EP0546315A1 - Steam condenser - Google Patents

Steam condenser Download PDF

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Publication number
EP0546315A1
EP0546315A1 EP92118798A EP92118798A EP0546315A1 EP 0546315 A1 EP0546315 A1 EP 0546315A1 EP 92118798 A EP92118798 A EP 92118798A EP 92118798 A EP92118798 A EP 92118798A EP 0546315 A1 EP0546315 A1 EP 0546315A1
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EP
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Prior art keywords
cooler
tubes
cooling water
steam condenser
steam
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EP92118798A
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German (de)
French (fr)
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EP0546315B1 (en
Inventor
Jerg Dipl.-Ing. Scheurlen
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Balcke Duerr GmbH
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PreussenElektra AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium

Definitions

  • the invention relates to a steam condenser with at least one tube bundle through which cooling water flows, the tubes of which are fastened at their ends in tube sheets and are supported along their length by a plurality of supporting walls, with annular gaps between the tubular jacket surface and the inner wall of the bore in the passage of the tubes through the supporting walls result in the support wall, and to which a cooler for the non-condensable gases is assigned, the tubes of which are separated from the tubes above by at least one cover, the non-condensable gases, in particular air, being sucked out of the space formed by the cover.
  • a steam condenser of the type described above is known for example from EP-A 325 758.
  • the non-condensable gases are sucked out of the cooler over the entire length of the cooler.
  • the pressure at the end of the flow path in the condenser is higher on the cooling water outlet side than on the cooling water inlet side, because there the temperature difference between steam and cooling water is smaller, i.e. less steam flows and condenses and therefore the pressure losses are smaller.
  • the difference between the pressure in the respective field of the condenser and the pressure in the suction line on the cooling water outlet side is greater than on the inlet side.
  • the non-condensable gases are therefore primarily extracted from the fields of the condenser on the cooling water outlet side, although fewer non-condensable gases are produced here due to the lower condensation output.
  • the invention has for its object to develop a steam condenser of the type described in such a way that the extraction of the non-condensable gases from the condenser cooler is improved without great technical effort.
  • the solution to this problem by the invention is characterized in that the suction of the non-condensable gases from the space formed by the cover of the cooler takes place only in the vicinity of the tube sheet on the cooling water inlet side.
  • the non-condensable gases are led to the coldest point of the cooler, namely in the vicinity of the cooling water inlet, before being sucked off by flow along the cooler tubes, so that the greatest possible mixture subcooling takes place here, due to the residual condensation of the steam component Reduction of the proportion of the extracted vapor in relation to the total amount extracted and thus leads to a large proportion of non-condensable gases.
  • the total power to be installed for the extraction can be reduced as a result, and the condenser is also less sensitive to possible air ingress than the known construction.
  • the annular gaps between the inner wall of the bores provided in the support walls and the lateral surface of the tubes of the cooler which are passed through these bores can be made larger in the suction area of the cooler than in the remaining area of the cooler and the condenser. In this way, the flow of the non-condensable gases along the tubes in the region of the cooler achieved by the invention is taken into account.
  • the area of the annular gaps in the area of the cooler can increase from the support walls on the cooling water outlet side to the support walls on the cooling water inlet side. This takes into account that the volume of the non-condensable gases flowing in the direction of the tube sheet on the cooling water inlet side increases.
  • the area of the annular gaps can be increased either by increasing the size of the annular gaps or by increasing the number of enlarged annular gaps per supporting wall in the support walls facing the tube plate on the cooling water inlet side.
  • the invention further proposes to arrange an additional supporting wall for part of the cooler tubes in the region of the mouth of the suction line. This additional supporting wall prevents transverse vibrations of the pipes in the mouth area of the suction line, especially when the condenser begins to be evacuated, in which relatively large amounts of air are drawn out of the condenser through the suction line.
  • the invention proposes to arrange in the area of the mouth of the suction line a baffle that runs parallel to the cooler tubes and extends over part of the length of the cooler tubes and is attached to the cover.
  • This baffle forms a kind of baffle for the steam-gas mixture coming from this first field and also prevents excessive steam from being sucked out of the first field of the cooler despite the condensate in this area tors greatest suction.
  • a cross flow of the gases to be extracted is forced through the baffle in the extraction area of the cooler.
  • a steam condenser shown in Fig. 1 shows a tube bundle indicated by dash-dotted hatched areas, which - possibly together with other tube bundles - is arranged in a condenser housing, not shown in the drawing, and steam is applied to it from above, which comes from the exhaust pipe Steam turbine comes and is to be condensed in the condenser.
  • So-called steam passages are formed in order to achieve a homogeneous steam flow and the most uniform possible application of the steam condenser tubes forming the tube bundle, so that a cross-section of the tube bundle results, as can be seen in FIG. 1.
  • the tube bundle forms two bundle halves 1a and 1b which are arranged symmetrically to a vertical central axis and which are triangular in cross section and which are arranged above a further bundle section 1c.
  • 1 condensate drain plates 2 are arranged between the bundle halves 1 a and 1 b and the bundle section.
  • a cooler 3 is provided centrally between the bundle halves 1 and 1 and the bundle section 1c, from which the non-condensable gases, in particular air, are sucked out of the steam condenser.
  • the cooler area of the steam condenser is shown enlarged in FIGS. 2 to 5.
  • FIGS. 4 and 5 show that the cooler 3, like the tube bundle of the steam condenser formed by the bundle halves 1 and 1 and by the bundle section 1 c, is formed by tubes 4, which are fastened at their ends in tube plates 5a, 5b without gaps.
  • tube plates 5a, 5b can be seen in section in FIG. 3.
  • Fig. 3 further shows that the tubes 4 are supported along their length by a plurality of support walls 6, wherein when the tubes 4 pass through these support walls 6, due to the design, annular gaps 10 between the outer surface of the tubes 4 and the respective support wall 6 provided with holes surrender.
  • the annular gaps 10 are drawn exaggeratedly large in FIGS. 4 and 5. They normally have a width of 0.1 to 0.2 mm, the enlarged gaps approx. 0.5 to 1 mm.
  • the tubes 4 of the cooler 3 are separated from the overlying tubes of the bundle halves 1 and 1 by a cover 7 which prevents steam to be condensed and condensate dripping from the tubes of the bundle halves 1 and 1b Enter the cooler 3 from above.
  • This cover 7 is also shown in FIG. 3.
  • the steam to be condensed coming from the exhaust pipe of a turbine, is introduced into the steam condenser from above. Accordingly, coming from above, it acts on the tubes of the tube bundle divided into the bundle halves 1a and 1 and in the bundle section 1c, the tubes 4 of which are flowed through by cooling water.
  • the flow of cooling water K through the pipes 4 is indicated in FIG. 3 by the horizontal arrow.
  • the steam is deposited on the pipes 4 through which cooling water flows.
  • the condensate flows down or drips down and in this way reaches either the condensate drain plates 2 or the bottom of the condenser housing, not shown, so that it can be returned to the water-steam cycle.
  • the steam supplied to the condenser is non-condensable gases, especially air, frequently volatile alkalizing agents (e.g. ammonia), small amounts of noble gas and possibly Containing hydrogen is ensured by arranging the cooler 3 that these are sucked out of the steam condenser in order to avoid an accumulation of these non-condensable gases in the condenser and thus a deterioration in the efficiency of the condenser. Care must be taken to ensure that as little steam as possible is sucked out of the steam condenser with the suction of the non-condensable gases in order to avoid steam losses.
  • non-condensable gases especially air, frequently volatile alkalizing agents (e.g. ammonia)
  • the non-condensable gases are extracted at a central location in the steam condenser, which is protected by the cover 7 against direct exposure to steam to be condensed.
  • the proportion of steam during suction from the cooler 3 and thus the inevitable loss of steam is reduced.
  • the non-condensable gases are extracted from the space of the cooler 3 formed by the cover 7 only in the vicinity of the tube sheet 5a on the cooling water inlet side, i.e. in the area of the tube plate 5a visible on the left in FIG. 3.
  • a suction connection 8 can be seen in the immediate vicinity of this tube sheet 5a, to which a suction line 9 is connected according to FIG. 1.
  • This arrangement of the suction on the inlet side of the cooling water leads the non-condensable gases to the coldest point of the cooler 3 prior to their suction by flow along the pipes 4.
  • annular gaps 10 are between the inner wall of the holes provided in the support walls 6 and the lateral surface of the tubes 4 of the cooler 3 passed through these holes in the suction area of the Cooler 3 is larger than in the rest of the cooler.
  • FIGS. 4 and 5 show that the annular gap 10a formed between the tubes 4 and the support wall 6 adjacent to the suction port 8 is larger than the corresponding annular gap 10b in the support wall 6, which is adjacent to the tube sheet 5b.
  • either the size of the annular gaps 10 with the same number of annular gaps 10 per support wall 6 from the support walls 6 on the cooling water outlet side to the support walls 6 on the cooling water inlet side can be used increase or the number of enlarged annular gaps 10 per support wall 6 increases from the support walls 6 on the cooling water outlet side to the support walls 6 on the cooling water inlet side.
  • an additional supporting wall 11 can be arranged, which is shown in FIG. 3 is drawn.
  • a baffle 12 which runs parallel to the tubes 4 of the cooler 3 and which forms a type of baffle for the steam-gas mixture coming from this first field of the cooler 3.
  • the normal flow direction of the steam D and the non-condensable gases G within the cooler 3 is indicated by arrows in FIG. 3.

Abstract

The invention relates to a steam condenser having at least one tube bundle through which cooling water flows and whose tubes (4) are fixed at their ends in tube plates (5a, 5b) and are supported on their length by a plurality of supporting walls (6). The design causes annular gaps (10) where the tubes (4) penetrate the supporting walls (6). Furthermore, there is arranged in the steam condenser a cooler (3) for the noncondensible gases, whose tubes (4) are separated by at least one cover (7) from the tubes of the condenser which are situated thereabove. The noncondensible gases are sucked out of the space in the cooler (3) which is formed by the cover (7) exclusively in the vicinity of the tube plate (5a) on the side of the cooling water inlet. <IMAGE>

Description

Die Erfindung betrifft einen Dampfkondensator mit mindestens einem kühlwasserdurchströmten Rohrbündel, dessen Rohre an ihren Enden in Rohrböden befestigt und auf ihrer Länge durch mehrere Stützwände unterstützt sind, wobei sich bei der Durchführung der Rohre durch die Stützwände konstruktionsbedingt Ringspalte zwischen der Rohrmantelfläche und der Innenwand der Bohrung in der Stützwand ergeben, und dem ein Kühler für die nicht kondensierbaren Gase zugeordnet ist, dessen Rohre durch mindestens eine Abdeckung von den darüberliegenden Rohren getrennt sind, wobei die nicht kondensierbaren Gase, insbesondere Luft, aus dem durch die Abdeckung gebildeten Raum abgesaugt werden.The invention relates to a steam condenser with at least one tube bundle through which cooling water flows, the tubes of which are fastened at their ends in tube sheets and are supported along their length by a plurality of supporting walls, with annular gaps between the tubular jacket surface and the inner wall of the bore in the passage of the tubes through the supporting walls result in the support wall, and to which a cooler for the non-condensable gases is assigned, the tubes of which are separated from the tubes above by at least one cover, the non-condensable gases, in particular air, being sucked out of the space formed by the cover.

Ein Dampfkondensator der voranstehend beschriebenen Art ist beispielsweise aus der EP-A 325 758 bekannt. Bei dieser bekannten Konstruktion werden die nicht kondensierbaren Gase über die gesamte Länge des Kühlers aus dem Kühler abgesaugt. Der Druck am Ende des Strömungsweges im Kondensator ist jedoch auf der Kühlwasseraustrittsseite höher als auf der Kühlwassereintrittsseite, weil dort die Temperaturdifferenz zwischen Dampf und Kühlwasser kleiner ist, also weniger Dampf strömt und kondensiert und deshalb die Druckverluste kleiner sind. Dadurch ist die Differenz zwischen dem Druck im jeweiligen Feld des Kondensators und dem Druck in der Saugleitung auf der Kühlwasseraustrittsseite größer als auf der Eintrittsseite. Bei dem bekannten Dampfkondensator werden deshalb die nicht kondensierbaren Gase primär aus den kühlwasseraustrittsseitigen Feldern des Kondensators abgesaugt, obwohl hier wegen der geringeren Kondensationsleistung weniger nicht kondensierbare Gase anfallen. Dies führt bei der bekannten Konstruktion zu dem Nachteil, daß bei einer knappen Auslegung des Kondensators und bei unerwarteten Lufteinbrüchen in den Kondensator ein Stau von nicht kondensierbaren Gasen im leistungsfähigsten Teil des Kondensators auftritt; dieser Stau von nicht kondensierbaren Gasen ist in diesem Teil des Kondensators besonders störend und führt deshalb zu einer besonders starken Verschlechterung des Kondensator-Wirkungsgrades.A steam condenser of the type described above is known for example from EP-A 325 758. In this known construction, the non-condensable gases are sucked out of the cooler over the entire length of the cooler. However, the pressure at the end of the flow path in the condenser is higher on the cooling water outlet side than on the cooling water inlet side, because there the temperature difference between steam and cooling water is smaller, i.e. less steam flows and condenses and therefore the pressure losses are smaller. As a result, the difference between the pressure in the respective field of the condenser and the pressure in the suction line on the cooling water outlet side is greater than on the inlet side. In the known steam condenser, the non-condensable gases are therefore primarily extracted from the fields of the condenser on the cooling water outlet side, although fewer non-condensable gases are produced here due to the lower condensation output. In the known construction, this leads to the disadvantage that, in the case of a short design of the capacitor and in the event of unexpected air ingress into the capacitor, a jam of non-condensable gases occurs in the most powerful part of the capacitor; this accumulation of non-condensable gases is particularly disturbing in this part of the capacitor and therefore leads to a particularly severe deterioration in the efficiency of the capacitor.

Der Erfindung liegt die Aufgabe zugrunde, einen Dampfkondensator der eingangs beschriebenen Art derart weiterzubilden, daß die Absaugung der nicht kondensierbaren Gase aus dem Kühler des Kondensators ohne großen technischen Aufwand verbessert wird.The invention has for its object to develop a steam condenser of the type described in such a way that the extraction of the non-condensable gases from the condenser cooler is improved without great technical effort.

Die Lösung dieser Aufgabenstellung durch die Erfindung ist dadurch gekennzeichnet, daß die Absaugung der nicht kondensierbaren Gase aus dem durch die Abdeckung gebildeten Raum des Kühlers ausschließlich in der Nähe des kühlwassereintrittsseitigen Rohrbodens erfolgt.The solution to this problem by the invention is characterized in that the suction of the non-condensable gases from the space formed by the cover of the cooler takes place only in the vicinity of the tube sheet on the cooling water inlet side.

Durch diese erfindungsgemäße Absaugung werden die nicht kondensierbaren Gase vor ihrer Absaugung durch Strömung längs der Kühlerrohre an die kälteste Stelle des Kühlers, nämlich in die Nähe des Kühlwassereintritts geführt, so daß hier die größtmögliche Gemisch-Unterkühlung stattfindet, die durch die Restkondensation des Dampfanteils zu einer Verringerung des Anteils des abgesaugten Dampfes im Verhältnis zur abgesaugten Gesamtmenge und damit zu einem großen Anteil nicht kondensierbarer Gase führt. Als Ergebnis kann hierdurch die insgesamt zu installierende Leistung für die Absaugung reduziert werden, außerdem ist der Kondensator gegenüber eventuellen Lufteinbrüchen unempfindlicher als die bekannte Konstruktion.By means of this suction according to the invention, the non-condensable gases are led to the coldest point of the cooler, namely in the vicinity of the cooling water inlet, before being sucked off by flow along the cooler tubes, so that the greatest possible mixture subcooling takes place here, due to the residual condensation of the steam component Reduction of the proportion of the extracted vapor in relation to the total amount extracted and thus leads to a large proportion of non-condensable gases. As a result, the total power to be installed for the extraction can be reduced as a result, and the condenser is also less sensitive to possible air ingress than the known construction.

Gemäß einem weiteren Merkmal der Erfindung können die Ringspalte zwischen der Innenwand der in den Stützwänden vorgesehenen Bohrungen und der Mantelfläche der durch diese Bohrungen hindurchgeführten Rohre des Kühlers im Absaugebereich des Kühlers größer ausgeführt sein als im restlichen Bereich des Kühlers und des Kondensators. Hierdurch wird der mit der Erfindung erzielten Strömung der nicht kondensierbaren Gase längs der Rohre im Bereich des Kühlers Rechnung getragen. In Weiterbildung der Erfindung kann die Fläche der Ringspalte im Bereich des Kühlers von den kühlwasseraustrittsseitigen Stützwänden zu den kühlwassereintrittsseitigen Stützwänden zunehmen. Hierdurch wird berücksichtigt, daß das Volumen der in Richtung auf den kühlwassereintrittsseitigen Rohrboden strömenden, nicht kondensierbaren Gase zunimmt. Die Fläche der Ringspalte kann hierbei dadurch vergrößert werden, daß entweder die Größe der Ringspalte zunimmt oder daß in den zum kühlwassereintrittsseitigen Rohrboden hin liegenden Stützwänden die Anzahl der vergrößerten Ringspalte pro Stützwand zunimmt. Mit der Erfindung wird weiterhin vorgeschlagen, im Bereich der Mündung der Absaugleitung eine zusätzliche Stützwand für einen Teil der Kühlerrohre anzuordnen. Diese zusätzliche Stützwand verhindert Querschwingungen der Rohre im Mündungsbereich der Absaugleitung, insbesondere bei einem Beginn der Evakuierung des Kondensators, bei dem verhältnismäßig große Luftmengen aus dem Kondensator durch die Absaugleitung abgezogen werden.According to a further feature of the invention, the annular gaps between the inner wall of the bores provided in the support walls and the lateral surface of the tubes of the cooler which are passed through these bores can be made larger in the suction area of the cooler than in the remaining area of the cooler and the condenser. In this way, the flow of the non-condensable gases along the tubes in the region of the cooler achieved by the invention is taken into account. In a further development of the invention, the area of the annular gaps in the area of the cooler can increase from the support walls on the cooling water outlet side to the support walls on the cooling water inlet side. This takes into account that the volume of the non-condensable gases flowing in the direction of the tube sheet on the cooling water inlet side increases. The area of the annular gaps can be increased either by increasing the size of the annular gaps or by increasing the number of enlarged annular gaps per supporting wall in the support walls facing the tube plate on the cooling water inlet side. The invention further proposes to arrange an additional supporting wall for part of the cooler tubes in the region of the mouth of the suction line. This additional supporting wall prevents transverse vibrations of the pipes in the mouth area of the suction line, especially when the condenser begins to be evacuated, in which relatively large amounts of air are drawn out of the condenser through the suction line.

Mit der Erfindung wird schließlich vorgeschlagen, im Bereich der Mündung der Absaugleitung ein parallel zu den Kühlerrohren und über einen Teil der Länge der Kühlerrohre verlaufendes Leitblech anzuordnen, das an der Abdeckung befestigt ist. Dieses Leitblech bildet eine Art Schikane für das aus diesem ersten Feld kommende Dampf-Gasgemisch und verhindert weiterhin das Absaugen von zuviel Dampf aus dem ersten Feld des Kühlers trotz der in diesem Bereich des Kondensators größten Saugwirkung. In Verbindung mit der zusätzlichen Stützwand wird durch das Leitblech eine Querströmung der abzusaugenden Gase im Absaugbereich des Kühlers erzwungen.Finally, the invention proposes to arrange in the area of the mouth of the suction line a baffle that runs parallel to the cooler tubes and extends over part of the length of the cooler tubes and is attached to the cover. This baffle forms a kind of baffle for the steam-gas mixture coming from this first field and also prevents excessive steam from being sucked out of the first field of the cooler despite the condensate in this area tors greatest suction. In conjunction with the additional support wall, a cross flow of the gases to be extracted is forced through the baffle in the extraction area of the cooler.

Auf der Zeichnung ist ein Ausführungsbeispiel des erfindungsgemäßen Dampfkondensators dargestellt, und zwar zeigen:

  • Fig. 1 einen schematischen Querschnitt durch einen Teil eines Dampfkondensators,
  • Fig. 2 einen vergrößert dargestellten Ausschnitt aus Fig. 1 im Bereich des Kühlers,
  • Fig. 3 einen Schnitt durch den Kühler gemäß der Schnittlinie III - III in Fig. 2,
  • Fig. 4 ein vergrößert dargestelltes Detail entsprechend dem Kreis IV in Fig. 3 und
  • Fig. 5 ein weiteres Detail entsprechend dem Kreis V in Fig. 3.
An exemplary embodiment of the steam condenser according to the invention is shown in the drawing, namely:
  • 1 shows a schematic cross section through part of a steam condenser,
  • 2 shows an enlarged detail from FIG. 1 in the area of the cooler,
  • 3 shows a section through the cooler according to section line III-III in FIG. 2,
  • Fig. 4 is an enlarged detail corresponding to the circle IV in Fig. 3 and
  • 5 shows a further detail corresponding to the circle V in FIG. 3.

Der in Fig. 1 dargestellte Teil eines Dampfkondensators zeigt ein durch strichpunktiert schraffierte Flächen angedeutetes Rohrbündel, das - ggf. gemeinsam mit weiteren Rohrbündeln - in einem auf der Zeichnung nicht dargestellten Kondensatorgehäuse angeordnet ist und von oben her mit Dampf beaufschlagt wird, der vom Abdampfstutzen einer Dampfturbine kommt und im Kondensator kondensiert werden soll. Um eine homogene Dampfströmung und eine möglichst gleichmäßige Beaufschlagung der das Rohrbündel bildenden Rohre des Dampfkondensators zu erzielen, werden sogenannte Dampfgassen gebildet, so daß sich ein Querschnitt des Rohrbündels ergibt, wie er in Fig. 1 zu erkennen ist.The part of a steam condenser shown in Fig. 1 shows a tube bundle indicated by dash-dotted hatched areas, which - possibly together with other tube bundles - is arranged in a condenser housing, not shown in the drawing, and steam is applied to it from above, which comes from the exhaust pipe Steam turbine comes and is to be condensed in the condenser. So-called steam passages are formed in order to achieve a homogeneous steam flow and the most uniform possible application of the steam condenser tubes forming the tube bundle, so that a cross-section of the tube bundle results, as can be seen in FIG. 1.

Entsprechend dieser Darstellung bildet das Rohrbündel zwei symmetrisch zu einer senkrechten Mittelachse angeordnete, im Querschnitt dreieckförmige Bündelhälften 1a und 1b, die oberhalb eines weiteren Bündelabschnittes 1c angeordnet sind. Beim Ausführungsbeispiel sind zwischen den Bündelhälften 1a bzw. 1b und dem Bündelabschnitt 1 Kondensatableitbleche 2 angeordnet. Mittig zwischen den Bündelhälften 1 und 1 und dem Bündelabschnitt 1c ist ein Kühler 3 vorgesehen, aus dem die nicht kondensierbaren Gase, insbesondere Luft aus dem Dampfkondensator abgesaugt werden. Der Kühlerbereich des Dampfkondensators ist vergrößert in den Fig. 2 bis 5 dargestellt.According to this illustration, the tube bundle forms two bundle halves 1a and 1b which are arranged symmetrically to a vertical central axis and which are triangular in cross section and which are arranged above a further bundle section 1c. In the exemplary embodiment, 1 condensate drain plates 2 are arranged between the bundle halves 1 a and 1 b and the bundle section. A cooler 3 is provided centrally between the bundle halves 1 and 1 and the bundle section 1c, from which the non-condensable gases, in particular air, are sucked out of the steam condenser. The cooler area of the steam condenser is shown enlarged in FIGS. 2 to 5.

Diese Darstellungen lassen erkennen, daß der Kühler 3 ebenso wie das durch die Bündelhälften 1 und 1 sowie durch den Bündelabschnitt 1 c gebildete Rohrbündel des Dampfkondensators durch Rohre 4 gebildet wird, die an ihren Enden in Rohrböden 5a,5b spaltfrei befestigt sind. Diese Rohrböden 5a,5b sind im Schnitt in Fig. 3 zu erkennen. Die Fig. 3 zeigt weiterhin, daß die Rohre 4 auf ihrer Länge durch mehrere Stützwände 6 unterstützt sind, wobei sich bei der Durchführung der Rohre 4 durch diese Stützwände 6 konstruktionsbedingt Ringspalte 10 zwischen der Mantelfläche der Rohre 4 und der mit Bohrungen versehenen jeweiligen Stützwand 6 ergeben. Die Ringspalte 10 sind in Fig. 4 und 5 übertrieben groß gezeichnet. Sie haben normal eine Breite von 0,1 bis 0,2 mm, die vergrößerten Spalte ca. 0,5 bis 1 mm.These representations show that the cooler 3, like the tube bundle of the steam condenser formed by the bundle halves 1 and 1 and by the bundle section 1 c, is formed by tubes 4, which are fastened at their ends in tube plates 5a, 5b without gaps. These tube plates 5a, 5b can be seen in section in FIG. 3. Fig. 3 further shows that the tubes 4 are supported along their length by a plurality of support walls 6, wherein when the tubes 4 pass through these support walls 6, due to the design, annular gaps 10 between the outer surface of the tubes 4 and the respective support wall 6 provided with holes surrender. The annular gaps 10 are drawn exaggeratedly large in FIGS. 4 and 5. They normally have a width of 0.1 to 0.2 mm, the enlarged gaps approx. 0.5 to 1 mm.

Wie insbesondere aus Fig. 2 hervorgeht, sind die Rohre 4 des Kühlers 3 von den darüberliegenden Rohren der Bündelhälften 1 und 1 durch eine Abdeckung 7 getrennt, welche verhindert, daß zu kondensierender Dampf und von den Rohren der Bündelhälften 1 und 1 b abtropfendes Kondensat von oben her in den Kühler 3 eintreten. Diese Abdeckung 7 ist auch in Fig. 3 eingezeichnet.As can be seen in particular from Fig. 2, the tubes 4 of the cooler 3 are separated from the overlying tubes of the bundle halves 1 and 1 by a cover 7 which prevents steam to be condensed and condensate dripping from the tubes of the bundle halves 1 and 1b Enter the cooler 3 from above. This cover 7 is also shown in FIG. 3.

Der zu kondensierende, aus dem Abdampfstutzen einer Turbine kommende Dampf wird von oben her in den Dampfkondensator eingeführt. Er beaufschlagt demzufolge von oben kommend die Rohre des in die Bündelhälften 1a und 1 sowie in den Bündelabschnitt 1c aufgeteilten Rohrbündels, dessen Rohre 4 von Kühlwasser durchströmt sind. Die Durchströmung der Rohre 4 mit Kühlwasser K ist in Fig. 3 durch den waagerechten Pfeil angedeutet. Infolge der Temperaturdifferenz schlägt sich der Dampf an den kühlwasserdurchflossenen Rohren 4 nieder. Das Kondensat fließt bzw. tropft nach unten ab und gelangt auf diese Weise entweder auf die Kondensatableitbleche 2 oder auf den Boden des nicht dargestellten Kondensatorgehäuses, so daß es in den Wasser-Dampf-Kreislauf zurückgeführt werden kann.The steam to be condensed, coming from the exhaust pipe of a turbine, is introduced into the steam condenser from above. Accordingly, coming from above, it acts on the tubes of the tube bundle divided into the bundle halves 1a and 1 and in the bundle section 1c, the tubes 4 of which are flowed through by cooling water. The flow of cooling water K through the pipes 4 is indicated in FIG. 3 by the horizontal arrow. As a result of the temperature difference, the steam is deposited on the pipes 4 through which cooling water flows. The condensate flows down or drips down and in this way reaches either the condensate drain plates 2 or the bottom of the condenser housing, not shown, so that it can be returned to the water-steam cycle.

Da der dem Kondensator zugeführte Dampf nicht kondensierbare Gase, insbesondere Luft, häufig flüchtige Alkalisierungsmittel (z.B. Ammoniak), geringe Mengen Edelgas und u.U. Wasserstoff enthält, wird durch Anordnung des Kühlers 3 dafür gesorgt, daß diese aus dem Dampfkondensator abgesaugt werden, um eine Ansammlung dieser nicht kondensierbaren Gase im Kondensator und damit eine Wirkungsgradverschlechterung des Kondensators zu vermeiden. Hierbei muß darauf geachtet werden, daß mit der Absaugung der nicht kondensierbaren Gase möglichst wenig Dampf aus dem Dampfkondensator abgesaugt wird, um Dampfverluste zu vermeiden.Since the steam supplied to the condenser is non-condensable gases, especially air, frequently volatile alkalizing agents (e.g. ammonia), small amounts of noble gas and possibly Containing hydrogen is ensured by arranging the cooler 3 that these are sucked out of the steam condenser in order to avoid an accumulation of these non-condensable gases in the condenser and thus a deterioration in the efficiency of the condenser. Care must be taken to ensure that as little steam as possible is sucked out of the steam condenser with the suction of the non-condensable gases in order to avoid steam losses.

Zu diesem Zweck erfolgt die Absaugung der nicht kondensierbaren Gase an einer möglichst zentralen Stelle im Dampfkondensator, die durch die Abdeckung 7 vor einer direkten Beaufschlagung mit zu kondensierendem Dampf geschützt ist. Die unterhalb dieser Abdeckung 7 angeordneten, ebenfalls von Kühlwasser durchströmten Rohre 4 bewirken durch ihre Kühlwirkung eine Unterkühlung des insbesondere von unten und von der Seite her in den Kühler 3 eintretenden Dampf-Gas-Gemisches, so daß auch im Bereich des Kühlers 3 eine Kondensierung des Dampfes erfolgt. Hierdurch wird der Dampfanteil bei der Absaugung aus dem Kühler 3 und damit der unvermeidbare Dampfverlust herabgesetzt.For this purpose, the non-condensable gases are extracted at a central location in the steam condenser, which is protected by the cover 7 against direct exposure to steam to be condensed. The arranged below this cover 7, also flowed through by cooling water pipes 4 cause by their cooling effect subcooling the steam-gas mixture entering the cooler 3, in particular from below and from the side, so that also in the area of the cooler 3 Condensation of the steam takes place. As a result, the proportion of steam during suction from the cooler 3 and thus the inevitable loss of steam is reduced.

Um diesen Dampfverlust weiter zu reduzieren, erfolgt bei dem voranstehend beschriebenen Dampfkondensator die Absaugung der nicht kondensierbaren Gase aus dem durch die Abdeckung 7 gebildeten Raum des Kühlers 3 ausschließlich in der Nähe des kühlwassereintrittsseitigen Rohrbodens 5a, d.h. im Bereich des in Fig. 3 links erkennbaren Rohrbodens 5a. Beim Ausführungsbeispiel ist in unmittelbarer Nähe dieses Rohrbodens 5a ein Absaugstutzen 8 zu erkennen, an den gemäß Fig. 1 eine Absaugleitung 9 angeschlossen ist. Durch diese Anordnung der Absaugung an der Eintrittsseite des Kühlwasser werden die nicht kondensierbaren Gase vor ihrer Absaugung durch Strömung längs der Rohre 4 an die kälteste Stelle des Kühlers 3 geführt. Da hier die größtmögliche Unterkühlung des Gas-Dampf-Gemisches stattfindet, ergibt sich eine größtmögliche Restkondensation des Dampfanteils und damit eine erhebliche Verringerung des Anteils des durch die Absaugleitung 9 abgesaugten Dampfes im Verhältnis zur abgesaugten Gesamtmenge. Hierdurch wird nicht nur der Dampfverlust reduziert; es kann auch die insgesamt zu installierende Leistung für die Absaugung infolge der Herabsetzung der abgesaugten Dampfmenge reduziert werden. Außerdem wird der Dampfkondensator unempfindlicher gegenüber größeren Lufteinbrüchen.In order to further reduce this steam loss, in the steam condenser described above, the non-condensable gases are extracted from the space of the cooler 3 formed by the cover 7 only in the vicinity of the tube sheet 5a on the cooling water inlet side, i.e. in the area of the tube plate 5a visible on the left in FIG. 3. In the exemplary embodiment, a suction connection 8 can be seen in the immediate vicinity of this tube sheet 5a, to which a suction line 9 is connected according to FIG. 1. This arrangement of the suction on the inlet side of the cooling water leads the non-condensable gases to the coldest point of the cooler 3 prior to their suction by flow along the pipes 4. Since the greatest possible subcooling of the gas-steam mixture takes place here, there is the greatest possible residual condensation of the steam portion and thus a considerable reduction in the portion of the vapor extracted through the suction line 9 in relation to the total amount extracted. This not only reduces steam loss; it is also possible to reduce the total power to be installed for the extraction as a result of the reduction in the quantity of steam extracted. In addition, the steam condenser is less sensitive to larger air ingress.

Um der Strömung der nicht kondensierbaren Gase längs der Rohre 4 im Bereich des Kühlers 3 Rechnung zu tragen, sind die Ringspalte 10 zwischen der Innenwand der in den Stützwänden 6 vorgesehenen Bohrungen und der Mantelfläche der durch diese Bohrungen hindurchgeführten Rohre 4 des Kühlers 3 im Absaugbereich des Kühlers 3 größer ausgeführt als im restlichen Bereich des Kühlers. Diese Situation ist durch die Detaildarstellungen in den Fig. 4 und 5 verdeutlicht. Diese zeigen, daß der zwischen den Rohren 4 und der dem Absaugstutzen 8 benachbarten Stützwand 6 ausgebildete Ringspalt 10a größer ist als der entsprechende Ringspalt 10b in der Stützwand 6, die dem Rohrboden 5b benachbart ist.In order to take into account the flow of the non-condensable gases along the tubes 4 in the area of the cooler 3, the annular gaps 10 are between the inner wall of the holes provided in the support walls 6 and the lateral surface of the tubes 4 of the cooler 3 passed through these holes in the suction area of the Cooler 3 is larger than in the rest of the cooler. This situation is illustrated by the detailed representations in FIGS. 4 and 5. These show that the annular gap 10a formed between the tubes 4 and the support wall 6 adjacent to the suction port 8 is larger than the corresponding annular gap 10b in the support wall 6, which is adjacent to the tube sheet 5b.

Um die Fläche der Ringspalte 10 im Bereich des Kühlers 3 von den kühlwasseraustrittsseitigen Stützwänden 6 zu den kühlwassereintrittsseitigen Stützwänden 6 zu vergrößern, kann entweder die Größe der Ringspalte 10 bei gleicher Anzahl von Ringspalten 10 pro Stützwand 6 von den kühlwasseraustrittsseitigen Stützwänden 6 zu den kühlwassereintrittsseitigen Stützwänden 6 zunehmen oder die Anzahl vergrößerter Ringspalte 10 pro Stützwand 6 von den kühlwasseraustrittsseitigen Stützwänden 6 zu den kühlwassereintrittsseitigen Stützwänden 6 zunehmen.In order to increase the area of the annular gaps 10 in the area of the cooler 3 from the support walls 6 on the cooling water outlet side to the support walls 6 on the cooling water inlet side, either the size of the annular gaps 10 with the same number of annular gaps 10 per support wall 6 from the support walls 6 on the cooling water outlet side to the support walls 6 on the cooling water inlet side can be used increase or the number of enlarged annular gaps 10 per support wall 6 increases from the support walls 6 on the cooling water outlet side to the support walls 6 on the cooling water inlet side.

Um insbesondere bei einem Beginn der Evakuierung des Kondensators, bei dem verhältnismäßig große Luftmengen aus dem Kondensator durch die Absaugleitung 8 abgezogen werden, Querschwingungen der Rohre 4 im Mündungsbereich der Absaugleitung 8 zu verhindern, kann eine zusätzliche Stützwand 11 angeordnet werden, die in Fig. 3 eingezeichnet ist. Außerdem ist es möglich, im Bereich der Mündung der Absaugleitung 8 ein parallel zu den Rohren 4 des Kühlers 3 verlaufendes Leitblech 12 anzuordnen, das eine Art Schikane für das aus diesem ersten Feld des Kühlers 3 kommende Dampf-Gas-Gemisch bildet. Die normale Strömungsrichtung des Dampfes D und der nicht kondensierbaren Gase G innerhalb des Kühlers 3 ist mit Pfeilen in Fig. 3 angedeutet.In order to prevent transverse vibrations of the pipes 4 in the mouth area of the suction line 8, in particular at the start of the evacuation of the condenser, in which relatively large amounts of air are drawn out of the condenser through the suction line 8, an additional supporting wall 11 can be arranged, which is shown in FIG. 3 is drawn. In addition, it is possible to arrange in the area of the mouth of the suction line 8 a baffle 12 which runs parallel to the tubes 4 of the cooler 3 and which forms a type of baffle for the steam-gas mixture coming from this first field of the cooler 3. The normal flow direction of the steam D and the non-condensable gases G within the cooler 3 is indicated by arrows in FIG. 3.

Bezugszeichenliste:Reference symbol list:

  • D DampfD steam
  • G GasG gas
  • K KühlwasserK cooling water
  • 1a Bündelhälfte1a half of the bundle
  • 1 b Bündelhälfte1 b bundle half
  • 1c Bündelabschnitt1c bundle section
  • 2 Kondensatableitblech2 condensate drain plate
  • 3 Kühler3 coolers
  • 4 Rohr4 pipe
  • 5a Rohrboden5a tube sheet
  • 5b Rohrboden5b tube sheet
  • 6 Stützwand6 retaining wall
  • 7 Abdeckung7 cover
  • 8 Absaugstutzen8 extraction nozzles
  • 9 Absaugleitung9 suction line
  • 10 Ringspalt10 annular gap
  • 10a Ringspalt10a annular gap
  • 10b Ringspalt10b annular gap
  • 11 zusätzliche Stützwand11 additional retaining wall
  • 12 Leitblech12 baffle

Claims (7)

1. Dampfkondensator mit mindestens einem kühlwasserdurchströmten Rohrbündel, dessen Rohre an ihren Enden in Rohrböden befestigt und auf ihrer Länge durch mehrere Stützwände unterstütz sind, wobei sich bei der Durchführung der Rohre durch die Stützwände konstruktionsbedingt Ringspalte zwischen der Rohrmantelfläche und der Innenwand der Bohrung in der Stützwand ergeben, und dem ein Kühler für die nicht kondensierbaren Gase zugeordnet ist, dessen Rohre durch mindestens eine Abdeckung von den darüberliegenden Rohren getrennt sind, wobei die nicht kondensierbaren Gase, insbesondere Luft, aus dem durch die Abdeckung gebildeten Raum abgesaugt werden,
dadurch gekennzeichnet,
daß die Absaugung der nicht kondensierbaren Gase aus dem durch die Abdeckung (7) gebildeten Raum des Kühlers (3) ausschließlich in der Nähe des kühlwassereintrittsseitigen Rohrbodens (5a) erfolgt.1.Steam condenser with at least one tube bundle through which cooling water flows, the tubes of which are fastened at their ends in tube sheets and are supported along their length by a plurality of supporting walls, with annular gaps between the tubular jacket surface and the inner wall of the bore in the supporting wall when the tubes are passed through the supporting walls result, and which is assigned a cooler for the non-condensable gases, the tubes of which are separated from the tubes above by at least one cover, the non-condensable gases, in particular air, being removed from the space formed by the cover be sucked
characterized,
that the suction of the non-condensable gases from the space formed by the cover (7) of the cooler (3) takes place only in the vicinity of the tube sheet (5a) on the cooling water inlet side. 2. Dampfkondensator nach Anspruch 1, dadurch gekennzeichnet, daß die Ringspalte (10) zwischen der Innenwand der in den Stützwänden (6) vorgesehenen Bohrungen und der Mantelfläche der durch diese Bohrungen hindurchgeführten Rohre (4) des Kühlers (3) im Absaugebereich des Kühlers (3) größer ausgeführt sind als im restlichen Bereich des Kühlers (3).2. Steam condenser according to claim 1, characterized in that the annular gaps (10) between the inner wall of the bores provided in the supporting walls (6) and the lateral surface of the tubes (4) of the cooler (3) passed through these bores in the suction area of the cooler ( 3) are larger than in the rest of the cooler (3). 3. Dampfkondensator nach Anspruch 1 und 2, dadurch gekennzeichnet, daß die Fläche der Ringspalte (10) im Bereich des Kühlers (3) von den kühlwasseraustrittsseitigen Stützwänden (6) zu den kühlwassereintrittsseitigen Stützwänden (6) zunimmt.3. Steam condenser according to claim 1 and 2, characterized in that the area of the annular gaps (10) in the region of the cooler (3) increases from the cooling water outlet side support walls (6) to the cooling water inlet side support walls (6). 4. Dampfkondensator nach Anspruch 3, dadurch gekennzeichnet, daß die Größe der Ringspalte (10) bei gleicher Anzahl von Ringspalten (10) pro Stützwand (6) von den kühlwasseraustrittsseitigen Stützwänden (6) zu den kühlwassereintrittsseitigen Stützwänden (6) zunimmt.4. Steam condenser according to claim 3, characterized in that the size of the annular gaps (10) increases with the same number of annular gaps (10) per supporting wall (6) from the cooling water outlet-side supporting walls (6) to the cooling water inlet-side supporting walls (6). 5. Dampfkondensator nach Anspruch 3, dadurch gekennzeichnet, daß die Anzahl vergrößerter Ringspalte (10) pro Stützwand (6) von den kühlwasseraustrittsseitigen Stützwänden (6) zu den kühlwassereintrittsseitigen Stützwänden (6) zunimmt.5. Steam condenser according to claim 3, characterized in that the number of enlarged annular gaps (10) per support wall (6) increases from the cooling water outlet-side support walls (6) to the cooling water inlet-side support walls (6). 6. Dampfkondensator nach mindestens einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß im Bereich der Mündung der Absaugleitung (8) eine zusätzliche Stützwand (11) für einen Teil der Kühlerrohre (4) angeordnet ist.6. Steam condenser according to at least one of claims 1 to 5, characterized in that in the region of the mouth of the suction line (8) an additional support wall (11) for part of the cooler tubes (4) is arranged. 7. Dampfkondensator nach mindestens einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß im Bereich der Mündung der Absaugleitung (8) ein parallel zu den Kühlerrohren (4) und über einen Teil der Länge der Kühlerrohre (4) verlaufendes Leitblech (12) angeordnet ist, das an der Abdeckung (7) befestigt ist.7. Steam condenser according to at least one of claims 1 to 6, characterized in that in the region of the mouth of the suction line (8) a parallel to the cooler tubes (4) and over part of the length of the cooler tubes (4) extending baffle (12) is arranged is attached to the cover (7).
EP19920118798 1991-12-13 1992-11-03 Steam condenser Expired - Lifetime EP0546315B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4141132 1991-12-13
DE19914141132 DE4141132C2 (en) 1991-12-13 1991-12-13 Steam condenser

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EP0546315A1 true EP0546315A1 (en) 1993-06-16
EP0546315B1 EP0546315B1 (en) 1995-03-29

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19604704C1 (en) * 1996-02-09 1997-03-06 Balcke Duerr Gmbh Steam condenser for power plant
EP0976998A1 (en) * 1998-07-30 2000-02-02 Asea Brown Boveri AG Steam condenser
EP1014022A1 (en) * 1998-12-24 2000-06-28 ABB Alstom Power (Schweiz) AG Surface condenser
CN102588018A (en) * 2012-03-17 2012-07-18 华电电力科学研究院 Method for optimizing cold end of fossil power generation unit on basis of TEPEE two-mountain-peak-shaped tube bundle

Citations (3)

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Publication number Priority date Publication date Assignee Title
DE583927C (en) * 1929-12-09 1933-09-12 Westinghouse Electric & Mfg Co Air cooler for condensers with a ring-shaped tube bundle supported by walls
US3349841A (en) * 1966-08-04 1967-10-31 Ingersoll Rand Co Air cooler for surface condensers
GB1184953A (en) * 1966-04-01 1970-03-18 Sulzer Ag Tubular Heat Exchangers

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH423819A (en) * 1965-01-15 1966-11-15 Bbc Brown Boveri & Cie Condensation system for steam turbine exhaust steam
ES2021132B3 (en) * 1988-01-22 1991-10-16 Asea Brown Boveri STEAM CONDENSER

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE583927C (en) * 1929-12-09 1933-09-12 Westinghouse Electric & Mfg Co Air cooler for condensers with a ring-shaped tube bundle supported by walls
GB1184953A (en) * 1966-04-01 1970-03-18 Sulzer Ag Tubular Heat Exchangers
US3349841A (en) * 1966-08-04 1967-10-31 Ingersoll Rand Co Air cooler for surface condensers

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DE4141132C1 (en) 1993-02-11
ES2071406T3 (en) 1995-06-16
DE4141132C2 (en) 1995-06-29
EP0546315B1 (en) 1995-03-29

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