EP0985803A1 - Turbine stage with radial inlet and axial outlet - Google Patents

Turbine stage with radial inlet and axial outlet Download PDF

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Publication number
EP0985803A1
EP0985803A1 EP98810899A EP98810899A EP0985803A1 EP 0985803 A1 EP0985803 A1 EP 0985803A1 EP 98810899 A EP98810899 A EP 98810899A EP 98810899 A EP98810899 A EP 98810899A EP 0985803 A1 EP0985803 A1 EP 0985803A1
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EP
European Patent Office
Prior art keywords
flow
axial
radial
channel
main
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Granted
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EP98810899A
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German (de)
French (fr)
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EP0985803B1 (en
Inventor
Roland Löpfe
Said Dr. Havakechian
Patrick Dr. Escher
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Alstom SA
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ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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Priority to DE59807746T priority Critical patent/DE59807746D1/en
Priority to EP19980810899 priority patent/EP0985803B1/en
Publication of EP0985803A1 publication Critical patent/EP0985803A1/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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/04—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially axially
    • 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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
    • F01D9/048—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector for radial admission

Definitions

  • the present invention relates to a turbine stage with radial inflow and axial outflow, in which a main flow in one Guide blading is directed radially towards a machine axis and one Barrel blading is flowed through in the main axial flow direction a housing-side duct wall and a hub-side duct wall one Include flow channel, which flow channel from a radial extending part, a part extending in the main axial direction, and one There is radial-axial flow deflection, which radial-axial flow deflection a main radial flow into an axial one Redirects main flow.
  • the first stage of a steam turbine group is often of the radial-axial type executed, in which the guide blading in radial and the Blades are blown through in the main axial direction.
  • the main advantage of this arrangement is that it is simple
  • the staggering of the guide vanes has to be adapted Power and volume flow class can take place.
  • the radial flow In this case, guide vanes can be attached to the housing on both sides, so that no seal against the rotating shaft is installed here got to.
  • the necessary radial-axial flow deflection a very inhomogeneous and lossy flow of the impeller are accepted. Because of the flow diversion a radial pressure gradient is induced in the flow channel in such a way that the pressure from the housing to the hub increases.
  • the object of the present invention is in a turbine stage with radial Inflow and axial outflow, in which a main flow in one Guide blading is directed radially towards a machine axis and one Barrel blading is flowed through in the main axial flow direction a housing-side duct wall and a hub-side duct wall one Include flow channel, which flow channel from a radial extending part, a part extending in the main axial direction, and one There is radial-axial flow deflection, which radial-axial flow deflection a main radial flow into an axial one Redirects main flow, the most homogeneous flow possible To create playpens.
  • the Exit gap of the seal should be designed so that the leakage is as possible parallel to the main flow along the hub, creating potential harmful interactions with the main flow are further reduced become.
  • the single figure shows an example of the embodiment according to the invention a radial-axial turbine stage.
  • the outer radius of the flow deflection is indeed through the housing formed, due to the function, the designation "hub-side Flow diversion "used.
  • the housing-side wall 27 of the overflow channel 50 receives the housing-side wall 27 of the overflow channel 50 for this purpose, immediately downstream of the deflection, a kink A, downstream which it is guided divergent by the machine axis 10. From the Counter-kink B, the housing-side wall 27 again runs parallel to Machine axis 10, or towards this. Likewise, the hub-side wall 28 downstream of a kink AA away from the machine axis 10 and from Counter kink point BB again parallel.
  • the location of the hub-side kinks AA and BB advantageously becomes one Distance downstream of the corresponding bends A and B on the housing side chosen.
  • the pronounced maximum speed, which is on the hub side Deflection 26 forms, dismantled; furthermore, the seal exit gap 30 additionally supplied mass flow of the main flow under largely avoid harmful interactions.
  • the flow upstream of the Impeller La accelerated in the axial direction which if necessary Areas of excessive impeller incorrect flow occur in particular of the hub-side channel wall 28 can be significantly reduced.
  • the location of the seal exit gap 30 is advantageously at one point selected the highest possible pressure in the flow channel, and such that by the centrifugal force of the main flow the penetration depth of the Leakage flow in the flow channel is limited. The latter can continue to be supported by the fact that the exit gap 30 at the end of the Radial-axial deflection is placed, and the outlet gap 30 through its Design the leakage flow as laminar as possible and parallel to the hub side Channel wall 28 leads.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

At the turbine step, in a steam turbine, the working medium is deflected from an inflow spiral (41) through the inflow channel (40) into a radial direction by a guide grid (Le). At the following downstream flow channel (50), the flow is deflected so that it has an axial flow through the following turbine wheel (La). The structure of the wall contours (27,28) of the housing (20) and hub (21) give the main flow line (51) initially a direction component which is radially outwards and then, shortly before the turbine wheel (La), a pure axial alignment. The flow through the turbine wheel (La) is homogenized by a curvature which is against the original deflection curvature. The kink points (AA,BB) at the channel wall (28), at the hub side, are downstream of the corresponding kink points (A,B) at the housing side of the channel. The flow is additionally homogenized by the divergent-convergent channel contour structure.

Description

Technisches GebietTechnical field

Die vorliegende Erfindung betrifft eine Turbinenstufe mit radialer Zuströmung und axialer Abströmung, bei der eine Hauptströmung in einer Leitbeschaufelung radial zu einer Maschinenachse hin gerichtet ist und eine Laufbeschaufelung in axialer Hauptströmungsrichtung durchströmt wird, wobei eine gehäuseseitige Kanalwand und eine nabenseitige Kanalwand einen Strömungskanal einschliessen, welcher Strömungskanal aus einem radial verlaufenden Teil, einem in axialer Hauptrichtung verlaufenden Teil, und einer Radial-Axial-Strömungsumlenkung besteht, welche Radial-Axial-Strömungsumlenkung eine radiale Hauptströmung in eine axiale Hauptströmung umlenkt.The present invention relates to a turbine stage with radial inflow and axial outflow, in which a main flow in one Guide blading is directed radially towards a machine axis and one Barrel blading is flowed through in the main axial flow direction a housing-side duct wall and a hub-side duct wall one Include flow channel, which flow channel from a radial extending part, a part extending in the main axial direction, and one There is radial-axial flow deflection, which radial-axial flow deflection a main radial flow into an axial one Redirects main flow.

Stand der TechnikState of the art

Die erste Stufe einer Dampfturbogruppe wird häufig in radial-axialer Bauart ausgeführt, bei der die Leitbeschaufelung in radialer und die Laufbeschaufelung in axialer Hauptrichtung durchströmt werden. Ein Hauptvorteil dieser Anordnung ist darin zu sehen, dass durch eine einfach vorzunehmende Umstaffelung der Leitschaufeln eine Anpassung der Leistungs- und Volumenstromklasse erfolgen kann. Die radial angeströmten Leitschaufeln können in diesem Falle beidseitig am Gehäuse befestigt sein, so, dass hier keine Dichtung gegenüber der rotierenden Welle eingebaut werden muss. Andererseits muss durch die notwendige Radial-Axial-Strömungsumlenkung eine sehr inhomogene und verlustbehaftete Anströmung des Laufrades in Kauf genommen werden. Aufgrund der Strömungsumlenkung wird ein radialer Druckgradient im Strömungskanal induziert, dergestalt, dass der Druck vom Gehäuse zur Nabe hin zunimmt. Insbesondere bei einem kleinen Abströmwinkel des Leitgitters und einer daraus resultierenden drallarmen Strömung zwischen Leit- und Laufgitter besteht darüber hinaus die Gefahr einer gehäuseseitigen Strömungsablösung beim Übergang von der radialen zur axialen Hauptströmung. Beide Faktoren führen potentiell zu schädlichen Sekundärströmungen im unmittelbar stromab gelegenen Laufrad.The first stage of a steam turbine group is often of the radial-axial type executed, in which the guide blading in radial and the Blades are blown through in the main axial direction. On The main advantage of this arrangement is that it is simple The staggering of the guide vanes has to be adapted Power and volume flow class can take place. The radial flow In this case, guide vanes can be attached to the housing on both sides, so that no seal against the rotating shaft is installed here got to. On the other hand, the necessary radial-axial flow deflection a very inhomogeneous and lossy flow of the impeller are accepted. Because of the flow diversion a radial pressure gradient is induced in the flow channel in such a way that the pressure from the housing to the hub increases. Especially with one small outflow angle of the guide vane and a resulting one There is also a low-swirl flow between the guide and playpen Danger of flow separation on the housing side during the transition from the radial to the main axial flow. Both factors potentially lead to harmful secondary currents in the immediately downstream impeller.

Leckageströmungen, die etwa aus einer Dichtung zwischen einem Schubausgleichskolben und dem Strömungskanal resultieren, können zu einer zusätzlichen Fehlanströmung des Laufgitters in Nabennähe führen.Leakage flows that arise from a seal between one Thrust compensating pistons and the flow channel can result in a lead to additional incorrect flow of air on the playpen near the hub.

Darstellung der ErfindungPresentation of the invention

Aufgabe der vorliegenden Erfindung ist, bei einer Turbinenstufe mit radialer Zuströmung und axialer Abströmung, bei der eine Hauptströmung in einer Leitbeschaufelung radial zu einer Maschinenachse hin gerichtet ist und eine Laufbeschaufelung in axialer Hauptströmungsrichtung durchströmt wird, wobei eine gehäuseseitige Kanalwand und eine nabenseitige Kanalwand einen Strömungskanal einschliessen, welcher Strömungskanal aus einem radial verlaufenden Teil, einem in axialer Hauptrichtung verlaufenden Teil, und einer Radial-Axial-Strömungsumlenkung besteht, welche Radial-Axial-Strömungsumlenkung eine radiale Hauptströmung in eine axiale Hauptströmung umlenkt, eine möglichst homogene Anströmung des Laufgitters zu schaffen.The object of the present invention is in a turbine stage with radial Inflow and axial outflow, in which a main flow in one Guide blading is directed radially towards a machine axis and one Barrel blading is flowed through in the main axial flow direction a housing-side duct wall and a hub-side duct wall one Include flow channel, which flow channel from a radial extending part, a part extending in the main axial direction, and one There is radial-axial flow deflection, which radial-axial flow deflection a main radial flow into an axial one Redirects main flow, the most homogeneous flow possible To create playpens.

Erfindungsgemäss wird dies dadurch erreicht, dass stromab der Radial-Axial-Strömungsumlenkung der in axialer Hauptrichtung gerichtete Teil des Strömungskanals in einem ersten Abschnitt von der Maschinenachse weg weist, und unmittelbar vor der Laufbeschaufelung in rein axialer Richtung verläuft.. Durch die Krümmung der Hauptstromlinie entgegen der ursprünglichen Umlenkung wird eine Homogenisierung der Axialgeschwindigkeit und des Druckes über der Kanalhöhe erreicht.This is achieved according to the invention in that downstream of the radial-axial flow deflection the part of the axially directed Flow channel in a first section away from the machine axis points, and immediately before the blading in the purely axial direction runs .. By the curvature of the main streamline against the original redirection becomes a homogenization of the Axial speed and pressure above the duct height reached.

Aufgrund der vergrösserten Länge des Zuströmkanals kann es abhängig von der Kanalgeometrie zu einem unerwünscht starken Anwachsen der Grenzschichten kommen. Innerhalb der Grenzschicht stellt sich, abhängig von der spezifischen Stufenkinematik, unter Umständen insbesondere nabenseitig ein krasses Missverhältnis von Axial- und Umfangsgeschwindigkeit ein: Zur Nabe hin nimmt aufgrund der Rotation der Welle die Umfangsgeschwindigkeit des Arbeitsmediums weniger stark ab als die Axialkomponente. In der nabenseitigen Grenzschicht wandert der Staupunkt der Anströmung einer Laufschaufel somit auf die Druckseite, wodurch die akute Gefahr der saugseitigen Ablösung besteht. Die radiale Ausdehnung des betroffenen Schaufelbereichs wird verkleinert, indem die Strömung unmittelbar vor dem Laufradeintritt in Richtung der Maschinenachse beschleunigt, das heisst der Querschnitt des Strömungskanals verkleinert, wird.Due to the increased length of the inflow channel, it may depend on the channel geometry to an undesirably strong increase in the Boundary layers come. Within the boundary layer, depending on the specific step kinematics, in particular under certain circumstances on the hub side a gross mismatch between axial and peripheral speed on: Due to the rotation of the shaft, the Peripheral speed of the working medium less than that Axial component. The stagnation point migrates in the hub-side boundary layer the flow of a blade on the pressure side, which causes the acute There is a risk of detachment on the suction side. The radial expansion of the affected blade area is reduced by the flow immediately accelerates in the direction of the machine axis before entering the impeller means the cross section of the flow channel is reduced.

Unmittelbar stromab der Radial-Axial-Strömungsumlenkung hingegen ist eine Querschnittserweiterung des Strömungskanals von Vorteil. Bei geringem Drall der Leitrad-Abströmung steigt hierdurch einerseits die Ablösegefahr der Strömung auf der Gehäuseseite, jedoch werden die nabenseitig vorliegenden ausgeprägten Geschwindigkeitsmaxima abgebaut, was ebenfalls zu einer Vergleichmässigung des Axialgeschwindigkeitsprofils beiträgt. Die Querschnittserweiterung ist, wie unten dargestellt, ebenso von Vorteil, wenn eine Leckageströmung zugemischt werden muss. On the other hand, immediately downstream of the radial-axial flow deflection is one Cross-sectional expansion of the flow channel is an advantage. With little twist the outflow of the stator thus increases the risk of separation Flow on the housing side, however, the existing ones on the hub side pronounced speed maxima reduced, which also leads to a Uniformity of the axial speed profile contributes. The Cross-sectional expansion, as shown below, is also beneficial if a leakage flow must be added.

Bei Maschinen der eingangs erwähnten Bauart ist häufig auf der Einströmseite ein Schubausgleichskolben auf der Welle angeordnet. In diesem Fall muss eine Leckageströmung aus der Abdichtung zwischen Welle und Gehäuse in den Überströmkanal zwischen Leit- und Laufbeschaufelung eingebracht werden. Die Leckageströmung birgt jedoch ein zusätzliches Potential zur Störung der Hauptströmung und der Fehlanströmung des Laufgitters. Dieser Störeffekt kann durch mehrere, teilweise bereits vorweggenommene Massnahmen deutlich reduziert werden. Hierzu wird der Austrittsspalt der Dichtung nabenseitig am stromab gelegenen Ende der Radial-Axial-Strömungsumlenkung plaziert. Durch die Strömungsumlenkung einerseits und die stromab gelegene Querschnittserweiterung des Strömungskanals besteht somit an der Stelle, an der der Leckagestrom eingebracht wird, ein Gebiet hohen Druckes im Überströmkanal, wodurch der Leckagemassenstrom bei gegebener Dichtungsgeometrie reduziert wird. Zusätzlich kann der Austrittsspalt der Dichtung so ausgebildet werden, dass die Leckage möglichst parallel zur Hauptströmung entlang der Nabe geführt wird, wodurch potentielle schädliche Wechselwirkungen mit der Hauptströmung nochmals reduziert werden.In the case of machines of the type mentioned at the outset, it is often on the inflow side a thrust compensation piston is arranged on the shaft. In this case a leakage flow from the seal between the shaft and housing in the overflow channel between guide and blading introduced become. However, the leakage flow has additional potential Disruption of the main flow and incorrect flow against the playpen. This Interference can be caused by several, some already anticipated Measures are significantly reduced. For this purpose, the exit gap of the Seal on the hub side at the downstream end of the radial-axial flow deflection placed. Due to the flow deflection on the one hand and there is the downstream cross-sectional expansion of the flow channel thus an area at the point at which the leakage flow is introduced high pressure in the overflow channel, whereby the leakage mass flow at given seal geometry is reduced. In addition, the Exit gap of the seal should be designed so that the leakage is as possible parallel to the main flow along the hub, creating potential harmful interactions with the main flow are further reduced become.

Im folgenden wird ein Beispiel für die Ausführung der Erfindung anhand der Zeichnung erläutert.The following is an example of the implementation of the invention using the Drawing explained.

Kurze Beschreibung der ZeichnungBrief description of the drawing

Die einzige Figur zeigt ein Beispiel für die erfindungsgemässe Ausführung einer radial-axialen Turbinenstufe. The single figure shows an example of the embodiment according to the invention a radial-axial turbine stage.

Der Aussenradius der Strömungsumlenkung wird zwar durch das Gehäuse gebildet, aufgrund der Funktion wird dennoch die Bezeichnung "nabenseitige Strömungsumlenkung" gebraucht.The outer radius of the flow deflection is indeed through the housing formed, due to the function, the designation "hub-side Flow diversion "used.

Weg zur Ausführung der ErfindungWay of carrying out the invention

Bei der in der Abbildung dargestellten radial-axialen Turbinenstufe strömt das Arbeitsmedium aus der asymmetrisch ausgebildeten Einströmspirale durch den Einströmkanal 40 in radialer Richtung durch das Leitgitter Le in den Überströmkanal 50, und wird in der durch die Kanalwände 25, 26 gebildete Radial-Axial-Strömungsumlenkung in axiale Richtung gelenkt. Erfindungsgemäss werden die Kanalwände 27, 28 bis zum Eintritt in das Laufgitter La so gestaltet, dass der Hauptstromlinie 51 unmittelbar stromab der Radial-Axial-Strömungsumlenkung eine radial nach aussen gerichtete Komponente aufgeprägt wird, und die Hauptstromlinie 51 unmittelbar stromauf des Laufrades La wieder in rein axiale Richtung geführt wird. Im Ausführungsbeispiel erhält die gehäuseseitige Wand 27 des Überströmkanals 50 hierzu unmittelbar stromab der Umlenkung eine Knickstelle A, stromab derer sie von der Maschinenachse 10 divergent geführt wird. Ab der Gegenknickstelle B verläuft die gehäuseseitige Wand 27 wieder parallel zur Maschinenachse 10, oder auf diese zu. Ebenso wird die nabenseitige Wand 28 stromab einer Knickstelle AA von der Maschinenachse 10 weg- und ab der Gegenknickstelle BB wieder parallel geführt.This flows in the radial-axial turbine stage shown in the figure Working medium from the asymmetrically designed inflow spiral through the Inflow channel 40 in the radial direction through the guide grill Le in the Overflow channel 50, and is formed in the by the channel walls 25, 26 Radial-axial flow deflection directed in the axial direction. According to the invention, the channel walls 27, 28 until they enter the Playpen La designed so that the main streamline 51 immediately downstream of the Radial-axial flow deflection is directed radially outwards Component is impressed, and the main streamline 51 immediately upstream of the impeller La is again guided in the purely axial direction. in the Embodiment receives the housing-side wall 27 of the overflow channel 50 for this purpose, immediately downstream of the deflection, a kink A, downstream which it is guided divergent by the machine axis 10. From the Counter-kink B, the housing-side wall 27 again runs parallel to Machine axis 10, or towards this. Likewise, the hub-side wall 28 downstream of a kink AA away from the machine axis 10 and from Counter kink point BB again parallel.

Mit Vorteil wird die Lage der nabenseitigen Knickstellen AA und BB eine Strecke stromab der korrespondierenden gehäuseseitigen Knickstellen A und B gewählt. Hierdurch entsteht ein divergent-konvergenter Verlauf des Strömungskanals 50 im wesentlich axial gerichteten Teil des Strömungskanals 50 stromab der Radial-Axial-Strömungsumlenkung. Im divergenten Teil wird das ausgeprägte Geschwindigkeitsmaximum, das sich an der nabenseitigen Umlenkung 26 ausbildet, abgebaut; weiterhin wird der aus dem DichtungsAustrittsspalt 30 zusätzlich zugeführte Massenstrom der Hauptströmung unter weitgehender Vermeidung schädlicher Wechselwirkungen zugeführt. Im konvergentenTeil des Strömungskanals 50 wird die Strömung stromauf des Laufrades La in axialer Richtung beschleunigt, wodurch gegebenenfalls auftretende Gebiete übermässiger Laufrad-Fehlanströmung insbesondere an der nabenseitigen Kanalwand 28 signifikant verkleinert werden.The location of the hub-side kinks AA and BB advantageously becomes one Distance downstream of the corresponding bends A and B on the housing side chosen. This creates a divergent-convergent course of the Flow channel 50 in the substantially axially directed part of the flow channel 50 downstream of the radial-axial flow deflection. In the divergent part the pronounced maximum speed, which is on the hub side Deflection 26 forms, dismantled; furthermore, the seal exit gap 30 additionally supplied mass flow of the main flow under largely avoid harmful interactions. in the convergent part of the flow channel 50, the flow upstream of the Impeller La accelerated in the axial direction, which if necessary Areas of excessive impeller incorrect flow occur in particular of the hub-side channel wall 28 can be significantly reduced.

Die Lage des Dichtungs-Austrittsspaltes 30 wird mit Vorteil an einer Stelle möglichst hohen Druckes im Strömungskanal gewählt, und dergestalt, dass durch die Zentrifugalkraft der Hauptströmung die Eindringtiefe der Leckageströmung in den Strömungskanal begrenzt wird. Letzteres kann weiterhin dadurch unterstützt werden, dass der Austriftsspalt 30 am Ende der Radial-Axial-Umlenkung plaziert wird, und der Austrittsspalt 30 durch seine Gestaltung den Leckagestrom möglichst laminar und parallel zur nabenseitigen Kanalwand 28 führt. The location of the seal exit gap 30 is advantageously at one point selected the highest possible pressure in the flow channel, and such that by the centrifugal force of the main flow the penetration depth of the Leakage flow in the flow channel is limited. The latter can continue to be supported by the fact that the exit gap 30 at the end of the Radial-axial deflection is placed, and the outlet gap 30 through its Design the leakage flow as laminar as possible and parallel to the hub side Channel wall 28 leads.

BezugszeichenlisteReference list

1010th
MaschinenachseMachine axis
2020th
Gehäusecasing
2121
Nabehub
2525th
gehäuseseitige Strömungsbegrenzung der radial-axial-UmlenkungFlow limitation of the radial-axial deflection on the housing side
2626
nabenseitige Strömungsbegrenzung der radial-axial-UmlenkungFlow limitation of the radial-axial deflection on the hub side
2727
gehäuseseitige Kanalwandduct wall on the housing side
2828
nabenseitige Kanalwandchannel wall on the hub side
3030th
Leckagespalt einer berührungslosen DichtungLeakage gap of a non-contact seal
4040
radiale Einlaufstreckeradial inlet section
4141
EinlaufspiraleInlet spiral
5050
Überströmkanal vom Leitrad zum LaufradOverflow channel from the stator to the impeller
5151
HauptstromlinieMain streamline
AA
gehäuseseitige Knickstellekink on the housing side
BB
gehäuseseitige Gegenknickstellecounter kink on the housing side
AAAA
nabenseitige Knickstellehub-side kink
BBBB
nabenseitige Gegenknickstellecounterbend on the hub side
LeLe
LeitgitterGuide grill
LaLa
LaufgitterPlaypen

Claims (8)

Turbinenstufe mit radialer Zuströmung und axialer Abströmung, bei der eine Hauptströmung in einer Leitbeschaufelung (Le) radial zu einer Maschinenachse (10) hin gerichtet ist und eine Laufbeschaufelung (La) in axialer Hauptströmungsrichtung durchströmt wird, wobei eine gehäuseseitige Kanalwand (27) und eine nabenseitige Kanalwand (28) einen Strömungskanal (50) einschliessen, welcher Strömungskanal aus einem radial verlaufenden Teil, einem in axialer Hauptrichtung verlaufenden Teil, und einer Radial-Axial-Strömungsumlenkung besteht, welche Radial-Axial-Strömungsumlenkung eine radiale Hauptströmung in eine axiale Hauptströmung umlenkt , dadurch gekennzeichnet, dass stromab der Radial-Axial-Strömungsumlenkung der in axialer Hauptrichtung gerichtete Teil des Strömungskanals (50) in einem ersten Teil von der Maschinenachse (10) weg weist, und unmittelbar vor der Laufbeschaufelung (La) in rein axiale Richtung geführt ist.Turbine stage with radial inflow and axial outflow, with one Main flow in a guide blading (Le) radial to one Machine axis (10) is directed and a blading (La) in axial main flow direction is flowed through, one channel wall (27) on the housing side and a channel wall (28) on the hub side include a flow channel (50), which flow channel consists of a radially running part, a running in the axial main direction Part, and there is a radial-axial flow deflection, which radial-axial flow deflection a main radial flow into an axial one Diverts main flow, characterized in that downstream of the Radial-axial flow deflection of the directed in the axial main direction Part of the flow channel (50) in a first part of the Machine axis (10) points away, and immediately before Blading (La) is guided in a purely axial direction. Turbinenstufe nach Anspruch 1, dadurch gekennzeichnet, dass der Strömungskanal (50) unmittelbar stromauf der Laufbeschaufelung (La) eine Abnahme des durchströmten Querschnitts aufweist.Turbine stage according to claim 1, characterized in that the Flow channel (50) immediately upstream of the blading (La) one Has a decrease in the cross-section flowed through. Turbinenstufe nach einem der Ansprüche 1 oder 2,dadurch gekennzeichnet, dass der Strömungskanal (50) unmittelbar stromab der Radial-Axial-Strömungsumlenkung eine Querschnittserweiterung aufweist.Turbine stage according to one of claims 1 or 2, characterized characterized in that the flow channel (50) immediately downstream of the Radial-axial flow deflection has a cross-sectional expansion. Turbinenstufe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die gehäuseseitige Kanalwand (27) zwischen der Radial-Axial-Strömungsumlenkung und dem Laufrad-Eintritt mindestens eine Knickstelle (A) aufweist, stromab derer die gehäuseseitige Kanalwand (27) in Hauptströmungsrichtung (51) von der Maschinenachse (10) weg weist, und, dass stromab der Knickstelle (A) mindestens eine Gegenknickstelle (B) angeordnet ist.Turbine stage according to one of claims 1 to 3, characterized in that the housing-side channel wall (27) between the radial-axial flow deflection and the impeller inlet at least one kink (A), downstream of which the housing-side duct wall (27) in Main flow direction (51) points away from the machine axis (10), and, that at least one counter kink (B) downstream of the kink (A) is arranged. Turbinenstufe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die nabenseitige Kanalwand (28) zwischen der Radial-Axial-Strömungsumlenkung und dem Laufrad-Eintritt mindestens eine Knickstelle (AA) aufweist, stromab derer die nabenseitige Kanalwand (28) in Hauptströmungsrichtung (51) von der Maschinenachse (10) weg weist, und, dass stromab der Knickstelle (AA) mindestens eine Gegenknickstelle (BB) angeordnet ist.Turbine stage according to one of claims 1 to 4, characterized in that that the hub-side channel wall (28) between the radial-axial flow deflection and the impeller inlet at least one kink (AA), downstream of which the hub-side channel wall (28) in Main flow direction (51) points away from the machine axis (10), and, that at least one counter kink (BB) downstream of the kink (AA) is arranged. Turbinenstufe nach Anspruch 5, dadurch gekennzeichnet, dass die nabenseitigen Knickstellen (AA, BB) stromab der korrespondierenden gehäusesitigen Knickstellen (A, B)angeordnet sind.Turbine stage according to claim 5, characterized in that the hub-side kinks (AA, BB) downstream of the corresponding one kinks (A, B) on the housing side are arranged. Turbinenstufe nach einem der Ansprüche 1 bis 6, bei der ein Leckagestrom einer berührungslosen Dichtung in die Hauptströmung einströmt, dadurch gekennzeichnet, dass ein Austrittsspalt der berührungslosen Dichtung so angeordnet wird, dass der Leckagestrom an einer Stelle höchsten Druckes im Strömungskanal eingebracht ist.Turbine stage according to one of claims 1 to 6, in which a leakage flow a non-contact seal flows into the main flow, thereby characterized in that an exit gap of the non-contact seal is arranged that the leakage flow at a point of maximum pressure is introduced in the flow channel. Turbinenstufe nach einem der Ansprüche 1 bis 7, bei der ein Leckagestrom einer berührungslosen Dichtung in die Hauptströmung einströmt, dadurch gekennzeichnet, dass eine Leckageströmung parallel zur Hauptströmung geführt ist.Turbine stage according to one of claims 1 to 7, in which a leakage flow a non-contact seal flows into the main flow, thereby characterized that a leakage flow parallel to the main flow is led.
EP19980810899 1998-09-10 1998-09-10 Turbine stage with radial inlet and axial outlet Expired - Lifetime EP0985803B1 (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1496196A1 (en) * 2003-07-08 2005-01-12 Siemens Aktiengesellschaft Steam turbine
GB2440344A (en) * 2006-07-26 2008-01-30 Christopher Freeman Impulse turbine design
CN101094971B (en) * 2004-11-02 2011-03-09 阿尔斯托姆科技有限公司 Optimised turbine stage for a turbine engine and layout method

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2429936A (en) * 1943-12-18 1947-10-28 Allis Chalmers Mfg Co Turbine mounting
DE1076145B (en) * 1953-08-25 1960-02-25 Siemens Ag High pressure turbine with radial blading of the constant pressure control stage
GB1162440A (en) * 1967-06-05 1969-08-27 Shell Int Research Gas Turbine.
DE2231015A1 (en) * 1972-05-31 1973-12-20 Bbc Brown Boveri & Cie FIRST STAGE OF A DOUBLE FLOW LOW PRESSURE STEAM TURBINE OF HIGH PERFORMANCE
EP0024275A1 (en) * 1979-08-15 1981-03-04 BBC Aktiengesellschaft Brown, Boveri & Cie. Arresting of nozzle rings
DE4014976C1 (en) * 1990-05-10 1991-07-25 Mtu Friedrichshafen Gmbh Exhaust turbocharger with two-stage axial exhaust turbine - has duct section, adjacent to first turbine stage, as part of axially displaceable ring slider

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2429936A (en) * 1943-12-18 1947-10-28 Allis Chalmers Mfg Co Turbine mounting
DE1076145B (en) * 1953-08-25 1960-02-25 Siemens Ag High pressure turbine with radial blading of the constant pressure control stage
GB1162440A (en) * 1967-06-05 1969-08-27 Shell Int Research Gas Turbine.
DE2231015A1 (en) * 1972-05-31 1973-12-20 Bbc Brown Boveri & Cie FIRST STAGE OF A DOUBLE FLOW LOW PRESSURE STEAM TURBINE OF HIGH PERFORMANCE
EP0024275A1 (en) * 1979-08-15 1981-03-04 BBC Aktiengesellschaft Brown, Boveri & Cie. Arresting of nozzle rings
DE4014976C1 (en) * 1990-05-10 1991-07-25 Mtu Friedrichshafen Gmbh Exhaust turbocharger with two-stage axial exhaust turbine - has duct section, adjacent to first turbine stage, as part of axially displaceable ring slider

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1496196A1 (en) * 2003-07-08 2005-01-12 Siemens Aktiengesellschaft Steam turbine
WO2005005783A1 (en) * 2003-07-08 2005-01-20 Siemens Aktiengesellschaft Steam turbine
CN101094971B (en) * 2004-11-02 2011-03-09 阿尔斯托姆科技有限公司 Optimised turbine stage for a turbine engine and layout method
GB2440344A (en) * 2006-07-26 2008-01-30 Christopher Freeman Impulse turbine design

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