EP0035450B1 - Dampferzeuger mit Vorwärmung - Google Patents

Dampferzeuger mit Vorwärmung Download PDF

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Publication number
EP0035450B1
EP0035450B1 EP81400308A EP81400308A EP0035450B1 EP 0035450 B1 EP0035450 B1 EP 0035450B1 EP 81400308 A EP81400308 A EP 81400308A EP 81400308 A EP81400308 A EP 81400308A EP 0035450 B1 EP0035450 B1 EP 0035450B1
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EP
European Patent Office
Prior art keywords
steam generator
cold
envelope
branch
plate
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Expired
Application number
EP81400308A
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English (en)
French (fr)
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EP0035450A1 (de
Inventor
Jean-Claude Yazidjian
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Areva NP SAS
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Framatome SA
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Priority to AT81400308T priority Critical patent/ATE4932T1/de
Publication of EP0035450A1 publication Critical patent/EP0035450A1/de
Application granted granted Critical
Publication of EP0035450B1 publication Critical patent/EP0035450B1/de
Expired legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/023—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers with heating tubes, for nuclear reactors as far as they are not classified, according to a specified heating fluid, in another group
    • F22B1/025—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers with heating tubes, for nuclear reactors as far as they are not classified, according to a specified heating fluid, in another group with vertical U shaped tubes carried on a horizontal tube sheet

Definitions

  • the invention relates to a steam generator, which can be used for example in a nuclear installation, for the production of electrical energy or for naval propulsion.
  • a conventional type steam generator comprises a cylindrical outer enclosure of vertical axis, resistant to pressure and closed at each end by a cap.
  • a horizontal tubular plate is arranged inside the enclosure, integral with the latter and delimiting with the lower cap a chamber separated into two collectors, respectively for admission and evacuation of a primary heat-transfer fluid.
  • a bundle of U-shaped tubes is mounted on the tube plate.
  • Each U-shaped tube has a hot leg which communicates with the intake manifold and a cold leg which communicates with the exhaust manifold, the set of hot legs constituting the hot branch and the set of cold legs constituting the cold branch .
  • a secondary envelope surrounds the bundle without resting on the tube plate and defines an annular space with the outer enclosure.
  • a water intake device is provided for supplying the annular space with secondary water.
  • This secondary water rises along the bundle tubes and vaporizes on contact.
  • the steam produced is discharged through an opening in the upper cap.
  • the water from the separators called recirculation water, returns to the tubular plate using the annular space between the outer enclosure and the secondary envelope, before rising again along the bundle of U-shaped tubes.
  • Recirculation water mixes a food water which comes from the intake device of which we spoke above. This intake device is placed in the upper part of the steam generator so that the mixture of drinking water and recirculating water is homogeneous before it enters the tube bundle.
  • the generator of the conventional type which has just been described has the following drawback in particular: the primary-secondary exchange surface is not used optimally; therefore, the thermal efficiency of the entire generator is not maximum.
  • this configuration has several drawbacks.
  • the inlet and guide structures of this water must be relatively tight.
  • it has the drawback due to the fact that at low load or during certain operating transients (introduction of emergency water), the temperature of the drinking water decreases. This water can then initiate in the structures with which it comes into contact (tubes, tube plate, pressure vessel) unacceptable thermal stresses.
  • This geometry is expressed in relation to the theoretical case considered above by a drop in the saturation pressure delivered by the steam generator and complex structures to be installed in the lower part of the device.
  • the preheater floor can create bending stresses in the tubes (pressure deformation of the tube plate, differential expansion of the tube plate and the preheater floor), and also makes the casing operation difficult because of its lower permeability than that of the tube bundle spacer plates and its proximity to the tubular plate.
  • this floor cannot be perfectly sealed, so that part of the drinking water passes through it and goes towards the hot branch; this decreases the overall performance of the steam generator.
  • the steam generator of the type described in French application No. 2 285 573 has the disadvantage of having a more restricted space for the tubes for a given diameter of the envelope under pressure, part of the space being occupied. by the preheater.
  • this embodiment leads to a very complex structure and the thickness of the central box means that the number of U-shaped tubes has to be reduced, for a given diameter of the secondary envelope.
  • this generator has an efficiency, on the cold branch side, which is improved compared to conventional recirculation water generators, this efficiency is not yet very good.
  • the object of the invention is therefore to propose a new steam generator provided with a preheating device the structure of which is simple, leaves the maximum space available for the U-shaped tubes and does not cause thermal stress and whose performance is improved.
  • the invention applies to any conventional type steam generator, in accordance with the description which we have made above, and in which means are provided for separating the interior of the secondary envelope into two zones, one zone cold branch and a hot branch area.
  • the steam generator is also separated, outside the envelope, into two zones, a cold branch zone and a hot branch zone, these zones communicating respectively with the cold branch and hot branch zones located at the inside of the envelope;
  • the separation means are constituted by a skirt surrounding a part of the secondary envelope, on the side of the cold branch, and constituting with said envelope a closed space on the sides and at its lower part, while leaving a passage towards the zone cold branch from the inside of the envelope, and open at its upper part; so that the secondary water recirculated after passing through the separators, called recirculation water, can return to the bundle of U-shaped tubes both through the cold branch zone and through the hot branch zone, but as the water secondary food, arriving by an intake device located at the top of the generator circulates most of its flow in the cold branch area.
  • the generator according to the invention comprises means for distributing the recirculating water between the two zones, cold branch and hot branch, and for balancing, at the level of the tube plate, the pressures in these two zones.
  • a distribution flange placed in the space between the secondary casing and the skirt, perpendicular to the direction of the secondary water current of the cold branch zone; on the other hand, a distribution plate placed inside the secondary envelope in each of the zones, cold branch and hot branch, perpendicular to the direction of the U-shaped tubes, these two plates generally being of different permeability.
  • the skirt is located at a constant distance from the secondary casing, defining with it a space whose section by a plane parallel to the tubular plate is a ring sector whose the angle may vary with the section plane; the skirt extends vertically from the tube plate to the food water intake device; its sides are folded back towards the secondary envelope and welded to this envelope; its lower part is connected to the tubular plate by a semi-sealed connection limiting leakage school.perschen movements of the skirt relative to the plate so as to accommodate the relative deformations due to pressure and expansion.
  • the skirt is merged with the external enclosure, except for the edges which are constituted by two vertical partitions extending between the external enclosure and the secondary envelope.
  • the vertical partition separating the cold branch zone from the hot branch zone inside the secondary envelope extends from the tubular plate to a height at least equal to the height necessary for preheating the drinking water; it is welded on the sides inside the secondary envelope and connected to the tube plate by a semi-sealed partition.
  • the lower part of the skirt can be engaged in a rail secured to the outer enclosure and not to the tubular plate, in order to reduce the stresses in this plate.
  • the secondary food water is sent for all of its flow in the cold branch zone.
  • the steam generator shown in Figures 1, 2 and 3 comprises a cylindrical outer enclosure 1 of vertical axis, resistant to pressure, closed at each end by a cap.
  • the upper cap has not been shown but we can see the lower cap 2.
  • a horizontal tubular plate 3 is arranged inside the enclosure 1, integral with the latter and delimiting with the lower cap 2 a separate chamber in two manifolds 4 and 5, the manifold 4 being an intake manifold and the manifold 5 a discharge manifold of a primary heat-transfer fluid; this primary fluid can for example come from a nuclear power plant reactor.
  • U-shaped tubes, 6, grouped in a bundle, are mounted on the tube plate 3 and each have a hot leg 7 which communicates with the intake manifold 4 and a cold leg 8 which communicates with the exhaust manifold 5; the set of hot legs 7 constitutes the hot branch and the set of cold legs constitutes the cold branch.
  • a secondary envelope 9 surrounds the bundle of tubes 6 without resting on the tube plate 3 and defines an annular space 10 with the outer enclosure.
  • An inlet device 11 for supplying the annular space 10 with secondary water is provided in the upper part of the generator.
  • This water is intended to descend to the tubular plate 3 then to rise along the tubes 6 and to heat up and then vaporize on contact.
  • a set of separator-dryers 12 intended to separate the vapor obtained in the upper part of the tubes; this vapor is then discharged through an opening in the upper cap, not shown.
  • FIG. 2 shows the spacer plates 13 which hold the tube bundle 6. These plates 13 and the secondary envelope 9 are blocked in translation relative to the external enclosure 1 by blocks 14.
  • a skirt 16 surrounds part of the secondary envelope 9, on the side of the cold branch and constitutes with the envelope 9 a space 17 closed on the sides and at its lower part.
  • the space 17 constitutes the circuit for the return of the recirculation water to the cold branch or the return of the cold branch water, while the annular space 10 between the pressurized enclosure 1 and the secondary envelope 9, d 'on the one hand, and the space between the enclosure 1 and the skirt 16, which will be called 10', on the other hand, delimit the return of hot branch water.
  • the sides 18 and 18 ′ of the skirt 16 are folded over the secondary casing 9 and welded to the latter, thus preventing the passage of fluid from the cold branch water return to the hot branch water return.
  • the lower part of the skirt 16 is connected to the tube plate 3 by a semi-tight connection limiting leaks.
  • This link is made up here by the groove 19a of a semi-circular rail 19 welded to the tubular plate in which a flange 19b of the lower part of the skirt 16 is fitted.
  • the lower part of the sides 18 and 18 ′ is engaged in the ends 20a and 20b of a straight rail 20.
  • a vertical partition 21 separates the cold legs 8 from the hot legs 7.
  • This vertical partition 21 is engaged in the rectilinear rail 20.
  • the plate 21 is in fact placed in the extension of the plate partition 22 separating the collectors 4 and 5. It is welded to the secondary casing 9 and extends vertically to a height at least equal to the height necessary for preheating the drinking water. The partition 21 can thus prevent transverse flows in the bundle before all the food water is preheated.
  • a feed water inlet manifold is fixed in the tubing 11 and is provided with J-shaped tubes, 23, the openings of which open in the upper part of the cold branch water return 17.
  • a flange 24 provided with orifices is located at the lower part of the space 17 and is intended to create a pressure drop there. This flange 24 also allows a homogeneous supply of the cold branch.
  • Distribution plates 25a and 25b with different permeabilities are located inside the secondary envelope 9, one on the hot branch side and the other on the cold branch side, perpendicular to the direction of the tubes U. These plates have main function to ensure a good sweeping of the tube plate in order to avoid the creation of areas of low speed of water near the tube plate. They also contribute to the balance of pressures at the bottom of the bundle between cold branch and hot branch and make it possible to avoid water flows from one branch to the other.
  • the steam generator according to the invention operates in the following manner: the primary heat transfer fluid circulates upwards in the tubes on the hot branch side and descends on the cold branch side.
  • the secondary water in upward flow is partially vaporized in the bundle of tubes to a vapor titer of 20 to 40%; the emulsion thus produced is directed into a separation-drying assembly ensuring the separation of the water and the vapor and the drying of the latter.
  • the separated water called recirculation water, returns to the base of the bundle according to the arrowed circuits represented in FIG. 2, which include a common area A, a cold branch water return circuit B and a branch water return circuit hot C.
  • Part of the secondary recirculation water is mixed with the drinking water coming from the intake device 11, while the remaining part penetrates directly into the hot branch, and the whole is again vaporized. In operation, a single water level is established at the head of the circuit in the vicinity of the base of the separators 12.
  • the recirculation water is distributed uniformly in a space between the external enclosure and the secondary envelope, here, at full load, a large fraction of the recirculation water, greater than 50%, goes towards the hot branch of the bundle by the return of hot branch water, that is to say through spaces 10 and 10 ', while the remaining fraction of the recirculation water is mixed in the cold branch water return 17 to all of the food water coming from the tubing 11, before reaching the tube plate 3 and the preheating zone (that is to say the cold branch zone included in the inside the secondary envelope 9).
  • This fractionation of the recirculation water results from the pressure drop effect created on the one hand by the flange 24 and on the other hand by the difference in permeability of the distribution plates 25a and 25b located one in the branch hot and the other in the cold branch.
  • the solution of our invention causes a drop in the pressure delivered by the steam generator, due to the reduction of the primary-secondary temperature difference.
  • this reduction in the temperature difference is partially offset by an increase in the transfer coefficient in the secondary film due to an increase in the total flow rate passing through the cold branch zone of the bundle and a very satisfactory yield is obtained.
  • the flange 8 and the distribution plates 25a and 25b are adjusted so as to obtain an optimal distribution of the pressure losses, that is to say a distribution for which, at nominal point, therefore at full load, the fraction of recirculation water going towards the hot branch side is close to 100%.
  • the relative proportion of recirculating water / drinking water naturally increases in the return of cold branch water, which has the effect of compensating for the drop in temperature of drinking water.
  • the temperature of the mixture arriving on the tube plate remains substantially constant both at full load and at low load.
  • FIGS. 4, 5 and 6 represent a second embodiment of the skirt 16.
  • the skirt 16 is such that the section of this skirt by a plane parallel to the tubular plate is a ring sector, but this ring sector has an angle which varies with the section plane. From the upper part of the steam generator to an intermediate plane 26, the angle of the sector of the ring is less than 180 °, whereas, from the intermediate plane 26 to the level of the tube plate 3, the ring sector increases continuously by the value it has at the level of the intermediate plane 26 to 180 °.
  • the skirt 16 is located at a distance from the secondary envelope 9 which is equal to the distance between the external enclosure 1 and the secondary envelope 9; this amounts to saying that the skirt 16 is merged with the outer enclosure 1, except for the sides 18 and 18 '.
  • the skirt is formed only by these sides 18 and 18 ', that is to say by a simple set of two vertical partitions extending between the enclosure 1 and the casing 9 in extension of the vertical partition 21.
  • FIGS. 8, 9, 10 and 11 show examples of semi-sealed connections, between the lower parts of the skirt and of the vertical partition 21 and the tube plate 3.
  • Figure 8 shows the lower parts engaged in rails.
  • the vertical partition 21 is engaged in a rail 20.
  • the lower part of the skirt, 19b, is engaged in the groove 19a of a rail 19.
  • the rail 19 can be fixed either directly on the tubular plate or, preferably, on the outer enclosure, as shown in Figure 8c.
  • the semi-sealed connections are made by means of labyrinth seals secured either to the tubular plate (FIG. 9a) or directly to the outer enclosure 1 (FIG. 9b).
  • FIG. 10 shows a system for connecting the lower parts by means of joint covers.
  • the joint covers 27 are fixed by sectors to the lower parts of the vertical partition 21 or of the skirt 16 by means of bolts 28. The clearance between the joint covers and the tube plate is canceled during assembly.
  • the present invention has many advantages.
  • the present invention makes it possible to obtain a vapor pressure higher than that of a conventional steam generator and close to that of steam generators with integrated preheater, while being of a very simple structure.
  • the invention solves the problems of thermal shock at the level of the tube plate and at the level of the external enclosure. Indeed, the introduction of drinking water is carried out in the upper part of the generator, that is to say away from the tube plate, and this water is mixed on the cold branch side with a fraction of warmer recirculating water. ; this fraction of recirculating water increases at low load, that is to say when the temperature and the flow rate of drinking water decrease. The temperature of the secondary water arriving on the secondary plate is therefore practically constant. As for the pressure vessel 1, it is maintained at a uniform temperature since it is always in contact with the recirculating water contained in the annular spaces 10 and 10 ′, and not with drinking water.
  • Another important advantage of the invention lies in the fact of its very simple structure.
  • distribution plates 25a and 25b it can be added that these can be located in different planes.

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Claims (12)

1. Dampferzeuger mit einer äußeren zylindrischen Hülle (1) mit vertikaler Achse, die druckfest ausgebildet und an jedem Ende mit einer Kalotte verschlossen ist, mit einer horizontalen Rohr-Platte (3), die im Inneren der Hülle fest verbunden mit dieser angeordnet ist und mit der unteren Kalotte (2) zusammen eine in zwei Sammeleinrichtungen, nämlich eine für den Einlaß (4) und eine für den Auslaß (5), für ein primäres, als Wärmeträger dienendes Fluid unterteilte Kammer begrenzt, mit einem Bündel von U-förmigen Rohren (6), die auf der Rohr-Platte (3) montiert sind und von welchen jedes einen warmen Schenkel (7), der mit der Einlaß-Sammeleinrichtung kommuniziert, und einen kalten Schenkel (8) aufweist, der mit der Auslaß-Sammeleinrichtung kommuniziert, wobei alle warmen Schenkel zusammen die warme Teilzone und alle kalten Schenkel zusammen die kalte Teilzone bilden, mit einer sekundären Hülle (9), welche das Rohrbündel (6) umgibt, ohne auf der Rohr-Platte (3) abgestützt zu sein, und welche zusammen mit der äußeren Hülle (1) einen ringförmigen Raum (10) bildet, mit einer Trennungseinrichtung (21), welche das Innere der sekundären Hülle (9) in zwei Zonen, eine kalte Teilzone und eine warme Teilzone, teilt, mit einer Einlaßvorrichtung (11) für die Speisung des ringförmigen Raums (10) mit sekundärem Wasser, das dazu bestimmt ist, in den Rohren (6) des Rohrbündels hochzusteigen, und bei Berührung mit den Rohren zu verdampfen, und im oberen Teil der Hülle mit einer Anordnung von Trennungseinrichtungen (12) und einer Öffnung, die in der oberen Kalotte für das Austreten des erzeugten Dampfes ausgespart ist, dadurch gekennzeichnet, daß der Dampferzeuger auch außerhalb der sekundären Hülle (9) in zwei Zonen, eine kalte Teilzone (17) und eine warme Teilzone (10 + 10') geteilt ist, welche Zonen jeweils mit den kalten und warmen Teilzonen im Inneren der Hülle (9) kommunizieren, wobei die Trennungseinrichtungen aus einem Schurz (16) bestehen, der einen Teil der sekundären Hülle (9) auf der Seite der kalten Teilzone umgibt und mit der Hülle (9) zusammen einen Raum (17) bildet, der an den Seiten und in seinem unteren Abschnitt geschlossen ist, jedoch einen Durchlaß zur kalten Teilzone im Inneren der Hülle (9) freiläßt und in seinem oberen Abschnitt offen ist, so daß das sekundäre Wasser, das nach dem Durchlaufen der Trennungseinrichtung wieder der Zirkulation zugeführt wird und als Umwälzwasser bezeichnet wird, zu dem Bündel (6) von U-förmigen Rohren sowohl durch die kalte Teilzone (17) als auch durch die warme Teilzone (10 oder 10') zurückkehren kann, jedoch der wesentliche Anteil des sekundären Speisungswassers, das von der im oberen Teil des Dampferzeugers gelegenen Einlaß-einrichtung (11) kommt, in der kalten Teilzone (17) zirkuliert.
2. Dampferzeuger nach Anspruch 1, dadurch gekennzeichnet, daß er Einrichtungen (25a, 25b) für die Verteilung des Umwälzwassers zwischen den beiden Zonen, der kalten und der warmen Teilzone, und für den Ausgleich der Drücke zwischen den beiden Zonen auf der Höhe der Rohr-Platte (3) aufweist.
3. Dampferzeuger nach Anspruch 2, dadurch gekennzeichnet, daß ein Teilungsbund (24) in dem Raum (17), der zwischen der sekundären Hülle (9) und dem Schurz (16) eingeschlossen ist, senkrecht in bezug auf die Strömungsrichtung des sekundären Wassers in der kalten Teilzone vorgesehen ist.
4. Dampferzeuger nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß im Inneren der sekundären Hülle (9) sowohl in der kalten als auch in der warmen Teilzone eine Verteilerplatte (25b, 25a) senkrecht in bezug auf die Richtung der U-förmigen Rohre angeordnet ist und daß die beiden Platten von unterschiedlicher Durchlässigkeit sind.
5. Dampferzeuger nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Schurz (16) in einem konstanten Abstand von der sekundären Hülle (9) angeordnet ist und mit dieser zusammen einen Raum (17) begrenzt, dessen Querschnitt in einer parallel zur Rohr-Platte verlaufenden Ebene ein Ringsektor ist, dessen Winkel je nach der Schnittebene variieren kann, daß sich der Schurz (16) vertikal von der Rohr-Platte (3) bis zur Einlaßeinrichtung (11) für das Speisungswasser erstreckt, daß seine Seiten (18, 18') gegen die sekundäre Hülle (9) umgebogen bzw. umgelegt und mit dieser Hülle verschweißt sind und daß sein unterer Abschnitt mit der Rohr-Platte (3) durch eine halbdichte Verbindung (19) verbunden ist.
6. Dampferzeuger nach Anspruch 5, dadurch gekennzeichnet, daß der Schurz mit Ausnahme jener Seiten, die aus zwei vertikalen Trenn- bzw. Zwischenwänden (18, 18') bestehen, welche sich zwischen der äußeren Hülle (1) und der sekundären Hülle (9) erstrecken, mit der äußeren Hülle (1) zusammenfällt.
7. Dampferzeuger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß sich die vertikale Trenn- bzw. Zwischenwand (21), welche die warme und die kalte Teilzone im Inneren der sekundären Hülle (9) trennt, von der Rohr-Platte (3) aus bis zu einer Höhe erstreckt, die wenigstens gleich der Höhe ist, welche für das Vorwärmen des Speisungswassers erforderlich ist, und daß die Wand an den Seiten an das Innere der sekundären Hülle (9) angeschweißt und mit der Rohr-Platte (3) durch eine halbdichte Verbindung (20) verbunden ist.
8. Dampferzeuger nach einem der Ansprüche 5, 6 oder 7, dadurch gekennzeichnet, daß die unteren Abschnitte des Schurzes (16) und der vertikalen Trenn- bzw. Zwischenwand (21) mit Schienen (19, 20) in Eingriff stehen, die fest mit der Rohr-Platte verbunden sind.
9. Dampferzeuger nach Anspruch 8, dadurch gekennzeichnet, daß die vertikale Trenn- bzw. Zwischenwand (21) und die Seiten (18, 18'), die zum Schurz (16) hin umgebogen sind, mit einer gleichen, geradlinigen Schiene in Eingriff stehen.
10. Damferzeuger nach einem der Ansprüche 5, 6 oder 7, dadurch gekennzeichnet, daß der untere Abschnitt des Schurzes (16) mit einer fest mit der äußeren Hülle verbundenen Schiene (19) in Eingriff steht.
11. Dampferzeuger nach einem der Ansprüche 5, 6 oder 7, dadurch gekennzeichnet, daß die unteren Abschnitte des Schurzes (16) und der vertikalen Trenn- bzw. Zwischenwand (21) mit der Rohr-Platte (3) mittels T-Stoß-Verbindungen mit Federn verbunden sind.
12. Dampferzeuger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die gesamte Menge an sekundärem Speisungswasser in die kalte Teilzone eingebracht wird.
EP81400308A 1980-02-29 1981-02-27 Dampferzeuger mit Vorwärmung Expired EP0035450B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81400308T ATE4932T1 (de) 1980-02-29 1981-02-27 Dampferzeuger mit vorwaermung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8004533 1980-02-29
FR8004533A FR2477265A1 (fr) 1980-02-29 1980-02-29 Generateur de vapeur a prechauffage

Publications (2)

Publication Number Publication Date
EP0035450A1 EP0035450A1 (de) 1981-09-09
EP0035450B1 true EP0035450B1 (de) 1983-10-05

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US (1) US4357908A (de)
EP (1) EP0035450B1 (de)
JP (1) JPS56137002A (de)
AT (1) ATE4932T1 (de)
BR (1) BR8101111A (de)
CA (1) CA1149248A (de)
DE (1) DE3161076D1 (de)
ES (1) ES8207341A1 (de)
FR (1) FR2477265A1 (de)
SU (1) SU1225496A3 (de)
YU (1) YU41763B (de)
ZA (1) ZA811219B (de)

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US4736713A (en) * 1984-11-15 1988-04-12 Westinghouse Electric Corp. Foraminous or perforated flow distribution plate
EP0183049B1 (de) * 1984-11-15 1989-10-18 Westinghouse Electric Corporation Strömungsverteilerlochplatte
DE3529634A1 (de) * 1985-08-19 1987-02-26 Steinmueller Gmbh L & C Waermetauscher fuer den waermetausch zwischen einem heissen gas und einem in rohrbuendelheizflaechen gefuehrten stroemungsmittel, insbesondere dampferzeuger fuer gasgekuehlte hochtemperaturreaktoren
US4704994A (en) * 1986-04-16 1987-11-10 Westinghouse Electric Corp. Flow boosting and sludge managing system for steam generator tube sheet
US4777911A (en) * 1986-06-17 1988-10-18 Westinghouse Electric Corp. Stayrod configuration for facilitating steam generator sludge lancing
FR2644926B1 (fr) * 1989-03-22 1991-06-07 Framatome Sa Generateur de vapeur a prechauffage
FR2657948B1 (fr) * 1990-02-08 1992-05-29 Framatome Sa Generateur de vapeur a distributeur, en particulier pour centrale nucleaire.
JP2952102B2 (ja) * 1991-04-05 1999-09-20 ウエスチングハウス・エレクトリック・コーポレイション 熱交換器
US5213065A (en) * 1991-08-23 1993-05-25 Westinghouse Electric Corp. Steam generator feedwater distribution system
FR2685444B1 (fr) * 1991-12-19 1994-02-04 Framatome Generateur de vapeur a prechauffage.
FR2690504B1 (fr) * 1992-04-28 1994-06-03 Framatome Sa Generateur de vapeur a dispositif de distribution et de reparation de l'eau alimentaire et de l'eau de recirculation dans la partie secondaire.
FR2700383B1 (fr) * 1993-01-11 1995-02-10 Framatome Sa Echangeur de chaleur dans lequel l'alimentation en fluide secondaire s'effectue en partie haute par un boîtier d'alimentation ouvert vers le bas.
US5307802A (en) * 1993-09-13 1994-05-03 Placek Edward A High efficiency steam generator
DE59708896D1 (de) * 1997-10-09 2003-01-16 Alstom Switzerland Ltd Niederdruck-Speisewasservorwärmer
FR2778224B1 (fr) * 1998-05-04 2000-07-28 Framatome Sa Generateur de vapeur comportant un dispositif d'alimentation en eau perfectionne
JP2002031694A (ja) * 2000-07-14 2002-01-31 Toshiba Corp 超臨界圧水炉とその発電プラント
JP5055165B2 (ja) * 2008-02-29 2012-10-24 三菱重工業株式会社 蒸気発生器
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US9057516B2 (en) * 2011-11-28 2015-06-16 Trimeteor Oil and Gas Corporation Superheated steam generators
JP2013160695A (ja) * 2012-02-07 2013-08-19 Mitsubishi Heavy Ind Ltd 蒸気発生器用給水管
CN107289436A (zh) * 2016-03-31 2017-10-24 华北电力大学 一种具有提高蒸汽发生器换热效率的支撑导流结构

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Also Published As

Publication number Publication date
ES499732A0 (es) 1982-09-01
FR2477265A1 (fr) 1981-09-04
ATE4932T1 (de) 1983-10-15
ZA811219B (en) 1982-06-30
SU1225496A3 (ru) 1986-04-15
EP0035450A1 (de) 1981-09-09
JPS56137002A (en) 1981-10-26
FR2477265B1 (de) 1982-02-26
JPH0217762B2 (de) 1990-04-23
YU41763B (en) 1987-12-31
DE3161076D1 (en) 1983-11-10
CA1149248A (fr) 1983-07-05
ES8207341A1 (es) 1982-09-01
BR8101111A (pt) 1981-09-01
US4357908A (en) 1982-11-09
YU37681A (en) 1984-02-29

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