DE102020203339A1 - Heat exchanger - Google Patents

Abstract

The invention relates to a heat exchanger (1). The heat exchanger (1) comprises a transfer block (2) made up of a plurality of first flow spaces (2a) and a plurality of second flow spaces (2b) which are arranged one above the other and alternately in a stacking direction (SR). The flow spaces (2a, 2b) are delimited to the outside by walls made of a stainless steel alloy and fluidically separated from one another. A first medium can flow through the first flow spaces (2a) and a second medium can flow through the second flow spaces (2b). In the second flow spaces (2b) there are corrugated structure plates (5) each made up of several individual ribs (6) which extend in the flow direction (MR) of the second medium and are adjacent transversely to the flow direction (MR) of the second medium. The corrugated structure plates (5) are materially connected to the walls of the associated second flow spaces (2b). According to the invention, the corrugated structure plates (5) are formed from a carrier material with a catalytic coating and form a catalyst in which the second medium can be chemically converted by means of catalysis.

Description

The invention relates to a heat exchanger according to the preamble of claim 1.

Catalysts are used in both internal combustion engine and fuel cell applications. In a fuel cell application, for example, the fuel - for example hydrogen and / or methane - can be obtained from biofuel in a catalyst - a so-called reformer - by means of catalysis, which is then used in the downstream fuel cell to generate energy. Usually, the fuel cannot be completely converted in the fuel cell, so that an unused residual amount of the fuel remains. The residual amount of fuel can then be chemically converted into further substances in a catalyst connected downstream of the fuel cell. In an internal combustion engine application, for example, the exhaust gas can be chemically converted into other substances in a catalytic converter. Since the catalysis in the catalytic converter takes place at a high temperature, the working medium is usually preheated to the required temperature by means of an upstream heat exchanger. Such a connection of the heat exchanger and the catalytic converter leads to disadvantages with regard to installation space, costs, weight and efficiency.

The object of the invention is therefore to provide an improved or at least alternative embodiment for a connection of a heat exchanger and a catalyst of the generic type, in which the disadvantages described are overcome.

According to the invention, this object is achieved by the subject matter of independent claim 1. Advantageous embodiments are the subject of the dependent claims.

A heat exchanger comprises a transfer block made up of a plurality of first flow spaces and a plurality of second flow spaces which are arranged one above the other and alternately in a stacking direction. A first medium can flow through the first flow spaces and a second medium can flow through the second flow spaces, so that the media in the transfer block can exchange heat with one another. The respective flow spaces are delimited to the outside by walls made of a stainless steel alloy and fluidically separated from one another. In the second flow spaces, corrugated structure plates each made up of a plurality of individual ribs are arranged, which extend in the flow direction of the second medium and are adjacent transversely to the flow direction of the second medium. The corrugated structure plates are materially connected to the walls of the associated second flow spaces. According to the invention, the corrugated structure plates are formed from a carrier material with a catalytic coating and form a catalyst in which the second medium can be chemically converted by means of catalysis. The catalyst is thus integrated in the heat exchanger according to the invention, so that compared to the conventional connection of a separate heat exchanger and a separate catalyst, costs, installation space and weight are reduced and efficiency is improved.

The transfer block of the heat exchanger according to the invention can be flowed through by the first medium and the second medium. The first medium or the second medium can be a liquid or a gas or a gas-liquid mixture. The direction of flow of the first medium and the direction of flow of the second medium are aligned transversely to the stacking direction. The flow of the second medium in the second flow spaces is predetermined by the embodiment of the individual ribs of the corrugated structure plates. In order to simplify the description, in the following the flow direction of the second medium is always assumed to be perpendicular to the stacking direction and along the main extension of the individual ribs of the corrugated structure plates. In addition, it is assumed that a direction defined transversely to the flow direction of the second medium is always perpendicular to the stacking direction and to the flow direction of the second medium. It goes without saying that the actual flow of the second medium can deviate slightly from the defined flow direction.

In one possible embodiment, the heat exchanger can be a flat tube heat exchanger. The transmission block is then formed from several flat tubes, between which spaces are formed. The flat tubes and the gaps alternate in the stacking direction. The first flow spaces can then be formed by the intermediate spaces and the second flow spaces can then be formed by the flat tubes with the corrugated structure plates. The walls of the flow spaces are then formed by the flat tubes. The second medium can flow through the flat tubes and the first medium can flow through the intermediate spaces, so that the two media in the transfer block are fluidically separated from one another. The corrugated structure plate arranged in the respective flat tube can be flowed around on both sides from the outside by the second medium, so that the second medium comes into direct contact with the catalytic coating and the catalysis can take place in the second medium. The corrugated structure plate thus provides a reaction surface for the catalysis. The respective corrugated structure plate is supported on both sides in the stacking direction on the associated flat tube away. Appropriately, the respective corrugated structure plate is materially connected to the flat tube at contact points. No fluid-tight material connection is required at these contact points. However, the integral connection can improve the heat transfer and the operational stability of the heat exchanger. The flat tubes are then made of the stainless steel alloy and the corrugated structure plates are formed from the carrier material with the catalytic coating.

In an alternative embodiment, the heat exchanger can be a stacked plate heat exchanger. The transfer block of the heat exchanger is then formed from several discs stacked one on top of the other. The first flow spaces and the second flow spaces are formed alternately between the adjacent disks. The flow spaces are then separated from one another by the disks and the walls of the flow spaces are then formed by the disks. The two media remain fluidically separated from one another via the panes and can exchange heat with one another. The corrugated structure plates are arranged in the second flow spaces, and are supported on adjacent disks on both sides in the stacking direction. The corrugated structure plate then provides a reaction surface for the catalysis of the second medium. Appropriately, the respective corrugated structure plate is materially connected to the associated panes at contact points. No fluid-tight material connection is required at these contact points. However, the integral connection can improve the heat transfer and the operational stability of the heat exchanger. The disks are then made of the stainless steel alloy and the corrugated structure plates are formed from the carrier material with the catalytic coating.

In principle, other alternative embodiments of the heat transfer are also conceivable.

In the heat exchanger according to the invention, the walls of the flow spaces and the corrugated structure plates are formed from different materials. The carrier material of the corrugated structure plates can be optimized with regard to the adhesion of the catalytic coating. The stainless steel alloy of the walls of the flow spaces, on the other hand, can be optimized with regard to the fluid-tight connection - for example soldering or welding - of the walls to one another and / or to other components of the heat exchanger. If the walls of the flow spaces are soldered to one another and / or to the other components of the heat exchanger, the stainless steel alloy can be optimized with regard to the adhesion of the solder. There is no need for a fluid-tight, cohesive connection between the carrier material of the corrugated structure plates and the stainless steel alloy of the walls of the flow spaces.

It can advantageously be provided that the stainless steel alloy is a ferritic chromium steel with a chromium content of 17-20%. The ferritic chrome steel can, for example, be a 1.4521 steel standardized according to DIN-EN-10088. Alternatively, the stainless steel alloy can be a ferritic chromium steel with a chromium content of 17-20% and a niobium coating or a ferritic chromium steel with a chromium content of 17-20% and a niobium additive. Due to the niobium coating or the addition of niobium, the chromium steel can be optimized in particular with regard to the adhesion of the solder.

The carrier material of the corrugated structure plates can be a chromium-aluminum steel with a chromium content of 17-20% and an aluminum content of 2-10%, preferably 3-7%. The chrome-aluminum steel can, for example, be a 1.4737 steel standardized according to DIN-EN-10088. Alternatively, the chrome-aluminum steel can be, for example, a 1.4767 steel standardized according to DIN-EN-10088. The carrier material can be optimized in particular with regard to good adhesion of the catalytic coating.

The catalytic coating can be an austenitic chromium-nickel steel with a chromium content of 17.5-19.5% and a nickel content of 8-10.5%. The austenitic chrome-nickel steel can, for example, be a 1.4301 steel standardized according to DIN-EN-10088. Alternatively, the catalytic coating can be an austenitic chromium-nickel-molybdenum steel with a chromium content of 16.5-18.5% and a nickel content of 10-13% and a molybdenum content of 2-2, 5%. The austenitic chrome-nickel-molybdenum steel can, for example, be a 1.4404 steel standardized according to DIN-EN-10088. Alternatively, the catalytic coating can be an austenitic chromium-nickel-silicon steel with a chromium content of 19-21% and a nickel content of 11-13% and a silicon content of 1.5-2.5% be. The austenitic chromium-nickel-silicon steel can, for example, be a 1.4828 steel standardized according to DIN-EN-10088. The catalytic coating can be optimized in particular with regard to good adhesion to the carrier material and to temperature resistance.

It goes without saying that the above-mentioned steels can also comprise further constituents - such as, for example, iron and / or molybdenum and / or titanium and / or silicon and / or carbon.

In an advantageous embodiment of the heat exchanger, the walls of the second flow spaces and the corrugated structure plates can be soldered to one another using a nickel-based solder. The nickel-based solder is preferably in the form of a nickel-based solder foil. The nickel-based solder can, for example, be a BNi-5 (9% Cr-10% Si-Ni) solder. Alternatively, the walls of the second flow spaces and the corrugated structure plates can also be welded to one another. The walls of the flow spaces can advantageously be soldered to one another and / or to the other components of the heat exchanger using a solder with a phosphorus content. The phosphorus content can improve the wetting of the stainless steel alloy of the walls and the soldering stability. In particular, gaps between the walls of the flow spaces and / or between the walls of the flow spaces and the other components of the heat exchanger can be better filled and the tightness of the soldered connection can thereby be improved. It is conceivable that during the manufacture of the heat exchanger, first the corrugated structure plates with the walls of the second flow spaces and then optionally the walls of the flow spaces with one another to form the transfer block and then the transfer block with the other components of the heat exchanger are materially connected. Alternatively, it is also conceivable that the walls of the flow spaces, the corrugated structure plates and the other components of the heat exchanger are materially connected to one another in one step. The material connection can be made by soldering or welding.

In the advantageous embodiment of the heat exchanger, it is provided that the product between the squared rib density of the respective corrugated structure plate and the wall thickness of the respective corrugated structure plate is between 0.5 / mm and 1.5 / mm, preferably between 0.6 / mm and 1.1 / mm, lies. With the product smaller than 0.8 / mm, a higher temperature can be reached on the corrugated structure sheets than with the product larger than 0.8 / mm. If, for example, a high degree of conversion is required in the catalysis of the second medium and this cannot be achieved due to the temperature of one of the media or the two media in the heat exchanger, the rib density and the wall thickness can be adjusted accordingly and the product less than 0.8 / mm be. This can be used, for example, in an internal combustion engine application to improve the efficiency of the catalysis during a cold start of the internal combustion engine. The product greater than 0.8 / mm, on the other hand, is to be preferred if there are particularly high demands on the heat transfer in the heat exchanger at high temperatures of the two media and above the working temperature of the catalytic coating.

If the rib density of the corrugated structure plate increases, the reaction surface of the corrugated structure plate available for catalysis also increases. When the rib density is increased, the degree of catalytic conversion and the heat transfer in the heat exchanger can accordingly be increased. However, as the density of ribs increases, so does the number of individual ribs. The higher the number of individual ribs, the smaller the cross-sections that can be flowed through, so that the risk of blocking increases. The cross-sections of the individual ribs through which the flow can flow can already be blocked when the corrugated structure plate is soldered to the walls of the second flow spaces or when the catalytic coating is applied. The wall thickness of the corrugated structure plate is dependent on the rib density due to the technical feasibility. With the high rib density, the wall thickness can be reduced for process and cost reasons, and with the low rib density and the high wall thickness, complex geometries can be implemented to improve heat transfer.

The wall thickness of the respective corrugated structure plate is defined in the stacking direction and can advantageously be between 0.05 mm and 0.2 mm. The wall thickness of the respective corrugated structure plate can preferably be between 0.08 mm and 0.16 mm. The rib density of the respective corrugated structure plate is determined by the ratio between the number of individual ribs in the corrugated structure plate and the width of the corrugated structure plate defined transversely to the direction of flow of the second medium. The rib density of the corrugated structure plate can be between 35 / dm and 150 / dm. The rib density can preferably be between 50 / dm and 150 / dm and more preferably between 70 / dm and 150 / dm.

It can advantageously be provided that the respective individual rib of the corrugated structure plate has two side walls oriented transversely to the direction of flow of the second medium. The side walls are each aligned at a wall angle to the stacking direction. The wall angle can advantageously be between 1 ° and 6 °, preferably between 2 ° and 4 °. Appropriately, the adjacent side walls are each designed to be inclined to one another and have an angle of inclination to one another which corresponds to the doubled wall angle. Accordingly, the angle of inclination is between 2 ° and 12 °, preferably between 4 ° and 8 °.

When designing the corrugated structure plate, the aim is in particular to achieve a high temperature on the corrugated structure plate in order to achieve the most efficient possible catalysis in the second medium. In addition to the rib density and the wall thickness, the geometry of the corrugated structure plate also plays a major role. Some advantageous designs of the corrugated structure plates are described below. It is understood, however, that this Configurations are only exemplary and other configurations of the corrugated structure plates are also conceivable.

In an advantageous embodiment of the corrugated structure plate, the corrugated structure plate can be a turbulence plate with several corrugated sections. The corrugated sections follow one another in the direction of flow of the second medium and are each formed from a plurality of individual ribs adjacent to the direction of flow of the second medium. The individual ribs of the respective adjacent corrugated sections are offset relative to one another transversely to the direction of flow of the second medium. For example, the offset of the individual ribs of the adjacent corrugated sections can be 1/2 or 1/3 of the width of the individual rib defined transversely to the direction of flow.

The length of the corrugated sections defined in the direction of flow of the second medium can advantageously be between 1 mm and 5 mm, preferably between 1 mm and 3 mm, more preferably between 1 mm and 2 mm. The rib density of the respective corrugated sections can be identical. The rib density can also be adapted in such a way that the risk of blocking in the turbulence plate is reduced and a high temperature can be achieved on the turbulence plate. The rib density of the respective corrugated section can advantageously be between 45 / dm and 75 / dm, preferably between 55 / dm and 65 / dm.

If the side walls of the individual ribs of the respective corrugated section have the wall angle defined above to the stacking direction, the product between the double transverse flow direction of the second medium defined width of the respective single rib and the wall angle can be less than 120 mm °, preferably less than 60 mm °. The geometries of the turbulence plate corresponding to the product of less than 120 mm ° can be realized with hot forming when the turbulence plate is manufactured. The geometries corresponding to the preferred product of less than 60 mm ° can also be realized with cold forming when producing the turbulence plate. Advantageously, the product between the width of the respective individual rib defined transversely to the direction of flow of the second medium and the sine of the wall angle can be smaller than the halved ratio between one and the rib density of the respective corrugation section defined transversely to the direction of flow of the second medium.

In a further development of the turbulence plate, it can advantageously be provided that the individual ribs of the adjacent shaft sections are aligned with one another at an angle of attack. The angle of attack can advantageously be between 136 ° and 176 °, preferably between 146 ° and 166 °. Advantageously, the individual ribs of the adjacent corrugated sections can each have an identical angle to the direction of flow of the second medium. This angle then corresponds to a halved difference between 180 ° and the angle of attack.

In an advantageous embodiment of the corrugated structure plate, the corrugated structure plate can be a corrugated ribbed plate with several individual ribs. The individual ribs extend in the flow direction of the second medium over the entire length of the corrugated rib plate. The rib density of the corrugated ribbed plate can advantageously be between 50 / dm and 150 / dm, preferably between 60 / dm and 150 / dm, more preferably between 70 / dm and 120 / dm.

Advantageously, the respective individual ribs can form a wave in the flow direction of the second medium with a wavelength defined in the flow direction of the second medium and with a wave width defined transversely to the flow direction of the second medium. The wavelength can advantageously be between 7 mm and 12 mm, preferably between 9 mm and 10 mm. The wave width can be between 0.5 mm and 2 mm, preferably between 1 mm and 1.5 mm.

Further important features and advantages of the invention emerge from the subclaims, from the drawings and from the associated description of the figures on the basis of the drawings.

It goes without saying that the features mentioned above and those yet to be explained below can be used not only in the respectively specified combination, but also in other combinations or on their own, without departing from the scope of the present invention.

Preferred exemplary embodiments of the invention are shown in the drawings and are explained in more detail in the following description, with the same reference symbols referring to the same or similar or functionally identical components.

• 1 eine Explosionsansicht eines erfindungsgemäßen Wärmeübertragers;
• 2 eine Explosionsansicht des erfindungsgemäßen Wärmeübertragers, der an einem zweiten Strömungsraum geschnitten ist;
• 3 eine Explosionsansicht des erfindungsgemäßen Wärmeübertragers, der an einem ersten Strömungsraum geschnitten;
• 4 eine Ansicht einer Wellstrukturplatte des erfindungsgemäßen Wärmeübertragers in Form einer Wellrippenplatte;
• 5 eine Draufsicht auf die Wellrippenplatte aus 4 mit einer Schnittebene A-A;
• 6 eine Seitenansicht der Wellrippenplatte aus 4 mit einer Schnittebene B-B;
• 7 und 8 Schnittansichten der Wellrippenplatte aus 4 in den Schnittebenen A-A und B-B;
• 9 eine Ansicht einer Wellstrukturplatte des erfindungsgemäßen Wärmeübertragers in Form einer Turbulenzplatte;
• 10 eine Draufsicht auf die Turbulenzplatte aus 9 mit einer Schnittebene C-C;
• 11 eine Schnittansicht der Turbulenzplatte aus 9 in der Schnittebene C-C;
• 12 eine Ansicht einer Wellstrukturplatte des erfindungsgemäßen Wärmeübertragers in Form einer abweichend ausgestalteten Turbulenzplatte;
• 13 eine Draufsicht auf die Turbulenzplatte aus 12 mit Schnittebenen D-D und E-E;
• 14 und 15 Schnittansichten der Turbulenzplatte aus 13 in den Schnittebenen D-D und E-E.

It show, each schematically

• 1 an exploded view of a heat exchanger according to the invention;
• 2 an exploded view of the heat exchanger according to the invention, which is cut at a second flow space;
• 3 an exploded view of the heat exchanger according to the invention, which is cut at a first flow space;
• 4th a view of a corrugated structure plate of the heat exchanger according to the invention in the form of a corrugated rib plate;
• 5 a top view of the corrugated fin plate 4th with a cutting plane AA;
• 6th a side view of the corrugated fin plate 4th with a cutting plane BB;
• 7th and 8th Sectional views of the corrugated ribbed plate 4th in the sectional planes AA and BB;
• 9 a view of a corrugated structure plate of the heat exchanger according to the invention in the form of a turbulence plate;
• 10 a top view of the turbulence plate 9 with a cutting plane CC;
• 11 a sectional view of the turbulence plate from 9 in the section plane CC;
• 12th a view of a corrugated structure plate of the heat exchanger according to the invention in the form of a differently designed turbulence plate;
• 13th a top view of the turbulence plate 12th with sectional planes DD and EE;
• 14th and 15th Sectional views of the turbulence plate 13th in the sectional planes DD and EE.

1 shows an exploded view of a heat exchanger according to the invention 1 . The heat exchanger 1 includes a transformer block 2 with several first flow spaces 2a and with a plurality of second flow spaces 2 B . The flow spaces 2a and 2 B are arranged one above the other and alternately in a stacking direction SR. The first flow spaces 2a are through a first medium and the second flow spaces 2 B can be flown through by a second medium. The flow spaces 2a and 2 B are delimited to the outside by walls and fluidically separated from one another. In 2 Figure 3 is an exploded view of the heat exchanger of the present invention 1 shown at one of the second flow spaces 2 B is cut. 3 shows an exploded view of the heat exchanger according to the invention 1 at one of the first flow spaces 2a is cut.

In the embodiment shown here, the heat exchanger is 1 a flat tube heat exchanger and the transfer block 2 is made up of several flat tubes 4b educated. The flat tubes 4b are arranged in rows spaced from one another in the stacking direction ST, so that between the flat tubes 4b Gaps 4a are formed. The spaces in between 4a can flow through the first medium and thus correspond to the first flow spaces 2a . The flat tubes 4b can flow through the second medium and correspond to the second flow spaces 2 B . In the flat tubes 4b are corrugated sheets 5 arranged. The corrugated structure sheets 5 have several individual ribs 6th and the second medium can flow around them on the outside. For a better understanding, in 1 one of the flat tubes 4b with the corrugated structure plate 5 outside of the transfer block 2 shown.

In the embodiment shown, the heat exchanger 1 also a housing 11 on that the transfer block 2 records. On the case 11 are a first entry 12a and first outlet 12b arranged for the first medium. The first medium consequently flows into the heat exchanger 1 about the first admission 12a one and is inside the case 11 in the interstices 4a distributed. Referring to 3 can do this in the spaces in between 4a Lead structures 13th be provided that the first medium from the initial inlet 12a to the first outlet 12b to lead. The lead structures 13th can for example be realized by separate ribs. Through the lead structures 13th can increase the efficiency of the heat exchanger 1 increase. From the spaces in between 4a the first medium flows through the first outlet 12b from the heat exchanger 1 Out.

Furthermore, the heat exchanger 1 in the embodiment shown, two tube sheets 3a and 3b into which the respective flat tubes 4b open on both sides. On the tube sheet 3a is a distribution box 9a and on the tube sheet 3b is a collection box 9b arranged for the second medium. In the distribution box 9a is a second entry 10a and in the collecting box 9b is a second outlet 10b shaped. The second medium consequently flows into the heat exchanger 1 via the second inlet 10a and is via the distribution box 9a in the flat tubes 4b distributed. In the collection box 9b becomes the second medium from the flat tubes 4b collected and via the second outlet 10b from the heat exchanger 1 led out. As in 2 indicated with arrows, the second medium is in the flat tubes 4b not diverted and flows through the respective corrugated structure plates 5 in a flow direction MR. The flow direction MR of the second medium is oriented transversely to the stacking direction SR and corresponds to the main extent of the individual ribs 6th of the respective corrugated structure sheets 5 or the longitudinal direction of the transmission block 2 or the longitudinal direction of the flat tubes 4b . As a result, a sufficient reaction surface can be provided for the catalysis of the second medium.

The flat tubes 4b are made of a stainless steel alloy and the corrugated structure plates 5 are formed from a carrier material with a catalytic coating. The corrugated structure sheets 5 form in the heat exchanger 1 a catalyst in which the second medium can be chemically converted by means of catalysis.

The stainless steel alloy can be, for example, a ferritic chromium steel 1.4521, optionally with a niobium coating or with a niobium additive. The carrier material of the corrugated structure panels 5 can be, for example, a chrome-aluminum steel 1.4737 or 1.4767. The catalytic coating can be an austenitic chromium-nickel steel 1.4301 or an austenitic chromium-nickel-molybdenum steel 1.4404 or an austenitic chromium-nickel-silicon steel 1.4828. The flat tubes 4b and the corrugated structure plates 5 can be soldered to one another using a nickel-based solder - for example a BNi-5 (9% Cr-10% Si-Ni) solder. Alternatively, the flat tubes 4b and the corrugated structure plates 5 be welded together. The flat tubes 4b can with the tube sheets 3a and 3b be soldered using a solder with a phosphorus content.

The respective corrugated structure plate 5 is at least characterized by the rib density RD - only indicated in the figures - and the wall thickness D. The wall thickness D is determined in the stacking direction SR and is between 0.05 mm and 0.2 mm, preferably between 0.08 mm and 0.16 mm. The rib density RD of the respective corrugated structure sheet 5 is by the ratio of the number of individual ribs 6th transverse to the direction of flow MR and the width B of the corrugated structure plate 5 determined transversely to the direction of flow MR. The rib density RD of the corrugated structure panel 5 is between 35 / dm and 150 / dm, preferably between 50 / dm and 150 / dm, more preferably between 70 / dm and 150 / dm. Furthermore, the product RD ² * D of the squared rib density RD and the wall thickness D is between 0.5 / mm and 1.5 / mm, preferably between 0.6 / mm and 1.1 / mm.

4th shows a view of the corrugated structure plate 5 of the heat exchanger 1 in the form of a - also in 1 and 2 shown - corrugated ribbed plate 5a . 5 shows a plan view of the corrugated fin plate 5a with a cutting plane AA. In 6th Fig. 3 is a side view of the corrugated fin plate 5a shown with a section plane BB. 7th and 8th show sectional views of the corrugated ribbed plate 5a in the cutting planes AA and BB. The corrugated ribbed plate 5a is characterized by the fact that the individual ribs 6th extending over the entire length L of the corrugated ribbed plate 5a extend and are wavy. A wavelength WL through the respective single rib 6th The wave formed is defined in the flow direction MR and is between 7 mm and 12 mm, preferably between 9 mm and 10 mm. A wave width WB of this wave is defined transversely to the flow direction MR and is between 0.5 mm and 2 mm, preferably between 1 mm and 1.5 mm. The rib density RD of the corrugated ribbed plate 5a can be between 50 / dm and 150 / dm, preferably between 60 / dm and 150 / dm, more preferably between 70 / dm and 120 / dm. As in 8th recognizable, shows the respective single rib 6th two side walls aligned transversely to the direction of flow MR 8a and 8b on. The side walls 8a and 8b are each aligned at a wall angle W to the stacking direction SR and inclined to one another. The wall angle W is between 1 ° and 6 °, preferably between 2 ° and 4 °.

9 shows a view of the corrugated structure plate 5 in the form of a turbulence plate 5b . In 10 Figure 3 is a top plan view of the turbulence plate 5b shown with a section plane CC. 11 Figure 3 shows a sectional view of the turbulence plate 5b in the section plane CC. The turbulence plate 5b is characterized by several corrugated sections 7th which follow one another in the direction of flow MR. The respective corrugated sections 7th show the single ribs 6th which are adjacent transversely to the flow direction MR. The neighboring corrugated sections 7th are, however, offset by an offset V transversely to the direction of flow MR. As a result, the individual ribs also point 6th of the adjacent corrugation sections 7th the offset V to each other. The offset V is here 1/2 of the width BR of the individual rib 6th , as in particular in 11 is recognizable.

The length LA of the corrugated sections 7th is defined in the direction of flow MR and can be between 2 mm and 6 mm, preferably between 2 mm and 4 mm. The width BR of the respective single rib 6th is defined transversely to the direction of flow MR and is between 1 mm and 5 mm, preferably between 1 mm and 3 mm, more preferably between 1 mm and 2 mm. The rib density RD of the respective corrugated sections 7th is identical and is between 45 / dm and 75 / dm, preferably between 55 / dm and 65 / dm. As in particular in 11 can be seen, show the side walls 8a and 8b of the respective individual ribs 6th in each case the wall angle W to the stacking direction SR. The wall angle W is between 1 ° and 6 °, preferably between 2 ° and 4 °. The product 2 * BR * W between twice the width BR and the wall angle W can be less than 120 mm °, preferably less than 60 mm °. The product BR * sin (W) between the width BR and the sine of the wall angle W can also be smaller than the halved ratio 1 / (2 * RD) be between one and the rib density RD.

12th shows a view of the corrugated structure plate 5 in the form of a differently designed turbulence plate 5c . 13th shows a top view of the turbulence plate 5c with the sectional planes DD and EE. In 14th and 15th are sectional views of the turbulence plate 5c shown in the sectional planes DD and EE. The turbulence plate 5c is characterized by the fact that the individual ribs 6th of the adjacent shaft sections 7th are aligned at an angle of attack A. The angle of incidence A can be between 136 ° and 176 °, preferably between 146 ° and 166 °. Otherwise, the turbulence plate shown here corresponds to 5c the turbulence plate 5b the end 9-11 .

Claims (10)

Heat exchanger (1), - wherein the heat exchanger (1) comprises a transfer block (2) with a plurality of first flow spaces (2a) and with a plurality of second flow spaces (2b), which are arranged one above the other and alternately in a stacking direction (SR), - the Flow spaces (2a, 2b) are delimited to the outside by walls made of a stainless steel alloy and fluidically separated from one another, - wherein the first flow spaces (2a) can be flowed through by a first medium and the second flow spaces (2b) by a second medium, so that the media can exchange heat with one another in the transfer block (2), - corrugated structure plates (5) each made up of several individual ribs (6) arranged in the second flow spaces (2b) and connected to the walls of the associated second flow spaces (2b) in a materially bonded manner, and - the individual ribs (6) extend in the flow direction (MR) of the second medium and are adjacent transversely to the flow direction (MR) of the second medium rt, characterized in that the corrugated structure plates (5) are formed from a carrier material with a catalytic coating and form a catalyst in which the second medium can be chemically converted by means of catalysis. Heat exchanger after Claim 1 Characterized in that - the stainless steel alloy is a ferritic chromium steel with a chromium content of 17-20% or a ferritic chromium steel with a chromium content of 17-20% and a niobium coating or a ferritic niobium-chromium -Steel with a chromium proportion of 17-20% and a niobium addition, and / or - that the carrier material is a chromium-aluminum steel with a chromium proportion of 17-20% and an aluminum proportion of 2 -10%, preferably from 3-7%, and / or that the catalytic coating is an austenitic chromium-nickel steel with a chromium content of 17.5-19.5% and a nickel content of 8 -10.5% or an austenitic chromium-nickel-molybdenum steel with a chromium content of 16.5-18.5% and a nickel content of 10-13% and a molybdenum content of 2-2 , 5% or an austenitic chromium-nickel-silicon steel with a chromium content of 19-21% and a nickel content of 11-13% and a silicon content of 1.5-2.5%. Heat exchanger after Claim 1 or 2 , characterized in - that the walls of the second flow spaces (2b) and the corrugated structure plates (5) are soldered or welded to one another via a nickel-based solder, preferably in the form of a nickel-based solder foil, and / or - that the walls of the flow spaces (2a , 2b) are soldered together using a solder with a phosphorus content. Heat exchanger according to one of the Claims 1 until 3 , characterized in that the product (RD ^{2 *} D) between the squared rib density (RD) of the respective corrugated structure plate (5) and the wall thickness (D) of the respective corrugated structure plate (5) between 0.5 / mm and 1.5 / mm , preferably between 0.6 / mm and 1.1 / mm. Heat exchanger according to one of the Claims 1 until 4th , characterized in that the respective single rib (6) of the corrugated structure plate (5) has two side walls (8a, 8b) aligned transversely to the flow direction (MR) of the second medium, each of which is aligned at a wall angle (W) to the stacking direction (SR) . Heat exchanger according to one of the Claims 1 until 5 , characterized in - that the corrugated structure plate (5) is a turbulence plate (5b, 5c) with several corrugated sections (7) following one another in the flow direction (MR) of the second medium, and - that the individual ribs (6) of the respective adjacent corrugated sections (7 ) are offset relative to one another transversely to the direction of flow (MR) of the second medium. Heat exchanger after Claim 5 and 6th Characterized in - that the product (2 * BR * W) between the double cross-flow direction (MD) of the second medium defined width (BR) of the respective individual rib (6) and the wall angle (W) of less than 120 mm °, preferably less 60 mm °, and / or - that the product (BR * sin (W)) between the transverse flow direction (MR) of the second medium defined width (BR) of the respective single rib (6) and the sine of the wall angle (sin ( W)) is less than the halved ratio (1 / (2 * RD)) between one and the rib density (RD) of the respective wall section (7) defined transversely to the direction of flow (MR) of the second medium. Heat exchanger after Claim 6 or 7th , characterized in that the individual ribs (6) of the adjacent shaft sections (7) are aligned with one another at an angle of attack (A). Heat exchanger according to one of the Claims 1 until 5 , characterized in that the corrugated structure plate (5) is a corrugated rib plate (5a), the individual ribs (6) of the corrugated rib plate (5a) extending in the flow direction (MR) of the second medium over the entire length (L) of the corrugated ribbed plate (5a). Heat exchanger after Claim 9 , characterized in that the respective individual ribs (6) in the flow direction (MR) of the second medium have a wave with a wavelength (WL) defined in the flow direction (MR) of the second medium and with a wave width defined transversely to the flow direction (MR) of the second medium (WB) form.

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