EP0374645A1 - Multiple housing steam turbine unit - Google Patents

Multiple housing steam turbine unit Download PDF

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Publication number
EP0374645A1
EP0374645A1 EP89122742A EP89122742A EP0374645A1 EP 0374645 A1 EP0374645 A1 EP 0374645A1 EP 89122742 A EP89122742 A EP 89122742A EP 89122742 A EP89122742 A EP 89122742A EP 0374645 A1 EP0374645 A1 EP 0374645A1
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EP
European Patent Office
Prior art keywords
lever
turbine
casing
bearing
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP89122742A
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German (de)
French (fr)
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EP0374645B1 (en
Inventor
Pierre Meylan
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ABB Asea Brown Boveri Ltd
ABB AB
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ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/28—Supporting or mounting arrangements, e.g. for turbine casing
    • 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
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/162—Bearing supports
    • 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
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • F01D25/26—Double casings; Measures against temperature strain in casings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S248/00—Supports
    • Y10S248/901—Support having temperature or pressure responsive feature

Definitions

  • the present invention relates to a multi-casing steam turbine set with a high-pressure part turbine, a medium-pressure part turbine and at least one low-pressure part turbine, which low-pressure part turbines are designed with two housings, each with an outer housing and an inner housing that is mounted inside and displaceable relative to the latter, with the rotors of all the partial turbines sitting on a common shaft train an axial bearing arranged between the medium-pressure part turbine and the high-pressure part turbine is fixed axially in both directions, and with elements for compensating for the axial displacements of the rotor relative to their inner housings that occur due to the thermal expansions during operation
  • a bearing point between the high-pressure part turbine, hereinafter referred to as “high-pressure part”, and the medium-pressure part turbine, hereinafter referred to as “medium-pressure part”, is designed as a fixed point from which the high-pressure part and the medium-pressure part with the subsequent low-pressure parts can move freely in opposite directions can expand.
  • a multi-casing turbine with such a choice for the compensation of the axial play changes due to thermal expansion is described in DE-PS 1 216 322 by Rateau.
  • a single-case medium pressure part which takes part in the displacement due to the thermal expansions together with its turbine runner, transmits these via coupling rods, which extend into the outer housing of the low-pressure part with two housings, to the inner housing to which they are articulated.
  • the shaft with the turbine rotor shifts because of the essentially the same temperature as that of the inner housing by the same distance as this with its blading, so that the axial play between the guide and rotor blades is maintained in practically the same size as in the cold state.
  • the fixed point of the shaft from which the medium-pressure part with the inner housings of the low-pressure parts coupled to it and on the other hand freely expand and shift in the opposite direction of the high-pressure part, is located at a bearing point between the latter and the medium-pressure part.
  • the present invention arose from the task of avoiding the sealing problems mentioned in a multi-casing steam turbine and of designing the device for maintaining the axial clearances between the guide vanes and the rotor blade rings of the low-pressure parts as simply, uncomplicatedly and reliably as possible.
  • the multi-housing steam turbine set according to the invention is characterized in that in order to maintain the axial play between the guide blades and the rotor blades of the turbine parts at operating temperature, a pair of levers is provided on both sides of the inner housing, with a two-armed slide lever and a one-armed expansion lever articulated thereon via an axis, the other end of the slide lever on an outer housing-fixed bearing block and the other end of the expansion lever is articulated on a bearing pin fixed on the inner housing, and that the sliding lever engages with an elongated hole in an inner housing-fixed bearing pin between its articulation points on the bearing block and on the expansion lever, the axis of which divides the sliding lever into its lever arms, whereby an extension ⁇ l in operation caused by the thermal expansion of the distance between the two inner housing-fixed bearing journals via the expansion lever and the sliding lever a displacement ⁇ x of the inner housing compared to the bearing blocks fixed to the outer housing.
  • the shaft train 4 is fixed in a bearing housing 5 located between the high-pressure part and the medium-pressure part 1 by a double-sided axial bearing 6 in both directions. From this fixed point, the high-pressure part, not shown, can expand to the left unhindered, since its housing extends in a known manner by means of support claws slidably supported on slideways, wherein the tilting about the shaft axis due to the reaction torque is prevented by a support which forms an axial support of the center housing.
  • the figure shows such a support 7 for the housing 8 of the medium pressure part 1.
  • the housing 8 and the bearing housing 5 are axially fixed together.
  • the outer housings 9 and 10 of the low-pressure parts 2 and 3 are fastened to the base plate and their inner housings 11 and 12 in the outer housing in question are also axially displaceable in a known manner and secured against tipping.
  • the steam outlet line on the medium-pressure turbine section 1 is designated 13 and the two steam supply lines to the low-pressure turbines 2 and 3 are designated 14 and 15.
  • the simplification according to the invention compared to the prior art mentioned at the outset is that instead of coupling rods or other rigid transmission members between the individual partial turbines, a lever system is used which, in the operating state of the turbine, brings about the displacements of the inner housing, which compensate for the displacements of those on the shaft train seated rotors and thus to maintain the axial play between the guide and the rotor blades of the turbine parts are required.
  • This lever system includes a pair of levers in each turbine section on both sides of the respective inner housing, one of which has a pivot point that is stationary on the outer housing, while two further pivot points are provided for each pair of levers on the side of the lower housing parts of the displaceable inner housing.
  • the lever system will now be described with reference to FIGS. 1-3.
  • the vertical axial section shown in FIG. 1 shows three partial turbines of a steam turbine generator set, namely the medium-pressure turbine section 1, to the left of which a high-pressure section turbine, not shown, is connected, and the two low-pressure turbine sections 2 and 3, to the right of which there is generally an electrical circuit, not shown Connects the generator.
  • the lever pairs 18 forming the lever system for the temperature-dependent displacement are only shown in the two low-pressure parts 2 and 3. In principle, they can also be used for all other existing partial turbines of a multi-casing steam turbine generator set.
  • Fig.1 the lever pairs designated 18 and 19 are shown in their position when the system is cold and at a standstill.
  • the two pairs of levers 18, 19 provided for each low-pressure part only the rear ones, for the most part, are concealed in the illustration according to FIG. 1 and are therefore drawn with dashed lines.
  • Their arrangements are clearer from FIGS. 2 and 3, which are even more simplified compared to FIG.
  • the spatial arrangement of the pair of levers 18 from FIG. 3 can be seen from it.
  • the same arrangement also applies to the pair of levers 19, but which differs from the pair 18 in terms of the lever dimensions in accordance with the displacement path of the inner housing 12 required relative to the inner housing 11.
  • the lever pairs 18 each consist of a long one on his one end in an outer housing or foundation-fixed bearing block 21 pivotally mounted, two-armed lever 20, hereinafter called the slide lever, with the lever arms a and b, and a shorter, one-armed lever 22, hereinafter called the expansion lever. This is supported at one end on a bearing journal 23 fixed to the inner housing at the level of the shaft axis.
  • the slide lever 20 also has an elongated hole 25 in the height of the shaft axis, in which a further bearing journal 26 provided at the height of the shaft axis engages.
  • a sliding block will be provided in the slot 25, which receives such a pin 26.
  • the lengths x1 and x2 are the distances between the fixed bearing blocks 21 and 28 of the slide levers 20 and 27 from point A as the starting point for the axial displacements of the turbine rotor seated on the shaft 4. From the displacements ⁇ x1 and ⁇ x2 of the inner housing 11 and 12 required for the warm turbine, where ⁇ x2> ⁇ x1, from their starting positions in a cold system and given a distance 1 between the two inner housing journals 23 and 26, the lever arms a1, b1 and a2 can be used , b2 determine the slide lever 20 of the pair of levers 18 and 27 of the pair of levers 19.
  • the distance 1 between the journals 23 and 26 on the inner housing should be as large as the length of the inner housing allows.
  • the length d of the expansion lever can be freely selected, for example within the scope of the length of the inner housing.
  • the expansion lever 22 of the pair of levers 18 is longer than that, 29, of the pair of levers 19, which has to cope with a greater displacement of the pair of levers assigned to it.
  • FIGS. 5 and 6 show the relationship between the thermal expansion ⁇ l of an inner housing between its two articulation points of the expansion lever and the slide lever and the displacement ⁇ x required to maintain the prescribed axial play between the blades.
  • the change ⁇ from ⁇ see FIGS. 5 and 6, can also be neglected because of its slight influence on the pivoting of the slide lever.
  • ⁇ X f (l, a, b) from the proportionality of the lever arms a, b and the circular arcs described by their end points when pivoting by the angle ⁇ : ⁇ X / ⁇ l ⁇ b / a and from this ⁇ X ⁇ (b / a) ⁇ l.
  • the angle ⁇ which depends on a and l, on the sliding angle by which the sliding lever pivots when ⁇ l occurs.
  • the angle ⁇ i.e. the ratio a / l and also a / b, should not be chosen too small.
  • low-friction intermediate layers or coatings will be provided to minimize the adjustment forces on the sliding surfaces of the supports of the inner housing. The adjustment forces can also be kept small by using pendulum supports with very small changes in height when commuting.
  • hydraulic cylinders which communicate with one another and which have piston diameters of different sizes in accordance with the transmission ratio ⁇ l / ⁇ x.
  • a hydraulic cylinder clamped between the end points of the reference path 1 hydrostatically transmits the displacement ⁇ l of its piston to a hydraulic cylinder which displaces the component to be displaced by another by ⁇ x.
  • a coupling between ⁇ l and ⁇ x is also conceivable by using electrical or magnetic variables, the values of which change with ⁇ l and are used to actuate an electrical or electrohydraulic servo device to generate the displacement ⁇ x.
  • the articulation points 23 and 26 on the inner housing for the expansion lever and pivot point of the slide lever will normally be provided on the inner housing lower part in a horizontal plane. If for some reason this is not possible or would be impractical, these articulation points could also be provided on the upper part of the inner housing or one at the bottom and the other at the top and therefore also lie in an inclined plane.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)

Abstract

Um die im Betrieb auftretenden axialen Verschiebungen der Rotoren von Dampfturbinen durch gleichzeitiges Verschieben des Innengehäuses (11, 12) auszugleichen und dadurch das axiale Spiel zwischen den Leit- und Laufschaufelreihen konstant zu halten, ist das Innengehäuse (11, 12) einer Zweigehäuseturbine in ihrem Aussengehäuse (9, 10) diesem gegenüber verschieblich abgestützt. Zur Verschiebung dienen Hebelpaare (18, 19) mit je einem zweiarmigen Schiebehebel (20, 27), die sich auf aussengehäusefeste Lagerböcke (21, 28) abstützen, und einem damit zusammenwirkenden Dehnungshebel (22, 29). Eine durch die Betriebswärme auftretende Verlängerung (Δl) eines zwischen zwei Lagerzapfen (23, 26) liegenden Abschnitts der Länge (l) des Innengehäuses (11, 12) überträgt der Dehnungshebele (22, 29) auf den Schiebehebel (20, 27), dessen Schwenkung um den Lagerzapfen (26) im Uhrzeigersinn die erforderliche Verschiebung (Δx1, Δx2) bewirkt.In order to compensate for the axial displacements of the rotors of steam turbines during operation by simultaneously displacing the inner casing (11, 12) and thereby keeping the axial play between the guide and rotor blade rows constant, the inner casing (11, 12) of a two-casing turbine is in its outer casing (9, 10) slidably supported against this. Lever pairs (18, 19), each with a two-armed sliding lever (20, 27), which are supported on bearing blocks (21, 28) fixed to the outer housing, and a cooperating expansion lever (22, 29) are used for the displacement. An extension (Δl) of the section of length (l) of the inner housing (11, 12) lying between two bearing journals (23, 26) is transmitted by the operating heat of the expansion lever (22, 29) to the slide lever (20, 27), the Swiveling around the trunnion (26) clockwise causes the required displacement (Δx1, Δx2).

Description

Die vorliegende Erfindung betrifft einen Mehrgehäusedampfturbosatz mit einer Hochdruckteilturbine, einer Mitteldruckteilturbine und mindestens einer Niederdruckteilturbine, welche Niederdruckteilturbinen zweigehäusig mit je einem Aussengehäuse und einem innerhalb desselben und gegenüber diesem verschieblich gelagerten Innengehäuse ausgeführt sind, wobei die Läufer aller Teilturbinen auf einem gemeinsamen Wellenstrang sitzen, der an einem zwischen der Mitteldruckteilturbine und der Hoch­druckteilturbine angeordneten Axiallager axial nach beiden Richtungen fixiert ist, sowie mit Elementen zum Ausgleich der durch die Wärmedehnungen im Betrieb auftretenden axialen Ver­schiebungen der Läufer gegenüber deren InnengehäusenThe present invention relates to a multi-casing steam turbine set with a high-pressure part turbine, a medium-pressure part turbine and at least one low-pressure part turbine, which low-pressure part turbines are designed with two housings, each with an outer housing and an inner housing that is mounted inside and displaceable relative to the latter, with the rotors of all the partial turbines sitting on a common shaft train an axial bearing arranged between the medium-pressure part turbine and the high-pressure part turbine is fixed axially in both directions, and with elements for compensating for the axial displacements of the rotor relative to their inner housings that occur due to the thermal expansions during operation

Technisches GebietTechnical field

Bei Mehrgehäuseturbinen, die neben einer Hochdruckteilturbine eine Mitteldruckteilturbine und mindestens noch eine Nieder­druckteilturbine aufweisen, sind Massnahmen vorzusehen, die dafür sorgen, dass die mindesterforderlichen Axialspiele zwi­schen einander benachbarten Lauf- und Leitschaufelkränzen im Betrieb aufrechterhalten bleiben. Bei solchen Turbinen, deren Teilturbinen als Zweigehäuseturbinen mit einem Innen- und ei­nem Aussengehäuse ausgeführt sind, bestehen solche Massnahmen gewöhnlich aus Verbindungsgliedern zwischen dem Innengehäuse der Mitteldruckturbine und dem Innengehäuse der anschliessen­den Niederdruckturbine sowie zwischen deren Innengehäuse und dem Innengehäuse einer eventuellen weiteren Niederdruckturbine und so fort, falls noch mehr Niederdruckteilturbinen vorhanden sein sollten. Dabei ist etwa eine Lagerstelle zwischen der Hochdruckteilturbine, im folgenden kurz "Hochdruckteil" ge­nannt, und der Mitteldruckteilturbine, im folgenden als "Mitteldruckteil" bezeichnet, als Fixpunkt ausgebildet, von dem ausgehend der Hochdruckteil und der Mitteldruckteil mit den anschliessenden Niederdruckteilen sich in entgegengesetz­ten Richtungen ungehindert ausdehnen können.In the case of multi-casing turbines which, in addition to a high-pressure turbine section, have a medium-pressure turbine section and at least one low-pressure turbine section, measures must be taken to ensure that the minimum required axial play between adjacent rotor and guide vane rings is maintained during operation. In such turbines, the partial turbines of which are designed as two-casing turbines with an inner and an outer casing, such measures usually consist of connecting links between the inner casing of the medium-pressure turbine and the inner casing of the adjoining low-pressure turbine, and between their inner casing and the inner casing of a possible further low-pressure turbine, and so on, if there are more low-pressure turbine parts should be. For example, a bearing point between the high-pressure part turbine, hereinafter referred to as "high-pressure part", and the medium-pressure part turbine, hereinafter referred to as "medium-pressure part", is designed as a fixed point from which the high-pressure part and the medium-pressure part with the subsequent low-pressure parts can move freely in opposite directions can expand.

Stand der TechnikState of the art

Eine Mehrgehäuseturbine mit einer solchen Konseption für die Kompensation der Axialspieländerungen infolge der Wärmedehnun­gen ist in der DE-PS 1 216 322 von Rateau beschrieben. Dabei überträgt ein eingehäusiger Mitteldruckteil, der die Verschie­bung durch die Wärmedehnungen gemeinsam mit seinem Turbinen­läufer mitmacht, diese über Kuppelstangen, die sich in das Aussengehäuse des zweigehäusig ausgeführten Niederdruckteiles hinein erstrecken, auf Innengehäuse, an dem sie angelenkt sind. Die Welle mit dem Turbinenläufer verschiebt sich wegen der im wesentlichen gleichen Temperatur wie jene des Innenge­häuses um dieselbe Strecke wie dieses mit seiner Beschaufe­lung, so dass die Axialspiele zwischen den Leit- und den Lauf­schaufelkränzen in praktisch gleicher Grösse wie im kalten Zu­stand erhalten bleiben. Der Fixpunkt der Welle, von dem aus sich einerseits der Mitteldruckteil mit den daran angekoppel­ten Innengehäusen der Niederdruckteile und andererseits in der entgegengesetzten Richtung der Hochdruckteil frei ausdehnen und verschieben können, befindet sich an einer Lagerstelle zwischen letzterem und dem Mitteldruckteil.A multi-casing turbine with such a choice for the compensation of the axial play changes due to thermal expansion is described in DE-PS 1 216 322 by Rateau. A single-case medium pressure part, which takes part in the displacement due to the thermal expansions together with its turbine runner, transmits these via coupling rods, which extend into the outer housing of the low-pressure part with two housings, to the inner housing to which they are articulated. The shaft with the turbine rotor shifts because of the essentially the same temperature as that of the inner housing by the same distance as this with its blading, so that the axial play between the guide and rotor blades is maintained in practically the same size as in the cold state. The fixed point of the shaft, from which the medium-pressure part with the inner housings of the low-pressure parts coupled to it and on the other hand freely expand and shift in the opposite direction of the high-pressure part, is located at a bearing point between the latter and the medium-pressure part.

Problematisch sind bei dieser Ausführung die Abdichtungen an den Durchführungsstellen der Kuppelstangen an den Aussengehäu­sen der Niederdruckteile. Im erwähnten Patent werden hierfür Wellrohre oder Faltenbälge oder Stopfbüchsen oder dergleichen vorgeschlagen, die jedoch allesamt eine mögliche Fehlerquelle darstellen.The problem with this version are the seals at the lead-through points of the coupling rods on the outer casings of the low-pressure parts. In the mentioned patent, corrugated pipes or bellows or stuffing boxes or the like are used for this proposed, but all of which represent a possible source of error.

Die vorliegende Erfindung entstand aus der Aufgabe, die ge­nannten Dichtungsprobleme bei einer Mehrgehäusedampfturbine zu vermeiden und die Einrichtung zur Erhaltung der Axialspiele zwischen den Leit- und den Laufschaufelkränzen der Nieder­druckteile möglichst einfach, unkompliziert und betriebssicher zu gestalten.The present invention arose from the task of avoiding the sealing problems mentioned in a multi-casing steam turbine and of designing the device for maintaining the axial clearances between the guide vanes and the rotor blade rings of the low-pressure parts as simply, uncomplicatedly and reliably as possible.

Definition der ErfindungDefinition of the invention

Der erfindungsgemässe Mehrgehäusedampfturbosatz ist dadurch gekennzeichnet,dass zur Aufrechterhaltung der Axialspiele zwi­schen den Leitbeschaufelungen und den Laufbeschaufelungen der Teilturbinen bei Betriebstemperatur beidseitig der Innenge­häuse je ein Hebelpaar vorgesehen ist, mit einem zweiarmigen Schiebehebel und einem an diesen über eine Achse angelenkten einarmigen Dehnungshebel, wobei das andere Ende des Schiebehe­bels an einem aussengehäusefesten Lagerbock und das andere Ende des Dehnungshebels an einem innengehäusefesten Lagerzap­fen angelenkt ist, und dass der Schiebehebel zwischen seinen Anlenkpunkten am Lagerbock und am Dehnungshebel mit einem Langloch in einen innengehäusefesten Lagerzapfen eingreift, dessen Achse den Schiebehebel in seine Hebelarme unterteilt, wobei eine im Betrieb durch die Wärmedehnung verursachte Ver­längerung Δl des Abstandes zwischen den beiden innengehäusefe­sten Lagerzapfen über den Dehnungshebel und über den Schiebe­hebel eine Verschiebung Δx des Innengehäuses gegenüber den aussengehäusefesten Lagerböcken erzeugt.The multi-housing steam turbine set according to the invention is characterized in that in order to maintain the axial play between the guide blades and the rotor blades of the turbine parts at operating temperature, a pair of levers is provided on both sides of the inner housing, with a two-armed slide lever and a one-armed expansion lever articulated thereon via an axis, the other end of the slide lever on an outer housing-fixed bearing block and the other end of the expansion lever is articulated on a bearing pin fixed on the inner housing, and that the sliding lever engages with an elongated hole in an inner housing-fixed bearing pin between its articulation points on the bearing block and on the expansion lever, the axis of which divides the sliding lever into its lever arms, whereby an extension Δl in operation caused by the thermal expansion of the distance between the two inner housing-fixed bearing journals via the expansion lever and the sliding lever a displacement Δx of the inner housing compared to the bearing blocks fixed to the outer housing.

Beschreibung der FigurenDescription of the figures

Anhand der in der Zeichnung dargestellten Figuren wird die Er­findung im folgenden näher beschrieben. In der Zeichnung stel­len schematisiert dar:

  • Fig.1 einen axialen Längsschnitt einer Mitteldruck- und zweier Niederdruckteilturbinen einer Dampfkraftan­lage, die
  • Fig. 2 und 3 einen Querschnitt bzw. einen Längsschnitt durch die beiden Niederdruckteilturbinen nach Fig .1 ent­sprechend den Schnittverläufen III-III und II-II, und die
  • Fig. 4 bis 6 erläuternde Skizzen zu den kniematischen Bezie­hungen zwischen den Elementen der Vorstelleinrich­tung für das Innengehäuse.
The invention is described in more detail below with reference to the figures shown in the drawing. In the drawing there are shown schematically:
  • 1 shows an axial longitudinal section of a medium-pressure and two low-pressure turbine parts of a steam power plant, the
  • 2 and 3 show a cross section and a longitudinal section through the two low-pressure turbine parts according to FIG. 1 corresponding to the section profiles III-III and II-II, and
  • Fig. 4 to 6 explanatory sketches on the knee relations between the elements of the adjusting device for the inner housing.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die Fig.1 zeigt eine Mitteldruckteilturbine 1, deren links davon befindliche, nicht dargestellte Hochdruckteilturbine sowie zwei oder gegebenenfalls mehrere Niedruckturbinen 2 und 3 ihre Leistung über einen gemeinsamen Wellenstrang 4 an einen nicht dargestellten, am rechten Ende des Wellenstranges angekuppelten elektrischen Generator abzugeben. Der Wellenstrang 4 ist in einem zwischen dem Hochdruckteil und dem Mitteldruckteil 1 befindlichen Lagergehäuse 5 durch ein doppelseitiges Axiallager 6 nach beiden Richtungen hin fixiert. Von diesem Fixpunkt aus kann sich der nicht dargestellte Hochdruckteil nach links unbehindert ausdehnen, da sich sein Gehäuse auf bekannte Weise über Auflagerpratzen auf Gleitbahnen verschieblich abstützt, wobei das Kippen um die Wellenachse infolge des Reaktionsmoments durch eine Abstützung verhindert wird, die eine axiale Halterung des Mittelgehäuses bildet. Die Figur zeigt eine solche Abstützung 7 für das Gehäuse 8 des Mitteldruckteils 1. Das Gehäuse 8 und das Lagergehäuse 5 sind axial fest miteinander verbunden.1 shows a medium-pressure turbine section 1, the high-pressure turbine section, not shown to the left of it, and two or possibly more low-pressure turbines 2 and 3 deliver their power via a common shaft train 4 to an electrical generator, not shown, coupled to the right end of the shaft train. The shaft train 4 is fixed in a bearing housing 5 located between the high-pressure part and the medium-pressure part 1 by a double-sided axial bearing 6 in both directions. From this fixed point, the high-pressure part, not shown, can expand to the left unhindered, since its housing extends in a known manner by means of support claws slidably supported on slideways, wherein the tilting about the shaft axis due to the reaction torque is prevented by a support which forms an axial support of the center housing. The figure shows such a support 7 for the housing 8 of the medium pressure part 1. The housing 8 and the bearing housing 5 are axially fixed together.

Die Aussengehäuse 9 und 10 der Niederdruckteile 2 bzw. 3 sind auf der Grundplatte befestigt und ihre Innengehäuse 11 bzw. 12 im betreffenden Aussengehäuse diesem gegenüber ebenfalls auf bekannte Weise axialverschieblich und gegen Kippen gesichert gelagert. Die Dampfauslassleitung an der Mitteldruckteiltur­bine 1 ist mit 13 und die beiden Dampfzuleitungen zu den Nie­derdruckturbinen 2 und 3 sind mit 14 und 15 bezeichnet.The outer housings 9 and 10 of the low-pressure parts 2 and 3 are fastened to the base plate and their inner housings 11 and 12 in the outer housing in question are also axially displaceable in a known manner and secured against tipping. The steam outlet line on the medium-pressure turbine section 1 is designated 13 and the two steam supply lines to the low-pressure turbines 2 and 3 are designated 14 and 15.

Die erfindungsgemässe Vereinfachung gegenüber dem eingangs ge­nannten Stand der Technik besteht darin, dass anstelle von Kuppelstangen oder sonstigen starren Übertragungsgliedern zwi­schen den einzelnen Teilturbinen ein Hebelsystem verwendet wird, das im Betriebszustand der Turbine die Verschiebungen der Innengehäuse bewerkstelligt, welche zum Ausgleich der Verschiebungen der auf dem Wellenstrang sitzenden Rotoren und damit zur Aufrechterhaltung der Axialspiele zwischen den Leit- und den Laufbeschaufelungen der Teilturbinen erforderlich sind.The simplification according to the invention compared to the prior art mentioned at the outset is that instead of coupling rods or other rigid transmission members between the individual partial turbines, a lever system is used which, in the operating state of the turbine, brings about the displacements of the inner housing, which compensate for the displacements of those on the shaft train seated rotors and thus to maintain the axial play between the guide and the rotor blades of the turbine parts are required.

Zu diesem Hebelsystem gehören in jeder Teilturbine je ein He­belpaar beidseits des jeweiligen Innengehäuses, dessen einer Anlenkpunkt sich ortsfest am Aussengehäuse befindet, während zwei weitere Anlenkpunkte für jedes Hebelpaar seitlich an den Gehäuseunterteilen der verschiebbaren Innengehäuse vorgesehen sind.This lever system includes a pair of levers in each turbine section on both sides of the respective inner housing, one of which has a pivot point that is stationary on the outer housing, while two further pivot points are provided for each pair of levers on the side of the lower housing parts of the displaceable inner housing.

Die Vorteile dieser Konzeption bestehen, wie aus der folgenden genannten Beschreibung noch deutlich wird, gegenüber den ein­gangs beschriebenen bekannten Bauarten vor allem darin, dass die Verschiebung jedes einzelnen Innengehäuses individuell, unabhängig von den benachbarten, erfolgt. Sodann geschieht diese Verschiebung selbsttätig in Abhängigkeit von der in der betreffenden Teilturbine herrschenden Temperatur. Ferner fal­len die oben beschriebenen Dichtprobleme der bekannten Bauar­ten weg, da zwischen den die Verschiebung bewirkenden Elemen­ten der einzelnen Teilturbinen keine körperlichen Verbindungen bestehen und die erwähnten Dichteinrichtungen sich daher erüb­rigen.The advantages of this concept, as will become clear from the description mentioned below, above all compared to the known designs described at the outset are that each individual inner housing is displaced individually, independently of the neighboring ones. Then happens this shift automatically as a function of the temperature prevailing in the sub-turbine in question. Furthermore, the sealing problems of the known types described above are eliminated, since there are no physical connections between the elements of the individual partial turbines which cause the displacement, and the sealing devices mentioned are therefore unnecessary.

Das Hebelsystem wird nun anhand der Fig. 1 - 3 näher beschrie­ben. Der in Fig.1 dargestellte vertikale Axialschnitt zeigt drei Teilturbinen eines Dampfturbogeneratorsatzes, nämlich die Mitteldruckteilturbine 1, an die sich links davon eine nicht dargestellte Hochdruckteilturbine anschliesst, sowie die zwei Niederdruckteilturbinen 2 und 3, an die sich rechts davon in der Regel ein nicht gezeigter elektrischer Generator an­schliesst. In Fig.1 sind die das Hebelsystem für die tempera­turabhängige Verschiebung bildenden Hebelpaare 18 der Einfach­heit halber nur in den beiden Niederdruckteilen 2 und 3 einge­zeichnet. Prinzipiell in gleicher Weise sind sie auch für alle anderen vorhandenen Teilturbinen eines mehrgehäusigen Dampf­turbogeneratorsatzes anwendbar.The lever system will now be described with reference to FIGS. 1-3. The vertical axial section shown in FIG. 1 shows three partial turbines of a steam turbine generator set, namely the medium-pressure turbine section 1, to the left of which a high-pressure section turbine, not shown, is connected, and the two low-pressure turbine sections 2 and 3, to the right of which there is generally an electrical circuit, not shown Connects the generator. In FIG. 1, for the sake of simplicity, the lever pairs 18 forming the lever system for the temperature-dependent displacement are only shown in the two low-pressure parts 2 and 3. In principle, they can also be used for all other existing partial turbines of a multi-casing steam turbine generator set.

In Fig.1 sind die mit 18 bzw. 19 bezeichneten Hebelpaare in ihrer Stellung bei kalter Anlage, im Stillstand, gezeigt. Von den je zwei für jeden Niederdruckteil vorgesehenen Hebelpaaren 18, 19 sind in der Darstellung nach Fig.1 nur die jeweils hin­teren, zum grössten Teil verdeckt vorhanden und daher entsprechend strichliert gezeichnet. Ihre Anordnungen gehen aus den Fig.2 und 3, die gegenüber Fig.1 noch weiter verein­facht sind, klarer hervor.In Fig.1 the lever pairs designated 18 and 19 are shown in their position when the system is cold and at a standstill. Of the two pairs of levers 18, 19 provided for each low-pressure part, only the rear ones, for the most part, are concealed in the illustration according to FIG. 1 and are therefore drawn with dashed lines. Their arrangements are clearer from FIGS. 2 and 3, which are even more simplified compared to FIG.

Die Fig.2 entspricht dem in Fig.3 eingezeichneten Schnittver­lauf II-II. Man erkennt aus ihr die räumliche Anordnung des Hebelpaares 18 aus Fig. 3. Die gleiche Anordnung gilt auch für das Hebelpaar 19, das sich aber vom Paar 18 durch die Hebelab­messungen unterscheidet entsprechend dem gegenüber dem Innen­gehäuse 11 erforderlichen Verschiebungsweg des Innengehäuses 12. Die Hebelpaare 18 bestehen aus je einem langen, an seinem einen Ende in einem aussengehäuse- oder fundamentfesten Lager­bock 21 schwenkbar gelagerten, zweiarmigen Hebel 20, im fol­genden Schiebehebel genannt, mit den Hebelarmen a und b, und einem kürzeren, einarmigen Hebel 22, im folgenden Dehnungshe­bel genannt. Dieser ist mit seinem einen Ende auf einem innen­gehäusefesten Lagerzapfen 23 in Höhe der Wellenachse gelagert. Die beiden anderen Enden der zwei Hebel 20 und 22 sind durch eine Achse 24 gegeneinander schwenkbar miteinander verbunden. Der Schiebehebel 20 weist ferner in Höhe der Wellenachse aus kinematischen Gründen ein Langloch 25 auf, in dem ein weiterer, in Höhe der Wellenachse vorgesehener innengehäusefester Lagerzapfen 26 eingreift. Praktisch wird im Langloch 25 natürlich ein Gleitstein vorgesehen sein, der einen solchen Zapfen 26 aufnimmt.2 corresponds to the section II-II shown in FIG. The spatial arrangement of the pair of levers 18 from FIG. 3 can be seen from it. The same arrangement also applies to the pair of levers 19, but which differs from the pair 18 in terms of the lever dimensions in accordance with the displacement path of the inner housing 12 required relative to the inner housing 11. The lever pairs 18 each consist of a long one on his one end in an outer housing or foundation-fixed bearing block 21 pivotally mounted, two-armed lever 20, hereinafter called the slide lever, with the lever arms a and b, and a shorter, one-armed lever 22, hereinafter called the expansion lever. This is supported at one end on a bearing journal 23 fixed to the inner housing at the level of the shaft axis. The other two ends of the two levers 20 and 22 are pivotally connected to one another by an axis 24. For kinematic reasons, the slide lever 20 also has an elongated hole 25 in the height of the shaft axis, in which a further bearing journal 26 provided at the height of the shaft axis engages. In practice, of course, a sliding block will be provided in the slot 25, which receives such a pin 26.

Die Längen x₁ und x₂ sind die Abstände der fundamentfesten La­gerböcke 21 und 28 der Schiebehebel 20 bzw. 27 von der Stelle A als Ausgangspunkt für die axialen Verschiebungen der auf der Welle 4 sitzenden Turbinenläufer. Aus den für die warme Tur­bine erforderlichen Verschiebungen Δx₁ und Δx₂ der Innenge­häuse 11 bzw. 12, wobei Δx₂ > Δx₁, aus ihren Ausgangsstellungen bei kalter Anlage und gegebenem Abstand 1 der beiden innengehäusefesten Lagerzapfen 23 und 26 lassen sich die Hebelarme a₁, b₁ bzw. a₂, b₂ der Schiebehebel 20 des Hebelpaares 18 bzw. 27 des Hebelpaares 19 bestimmen. Der Abstand 1 zwischen den Lagerzapfen 23 und 26 am Innengehäuse sollte dabei so gross sein wie es die Länge des Innengehäuses gestattet. Frei wählbar ist dabei, etwa im Rahmen der Länge des Innengehäuses, die Länge d des Dehnungshebels. In Fig .3 ist der Dehnungshebel 22 des Hebelpaares 18 länger als jener, 29, des Hebelpaares 19, das eine grössere Verschiebung des ihm zugeordneten Hebelpaares zu bewältigen hat.The lengths x₁ and x₂ are the distances between the fixed bearing blocks 21 and 28 of the slide levers 20 and 27 from point A as the starting point for the axial displacements of the turbine rotor seated on the shaft 4. From the displacements Δx₁ and Δx₂ of the inner housing 11 and 12 required for the warm turbine, where Δx₂> Δx₁, from their starting positions in a cold system and given a distance 1 between the two inner housing journals 23 and 26, the lever arms a₁, b₁ and a₂ can be used , b₂ determine the slide lever 20 of the pair of levers 18 and 27 of the pair of levers 19. The distance 1 between the journals 23 and 26 on the inner housing should be as large as the length of the inner housing allows. The length d of the expansion lever can be freely selected, for example within the scope of the length of the inner housing. In Fig. 3, the expansion lever 22 of the pair of levers 18 is longer than that, 29, of the pair of levers 19, which has to cope with a greater displacement of the pair of levers assigned to it.

Aus Fig.4 geht der Zusammenhang zwischen der Wärmedehnung Δl eines Innengehäuses zwischen seinen beiden Anlenkpunkten des Dehnungshebels und des Schiebehebels und der zur Einhaltung der vorgeschriebenen Axialspiele zwischen den Beschaufelungen erforderlichen Verschiebung Δx hervor. Dabei kann die Ver­ schiebung des Gelenks 11 bzw. 24, das den oberen Arm a des Schiebehebels mit dem Dehnungshebel verbindet und in Fig.4 mit ≈Δl bezeichnet ist, wegen des im allgemeinen kleinen Winkels α zwischen dem Dehnungshebel 22 bzw. 29 und der Horizontalen als gleich Δl angenommen werden. Die Änderung Δα von α, siehe die Fi.5 und 6, kann wegen ihres geringfügigen Einflusses auf die Schwenkung des Schiebehebels ebenfalls vernachlässigt werden. Mit diesen Annahmen gilt für ΔX = f( l,a,b) aus der Proportionalität der Hebelarme a, b und der von ihren Endpunkten beim Schwenken um den Winkel σ beschriebenen Kreis­bögen: ΔX/Δl ≈ b/a und daraus ΔX ≈ (b/a)Δl.4 shows the relationship between the thermal expansion Δl of an inner housing between its two articulation points of the expansion lever and the slide lever and the displacement Δx required to maintain the prescribed axial play between the blades. The Ver shift of the joint 11 or 24, which connects the upper arm a of the slide lever with the expansion lever and is designated in Fig.4 with ≈Δl, because of the generally small angle α between the expansion lever 22 or 29 and the horizontal as equal to Δl be accepted. The change Δα from α, see FIGS. 5 and 6, can also be neglected because of its slight influence on the pivoting of the slide lever. With these assumptions, the following applies to ΔX = f (l, a, b) from the proportionality of the lever arms a, b and the circular arcs described by their end points when pivoting by the angle σ: ΔX / Δl ≈ b / a and from this ΔX ≈ (b / a) Δl.

Für ein konkretes Beispiel mit 1 = 25000 mm, a = 500 und b = 1000 mm sowie Δl = 10 mm ergibt sich eine Verschiebung des In­nengehäuses um 20 mm. Der Winkel α ist dabei ≈ 11°. Durch ent­sprechende Wahl der Arme a und b des Schiebehebels lassen sich bei Kenntnis der wärmedehnung Δl beliebige Verschiebungen Δx der Innengehäuse erhalten.For a specific example with 1 = 25000 mm, a = 500 and b = 1000 mm and Δl = 10 mm, the inner housing is shifted by 20 mm. The angle α is ≈ 11 °. By appropriate selection of the arms a and b of the slide lever, any displacements Δx of the inner housing can be obtained with knowledge of the thermal expansion Δl.

Die Fig.5 und 6 zeigen den Einfluss der Grösse des Winkels α, der von a und l abhängt, auf den Schiebewinkel , um den der Schiebehebel bei Auftreten von Δl schwenkt. Je kleiner α gewählt wird, um so grösser ist σ und, bei gegebenem b, die Verschiebung Δx, um so grösser aber andererseits, bei gegebenem Verschiebewiderstand die davon abhängige Behinderung der thermischen Dehnung Δl des Abstandes l der Anlenkpunkte 23 und 26 am Innengehäuse. Um die damit verbundenen Verspannungen zu vermeiden, sollte der Winkel α, d.h., das Verhältnis a/l und auch a/b, nicht zu klein gewählt werden. Überdies wird man zur Minimierung der Verstellkräfte an den Gleitflächen der Auflager des Innengehäuses reibungsarme Zwischenlagen oder Be­schichtungen vorsehen. Auch durch Verwendung von Pendelstützen mit sehr geringen Höhenänderungen beim Pendeln lassen sich die Verstellkräfte klein halten.5 and 6 show the influence of the size of the angle α, which depends on a and l, on the sliding angle by which the sliding lever pivots when Δl occurs. The smaller α is selected, the greater is σ and, given b, the displacement Δx, but the greater, on the other hand, the given impedance to the thermal expansion Δl of the distance l of the articulation points 23 and 26 on the inner housing for a given displacement resistance. In order to avoid the associated tension, the angle α, i.e. the ratio a / l and also a / b, should not be chosen too small. In addition, low-friction intermediate layers or coatings will be provided to minimize the adjustment forces on the sliding surfaces of the supports of the inner housing. The adjustment forces can also be kept small by using pendulum supports with very small changes in height when commuting.

Das vorliegende Prinzip, eine Verschiebung gewünschter Grösse eines thermisch beanspruchten Gehäuses gegenüber einem anderen Bauteil von der thermischen Längenänderung einer Abmessung dieses Gehäuses selbst abzuleiten, ist auch auf andere Fälle anwendbar, bei denen Wärmedehnungen andernfalls die Funktion einer Maschine beeinträchtigen oder zunichte machen würden.The present principle, a shift in the desired size of a thermally stressed housing compared to another component from the thermal change in length of a dimension deriving this housing itself can also be applied to other cases in which thermal expansion would otherwise impair or destroy the function of a machine.

Eine andere, bei thermischen Maschinen mit hohen Arbeitstem­peraturen aber wohl schwieriger ausführbare Möglichkeit, dieses Prinzip anzuwenden, bieten miteinander kommunizierende Hydraulikzylinder mit entsprechend dem Übersetzungsverhältnis Δl/Δx verschieden grossen Kolbendurchmessern. Ein zwischen den Endpunkten der Referenzstrecke l eingespannter Hydraulikzylin­der leitet die Verschiebung Δl seines Kolbens hydrostatisch an einen Hydraulikzylinder weiter, der den zu verschiebenden Bau­teil gegenüber einem anderen um Δx verschiebt.Another possibility of using this principle, which is probably more difficult to implement in thermal machines with high working temperatures, is provided by hydraulic cylinders which communicate with one another and which have piston diameters of different sizes in accordance with the transmission ratio Δl / Δx. A hydraulic cylinder clamped between the end points of the reference path 1 hydrostatically transmits the displacement Δl of its piston to a hydraulic cylinder which displaces the component to be displaced by another by Δx.

Denkbar ist auch eine Kupplung zwischen Δl und Δx durch Benut­zung elektrischer oder magnetischer Grössen, deren Werte sich durch Δl ändern und zur Betätigung einer elektrischen oder elektrohydraulischen Servoeinrichtung zur Erzeugung der Ver­schiebung Δx benutzt werden.
Die Anlenkpunkte 23 und 26 am Innengehäuse für den Dehnungshe­bel und Drehpunkt des Schiebehebels wird man normalerweise am Innengehäuseunterteil in einer horizontalen Ebene vorsehen. Falls dies aus irgendwelchen Gründen nicht möglich ist oder unpraktisch wäre, könnten diese Anlenkpunkte auch am Innengehäuseoberteil oder der eine unten und der andere oben vorgesehen sein und daher auch in einer geneigten Ebene liegen.A coupling between Δl and Δx is also conceivable by using electrical or magnetic variables, the values of which change with Δl and are used to actuate an electrical or electrohydraulic servo device to generate the displacement Δx.
The articulation points 23 and 26 on the inner housing for the expansion lever and pivot point of the slide lever will normally be provided on the inner housing lower part in a horizontal plane. If for some reason this is not possible or would be impractical, these articulation points could also be provided on the upper part of the inner housing or one at the bottom and the other at the top and therefore also lie in an inclined plane.

Claims (1)

Mehrgehäusedampfturbosatz, mit einer Hochdruckteilturbine, einer Mitteldruckteilturbine (1) und mindestens einer Nieder­druckteilturbine (2, 3), welche Niederdruckteilturbinen zwei­gehäusig mit je einem Aussengehäuse (9, 10) und einem inner­halb desselben und gegenüber diesem verschieblich gelagerten Innengehäuse (11, 12) ausgeführt sind, wobei die Läufer (16, 17) aller Teilturbinen (1, 2, 3) auf einem gemeinsamen Wellen­strang (4) sitzen, der an einem zwischen der Mitteldruckteil­turbine (1) und der Hochdruckteilturbine angeordneten Axiallager (6) axial nach beiden Richtungen fixiert ist, dadurch gekennzeichnet, dass zur Aufrechterhaltung der Axial­spiele zwischen den Leitbeschaufelungen und den Laufbeschaufe­lungen der Teilturbinen (2, 3) bei Betriebstemperatur beidseitig der Innengehäuse (11, 12) je ein Hebelpaar (18, 19) vorgesehen ist, mit einem zweiarmigen Schiebehebel (20, 27) und einem an diesen über eine Achse (24) angelenkten einarmigen Dehnungshebel (22, 29), wobei das andere Ende des Schiebehebels (20, 27) an einem aussengehäusefesten Lagerbock (21, 28) und das andere Ende des Dehnungshebels (22, 29) an einem innengehäusefesten Lagerzapfen (23) angelenkt ist, und dass der Schiebehebel (20, 27) zwischen seinen Anlenkpunkten am Lagerbock (21, 28) und am Dehnungshebel (22) mit einem Langloch (25) in einem innengehäusefesten Lagerzapfen (26) eingreift, dessen Achse den Schiebehebel in seine Hebelarme (a, b) unterteilt, wobei eine im Betrieb durch die Wärmedehnung verursachte Verlängerung Δl des Abstandes (l) zwischen den beiden innengehäusefesten Lagerzapfen (23, 26) über den Dehnungshebel (22, 29) und über den Schiebehebel (20, 27) eine Verschiebung Δx des Innengehäuses (11, 12) gegenüber den aussengehäusefesten Lagerböcken (21, 28) erzeugt.Multi-casing steam turbine set, with a high-pressure part turbine, a medium-pressure part turbine (1) and at least one low-pressure part turbine (2, 3), which low-pressure part turbines are constructed in two casings, each with an outer casing (9, 10) and an inner casing (11, 12) that is displaceably mounted within the casing , The rotors (16, 17) of all the partial turbines (1, 2, 3) are seated on a common shaft train (4) which is fixed axially in both directions to an axial bearing (6) arranged between the medium-pressure turbine part (1) and the high-pressure turbine part , characterized in that a pair of levers (18, 19) is provided on both sides of the inner casing (11, 12) to maintain the axial play between the guide blades and the rotor blades of the partial turbines (2, 3), with a two-armed sliding lever (20, 27) and a one-armed expansion lever (22, 29) articulated thereon via an axle (24), the other end of the slide lever (20, 27) being articulated on a bearing block (21, 28) fixed to the outer housing and the other end of the expansion lever (22, 29) being articulated on a bearing journal (23) fixed on the inner housing, and in that the sliding lever (20, 27) between its articulation points on the bearing block (21, 28) and on the expansion lever (22) with an elongated hole (25) engages in a bearing journal (26) fixed to the inner housing, the axis of which divides the sliding lever into its lever arms (a, b), one during operation by the thermal expansion caused an extension Δl of the distance (l) between the two inner bearing journals (23, 26) via the expansion lever (22, 29) and the slide lever (20, 27) a displacement Δx of the inner housing (11, 12) compared to the outer housing Bearing blocks (21, 28) generated.
EP89122742A 1988-12-23 1989-12-09 Multiple housing steam turbine unit Expired - Lifetime EP0374645B1 (en)

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US6092986A (en) * 1996-07-24 2000-07-25 Siemens Aktiengesellschaft Turbine plant having a thrust element, and thrust element
EP1764485A1 (en) 2005-09-15 2007-03-21 Siemens Aktiengesellschaft Device for the support of rotary machines of a stationary turboset
US8525362B2 (en) 2010-09-03 2013-09-03 Alstom Technology Ltd Steam turbine plant
DE102011111707B4 (en) 2010-09-03 2021-07-29 General Electric Technology Gmbh Steam turbine plant

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US5051061A (en) 1991-09-24
EP0374645B1 (en) 1992-11-04
DE58902622D1 (en) 1992-12-10

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