EP0985803B1 - Turbine stage with radial inlet and axial outlet - Google Patents
Turbine stage with radial inlet and axial outlet Download PDFInfo
- Publication number
- EP0985803B1 EP0985803B1 EP19980810899 EP98810899A EP0985803B1 EP 0985803 B1 EP0985803 B1 EP 0985803B1 EP 19980810899 EP19980810899 EP 19980810899 EP 98810899 A EP98810899 A EP 98810899A EP 0985803 B1 EP0985803 B1 EP 0985803B1
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- flow
- axial
- radial
- turbine stage
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- 238000011144 upstream manufacturing Methods 0.000 claims description 3
- 230000003993 interaction Effects 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 241000792859 Enema Species 0.000 description 1
- 230000001154 acute effect Effects 0.000 description 1
- 230000003466 anti-cipated effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000007920 enema Substances 0.000 description 1
- 229940095399 enema Drugs 0.000 description 1
- 238000000265 homogenisation Methods 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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Classifications
-
- 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 blades are directed radially towards a machine axis and a 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 running in the axial main direction, and one There is radial-axial flow deflection, which is 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. See, for example, document DE-A-2 231 015
- the main advantage of this arrangement is that it is simple
- the staggering of the guide vanes 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.
- 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 blades are directed radially towards a machine axis and a 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 running in the axial main direction, and one There is radial-axial flow deflection, which is radial-axial flow deflection a main radial flow into an axial one Redirects main flow, the most homogeneous flow possible To create playpens.
- this is achieved 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 ..
- curvature of the main streamline against the original redirection becomes a homogenization of the Axial speed and pressure above the duct height reached.
- 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 selected.
- the pronounced maximum speed, which is on the hub side Deflection 26 forms, dismantled; furthermore, the seal outlet gap 30 additionally supplied mass flow of the main flow below 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)
Description
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 blades are directed radially towards a machine axis and a 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 running in the axial main direction, and one There is radial-axial flow deflection, which is radial-axial flow deflection a main radial flow into an axial one Redirects main flow.
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. Siehe hierzu z.B das Dokument DE-A-2 231 015. 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. See, for example, document DE-A-2 231 015 The main advantage of this arrangement is that it is simple The staggering of the guide vanes 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.
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 Strörnungskanal 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 blades are directed radially towards a machine axis and a 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 running in the axial main direction, and one There is radial-axial flow deflection, which is 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.According to the invention, this is achieved 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 blatant mismatch between axial and circumferential 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 ones on the hub side are present 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 beginning, there 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 introduced the overflow channel between guide and blading 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 the downstream cross-sectional expansion of the flow channel exists 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.
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.
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
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 Dichtungs-Austrittsspalt
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
selected. This creates a divergent-convergent course of the
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
- 1010
- Maschinenachsemachine axis
- 2020
- Gehäusecasing
- 2121
- Nabehub
- 2525
- 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
- 3030
- Leckagespalt einer berührungslosen DichtungLeakage gap of a non-contact seal
- 4040
- radiale Einlaufstreckeradial inlet section
- 4141
- Einlaufspiraleenema spiral
- 5050
- Überströmkanal vom Leitrad zum LaufradOverflow channel from the stator to the impeller
- 5151
- HauptstromlinieMain power line
- 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 grid
- LaLa
- Laufgitterpen
Claims (8)
- Turbine stage with radial inlet flow and axial outlet flow, in which, in guide blading (Le), a main flow is directed radially relative to a machine centre line (10) and flow through rotor blading (La) takes place in an axial main flow direction, in which arrangement a casing-side duct wall (27) and a hub-side duct wall (28) enclose a flow duct (50), which flow duct consists of a radially extending part, a part extending in an axial main direction and a radial/axial flow deflection arrangement, which radial/axial flow deflection arrangement deflects a radial main flow into an axial main flow, characterized in that downstream of the radial/axial flow deflection arrangement, the part of the flow duct (50) directed in an axial main direction is directed away from the machine centre line (10) in a first part and is guided into a purely axial direction immediately before the rotor blading (La).
- Turbine stage according to Claim 1, characterized in that the flow duct (50) has a reduction of the flow cross section immediately upstream of the rotor blading (La).
- Turbine stage according to one of Claims 1 or 2, characterized in that the flow duct (50) has an increase in cross section immediately downstream of the radial/axial deflection arrangement.
- Turbine stage according to one of Claims 1 to 3, characterized in that the casing-side duct wall (27) has at least one kink location (A) between the radial/axial flow deflection arrangement and the rotor inlet, the casing-side duct wall (27) being directed away from the machine centre line (10) in a main flow direction (51) downstream of which kink location (A), and in that at least one opposing kink location (B) is arranged downstream of the kink location (A).
- Turbine stage according to one of Claims 1 to 4, characterized in that the hub-side duct wall (28) has at least one kink location (AA) between the radial/axial flow deflection arrangement and the rotor inlet, the hub-side duct wall (28) being directed away from the machine centre line (10) in a main flow direction (51) downstream of which kink location (AA), and in that at least one opposing kink location (BB) is arranged downstream of the kink location (AA).
- Turbine stage according to Claim 5, characterized in that the hub-side kink locations (AA, BB) are arranged downstream of the corresponding casing-side kink locations (A, B).
- Turbine stage according to one of Claims 1 to 6, in which a leakage flow of a contactless seat flows into the main flow, characterized in that an outlet gap of the contactless seal is arranged in such a way that the leakage flow is introduced into the flow duct at a location of maximum pressure.
- Turbine stage according to one of Claims 1 to 7, in which a leakage flow of a contactless seal flows into the main flow, characterized in that a leakage flow is guided parallel to the main flow.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP19980810899 EP0985803B1 (en) | 1998-09-10 | 1998-09-10 | Turbine stage with radial inlet and axial outlet |
| DE59807746T DE59807746D1 (en) | 1998-09-10 | 1998-09-10 | Turbine stage with radial inflow and axial outflow |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP19980810899 EP0985803B1 (en) | 1998-09-10 | 1998-09-10 | Turbine stage with radial inlet and axial outlet |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0985803A1 EP0985803A1 (en) | 2000-03-15 |
| EP0985803B1 true EP0985803B1 (en) | 2003-04-02 |
Family
ID=8236307
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP19980810899 Expired - Lifetime EP0985803B1 (en) | 1998-09-10 | 1998-09-10 | Turbine stage with radial inlet and axial outlet |
Country Status (2)
| Country | Link |
|---|---|
| EP (1) | EP0985803B1 (en) |
| DE (1) | DE59807746D1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1496196A1 (en) * | 2003-07-08 | 2005-01-12 | 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 |
Family Cites Families (6)
| 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. |
| CH545414A (en) * | 1972-05-31 | 1973-12-15 | 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 |
-
1998
- 1998-09-10 DE DE59807746T patent/DE59807746D1/en not_active Expired - Fee Related
- 1998-09-10 EP EP19980810899 patent/EP0985803B1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| EP0985803A1 (en) | 2000-03-15 |
| DE59807746D1 (en) | 2003-05-08 |
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