EP0013045B1 - Steam-generation plant - Google Patents

Steam-generation plant Download PDF

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Publication number
EP0013045B1
EP0013045B1 EP79200749A EP79200749A EP0013045B1 EP 0013045 B1 EP0013045 B1 EP 0013045B1 EP 79200749 A EP79200749 A EP 79200749A EP 79200749 A EP79200749 A EP 79200749A EP 0013045 B1 EP0013045 B1 EP 0013045B1
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Prior art keywords
water
control valve
separator
steam
plant according
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EP79200749A
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German (de)
French (fr)
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EP0013045A1 (en
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Heinz Dr. Juzi
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Sulzer AG
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Gebrueder Sulzer AG
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    • 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
    • F01K3/20—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters with heating by combustion gases of main boiler
    • F01K3/22—Controlling, e.g. starting, stopping

Definitions

  • the invention relates to a steam generator system according to the preamble of claim 1.
  • the object of the invention is to improve the steam generator system of the type mentioned at the outset in such a way that the disadvantages are avoided.
  • this object is achieved by the features according to the characterizing part of claim 1. This will prior to lowering the pressure of the water flowing in the water drain line. H. upstream of the first control valve, the water in the heat exchanger is cooled to a temperature which is substantially below the saturated steam temperature, so that there is no longer any risk of cavitation for the first control valve. Because of the staggered operation of the two control valves, the duration during which the second valve is flowed through is considerably reduced. Since the second valve is in the secondary line, which can also branch off from the water outlet line upstream of the heat exchanger, the gradation prevents rapid erosion of the second control valve in this arrangement as well.
  • the staggered use of the two control valves allows the first control valve to be made smaller for a given amount of water to be fed to the feed water vessel. This in turn allows the safety blow-off device in the feed water vessel to be made smaller. Both are associated with significant savings.
  • a steam generator system is known from FIG. 2 of DE-AS 1290940, in which - similar to the characterizing part of the new claim 1 - the heat exchanger is connected upstream of the first control valve in the flow direction of the water from the separator and means for influencing two depending on the water content of the heat exchanger Control valves are provided in such a way that when the level in the heat exchanger rises, the first and then the second control valve opens first, and that when the level falls, the second control valve closes and then the first control valve closes.
  • the heat exchanger there is designed as a control preheater in which - depending on the amount of water covering the heating surface - more or less steam is condensed.
  • the purpose of this is to influence the amount of steam flowing through a post-heater depending on the hot steam temperature and thus the temperature of the steam.
  • the invention is a water-water heat exchanger, which is flooded with water on the primary side. The primary-side Wa SSE is therefore cooled down considerably.
  • the arrangement according to the claim further reduces the risk of cavitation erosions occurring at the second control valve.
  • a larger amount of heat can be recuperated in heat transfer.
  • the claim 3 gives a dimensioning rule for the cross section of the first control valve, which has the additional advantage of a smaller dimensioning of the safety blow-off device.
  • the first control valve is to be designed in such a way that it does not exceed 125% of the water accumulated under these conditions in the separator under the pressure and temperature conditions of the specified minimum load. H. a maximum of 18.7% of the full-load feed water can let through, but not the full 30% that temporarily flows into the separator when starting, or the even larger amount of water that briefly gets into the separator when the steam starts up
  • the capacitor is protected.
  • the isolator is preferably provided with an injection cooler.
  • the arrangement according to claim 6 allows to get by with a single level sensor on the water separator.
  • the dimensioning rule according to claim 7 allows the invention to be used in systems in which the separator is operated dry at full load.
  • the circuit according to claim 8 brings considerable savings to safety blow-off devices in the event that the separator is driven dry at full load.
  • Condensate separators according to claim 9, also called condensate plugs, are known separator elements which probably allow water to escape, but not steam. They have largely proven themselves in practice and are reliable and inexpensive, redundant means for preventing steam from entering the feed water tank.
  • a feed line 2 with feed pump 3 and two high-pressure preheaters 4 and 5 leads from a feed water tank 1 to the secondary side of a heat exchanger 6 and from there to an economizer 10 of a steam generator 11.
  • the economizer 10 exits via a line 14 connected to an evaporator 15, which forms the wall tube of a combustion chamber 16.
  • a furnace 17 opens into this combustion chamber 16.
  • the evaporator 15 is connected to a water separator 20, which has an outlet 21 for separated water at the bottom and is provided at the top with a steam discharge line 22, which leads to a superheater 24, which is in the steam generator 11 in the room is arranged above the combustion chamber 16.
  • a live steam line 30 leads from the superheater 24 via a live steam valve 31 to a turbine 32 which is seated on a common shaft with a generator 33.
  • a condenser 35 with a hotwell 36 is connected.
  • a condensate line 40 leads via a first condensate pump 41, a condensate cleaning system 42, a second condensate pump 43 and a low-pressure preheater 44 to a degassing tower 45 arranged on the feed water tank 1.
  • a safety blow-off device 47 is located on the feed water tank 1 is represented by a safety valve.
  • a pressure transmitter (not shown) on the feed water tank 1, which acts on valves fitted in the bleed steam lines of the high-pressure preheaters 4 and 5 in the sense that the steam pressure in the feed water tank is regulated by influencing the temperature of the feed water at the inlet of the heat exchanger 6.
  • a water outlet line 50 leads via the primary side of the heat exchanger 6, a check valve 51 and a first control valve 52 to the feed water tank 1.
  • a secondary line 55 is connected, which leads via a second control valve 56 to a water-steam separator 57, the steam outlet 58 of which is connected to the steam chamber of the condenser 35 and the water outlet 59 of which is connected to the hotwell 36.
  • An injection water line 60 branches off from the condensate line 40 between the condensate cleaning system 42 and the second condensate pump 43 and opens into the secondary line 55 at an injection point 61 directly upstream of the water-steam separator 57.
  • a second level transmitter 70 and 71 are arranged, the outputs of which are connected to a controller 72 and 73, respectively.
  • the output of the controller 72 influences the first control valve 52, while the output of the second controller 73 acts on the second control valve 56.
  • the regulators 72 and 73 are designed such that when the water level rises, the first regulating valve 52 opens first and then the second regulating valve 56, while when the water level falls, the second regulating valve 56 and then the first regulating valve 52 close first.
  • the opening and closing movements of the two control valves can adjoin or overlap; however, there may also be a margin between the two strokes.
  • a water discharge line 76 is connected to the water outlet line 50 between the outlet 21 and the heat exchanger 6, said water discharge line 76 or directly via a third control valve 77 between the second control valve 56 and the injection point 61 opens into the water-steam separator 57.
  • This third control valve 77 is actuated by a level sensor 78 via a controller 79, which is designed analogously to the controllers 72 and 73 and is set such that the third control valve 77 opens in third place when the level rises and closes in first place when the level falls.
  • the first control valve 52 is able to discharge the entire amount of water separated in the separator 20.
  • the level in the separator drops so far that the second control valve 56 closes. This recuperates all of the heat contained in the returned water. If the steam generator output rises further, the water content at the outlet of the evaporator 15 drops. The level in the separator 20 drops further, and the first control valve 52 is also moved successively into the closed position. Finally, slightly overheated steam enters the separator 20, which evaporates the water still present there.
  • the system described allows the evaporator 15 from zero to a limit load, for. B. 30% to feed with approximately constant amount of feed water, the excess water from the separator 20 is returned to the feed water tank 1, and to drive above this load with a dry separator.
  • the system is also suitable for the known concept, according to which the evaporator 15 above the limit load of z. B. 30% is driven with low humidity.
  • the device functions as described, but with the difference that at high water levels in the water separator 20, part of the water flows through the discharge line 76 flows past the heat exchanger directly to the condenser 35.
  • E; is a question of the operational management of the system, ot it is economical to provide the discharge line 76 with the third control valve 77.
  • control valves 52, 56 and 77 could also be controlled in cascade by the position of the first control valve 52 acting as a control variable on the position of the second control valve 56, during the position of which influences the third control valve 77.
  • the attempt to reduce the size of the safety blow-off device 47 on the feed water tank 1 creates the risk that, when the first control valve 52 is opened due to a fault, the pressure in the feed water tank 1 rises rapidly at full load and the dry separator 20 and the feed water tank could explode.
  • the first control valve 52 - or a shut-off valve arranged in series therewith - can be influenced by an aggregate state, which is arranged in the water outlet line 50 and closes the first control valve or, if appropriate, the shut-off valve when steam occurs therein.
  • a static or dynamic condensing plug can also be arranged in series with the first control valve 52, which only allows water to flow through, but not steam.
  • a so-called negative safety valve can also be installed in series with the first control valve 52, which is actuated in a closing sense by the pressure in the feed water tank 1 as soon as this pressure exceeds a certain limit value. It may also be expedient to arrange a tear membrane in addition to the safety blow-off device dimensioned according to claim 8, the cross-section of which is designed, together with that of the blow-off device 47, for the full steam flow occurring in the feed water tank in the event of a malfunction.

Description

Die Erfindung betrifft eine Dampferzeugeranlage nach dem Oberbegriff des Anspruchs 1.The invention relates to a steam generator system according to the preamble of claim 1.

Aus der US-PS 3338053 ist eine solche Anlage bekannt, bei der das erste Regelventil stromoberhalb des Wärmeübertragers angeordnet ist. Bei dieser Anordnung sind sowohl das erste Regelventil wie auch die Eingangspartien des Wärmeübertragers hohem Verschleiss durch Kavitation ausgesetzt, da das in der Wasserablaufleitung strömende Wasser von Satt-Zustand verhältnismässig hohe Geschwindigkeiten annimmt. Solcher Verschleiss setzt die Betriebssicherheit herab; er führt zu kostenspieligen Reparaturen, zu Stillstandzeiten sowie zur Verschmutzung des Systems durch Erosionsprodukte.From US-PS 3338053 such a system is known in which the first control valve is arranged upstream of the heat exchanger. With this arrangement, both the first control valve and the input parts of the heat exchanger are subject to high wear due to cavitation, since the water flowing in the water drainage line from a saturated state assumes relatively high speeds. Such wear reduces operational safety; it leads to costly repairs, downtimes and contamination of the system by erosion products.

Es ist Aufgabe der Erfindung, die Dampferzeugeranlage der eingangs genannten Art so zu verbessern, dass die Nachteile vermieden werden.The object of the invention is to improve the steam generator system of the type mentioned at the outset in such a way that the disadvantages are avoided.

Diese Aufgabe wird erfindungsgemäss durch die Merkmale nach dem Kennzeichen des Anspruchs 1 gelöst. Dadurch wird vor dem Herabsetzen des Druckes des in der Wasserablaufleitung strömenden Wassers, d. h. stromoberhalb des ersten Regelventils, das Wasser im Wärmeübertrager auf eine Temperatur gekühlt, die wesentlich unter der Sattdampftemperatur liegt, so dass für das erste Regelventil keine Kavitationsgefahr mehr besteht. Wegen des gestaffelten Betriebes der beiden Regelventile wird die Dauer, während der das zweite Ventil durchströmt wird, erheblich herabgesetzt. Da das zweite Ventil in der Nebenleitung liegt, die auch stromoberhalb des Wärmeübertragers von der Wasseraustrittsleitung abzweigen kann, wird auch in diesem Anordnungsfall durch die Staffelung eine schnelle Erosion des zweiten Regelventils verhindert. Überdies gestattet der gestaffelte Einsatz der beiden Regelventile für eine gegebene, dem Speisewassergefäss zuzuführende Wassermenge, das erste Regelventil kleiner zu bemessen. Dies wiederum erlaubt, die Sicherheitsabblaseeinrichtung im Speisewassergefäss kleiner zu bemessen. Beides ist mit beträchtlichen Einsparungen verbunden.According to the invention, this object is achieved by the features according to the characterizing part of claim 1. This will prior to lowering the pressure of the water flowing in the water drain line. H. upstream of the first control valve, the water in the heat exchanger is cooled to a temperature which is substantially below the saturated steam temperature, so that there is no longer any risk of cavitation for the first control valve. Because of the staggered operation of the two control valves, the duration during which the second valve is flowed through is considerably reduced. Since the second valve is in the secondary line, which can also branch off from the water outlet line upstream of the heat exchanger, the gradation prevents rapid erosion of the second control valve in this arrangement as well. In addition, the staggered use of the two control valves allows the first control valve to be made smaller for a given amount of water to be fed to the feed water vessel. This in turn allows the safety blow-off device in the feed water vessel to be made smaller. Both are associated with significant savings.

Aus Fig.2 der DE-AS 1290940 ist eine Dampferzeugeranlage bekannt, bei der - ähnlich dem Kennzeichen des neuen Anspruchs 1 - der Wärmeübertrager in Strömungsrichtung des Wassers aus dem Abscheider dem ersten Regelventil vorgeschaltet ist und Mittel zum vom Wasserinhalt des Wärmeübertragers abhängigen Beeinflussen von zwei Regelventilen derart vorgesehen sind, dass bei steigendem Niveau im Wärmeübertrager zuerst das erste und dann das zweite Regelventil öffnet und dass bei fallendem Niveau zuerst das zweite Regelventil und dann das erste Regelventil schliesst. Dass bei diesem Dampferzeuger das Niveau nicht im Abscheider, sondern im Wärmeübertrager gemessen wird, stellt einen wesentlichen Unterschied zur Erfindung dar; der Wärmeübertrager ist dort nämlich als Regelvorwärmer ausgebildet, in dem - abhängig von der Menge des die Heizfläche bedeckenden Wassers - mehr oder weniger Dampf kondensiert wird. Es wird damit bezweckt, durch in Abhängigkeit von de Heissdampftemperatur erfolgendes Einstellen de Niveaus die einen Nachüberhitzer durchströmer de Dampfmenge und damit die Temperatur de Dampfes zu beeinflussen. Im Gegensatz dazu har delt es sich bei der Erfindung um einen Wasse Wasser-Wärmeübertrager, der primärseitig stel mit Wasser geflutet ist. Das Primärseitige WaSSE wird daher erheblich zurückgekühlt. Mit der Anl: ge nach der Erfindung kann die Aufgabe der DE AS 1290940 nicht gelöst werden; umgekehrt läs: sich aber auch mit der bekannten Anlage die Au gabe der Erfindung nicht lösen: Das Kondens verlässt dort den Wärmeübertrager praktisch ir Satt-Zustand, was im ersten Regelventil zu Kav tationserosionen führt. Ausserdem lässt sich b4 der bekannten Anordnung weder das erste Rege ventil noch das nicht gezeichnete, auf dem SpeisE behälter angeordnete Sicherheitsventil verkle nern. Gerade beim Anfahren würde ja wegen dE zu tiefen Heissdampftemperatur der Sollwert fi das Wasserniveau im Wärmeübertrager auf de Minimalwert gesenkt. Dieser Sollwert kann vo der Regelung nur dann erreicht werden, wenn da erste Regelventil gross genug ist. Die DE-AS kan daher für die Erfingung keinerlei Anregung geberA steam generator system is known from FIG. 2 of DE-AS 1290940, in which - similar to the characterizing part of the new claim 1 - the heat exchanger is connected upstream of the first control valve in the flow direction of the water from the separator and means for influencing two depending on the water content of the heat exchanger Control valves are provided in such a way that when the level in the heat exchanger rises, the first and then the second control valve opens first, and that when the level falls, the second control valve closes and then the first control valve closes. The fact that the level of this steam generator is measured not in the separator, but in the heat exchanger, is an essential difference from the invention; the heat exchanger there is designed as a control preheater in which - depending on the amount of water covering the heating surface - more or less steam is condensed. The purpose of this is to influence the amount of steam flowing through a post-heater depending on the hot steam temperature and thus the temperature of the steam. In contrast, the invention is a water-water heat exchanger, which is flooded with water on the primary side. The primary-side Wa SSE is therefore cooled down considerably. With the system according to the invention, the task of DE AS 1290940 cannot be achieved; Conversely, the problem of the invention cannot be solved even with the known system: the condensate leaves the heat exchanger practically in a saturated state, which leads to cavitation erosion in the first control valve. In addition, b 4 of the known arrangement, neither the first rain valve nor the non-illustrated safety valve arranged on the feed container can be reduced. Especially when starting'd d due to low E superheated steam temperature set point, the water level in the heat exchanger fi on de minimum value lowered. This setpoint can only be reached by the control if the first control valve is large enough. The DE-AS can therefore give no suggestion for the invention

Bei der Anlage nach der GB-PS 816765 feh nicht nur eine vom am Verdampfer angeschlossi ne Abscheider zum Speisewassergefäss zurücl führende Wasseraustrittsleitung, sondern auc ein Wärmeübertrager zwischen diesem Absche der und den Regelventilen, so dass auch hier di Erfingungsaufgabe nicht gelöst werden kani Auch die GB-PS kann daher für die Erfindun keine Anregung geben.In the system according to GB-PS 816765, not only does a water outlet line lead back from the separator connected to the evaporator to the feed water vessel, but also a heat exchanger between this separator and the control valves, so that the task of invention cannot be solved here either -PS can therefore give no suggestion for the invention.

Durch die Anordnung nach dem Anspruch wird die Gefahr des Auftretens von Kavitation erosionen am zweiten Regelventil weiter vermin dert. Ausserdem lässt sich im Wärmeübertragi eine grössere Wärmemenge rekuperieren.The arrangement according to the claim further reduces the risk of cavitation erosions occurring at the second control valve. In addition, a larger amount of heat can be recuperated in heat transfer.

Der Anspruch 3 gibt eine Bemessungsvorschri für den Querschnitt des ersten Regelventils, fi die der zusätzliche Vorteil einer kleineren Beme sung der Sicherheitsabblaseeinrichtung voll zi Geltung kommt. Die beanspruchte Bemessung vorschrift ist folgendermassen zu verstehen:The claim 3 gives a dimensioning rule for the cross section of the first control valve, which has the additional advantage of a smaller dimensioning of the safety blow-off device. The claimed design specification is to be understood as follows:

Wenn der Dampferzeuger bei Mindestlast b trieben wird, wobei z. B. 15% der normale Dampfmenge produziert wird und die Speisewa sermenge z. B. 30% der Menge bei Normalla beträgt, fallen im Wasserabscheider 15% Wass an. Nach der Bemessungsvorschrift ist das ers Regelventil so auszulegen, dass es bei den Druc und Temperaturbedingungen der genannten Mi destlast nicht mehr als 125% des unter diese Bedingungen im Abscheider anfallenden Wa sers, d. h. höchstens 18,7% der Vollast-Speisewa sermenge durchlassen kann, nicht aber die volle 30%, die beim Anfahren vorübergehend in de Abscheider strömen, oder die noch grössere Wa sermenge, die beim Dampfaufstoss während de Anfahrens kurzzeitig in den Abscheider gelangtIf the steam generator is driven at minimum load b, z. B. 15% of the normal amount of steam is produced and the amount of feed water z. B. is 30% of the amount at Normalla, 15% water accumulate in the water separator. According to the design specification, the first control valve is to be designed in such a way that it does not exceed 125% of the water accumulated under these conditions in the separator under the pressure and temperature conditions of the specified minimum load. H. a maximum of 18.7% of the full-load feed water can let through, but not the full 30% that temporarily flows into the separator when starting, or the even larger amount of water that briefly gets into the separator when the steam starts up

Durch die Massnahme nach Anspruch 4 lasse sich weitere Einsparungen erzielen, indem sich die Grösse des Wärmeübertragers bezüglich der Gesamtkosten optimieren lässt.By the measure according to claim 4 let further savings can be achieved by optimizing the size of the heat exchanger in terms of total costs.

Durch das Einschalten eines Dampf/Wasser-Trenners gemäss Anspruch 5 wird der Kondensator geschont. Der Trenner wird, wie an sich bekannt, vorzugsweise mit Einspritzkühler versehen.By switching on a steam / water separator according to claim 5, the capacitor is protected. As is known per se, the isolator is preferably provided with an injection cooler.

Die Anordnung nach Anspruch 6 erlaubt, mit einem einzigen Niveaugeber am Wasserabscheider auszukommen.The arrangement according to claim 6 allows to get by with a single level sensor on the water separator.

Die Bemessungsregel nach Anspruch 7 erlaubt, die Erfindung in Anlagen anzuwenden, in denen der Abscheider im Vollastbetrieb trocken gefahren wird.The dimensioning rule according to claim 7 allows the invention to be used in systems in which the separator is operated dry at full load.

Die Schaltung nach Anspruch 8 bringt erhebliche Einsparungen an Sicherheitsabblaseeinrichtungen für den Fall, dass der Abscheider bei Volllast trocken gefahren wird.The circuit according to claim 8 brings considerable savings to safety blow-off devices in the event that the separator is driven dry at full load.

Kondensatabscheider nach Anspruch 9, auch Kondenstöpfe genannt, sind bekannte Abscheiderorgane, die wohl Wasser, nicht aber Dampf austreten lassen. Sie haben sich in der Praxis weitgehend bewährt und sind zuverlässige und kostengünstige, redundante Mittel zum Verhindern des Eintritts von Dampf in den Speisewasserbehälter.Condensate separators according to claim 9, also called condensate plugs, are known separator elements which probably allow water to escape, but not steam. They have largely proven themselves in practice and are reliable and inexpensive, redundant means for preventing steam from entering the feed water tank.

Die Erfindung wird nun an einem zeichnerisch dargestellten Ausführungsbeispiel näher erläutert. Es zeigen:

  • Fig. ein Schema einer Dampferzeugeranlage nach der Erfindung und
  • Fig. eine alternative Regelschaltung zum Betätigen der Regelventile.
The invention will now be explained in more detail using an illustrated embodiment. Show it:
  • Fig. Is a diagram of a steam generator system according to the invention and
  • Fig. An alternative control circuit for operating the control valves.

In der Anlage gemäss Fig. führt von einem Speisewasserbehälter 1 eine Speiseleitung 2 mit Speisepumpe 3 und zwei Hochdruckvorwärmern 4 und 5 zur Sekundärseite eines Wärmeübertragers 6 und von dort zu einem Economiser 10 eines Dampferzeugers 11. Der Austritt des Economisers 10 ist über eine Leitung 14 mit einem Verdampfer 15 verbunden, der die Wandberohrung einer Brennkammer 16 bildet. In diese Brennkammer 16 mündet eine Feuerung 17. Der Verdampfer 15 ist mit einem Wasserabscheider 20 verbunden, der unten einen Austritt 21 für abgeschiedenes Wasser aufweist und oben mit einer Dampfabfuhrleitung 22 versehen ist, die zu einem Überhitzer 24 führt, der im Dampferzeuger 11 im Raum oberhalb der Brennkammer 16 angeordnet ist. Eine Frischdampfleitung 30 führt vom Überhitzer 24 über ein Frischdampfventil 31 zu einer Turbine 32, die mit einem Generator 33 auf einer gemeinsamen Welle sitzt. Am Niederdruckende der Turbine 32 ist ein Kondensator 35 mit Hotwell 36 angeschlossen. Aus diesem Hotwell 36 führt eine Kondensatleitung 40 über eine erste Kondensatpumpe 41, eine Kondensatreinigungsanlage 42, eine zweite Kondensatpumpe 43 und einen Niederdruckvorwärmer 44 zu einem auf dem Speisewasserbehälter 1 angeordneten Entgaserturm 45. Neben diesem Entgaserturm befindet sich auf dem Speisewasserbehälter 1 eine Sicherheitsabblaseeinrichtung 47, die durch ein Sicherheitsventil dargestellt ist. Es kann überdies auf dem Speisewasserbehälter 1 ein nicht gezeichneter Druckgeber vorhanden sein, der auf in den Anzapfdampfleitungen der Hochdruckvorwärmer 4 und 5 angebrachte Ventile in dem Sinne einwirkt, dass durch Beeinflussen der Temperatur des Speisewassers am Eintritt des Wärmeübertragers 6 der Dampfdruck im Speisewasserbehälter geregelt wird.In the system according to FIG. 1, a feed line 2 with feed pump 3 and two high-pressure preheaters 4 and 5 leads from a feed water tank 1 to the secondary side of a heat exchanger 6 and from there to an economizer 10 of a steam generator 11. The economizer 10 exits via a line 14 connected to an evaporator 15, which forms the wall tube of a combustion chamber 16. A furnace 17 opens into this combustion chamber 16. The evaporator 15 is connected to a water separator 20, which has an outlet 21 for separated water at the bottom and is provided at the top with a steam discharge line 22, which leads to a superheater 24, which is in the steam generator 11 in the room is arranged above the combustion chamber 16. A live steam line 30 leads from the superheater 24 via a live steam valve 31 to a turbine 32 which is seated on a common shaft with a generator 33. At the low pressure end of the turbine 32, a condenser 35 with a hotwell 36 is connected. From this hotwell 36, a condensate line 40 leads via a first condensate pump 41, a condensate cleaning system 42, a second condensate pump 43 and a low-pressure preheater 44 to a degassing tower 45 arranged on the feed water tank 1. In addition to this degassing tower, a safety blow-off device 47 is located on the feed water tank 1 is represented by a safety valve. There may also be a pressure transmitter (not shown) on the feed water tank 1, which acts on valves fitted in the bleed steam lines of the high-pressure preheaters 4 and 5 in the sense that the steam pressure in the feed water tank is regulated by influencing the temperature of the feed water at the inlet of the heat exchanger 6.

Vom Austritt 21 des Abscheiders 20 führt eine Wasseraustrittsleitung 50 über die Primärseite des Wärmeübertragers 6, ein Rückschlagventil 51 und ein erstes Regelventil 52 zum Speisewasserbehälter 1. An der Wasseraustrittsleitung 50 ist zwischen dem Wärmeübertrager 6 und dem ersten Regelventil 52, und zwar noch stromoberhalb des Rückschlagventils 51, eine Nebenleitung 55 angeschlossen, die über ein zweites Regelventil 56 zu einem Wasser-Dampftrenner 57 führt, dessen Dampfaustritt 58 mit dem Dampfraum des Kondensators 35 und dessen Wasseraustritt 59 mit dem Hotwell 36 verbunden ist. Von der Kondensatleitung 40 zweigt zwischen der Kondensatreinigungsanlage 42 und der zweiten Kondensatpumpe 43 eine Einspritzwasserleitung 60 ab, die an einer dem Wasser-Dampftrenner 57 direkt vorgelagerten Einspritzstelle 61 in die Nebenleitung 55 mündet.From the outlet 21 of the separator 20, a water outlet line 50 leads via the primary side of the heat exchanger 6, a check valve 51 and a first control valve 52 to the feed water tank 1. At the water outlet line 50 there is between the heat exchanger 6 and the first control valve 52, namely upstream of the check valve 51, a secondary line 55 is connected, which leads via a second control valve 56 to a water-steam separator 57, the steam outlet 58 of which is connected to the steam chamber of the condenser 35 and the water outlet 59 of which is connected to the hotwell 36. An injection water line 60 branches off from the condensate line 40 between the condensate cleaning system 42 and the second condensate pump 43 and opens into the secondary line 55 at an injection point 61 directly upstream of the water-steam separator 57.

Im Abscheider 20 sind ein erster und darüber ein zweiter Niveaugeber 70 bzw. 71 angeordnet, deren Ausgänge mit je einem Regler 72 bzw. 73 verbunden sind. Der Ausgang des Reglers 72 beeinflusst das erste Regelventil 52, während der Ausgang des zweiten Reglers 73 auf das zweite Regelventil 56 einwirkt. Die Regler 72 und 73 sind so konzpiert, dass beim Ansteigen des Wasserniveaus zuerst das erste Regelventil 52 und hernach das zweite Regelventil 56 öffnet, während beim Absinken des Wasserniveaus zuerst das zweite Regelventil 56 und dann das erste Regelventil 52 schliesst. Die Öffnungs- und Schliessbewegungen der beiden Regelventile können aneinandergrenzen oder sich überlappen; es kann aber auch ein Spielraum zwischen den beiden Hüben vorgesehen sein.In the separator 20 a first and above it a second level transmitter 70 and 71 are arranged, the outputs of which are connected to a controller 72 and 73, respectively. The output of the controller 72 influences the first control valve 52, while the output of the second controller 73 acts on the second control valve 56. The regulators 72 and 73 are designed such that when the water level rises, the first regulating valve 52 opens first and then the second regulating valve 56, while when the water level falls, the second regulating valve 56 and then the first regulating valve 52 close first. The opening and closing movements of the two control valves can adjoin or overlap; however, there may also be a margin between the two strokes.

Im weiteren ist in Fig. 1 als weiterentwickelte Form der Erfindung an der Wasseraustrittsleitung 50 zwischen dem Austritt 21 und dem Wärmeübertrager 6 eine Wasserabfuhrleitung 76 angeschlossen, die über ein drittes Regelventil 77 zwischen dem zweiten Regelventil 56 und der Einspritzstelle 61 in die Nebenleitung 55 oder direkt in den Wasser-Dampftrenner 57 einmündet. Dieses dritte Regelventil 77 wird von einem Niveaugeber 78 über einen Regler 79 betätigt, der analog zu den Reglern 72 und 73 ausgebildet und so eingestellt ist, dass das dritte Regelventil 77 bei steigendem Niveau an dritter Stelle öffnet und bei fallendem Niveau an erster Stelle schliesst.Furthermore, in FIG. 1, as a further developed form of the invention, a water discharge line 76 is connected to the water outlet line 50 between the outlet 21 and the heat exchanger 6, said water discharge line 76 or directly via a third control valve 77 between the second control valve 56 and the injection point 61 opens into the water-steam separator 57. This third control valve 77 is actuated by a level sensor 78 via a controller 79, which is designed analogously to the controllers 72 and 73 and is set such that the third control valve 77 opens in third place when the level rises and closes in first place when the level falls.

Bei der nun folgenden Funktionsbeschreibung der Einrichtung wird zunächst vorausgesetzt, das die Wasserabfuhrleitung 76 mit dem dritten Regelventil 77, der Niveaugeber 78 und der Regler 79 nicht vorhanden sind. Das Anfahren der Dampferzeugeranlage aus dem kalten Zustand wickelt sich dann wie folgt ab:

  • Zunächst wird mittels der Speisepumpe 3 Wasser aus dem Speisewasserbehälter 1 über die Leitung 2, den Economiser 10, die Leitung 14 und den Verdampfer 15 in den Abscheider 20 eingespeist. Mit steigendem Niveau im Abscheider öffnen die Regelventile 52 und 56 nacheinander. Damit strömt entsprechend der Druckdifferenz am ersten Regelventil 52 ein Teil des Wassers über dieses in den Speisewasserbehälter 1 zurück, während der Rest des Wassers über das zweite Regelventil 56 in den Kondensator 35 gelangt. Nun wird das Feuer gezündet. Damit entsteht im Verdampfer 15 Dampf, was einen starken Wasserausstoss in den Abscheider 20 zur Folge hat. Das zweite Regelventil 56 wird dabei voll geöffnet und zudem wird die Speicherkapazität des Abscheiders 20 beansprucht. Im weiteren Verlauf des Anfahrvorganges steigt der Druck im Dampferzeuger , so dass die Durchströmungsgeschwindigkeit in den Regelventilen 52 und 56 zunimmt. Bei gleichbleibender Fördermenge der Speisepumpe 3 beginnt wegen des sinkenden Niveaus im Abscheider 20 das zweite Regelventil 56 sich in Schliessrichtung zu bewegen. Wegen der steigenden Enthalphie des über die Austrittsleitung 50 rückgeführten Wassers wird das Speisewasser im Wärmeübertrager 6 zunehmend aufgewärmt. Es wird somit ein zunehmender Teil der im rückgeführten Wasser enthaltenen Wärme im Wärmeübertrager 6 rekuperiert und ein weiterer, erheblicher Teil der Wärme dem Speisewasserbehälter 1 zugeführt, während ein mit steigender Last, d. h. mit steigendem Druck im Dampferzeuger, abnehmender Teil der Wärme in den Kondensator 35 abgeführt wird.
In the following functional description of the device, it is initially assumed that the water discharge line 76 with the third control valve 77, the level transmitter 78 and the controller 79 are not present. The start-up of the steam generator system from the cold state then takes place as follows:
  • First, by means of the feed pump 3, water is fed from the feed water tank 1 via the lei device 2, the economizer 10, the line 14 and the evaporator 15 fed into the separator 20. As the level in the separator rises, the control valves 52 and 56 open one after the other. In accordance with the pressure difference at the first control valve 52, part of the water thus flows back into the feed water tank 1, while the rest of the water reaches the condenser 35 via the second control valve 56. Now the fire is lit. This creates 15 steam in the evaporator, which results in a strong water output in the separator 20. The second control valve 56 is fully opened and the storage capacity of the separator 20 is also used. As the start-up process continues, the pressure in the steam generator rises, so that the flow rate in the control valves 52 and 56 increases. With the delivery rate of the feed pump 3 remaining the same, the second control valve 56 begins to move in the closing direction because of the falling level in the separator 20. Because of the increasing enthalpy of the water returned via the outlet line 50, the feed water in the heat exchanger 6 is increasingly warmed up. An increasing part of the heat contained in the recirculated water is thus recuperated in the heat exchanger 6 and a further, substantial part of the heat is fed to the feed water tank 1, while a decreasing part of the heat with increasing load, ie with increasing pressure in the steam generator, into the condenser 35 is dissipated.

Hat der Dampferzeuger seine Mindestlast, z. B. 15%, und den zugehörigen Druck erreicht, so vermag das erste Regelventil 52 die gesamte im Ascheider 20 abgeschiedene Wassermenge abzuführen. Das Niveau im Abscheider sinkt soweit, dass das zweite Regelventil 56 schliesst. Damit wird die gesamte im rückgeführten Wasser enthaltene Wärme rekuperiert. Bei weiterem Ansteigen der Dampferzeugerleistung sinkt der Wassergehalt am Austritt des Verdampfers 15. Das Niveau im Abscheider 20 sinkt weiter und dabei wird auch das erste Regelventil 52 sukzessive in Schliessstellung bewegt. Schliesslich tritt leicht überhitzter Dampf in den Abscheider 20, der das dort noch vorhandene Wasser verdampft.Has the steam generator its minimum load, e.g. B. 15%, and reaches the associated pressure, the first control valve 52 is able to discharge the entire amount of water separated in the separator 20. The level in the separator drops so far that the second control valve 56 closes. This recuperates all of the heat contained in the returned water. If the steam generator output rises further, the water content at the outlet of the evaporator 15 drops. The level in the separator 20 drops further, and the first control valve 52 is also moved successively into the closed position. Finally, slightly overheated steam enters the separator 20, which evaporates the water still present there.

Wie aus dieser Beschreibung hervorgeht, gestattet die beschriebene Anlage den Verdampfer 15 von Null bis zu einer Grenzlast, z. B. 30%, mit etwa konstanter Speisewassermenge zu beschikken, wobei das überschüssige Wasser aus dem Abscheider 20 in den Speisewasserbehälter 1 zurückgeführt wird, und oberhalb dieser Last mit trockenem Abscheider zu fahren. Selbstverständlich eignet sich die Anlage auch für das bekannte Konzept, gemäss dem der Verdampfer 15 oberhalb der erwähnten Grenzlast von z. B. 30% mit geringer Feuchtigkeit gefahren wird.As is apparent from this description, the system described allows the evaporator 15 from zero to a limit load, for. B. 30% to feed with approximately constant amount of feed water, the excess water from the separator 20 is returned to the feed water tank 1, and to drive above this load with a dry separator. Of course, the system is also suitable for the known concept, according to which the evaporator 15 above the limit load of z. B. 30% is driven with low humidity.

Sind in der Anlage die Wasserabfuhrleitung 76 mit dem dritten Regelventil 77, der Niveaugeber 78 und der Regler 79 vorhanden, so funktioniert die Einrichtung wie beschrieben, jedoch mit dem Unterschied, dass jeweils bei hohem Wasserstand im Wasserabscheider 20 ein Teil des Wassers über die Abfuhrleitung 76 am Wärmeübertrager vorbei direkt zum Kondensator 35 strömt. Dies ha den Vorteil, dass der Wärmeübertrager 6 kleine gebaut werden kann als wenn die Abfuhrleitunc 76 zwischen dem Wärmeübertrager 6 und de Abzweigung der Nebenleitung 55 an die Wasser austrittsleitung 50 angeschlossen wäre. Als Nach teil ist aber zu berücksichtigen, dass während ei nes bestimmten kurzen Abschnittes der Anfahrzei mehr Wärme im Kondensator 35 verlorengeht. E; ist eine Frage der Betriebsführung der Anlage, ot es wirtschaftlich ist, die Abfuhrleitung 76 mit derr dritten Regelventil 77 vorzusehen.If the water discharge line 76 with the third control valve 77, the level transmitter 78 and the controller 79 are present in the system, the device functions as described, but with the difference that at high water levels in the water separator 20, part of the water flows through the discharge line 76 flows past the heat exchanger directly to the condenser 35. This has the advantage that the heat exchanger 6 can be made smaller than if the discharge line 76 between the heat exchanger 6 and the branch of the branch line 55 were connected to the water outlet line 50. As a part, it must be taken into account that more heat is lost in the condenser 35 during a certain short section of the start-up time. E; is a question of the operational management of the system, ot it is economical to provide the discharge line 76 with the third control valve 77.

Bei längerem Betrieb mit Mindestlast kann e: vorkommen, dass die Wärme, die mit dem übe das erste Regelventil 52 strömenden Wasser ir den Speisewasserbehälter 1 zurückgeführt wird zu einem Ansteigen des Druckes im Speisewas serbehälter führt, so dass der Abblasedruck de Sicherheitsabblaseeinrichtung 47 erreicht wirc und diese Einrichtung öffnet. Um ein solches Ab blasen zu vermeiden, kann der erwähnte, auf Ven tile in den Anzapfleitungen zu den Hochdruckvor wärmern 4, 5 wirkende Druckgeber vorgeseher sein, durch den nun das eine, das andere ode beide dieser Ventile in Drossel- oder Schliessstel lung bewegt werden. Dadurch sinkt die Tempera tur des Speisewassers am Eintritt des Wärme übertragers 6, so dass das über das erste Regel ventil 52 in den Speisewasserbehälter 1 zurückge führte Wasser auf einen Wert zurückgekühlt wird der ein Ansprechen der Abblasevorrichtung 4i ausschliesst.In the case of longer operation with a minimum load, e: the heat that is returned to the feed water tank 1 with the water flowing through the first control valve 52 leads to an increase in the pressure in the feed water tank, so that the blow-off pressure reaches the safety blow-off device 47 and this facility opens. To avoid such a blow off, the mentioned, on Ven tile in the bleed lines to the high pressure preheaters 4, 5 acting pressure transducers can be provided, through which one or the other or both of these valves are moved in throttle or closed position . As a result, the temperature of the feed water at the inlet of the heat exchanger 6 drops, so that the water returned via the first control valve 52 into the feed water container 1 is cooled back to a value which excludes a response of the blow-off device 4i.

In Fig.2 sind wiederum der Wasserabscheidei 20 und die drei Regelventile 52, 56 und 77 darge stellt. Am Abscheider 20 ist anstelle der drei Ni veaugeber 70, 71 und 78 jedoch nur ein einzigem Niveaugeber 80 angeordnet, dessen Ausgang au drei parallelgeschaltete Proportionalglieder 81, 82 und 83 wirkt, deren Ausgang zu den Regelventiler 52, 56 bzw. 77 führt. Die Proportionalglieder 81 bi: 83 wandeln das Eingangssignal x nach dem je weils auf ihnen dargestellten Diagramm in eir Ausgangssignal y um. Es ist leicht zu erkennen dass beim Ansteigen des Wertes x von 0 an zu nächst das erste Regelventil 52 etwa linear öffne und schliesslich in einen asymptotisch verlaufen den Bereich gelangt. Zu Beginn dieses Bereiche: beginnt dann das zweite Regelventil 56 etwa li. near zu öffnen. Sobald dieses Regelventil in sei. nen asymptotisch verlaufenden Bereich gelangt beginnt das dritte Regelventil 77 zu öffnen.In Figure 2, the water separator 20 and the three control valves 52, 56 and 77 are Darge again. On the separator 20, instead of the three level sensors 70, 71 and 78, however, only a single level sensor 80 is arranged, the output of which acts on three parallel elements 81, 82 and 83 connected in parallel, the output of which leads to the control valves 52, 56 and 77, respectively. The proportional elements 81 bi: 83 convert the input signal x into an output signal y according to the diagram shown on them. It is easy to see that when the value x increases from 0 to the next, the first control valve 52 opens approximately linearly and finally reaches an area that is asymptotic. At the beginning of this range: the second control valve 56 then begins approximately on the left. near to open. As soon as this control valve is in. When the asymptotic area arrives, the third control valve 77 begins to open.

Neben diesen beiden, in Fig. und in Fig. 2 dar gestellten Möglichkeiten der Beeinflussung dei Regelventile 52, 56, 77 sind noch verschiedene andere Möglichkeiten denkbar. Insbesondere isi es auch möglich, in der Schaltung nach Fig.2 zwischen dem Niveaugeber 80 und dem Verzwei gungspunkt der das Niveau-Signal x führender Leitung eine PI-Regler mit schwachem I-Anteil ein zuschalten, der den Schwankungsbereich des Ni veaus im Abscheider 20 verkleinert. Dabei werder zweckmässige Mittel vorgesehen, die das Aus gangssignal dieses PI-Reglers bei trocken gefahre nem Abscheider begrenzen.In addition to these two options in FIG. 2 and FIG. 2 for influencing the control valves 52, 56, 77, various other options are also conceivable. In particular, it is also possible to switch on a PI controller with a weak I component in the circuit according to FIG. 2 between the level transmitter 80 and the branching point of the line carrying the level signal x, which controls the fluctuation range of the level in the separator 20 downsized. Appropriate means are provided to limit the output signal of this PI controller when the separator is dry.

Anstatt die Regelventile 52, 56 und 77 parallel zu steuern, könnten sie auch in Kaskade gesteuert werden, indem die Stellung des ersten Regelventils 52 als Regelgrösse auf die Stellung des zweiten Regelventils 56 einwirkt, während dessen Stellung das dritte Regelventil 77 beeinflusst.Instead of controlling the control valves 52, 56 and 77 in parallel, they could also be controlled in cascade by the position of the first control valve 52 acting as a control variable on the position of the second control valve 56, during the position of which influences the third control valve 77.

Durch das Bestreben, die Sicherheitsabblaseeinrichtung 47 auf dem Speisewasserbehälter 1 zu verkleinern, wird das Risiko geschaffen, dass bei störungsbedingtem Öffnen des ersten Regelventils 52 bei Vollast und trockenem Abscheider 20 der Druck im Speisewasserbehälter 1 rasch ansteigt und der Speisewasserbehälter explodieren könnte. Um dieses Risiko angemessen zu verringern, kann das erste Regelventil 52 - oder ein dazu in Serie angeordnetes Absperrventil - durch einen Aggregatzustandgeber beeinflusst sein, der in der Wasseraustrittsleitung 50 angeordnet ist und das erste Regelventil oder gegebenenfalls das Absperrventil schliesst, wenn darin Dampf auftritt. Es kann auch, in Serie zum ersten Regelventil 52, ein statisch oder dynamisch wirkender Kondenstopf angeordnet sein, der nur Wasser, nicht aber Dampf durchströmen lässt. Schliesslich lässt sich auch, in Serie zum ersten Regelventil 52, ein sogenanntes negatives Sicherheitsventil anbringen, das vom Druck im Speisewasserbehälter 1 in schliessendem Sinne betätigt wird, sobald dieser Druck einen bestimmten Grenzwert übersteigt. Es kann auch zweckmässig sein, ausser der gemäss Anspruch 8 dimensionierten Sicherheitsabblaseeinrichtung eine Reissmembran anzuordnen, deren Querschnitt zusammen mit demjenigen der Abblaseeinrichtung 47 für den im genannten Störungsfall im Speisewasserbehälter entstehenden vollen Dampfstrom ausgelegt ist.The attempt to reduce the size of the safety blow-off device 47 on the feed water tank 1 creates the risk that, when the first control valve 52 is opened due to a fault, the pressure in the feed water tank 1 rises rapidly at full load and the dry separator 20 and the feed water tank could explode. In order to adequately reduce this risk, the first control valve 52 - or a shut-off valve arranged in series therewith - can be influenced by an aggregate state, which is arranged in the water outlet line 50 and closes the first control valve or, if appropriate, the shut-off valve when steam occurs therein. A static or dynamic condensing plug can also be arranged in series with the first control valve 52, which only allows water to flow through, but not steam. Finally, a so-called negative safety valve can also be installed in series with the first control valve 52, which is actuated in a closing sense by the pressure in the feed water tank 1 as soon as this pressure exceeds a certain limit value. It may also be expedient to arrange a tear membrane in addition to the safety blow-off device dimensioned according to claim 8, the cross-section of which is designed, together with that of the blow-off device 47, for the full steam flow occurring in the feed water tank in the event of a malfunction.

Claims (9)

1. A steam-raising plant having an evaporator (15) and, disposed thereafter, a water separator (20) whose water outlet line (50) returns to a feed water tank (1) by way of a heat exchanger (6), flowed through on the secondary side by feed water, and by way of a first control valve (52) responsive to the water content of the separator (20), a secondary line (55) branching off the separator outlet line (50) upstream of the first control valve (52) and extending to a condenser (35) and having a second valve (56) responsive to the water content of the water separator (20), characterised in the heat exchanger (6) ist disposed before the first control valve (52) as considered in the direction of water flow in the water outlet line (50) an means (70, 72; 71, 73) for acting on the two control valves (52; 56) in dependence upon the water content of the water separator (20) are provided, of a kind such that when the level in the separator (20) rises, first the first control valve (52) and then the second control valve (56) open, whereas when such level drops, first the second control valve (56), then the first control valve (52), close.
2. A plant according to claim 1, characterised in that the secondary line (55) branches off the water separator outlet line (50) downstream of the heat exchanger (6).
3. A plant according to claim 1 or 2, characterised in that the first control valve (52) is of small dimensions such as to be able to pass, with the steam producer (11) on minimum load and in the fully open state, at most 125% of the water then accumulating in the water separator (20) but as to be unable to pass the total quantity of water accumulating at start-up of the steam producer.
4. A plant according to any of claims 1 to 3, characterised in that an additional water discharge line (76) extends from the water separator (20), bypassing the heat exchanger (6) and extending by way of a third control valve (77), to the condenser (35) and is so actuated by a controller (79) as to open in dependence upon the water content of the separator (20) only when the other two control valves (52, 56) are open and as to close before the other two control valves (52, 56) have closed.
5. A plant according to any of claims 1 to 4, characterised in that the secondary line (55) and possibly the additional water discharge line (76) extend to the condenser (35) by way of a steam trap (57).
6. A plant according to any of claims 1 to 5, characterised in that a level indicator (80) is disposed on the separator (20) and its output is connected by way of two and possibly three differently adjusted proportional elements (81, 82, 83 respectively) to the first and second control valve (52, 56) and to the third control valve (77) respectively.
7. A plant according to any of claims 1 to 6, characterised in that the feed water tank (1) has a blow-off valve (47) so devised that the low- pressure wet steam which is produced on full-load operation of the steam producer (11) in the event of incorrect opening of the first control valve (52) is blown off without an excessive increase ii pressure.
8. A plant according to any of claims 1 to E characterised in that the first control valve (52) i also so acted on by a sender determining the overall state before the latter valve as to pas water but not steam; and the feed water tank (1 has a blow-off device via which the steam evolvei in the feed water tank from the return water oi expansion is blown off without an excessive pressure increase.
9. A plant according to claim 8, characterised ii that the sender determining the overall state is condensate separator which precedes the firs control valve (52).
EP79200749A 1978-12-22 1979-12-11 Steam-generation plant Expired EP0013045B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1309678A CH635184A5 (en) 1978-12-22 1978-12-22 STEAM GENERATOR SYSTEM.
CH13096/78 1978-12-22

Publications (2)

Publication Number Publication Date
EP0013045A1 EP0013045A1 (en) 1980-07-09
EP0013045B1 true EP0013045B1 (en) 1984-03-07

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US (1) US4290390A (en)
EP (1) EP0013045B1 (en)
JP (1) JPS5589604A (en)
AU (1) AU531456B2 (en)
CA (1) CA1129277A (en)
CH (1) CH635184A5 (en)
DE (1) DE2966769D1 (en)
FI (1) FI67753C (en)
PL (1) PL219838A1 (en)
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CA1129277A (en) 1982-08-10
AU531456B2 (en) 1983-08-25
FI67753B (en) 1985-01-31
PL219838A1 (en) 1980-09-08
CH635184A5 (en) 1983-03-15
FI793736A (en) 1980-06-23
US4290390A (en) 1981-09-22
JPS6136121B2 (en) 1986-08-16
DE2966769D1 (en) 1984-04-12
JPS5589604A (en) 1980-07-07
YU301179A (en) 1982-10-31
EP0013045A1 (en) 1980-07-09
AU5400379A (en) 1980-06-26
FI67753C (en) 1985-05-10

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