EP2011963B1 - Method for operating a gas turbine with axial thrust balance - Google Patents
Method for operating a gas turbine with axial thrust balance Download PDFInfo
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- EP2011963B1 EP2011963B1 EP08159584.5A EP08159584A EP2011963B1 EP 2011963 B1 EP2011963 B1 EP 2011963B1 EP 08159584 A EP08159584 A EP 08159584A EP 2011963 B1 EP2011963 B1 EP 2011963B1
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- 238000000034 method Methods 0.000 title claims description 24
- 238000001816 cooling Methods 0.000 claims description 15
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- 230000004323 axial length Effects 0.000 description 1
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- 238000012821 model calculation Methods 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000009420 retrofitting Methods 0.000 description 1
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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
- F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
- F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
Definitions
- the invention relates to a method for operating a gas turbine with axial thrust compensation and a gas turbine with apparatus for carrying out the method.
- the axial thrust of a gas turbine is the resulting force of aerodynamic forces and compressive forces, which exert an axial force on the rotor in the compressor and turbine, as well as all acting in the axial direction of the rotor pressure forces.
- the resulting thrust is absorbed by a thrust bearing.
- gas turbines are designed to have a minimum thrust at idle.
- the axial thrust increases proportionally to the load.
- a counterforce to the thrust balance can be applied against the increasing axial load with the load.
- the maximum thrust to be absorbed by the thrust bearing can be reduced. Accordingly, the size and the power loss of the thrust bearing can be reduced.
- the thrust of turbines and compressors as well as the compressive forces acting on the rotor in the axial direction are determined by operating parameters, in particular the position of compressor guide vanes and compressor discharge pressure as well as the design. He is determined by the selected geometries, in particular by the geometries of the blade channels and the degrees of reaction of the turbine stages.
- the operating parameters are of the desired Process and operating concept of the gas turbine dependent. The load-dependency of the thrust can not be changed once the design has been selected.
- the thrust load compensation device In the US5735666 a method is described in which, via a magnetically operated thrust load compensation device, the thrust loads, which load on a thrust bearing regulated.
- the thrust load compensation device generates a compensation thrust as soon as a sensor detects a rotational speed of the thrust bearing which is below a threshold value.
- a pressure compensating piston is in the US4653267 shown.
- the pressure balance piston in the middle part, that is the between compressor and turbine geiegenen part, running a two-shaft system.
- the axial force of the piston is reduced in normal operation by a second chamber pressurized with leakage air. Air can be discharged from this second chamber via a valve and thus the pressure level in this chamber can be reduced. By changing the pressure level in the second chamber, the resulting axial force of the pressure compensating piston is regulated.
- the advantage of this arrangement is that the air discharged from the second chamber for control can continue to be used for turbine cooling.
- Additional structural parts are needed to generate the pressure compensation piston.
- the object of the present invention is to provide a controllable thrust balance in gas turbines without the use of additional structural components, which at high load and in particular at the design point has no additional cooling air consumption for acting on pressure equalizing piston or the like result.
- the controllable thrust balance in gas turbines to be retrofitted, the one accordingly EP0447886 have executed middle part.
- the invention relates to a method according to claim 1.
- a gas turbine is designed with respect to aerodynamic forces and compressive forces exerting an axial force on the rotor so that it has a negative thrust at idle and deep part load.
- a negative thrust is a thrust that points from the turbine towards the compressor. Further, it is designed so that it has a positive thrust at high gas turbine load and especially at full load.
- an additional thrust in the main thrust direction that is to say a positive thrust in the direction of the compressor to the turbine, is applied at idle and part load.
- the resulting maximum thrust force to be absorbed by the at least one thrust bearing is consequently smaller than in a conventionally designed gas turbine without thrust balance.
- a thrust reversal in loading or unloading of the gas turbine is prevented by the additional thrust.
- the load range in which an additional thrust is applied is, for example, in the range from idle to about 60% full load.
- the part load range in which an additional boost is applied for example, to about 90% full load range.
- the partial load range in which additional thrust is applied for example, only up to about 10% full load range.
- the additional thrust is generated by a method for regulating the pressure on the end face or on a partial surface of the end face of the turbine rotor.
- a substantially annular space between the drum cover and the first turbine disk which is closed by a rotor seal a turbine blade root seal, divided by a seal in an outer and an inner annulus.
- the turbine rotor is supplied with high-pressure cooling air from the outer annular space, which is fed into this annular space with the highest possible tangential velocity.
- the static pressure in the outer annulus is due to the strong acceleration to the highest possible tangential velocity significantly below the compressor end pressure.
- a swirl nozzle is used, for example.
- the ratio of the pressure drop across the rotor seal and turbine disk seal is inversely proportional to the ratio of the equivalent areas of both seals.
- the rotor seal has a significantly smaller equivalent area than the turbine disk seal.
- the pressure drop across the rotor seal is correspondingly much larger than that over the turbine disk seal. The pressure in the inner annular space is therefore determined when the control valve is closed essentially by the pressure in the outer annular space.
- the inner annular space is acted upon by at least one line from Kompressorplenum or other suitable extraction point with compressed air.
- at least one control valve is provided to control the pressurization.
- pressurize for example, externally supplied compressed air or steam can be used or an externally supplied medium can be used in combination with compressor air.
- the advantage of this method is that in the high load range no additional pressurization is required and thus no compressed air is consumed under performance andumblesgradeinbusse. Even if the pressurization is active at partial load, the air escaping via the seal between the inner and outer annular space is usefully added to the rotor cooling air.
- the at least one control valve may be open at low load and closed when a discrete limit is exceeded. Conversely, the at least one control valve is opened again when it falls below the discrete limit value.
- a hysteresis can be provided.
- Another control option is, for example, a closure of the control valve proportional to the load.
- the position of the control valve is not specified as a function of the load, but the pressure ratio between the inner annular space and compressor discharge pressure is predetermined and this ratio is regulated via the control valve.
- the target value is not necessarily constant, but is, for example, a function of the load.
- the function can, for example, be determined in such a way that a constant axial thrust is achieved over the widest possible operating range.
- the position of the control valve or the target value of the pressure conditions in the inner annular space can for example also be provided as a function of the Ver Whyreintrittsleitschaufelwinkel or the relative load. Regulations depending on combinations of parameters or other relevant parameters are also possible.
- a special case is the application in connection with the upgrade of a gas turbine.
- a change in one of the main components turbine or compressor can lead to a reduction of the axial thrust. This will be the case, for example, when the compressor thrust increases due to an upgrade compressor with virtually unchanged intake mass flow and thus virtually unchanged compressor discharge pressure and turbine thrust.
- the increase in compressor thrust can cause a thrust reverser after the upgrade.
- the method according to the invention can be used and a controlled additional thrust can be applied.
- One embodiment is a gas turbine with a seal that divides the substantially annular space between the drum cover and the first turbine disk into an outer and an inner annular space. It has at least one line from the compressor plenum to the drum cover, at least one control valve in this line and at least one inlet into the inner annulus.
- a labyrinth seal is an example of a suitable seal.
- the introduction into the inner annulus of the drum cover is a generally annular plenum connected to the inner annulus through a plurality of orifices.
- At least one pressure gauge is also provided in the inner annulus and in the compressor plenum.
- the at least one supply line for pressurizing the inner plenum is not connected to the Kompressplplenum, but another suitable extraction point for compressor air via at least one control valve.
- the invention is based on embodiments in the Fig. 1 to 4 shown schematically.
- a gas turbine with a device for carrying out the method according to the invention essentially has at least one compressor, at least one combustion chamber and at least one turbine, which drives the compressor and a generator via at least one shaft.
- Fig. 1 shows a section through the middle part of a gas turbine, that is, the area between the compressor and turbine and the final stage of the compressor and the first stage of the turbine.
- the compressor 1 compresses the air. Most of the air is introduced via the Kompressplplenum 2 in a combustion chamber 3 and mixed with fuel, which burns there. From there, the hot fuel gases flow under labor output through a turbine 4. Turbine 4 and compressor 1 are arranged on a common shaft 18, wherein the part of the shaft located between compressor 1 and turbine 4 is designed as a drum 6.
- the high-pressure part of the rotor cooling air is swirled after the last compressor blade discharged through an annular channel 7 between the rotor drum 6 and drum cover 5 and introduced via the rotor cooling air supply 12 and a swirl grille 13 in an annular space between the drum cover and a first turbine disk.
- This annulus is divided by a seal 9 in an inner annulus 10 and an outer annulus 11.
- the outer annular space is bounded, for example, by the rear side of a drum cover 5, an inner platform of a first turbine guide vane facing the rotor 18, a first turbine disk and the seal 9.
- the inner annular space is bounded, for example, by the rear side of a drum cover 5, a seal 9, a first turbine disk of a rotor seal 8 and the walls of a part of an annular channel 7 lying downstream of a rotor seal 8.
- the seal 9 can be performed, for example, as a labyrinth seal 21.
- a labyrinth seal 21 For receiving the labyrinth seal 21, for example, as in Fig. 2 shown, offset from each other, referred to as balconies projections on a drum cover 19 and a first turbine disk 20 are provided.
- the rotor cooling air supply 12 may be connected, for example via a swirl grille 13 with an outer annular space 11 that accelerates the rotor cooling air tangentially and thus lowers the static pressure in an outer annular space 11. From the one outer annular space 11, the rotor cooling air enters a first turbine disk.
- An annular space is divided by a seal 9 into an inner 10 and outer annular space 11 in front of a first turbine disk, ie the substantially annular space between the drum cover 5 and the first turbine disk, which is closed by a rotor seal 8, a turbine blade root seal 24. This division makes it possible to pressurize the inner annulus 10 via a pressure line 14 and a control valve 15 with compressed air from the Kompressplplenum 2.
- the introduction 16 of the compressed air into the inner annular space 10 can take place via holes through the drum cover or, as in Fig. 1 represented, via a plenum 17.
- the compressed air is fed via the at least one pressure line 14 into the plenum 17. From there it passes via the introduction 16, which is designed, for example, as a plurality of holes in the inner annular space 10th
- the inner annular space 10 is applied at partial load to increase the thrust by opening the control valve 15 via the pressure line 14 and the introduction 16 with pressure.
- This air passes together with the leakage air of the rotor seal 8 in the outer annular space 11.
- Fig. 3 the resulting axial thrust for control is shown as a function of the gas turbine load in regulation with a limit value and hysteresis.
- the control valve 15 is initially open at low load of the gas turbine. After exceeding a limit value ⁇ , the control valve is closed and remains closed in the upper load range (solid line). When reducing the load, the control valve 15 when falling below the load ⁇ is opened again (dashed line).
- dashed lines show the thrust profile with thrust reversal, which would result without additional thrust in the lower load range.
- Fig. 4 shows the idealized thrust curve (solid line) over gas turbine load when controlling the load-dependent pressure ratio between pressure in the inner annulus and compressor end pressure.
- the control valve 15 is initially open at low load of the gas turbine. From reaching a target thrust, for example, at the load ⁇ , the thrust is kept constant by changing the pressure in the inner annulus. Only when the control valve 15 is completely closed, which is the case, for example, at the load ⁇ , the thrust continues to increase to reach its maximum value at full load.
- the dependence of the pressure ratio of load can be determined by model calculations or from experiments and programmed in the gas turbine controller.
- dashed lines show the thrust curve with thrust reversal, which would result without additional thrust.
- seals (8 and / or 9) can be designed as a brush seal.
Description
Die Erfindung betrifft ein Verfahren zum Betrieb einer Gasturbine mit Axialschubausgleich sowie eine Gasturbine mit Vorrichtung zur Ausführung des Verfahrens.The invention relates to a method for operating a gas turbine with axial thrust compensation and a gas turbine with apparatus for carrying out the method.
Der Axialschub einer Gasturbine ist die resultierende Kraft aus aerodynamischen Kräften und Druckkräften, die in Kompressor und Turbine eine Axialkraft auf den Rotor ausüben, sowie aller in axialer Richtung auf den Rotor wirkenden Druckkräfte. Der resultierende Schub wird von einem Axiallager aufgenommen. Typischerweise werden Gasturbinen so ausgelegt, dass sie bei Leerlauf einen Minimalschub aufweisen. Der Axialschub steigt proportional zur Last. Um den Axialschub auszugleichen, kann gegen den mit der Last zunehmenden Axialschub eine Gegenkraft zum Schubausgleich aufgebracht werden. Dadurch kann der maximale, von dem Axiallager aufzunehmende Schub reduziert werden. Entsprechend kann die Baugrösse und die Verlustleistung des Axiallagers reduziert werden.The axial thrust of a gas turbine is the resulting force of aerodynamic forces and compressive forces, which exert an axial force on the rotor in the compressor and turbine, as well as all acting in the axial direction of the rotor pressure forces. The resulting thrust is absorbed by a thrust bearing. Typically, gas turbines are designed to have a minimum thrust at idle. The axial thrust increases proportionally to the load. To compensate for the axial thrust, a counterforce to the thrust balance can be applied against the increasing axial load with the load. As a result, the maximum thrust to be absorbed by the thrust bearing can be reduced. Accordingly, the size and the power loss of the thrust bearing can be reduced.
Der Schub von Turbinen und Kompressoren sowie die in axialer Richtung auf den Rotor wirkenden Druckkräfte werden von Betriebsparametern, insbesondere der Stellung von Verdichterleitschaufeln und Kompressoraustrittsdruck sowie durch das Design bestimmt. Dabei ist er von den gewählten Geometrien, insbesondere durch die Geometrien der Schaufelkanäle und den Reaktionsgraden der Turbinenstufen bestimmt. Die Betriebsparameter sind von dem gewünschten Prozess und Betriebskonzept der Gasturbine abhängig. Die Lastabhängigkeit des Schubes kann bei einmal gewähltem Design nicht mehr verändert werden.The thrust of turbines and compressors as well as the compressive forces acting on the rotor in the axial direction are determined by operating parameters, in particular the position of compressor guide vanes and compressor discharge pressure as well as the design. He is determined by the selected geometries, in particular by the geometries of the blade channels and the degrees of reaction of the turbine stages. The operating parameters are of the desired Process and operating concept of the gas turbine dependent. The load-dependency of the thrust can not be changed once the design has been selected.
Das Problem des Schubausgleiches bei Gasturbinen ist lange bekannt und eine grosse Zahl von Lösungsansätzen wurde in der Literatur vorgeschlagen. Insbesondere sind verschiedene Möglichkeiten den Axialschub über Druckausgleichszylinder zu kompensieren und damit die Last auf die Axiallager zu reduzieren bekannt. Zur Regelung des Schubausgleiches mittels einer Gegenkraft in einer Gasturbine sind ebenfalls verschiedene Verfahren entwickelt worden.The problem of thrust balance in gas turbines has long been known and a large number of approaches have been proposed in the literature. In particular, various ways to compensate for the axial thrust via pressure compensation cylinder and thus to reduce the load on the thrust bearings are known. To control the thrust balance by means of a counterforce in a gas turbine, various methods have also been developed.
In der
In der
In der
Eine andere Ausführung eines Druckausgleichskolbens ist in der
und insbesondere bei Ausführungen gemäss der
and in particular in embodiments according to
Ein anderer Ansatz zur Reduktion der Axialkräfte wird in der
Der vorliegenden Erfindung ist die Aufgabe gestellt, einen regelbaren Schubausgleich bei Gasturbinen ohne Verwendung zusätzlicher Strukturbauteile zu schaffen, der bei hoher Last und insbesondere im Auslegungspunkt keinen zusätzlichen Kühlluftverbrauch zur Beaufschlagung von Druckausgleichskolben oder ähnlichem zur Folge hat. Ausserdem soll der regelbare Schubausgleich in Gasturbinen nachrüstbar sein, die einen entsprechend
Die Erfindung betrifft ein Verfahren gemäß Anspruch 1.The invention relates to a method according to claim 1.
Zur Lösung der oben gegebenen Aufgabe wird eine Gasturbine in bezug auf aerodynamische Kräfte und Druckkräfte, die eine Axialkraft auf den Rotor ausüben, so ausgelegt, dass sie bei Leerlauf und tiefer Teillast einen negativen Schub hat. Ein negativer Schub ist ein Schub, der von der Turbine in Richtung Kompressor weist. Weiter wird sie so ausgelegt, dass sie bei hoher Gasturbinenlast und insbesondere bei Volllast einen positiven Schub aufweist. Um im gesamten Lastbereich der Gasturbine eine resultierende positive Kraft auf das mindestens eine Axiallager zu gewährleisten, wird bei Leerlauf und Teillast geregelt ein Zusatzschub in Hauptschubrichtung, das heisst ein positiver Schub in Richtung von Kompressor zur Turbine, aufgebracht.To achieve the above object, a gas turbine is designed with respect to aerodynamic forces and compressive forces exerting an axial force on the rotor so that it has a negative thrust at idle and deep part load. A negative thrust is a thrust that points from the turbine towards the compressor. Further, it is designed so that it has a positive thrust at high gas turbine load and especially at full load. In order to ensure a positive force on the at least one axial bearing in the entire load range of the gas turbine, an additional thrust in the main thrust direction, that is to say a positive thrust in the direction of the compressor to the turbine, is applied at idle and part load.
Die resultierende maximale Schubkraft, die von dem mindestens einen Axiallager aufzunehmen ist, ist in Konsequenz kleiner als bei einer herkömmlich ausgelegten Gasturbine ohne Schubausgleich. Ausserdem wird durch den Zusatzschub eine Schubumkehr bei Belasten oder Entlasten der Gasturbine verhindert. Der Lastbereich in dem ein Zusatzschub aufgebracht wird, liegt beispielsweise im Bereich von Leerlauf bis etwa 60% Volllast. Bei einer Gasturbine, die für Volllastbetrieb optimiert wird, kann der Teillastbereich, in dem ein Zusatzschub aufgebracht wird, beispielsweise bis etwa 90% Volllast reichen. Bei einer Nachrüstung kann der Teillastbereich, in dem Zusatzschub aufgebracht wird, beispielsweise nur bis etwa 10% Volllast reichen.The resulting maximum thrust force to be absorbed by the at least one thrust bearing is consequently smaller than in a conventionally designed gas turbine without thrust balance. In addition, a thrust reversal in loading or unloading of the gas turbine is prevented by the additional thrust. The load range in which an additional thrust is applied is, for example, in the range from idle to about 60% full load. In a gas turbine that is optimized for full load operation, the part load range in which an additional boost is applied, for example, to about 90% full load range. For retrofitting, the partial load range in which additional thrust is applied, for example, only up to about 10% full load range.
Der Zusatzschub wird durch ein Verfahren zur Regelung des Druckes an der Stirnseite oder an einer Teilfläche der Stirnseite des Turbinenrotors erzeugt.The additional thrust is generated by a method for regulating the pressure on the end face or on a partial surface of the end face of the turbine rotor.
Zu diesem Zweck wird ein im wesentlichen ringförmiger Raum zwischen Trommelabdeckung und erster Turbinenscheibe, der durch eine Rotordichtung eine Turbinenschaufelfussdichtung abgeschlossen ist, durch eine Dichtung in einen äusseren und einen inneren Ringraum geteilt. Beispielsweise wird von dem äusseren Ringraum der Turbinenrotor mit Hochdruckkühlluft versorgt, die in diesen Ringraum mit einer möglichst hohen Tangentialgeschwindigkeit eingespeist wird. Dabei liegt der statische Druck in dem äusseren Ringraum infolge der starken Beschleunigung auf die möglichst hohe Tangentialgeschwindigkeit deutlich unter Kompressorenddruck. Zur Beschleunigung der Kühlluft auf eine möglichst hohe Tangentialgeschwindigkeit wird beispielsweise eine Dralldüse verwendet. Es können aber auch beispielsweise gerichtete Bohrungen, zur Beschleunigung in Tangentialrichtung verwendet werden.For this purpose, a substantially annular space between the drum cover and the first turbine disk, which is closed by a rotor seal a turbine blade root seal, divided by a seal in an outer and an inner annulus. For example, the turbine rotor is supplied with high-pressure cooling air from the outer annular space, which is fed into this annular space with the highest possible tangential velocity. In this case, the static pressure in the outer annulus is due to the strong acceleration to the highest possible tangential velocity significantly below the compressor end pressure. To accelerate the cooling air to the highest possible tangential velocity, a swirl nozzle is used, for example. However, it is also possible, for example, to use directional bores for acceleration in the tangential direction.
Bei geschlossenem Regelventil, wenn keine zusätzliche Druckluft in den inneren Ringraum zugeführt wird, ist das Verhältnis des Druckabfalls über Rotordichtung und Turbinenscheibendichtung umgekehrt proportional zu dem Verhältnis der äquivalenten Flächen beider Dichtungen. Typischerweise weist die Rotordichtung eine deutlich kleinere äquivalente Fläche als die Turbinenscheibendichtung auf. Der Druckabfall über die Rotordichtung ist entsprechend viel grösser als der über die Turbinenscheibendichtung. Der Druck in dem inneren Ringraum ist daher bei geschlossenem Regelventil im wesentlichen durch den Druck im äusseren Ringraum bestimmt.With the control valve closed, if no additional compressed air is supplied to the inner annulus, the ratio of the pressure drop across the rotor seal and turbine disk seal is inversely proportional to the ratio of the equivalent areas of both seals. Typically, the rotor seal has a significantly smaller equivalent area than the turbine disk seal. The pressure drop across the rotor seal is correspondingly much larger than that over the turbine disk seal. The pressure in the inner annular space is therefore determined when the control valve is closed essentially by the pressure in the outer annular space.
Um einen Zusatzschub in Hauptschubrichtung zu erzeugen, wird der innere Ringraum über mindestens eine Leitung vom Kompressorplenum oder einer anderen geeigneten Entnahmestelle mit Druckluft beaufschlagt. Zur Regelung der Druckbeaufschlagung ist mindestens ein Regelventil vorgesehen. Durch die Druckbeaufschlagung wird eine Zusatzkraft in Hauptschubrichtung aufgebracht, so dass im gesamten Betriebsbereich der Gasturbine ein positiver resultierender Schub auf das mindestens eine Axiallager sichergestellt ist und eine Schubumkehr vermieden wird.In order to produce an additional thrust in the main direction of thrust, the inner annular space is acted upon by at least one line from Kompressorplenum or other suitable extraction point with compressed air. To control the pressurization at least one control valve is provided. By applying pressure an additional force is applied in the main direction of thrust, so that in the entire operating range of the gas turbine, a positive resulting thrust is ensured on the at least one thrust bearing and thrust reversal is avoided.
Je tiefer der statische Druck im Ringraum bei geschlossenem Regelventil ist, desto grösser wird bei Verwendung von Kompressorendluft der Regelbereich der Zusatzschubkraft. Die oben erwähnte Absenkung des statischen Drucks durch Einspeisung der Kühlluft über eine Dralldüse führt also zu einer Vergrösserung des Regelbereichs.The lower the static pressure in the annular space with the control valve closed, the greater the control range of the additional thrust force when using compressor discharge air. The above-mentioned reduction of the static pressure by feeding the cooling air through a swirl nozzle thus leads to an increase in the control range.
Zur Druckbeaufschlagung kann beispielsweise auch extern zugeführte Druckluft oder Dampf verwendet werden oder ein extern zugeführtes Medium in Kombination mit Kompressorluft verwendet werden.To pressurize, for example, externally supplied compressed air or steam can be used or an externally supplied medium can be used in combination with compressor air.
Neben der Nutzung bestehender Strukturteile besteht der Vorteil dieses Verfahrens darin, dass im hohen Lastbereich keine zusätzliche Druckbeaufschlagung erforderlich ist und damit keine komprimierte Luft unter Leistungs- und Wirkungsgradeinbusse verbraucht wird. Selbst wenn die Druckbeaufschlagung bei Teillast aktiv ist, wird die über die Dichtung zwischen innerem und äusseren Ringraum entweichende Luft nutzbringend der Rotorkühlluft beigemischt.In addition to the use of existing structural parts, the advantage of this method is that in the high load range no additional pressurization is required and thus no compressed air is consumed under performance and Wirkungsgradeinbusse. Even if the pressurization is active at partial load, the air escaping via the seal between the inner and outer annular space is usefully added to the rotor cooling air.
Zur Regelung der Druckbeaufschlagung sind verschiedene Verfahren denkbar. Beispielsweise kann das mindestens eine Regelventil bei tiefer Last geöffnet sein und beim Überschreiten eines diskreten Grenzwerts geschlossen werden. Umgekehrt wird das mindestens eine Regelventil beim Unterschreiten des diskreten Grenzwertes wieder geöffnet. Um bei Lasten nahe des Grenzwertes ständiges Schalten des mindestens einen Regelventils zu vermeiden, kann eine Hysterese vorgesehen werden.Various methods are conceivable for regulating the pressurization. For example, the at least one control valve may be open at low load and closed when a discrete limit is exceeded. Conversely, the at least one control valve is opened again when it falls below the discrete limit value. In order to avoid constant switching of the at least one control valve at loads close to the limit value, a hysteresis can be provided.
Eine andere Regelungsmöglichkeit ist beispielsweise ein Schliessen des Regelventils proportional zur Last.Another control option is, for example, a closure of the control valve proportional to the load.
In einer weitern Regelung wird nicht die Stellung des Regelventils in Abhängigkeit der Last vorgegeben, sondern das Druckverhältnis zwischen innerem Ringraum und Kompressorenddruck vorgegeben und dies Verhältnis über das Regelventil geregelt. Dabei ist der Zielwert nicht notwendig konstant, sondern ist beispielsweise eine Funktion der Last. Die Funktion kann beispielsweise so bestimmt werden, dass über einen möglichst weiten Betriebsbereich ein konstanter Axialschub erreicht wird.In a further regulation, the position of the control valve is not specified as a function of the load, but the pressure ratio between the inner annular space and compressor discharge pressure is predetermined and this ratio is regulated via the control valve. The target value is not necessarily constant, but is, for example, a function of the load. The function can, for example, be determined in such a way that a constant axial thrust is achieved over the widest possible operating range.
Die Stellung des Regelventils oder der Zielwert der Druckverhältnisse im inneren Ringraum kann beispielsweise auch in Abhängigkeit von dem Verdichtereintrittsleitschaufelwinkel oder der relativen Last vorgesehen werden. Regelungen abhängig von Kombinationen von Parametern oder weiteren relevanten Parametern sind ebenfalls möglich.The position of the control valve or the target value of the pressure conditions in the inner annular space can for example also be provided as a function of the Verdichtereintrittsleitschaufelwinkel or the relative load. Regulations depending on combinations of parameters or other relevant parameters are also possible.
Neben der Anwendung des Verfahrens für die Auslegung und Entwicklung von Neuanlagen, ist ein Spezialfall die Anwendung in Verbindung mit dem Upgrade einer Gasturbine. Bei dem Upgrade einer Gasturbine kann es durch Änderung an einer der Hauptkomponenten Turbine oder Kompressor zu einer Reduktion des Axialschubes kommen. Dies wird zum Beispiel der Fall sein, wenn durch einen Upgrade- Kompressor bei praktisch unverändertem Ansaugmassenstrom und damit praktisch unverändertem Kompressoraustrittsdruck und Turbinenschub der Kompressorschub zunimmt. Durch die Zunahme des Kompressorschubes kann es nach dem Upgrade zu einer Schubumkehr kommen. Um diese zu vermeiden, kann das erfindungsgemässe Verfahren angewandt werden und ein geregelter Zusatzschub aufgebracht werden.In addition to the application of the process for the design and development of new plants, a special case is the application in connection with the upgrade of a gas turbine. When upgrading a gas turbine, a change in one of the main components turbine or compressor can lead to a reduction of the axial thrust. This will be the case, for example, when the compressor thrust increases due to an upgrade compressor with virtually unchanged intake mass flow and thus virtually unchanged compressor discharge pressure and turbine thrust. The increase in compressor thrust can cause a thrust reverser after the upgrade. To avoid this, the method according to the invention can be used and a controlled additional thrust can be applied.
Neben dem Verfahren ist eine Gasturbine mit reduziertem maximalen Axialschub, mit wenigstens einer mit Druck beaufschlagbare Teilfläche des Turbinenrotors, beschrieben.In addition to the method, a gas turbine with reduced maximum axial thrust, with at least one pressurizable partial surface of the turbine rotor is described.
Eine Ausführung ist eine Gasturbine mit einer Dichtung, die den im wesentlichen ringförmigen Raum zwischen Trommelabdeckung und erster Turbinenscheibe in einen äusseren und einen inneren Ringraum teilt. Sie verfügt über mindestens eine Leitung vom Kompressorplenum zur Trommelabdeckung, mindestens ein Regelventil in dieser Leitung und mindestens eine Einleitung in den inneren Ringraum. Es gibt verschiedene, dem Fachmann bekannte Möglichkeiten eine Dichtung zwischen der Stirnfläche des Turbinenrotors und Trommelabdeckung auszuführen. Eine Labyrinthdichtung ist ein Beispiel für eine geeignete Dichtung.One embodiment is a gas turbine with a seal that divides the substantially annular space between the drum cover and the first turbine disk into an outer and an inner annular space. It has at least one line from the compressor plenum to the drum cover, at least one control valve in this line and at least one inlet into the inner annulus. There are various ways known to those skilled to perform a seal between the end face of the turbine rotor and drum cover. A labyrinth seal is an example of a suitable seal.
Bei einer Gasturbine mit mehr als einer Turbine sind Ringräume zur Druckbeaufschlagung an der Stirnfläche mindestens einer Turbine oder in Kombination bei mehreren oder allen Turbinen geteilt und mit mindestens einer regelbaren Druckluftversorgung ausgeführt.In a gas turbine with more than one turbine annular spaces for pressurization at the end face of at least one turbine or in combination divided at several or all turbines and running with at least one adjustable compressed air supply.
Für die Einleitung der Druckluft in den inneren Ringraum sind ebenfalls verschiedene Möglichkeiten bekannt. Dies kann beispielsweise eine Bohrung durch die Trommelabdeckung sein. In einer weiteren beispielhaften Ausführung ist die Einleitung in den inneren Ringraum der Trommelabdeckung ein im wesentlichen ringförmiges Plenum, das durch eine Vielzahl von Öffnung mit dem inneren Ringraum verbunden ist.For the introduction of compressed air into the inner annulus various possibilities are also known. This can be, for example, a hole through the drum cover. In another exemplary embodiment, the introduction into the inner annulus of the drum cover is a generally annular plenum connected to the inner annulus through a plurality of orifices.
In einer weiteren Ausführung ist ausserdem mindestens ein Druckmessgerät in dem inneren Ringraum und im Kompressorplenum vorgesehen.In a further embodiment, at least one pressure gauge is also provided in the inner annulus and in the compressor plenum.
In einer weiteren Ausführung ist die mindestens eine Zuleitung für Druckbeaufschlagung des inneren Plenums nicht mit dem Kompressorplenum, sondern einer anderen geeigneten Entnahmestelle für Kompressorluft über mindestens ein Regelventil verbunden.In a further embodiment, the at least one supply line for pressurizing the inner plenum is not connected to the Kompressplplenum, but another suitable extraction point for compressor air via at least one control valve.
Die Erfindung ist anhand von Ausführungsbeispielen in den
Es zeigen:
-
Fig. 1 Schnitt durch die Mittelpartie einer Gasturbine mit innerem und äusserem Ringraum sowie einer Zuführung für Druckbeaufschlagung des inneren Ringraumes. -
Fig. 2 Detailsauschnitt des Schnittes der Mittelpartie für eine Ausführung der Turbinenscheibendichtung als Labyrinthdichtung. -
Fig. 3 Schubverlauf über Last bei Regelung über einen Grenzwert mit Hysterese. -
Fig. 4 Idealisierter Schubverlauf über Last bei Regelung auf das lastabhängige Druckverhältnis zwischen Druck im inneren Ringraum und Kompressorenddruck.
-
Fig. 1 Section through the middle part of a gas turbine with inner and outer annular space and a supply for pressurizing the inner annulus. -
Fig. 2 Detail section of the section of the central part for an execution of the turbine disk seal as a labyrinth seal. -
Fig. 3 Thrust curve over load at control over a limit value with hysteresis. -
Fig. 4 Idealized shear progression via load during regulation to the load-dependent pressure ratio between pressure in the inner annulus and compressor discharge pressure.
Eine Gasturbine mit einer Vorrichtung zur Durchführung des erfindungsgemässen Verfahrens weist im wesentlichen mindestens einen Verdichter, mindestens eine Brennkammer und mindestens eine Turbine auf, die über mindestens eine Welle den Verdichter und einen Generator antreibt.A gas turbine with a device for carrying out the method according to the invention essentially has at least one compressor, at least one combustion chamber and at least one turbine, which drives the compressor and a generator via at least one shaft.
Der Verdichter 1 verdichtet die Luft. Der grösste Teil der Luft wird über das Kompressorplenum 2 in eine Brennkammer 3 eingeleitet und mit Brennstoff vermischt, der dort verbrennt. Von dort fliessen die heissen Brenngase unter Arbeitsabgabe durch eine Turbine 4 ab. Turbine 4 und Verdichter 1 sind auf einer gemeinsamen Welle 18 angeordnet, wobei der zwischen Verdichter 1 und Turbine 4 gelegene Teil der Welle als Trommel 6 ausgeführt ist.The compressor 1 compresses the air. Most of the air is introduced via the Kompressplplenum 2 in a
Der Hochdruckteil der Rotorkühlluft wird nach der letzten Kompressorschaufel drallbehaftet durch einen Ringkanal 7 zwischen Rotor- Trommel 6 und Trommelabdeckung 5 abgeleitet und über die Rotorkühlluftzuführung 12 und ein Drallgitter 13 in einen Ringraum zwischen Trommelabdeckung und einer ersten Turbinenscheibe eingeleitet. Dieser Ringraum wird durch eine Dichtung 9 in einen inneren Ringraum 10 und einen äusseren Ringraum 11 geteilt.The high-pressure part of the rotor cooling air is swirled after the last compressor blade discharged through an
Der äussere Ringraum wird beispielsweise durch die Hinterseite einer Trommelabdeckung 5, einer dem Rotor 18 zugewandten innere Plattform einer ersten Turbinenleitschaufel, einer ersten Turbinenscheibe sowie der Dichtung 9 begrenzt.The outer annular space is bounded, for example, by the rear side of a
Der innere Ringraum wird beispielsweise durch die Hinterseite einer Trommelabdeckung 5, einer Dichtung 9, einer ersten Turbinenscheibe einer Rotordichtung 8 sowie den Wänden eines stromab einer Rotordichtung 8 liegenden Teils eines Ringkanals 7 begrenzt.The inner annular space is bounded, for example, by the rear side of a
Die Dichtung 9 kann beispielsweise als Labyrinthdichtung 21 ausgeführt werden. Zur Aufnahme der Labyrinthdichtung 21 können beispielsweise, wie in
Die Rotorkühlluftzuführung 12 kann beispielsweise über ein Drallgitter 13 mit einem äusseren Ringraum 11 verbunden sein, dass die Rotorkühlluft tangential beschleunigt und damit den statischen Druck in einem äusseren Ringraum 11 absenkt. Von dem einen äusseren Ringraum 11 tritt die Rotorkühlluft in eine erste Turbinenscheibe ein. Ein Ringraum wird vor einer ersten Turbinenscheibe, d.h. der im wesentlichen ringförmige Raum zwischen Trommelabdeckung 5 und erster Turbinenscheibe, der durch eine Rotordichtung 8 eine Turbinenschaufelfussdichtung 24 abgeschlossen ist, durch eine Dichtung 9 in einen inneren 10 und äusseren Ringraum 11 geteilt. Diese Teilung erlaubt es, den inneren Ringraum 10 über eine Druckleitung 14 und ein Regelventil 15 mit Druckluft aus dem Kompressorplenum 2 zu beaufschlagen. Die Einleitung 16 der Druckluft in den inneren Ringraum 10 kann dabei über Bohrungen durch die Trommelabdeckung erfolgen oder, wie in
Der innere Ringraum 10 wird bei Teillast zur Erhöhung der Schubkraft durch öffnen des Regelventils 15 über die Druckleitung 14 und die Einleitung 16 mit Druck beaufschlagt. Über die Turbinenscheibendichtung 9 gelangt diese Luft zusammen mit der Leckageluft der Rotordichtung 8 in den äusseren Ringraum 11. Für die Regelung der Druckbeaufschlagung sind mehrere Möglichkeiten gegeben.The inner
In
Selbstverständlich ist die Erfindung nicht auf die hier gezeigten und beschriebenen Ausführungen beschränkt. Beispielsweise können die Dichtungen (8 und/ oder 9) als Bürstendichtung ausgeführt sein.Of course, the invention is not limited to the embodiments shown and described here. For example, the seals (8 and / or 9) can be designed as a brush seal.
- 11
- Verdichter (nur die zwei letzten Stufen dargestellt)Compressor (only the last two stages shown)
- 22
- Kompressorplenumcompressor plenary
- 33
- Brennkammercombustion chamber
- 44
- Turbine (nur die erste Stufe dargestellt)Turbine (only the first stage shown)
- 55
- Trommelabdeckungdrum cover
- 66
- Rotor- TrommelRotor drum
- 77
- Ringkanalannular channel
- 88th
- Rotordichtungrotor seal
- 99
- TurbinenscheibendichtungTurbine disc seal
- 1010
- Innerer RingraumInner annulus
- 1111
- Äusserer RingraumOuter annulus
- 1212
- RotorkühlluftzuführungRotor cooling air supply
- 1313
- Drallgitterswirl cascade
- 1414
- Druckleitungpressure line
- 1515
- Regelventilcontrol valve
- 1616
- Einleitungintroduction
- 1717
- Plenumplenum
- 1818
- Wellewave
- 1919
- Vorsprung der WellenabdeckungProjection of the shaft cover
- 2020
- Vorsprung der ersten TurbinenscheibeProjection of the first turbine disk
- 2121
- Labyrinthdichtunglabyrinth seal
- 2222
- Schaufelfussblade root
- 2323
- Laufschaufelblade
- 2424
- TurbinenschaufelfussdichtungTurbine blade root seal
Claims (8)
- Method for operating a gas turbine with axial thrust balance, wherein the gas turbine is configured, with respect to aerodynamic forces and compressive forces which exert axial forces on the rotor, such that these forces result in a negative thrust during no-load operation and at low partial load and in a positive thrust at high load and at full load, and such that a positive auxiliary thrust is applied with which the resulting axial bearing force is kept positive in the entire load range, and that at the high load range, no compressed air is consumed for pressurisation, characterised in that the auxiliary thrust is produced by controlling the pressure at the front face or at a partial front face of the turbine rotor, wherein a substantially annular chamber between the drum cover and a first turbine disc is divided by a seal into an outer annular chamber (11) and an inner annular chamber (10), and one of these two chambers is pressurised for thrust control.
- The method according to claim 1, characterised in that the outer annular chamber (11) is used to supply cooling air to the turbine rotor, and the inner annular chamber (10) is used for thrust control.
- Method according to one of claims 1 or 2, characterised in that- compressed air from a compressor plenum (2), and/or- compressed air from a compressor take-off before the compressor end, and/or- compressed air from an external source, and/or- steam from an external sourceis used for thrust control.
- Method according to any of claims 1 to 3, characterised in that the thrust force is controlled via at least one control valve (15) for pressurisation, which valve is opened at low load and closed when the pressure exceeds a discrete limit value, and the control valve (15) is opened again when the pressure falls below the discrete limit value.
- Method according to claim 4, characterised in that the limit value for opening of the at least one control valve (15) is higher than the limit value for closure.
- Method according to any of claims 1 to 3, characterised in that the at least one control valve (15) for setting the additional thrust is closed in proportion to the load.
- Method according to any of claims 1 to 3, characterised in that to control the additional thrust, the pressure ratio between the inner annular chamber (10) and the compressor end pressure (2) is predefined and that this ratio is controlled via the at least one control valve (15).
- Method according to claim 7, characterised in that the pressure ratio between the inner annular chamber and the compressor end pressure is- a function of the load, or- a function of another relevant operating parameter or a combination of operating parameters of the gas turbine.
Applications Claiming Priority (1)
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CH10792007 | 2007-07-04 |
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EP2011963A1 EP2011963A1 (en) | 2009-01-07 |
EP2011963B1 true EP2011963B1 (en) | 2018-04-04 |
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EP08159584.5A Active EP2011963B1 (en) | 2007-07-04 | 2008-07-03 | Method for operating a gas turbine with axial thrust balance |
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US (1) | US8092150B2 (en) |
EP (1) | EP2011963B1 (en) |
JP (1) | JP5511158B2 (en) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8182201B2 (en) * | 2009-04-24 | 2012-05-22 | Pratt & Whitney Canada Corp. | Load distribution system for gas turbine engine |
US20130195627A1 (en) | 2012-01-27 | 2013-08-01 | Jorn A. Glahn | Thrust balance system for gas turbine engine |
US10815891B2 (en) * | 2012-09-28 | 2020-10-27 | Raytheon Technologies Corporation | Inner diffuser case struts for a combustor of a gas turbine engine |
ITCO20120066A1 (en) * | 2012-12-20 | 2014-06-21 | Nuovo Pignone Srl | METHOD TO BALANCE THE PUSH, TURBINE AND ENGINE IN TURBINE |
US9869190B2 (en) | 2014-05-30 | 2018-01-16 | General Electric Company | Variable-pitch rotor with remote counterweights |
US10072510B2 (en) | 2014-11-21 | 2018-09-11 | General Electric Company | Variable pitch fan for gas turbine engine and method of assembling the same |
EP3037674A1 (en) * | 2014-12-22 | 2016-06-29 | Alstom Technology Ltd | Engine and method for operating said engine |
US10100653B2 (en) | 2015-10-08 | 2018-10-16 | General Electric Company | Variable pitch fan blade retention system |
US20190063222A1 (en) * | 2016-02-04 | 2019-02-28 | Siemens Aktiengesellschaft | Gas turbine having axial thrust piston and radial bearing |
DE102016201685A1 (en) * | 2016-02-04 | 2017-08-10 | Siemens Aktiengesellschaft | Method for the axial force compensation of a rotor of a gas turbine |
US10325061B2 (en) * | 2016-03-29 | 2019-06-18 | Mentor Graphics Corporation | Automatic axial thrust analysis of turbomachinery designs |
DE102017205055A1 (en) | 2017-03-24 | 2018-09-27 | Siemens Aktiengesellschaft | Method for the axial thrust control of a rotor of a turbomachine |
US10801549B2 (en) * | 2018-05-31 | 2020-10-13 | General Electric Company | Axial load management system |
US11674435B2 (en) | 2021-06-29 | 2023-06-13 | General Electric Company | Levered counterweight feathering system |
US11795964B2 (en) | 2021-07-16 | 2023-10-24 | General Electric Company | Levered counterweight feathering system |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH246779A (en) * | 1945-10-13 | 1947-01-31 | Bbc Brown Boveri & Cie | Turbomachine with axial thrust compensation device. |
US2647684A (en) * | 1947-03-13 | 1953-08-04 | Rolls Royce | Gas turbine engine |
US3704077A (en) * | 1970-11-03 | 1972-11-28 | Barber Colman Co | Thrust controller for propulsion systems with commonly driven, controllable pitch propellers |
US4018045A (en) * | 1971-06-25 | 1977-04-19 | Motoren- Und Turbinen-Union Munchen Gmbh | Regulating device for a prime mover, more particularly for a single-spool gas turbine |
US3989410A (en) * | 1974-11-27 | 1976-11-02 | General Electric Company | Labyrinth seal system |
US4653267A (en) | 1983-05-31 | 1987-03-31 | United Technologies Corporation | Thrust balancing and cooling system |
JPS59226235A (en) * | 1983-05-31 | 1984-12-19 | ユナイテツド・テクノロジ−ズ・コ−ポレイシヨン | Gas turbine engine |
US4730977A (en) | 1986-12-31 | 1988-03-15 | General Electric Company | Thrust bearing loading arrangement for gas turbine engines |
US4864810A (en) * | 1987-01-28 | 1989-09-12 | General Electric Company | Tractor steam piston balancing |
EP0447886B1 (en) | 1990-03-23 | 1994-07-13 | Asea Brown Boveri Ag | Axial flow gas turbine |
DE4433289A1 (en) | 1994-09-19 | 1996-03-21 | Abb Management Ag | Axial gas turbine |
US5760289A (en) | 1996-01-02 | 1998-06-02 | General Electric Company | System for balancing loads on a thrust bearing of a gas turbine engine rotor and process for calibrating control therefor |
US5735666A (en) * | 1996-12-31 | 1998-04-07 | General Electric Company | System and method of controlling thrust forces on a thrust bearing in a rotating structure of a gas turbine engine |
SE514159C2 (en) * | 1998-05-25 | 2001-01-15 | Abb Ab | Gas turbine assembly including a balancing means |
DE10358625A1 (en) | 2003-12-11 | 2005-07-07 | Rolls-Royce Deutschland Ltd & Co Kg | Arrangement for bearing relief in a gas turbine |
US20070122265A1 (en) * | 2005-11-30 | 2007-05-31 | General Electric Company | Rotor thrust balancing apparatus and method |
US8147178B2 (en) * | 2008-12-23 | 2012-04-03 | General Electric Company | Centrifugal compressor forward thrust and turbine cooling apparatus |
US8682562B2 (en) * | 2009-05-08 | 2014-03-25 | Rolls-Royce Corporation | Turbine engine thrust scheduling |
-
2008
- 2008-07-03 EP EP08159584.5A patent/EP2011963B1/en active Active
- 2008-07-03 US US12/167,800 patent/US8092150B2/en active Active
- 2008-07-04 JP JP2008175274A patent/JP5511158B2/en not_active Expired - Fee Related
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---|
None * |
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US20090067984A1 (en) | 2009-03-12 |
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