EP1876391B1 - Échangeur de chaleur et méthode pour sa fabrication - Google Patents

Échangeur de chaleur et méthode pour sa fabrication Download PDF

Info

Publication number
EP1876391B1
EP1876391B1 EP20060014059 EP06014059A EP1876391B1 EP 1876391 B1 EP1876391 B1 EP 1876391B1 EP 20060014059 EP20060014059 EP 20060014059 EP 06014059 A EP06014059 A EP 06014059A EP 1876391 B1 EP1876391 B1 EP 1876391B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
exchanger according
pipes
area
deflection means
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.)
Expired - Fee Related
Application number
EP20060014059
Other languages
German (de)
English (en)
Other versions
EP1876391A1 (fr
Inventor
Wilhelm Bruckmann
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.)
Balcke Duerr GmbH
Original Assignee
Balcke Duerr 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 Balcke Duerr GmbH filed Critical Balcke Duerr GmbH
Priority to EP20060014059 priority Critical patent/EP1876391B1/fr
Priority to DE200650004797 priority patent/DE502006004797D1/de
Publication of EP1876391A1 publication Critical patent/EP1876391A1/fr
Application granted granted Critical
Publication of EP1876391B1 publication Critical patent/EP1876391B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G1/00—Steam superheating characterised by heating method
    • F22G1/005—Steam superheating characterised by heating method the heat being supplied by steam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G3/00—Steam superheaters characterised by constructional features; Details of component parts thereof
    • F22G3/006—Steam superheaters with heating tubes
    • 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
    • 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
    • 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

Definitions

  • the present invention relates to a heat exchanger and a method for its production.
  • the heat exchanger is a steam-heated reheater having a channel extending in a longitudinal direction through which a medium to be heated can flow.
  • the medium to be heated is usually water vapor, but it can be generally suitable media such as gases, liquids or mixtures thereof.
  • a plurality of heat exchanger tubes is arranged, which also extend in the channel longitudinal direction and which can be traversed by a heating medium.
  • the heating medium is usually also water vapor, which, however, has a higher temperature than the medium to be heated. But here, too, it can generally be appropriately suitable media such as gases, liquids or mixtures thereof.
  • the steam to be heated flows in the channel in the channel longitudinal direction, along the outside of the heat exchanger tubes and is heated by the hotter heat exchanger tubes.
  • the heat exchanger tubes are arranged as a tube bundle between at least one distribution chamber and at least one collecting chamber and connected via tube sheets with the respective chambers.
  • the heat exchanger tubes are so closely spaced from one another that the medium to be heated can enter between them and, in the further course, can flow along the tubes in the longitudinal direction.
  • the heating medium flows from the distribution chamber into the heat exchanger tubes and leaves them in the collection chamber.
  • the tubesheets are solid components, in which the heat exchanger tubes are held in corresponding recesses.
  • the invention is therefore based on the object , a heat exchanger with significantly reduced pressure losses, which also allows an effective removal of inert gases from the heating medium, and to provide a manufacturing method for such a heat exchanger.
  • a heat exchanger having the features of claim 1 and with a manufacturing method having the features of claim 27.
  • it is a heat exchanger, in particular steam-heated reheater of the type described above, but which differs from the conventional types in that the heat exchanger tubes are arranged as a ring-shaped tube bundle with a non-central area.
  • annular is understood in this context not only an annular tube bundle. It can also be elliptical or angular rings. It is crucial that this annular tube bundle has in its center a central region which is not drilled.
  • the bundle-shaped, although dense, but still spaced next to each other arranged heat exchanger tubes with the unthreaded central region form a channel longitudinally extending, located in the interior, flow channel-like area.
  • at least one outer deflecting means is provided according to the invention for achieving a transverse flow in the medium to be heated, directed at the non-centered central area.
  • the medium to be heated sweeps transversely through the deflecting means from the outside to the inside over the heat exchanger tubes and not along the heat exchanger tube in the longitudinal direction as in the case of the generic heat exchangers.
  • the pressure loss compared to longitudinal flow Lower tube bundles with centered hole to approx. 25% of previous values.
  • the resulting power gain can be up to 8 MWe for a 1300 MWe nuclear power plant.
  • the vent with a suction port is used to extract, for example, inert gases from the heating medium.
  • the suction opening should preferably be in the region of the curved floor area.
  • This space can be used in certain embodiments of the heat exchanger for the collection of condensate liquid, which accumulate on the condensate, the inert gases. Now, if this space is increased, results in a larger buffer for itself accumulating condensate, without thereby reducing the space for the extraction of inert gases.
  • the suction opening of the vent is disposed between maximum bulge of the curved bottom portion and the drilled bottom portion of the tube bottom of the collection chamber. Then the suction is above the tube sheet, ie higher than usual. This has the advantage that the space for collecting condensate in the collection chamber again increases compared to conventional collection chambers.
  • the unthreaded central region of the tube bundle has a minimum width which is greater than the maximum ring thickness of the tube bundle.
  • Under the maximum ring thickness of the tube bundle ring is in a symmetrical circular ring half the difference between outside and Inner diameter of the annulus to understand.
  • This ratio value ensures that there is a sufficiently large, central, untouched area in which the medium to be heated, which enters the central area across the heat exchanger tubes, can change its flow direction without major friction losses. It is therefore not hindered in his direction change by running in the channel longitudinal direction heat exchanger tubes.
  • the outer deflection means may be annular, wherein it is particularly preferably at least partially conically shaped.
  • the outer deflection means generates a uniformly deflected flow in the channel and, in particular in the case of a symmetrical arrangement in relation to the channel longitudinal axis, also a symmetrical deflection.
  • the quasi-annular streams, which are directed in each case towards the center therefore flow toward one another in the radial direction and meet in the non-centered central region of the tube bundle, where they deflect each other in the direction of the channel longitudinal axis.
  • a flow aligned in the channel longitudinal direction then arises in the non-central region of the tube bundle.
  • the outer deflecting means extends from a channel wall of the channel inwardly to at least the outer peripheral portion of the tube bundle, preferably even to its non-centered central portion and slightly beyond. This has the advantage that the outer deflecting means then ensures that there is a transverse flow over the individual heat exchanger tubes of the tube bundle and the transverse flow only changes in the non-central area into a longitudinal flow.
  • the outer deflection is attached to the channel wall.
  • the deflection can be well attached to the channel wall, since this is usually sufficiently stable to carry the introduced from the outer deflection forces.
  • One of the chambers so either the collection chamber or the distribution chamber, has a tube plate having an annular, drilled bottom portion.
  • the Berohrungsmuster this drilled floor area corresponds to that of the tube bundle ring, since the tubes are passed through the tubesheet and held by the tubesheet in the heat exchanger.
  • the drilled ground area surrounds one mossy ground area, where the mossy ground area is thinner than the drilled ground area.
  • the drilled floor area thus serves to hold the heat exchanger tubes in order to connect them to the respectively adjoining chamber and the non-drilled floor area serves for sealing.
  • the pristine floor area has greater elasticity than the drilled floor area. So it can be made of a softer material with a lower modulus of elasticity than the drilled area.
  • the untapped floor area is made thinner than the drilled floor area.
  • This measure can supplement or replace the execution of the non-ground area of softer material.
  • the inventive embodiment of the tube plates has the advantage that arrival or Abfahrvor réelle the heat exchanger according to the invention are much faster possible than in generic conventional heat exchangers. The heat exchanger and thus the entire system or the power plant can therefore be operated much more flexible.
  • the mossy floor area has a domed area.
  • the curvature can be done with a constant radius or a variable radius. It is only important that the deformability of the non-drilled soil area is increased by this shaping so that as few stresses as possible are introduced from the non-drilled soil area into the drilled soil area.
  • the domed Areas of both tubes in the same direction bulged.
  • a vent with a suction port is arranged, which serves for the extraction of, for example, inert gases from the heating medium.
  • the suction opening should be in the area of the arched floor area.
  • This space can be used in certain embodiments of the heat exchanger for the collection of condensate liquid, which accumulate on the condensate, the inert gases. Now, if this space is increased, results in a larger buffer for itself accumulating condensate, without thereby reducing the space for the extraction of inert gases.
  • the suction opening of the vent is disposed between maximum bulge of the curved bottom portion and the drilled bottom portion of the tube bottom of the collection chamber. Then the suction is above the tube sheet, ie higher than usual. This has the advantage that the space for collecting condensate in the collection chamber again increases compared to conventional collection chambers.
  • the untapped floor area consists of a press plate. It is also advantageous if the drilled floor area consists of a forged part.
  • the press plate can be easily formed and is inexpensive, while the forged part has a high strength, which is particularly advantageous for the secure holding of the tubes. This is expediently a forged steel.
  • the outer deflection means preferably has a expansion compensator for compensating for different strains. Such differences in expansion may arise, for example, from the different changes in length of the deflection means or the heat exchanger tubes with respect to the channel walls.
  • the expansion compensator is a correspondingly suitable compensation spring which prevents excessive loading of the deflection means.
  • the expansion compensator therefore preferably has a ring plate with shafts running coaxially to its longitudinal axis. It is therefore an annularly curved corrugated sheet, the waves either parallel to the longitudinal axis or transverse to the longitudinal axis, that is radial, run. In any case, it is ensured by such an arrangement that by stretching or compressing the waves sufficient deformation is available to ensure differences in expansion between the deflection and the channel wall and the heat exchanger tubes.
  • the expansion compensator is preferably made of stainless steel. This takes account of the increased stresses, in particular of many deformation changes under permanent steam stress.
  • At least one inner deflection means for achieving a cross-flow in the medium to be heated is arranged in the non-central area of the tube bundle. This can ensure that a flow of the medium to be heated, directed from the outer deflecting means into the inner, non-centered central area, is again directed back out of the non-drilled central area towards the channel wall. Therefore, inner and outer deflection means are preferably arranged alternately along the channel longitudinal axis. This results in a serpentine, meandering flow through the heat exchanger, which preferably has at least one to four transversely to the channel longitudinal axis extending flow paths.
  • the inner deflection means extends at least over the entire non-central area of the tube bundle. It may be a disc in the simplest embodiment. This can be made very good and easy.
  • the heat exchanger tubes are supported in their course by at least one annular support means transversely to their longitudinal axes. This prevents excessive deformation or vibration of the heat exchanger tubes due to the cross flow of the medium to be heated. In addition, a buckling of individual heat exchanger tubes is prevented due to larger normal stresses.
  • the width of the support means approximately correspond to the ring width of the tube bundle, since it then also contributes to a deflection of the flow across the heat exchanger tubes.
  • the support means can also protrude slightly beyond the ring width of the tube bundle both inwardly and outwardly to be more stable and redirect even more parts of the flow of the medium to be heated.
  • a deflection is attached to at least one support means. This has the advantage that one already uses existing support means for fixing the deflection.
  • At least one support means and / or a deflection means is attached to at least one heat exchanger tube.
  • the support means or deflection always remains fixed in its position relative to the heat exchanger tube.
  • At least one support means and / or a deflection means has at least one recess for the passage of a heat exchanger tube. That is, the heat exchanger tube is passed through the support means or the deflection means, it being expedient if all the heat exchanger tubes are performed by the support means or deflection means. If all the heat exchanger tubes are performed by their own recesses, then the support means or the deflecting means supports the heat exchanger tubes against each other. Also, the support means or the deflection can be connected in the region of the recesses with the heat exchanger tubes.
  • the deflection means can be fastened directly to the channel wall without a expansion compensator. Then thermal expansion of the heat exchanger tubes can not be transferred to the deflection. It can therefore not come to harmful voltages between the deflection and the channel wall.
  • the heat exchanger tubes finned tubes.
  • the surface of the heat exchanger tubes flushed around by the medium to be heated is increased.
  • it is low-finned finned tubes, since the weight of the heat exchanger can be reduced as a whole by their use. This is especially advantageous during transport and during assembly.
  • the ribs of the heat exchanger tubes do not run parallel to the longitudinal axis of the tubes. This reduces the flow resistance of the heat exchanger tubes and the deflection of the flow transversely to the tube longitudinal axis is supported by the surface of the tubes.
  • the above-mentioned object is also achieved by a method for producing a heat exchanger, in which an existing heat exchanger of conventional design is rebuilt.
  • an existing tube bundle is removed in a first step, in a second step, the original tubesheets are rebuilt to the previously described tube sheets according to the invention with annularly bored bottom portion, and in a third step, an annular tube bundle with new heat exchanger tubes and at least one deflection means to achieve Cross-flow installed in the heat exchanger.
  • the production method according to the invention is therefore based on the astonishing knowledge that it is possible to use a heat exchanger through which a heat exchanger flows longitudinally and substantially parallel to the channel axis To be able to use output product for the production of a completely different flowed through heat exchanger. Accordingly, the conversion succeeds without setting a larger footprint. Therefore, it is possible to produce water separators and reheaters of the first generation to water separators and reheaters according to the invention design on the spot, ie in the power plant. In such a case, therefore, the water separator and reheater of the first generation is the starting product for the production of the heat exchanger according to the invention, wherein its outer shell, ie channel wall, essentially remains and only the interior is replaced.
  • the original tubesheets are rebuilt against tube plates, as described above, with an annularly drilled bottom area.
  • This is particularly successful when it is found during the upgrade of a heat exchanger that the original tube sheet or the original tube plates have little signs of wear, so a focus mainly on the heat exchanger tubes.
  • only the area of the tubesheet that has subsequently been milled out must be cut out and replaced by a more elastic or thinner floor area. This can be done on the spot in the power plant and also has the advantage that you do not have to completely rebuild the very expensive tube sheets.
  • the new heat exchanger tubes are installed as a preassembled package together with at least one support means and / or deflection means and / or at least one tubesheet.
  • the in Fig. 1 shown heat exchanger 1 is a water separator reheater for a German nuclear power plant of the first generation, which can be installed in place of a conventional Wasserabscheider reheater because it has its outer dimensions. Therefore, this heat exchanger 1 has a channel 3 extending in a longitudinal direction 2 in which a plurality of heat exchanger tubes 4 are arranged as a tube bundle 5 between an uppermost distribution chamber 6 and a lower collection chamber 7.
  • the heat exchanger tubes 4 of the tube bundle 5 are connected via a first tube plate 8 with the distribution chamber 6 and a second tube plate 9 with the collection chamber 7 and are each held by them in their position in the heat exchanger 1.
  • the distribution chamber 6 in this case has a Bankdampfeinbergsstutzen 36 through which the heating steam is introduced into the distribution chamber 6 and from there into the heat exchanger tubes 4.
  • the collection chamber 7 has a Bankdampfkondensataustritt 37, is discharged through the leaking from the heat exchanger tubes 4 condensate and some of the residual steam.
  • a manhole 38 is provided both in the distribution chamber 6 as in the collection chamber 7, through which, for example, maintenance personnel can enter into the chambers 6 and 7 for maintenance.
  • the tube bundle 5 extending between the distribution chamber 6 and the collection chamber 7 is designed in the form of a ring with a non-centered central region 10, as well as the Fig. 2 can be seen.
  • it is an embodiment of the tube bundle 5 with a substantially circular base.
  • the width of the non-centered central region 10 of the tube bundle 5 corresponds to the inner diameter of the annular tube bundle 5. The is about five and a half times wider than the ring thickness, which is chosen consistently strong over the entire ring.
  • an outer deflection means 11 is also installed in the channel 3 of the heat exchanger 1.
  • This is a partially cone-shaped steel sheet, which extends from the channel wall 12 inwardly to the inner, non-centered central region 10.
  • the deflection means 11 is constructed so that at the upper edge of the cone-shaped portion 13, an annular, flat plate 14 connects, while at the bottom of the cone-shaped portion 13, a compensator 15 is arranged.
  • the compensator 15 here is a cylindrically curved ring made of a stainless steel corrugated sheet, whose own, central longitudinal axis is arranged coaxially to the channel longitudinal axis 2 and channel longitudinal direction 2. Accordingly, the compensator 15 compensates for differences in length between the deflection means 11 and the channel wall 12, especially in this direction. Such differences in length may result due to different temperatures in the heat exchanger tubes 4 and the channel wall 12. Since the outer deflection means 11 is attached to both the heat exchanger tubes 4 as well as to the channel wall 12, these changes in length without the compensator 15 could lead to a rupture of the deflection means 11.
  • the tube plates 8 and 9 of both the distribution chamber 6 and the collection chamber 7 are each constructed in such a way that they have a drilled bottom region 16 and a non-drilled bottom region 17.
  • the tube plate 9 of the collection chamber 7 is designed as an open ring in the interior, which has only one drilled bottom region 16.
  • the drilled bottom portion 16 in all embodiments is a solid and forged carbon steel ring having a plurality of bores in each of which a heat exchanger tube 4, for example, by hydraulic pipe inside expansion with external edge welding, is fixed. The pattern of the bores corresponds in each case to the bore pattern of the tube bundle 5.
  • the non-tapped regions 17 are in the exemplary embodiments of FIGS Fig. 1 and Fig. 8 designed as curved press plates. This has the advantage that the press plates 17 are heated quickly and deform so that no appreciable stresses are introduced into the drilled bottom regions 16. Therefore, with the heat exchangers 1 according to the invention faster startup and shutdown operations than hitherto possible, so that they allow a more flexible operation of the entire system.
  • a vent 18 is arranged in the collecting chamber 7, the suction opening 19 of which lies above the drilled bottom area 16 and below the maximum bulge of the unrooved floor 17.
  • This intake 19 is thus higher arranged as in conventional heat exchangers, which creates more space for the collection of condensate or for above the condensate accumulating inert gases.
  • the buffering effect of the heat exchanger according to the invention increases in an advantageous manner.
  • Fig. 1 and Fig. 2 shown heat exchanger 1 eight support means 20. These are perforated metal rings whose hole pattern correspond to that of the tube bundle 5. In the recesses 21, the heat exchanger tubes 4 penetrate the support means 20.
  • the heat exchanger tubes 4 are finned tubes which are provided with ribs 22 at their outer peripheral sides. Like the one Fig. 3 it can be seen, these are low ribbed finned tubes.
  • the ribs 22 are thus relatively short and closely spaced. In this case, the ribs 22 extend transversely to the tube longitudinal axis 23, which is substantially parallel to the channel longitudinal axis 2 and channel longitudinal direction 2, that is without major deviation from the angular position of the channel longitudinal axis 2 and channel longitudinal direction 2, runs. This shape of the rib reduces the flow resistance and makes the tubes 4 lighter.
  • a crossing point between a heat exchanger tube 4 and the outer baffle 11 is a node that allows the omission of a compensator 15 on the baffle 11.
  • the baffle 11 is not attached to the heat exchanger tube 4. Rather, here is the recess 21 wider than the outer diameter of the heat exchanger tube 4. So that the deflecting means 11 can not be wedged or clamped to the ribs 21 of the heat exchanger tube 4, a the deflector 4 associated penetration area 24 of the outer skin of the heat exchanger tube 4 is made untouched and smooth. This penetration region 24 is longer than the deflecting means 11 is thick in order to be able to act even when changing the relative position of the two components.
  • Fig. 4 an alternative embodiment of such a crossing region is shown.
  • the deflection 11 is attached to the heat exchanger tube 4 via half-shell-shaped mounting shoes 25.
  • the half-shell-shaped fastening shoes 25 are welded to the deflecting means 11 and there to the upper ring 14 and have on their facing the heat exchanger tube 4 inside a the rib pattern of the heat exchanger tube 4 corresponding rib structure. Therefore, the ribs 26 of the fastening shoes 24 engage in the ribs 21 of the heat exchanger tube 4 and prevent twisting or displacement of the deflection means 11.
  • the in Fig. 1 shown Wasserabscheider reheater 1 flows through steam to be heated 27.
  • the steam to be heated 27 enters the reheater 1 in the inlet region 28 and initially flows vertically upward toward the outlet opening 31.
  • the steam to be heated 27 is directed by a conical taper 29 of the channel 3 to the heat exchanger tubes 4.
  • the steam 27 to be heated flows transversely across the heat exchanger tubes 4 of the annular tube bundle 5 into the inner, unthreaded central region 10. Due to the symmetrical in this area embodiment of the channel wall 12 of the heat exchanger 1 meet there in opposite directions inwardly flowing cross flows each other and divert against each other so that the steam 27 rises vertically in the sequence.
  • the friction loss is reduced in this heat exchanger compared to a conventional tube bundle with a central bored area.
  • the heat exchanger 1 according to the invention in addition to an outer baffle 11, the other steam strands 30 deflects so that the channel 3 is also not substantially in the sequence but longitudinally meandering transversely.
  • the deflecting means 11 Since the deflecting means 11 is arranged below an outlet opening 31, the steam to be heated 30, after being directed by the deflecting means 11 onto the non-central area 10, flows first inwardly and then laterally outwards towards the outlet opening 31, over which then heated steam leaves the reheater 1.
  • a vertically extending perforated plate 39 is arranged in front of the outlet opening 31. This perforated plate 39 is attached to support rings 20.
  • FIGS. 7 and 8 two further embodiments of inventive heat exchanger 1 are shown, in which the water vapor, as in Fig. 7 to recognize at least three transverse paths on the heat exchanger tubes 4 cover or as in Fig. 8 shown, the heat exchanger tubes 4 must cross at least four times.
  • outer, partially conically shaped deflection 11 are arranged in alternation with inner deflection means 33 along the channel longitudinal axis 2.
  • a single inner deflection means 33 and an overlying outer deflection means 11 is sufficient to achieve three cross-flow paths, as symbolized by the arrow 34.
  • the steam to be heated 27 occurs centrally in the middle of the channel 3, since here the collection chamber located below 7 is designed annular.
  • the water vapor 27 to be heated enters as an annular jet between the cylindrical outer side of the collecting chamber 7 and the channel wall 12. Since in this embodiment, too, only an inner deflection means 33 is provided, which, however, is located between two outer deflection means 11, the steam to be heated 27 has to pass across the annular tube bundle 5 at least four times before it leaves the heat exchanger 1 via the outlet opening 31 as symbolized by the arrow 35. This is called a four-way heat exchanger.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (27)

  1. Échangeur de chaleur (1), en particulier surchauffeur intermédiaire chauffé à la vapeur, avec un canal (3) s'étendant dans le sens longitudinal (2) qui peut être parcouru par un fluide à chauffer et avec une pluralité de tubes d'échangeur de chaleur (4) disposés dans celui-ci et s'étendant dans le sens longitudinal du canal (2), qui peuvent être parcourus par un fluide caloporteur et qui sont disposés sous forme de faisceaux de tubes (5) entre au moins une chambre de distribution (6) et au moins une chambre de collecte (7) et sont reliés par des plaques tubulaires (8, 9) avec les différentes chambres (6, 7),
    dans lequel les tubes d'échangeur de chaleur (4) sont disposés sous la forme d'un faisceau de tubes (5) annulaire avec une zone centrale sans tubes (10), et dans lequel est prévu dans le canal (3) au moins un moyen de déviation externe (11) pour obtenir un écoulement transversal dirigé vers la zone centrale sans tubes (10) dans le fluide à chauffer,
    dans lequel, parmi les chambres (6, 7), la chambre de collecte (7) au moins possède une plaque tubulaire (8, 9) présentant une zone de plaque (16) annulaire pourvue de tubes où la disposition des tubes correspond à celle du faisceau de tubes (5) et qui entoure une zone de plaque sans tubes (17), laquelle zone de plaque sans tubes (17) a une plus grande élasticité que la zone de plaque pourvue de tubes (16), et dans lequel la zone de plaque sans tubes (17) présente une zone bombée,
    caractérisé en ce
    qu'il est prévu dans la chambre de collecte (7) une purge d'air (18) avec une ouverture d'aspiration (19), laquelle ouverture d'aspiration (19) se trouve au niveau de la zone bombée, en ce que l'ouverture d'aspiration (19) de la purge d'air (18) se situe entre le bombement maximal de la zone bombée et la zone de plaque pourvue de tubes (16) de la plaque tubulaire (9) de la chambre de collecte (7), et en ce que la zone bombée de la plaque tubulaire (9) de la chambre de collecte (7) est bombée en direction de la chambre de distribution (6).
  2. Échangeur de chaleur selon la revendication 1,
    caractérisé en ce
    que la zone centrale sans tubes (10) du faisceau de tubes (5) a une largeur minimale plus grande que la largeur maximale de l'anneau du faisceau de tubes (5).
  3. Échangeur de chaleur selon la revendication 1 ou 2,
    caractérisé en ce
    que le moyen de déviation externe (11) est en forme d'anneau.
  4. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    que le moyen de déviation externe (11) a une forme conique par endroits.
  5. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    que le moyen de déviation externe (11) s'étend d'une paroi (12) du canal (3) vers l'intérieur jusqu'au moins à la zone de circonférence extérieure du faisceau de tube (5), de préférence jusqu'à la zone centrale sans tubes (10) de celui-ci.
  6. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    que le moyen de déviation externe (11) est fixé sur la paroi (12) du canal.
  7. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    que la zone de plaque sans tubes (17) est plus mince que la zone de plaque pourvue de tubes (16).
  8. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    que la plaque tubulaire (8) de la chambre de distribution (6) et la plaque tubulaire (9) de la chambre de collecte (7) sont de conformation identique.
  9. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    que les zones bombées des deux plaques tubulaires (8, 9) sont bombées dans le même sens.
  10. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    que la zone de plaque sans tubes (17) est faite d'une tôle emboutie.
  11. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    que la zone de plaque pourvue de tubes (16) est faite d'une pièce forgée.
  12. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    que le moyen de déviation externe (11) présente un compensateur de dilatation (15) pour compenser les dilatations différentes.
  13. Échangeur de chaleur selon la revendication 12,
    caractérisé en ce
    que le compensateur de dilatation (15) présente une tôle annulaire avec des ondulations coaxiales par rapport à son axe longitudinal.
  14. Échangeur de chaleur selon la revendication 12 ou 13,
    caractérisé en ce
    que le compensateur de dilatation (15) est fait d'acier inoxydable.
  15. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    qu'il est prévu dans la zone centrale sans tubes (10) du faisceau de tubes (5) au moins un moyen de déviation interne (33) pour obtenir un écoulement transversal dans le fluide à chauffer.
  16. Échangeur de chaleur selon la revendication 15,
    caractérisé en ce
    que le moyen de déviation interne (33) s'étend au moins sur toute la zone centrale sans tubes (10) du faisceau de tubes (5).
  17. Échangeur de chaleur selon la revendication 15 ou 16,
    caractérisé en ce
    que le moyen de déviation interne (33) est une plaque.
  18. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    que les tubes d'échangeur de chaleur (4) sont soutenus sur leur longueur perpendiculairement à leurs axes longitudinaux (23) par au moins un moyen de soutien (20) annulaire.
  19. Échangeur de chaleur selon la revendication 18,
    caractérisé en ce
    que la largeur du moyen de soutien (20) correspond approximativement à la largeur de l'anneau du faisceau de tubes (5).
  20. Échangeur de chaleur selon la revendication 18 ou 19,
    caractérisé en ce
    qu'un moyen de déviation (11, 33) est fixé à au moins un moyen de soutien (20).
  21. Échangeur de chaleur selon l'une des revendications 18 à 20,
    caractérisé en ce
    qu'au moins un moyen de soutien (20) et/ou moyen de déviation (33) sont fixés à au moins un tube d'échangeur de chaleur (4).
  22. Échangeur de chaleur selon l'une des revendications 20 à 21,
    caractérisé en ce
    qu'au moins un moyen de soutien (20) et/ou un moyen de déviation (33) présentent au moins un évidement (21) pour le passage d'un tube d'échangeur de chaleur (4).
  23. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    qu'il est prévu le long de l'axe longitudinal du canal (2) des moyens de déviation externes (11) et des moyens de déviation internes (33) alternés.
  24. Échangeur de chaleur selon l'une des revendications précédentes,
    caractérisé en ce
    que les tubes d'échangeur de chaleur (4) sont des tubes à ailettes.
  25. Échangeur de chaleur selon la revendication 24,
    caractérisé en ce
    que les ailettes (22) sont perpendiculaires à l'axe longitudinal (23) du tube d'échangeur de chaleur (4).
  26. Procédé pour la fabrication d'un échangeur de chaleur (1) selon l'une des revendications précédentes, dans lequel un échangeur de chaleur existant de construction usuelle est modifié, dans lequel, dans une première étape, un faisceau de tubes existant est démonté, dans une deuxième étape les plaques tubulaires d'origines sont modifiées en plaques tubulaires (8, 9) selon l'une des revendications 7 à 11 avec une zone de plaque pourvue de tubes (16) annulaire et dans une troisième étape, un faisceau de tubes (5) annulaire avec des nouveaux tubes d'échangeur de chaleur (4) et au moins un moyen de déviation (11, 33) pour obtenir un écoulement transversal dans l'échangeur de chaleur est mis en place.
  27. Procédé selon la revendication 26,
    caractérisé en ce
    que les nouveaux tubes d'échangeur de chaleur (4) sont montés sous la forme d'un paquet pré-assemblé avec au moins un moyen de soutien (20) et/ou moyen de déviation (11, 33) et/ou au moins une plaque tubulaire (8, 9).
EP20060014059 2006-07-06 2006-07-06 Échangeur de chaleur et méthode pour sa fabrication Expired - Fee Related EP1876391B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20060014059 EP1876391B1 (fr) 2006-07-06 2006-07-06 Échangeur de chaleur et méthode pour sa fabrication
DE200650004797 DE502006004797D1 (de) 2006-07-06 2006-07-06 Wärmetauscher und ein Verfahren zu dessen Herstellung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20060014059 EP1876391B1 (fr) 2006-07-06 2006-07-06 Échangeur de chaleur et méthode pour sa fabrication

Publications (2)

Publication Number Publication Date
EP1876391A1 EP1876391A1 (fr) 2008-01-09
EP1876391B1 true EP1876391B1 (fr) 2009-09-09

Family

ID=37943953

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060014059 Expired - Fee Related EP1876391B1 (fr) 2006-07-06 2006-07-06 Échangeur de chaleur et méthode pour sa fabrication

Country Status (2)

Country Link
EP (1) EP1876391B1 (fr)
DE (1) DE502006004797D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103733011A (zh) * 2011-08-11 2014-04-16 奥图泰有限公司 气体-气体换热器

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2584301B1 (fr) * 2011-10-19 2014-08-13 WS-Wärmeprozesstechnik GmbH Caloporteur à température élevée
EP2957852B1 (fr) * 2014-06-17 2018-12-05 Borgwarner Emissions Systems Spain, S.L.U. Déflecteurs d'écoulement
KR102514159B1 (ko) * 2017-12-22 2023-03-24 존 코케릴 에스.에이. 집광형 태양열 발전소 (ⅲ) 의 용융 염 증기 발생기용 열교환기
WO2019115306A1 (fr) * 2017-12-11 2019-06-20 Cockerill Maintenance & Ingenierie S.A. Échangeur de chaleur pour générateur de vapeur à sels fondus dans une centrale à énergie solaire concentrée (iii)
CN109000214B (zh) * 2018-08-28 2024-04-02 新疆桑顿能源科技有限公司 油田专用过热蒸汽发生器及其应用工艺

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3254705A (en) * 1960-08-22 1966-06-07 Bethlehem Steel Corp Steam generator
GB1263253A (en) * 1968-04-16 1972-02-09 Foster Wheeler Brown Boilers Heat exchangers
CH579234A5 (fr) * 1974-06-06 1976-08-31 Sulzer Ag
DE2813808A1 (de) * 1978-03-31 1979-10-04 Hochtemperatur Reaktorbau Gmbh Dampferzeuger fuer eine kernreaktoranlage
US4429739A (en) * 1980-08-29 1984-02-07 Phillips Petroleum Company Heat exchanger
DE3209584C2 (de) 1982-03-17 1986-02-06 Balcke-Dürr AG, 4030 Ratingen Vorrichtung zum Überhitzen von Dampf
SE430716B (sv) 1982-04-22 1983-12-05 Stal Laval Apparat Ab Mellanoverhettare
DE3544517C1 (de) 1985-12-17 1987-09-03 Balcke Duerr Ag Waermetauscher
DE19953612A1 (de) * 1999-11-08 2001-05-10 Abb Alstom Power Ch Ag Wärmetauscher

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103733011A (zh) * 2011-08-11 2014-04-16 奥图泰有限公司 气体-气体换热器

Also Published As

Publication number Publication date
DE502006004797D1 (de) 2009-10-22
EP1876391A1 (fr) 2008-01-09

Similar Documents

Publication Publication Date Title
DE102007024934B4 (de) Rohrbündelreaktoren mit Druckflüssigkeitskühlung
EP1876391B1 (fr) Échangeur de chaleur et méthode pour sa fabrication
EP0889201B1 (fr) Ensemble des jets d'air pour un procédé de chauffage ou de refroidissement par convection
DE60103389T2 (de) Ein wärmetauscher
EP3201550B1 (fr) Installation pour la condensation de vapeur
WO2009152830A1 (fr) Jeu d’adaptation pour un échangeur de chaleur à faisceau tubulaire
DE3332128T1 (de) Rohrträgergitter und Abstandshalter hierfür
DE3840460A1 (de) Waermetauscher
DE2209119A1 (de) Wärmetauscher
DE102009050087A1 (de) Zyklonabscheider zur Phasenseparation eines Mehrphasen-Fluidstroms, Dampfturbinenanlage mit einem Zyklonabscheider und zugehöriges Betriebsverfahren
EP3171117B1 (fr) Échangeur de chaleur régénératif comprenant un joint amélioré
DE2459472C2 (de) Gasbeheizter dampferzeuger, insbesondere fuer kernreaktoranlagen
DE4101918A1 (de) Verbrennungsanlage
DE10333463C5 (de) Rohrbündelwärmetauscher
DE2639951C3 (de) Wärmeübertrager
DE102018117457A1 (de) Wärmetauscher
EP0391266B1 (fr) Echangeur de chaleur
DE102005059502A1 (de) Heißkammer
EP0481573B1 (fr) Dispositif pour réduction de pression d'un média à gaz
DE2414295C2 (de) Wärmeaustauscher zur Kondensation von Dampf
DE102021129828A1 (de) Druckreduziervorrichtung für ein strömendes Fluid
EP1126227A1 (fr) Condenseur de vapeur
WO2021013312A1 (fr) Échangeur de chaleur à faisceau tubulaire
DE2609571C2 (de) Abblaseeinrichtung zur Überdruckbegrenzung bei Kernkraftwerken, insbesondere bei Siedewasser-Kernkraftwerken
DE2308317A1 (de) Waermetauscher mit rohrfoermig angeordnetem rohrbuendel

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20080328

AKX Designation fees paid

Designated state(s): DE

17Q First examination report despatched

Effective date: 20081205

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE

REF Corresponds to:

Ref document number: 502006004797

Country of ref document: DE

Date of ref document: 20091022

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20100610

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20190726

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502006004797

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210202