EP2601383A1 - Gas turbine rotor comprising an axially displaceable turbine rotor shaft - Google Patents

Gas turbine rotor comprising an axially displaceable turbine rotor shaft

Info

Publication number
EP2601383A1
EP2601383A1 EP11740864.1A EP11740864A EP2601383A1 EP 2601383 A1 EP2601383 A1 EP 2601383A1 EP 11740864 A EP11740864 A EP 11740864A EP 2601383 A1 EP2601383 A1 EP 2601383A1
Authority
EP
European Patent Office
Prior art keywords
rotor shaft
compressor
gas turbine
turbine rotor
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.)
Withdrawn
Application number
EP11740864.1A
Other languages
German (de)
French (fr)
Inventor
Stefan Braun
Christopher Butzeck
Jürgen Hahn
Peter Schröder
Hubertus Michael Wigger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP11740864.1A priority Critical patent/EP2601383A1/en
Publication of EP2601383A1 publication Critical patent/EP2601383A1/en
Withdrawn legal-status Critical Current

Links

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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/026—Shaft to shaft connections
    • 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
    • F01D11/14—Adjusting or regulating tip-clearance, i.e. distance between rotor-blade tips and stator casing
    • F01D11/20—Actively adjusting tip-clearance
    • F01D11/22—Actively adjusting tip-clearance by mechanically actuating the stator or rotor components, e.g. moving shroud sections relative to the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D1/101—Quick-acting couplings in which the parts are connected by simply bringing them together axially without axial retaining means rotating with the coupling
    • 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
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/37—Retaining components in desired mutual position by a press fit connection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections

Definitions

  • the invention relates to a gas turbine rotor according to the
  • Gas turbines comprise, in addition to one or more combustion chambers essentially a compressor and a downstream turbine, via a common rotor shaft in the axial
  • Energy production is the highest possible efficiency, ie the ratio of generated to the energy used a significant size.
  • Gap optimization is used to optimize the overall efficiency of the gas turbine.
  • the gas turbine rotor is moved counter to the flow direction of the hot gas to minimize the radial gap between the blade tips and the hot gas duct wall in a conically shaped hot gas duct.
  • Compressor rotor connects, it is mounted so that it can be moved in the axial direction. This can be used to optimize the turbine column in favor of
  • Compressor column adjusted to the detriment of the compressor efficiency. In order to avoid this opposite effect and thus to further optimize the overall efficiency, it was already considered to separate the common rotor at the interface of the compressor to the turbine and the two
  • Turbine efficiency through the hydraulic gap optimization thus no longer causes a simultaneous deterioration of the compressor efficiency, which would counteract the actual goal.
  • the object of the invention is to further improve
  • a gas turbine rotor for a gas turbine comprising a compressor rotor shaft and a compressor rotor shaft axially displaceable turbine rotor shaft and the two rotor shafts always connecting
  • the compressor rotor shaft is designed as a hollow shaft through which the turbine rotor shaft is passed.
  • Compressor rotor shaft designed as a hollow shaft is the extended end of the turbine rotor shaft through this
  • Positioning of the compressor rotor shaft and provided for axial positioning of the turbine rotor shaft, can both the compressor rotor and the turbine rotor are displaced independently of each other with respect to the gas turbine casing.
  • the gap optimization can thus be carried out separately for both parts - turbine and compressor - so that an optimal overall efficiency of the gas turbine can be achieved.
  • Efficiency losses in the compressor which arise in known rigid couplings of the two shafts due to an axial displacement in favor of the turbine efficiency, can be avoided.
  • the gas turbine can also operate in an extended operating range, such as part load or hot start.
  • an extended operating range such as part load or hot start.
  • FIG. 1 shows schematically a known gas turbine rotor
  • FIG. 3 shows a section through that shown in FIG
  • Gas turbine rotor for a gas turbine.
  • the gas turbine comprises in addition to a combustion device 1 for generating
  • Hot gas a compressor 10 with a compressor rotor shaft 100, a turbine 20 with a turbine rotor shaft 200 and a positive coupling device 300 between Compressor and turbine rotor shaft.
  • the two rotor shafts 100 and 200 are mounted so that an axial displacement of both rotor shafts is possible.
  • the coupling 300 is designed so that the traction even at a defined displacement of the two rotor shafts or
  • FIG. 2 schematically shows a first concrete embodiment of the gas turbine rotor according to the invention.
  • the rotor shaft 200 of the turbine 20 is here, as far as extended in the direction of the compressor 10, that the extended end 210 of the
  • Compressor rotor shaft 100 completely overlapped. About here only indicated bearing R is this elongated turbine rotor shaft 200 radially mounted in a known manner. There is also a
  • Thrust bearing T-HSO for axial displacement of the
  • Turbine rotor shaft 200 for the purpose of hydraulic
  • Compressor rotor shaft 100 is shown in the here
  • Embodiment designed as a hollow shaft which also has a thrust bearing V-HSO for axial displacement of the
  • Compressor rotor shaft 100 for the purpose of hydraulic
  • Gap optimization in the compressor 10 has. Characterized in that the turbine rotor shaft 200 is extended beyond the compressor rotor shaft 100 out, the coupling device 300 over a large area over the circumference of
  • Turbine rotor shaft extension 210 are formed.
  • the turbine rotor shaft extension 210 thus forms here
  • the two thrust bearings T-HSO and V-HSO are arranged at the cold, inflow end of the compressor 10. With the help of the two thrust bearings T-HSO, V-HSO, it is possible to use the two rotor shafts 100, 200 independently of each other
  • the coupling device can be designed, for example, as a splined connection 310.
  • a spline of the spline connection 310 extends on an inner surface of the hollow shaft
  • Compressor 10 is indicated as a convergent flow channel and the turbine 20 as a divergent flow channel in which the arranged on the rotor shafts blades are located.
  • Clutch device is divided into two areas 321 and 322 on both sides of the compressor rotor shaft 100. The teeth and thus the non-positive coupling
  • Compressor rotor shaft can be extended in a suitable manner and engage in a trained as a hollow shaft turbine rotor shaft.
  • the coupling devices of the two embodiments shown could be combined in order to achieve an even better torque transmission. It is always essential that the gas turbine rotor according to the invention is designed so that in a hydraulic Spaltoptimierung the efficiency losses in the compressor can not be increased and by a separate shifting of the
  • Compressor 10 possibly even can be improved. So could by such a separate gap optimization on the part of the compressor beyond the normal state, a
  • Part-load operation can be used.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Bearings For Parts Moving Linearly (AREA)

Abstract

The invention relates to a gas turbine rotor for a gas turbine comprising a compressor rotor shaft (100), a turbine rotor shaft (200) and a coupling device (310) frictionally connecting the two rotor shafts, wherein the coupling device (310) is designed in such a way that the friction connection also exists when the two rotor shafts (100, 200) are displaced relative to one another. In this case, the turbine rotor shaft (200) is lengthened at the end facing the compressor rotor shaft (100) in such a way that said turbine rotor shaft (200) overlaps with the compressor rotor shaft (100) in the axial direction (A) and the coupling device (300) connects this lengthened end (210) of the turbine rotor shaft (200) to the compressor rotor shaft (100) in the radial direction (R).

Description

Beschreibung description
GASTURBINENROTOR MIT EINER AXIAL VERSCHIEBLICHEN TURBINENROTORWELLE Die Erfindung betrifft einen Gasturbinenrotor gemäß dem GAS TURBINE ROTOR WITH AN AXIAL SHIFT TURBINE ROTOR SHAFT The invention relates to a gas turbine rotor according to the
Oberbegriff des Anspruchs 1, eine entsprechende Gasturbine gemäß Anspruch 4 sowie demgemäße Rotorwellen für den  The preamble of claim 1, a corresponding gas turbine according to claim 4 and the corresponding rotor shafts for the
Verdichter und die Turbine einer solchen Gasturbine. Gasturbinen umfassen neben einer oder mehrerer Brennkammern im Wesentlichen einen Verdichter und eine nachgeschaltete Turbine, die über eine gemeinsame Rotorwelle in axialer Compressor and the turbine of such a gas turbine. Gas turbines comprise, in addition to one or more combustion chambers essentially a compressor and a downstream turbine, via a common rotor shaft in the axial
Richtung verbunden sind. Wie bei jeder Maschine zur Direction are connected. As with any machine for
Energieerzeugung ist ein möglichst hoher Wirkungsgrad, also das Verhältnis von erzeugter zur eingesetzten Energie eine wesentliche Größe. Energy production is the highest possible efficiency, ie the ratio of generated to the energy used a significant size.
Bei Gasturbinen kommt daher das in der EP 1 131 537 Bl beschriebene Verfahren der sogenannten hydraulischen In gas turbines, therefore, the method described in EP 1 131 537 Bl of the so-called hydraulic
Spaltoptimierung zum Einsatz, um den Gesamtwirkungsgrad der Gasturbine zu optimieren. Dabei wird der Gasturbinenrotor entgegen der Strömungsrichtung des Heißgases verschoben, um bei einem konisch gestalteten Heißgaskanal den Radialspalt zwischen den Laufschaufelspitzen und der Heißgaskanalwand zu minimieren. Der Zuganker, der den Turbinenrotor mit dem Gap optimization is used to optimize the overall efficiency of the gas turbine. In this case, the gas turbine rotor is moved counter to the flow direction of the hot gas to minimize the radial gap between the blade tips and the hot gas duct wall in a conically shaped hot gas duct. The tie rod connecting the turbine rotor with the
Verdichterrotor verbindet, ist dabei so gelagert, dass er in Axialrichtung verschoben werden kann. Dadurch können zur Optimierung die Turbinenspalte zugunsten des  Compressor rotor connects, it is mounted so that it can be moved in the axial direction. This can be used to optimize the turbine column in favor of
Turbinenwirkungsgrades verschoben werden. Gleichzeitig werden durch die damit einhergehende Verschiebung des  Turbine efficiency shifted. At the same time, the associated shift of the
Verdichterrotors aber auch gleichzeitig die radialen  Compressor rotor but also the same radial
Verdichterspalte zum Nachteil des Verdichterwirkungsgrades verstellt. Um diesen gegenläufigen Effekt zu vermeiden und damit den Gesamtwirkungsgrad weiter zu optimieren wurde bereits angedacht, den gemeinsamen Rotor an der Schnittstelle von Verdichter zur Turbine aufzutrennen und die beiden Compressor column adjusted to the detriment of the compressor efficiency. In order to avoid this opposite effect and thus to further optimize the overall efficiency, it was already considered to separate the common rotor at the interface of the compressor to the turbine and the two
Rotorteile über eine axiale Kupplung kraftschlüssig zu koppeln. Die Kupplung muss dabei aber so ausgeführt sein, dass der Kraftschluss auch noch bei einer axialen Verschiebung der Turbinenrotorwelle, relativ zur To couple rotor parts via an axial coupling frictionally. But the coupling has to be made that the frictional connection even with an axial displacement of the turbine rotor shaft, relative to
Verdichterrotorwelle, gegeben ist. Somit kann der Compressor rotor shaft, is given. Thus, the
Turbinenrotor verschoben und damit deren Wirkungsgrad Turbine rotor shifted and thus their efficiency
optimiert werden, ohne dass gleichzeitig der Verdichterrotor verschoben werden muss. Eine Erhöhung des be optimized without the same time the compressor rotor must be moved. An increase in the
Turbinenwirkungsgrads durch die hydraulische Spaltoptimierung bewirkt damit nicht mehr gleichzeitig eine Verschlechterung des Verdichterwirkungsgrads, was dem eigentlichen Ziel entgegenwirken würde.  Turbine efficiency through the hydraulic gap optimization thus no longer causes a simultaneous deterioration of the compressor efficiency, which would counteract the actual goal.
Aufgabe der Erfindung ist es, einen weiter verbesserten The object of the invention is to further improve
Gasturbinenrotor für eine Gasturbine bereitzustellen. To provide gas turbine rotor for a gas turbine.
Diese Aufgabe wird gelöst mit einem Gasturbinenrotor für eine Gasturbine, umfassend eine Verdichterrotorwelle und eine zur Verdichterrotorwelle axial verschiebliche Turbinenrotorwelle sowie eine die beiden Rotorwellen stets verbindende This object is achieved with a gas turbine rotor for a gas turbine, comprising a compressor rotor shaft and a compressor rotor shaft axially displaceable turbine rotor shaft and the two rotor shafts always connecting
Kupplungseinrichtung, wobei die Verdichterrotorwelle als Hohlwelle ausgeführt ist, durch die die Turbinenrotorwelle hindurchgeführt ist. Coupling device, wherein the compressor rotor shaft is designed as a hollow shaft through which the turbine rotor shaft is passed.
Durch die Verlängerung der Turbinenrotorwelle über die gesamte axiale Länge der Verdichterrotorwelle hinaus, ist eine besonders große Auflagefläche für die Due to the extension of the turbine rotor shaft over the entire axial length of the compressor rotor shaft addition, a particularly large bearing surface for the
Kupplungseinrichtung und damit die Momentenübertragung vom Turbinenrotor zum Verdichterrotor gegeben. Ist die  Coupling device and thus given the torque transfer from the turbine rotor to the compressor rotor. Is the
Verdichterrotorwelle als Hohlwelle ausgeführt, ist das verlängerte Ende der Turbinenrotorwelle durch diese Compressor rotor shaft designed as a hollow shaft, is the extended end of the turbine rotor shaft through this
hindurchgeführt, so dass beide Rotorwellen in der Gasturbine eine gemeinsame Achse aufweisen. Wird die passed through, so that both rotor shafts in the gas turbine have a common axis. Will the
Kupplungseinrichtung in zwei Bereiche, die sich an den beiden Enden der Verdichterrotorwelle befinden, aufgeteilt, besteht eine besonders robuste Kupplungseinrichtung.  Split coupling device in two areas, which are located at the two ends of the compressor rotor shaft, there is a particularly robust coupling device.
Werden in der Gasturbine zwei Lager, eines zur axialen Are in the gas turbine two bearings, one for axial
Positionierung der Verdichterrotorwelle und eines zur axialen Positionierung der Turbinenrotorwelle vorgesehen, können sowohl Verdichterrotor als auch Turbinenrotor in Bezug auf das Gasturbinengehäuse unabhängig voneinander verschoben werden. Die Spaltoptimierung kann somit für beide Teile - Turbine und Verdichter - getrennt voneinander erfolgen, so dass ein optimaler Gesamtwirkungsgrad der Gasturbine erreicht werden kann. Wirkungsgradverluste im Verdichter, die bei bekannten starren Kopplungen der beiden Wellen aufgrund einer axialen Verschiebung zugunsten des Turbinenwirkungsgrads entstehen, können so vermieden werden. Durch die Kombination der erfindungsgemäßen Ausbildung der beiden Rotorwellen und der Kupplungseinrichtung mit den beiden Lagern zur axialen Verschiebung kann somit eine Spaltoptimierung im Verdichter als auch in der Turbine unabhängig voneinander erfolgen, ohne dass die Funktionsweise des Gasturbinenrotors eingeschränkt wird. Durch eine solche individuelle Einstellung lässt sich die Gasturbine auch in einem erweiterten Betriebsbereich, wie beispielsweise Teillast oder Heißstart, betreiben. So kann es insbesondere beim Heißstart notwendig sein, die Spalte sogar zu vergrößern, um ein Anstreifen der Verdichterschaufeln am Gehäuse in diesem kritischen Zustand zu vermeiden. Positioning of the compressor rotor shaft and provided for axial positioning of the turbine rotor shaft, can both the compressor rotor and the turbine rotor are displaced independently of each other with respect to the gas turbine casing. The gap optimization can thus be carried out separately for both parts - turbine and compressor - so that an optimal overall efficiency of the gas turbine can be achieved. Efficiency losses in the compressor, which arise in known rigid couplings of the two shafts due to an axial displacement in favor of the turbine efficiency, can be avoided. By combining the inventive design of the two rotor shafts and the coupling device with the two bearings for axial displacement thus a gap optimization in the compressor and in the turbine can be done independently, without the operation of the gas turbine rotor is limited. By such an individual adjustment, the gas turbine can also operate in an extended operating range, such as part load or hot start. Thus, it may be necessary, in particular during the hot start, to even increase the gap in order to prevent the compressor blades from rubbing against the housing in this critical state.
Die Erfindung soll nun anhand der nachfolgenden Figuren beispielhaft erläutert werden. Es zeigen: The invention will now be explained by way of example with reference to the following figures. Show it:
FIG 1 schematisch eine bekannter Gasturbinenrotor einer 1 shows schematically a known gas turbine rotor a
Gasturbine,  Gas turbine,
FIG 2 schematisch eine erste erfindungsgemäße Ausbildung der Kupplungseinrichtung,  2 schematically shows a first embodiment of the coupling device according to the invention,
FIG 3 ein Schnitt durch das in FIG 2 gezeigte 3 shows a section through that shown in FIG
Ausführungsbeispiel .  Embodiment.
FIG 4 schematisch ein zweites Ausführungsbeispiel. 4 shows schematically a second embodiment.
Der in FIG 1 schematisch dargestellte bekannte The schematically illustrated in Figure 1 known
Gasturbinenrotor für eine Gasturbine. Die Gasturbine umfasst neben einer Verbrennungseinrichtung 1 zur Erzeugung von Gas turbine rotor for a gas turbine. The gas turbine comprises in addition to a combustion device 1 for generating
Heißgas einen Verdichter 10 mit einer Verdichterrotorwelle 100, eine Turbine 20 mit einer Turbinenrotorwelle 200 und einer kraftschlüssigen Kupplungseinrichtung 300 zwischen Verdichter- und Turbinenrotorwelle . Über entsprechende Hot gas a compressor 10 with a compressor rotor shaft 100, a turbine 20 with a turbine rotor shaft 200 and a positive coupling device 300 between Compressor and turbine rotor shaft. About appropriate
Auflager (schematisch angedeutet) sind die beiden Rotorwellen 100 und 200 so gelagert, dass eine axiale Verschiebung beider Rotorwellen möglich ist. Die Kupplung 300 ist dabei so ausgebildet, dass der Kraftschluss auch noch bei einer definierten Verschiebung der beiden Rotorwellen zu- bzw. Support (indicated schematically), the two rotor shafts 100 and 200 are mounted so that an axial displacement of both rotor shafts is possible. The coupling 300 is designed so that the traction even at a defined displacement of the two rotor shafts or
gegeneinander stets gegeben ist. is always given to each other.
FIG 2 zeigt schematisch eine erste konkrete Aus führungs form des erfindungsgemäßen Gasturbinenrotors. Die Rotorwelle 200 der Turbine 20 ist hier, soweit in Richtung des Verdichters 10 verlängert, dass das verlängerte Ende 210 die 2 schematically shows a first concrete embodiment of the gas turbine rotor according to the invention. The rotor shaft 200 of the turbine 20 is here, as far as extended in the direction of the compressor 10, that the extended end 210 of the
Verdichterrotorwelle 100 vollständig überlappt. Über hier nur angedeutete Lager R ist diese verlängerte Turbinenrotorwelle 200 in bekannter Weise radial gelagert. Zudem ist ein Compressor rotor shaft 100 completely overlapped. About here only indicated bearing R is this elongated turbine rotor shaft 200 radially mounted in a known manner. There is also a
Axiallager T-HSO zur axialen Verschiebung der Thrust bearing T-HSO for axial displacement of the
Turbinenrotorwelle 200 zum Zwecke der hydraulischen Turbine rotor shaft 200 for the purpose of hydraulic
Spaltoptimierung in der Turbine 20 vorgesehen. Die Gap optimization provided in the turbine 20. The
Verdichterrotorwelle 100 ist in dem hier dargestellten Compressor rotor shaft 100 is shown in the here
Ausführungsbeispiel als Hohlwelle ausgeführt, die zudem ein Axiallager V-HSO für eine axiale Verschiebung des Embodiment designed as a hollow shaft, which also has a thrust bearing V-HSO for axial displacement of the
Verdichterrotorwelle 100 zum Zwecke der hydraulischen Compressor rotor shaft 100 for the purpose of hydraulic
Spaltoptimierung im Verdichter 10 aufweist. Dadurch, dass die Turbinenrotorwelle 200 über die Verdichterrotorwelle 100 hinaus verlängert ist, kann die Kupplungseinrichtung 300 großflächig über den Umfang der Gap optimization in the compressor 10 has. Characterized in that the turbine rotor shaft 200 is extended beyond the compressor rotor shaft 100 out, the coupling device 300 over a large area over the circumference of
Turbinenrotorwellenverlängerung 210 ausgebildet werden. Die Turbinenrotorwellenverlängerung 210 bildet hier somit  Turbine rotor shaft extension 210 are formed. The turbine rotor shaft extension 210 thus forms here
zugleich das Radiallager für den Verdichter. at the same time the radial bearing for the compressor.
Die beiden Axiallager T-HSO und V-HSO sind dabei am kalten, einströmseitigen Ende des Verdichters 10 angeordnet. Mit Hilfe der beiden Axiallager T-HSO, V-HSO ist es möglich, die beiden Rotorwellen 100, 200 unabhängig voneinander zu The two thrust bearings T-HSO and V-HSO are arranged at the cold, inflow end of the compressor 10. With the help of the two thrust bearings T-HSO, V-HSO, it is possible to use the two rotor shafts 100, 200 independently of each other
positionieren und unabhängig voneinander zu verschieben. Wie anhand des in FIG 3 dargestellten Schnitts durch den Gasturbinenrotor zu sehen ist, kann die Kupplungseinrichtung beispielsweise als Keilwellenverbindung 310 ausgebildet sein. Ein Keilwellenkranz der Keilwellenverbindung 310 erstreckt sich dabei auf einer Innenfläche der als Hohlwelle position and move independently. As can be seen by means of the section through the gas turbine rotor shown in FIG. 3, the coupling device can be designed, for example, as a splined connection 310. A spline of the spline connection 310 extends on an inner surface of the hollow shaft
ausgebildeten Verdichterrotorwelle 100 und der zweite, mit dem ersten Keilwellenkranz korrespondierende, Keilwellenkranz erstreckt sich auf der Außenfläche des verlängerten Endes 210 der Turbinenrotorwelle 200. Beide Keilwellenkränze greifen dabei so ineinander, dass die kraftschlüssige Kupplung der Verdichterrotorwelle 100 mit der Turbinenrotorwelle 200 gewährleistet ist. Zum besseren Verständnis der Anordnung innerhalb der Gasturbine ist in FIG 2 und FIG 4 der formed compressor rotor shaft 100 and the second, corresponding to the first spline ring, spline ring extends on the outer surface of the elongated end 210 of the turbine rotor shaft 200. Both splines engage each other so that the frictional coupling of the compressor rotor shaft 100 is ensured with the turbine rotor shaft 200. For a better understanding of the arrangement within the gas turbine 2 is shown in FIG
Verdichter 10 als konvergente Strömungskanal und die Turbine 20 als divergente Strömungskanal angedeutet, in denen die an den Rotorwellen angeordneten Laufschaufeln angesiedelt sind. Compressor 10 is indicated as a convergent flow channel and the turbine 20 as a divergent flow channel in which the arranged on the rotor shafts blades are located.
FIG 4 zeigt eine alternative Ausführung bei der die 4 shows an alternative embodiment in which the
Kupplungseinrichtung in zwei Bereiche 321 und 322 an den beiden Seiten der Verdichterrotorwelle 100 aufgeteilt ist. Die Verzahnung und damit die kraftschlüssige Kupplung Clutch device is divided into two areas 321 and 322 on both sides of the compressor rotor shaft 100. The teeth and thus the non-positive coupling
zwischen Verdichter- und Turbinenrotorwelle 100,200 kann dabei auch so wie in FIG 3 gezeigt, ausgebildet sein. Im Übrigen weist sie die gleichen Merkmale wie die Ausführung aus FIG 2 auf. between the compressor and turbine rotor shaft 100, 200 may also be formed as shown in FIG. Moreover, it has the same features as the embodiment of FIG.
Die vorliegende Erfindung ist nicht beschränkt auf die zuvor beschriebenen Ausführungen. Vielmehr sind auch Kombinationen, Abwandlungen bzw. Ergänzungen einzelner Merkmale denkbar, die zu weiteren möglichen Aus führungs formen der erfinderischen Idee führen können. So könnte beispielsweise auch die The present invention is not limited to the previously described embodiments. Rather, combinations, modifications or additions of individual features are conceivable that can lead to further possible imple mentation forms of the inventive idea. For example, the
Verdichterrotorwelle in geeigneter Weise verlängert werden und in eine als Hohlwelle ausgebildete Turbinenrotorwelle eingreifen. Zudem könnten die Kupplungseinrichtungen der beiden gezeigten Ausführungen kombiniert werden, um eine noch bessere Momentenübertragung zu erreichen. Wesentlich dabei ist immer, dass der erfindungsgemäße Gasturbinenrotor so ausgebildet ist, dass bei einer hydraulischen Spaltoptimierung die Wirkungsgradverluste im Verdichter nicht erhöht werden und durch ein separates Verschieben des Compressor rotor shaft can be extended in a suitable manner and engage in a trained as a hollow shaft turbine rotor shaft. In addition, the coupling devices of the two embodiments shown could be combined in order to achieve an even better torque transmission. It is always essential that the gas turbine rotor according to the invention is designed so that in a hydraulic Spaltoptimierung the efficiency losses in the compressor can not be increased and by a separate shifting of the
Verdichters 10, ggf. sogar verbessert werden können. So könnte durch solch eine separate Spaltoptimierung auf Seiten des Verdichters über den Normalzustand hinaus, ein Compressor 10, possibly even can be improved. So could by such a separate gap optimization on the part of the compressor beyond the normal state, a
zusätzlicher Wirkungsgradgewinn und ein erweiterter additional efficiency gain and an extended
Betriebsbereich der gesamten Gasturbine, erreicht werden. Durch die getrennte Verschiebung von Verdichter und Turbine, relativ zum Gehäuse der Gasturbine und die damit erzielte getrennte Spaltoptimierung, kann die Gasturbine an den jeweiligen Strömungszustand angepasst und somit auch im Operating range of the entire gas turbine can be achieved. Due to the separate displacement of compressor and turbine, relative to the housing of the gas turbine and thus achieved separate gap optimization, the gas turbine can be adapted to the respective flow state and thus in the
Teillastbetrieb eingesetzt werden. Part-load operation can be used.

Claims

Patentansprüche claims
1. Gasturbinenrotor für eine Gasturbine, 1. gas turbine rotor for a gas turbine,
umfassend eine Verdichterrotorwelle (100) und eine zur comprising a compressor rotor shaft (100) and a to the
Verdichterrotorwelle (100) axial verschiebliche Compressor rotor shaft (100) axially displaceable
Turbinenrotorwelle (200) sowie eine die beiden Rotorwellen (100,200) stets verbindende Kupplungseinrichtung (300), d a d u r c h g e k e n n z e i c h n e t , d a s s  Turbine rotor shaft (200) and a clutch device (300), the two rotor shafts (100,200) always connecting, d a d u c c h e c e n e c e n e, d a s s
die Verdichterrotorwelle (100) als Hohlwelle ausgeführt ist, durch die die Turbinenrotorwelle (200) hindurchgeführt ist. the compressor rotor shaft (100) is designed as a hollow shaft, through which the turbine rotor shaft (200) is passed.
2. Gasturbinenrotor nach Anspruch 1, 2. Gas turbine rotor according to claim 1,
d a d u r c h g e k e n n z e i c h n e t , d a s s d a d u r c h e s e n c i n e s, d a s s
die Kupplungseinrichtung eine Keilwellenverbindung (310) ist, dessen einer Keilwellenkranz sich auf einer Innenfläche der als Hohlwelle ausgebildeten Verdichterrotorwelle in the coupling device is a splined connection (310), one of whose splines is formed on an inner surface of the compressor rotor shaft formed as a hollow shaft
Umfangsrichtung erstreckt und dessen zweiter mit dem ersten Keilwellenkranz korrespondierender Keilwellenkranz sich auf der Außenfläche des verlängerten Endes (210) der Circumferentially extending and the second corresponding with the first spline ring spline on the outer surface of the extended end (210) of the
Turbinenrotorwelle (200) in Umfangsrichtung erstreckt. Turbine rotor shaft (200) extends in the circumferential direction.
3. Gasturbinenrotor nach einem der Ansprüche 1 bis 2, 3. Gas turbine rotor according to one of claims 1 to 2,
d a d u r c h g e k e n n z e i c h n e t , d a s s d a d u r c h e s e n c i n e s, d a s s
die Kupplungseinrichtung zwei Bereiche (321,322) zur the coupling device two areas (321.322) for
kraftschlüssigen Verbindung von Verdichterrotorwelle (100) und Turbinenrotorwelle (200) umfasst, wobei der erste Bereich (321) sich an einem Ende der Verdichterrotorwelle (100) und der zweite Bereich (322) sich am zweiten Ende der non-positive connection of compressor rotor shaft (100) and turbine rotor shaft (200), wherein the first region (321) at one end of the compressor rotor shaft (100) and the second region (322) at the second end of the
Verdichterrotorwelle (100) befindet. Compressor rotor shaft (100) is located.
4. Gasturbine mit einem Verdichter (10), einer Turbine (20) und einem Gasturbinenrotor nach einem der Ansprüche 1 bis 3. 4. Gas turbine with a compressor (10), a turbine (20) and a gas turbine rotor according to one of claims 1 to 3.
5. Gasturbine nach Anspruch 4, 5. Gas turbine according to claim 4,
d a d u r c h g e k e n n z e i c h n e t , d a s s d a d u r c h e s e n c i n e s, d a s s
ein erstes Axiallager (V-HSO) für eine axiale Positionierung der Verdichterrotorwelle (100) und ein zweites Axiallager (T- HSO) für die axiale Positionierung der Turbinenrotorwelle (200) vorgesehen ist. a first thrust bearing (V-HSO) for axial positioning of the compressor rotor shaft (100) and a second thrust bearing (T-HSO) for axial positioning of the turbine rotor shaft (200) is provided.
6. Gasturbine nach Anspruch 5, 6. Gas turbine according to claim 5,
d a d u r c h g e k e n n z e i c h n e t , d a s s das erster Axiallager (V-HSO) und das zweite Axiallager (T- HSO) am einströmseitigen Ende des Verdichters (10) angeordnet sind . That is, the first thrust bearing (V-HSO) and the second thrust bearing (T-HSO) are disposed at the upstream end of the compressor (10).
7. Verdichterrotorwelle (100) für eine Gasturbine, die als Hohlwelle so ausgebildet ist, dass sie als Teil einer 7. compressor rotor shaft (100) for a gas turbine, which is designed as a hollow shaft, that they as part of a
Kupplungseinrichtung (310,321,322) in einem Gasturbinenrotor nach Anspruch 1 bis 3 Verwendung findet.  Coupling device (310,321,322) in a gas turbine rotor according to claim 1 to 3 is used.
8. Turbinenrotorwelle (200) für eine Gasturbine, die an einem Ende so verlängert ist, dass sie als Teil einer 8. Turbine rotor shaft (200) for a gas turbine, which is extended at one end so that they are part of a
Kupplungseinrichtung (310,321,322) in einem Gasturbinenrotor nach Anspruch 1 bis 3 Verwendung findet.  Coupling device (310,321,322) in a gas turbine rotor according to claim 1 to 3 is used.
EP11740864.1A 2010-08-05 2011-07-20 Gas turbine rotor comprising an axially displaceable turbine rotor shaft Withdrawn EP2601383A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11740864.1A EP2601383A1 (en) 2010-08-05 2011-07-20 Gas turbine rotor comprising an axially displaceable turbine rotor shaft

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP10171951A EP2415966A1 (en) 2010-08-05 2010-08-05 Power train for a gas turbine
PCT/EP2011/062410 WO2012016830A1 (en) 2010-08-05 2011-07-20 Gas turbine rotor comprising an axially displaceable turbine rotor shaft
EP11740864.1A EP2601383A1 (en) 2010-08-05 2011-07-20 Gas turbine rotor comprising an axially displaceable turbine rotor shaft

Publications (1)

Publication Number Publication Date
EP2601383A1 true EP2601383A1 (en) 2013-06-12

Family

ID=43431957

Family Applications (2)

Application Number Title Priority Date Filing Date
EP10171951A Withdrawn EP2415966A1 (en) 2010-08-05 2010-08-05 Power train for a gas turbine
EP11740864.1A Withdrawn EP2601383A1 (en) 2010-08-05 2011-07-20 Gas turbine rotor comprising an axially displaceable turbine rotor shaft

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP10171951A Withdrawn EP2415966A1 (en) 2010-08-05 2010-08-05 Power train for a gas turbine

Country Status (6)

Country Link
US (1) US9243499B2 (en)
EP (2) EP2415966A1 (en)
JP (1) JP5512893B2 (en)
CN (1) CN103097664B (en)
RU (1) RU2013109401A (en)
WO (1) WO2012016830A1 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9109608B2 (en) * 2011-12-15 2015-08-18 Siemens Energy, Inc. Compressor airfoil tip clearance optimization system
US11143051B2 (en) 2013-10-02 2021-10-12 Raytheon Technologies Corporation Translating compressor and turbine rotors for clearance control
DE102014203318A1 (en) * 2014-02-25 2015-08-27 Siemens Aktiengesellschaft Method for operating a gas turbine with active hydraulic gap adjustment
RU2572744C1 (en) * 2014-10-14 2016-01-20 Открытое акционерное общество "Авиадвигатель" Gas turbine bypass engine
CN106224016B (en) * 2016-08-31 2018-01-12 中国南方航空工业(集团)有限公司 Turbine rotor, engine and the method for improving engine rotor centering reliability
CN111828117B (en) * 2020-07-09 2022-09-23 北京京桥热电有限责任公司 Heat supply control method, device and system for gas-steam combined cycle unit
CN113700732B (en) * 2021-08-25 2023-09-05 中国科学院工程热物理研究所 Gas turbine rotor supporting system based on sliding bearing and thrust disc
DE102022111499B3 (en) 2022-05-09 2023-06-29 Sascha Larch Launch vehicle propulsion stage, launch vehicle and method of operating a launch vehicle

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB658778A (en) * 1948-10-28 1951-10-10 Rolls Royce Improvements relating to rotary fluid machine assemblies
CA1126168A (en) * 1980-04-30 1982-06-22 William D. Long Ceramic radial turbine wheel
US4611464A (en) * 1984-05-02 1986-09-16 United Technologies Corporation Rotor assembly for a gas turbine engine and method of disassembly
US4639194A (en) * 1984-05-02 1987-01-27 General Motors Corporation Hybrid gas turbine rotor
JPS6432135U (en) * 1987-08-20 1989-02-28
JP2863199B2 (en) * 1989-06-07 1999-03-03 ヤンマーディーゼル株式会社 Gas turbine engine
US5282358A (en) * 1991-05-28 1994-02-01 General Electric Company Gas turbine engine dual inner central drive shaft
US5580183A (en) * 1994-04-29 1996-12-03 United Technologies Corporation Gas turbine engine spline arrangement
US5533825A (en) * 1994-11-14 1996-07-09 General Electric Company Parabolically helical spline shaft coupling
JP3032135U (en) 1996-06-07 1996-12-17 純郎 河村 Hospital / nursing beds
DE59910772D1 (en) 1998-11-11 2004-11-11 Siemens Ag METHOD FOR OPERATING A FLOWING MACHINE
JP2002201901A (en) * 2000-12-28 2002-07-19 Ishikawajima Harima Heavy Ind Co Ltd Spline tightening structure
GB2383380B (en) * 2001-12-19 2005-05-25 Rolls Royce Plc Rotor assemblies for gas turbine engines
DE102005048982A1 (en) * 2005-10-13 2007-04-19 Mtu Aero Engines Gmbh Apparatus and method for axially displacing a turbine rotor
FR2905414B1 (en) * 2006-08-29 2013-03-01 Snecma DEVICE FOR DRIVING THE ROTOR OF AN AUXILIARY EQUIPMENT OF A TURBOMOTEUR.
US7748925B2 (en) * 2006-09-15 2010-07-06 Aichi Machine Industry Co., Ltd. Rotating member fixing structure
FR2909146B1 (en) * 2006-11-28 2009-06-05 Snecma Sa DEVICE FOR CONNECTING TWO ROTARY TREES, PARTICULARLY IN A TURBOMACHINE.
US7716914B2 (en) * 2006-12-21 2010-05-18 General Electric Company Turbofan engine assembly and method of assembling same
FR2917783B1 (en) * 2007-06-25 2013-04-12 Snecma ENGINE SHAFT CONNECTION SYSTEM WITH SELF-EXTRACTOR NUT
FR2918726A1 (en) 2007-07-11 2009-01-16 Snecma Sa Cylindrical low-pressure turbine and compressor shafts connector for aeronautical turbomachine, has shafts with sets of teeth, where each tooth of one set has constant thickness, and teeth flanks forming clearance before applying torque

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012016830A1 *

Also Published As

Publication number Publication date
US9243499B2 (en) 2016-01-26
US20130129478A1 (en) 2013-05-23
JP5512893B2 (en) 2014-06-04
WO2012016830A1 (en) 2012-02-09
EP2415966A1 (en) 2012-02-08
CN103097664B (en) 2015-11-25
CN103097664A (en) 2013-05-08
JP2013534287A (en) 2013-09-02
RU2013109401A (en) 2014-09-10

Similar Documents

Publication Publication Date Title
WO2012016830A1 (en) Gas turbine rotor comprising an axially displaceable turbine rotor shaft
DE602004000204T2 (en) Device for fixing an engine shaft on a bearing
EP1945931B1 (en) Device for axially displacing a turbine rotor
EP1898054B1 (en) Gas turbine
DE10210866C5 (en) Guide vane mounting in a flow channel of an aircraft gas turbine
DE102012107419A1 (en) Angle change mechanism for open rotor structure
EP3524781B1 (en) Connecting device for an adjustable vane of a gas turbine
EP2132414B1 (en) Shiplap arrangement
DE112006000603T5 (en) Guide wheel and blade for a turbomachinery
CH700973B1 (en) Turbine housing with the inner and outer housing assembly mounted on flexural nodal points.
DE102009004991A1 (en) Wind turbine
EP1076765B1 (en) Bloom mixer for a turbofan engine
WO2016165950A1 (en) Guide vane adjusting device and turbomachine
DE102014100087A1 (en) Interior structure of a turbine blade
EP2344723B1 (en) Gas turbine with seal plates on the turbine disk
EP3273001A2 (en) Methods of manufacturing a tandem guide vane segment
EP2140111B1 (en) Turbomachine
CH694257A5 (en) Steam turbine.
EP2652350B1 (en) Method for producing a coupling segment of a flexible coupling
EP1653049A1 (en) Vane ring assembly for gas turbines and method to modify the same
EP2824288A1 (en) Gas turbine engine
EP3505295B1 (en) Arrangement with a press with two parts and at least one gripping element
EP3227578B1 (en) Joint shaft, in particular universal joint shaft
WO2019011464A1 (en) Connection device for a turbocharger, and turbocharger
EP3379037B1 (en) Seal on the inner ring of a guide blade assembly

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20130124

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20160708

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20161119