EP0088944B1 - Axial flow steam turbine, especially of the double-flow type - Google Patents

Axial flow steam turbine, especially of the double-flow type Download PDF

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Publication number
EP0088944B1
EP0088944B1 EP83102038A EP83102038A EP0088944B1 EP 0088944 B1 EP0088944 B1 EP 0088944B1 EP 83102038 A EP83102038 A EP 83102038A EP 83102038 A EP83102038 A EP 83102038A EP 0088944 B1 EP0088944 B1 EP 0088944B1
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EP
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Prior art keywords
shaft
steam
steam turbine
flow
nozzles
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EP83102038A
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German (de)
French (fr)
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EP0088944A1 (en
Inventor
Herbert Keller
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Siemens AG
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Kraftwerk Union AG
Siemens AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F01D3/02—Machines or engines with axial-thrust balancing effected by working-fluid characterised by having one fluid flow in one axial direction and another fluid flow in the opposite direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/08—Cooling; Heating; Heat-insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/08—Heating, heat-insulating or cooling means

Definitions

  • the invention relates to an axially loaded steam turbine according to the preamble of claim 1.
  • Such a steam turbine is known from FR-A-851 531.
  • a shaft shield is arranged in the region of the steam inflow taking place in the axial center, which shaft shield is attached to the radially inner ends of the guide vanes of the first guide vane rings of both flows.
  • the shaft shield enclosing the shaft at a distance is formed on the outer circumference in such a way that the steam flowing in in the radial direction is divided equally between the two floods and deflected in the axial direction. The shaft shielding thus prevents an immediate flow against the shaft surface by the steam flowing in in the radial direction.
  • the invention is based on the object, in an axially loaded steam turbine of the type mentioned, to further reduce the thermal stresses of the shaft in the region of the steam inflow, likewise without the use of cooling steam generated externally to the turbine, but in this case the shaft shielding ring itself as a device for pressure and Take advantage of lowering the temperature of the live steam.
  • a small partial flow of the total inflowing steam is fed through tangentially arranged nozzles to the shaft area under the shaft shield.
  • the speed at which this partial flow enters the annular channel formed between the shaft and the shaft shield corresponds to the gradient processed in the first guide vane ring.
  • the nozzles introduced into the shaft shielding are aligned with respect to the direction of rotation of the shaft in such a way that the swirl flow which forms in the ring channel leads the shaft circumferential speed.
  • the boundary layer temperature on the shaft corresponds to the static temperature of the steam which is reduced by the increase in the kinetic energy, increased by the proportion of the damming temperature of the comparatively low relative speed between the swirl flow and the shaft circumferential speed. Effective cooling of the shaft in the area of the steam inflow and in the area of the blade attachment of the first blade ring can thus be achieved by the nozzles introduced tangentially into the shaft shield.
  • incoming partial flow is then divided equally into two swirl flows, which each flow in the axial direction along the shaft up to the first rotor blade ring.
  • a further improvement in the cooling effect can be achieved in that the first stage is designed as a weak reaction stage or, in the case of a double-flow version, that the first stage is designed as a weak reaction stage in both floods. This is intended to process as large a gradient as possible in the first guide vane ring, so that the static temperature of the partial flow introduced into the ring channel is reduced as much as possible by the corresponding increase in the kinetic energy.
  • the cross section of the nozzles is dimensioned such that the steam mass flow entering the annular duct is approximately 3% of the total steam mass flow supplied in the region of the steam inflow.
  • the nozzles 8 are designed such that, seen in the direction of rotation of the shaft indicated by the arrow 9, they open tangentially into the annular channel 4 formed between the shaft 5 and the shaft shield 6. Since the partial flow diverted from the inflowing steam enters tangentially into the ring channel 4 through the nozzles 8, a swirl flow indicated by the arrow 10 forms there, which leads the wave circumferential speed.
  • the swirl flow 10 is then divided into two swirl flows starting from the axial center M, which are indicated in FIG. 1 by the arrows 11 and 11 'and along the shaft 5 as far as the rotor blades 12 and 12' of the respective first rotor blade ring of the two floods.
  • the speed at which the partial flow diverted from the incoming steam enters the nozzles 8 thus corresponds to the gradient processed in the first guide vane ring of the two floods, and this speed of entry can be increased by eliminating the respective first stage as a weak reaction stage.
  • the shaft shield 6 prevents a direct flow against the surface of the shaft 5 by the hot steam flowing radially in the direction of the arrow 1.
  • the boundary layer temperature of the swirl flows 10 or 11 and 11 'in the ring channel 4 corresponds to the static temperature of the steam reduced by the increase in the kinetic energy, increased by the accumulation temperature portion of the relative speed between the swirl flow 10 or 11 and 11' and the shaft circumferential speed.
  • the congestion temperature proportion is low, since the relative speed mentioned is also comparatively low due to the selected orientation of the nozzles 8.
  • the steam mass flow entering the annular duct 4 through the nozzles 8 is approximately 3% of the total steam mass flow supplied through the inflow duct 2.
  • the temperature drop in the area of the shaft 5 below the shaft shield 6 is 20 ° K at the beginning of the swirl field in the axial center M and at 10 to 15 ° K at the respective end of the swirl field compared to the temperature of the incoming steam.
  • the increase in consumption required for this cooling of the shaft is approximately 0.06% and thus corresponds to the values which can be achieved with external cooling by cooling steam introduced from the outside.
  • the slight reduction in the cooling effect at the respective end of the swirl field can possibly be avoided by an additional row of blades arranged on the shaft 5. This row of moving blades arranged in the axial center M and in the annular channel 4 could expediently be designed as a free jet turbine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Description

Die Erfindung bezieht sich auf eine axial beaufschlagte Dampfturbine gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to an axially loaded steam turbine according to the preamble of claim 1.

Eine derartige Dampfturbine ist aus der FR-A-851 531 bekannt. Bei einer dort dargestellten zweiflutigen Dampfturbine ist im Bereich der in der axialen Mitte erfolgenden Dampfeinströmung eine Wellenabschirmung angeordnet, welche an den radial inneren Enden der Leitschaufeln der ersten Leitschaufelkränze beider Fluten befestigt ist. Die die Welle mit Abstand umschließende Wellenabschirmung ist dabei am Außenumfang so ausgebildet, daß der in radialer Richtung einströmende Dampf auf beide Fluten gleichmäßig aufgeteilt und in die axiale Richtung umgelenkt wird. Die Wellenabschirmung verhindert somit ein unmittelbares Anströmen der Wellenoberfläche durch den in radialer Richtung einströmenden Dampf.Such a steam turbine is known from FR-A-851 531. In the case of a double-flow steam turbine shown there, a shaft shield is arranged in the region of the steam inflow taking place in the axial center, which shaft shield is attached to the radially inner ends of the guide vanes of the first guide vane rings of both flows. The shaft shield enclosing the shaft at a distance is formed on the outer circumference in such a way that the steam flowing in in the radial direction is divided equally between the two floods and deflected in the axial direction. The shaft shielding thus prevents an immediate flow against the shaft surface by the steam flowing in in the radial direction.

Aus W. Traupel « Thermische Turbomaschinen •, Band 2, 2. Auflage, Springer-Verlag, Berlin, Heidelberg, New York, 1968, Seite 341, ist es auch bekannt, bei einer axial beaufschlagten einflutigen Dampfturbine im Bereich der Dampfeinströmung ein Abschirmblech anzuordnen und in den zwischen Welle und Abschirmblech gebildeten Ringkanal von außen her Kühldampf einzuführen. Der Kühldampf strömt dann in dem Ringkanal bis vor den ersten Laufschaufelkranz. Auf diese Weise können die zusätzlich zu den hohen Fliehkraftbeanspruchungen der Welle im Bereich der Dampfeinströmung und im Bereich der Laufschaufelbefestigung des ersten Laufschaufelkranzes auftretenden thermischen Beanspruchungen reduziert werden. Hierzu ist jedoch die mit einigem Aufwand verbundene Bereitstellung von Kühldampf erforderlich. Außerdem ist eine derartige von außen her erfolgende Einleitung von Kühldampf in den zwischen Welle-. nabschirmung und Welle gebildeten Ringkanal bei zweiflutigen Dampfturbinen nur möglich, wenn die Leitung für die Zufuhr des Kühldampfes im Bereich der Dampfeinströmung verlegt wird. Eine derartige Ausführung ist aus der Zeitschrift « BBC-Nachrichten », 1980, Heft 10, Seite 378, und durch die DE-A-21 40490 bekannt. Durch die Verlegung der Leitung für die Zufuhr des Kühldampfes in den Bereich der Dampfeinströmung entstehen jedoch zusätzliche Strömungsverluste. Die Kühlung der Welle im Bereich der Dampfeinströmung durch Kühldampf ist auch thermodynamisch ungünstig, weil der kalte Kühldampf die mittlere Arbeitsmitteltemperatur in der Dampfturbine absenkt. Durch die Zufuhr von Kühldampf können aber auch regeltechnische Probleme im Falle einer Lastabschaltung entstehen, da der Kühldampf die Dampfturbine bzw. den Turbosatz auf Überdrehzahl bringen könnte, sofern die Kühldampfzufuhr nicht durch separate Sicherheitsventile abgeschaltet wird.From W. Traupel “Thermal Turbomachinery •, Volume 2, 2nd Edition, Springer-Verlag, Berlin, Heidelberg, New York, 1968, page 341, it is also known to arrange a shielding plate for an axially loaded single-flow steam turbine in the area of the steam inflow and to introduce cooling steam from the outside into the annular channel formed between the shaft and the shielding plate. The cooling steam then flows in the ring channel up to the first rotor blade ring. In this way, the thermal stresses occurring in addition to the high centrifugal force stresses of the shaft in the area of the steam inflow and in the area of the rotor blade attachment of the first rotor blade ring can be reduced. However, this requires the provision of cooling steam, which involves some effort. In addition, such an external introduction of cooling steam is in the between shaft. Shielding and shaft formed ring channel in double-flow steam turbines only possible if the line for the supply of cooling steam is laid in the area of the steam inflow. Such an embodiment is known from the magazine “BBC-Nachrichten”, 1980, number 10, page 378, and from DE-A-21 40490. However, laying the line for supplying the cooling steam in the area of the steam inflow creates additional flow losses. The cooling of the shaft in the area of the steam inflow by cooling steam is also thermodynamically unfavorable because the cold cooling steam lowers the average working fluid temperature in the steam turbine. The supply of cooling steam can also cause control problems in the event of a load shutdown, since the cooling steam could bring the steam turbine or the turbo set to overspeed if the cooling steam supply is not switched off by separate safety valves.

Es ist durch die US-A-3 817 654 bekannt, den Wellenkühldampf durch Teilentspannung des Frischdampfes im Düsenkranz einer ersten Aktions-Schaufelstufe bei einer doppelflutigen Dampfturbine derart zu erzeugen, daß dieser teilentspannte Dampf einen etwas höheren Druck als der im Düsenkranz der anderen ersten Schaufelstufe teilentspannte Dampf aufweist. Als Wellenkühldampf wird dann eine Teildampfmenge abgezweigt, welche aufgrund des Druckgefälles in einer gegenläufigen Schleife unter dem Wellenabschirmring und über die Wellenoberfläche zur gegenüberliegenden ersten Stufe der doppelflutigen Beschaufelung geführt wird. Bei der Erfindung wird zwar gleichfalls turbinenintern erzeugter Wellenkühldampf verwendet, es ist jedoch eine unterschiedliche Auslegung von Beschaufelungsstufen und eine 180°-Umlenkung von Dampfteilströmen nicht erforderlich.It is known from US-A-3 817 654 to generate the wave cooling steam by partially releasing the live steam in the nozzle ring of a first action blade stage in a double-flow steam turbine in such a way that this partially expanded steam has a slightly higher pressure than that in the nozzle ring of the other first blade stage has partially relaxed steam. A partial steam quantity is then branched off as wave cooling steam, which, due to the pressure gradient, is led in a counter-rotating loop under the shaft shielding ring and over the shaft surface to the opposite first stage of the double-flow blading. Although shaft cooling steam generated internally in the turbine is also used in the invention, a different design of blading stages and a 180 ° deflection of partial steam flows is not necessary.

Der Erfindung liegt die Aufgabe zugrunde, bei einer axial beaufschlagten Dampfturbine der eingangs genannten Art die thermischen Beanspruchungen der Welle im Bereich der Dampfeinströmung ebenfalls ohne die Verwendung von turbinen-extern erzeugtem Kühldampf weiter zu reduzieren, dabei jedoch den Wellenabschirmring selbst als Einrichtung zur Druck- und Temperaturabsenkung des Frischdampfes auszunutzen.The invention is based on the object, in an axially loaded steam turbine of the type mentioned, to further reduce the thermal stresses of the shaft in the region of the steam inflow, likewise without the use of cooling steam generated externally to the turbine, but in this case the shaft shielding ring itself as a device for pressure and Take advantage of lowering the temperature of the live steam.

Diese Aufgabe wird erfindungsgemäß durch die im kennzeichnenden Teil des Patentanspruches 1 aufgeführten Merkmale gelöst.This object is achieved by the features listed in the characterizing part of claim 1.

Bei der erfindungsgemäßen Dampfturbine wird also unter Umgehung des ersten Leitschaufelkranzes ein geringer Teilstrom des insgesamt einströmenden Dampfes durch tangential angeordnete Düsen dem unter der Wellenabschirmung liegenden Wellenbereich zugeführt. Die Geschwindigkeit, mit welcher dieser Teilstrom in den zwischen Welle und Wellenabschirmung gebildeten Ringskanal eintritt, entspricht dem im ersten Leitschaufelkranz verarbeiteten Gefälle. Die in die Wellenabschirmung eingebrachten Düsen sind dabei in bezug auf die Drehrichtung der Welle so ausgerichtet, daß die sich im Ringkanal ausbildende Drallströmung der Wellenumfangsgeschwindigkeit vorauseilt. Die Grenzschichttemperatur an der Welle entspricht dann der durch die Erhöhung der kinetischen Energie abgesenkten statischen Temperatur des Dampfes, vermehrt um den Stautemperaturanteil der vergleichsweise geringen Relativgeschwindigkeit zwischen der Drallströmung und der Wellenumfangsgeschwindigkeit. Durch die in die Wellenabschirmung tangential eingebrachten Düsen kann somit eine wirksame Kühlung der Welle im Bereich der Dampfeinströmung und im Bereich der Laufschaufelbefestigung des ersten Laufschaufelkranzes erzielt werden.In the steam turbine according to the invention, bypassing the first guide vane ring, a small partial flow of the total inflowing steam is fed through tangentially arranged nozzles to the shaft area under the shaft shield. The speed at which this partial flow enters the annular channel formed between the shaft and the shaft shield corresponds to the gradient processed in the first guide vane ring. The nozzles introduced into the shaft shielding are aligned with respect to the direction of rotation of the shaft in such a way that the swirl flow which forms in the ring channel leads the shaft circumferential speed. The boundary layer temperature on the shaft then corresponds to the static temperature of the steam which is reduced by the increase in the kinetic energy, increased by the proportion of the damming temperature of the comparatively low relative speed between the swirl flow and the shaft circumferential speed. Effective cooling of the shaft in the area of the steam inflow and in the area of the blade attachment of the first blade ring can thus be achieved by the nozzles introduced tangentially into the shaft shield.

Bei einer axial beaufschlagten Dampfturbine in zweiflutiger Ausführung, bei welcher die Wellenabschirmung an den radial inneren "Enden der Leitschaufeln der ersten Leitschaufelkränze beider Fluten befestigt ist, ist bei einer bevorzugten Ausführungsform vorgesehen, daß die Düsen in der axialen Mitte in den Ringkanal einmünden. Der durch die mittigen Düsen in den RingkanalIn the case of an axially loaded steam turbine in a double-flow design, in which the shaft shield is attached to the radially inner ends of the guide vanes of the first guide vane rings of both floods, in a preferred embodiment it is provided that the nozzles open into the annular channel in the axial center the central nozzles in the ring channel

eintretende Teilstrom wird dann gleichmäßig in zwei Drallströmungen aufgeteilt, welche in axialer Richtung entlang der Welle jeweils bis zum ersten Laufschaufelkranz strömen.incoming partial flow is then divided equally into two swirl flows, which each flow in the axial direction along the shaft up to the first rotor blade ring.

Eine weitere Verbesserung der Kühlwirkung kann dadurch erzielt werden, daß die erste Stufe als Schwachreaktions-Stufe ausgebildet ist bzw. daß bei einer zweiflutigen Ausführung bei beiden Fluten jeweils die erste Stufe als Schwachreaktions-Stufe ausgebildet ist. Hierdurch soll ein möglichst großes Gefälle im ersten Leitschaufelkranz verarbeitet werden, so daß durch die entsprechende Erhöhung der kinetischen Energie die statische Temperatur des in den Ringkanal eingeleiteten Teilstromes möglichst weit abgesenkt wird.A further improvement in the cooling effect can be achieved in that the first stage is designed as a weak reaction stage or, in the case of a double-flow version, that the first stage is designed as a weak reaction stage in both floods. This is intended to process as large a gradient as possible in the first guide vane ring, so that the static temperature of the partial flow introduced into the ring channel is reduced as much as possible by the corresponding increase in the kinetic energy.

Weiterhin hat es sich aus fertigungstechnischen Gründen als zweckmäßig erwiesen, wenn insgesamt vier über den Umfang der Wellenabschirmung gleichmäßig verteilt angeordnete Düsen vorgesehen sind.Furthermore, it has proven to be expedient for manufacturing reasons if a total of four nozzles are provided which are arranged uniformly distributed over the circumference of the shaft shielding.

Bei einer weiteren bevorzugten Ausgestaltung der erfindungsgemäßen Dampfturbine ist der Querschnitt der Düsen derart bemessen, daß der in den Ringkanal gelangende Dampfmassenstrom etwa 3 % des insgesamt im Bereich der Dampfeinströmung zugeführten Dampfmassenstromes beträgt. Hierdurch kann bei einer wirksamen Kühlung der Welle die durch die teilweise Umgehung des ersten Leitschaufelkranzes bedingte Verbrauchserhöhung auf äußerst niedrige Werte begrenzt werden.In a further preferred embodiment of the steam turbine according to the invention, the cross section of the nozzles is dimensioned such that the steam mass flow entering the annular duct is approximately 3% of the total steam mass flow supplied in the region of the steam inflow. In this way, with effective cooling of the shaft, the increase in consumption due to the partial bypassing of the first guide vane ring can be limited to extremely low values.

Im folgenden wird ein Ausführungsbeispiel der Erfindung anhand der Zeichnung näher erläutert. Dabei zeigt in stark vereinfachter schematischer Darstellung

  • Figur 1 den Einströmbereich einer zweiflutigen Dampfturbine im Längsschnitt und
  • Figur 2 einen Querschnitt gemäß der Linie 11-11 der Fig. 1.
Gemäß Fig. 1 strömt der Dampf in Richtung des Pfeiles 1 radial nach innen durch einen ringförmigen Einströmkanal 2, welcher durch die Leitschaufelträger 3 bzw. 3' der beiden spiegelbildlich zur axialen Mitte M angeordneten Fluten gebildet ist. Der in radialer Richtung einströmende Dampf wird dann unter Umlenkung in die axiale Richtung auf beide Fluten gleichmäßig aufgeteilt, wobei jedoch ein geringer Teilstrom in einen Ringkanal 4 eingeleitet wird, welcher zwischen der Welle 5 und einer dazu konzentrischen Wellenabschirmung 6 gebildet ist und durch eine entsprechende Formgebung von Welle 5 und Wellenabschirmung 6 von der axialen Mitte M ausgehend nach beiden Seiten hin etwas ansteigt. Die Wellenabschirmung 6 ist an den radial inneren Enden der Leitschaufeln 7 bzw. 7' des jeweils ersten Leitschaufelkranzes beider Fluten befestigt. Die Leitschaufeln 7 und 7' sind ihrerseits in die Leitschaufelträger 3 bzw. 3' eingesetzt.An exemplary embodiment of the invention is explained in more detail below with reference to the drawing. It shows in a highly simplified schematic representation
  • Figure 1 shows the inflow area of a double-flow steam turbine in longitudinal section and
  • 2 shows a cross section along the line 11-11 of FIG. 1st
1, the steam flows in the direction of arrow 1 radially inward through an annular inflow channel 2, which is formed by the guide vane carriers 3 and 3 'of the two floods arranged in mirror image to the axial center M. The steam flowing in in the radial direction is then divided equally between the two floods by deflection in the axial direction, but a small partial flow is introduced into an annular channel 4 which is formed between the shaft 5 and a shaft shield 6 concentric therewith and by a corresponding shaping from shaft 5 and shaft shield 6 slightly rising from the axial center M towards both sides. The shaft shield 6 is fastened to the radially inner ends of the guide vanes 7 and 7 'of the first guide vane ring in each case of both floods. The guide vanes 7 and 7 'are in turn inserted into the guide vane carriers 3 and 3'.

In die Wellenabschirmung 6 sind nun insgesamt vier über den Umfang gleichmäßig verteilt angeordnete Düsen 8 als Bohrungen eingebracht. Wie es insbesondere aus dem Querschnitt der Fig. 2 ersichtlich ist, sind die Düsen 8 so ausgebildet, daß sie in der durch den Pfeil 9 angedeuteten Drehrichtung der Welle gesehen tangential in den zwischen Welle 5 und Wellenabschirmung 6 gebildeten Ringkanal 4 einmünden. Da der von dem einströmenden Dampf abgezweigte Teilstrom durch die Düsen 8 tangential in den Ringkanal 4 eintritt, bildet sich dort eine durch den Pfeil 10 angedeutete Drallströmung aus, welche der Wellenumfangsgeschwindigkeit vorauseilt.A total of four nozzles 8, which are uniformly distributed over the circumference, are now introduced into the shaft shield 6 as bores. As can be seen in particular from the cross section of FIG. 2, the nozzles 8 are designed such that, seen in the direction of rotation of the shaft indicated by the arrow 9, they open tangentially into the annular channel 4 formed between the shaft 5 and the shaft shield 6. Since the partial flow diverted from the inflowing steam enters tangentially into the ring channel 4 through the nozzles 8, a swirl flow indicated by the arrow 10 forms there, which leads the wave circumferential speed.

Die Drallströmung 10 teilt sich dann in zwei von der axialen Mitte M ausgehende Drallströmungen auf, welche in der Fig. 1 durch die Pfeile 11 und 11' angedeutet sind und die Welle 5 entlang bis zu den Laufschaufeln 12 bzw. 12' des jeweils ersten Laufschaufelkranzes der beiden Fluten strömen. Dabei umgehen die beiden Drallströmungen 11 und 11' die Leitschaufeln 7 bzw. 7' des jeweils ersten Leitschaufelkranzes beider Fluten. Die Geschwindigkeit mit welcher der von dem einströmenden Dampf abgezweigte Teilstrom in die Düsen 8 eintritt entspricht damit dem jeweils im ersten Leitschaufelkranz der beiden Fluten verarbeiteten Gefälle, wobei diese Eintrittsgeschwindigkeit durch eine Ausbindung der jeweils ersten Stufe als Schwachreaktions-Stufe gesteigert werden kann.The swirl flow 10 is then divided into two swirl flows starting from the axial center M, which are indicated in FIG. 1 by the arrows 11 and 11 'and along the shaft 5 as far as the rotor blades 12 and 12' of the respective first rotor blade ring of the two floods. The two swirl flows 11 and 11 'bypass the guide vanes 7 and 7' of the first guide vane ring of both floods. The speed at which the partial flow diverted from the incoming steam enters the nozzles 8 thus corresponds to the gradient processed in the first guide vane ring of the two floods, and this speed of entry can be increased by eliminating the respective first stage as a weak reaction stage.

Die Wellenabschirmung 6 verhindert einerseits ein unmittelbares Anströmen der Oberfläche der Welle 5 durch den in Richtung des Pfeiles 1 radial einströmenden heißen Dampf. Andererseits entspricht die Grenzschichttemperatur der Drallströmungen 10 bzw. 11 und 11' in dem Ringkanal 4 der durch die Erhöhung der kinetischen Energie abgesenkten statischen Temperatur des Dampfes, vermehrt um den Stautemperaturanteil der Relativgeschwindigkeit zwischen Drallströmung 10 bzw. 11 und 11' und Wellenumfangsgeschwindigkeit. Der Stautemperaturanteil ist dabei gering, da die genannte Relativgeschwindigkeit durch die gewählte Ausrichtung der Düsen 8 ebenfalls vergleichsweise gering ist.On the one hand, the shaft shield 6 prevents a direct flow against the surface of the shaft 5 by the hot steam flowing radially in the direction of the arrow 1. On the other hand, the boundary layer temperature of the swirl flows 10 or 11 and 11 'in the ring channel 4 corresponds to the static temperature of the steam reduced by the increase in the kinetic energy, increased by the accumulation temperature portion of the relative speed between the swirl flow 10 or 11 and 11' and the shaft circumferential speed. The congestion temperature proportion is low, since the relative speed mentioned is also comparatively low due to the selected orientation of the nozzles 8.

Der in den Ringkanal 4 durch die Düsen 8 eintretende Dampfmassenstrom beträgt etwa 3 % des insgesamt durch den Einströmkanal 2 zugeführten Dampfmassenstromes. Die Temperaturabsenkung in dem unterhalb der Wellenabschirmung 6 liegenden Bereich der Welle 5 liegt gegenüber der Temperatur des einströmenden Dampfes bei 20 °K am Anfang des Drallfeldes in der axialen Mitte M und bei 10 bis 15 °K am jeweiligen Ende des Drallfeldes. Die für diese Kühlung der Welle erforderliche Verbrauchserhöhung liegt bei ungefähr 0,06 % und entspricht damit den bei Fremdkühlung durch von außen her eingeleiteten Kühldampf erreichbaren Werten. Die geringfügige Verringerung der Kühlwirkung am jeweiligen Ende des Drallfeldes kann ggf. durch eine auf der Welle 5 zusätzlich angeordnete Laufschaufelreihe vermieden werden. Diese in der axialen Mitte M und im Ringkanal 4 angeordnete Laufschaufelreihe könnte zweckmäßigerweise als Freistrahlturbine ausgebildet werden.The steam mass flow entering the annular duct 4 through the nozzles 8 is approximately 3% of the total steam mass flow supplied through the inflow duct 2. The temperature drop in the area of the shaft 5 below the shaft shield 6 is 20 ° K at the beginning of the swirl field in the axial center M and at 10 to 15 ° K at the respective end of the swirl field compared to the temperature of the incoming steam. The increase in consumption required for this cooling of the shaft is approximately 0.06% and thus corresponds to the values which can be achieved with external cooling by cooling steam introduced from the outside. The slight reduction in the cooling effect at the respective end of the swirl field can possibly be avoided by an additional row of blades arranged on the shaft 5. This row of moving blades arranged in the axial center M and in the annular channel 4 could expediently be designed as a free jet turbine.

Claims (6)

1. An axial flow steam turbine, especially of the double-flow type, having an annular shaft screen (6) which is arranged in the area of a steam inflow (1, 2), which is spaced from and surrounds a shaft (5) and which is connected to the radial inner ends of guide vanes (7, 7') of a first guide vane ring, characterised in that nozzles (8) are formed in the shaft screen (6), which (nozzles), seen in the direction of rotation (9) of the shaft (5), discharge tangentially into an annular channel (4) formed between the shaft (5) and the shaft screen (6).
2. An axial flow steam turbine of the double-flow type according to claim 1, in which the shaft screen (6) is connected to the radial inner ends of the guide vanes (7, 7') of first guide vane rings of both flows, characterised in that the nozzles (8) discharge into the annular channel (4) at an axial midpoint.
3. An axial flow steam turbine according to claim 1, characterised in that, the first stage is formed as a low degree reaction stage.
4. An axial flow steam turbine of the double-flow type according to claim 2, characterised in that the first stage of each of the flows is formed as a low degree reaction stage.
5. An axial flow steam turbine according to (any) one of the preceding claims, characterised in that there is provided a total of four nozzles (8), equally distributed around the periphery of the shaft screen (6).
6. An axial flow steam turbine according to (any) one of the preceding claims, characterised in that the cross-section of the nozzles (8) is determined so that the mass flow of steam arriving in the annular channel (4) is about 3 % of the total mass flow of steam supplied in the area of the steam inflow.
EP83102038A 1982-03-16 1983-03-02 Axial flow steam turbine, especially of the double-flow type Expired EP0088944B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83102038T ATE16303T1 (en) 1982-03-16 1983-03-02 AXIALLY ACTUATED STEAM TURBINE, PARTICULARLY IN A TWO-SCREW VERSION.

Applications Claiming Priority (2)

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DE19823209506 DE3209506A1 (en) 1982-03-16 1982-03-16 AXIAL STEAM TURBINE IN PARTICULAR, IN PARTICULAR VERSION
DE3209506 1982-03-16

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EP0088944A1 EP0088944A1 (en) 1983-09-21
EP0088944B1 true EP0088944B1 (en) 1985-10-30

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EP (1) EP0088944B1 (en)
JP (1) JPS58167802A (en)
AR (1) AR229899A1 (en)
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DE (2) DE3209506A1 (en)
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CN107002494A (en) * 2014-10-15 2017-08-01 西门子公司 The controllable cooling of turbine wheel shaft

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CN107002494A (en) * 2014-10-15 2017-08-01 西门子公司 The controllable cooling of turbine wheel shaft

Also Published As

Publication number Publication date
BR8301277A (en) 1983-11-22
EP0088944A1 (en) 1983-09-21
DE3361096D1 (en) 1985-12-05
AR229899A1 (en) 1983-12-30
IN158028B (en) 1986-08-16
ATE16303T1 (en) 1985-11-15
JPH0440522B2 (en) 1992-07-03
JPS58167802A (en) 1983-10-04
ES520606A0 (en) 1983-12-16
US4571153A (en) 1986-02-18
ES8401567A1 (en) 1983-12-16
DE3209506A1 (en) 1983-09-22

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