EP1945911B1 - Steam turbine - Google Patents
Steam turbine Download PDFInfo
- Publication number
- EP1945911B1 EP1945911B1 EP06819128A EP06819128A EP1945911B1 EP 1945911 B1 EP1945911 B1 EP 1945911B1 EP 06819128 A EP06819128 A EP 06819128A EP 06819128 A EP06819128 A EP 06819128A EP 1945911 B1 EP1945911 B1 EP 1945911B1
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- EP
- European Patent Office
- Prior art keywords
- steam
- turbine
- line
- steam turbine
- 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.)
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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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/12—Cooling
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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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
- F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
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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 having a housing, wherein a turbine shaft having a thrust balance piston rotatably mounted within the housing and directed along a rotation axis, wherein a flow channel between the housing and the turbine shaft is formed, wherein the turbine shaft in its interior a cooling pipe for guiding Has cooling steam in the direction of the axis of rotation and the cooling line is connected to at least one inflow line for the inflow of cooling steam from the flow channel in the cooling line.
- 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 the working medium, which, however, is subject to completely different temperature and pressure conditions than the steam in a steam turbine.
- gas turbines has steam turbines z. As the one part turbine incoming working fluid 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 flowing through the flow space formed by the housing jacket with heated and pressurized steam, the rotor passes through the blades set the steam in rotation.
- 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. In this case, it is usually part of a vane ring, which comprises a number of vanes, which are 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 number of vane rows are arranged one behind the other.
- the steam turbine shafts which are rotatably mounted in the steam turbines, are subjected to a great deal of thermal stress during operation.
- the development and production of a steam turbine shaft is both expensive and time consuming.
- Steam turbine shafts are considered to be the most stressed and expensive components of a steam turbine. This increasingly applies to high steam temperatures.
- steam turbines in contrast to the gas turbine, have no compressor unit and, moreover, the shafts of the steam turbine are generally accessible only radially.
- 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 caused by the working fluid force the shaft is formed in one direction a counter force in the opposite direction.
- a cooling of a steam turbine shaft is inter alia in the EP 0 991 850 B1 described.
- a compact or high-pressure and medium-pressure turbine part is performed by a compound in the shaft through which a cooling medium can flow.
- a disadvantage here is felt that between two different expansion sections 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 with a housing, wherein a turbine piston having a thrust balance piston rotatably mounted within the housing and directed along a rotation axis, wherein a flow channel between the housing and the turbine shaft is formed, wherein the turbine shaft in its interior a cooling pipe to Having leadership of cooling steam in the direction of the axis of rotation and the cooling line on the one hand at least one inflow line is connected to the inflow of cooling steam from the flow channel into the cooling line, the cooling line being connected to at least one outflow line for guiding cooling steam to a thrust-compensating piston skirt surface, the steam turbine having a return line for returning a mixed vapor formed from the cooling steam and a compensation piston leakage, formed, wherein the return flows into the flow channel.
- a steam turbine with a steam turbine shaft which is in each case hollow in the hot during operation and is provided with an internal cooling.
- the invention is based on the aspect that during operation expanded steam is guided through the shaft interior to the balance piston and there cools the highly stressed compensation piston.
- the proposed cooling option especially those steam turbine shafts can be cooled, which have a balance piston.
- a K partial turbine is to be understood as meaning a compact partial turbine which has a high-pressure and medium-pressure region located on a steam turbine shaft.
- the advantage of the invention is to be seen, inter alia, that the steam turbine shaft can be formed on the one hand creep stable and on the other hand reacts flexibly to thermal loads. For example, during a load change in which a higher thermal load can occur, the cooling causes the thermal load of the shaft to eventually decrease. This is especially true for the areas that are particularly thermally stressed, such. B. the inflow or the balance piston.
- the invention is based on the aspect that the cooling steam is mixed with a compensation piston leakage steam and this mixed steam is again supplied to the flow channel to continue to work there.
- the efficiency of the steam turbine thereby increases.
- a hollow steam turbine shaft has a lower mass compared to a solid shaft and thus also a lower heat capacity a solid shaft and a larger flowed surface. As a result, a rapid warm-up of the steam turbine shaft is possible.
- Another aspect of the invention is that the creep strength of the material used for the steam turbine shaft is increased by the improved cooling.
- the creep rupture strength can be increased by a factor greater than 2 compared to a solid shaft, so that the above-described voltage increase is overcompensated. This leads to an extension of the field of application of the steam turbine shaft.
- the radial clearance can be reduced by the diameter of the hollow shaft is increased by radial centrifugal forces.
- the radial centrifugal force is proportional to the square of the speed. An increase in the speed thus causes a reduction of radial play, which leads to an increase in the overall efficiency of the steam turbine.
- Another aspect of the invention is that hollow shafts can be produced inexpensively.
- the housing comprises an inner housing and an outer housing.
- High-pressure turbine sections as well as medium-pressure and compact turbine sections are among the most thermally stable steam turbines.
- high-pressure, medium-pressure and compact turbine sections with an inner housing are arranged on the vanes and formed around the inner housing arranged outer housing.
- the turbine shaft has at least two regions made of different materials in the axial direction.
- thermally stressed areas is usually high quality material used.
- 10% chromium steel can be used in the thermally stressed areas.
- 1% chromium steel can be used in the areas of low thermal stress 1% chromium steel.
- the turbine shaft has three regions of different materials in the axial direction.
- the two outer regions are made of the same material.
- targeted material can be selected for the respective area of the steam turbine shaft of different thermal load.
- the areas comprising different materials are welded together.
- the welding creates a stable turbine shaft.
- the regions consisting of different materials are connected to one another by means of a Hirth toothing.
- the main advantage of the Hirth toothing is the particularly high thermal flexibility of the turbine shaft. Another advantage is that this usually leads to the turbine shaft can be made quickly.
- the turbine shaft can be formed inexpensively.
- the two outer regions are designed as a solid shaft and the intermediate region lying between them as a hollow shaft. It is equally advantageous if the regions consisting of different materials are connected to one another by means of a flange connection. This can be helpful during revision work because the different areas can be easily separated from each other.
- the areas comprising different materials are welded together by at least one weld.
- the inflow line and the outflow line are integrated in the Hirth toothing.
- the Hirth toothing which may have a trapezoidal, rectangular or triangular toothing, be made with a recess formed as an inflow and / or outflow line.
- This has a very easy way to form an inflow and / or outflow line.
- the recess in the trapezoidal, rectangular or triangular toothing can be adapted depending on the calculated passage volume of the cooling steam.
- the production of such recesses on a Hirth toothing is relatively simple and can also be carried out quickly. This results in cost advantages.
- the return line is arranged within the outer housing.
- the return line can also be designed as a bore in the inner housing.
- 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 turbine shaft 5 is rotatably mounted about an axis of rotation 6.
- the turbine shaft 5 includes blades 7 disposed in grooves on a surface of the turbine shaft 5.
- the inner case 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 turbine shaft 5.
- the rotation of the turbine shaft 5 finally drives a generator, not shown, for power supply.
- the high pressure turbine part 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 turbine section 1 from the outlet 33.
- the steam exerts an action force 11 in the flow direction 13. The result is that the turbine shaft 4 would perform a movement in the flow direction 13.
- FIG. 2 a section of a steam turbine 1 is shown.
- the steam turbine has an outer casing 2, an inner casing 3 and a turbine shaft 5.
- the steam turbine 1 has moving blades 7 and guide vanes 8. live steam passes through the inflow region 10 via a diagonal stage 15 in the flow channel 9. The steam relaxes and cools down. The internal energy of the steam is converted into rotational energy of the turbine shaft 5.
- the cooling line 17 is in this case formed as a cavity within the turbine shaft 5.
- Other embodiments are conceivable. So z. Example, instead of a cavity 17 form a line, not shown, within the turbine shaft 5.
- the turbine shaft 5 is rotatably mounted within the housing 2, 3 and directed along a rotation axis 6. Between the housing 2, 3 and the turbine shaft 5, a flow channel 9 is formed.
- the cooling line 17 is in this case designed to guide cooling steam in the direction of the axis of rotation 6.
- the cooling line 17 is on the one hand fluidly connected to at least one inflow line 16.
- the inflow line 16 is designed for the inflow of cooling steam from the flow channel 9 into the cooling line 17.
- the inflow line 16 may in this case be aligned radially with respect to the axis of rotation 6.
- Other embodiments of the inflow line 16 are conceivable.
- the inflow line 16 can be designed to be inclined perpendicular to the axis of rotation 6.
- the cooling line 16 could run in a spiral shape from the flow channel 9 to the cooling line 17.
- the cross section of the cooling line 16 can vary from the flow channel 9 to the cooling line 17.
- the cooling line 17 is connected to at least one outflow line 18 for guiding the cooling steam onto a thrust balance piston skirt surface 19.
- the effluent from the discharge line 18 cooling steam is distributed on the thrust balance piston skirt surface 19 and cools this off.
- the housing 2, 3 comprises an inner housing 3 and an outer housing 2.
- the cooling steam flowing out of the discharge line 18 flows in two directions. On the one hand in the direction of the main flow direction 13 and the other in one of the main flow 13 opposite direction.
- a portion of the live steam flows via the inflow region 10 between the inner casing 3 and the turbine shaft 5 in the direction of the thrust balance piston 4.
- This so-called piston leakage steam 20 mixes with the cooling steam flowing out of the outflow line and is returned to the flow channel 9 by means of a return line 21. It makes sense that this return line 21 begins between inflow 10 and the outlet of the discharge line 18.
- a partial flow of the cooling steam can be directed in the direction of the main flow 13 and lock the piston leakage 20. In this way, the above-described cooling of the piston surface 18 is ensured.
- This mixed steam formed from the cooling steam and a compensating piston leakage steam is flowed in at a suitable point in the flow channel 9 in order to perform work there.
- the return line 21 may be formed as an external line within the outer housing 2.
- the return line 21 may also be formed as a bore within the inner housing 3.
- FIG. 3 a turbine shaft 5 is shown.
- the turbine shaft 5 is made of a material that takes into account the thermal stresses.
- the turbine shaft 5 is formed of a material.
- FIG. 4 a further turbine shaft 5 is shown, wherein this turbine shaft 5 in the flow direction 13 has at least two regions made of different materials.
- the turbine shaft 5 in the axial flow direction 13 may comprise three regions 24, 23, 22 made of different materials.
- the central region 22 may for example be made of a temperature-resistant 10% chromium steel and the two outer regions 23 and 24 made of the same material such. B. 1% chromium steel.
- the turbine shaft 5 is connected by means of welded joints 25 and 26.
- the turbine shaft 5 can be designed as a hollow shaft in its central region 22 and in its outer regions 23, 24 as a solid shaft.
- the turbine shaft 5 can be made of different materials existing areas 22, 23, 24 by means of a flange 40 with each other, wherein the inflow line 16 and the discharge line 18 is integrated in the flange connection.
- FIG. 5 an alternative embodiment of the turbine shaft 5 is shown.
- the difference to the in FIG. 4 shown turbine shaft is that in FIG. 5 shown turbine shaft 5 is composed by means of a Hirth toothing 27, 28.
- a tie rod 29 must be formed, which is arranged such that the two outer regions 23 and 24 are pressed against the central region 22.
- the central region 22 comprises one or more sections which are tubular or disk-shaped are and each may contain one or more blade stages:
- the turbine shaft 5 by means of a Hirth toothing 30, 31 connected to each other, wherein the inflow line 16 and the discharge line 18 in the Hirth toothing 30, 31 is integrated.
- FIG. 7 a further alternative embodiment of the turbine shaft 5 is shown.
- the turbine shaft 5 comprises at least two regions 22 'and 23' formed of different materials.
- the area 23 ' is flanged to the area 22'.
- the screwing takes place by means of suitable expansion shank bolts 39.
- the flange connection 40 is centered according to the prior art.
- a thread 41 for grasping the screw 39 is formed in the region 22 '.
- the screwing of the region 23 'with the region 22' preferably takes place from the cooler side.
- FIG. 8 is a sectional view of the bolted connection from the FIG. 7 to see. It can also be seen in this illustration that the discharge line 18 integrates into the connection through recesses. This is in a perspective view of a part of the turbine shaft 5 in the FIG. 5 shown.
- FIG. 10 is a perspective view of a Hirth toothing 30, 31 to see.
- the middle region 2 in this case has one according to FIG. 10 illustrated Hirth toothing 30, 31 on.
- the two outer regions 24 and 23 made of different materials likewise have a Hirth toothing 30, 31.
- FIG. 11 is a cross-sectional view of the Hirth serration 30, 31 can be seen.
- the left part is, for example, the left region 24 and the right part of the central region 22 is connected to one another via the Hirth toothing 30.
- the inflow line 16 is integrated in the Hirth toothing.
- FIG. 11 illustrated cross-sectional illustration may also represent the discharge line 18.
- the left-hand region would be the middle region 22 and the right-hand region 23 connected via the Hirth toothing 31.
- the outflow line 18 is integrated in the Hirth toothing 30, 31.
- In the FIG. 11 illustrated embodiment has a triangular toothing.
- the inflow line 16 or the outflow line 18 is formed via recesses 32 of the Hirth toothing 30, 31.
- Possible embodiments of the Hirth toothing are a trapezoidal, rectangular or triangular toothing. Other embodiments are possible.
- the temperature is plotted in a linear scale of 400 to 600 ° C.
- the creep rupture strength R m is 200,000 h in a linear scale of 30 to 530 N mm 2 applied.
- the upper curve 37 shows the temperature behavior for the material 30 CrMoNiV5-11 and the lower curve 38 shows the temperature behavior for the material X12CrMoWVNbN10-1-1.
- the invention is not limited to the formation of a high-pressure turbine section as an embodiment of a steam turbine 1, the turbine shaft 5 according to the invention can also be used in a medium-pressure or a compact turbine section (high pressure and medium pressure within a housing). Likewise, the turbine shaft 5 can be used in other types of steam turbine.
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Abstract
Description
Die Erfindung betrifft eine Dampfturbine mit einem Gehäuse, wobei eine einen Schubausgleichskolben aufweisende Turbinenwelle drehgelagert innerhalb des Gehäuses angeordnet und entlang einer Rotationsachse gerichtet ist, wobei ein Strömungskanal zwischen dem Gehäuse und der Turbinenwelle ausgebildet ist, wobei die Turbinenwelle in ihrem Inneren eine Kühlleitung zur Führung von Kühldampf in Richtung der Rotationsachse aufweist und die Kühlleitung mit zumindest einer Zuströmleitung zur Zuströmung von Kühldampf aus dem Strömungskanal in die Kühlleitung verbunden ist.The invention relates to a steam turbine having a housing, wherein a turbine shaft having a thrust balance piston rotatably mounted within the housing and directed along a rotation axis, wherein a flow channel between the housing and the turbine shaft is formed, wherein the turbine shaft in its interior a cooling pipe for guiding Has cooling steam in the direction of the axis of rotation and the cooling line is connected to at least one inflow line for the inflow of cooling steam from the flow channel in the cooling line.
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, das 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.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 the working medium, which, however, is subject to completely different temperature and pressure conditions than the steam in a steam turbine. In contrast to gas turbines has steam turbines z. As the one part turbine incoming working fluid 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.
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 ist eine Anzahl von Leitschaufelreihen hintereinander angeordnet.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 passes through the blades set the steam in rotation. 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. In this case, it is usually part of a vane ring, which comprises a number of vanes, which are 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 number 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 dem Dampfturbinengehäuse separat, d. h. zusätzlich zum Arbeitsmedium zugeführtes Kühlmedium bewirkt. Dagegen erfolgt eine passive Kühlung lediglich durch eine geeignete Führung oder Verwendung des Arbeitsmediums. Eine übliche 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, a distinction must be made between active cooling and passive cooling. In the case of active cooling, cooling is effected separately by a cooling medium supplied to the steam turbine housing, that is to say in addition to the working medium. In contrast, a passive cooling is done only by a suitable leadership or use of the working medium. A conventional 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 become. However, this can only achieve a very limited cooling effect on the housing.
Die in den Dampfturbinen drehbar gelagerten Dampfturbinenwellen werden im Betrieb thermisch sehr beansprucht. Die Entwicklung und Herstellung einer Dampfturbinenwelle ist zugleich teuer und zeitaufwändig. Die Dampfturbinenwellen gelten als die am höchsten beanspruchten und teuersten Komponenten einer Dampfturbine. Dies gilt zunehmend für hohe Dampftemperaturen.The steam turbine shafts, which are rotatably mounted in the steam turbines, are subjected to a great deal of thermal stress during operation. The development and production of a steam turbine shaft is both expensive and time consuming. Steam turbine shafts are considered to be the most stressed and expensive components of a steam turbine. This increasingly applies to high steam temperatures.
Mitunter aufgrund der hohen Massen der Dampfturbinenwellen sind diese thermisch träge, was sich negativ bei einem thermischen Lastwechseln eines Turbosatzes auswirkt. Das bedeutet, dass die Reaktion der gesamten Dampfturbine auf einen Lastwechsel im starken Maße von der Schnelligkeit der Dampfturbinenwelle auf thermisch veränderte Bedingungen reagieren zu können, abhängt. Zur Überwachung der Dampfturbinenwelle wird standardmäßig die Temperatur überwacht, was aufwändig und kostspielig ist.Sometimes due to the high masses of the steam turbine shafts these are thermally inert, which has a negative effect on thermal load changes of a turbine set. This means that the response of the entire steam turbine to a load change depends strongly on the speed of the steam turbine shaft to respond to thermally altered conditions depends. To monitor the steam turbine shaft, the temperature is monitored by default, which is complex and costly.
Eine Eigenschaft der Dampfturbinenwellen ist, dass diese über keine wesentliche Wärmesenke verfügen. Daher gestaltet sich die Kühlung der an der Dampfturbinenwelle angeordneten Laufschaufeln als schwierig.One characteristic of steam turbine shafts is that they have no significant heat sink. Therefore, the cooling of the blades arranged on the steam turbine shaft is difficult.
Zur Verbesserung der Anpassung einer Dampfturbinenwelle auf eine thermische Beanspruchung ist es bekannt, diese im Einströmbereich auszuhöhlen oder als Hohlwelle auszubilden. Diese Hohlräume sind in der Regel abgeschlossen und mit Luft gefüllt.To improve the adaptation of a steam turbine shaft to a thermal stress, it is known to hollow out these in the inflow region or to form it as a hollow shaft. These cavities are usually completed and filled with air.
Allerdings wirken sich die im Betrieb auftretenden hohen Spannungen, die zum großen Teil aus Tangentialspannungen aus der Fliehkraft bestehen, nachteilig auf die vorgenannten Dampfturbinen-Hohlwellen aus. Diese Spannungen sind in etwa doppelt so hoch wie die Spannungen, die bei entsprechenden Vollwellen auftreten würden. Dies hat einen starken Einfluss auf die Werkstoffauswahl der Hohlwellen, was dazu führen kann, dass die Hohlwellen für hohe Dampfzustände nicht geeignet bzw. nicht realisierbar sind.However, the high voltages that occur during operation, which largely consist of tangential stresses from the centrifugal force, have an adverse effect on the aforementioned steam turbine hollow shafts. These voltages are about twice as high as the voltages that would occur at corresponding full waves. This has a strong influence on the choice of material of the hollow shafts, which can lead to the fact that the hollow shafts for high steam conditions are not suitable or not feasible.
Im Gasturbinenbau ist es bekannt, luftgekühlte Hohlwellen als dünnwandige Schweißkonstruktionen auszuführen. Es ist unter anderem bekannt, die Gasturbinenwellen über eine so genannte Hirth-Verzahnung mit Scheiben auszubilden. Diese Gasturbinenwellen weisen dafür einen zentralen Zuganker auf.In gas turbine construction, it is known to carry air-cooled hollow shafts as thin-walled welded constructions. It is known, inter alia, to form the gas turbine shafts via a so-called Hirth toothing with discs. These gas turbine shafts have for this purpose a central tie rod.
Allerdings ist eine direkte Übertragung der Kühlprinzipien bei Gasturbinen auf den Dampfturbinenbau in der Regel nicht möglich, da eine Dampfturbine im Gegensatz zur Gasturbine als geschlossenes System betrieben wird. Darunter ist zu verstehen, dass das Arbeitsmedium in einem Kreislauf sich befindet und nicht in die Umgebung abgeführt wird. Das bei einer Gasturbine eingesetzte Arbeitsmedium, das im Grunde genommen aus Luft und Abgas besteht, wird nach dem Durchtritt durch die Turbineneinheit der Gasturbine in die Umgebung abgegeben.However, a direct transfer of cooling principles in gas turbines on the steam turbine construction is usually not possible, since a steam turbine is operated in contrast to the gas turbine as a closed system. By this is meant that the working fluid is in a circuit and is not discharged into the environment. The working medium used in a gas turbine, which basically consists of air and exhaust gas, is released into the environment after passing through the turbine unit of the gas turbine.
Dampfturbinen weisen darüber hinaus im Gegensatz zur Gasturbine keine Verdichtereinheit auf und des Weiteren sind die Wellen der Dampfturbine im Allgemeinen nur radial zugänglich.In addition, steam turbines, in contrast to the gas turbine, have no compressor unit and, moreover, the shafts of the steam turbine are generally accessible only radially.
Dampfturbinen mit einer Dampfeintrittstemperatur von ungefähr 600°C wurden in den 1950er Jahren entwickelt und gebaut. Diese Dampfturbinen wiesen eine radiale Beschaufelung auf. Der heutige Stand der Technik im Dampfturbinenbau umfasst Wellenkühlungen mit radialer Anordnung der ersten Leitschaufelreihe in Form von Diagonal- oder Regelstufen auf. Nachteilig bei dieser Ausführungsform ist jedoch die geringe Kühlwirkung dieser Diagonal- oder Regelstufen.Steam turbines with a steam inlet temperature of about 600 ° C were developed and built in the 1950s. These steam turbines had a radial blading. The current state of the art in steam turbine construction includes shaft cooling with radial arrangement of the first row of vanes in the form of diagonal or control stages. A disadvantage of this embodiment, however, is the low cooling effect of these diagonal or control stages.
Besonders thermisch belastet werden bei den Dampfturbinenwellen 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 die Welle in einer Richtung eine Gegenkraft in Gegenrichtung ausgebildet wird.The piston and inflow areas are particularly thermally stressed in the steam turbine shafts. 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 caused by the working fluid force the shaft is formed in one direction a counter force in the opposite direction.
Eine Kühlung einer Dampfturbinenwelle ist unter anderem in der
In der
Die
In er
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 mit einem Gehäuse, wobei eine einen Schubausgleichskolben aufweisende Turbinenwelle drehgelagert innerhalb des Gehäuses angeordnet und entlang einer Rotationsachse gerichtet ist, wobei ein Strömungskanal zwischen dem Gehäuse und der Turbinenwelle ausgebildet ist, wobei die Turbinenwelle in ihrem Inneren eine Kühlleitung zur Führung von Kühldampf in Richtung der Rotationsachse aufweist und die Kühlleitung einerseits mit zumindest einer Zuströmleitung zur Zuströmung von Kühldampf aus dem Strömungskanal in die Kühlleitung verbunden ist, wobei die Kühlleitung andererseits mit zumindest einer Abströmleitung zur Führung von Kühldampf auf eine Schubausgleichskolbenmanteloberfläche verbunden ist, wobei die Dampfturbine mit einer Rückführungsleitung zur Rückführung eines Mischdampfes, gebildet aus dem Kühldampf und einem Ausgleichskolbenleckdampf, ausgebildet, wobei die Rückführung in den Strömungskanal mündet.This object is achieved by a steam turbine with a housing, wherein a turbine piston having a thrust balance piston rotatably mounted within the housing and directed along a rotation axis, wherein a flow channel between the housing and the turbine shaft is formed, wherein the turbine shaft in its interior a cooling pipe to Having leadership of cooling steam in the direction of the axis of rotation and the cooling line on the one hand at least one inflow line is connected to the inflow of cooling steam from the flow channel into the cooling line, the cooling line being connected to at least one outflow line for guiding cooling steam to a thrust-compensating piston skirt surface, the steam turbine having a return line for returning a mixed vapor formed from the cooling steam and a compensation piston leakage, formed, wherein the return flows into the flow channel.
Es wird somit eine Dampfturbine mit einer Dampfturbinenwelle vorgeschlagen, die in den während des Betriebes heißen Bereichen jeweils hohl ist und mit einer internen Kühlung versehen ist. Die Erfindung geht von dem Aspekt aus, dass während des Betriebes expandierter Dampf durch das Welleninnere zum Ausgleichskolben geführt wird und dort den thermisch sehr beanspruchten Ausgleichskolben kühlt. Mit der vorgeschlagenen Kühlmöglichkeit können vor allem diejenigen Dampfturbinenwellen gekühlt werden, die einen Ausgleichskolben aufweisen. Dies wären z. B. Hochdruck-, Mitteldruck- sowie K-Teilturbinen. Wobei unter einer K-Teilturbine eine Kompakt-Teilturbine zu verstehen ist, die einen auf einer Dampfturbinenwelle befindlichen Hochdruck- und Mitteldruckbereich aufweist. Der Vorteil der Erfindung ist unter anderem darin zu sehen, dass die Dampfturbinenwelle zum einen kriechstabil ausgebildet werden kann und zum anderen flexibel auf thermische Belastungen reagiert. Bei einem Lastwechsel beispielsweise, bei dem eine höhere thermische Belastung auftreten kann, führt die Kühlung dazu, dass die thermische Belastung der Welle schließlich abnimmt. Dies gilt insbesondere für die Bereiche, die besonders thermisch belastet sind, wie z. B. der Einströmbereich oder der Ausgleichskolben.It is thus proposed a steam turbine with a steam turbine shaft, which is in each case hollow in the hot during operation and is provided with an internal cooling. The invention is based on the aspect that during operation expanded steam is guided through the shaft interior to the balance piston and there cools the highly stressed compensation piston. With the proposed cooling option, especially those steam turbine shafts can be cooled, which have a balance piston. This would be z. B. high pressure, medium pressure and K-part turbines. Whereby a K partial turbine is to be understood as meaning a compact partial turbine which has a high-pressure and medium-pressure region located on a steam turbine shaft. The advantage of the invention is to be seen, inter alia, that the steam turbine shaft can be formed on the one hand creep stable and on the other hand reacts flexibly to thermal loads. For example, during a load change in which a higher thermal load can occur, the cooling causes the thermal load of the shaft to eventually decrease. This is especially true for the areas that are particularly thermally stressed, such. B. the inflow or the balance piston.
Dabei geht die Erfindung von dem Aspekt aus, dass der Kühldampf mit einem Ausgleichskolbenleckdampf vermischt wird und dieser gebildete Mischdampf wieder dem Strömungskanal zugeführt wird um dort weiter Arbeit zu leisten. Der Wirkungsgrad der Dampfturbine erhöht sich dadurch.The invention is based on the aspect that the cooling steam is mixed with a compensation piston leakage steam and this mixed steam is again supplied to the flow channel to continue to work there. The efficiency of the steam turbine thereby increases.
Dadurch ist ein schnelles Anfahren der Dampfturbine möglich, was für die heutige Zeit einen besonderen Aspekt darstellt, bei dem es darum geht, Energie schnell zur Verfügung zu stellen. Des Weiteren entsteht ein Vorteil durch die erfindungsgemäße Dampfturbine dadurch, dass die Kosten für eine Wellenüberwachung geringer ausfallen können. Eine hohle Dampfturbinenwelle weist eine geringere Masse gegenüber einer Vollwelle auf und dadurch auch eine geringere Wärmekapazität gegenüber einer Vollwelle sowie eine größere beströmte Oberfläche. Dadurch ist ein schnelles Aufwärmen der Dampfturbinenwelle möglich.This allows a quick start-up of the steam turbine, which is a special aspect for the present time, which is about providing energy quickly available. Furthermore, there is an advantage of the steam turbine according to the invention in that the costs for wave monitoring can be lower. A hollow steam turbine shaft has a lower mass compared to a solid shaft and thus also a lower heat capacity a solid shaft and a larger flowed surface. As a result, a rapid warm-up of the steam turbine shaft is possible.
Ein weiterer Aspekt der Erfindung ist, dass die Zeitstandsfestigkeit des für die Dampfturbinenwelle eingesetzten Materials durch die verbesserte Kühlung erhöht wird. Die Zeitstandsfestigkeit kann hierbei um einen Faktor größer als 2 gegenüber einer Vollwelle erhöht werden, sodass die oben beschriebene Spannungserhöhung überkompensiert wird. Dies führt zu einer Erweiterung des Einsatzbereiches der Dampfturbinenwelle.Another aspect of the invention is that the creep strength of the material used for the steam turbine shaft is increased by the improved cooling. The creep rupture strength can be increased by a factor greater than 2 compared to a solid shaft, so that the above-described voltage increase is overcompensated. This leads to an extension of the field of application of the steam turbine shaft.
Ein weiterer Aspekt der Erfindung ist es, dass die Radialspiele verkleinert werden können, indem der Durchmesser der Hohlwelle durch radiale Fliehkräfte vergrößert wird. Die radiale Fliehkraft ist proportional zum Quadrat der Drehzahl. Eine Vergrößerung der Drehzahl bewirkt demnach eine Verkleinerung von Radialspielen, was zu einer Steigerung des Gesamtwirkungsgrades der Dampfturbine führt.Another aspect of the invention is that the radial clearance can be reduced by the diameter of the hollow shaft is increased by radial centrifugal forces. The radial centrifugal force is proportional to the square of the speed. An increase in the speed thus causes a reduction of radial play, which leads to an increase in the overall efficiency of the steam turbine.
Ein weiterer Aspekt der Erfindung ist es, dass Hohlwellen kostengünstig hergestellt werden können.Another aspect of the invention is that hollow shafts can be produced inexpensively.
In einer vorteilhaften Weiterbildung umfasst das Gehäuse ein Innengehäuse und ein Außengehäuse. Hochdruck-Teilturbinen als auch Mitteldruck- und Kompakt-Teilturbinen gehören zu den am thermisch belastbarsten Dampfturbinen. In der Regel werden Hochdruck-, Mitteldruck- sowie Kompakt-Teilturbinen mit einem Innengehäuse, an dem Leitschaufeln angeordnet sind und einem um das Innengehäuse angeordneten Außengehäuse ausgebildet.In an advantageous development, the housing comprises an inner housing and an outer housing. High-pressure turbine sections as well as medium-pressure and compact turbine sections are among the most thermally stable steam turbines. In general, high-pressure, medium-pressure and compact turbine sections with an inner housing, are arranged on the vanes and formed around the inner housing arranged outer housing.
In einer vorteilhaften Weiterbildung weist die Turbinenwelle in axialer Richtung zumindest zwei Bereiche aus verschiedenen Materialien auf.In an advantageous development, the turbine shaft has at least two regions made of different materials in the axial direction.
Dadurch können Kosten eingespart werden. In den thermisch belasteten Bereichen wird in der Regel hochwertiges Material eingesetzt. Beispielsweise kann in den thermisch belasteten Bereichen 10%iger Chromstahl verwendet werden. Wohingegen in den Bereichen niedriger thermischer Belastung 1%iger Chromstahl verwendet werden kann.This can save costs. In the thermally stressed areas is usually high quality material used. For example, 10% chromium steel can be used in the thermally stressed areas. Whereas in the areas of low thermal stress 1% chromium steel can be used.
Zweckdienlicherweise weist die Turbinenwelle in axialer Richtung drei Bereiche aus verschiedenen Materialien auf. Insbesondere bestehen die beiden äußeren Bereiche aus dem gleichen Material. Dadurch kann zielgerichtet geeignetes Material für den jeweiligen Bereich der Dampfturbinenwelle unterschiedlicher thermischer Belastung ausgewählt werden.Conveniently, the turbine shaft has three regions of different materials in the axial direction. In particular, the two outer regions are made of the same material. As a result, targeted material can be selected for the respective area of the steam turbine shaft of different thermal load.
Vorteilhafterweise werden die aus verschiedenen Materialien umfassenden Bereiche miteinander verscheißt. Durch die Schweißung wird eine stabile Turbinenwelle ausgebildet.Advantageously, the areas comprising different materials are welded together. The welding creates a stable turbine shaft.
In einer weiteren vorteilhaften alternativen Ausführungsform sind die aus verschiedenen Materialien bestehenden Bereiche mittels einer Hirth-Verzahnung miteinander verbunden. Der wesentliche Vorteil der Hirth-Verzahnung ist die besonders hohe thermische Flexibilität der Turbinenwelle. Ein weiterer Vorteil liegt darin, dass diese in der Regel dazu führt, dass die Turbinenwelle schnell gefertigt werden kann. Darüber hinaus kann die Turbinenwelle kostengünstig ausgebildet werden.In a further advantageous alternative embodiment, the regions consisting of different materials are connected to one another by means of a Hirth toothing. The main advantage of the Hirth toothing is the particularly high thermal flexibility of the turbine shaft. Another advantage is that this usually leads to the turbine shaft can be made quickly. In addition, the turbine shaft can be formed inexpensively.
In einer weiteren vorteilhaften Weiterbildung sind die beiden äußeren Bereiche als Vollwelle und der dazwischen liegende mittlere Bereich als Hohlwelle ausgebildet. Ebenso vorteilhaft ist es, wenn die aus verschiedenen Materialien bestehenden Bereiche mittels einer Flanschverbindung miteinander verbunden sind. Dies kann bei Revisionsarbeiten hilfreich sein, da die verschiedenen Bereiche voneinander leicht getrennt werden können.In a further advantageous development, the two outer regions are designed as a solid shaft and the intermediate region lying between them as a hollow shaft. It is equally advantageous if the regions consisting of different materials are connected to one another by means of a flange connection. This can be helpful during revision work because the different areas can be easily separated from each other.
Ebenso ist es vorteilhaft, wenn die Zuströmleitung und die Abströmleitung in der Flanschverbindung integriert sind.It is likewise advantageous if the inflow line and the outflow line are integrated in the flange connection.
Zweckdienlicherweise werden die aus verschiedenen Materialien umfassenden Bereiche durch mindestens eine Schweißnaht miteinander verschweißt.Conveniently, the areas comprising different materials are welded together by at least one weld.
Sehr vorteilhaft ist es, wenn die Zuströmleitung und die Abströmleitung in der Hirth-Verzahnung integriert sind. Dabei kann die Hirth-Verzahnung, die eine Trapez-, rechteckige oder dreieckige Verzahnung aufweisen kann, mit einer als Zuström-und/oder Abströmleitung ausgebildeten Ausnehmung gefertigt sein. Dadurch hat man eine sehr einfache Möglichkeit, eine Zuström- und/oder Abströmleitung auszubilden. Beispielsweise kann die Ausnehmung in der Trapez-, rechteckigen oder dreieckigen Verzahnung je nach berechnetem Durchtrittsvolumen des Kühldampfes angepasst ausgebildet sein. Die Fertigung solcher Ausnehmungen auf einer Hirth-Verzahnung ist vergleichsweise einfach und kann darüber hinaus schnell durchgeführt werden. Dadurch entstehen Kostenvorteile.It is very advantageous if the inflow line and the outflow line are integrated in the Hirth toothing. In this case, the Hirth toothing, which may have a trapezoidal, rectangular or triangular toothing, be made with a recess formed as an inflow and / or outflow line. This has a very easy way to form an inflow and / or outflow line. For example, the recess in the trapezoidal, rectangular or triangular toothing can be adapted depending on the calculated passage volume of the cooling steam. The production of such recesses on a Hirth toothing is relatively simple and can also be carried out quickly. This results in cost advantages.
Vorteilhafterweise wird die Rückführungsleitung innerhalb des Außengehäuses angeordnet. Die Rückführungsleitung kann auch als Bohrung im Innengehäuse ausgebildet sein.Advantageously, the return line is arranged within the outer housing. The return line can also be designed as a bore in the inner housing.
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.
- Figur 1FIG. 1
- eine Querschnittsansicht einer Hochdruck-Teilturbine gemäß dem Stand der Technik,a cross-sectional view of a high pressure turbine part according to the prior art,
- Figur 2FIG. 2
- einen Schnitt durch einen Teil einer Teilturbine,a section through a part of a sub-turbine,
- Figur 3FIG. 3
- einen Schnitt durch eine Turbinenwelle,a section through a turbine shaft,
- Figur 4FIG. 4
- einen Schnitt durch eine Turbinenwelle in alternativer Ausführungsform,a section through a turbine shaft in an alternative embodiment,
- Figur 5FIG. 5
- einen Schnitt durch eine Turbinewelle in alternativer Ausführungsform,a section through a turbine shaft in an alternative embodiment,
- Figur 6FIG. 6
- einen Schnitt durch eine Turbinenwelle in alternativer Ausführungsform,a section through a turbine shaft in an alternative embodiment,
- Figur 7FIG. 7
- einen Schnitt durch eine Turbinenwelle in alternativer Ausführungsform,a section through a turbine shaft in an alternative embodiment,
- Figur 8FIG. 8
- eine vergrößerte Darstellung einer Flanschverbindung,an enlarged view of a flange connection,
- Figur 9FIG. 9
- eine perspektivische Darstellung eines Teiles der Flanschverbindung,a perspective view of a part of the flange,
- Figur 10FIG. 10
- eine perspektivische Darstellung des Prinzips einer Hirth-Verzahnung,a perspective view of the principle of a Hirth toothing,
- Figur 11FIG. 11
- eine Schnittdarstellung einer Hirth-Verzahnung mit Durchlasskanälen in Dreieck-Form,a sectional view of a Hirth toothing with passage channels in a triangular shape,
- Figur 12FIG. 12
- einen Schnitt durch eine Hirth-Verzahnung in Trapezform mit Durchgangsbohrungen,a section through a Hirth toothing in trapezoidal shape with through holes,
- Figur 13FIG. 13
- Kurve mit Darstellung der relativen Zeitstandsfestigkeit in Abhängigkeit der Temperatur.Curve showing relative creep rupture strength as a function of temperature.
In der
In der
Der Dampf wird nach einer bestimmten Anzahl von Turbinenstufen, die aus Leit- 8 und Laufschaufeln 7 gebildet werden, über eine Zuströmleitung 16 mit einer Kühlleitung 17 strömungstechnisch verbunden. Die Kühlleitung 17 ist hierbei als Hohlraum innerhalb der Turbinenwelle 5 ausgebildet. Andere Ausführungsformen sind denkbar. So ist z. B. möglich, statt eines Hohlraums 17 eine nicht dargestellte Leitung innerhalb der Turbinenwelle 5 auszubilden.After a certain number of turbine stages, which are formed by
Die Turbinenwelle 5 ist drehgelagert innerhalb des Gehäuses 2, 3 angeordnet und entlang einer Rotationsachse 6 gerichtet. Zwischen dem Gehäuse 2, 3 und der Turbinenwelle 5 wird ein Strömungskanal 9 ausgebildet. Die Kühlleitung 17 ist hierbei zur Führung von Kühldampf in Richtung der Rotationsachse 6 ausgebildet. Die Kühlleitung 17 ist einerseits mit zumindest einer Zuströmungsleitung 16 strömungstechnisch verbunden. Die Zuströmleitung 16 ist zur Zuströmung von Kühldampf aus dem Strömungskanal 9 in die Kühlleitung 17 ausgebildet.The
Die Zuströmleitung 16 kann hierbei radial zur Rotationsachse 6 ausgerichtet sein. Andere Ausführungsformen der Zuströmleitung 16 sind denkbar. So kann beispielsweise die Zuströmleitung 16 senkrecht zur Rotationsachse 6 geneigt ausgebildet sein. Die Kühlleitung 16 könnte spiralförmig von dem Strömungskanal 9 zur Kühlleitung 17 verlaufen. Der Querschnitt der Kühlleitung 16 kann von dem Strömungskanal 9 zur Kühlleitung 17 variieren.The
Die Kühlleitung 17 ist andererseits mit zumindest einer Abströmleitung 18 zur Führung des Kühldampfes auf eine Schubausgleichskolbenmanteloberfläche 19 verbunden.On the other hand, the cooling
Der aus der Abströmleitung 18 ausströmende Kühldampf verteilt sich auf der Schubausgleichskolbenmanteloberfläche 19 und kühlt hierbei diese ab.The effluent from the
Das Gehäuse 2, 3 umfasst ein Innengehäuse 3 und ein Außengehäuse 2. Der aus der Abströmleitung 18 ausströmende Kühldampf strömt in zwei Richtungen. Zum einen in Richtung der Hauptströmungsrichtung 13 und zum anderen in einer der Hauptströmung 13 entgegen gesetzten Richtung. Über den Einströmbereich 10 strömt ein Teil des Frischdampfes zwischen dem Innengehäuse 3 und der Turbinenwelle 5 in Richtung des Schubausgleichskolbens 4. Dieser so genannte Kolbenleckdampf 20 vermischt sich mit dem aus der Abströmleitung ausströmenden Kühldampf und wird mittels einer Rückführungsleitung 21 in den Strömungskanal 9 zurückgeführt. Sinnvollerweise beginnt diese Rückführungsleitung 21 zwischen Einströmung 10 und dem Austritt der Abströmleitung 18. Somit kann ein Teilstrom des Kühldampfes in Richtung der Hauptströmung 13 geleitet werden und den Kolbenleckdampf 20 sperren. Auf diese Weise wird die oben beschriebene Kühlung der Kolbenoberfläche 18 sichergestellt. Dieser aus dem Kühldampf und einem Ausgleichskolbenleckdampf gebildete Mischdampf wird an geeigneter Stelle im Strömungskanal 9 eingeströmt um dort Arbeit zu leisten.The
Die Rückführungsleitung 21 kann als externe Leitung innerhalb des Außengehäuses 2 ausgebildet sein. Die Rückführungsleitung 21 kann auch als Bohrung innerhalb des Innengehäuses 3 ausgebildet sein.The
In der
Durch die Schraffur in der
In der
Die Turbinenwelle 5 kann in ihrem mittleren Bereich 22 als Hohlwelle und in ihren äußeren Bereichen 23, 24 als Vollwelle ausgeführt werden.The
Sofern die Bereiche 22, 23, 24 miteinander verschweißt werden, wird mindestens eine Schweißnaht verwendet.If the
Die Turbinenwelle 5 kann aus verschiedenen Materialien bestehenden Bereiche 22, 23, 24 mittels einer Flanschverbindung 40 miteinander verbunden werden, wobei die Zuströmleitung 16 und die Abströmleitung 18 in der Flanschverbindung integriert ist.The
In der
In einer weiteren alternativen Ausführungsform wird, wie in
In der
In der
In der
In der
Die Zuströmleitung 16 bzw. die Abströmleitung 18 ist über Ausnehmungen 32 der Hirth-Verzahnung 30, 31 ausgebildet.The
In der
In der
Auf der x-Achse 35 ist die Temperatur in einer linearen Skala von 400 bis 600°C aufgetragen. Auf der y-Achse 36 ist die Zeitstandsfestigkeit Rm,200000h in einer linearen Skala von 30 bis 530
Es hat sich gezeigt, dass zusätzlich zur erfindungsgemäßen Führung des Kühldampfes eine Auftragung einer Wärmedämmschicht auf die Oberflächen der thermisch beanspruchten Bauteile den Effekt der wirksamen Kühlung erhöht.It has been found that in addition to the guidance of the cooling steam according to the invention, a plot of a thermal barrier coating on the surfaces of the thermally stressed components increases the effect of effective cooling.
Durch den Einsatz des Zugankers 29 wird ein Teil der Axialkräfte übernommen. Dadurch kann die Turbinenwelle 5 dünnwandiger ausgebildet werden, was sich auf die thermische Flexibilität und die Ausbildung der Radialspiele positiv auswirkt.Through the use of the
Die Erfindung ist nicht auf die Ausbildung einer Hochdruck-Teilturbine als Ausführungsform einer Dampfturbine 1 einzuschränken, die erfindungsgemäße Turbinenwelle 5 kann auch in einer Mitteldruck- oder einer Kompakt-Teilturbine (Hochdruck- und Mitteldruck innerhalb eines Gehäuses) eingesetzt werden. Ebenso kann die Turbinenwelle 5 in anderen Dampfturbinentypen eingesetzt werden.The invention is not limited to the formation of a high-pressure turbine section as an embodiment of a steam turbine 1, the
Claims (14)
- Steam turbine (1) with a casing (2, 3),
wherein a turbine shaft (5), which has a thrust compensating piston (4), is arranged in a rotatably mounted manner inside the casing (2, 3), and is oriented along a rotational axis (6),
wherein a flow passage (9) is formed between the casing (2, 3) and the turbine shaft (5),
wherein the turbine shaft (5) has a cooling line (17) within it for guiding cooling steam in the direction of the rotational axis (6), and the cooling line (17) is connected on one side to at least one inflow line (16) for inflow of cooling steam from the flow passage (9) into the cooling line (17), wherein
the cooling line (17) is connected on the other side to at least one outflow line (18) for guiding cooling steam onto a generated surface (19) of the thrust compensating piston,
characterized by
a return line (21) for return of mixed steam which is formed from the cooling steam, which flows out of the outflow line (18), and some live steam, which as compensating piston leakage steam flows between the casing (2, 3) and the turbine shaft (5) in the direction of the thrust compensating piston (4),
wherein the return line (21) leads into the flow passage (9). - Steam turbine (1) according to Claim 1,
wherein the casing (2, 3) comprises an inner casing (3) and an outer casing (2). - Steam turbine (1) according to either of Claims 1 or 2,
wherein the turbine shaft (5) in the axial direction (34) has at least two sections consisting of different materials. - Steam turbine (1) according to Claim 1, 2 or 3,
wherein the turbine shaft (5) in the axial direction (34) has three sections (22, 23, 24) consisting of different materials. - Steam turbine (1) according to Claim 4,
wherein the two outer sections (23, 24) consist of the same material. - Steam turbine (1) according to Claim 3, 4 or 5,
wherein the sections consisting of different materials (22, 23, 24) are welded to each other. - Steam turbine (1) according to Claim 3, 4, 5 or 6,
wherein the sections (23, 24) are formed as a solid shaft and the section (22) is formed as a hollow shaft. - Steam turbine (1) according to Claim 3, 4, 5 or 7,
wherein the sections consisting of different materials (22, 23, 24) are interconnected by means of a Hirth toothing (30, 31). - Steam turbine (1) according to Claim 3, 4, 5 or 7,
wherein the sections consisting of different materials (22, 23, 24) are interconnected by means of a flanged connection (40). - Steam turbine (1) according to Claim 8,
wherein the inflow line (16) and the outflow line (18) are integrated in the Hirth toothing (30, 31). - Steam turbine (1) according to Claim 9,
wherein the inflow line (16) and the outflow line (18) are integrated in the flanged connection (40). - Steam turbine (1) according to Claim 8,
wherein the Hirth toothing (30, 31) has trapezoidal, rectangular or triangular serrations with a recess (32) which is formed as an inflow line (16) and/or outflow line (18). - Steam turbine (1) according to one of the preceding claims,
wherein the return line (21) is arranged inside the outer casing (2). - Steam turbine (1) according to one of the preceding claims,
wherein the return line (21) is formed as a bore in the inner casing (2).
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PL06819128T PL1945911T3 (en) | 2005-10-31 | 2006-10-24 | Steam turbine |
EP06819128A EP1945911B1 (en) | 2005-10-31 | 2006-10-24 | Steam turbine |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP05023760A EP1780376A1 (en) | 2005-10-31 | 2005-10-31 | Steam turbine |
PCT/EP2006/067717 WO2007051733A1 (en) | 2005-10-31 | 2006-10-24 | Steam turbine |
EP06819128A EP1945911B1 (en) | 2005-10-31 | 2006-10-24 | Steam turbine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1945911A1 EP1945911A1 (en) | 2008-07-23 |
EP1945911B1 true EP1945911B1 (en) | 2009-12-02 |
Family
ID=35985854
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05023760A Withdrawn EP1780376A1 (en) | 2005-10-31 | 2005-10-31 | Steam turbine |
EP06819128A Not-in-force EP1945911B1 (en) | 2005-10-31 | 2006-10-24 | Steam turbine |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05023760A Withdrawn EP1780376A1 (en) | 2005-10-31 | 2005-10-31 | Steam turbine |
Country Status (11)
Country | Link |
---|---|
US (1) | US8128341B2 (en) |
EP (2) | EP1780376A1 (en) |
JP (1) | JP4662570B2 (en) |
KR (1) | KR101014151B1 (en) |
CN (1) | CN101300405B (en) |
AT (1) | ATE450693T1 (en) |
DE (1) | DE502006005550D1 (en) |
ES (1) | ES2336610T3 (en) |
PL (1) | PL1945911T3 (en) |
RU (1) | RU2410545C2 (en) |
WO (1) | WO2007051733A1 (en) |
Cited By (1)
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US8128341B2 (en) | 2005-10-31 | 2012-03-06 | Siemens Aktiengesellschaft | Steam turbine |
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-
2005
- 2005-10-31 EP EP05023760A patent/EP1780376A1/en not_active Withdrawn
-
2006
- 2006-10-24 AT AT06819128T patent/ATE450693T1/en active
- 2006-10-24 WO PCT/EP2006/067717 patent/WO2007051733A1/en active Application Filing
- 2006-10-24 US US12/084,300 patent/US8128341B2/en not_active Expired - Fee Related
- 2006-10-24 PL PL06819128T patent/PL1945911T3/en unknown
- 2006-10-24 KR KR1020087012683A patent/KR101014151B1/en not_active IP Right Cessation
- 2006-10-24 RU RU2008121935/06A patent/RU2410545C2/en not_active IP Right Cessation
- 2006-10-24 EP EP06819128A patent/EP1945911B1/en not_active Not-in-force
- 2006-10-24 CN CN2006800405336A patent/CN101300405B/en not_active Expired - Fee Related
- 2006-10-24 JP JP2008537085A patent/JP4662570B2/en not_active Expired - Fee Related
- 2006-10-24 ES ES06819128T patent/ES2336610T3/en active Active
- 2006-10-24 DE DE502006005550T patent/DE502006005550D1/en active Active
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8128341B2 (en) | 2005-10-31 | 2012-03-06 | Siemens Aktiengesellschaft | Steam turbine |
Also Published As
Publication number | Publication date |
---|---|
DE502006005550D1 (en) | 2010-01-14 |
KR101014151B1 (en) | 2011-02-14 |
JP2009513866A (en) | 2009-04-02 |
CN101300405B (en) | 2013-05-29 |
ES2336610T3 (en) | 2010-04-14 |
US8128341B2 (en) | 2012-03-06 |
CN101300405A (en) | 2008-11-05 |
RU2008121935A (en) | 2009-12-10 |
PL1945911T3 (en) | 2010-05-31 |
WO2007051733A1 (en) | 2007-05-10 |
ATE450693T1 (en) | 2009-12-15 |
RU2410545C2 (en) | 2011-01-27 |
EP1945911A1 (en) | 2008-07-23 |
JP4662570B2 (en) | 2011-03-30 |
KR20080068893A (en) | 2008-07-24 |
EP1780376A1 (en) | 2007-05-02 |
US20090185895A1 (en) | 2009-07-23 |
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