EP0128252A1 - Kernkraftanlage und Apparat zum Überhitzen von Dampf - Google Patents

Kernkraftanlage und Apparat zum Überhitzen von Dampf Download PDF

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Publication number
EP0128252A1
EP0128252A1 EP83303403A EP83303403A EP0128252A1 EP 0128252 A1 EP0128252 A1 EP 0128252A1 EP 83303403 A EP83303403 A EP 83303403A EP 83303403 A EP83303403 A EP 83303403A EP 0128252 A1 EP0128252 A1 EP 0128252A1
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EP
European Patent Office
Prior art keywords
tubes
steam
vapor
header
banks
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
EP83303403A
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English (en)
French (fr)
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EP0128252B1 (de
Inventor
Donald C. Schluderberg
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.)
Babcock and Wilcox Co
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Babcock and Wilcox Co
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Filing date
Publication date
Application filed by Babcock and Wilcox Co filed Critical Babcock and Wilcox Co
Priority to DE8383303403T priority Critical patent/DE3372035D1/de
Priority to EP19830303403 priority patent/EP0128252B1/de
Publication of EP0128252A1 publication Critical patent/EP0128252A1/de
Application granted granted Critical
Publication of EP0128252B1 publication Critical patent/EP0128252B1/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
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/26—Steam-separating arrangements
    • F22B37/266—Separator reheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/18—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters
    • F01K3/181—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters using nuclear heat
    • F01K3/183—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters using nuclear heat one heater being a fired superheater
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0058—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having different orientations to each other or crossing the conduit for the other heat exchange medium

Definitions

  • This invention relates to nuclear power plant and to apparatus for superheating steam.
  • a moisture separator-reheater is commonly provided between a high pressure and a low pressure turbine to increase the plant efficiency and also protect the turbine blades of the low pressure turbine by reducing moisture in the steam which is to be expanded in the low pressure turbine.
  • the reheater for a fossil power plant may be located within the steam generator and heat supplied by combustion of fuel in the steam generator is thus utilized to reheat the steam to a desired degree of superheat. Throttle steam or steam extracted from the high pressure turbine may also be used to reheat the main steam after it has been exhausted from the high pressure turbine. Likewise in a nuclear power plant, heat supplied by the reactor core may be used to reheat the steam before it is provided to a lower pressure turbine.
  • Moisture separator-reheaters for steam power generation typically employ large cylindrical shells containing moisture separators and heat transfer tubes extending therethrough.
  • the separators are typically of an inertia! -type and separate water from wet steam exhausted from the high pressure turbine. This steam is then directed to the heat exchange portion of the unit.
  • the heat transfer tubes of the heat exchange portion may employ throttle steam and/or extraction steam to reheat the main steam flow. The water separated from the main steam is then drained at the bottom of the unit while the dried and reheated main steam is directed to the low pressure turbine.
  • a common problem with horizontally disposed moisture separator-reheaters is unequal heat transfer and flow oscillations.
  • the lowermost tubes of a tube bundle are subjected to a high temperature differential while tubes high in a tube bundle receive shell side flow which has already been partially heated by the lower tubes.
  • the lower tubes may tend to accumulate water until they no longer carry steam along their entire length. Subcooling of the water in the lower tubes may then occur while steam may pass through the entire length of tubes higher up in the bundle. Such occurrences may create an unstable condition which results in reduced overall heat transfer and potentially damaging cyclical thermal stresses on the tubes and tube sheets.
  • Another proposal directed to this problem provides in a water separator-superheater structure a plurality of horizontally disposed netting mattresses arranged in superposed stepped relation through which the main steam passes to be dried after which it passes through a single bank of heat exchange tubes which are disposed at an inclined angle in order to promote self-draining.
  • An inlet header is provided at the upper end of the tubes and an outlet header is provided at the lower end of these tubes.
  • Such an arrangement does not utilize the available space to provide heat transfer surface as effectively as may be desired. It is therefore desirable to more effectively utilize the available space within the shell of a moisture separator-reheater to provide a greater heat transfer area therein while also providing adequate means for separating moisture from the steam.
  • a nuclear power plant including a steam turbine and a nuclear steam generator for discharging steam for driving the turbine, the plant being characterised by
  • the invention also provides a nuclear power plant including a steam turbine and a steam generator for discharging steam for driving the turbine, the plant being characterised by
  • the invention provides apparatus for superheating steam, the apparatus being characterised by
  • the invention provides apparatus for superheating steam, the apparatus being characterised by a shell, inlet means in the shell for receiving steam, outlet means in the shell for discharging the steam, and a bundle of inclined tubes positioned in the flow path of the steam to provide a flow of vapor for transferring heat to the steam, each of the tubes having a closed upper end and a lower end which opens into a header, and the header being connected to a source of vapor and a condensate drain.
  • Embodiments of the present invention described hereinbelow can: provide increased output for a nuclear power plant which has excess turbine-generator capacity; provide a peak load or power upgrade device for nuclear power plants; increase the thermal efficiency of a nuclear power plant; provide a moisture separator-superheater which more efficiently utilizes the heat provided in the reheating steam for more efficient operation thereof; reduce the possibility of radiation contamination of such a superheater and of a separately fired vapor generator supplying vapor thereto; provide such a superheater which more effectively utilizes the available space within the superheater for providing heat transfer surface; simplify and reduce the expense of fabrication of such a moisture separator-superheater; and reduce the power loss which would otherwise result from a large pressure drop of the main steam as it passes through a moisture separator-superheater.
  • FIG. 1 there is illustrated a portion of a nuclear power plant 10 wherein steam is supplied from a conventional nuclear steam generator 11 to a high pressure turbine illustrated at 12 (hereinafter referred to as "HP turbine"). After expansion of this main steam through the HP turbine 12 to perform work, it is exhausted to an apparatus for superheating steam such as the moisture separator-reheater illustrated at 14 for removal of moisture therefrom and for reheating the main steam prior to its discharge to a lower pressure steam turbine illustrated at 16 (hereinafter referred to as "LP turbine").
  • HP turbine high pressure turbine illustrated at 12
  • LP turbine lower pressure steam turbine
  • the main steam is exhausted to a condenser 17 for condensing thereof, and the condensate is then returned via feed pump 19 and other conventional apparatus such as feed water heaters (not shown) to the nuclear steam generator 11 whereby the steam cycle is repeated with the addition of heat to produce the main steam and the return of the main steam to the HP turbine 12.
  • the HP and LP turbines 12 and 16 respectively provide power output such as through means of an electrical generator illustrated at 18.
  • the power plant may have more than two such turbines and an apparatus for superheating steam may be provided in the flow path of steam between any two successive turbines in accordance with this invention.
  • the power plant may also be provided with an intermediate pressure steam turbine.
  • the output of a nuclear plant may be increased where excess turbine-generator capacity exists if reactor supplied heat which is normally used to reheat the main steam is instead utilized for increasing the number of degrees of superheat of the main steam to perform additional work in the HP turbine and heat from another source is provided to reheat the main steam before its delivery to the LP turbine. Since the expense of a nuclear reactor is such that it is desirable to make maximum use of it, in order to provide such increased output in accordance with one aspect of this invention, the moisture separator-reheater 14 is supplied with vapor such as steam from a separately fired vapor generator such as the steam generator illustrated at 20 for transferring heat to the main steam as it passes through the heat exchange apparatus 14.
  • vapor such as steam from a separately fired vapor generator such as the steam generator illustrated at 20 for transferring heat to the main steam as it passes through the heat exchange apparatus 14.
  • This steam generator 20 is separately fired in order not to utilize any of the heat supplied by the nuclear reactor whereby the steam generator 20 may function as a peak load or power upgrade device with maximum use being made of the reactor supplied heat to increase the power output of the plant when excess turbine-generator capacity exists.
  • additional heat may be added to the main steam by a separately fired steam generator 20 before its passage through the LP turbine 16 for even greater power output than could otherwise be provided by the nuclear reactor by itself.
  • the steam generator 20 for providing reheat vapor to the reheater 14 is fossil fuel-fired.
  • a "fossil fuel-fired vapor generator” is defined as a non-nuclear vapor generator and is meant to include any of the various non-nuclear vapor generators which burn various fossil fuels such as, for example, oil, gas, coal, and coal-water mixtures, and is also meant to include vapor generators supplied with heat from such non-nuclear energy sources as solar and geothermal.
  • the vapor After the vapor has given up heat to the main steam in the moisture separator-reheater 14 and has condensed as it passes through the tubes thereof, it is returned to the fossil fuel-fired steam generator 20 such as by means of the feed pump illustrated at 22 so that additional heat may be added to it for its return to the moisture separator-reheater 14, and the cycle is repeated.
  • the steam supplied by many fossil fuel-fired vapor generators 20 can be provided at a higher pressure than the pressure of steam which may otherwise be provided by a conventional nuclear steam generator for reheating the main steam to thereby provide a higher reheat temperature.
  • a fossil fuel-fired vapor generator providing saturated steam at 650°F (343 0 C) should be able to reheat main steam from a high pressure turbine from around 380°F (193°C ) to more than 600 o F (3160C )
  • many conventional nuclear steam generators are not designed to provide reheat saturated steam having a temperature above about 310°F (266°C).
  • Apparatus 30 is a preferred embodiment of the heat exchange apparatus which is illustrated at 14 in Figure 1.
  • Apparatus 30 is provided with an elongate, horizontally disposed, generally cylindrical shell 32 supported by members 33.
  • a main steam inlet 34 opens into the shell 32 to supply steam to be superheated, such as steam exhausted from HP turbine 12 in Fig. 1 which is to be reheated before its delivery to LP turbine 16.
  • a diffuser separator 36 is provided at the main steam inlet 34 to use the velocity head of the incoming steam to remove a major portion of the entrained moisture which is then drained from the apparatus 30 through line 37.
  • a moisture content of 10 to 12 per cent may be reduced to a level in the neighborhood of 1 to 2 per cent utilizing the energy that would otherwise be lost at the inlet 34 to the apparatus 30.
  • the diffuser separator 36 may actually recover a portion of the velocity head normally lost to yield a pressure rise of perhaps 0.5 1bf/in 2 (3.45 kPa) to thereby reduce the power loss which would otherwise result as the main steam passes through the apparatus 30.
  • Apparatus 30 is provided with at least one bundle of tubes such as high pressure bundle 40 of tubes which may be supplied with heating vapor from such sources as turbine throttle steam or from a fossil fuel-fired steam generator.
  • a low pressure bundle 42 of tubes is also preferably provided which may use extraction steam so that the amount of throttle steam required for the high pressure bundle may be reduced for improvement in power output, or it also may use steam from a fossil fuel-fired steam generator.
  • the low pressure tube bundle of a conventional reheater which has flow control devices is supplied with extraction steam, its drains may, due to pressure drop of the reheat steam in its passage through the reheater tubes, have to be routed to a lower pressure feed water heater than the feed water heater to which the drains could have otherwise been directly routed.
  • each of the tube bundles 40 and 42 is provided with an outlet header 44 from which extends drain line 65.
  • Each drain line 6fi is routed as illustrated in Fig. 2 to provide some flexibility of movement to allow for expansions and contractions of the respective tube bundles.
  • Each outlet header 44 extends generally longitudinally of heat exchange apparatus 30 and is located preferably about midway between the sides thereof and generally below mid-height of the shell.
  • the tubes illustrated schematically at 46 of the tube bundles 40 and 42 open into and extend in an upward direction from the respective outlet header 44 and are inclined.
  • these tubes 46 are disposed to lie substantially parallel to a plane which is perpendicular to the longitudinal axis of the shell.
  • Fig. 3 is a view taken is such a plane.
  • each tube bundle 40 and 42 is comprised of two banks 48 and 50 of tubes extending from the respective outlet header 44 in generally the configuration of a "V" as viewed in a cross-section of the apparatus 30 taken in a plane perpendicular to the longitudinal axis thereof as shown in Figure 3.
  • a first bank 48 of tubes extends from the respective outlet header 44 in a direction upwardly and outwardly toward one side 52 of the shell 32 on one side of the vertical longitudinal centerplane 60 of the shell, and a second bank 50 of tubes extends upwardly and outwardly from the respective outlet header 44 to the other side 54 of the shell.
  • the angle illustrated at 56 at which each of the tubes 46 of the first bank 48 extends relative to the vertical longitudinal centerplane 60 of the apparatus 30 is opposed to the angle illustrated at 58 at which each of the tubes of the second bank extends relative to the centerplane 60.
  • each of these tubes 46 extends is not critical to this invention. However, an angle in the range of around 30 to 60 degrees is believed to effectively utilize the space available within the shell and provide adequate inclination of the tubes.
  • the tubes 46 of the first bank 48 terminate at and open into a first inlet header 62 which is preferably adjacent the shell 32 on one side of the centerplane 60 thereof, and the tubes 46 of the second bank 50 terminate at and open into a second inlet header 64 which is preferably adjacent the shell 32 on the other side of the centerplane 60.
  • each of the headers 62 and 64 extends in a direction substantially parallel to the longitudinal axis of the shell 32.
  • the outlet header 44 of the high pressure bundle 40 of tubes is disposed above the outlet header 44 of the low pressure bundle 42 of tubes, and each of the inlet headers 62 and 64 thereof is disposed above respective inlet headers 62 and 64 of the low pressure bundle 42 of tubes.
  • the inlet headers 62 and 64 are connected through lines 66 to a source or sources of vapor such as steam from a fossil fuel-fired steam generator, turbine extraction steam, or throttle steam to provide heating steam to the inclined tubes 46 of the tube bundles.
  • a source or sources of vapor such as steam from a fossil fuel-fired steam generator, turbine extraction steam, or throttle steam to provide heating steam to the inclined tubes 46 of the tube bundles.
  • These tubes 46 are short (they generally do not extend in a longitudinal direction of the shell 32) and inclined, to quickly drain condensate over a short distance by gravity to thus provide a means for condensing the steam in the tubes without sub-cooling it and to thereby provide more efficient heat transfer and greater power output.
  • a short tube is meant a tube the length of which is less than the shell diameter of the heat exchanger in which the tube is located.
  • the shell diameter is measured in a plane perpendicular to the longitudinal axis of the heat exchanger. However, it is recognized that a negligible amount of sub-cooling may occur. Condensate collecting in each of the outlet headers 44 may then be removed by draining it to respective vented drain tanks or by other suitable means through drain lines 65 after which it may be returned to the main steam cycle or to the fossil fuel-fired steam generator for reheating as previously described.
  • each of the tube bundles 40 and 42 is supported at each respective upper inlet header 62 and 64 by a member 67 attached thereto which is supported by a member 68 attached to the shell 32.
  • a portion of each member 67 is slideably supported by a portion of the respective member 68 to allow for expansions and contractions of the inlet headers 62 and 64.
  • Each of the lower outlet headers 44 is suspended from the respective upper headers 62 and 64 by the respective tube banks 48 and 50 to allow for expansions and contractions of the tubes 46 and outlet headers 44.
  • the secondary moisture separators 38 are disposed in the steam path between the primary separator 36 and the low pressure bundle 42 of tubes and are slidably supported by members 63 to allow for expansions and contractions.
  • the main steam After passing through the primary separator 36 at the steam inlet 34, the main steam passes through the secondary separators 38 on one side or the other of the outlet headers 44 after which it passes upwardly and between the outlet headers 44 and respective inlet headers 62 and 64 and over the inclined tubes 46 whereby heat is exchanged from the heating steam in the inclined tubes 46 to the main steam after which the resulting dried and superheated main steam continues to pass upwardly and is discharged at an outlet illustrated at 69 which is disposed at the top of the apparatus 30.
  • the main steam is then routed to a steam turbine such as LP turbine 16 in Fig. 1 for use therein.
  • Baffles 61 may also be provided at suitable locations for regulation of steam flow through the reheater 30.
  • the headers 44, 62, and 64 extend through apertures in the baffles 61 which apertures provide sufficient clearance to allow for differential motion between the baffles and headers during expansions and contractions. However, such clearances which are perhaps one-sixteenth to one-eighth inch (about 2 to 3 mm ), allow steam flow through the apertures which results in reduction of efficiency of the reheater 30.
  • plates (not shown) which are anchored to the respective headers and which overlap the respective apertures are provided adjacent and parallel to the respective baffles.
  • Apparatus 70 is provided with a horizontally disposed generally cylindrical shell 72 having a main steam inlet 74, a main steam outlet 76, a primary separator 78, a primary separator drain 79, secondary separators 80 and secondary separator drain 81 similar to those provided in the apparatus 30 of Figures 2 and 3.
  • Two bundles 82 and 84 of tubes 86, each bundle provided with two banks 88 and 90 of tubes 86 extending in a "V" configuration from a respective lower header 92, are also provided.
  • each lower header 92 is positioned approximately midway between the sides 94 and 96 of the shell 72 and the tubes 86 extend upwardly and outwardly therefrom to locations on respective sides of the vertical longitudinal centerplane 98 of the shell which are adjacent the shell 72.
  • each lower header 92 serves as both a heating steam inlet header and a condensate outlet header.
  • the tubes 86 of each bank 88 and 90 extend upwardly and terminate at closed ends in order to eliminate the expense of providing additional headers and of providing joints between the tubes and headers that would otherwise be required, to increase available room for corrugated scrubbers, and to permit the use of longer tubes in each tube bank 88 and 90 whereby the number of tube-to-header joints may be even further reduced since a lesser number of tubes would thus be required.
  • Such a construction is also provided to simplify fabrication, inspection, and maintenance of the apparatus 70.
  • the upper closed ends 100 of the tubes 86 are inserted in apertures 102 in support plates 104. Support plates 104 slide in and are supported by guides 106 which guides are in turn anchored to the shell 72.
  • one of the tubes 86 is shown opening into a header 92 and extending between a header tube sheet 108 and a support plate 104.
  • Each of the tubes 86 is closed by means such as plugging with plug member 110, it being preferable that they be plugged over a distance illustrated at 112 from the support plate 104 in a direction toward the respective header 92 of at least about 50 mm (2 inches) beyond the edge of the support plate 104 in order to prevent uneven heating of the support plate 104 and thereby reduce stresses from expansions and contractions.
  • the tubes 86 are provided with suitable fins 113 along their length for improved heat transfer in accordance with conventional practice. However, in order to provide increased strength to the header tube sheets 108, the portions of the tubes 86 which are inserted and expanded into the tube sheets 108 are not provided with fins so that reduced diameter apertures 114 may be provided in the tube sheets 108 for insertion of tubes 86.
  • heating steam is provided to the inlet headers 92 through lines 116.
  • This heating steam flows upwardly from the respective inlet header 92 into the tubes 86 which are in communication therewith and gives up heat in heat exchange relation to the main steam which is simultaneously flowing past the tubes 86.
  • the heating steam in the tubes 86 is expected to continue giving up heat to the main steam until it condenses after which the condensate thus formed is expected to flow by gravity down along the walls of the tubes 86 and back to the respective inlet header 92, and the condensing of the steam is expected to result in lower pressures for drawing of more steam into the tubes.
  • the steam is expected to become condensed, but not sub-cooled, for improved heat transfer efficiency.
  • the condensate is then discharged from the inlet header 92 to a conventional vented surge tank (not shown) or other suitable condensate receiving apparatus through condensate removal lines 118.
  • the rate of condensate flow is expected to be no more than about 25 lb (11 kg) per hour from each tube 86.
  • Such a flow rate would not require a significant portion of tube cross-section for a typical tube diameter of about one inch (2.5 cm). Therefore it is believed that "flooding" of the tubes 86 and the resulting loss of heat transfer efficiency will not normally occur.
  • the reheater 14 preferably is positioned adjacent the turbines 12 and 16, as illustrated in Figure 1, to thereby reduce the pressure losses which would otherwise result from lengthy pipe runs. This position is distinguished from the locations of the nuclear steam generator and the fossil fuel-fired steam generator 20 which may be positioned remote from the turbines 12 and 16.
  • the heating vapor to be supplied to the tubes of an apparatus 14 embodying this invention is not limited to steam but may include other satisfactory vapors such as, for example, the vapors of organic fluids such as diphenyl oxide and silicone fluid.
  • Niether is either of the apparatus 30 and 70 required to have two bundles of tubes.
  • this invention is meant to include a heat exchange apparatus having a single bundle of tubes.
  • either of the apparatus 30 and 70 may be utilized to superheat steam for other purposes such as superheating steam from a steam generator for delivery to a HP turbine.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • High Energy & Nuclear Physics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP19830303403 1983-06-13 1983-06-13 Kernkraftanlage und Apparat zum Überhitzen von Dampf Expired EP0128252B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE8383303403T DE3372035D1 (en) 1983-06-13 1983-06-13 Nuclear power plant and apparatus for superheating steam
EP19830303403 EP0128252B1 (de) 1983-06-13 1983-06-13 Kernkraftanlage und Apparat zum Überhitzen von Dampf

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19830303403 EP0128252B1 (de) 1983-06-13 1983-06-13 Kernkraftanlage und Apparat zum Überhitzen von Dampf

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EP0128252A1 true EP0128252A1 (de) 1984-12-19
EP0128252B1 EP0128252B1 (de) 1987-06-10

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0206303A1 (de) * 1985-06-22 1986-12-30 L. & C. Steinmüller GmbH Vorrichtung zum Trocknen und Überhitzen von Dampf
WO1994007006A1 (en) * 1992-09-17 1994-03-31 Ansaldo Vølund A/S Method and plant for producing high steam temperatures when burning problematic fuels
WO2007014538A3 (de) * 2005-08-02 2007-05-18 Ecoenergy Ges Fuer En Und Umwe Verfahren und vorrichtung zur erzeugung von überhitztem dampf
WO2012041980A3 (de) * 2010-09-30 2013-05-30 Siemens Aktiengesellschaft Vorrichtung und verfahren zum erzeugen von überhitztem wasserdampf
WO2013132132A3 (es) * 2012-03-09 2014-07-31 Sener, Ingenieria Y Sistemas, S.A. Procedimiento para incrementar la eficiencia de la generación eléctrica en centrales nucleares
EP2530257A3 (de) * 2011-05-30 2017-12-20 Robert Bosch Gmbh Abwärmenutzungsanlage
CN115206562A (zh) * 2022-06-24 2022-10-18 中核武汉核电运行技术股份有限公司 一种用于堵管工艺考核的压力温度瞬态试验装置

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR542101A (de) * 1922-08-05
GB316804A (en) * 1928-09-17 1929-08-08 Siemens Ag Improvements in or relating to steam power plant with intermediate superheating
US1759011A (en) * 1928-04-30 1930-05-20 Superheater Co Ltd Reheater
GB679083A (en) * 1950-11-30 1952-09-10 Bbc Brown Boveri & Cie Plant for the industrial utilization of heat produced in a nuclear reactor
FR2011992A1 (de) * 1968-06-27 1970-03-13 Bbc Brown Boveri & Cie
FR2232734A1 (de) * 1973-06-07 1975-01-03 Stal Laval Apparat Ab
FR2274121A1 (fr) * 1974-06-06 1976-01-02 Sulzer Ag Procede de resurchauffe de vapeur partiellement detendue et centrale nucleaire pour la mise en oeuvre du procede
DE2703024A1 (de) * 1977-01-26 1978-07-27 Steinmueller Gmbh L & C Vorrichtung zum trocknen von nassdampf und anschliessendem ueberhitzen des getrockneten dampfes

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR542101A (de) * 1922-08-05
US1759011A (en) * 1928-04-30 1930-05-20 Superheater Co Ltd Reheater
GB316804A (en) * 1928-09-17 1929-08-08 Siemens Ag Improvements in or relating to steam power plant with intermediate superheating
GB679083A (en) * 1950-11-30 1952-09-10 Bbc Brown Boveri & Cie Plant for the industrial utilization of heat produced in a nuclear reactor
FR2011992A1 (de) * 1968-06-27 1970-03-13 Bbc Brown Boveri & Cie
FR2232734A1 (de) * 1973-06-07 1975-01-03 Stal Laval Apparat Ab
FR2274121A1 (fr) * 1974-06-06 1976-01-02 Sulzer Ag Procede de resurchauffe de vapeur partiellement detendue et centrale nucleaire pour la mise en oeuvre du procede
DE2703024A1 (de) * 1977-01-26 1978-07-27 Steinmueller Gmbh L & C Vorrichtung zum trocknen von nassdampf und anschliessendem ueberhitzen des getrockneten dampfes

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0206303A1 (de) * 1985-06-22 1986-12-30 L. & C. Steinmüller GmbH Vorrichtung zum Trocknen und Überhitzen von Dampf
WO1994007006A1 (en) * 1992-09-17 1994-03-31 Ansaldo Vølund A/S Method and plant for producing high steam temperatures when burning problematic fuels
US5619933A (en) * 1992-09-17 1997-04-15 Ansaldo Volund A/S Method and plant for producing high steam temperatures when burning problematic fuels
WO2007014538A3 (de) * 2005-08-02 2007-05-18 Ecoenergy Ges Fuer En Und Umwe Verfahren und vorrichtung zur erzeugung von überhitztem dampf
WO2012041980A3 (de) * 2010-09-30 2013-05-30 Siemens Aktiengesellschaft Vorrichtung und verfahren zum erzeugen von überhitztem wasserdampf
US20130233301A1 (en) * 2010-09-30 2013-09-12 Guenther Beckesch Apparatus and method for producing superheated steam by means of a solar-thermally operated reheater and use of the superheated steam
CN103429853A (zh) * 2010-09-30 2013-12-04 西门子公司 制造过热水蒸汽的装置和方法
EP2530257A3 (de) * 2011-05-30 2017-12-20 Robert Bosch Gmbh Abwärmenutzungsanlage
WO2013132132A3 (es) * 2012-03-09 2014-07-31 Sener, Ingenieria Y Sistemas, S.A. Procedimiento para incrementar la eficiencia de la generación eléctrica en centrales nucleares
CN115206562A (zh) * 2022-06-24 2022-10-18 中核武汉核电运行技术股份有限公司 一种用于堵管工艺考核的压力温度瞬态试验装置

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Publication number Publication date
DE3372035D1 (en) 1987-07-16
EP0128252B1 (de) 1987-06-10

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