EP2078821A1 - Steam turbine - Google Patents

Steam turbine Download PDF

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Publication number
EP2078821A1
EP2078821A1 EP08000385A EP08000385A EP2078821A1 EP 2078821 A1 EP2078821 A1 EP 2078821A1 EP 08000385 A EP08000385 A EP 08000385A EP 08000385 A EP08000385 A EP 08000385A EP 2078821 A1 EP2078821 A1 EP 2078821A1
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EP
European Patent Office
Prior art keywords
control wheel
section
flow path
cross
inner housing
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
EP08000385A
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German (de)
French (fr)
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EP2078821B1 (en
Inventor
Olaf Schmidt
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
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Siemens AG
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Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to PL08000385T priority Critical patent/PL2078821T3/en
Priority to EP08000385A priority patent/EP2078821B1/en
Priority to DE502008002724T priority patent/DE502008002724D1/en
Priority to AT08000385T priority patent/ATE500400T1/en
Publication of EP2078821A1 publication Critical patent/EP2078821A1/en
Application granted granted Critical
Publication of EP2078821B1 publication Critical patent/EP2078821B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/023—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines the working-fluid being divided into several separate flows ; several separate fluid flows being united in a single flow; the machine or engine having provision for two or more different possible fluid flow paths
    • 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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/10—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines having two or more stages subjected to working-fluid flow without essential intermediate pressure change, i.e. with velocity stages
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/18—Final actuators arranged in stator parts varying effective number of nozzles or guide conduits, e.g. sequentially operable valves for steam turbines
    • 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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
    • F01D9/047—Nozzle boxes
    • 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

Definitions

  • the invention relates to a steam turbine with a rotor, on which a first control wheel and a reaction part are arranged according to the features of the preamble of claim 1
  • the maximum possible volume flow is limited, inter alia, by the mechanical strength of the components of the control wheel.
  • the volume flow required for many applications at a given speed can only be achieved with the maximum pressure ratio via the control wheel. If the maximum pressure ratio is not reached, then this leads to efficiency losses in the control wheel and thus to an increased steam consumption, since the control wheel can not be operated in optimal efficiency. If, instead, the speed is reduced, this either leads to an increase in costs, because more stages are required for the steam turbine as well as the driven machine, for example the compressor, and / or also for an increased steam consumption, since the driven machine, e.g. B. the compressor can not be operated at optimum speed.
  • the invention has for its object to make the generic steam turbine so that the flow rate can be increased with the same efficiency, without the steam consumption or system costs are increased.
  • the steam turbine has an inner casing 1 and a rotor 2 rotating in the inner casing 1.
  • a reaction part with a plurality of impellers 4 provided with blades is arranged, which circulate in a flow-passage channel 5 delimited by the housing.
  • a ring of housing-fixed guide wheels 6 is arranged before each ring of wheels 4, a ring of housing-fixed guide wheels 6 is arranged.
  • a first control wheel 7 is disposed in front of the reaction part 3, which is provided on its periphery with blades.
  • the inner housing 1 consists of a lower part 1a and an upper part 1b, which are interconnected along a horizontal parting line.
  • the inner casing 1 is provided with an inlet part 8 serving as a steam supply, which has a plurality of inflow bores 9 which are connected to supply ducts (not shown) provided with steam valves.
  • the inflow holes 9 are connected within the inner housing 1 with an inflow segmentation 10, which are in communication with the inflow section 11 of the first control wheel 7 formed by nozzles.
  • the outflow cross section of the first control wheel 7 is in turn connected to the flow cross section 12 of the flow ring channel 5 in connection.
  • the flow cross section 12 of the flow ring channel 5 is formed by the first ring of the guide wheels 6.
  • first flow path 14 and the third flow path 16 are guided in parallel between the steam feed or the inflow part 8 and the inflow cross sections 12, 18 of the two control wheels 7, 13.
  • the second flow path 15 and the fourth flow path 17 unite behind the outflow cross sections and open together into the flow cross section 12 of the flow channel 5.
  • the first flow path 15 is led out of the inner housing 1, guided around the outside around the first control wheel 7 and guided back into the inner housing 1 behind the first control wheel 7, where the 2nd flow path merges with the fourth flow path 17 and in the inflow cross section 12 of the flow ring channel 5 opens.
  • the third flow path 16 is separated from the second flow path 15 by the inner housing 1 out.
  • a radially inner annular channel 19 and a radially outer annular channel 20 are formed which lead to the inflow cross section 11, 18 or the nozzles of the first and second control wheels 7, 13 and which guide the first flow path 14 and the third flow path 16 represent.
  • Behind the first control wheel 7 a plurality of evenly distributed over the circumference overflow pipes 21 are led out by penetration of the outer annular channel 20 sealed from the inner housing 1.
  • the overflow tubes 21 are guided back into the inner housing 1 behind the second control wheel 13.
  • the total cross section of the overflow tubes 21 is dimensioned sufficiently large, so that the flow losses remain low.
  • the overflow tubes 21 are arranged so that flow losses in the flow of the nozzles of the second control wheel 13 remain small.
  • the overflow tubes 21 are to be sealed on the high pressure side, z. B. welding, and there are suitable measures z. B. Federal seats to minimize leakage.
  • the overflow pipes 21 must be guided with heat-elastic play with the casting contour of the inner housing 1.
  • the live steam is passed through the inner annular channel 19 of the inflow segmentation 10 and the nozzles at the flow cross section 11 on the first control wheel 7 and relaxed. After relaxing the steam flows through the overflow pipes 21 behind the second control wheel 13.
  • the live steam supply for the second control wheel 13 takes place within the outer annular channel 20 of the Einströmsegment réelle 10 past the overflow pipes 21 toward the Anströmquerites 18 of the second control wheel 13.
  • After relaxation combine the vapor streams of the first and second control wheel 7, 13, flow-through the downstream stages of the reaction part 3 of the steam turbine and relax further. Relative to the previous solution with a single control wheel is by the inventive solution achieved a total loading of the control level of 200%.
  • the upper part 1b and the lower part 1a of the inner housing 1 are fluidly separated from each other.
  • the second flow path 15 is guided through the lower part 1a of the inner casing 1 to the lower part of the flow cross-section 18 of the second control wheel 13 and the third flow path 16 through the upper part 1b of the inner housing 1 to the upper part of the flow cross-section 18 of the second control wheel 13 ,
  • an inner channel 22 is formed in the inflow segmentation 10, which leads to the inflow cross section 11 or the nozzles of the first control wheel 7 and which represents the first flow path 14.
  • a channel 23 of semicircular cross section is arranged, which bridges the first control wheel 7 and leads to the upper part of the flow cross section 18 of the second control wheel 13.
  • a gap 24 of semicircular cross section between the rotor 2 and the inner wall of the inner housing 1 is provided, which leads to the lower part of the flow cross section 18 of the second control wheel 13.
  • the live steam passes through the inner channel 22 of the Einströmsegmenttechnik 10 to flow cross-section 11 of the first control wheel 7.
  • the relaxed steam is forced in the upper part 1 b of the inner housing 1 to flow around the rotor 2 tangentially so as to flow into the lower part 1 a of Inner housing 1 to arrive.
  • the relaxed steam of the first control wheel 7 thus flows exclusively in the lower part 1a of the inner housing 1 and reaches the second control wheel 13, wherein no work is done here.
  • the second control wheel 13 is acted upon exclusively in the upper part 1b of the inner housing 1 with live steam. Only after the expansion is completed on the second control wheel 13, the Combine steam flows and continue to relax in the direction of the downstream stages of the reaction part 3 of the steam turbine.
  • the first control wheel 7 is fully applied, while the second control wheel 13 is only half-acted. Therefore, it is assumed that a total admission of about 150%, based on the previously existing solution with a single control wheel.
  • the advantage of this second variant over the first variant is that the special deflection of the steam by means of the overflow tubes 21 is eliminated. However, this advantage is achieved at the expense of a 50% lower load on the control stage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Turbines (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

The turbine has a regulating wheel (13) arranged on a rotor (2) between another regulating wheel (7) and a reaction part (3), where the former regulating wheel is provided with a blade. A flow cross section (18) of the former regulating wheel is connected with a damping guide by a flow path (16) parallel to another flow path (14) guided by the latter regulating wheel. The flow cross section of the former regulating wheel is connected with a flow cross section (12) of the reaction part by third flow path (17) combined with a flow cross section of the latter regulating wheel.

Description

Die Erfindung betrifft eine Dampfturbine mit einem Rotor, auf dem ein erstes Regelrad und ein Reaktionsteil angeordnet sind gemäß den Merkmalen des Oberbegriffes des Anspruches 1The invention relates to a steam turbine with a rotor, on which a first control wheel and a reaction part are arranged according to the features of the preamble of claim 1

In derartigen Industriedampfturbinen ist der maximal mögliche Volumenstrom unter anderem durch die mechanische Festigkeit der Komponenten des Regelrads begrenzt. Der für viele Anwendungen erforderliche Volumenstrom bei vorgegebener Drehzahl kann nur bei maximalem Druckverhältnis über das Regelrad erzielt werden. Wenn das maximale Druckverhältnis nicht erreicht wird, dann führt das zu Wirkungsgradverlusten im Regelrad und damit zu einem erhöhten Dampfverbrauch, da das Regelrad nicht mehr im Wirkungsgradoptimum betrieben werden kann. Wird stattdessen die Drehzahl reduziert, führt das entweder zur Kostensteigerung, weil für die Dampfturbine wie auch die angetriebene Maschine, zum Beispiel den Kompressor, mehr Stufen erforderlich werden und/oder ebenfalls zu einem vergrößerten Dampfverbrauch, da die angetriebene Maschine, z. B. der Kompressor, nicht mit optimaler Drehzahl betrieben werden kann.In such industrial steam turbines, the maximum possible volume flow is limited, inter alia, by the mechanical strength of the components of the control wheel. The volume flow required for many applications at a given speed can only be achieved with the maximum pressure ratio via the control wheel. If the maximum pressure ratio is not reached, then this leads to efficiency losses in the control wheel and thus to an increased steam consumption, since the control wheel can not be operated in optimal efficiency. If, instead, the speed is reduced, this either leads to an increase in costs, because more stages are required for the steam turbine as well as the driven machine, for example the compressor, and / or also for an increased steam consumption, since the driven machine, e.g. B. the compressor can not be operated at optimum speed.

Bei Gegendruckturbinen mit hohem Gegendruck von größer 40 bar und Turbinen mit Entnahmedruck von größer 40 bar führen die oben aufgezeigten Schwierigkeiten hinsichtlich des erforderlichen Volumenstromes zur eingeschränkten Baubarkeit von Anwendungen mit hoher Drehzahl und gleichzeitig hoher Leistung und/oder Entnahmemenge, weil das Verhältnis der Drücke am Dampfeintritt und Dampfaustritt bzw. der Entnahmestelle relativ klein ist und somit große Strömungsquerschnitte, damit relativ große Laufschaufein im Regelrad erfordern. Damit treten gleichzeitig hohe Fliehkräfte und hohe Dampfbiegespannungen im Regelrad in solchen Anwendungen auf.In backpressure turbines with a high back pressure of greater than 40 bar and turbines with extraction pressure greater than 40 bar, the above-mentioned difficulties in terms of volume flow required for limited buildability of applications at high speed and high power and / or removal rate, because the ratio of the pressures at the steam inlet and steam outlet or the sampling point is relatively small and thus large flow cross-sections, thus requiring relatively large Laufschaufein in the control wheel. At the same time, high centrifugal forces and high steam bending stresses occur in the control wheel in such applications.

Bisher werden Industriedampfturbinen mit hohem Gegendruck von größer 40 bar und Turbinen mit Entnahmedruck von größer 40 bar mit Innengehäuse und einem oder gar keinem Regelrad ausgeführt. Der mögliche Volumenstrom bei gegebener Leistung ist wie erwähnt durch die Festigkeit des Regelrades begrenzt. Die Maschinen werden an der Obergrenze für den Volumenstrom bei gegebener Drehzahl betrieben, was zu einem erhöhten Dampfverbrauch führt, wenn das maximale Druckverhältnis nicht erreicht wird oder bei verringerter Drehzahl mit den erforderlichen zusätzlichen Stufen für Dampfturbine und angetriebene Maschine für gesteigerte Anlagenkosten und/oder verringerte Energiewirkungsgrade sorgt. Wird auf das Regelrad verzichtet, sind im Teillastbereich relativ mäßige Wirkungsgrade zu erzielen.So far, industrial steam turbines with high back pressure of greater than 40 bar and turbines with extraction pressure of greater than 40 Bar designed with inner housing and one or no control wheel. The possible volume flow at a given power is as mentioned limited by the strength of the control wheel. The machines operate at the upper limit of the volumetric flow rate at a given speed, resulting in increased steam consumption when the maximum pressure ratio is not achieved or at reduced speed with the required additional steam turbine and power plant stages for increased equipment costs and / or reduced energy efficiencies provides. If the control wheel is omitted, relatively moderate efficiencies can be achieved in the partial load range.

Der Erfindung liegt die Aufgabe zugrunde, die gattungsgemäße Dampfturbine so zu gestalten, dass der Volumenstrom bei gleichem Wirkungsgrad erhöht werden kann, ohne dass der Dampfverbrauch oder die Anlagenkosten erhöht werden.The invention has for its object to make the generic steam turbine so that the flow rate can be increased with the same efficiency, without the steam consumption or system costs are increased.

Die Aufgabe wird bei einer gattungsgemäßen Dampfturbine durch die kennzeichnenden Merkmale des Anspruches 1 gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand der Unteransprüche.The object is achieved in a generic steam turbine by the characterizing features of claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.

Verglichen mit der bisherigen Lösung mit einem Regelrad kann durch den erfindungsgemäßen Einsatz von zwei und mehr Regelrädern der zweifache oder mehrfache Volumenstrom bei gleichem Wirkungsgrad durchgesetzt werden. Das ermöglicht den Antrieb von Arbeitsmaschinen mit hoher Leistung bei hohen Drehzahlen und damit den Bau kompakter und dadurch kostengünstiger Maschinen und/oder Wirkungsgradverbesserungen in den angetriebenen Maschinen. In den meisten Fällen ist jedoch die Ausnutzung des Limits nicht erforderlich, und die Dampfturbine kann mit optimal beaufschlagten Regelstufen und nachgeschalteten Stufen, auch bei Turbinen mit hohem Gegendruck oder Entnahmedruck, mit einem deutlich geringeren Dampfverbrauch betrieben werden.Compared with the previous solution with a control wheel can be enforced by the inventive use of two or more control wheels of the double or multiple flow with the same efficiency. This allows the drive of high-performance machines at high speeds and thus the construction of compact and thus more cost-effective machines and / or efficiency improvements in the driven machines. In most cases, however, the utilization of the limit is not required, and the steam turbine can be operated with optimally applied control stages and downstream stages, even in turbines with high back pressure or extraction pressure, with a significantly lower steam consumption.

Zwei besondere Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden im Folgenden näher erläutert. Es zeigen:

Fig. 1
perspektivisch eine Dampfturbine mit einem Innengehäuse;
Fig. 2
den Schnitt II -II nach Fig. 1;
Fig. 3
den Schnitt III -III nach Fig. 1;
Fig. 4
perspektivisch eine Dampfturbine mit einem Innengehäuse gemäß einer anderen Ausführungsform;
Fig. 5
den Schnitt V -V nach Fig. 4 und
Fig. 6
den Schnitt VI -VI nach Fig. 4.
Two particular embodiments of the invention are illustrated in the drawings and will be explained in more detail below. Show it:
Fig. 1
in perspective, a steam turbine with an inner housing;
Fig. 2
the section II -II after Fig. 1 ;
Fig. 3
the section III -III after Fig. 1 ;
Fig. 4
in perspective, a steam turbine with an inner housing according to another embodiment;
Fig. 5
the section V-V after Fig. 4 and
Fig. 6
the section VI -VI after Fig. 4 ,

Die Dampfturbine weist ein Innengehäuse 1 und einen in dem Innengehäuse 1 rotierenden Rotor 2 auf. Auf dem Rotor 2 ist ein Reaktionsteil mit mehreren mit Laufschaufeln versehenen Laufrädern 4 angeordnet, die in einem durch das Gehäuse begrenzten Strömungsringkanal 5 umlaufen. Vor jedem Kranz von Laufrädern 4 ist ein Kranz von gehäusefesten Leiträdern 6 angeordnet. Auf dem Rotor 2 ist vor dem Reaktionsteil 3 ein erstes Regelrad 7 angeordnet, das auf seinem Umfang mit Schaufeln versehen ist.The steam turbine has an inner casing 1 and a rotor 2 rotating in the inner casing 1. On the rotor 2, a reaction part with a plurality of impellers 4 provided with blades is arranged, which circulate in a flow-passage channel 5 delimited by the housing. Before each ring of wheels 4, a ring of housing-fixed guide wheels 6 is arranged. On the rotor 2, a first control wheel 7 is disposed in front of the reaction part 3, which is provided on its periphery with blades.

Das Innengehäuse 1 besteht aus einem Unterteil 1a und einem Oberteil 1b, die längs einer horizontalen Trennfuge miteinander verbunden sind. Das Innengehäuse 1 ist mit einem als Dampfzuführung dienenden Einströmteil 8 versehen, das mehrere Einströmbohrungen 9 aufweist, die mit nicht gezeigten mit Dampfventilen versehenen Zufuhrkanälen verbunden sind.The inner housing 1 consists of a lower part 1a and an upper part 1b, which are interconnected along a horizontal parting line. The inner casing 1 is provided with an inlet part 8 serving as a steam supply, which has a plurality of inflow bores 9 which are connected to supply ducts (not shown) provided with steam valves.

Die Einströmbohrungen 9 sind innerhalb des Innengehäuses 1 mit einer Einströmsegmentierung 10 verbunden, die mit dem durch Düsen gebildeten Anströmquerschnitt 11 des ersten Regelrades 7 in Verbindung stehen. Der Abströmquerschnitt des ersten Regelrades 7 steht seinerseits mit dem Anströmquerschnitt 12 des Strömungsringkanals 5 in Verbindung. Der Anströmquerschnitt 12 des Strömungsringkanals 5 ist durch den ersten Kranz der Leiträder 6 gebildet.The inflow holes 9 are connected within the inner housing 1 with an inflow segmentation 10, which are in communication with the inflow section 11 of the first control wheel 7 formed by nozzles. The outflow cross section of the first control wheel 7 is in turn connected to the flow cross section 12 of the flow ring channel 5 in connection. The flow cross section 12 of the flow ring channel 5 is formed by the first ring of the guide wheels 6.

Zwischen dem ersten Regelrad 7 und dem Reaktionsteil 3 ist auf dem Rotor 2 ein zweites gleichartiges Regelrad 13 angeordnet. Anstelle eines Regelrades können auch mehrere Regelräder vorgesehen werden. Hinsichtlich der Strömung des Dampfes innerhalb des Innengehäuses 1 sind die Regelräder 7, 13 parallel geschaltet. Dazu sind vier Strömungspfade gebildet, die im Zusammenhang mit zwei in den Fig. 1 bis 3 und 4 bis 6 gezeigten Varianten nachfolgend beschrieben werden:

  • Der 1. Strömungspfad 14 verläuft von der Dampfzuführung oder dem Einströmteil 8 zu dem Anströmquerschnitt 11 des ersten Regelrades 7;
  • der 2. Strömungspfad 15 verläuft vom Abströmquerschnitt des ersten Regelrades 7 zum Strömungsringkanal 5;
  • der 3. Strömungspfad 16 verläuft von der Dampfzuführung oder dem Einströmteil 8 zu dem Anströmquerschnitt 18 des zweiten Regelrades 13 und
  • der 4. Strömungspfad 17 verläuft vom Abströmquerschnitt des zweiten Regelrades 13 zum Strömungsringkanal 5.
Between the first control wheel 7 and the reaction part 3, a second similar control wheel 13 is arranged on the rotor 2. Instead of a control wheel and more control wheels can be provided. With regard to the flow of steam within the inner housing 1, the control wheels 7, 13 are connected in parallel. For this purpose, four flow paths are formed, which in connection with two in the Fig. 1 to 3 and 4 to 6 variants shown below are described below:
  • The first flow path 14 extends from the steam supply or the inflow part 8 to the inflow cross section 11 of the first control wheel 7;
  • the second flow path 15 extends from the outflow cross section of the first control wheel 7 to the flow channel 5;
  • the third flow path 16 extends from the steam supply or the inflow part 8 to the flow cross-section 18 of the second control wheel 13 and
  • the fourth flow path 17 extends from the outflow cross section of the second control wheel 13 to the flow channel 5.

In beiden Varianten sind der 1. Strömungspfad 14 und der 3. Strömungspfad 16 zwischen der Dampfzuführung oder dem Einströmteil 8 und den Anströmquerschnitten 12, 18 der beiden Regelräder 7, 13 parallel geführt. Der 2. Strömungspfad 15 und der 4. Strömungspfad 17 vereinigen sich hinter den Abströmquerschnitten und münden gemeinsam in den Anströmquerschnitt 12 des Strömungsringkanals 5 ein.In both variants, the first flow path 14 and the third flow path 16 are guided in parallel between the steam feed or the inflow part 8 and the inflow cross sections 12, 18 of the two control wheels 7, 13. The second flow path 15 and the fourth flow path 17 unite behind the outflow cross sections and open together into the flow cross section 12 of the flow channel 5.

Bei der in den Fig. 1 bis 3 dargestellten ersten Variante ist der 2. Strömungspfad 15 aus dem Innengehäuse 1 herausgeführt, außen um das erste Regelrad 7 herumgeführt und hinter dem ersten Regelrad 7 wieder in das Innengehäuse 1 hineingeführt, wo der 2. Strömungspfad sich mit dem 4. Strömungspfad 17 vereinigt und in den Anströmquerschnitt 12 des Strömungsringkanals 5 einmündet. Der 3. Strömungspfad 16 ist getrennt von dem 2. Strömungspfad 15 durch das Innengehäuse 1 geführt.In the in the Fig. 1 to 3 the first flow path 15 is led out of the inner housing 1, guided around the outside around the first control wheel 7 and guided back into the inner housing 1 behind the first control wheel 7, where the 2nd flow path merges with the fourth flow path 17 and in the inflow cross section 12 of the flow ring channel 5 opens. The third flow path 16 is separated from the second flow path 15 by the inner housing 1 out.

Gemäß den Fig. 1 bis 3 ist in der Einströmsegmentierung 10 ein radial innerer Ringkanal 19 und ein radial äußerer Ringkanal 20 gebildet, die zu dem Anströmquerschnitt 11, 18 oder den Düsen des ersten und des zweiten Regelrades 7, 13 führen und die den 1. Strömungspfad 14 und den 3. Strömungspfad 16 darstellen. Hinter dem ersten Regelrad 7 sind mehrere gleichmäßig über den Umfang verteilte Überströmrohre 21 unter Durchdringung des äußeren Ringkanals 20 abgedichtet aus dem Innengehäuse 1 herausgeführt. Die Überströmrohre 21 sind hinter dem zweiten Regelrad 13 wieder in das Innengehäuse 1 hineingeführt. Der Gesamtquerschnitt der Überströmrohre 21 ist ausreichend groß bemessen, so dass die Strömungsverluste gering bleiben. Die Überströmrohre 21 sind so angeordnet, dass auch Strömungsverluste in der Anströmung der Düsen des zweiten Regelrades 13 klein bleiben. Die Überströmrohre 21 sind auf der Hochdruckseite abzudichten, z. B. einzuschweißen, und es sind geeignete Maßnahmen z. B. Bundsitze vorzusehen, um Leckagen zu minimieren. Die Überströmrohre 21 müssen wärmeelastisch mit Spiel durch die Gusskontur des Innengehäuses 1 geführt werden.According to the Fig. 1 to 3 In the inflow segmentation 10, a radially inner annular channel 19 and a radially outer annular channel 20 are formed which lead to the inflow cross section 11, 18 or the nozzles of the first and second control wheels 7, 13 and which guide the first flow path 14 and the third flow path 16 represent. Behind the first control wheel 7 a plurality of evenly distributed over the circumference overflow pipes 21 are led out by penetration of the outer annular channel 20 sealed from the inner housing 1. The overflow tubes 21 are guided back into the inner housing 1 behind the second control wheel 13. The total cross section of the overflow tubes 21 is dimensioned sufficiently large, so that the flow losses remain low. The overflow tubes 21 are arranged so that flow losses in the flow of the nozzles of the second control wheel 13 remain small. The overflow tubes 21 are to be sealed on the high pressure side, z. B. welding, and there are suitable measures z. B. Federal seats to minimize leakage. The overflow pipes 21 must be guided with heat-elastic play with the casting contour of the inner housing 1.

Der Frischdampf wird durch den inneren Ringkanal 19 der Einströmsegmentierung 10 und die Düsen am Anströmquerschnitt 11 auf das erste Regelrad 7 geleitet und entspannt. Nach dem Entspannen strömt der Dampf über die Überströmrohre 21 hinter das zweite Regelrad 13. Die Frischdampfzuführung für das zweite Regelrad 13 erfolgt innerhalb des äußeren Ringkanal 20 der Einströmsegmentierung 10 vorbei an den Überströmrohren 21 hin zu dem Anströmquerschnitt 18 des zweiten Regelrades 13. Nach der Entspannung vereinigen sich die Dampfströme des ersten und des zweiten Regelrades 7, 13, strömen-durch die nachgeschalteten Stufen des Reaktionsteiles 3 der Dampfturbine und entspannen weiter. Bezogen auf die bisherige Lösung mit einem einzigen Regelrad wird durch die erfindungsgemäße Lösung eine Gesamtbeaufschlagung der Regelstufe von 200% erreicht.The live steam is passed through the inner annular channel 19 of the inflow segmentation 10 and the nozzles at the flow cross section 11 on the first control wheel 7 and relaxed. After relaxing the steam flows through the overflow pipes 21 behind the second control wheel 13. The live steam supply for the second control wheel 13 takes place within the outer annular channel 20 of the Einströmsegmentierung 10 past the overflow pipes 21 toward the Anströmquerschnitt 18 of the second control wheel 13. After relaxation combine the vapor streams of the first and second control wheel 7, 13, flow-through the downstream stages of the reaction part 3 of the steam turbine and relax further. Relative to the previous solution with a single control wheel is by the inventive solution achieved a total loading of the control level of 200%.

Bei der in den Fig. 4 bis 6 dargestellten zweiten Variante sind der Oberteil 1b und der Unterteil 1a des Innengehäuses 1 strömungsmäßig voneinander getrennt. Der 2. Strömungspfad 15 ist durch den Unterteil 1a des Innengegehäuse 1 zu dem unteren Teil des Anströmquerschnittes 18 des zweiten Regelrades 13 und der 3. Strömungspfad 16 ist durch den Oberteil 1b des Innengehäuses 1 zu dem oberen Teil des Anströmquerschnittes 18 des zweiten Regelrades 13 geführt.In the in the 4 to 6 illustrated second variant, the upper part 1b and the lower part 1a of the inner housing 1 are fluidly separated from each other. The second flow path 15 is guided through the lower part 1a of the inner casing 1 to the lower part of the flow cross-section 18 of the second control wheel 13 and the third flow path 16 through the upper part 1b of the inner housing 1 to the upper part of the flow cross-section 18 of the second control wheel 13 ,

Gemäß den Fig. 4 bis 6 ist wiederum in der Einströmsegmentierung 10 ein innerer Kanal 22 gebildet, der zu dem Anströmquerschnitt 11 oder den Düsen des ersten Regelrades 7 führt und der den 1. Strömungspfad 14 darstellt. Im Oberteil 1b des Innengehäuses 1 ist ein Kanal 23 von halbkreisförmigem Querschnitt angeordnet, der das erste Regelrad 7 überbrückt und zu dem oberen Teil des Anströmquerschnittes 18 des zweiten Regelrades 13 führt. Im Unterteil 1a des Innengehäuses 1 ist ein Zwischenraum 24 von halbkreisförmigem Querschnitt zwischen dem Rotor 2 und der Innenwand des Innengehäuses 1 vorgesehen, der zu dem unteren Teil des Anströmquerschnittes 18 des zweiten Regelrades 13 führt.According to the 4 to 6 In turn, an inner channel 22 is formed in the inflow segmentation 10, which leads to the inflow cross section 11 or the nozzles of the first control wheel 7 and which represents the first flow path 14. In the upper part 1 b of the inner housing 1, a channel 23 of semicircular cross section is arranged, which bridges the first control wheel 7 and leads to the upper part of the flow cross section 18 of the second control wheel 13. In the lower part 1a of the inner housing 1, a gap 24 of semicircular cross section between the rotor 2 and the inner wall of the inner housing 1 is provided, which leads to the lower part of the flow cross section 18 of the second control wheel 13.

Wie bei der ersten Variante gelangt der Frischdampf durch den inneren Kanal 22 der Einströmsegmentierung 10 zum Anströmquerschnitt 11 des ersten Regelrades 7. Der entspannte Dampf wird im Oberteil 1b des Innengehäuses 1 gezwungen, den Rotor 2 tangential zu umströmen, um so in den Unterteil 1a des Innengehäuses 1 zu gelangen. Der entspannte Dampf des ersten Regelrades 7 strömt also ausschließlich im Unterteil 1a des Innengehäuses 1 und gelangt zum zweiten Regelrad 13, wobei hier keine Arbeit verrichtet wird. Das zweite Regelrad 13 wird ausschließlich im Oberteil 1b des Innengehäuses 1 mit Frischdampf beaufschlagt. Erst nachdem die Expansion am zweiten Regelrad 13 vollzogen ist, können sich die Dampfströme vereinigen und in Richtung der nachgeschalteten Stufen des Reaktionsteiles 3 der Dampfturbine weiter entspannen.As in the first variant of the live steam passes through the inner channel 22 of the Einströmsegmentierung 10 to flow cross-section 11 of the first control wheel 7. The relaxed steam is forced in the upper part 1 b of the inner housing 1 to flow around the rotor 2 tangentially so as to flow into the lower part 1 a of Inner housing 1 to arrive. The relaxed steam of the first control wheel 7 thus flows exclusively in the lower part 1a of the inner housing 1 and reaches the second control wheel 13, wherein no work is done here. The second control wheel 13 is acted upon exclusively in the upper part 1b of the inner housing 1 with live steam. Only after the expansion is completed on the second control wheel 13, the Combine steam flows and continue to relax in the direction of the downstream stages of the reaction part 3 of the steam turbine.

Das erste Regelrad 7 ist voll beaufschlagt, während das zweite Regelrad 13 nur halbbeaufschlagt ist. Daher geht man von einer Gesamtbeaufschlagung von ca. 150% aus, bezogen auf die bisher existierende Lösung mit einem einzigen Regelrad. Der Vorteil dieser 2. Variante gegenüber der ersten Variante ist, dass die besondere Umlenkung des Dampfes mittels der Überströmrohre 21 entfällt. Jedoch wird dieser Vorteil zu Lasten einer um 50% geringeren Beaufschlagung der Regelstufe erreicht.The first control wheel 7 is fully applied, while the second control wheel 13 is only half-acted. Therefore, it is assumed that a total admission of about 150%, based on the previously existing solution with a single control wheel. The advantage of this second variant over the first variant is that the special deflection of the steam by means of the overflow tubes 21 is eliminated. However, this advantage is achieved at the expense of a 50% lower load on the control stage.

Claims (6)

Dampfturbine mit einem Rotor (2), auf dem ein mit Schaufeln versehenes erstes Regelrad (7) und ein Reaktionsteil (3) mit einem oder mehreren mit Laufschaufeln versehenen Laufrädern (4) angeordnet sind, und mit einem aus einem Oberteil (1b) und einem Unterteil (1a) bestehenden Innengehäuse (1), das mit einer Dampfzuführung versehen ist, wobei die Dampfzuführung über einen ersten Strömungspfad (14) mit dem Anströmquerschnitt (11) des ersten Regelrades (7) verbunden ist und wobei der Abströmquerschnitt des ersten Regelrades (7) über einen zweiten Strömungspfad (15) mit dem Anströmquerschnitt (12) des Reaktionsteiles (3) verbunden ist,
dadurch gekennzeichnet, dass
auf dem Rotor (2) zwischen dem ersten Regelrad (7) und dem Reaktionsteil (3) mindestens ein zweites mit Schaufeln versehenes Regelrad (13) angeordnet ist,
dass der Anströmquerschnitt (18) des zweiten Regelrades (13) über einen dritten Strömungspfad (16) parallel zu dem zu dem ersten Regelrad (7) führenden ersten Strömungspfad (14) mit der Dampfzuführung verbunden ist und
dass der Abströmquerschnitt des zweiten Regelrades (13) zusammen mit dem Abströmquerschnitt des ersten Regelrad (7) über einen vierten Strömungspfad (17) mit dem Anströmquerschnitt (12) des Reaktionsteiles (3) verbunden ist.A steam turbine having a rotor (2) on which a blade-equipped first control wheel (7) and a reaction part (3) with one or more blades provided with blades (4) are arranged, and with one of an upper part (1 b) and a Lower part (1 a) existing inner housing (1), which is provided with a steam supply, wherein the steam supply via a first flow path (14) with the flow cross section (11) of the first control wheel (7) is connected and wherein the outflow cross section of the first control wheel (7 ) is connected via a second flow path (15) with the flow cross-section (12) of the reaction part (3),
characterized in that
on the rotor (2) between the first control wheel (7) and the reaction part (3) at least a second blades provided with control wheel (13) is arranged,
that the flow cross-section (18) of the second control wheel (13) via a third flow path (16) parallel to the first control wheel (7) leading first flow path (14) is connected to the steam supply and
the outflow cross section of the second control wheel (13) is connected together with the outflow cross section of the first control wheel (7) via a fourth flow path (17) to the flow cross section (12) of the reaction part (3). Dampfturbine nach Anspruch 1,
dadurch gekennzeichnet, dass
der zweite, von dem Abströmquerschnitt des ersten Regelrades (7) zu dem Anströmquerschnitt (12) des Reaktionsteiles (3) führende Strömungspfad (15) aus dem Innengehäuse (1) herausgeführt und um das erste Regelrad (7) herum wieder in das Innengehäuse (1) hineingeführt ist und dass der dritte, von der Dampfzuführung zu dem Anströmquerschnitt (18) des zweiten Regelrades (13) führende Strömungspfad (16) getrennt von dem zweiten Strömungspfad (15) durch den Oberteil (1b) und den Unterteil (1a) des Innengehäuses (1) geführt ist.Steam turbine according to claim 1,
characterized in that
the second, of the outflow cross section of the first control wheel (7) leading to the flow cross section (12) of the reaction part (3) leading out flow path (15) from the inner housing (1) and around the first control wheel (7) around back into the inner housing (1 ) and that the third, from the steam supply to the Anströmquerschnitt (18) of the second control wheel (13) leading flow path (16) separated from the second flow path (15) through the upper part (1b) and the lower part (1a) of the inner housing (1) is guided. Dampfturbine nach Anspruch 1,
dadurch gekennzeichnet, dass
der zweite, von dem Abströmquerschnitt des ersten Regelrades (7) ausgehende Strömungspfad (15) durch den Unterteil (1a) des Innengehäuses (1) zu dem unteren Teil des Anströmquerschnittes (18) des zweiten Regelrades (13) geführt ist und dass der dritte, von der Dampfzuführung zu dem Anströmquerschnitt (18) des zweiten Regelrades (13) führende Strömungspfad (16) um das erste Regelrad (7) herum durch den Oberteil (1b) des Innengehäuses (1) geführt ist.Steam turbine according to claim 1,
characterized in that
the second, from the outflow cross section of the first control wheel (7) outgoing flow path (15) through the lower part (1 a) of the inner housing (1) to the lower part of the flow cross-section (18) of the second control wheel (13) is guided and that the third, from the steam supply to the flow cross-section (18) of the second control wheel (13) leading flow path (16) around the first control wheel (7) around by the upper part (1b) of the inner housing (1) is guided. Dampfturbine nach Anspruch 1 und 2,
dadurch gekennzeichnet, dass
der zweite von dem Abströmquerschnitt des ersten Regelrades (7) ausgehende Strömungspfad (15) durch mehrere Überströmrohre (21) gebildet ist, die aus dem Oberteil (1b) und Unterteil (1a) des Innengehäuses (1) herausgeführt sind und hinter dem zweiten Regelrad (13) wieder in das Oberteil (1b) und Unterteil (1a) des Innengehäuses (1) hineingeführt sind.Steam turbine according to claim 1 and 2,
characterized in that
the second from the Abströmquerschnitt the first control wheel (7) outgoing flow path (15) is formed by a plurality of overflow tubes (21), which are led out of the upper part (1b) and lower part (1a) of the inner housing (1) and behind the second control wheel ( 13) are again guided into the upper part (1b) and lower part (1a) of the inner housing (1). Dampfturbine nach Anspruch 1 und 3,
dadurch gekennzeichnet, dass
der zweite, von den Abströmquerschnitt des ersten Regelrades (13) ausgehende Strömungspfad (15) durch einen Zwischenraum (24) zwischen dem Rotor (2) und der Wand des Unterteils (1a) des Innengehäuses (1) gebildet ist und dass der dritte von der Dampfzuführung zu dem Anströmquerschnitt (18) des zweiten Regelrades (13) führende Strömungspfad (16) durch einen Kanal (23) gebildet ist, der im Oberteil (1b) des Innengehäuses (1) unter Überbrückung des ersten Regelrades (7) angeordnet ist.Steam turbine according to claim 1 and 3,
characterized in that
the second, from the outflow cross section of the first control wheel (13) outgoing flow path (15) by a gap (24) between the rotor (2) and the wall of the lower part (1 a) of the inner housing (1) is formed and that the third of the Steam supply to the Anströmquerschnitt (18) of the second control wheel (13) leading flow path (16) by a channel (23) is formed in the upper part (1b) of the inner housing (1) with bridging the first control wheel (7). Dampfturbine nach Anspruch 5,
dadurch gekennzeichnet, dass
der dritte Strömungspfad (16) durch den Kanal (23) mit einem halbringförmigen Querschnitt ausgebildet ist.Steam turbine according to claim 5,
characterized in that
the third flow path (16) is formed through the channel (23) with a semi-annular cross-section.
EP08000385A 2008-01-10 2008-01-10 Steam turbine Not-in-force EP2078821B1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PL08000385T PL2078821T3 (en) 2008-01-10 2008-01-10 Steam turbine
EP08000385A EP2078821B1 (en) 2008-01-10 2008-01-10 Steam turbine
DE502008002724T DE502008002724D1 (en) 2008-01-10 2008-01-10 steam turbine
AT08000385T ATE500400T1 (en) 2008-01-10 2008-01-10 STEAM TURBINE

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08000385A EP2078821B1 (en) 2008-01-10 2008-01-10 Steam turbine

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EP2078821A1 true EP2078821A1 (en) 2009-07-15
EP2078821B1 EP2078821B1 (en) 2011-03-02

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITCO20130001A1 (en) * 2013-01-23 2014-07-24 Nuovo Pignone Srl INTERNAL CASING FOR STEAM TURBINE ENGINE

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD290703A5 (en) * 1989-12-22 1991-06-06 Veb Bergmann-Borsig,De INTRODUCTION OF A SINGLE-SIDED STEAM TURBINE WITH A DUESTRY GROUP CONTROL
EP0575659A1 (en) * 1992-06-26 1993-12-29 Asea Brown Boveri Ag Inlet casing for a steam turbine
DE4344070A1 (en) * 1993-01-25 1994-07-28 Abb Patent Gmbh Steam turbine with facility to disconnect part of steam mass flow
EP1632650A1 (en) * 2004-09-01 2006-03-08 Siemens Aktiengesellschaft Steam turbine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD290703A5 (en) * 1989-12-22 1991-06-06 Veb Bergmann-Borsig,De INTRODUCTION OF A SINGLE-SIDED STEAM TURBINE WITH A DUESTRY GROUP CONTROL
EP0575659A1 (en) * 1992-06-26 1993-12-29 Asea Brown Boveri Ag Inlet casing for a steam turbine
DE4344070A1 (en) * 1993-01-25 1994-07-28 Abb Patent Gmbh Steam turbine with facility to disconnect part of steam mass flow
EP1632650A1 (en) * 2004-09-01 2006-03-08 Siemens Aktiengesellschaft Steam turbine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITCO20130001A1 (en) * 2013-01-23 2014-07-24 Nuovo Pignone Srl INTERNAL CASING FOR STEAM TURBINE ENGINE
WO2014114657A1 (en) * 2013-01-23 2014-07-31 Nuovo Pignone Srl Inner casing with impulse and reaction stages for a steam turbine engine
US10094245B2 (en) 2013-01-23 2018-10-09 Nuovo Pignone Srl Inner casing for steam turbine engine
US10844748B2 (en) 2013-01-23 2020-11-24 Nuovo Pignone Srl Inner casing for steam turbine engine

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ATE500400T1 (en) 2011-03-15
PL2078821T3 (en) 2011-07-29
EP2078821B1 (en) 2011-03-02
DE502008002724D1 (en) 2011-04-14

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