EP0035450A1 - Dampferzeuger mit Vorwärmung - Google Patents

Dampferzeuger mit Vorwärmung Download PDF

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Publication number
EP0035450A1
EP0035450A1 EP81400308A EP81400308A EP0035450A1 EP 0035450 A1 EP0035450 A1 EP 0035450A1 EP 81400308 A EP81400308 A EP 81400308A EP 81400308 A EP81400308 A EP 81400308A EP 0035450 A1 EP0035450 A1 EP 0035450A1
Authority
EP
European Patent Office
Prior art keywords
branch
steam generator
cold
water
envelope
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.)
Granted
Application number
EP81400308A
Other languages
English (en)
French (fr)
Other versions
EP0035450B1 (de
Inventor
Jean-Claude Yazidjian
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.)
Areva NP SAS
Original Assignee
Framatome SA
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 Framatome SA filed Critical Framatome SA
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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Classifications

    • 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 has 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 of the floor can create contrain - your bending in the tube (pressure deformation of the tube plate, differential expansion of the tube plate of the preheater and the floor), and further makes difficult the casing operation because its lower permeability than that of the spacer plates of the tube bundle and its proximity to the tube plate.
  • this floor cannot be perfectly sealed, so that part of the drinking water passes through it and goes towards the hot branch: this reduces the overall performance of the steam generator.
  • the steam generator of the type described in the French application No. 2285573 has the disadvantage of comprising a smaller space for the tubes for a given diameter of the in- 'develops under pressure, part of the space being occupied by the preheater.
  • the object of the invention is therefore to propose a new steam generator provided with a preheating device but which does not have the drawbacks of the prior art.
  • the invention applies to any conventional type steam generator, as described above.
  • the steam generator is separated into two zones, a cold branch zone and a hot branch zone, the separation being carried out on the one hand, inside the secondary envelope, by a vertical partition separating the cold legs hot legs, on the other hand. outside the secondary envelope, 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 removed and at its lower part, while leaving a passage towards the cold branch zone of the interior 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 envelope, defining with it a space whose section by a plane parallel to the tabular plate is a sector of a ring whose the angle may vary with the section plane; the skirt extends vertically from the tube plate to the feed 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-tight connection limiting leaks but allowing 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 water. food; it is welded on the sides inside the secondary casing 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 at two collectors 4 and 5, the manifold 4 being an intake manifold and the manifold 5 a discharge manifold for 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 external 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 a part of the secondary envelope 9, of 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 connection is here constituted by the goige 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 wedge 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 partition plate 22 separating the collectors 4 and 5. It is welded to the secondary envelope 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 the flow of water from one branch to the other.
  • 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 water and steam and the drying thereof.
  • 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 return circuit from the cold branch B and a return circuit from the branch hot C.
  • Part of the secondary recirculation water is mixed with the drinking water coming from the device / diadmissior 11 while 1 remaining part penetrates directly into the hot branch, and the whole is vaporized again.
  • 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 in the primary-secondary temperature gap.
  • 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 tube 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 ring sector is less than 180 °, while, from the intermediate plane 26 to the level of the tube plate 3, the sector d 'ring increases continuously from the value it has at the intermediate plane 26 up 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 external 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 on the lower parts of the vertical partition 21 or of the skirt 16 by means of bolts 28. The clearance between the covers is canceled during assembly. joints and the tube plate.
  • 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 with a fraction of hotter 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 pressurized enclosure 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.
  • the sealing requirements in the zone of the tube plate are limited due to the adjustment of the pressures hot branch-cold branch provided by the distribution plates.
  • the transverse flows inside the envelope are condaire at the top of the preheating zone are also minimized.
  • Another important advantage of the invention resides in the fact of its very smooth structure.
  • distribution plates 25a and 25b it can be added that these can be located in different planes.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Devices For Medical Bathing And Washing (AREA)
  • Control Of Turbines (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Detergent Compositions (AREA)
  • Permanent Magnet Type Synchronous Machine (AREA)
  • Cleaning And De-Greasing Of Metallic Materials By Chemical Methods (AREA)
  • Sorption Type Refrigeration Machines (AREA)
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 true EP0035450A1 (de) 1981-09-09
EP0035450B1 EP0035450B1 (de) 1983-10-05

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ID=9239150

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81400308A Expired EP0035450B1 (de) 1980-02-29 1981-02-27 Dampferzeuger mit Vorwärmung

Country Status (12)

Country Link
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) ES499732A0 (de)
FR (1) FR2477265A1 (de)
SU (1) SU1225496A3 (de)
YU (1) YU41763B (de)
ZA (1) ZA811219B (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2566511A1 (fr) * 1984-06-22 1985-12-27 Westinghouse Electric Corp Generateur de vapeur hybride a prechauffage et recirculation
EP0183049A1 (de) * 1984-11-15 1986-06-04 Westinghouse Electric Corporation Strömungsverteilerlochplatte
US4694897A (en) * 1985-08-19 1987-09-22 L. & C. Steinmuller Gmbh Heat exchanger for heat exchange between hot gas and medium flowing through tube bundles
US4736713A (en) * 1984-11-15 1988-04-12 Westinghouse Electric Corp. Foraminous or perforated flow distribution plate
EP0389361A1 (de) * 1989-03-22 1990-09-26 Framatome Dampferzeuger mit Vorwärmung
FR2657948A1 (fr) * 1990-02-08 1991-08-09 Framatome Sa Generateur de vapeur a distributeur, en particulier pour centrale nucleaire.
EP2246616A1 (de) * 2008-02-29 2010-11-03 Mitsubishi Heavy Industries, Ltd. Dampferzeuger
FR2945104A1 (fr) * 2009-04-29 2010-11-05 Babcock & Wilcox Canada Ltd Piege a debris d'eau d'alimentation
EP2508799A1 (de) * 2011-04-04 2012-10-10 Mitsubishi Heavy Industries Dampferzeuger
EP2814039A4 (de) * 2012-02-07 2015-11-04 Mitsubishi Heavy Ind Ltd Wasserversorgungsleitung für dampferzeuger

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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
EP0908669B1 (de) * 1997-10-09 2002-12-04 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
US9683732B2 (en) * 2011-10-13 2017-06-20 Westinghouse Electric Company Anti-clogging steam generator tube bundle
US9057516B2 (en) * 2011-11-28 2015-06-16 Trimeteor Oil and Gas Corporation Superheated steam generators
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

Citations (1)

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FR2285573A1 (fr) * 1974-09-18 1976-04-16 Westinghouse Electric Corp Evaporateur

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AT249087B (de) * 1963-10-31 1966-09-26 Waagner Biro Ag Einrichtung zur Erzeugung von im wesentlichen trockenem Dampf
US3651789A (en) * 1968-06-13 1972-03-28 Westinghouse Electric Corp Steam generator
DE2231181A1 (de) * 1972-06-26 1974-01-10 Siemens Ag Dampferzeuger
US3921591A (en) * 1972-06-26 1975-11-25 Siemens Ag Pressurized-water coolant nuclear reactor steam generator
US3885621A (en) * 1974-03-29 1975-05-27 Westinghouse Electric Corp Vent condenser for a feedwater heater
US3906905A (en) * 1974-08-20 1975-09-23 Commissariat Energie Atomique Steam generator
DE2612081A1 (de) * 1976-03-22 1977-10-20 Kraftwerk Union Ag Dampferzeuger fuer druckwasser- kernreaktoren
US4098329A (en) * 1976-07-29 1978-07-04 The United States Of America As Represented By The United States Department Of Energy Modular heat exchanger
FR2387417A1 (fr) * 1977-04-12 1978-11-10 Commissariat Energie Atomique Generateur de vapeur a eau pressurisee
US4131085A (en) * 1977-05-04 1978-12-26 The Babcock & Wilcox Company Vapor generating unit blowdown arrangement
FR2394750A1 (fr) * 1977-06-15 1979-01-12 Commissariat Energie Atomique Generateur de vapeur
DE2735450A1 (de) * 1977-08-05 1979-02-15 Kraftwerk Union Ag Dampferzeuger fuer kernkraftwerke, insbesondere fuer druckwasserreaktoren
US4261300A (en) * 1978-12-26 1981-04-14 Combustion Engineering, Inc. Nuclear steam generator
CA1130786A (en) * 1979-03-19 1982-08-31 Anthony Ruhe Double plate flow distributor

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2285573A1 (fr) * 1974-09-18 1976-04-16 Westinghouse Electric Corp Evaporateur

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2566511A1 (fr) * 1984-06-22 1985-12-27 Westinghouse Electric Corp Generateur de vapeur hybride a prechauffage et recirculation
EP0183049A1 (de) * 1984-11-15 1986-06-04 Westinghouse Electric Corporation Strömungsverteilerlochplatte
US4736713A (en) * 1984-11-15 1988-04-12 Westinghouse Electric Corp. Foraminous or perforated flow distribution plate
US4694897A (en) * 1985-08-19 1987-09-22 L. & C. Steinmuller Gmbh Heat exchanger for heat exchange between hot gas and medium flowing through tube bundles
EP0389361A1 (de) * 1989-03-22 1990-09-26 Framatome Dampferzeuger mit Vorwärmung
EP0441697A1 (de) * 1990-02-08 1991-08-14 Framatome Dampferzeuger mit Verteiler, insbesondere für Atomkraftwerk
FR2657948A1 (fr) * 1990-02-08 1991-08-09 Framatome Sa Generateur de vapeur a distributeur, en particulier pour centrale nucleaire.
EP2246616A1 (de) * 2008-02-29 2010-11-03 Mitsubishi Heavy Industries, Ltd. Dampferzeuger
EP2246616A4 (de) * 2008-02-29 2015-04-08 Mitsubishi Heavy Ind Ltd Dampferzeuger
FR2945104A1 (fr) * 2009-04-29 2010-11-05 Babcock & Wilcox Canada Ltd Piege a debris d'eau d'alimentation
EP2508799A1 (de) * 2011-04-04 2012-10-10 Mitsubishi Heavy Industries Dampferzeuger
US9182113B2 (en) 2011-04-04 2015-11-10 Mitsubishi Heavy Industries, Ltd. Steam generator
EP2814039A4 (de) * 2012-02-07 2015-11-04 Mitsubishi Heavy Ind Ltd Wasserversorgungsleitung für dampferzeuger

Also Published As

Publication number Publication date
CA1149248A (fr) 1983-07-05
BR8101111A (pt) 1981-09-01
JPS56137002A (en) 1981-10-26
DE3161076D1 (en) 1983-11-10
FR2477265B1 (de) 1982-02-26
EP0035450B1 (de) 1983-10-05
YU37681A (en) 1984-02-29
JPH0217762B2 (de) 1990-04-23
FR2477265A1 (fr) 1981-09-04
US4357908A (en) 1982-11-09
ES8207341A1 (es) 1982-09-01
YU41763B (en) 1987-12-31
ATE4932T1 (de) 1983-10-15
ZA811219B (en) 1982-06-30
SU1225496A3 (ru) 1986-04-15
ES499732A0 (es) 1982-09-01

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