EP2775096A2 - Diffuser assembly for an exhaust housing of a steam turbine, and steam turbine with the same - Google Patents

Diffuser assembly for an exhaust housing of a steam turbine, and steam turbine with the same Download PDF

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Publication number
EP2775096A2
EP2775096A2 EP14151870.4A EP14151870A EP2775096A2 EP 2775096 A2 EP2775096 A2 EP 2775096A2 EP 14151870 A EP14151870 A EP 14151870A EP 2775096 A2 EP2775096 A2 EP 2775096A2
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EP
European Patent Office
Prior art keywords
steam
diffuser
flow
blade ring
steam turbine
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
EP14151870.4A
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German (de)
French (fr)
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EP2775096B1 (en
EP2775096A3 (en
Inventor
Andreas Mucha
Christoph Sporbert
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Siemens AG
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Siemens AG
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Publication of EP2775096A3 publication Critical patent/EP2775096A3/en
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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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/141—Shape, i.e. outer, aerodynamic form
    • F01D5/142—Shape, i.e. outer, aerodynamic form of the blades of successive rotor or stator blade-rows
    • F01D5/143—Contour of the outer or inner working fluid flow path wall, i.e. shroud or hub contour
    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/08—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator
    • F01D11/10—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator using sealing fluid, e.g. steam
    • 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
    • F01D25/30—Exhaust heads, chambers, or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines

Definitions

  • the present invention relates to a diffuser assembly for an exhaust steam housing of a steam turbine according to the preamble of claim 1, and to a steam turbine equipped with such a diffuser arrangement.
  • Such a diffuser arrangement ie comprising a diffuser having an inlet end for receiving exhaust steam in the flow direction behind a provided with a shroud blade ring of a final stage of the steam turbine, and with a diverging viewed in the flow direction annular wall which limits a flowing into the Abdampfgepuruse diffuser flow path is made the general state of the art concerning steam turbine plants.
  • the final stage of condensing steam turbines is usually followed by a diffuser to convert kinetic energy of the exhaust steam into potential energy before the exhaust steam is supplied to the condenser of the relevant water-steam cycle.
  • the static pressure of the exhaust steam is thereby advantageously raised (to a "condenser inlet pressure"), which is why one speaks in this context of a pressure recovery.
  • this object is achieved by a diffuser arrangement according to claim 1 or a steam turbine equipped therewith (claim 5).
  • the injected boundary layer flow along the annular wall causes a reduction in the risk of boundary layer separation, wherein at the same time advantageously the vapor leakage amount over the blade ring is reduced by the sealing steam flow.
  • the axial extent of the flow guide lip is greater than 50% of the axial extent of the shroud and / or the axial extent of the flow guide lip is less than 200% of the axial extent of the shroud.
  • the flow-guiding lip protrudes into the annular gap over an axial extent of 10% of the shroud and / or projects the flow-guiding lip into the annular gap over an axial extent of less than 60% of the axial extent of the shroud.
  • the axial extent of the annular groove is less than 50% of the axial extent of the shroud and / or greater than 5% of the axial extent of the shroud.
  • the annular groove is preferably arranged at least approximately in the middle between the axial ends of the shroud.
  • the flow guide lip protrudes into the annular gap into the region of the annular groove.
  • this lip section is preferably likewise curved in adaptation to a curved course of the annular wall, for instance to provide a flow direction substantially constant Cross-sectional area between lip and ring wall.
  • the flow-guiding lip has a radially inwardly directed shoulder, viewed in the axial direction, at the location of the rear end of the outer circumference of the blade ring.
  • the flow guide lip can, for. B. configured and arranged so that the introduced into the annular gap between the annular wall and the blade ring tapped steam is divided into more than 20% in the sealing steam flow and / or more than 20% in the boundary layer flow.
  • steam can also be branched off from a higher pressure stage (viewed in the direction of turbine flow upstream of said rotor blade ring of the final stage or upstream of this final stage) and guided to the annular groove by means of suitable bleed passages.
  • bleed passages can each lead directly to the annular groove, or, if present, open into the mentioned radial passage in the diffuser. From such radial passages in the diffuser may be provided more, z. B. distributed at equal angular intervals over the circumference of the diffuser.
  • a provided for supplying the annular groove with the tapped steam passage is provided with a check valve.
  • This passage may in particular z. B. act to the aforementioned radial passage in the diffuser.
  • the check valve advantageously a backflow can be avoided.
  • the term "check valves" is to be interpreted broadly in the context of the invention and should therefore not only include such a check valve in the strict sense but also other to avoid backflow suitable fittings.
  • the object stated at the outset is achieved by a steam turbine, which with a diffuser assembly of the type described is equipped.
  • the steam turbine can hereby z. B. in a conventional manner as Kondensationsdampfturbine in a water-steam cycle (condensing turbine plant) can be used.
  • Fig. 1 shows a steam turbine 10 which is coupled via a turbine rotor shaft 12 to a rotary driven work machine 14 (eg electrical generator).
  • a rotary driven work machine 14 eg electrical generator
  • the turbine 10 includes a turbine housing 16 having a turbine rotor 18 rotatably mounted therein about an axial axis A.
  • Blades 20 are mounted on the circumference of the turbine rotor 18 in the radial direction thereof which cooperate with stator blades 22 stationarily mounted in the turbine housing 16 in turbine operation to operate in a turbine Steam flow to convert energy from supplied steam to mechanical rotary energy of the turbine rotor shaft 12.
  • FIG. 1 drawn arrows illustrate this steam flow, starting from a live steam inlet 24 to a Abdampfauslass 26th
  • the rotary bearing of the turbine rotor shaft 12 is in the illustrated embodiment by means of a first bearing device 28 and a second storage device 30 accomplished.
  • Abdampfgepatuse 32 The section of the turbine housing 16, which is traversed by the steam in the last turbine operation and opens into the exhaust steam outlet 26, is referred to as Abdampfgepatuse 32.
  • the turbine 10 according to the pressure level of the steam flowing through the turbine 10, a high-pressure stage 40, a medium-pressure stage 42 and a low pressure stage or power amplifier 44, which are sequentially flowed through by the steam as shown, and in each case from structurally combined running and Leitschaufelkränzen are formed.
  • the attachment of the vanes 22 in the individual turbine stages 40, 42 and 44 is realized with respective vane carriers 46, 48 and 50, respectively.
  • the final stage in this case the low-pressure stage 44, is arranged downstream of a so-called diffuser or the output of the relevant turbine stage with such a steam generator Design diffuser functionality.
  • the diffuser kinetic energy of the exhaust steam is converted into potential energy and thus advantageously raises the static pressure of the exhaust steam to the usually higher condenser pressure.
  • a so-called diffuser arrangement in the exhaust steam housing 32 is provided downstream in the axial region of the detail or area shown at II.
  • Fig. 2 illustrates the example of a modification of in Fig. 1 shown at II details at the output of the output stage 44 of the turbine 10, a diffuser assembly according to the invention 60.
  • a steam turbine according to the invention is thus provided.
  • FIG. 2 illustrated diffuser assembly 60 is hereinafter for use in the steam turbine 10 of Fig. 1 explained.
  • the diffuser assembly 60 ( Fig. 2 ) is in this case in the exhaust steam housing 32 ( Fig. 1 ) and comprises a diffuser (diffuser housing 62) with an inlet end 64 for receiving Abdampf in the flow direction behind the provided according to this modification with a shroud 66 last blade ring 68 of the output stage 44, and with a diverging viewed in the flow direction annular wall 70, a into the exhaust steam housing 32 opening diffuser flow path (see, arrow in Fig. 2 ) limited.
  • Fig. 2 shows only the in Fig. 1 upper part (detail II in Fig. 1 ) of the overall ring-like around the axial axis A around extending diffuser assembly 60th
  • the blade ring 68 is formed by a plurality of blades 20 protruding radially from the turbine runner 18 in the illustrated area, the distal ends (radially outer ends) of which are connected by the circumferential circumferential stabilizing shroud 66.
  • the desired pressure increase takes place in the exhaust steam flow along the diffuser flow path (see arrow) to a pressure p3, which in the example shown is, for. B. the input pressure of a connected to the output of Abdampfauslasses 26 of the steam turbine 10 (not shown) capacitor corresponding to the steam turbine plant concerned.
  • p3 the input pressure of a connected to the output of Abdampfauslasses 26 of the steam turbine 10 (not shown) capacitor corresponding to the steam turbine plant concerned.
  • p2 p2 ⁇ p3
  • the pressure immediately before the illustrated blade ring 68 is denoted by p1 and, depending on the configuration of the blade ring 68, is usually greater than p2, so that the following applies: p1 ⁇ p2 ⁇ p3.
  • a pressure pA in the exhaust steam housing substantially corresponds to the diffuser outlet pressure p3.
  • the flow guide lip 76 is thus used to guide and split the tapped and the ring groove 72 again recycled steam flow and is z. B. executed as a separate (eg., Annular rotationally symmetric) component and can in this case z. B. be secured by means of suitable spacers on the diffuser 62.
  • the leakage rate of exhaust steam flowing over the blade ring 68 (in the annular gap 74) is advantageously reduced and, on the other hand, the boundary layer flow advantageously reduces the risk of boundary layer separation which reduces the diffuser efficiency.
  • the annular groove 74 For operation of the diffuser assembly 60, the annular groove 74 must be supplied with steam of a sufficiently high pressure (here: greater than p2), so that this steam can be divided into the two mentioned partial flows.
  • this steam supply is realized in a simple manner by disposing, distributed over the circumference of the diffuser 62, a number of radial passages (eg boreholes), of which Fig. 2 one can be seen and designated 78.
  • the radial passage 78 passes through the diffuser 62 in the radial direction for this purpose.
  • the advantage of the illustrated diffuser arrangement 60 is the avoidance or reduction of the flow losses which often occur in this area in known steam turbines. On the one hand can be reduced by the Sperrbedampfung the leakage amount above the corresponding tread. On the other hand, by introducing a portion of the branched vapor into the diffuser, the boundary layer (at the annular wall 70) is stabilized. Both effects lead to an advantageous increase in turbine efficiency.
  • the flow guide lip 76 in the axial direction at the location of the rear end of the outer periphery of the blade ring 68 has a radially inwardly directed shoulder 82, so that the sealing steam flow in this area forcibly also a little way in the radial direction in an annular gap between the shroud 66 and this shoulder 82 must flow, which further improves the leakage reduction.
  • a shoulder extends in the radial direction preferably as shown to the inner periphery of the respective shroud.

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

Abstract

The arrangement (60) has an annular wall (70) formed with a supplyable annular groove (72) and arranged along flow direction at a location of a moving blade collar (68) for introducing vapor into an annular gap (74) between the annular wall and the blade collar. An inlet end (64) of a diffuser (62) is extended along circumferential direction and axial direction against the flow direction. A flow guide lip (76) divides the vapor into a check steam flow at an external periphery of the blade collar and a boundary layer flow along the annular wall that is projected into the gap.

Description

Die vorliegende Erfindung betrifft eine Diffusoranordnung für ein Abdampfgehäuse einer Dampfturbine nach dem Oberbegriff des Anspruchs 1, sowie eine mit einer derartigen Diffusoranordnung ausgestattete Dampfturbine.The present invention relates to a diffuser assembly for an exhaust steam housing of a steam turbine according to the preamble of claim 1, and to a steam turbine equipped with such a diffuser arrangement.

Eine derartige Diffusoranordnung, also umfassend einen Diffusor mit einem Einlassende zur Aufnahme von Abdampf in Strömungsrichtung betrachtet hinter einem mit einem Deckband versehenen Laufschaufelkranz einer Endstufe der Dampfturbine, und mit einer in Strömungsrichtung betrachtet divergierenden Ringwand, die einen in das Abdampfgehäuse mündenden Diffusorströmungspfad begrenzt, ist aus dem allgemeinen Stand der Technik betreffend Dampfturbinenanlagen bekannt.Such a diffuser arrangement, ie comprising a diffuser having an inlet end for receiving exhaust steam in the flow direction behind a provided with a shroud blade ring of a final stage of the steam turbine, and with a diverging viewed in the flow direction annular wall which limits a flowing into the Abdampfgehäuse diffuser flow path is made the general state of the art concerning steam turbine plants.

Insbesondere der Endstufe von Kondensationsdampfturbinen ist in der Regel ein Diffusor nachgeschaltet, um damit kinetische Energie des Abdampfes in potenzielle Energie umzuwandeln, bevor der Abdampf dem Kondensator des betreffenden Wasser-Dampf-Kreislaufes zugeführt wird. Der statische Druck des Abdampfes wird hierbei vorteilhaft angehoben (auf einen "Kondensatoreingangsdruck"), weswegen man in diesem Zusammenhang auch von einem Druckrückgewinn spricht.In particular, the final stage of condensing steam turbines is usually followed by a diffuser to convert kinetic energy of the exhaust steam into potential energy before the exhaust steam is supplied to the condenser of the relevant water-steam cycle. The static pressure of the exhaust steam is thereby advantageously raised (to a "condenser inlet pressure"), which is why one speaks in this context of a pressure recovery.

Infolge des in Strömungsrichtung betrachtet positiven Druckgradienten im Bereich des Diffusors neigt die Strömung im Diffusor insbesondere gehäuseseitig zum Ablösen. Ein solches Abreißen der Grenzschichtströmung reduziert die Wirksamkeit des Diffusors und verringert damit den Turbinenwirkungsgrad.As a result of the positive pressure gradient in the region of the diffuser, as viewed in the flow direction, the flow in the diffuser in particular tends to detach on the housing side. Such demolition of the boundary layer flow reduces the effectiveness of the diffuser and thus reduces turbine efficiency.

Diese Problematik der Grenzschichtablösung im Diffusor ergibt sich vor allem dann, wenn der betreffende Laufschaufelkranz der Endstufe mit einem so genannten Deckband ausgeführt ist, d. h. mit einer am Außenumfang des Laufschaufelkranzes umlaufend ausgebildeten Stabilisierungsstruktur. In diesem Fall entfällt die ansonsten vorhandene strömungsstabilisierende Wirkung einer dort vorhandenen Spaltströmung (Energetisierung der Grenzschicht).This problem of boundary layer separation in the diffuser arises especially when the relevant blade ring of the final stage is designed with a so-called shroud, ie with a circumferential on the outer circumference of the blade ring trained stabilization structure. In this case, the otherwise existing flow-stabilizing effect of a gap flow existing there (energization of the boundary layer) is eliminated.

Durch den Einsatz freistehender Laufschaufeln, also einem Laufschaufelkranz ohne Deckband, wird dieses Problem zwar vermieden. In diesem Fall ergeben sich jedoch höhere Dampfleckagemengen über dem Laufschaufelkranz, was zu einer entsprechenden Reduzierung des Wirkungsgrades der Endstufe führt.By using free-standing blades, so a blade ring without shroud, this problem is indeed avoided. In this case, however, higher Dampfleckagemengen arise over the blade ring, resulting in a corresponding reduction in the efficiency of the power amplifier.

Es ist eine Aufgabe der vorliegenden Erfindung, bei einer Diffusoranordnung der eingangs genannten Art eine geringe Neigung zur Grenzschichtablösung bei gleichzeitig niedriger Dampfleckagerate über dem Laufschaufelkranz zu erzielen.It is an object of the present invention, in a diffuser arrangement of the type mentioned in the beginning to achieve a low tendency for boundary layer separation with a simultaneously low steam leakage rate over the blade ring.

Gemäß der Erfindung wird diese Aufgabe gelöst durch eine Diffusoranordnung nach Anspruch 1 bzw. eine damit ausgestattete Dampfturbine (Anspruch 5).According to the invention, this object is achieved by a diffuser arrangement according to claim 1 or a steam turbine equipped therewith (claim 5).

Die erfindungsgemäße Diffusoranordnung ist gekennzeichnet durch:

  • eine mit Dampf, welcher aus dem Abdampfgehäuse und/oder aus einer höheren Druckstufe der Dampfturbine abgezapft wurde, versorgbare Ringnut in der Ringwand, welche in Strömungsrichtung betrachtet an der Stelle des Laufschaufelkranzes angeordnet ist, zur Einleitung des abgezapften Dampfes in einen Ringspalt zwischen der Ringwand und dem Laufschaufelkranz, und
  • eine am Einlassende des Diffusors in Umfangsrichtung umlaufend ausgebildete und in Axialrichtung entgegen der Strömungsrichtung in den Ringspalt hineinragende Strömungsführungslippe zur Aufteilung des eingeleiteten Dampfes einerseits in eine Sperrdampfströmung am Außenumfang des Laufschaufelkranzes und andererseits in eine Grenzschichtströmung entlang der Ringwand.
The diffuser arrangement according to the invention is characterized by:
  • a with steam, which was tapped from the Abdampfgehäuse and / or from a higher pressure stage of the steam turbine, supplyable annular groove in the annular wall, which is arranged in the flow direction at the location of the blade ring, for introducing the tapped steam into an annular gap between the annular wall and the blade ring, and
  • a flow guide lip peripherally circumferentially formed at the inlet end of the diffuser and projecting in the axial direction against the flow direction into the annular gap for dividing the steam introduced on the one hand into a sealing steam flow on the outer circumference of the rotor blade ring and on the other hand into a boundary layer flow along the annular wall.

Mit anderen Worten ist beim Einsatz der Erfindung vorgesehen, Dampf aus dem Abdampfgehäuse bzw. einer höheren Druckstufe (bezogen auf die "Endstufe" bzw. dessen besagten Laufschaufelkranz, d. h. insbesondere z. B. so genannte Hochdruckstufe oder Mitteldruckstufe) zu entnehmen und einen Teil dieses abgezapften Dampfes als "Sperrdampf" (mit abdichtender Wirkung für den Ringspalt zwischen Diffusor-Ringwand und Turbinen-Laufschaufelkranz) über dem Endstufenlaufschaufelkranz wiedereinzuleiten, wobei ein anderer Teil des abgezapften Dampfes stromab des Laufschaufelkranzes entlang der Ringwand gewissermaßen in die Grenzschicht eingeblasen wird. Die erfindungsgemäß vorgesehene Strömungsführungslippe bewirkt hierbei in einfacher Weise die gewünschte Aufteilung des Dampfes einerseits in die Sperrdampfströmung und andererseits in die Grenzschichtströmung.In other words, it is provided when using the invention to remove steam from the exhaust steam housing or a higher pressure stage (based on the "final stage" or said rotor blade ring, ie in particular, for example, so-called high-pressure stage or medium-pressure stage) and a part of this tapped steam as "sealing steam" (with sealing effect for the annular gap between the diffuser ring wall and turbine blade ring) reintroduce over the Endstufenlaufschaufelkranz, wherein another part of the tapped steam downstream of the blade ring along the annular wall is injected into the boundary layer so to speak. The flow guide lip provided according to the invention in this case brings about in a simple manner the desired distribution of the vapor on the one hand into the sealing vapor flow and on the other hand into the boundary layer flow.

Vorteilhaft bewirkt die eingeblasene Grenzschichtströmung entlang der Ringwand eine Verringerung des Risikos der Grenzschichtablösung, wobei durch die Sperrdampfströmung gleichzeitig vorteilhaft die Dampfleckagemenge über dem Laufschaufelkranz verringert wird.Advantageously, the injected boundary layer flow along the annular wall causes a reduction in the risk of boundary layer separation, wherein at the same time advantageously the vapor leakage amount over the blade ring is reduced by the sealing steam flow.

In einer Ausführungsform ist vorgesehen, dass die axiale Ausdehnung der Stromführungslippe größer als 50% der axialen Ausdehnung des Deckbandes ist und/oder die axiale Ausdehnung der Strömungsführungslippe kleiner als 200% der axialen Ausdehnung des Deckbandes ist.In one embodiment, it is provided that the axial extent of the flow guide lip is greater than 50% of the axial extent of the shroud and / or the axial extent of the flow guide lip is less than 200% of the axial extent of the shroud.

In einer Ausführungsform ragt die Strömungsführungslippe über eine axiale Ausdehnung von 10% des Deckbandes in den Ringspalt hinein und/oder ragt die Strömungsführungslippe über eine axiale Erstreckung von weniger als 60% der axialen Ausdehnung des Deckbandes in den Ringspalt hinein.In one embodiment, the flow-guiding lip protrudes into the annular gap over an axial extent of 10% of the shroud and / or projects the flow-guiding lip into the annular gap over an axial extent of less than 60% of the axial extent of the shroud.

In einer Ausführungsform ist die axiale Erstreckung der Ringnut kleiner als 50% der axialen Erstreckung des Deckbandes und/oder größer als 5% der axialen Erstreckung des Deckbandes.In one embodiment, the axial extent of the annular groove is less than 50% of the axial extent of the shroud and / or greater than 5% of the axial extent of the shroud.

In Axialrichtung betrachtet ist die Ringnut bevorzugt wenigstens annähernd in der Mitte zwischen den axialen Enden des Deckbandes angeordnet.Viewed in the axial direction, the annular groove is preferably arranged at least approximately in the middle between the axial ends of the shroud.

In einer Ausführungsform ragt die Strömungsführungslippe in Axialrichtung betrachtet bis in den Bereich der Ringnut in den Ringspalt hinein.In one embodiment, viewed in the axial direction, the flow guide lip protrudes into the annular gap into the region of the annular groove.

Was denjenigen Abschnitt der Strömungsführungslippe anbelangt, welcher dem Ringspalt abgewandt ist und im Bereich des Einlassendes des Diffusors in den Diffusorströmungspfad hineinragt, so ist dieser Lippenabschnitt bevorzugt in Anpassung an einen gekrümmten Verlauf der Ringwand ebenfalls gekrümmt ausgebildet, etwa zur Schaffung eines in Durchströmungsrichtung im Wesentlichen konstanten Querschnittsfläche zwischen Lippe und Ringwand.As regards the section of the flow guide lip which faces away from the annular gap and projects into the diffuser flow path in the region of the inlet end of the diffuser, this lip section is preferably likewise curved in adaptation to a curved course of the annular wall, for instance to provide a flow direction substantially constant Cross-sectional area between lip and ring wall.

In einer Ausführungsform ist vorgesehen, dass die Strömungsführungslippe in Axialrichtung betrachtet an der Stelle des hinteren Endes des Außenumfangs des Laufschaufelkranzes eine nach radial innen gerichtete Schulter aufweist.In one embodiment, it is provided that the flow-guiding lip has a radially inwardly directed shoulder, viewed in the axial direction, at the location of the rear end of the outer circumference of the blade ring.

Mit einer derartigen Schulter kann vorteilhaft ein die Wirkung der Sperrdampfströmung verbessernder axialer Spalt (verengte Stelle) zwischen dieser Schulter und dem Außenumfang des Laufschaufelkranzes vorgesehen werden.With such a shoulder, an effect of the sealing steam flow improving axial gap (narrowed point) between this shoulder and the outer periphery of the blade ring can be advantageously provided.

Die Strömungsführungslippe kann z. B. so ausgestaltet und angeordnet sein, dass der in den Ringspalt zwischen der Ringwand und dem Laufschaufelkranz eingeleitete abgezapfte Dampf zu mehr als 20% in die Sperrdampfströmung und/oder zu mehr als 20% in die Grenzschichtströmung aufgeteilt wird.The flow guide lip can, for. B. configured and arranged so that the introduced into the annular gap between the annular wall and the blade ring tapped steam is divided into more than 20% in the sealing steam flow and / or more than 20% in the boundary layer flow.

In einer Ausführungsform ist vorgesehen, dass eine Versorgung der Ringnut mit dem abgezapften Dampf durch wenigstens eine in Radialrichtung durch den Diffusor sich erstreckende Passage erfolgt.In one embodiment it is provided that a supply of the annular groove with the tapped steam by at least one radially extending through the diffuser passage.

Wenn diese Passage den Diffusor in Radialrichtung vollständig durchsetzt und das radial äußere Ende der Passage in das Abdampfgehäuse mündet, so kann damit in einfacher Weise Dampf aus dem Abdampfgehäuse abgezapft und über die Passage zur Ringnut geführt werden.If this passage completely penetrates the diffuser in the radial direction and the radially outer end of the passage opens into the exhaust steam housing, steam can be tapped out of the exhaust steam housing in a simple manner and guided via the passage to the annular groove.

Alternativ oder zusätzlich zu einer derartigen Dampfabzweigung aus dem Abdampfgehäuse kann durch geeignete Abzapfpassagen auch Dampf aus einer höheren Druckstufe (in Turbinenströmungsrichtung betrachtet vor dem genannten Laufschaufelkranz der Endstufe bzw. vor dieser Endstufe) abgezweigt und zur Ringnut geführt werden. Eine oder mehrere derartige Abzapfpassagen können hierbei jeweils direkt zur Ringnut führen, oder, falls vorhanden, in die erwähnte Radialpassage im Diffusor einmünden. Von derartigen Radialpassagen im Diffusor können mehrere vorgesehen sein, z. B. in gleichen Winkelabständen über den Umfang des Diffusors verteilt.Alternatively or in addition to such a steam branching from the exhaust steam housing, steam can also be branched off from a higher pressure stage (viewed in the direction of turbine flow upstream of said rotor blade ring of the final stage or upstream of this final stage) and guided to the annular groove by means of suitable bleed passages. One or more such bleed passages can each lead directly to the annular groove, or, if present, open into the mentioned radial passage in the diffuser. From such radial passages in the diffuser may be provided more, z. B. distributed at equal angular intervals over the circumference of the diffuser.

In einer Ausführungsform ist vorgesehen, dass eine zur Versorgung der Ringnut mit dem abgezapften Dampf vorgesehene Passage mit einem Rückschlagventil versehen ist. Bei dieser Passage kann es sich insbesondere z. B. um die erwähnte Radialpassage im Diffusor handeln. Mit dem Rückschlagventil kann vorteilhaft eine Rückströmung vermieden werden. Der Begriff "Rückschlagventilen" ist im Sinne der Erfindung breit auszulegen und soll daher nicht nur ein solches Rückschlagventil im engeren Sinne sondern auch andere zur Vermeidung einer Rückströmung geeignete Armaturen umfassen.In one embodiment, it is provided that a provided for supplying the annular groove with the tapped steam passage is provided with a check valve. This passage may in particular z. B. act to the aforementioned radial passage in the diffuser. With the check valve advantageously a backflow can be avoided. The term "check valves" is to be interpreted broadly in the context of the invention and should therefore not only include such a check valve in the strict sense but also other to avoid backflow suitable fittings.

Gemäß eines weiteren Aspekts der Erfindung wird die eingangs gestellte Aufgabe durch eine Dampfturbine gelöst, welche mit einer Diffusoranordnung der beschriebenen Art ausgestattet ist.According to a further aspect of the invention, the object stated at the outset is achieved by a steam turbine, which with a diffuser assembly of the type described is equipped.

Die Dampfturbine kann hierbei z. B. in an sich bekannter Art als Kondensationsdampfturbine in einem Wasser-Dampf-Kreislauf (Kondensationsdampfturbinenanlage) verwendet werden.The steam turbine can hereby z. B. in a conventional manner as Kondensationsdampfturbine in a water-steam cycle (condensing turbine plant) can be used.

Die Erfindung wird nachfolgend anhand von Ausführungsbeispielen mit Bezug auf die beigefügten Zeichnungen weiter beschrieben. Es stellen dar:

Fig. 1
eine schematische Längsschnittansicht einer Dampfturbine von herkömmlicher Bauart, und
Fig. 2
ein Detail aus Fig. 1, jedoch in modifizierter Ausgestaltung, zur Veranschaulichung eines Ausführungsbeispiels der Erfindung.
The invention will be further described by means of embodiments with reference to the accompanying drawings. They show:
Fig. 1
a schematic longitudinal sectional view of a steam turbine of conventional design, and
Fig. 2
a detail from Fig. 1 but in modified form, to illustrate an embodiment of the invention.

Fig. 1 zeigt eine Dampfturbine 10, welche über eine Turbinenläuferwelle 12 mit einer drehangetriebenen Arbeitsmaschine 14 (z. B. elektrischer Generator) gekoppelt ist. Fig. 1 shows a steam turbine 10 which is coupled via a turbine rotor shaft 12 to a rotary driven work machine 14 (eg electrical generator).

Die Turbine 10 umfasst ein Turbinengehäuse 16 mit einem darin um eine axiale Achse A drehbar gelagerten Turbinenläufer 18. Am Umfang des Turbinenläufers 18 sind in Radialrichtung davon abstehend Laufschaufeln 20 befestigt, welche mit stationär im Turbinengehäuse 16 befestigten Leitschaufeln 22 im Turbinenbetrieb zusammenwirken, um bei einer Dampfdurchströmung Energie von zugeführtem Dampf in mechanische Drehenergie der Turbinenläuferwelle 12 umzuwandeln.The turbine 10 includes a turbine housing 16 having a turbine rotor 18 rotatably mounted therein about an axial axis A. Blades 20 are mounted on the circumference of the turbine rotor 18 in the radial direction thereof which cooperate with stator blades 22 stationarily mounted in the turbine housing 16 in turbine operation to operate in a turbine Steam flow to convert energy from supplied steam to mechanical rotary energy of the turbine rotor shaft 12.

Die in Fig. 1 eingezeichneten Pfeile veranschaulichen diese Dampfdurchströmung ausgehend von einem Frischdampfeinlass 24 zu einem Abdampfauslass 26.In the Fig. 1 drawn arrows illustrate this steam flow, starting from a live steam inlet 24 to a Abdampfauslass 26th

Die Drehlagerung der Turbinenläuferwelle 12 ist im dargestellten Ausführungsbeispiel mittels einer ersten Lagereinrichtung 28 und einer zweiten Lagereinrichtung 30 bewerkstelligt.The rotary bearing of the turbine rotor shaft 12 is in the illustrated embodiment by means of a first bearing device 28 and a second storage device 30 accomplished.

Derjenige Abschnitt des Turbinengehäuses 16, welcher im Turbinenbetrieb zuletzt vom Dampf durchströmt wird und in den Abdampfauslass 26 mündet, wird als Abdampfgehäuse 32 bezeichnet.The section of the turbine housing 16, which is traversed by the steam in the last turbine operation and opens into the exhaust steam outlet 26, is referred to as Abdampfgehäuse 32.

Im dargestellten Ausführungsbeispiel umfasst die Turbine 10 entsprechend dem Druckniveau des die Turbine 10 durchströmenden Dampfes eine Hochdruckstufe 40, eine Mitteldruckstufe 42 und eine Niederdruckstufe bzw. Endstufe 44, welche wie dargestellt nacheinander von dem Dampf durchströmt werden, und jeweils aus baulich zusammengefassten Lauf- und Leitschaufelkränzen gebildet sind. Die Befestigung der Leitschaufeln 22 in den einzelnen Turbinenstufen 40, 42 und 44 ist mit jeweiligen Leitschaufelträgern 46, 48 bzw. 50 realisiert.In the illustrated embodiment, the turbine 10 according to the pressure level of the steam flowing through the turbine 10, a high-pressure stage 40, a medium-pressure stage 42 and a low pressure stage or power amplifier 44, which are sequentially flowed through by the steam as shown, and in each case from structurally combined running and Leitschaufelkränzen are formed. The attachment of the vanes 22 in the individual turbine stages 40, 42 and 44 is realized with respective vane carriers 46, 48 and 50, respectively.

Die bis hierher beschriebene grundsätzliche Konstruktion der Dampfturbine 10 ist aus dem Stand der Technik bekannt (vgl. z. B. WO 2012/175328 A1 ).The basic construction of the steam turbine 10 described so far is known from the prior art (cf. WO 2012/175328 A1 ).

Bei der üblichen Verwendung einer Dampfturbine der in Fig. 1 dargestellten Art als Kondensationsdampfturbine in einem Wasser-Dampf-Kreislauf (Kondensationsdampfturbinenanlage) ist es des Weiteren aus dem allgemeinen Stand der Technik bekannt, der Endstufe, hier also der Niederdruckstufe 44, einen so genannten Diffusor nachzuordnen bzw. den Ausgang der betreffenden Turbinenstufe mit einer derartigen Diffusorfunktionalität auszugestalten. Mit dem Diffusor wird kinetische Energie des Abdampfes in potenzielle Energie umgewandelt und somit vorteilhaft der statische Druck des Abdampfes auf den üblicherweise höheren Kondensatordruck angehoben.In the usual use of a steam turbine of Fig. 1 Furthermore, it is known from the general state of the art that the final stage, in this case the low-pressure stage 44, is arranged downstream of a so-called diffuser or the output of the relevant turbine stage with such a steam generator Design diffuser functionality. With the diffuser kinetic energy of the exhaust steam is converted into potential energy and thus advantageously raises the static pressure of the exhaust steam to the usually higher condenser pressure.

Im dargestellten Beispiel gemäß Fig. 1 ist hierzu im axialen Bereich des bei II gezeigten Details oder diesem Bereich nachgeordnet eine so genannte Diffusoranordnung im Abdampfgehäuse 32 vorzusehen.In the example shown according to Fig. 1 For this purpose, a so-called diffuser arrangement in the exhaust steam housing 32 is provided downstream in the axial region of the detail or area shown at II.

Fig. 2 veranschaulicht am Beispiel einer Modifikation des in Fig. 1 bei II dargestellten Details am Ausgang der Endstufe 44 der Turbine 10 eine erfindungsgemäße Diffusoranordnung 60. Durch eine entsprechende Modifikation der Dampfturbine 10 von Fig. 1 in diesem Bereich wird somit eine erfindungsgemäße Dampfturbine bereitgestellt. Fig. 2 illustrates the example of a modification of in Fig. 1 shown at II details at the output of the output stage 44 of the turbine 10, a diffuser assembly according to the invention 60. By a corresponding modification of the steam turbine 10 of Fig. 1 In this area, a steam turbine according to the invention is thus provided.

Die mit Fig. 2 veranschaulichte Diffusoranordnung 60 sei im Folgenden zur Verwendung bei der Dampfturbine 10 von Fig. 1 erläutert.With Fig. 2 illustrated diffuser assembly 60 is hereinafter for use in the steam turbine 10 of Fig. 1 explained.

Die Diffusoranordnung 60 (Fig. 2) ist in diesem Fall im Abdampfgehäuse 32 (Fig. 1) angeordnet und umfasst einen Diffusor (Diffusorgehäuse 62) mit einem Einlassende 64 zur Aufnahme von Abdampf in Strömungsrichtung betrachtet hinter dem gemäß dieser Modifikation mit einem Deckband 66 versehenen letzten Laufschaufelkranz 68 der Endstufe 44, und mit einer in Strömungsrichtung betrachtet divergierenden Ringwand 70, die einen in das Abdampfgehäuse 32 mündenden Diffusorströmungspfad (vgl. Pfeil in Fig. 2) begrenzt.The diffuser assembly 60 ( Fig. 2 ) is in this case in the exhaust steam housing 32 ( Fig. 1 ) and comprises a diffuser (diffuser housing 62) with an inlet end 64 for receiving Abdampf in the flow direction behind the provided according to this modification with a shroud 66 last blade ring 68 of the output stage 44, and with a diverging viewed in the flow direction annular wall 70, a into the exhaust steam housing 32 opening diffuser flow path (see, arrow in Fig. 2 ) limited.

Fig. 2 zeigt hierbei lediglich den in Fig. 1 oberen Teil (Detail II in Fig. 1) der insgesamt ringartig um die axiale Achse A herum sich erstreckenden Diffusoranordnung 60. Fig. 2 shows only the in Fig. 1 upper part (detail II in Fig. 1 ) of the overall ring-like around the axial axis A around extending diffuser assembly 60th

Der Laufschaufelkranz 68 wird durch eine Vielzahl von im dargestellten Bereich radial von dem Turbinenläufer 18 abstehenden Laufschaufeln 20 gebildet, deren distale (radial äußeren) Enden durch das in Umfangsrichtung umlaufende, stabilisierende Deckband 66 verbunden sind.The blade ring 68 is formed by a plurality of blades 20 protruding radially from the turbine runner 18 in the illustrated area, the distal ends (radially outer ends) of which are connected by the circumferential circumferential stabilizing shroud 66.

Durch die divergierende Gestaltung des Diffusors 62 bzw. von dessen Ringwand 70 erfolgt in der Abdampfströmung entlang des Diffusorströmungspfades (vgl. Pfeil) die gewünschte Druckerhöhung (Druckrückgewinn) auf einen Druck p3, der im dargestellten Beispiel z. B. dem Eingangsdruck eines am Ausgang des Abdampfauslasses 26 der Dampfturbine 10 angeschlossenen (nicht dargestellten) Kondensators der betreffenden Dampfturbinenanlage entspricht. Beim Eintritt des Abdampfes in den Diffusor 62, d. h. am Einlassende 64 des Diffusors 62 herrscht ein Druck p2 (p2 < p3). Der Druck unmittelbar vor dem dargestellten Laufschaufelkranz 68 ist mit p1 bezeichnet und je nach Ausgestaltung des Laufschaufelkranzes 68 üblicherweise größer als p2, so dass gilt: p1 < p2 < p3.As a result of the divergent design of the diffuser 62 or its annular wall 70, the desired pressure increase (pressure recovery) takes place in the exhaust steam flow along the diffuser flow path (see arrow) to a pressure p3, which in the example shown is, for. B. the input pressure of a connected to the output of Abdampfauslasses 26 of the steam turbine 10 (not shown) capacitor corresponding to the steam turbine plant concerned. When the exhaust steam enters the diffuser 62, ie at the inlet end 64 of the diffuser 62, there is a pressure p2 (p2 <p3). The pressure immediately before the illustrated blade ring 68 is denoted by p1 and, depending on the configuration of the blade ring 68, is usually greater than p2, so that the following applies: p1 <p2 <p3.

Aufgrund der relativ großen Mündungsquerschnittsfläche vom Ausgang des Diffusors 62 (in Fig. 2 rechts) in das Abdampfgehäuse 32 entspricht ein Druck pA im Abdampfgehäuse im Wesentlichen dem Diffusorausgangsdruck p3.Due to the relatively large orifice cross-sectional area from the exit of the diffuser 62 (in FIG Fig. 2 right) into the exhaust steam housing 32, a pressure pA in the exhaust steam housing substantially corresponds to the diffuser outlet pressure p3.

Eine Besonderheit der Diffusoranordnung 60 (bzw. der damit ausgestatteten Dampfturbine) besteht nun darin, dass die Diffusoranordnung 60 ferner umfasst:

  • eine mit Dampf, welcher aus dem Abdampfgehäuse 32 und/oder aus einer höheren Druckstufe, z. B. einem weiter stromaufwärts gelegenen Teil der Endstufe 44, oder der Mitteldruckstufe 42, oder der Hochdruckstufe 40, abgezapft wurde, versorgbare Ringnut 72 in der Ringwand 70, welche in Strömungsrichtung (vgl. Pfeil) betrachtet an der Stelle des Laufschaufelkranzes 68 angeordnet ist, zur Einleitung des abgezapften Dampfes in einen Ringspalt 74 zwischen der Ringwand 70 und dem (an seinem Außenumfang mit dem Deckband 66 versehenen) Laufschaufelkranz 68, und
  • eine am Einlassende 64 des Diffusors 62 in Umfangsrichtung umlaufend ausgebildete und in Axialrichtung (vgl. Achse A) entgegen der Strömungsrichtung (vgl. Pfeil) in den Ringspalt 74 hineinragende Strömungsführungslippe 76 zur Aufteilung des eingeleiteten Dampfes (vgl. kleine Pfeile in Fig. 2) einerseits in eine Sperrdampfströmung am Außenumfang des Laufschaufelkranzes 68 bzw. Deckbandes 66 und andererseits in eine Grenzschichtströmung entlang der Ringwand 70.
A special feature of the diffuser arrangement 60 (or the steam turbine equipped therewith) is that the diffuser arrangement 60 further comprises:
  • one with steam, which from the Abdampfgehäuse 32 and / or from a higher pressure level, z. B. a further upstream part of the output stage 44, or the intermediate-pressure stage 42, or the high-pressure stage 40 was tapped, supplyable annular groove 72 in the annular wall 70, which in the flow direction (see arrow) is viewed at the location of the blade ring 68, for introducing the tapped steam into an annular gap 74 between the annular wall 70 and the (provided on its outer periphery with the shroud 66) blade ring 68, and
  • a flow-guiding lip 76 extending circumferentially around the inlet end 64 of the diffuser 62 and projecting in the axial direction (see axis A) against the flow direction (see arrow) into the annular gap 74 for dividing the introduced steam (compare small arrows in FIG Fig. 2 On the one hand into a sealing steam flow on the outer circumference of the blade ring 68 or shroud 66 and on the other hand in a boundary layer flow along the annular wall 70th

Die Strömungsführungslippe 76 wird somit zur Führung und Aufteilung der abgezapften und über die Ringnut 72 wieder rückgeführten Dampfströmung eingesetzt und ist z. B. als ein separates (z. B. ringförmig rotationssymmetrisches) Bauteil ausgeführt und kann hierbei z. B. mittels geeigneten Abstandshaltern am Diffusor 62 befestigt sein.The flow guide lip 76 is thus used to guide and split the tapped and the ring groove 72 again recycled steam flow and is z. B. executed as a separate (eg., Annular rotationally symmetric) component and can in this case z. B. be secured by means of suitable spacers on the diffuser 62.

Vorteilhaft wird mit dieser Gestaltung einerseits durch die Sperrdampfströmung die Leckagerate von über dem Laufschaufelkranz 68 (im Ringspalt 74) strömenden Abdampfes vorteilhaft verringert und andererseits durch die Grenzschichtströmung das Risiko einer die Diffusoreffizienz verringernden Grenzschichtablösung vorteilhaft verringert.Advantageously, with this design on the one hand by the sealing steam flow, the leakage rate of exhaust steam flowing over the blade ring 68 (in the annular gap 74) is advantageously reduced and, on the other hand, the boundary layer flow advantageously reduces the risk of boundary layer separation which reduces the diffuser efficiency.

Zum Betrieb der Diffusoranordnung 60 muss die Ringnut 74 mit Dampf eines ausreichend hohen Druckes (hier: größer als p2) versorgt werden, damit dieser Dampf in die beiden erwähnten Teilströmungen aufgeteilt werden kann.For operation of the diffuser assembly 60, the annular groove 74 must be supplied with steam of a sufficiently high pressure (here: greater than p2), so that this steam can be divided into the two mentioned partial flows.

Im dargestellten Beispiel ist diese Dampfversorgung in einfacher Weise dadurch realisiert, dass über den Umfang des Diffusors 62 verteilt einige Radialpassagen (z. B. Bohrungen) angeordnet sind, von denen in Fig. 2 eine ersichtlich und mit 78 bezeichnet ist.In the example shown, this steam supply is realized in a simple manner by disposing, distributed over the circumference of the diffuser 62, a number of radial passages (eg boreholes), of which Fig. 2 one can be seen and designated 78.

Durch diese Radialpassage(n) 78 hindurch erfolgt eine Dampfüberleitung aus dem Abdampfgehäuse 32 zum Ringspalt 74.Through this radial passage (s) 78, a vapor transfer takes place from the exhaust steam housing 32 to the annular gap 74.

Die Radialpassage 78 durchsetzt hierfür den Diffusor 62 in radialer Richtung.The radial passage 78 passes through the diffuser 62 in the radial direction for this purpose.

Zur Vermeidung einer Rückströmung können derartige Versorgungspassagen mit geeigneten Regelarmaturen wie z. B. dem in Fig. 2 bei 80 symbolisierten Rückschlagventil versehen sein.To avoid a backflow such supply passages with suitable control valves such. B. the in Fig. 2 to be provided at 80 symbolized check valve.

Der Vorteil der dargestellten Diffusoranordnung 60 besteht in der Vermeidung bzw. Abminderung der in diesem Bereich bei bekannten Dampfturbinen oftmals auftretenden Strömungsverluste. Zum einen kann durch die Sperrbedampfung die Leckagemenge über dem entsprechenden Laufkranz reduziert werden. Zum anderen wird durch die Einleitung eines Teils des abgezweigten Dampfes in den Diffusor die Grenzschicht (an der Ringwand 70) stabilisiert. Beide Effekte führen zu einer vorteilhaften Erhöhung des Turbinenwirkungsgrades.The advantage of the illustrated diffuser arrangement 60 is the avoidance or reduction of the flow losses which often occur in this area in known steam turbines. On the one hand can be reduced by the Sperrbedampfung the leakage amount above the corresponding tread. On the other hand, by introducing a portion of the branched vapor into the diffuser, the boundary layer (at the annular wall 70) is stabilized. Both effects lead to an advantageous increase in turbine efficiency.

Im dargestellten Beispiel weist die Strömungsführungslippe 76 in Axialrichtung betrachtet an der Stelle des hinteren Endes des Außenumfangs des Laufschaufelkranzes 68 eine nach radial innen gerichtete Schulter 82 auf, so dass die Sperrdampfströmung in diesem Bereich zwangsweise auch ein Stück weit in Radialrichtung in einem Ringspalt zwischen dem Deckband 66 und dieser Schulter 82 strömen muss, was die Leckageverminderung weiter verbessert. Eine solche Schulter erstreckt sich in radialer Richtung bevorzugt wie dargestellt bis zum Innenumfang des betreffenden Deckbandes.In the example shown, the flow guide lip 76 in the axial direction at the location of the rear end of the outer periphery of the blade ring 68 has a radially inwardly directed shoulder 82, so that the sealing steam flow in this area forcibly also a little way in the radial direction in an annular gap between the shroud 66 and this shoulder 82 must flow, which further improves the leakage reduction. Such a shoulder extends in the radial direction preferably as shown to the inner periphery of the respective shroud.

Im Hinblick auf eine möglichst hohe Wirksamkeit der Strömungsführungslippe 76 kann deren Ausgestaltung bzw. Anordnung im Diffusor- bzw. Diffusoreinlassbereich 64 dem jeweiligen Anwendungsfall angepasst optimiert werden. Unter diesem Aspekt können ganz allgemein z. B. folgende Gestaltungsdetails, einzeln oder kombinuert, von Vorteil sein:

  • Die axiale Ausdehnung der Lippe (76) beträgt mehr als 50% der axialen Ausdehnung des Deckbandes (66) und/oder weniger als 200% der axialen Ausdehnung des Deckbandes (66).
  • Die Lippe (76) ragt um mehr als 10% der axialen Ausdehnung des Deckbandes (66) und/oder um weniger als 60% der axialen Ausdehnung des Deckbandes (66) in den Ringspalt (74) hinein.
  • Die Lippe (76) endet im Ringspalt (74) an einer axialen Stelle, an welcher auch die Ringnut (72) vorgesehen ist. Im dargestellten Beispiel endet die Lippe 76 z. B. am axial betrachtet stromabwärtigen Ende der Ringnut 72.
  • Die Lippe (76) besitzt einen an den gekrümmten (divergierenden) Verlauf der Ringwand (70) angepasst ebenfalls gekrümmten Verlauf. Im dargestellten Beispiel ist eine derartige Krümmung der Lippe 76 sowohl auf ihrer radial äußeren als auch auf ihrer radial inneren Seite vorgesehen. Die Krümmung an der radial äußeren Seite ist bevorzugt zur Schaffung eines ringförmigen Grenzströmungspfades mit im Pfadverlauf einheitlichem Strömungsquerschnitt vorgesehen.
  • Die Lippe (76) besitzt eine Wandungsstärke, die sich in Richtung des Diffusorströmungspfades kontinuierlich verjüngt.
With regard to the highest possible effectiveness of the flow guide lip 76, its configuration or arrangement in the diffuser or diffuser inlet region 64 can be optimized for the respective application. In this aspect, in general z. B. the following design details, individually or in combination, be beneficial:
  • The axial extent of the lip (76) is more than 50% of the axial extent of the shroud (66) and / or less than 200% of the axial extent of the shroud (66).
  • The lip (76) projects into the annular gap (74) by more than 10% of the axial extent of the shroud (66) and / or by less than 60% of the axial extent of the shroud (66).
  • The lip (76) ends in the annular gap (74) at an axial point at which the annular groove (72) is provided. In the example shown, the lip 76 ends z. B. at the axially downstream end of the annular groove 72nd
  • The lip (76) has a curve which is also adapted to the curved (divergent) course of the annular wall (70). In the illustrated example, such a curvature of the lip 76 is provided both on its radially outer and on its radially inner side. The curvature on the radially outer side is preferably provided for providing an annular boundary flow path with a flow cross-section uniform in the path.
  • The lip (76) has a wall thickness that tapers continuously in the direction of the diffuser flow path.

Claims (5)

Diffusoranordnung (60) für ein Abdampfgehäuse (32) einer Dampfturbine (10), umfassend einen Diffusor (62) mit einem Einlassende (64) zur Aufnahme von Abdampf in Strömungsrichtung betrachtet hinter einem mit einem Deckband (60) versehenen Laufschaufelkranz (68) einer Endstufe (44) der Dampfturbine (10), und mit einer in Strömungsrichtung betrachtet divergierenden Ringwand (70), die einen in das Abdampfgehäuse (32) mündenden Diffusorströmungspfad begrenzt,
dadurch gekennzeichnet, dass die Diffusoranordnung (60) ferner umfasst: - eine mit Dampf, welcher aus dem Abdampfgehäuse (32) und/oder aus einer höheren Druckstufe (44, 42, 40) der Dampfturbine (10) abgezapft wurde, versorgbare Ringnut (72) in der Ringwand (70), welche in Strömungsrichtung betrachtet an der Stelle des Laufschaufelkranzes (68) angeordnet ist, zur Einleitung des abgezapften Dampfes in einen Ringspalt (74) zwischen der Ringwand (70) und dem Laufschaufelkranz (68), und - eine am Einlassende (64) des Diffusors (62) in Umfangsrichtung umlaufend ausgebildete und in Axialrichtung entgegen der Strömungsrichtung in den Ringspalt (74) hineinragende Strömungsführungslippe (76) zur Aufteilung des eingeleiteten Dampfes einerseits in eine Sperrdampfströmung am Außenumfang des Laufschaufelkranzes (68) und andererseits in eine Grenzschichtströmung entlang der Ringwand (70). Diffuser assembly (60) for an exhaust steam housing (32) of a steam turbine (10), comprising a diffuser (62) having an inlet end (64) for receiving Abdampf in the flow direction behind a provided with a shroud (60) blade ring (68) of a final stage (44) the steam turbine (10), and with a viewed in the flow direction diverging annular wall (70) defining a in the exhaust steam housing (32) opening out Diffusorströmungspfad,
characterized in that the diffuser assembly (60) further comprises: - One with steam, which was tapped from the Abdampfgehäuse (32) and / or from a higher pressure stage (44, 42, 40) of the steam turbine (10), supplyable annular groove (72) in the annular wall (70), which viewed in the flow direction is arranged at the location of the blade ring (68) for introducing the tapped vapor into an annular gap (74) between the annular wall (70) and the blade ring (68), and - A at the inlet end (64) of the diffuser (62) circumferentially circumferentially formed and in the axial direction against the flow direction in the annular gap (74) projecting flow guide lip (76) for dividing the steam introduced on the one hand in a sealing steam flow on the outer circumference of the blade ring (68) and on the other hand, in a boundary layer flow along the annular wall (70). Diffusoranordnung (60) nach Anspruch 1, wobei die Strömungsführungslippe (76) in Axialrichtung betrachtet an der Stelle des hinteren Endes des Außenumfangs des Laufschaufelkranzes (68) eine nach radial innen gerichtete Schulter (82) aufweist.The diffuser assembly (60) of claim 1, wherein the flow guide lip (76) has a radially inwardly directed shoulder (82) at the location of the trailing end of the outer periphery of the blade ring (68) viewed in the axial direction. Diffusoranordnung (60) nach einem der vorangehenden Ansprüche, wobei eine Versorgung der Ringnut (72) mit dem abgezapften Dampf durch wenigstens eine in Radialrichtung durch den Diffusor (62) sich erstreckende Passage (78) erfolgt.A diffuser assembly (60) according to any one of the preceding claims, wherein a supply of the annular groove (72) with the tapped steam through at least one in the radial direction through the diffuser (62) extending passage (78) takes place. Diffusoranordnung (60) nach einem der vorangehenden Ansprüche, wobei eine zur Versorgung der Ringnut mit dem abgezapften Dampf vorgesehene Passage (78) mit einem Rückschlagventil (80) versehen ist.A diffuser assembly (60) according to any one of the preceding claims, wherein a passage (78) provided for supplying the annular groove with the tapped vapor is provided with a check valve (80). Dampfturbine (10), ausgestattet mit einer Diffusoranordnung (60) nach einem der vorangehenden Ansprüche.Steam turbine (10) equipped with a diffuser assembly (60) according to any one of the preceding claims.
EP14151870.4A 2013-03-08 2014-01-21 Diffuser assembly for an exhaust housing of a steam turbine, and steam turbine with the same Active EP2775096B1 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3034784A1 (en) * 2014-12-19 2016-06-22 Siemens Aktiengesellschaft Cooling means for flow engines
EP3290650A1 (en) * 2016-08-29 2018-03-07 Mitsubishi Hitachi Power Systems, Ltd. Low-pressure steam turbine diffuser for reducing shock losses

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59165802A (en) * 1983-03-09 1984-09-19 Toshiba Corp Cooling apparatus for moving blade shroud of steam turbine
DE19905994A1 (en) * 1999-02-15 2000-08-24 Peter Kraus Procedure to prevent shock boundary layer pulsations with annular diffusers in steam turbines entails providing time-controlled blow-in excitation in rear shell region in dead water zone
EP1970539A1 (en) * 2007-03-13 2008-09-17 Siemens Aktiengesellschaft Diffuser assembly
US20120163969A1 (en) * 2010-12-23 2012-06-28 General Electric Company Turbine including exhaust hood
WO2012175328A1 (en) 2011-06-20 2012-12-27 Siemens Aktiengesellschaft Steam-turbine system, comprising a steam turbine and a rotational device for the rotational drive of a turbine rotor shaft during the turbine start-up

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3034784A1 (en) * 2014-12-19 2016-06-22 Siemens Aktiengesellschaft Cooling means for flow engines
WO2016096420A1 (en) * 2014-12-19 2016-06-23 Siemens Aktiengesellschaft Cooling possibility for hydrodynamic machines
EP3290650A1 (en) * 2016-08-29 2018-03-07 Mitsubishi Hitachi Power Systems, Ltd. Low-pressure steam turbine diffuser for reducing shock losses
CN107795344A (en) * 2016-08-29 2018-03-13 三菱日立电力系统株式会社 Turbine

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EP2775096A3 (en) 2018-02-21
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