EP2078137A1 - Rotor for a turbo-machine - Google Patents

Rotor for a turbo-machine

Info

Publication number
EP2078137A1
EP2078137A1 EP07803598A EP07803598A EP2078137A1 EP 2078137 A1 EP2078137 A1 EP 2078137A1 EP 07803598 A EP07803598 A EP 07803598A EP 07803598 A EP07803598 A EP 07803598A EP 2078137 A1 EP2078137 A1 EP 2078137A1
Authority
EP
European Patent Office
Prior art keywords
rotor
steam turbine
turbine according
designed
cooling
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.)
Granted
Application number
EP07803598A
Other languages
German (de)
French (fr)
Other versions
EP2078137B1 (en
Inventor
Kai Wieghardt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP07803598A priority Critical patent/EP2078137B1/en
Publication of EP2078137A1 publication Critical patent/EP2078137A1/en
Application granted granted Critical
Publication of EP2078137B1 publication Critical patent/EP2078137B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/08—Heating, heat-insulating or cooling means
    • F01D5/085—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor
    • 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
    • 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
    • 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
    • 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 Kuhlmedium, 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.
  • gas turbines for steam turbines has eg a turbine inflow end ⁇ working medium with the highest temperature at the same time 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.
  • a vane is usually held at a first location along an inside of the steam turbine house. It is usually part of a Blade which comprises a number of vanes arranged along an inner circumference on the inside of the steam turbine housing. 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.
  • 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 characteristic of the steam turbine rotor is that they do not have any 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.
  • Rotor through which a cooling medium can flow, carried out.
  • a disadvantage here is felt that between two ver ⁇ different expansion sections no controllable bypass can be formed from ⁇ .
  • problems in on-site 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 fürfuh ⁇ tion for carrying out external Kuhlmedium, wherein the rotor is at least partially hollow, with a Supply line for passing the external Kuhlmediums is provided in the cavity of the rotor.
  • Cooling medium is guided to a suitable location 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 immediately cools thermally stressed parts such as the thrust balance piston, is therefore improved by the cooling medium is guided by the housing in the cavity of the rotor after the passage.
  • 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 can be adjusted.
  • Steam turbines are usually used at different loads. So a steam turbine at full load operation ⁇ or Operalastbet ⁇ eb example operated.
  • the cooling requirements for the various load operations are different, so the requirement for the cooling of the steam turbine in part load operation is lower than in full load operation.
  • the invention is advantageously developed further, if the rotor is designed such that the cooling medium via rotor Cooling lines rst from the cavity rst.
  • the Kuhlmedrum first flows through external lines through the housing in the cavity of the rotor and then flows at appropriate points from the rotor back into the main flow.
  • the cooling medium flows and cools the rotor from the inside.
  • the outflow of Kuhlmediums from the rotor takes place at one or more downstream locations.
  • the cooling medium fulfills two tasks, so to speak, on the one hand, the cooling medium cools the rotor at appropriate locations and on the other, the Kuhlmedium contributes to the efficiency in which it is fed back into the main flow and performed on the guide and moving blades work.
  • the supply line is arranged in the region of a steam flow range. As a result, a suitable point for the supply line is found, since it is precisely the area of the steam inflow area which is exposed to very high thermal loads and therefore requires a preferred cooling.
  • the supply line is arranged next to a thrust balance piston.
  • 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 flow through the rotor blades.
  • This provides the advantage that in addition to the rotor and the blades can be cooled.
  • it is preferred to use the film cooling of the rotor blades known from gas turbine technology. In this way, the blade foot or can be cooled effectively at ⁇ particular thermally stressed regions of the rotor.
  • the rotor is made of disk rotors and braced with a tie rod.
  • the disk rotor is formed with a toothing for transmitting a torque.
  • the rotor made of different materials can be formed from ⁇ . It is conceivable, for example, that a disk runner, which is exposed to lower thermal loads than a disk runner, which is exposed to high thermal stress, is performed with a material which is kos ⁇ ten redesigner and yet withstand the thermal loads.
  • the toothing is designed such that the cooling medium can flow between two adjacent disk rotors.
  • the toothing is formed such that the toothing fürt ⁇ tts- openings.
  • channels can be provided in the so-called Hirth toothing. Through these channels, the cooling medium is strombar.
  • FIG. 2 shows a cross section of a rotor of a steam turbine and a part of a housing
  • 3 shows a cross section through a rotor
  • FIG. 5 shows a cross section of a toothing in an alternative embodiment.
  • FIG. 1 shows a section through a high-pressure partial turbine 1 according to the prior art.
  • the high-pressure partial turbine 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 partial turbine 1 has a flow-in region 10, through which live steam flows into the high-pressure partial turbine 1 during operation.
  • the live steam may have steam parameters above 300 bar and above 620 ° C.
  • the live steam relaxing in the flow direction 13 alternately flows past the guide vanes 8 and rotor 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 part turbine 1 may drive other plant components other than a generator, such as a compressor, a propeller, or the like.
  • the steam flows through the flow channel 9 and flows out of the high-pressure part of the turbine 1 from the outlet 33.
  • the steam in this case exerts a force action ⁇ 11 in the direction of flow.
  • FIG 2 a section of a steam turbine 1 is shown.
  • the steam turbine has a housing 39.
  • the housing 39 could be a réellegehause 3 or 2.05.gehause.
  • the steam turbine according to FIG. 2 is designed in such a way that the housing 39 has a passage 20 for the passage of 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 supply line 23 for passing through 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 by 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. For the sake of clarity, neither guide 8 nor moving blades 7 are shown in FIG.
  • 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 can be designed in such a way that the rotor 5 has blades 7, which are designed in such a way that the cooling medium 21 can flow through the blade 7. As a result, the rotor blade 7 are cooled.
  • the rotor blades 7 in this case have individual fürerieso réelleen.
  • the blades 7 are cooled by the so-called film cooling.
  • the film cooling is known from gas turbine technology.
  • the rotor 5 is formed such that the blade root, the balance piston 4 or other kriti ⁇ cal areas that are thermally loaded, are cool.
  • the m rotor 2 shown m FIG 2 is welded to a weld 26 of two sub-rotors 27, 28.
  • a rotor is shown, which is constructed from three disk rotors 29, 30, 31.
  • the rotor may in alternative forms Ausfuh approximately ⁇ are remote from only two Scheibenlau-. 5
  • the three disk runners 29, 30, 31 are clamped firmly together by means of a tie rod 32.
  • the tie rod at its ends a thread 34.
  • a movement of the tie rod 32 takes place in the rotation axis direction, which leads to the fact that the three disc rotors 29, 30, 31 are printed together.
  • the disk runners 29, 30, 31 at their points of contact 35, 36 have a toothing for transmitting a torque.
  • the toothing can be designed as a Hirth, rectangular or trapezoidal toothing.
  • 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 strombar.
  • FIG. 5 shows an alternative embodiment of a toothing 37, 38 is shown.
  • the toothing 38 shown in FIG. 5 is designed as a trapezoid toothing 38.
  • the trapezoidal toothing 38 is designed in such a way that supply lines 23 are formed, through which the cooling medium 21 can flow.

Abstract

The turbine (1) has a housing (39) provided with a feedthrough (20) for feeding an external cooling agent (21), and a rotor (5) that is partly formed in a hollow shape. The rotor includes a supply line (23) for feeding the external cooling agent into a hollow space (22) of the rotor via rotor cooling lines (24). The supply line is arranged adjacent to a balance piston (4). The rotor includes rotor blades allowing the flow of the cooling agent. The rotor blades are cooled by film cooling.

Description

Beschreibungdescription
Rotor für eine StromungsmaschineRotor for a flow machine
Die Erfindung betrifft eine Dampfturbine umfassend ein Gehäuse und einen Rotor, wobei das Gehäuse eine Durchfuhrung zum Durchfuhren von externem Kuhlmedium 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 Kuhlmedium, wherein the rotor is at least partially hollow.
Zur Steigerung des Wirkungsgrades einer Dampfturbine tragt die Verwendung von Dampf mit höheren Drucken 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 contributes to higher pressures and temperatures. 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 zustromende Arbeits¬ medium mit der höchsten Temperatur gleichzeitig den höchsten Druck auf. Ein offenes Kuhlsystem, wie bei Gasturbinen, ist also nicht ohne externe Zufuhrung realisierbar. Eine Dampfturbine umfasst üblicherweise einen mit Schaufeln besetzten drehbar gelagerten Rotor, der innerhalb eines Gehausemantels angeordnet ist. Bei Durchstromung des vom Gehausemantel ge- bildeten Stromungsraumes 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 Gehausemantel sind darüber hinaus üblicherweise stationäre Leitschau- fein angebracht, welche in die Zwischenräume der Laufschau¬ feln greifen. Eine Leitschaufel ist üblicherweise an einer ersten Stelle entlang einer Innenseite des Dampfturbinenge- hauses gehalten. Dabei ist sie üblicherweise Teil eines Leit- schaufelkranzes, welcher eine Anzahl von Leitschaufeln um- fasst, die entlang eines Innenumfangs an der Innenseite des Dampfturbinengehauses angeordnet sind. Dabei weist jede Leitschaufel mit ihrem Schaufelblatt radial nach innen. Ein Leit- schaufelkranz 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 for steam turbines has eg a turbine inflow end ¬ working medium with the highest temperature at the same time 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 the flow space formed by the housing jacket is passed through 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. On Gehausemantel also stationary Leitschau- are usually fine attached, which engage in the spaces between the Laufschau ¬ blades. A vane is usually held at a first location along an inside of the steam turbine house. It is usually part of a Blade which comprises a number of vanes arranged along an inner circumference on the inside of the steam turbine housing. 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 Kuhlmittelmetho¬ den zur Kühlung eines Dampfturbmengehauses 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 Arbeitsme- dium zugefuhrtes Kuhlmedium bewirkt. Dagegen erfolgt eine passive Kühlung lediglich durch eine geeignete Fuhrung oder Verwendung des Arbeitsmediums. Eine bekannte Kühlung eines Dampfturbmengehauses beschrankt sich auf eine passive Küh¬ lung. So ist beispielsweise bekannt, ein Innengehause einer Dampfturbine mit kühlem, bereits expandiertem Dampf zu umströmen. Dies hat jedoch den Nachteil, dass eine Temperaturdifferenz über die Innengehausewandung beschrankt bleiben muss, da sich sonst bei einer zu großen Temperaturdifferenz das Innengehause thermisch zu stark verformen wurde. Bei einer Umstromung des Innengehauses findet zwar eine Warmeab- fuhr statt, jedoch erfolgt die Warmeabfuhr relativ weit entfernt von der Stelle der Wärmezufuhr. Eine Warmeabfuhr in un¬ mittelbarer Nahe der Wärmezufuhr ist bisher nicht in ausreichendem Maße verwirklicht worden. Eine weitere passive Kuh- lung kann mittels einer geeigneten Gestaltung der Expansion des Arbeitsmediums in einer so genannten Diagonalstufe er¬ reicht werden. Hierüber lasst sich allerdings nur eine sehr begrenzte Kuhlwirkung auf das Gehäuse erzielen.An essential role in increasing the efficiency plays the cooling. In the previously known Kuhlmittelmetho ¬ the cooling of a Dampfturbmengehauses is to distinguish between an active cooling and a passive cooling. In the case of active cooling, cooling is effected separately by means of a steam turbine, ie 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 Dampfturbmengehauses limited to a passive Küh ¬ ment. For example, it is known to flow around an interior of a steam turbine with cool, already expanded steam. However, this has the disadvantage that a temperature difference on the Innengehausewandung must remain limited, otherwise the inner housing would thermally deform too much at too large a temperature difference. Although a heat dissipation takes place when the inner casing flows around, the heat removal takes place relatively far away from the point of heat supply. A heat dissipation in un ¬ indirect near the heat has not been sufficiently achieved. Another passive cow lung, by means of a suitable design of the expansion of the working medium in a so-called diagonal stage he ¬ be sufficient. However, this can only be achieved 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 zeitaufwandig. 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 Warmesenke verfugen. Daher gestaltet sich die Kühlung der an dem Dampfturbinenrotor angeordneten Laufschaufeln als schwierig.A characteristic of the steam turbine rotor is that they do not have any significant heat sink. Therefore, the cooling of the blades arranged on the steam turbine rotor is difficult.
Besonders thermisch belastet werden bei den Dampfturbinen¬ rotoren die Kolben- und Einstrombereiche. 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.Particularly thermally loaded in the steam turbine ¬ rotors, the piston and inflow areas. 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 ist in der EP 0 991 850 Bl beschrieben. Dabei wird eine Kompakt- bzw. Hochdruck- und Mitteldruck-Teilturbme durch eine Verbindung in demA cooling of a steam turbine rotor is described in EP 0 991 850 Bl. Here is a compact or high pressure and medium pressure Teilturbme by a compound in the
Rotor, durch die ein Kuhlmedium strömen kann, ausgeführt. Als nachteilig wird hierbei empfunden, dass zwischen zwei ver¬ schiedenen Expansionsabschnitten kein regelbarer Bypass aus¬ gebildet werden kann. Darüber hinaus sind Probleme im insta- tionaren Betrieb möglich.Rotor, through which a cooling medium can flow, carried out. A disadvantage here is felt that between two ver ¬ different expansion sections no controllable bypass can be formed from ¬ . In addition, problems in on-site operation are possible.
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.
Gelost wird diese Aufgabe durch eine Dampfturbine, umfassend ein Gehäuse und einen Rotor, wobei das Gehäuse eine Durchfuh¬ rung zum Durchfuhren von externem Kuhlmedium aufweist, wobei der Rotor zumindest teilweise hohl ausgeführt ist, wobei eine Zuleitung zum Durchfuhren des externen Kuhlmediums in den Hohlraum des Rotors vorgesehen ist.This object is achieved by a steam turbine, comprising a housing and a rotor, wherein the housing has a Durchfuh ¬ tion for carrying out external Kuhlmedium, wherein the rotor is at least partially hollow, with a Supply line for passing the external Kuhlmediums is provided in the cavity of the rotor.
Mit der Erfindung wird daher vorgeschlagen, externes Kuhlme- dium in den Rotor der Dampfturbine zuzuführen, wobei dasWith the invention it is therefore proposed to supply external cooling medium into the rotor of the steam turbine, wherein the
Kuhlmedium an eine geeignete Stelle des Rotors gefuhrt wird. Hierbei wird als geeignete Stelle der Hohlraum verwendet. Der Hohlraum ist zweckmaßigerweise an den Stellen angebracht, die einer hohen thermischen Belastung ausgesetzt sind.Cooling medium is guided to a suitable location 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 Kuhlmedium in die Dampfturbine eingeströmt wird und thermisch belastete Teile wie den Schubausgleichskolben unmittelbar kühlt, wird demnach verbessert, indem das Kuhlmedium nach der Durchfuh- rung durch das Gehäuse in den Hohlraum des Rotors gefuhrt wird. Dazu muss der Kuhldampf einen höheren Druck als an der Einströmung aufweisen, damit dieser in den Hohlraum gefuhrt werden kann.The hitherto known method, in which the external cooling medium is flowed into the steam turbine and immediately cools thermally stressed parts such as the thrust balance piston, is therefore improved by the cooling medium is guided by the housing in the cavity of the rotor after the passage. For this, the cooling steam must have a higher pressure than at the inflow, so that it can be guided into the cavity.
Ein Vorteil dieses erfmdungsgemaßen Kuhlprinzips ist es, dass die Temperatur des Kuhlmediums einstellbar ist. Dampfturbinen werden in der Regel bei unterschiedlichen Lasten verwendet. So wird beispielsweise eine Dampfturbine im Voll¬ lastbetrieb oder im Teillastbetπeb betrieben. Die Kuhlanfor- derungen für die verschiedenen Lastbetriebe sind unterschiedlich, so ist die Anforderung an die Kühlung der Dampfturbine im Teillastbetπeb geringer als beim Volllastbetrieb.An advantage of this cooling principle according to the invention is that the temperature of the cooling medium can be adjusted. Steam turbines are usually used at different loads. So a steam turbine at full load operation ¬ or Teillastbetπeb example operated. The cooling requirements for the various load operations are different, so the requirement for the cooling of the steam turbine in part load operation is lower than in full load operation.
Im Volllastbetrieb wird daher mehr Kuhlmedium bzw. eine nied- rigere Temperatur des Kuhlmediums gefordert, was erfindungs- gemaß ohne weiteres möglich ist, da die Temperatur des Kuhl¬ mediums leicht geregelt werden kann.Therefore at full load more cooling medium or a nied- challenging temperature of Kuhlmediums is required, which is inventiveness PURSUANT easily possible, since the temperature of Kuhl ¬ medium can be easily controlled.
Vorteilhafte Weiterbildungen sind in den Unteranspruchen dar- gestellt.Advantageous developments are set forth in the subclaims.
So wird die Erfindung vorteilhaft weitergebildet, wenn der Rotor derart ausgebildet ist, dass das Kuhlmedium über Rotor- kuhlleitungen aus dem Hohlraum strombar rst. Das Kuhlmedrum 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 Hauptstromung . Dabei be- strömt und kühlt das Kuhlmedium den Rotor von innen. Das Ausstromen des Kuhlmediums aus dem Rotor erfolgt an einer oder mehreren stromab gelegenen Stellen.Thus, the invention is advantageously developed further, if the rotor is designed such that the cooling medium via rotor Cooling lines rst from the cavity rst. The Kuhlmedrum first flows through external lines through the housing in the cavity of the rotor and then flows at appropriate points from the rotor back into the main flow. The cooling medium flows and cools the rotor from the inside. The outflow of Kuhlmediums from the rotor takes place at one or more downstream locations.
Durch diese Maßnahme erfüllt das Kuhlmedium sozusagen zwei Aufgaben, zum einen kühlt das Kuhlmedium den Rotor an geeigneten Stellen und zum anderen tragt das Kuhlmedium zum Wirkungsgrad bei, in dem es der Hauptstromung 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 appropriate locations and on the other, the Kuhlmedium contributes to the efficiency in which it is fed back into the main flow and performed on the guide and moving blades work.
In einer vorteilhaften Weiterbildung ist die Zuleitung im Bereich eines Dampfemstrombereiches angeordnet. Dadurch ist eine geeignete Stelle für die Zuleitung gefunden, da gerade der Bereich des Dampfeinstrombereiches sehr hohen thermischen Belastungen ausgesetzt ist und daher einer bevorzugten Kuh- lung bedarf.In an advantageous development, the supply line is arranged in the region of a steam flow range. As a result, a suitable point for the supply line is found, since it is precisely the area of the steam inflow area which 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 Kuhlmedium, bevor es in den Hohlraum des Rotors gefuhrt 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. As a result, it is 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 Lauf- schaufeln auf, die derart ausgebildet sind, dass das Kuhlmedium durch die Laufschaufeln strombar ist. Dadurch wird der Vorteil erzielt, dass neben dem Rotor auch die Laufschaufeln gekühlt werden können. Dabei wird bevorzugt die aus der Gas- turbmentechnologie bekannte Filmkuhlung der Laufschaufeln verwendet. Auf diese Weise können auch Schaufelfuße oder an¬ dere thermisch belastete Bereiche des Rotors wirksam gekühlt werden. In einer vorteilhaften Weiterbildung ist der Rotor aus Schei- benlaufern ausgeführt und mit einem Zuganker verspannt.In an advantageous development, the rotor has rotor blades which are designed such that the cooling medium can flow through the rotor blades. This provides the advantage that in addition to the rotor and the blades can be cooled. In this case, it is preferred to use the film cooling of the rotor blades known from gas turbine technology. In this way, the blade foot or can be cooled effectively at ¬ particular thermally stressed regions of the rotor. In an advantageous development, the rotor is made of disk rotors and braced with a tie rod.
Ebenso vorteilhaft ist es, wenn der Scheibenlaufer mit einer Verzahnung zum Übertragen eines Drehmomentes ausgebildet ist. Dadurch kann der Rotor aus unterschiedlichen Materialien aus¬ gebildet werden. Denkbar ist beispielsweise, dass ein Schei- benlaufer, der geringeren thermischen Belastungen ausgesetzt ist als ein Scheibenlaufer, der hohen thermischen Belastung ausgesetzt ist, mit einem Material ausgeführt wird, das kos¬ tengünstiger ist und dennoch den thermischen Belastungen standhalt .It is equally advantageous if the disk rotor is formed with a toothing for transmitting a torque. Thereby, the rotor made of different materials can be formed from ¬. It is conceivable, for example, that a disk runner, which is exposed to lower thermal loads than a disk runner, which is exposed to high thermal stress, is performed with a material which is kos ¬ tengünstiger and yet withstand the thermal loads.
In einer weiteren vorteilhaften Weiterbildung ist die Verzah- nung derart ausgebildet, dass das Kuhlmedium zwischen zwei benachbarten Scheibenlaufern strombar ist. Dazu wird die Verzahnung derart ausgebildet, dass die Verzahnung Durchtπtts- offnungen aufweist. Beispielsweise können Kanäle in der so genannten Hirthverzahnung vorgesehen sein. Durch diese Kanäle ist das Kuhlmedium strombar. Diese Ausfuhrungsform bietet den Vorteil, dass für die Durchfuhrung des Kuhlmediums über Radi- alkanale keine zusätzlichen Bohrungen ausgeführt werden müs¬ sen, zusätzliche Bohrungen im Rotor verursachen eine hohe Spannungskonzentration durch zusätzliche Kerben. Solche Span- nungskonzentrationen entfallen, wenn das Kuhlmedium durch die Verzahnung gefuhrt wird.In a further advantageous development, the toothing is designed such that the cooling medium can flow between two adjacent disk rotors. For this purpose, the toothing is formed such that the toothing Durchtπtts- openings. For example, channels can be provided in the so-called Hirth toothing. Through these channels, the cooling medium is strombar. This embodiment offers the advantage that, for the execution of the Kuhlmediums alkanals about radi- no additional holes are performed Müs ¬ sen, additional holes in the rotor cause a high stress concentration through additional notches. Such stress concentrations are eliminated if the cooling medium is guided through the toothing.
Ausfuhrungsbeispiele der Erfindung werden anhand der nachfolgenden Zeichnungen naher erläutert. Dabei haben Komponenten mit den gleichen Bezugszeichen die gleiche Funktionsweise.Exemplary 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:Show it:
FIG 1 ein Querschnitt einer Dampfturbine gemäß dem Stand der Technik,1 shows a cross section of a steam turbine according to the prior art,
FIG 2 ein Querschnitt eines Rotors einer Dampfturbine und eines Teils eines Gehäuses, FIG 3 Querschnitt durch einen Rotor,2 shows a cross section of a rotor of a steam turbine and a part of a housing, 3 shows a cross section through a rotor,
FIG 4 Querschnitt durch eine Verzahnung,4 cross section through a toothing,
FIG 5 Querschnitt einer Verzahnung in alternativer Ausfuhrungsform.5 shows a cross section of a toothing in an alternative embodiment.
In der FIG 1 ist ein Schnitt durch eine Hochdruck-Teilturbme 1 gemäß dem Stand der Technik dargestellt. Die Hochdruck- Teilturbme 1 als Ausfuhrungsform einer Dampfturbine umfasst ein Außengehause 2 und ein darin angeordnetes Innengehause 3. Innerhalb des Innengehauses 3 ist ein Rotor 5 um eine Rotati- onsachse 6 drehbar gelagert. Der Rotor 5 umfasst in Nuten auf einer Oberflache des Rotors 5 angeordnete Laufschaufeln 7. Das Innengehause 3 weist an seiner Innenflache in Nuten angeordnete Leitschaufeln 8 auf. Die Leit- 8 und Laufschaufeln 7 sind derart angeordnet, dass in einer Stromungsrichtung 13 ein Stromungskanal 9 ausgebildet ist. Die Hochdruck-Teilturbme 1 weist einen Einstrombereich 10 auf, durch den im Betrieb Frischdampf in die Hochdruck-Teilturbme 1 einströmt. Der Frischdampf kann Dampfparameter von über 300 bar und über 620°C aufweisen. Der in die Stromungsrichtung 13 sich ent- spannende Frischdampf strömt abwechselnd an den Leit- 8 und Laufschaufeln 7 vorbei, entspannt und kühlt sich ab. Der Dampf verliert hierbei an innerer Energie, der in Rotations¬ energie des Rotors 5 umgewandelt wird. Die Rotation des Rotors 5 treibt schließlich einen nicht dargestellten Genera- tor zur Energieversorgung an. Die Hochdruck-Teilturbme 1 kann selbstverständlich andere Anlagenkomponenten außer einem Generator antreiben, beispielsweise einen Verdichter, eine Schiffschraube oder ähnliches. Der Dampf durchströmt den Stromungskanal 9 und strömt aus der Hochdruck-Teilturbme 1 aus dem Auslass 33 aus. Der Dampf übt hierbei eine Aktions¬ kraft 11 in Stromungsrichtung 13 aus. Die Folge ist, dass der Rotor 5 eine Bewegung in Stromungsrichtung 13 vollziehen wurde. Eine tatsächliche Bewegung des Rotors 5 wird durch einen Ausgleichskolben 4 verhindert. Dies geschieht, indem in einem Ausgleichskolbenvorraum 12 Dampf mit entsprechendem Druck eingeströmt wird, der dazu fuhrt, dass in Folge des sich aufbauenden Druckes im Ausgleichskolbenvorraum 12 eine Kraft entgegen der Stromungsrichtung 13 entsteht, die idealer Weise genau so groß sein sollte wie die Aktionskraft 11. Der in dem Ausgleichskolbenvorraum 12 eingeströmte Dampf ist in der Regel abgezweigter Frischdampf, der sehr hohe Temperaturparameter aufweist. Demzufolge werden der Einstrombereich 10 und der Ausgleichskolben 4 des Rotors 5 thermisch stark beansprucht .FIG. 1 shows a section through a high-pressure partial turbine 1 according to the prior art. The high-pressure partial turbine 1 as an embodiment of a steam turbine comprises an outer housing 2 and an inner housing 3 arranged therein. Within the inner housing 3, 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 partial turbine 1 has a flow-in region 10, through which live steam flows into the high-pressure partial turbine 1 during operation. The live steam may have steam parameters above 300 bar and above 620 ° C. The live steam relaxing in the flow direction 13 alternately flows past the guide vanes 8 and rotor 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. Of course, the high pressure part turbine 1 may drive other plant components other than a generator, such as a compressor, a propeller, or the like. The steam flows through the flow channel 9 and flows out of the high-pressure part of the turbine 1 from the outlet 33. The steam in this case exerts a force action ¬ 11 in the direction of flow. 13 The result is that the rotor 5 has completed a movement in the direction of flow 13. An actual movement of the rotor 5 is through prevents a balance piston 4. This is done by 12 steam is flowed in a Ausgleichskolbenvorraum with a corresponding pressure, which leads to the fact that a force against the flow direction 13 arises due to the building up pressure in Ausgleichskolbenvorraum 12, which should ideally be exactly as large as the action force 11th The steam which has flowed into the compensating piston antechamber 12 is generally diverted live steam, which has very high temperature parameters. As a result, the inflow region 10 and the compensation piston 4 of the rotor 5 are subject to high thermal stress.
In der FIG 2 ist ein Ausschnitt einer Dampfturbine 1 dargestellt. Die Dampfturbine weist ein Gehäuse 39 auf. Der Uber- sichtigkeit wegen ist lediglich ein Teil des Gehäuses 39 in der FIG 2 dargestellt. Das Gehäuse 39 konnte ein Innengehause 3 oder ein Außengehause 2 sein.In FIG 2, a section of a steam turbine 1 is shown. The steam turbine has a housing 39. For the sake of clarity, only part of the housing 39 is shown in FIG. The housing 39 could be a Innengehause 3 or 2 Außengehause.
Die Dampfturbine gemäß FIG 2 wird erfmdungsgemaß derart aus- gefuhrt, dass das Gehäuse 39 eine Durchfuhrung 20 zum Durchfuhren von externem Kuhlmedium 21 aufweist. Der Rotor 5 wird hierbei zumindest teilweise hohl ausgeführt. Der Rotor 5 weist daher einen Hohlraum 22 auf. Der Rotor 5 weist eine Zu¬ leitung 23 zum Durchfuhren des externen Kuhlmediums 21 auf. Das Kuhlmedium 21 wird über die Durchfuhrung 20 und der Zuleitung 23 in den Hohlraum 22 gefuhrt. Eine erste Kuhlwirkung des Kuhlmediums 21 wird bereits im Gehäuse 39 im Bereich der Durchfuhrung 20 erreicht. Zweckmaßigerweise ist die Durchfuhrung 20 in der Nahe des Einstrombereiches 10 angeordnet. Der Einstrombereich 10 ist besonders thermisch belastet, da dort der Frischdampf einströmt. Das Kuhlmedium wird von der Durchfuhrung 20 zur Zuleitung 23 gefuhrt und in den Hohlraum 22 geströmt. Das Kuhlmedium 21 muss hierbei einen entsprechenden Druck aufweisen.According to the invention, the steam turbine according to FIG. 2 is designed in such a way that the housing 39 has a passage 20 for the passage of 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 supply line 23 for passing through 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. Expediently, 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 by 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.
Die Zuleitung 23 kann durch radiale Bohrungen erfolgen. Andere Ausfuhrungsformen wie z.B. schräg verlaufende Zuleitungen sind denkbar. Der Übersichtlichkeit wegen sind in der FIG 2 weder Leit- 8 noch Laufschaufeln 7 dargestellt. Der Rotor 5 ist derart ausgebildet, dass das Kuhlmedium 21 über Rotorkuhlleitungen 24 aus dem Hohlraum 22 strombar ist.The supply line 23 can be made by radial bores. Other embodiments such as inclined leads are conceivable. For the sake of clarity, neither guide 8 nor moving blades 7 are shown in FIG. The rotor 5 is designed such that the cooling medium 21 can be flowed out of the cavity 22 via rotor cooling lines 24.
Die Zuleitung 23 kann neben einem Ausgleichskolben 4 angeordnet werden. Da der Ausgleichskolben besonders thermisch belastet ist wäre dies eine vorteilhafte Ausfuhrungsform.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.
Das aus den Rotorkuhlleitung 24 ausströmende Kuhlmedium 21 vermischt sich mit dem aus dem Einstrombereich 10 kommenden Arbeitsmedium, das in der Regel ein Dampf ist. Das Kuhlmedium 21 kühlt unter anderem ab der Zuleitung 23 den Rotor 5 an einer Innenflache 25 des Hohlraums 22.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
Die Dampfturbine 1 kann derart ausgebildet sein, dass der Rotor 5 Laufschaufeln 7 aufweist, die derart ausgebildet sind, dass das Kuhlmedium 21 durch die Laufschaufel 7 strom- bar ist. Dadurch werden die Laufschaufei 7 gekühlt. Die Lauf- schaufeln 7 weisen hierbei einzelne Durchtrittsoffnungen auf. Die Laufschaufeln 7 werden durch die so genannte Filmkuhlung gekühlt. Die Filmkuhlung ist aus der Gasturbinentechnologie bekannt .The steam turbine 1 can be designed in such a way that the rotor 5 has blades 7, which are designed in such a way that the cooling medium 21 can flow through the blade 7. As a result, the rotor blade 7 are cooled. The rotor blades 7 in this case have individual Durchtrittsoffnungen. The blades 7 are cooled by the so-called film cooling. The film cooling is known from gas turbine technology.
Vorzugsweise ist der Rotor 5 derart ausgebildet, dass die Laufschaufelfuße, der Ausgleichskolben 4 oder andere kriti¬ sche Bereiche, die thermisch belastet sind, kuhlbar sind.Preferably, the rotor 5 is formed such that the blade root, the balance piston 4 or other kriti ¬ cal areas that are thermally loaded, are cool.
Der m FIG 2 dargestellte Rotor 5 ist an einer Schweißnaht 26 aus zwei Teilrotoren 27, 28 verschweißt. Dies bietet den Vor¬ teil, dass der erste Teilrotor 27, der thermisch besonders belastet ist, aus einem anderen thermisch belastbaren Material ausgeführt werden kann als der Teilrotor 28. Selbstver- standlich kann der Rotor 5 aus einem einheitlichen Material, d.h. ohne eine Schweißnaht 26 ausgeführt werden. In der FIG 3 ist ein Rotor dargestellt, der aus drei Schei- benlaufern 29, 30, 31 aufgebaut ist. In alternativen Ausfuh¬ rungsformen kann der Rotor 5 aus lediglich zwei Scheibenlau- fern ausgeführt werden. Die drei Scheibenlaufer 29, 30, 31 werden mittels eines Zugankers 32 fest miteinander verspannt. Dazu weist der Zuganker an seinen Enden ein Gewinde 34 auf. Durch Drehen des Zugankers 32 erfolgt eine Bewegung des Zugankers 32 in Rotationsachsenrichtung, was dazu fuhrt, dass die drei Scheibenlaufer 29, 30, 31 zusammengedruckt werden. Zweckmaßigerweise weisen die Scheibenlaufer 29, 30, 31 an ihren Beruhrungsstellen 35, 36 eine Verzahnung zum Übertragen eines Drehmomentes auf. Die Verzahnung kann als Hirth-, Rechteck- oder Trapezverzahnung ausgebildet sein.The m rotor 2 shown m FIG 2 is welded to a weld 26 of two sub-rotors 27, 28. This offers the Prior ¬ part, that the first part of the rotor 27, which is thermally particular pressure can be made of other thermally resilient material than the part of rotor 28 Selbstver- standlich, the rotor 5 of a uniform material, ie, without a welded seam 26 be executed. In FIG. 3, a rotor is shown, which is constructed from three disk rotors 29, 30, 31. The rotor may in alternative forms Ausfuh approximately ¬ are remote from only two Scheibenlau-. 5 The three disk runners 29, 30, 31 are clamped firmly together by means of a tie rod 32. For this purpose, the tie rod at its ends a thread 34. By turning the tie rod 32, a movement of the tie rod 32 takes place in the rotation axis direction, which leads to the fact that the three disc rotors 29, 30, 31 are printed together. Expediently, the disk runners 29, 30, 31 at their points of contact 35, 36 have a toothing for transmitting a torque. The toothing can be designed as a Hirth, rectangular or trapezoidal toothing.
In der FIG 4 ist eine erste Ausfuhrungsform einer Verzahnung 37, 38 dargestellt. Die Verzahnung 37, 38 ist als Dreiecksverzahnung 37 ausgeführt. Die Verzahnung 37 ist dabei derart ausgeführt, dass eine Zuleitung 23 ausgebildet ist. Durch die Zuleitung 23 ist das Kuhlmedium 21 strombar.4 shows 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 strombar.
In der FIG 5 ist eine alternative Ausfuhrungsform einer Verzahnung 37, 38 dargestellt. Die in der FIG 5 dargestellte Verzahnung 38 ist als eine Trapezverzahnung 38 ausgebildet. Dabei ist die Trapezverzahnung 38 derart ausgeführt, dass Zu- leitungen 23 ausgebildet sind, durch die das Kuhlmedium 21 strombar ist. 5 shows an alternative embodiment of a toothing 37, 38 is shown. The toothing 38 shown in FIG. 5 is designed as a trapezoid toothing 38. In this case, the trapezoidal toothing 38 is designed in such a way that supply lines 23 are formed, through which the cooling medium 21 can flow.

Claims

Patentansprüche claims
1. Dampfturbine, umfassend ein Gehäuse (2, 3, 39) und einen Rotor (5), wobei das Gehäuse (2, 3, 39) eine Durchfuhrung (20) zum Durchfuhren von externem Kuhlmedium (21) aufweist, wobei der Rotor (5) zumindest teilweise hohl ausgeführt ist, dadurch gekennzeichnet, dass der Rotor (5) eine Zuleitung (23) zum Durchfuhren des externen Kuhlmediums (21) in den Hohlraum (22) des Rotors (5) aufweist .A steam turbine, comprising a housing (2, 3, 39) and a rotor (5), wherein the housing (2, 3, 39) has a passage (20) for the passage of external Kuhlmedium (21), wherein the rotor ( 5) is at least partially hollow, characterized in that the rotor (5) has a feed line (23) for passing the external Kuhlmediums (21) into the cavity (22) of the rotor (5).
2. Dampfturbine nach Anspruch 1, wobei der Rotor (5) derart ausgebildet ist, dass das Kuhlmedium (21) über Rotorkuhlleitungen (24) aus dem Hohlraum (22) strombar ist.2. Steam turbine according to claim 1, wherein the rotor (5) is designed such that the Kuhlmedium (21) via rotor cooling lines (24) from the cavity (22) is strombar.
3. Dampfturbine nach Anspruch 1 oder 2, bei der die Zuleitung (23) im Bereich eines Emstromberei- ches (10) angeordnet ist.3. Steam turbine according to claim 1 or 2, wherein the supply line (23) in the region of an Emstromberei- ches (10) is arranged.
4. Dampfturbine nach Anspruch 1, 2 oder 3, bei der die Zuleitung (23) neben einem Ausgleichskolben (4) angeordnet ist.4. Steam turbine according to claim 1, 2 or 3, wherein the supply line (23) next to a compensating piston (4) is arranged.
5. Dampfturbine nach einem der vorhergehenden Ansprüche, bei der das aus dem Rotor (5) im Betrieb ausströmende Kuhlmedium (21) mit einem Stromungsmedium vermischbar ist.5. Steam turbine according to one of the preceding claims, wherein the effluent from the rotor (5) during operation Kuhlmedium (21) is mixable with a flow medium.
6. Dampfturbine nach einem der vorhergehenden Ansprüche, bei der der Rotor (5) Laufschaufeln (7) aufweist, die derart ausgebildet sind, dass das Kuhlmedium (21) durch die Laufschaufeln (7) strom- bar ist. 6. Steam turbine according to one of the preceding claims, wherein the rotor (5) comprises blades (7) which are formed such that the cooling medium (21) by the rotor blades (7) is current bar.
7. Dampfturbine nach Anspruch 6, bei der die Laufschaufeln (7) mittels Filmkuhlung kuhlbar sind.7. Steam turbine according to claim 6, wherein the blades (7) are coolable by means of film cooling.
8. Dampfturbine nach einem der vorhergehenden Ansprüche, wobei der Rotor (5) derart ausgebildet ist, dass Laufschaufelfuße, der Schubausgleichskolben (4) oder andere thermisch belastete Bereiche des Rotors (5) kuhlbar sind.8. Steam turbine according to one of the preceding claims, wherein the rotor (5) is designed such that the blade root, the thrust balance piston (4) or other thermally loaded areas of the rotor (5) are coolable.
9. Dampfturbine nach einem der vorhergehenden Ansprüche, wobei der Rotor (5) Austrittsoffnungen zum radialen Austreten des Kuhldampfes (21) aufweist.9. Steam turbine according to one of the preceding claims, wherein the rotor (5) Austrittsoffnungen for the radial leakage of Kuhldampfes (21).
10. Dampfturbine nach einem der vorhergehenden Ansprüche, wobei der Rotor (5) als verschweißte Hohlwelle ausgeführt ist.10. Steam turbine according to one of the preceding claims, wherein the rotor (5) is designed as a welded hollow shaft.
11. Dampfturbine nach einem der Ansprüche 1 bis 9, bei dem der Rotor (5) als ein mit einem Zuganker (32) verspannter Scheibenlaufer (29, 30, 31) ausgeführt ist.11. Steam turbine according to one of claims 1 to 9, wherein the rotor (5) is designed as a with a tie rod (32) braced disc rotor (29, 30, 31).
12. Dampfturbine nach Anspruch 11, bei dem die Scheibenlaufer (29, 30, 31) mit Verzahnungen (37,38) zum Übertragen eines Drehmomentes ausgebildet sind.12. Steam turbine according to claim 11, wherein the disc rotors (29, 30, 31) are formed with toothings (37, 38) for transmitting a torque.
13. Dampfturbine nach Anspruch 12, wobei die Verzahnung (37, 38) als Hirth-, Rechteck- oder Trapezverzahnung ausgebildet ist.13. Steam turbine according to claim 12, wherein the toothing (37, 38) is designed as Hirth, rectangular or trapezoidal toothing.
14. Dampfturbine nach Anspruch 11 oder 12, bei der die Verzahnung (37, 38) derart ausgebildet ist, dass das Kuhlmedium (21) zwischen zwei benachbarten Schei- benlaufern strombar ist.14. Steam turbine according to claim 11 or 12, wherein the toothing (37, 38) is designed such that the cooling medium (21) between two adjacent disk runners is strombar.
15. Dampfturbine nach Anspruch 14, wobei die Verzahnung (37, 38) Durchtrittsoffnungen aufweist 15. Steam turbine according to claim 14, wherein the toothing (37, 38) has Durchtrittsoffnungen
EP07803598A 2006-10-09 2007-09-25 Rotor for a turbo-machine Not-in-force EP2078137B1 (en)

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EP07803598A EP2078137B1 (en) 2006-10-09 2007-09-25 Rotor for a turbo-machine

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EP06021139A EP1911933A1 (en) 2006-10-09 2006-10-09 Rotor for a turbomachine
PCT/EP2007/060141 WO2008043663A1 (en) 2006-10-09 2007-09-25 Rotor for a turbo-machine
EP07803598A EP2078137B1 (en) 2006-10-09 2007-09-25 Rotor for a turbo-machine

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EP2078137B1 EP2078137B1 (en) 2010-02-17

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EP1911933A1 (en) 2008-04-16
ATE458125T1 (en) 2010-03-15
JP4990365B2 (en) 2012-08-01
DE502007002883D1 (en) 2010-04-01
EP2078137B1 (en) 2010-02-17
JP2010506080A (en) 2010-02-25

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