EP3546873A1 - Échangeur de chaleur à flux croisé radial - Google Patents

Échangeur de chaleur à flux croisé radial Download PDF

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Publication number
EP3546873A1
EP3546873A1 EP18165093.8A EP18165093A EP3546873A1 EP 3546873 A1 EP3546873 A1 EP 3546873A1 EP 18165093 A EP18165093 A EP 18165093A EP 3546873 A1 EP3546873 A1 EP 3546873A1
Authority
EP
European Patent Office
Prior art keywords
fluid
heat exchanger
openings
elements
flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP18165093.8A
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German (de)
English (en)
Inventor
Falco KLAUS
Max RÜBSAM
Christoph Moos
Martin PITZER
Reinhold Altensen
Felix HOLY
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Technische Hochshule Mittelhessen
Technische Hochschule Mittelhessen
Original Assignee
Technische Hochshule Mittelhessen
Technische Hochschule Mittelhessen
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Technische Hochshule Mittelhessen, Technische Hochschule Mittelhessen filed Critical Technische Hochshule Mittelhessen
Priority to EP18165093.8A priority Critical patent/EP3546873A1/fr
Publication of EP3546873A1 publication Critical patent/EP3546873A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/005—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having bent portions or being assembled from bent tubes or being tubes having a toroidal configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F28D21/001—Recuperative heat exchangers the heat being recuperated from exhaust gases for thermal power plants or industrial processes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0058—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having different orientations to each other or crossing the conduit for the other heat exchange medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/04—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form

Definitions

  • 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.
  • 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.
  • 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.
  • 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.
  • R-KS-WÜ radial cross-flow heat exchanger
  • 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 .
  • 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 .
  • 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.
  • 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.
  • 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 ⁇ ⁇ D / N relative to one another.
  • Umlenkrippen ULR 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.
  • 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).
  • 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.
  • 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 corresponds to the height H of the outer tube AR.
  • 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.
  • 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 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.
  • 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 .
  • each opening S U2 is connected via a trained as a hollow body WÜ element WE 2 with an opening S A2 .
  • 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.
  • 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.
  • 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.
  • 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 ⁇ 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 ).
  • 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 1
  • 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 ⁇ 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 .
  • 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).
  • 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.
  • a cladding tube HR with a diameter D HR which is greater than the diameter D of the outer tube AR.
  • 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.
  • 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 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.
  • the first fluid F1 using the Fig. 2a and 2b known (in Fig.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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.
  • 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- pro.de/download/rtzblatt%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 naval lockeritstationem material. A thin-walled version with wall thicknesses of approx.
  • 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 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.
  • 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.
  • I-WÜ R-KS-WÜ is suitable for technical systems, which have a cylindrical wall WI.
  • 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.
  • 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.
  • 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.
  • the first fluid F1 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.
  • 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.
  • 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.
  • the design of the wall WI as a cylinder which provides only a small surface for the heat transfer, limits the heat transfer.
  • WÜ the design of the wall WI as a cylinder
  • 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.
  • 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.
  • I-WÜ 11 R-KS-WÜ 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.
  • 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.
  • 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.
  • the WÜ elements WE 1 , WE 2 take 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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.
  • 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.
  • corrugated fins in Fig. 9 were a single corrugated rib WR in Fig. 3 located.
  • 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.
  • 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.
  • 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.
  • 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.
  • the first fluid F1 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.
  • 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.
  • 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.
  • 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.
  • Each N 90 WÜ elements WE 1 and WE 2 connect the outer rings AR 1 , AR 2 with the deflection chamber U.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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).
  • 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.
  • 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.
  • the combustion chamber BK, the recirculation chamber RK, the deflection chambers U and the cladding tube HR are arranged concentrically.
  • 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.
  • 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.
  • large angles eg 90 °, 180 °
  • a second fluid F2 is parallel to the axis of the assembly, which in Fig. 11 is illustrated by two arrows.
  • a series connection of several SA-WÜ 12 can be realized in a simple manner. As Fig.
  • Fig. 13 shows a further embodiment of a SA-WÜ 12, which causes an improved flow behavior.
  • 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.
  • 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.
  • 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.
  • Umlenkrippen 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.
  • 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.
  • the illustrated invention is not limited to the presented embodiments. These can be combined in an advantageous manner.
  • the in Fig. 10 imagined combustion chamber to be converted into a chemical reactor.
  • 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.
  • 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.
  • individual components of the R-KS-WÜ can be produced by additive manufacturing, also known as 3D printing.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP18165093.8A 2018-03-29 2018-03-29 Échangeur de chaleur à flux croisé radial Withdrawn EP3546873A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP18165093.8A EP3546873A1 (fr) 2018-03-29 2018-03-29 Échangeur de chaleur à flux croisé radial

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Application Number Priority Date Filing Date Title
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3889535A1 (fr) * 2020-02-07 2021-10-06 Raytheon Technologies Corporation Échangeur de chaleur monté sur conduit
US20230144708A1 (en) * 2020-02-28 2023-05-11 General Electric Company Circular crossflow heat exchanger

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2479071A (en) * 1943-04-27 1949-08-16 Bristol Aeroplane Co Ltd Heat exchanger
US3064947A (en) * 1959-02-20 1962-11-20 United Aircraft Corp Involute flat tube and plate fin radiator
US3785435A (en) * 1972-11-15 1974-01-15 Avco Corp Thermal damper for plate type heat exchangers
GB1492912A (en) * 1976-03-09 1977-11-23 United Stirling Ab & Co Hot gas engine heater head
US5117904A (en) * 1991-07-15 1992-06-02 Bond William H Heat exchanger
US20030131978A1 (en) * 2001-11-30 2003-07-17 Toyo Radiator Co., Ltd. Cylinder-type heat exchanger
EP1347529A2 (fr) * 2002-03-19 2003-09-24 Sulzer Hexis AG Batterie de cellules à combustible avec un échangeur de chaleur intégré

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2479071A (en) * 1943-04-27 1949-08-16 Bristol Aeroplane Co Ltd Heat exchanger
US3064947A (en) * 1959-02-20 1962-11-20 United Aircraft Corp Involute flat tube and plate fin radiator
US3785435A (en) * 1972-11-15 1974-01-15 Avco Corp Thermal damper for plate type heat exchangers
GB1492912A (en) * 1976-03-09 1977-11-23 United Stirling Ab & Co Hot gas engine heater head
US5117904A (en) * 1991-07-15 1992-06-02 Bond William H Heat exchanger
US20030131978A1 (en) * 2001-11-30 2003-07-17 Toyo Radiator Co., Ltd. Cylinder-type heat exchanger
EP1347529A2 (fr) * 2002-03-19 2003-09-24 Sulzer Hexis AG Batterie de cellules à combustible avec un échangeur de chaleur intégré

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3889535A1 (fr) * 2020-02-07 2021-10-06 Raytheon Technologies Corporation Échangeur de chaleur monté sur conduit
US11650018B2 (en) 2020-02-07 2023-05-16 Raytheon Technologies Corporation Duct mounted heat exchanger
US20230144708A1 (en) * 2020-02-28 2023-05-11 General Electric Company Circular crossflow heat exchanger

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