EP2078137B1 - Rotor for a turbo-machine - Google Patents
Rotor for a turbo-machine Download PDFInfo
- Publication number
- EP2078137B1 EP2078137B1 EP07803598A EP07803598A EP2078137B1 EP 2078137 B1 EP2078137 B1 EP 2078137B1 EP 07803598 A EP07803598 A EP 07803598A EP 07803598 A EP07803598 A EP 07803598A EP 2078137 B1 EP2078137 B1 EP 2078137B1
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- EP
- European Patent Office
- Prior art keywords
- rotor
- steam turbine
- turbine according
- designed
- steam
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/08—Heating, heat-insulating or cooling means
- F01D5/085—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/08—Heating, heat-insulating or cooling means
- F01D5/085—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor
- F01D5/088—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor in a closed cavity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/30—Application in turbines
- F05D2220/31—Application in turbines in steam turbines
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- 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
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/205—Cooling fluid recirculation, i.e. after cooling one or more components is the cooling fluid recovered and used elsewhere for other purposes
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- 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
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
- F05D2260/2322—Heat transfer, e.g. cooling characterized by the cooling medium steam
Definitions
- the invention relates to a steam turbine comprising a housing and a rotor, wherein the housing has a passage for the passage of external cooling medium, wherein the rotor is at least partially hollow.
- a steam turbine is understood to mean any turbine or sub-turbine through which a working medium in the form of steam flows.
- gas turbines are traversed with gas and / or air as a working medium, but that is subject to completely different temperature and pressure conditions than the steam in a steam turbine.
- the working medium having the highest temperature and flowing to a partial turbine at the same time has the highest pressure.
- An open cooling system, as in gas turbines, is therefore not feasible without external supply.
- a steam turbine typically includes a vaned rotatably mounted rotor disposed within a casing shell.
- the rotor When flowing through the flow space formed by the housing jacket with heated and pressurized steam, the rotor is set in rotation by the steam via the blades.
- the rotor-mounted blades are also referred to as blades.
- usually stationary guide vanes are mounted on the housing jacket, which engage in the intermediate spaces of the moving blades.
- a vane is typically held at a first location along an interior of the steam turbine casing. It is usually part of a vane ring, which comprises a number of vanes arranged along an inner periphery on the inside of the steam turbine casing. Each vane has its blade radially inward.
- a vane ring at a location along the axial extent is also referred to as a vane row.
- a plurality of vane rows are arranged one behind the other.
- the rotatably mounted in the steam turbine steam turbine rotors are subjected to thermal stress during operation.
- the development and production of a steam turbine rotor is both expensive and time consuming.
- the steam turbine rotors are considered the most stressed and expensive components of a steam turbine. This increasingly applies to high steam turbines.
- a feature of the steam turbine rotor is that they have no significant heat sink. Therefore, the cooling of the blades arranged on the steam turbine rotor is difficult.
- Piston area is to be understood as the area of a thrust balance piston.
- the thrust balance piston acts in a steam turbine such that a force caused by the working medium force is formed on the rotor in one direction counter-force in the opposite direction.
- a cooling of a steam turbine rotor according to the preamble of claim 1 is in the EP 0 991 850 B1 described.
- a disadvantage here is felt that between two different Expansicnsabitesen no controllable bypass can be formed.
- problems in transient operation are possible.
- the object of the invention is therefore to provide a steam turbine, which can be operated at high steam temperatures.
- a steam turbine comprising a housing and a rotor, wherein the housing has a passage for the passage of external cooling medium, wherein the rotor is at least partially hollow, wherein a Supply line for carrying out the external cooling medium is provided in the cavity of the rotor, and the passage is arranged in the housing in the region of the steam inflow.
- the invention is therefore proposed to supply external cooling medium in the rotor of the steam turbine, wherein the cooling medium is guided to a suitable point of the rotor.
- the cavity is used as a suitable location.
- the cavity is expediently attached to the places which are exposed to a high thermal load.
- the hitherto known method in which the external cooling medium is flowed into the steam turbine and directly cools thermally stressed parts such as the thrust balance piston, is therefore improved by the cooling medium is passed after passing through the housing into the cavity of the rotor.
- the cooling steam must have a higher pressure than at the inflow, so that it can be guided into the cavity.
- An advantage of this cooling principle according to the invention is that the temperature of the cooling medium is adjustable.
- Steam turbines are usually used at different loads. For example, a steam turbine is operated at full load or in partial load operation. The cooling requirements for the different load operations are different, so the demand for the cooling of the steam turbine in part load operation is lower than in full load operation.
- the invention is advantageously developed if the rotor is designed such that the cooling medium via rotor cooling pipes can be flowed out of the cavity.
- the cooling medium first flows through external lines through the housing into the cavity of the rotor and then flows at suitable locations from the rotor back into the main flow.
- the cooling medium flows and cools the rotor from the inside.
- the outflow of the cooling medium from the rotor takes place at one or more points downstream.
- the cooling medium fulfills two tasks, so to speak, on the one hand, the cooling medium cools the rotor at suitable locations and on the other, the cooling medium contributes to the efficiency in which it is fed back into the main flow and performs work on the guide vanes and blades.
- the supply line is arranged in the region of a steam inflow region. As a result, a suitable location for the supply line is found, since just the area of the steam inflow area is exposed to very high thermal loads and therefore requires a preferred cooling.
- the supply line is arranged next to a thrust balance piston. This makes it possible for the cooling medium, before it is guided into the cavity of the rotor, to cool the thrust balance piston.
- the thrust balance piston is subject to high thermal loads, especially at full load.
- the rotor has rotor blades which are designed such that the cooling medium can be flowed through the rotor blades.
- This provides the advantage that in addition to the rotor and the blades can be cooled.
- the film cooling of the rotor blades known from gas turbine technology is preferably used. In this way, blade roots or other thermally stressed areas of the rotor can be effectively cooled.
- the rotor is made of disc rotors and braced with a tie rod.
- the pancake is formed with a toothing for transmitting a torque.
- the rotor can be formed of different materials. It is conceivable, for example, that a pancake, which is exposed to lower thermal loads than a pancake, which is exposed to high thermal stress, is performed with a material that is less expensive and yet withstands the thermal stresses.
- the toothing is designed such that the cooling medium can be flowed between two adjacent disc rotors.
- the toothing is formed such that the toothing has passage openings.
- channels can be provided in the so-called Hirth toothing. Through these channels, the cooling medium is flowable.
- FIG. 1 is a section through a high-pressure turbine part 1 according to the prior art shown.
- the high-pressure turbine part 1 as an embodiment of a steam turbine comprises an outer housing 2 and an inner housing 3 arranged therein.
- a rotor 5 is rotatably mounted about a rotation axis 6.
- the rotor 5 comprises blades 7 arranged in grooves on a surface of the rotor 5.
- the inner housing 3 has guide vanes 8 arranged in grooves on its inner surface.
- the guide 8 and blades 7 are arranged such that in a flow direction 13, a flow channel 9 is formed.
- the high-pressure turbine section 1 has an inflow region 10, through which live steam flows into the high-pressure turbine section 1 during operation.
- the live steam may have steam parameters above 300 bar and above 620 ° C.
- the relaxing in the flow direction 13 live steam flows alternately past the guide 8 and blades 7, relaxes and cools down.
- the steam loses in this case to internal energy, which is converted into rotational energy of the rotor 5.
- the rotation of the rotor 5 finally drives a generator, not shown, for power supply.
- the high pressure turbine part 1 may drive other equipment other than a generator, such as a compressor, a marine propeller, or the like.
- the steam flows through the flow channel 9 and flows out of the high-pressure turbine section 1 from the outlet 33.
- the steam exerts an action force 11 in the flow direction 13. The result is that the rotor 5 would perform a movement in the flow direction 13.
- FIG. 2 a section of a steam turbine 1 is shown.
- the steam turbine has a housing 39.
- the housing 39 could be an inner housing 3 or an outer housing 2.
- the steam turbine according to FIG. 2 is carried out such that the housing 39 has a passage 20 for performing external cooling medium 21.
- the rotor 5 is in this case at least partially hollow.
- the rotor 5 therefore has a cavity 22.
- the rotor 5 has a feed line 23 for carrying out the external cooling medium 21.
- the cooling medium 21 is guided via the passage 20 and the supply line 23 into the cavity 22.
- a first cooling effect of the cooling medium 21 is already achieved in the housing 39 in the region of the passage 20.
- the passage 20 is arranged in the vicinity of the inflow region 10.
- the inflow region 10 is particularly thermally stressed, since there flows in the live steam.
- the cooling medium is guided from the passage 20 to the supply line 23 and flows into the cavity 22.
- the cooling medium 21 must in this case have a corresponding pressure.
- the supply line 23 can be made by radial bores. Other embodiments, such as inclined leads are conceivable.
- the rotor 5 is designed such that the cooling medium 21 can be flowed out of the cavity 22 via rotor cooling lines 24.
- the supply line 23 can be arranged next to a compensating piston 4. Since the balance piston is particularly thermally stressed, this would be an advantageous embodiment.
- the cooling medium 21 flowing out of the rotor cooling duct 24 mixes with the working medium coming from the inflow region 10, which as a rule is a vapor.
- the cooling medium 21 cools, inter alia, from the supply line 23, the rotor 5 on an inner surface 25 of the cavity 22nd
- the steam turbine 1 may be designed such that the rotor 5 has blades 7, which are designed such that the cooling medium 21 can be flowed through the blade 7. As a result, the blade 7 is cooled.
- the blades 7 in this case have individual openings.
- the blades 7 are cooled by the so-called film cooling. Film cooling is known from gas turbine technology.
- the rotor 5 is designed such that the blade feet, the balance piston 4 or other critical areas that are thermally stressed, are coolable.
- FIG. 2 illustrated rotor 5 is welded to a weld 26 of two partial rotors 27, 28.
- the rotor 5 can be made of a uniform material, ie without a weld 26.
- a rotor which is composed of three disc rotors 29, 30, 31.
- the rotor 5 may be made of only two disc rotors.
- the three pancake rollers 29, 30, 31 are firmly clamped together by means of a tie rod 32.
- the tie rod at its ends a thread 34.
- the tie rod 32 By turning the tie rod 32, a movement of the tie rod 32 in the rotation axis direction, which results in that the three pancake 29, 30, 31 are compressed.
- the pancake 29, 30, 31 at their points of contact 35, 36 has a toothing for transmitting a torque.
- the toothing can be designed as a Hirth, rectangular or trapezoidal toothing.
- FIG. 4 a first embodiment of a toothing 37, 38 is shown.
- the toothing 37, 38 is designed as a triangular toothing 37.
- the toothing 37 is designed such that a supply line 23 is formed. Through the supply line 23, the cooling medium 21 is flowable.
- toothing 38 is formed as a trapezoidal toothing 38.
- the trapezoidal toothing 38 is designed such that feed lines 23 are formed, through which the cooling medium 21 can be flowed.
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- General Engineering & Computer Science (AREA)
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Abstract
Description
Die Erfindung betrifft eine Dampfturbine umfassend ein Gehäuse und einen Rotor, wobei das Gehäuse eine Durchführung zum Durchführen von externem Kühlmedium aufweist, wobei der Rotor zumindest teilweise hohl ausgeführt ist.The invention relates to a steam turbine comprising a housing and a rotor, wherein the housing has a passage for the passage of external cooling medium, wherein the rotor is at least partially hollow.
Zur Steigerung des Wirkungsgrades einer Dampfturbine trägt die Verwendung von Dampf mit höheren Drücken und Temperaturen bei. Die Verwendung von Dampf mit einem solchen Dampfzustand stellt erhöhte Anforderungen an die entsprechende Dampfturbine.To increase the efficiency of a steam turbine, the use of steam at higher pressures and temperatures helps. The use of steam with such a steam condition places increased demands on the corresponding steam turbine.
Unter einer Dampfturbine im Sinne der vorliegenden Anmeldung wird jede Turbine oder Teilturbine verstanden, die von einem Arbeitsmedium in Form von Dampf durchströmt wird. Im Unterschied dazu werden Gasturbinen mit Gas und/oder Luft als Arbeitsmedium durchströmt, dass jedoch völlig anderen Temperatur- und Druckbedingungen unterliegt als der Dampf bei einer Dampfturbine. Im Gegensatz zu Gasturbinen weist bei Dampfturbinen z.B. das einer Teilturbine zuströmende Arbeitsmedium mit der höchsten Temperatur gleichzeitig den höchsten Druck auf. Ein offenes Kühlsystem, wie bei Gasturbinen, ist also nicht ohne externe Zuführung realisierbar. Eine Dampfturbine umfasst üblicherweise einen mit Schaufeln besetzten drehbar gelagerten Rotor, der innerhalb eines Gehäusemantels angeordnet ist. Bei Durchströmung des vom Gehäusemantel gebildeten Strömungsraumes mit erhitztem und unter Druck stehendem Dampf wird der Rotor über die Schaufeln durch den Dampf in Rotation versetzt. Die am Rotor angebrachten Schaufeln werden auch als Laufschaufeln bezeichnet. Am Gehäusemantel sind darüber hinaus üblicherweise stationäre Leitschaufeln angebracht, welche in die Zwischenräume der Laufschaufeln greifen. Eine Leitschaufel ist üblicherweise an einer ersten Stelle entlang einer Innenseite des Dampfturbinengehäuses gehalten. Dabei ist sie üblicherweise Teil eines Leitschaufelkranzes, welcher eine Anzahl von Leitschaufeln umfasst, die entlang eines Innenumfangs an der Innenseite des Dampfturbinengehäuses angeordnet sind. Dabei weist jede Leitschaufel mit ihrem Schaufelblatt radial nach innen. Ein Leitschaufelkranz an einer Stelle entlang der axialen Ausdehnung wird auch als Leitschaufelreihe bezeichnet. Üblicherweise sind mehrere Leitschaufelreihen hintereinander angeordnet.For the purposes of the present application, a steam turbine is understood to mean any turbine or sub-turbine through which a working medium in the form of steam flows. In contrast, gas turbines are traversed with gas and / or air as a working medium, but that is subject to completely different temperature and pressure conditions than the steam in a steam turbine. In contrast to gas turbines, in steam turbines, for example, the working medium having the highest temperature and flowing to a partial turbine at the same time has the highest pressure. An open cooling system, as in gas turbines, is therefore not feasible without external supply. A steam turbine typically includes a vaned rotatably mounted rotor disposed within a casing shell. When flowing through the flow space formed by the housing jacket with heated and pressurized steam, the rotor is set in rotation by the steam via the blades. The rotor-mounted blades are also referred to as blades. In addition, usually stationary guide vanes are mounted on the housing jacket, which engage in the intermediate spaces of the moving blades. A vane is typically held at a first location along an interior of the steam turbine casing. It is usually part of a vane ring, which comprises a number of vanes arranged along an inner periphery on the inside of the steam turbine casing. Each vane has its blade radially inward. A vane ring at a location along the axial extent is also referred to as a vane row. Usually, a plurality of vane rows are arranged one behind the other.
Eine wesentliche Rolle bei der Steigerung des Wirkungsgrades spielt die Kühlung. Bei den bisher bekannten Kühlmittelmethoden zur Kühlung eines Dampfturbinengehäuses ist, zwischen einer aktiven Kühlung und einer passiven Kühlung zu unterscheiden. Bei einer aktiven Kühlung wird eine Kühlung durch ein der Dampfturbine separat, d.h. zusätzlich zum Arbeitsmedium zugeführtes Kühlmedium bewirkt. Dagegen erfolgt eine passive Kühlung lediglich durch eine geeignete Führung oder Verwendung des Arbeitsmediums. Eine bekannte Kühlung eines Dampfturbinengehäuses beschränkt sich auf eine passive Kühlung. So ist beispielsweise bekannt, ein Innengehäuse einer Dampfturbine mit kühlem, bereits expandiertem Dampf zu umströmen. Dies hat jedoch den Nachteil, dass eine Temperaturdifferenz über die Innengehäusewandung beschränkt bleiben muss, da sich sonst bei einer zu großen Temperaturdifferenz das Innengehäuse thermisch zu stark verformen würde. Bei einer Umströmung des Innengehäuses findet zwar eine Wärmeabfuhr statt, jedoch erfolgt die Wärmeabfuhr relativ weit entfernt von der Stelle der Wärmezufuhr. Eine Wärmeabfuhr in unmittelbarer Nähe der Wärmezufuhr ist bisher nicht in ausreichendem Maße verwirklicht worden. Eine weitere passive Kühlung kann mittels einer geeigneten Gestaltung der Expansion des Arbeitsmediums in einer so genannten Diagonalstufe erreicht werden. Hierüber lässt sich allerdings nur eine sehr begrenzte Kühlwirkung auf das Gehäuse erzielen.An essential role in increasing the efficiency plays the cooling. In the previously known coolant methods for cooling a steam turbine housing is to distinguish between an active cooling and a passive cooling. With active cooling, cooling by one of the steam turbine is separated, i. effected in addition to the working medium supplied cooling medium. In contrast, a passive cooling is done only by a suitable leadership or use of the working medium. A known cooling of a steam turbine housing is limited to a passive cooling. For example, it is known to flow around an inner casing of a steam turbine with cool, already expanded steam. However, this has the disadvantage that a temperature difference over the Innengehäusewandung must remain limited, otherwise the inner housing would thermally deform too much at too large a temperature difference. Although a heat dissipation takes place in a flow around the inner housing, the heat removal takes place relatively far away from the point of heat supply. Heat removal in the immediate vicinity of the heat supply has not been realized sufficiently. Another passive cooling can be achieved by means of a suitable design of the expansion of the working medium in a so-called diagonal stage. However, this can only achieve a very limited cooling effect on the housing.
Die in den Dampfturbinen drehbar gelagerten Dampfturbinenrotoren werden im Betrieb thermisch sehr beansprucht. Die Entwicklung und Herstellung eines Dampfturbinenrotors ist zugleich teuer und zeitaufwändig. Die Dampfturbinenrotoren gelten als die am höchsten beanspruchten und teuersten Komponenten einer Dampfturbine. Dies gilt zunehmend für hohe Dampfturbinen.The rotatably mounted in the steam turbine steam turbine rotors are subjected to thermal stress during operation. The development and production of a steam turbine rotor is both expensive and time consuming. The steam turbine rotors are considered the most stressed and expensive components of a steam turbine. This increasingly applies to high steam turbines.
Eine Eigenschaft des Dampfturbinenrotors ist, dass diese über keine wesentliche Wärmesenke verfügen. Daher gestaltet sich die Kühlung der an dem Dampfturbinenrotor angeordneten Laufschaufeln als schwierig.A feature of the steam turbine rotor is that they have no significant heat sink. Therefore, the cooling of the blades arranged on the steam turbine rotor is difficult.
Besonders thermisch belastet werden bei den Dampfturbinenrotoren die Kolben- und Einströmbereiche. Mit Kolbenbereich ist der Bereich eines Schubausgleichskolbens zu verstehen. Der Schubausgleichskolben wirkt in einer Dampfturbine derart, dass eine durch das Arbeitsmedium hervorgerufene Kraft auf den Rotor in einer Richtung eine Gegenkraft in Gegenrichtung ausgebildet wird.The piston and inflow areas are particularly thermally stressed in the steam turbine rotors. Piston area is to be understood as the area of a thrust balance piston. The thrust balance piston acts in a steam turbine such that a force caused by the working medium force is formed on the rotor in one direction counter-force in the opposite direction.
Eine Kühlung eines Dampfturbinenrotors gemäß dem Oberbegriff von Anspruch 1 ist in der
Wünschenswert wäre es, eine Dampfturbine auszubilden, die für hohe Temperaturen geeignet ist.It would be desirable to form a steam turbine that is suitable for high temperatures.
Aufgabe der Erfindung ist es daher, eine Dampfturbine anzugeben, die bei hohen Dampftemperaturen betrieben werden kann.The object of the invention is therefore to provide a steam turbine, which can be operated at high steam temperatures.
Gelöst wird diese Aufgabe durch eine Dampfturbine, umfassend ein Gehäuse und einen Rotor, wobei das Gehäuse eine Durchführung zum Durchführen von externem Kühlmedium aufweist, wobei der Rotor zumindest teilweise hohl ausgeführt ist, wobei eine Zuleitung zum Durchführen des externen Kühlmediums in den Hohlraum des Rotors vorgesehen ist, und die Durchführung im Gehäuse im Bereich des Dampfeinströmbereichs angeordnet ist.This object is achieved by a steam turbine, comprising a housing and a rotor, wherein the housing has a passage for the passage of external cooling medium, wherein the rotor is at least partially hollow, wherein a Supply line for carrying out the external cooling medium is provided in the cavity of the rotor, and the passage is arranged in the housing in the region of the steam inflow.
Mit der Erfindung wird daher vorgeschlagen, externes Kühlmedium in den Rotor der Dampfturbine zuzuführen, wobei das Kühlmedium an eine geeignete Stelle des Rotors geführt wird. Hierbei wird als geeignete Stelle der Hohlraum verwendet. Der Hohlraum ist zweckmäßigerweise an den Stellen angebracht, die einer hohen thermischen Belastung ausgesetzt sind.With the invention is therefore proposed to supply external cooling medium in the rotor of the steam turbine, wherein the cooling medium is guided to a suitable point of the rotor. Here, the cavity is used as a suitable location. The cavity is expediently attached to the places which are exposed to a high thermal load.
Das bisher bekannte Verfahren, bei dem das externe Kühlmedium in die Dampfturbine eingeströmt wird und thermisch belastete Teile wie den Schubausgleichskolben unmittelbar kühlt, wird demnach verbessert, indem das Kühlmedium nach der Durchführung durch das Gehäuse in den Hohlraum des Rotors geführt wird. Dazu muss der Kühldampf einen höheren Druck als an der Einströmung aufweisen, damit dieser in den Hohlraum geführt werden kann.The hitherto known method, in which the external cooling medium is flowed into the steam turbine and directly cools thermally stressed parts such as the thrust balance piston, is therefore improved by the cooling medium is passed after passing through the housing into the cavity of the rotor. For this purpose, the cooling steam must have a higher pressure than at the inflow, so that it can be guided into the cavity.
Ein Vorteil dieses erfindungsgemäßen Kühlprinzips ist es, dass die Temperatur des Kühlmediums einstellbar ist. Dampfturbinen werden in der Regel bei unterschiedlichen Lasten verwendet. So wird beispielsweise eine Dampfturbine im Volllastbetrieb oder im Teillastbetrieb betrieben. Die Kühlanforderungen für die verschiedenen Lastbetriebe sind unterschiedlich, so ist die Anforderung an die Kühlung der Dampfturbine im Teillastbetrieb geringer als beim Volllastbetrieb.An advantage of this cooling principle according to the invention is that the temperature of the cooling medium is adjustable. Steam turbines are usually used at different loads. For example, a steam turbine is operated at full load or in partial load operation. The cooling requirements for the different load operations are different, so the demand for the cooling of the steam turbine in part load operation is lower than in full load operation.
Im Volllastbetrieb wird daher mehr Kühlmedium bzw. eine niedrigere Temperatur des Kühlmediums gefordert, was erfindungsgemäß ohne weiteres möglich ist, da die Temperatur des Kühlmediums leicht geregelt werden kann.In full load operation, therefore, more cooling medium or a lower temperature of the cooling medium is required, which according to the invention is readily possible, since the temperature of the cooling medium can be easily controlled.
Vorteilhafte Weiterbildungen sind in den Unteransprüchen dargestellt.Advantageous developments are shown in the subclaims.
So wird die Erfindung vorteilhaft weitergebildet, wenn der Rotor derart ausgebildet ist, dass das Kühlmedium über Rotorkühlleitungen aus dem Hohlraum strömbar ist. Das Kühlmedium strömt zunächst über externe Leitungen durch das Gehäuse in den Hohlraum des Rotors und strömt anschließend an geeigneten Stellen aus dem Rotor wieder in die Hauptströmung. Dabei beströmt und kühlt das Kühlmedium den Rotor von innen. Das Ausströmen des Kühlmediums aus dem Rotor erfolgt an einer oder mehreren stromab gelegenen Stellen.Thus, the invention is advantageously developed if the rotor is designed such that the cooling medium via rotor cooling pipes can be flowed out of the cavity. The cooling medium first flows through external lines through the housing into the cavity of the rotor and then flows at suitable locations from the rotor back into the main flow. The cooling medium flows and cools the rotor from the inside. The outflow of the cooling medium from the rotor takes place at one or more points downstream.
Durch diese Maßnahme erfüllt das Kühlmedium sozusagen zwei Aufgaben, zum einen kühlt das Kühlmedium den Rotor an geeigneten Stellen und zum anderen trägt das Kühlmedium zum Wirkungsgrad bei, in dem es der Hauptströmung wieder zugeführt wird und an den Leit- und Laufschaufeln Arbeit verrichtet.By this measure, the cooling medium fulfills two tasks, so to speak, on the one hand, the cooling medium cools the rotor at suitable locations and on the other, the cooling medium contributes to the efficiency in which it is fed back into the main flow and performs work on the guide vanes and blades.
In einer vorteilhaften Weiterbildung ist die Zuleitung im Bereich eines Dampfeinströmbereiches angeordnet. Dadurch ist eine geeignete Stelle für die Zuleitung gefunden, da gerade der Bereich des Dampfeinströmbereiches sehr hohen thermischen Belastungen ausgesetzt ist und daher einer bevorzugten Kühlung bedarf.In an advantageous development, the supply line is arranged in the region of a steam inflow region. As a result, a suitable location for the supply line is found, since just the area of the steam inflow area is exposed to very high thermal loads and therefore requires a preferred cooling.
In einer weiteren vorteilhaften Weiterbildung ist die Zuleitung neben einem Schubausgleichskolben angeordnet. Dadurch ist es möglich, dass das Kühlmedium, bevor es in den Hohlraum des Rotors geführt wird, den Schubausgleichskolben kühlt. Der Schubausgleichskolben wird vor allem bei Volllast thermisch stark belastet.In a further advantageous development, the supply line is arranged next to a thrust balance piston. This makes it possible for the cooling medium, before it is guided into the cavity of the rotor, to cool the thrust balance piston. The thrust balance piston is subject to high thermal loads, especially at full load.
In einer vorteilhaften Weiterbildung weist der Rotor Laufschaufeln auf, die derart ausgebildet sind, dass das Kühlmedium durch die Laufschaufeln strömbar ist. Dadurch wird der Vorteil erzielt, dass neben dem Rotor auch die Laufschaufeln gekühlt werden können. Dabei wird bevorzugt die aus der Gasturbinentechnologie bekannte Filmkühlung der Laufschaufeln verwendet. Auf diese Weise können auch Schaufelfüße oder andere thermisch belastete Bereiche des Rotors wirksam gekühlt werden.In an advantageous development, the rotor has rotor blades which are designed such that the cooling medium can be flowed through the rotor blades. This provides the advantage that in addition to the rotor and the blades can be cooled. In this case, the film cooling of the rotor blades known from gas turbine technology is preferably used. In this way, blade roots or other thermally stressed areas of the rotor can be effectively cooled.
In einer vorteilhaften Weiterbildung ist der Rotor aus Scheibenläufern ausgeführt und mit einem Zuganker verspannt.In an advantageous development of the rotor is made of disc rotors and braced with a tie rod.
Ebenso vorteilhaft ist es, wenn der Scheibenläufer mit einer Verzahnung zum Übertragen eines Drehmomentes ausgebildet ist. Dadurch kann der Rotor aus unterschiedlichen Materialien ausgebildet werden. Denkbar ist beispielsweise, dass ein Scheibenläufer, der geringeren thermischen Belastungen ausgesetzt ist als ein Scheibenläufer, der hohen thermischen Belastung ausgesetzt ist, mit einem Material ausgeführt wird, das kostengünstiger ist und dennoch den thermischen Belastungen standhält.It is equally advantageous if the pancake is formed with a toothing for transmitting a torque. As a result, the rotor can be formed of different materials. It is conceivable, for example, that a pancake, which is exposed to lower thermal loads than a pancake, which is exposed to high thermal stress, is performed with a material that is less expensive and yet withstands the thermal stresses.
In einer weiteren vorteilhaften Weiterbildung ist die Verzahnung derart ausgebildet, dass das Kühlmedium zwischen zwei benachbarten Scheibenläufern strömbar ist. Dazu wird die Verzahnung derart ausgebildet, dass die Verzahnung Durchtrittsöffnungen aufweist. Beispielsweise können Kanäle in der so genannten Hirthverzahnung vorgesehen sein. Durch diese Kanäle ist das Kühlmedium strömbar. Diese Ausführungsform bietet den Vorteil, dass für die Durchführung des Kühlmediums über Radialkanäle keine zusätzlichen Bohrungen ausgeführt werden müssen, zusätzliche Bohrungen im Rotor verursachen eine hohe Spannungskonzentration durch zusätzliche Kerben. Solche Spannungskonzentrationen entfallen, wenn das Kühlmedium durch die Verzahnung geführt wird.In a further advantageous development, the toothing is designed such that the cooling medium can be flowed between two adjacent disc rotors. For this purpose, the toothing is formed such that the toothing has passage openings. For example, channels can be provided in the so-called Hirth toothing. Through these channels, the cooling medium is flowable. This embodiment has the advantage that no additional bores have to be carried out for the passage of the cooling medium via radial channels, additional bores in the rotor cause a high concentration of stress by additional notches. Such stress concentrations omitted when the cooling medium is passed through the teeth.
Ausführungsbeispiele der Erfindung werden anhand der nachfolgenden Zeichnungen näher erläutert. Dabei haben Komponenten mit den gleichen Bezugszeichen die gleiche Funktionsweise.Embodiments of the invention will be explained in more detail with reference to the following drawings. In this case, components with the same reference numerals have the same functionality.
Es zeigen:
- FIG 1
- ein Querschnitt einer Dampfturbine gemäß dem Stand der Technik,
- FIG 2
- ein Querschnitt eines Rotors einer Dampfturbine und eines Teils eines Gehäuses,
- FIG 3
- Querschnitt durch einen Rotor,
- FIG 4
- Querschnitt durch eine Verzahnung,
- FIG 5
- Querschnitt einer Verzahnung in alternativer Ausführungsform.
- FIG. 1
- a cross section of a steam turbine according to the prior art,
- FIG. 2
- a cross section of a rotor of a steam turbine and a part of a housing,
- FIG. 3
- Cross section through a rotor,
- FIG. 4
- Cross section through a toothing,
- FIG. 5
- Cross-section of a toothing in an alternative embodiment.
In der
In der
Die Dampfturbine gemäß
Die Zuleitung 23 kann durch radiale Bohrungen erfolgen. Andere Ausführungsformen wie z.B. schräg verlaufende Zuleitungen sind denkbar.The
Der Übersichtlichkeit wegen sind in der
Die Zuleitung 23 kann neben einem Ausgleichskolben 4 angeordnet werden. Da der Ausgleichskolben besonders thermisch belastet ist wäre dies eine vorteilhafte Ausführungsform.The
Das aus den Rotorkühlleitung 24 ausströmende Kühlmedium 21 vermischt sich mit dem aus dem Einströmbereich 10 kommenden Arbeitsmedium, das in der Regel ein Dampf ist. Das Kühlmedium 21 kühlt unter anderem ab der Zuleitung 23 den Rotor 5 an einer Innenfläche 25 des Hohlraums 22.The cooling
Die Dampfturbine 1 kann derart ausgebildet sein, dass der Rotor 5 Laufschaufeln 7 aufweist, die derart ausgebildet sind, dass das Kühlmedium 21 durch die Laufschaufel 7 strömbar ist. Dadurch werden die Laufschaufel 7 gekühlt. Die Laufschaufeln 7 weisen hierbei einzelne Durchtrittsöffnungen auf. Die Laufschaufeln 7 werden durch die so genannte Filmkühlung gekühlt. Die Filmkühlung ist aus der Gasturbinentechnologie bekannt.The steam turbine 1 may be designed such that the rotor 5 has blades 7, which are designed such that the cooling
Vorzugsweise ist der Rotor 5 derart ausgebildet, dass die Laufschaufelfüße, der Ausgleichskolben 4 oder andere kritische Bereiche, die thermisch belastet sind, kühlbar sind.Preferably, the rotor 5 is designed such that the blade feet, the
Der in
In der
In der
In der
Claims (15)
- Steam turbine, comprising a casing (2, 3, 39), a rotor (5) and a steam inflow region (10), the casing (2, 3, 39) having a leadthrough (20) for leading through an external cooling medium (21), the rotor (5) being designed to be at least partially hollow, the rotor (5) having a supply line (23) for leading the external cooling medium (21) through into the cavity (22) of the rotor (5), characterized in that the leadthrough (20) is arranged in the casing in the region of the steam inflow region (10).
- Steam turbine according to Claim 1, the rotor (5) being designed in such a way that the cooling medium (21) can flow out of the cavity (22) via rotor cooling lines (24).
- Steam turbine according to Claim 1 or 2, in which the supply line (23) is arranged in the region of an inflow region (10).
- Steam turbine according to Claim 1, 2 or 3, in which the supply line (23) is arranged next to a balancing piston (4).
- Steam turbine according to one of the preceding claims, in which the cooling medium (21) flowing out of the rotor (5) during operation can be mixed with a flow medium.
- Steam turbine according to one of the preceding claims, in which the rotor (5) has moving blades (7) which are designed in such a way that the cooling medium (21) can flow through the moving blades (7).
- Steam turbine according to Claim 6, in which the moving blades (7) can be cooled by means of film cooling.
- Steam turbine according to one of the preceding claims, the rotor (5) being designed in such a way that moving-blade roots, the thrust-type balancing piston (4) or other thermally loaded regions of the rotor (5) can be cooled.
- Steam turbine according to one of the preceding claims, the rotor (5) having outlet orifices for radial outflow of the cooling steam (21).
- Steam turbine according to one of the preceding claims, the rotor (5) being designed as a welded hollow shaft.
- Steam turbine according to one of Claims 1 to 9, in which the rotor (5) is designed as a disc rotor (29, 30, 31) braced by means of a tie (32).
- Steam turbine according to Claim 11, in which the disc rotor (29, 30, 31) is designed with toothings (37, 38) for the transmission of a torque.
- Steam turbine according to Claim 12, the toothing (37, 38) being designed as a serration or a rectangular or trapezoidal toothing.
- Steam turbine according to Claim 11 or 12, in which the toothing (37, 38) is designed in such a way that the cooling medium (21) can flow between two adjacent disc rotors.
- Steam turbine according to Claim 14, the toothing (37, 38) having passage orifices.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP07803598A EP2078137B1 (en) | 2006-10-09 | 2007-09-25 | Rotor for a turbo-machine |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06021139A EP1911933A1 (en) | 2006-10-09 | 2006-10-09 | Rotor for a turbomachine |
EP07803598A EP2078137B1 (en) | 2006-10-09 | 2007-09-25 | Rotor for a turbo-machine |
PCT/EP2007/060141 WO2008043663A1 (en) | 2006-10-09 | 2007-09-25 | Rotor for a turbo-machine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2078137A1 EP2078137A1 (en) | 2009-07-15 |
EP2078137B1 true EP2078137B1 (en) | 2010-02-17 |
Family
ID=37872372
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06021139A Withdrawn EP1911933A1 (en) | 2006-10-09 | 2006-10-09 | Rotor for a turbomachine |
EP07803598A Not-in-force EP2078137B1 (en) | 2006-10-09 | 2007-09-25 | Rotor for a turbo-machine |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06021139A Withdrawn EP1911933A1 (en) | 2006-10-09 | 2006-10-09 | Rotor for a turbomachine |
Country Status (5)
Country | Link |
---|---|
EP (2) | EP1911933A1 (en) |
JP (1) | JP4990365B2 (en) |
AT (1) | ATE458125T1 (en) |
DE (1) | DE502007002883D1 (en) |
WO (1) | WO2008043663A1 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH699978A1 (en) | 2008-11-26 | 2010-05-31 | Alstom Technology Ltd | Steam turbine. |
ITMI20091740A1 (en) * | 2009-10-12 | 2011-04-13 | Alstom Technology Ltd | AXIAL STEAM TURBINE POWERED HIGH TEMPERATURE RADIAL |
JP6178273B2 (en) * | 2014-03-28 | 2017-08-09 | 株式会社東芝 | Steam turbine |
EP2998506A1 (en) * | 2014-09-19 | 2016-03-23 | Siemens Aktiengesellschaft | System for reducing the start-up time of a steam turbine |
CN109236378A (en) * | 2018-09-11 | 2019-01-18 | 上海发电设备成套设计研究院有限责任公司 | A kind of single stream high-temperature rotor for the high-parameter steam turbine that steam inside is cooling |
CN109236379A (en) * | 2018-09-11 | 2019-01-18 | 上海发电设备成套设计研究院有限责任公司 | A kind of double-current high-temperature rotor for the high-parameter steam turbine that steam inside is cooling |
CN109356663A (en) * | 2018-12-10 | 2019-02-19 | 上海发电设备成套设计研究院有限责任公司 | A kind of high-temperature rotor that 640 DEG C ~ 650 DEG C steam turbines inside is cooling |
JP7242597B2 (en) | 2020-03-12 | 2023-03-20 | 東芝エネルギーシステムズ株式会社 | turbine rotor |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5857007A (en) * | 1981-09-30 | 1983-04-05 | Hitachi Ltd | Nozzle diaphragm of steam turbine |
JPS63167001A (en) * | 1986-12-26 | 1988-07-11 | Fuji Electric Co Ltd | Reaction turbine |
DE4239710A1 (en) * | 1992-11-26 | 1994-06-01 | Abb Patent Gmbh | Rotor for steam turbine and current generation - comprises a welded assembly of largely pre-processed components belonging to a modular construction system standardising the rotor parts |
PL330755A1 (en) * | 1996-06-21 | 1999-05-24 | Siemens Ag | Turbine shaft as well as method of cooling same |
PT991850E (en) * | 1997-06-27 | 2002-07-31 | Siemens Ag | A STEAM TURBINE WITH INTERNAL REFRIGERATION AS A PROCESS FOR COOLING OF A TURBINE AXLE |
JPH11257007A (en) * | 1998-03-17 | 1999-09-21 | Hitachi Ltd | Steam turbine blade engaging part |
US6695582B2 (en) * | 2002-06-06 | 2004-02-24 | General Electric Company | Turbine blade wall cooling apparatus and method of fabrication |
EP1452688A1 (en) * | 2003-02-05 | 2004-09-01 | Siemens Aktiengesellschaft | Steam turbine rotor, method and use of actively cooling such a rotor |
DE10355738A1 (en) * | 2003-11-28 | 2005-06-16 | Alstom Technology Ltd | Rotor for a turbine |
EP1674669A1 (en) * | 2004-12-21 | 2006-06-28 | Siemens Aktiengesellschaft | Method of cooling a steam turbine |
-
2006
- 2006-10-09 EP EP06021139A patent/EP1911933A1/en not_active Withdrawn
-
2007
- 2007-09-25 DE DE502007002883T patent/DE502007002883D1/en active Active
- 2007-09-25 WO PCT/EP2007/060141 patent/WO2008043663A1/en active Application Filing
- 2007-09-25 AT AT07803598T patent/ATE458125T1/en active
- 2007-09-25 EP EP07803598A patent/EP2078137B1/en not_active Not-in-force
- 2007-09-25 JP JP2009530848A patent/JP4990365B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JP2010506080A (en) | 2010-02-25 |
JP4990365B2 (en) | 2012-08-01 |
WO2008043663A1 (en) | 2008-04-17 |
ATE458125T1 (en) | 2010-03-15 |
EP1911933A1 (en) | 2008-04-16 |
DE502007002883D1 (en) | 2010-04-01 |
EP2078137A1 (en) | 2009-07-15 |
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