EP3546873A1 - Radial cross-current heat transformer - Google Patents

Abstract

The invention relates to a suitable for the high temperature range up to 1100 ° C heat exchanger, which ensures efficient heat transfer between two flowing in spatially separated, concentrically arranged chambers fluids, wherein at least the inner chamber has a large dimension up to several meters transverse to the flow direction of in this Chamber having flowing fluid.

Description

Field of the invention

The field of the invention relates to renewable energies, in particular the efficiency increase in the production of renewable energies by reducing the release of process heat to the environment.

State of the art

Conventional power plants, based on the fossil fuels coal, oil, natural gas and nuclear fuel, discharge the process waste heat generated during their operation usually unused via cooling towers in the environment. They therefore only achieve efficiencies of less than 40%, older coal plants even under 20%.

The transition to a zero-emission energy industry that is needed worldwide requires not only the transition to renewable energy sources (solar heat, biogas, straw, wood), but also an efficiency revolution: the efficiency of power plants based on renewable energy sources must be higher than that of conventional power plants drastically increased. For this, the processes at higher temperatures, d. H. in the high temperature (HT) range (> 800 ° C, preferably up to 1100 ° C), and with large temperature differences, resulting process waste heat must be used optimally. Dynamic storage for large volumes of renewable energy is required, which in addition to the limited available mechanical (eg pumped storage, compressed air storage) and chemical storage (costly batteries) and thermal energy storage are required, which are suitable for returning this thermal energy in power plant processes ,

Efficient, durable and robust heat exchangers (WÜ), which are also known to the person skilled in the art as heat exchangers, are required for the energy transfer between different media to be ensured.

In heat exchangers flow two fluids F1, F2 with different initial temperature in directly adjacent chambers, which are separated by a highly heat-conducting partition, z. B. a metallic partition, are separated. In this case, heat energy is transferred from the fluid of higher temperature via the highly heat-conductive partition to the fluid of lower temperature. The term "fluid" in this application includes gases, liquids and supercritical media.

The expert WÜ are known in a variety of constructions, eg. B. Rohrbündel-WÜ, plate-WÜ, spiral-WÜ, double-pipe WÜ. The components of these usually made of metallic materials WÜ are structurally unevenly thermally stressed. This results in thermal stresses that limit their upper service temperature below 800 ° C, so they are not suitable for the HT range.

For the HT range currently only WÜ are known that non-metallic components in a complex design, eg. As of ceramic and / or glass fiber materials, and metallic components combine. These high-temperature heat exchangers (HT-WÜ) have a high failure rate in normal operation due to damage caused by thermal stresses. In addition, ceramic and glass-fiber materials generally have a low thermal conductivity compared to metals, which is disadvantageous for use as a heat exchanger. Special ceramics with high thermal conductivity, z. Based on SiC and AlN are available but very expensive. Furthermore, the processing of these materials is much more expensive compared to metals. Their use is therefore uneconomical.

The efficiency of heat transfer is also limited by the dimensions of the chambers in which the fluids F1 and F2 of different temperatures T ₁ and T ₂ flow, in particular when there is a laminar or near-laminar flow. Since fluids usually have a low thermal conductivity, only a slow heat transfer takes place transversely to the flow direction. In known double-tube WÜ, comprising an inner tube and concentrically extending outer tube, this leads in the case T ₁ < T ₂ that the flowing fluid in the inner tube (fluid F2), although efficient heat energy from its outer, adjacent to the highly heat-conductive partition layers on the other side of the partition wall flowing fluid (fluid F1) transmits, but that only slowly heat energy flows from the areas near the tube axis. The same applies to a reverse heat flow, ie the case T ₁ > T ₂ . In order to such a double-pipe WÜ works efficiently, it must have small pipe diameters in the order of 1 cm.

In industrial processes, however, process chambers with large diameters are used, in thermal power plants z. B. combustion chambers with an immediately associated, arranged above exhaust shaft, in chemical plants z. B. with positive or negative pressure acted upon reaction chambers, which are connected to a closed piping system. An efficient transfer of heat energy from a fluid laminar fluid F2 flowing approximately laminarly in the process chamber to a fluid F1, again explained below for T ₁ < T ₂ , which flows in a cylinder-ring-like chamber surrounding the process chamber, is not possible. Instead of a desired homogeneous temperature field (approximately constant temperature on (imaginary) sectional areas transverse to the flow direction), a temperature gradient builds up with maximum temperature in the region of the axis of the process chamber. Accordingly, in the case of T ₁ > T _2, a temperature gradient of minimum temperature builds up in the region of the axis of the process chamber. It would be conceivable to enhance the heat transfer by convection by the fluid F2 is put into turbulence, but that would be energy consuming and thus uneconomical.

It is not known from the prior art that WÜ ensures efficient heat transfer from the entire volume of a fluid F2 flowing in a large diameter tubular inner chamber to a fluid F1 which flows in an outer chamber surrounding the inner chamber in a cylindrically annular manner. Diameters from about 10 cm up to several meters are defined as large diameters in this application.

Object of the invention

The object of the present invention is to provide a HT-WÜ, which has a simple construction, efficient heat transfer (high heat flux) between two flowing in spatially separated chambers fluids F1 and F2 guaranteed, wherein at least one of the chambers has a large dimension (approx 10 cm or larger) across the flow direction, which is suitable for operation in the HT range is suitable up to 1100 ° C and thereby has a high robustness, cycle resistance (thermal shock resistance) and service life. The HT-WÜ should be suitable for industrial plants, especially power plants and chemical reactors. It should be constructed of materials whose costs are acceptable for the respective application.

Inventive solution of the problem

The object of the invention is achieved by a radial cross-flow heat exchanger (R-KS-WÜ) with the features of claim 1 and the associated dependent claims, by its particular embodiments as an integrated heat exchanger and as a stand-alone heat exchanger with the features of the claims 7 to 9 and by a modular heat exchanger unit with the features of claim 10.

Detailed description of the solution according to the invention Structure of the R-KS-WÜ

The R-KS-WÜ 10 according to the invention is in Fig. 1 schematically in isometric projection according to DIN ISO 5456-3 and in Fig. 2a-c shown in side view, wherein Fig. 2a the components, Fig. 2b and 2c Play the dimensions. It has an outer tube AR, which is designed in the form of a cylinder jacket and whose diameter D , as explained in Example 1, according to the geometry of a plant in which the R-KS-WÜ is installed and to be used, is selected. The preferred diameter D of the outer tube AR is in the range 0.3 m ≤ D ≤ 2.0 m, when the R-KS-WÜ is designed as a stand-alone heat exchanger (SA-WÜ), and in the range 1.5 m ≤ D ≤ 10 m when the R-KS-WÜ is designed as an integrated heat exchanger (I-WÜ). The range is preferably 2.5 m ≦ D ≦ 4 m. The height H of the outer tube AR should be selected from the range 0.4 D ≤ H ≤ 1.8 D.

The outer tube AR of height H has two sections of equal height H / 2, which are referred to below as outer rings AR ₁ and AR ₂ . A division into sections of different heights H ₁ , H ₂ with H ₁ + H ₂ = H would be possible, but is impractical and will not be described in detail.

The outer rings AR ₁ and AR ₂ each have a row R ₁ and R ₂ with a plurality of slot-shaped openings S _A1 and S _A2 of length L ₁ and L ₂ , which extend into the vicinity of the upper edge and the lower edge of the outer rings , In turn, equal lengths L ₁ = L ₂ = L and equal distances a from the upper and lower edges of the outer rings are preferred. The openings S ₁ , S ₂ may in particular have the shape of an elongated rectangle or be designed as elongated holes in which the narrow sides of the rectangle are replaced by semicircles. A first fluid F1 can be supplied via the openings S _A1 and can be discharged via the openings S _A2 . Preferably, the openings S _A1 , S _{A2 are distributed} equidistantly over the circumference of the outer rings AR ₁ , AR ₂ , ie have, viewed from the cylinder axis, equidistant angular distances. Variable angular distances would be possible, but complicate the structure unnecessarily and affect the operation of the R-KS-WÜ and the homogeneity of the flow profile of a flowing in the axial direction of the second fluid F2. Preferably, both outer rings also have the same number N , shape and arrangement of the openings S _A1 , S _A2 , so that they are made completely identical. In this case, two openings S _A1 and S _A2 can be exactly next to each other, but they can also, as in Fig. 1 by way of example, have an arbitrary offset < πD / N relative to one another.

On the outside of the outer tube AR, as in Fig. 2a and 2b recognizable, Umlenkrippen ULR attached, which serve to the parallel to the axis A of the R-KS-WÜ incoming first fluid F1 to the openings S _A1 zuzuleneken and flowing out of the openings S _A2 first fluid F1 again in a direction parallel to the axis A of To redirect R-KS-WÜ. The Umlenkrippen ULR thus have the function of vanes.

Furthermore, the R-KS-WÜ has a cylindrical, ie tubular, running deflection U with the diameter d . The diameter d of the deflection chamber is smaller than the diameter D of the outer tube AR. It is located, like Fig. 1 shows, inside the outer tube AR and is mounted concentrically to this, so that the arrangement an axis of symmetry, hereinafter referred to as axis A receives. The diameter d of the deflection chamber is to be selected from the range ( D - 0.7 m) ≤ d ≤ ( D - 0.2 m).

In contrast to the outer tube AR, the deflection chamber U is not designed as a cylinder jacket, but as a hollow cylinder closed on both sides with a cylinder jacket Z _U and closures G _U on its base surface and D _U on its top surface. In Fig. 2a is the hidden deflection U marked with the closures G _U and D _U by a dashed line. The height of this arrangement (deflection U with the closures G _U and D _U ) corresponds to the height H of the outer tube AR. (In Fig. 1 the closure G _{U is} omitted in order to look into the interior of the deflection chamber U.) The closures may be in the form of circular plates, for. B. as blind flanges, executed. It is advantageous to give the closures, instead of a flat shape, a flow-dynamically favorable shape, ie to carry them out as plates instead of outwardly arched paraboloids. The cylinder jacket Z _U is equipped with two rows of slot-shaped openings S _U1, S _U2 , the same length L and, relative to the axis A of the deflection chamber U, the same angular distances as the openings S _A1 , S _{A2 of} the outer rings AR ₁ and AR ₂ to have. The two rows of openings S _U1 , S _U2 are parallel to each other at a distance of 2 a . Their distance from the base or top surface of the deflection U is in each case a . The width B _{U of} these openings is determined by their number N and by the circumference πd of the deflection chamber U. For reasons of mechanical stability, the summed width of all openings should reach only half the circumference of the deflection chamber U. Thus, for the width B _{U of} the openings S _U1 , S _U2, an upper limit B _U = πd / 2 N results . Smaller widths are possible, but should not be below B _U = πd / 4 N.

The deflection chamber U is positioned in the interior of the arrangement with the outer rings AR ₁ and AR ₂ that the first row of their openings S _U1 in a plane, ie at the same height, with the openings S _{A1 of} the first outer ring AR ₁ , the second Row of their openings S _U2 in a plane, ie at the same height, with the openings S _{A2 of} the second outer ring AR ₂ is located. Preferably, the openings S _U1 , S _{U2 are} distributed equidistantly in both rows over the circumference of the deflection chamber U.

Each opening S _U1 is connected via a designed as a hollow body heat exchanger element (hereinafter: WÜ element) WE ₁ with an opening S _A1 . Likewise, each opening S _{U2 is} connected via a trained as a hollow body WÜ element WE ₂ with an opening S _A2 . For this purpose, the WÜ element WE ₁ or WE _{2 is designed} as a hollow body whose internal dimensions are adapted to the dimensions of the openings S _A1 , S _A2 , S _U1 , S _U2 . The length of the cross section of the WÜ elements is consistent with the length L of these openings. The width B _{WE of} its cross section is selected from the range 3 mm ≤ B _WE ≤ 20 mm. It is possible to change the width B _{WE of} the cross section on the length of the WÜ element. For space reasons, the WÜ element near the deflection chamber U should have a cross-section with a small width B _WE , which can be increased with increasing distance from the deflection chamber U, ie towards the outside. The shape of the cross section is extended by an elongated rectangle with possibly rounded corners in an oval or a circle. The wall thickness of the WÜ elements is preferably in the range between 0.5 mm and 2.5 mm. The expert selects the exact value for the wall thickness from the expected during operation of the R-KS-WÜ pressure differences between the fluids F1 and F2.

The walls of the outer tube AR and the deflection chamber are less involved in the heat transfer compared to the walls of the WÜ elements and can therefore be designed with a higher wall thickness. Preferably, the wall thicknesses of the outer tube AR and the deflection chamber U are in the range between 1 mm and 5 mm. Again, the expert selects the exact value based on the expected operating conditions, in particular the expected pressure differences and temperatures from.

For efficient heat transfer, the lowest possible wall thicknesses should be selected for the WÜ elements. The outer tube AR and the deflection chamber U are not so much involved in the heat transfer and can therefore be provided with a higher wall thickness.

The band-shaped WÜ elements can be guided on the shortest path, ie in a straight line, from an opening S _U1 or S _U2 to the nearest opening S _A1 or S _A2 . Preferably, however, they are curved blade-shaped and are guided to an offset on the outer ring opening S _A1 and _A2 S. The advantages of this blade-shaped embodiment are explained in Example 1, Section 1b). The blade-shaped bend of the WÜ elements follows a circular arc. It describes a pitch circle whose size ρ is to be selected from the range 100 ° to 200 °. The blade diameter S , defined by The diameter of the circle to which the circular arc described by the blade cross-section belongs is selected from the range 0.6 · ( D - d ) ≦ S ≦ 0.9 · ( D - d ). Instead of a circular arc, it is also possible to select a geometry deviating from the circular shape, for example, a spiral bending of the WÜ elements can take place. The amount of heat transferred by the WÜ elements WE ₁ , WE ₂ can be increased if the WÜ elements are designed as fin tubes, ie, fin-like planar structures are placed outside on the WÜ elements WE ₁ , WE ₂ . Fin tubes are known in the art. Another preferred way to increase the amount of heat transferred is to use rib members, e.g. B. corrugated fins which are installed between adjacent WÜ elements WE ₁ and / or WE ₂ . Also suitable are so-called lamellar gratings, which have intersecting rib elements. The installation of rib elements is explained in detail in Example 1, Section 1b).

Fig. 3 , A front view of the outer ring AR ₁ with the WÜ elements WE ₁ , shows for a selected circular arcuate WÜ element WE ₁ * the associated blade diameter 5 and the pitch circle ρ and, by way of example, a single corrugated fin WR. The axis A directed perpendicular to the plane of the drawing is symbolized by a dot.

The number N of blade-shaped WÜ elements to be connected to an outer ring is limited by the diameter d of the deflection chamber U. It should be selected from the range 50 · d / [m] ≤ N ≤ 150 · d / [m], where d is the distance in meters. N WÜ elements WE ₁ and to the outer ring AR ₂ N WÜ elements WE ₂ are thus connected to the outer ring AR ₁ . This results in a first flow path from the openings S _{A1 of} the first outer ring AR ₁ through the WÜ elements WE ₁ , the first row of the openings S _{U1 of} the deflection chamber U, the deflection chamber U, the second row of openings S _{U2 of} the deflection chamber, the WÜ Elements WE ₂ to the openings S _{A2 of} the second outer ring AR ₂ formed, in which the first fluid F1 is flowable.

The scoop-shaped WÜ elements WE ₁ and WE ₂ may be bent in the same direction but, in a preferred embodiment, they may also be bent in opposite directions. When bending in opposite directions, a more favorable flow guidance is achieved, since the swirl of the flow, based on the outer tube AR and the deflection chamber U, is maintained. The scoop-shaped design of the WÜ elements WE ₁ and WE ₂ has several technical advantageous effects, which are explained in detail in Example 1, Section 1b).

Through the outer tube AR, a second flow path, in which the second fluid F2 is flowable, predetermined, which is parallel to the common axis of the outer tube AR and the concentrically positioned deflection U through the spaces between the WÜ elements WE ₁ and WE ₂ passes through and the inner wall of the outer tube AR is limited.

Such a defined flow path must also be provided for the supply and discharge of the first fluid F1. For this purpose, it is necessary to provide a cladding tube HR with a diameter D _HR which is greater than the diameter D of the outer tube AR. Preferably, the cladding tube diameter D _{HR is selected} from the interval 1.05 D <D _HR <1.3 D. The cladding tube HR and the outer tube AR then define a cylindrical ring-like space with an annular cross-section. This cylindrical space, hereinafter referred to as outer shell AH, forms the flow path for the supply and discharge of the first fluid F1.

1. 1. Der R-KS-WÜ wird mit einer technischen Anlage verbunden, die eine zylindrische Wand aufweist. Dazu wird der Durchmesser seines Außenrohres AR so gewählt, das er mit dem Durchmesser der zylindrischen Wand übereinstimmt. Das Außenrohr AR wird, z. B. über eine Flanschverbindung, dicht mit der zylindrischen Wand verbunden, sodass es diese verlängert. Der verlängerte Bereich kann mit einem R-KS-WÜ oder einer Reihenschaltung aus mehreren R-KS-WÜ ausgestattet werden. Um einen räumlich begrenzten Strömungsweg für das erste Fluid F1 zu schaffen, wird ein zur zylindrischen Wand konzentrisches Hüllrohr HR bereitgestellt, das eine gemeinsame zweite, äußere Wand für die Anlage und für den verlängerten Bereich mit dem R-KS-WÜ bzw. der Reihenschaltung aus mehreren R-KS-WÜ bildet. Solche mit einer bestehenden Anlage verbundenen R-KS-WÜ werden nachfolgend als integrierte Wärmeübertrager (I-WÜ) bezeichnet und in Ausführungsbeispiel 1 detailliert beschrieben.
2. 2. Der R-KS-WÜ wird als anlagenunabhängiger Wärmeüberträger mit einem Außenrohr AR und einem Hüllrohr HR ausgestattet. Ein solcher R-KS-WÜ, der nicht in eine bestehende Anlage integriert ist, wird nachfolgend als Stand-Alone-Wärmeübertrager (SA-WÜ) bezeichnet und in Ausführungsbeispiel 2 detailliert beschrieben. Er kann für einen Volumenstromdurchsatz von 200 Nm³/h bis 2500 Nm³/h, bevorzugt ca. 1.000 Nm³/h (Normkubikmeter pro Stunde) ausgelegt werden.

Two substantially different embodiments are to be distinguished:

1. 1. The R-KS-WÜ is connected to a technical system, which has a cylindrical wall. For this purpose, the diameter of its outer tube AR is chosen so that it coincides with the diameter of the cylindrical wall. The outer tube AR is, for. B. via a flange, tightly connected to the cylindrical wall, so that it extends. The extended range can be equipped with an R-KS-WÜ or a series connection of several R-KS-WÜ. In order to provide a spatially limited flow path for the first fluid F1, a concentric to the cylindrical wall envelope tube HR is provided, which has a common second outer wall for the plant and for the extended area with the R-KS-WÜ or the series circuit several R-KS-WÜ forms. Such connected to an existing system R-KS-WÜ are hereinafter referred to as integrated heat exchanger (I-WÜ) and described in detail in Example 1.
2. 2. The R-KS-WÜ is equipped as an installation-independent heat exchanger with an outer tube AR and a cladding tube HR. Such an R-KS-WÜ, which is not integrated into an existing system, is hereinafter referred to as a stand-alone heat exchanger (SA-WÜ) and described in detail in Example 2. It can be designed for a volume flow rate of 200 Nm ³ / h to 2500 Nm ³ / h, preferably about 1,000 Nm ³ / h (standard cubic meter per hour).

It is always possible to realize a series connection of several R-KS-WÜ. It can be made up of several I-WÜ as well as several SA-WÜ. Such a series connection is referred to below as a modular heat exchanger unit. In the case of SA-WÜ, it is also possible to realize a modular heat exchanger unit as a parallel connection of several SA-WÜ, whereby the volume flow rate multiplied according to the number of SA-WÜ.

Fig. 4 shows in a simplified schematic representation of a section through an R-KS-WÜ according to Fig. 2a which is surrounded by a limited by a cladding HR cylindrical outer shell AH. The symmetry axis A, not shown, lies in the cutting plane and runs along the axis of the deflection chamber U. The base and top surfaces of the deflection chamber U are shown completely (not as a section). An up to the cladding tube HR reaching from the outer tube AR separator TV divides the outer shell AH in a first region 20 in which the supply of the first fluid F1 to the WÜ elements WE ₁ is carried out and in a second region 22 in which the removal of the first Fluids F1 from the WÜ elements WE ₂ takes place. The flow path of the first fluid F1 is marked by arrows. The scoop-shaped WÜ elements WE ₁ , WE ₂ are simplified symbolized by two planar connections. The separating device TV separates the cylinder-ring-like outer casing AH into two sections 20 and 22. A first fluid F1 fed to the outer casing flows from the section 20 of the outer casing AH through the WÜ elements WE ₁ to the deflection chamber U, flows through the latter and flows through the WÜ elements WE ₂ to section 22 of the outer shell AH. In the areas 20 and 22 of the outer shell AH, the first fluid F1 using the Fig. 2a and 2b known (in Fig. 4 For technical reasons not shown) Umlenkrippen guided, which direct the first fluid F1 in the section 20 in the direction of the openings S _A1 and in the section 22 of the openings S _{A2 back} in the original direction. The Umlenkrippen are placed on the outer tube AR and are designed so high that they reach into the vicinity of the cladding tube HR. Preferably, they lie with their upper edges on the cladding tube HR, but no absolutely tight connection between the cladding tube and the Umlenkrippen, z. B. produced by welding, is required. It may also remain a gap of 0.5 mm to 5 mm between the upper edges of the baffles and the cladding.

As in Fig. 4 indicated by the horizontal dashed lines, which extend the cladding tube HR and the outer tube AR, it is possible to continue the outer shell AH over its entire annular cross-section as far as desired in order to realize an I-WÜ and / or a series connection of I-WÜ , Furthermore, it is possible to lead away from individual sections of the outer shell AH one or more pipe connections to realize a SA-WÜ or a series circuit of SA-WÜ. The supply and discharge of the first fluid F1 takes place in both cases parallel to the axis of the arrangement. Before and behind the separator TV takes place, supported by the Fig. 2a, b known, in Fig. 4 Deflection ribs, not shown, a deflection of the flow by 90 ° in order to supply the first fluid F1 to the WÜ elements WE ₁ or to remove it from the WÜ elements WE ₂ . These deflections brake the flow, lead to the formation of vortices and introduce turbulence into the laminar flow profile of the first fluid F1.

Fig. 5 shows a schematic representation of an improved embodiment of a SA-WÜ, which avoids these adverse effects. It differs from the embodiment in FIG Fig. 4 in that the openings of the outer shell AH, which ensure the supply and discharge of the first fluid F1 parallel to the axis A of the arrangement, are closed by closures 24. They are replaced by openings 26 in the cladding tube HR, which allow the connection of pipes through which the first fluid F1 can be fed perpendicular to the axis of the arrangement. Several such connection possibilities for the supply as well as for the discharge of the first fluid F1 can be provided, which are distributed over the circumference of the cladding tube HR, preferably at uniform angular intervals. Preferably, the pipe connections are made inclined so that a tangential Supplying the first fluid F1 into the outer shell AH takes place, whereby a circular flow is generated in the outer shell. The direction of inclination of the pipe connections, which determines the direction of rotation of the circular flow, is selected so that it corresponds to the direction of rotation of the WÜ elements WE ₁ and WE ₂ connected to the outer pipe AR. Thus, the first fluid F1 is almost rectilinearly guided into the N channels formed by the WÜ elements WE ₁ and led out almost in a straight line from the N channels formed by the WÜ elements WE ₂ . The arrangement according to Fig. 4 necessary adverse deflections of the flow of the first fluid F1 by 90 ° in the supply to the WÜ elements WE ₁ and the discharge of the WÜ elements WE ₂ and their adverse effects are thus avoided. The number of openings 26 for pipe connections for the supply and discharge of the first fluid F1 can each be selected between 1 and N. In the case of N openings 26 thus each WÜ element is assigned a port. In each case 2 to 6 openings 26 are preferred for the supply and discharge of the first fluid F1. Further explanations are given in Example 2 in conjunction with Fig. 11 given.

Fig. 4 and 5 also show the position of a connecting element VE in the deflection U. This connection element is in Example 1, Section 1b), explained in more detail, as well as the conditions are called, under which it is necessary or dispensable.

All components of the R-KS-WÜ are made of HT-resistant materials. For reasons of cost, HT-solid metals are preferred, in particular heat-resistant steel. Suitable is z. B. grade 1.4841 steel (in accordance with standard EN 10095), which has high oxidation and chemical resistance at temperatures up to 1100 ° C (source: https://www.stahl-markt.de/download/datenblatt%204841.pdf .pdf, retrieved on 28.03.2018). At least the WÜ elements WE ₁ and WE ₂ must be able to conduct high heat fluxes in addition to their HT strength. For this purpose, they are thin-walled and / or run from hochwärmeleitfähigem material. A thin-walled version with wall thicknesses of approx. 0.5 mm is possible if the R-KS-WÜ is only exposed during operation to low pressure differences of 0 bar to 3 bar (300 kPa). Are in operation larger pressure differences it may be necessary, instead of heat-resistant steel, which has a mean thermal conductivity λ (for steel grade 1.4841 It. og data sheet:
λ = 15 W / m · K at 20 ° C, λ = 19 W / m · K at 500 ° C), to select a material of high thermal conductivity. High thermal conductivity in this application is understood to mean a thermal conductivity λ ≥ 100 W / m · K. Suitable for this purpose are refractory metals, in particular tungsten (λ = 167 W / mK at 20 ° C., λ = 111 W / mK at 1000 ° C.) and molybdenum (λ = 142 W / mK at 20 ° C., λ = 105 W / m · K at 1000 ° C), which also have a higher heat and corrosion resistance compared to steel (Source: WHS Sondermetalle e. K., https://www.whs-sondermetalle.de/de/werkstoffe /refraktaermetalle.html , retrieved on 24.01.2018), as well as MoW alloys.

Also suitable are nickel alloys, special ceramics with high thermal conductivity, z. Based on SiC and AlN, as well as composites.

The skilled person is able to calculate the required wall thickness of the WÜ elements for his specific application and to determine the necessary amount of material and their costs. He can thus judge whether the use of these more expensive materials compared to steel will pay for itself over the entire, multi-year, service life of the R-KS-WÜ.

The R-KS-WÜ according to the invention makes it possible to control even difficult process conditions due to its simple radially symmetrical construction, through which the process-related pressure and temperature loads are evenly distributed to the radially symmetric components, in particular the WÜ elements WE ₁ , WE ₂ .

The flow paths of the fluids F1 and F2 used can have a spatial connection with one another, which allows a mass flow of the first fluid F1 into the flow path of the second fluid F2 and vice versa. However, this spatial connection must not be within an R-KS-WÜ. It is positioned at a location of the flow path at which the first fluid F1 has already flowed through the outer casing AH and the R-KS-WÜ, in the case of a modular heat exchanger unit all the associated R-KS-WÜ. The first fluid F1 can be conducted there into the flow path of the second fluid F2 and, optionally after a chemical reaction, as a second fluid F2 in a cross-flow against the first fluid F1 continue to flow. Such a case is explained in Example 1, section 1c), using the example of a combustion chamber.

The fluids F1, F2 used can be gaseous or liquid in any combination. In special applications, d. H. if their critical pressure and their critical temperature are exceeded, they can also be in the supercritical state. Likewise, the state of aggregation of the fluids F1 and F2 may change upon heat transfer between them. For example, a fluid can pass from the gaseous to the liquid state with the release of heat (condensation) or can be converted from the liquid to the gaseous state by heat absorption (evaporation).

The fluids F1 and / or F2 may also be aggressive, chemically reactive substances. These are manageable since the person skilled in the art, as explained in Example 1, Section 1b), has a great freedom in the choice of material for the R-KS-WÜ. He can thus select materials that have a permanent chemical resistance to the fluids F1 and / or F2.

Exemplary embodiment 1: R-KS-WÜ, designed as integrated heat exchanger (I-WÜ)

An executed as I-WÜ R-KS-WÜ is suitable for technical systems, which have a cylindrical wall WI. Suitable z. B. plants of thermal process engineering, z. B. cylindrical combustion chambers with attached exhaust duct, which are limited by a wall WI and usually have a large diameter D _An (several meters). Such combustion chambers achieve a flow rate of about 5,000 - 100,000 Nm ³ / h (standard cubic meter per hour), for which the I-WÜ must be designed.

1a) integration of an I-WÜ into a thermal process engineering plant)

In the following, the integration of an I-WÜ in a tubular system of thermal process engineering (hereafter briefly: Appendix) will be described. It is assumed that a plant is limited by a cylindrical wall WI, which is an inner chamber IK surrounds. The diameter D _at such a plant, given by the diameter of the cylindrical wall WI, is usually in the range 1.5 m ≤ D _An ≤ 10 m.

It is provided an I-WÜ whose outer tube AR has the same diameter D as the system, so D = D _An . The I-WÜ is placed on the cylindrical wall WI.

An envelope tube HR is provided, which surrounds the cylindrical wall WI with the attached outer tube AR in a concentric arrangement, so that a cylindrical ring-like outer envelope AH is formed between the envelope tube HR and the cylindrical wall WI with the attached outer tube AR. The outer shell AH is thus bounded on the inside by the wall WI of the plant and the outer tube AR with the diameter D = D _An and outside by the cladding tube HR with the diameter D _HR . By the volume of the outer shell AH, a first fluid F1 is flowable, through the cylindrical inner chamber IK of the system, which is bounded by the wall WI to the outside, a second fluid F2 is flowable. Both flows are substantially parallel to the axis of the system and may be directed parallel to one another or antiparallel. On the one hand, it is possible for the first fluid F1 to have a lower temperature than the second fluid F2, so that thermal energy is transferred from the second fluid F2 through the wall WI to the first fluid F1. On the other hand, it is also possible that the first fluid F1 has a higher temperature than the second fluid F2, so that thermal energy is transferred from the first fluid F1 through the wall WI to the second fluid F2. Thus, such an arrangement already without the I-WÜ a heat exchanger, namely a double-pipe WÜ, dar. The heat transfer is limited to an approximately 0.5 cm to 1 cm (with laminar flow) and to about 10 cm ( in turbulent flow) thick boundary layer of the second fluid F2, which is adjacent to the wall WI. Also, the design of the wall WI as a cylinder, which provides only a small surface for the heat transfer, limits the heat transfer. Thus, it is a very inefficient WÜ, because it can only a small amount of heat between the fluid F2 in the central region of the inner chamber IK of the system, which is located in the vicinity of its axis, and the near wall surface layer of the fluid F2 be transferred.

This disadvantage is overcome here by the integrated into the system I-WÜ 11. A further improved heat transfer is achieved by integrating several inventive I-WÜ 11 in the form of a series circuit in the system.

Fig. 6 outlined an inventive I-WÜ 11, which is integrated in a system 30, in this case placed on this is.

The flow path of the fluid F1 is changed as follows by the I-WÜ integrated in the system 30: The separating device TV closes the fluid F1 the direct path through the cylinder-ring-like outer casing AH. In each case, two interconnected openings S _WI1 , S _A1 in the region of the outer ring AR ₁ and S _WI2 , S _A2 in the region of the outer ring AR ₂ open a new flow _path consisting of N channels, which flows from the outer shell AH through each of the openings S _WI1 , S _A1 continues through the connected WÜ element WE ₁ to an opening S _{U1 of} the deflection chamber U, continues along the axis of the deflection chamber U in the region of the openings S _U2 and from each of these openings by the connected WÜ Element WE ₂ leads to one of the openings S _WI2 , S _A2 and from there back into the outer shell AH on the original flow path of the fluid F1.

1b) Functioning of an I-WÜ in a thermal process engineering plant

The executed as I-WÜ 11 R-KS-WÜ is intended for use in plants of thermal process engineering, in which a first fluid F2 in an inner chamber IK and a second fluid F2 in a the inner chamber IK surrounding, of this by separate the wall WI, outer shell AH. Outside the I-WÜ the flow direction of the two fluids is usually antiparallel (countercurrent principle). A heat transfer between the two fluids takes place outside of the I-WÜ substantially by heat conduction through the wall WI and is limited by the thickness, the thermal conductivity of the material of the wall WI and their small area. In addition, the heat transfer coefficients of the fluids determine the thermal resistance.

Fig. 6 shows in a schematic representation in addition to the installation of an I-WÜ in a plant also changed with his help flow pattern. The scoop-shaped WÜ elements WE ₁ , WE ₂ are simplified symbolized by two planar connections.

I-WÜ 11 provides an additional area for heat transfer by conduction. This additional surface is formed by the wall surfaces of the scoop-shaped WÜ elements WE ₁ , WE ₂ , which are also advantageously distributed over the entire cross section of the inner chamber IK, in which the fluid F ₂ flows. The additional area for the heat transfer can be set arbitrarily large by the number N, width and length of the blade-shaped WÜ elements WE ₁ and WE ₂ are adjusted so that the required area is obtained. If the area provided by a single I-WÜ 11 is not sufficient for the required heat recovery, then, as in Fig. 7 shown schematically, a series connection of several I-WÜ 11 can be realized. The distance between the individual I-WÜ can be reduced so far that the tubes of the deflection chambers U are brought together. In this case, the deflection chambers but by at least one closure G _U or D _U (see Fig. 2a ) stay disconnected.

Fig. 8 schematically shows the flow through the WÜ elements: The first fluid F1 flows, as in Fig. 8a shown, from the outer shell AH through the openings S _{A1 of} the outer ring AR ₁ in the WÜ elements WE ₁ , centripetal through this through the openings S _U1 in the deflection U, flows through this in the direction of its axis and then flows, as in Fig. 8b shown, via the openings S _U2 in the WÜ elements WE ₂ , centrifugally through this through the openings S _{A2 of} the outer ring AR ₂ in the outer shell AH back. Through the wall surfaces of the blade-shaped WÜ elements WE ₁ , WE ₂ takes place by heat conduction an intense heat transfer between the two fluids F1 and F2 (assuming a temperature difference between the two), which is ensured by the following structural features: The WÜ elements WE ₁ , WE ₂ have a large specific surface (given by the quotient of their surface area and their volume) due to their cross-section in the form of an elongated rectangle, which may be rounded at the ends. Furthermore, the WÜ elements are made thin-walled, whereby their thermal resistance is minimized.

The centripetal and centrifugal flow of the first fluid F1 can be summarized by the term radial flow . The second fluid F2 flows in the inner chamber through the intermediate spaces between the respective N WÜ elements WE ₁ and WE ₂ , thus crosses the flow path of the first fluid F1 divided into 2 N channels. This also explains the term radial cross-flow heat exchanger R-KS-WÜ.

From the inventive paddle-shaped embodiment of the WÜ elements WE ₁ , WE ₂ result in several advantageous technical effects that apply to all embodiments of the R-KS-WÜ, ie both for an I-WÜ and for a further described in Example 2 below -Alone-WÜ (SA-WÜ):
A first advantageous technical effect of the scoop-shaped WÜ elements is to increase the total area available for the heat transfer between the fluids F1 and F2, which has already been explained.

A second advantageous technical effect of the blade-shaped WÜ elements consists in the substantial avoidance of thermal stresses in the arrangement of the R-KS-WÜ. Thermal stresses are to be understood here as thermally induced mechanical stresses which are based on the different thermal expansion of the materials used.

For example, is the thermal coefficient of expansion Δ l / l of the above proposed HT-strength steel 1.4841, averaged over the temperature range 20 ° C to 1000 ° C, Δ l / l = 19 · 10 ^-6 K ^-1. If an inventive R-KS-WÜ whose components are made of this steel grade, brought from its temperature in the off state (about 20 ° C) to an operating temperature of 1000 ° C, so is with an absolute length expansion of the components used by about 1.9% expected.

When using WÜ elements WE ₁ , WE ₂ , which run in a straight line on the shortest path between the deflection chamber U and the outer tube AR, high, non-compensable, thermal stresses induced in the arrangement, leading to early material fatigue and tearing the WU Elements WE ₁ , WE _{2 would lead} to the connection points to the outer tube AR and / or to the deflection chamber U.

Due to the blade-shaped design of the WÜ elements WE ₁ and WE ₂ , if their blades are bent in the same direction, a thermally induced expansion or contraction of the WÜ elements as well as the other components is converted directly into a rotation of the deflection U, whereby the buildup of thermal stresses is minimized. In contrast to known heat exchangers are WÜ elements WE ₁ and WE ₂ rigidly fixed only at one end, namely on the outer rings AR ₁ , AR ₂ , while their other end is movable together with the deflection U, so that they can expand unhindered. Due to the radially symmetrical arrangement, all WÜ elements of the same row, ie all WT elements WE ₁ at the level of the outer ring AR ₁ , receive identical thermal loads, ie show the same extent. The same applies to the WÜ elements WE ₂ in the region of the outer ring AR ₂ . As a result, the deflection chamber U is uniformly rotated in the region of each outer ring, so that no tensile and compressive stresses arise along its circumference.

However, a temperature difference occurs between the WÜ elements WE ₁ at the level of the outer ring AR ₁ and the WÜ elements WE ₂ at the level of the outer ring AR ₂ , so that the WÜ elements WE ₁ and WE ₂ expand to different degrees, resulting in a Twisting (torsion) of the deflection U leads. This twisting causes thermal stresses in the deflection chamber U, which are particularly large when the WÜ elements WE ₁ and the WÜ elements WE ₂ are bent in opposite directions, which can lead to material fatigue. To compensate for these thermal stresses, the deflection chamber U is divided at half its height into two sections and at this position a fluid-tight connecting element VE used (see Fig. 6 ). This connecting element VE ensures that both sections of the deflection chamber U are freely rotatable relative to each other, but the tightness of the deflection chamber U with respect to the fluids F1 and F2 is still ensured, ie, a mass flow between the fluids F1 and F2 is prevented. The execution of the connecting element VE is at the end of the application based on Fig. 15 explained.

Due to the paddle-shaped design of the WÜ elements WE ₁ and WE ₂ and the equipment of the deflection U with a connecting element VE, it is thus possible to reliably prevent premature material aging and failure of the components of the R-KS-WÜ, thereby increasing its life becomes. Since thermal stresses that are caused by different coefficients of thermal expansion are almost completely compensated, the components of the R-KS-WÜ can also be made of different materials whose coefficients of thermal expansion differ considerably, can be made without previously extensive simulations or experiments on the long-term stability and thermal shock resistance of the R-KS-WÜ must be performed. Different materials can thus be used flexibly. These materials can also be taken from different classes of materials. There are z. As metallic components, ceramic components and / or composite materials can be combined.

A third advantageous technical effect of the blade-shaped WÜ elements is the optimization of the flow behavior of the second fluid F2, which flows through the spaces between the WÜ elements in the axial direction of the R-KS-WÜ. For this purpose, the blades of the WÜ elements WE ₁ and the WÜ elements WE ₂ are bent in different directions. Such an optimized flow profile, ie a homogeneous, preferably laminar, flow of the second fluid F2 is aimed at, for example, for a combustion chamber with an exhaust duct arranged above it. The R-KS-WÜ according to the invention not only allows the heat energy of hot combustion gases to be used effectively, but also causes a low-turbulence flow of the second fluid F2 when it successively flows through the two rows of oppositely bent WT elements WE ₁ and WE ₂ , As a result, flow pressure losses of the second fluid F2 are kept low. Fig. 9 shows a view in the direction of the axis of an R-KS-WÜ, in which the WÜ elements WE ₁ are bent to the left, the underlying WÜ elements WE ₂ to the right. In the center is the deflection chamber U, whose interior is covered by the shutter Gu.

Both the heat transfer and the optimization of the flow profile can be supported by the fact that rib elements are installed in the spaces between each two adjacent WÜ elements WE ₁ and / or in the spaces between each two adjacent WÜ elements WE ₂ , so that the spaces receive an additional grid structure with flow channels parallel to the axis of the R-KS-WÜ. Suitable as rib elements are sheet-like structures known to the person skilled in the art as corrugated ribs, made of highly heat-conductive, HT-solid material, eg. B. metal bands. The corrugated fins should have the same width as the WÜ elements WE ₁ , WE ₂ , so that they wave each two adjacent WÜ elements on their entire width, in Fig. 9 So their dimension perpendicular to the plane, connect with each other. Because such corrugated fins in Fig. 9 not meaningfully representable, was a single corrugated rib WR in Fig. 3 located. In practice, all adjacent WÜ elements WE ₁ and WE _{2 are} connected by such corrugated fins, so that the entire cross section of the inner chamber IK is crossed by corrugated fins. On the one hand, the corrugated fins effectively remove thermal energy from the second fluid F 2 flowing through the grid structure, and on the other hand, they laminarize the flow of the second fluid F 2, so that an advantageous low-turbulence flow behavior is impressed on it. The connecting regions between the WÜ elements and the corrugated fins are preferably designed flat with a height of a few millimeters, so that a sufficiently large contact surface for the heat transfer from the corrugated fins to the WÜ elements is provided. The grid formed by the corrugated ribs thereby receives a distorted honeycomb-like shape. If only the flow profile is to be optimized, the corrugated ribs can also be made of any HT-solid material. They should have a smooth surface.

It is also possible, the interior of the WÜ elements WE ₁ , WE ₂ with rib elements R (recognizable in Fig. 1 ) to enhance heat transfer to the first fluid F1 flowing therein. This is particularly useful when the width B _{WE of} its cross-section, as described above, is increased to the outside.

1c) Particular embodiment: combustion chamber equipped with a series connection of three I-WÜ

Fig. 10a shows a schematic representation of a combustion chamber BK, on the wall WI a series circuit of three I-WÜ is placed, which form a take-off shaft K. This arrangement is surrounded by an outer shell AH. The outer shell AH is bounded on the inside by the wall WI and the outer tubes AR of the I-WÜ and on the outside by the jacket tube HR. The separation device TV every I-WÜ interrupts the direct flow of a flowing from above into the outer shell AH first fluid F1, so this in a known manner by the WÜ elements WE ₁ to the deflection chamber U and after flowing through the same via the WÜ elements WE _{2 flows} back into the outer shell AH. After flowing through all three I-WÜ the first fluid F1 is supplied via one or more supply lines Z of the combustion chamber BK. In the combustion chamber BK, the first fluid F1, in which it is z. B. may be air, with a fuel that may be solid, liquid or gaseous, brought into contact and reacted in a chemical combustion process with heat generation in a second fluid F2, here in hot combustion exhaust air with high CO ₂ content. As the process is continuously conducted, the second fluid F2 flowing transversely (cross-flow) through the interstices between the WÜ elements of I-WS, makes thermal contact with the first fluid F1 flowing in the WÜ elements, passing over the high heat-conductive walls the WÜ elements heat energy from the second fluid F2 is transferred to the first fluid F1. The residual heat contained in the second fluid F2, ie the combustion exhaust air, is thus effectively utilized by being used to preheat the first fluid F1 flowing to the combustion process. The efficiency of the combustion process is thereby increased.

The plant in operation uses the known chimney effect, wherein the outflowing second fluid F2 generates a negative pressure, so that the first fluid F1 (air to atmospheric pressure) is continuously sucked. Instead of air could be supplied as the first fluid F1 and oxygen or a combustible gas mixture, including but further technical measures (pipe feeds) are necessary.

For each of the three I-WÜ 11, the following parameters are selected:
The outer tube AR sealingly attached to the wall WI of the combustion chamber BK has a diameter D = 2.0 m and a height H = 1.0 m. The deflection chamber U has a diameter d = 1.3 m. Each N = 90 WÜ elements WE ₁ and WE ₂ connect the outer rings AR ₁ , AR ₂ with the deflection chamber U. The WÜ elements have a blade diameter S = 0.5 m and describe a partial circle ρ = 150 °.

Since the system is operated with low pressure differences (<20 kPa), all components can be designed with minimal wall thickness. Thus, the outer tube and the deflection chamber receive a wall thickness of 1 mm, the WÜ elements WE ₁ , WE _{2 has} a wall thickness of 0.5 mm. To compensate for the swirl of the flow of the second fluid F2 in the exhaust duct K, the WÜ elements WE ₁ and WE _{2 are} in opposite Directions bent. The resulting twisting (torsion) of the deflection chamber U during operation is compensated by a connecting element VE built into it. The width B _{WE of} the cross section of the WÜ elements, which is available for the flowing first fluid F1, is 10 mm. Its length, which coincides with the length L of the openings S _A1 , S _A2 , S _U1 , S _U2 , is 40 cm. The cladding HR has a diameter of 2.4 m. The disc-shaped separating device TV therefore has an outer diameter of 2.4 m and an inner diameter of 2.0 m. All components are made of high-temperature resistant steel.

1d) Particular embodiment: Combustion chamber, which is surrounded by a series connection of I-WÜ

Fig. 10b schematically shows in half side view (bottom) and in section along the plane X - X (top) an embodiment in which a series circuit of I-WÜ 11 is installed at the same level with a combustion chamber BK and thus surrounds. Compared to the previously described arrangement in Fig. 10a the total height of the arrangement can be reduced here to the height of the combustion chamber BK.

The cylindrical combustion chamber BK is closed at its top by a HT-solid top De and surrounded by a cylindrical ring-like recirculation chamber RK. In the area immediately below the ceiling De there is an annular connection between the combustion chamber BK and the return chamber RK. The return chamber RK is surrounded by the likewise cylindrical ring-shaped deflecting chambers U of the series connection of I-WÜ 11. This series connection can be formed from a freely selectable number ≥ 1 of I-WÜ (ie also by only one I-WÜ 11). In Fig. 10b For example, a series connection of four I-WÜ 11 is shown. The deflection chambers U are surrounded in a known manner with outer tubes AR having sections AR ₁ and AR ₂ , which are connected by WÜ elements WE ₁ and WE ₂ with the deflection chambers. The WÜ elements WE ₁ , WE ₂ are curved like a blade. The entire assembly is surrounded by a cladding tube HR, so that an outer shell AH between the cladding tube HR and the outer tubes AR is formed. Immediately above the bottom of the combustion chamber BK exists an annular connection VB ₂ from the return chamber RK to the cylindrical annular space in which the WÜ elements WE ₁ , WE ₂ extend. At the top of this cylindrical ring-like space is an outlet opening AO. The cladding tube HR has an inlet opening EO at the level of the first outer ring AR _{1 of} the uppermost I-WÜ. The deflection chambers U are separated from each other by their closures G _U , D _U , wherein the immediately adjacent closures G _U , D _U can be combined to form a single closure G _U + D _U. Each I-WÜ 11 has a separator TV, which is placed on its outer tube AR between the outer rings AR ₁ , AR ₂ and the cladding tube HR separates at this position. At the lower end of the jacket tube HR there is a connection VB ₁ of the outer shell AH to the combustion chamber BK. The combustion chamber BK, the recirculation chamber RK, the deflection chambers U and the cladding tube HR are arranged concentrically.

In this arrangement, the following flow profile is realized: A first fluid F1 (dashed arrows), which generally ambient temperature is supplied via the inlet opening EO the uppermost portion of the cladding tube HR, centripetally flows through the WÜ elements WE _{1 of} the uppermost I WÜ 11 to the deflection chamber U, flows through this, then flows centrifugally through the WÜ elements WE _{2 of} the uppermost I-WÜ 11 back to the lying below the uppermost portion of the cladding tube HR. Starting from there, the described flow pattern is repeated until all I-WÜ 11 have passed. From the lowermost portion of the cladding tube HR, the first fluid F1 is then supplied via the connection VB _{1 of} the combustion chamber BK. There it is converted in a combustion process into a second fluid F2 (solid arrows) with high temperature, which flows in the direction of the HT-solid ceiling of the combustion chamber and is passed there into the recirculation chamber RK. Through the return chamber RK, the second fluid F2 flows back down to the level of the bottom of the assembly and is then in the cylindrical annular space in which the WÜ elements WE ₁ , WE ₂ passes, and flows through the interstices of the WÜ elements WE ₁ , WE _{2 of} all I-WÜ. As these intermediate spaces flow through, an efficient heat transfer takes place between the second fluid F _{2 of} high temperature and the first fluid F1 flowing radially (alternately centripetally and centrifugally) through the WÜ elements WE ₁ , WE ₂ . Through the outlet opening AO, the cooled second fluid F2 is then released into the environment or fed to another process.

In the sectional view ( Fig. 10b above), the circles with dot indicate the upward flowing fluid F2, the circles with the cross the downward flowing fluid F2.

Exemplary embodiment 2: R-KS-WÜ, executed as stand-alone-WÜ (SA-WÜ)

Fig. 11 shows a concrete embodiment of the in Fig. 5 schematically represented SA-WÜ.

The SA-WÜ 11 is mounted on a holder comprising a base plate GP and a plurality of holding plates HP (partly hidden) with its axis directed horizontally. He has the known structure with an outer tube AR and a deflection U, which are connected by partially hidden WÜ elements WE ₁ and by WÜ elements WE ₂ . In addition, it is equipped with its own outer shell AH, which is limited by a cladding HR. The outer shell is divided in a known manner by a hidden separator. The cladding tube HR is provided with three evenly distributed over its circumference, ie offset here by 120 °, tangential ports T1, T2, via which a first fluid F1 fed and can be derived again after flowing through the SA-WÜ. The tangential ports T1, T2 are formed by pipe sockets, which are inclined so that they continue the curvature of the outer shell AH straight outward. They are oriented so that they point in the direction of the blade-shaped bend of the WÜ elements WE ₁ and WE ₂ , so that the first fluid F1 without abrupt deflections at large angles (eg 90 °, 180 °) from the terminals T1 in the WÜ elements WE ₁ flow in and can flow out of the WÜ elements WE ₂ to the connections T2.

The supply and discharge of a second fluid F2 is parallel to the axis of the assembly, which in Fig. 11 is illustrated by two arrows. For this purpose, a line, not shown, for. B. a pipe whose diameter corresponds to the diameter D of the outer tube, on the front and the (in Fig. 11 concealed) back of the SA-WÜ 12 connected to the outer tube AR. It is chosen a diameter D = 1 m. A series connection of several SA-WÜ 12 can be realized in a simple manner. As Fig. 12 the example of three SA-WÜ, these are to be arranged one behind the other along a common axis and via the connecting pipes V respectively connections between the first fluid F1 discharging port T2 of the first-passed SA-WÜ and the first fluid F1 supplying port T1 of the following pass through SA-WÜ.

Fig. 13 shows a further embodiment of a SA-WÜ 12, which causes an improved flow behavior. Instead of tangential tubular connections tangential ports T1, T2 are used with an elongated cross section, the length of the length L of the slot-shaped openings in the (hidden) outer tube AR, for the supply and discharge of the first fluid F1. The first fluid F1 can thereby flow with reduced flow resistance into the WÜ elements WE ₁ and out of the WÜ elements WE ₂ . To the terminals T1, T2 lines are connected, which supply the first fluid F1 of remotely located equipment to the SA-WÜ and lead away from it. The in Fig. 13 SA-WÜ shown has in each case 4 ports T1 and T2 (2 of which visible, two concealed on the back), which extend over in each case over a 90 ° angle region of the circumference of the SA-WÜ. Through this extended version, the terminals T1 and T2 assume also the function of a separator, thereby ensuring that the first fluid F1 to the predetermined flow path (covered) by the WÜ elements WE _1, the deflection chamber U and the WÜ elements WE ₂ follows. Via the outer flanges AF ₁ , AF ₂ further SA-WÜ can be connected to form a series connection.

Fig. 14 shows an embodiment of a series connection of two SA-WÜ, which also have the advantageous tangential ports T1, T2 with elongated cross-section. A first fluid F1 is fed via the connections T1 to the first SA-WÜ, passed in a known manner through its (covered) deflection chamber and exits via (unrecognizable) connections T2, which are covered by a deflecting tube UR ₁ . The deflection tube thus has the function of a cladding tube. Below the deflection tube UR ₁ are hidden Umlenkrippen, as they are made Fig. 2 are known which extend into the region of the deflection tube UR ₂ , which is part of the second SA-WÜ. The deflecting ribs are placed on the concealed outer tube and are designed so high that they reach into the vicinity of the deflection tubes UR ₁ , UR ₂ . Preferably, they are with their upper edges on the deflection tubes UR ₁ , UR ₂ , but no absolutely tight connection between the deflection tubes and the Umlenkrippen, z. B. produced by welding, is required. It may also remain a gap of 0.5 mm to 5 mm between the upper edges of the baffles and the deflection tubes. The first fluid F1 is directed by these deflecting ribs in the direction of the second SA-WÜ, which in Fig. 14 is symbolized by three curved arrows, and is supplied via the Umlenkrohr UR ₂ covered (not recognizable) ports T1 to the second SA-WÜ flows through in a known manner the deflection chamber and then flows through the visible port T2 and other hidden ports T2 again.

The remaining functions correspond to the embodiments presented above.

1. a) Sammeln der Prozessabwärme mehrerer technischer Anlagen
   Dazu wird die in einem ersten Fluid F1 gespeicherte Prozessabwärme einer beliebig großen Anzahl von Anlagen mithilfe von Rohrleitungen, die an die Anschlüsse T1 angeschlossen sind, dem SA-WÜ zugeführt und von dort auf ein zweites Fluid F2 übertragen. Bei dem zweiten Fluid F2 kann es sich z. B. um in einer Fernwärmeleitung strömendes Wasser handeln. Über Rohrleitungen, die an die Anschlüsse T2 angeschlossen sind, kann das erste Fluid F1 einem weiteren Prozess zugeführt oder, falls unbedenklich, in die Umgebung entlassen werden.
2. b) Wärmerückgewinnung aus einem Wärmespeicher
   In analoger Weise kann ein SA-WÜ zur Wärmerückgewinnung aus einem Wärmespeicher, vorzugsweise einem Hochtemperatur-Wärmespeicher (HT-WS), genutzt werden. Dabei wird das erste Fluid F1, bei dem es sich z. B. um Luft handeln kann, im HT-WS aufgeheizt, wird dann dem SA-WÜ zugeführt, wo es Wärmeenergie auf ein zweites Fluid F2 überträgt, und kann dann abgekühlt in die Umgebung entlassen (offener Kreislauf) oder in einem geschlossenen Kreislauf erneut dem HT-WS zugeführt werden. Das zweite Fluid F2 kann z. B. Wasserdampf sein, der bei Durchlaufen des SA-WÜ aufgeheizt und einem Dampfturbinenprozess zugeführt wird.
3. c) Unterstützung einer chemischen Reaktion
   Bei dem zweiten Fluid F2, das in einer an das Außenrohr AR angeschlossenen Rohrleitung strömt, kann es sich auch um ein reaktives Gemisch handeln, in welchem eine chemische Reaktion, z. B. eine Gleichgewichtsreaktion, abläuft. Die Rohrleitung fungiert dann somit als kontinuierlich durchströmter chemischer Reaktor.
   Handelt es sich dabei um eine exotherme Reaktion, so kann die freigesetzte Reaktionswärme im SA-WÜ vom zweiten Fluid F2 an ein erstes Fluid F1 übertragen werden, sodass das chemische Gleichgewicht in gewünschter Weise beeinflusst, d. h. in Richtung der Reaktionsprodukte verschoben wird.
   Handelt es sich dabei um eine endotherme Reaktion, so kann die benötigte Reaktionswärme dem zweiten Fluid F2 im SA-WÜ durch ein Fluid F1 zugeführt werden, sodass das chemische Gleichgewicht auch in diesem Fall in Richtung der Reaktionsprodukte verschoben wird.

The SA-WÜ enables the following technically advantageous applications:

1. a) collecting the process waste heat of several technical installations
   For this purpose, the process waste heat stored in a first fluid F1 of an arbitrarily large number of plants is supplied to the SA-WÜ by means of pipelines which are connected to the connections T1 and from there to a second fluid F2. In the second fluid F2 may be, for. B. to act in a district heating pipe flowing water. Via pipes which are connected to the connections T2, the first fluid F1 can be supplied to a further process or, if unobjectionable, discharged into the environment.
2. b) Heat recovery from a heat storage
   In an analogous manner, a SA-WÜ for heat recovery from a heat storage, preferably a high-temperature heat storage (HT-WS), can be used. In this case, the first fluid F1, in which it is z. B. can be air, heated in HT-WS, is then supplied to the SA-WÜ, where it transfers heat energy to a second fluid F2, and then cooled discharged into the environment (open circuit) or in a closed circuit again the HT-WS are supplied. The second fluid F2 may, for. As water vapor, the at Run through the SA-WÜ heated and fed to a steam turbine process.
3. c) supporting a chemical reaction
   In the second fluid F2, which flows in a pipe connected to the outer pipe AR, it may also be a reactive mixture in which a chemical reaction, for. B. an equilibrium reaction proceeds. The pipeline then acts as a continuous flow chemical reactor.
   If this is an exothermic reaction, then the released heat of reaction in the SA-WÜ can be transferred from the second fluid F2 to a first fluid F1, so that the chemical equilibrium is influenced in the desired manner, ie shifted in the direction of the reaction products.
   If this is an endothermic reaction, the required heat of reaction can be supplied to the second fluid F2 in the SA-WÜ by a fluid F1, so that the chemical equilibrium is also shifted in the direction of the reaction products in this case.

All applications can also be realized with a series connection of several SA-WÜ. In order to achieve a particularly high throughput, several SA-WÜ can be connected in parallel.

If the applications described are operated with fluids F1, F2, which have only a small pressure difference (<300 kPa), all components of SA-WÜ 12 can be made thin-walled. The parameters mentioned in example 1, section 1c) can be used. Since in a SA-WÜ no mass flow, ie no mass transfer, between the fluids F1 and F2 takes place, their composition and their function in the applications described above can also be reversed. For example, in application c), the first fluid F1 can also form the reactive mixture, while the supply or removal of the heat of reaction takes place via the second fluid F2.

Design of the connecting element VE

Fig. 15 shows in a sectional view (left) and in an isometric view (right), the connecting element VE for fluid-tight connection of two sections of a deflection U. It has two concentrically arranged metallic rings, one of the rings has a slightly larger diameter D _VE , the other has a slightly smaller diameter d _VE than the deflection chamber U (diameter d ). The two rings are connected by spacers together so that they on both sides of an annular gap width h = _VE (D _VE - _VE d) form / 2. Two graphite strips GB are inserted into the two annular gaps in such a way that one strip bears against the inner ring and the other strip bears against the outer ring. Between the two graphite bands GB remains on both sides of a gap of width a _VE , in each of which a portion of the split deflection U is inserted. The graphite belts GB allow sliding of the sections of the deflection chamber, that is to say a rotation of the sections, but enclose the sections in a fluid-tight manner. So that the sections can be safely positioned, a minimum width B _{VE of} the connecting element VE between 2 cm and 5 cm is to be selected, depending on the diameter d of the deflection chamber.

Closing remarks

The illustrated invention is not limited to the presented embodiments. These can be combined in an advantageous manner. For example, the in Fig. 10 imagined combustion chamber to be converted into a chemical reactor. For this purpose, the flow paths of the fluids F1 and F2 are to be separated and to close the combustion chamber pressure-tight with arranged above the exhaust duct. In this case, the feed for the fluid F1 are to be closed parallel to the axis of the arrangement and the discharge of the first fluid F1 to the combustion chamber. They are due to tangential inflows and outflows of the fluid F1 as in the Fig. 11 and 12 replaced SA-WÜ. Both fluids can be supplied and removed via pressure-resistant pipelines, it being possible for process heat from the second fluid F2, which flows through the combustion chamber, which has been converted into a chemical reactor, to be transmitted to the first fluid F1 via the I-WS. This can be done both a heat and a heat dissipation.

The R-KS-WÜ described in this application are oriented horizontally or vertically by way of example. It is of course possible to align the arrangements as desired, that is, to choose any inclination angle for the flow path of the fluid F2.

The described R-KS-WÜ have a cylindrical shape. Deviations from the cylindrical shape would be possible, but would lead to an uneven material load, an unfavorable flow behavior and a more complex construction. They are therefore technically meaningless.

In the production of the various embodiments of the R-KS-WÜ according to the invention, the skilled worker is not restricted in terms of the production of the individual components of the known manufacturing processes of primary forming and forming. Based on the joining technique of the individual components, the person skilled in the known cohesive connections such as welding and soldering are available.

Likewise, individual components of the R-KS-WÜ can be produced by additive manufacturing, also known as 3D printing.

The content of the documents cited and linked in this application is part of the disclosure.

List of reference numbers

10

- Radial Crossflow Heat Exchanger (R-KS-WÜ)

11

- integrated heat exchanger (I-WÜ)

12

- Stand-alone heat exchanger (SA-WÜ)

24

- Closures of the inlets and outlets of the first fluid F1 parallel to the axis A.

26

- Openings for supply and discharge of the first fluid F1 perpendicular to the axis A.

30

- Plant of thermal process engineering

A

- Symmetry axis of the R-KS-WÜ

AF ₁ , AF ₂

- external flanges

AH

- outer shell

AO

- outlet opening

AR

- outer tube

AR ₁ , AR ₂

- outer rings

BK

- combustion chamber

de

- ceiling of the combustion chamber

D _U

- Closure on the top surface of the deflection U

EO

- inlet opening

F1

- First fluid, the WÜ elements of the R-KS-WÜ radially flowing through

F2

- Second fluid, the interstices of the WÜ elements of the R-KS-WÜ flowing vertically

GB

- graphite tape

GP

- Base plate

G _U

- Closure at the base of the deflection U

HP

- Retaining plate

MR

- Cladding tube

IK

- Inner chamber of a plant 30

K

- Discharge shaft

R

- Rib elements

RK

- return chamber

R ₁ , R ₂

- Rows with slot-shaped openings S _A1 and S _A2

S _A1 , S _A2

- Slit-shaped openings of the outer rings AR ₁ , AR ₂

S _U1 , S _U2

- Slot-shaped openings in the cylinder jacket Z _{U of} the deflection U, arranged in two rows

T1, T2

- tangential connections

TV

dividing device

U

- deflection chamber

UR ₁ , UR ₂ -

change pipes

ULR

- deflecting ribs

V

- Connecting pipe

VB ₁

- Connection from the outer shell AH to the combustion chamber BK.

VB ₂

- Connection of the return chamber RK to the cylindrical annular space in which the WÜ elements WE ₁ , WE ₂ run

VE

- optional connection element (required if the deflection chamber is divided into two sections)

WE ₁

WÜ element, which connects an opening S _U1 with an opening S _A1

WE ₁ *

- WÜ element that in Fig. 3 to explain the parameters S and ρ is highlighted

WE ₂

WÜ element, which connects an opening S _U2 with an opening S _A2

WI

- Wall of a technical system in which an I-WÜ is integrated

WR

- corrugated rib

Z

- Supply to the combustion chamber

Z _U

- Cylinder jacket of the deflection U

List of formula symbols

a

- Distance between the openings S _U1 , S _U2 to the base or top surface of the deflection chamber

a _VE

- Gap between two graphite bands for a portion of the deflection tube U

B _U

- Width of the openings S _U1 , S _U2

B _VE

- Width of the connecting element VE

H _VE

- Gap without graphite tape

B _WE

- Width of the cross section of the WÜ elements WE ₁ , WE ₂

d

- Diameter of the deflection U

D

- Diameter of the outer tube AR

D _At

- Diameter of a system into which an I-WÜ is integrated

D _MR

- Diameter of the duct HR

D _VE , d _VE

- Outer and inner diameter of the connecting element VE

H

- Height of outer tube AR

L

Length of the slot-shaped openings S _A1 , S _A2 in the case of the same length ( L = L ₁ = L ₂ )

L ₁ , L ₂

- Length of the slot-shaped openings S _A1 , S _A2

N

Number of slot-shaped openings S _A1 , S _A2 per outer ring AR ₁ , AR ₂ , the openings S _U1 , S _{U2 of} the deflection chamber U and the WÜ elements WE ₁ and WE ₂

S

- Diameter blade-shaped curved WÜ elements WE ₁ , WE ₂ (blade diameter)

T ₁

- Temperature of the first fluid F1

T ₂

- Temperature of the second fluid F2

ρ

- Subcircuit of a circular arc following blade-shaped curved WÜ elements WE ₁ , WE ₂

Claims (15)

Radial cross-flow heat exchanger (10, 11, 12), comprising an outer tube (AR) and a concentrically mounted, located on both sides in its interior deflecting chamber (U),
characterized in that on the outside of the outer tube (AR) there is a separating device (TV) which divides the outer tube into two outer rings (AR ₁ , AR ₂ ), - The outer rings (AR ₁ , AR ₂ ) are each provided with a plurality of openings (S _A1 , S _A2 ), - The deflection chamber (U) has two rows of openings (S _U1 , S _U2 ), the number of the number of openings (S _A1 , S _A2 ) in the outer rings (AR ₁ , AR ₂ ) corresponds, wherein the first row of Openings (S _U1 ) at the same height with the openings (S _A1 ) of the first outer ring (AR ₁ ) and the second row of openings (S _U2 ) at the same height with the openings (S _A2 ) of the second outer ring (AR _2nd ), - Each opening (S _U1 ) of the first row is connected via a designed as a hollow body heat exchanger element (WE ₁ ) with an opening (S _A1 ) of the first outer ring (AR ₁ ) and each opening (S _U1 ) of the second row via a formed as a hollow body heat exchanger element (WE ₂ ) with an opening (S _A2 ) of the second outer ring (AR ₂ ) is connected, so that a first flow path from the openings (S _A1 ) of the first outer ring (AR ₁ ) centripetally through the heat exchanger elements (WE ₁ ), the first row of openings (S _U1 ) of the deflection chamber (U), the deflection chamber (U), the second row of openings (S _U2 ) of the deflection chamber (U), the heat exchanger elements (WE ₂ ) centrifugally to the openings (S _A2 ) of the second outer ring (AR ₂ ) is formed, in which a first fluid (F1) can be flowed is
and a second flow path, which runs parallel to the common axis (A) of the outer tube (AR) and the concentrically positioned deflection chamber (U) through gaps between the heat exchanger elements (WE ₁ , WE ₂ ) and is bounded by the inner wall of the outer tube AR, in which a second fluid (F2) is flowable. Radial cross-flow heat exchanger (10, 11, 12) according to claim 1, characterized in that the deflection chamber (U) is divided into two sections which are interconnected by a connecting element (VE), so that both sections of the deflection chamber (U) are freely rotatable against each other, wherein the tightness of the deflection chamber (U) with respect to the fluids F1 and F2 is ensured and a mass flow between the fluids F1 and F2 is prevented. Radial cross-flow heat exchanger (10, 11, 12) according to claim 1 or 2, characterized in that the heat exchanger elements (WE ₁ , WE ₂ ) are curved blade-shaped, wherein the heat exchanger elements (WE ₁ ), with the Openings (S _U1 ) of the first row are connected, bent in the same direction as the heat exchanger elements (WE ₂ ), which are connected to the openings (S _U2 ) of the second row, or the heat exchanger elements (WE ₁ ) , which are connected to the openings (S _U1 ) of the first row, in the opposite direction as the heat exchanger elements (WE ₂ ), which are connected to the openings (S _U2 ) of the second row, are bent. Radial cross-flow heat exchanger (10, 11, 12) according to claim 1, 2 or 3, characterized in that the openings (S _A1 , S _A2 ) of the outer rings (AR ₁ , AR ₂ ) equidistant over the circumference of the outer rings (AR ₁ , AR ₂ ) and the openings (S _U1 , S _U2 ) of the deflection chamber (U) are distributed equidistantly in both rows over the circumference of the deflection chamber (U). Radial cross-flow heat exchanger (10, 11, 12) according to claim 1, 2 or 3, characterized in that formed as a hollow body heat exchanger elements (WE ₁ , WE ₂ ) near the deflection chamber (U) has a cross section in the form of an elongated Rectangles, whose corners may be rounded, which remains the same lengthwise or widens outwards to an oval or a circle. Radial cross-flow heat exchanger (10, 11, 12) according to claim 1, 2 or 3, characterized in that designed as a hollow body heat exchanger elements (WE ₁ , WE ₂ ) are designed as fin tubes and / or that rib elements between adjacent heat exchanger Elements (WE ₁ , WE ₂ ) and / or inside the heat exchanger elements (WE ₁ , WE ₂ ) are installed. Radial cross-flow heat exchanger according to one of claims 1 to 6, designed as an integrated heat exchanger (11), characterized
that it is installed in a system that provides an inner wall (WI) by the outer tube (AR) is placed in a fluid-tight manner on the inner wall (WI) and an outer wall serving as a cladding tube (HR), so that between the cladding tube (HR) and the wall (WI) with the outer tube (AR) mounted on an outer shell (AH) is formed, which is separated by the cladding tube (HR) reaching separator (TV) in two spatially separated areas (20, 22) in that the wall (WI) is provided with openings (S _WI1 , S _WI2 ) which are positioned congruently with the openings (S _A1 , S _A2 ) of the outer rings (AR ₁ , AR ₂ ),
so that a fluid (F1) which can be supplied to the outer shell (AH) in the first region (20) can be discharged into and out of the second region (22) of the outer shell (AH) via the first flow path,
and that a second fluid (F2) is flowable through the space enclosed by the inner wall (WI) and the outer tube (AR), traversing the integrated heat exchanger (11) along the second flow path. Radial cross-flow heat exchanger according to one of claims 1 to 6, designed as a stand-alone heat exchanger (12), characterized in that it is equipped with a cladding tube (HR), so that between the cladding tube (HR) and the outer tube (AR ) an outer shell (AH) is formed, which is separated by a reaching to the cladding tube (HR) separating device (TV) in two spatially separated areas (20, 22),
so that a first fluid (F1) fed into the first region (20) of the outer casing (AH) can be discharged into and out of the second region (22) of the outer casing (AH) via the first flow path,
and that a conduit for supplying and discharging a second fluid (F2) is connected to the outer tube (AR) such that the second fluid (F2) is flowable along the second flow path through the radial cross-flow heat exchanger (12). Radial cross-flow heat exchanger (12) according to claim 8, characterized in that its outer shell (AH) with at least one tangential port (T ₁ ), via which the first fluid (F1) in the first region (20) of the outer shell (AH ) is fed, and with at least one tangential port (T ₂ ) through which the first fluid (F1) from the second region (22) of the outer shell (AH) can be discharged, is equipped. Modular heat exchanger unit, comprising a series arrangement of a plurality of radial cross-flow heat exchangers, which are designed as integrated heat exchangers (11) or comprising a series connection or a parallel connection of a plurality of radial cross-flow heat exchangers, which are used as stand-alone heat exchangers (12). are formed. Use of a radial cross-flow heat exchanger, designed as an integrated heat exchanger (11) according to claim 7 or a modular heat exchanger unit according to claim 10 in conjunction with a combustion chamber (BK) for heat transfer between one through the outer shell (AH) and the first flow path flowing first fluid (F1) and a through the from the inner wall (WI) of the combustion chamber (BK) with the mounted integrated heat exchanger (11) enclosed space along the second flow path flowing second fluid (F2). Use according to claim 11, characterized in that the first fluid (F1) after passing through the outer shell (AH) of the combustion chamber (BK) is supplied and converted into the second fluid (F2). Use of a radial cross-flow heat exchanger, designed as a stand-alone heat exchanger (12) according to claim 8 or 9 or a modular Heat exchanger unit according to claim 10 for heat transfer between a in the outer shell (AH) and the first flow path flowing first fluid (F1) and connected by a on both sides of the outer tube (AR) line and via the second flow path flowing second fluid (F2 ). Use according to claim 13, characterized in that the first fluid (F1) transfers process waste heat or heat from a heat storage to the second fluid (F2), whereby the composition and the function of both fluids can be interchanged. Use according to claim 13, characterized in that the second fluid (F2) is a reactive mixture in which an equilibrium reaction takes place, and in that the first fluid (F1) is supplied to or removed from the reaction heat by the second fluid (F2) the composition and function of both fluids can also be reversed.

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