EP2584301B1 - Caloporteur à température élevée - Google Patents

Caloporteur à température élevée Download PDF

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Publication number
EP2584301B1
EP2584301B1 EP11185815.5A EP11185815A EP2584301B1 EP 2584301 B1 EP2584301 B1 EP 2584301B1 EP 11185815 A EP11185815 A EP 11185815A EP 2584301 B1 EP2584301 B1 EP 2584301B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
flat
exchanger according
tubular heat
tube
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.)
Active
Application number
EP11185815.5A
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German (de)
English (en)
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EP2584301A1 (fr
Inventor
Joachim A. Wünning
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.)
WS Warmeprozesstechnik GmbH
Original Assignee
WS Warmeprozesstechnik GmbH
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 WS Warmeprozesstechnik GmbH filed Critical WS Warmeprozesstechnik GmbH
Priority to EP11185815.5A priority Critical patent/EP2584301B1/fr
Priority to JP2014536184A priority patent/JP6113175B2/ja
Priority to PCT/EP2012/069873 priority patent/WO2013057003A1/fr
Priority to US14/351,958 priority patent/US10914528B2/en
Priority to KR1020147010063A priority patent/KR20140092308A/ko
Publication of EP2584301A1 publication Critical patent/EP2584301A1/fr
Application granted granted Critical
Publication of EP2584301B1 publication Critical patent/EP2584301B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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    • 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
    • F28D7/16—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 in parallel spaced relation
    • F28D7/1615—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 in parallel spaced relation the conduits being inside a casing and extending at an angle to the longitudinal axis of the casing; the conduits 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
    • F28D7/16—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 in parallel spaced relation
    • F28D7/163—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1653—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape
    • F28D7/1661—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F28D7/16—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 in parallel spaced relation
    • 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
    • F28D7/16—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 in parallel spaced relation
    • F28D7/163—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1669—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having an annular shape; the conduits being assembled around a central distribution tube
    • F28D7/1676—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having an annular shape; the conduits being assembled around a central distribution tube with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F28D7/16—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 in parallel spaced relation
    • F28D7/1684—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 in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—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 in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/006—Tubular elements; Assemblies of tubular elements with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/224—Longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/226—Transversal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0243—Header boxes having a circular cross-section

Definitions

  • the invention relates to a high-temperature heat exchanger, in particular for gaseous media.
  • a heat exchanger with the features of the preamble of claim 1 is for example from the FR 2293684 known.
  • the energy efficiency of high-temperature processes can be significantly increased by means of gas / gas heat exchangers, when the heat exchangers transfer the heat content of one gas stream as completely as possible to another gas stream.
  • the gas streams may be, for example, educts and products of a chemical reaction process, for example in the form of a combustion process.
  • the reaction can take place, for example, in an SOFC fuel cell or a fuel cell system, in micro gas turbines or other heat engines.
  • the masses or heat capacity flows of the two gases for example, fresh air and exhaust gas
  • the WO 96/20808 a heat exchanger with a closed approximately cylindrical, closed by rounded end caps vessel and arranged at opposite ends of the vessel tube sheets.
  • the tube plates divide the interior into three separate rooms, namely, for example, two plenums and a tube bundle space between them.
  • the connections of the collecting chambers are, for example, arranged concentrically to the longitudinal axis of the cylindrical housing at the end caps. Inflow and outflow of the tube bundle space are arranged, for example, radially on the cylindrical housing wall.
  • the tubes of the tube bundle are for example straight and provided with sections of different cross section. It change round cross sections with oval cross sections.
  • EP 1 995 516 B1 an open heat exchanger with only one side taken flat tubes. These are round at their ends and flat in a middle section. In the flat portion, the cross section of the tube is formed by two gap defining portions which are curved with large radius, these being connected at their ends by portions which curve with a small radius are.
  • the flat tubes are arranged on concentric circles of the overall substantially rotationally symmetrical heat exchanger. The same number of tubes is provided on each circle. Corrugated spacers are arranged between the tubes.
  • This flat tube heat exchanger is operated in countercurrent operation. On the side facing the combustion chamber of the flat tubes nozzles are formed, which cause a high gas outlet velocity. This is specifically a Abgas139rekuperator, which should cause a flameless oxidation due to the high gas outlet velocity in the connected combustion chamber.
  • he should combine a high temperature spread, a high transfer efficiency, a high packing density and a long service life with low pressure losses and low production costs.
  • the flat tube heat exchanger has a closed housing in which two tubesheets and a tube bundle arranged between the tubesheets and carried by the tubesheets are arranged.
  • the tube bundle comprises at least some flat tubes extending in the tube bundle longitudinal direction.
  • the flat tubes are round at their ends and flat in a middle section.
  • the round in cross-section ends of the flat tubes may be circular or have a different round shape. For example, they may have an elliptical cross section, an oval cross section or even a polygonal cross section (triangular, square, rectangular, hexagonal or the like), which has a Round shape approximates.
  • the cross section of the round section lies between preferably 50% to 70% of the cross section of the flat cross section.
  • the flat cross sections are circular
  • the flat cross sections have an oval shape, which is preferably composed of arcuate end sections of small radius and straight wall sections without curvature.
  • such flat tubes are produced by initially starting from a tube having a section of circular cross-section and larger diameter between two sections of circular cross section and smaller diameter.
  • the section with a larger diameter can be flattened in a forming process, eg rolling process, eg between cylindrical rollers.
  • the configuration of the flat tubes described so far is preferred for all embodiments of the heat exchanger according to the invention.
  • three zones are formed in the tube bundle space, namely two cross-flow zones formed at the tube-bundle space connections and a longitudinal flow zone formed between these cross-flow zones.
  • the transverse flow zones are preferably defined by the fact that a section is provided in each case on both sides adjacent to the tubesheets, in that the flat tubes have a round cross section (preferably circular cross section) or circular polygonal cross section and are tapered in order to control the inflow or outflow of the gas transversely to the To allow flat tubes.
  • corresponding lanes are formed between the individual flat tubes. It is preferred to orient these streets in the inflow and outflow direction. In a rotationally symmetrical structure, these streets are preferably oriented radially.
  • the inflow or outflow can be done radially from the inside or radially from or to the outside.
  • the transverse flow direction defined by the cross-flow zone is preferably vertical to the flat sides of the flat tubes, that is oriented parallel to the surface normal direction of the flat sides. This concept can be applied to all embodiments of the heat exchanger.
  • the longitudinal flow zone is defined by the fact that there is essentially no crossflow in it.
  • the adjusting between the flat pipe sections flow runs anti-parallel to the flowing in the flat tubes flow.
  • the flow preferably does not alternate between the various longitudinal flow paths existing between the flat tubes. This is achieved by adjacent flat tubes are arranged touching each other or nearly touching with a small gap.
  • the flat tube heat exchanger can be constructed as a rectangle or as a round arrangement. In the rectangular arrangement, it has a cuboid tube bundle space. In the round arrangement, it has a cylindrical tube bundle space.
  • the heat exchanger is constructed in a round arrangement as a ring heat exchanger.
  • Its housing is then, for example, cylindrical or polygonal limited. Coaxially with the outer wall, the heat exchanger housing may have an inner wall. This may include other aggregates, such as, for example, a reactor in which the supplied process gas undergoes a chemical process, a burner, another heat source, or combinations thereof.
  • the longitudinal flow space, in which the flat portions of the flat tubes are arranged annular (ie, hollow cylindrical) is formed.
  • at least one of the two transverse flow spaces is preferably cylindrical and has a free central gas distribution space (gas collection space) from which the gas flow leads radially outwards between the round sections of the flat tubes (or vice versa).
  • the tube bundle preferably has an extension that is at most twice as long as the length of the transverse inflow zone measured in the tube bundle longitudinal direction.
  • the said measure also creates a good condition for being able to arrange the flat tubes in the tube bundle relatively dense, so that there is a good use of space and thus a compact design. This can also contribute that certain dimensions are met for the flat tubes.
  • the flat tubes Preferably, have an inner gap width s of 1 mm to 5 mm, preferably 1 mm to 3 mm. The optimal gap width is 2mm.
  • the free width of the flat tube interior is preferably 7 mm to 20 mm.
  • the flat tubes are preferably arranged in a packing density p of 0.9 m 2 / dm 3 to 0.2 m 2 / dm 3 .
  • spacing structures for example in the form of embossed knobs, ribs or the like, may be present on the flat tubes in order to fix the distance between the tubes.
  • the distance between the flat tubes is preferably at most in the order of the gap width.
  • the gap width is preferably at most a few millimeters.
  • the distance of the rounded portions of the flat tubes from each other is preferably less than the gap width.
  • Turbulence vortices may be formed on the inner and / or outer surfaces of the flat tubes turbulence generating elements, for example. Ribs, projections, dents or the like.
  • all flat tubes have the same shape, so they are uniform, which keeps the production costs low.
  • the tubes may be formed in one piece or in several parts. This can be expedient in particular with a very high temperature spread. It can pipes made of different materials butt joined to each other in particular welded. Thus, other materials can be used in the cold zone than in the warm zone.
  • an expansion element can be arranged, which compensates for expansion differences between the housing and the tube bundle.
  • the expansion compensation element is preferably arranged on the cold side of the heat exchanger.
  • heat exchanger tubes are arranged in an annular zone which encloses a central region, a burner with a combustion chamber can be arranged there, for example in order to heat a reactor present there. Between the combustion chamber and the heat exchanger, an insulating layer is preferably arranged. This combination of heat exchanger and combustion chamber is suitable, for example, for heating the cathode air for an SOFC fuel cell.
  • a catalytic reactor In the interior, in particular in the tube bundle space of the heat exchanger and a catalytic reactor may be mounted. This can be arranged, for example, as a reformer in the anode gas cycle of an SOFC fuel cell system.
  • the gas to be heated in the tubes and the heat-emitting gas is passed between the tubes. It can gases with very high inlet temperatures, such as. 1000 ° C are processed.
  • the heat transfer rates are based on the volume of construction in the same range as that of plate heat exchangers and regenerators at comparable gap widths.
  • welded plate heat exchangers are not suitable for such high temperatures.
  • the proposed flat tube heat exchanger is thus particularly suitable for decentralized power generation, e.g. in SOFC fuel cells or micro gas turbines. It does not require the changeover valves and controls required for regenerators.
  • FIG. 1 a flat tube heat exchanger 10 is illustrated, which is housed here in a cylindrical housing 11. At both ends of the housing 11 preferably curved closure cap 12, 13 are attached, which belong to the housing 11 and may be part of the same, for example.
  • the housing 11 encloses, together with the covers 12, 13, an interior which, through two tube sheets 14, 15 in a total of three spaces, namely an input-side collecting space 16 (FIG. FIG. 1 below), a tube bundle space 17 and an output-side collecting space 18 are divided.
  • the collecting chambers 16, 18 are each provided with a connection 19, 20.
  • the connection 19 is, for example, subjected to cold air. For example, hot air is to be delivered to the connection 20.
  • a tube bundle 21 is arranged between the tube sheets 14, 15, a tube bundle 21 is arranged.
  • This consists of numerous mutually preferably equal flat tubes 22.
  • the cross sections of the flat tubes 22 have straight flanks which define the inner gap cross-section between each other.
  • the flat flanks are interconnected by small radius bent sections.
  • Each flat tube 22 is preferably formed straight and arranged parallel to an imaginary central axis 23 of the housing 11.
  • the flat tubes 22 are anchored with their ends 24, 25 to the tube sheets 14, 15. For example, they are welded to the respective tubesheet 14, 15, brazed, pressed, crimped or connected in any other suitable manner.
  • the compound is fluid-tight and temperature-resistant.
  • Each flat tube 22 has a comparatively long central section A with a flat cross section and at its two ends 24, 25 a shorter section B with a circular cross section.
  • FIG. 2 illustrates the tube bundle 21 in the region of its section A in a sectional view.
  • each flat tube 22 has an inner gap cross-section whose width is 1 mm to 4 mm, preferably 2 mm to 3 mm. The circumference of this cross section is preferably between 20 mm and 40 mm.
  • the flat tubes 22 are each arranged in an annularly closed row, each row being circular (strictly speaking polygonal) and concentric with the central axis 23.
  • the flat tubes 22 are at least preferably arranged such that the individual flat tubes 22 just do not touch with their strongly curved sections. However, the remaining gaps between the flat tubes 22 within a row are small.
  • the flat tubes can alternatively also touch each other at any temperature or only at certain temperatures.
  • the flat sides of the flat tubes are oriented in the circumferential direction, that is tangent to the respective circle on which they are arranged.
  • annular spaces formed between the rows or boundaries of different flat tubes 22 are relatively narrow. It is largely free of other internals held annular flow channels.
  • the individual annular flow channels are largely separated from one another by the flat tube rings in terms of flow.
  • the flat tubes may be arranged in a single spiral wound row. Also, they can be slightly inclined against the circumferential direction, so be rotated slightly about their respective longitudinal axis. With the tangential direction they then enclose an acute angle.
  • the above statements regarding cross-sectional shape and tube spacing apply accordingly.
  • each of FIG. 2 illustrated annular array of tubes arranged in number so as to give a closed as possible row.
  • the number of flat tubes 22 in the rows do not match each other.
  • the number of tubes preferably increases radially from the inside to the outside.
  • the numbers of tubes of adjacent annular rows differ by 1 to 3, preferably 2.
  • FIG. 3 it can be seen, form the flat tubes 22 with their sections B, an arrangement which is radially flow-permeable, at least permeable than the arrangement of the sections A according to FIG. 2 , It forms flow paths 26 to 28, which allow a radial flow.
  • a cross-flow zone 29 is formed in the round sections B of the flat tubes 22 . This applies both to the ends 24 of the flat tubes adjacent to the upper tube bottom 14 and to the ends 25 of the flat tubes 22 which adjoin the lower base 15.
  • the tube bundle 21 has a thickness C in the transverse inflow direction, which is preferably at most twice as great the length of section B, ie the transverse inflow zone.
  • the flat portions A of the flat tubes 22 may extend into the lateral inflow zone 29. This is especially true if the transverse inflow, as it is also possible, is parallel or at an acute angle to the flat sides of the flat sections. This applies to all embodiments.
  • the lying between the two transverse flow zones 29 sections A of the flat tubes 22 form a longitudinal flow zone 30, which serves the actual heat exchange.
  • tube bundle space connections 31, 32 which may be arranged coaxially to the central axis 23, for example may be arranged coaxially to the central axis 23 and in this case, the closure cover 12, 13 and the tube sheets 14, 15 prevail.
  • the tube bundle connections 32, 33 can also be arranged elsewhere. For example, they may be formed by the housing 11 passing through in the areas B radially or tangentially to the housing 11 attaching. Further, concentric with the central axis 23, an inner housing wall 33 may be arranged. This can be formed by a solid body or a hollow body. It can surround other parts of the plant, a heat storage or the like, or it can be empty.
  • the housing 11 may be provided at a suitable location with a strain compensation element 34. Preferably, this is in the cylindrical portion of the housing 11 between the tubesheets 14, 15, preferably in the vicinity of the colder tube bottom, i. attached to the input-side terminal 19.
  • the expansion compensation element may allow, within certain limits, an axial expansion and compression of the housing 11, so that the distance between the tube sheets 14, 15 is determined by the temperature and thus the length of the tube bundle 21.
  • the housing 11 adapts accordingly.
  • the flat tube heat exchanger 10 described so far operates as follows:
  • the flat tube heat exchanger 10 via the tube bundle space 31 hot, preferably gaseous fluid, eg. Exhaust gas of a micro gas turbine or the like supplied. Above the approximately cylindrical central body enclosed by the inner housing wall 33, this flow is deflected essentially in the radial direction. She reaches the in FIG. 3 apparent lanes 26 to 28 and distributes radially and circumferentially in the tube bundle 21. Starting from the cross clean-flow zone 29, the hot gas stream then runs in the longitudinal direction substantially parallel to the central axis 23 through the annular zones between the flat tubes 22, which are in FIG. 2 can be seen. The heat contained in the hot gas flow is transferred to the wall of the flat tubes 22.
  • gaseous fluid eg. Exhaust gas of a micro gas turbine or the like supplied.
  • gaseous fluid eg. Exhaust gas of a micro gas turbine or the like supplied.
  • gaseous fluid eg. Exhaust gas of a micro gas turbine or the like supplied.
  • this flow is deflected
  • cold gas for example air at ambient temperature
  • inlet-side connection 19 cold gas
  • the supplied cool air absorbs a large part of the heat and can reach in the collecting space, for example. 800 ° or 900 °. It then flows via the output-side terminal 20.
  • the flat tube heat exchanger 10 Due to the illustrated flow structure, the flat tube heat exchanger 10 has only a small differential pressure requirement both for the hot gas stream and for the cold gas stream. The resulting pressure loss is low. Due to the narrow gap width of the flat tubes 22 and the dense arrangement thereof, a high heat utilization is achieved.
  • the exhaust gas leaving the tube bundle space 17 via the tube bundle connection 32 is, for example, cooled to low temperatures of a few 100.degree. C., for example 200.degree. C. or 300.degree.
  • FIGS. 4 to 6 illustrate optional details of the flat tube 22. Preferably, it has different circumferences in the sections A and B, as already explained above with reference to the cross sections.
  • each flat tube 22 with projections 35, for example. Be provided in the form of knobs or ribs, fins or the like. These projections 35 may serve as spacers to prevent flat tubes 22 of different rows from approaching too much and obstructing the flow channel therebetween. It is also possible to use these projections 35 as turbulence-generating elements in order to improve the heat transfer from the hot gases flowing between the flat tubes 22 to the flat tubes 22.
  • FIG. 7 illustrates a modified embodiment of the flat tube heat exchanger 10. This is here combined with a burner 36 for generating hot gas and structurally unified.
  • the tube bundle space connection 31 is designed or used as a supply air duct for combustion air.
  • a fuel channel 37 is arranged concentrically.
  • anode residual gas or another fuel can be conducted into the combustion chamber 38 via this.
  • the combustion chamber 38 may be arranged in the interior of the container enclosed by the inner housing wall 33.
  • Eie ignition electrode 39 which can extend through the fuel channel 37, for example, completes the burner.
  • the inner housing wall 33 may be internally provided with a thermally insulating lining 40.
  • the flat tube heat exchanger 10 forms a heat exchanger with an internal heat source.
  • the heat source is a burner.
  • other heat sources can also be integrated into the heat exchanger 10 with an otherwise identical design.
  • FIG. 8 illustrates such a flat tube heat exchanger 10.
  • the tube bundle 21 formed by the flat tubes 22 is enclosed by a rectangular in cross-section or square housing 11.
  • the flat tubes 22 are arranged in mutually parallel rows and formed as described above. Their round sections B form cross-flow zones.
  • the tube bundle space 17 can be supplied with hot gas via one or more connections 31. Cooled hot gas can be discharged via one or more ports 32 from the tube bundle space 17.
  • the collecting chambers 16, 18 may be box-shaped.
  • the tube bundle formed by the flat tubes 22 in the transverse inflow direction has a thickness which is preferably at most twice as long as the length of the section B, ie the transverse inflow zone. This serves to achieve a uniform gas distribution between the flat tubes 22.
  • the direction of the transverse inflow in the embodiment of the flat tube heat exchanger 10 after FIG. 8 is determined by the longitudinal direction of the terminals 31, 32 (in FIG. 8 perpendicular to the plane of the drawing) in the above embodiments, this direction is the radial direction.
  • the thickness C of the tube bundle 21 in the exemplary embodiment Figure 1 to 3 determined by the distance of the outer wall of the housing 11 with the inner housing wall 33. This distance C is preferably at most 1.5 to 2 times as long as the length B.
  • a flat tube heat exchanger 10 which is suitable for high temperatures, tolerates a high temperature spread and reaches countercurrent operation transmission efficiencies of over 80%. In addition, it has a high packing density, low pressure drops and eg less than 50 mbar, a high durability and robustness and low production costs.
  • the flat tube heat exchanger has flat tubes, which have flat heat exchanger sections and round ends. The rounded ends define transverse inflow zones which provide a uniform gas distribution of hot gas between the flat sections of the flat tubes 22 at low pressure drops. The efficiency of such a flat tube heat exchanger is comparable to that of a plate heat exchanger, but a much higher robustness is given.

Claims (15)

  1. Echangeur de chaleur tubulaire (10), destiné en particulier à des fluides gazeux,
    comprenant une enveloppe (11, 12, 13) fermée qui présente, sur deux côtés opposés, deux plaques tubulaires (14, 15) qui séparent, dans l'enveloppe (11, 12, 13), un espace collecteur (16) côté entrée, un espace de faisceau tubulaire (17) et un espace collecteur (18) côté sortie,
    comprenant un faisceau tubulaire (21) qui définit un sens longitudinal de faisceau tubulaire (23) et est constitué de tubes qui sont disposés parallèlement au sens longitudinal de faisceau tubulaire (23) et sont fixés aux plaques tubulaires (14, 15), sur des ouvertures correspondantes, de sorte que les tubes (22) communiquent avec les espaces collecteurs (16, 18),
    chaque espace collecteur (16, 18) étant doté d'au moins un raccord d'espace collecteur (19, 20), et l'espace de faisceau tubulaire (17) étant doté d'au moins deux raccords d'espace de faisceau tubulaire (31, 32) disposés à distance l'un de l'autre dans le sens longitudinal de faisceau tubulaire (23),
    l'espace de faisceau tubulaire (17) présentant trois zones, à savoir deux zones d'écoulement transversal (29), formées près des raccords d'espace de faisceau tubulaire (31, 32), et une zone d'écoulement longitudinal (30) formée entre ces zones d'écoulement transversal (29),
    caractérisé en ce que le faisceau tubulaire est constitué au moins majoritairement de tubes plats (22) de forme rectiligne, dotés d'extrémités (B) rondes ou polygonales.
  2. Echangeur de chaleur tubulaire selon la revendication 1, caractérisé en ce que les zones d'écoulement transversal (29) sont directement contiguës aux deux plaques tubulaires (14, 15).
  3. Echangeur de chaleur tubulaire selon la revendication 1 ou 2, caractérisé en ce que dans les zones d'écoulement transversal (29), les tubes plats (22) présentent respectivement une section ronde, circulaire ou polygonale, et présentent une section plate dans la zone d'écoulement longitudinal (30).
  4. Echangeur de chaleur tubulaire selon la revendication 3, caractérisé en ce que dans la zone d'écoulement longitudinal (30), les tubes plats (22) présentent une section plate avec des flancs plans.
  5. Echangeur de chaleur tubulaire selon une ou plusieurs des revendications précédentes, caractérisé en ce que, si le faisceau de tubes (21) présente, dans la zone d'écoulement transversal (29), une dimension transversale (C) dans le sens d'écoulement transversal (Q), et si la zone d'écoulement transversal (29) présente une longueur (B) dans le sens longitudinal de faisceau tubulaire (23), la longueur (B) correspond au moins à 0,5 fois la dimension transversale (C).
  6. Echangeur de chaleur tubulaire selon une ou plusieurs des revendications précédentes, caractérisé en ce que l'enveloppe (11, 12, 13) présente une paroi intérieure (33), fermée de façon annulaire en section, et une paroi extérieure (11), également fermée de façon annulaire en section.
  7. Echangeur de chaleur tubulaire selon la revendication 6, caractérisé en ce que la paroi intérieure (33) entoure une source de chaleur (36).
  8. Echangeur de chaleur tubulaire selon la revendication 6, caractérisé en ce que les tubes plats (22) sont disposés sur des cercles concentriques les uns par rapport aux autres.
  9. Echangeur de chaleur tubulaire selon la revendication 8, caractérisé en ce que des distances à mesurer dans la direction périphérique sont plus faibles que l'interstice des tronçons de tubes plats (A).
  10. Echangeur de chaleur tubulaire selon une ou plusieurs des revendications précédentes, caractérisé en ce que des voies d'écoulement transversal (26, 27, 28) sont aménagées entre les extrémités rondes des tubes plats.
  11. Echangeur de chaleur tubulaire selon la revendication 6, caractérisé en ce que les raccords d'espace de faisceau tubulaire (31, 32) sont disposés de manière à traverser la plaque tubulaire (14, 15).
  12. Echangeur de chaleur tubulaire selon une ou plusieurs des revendications précédentes, caractérisé en ce que les tubes plats (22) sont dotés de structures d'écartement (35).
  13. Echangeur de chaleur tubulaire selon une ou plusieurs des revendications précédentes, caractérisé en ce qu'au moins quelques-uns des tubes plats (22) sont dotés de structures (35) génératrices de turbulences.
  14. Echangeur de chaleur tubulaire selon une ou plusieurs des revendications précédentes, caractérisé en ce que l'enveloppe (11, 12, 13) est dotée d'au moins un élément compensateur de dilatation (34).
  15. Echangeur de chaleur tubulaire selon une ou plusieurs des revendications précédentes, caractérisé en ce qu'un catalyseur est disposé dans l'espace de faisceau tubulaire (17).
EP11185815.5A 2011-10-19 2011-10-19 Caloporteur à température élevée Active EP2584301B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP11185815.5A EP2584301B1 (fr) 2011-10-19 2011-10-19 Caloporteur à température élevée
JP2014536184A JP6113175B2 (ja) 2011-10-19 2012-10-08 高温熱交換器
PCT/EP2012/069873 WO2013057003A1 (fr) 2011-10-19 2012-10-08 Système de transfert de chaleur à haute température
US14/351,958 US10914528B2 (en) 2011-10-19 2012-10-08 High-temperature heat exchanger
KR1020147010063A KR20140092308A (ko) 2011-10-19 2012-10-08 고온 열교환기

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Application Number Priority Date Filing Date Title
EP11185815.5A EP2584301B1 (fr) 2011-10-19 2011-10-19 Caloporteur à température élevée

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EP2584301A1 EP2584301A1 (fr) 2013-04-24
EP2584301B1 true EP2584301B1 (fr) 2014-08-13

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US10914528B2 (en) 2021-02-09
US20140262174A1 (en) 2014-09-18
WO2013057003A1 (fr) 2013-04-25
JP6113175B2 (ja) 2017-04-12
JP2014531011A (ja) 2014-11-20
KR20140092308A (ko) 2014-07-23
EP2584301A1 (fr) 2013-04-24

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