (84) which are divided into two groups, each having a plurality of separate external gas channels, between which a mixing section (96) is arranged, open into the outer gas channels. 11/18 Austrian Patent Office AT12 584U1 2012-08-15
    [13]
    13. Heat exchanger (22) according to claim 12, characterized in that the inner gas guide (32) is guided successively through the two groups of inner tubes (84).
    [14]
    14. Heat exchanger (22) according to any one of the preceding claims, characterized in that the outer gas guide (34) extends in a counterflow to the inner gas guide (32).
    [15]
    15. Solid fuel combustion system with a combustion chamber, a heat exchanger (22) according to one of the preceding claims and a combustion chamber (18) with the hot gas connection (38) connecting the flue gas duct.
    [16]
    A solid fuel firing system (2) according to claim 15, characterized by an ambient air inlet (54), a hot air outlet (72), an ambient air duct (62) connecting the ambient air inlet (54) to the cooling gas port (58) of the heat exchanger (22), and a hot air duct (68) connecting an outside gas outlet of the heat exchanger (22) to the hot air outlet (72).
    [17]
    17. Mobile hay drying plant with a transportable frame (6, 8) in which a solid fuel burning plant (2) according to claim 15 or 16, and in particular a solid fuel container (4) are arranged. For this 6 sheets drawings 12/18
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE8223682U1|1982-07-31|1982-09-30|Ulbrich, geb. Spilker, Annmemarie, 5470 Andernach|Device for drying and retrieving freshly mown grass|
    DE3838894A1|1988-11-17|1990-05-23|Peter Voelskow|Waste disposal system which is composed of displaceable components|
    DE19538701A1|1994-10-20|1996-04-25|Bbk Blechbearbeitung & Kompone|Warm air heater|AT14751U1|2014-11-03|2016-05-15|Lasco Heutechnik Gmbh|Mobile solid fuel firing system|US1751725A|1926-01-07|1930-03-25|Walter M Cross|Heat exchanger|
    GB740380A|1953-02-20|1955-11-09|Parsons C A & Co Ltd|Improvements in and relating to heat exchangers|
    SE433532B|1978-05-22|1984-05-28|Lockmans Ing Byra Ab|LAMELLVERMEVEXLARE|
    FR2553182B1|1983-10-10|1988-05-06|Olivier Calmon|MOBILE HOT AIR GENERATOR|
    EP0321667B1|1987-12-22|1992-03-25|Hans Dr. Viessmann|Heater|WO2015090578A1|2013-12-18|2015-06-25|Mobil In Time Ag|Mobile warm air heating apparatus for solid fuels|
    AT14469U1|2014-03-12|2015-11-15|Lasco Heutechnik Gmbh|Mobile firing system|
    DE202014008158U1|2014-10-15|2014-10-30|Lasco Heutechnik Gmbh|Mobilie solid fuel firing system|
    WO2020143891A1|2019-01-08|2020-07-16|Machachou Abderrahim|Method for developing central air-conditioning, production of hot air and hot water|
    法律状态:
    2021-09-15| MK07| Expiry|Effective date: 20210731 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102011013284|2011-03-08|
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