EP2859192B1 - Inlet segment for a flow machine - Google Patents

Inlet segment for a flow machine Download PDF

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Publication number
EP2859192B1
EP2859192B1 EP13739171.0A EP13739171A EP2859192B1 EP 2859192 B1 EP2859192 B1 EP 2859192B1 EP 13739171 A EP13739171 A EP 13739171A EP 2859192 B1 EP2859192 B1 EP 2859192B1
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EP
European Patent Office
Prior art keywords
inflow
rotor
segment
bores
inflow segment
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.)
Not-in-force
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EP13739171.0A
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German (de)
French (fr)
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EP2859192A1 (en
Inventor
Ingo Förster
Christian Musch
Uwe Zander
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Siemens AG
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Siemens AG
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Priority to EP13739171.0A priority Critical patent/EP2859192B1/en
Publication of EP2859192A1 publication Critical patent/EP2859192A1/en
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Publication of EP2859192B1 publication Critical patent/EP2859192B1/en
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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
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F01D3/02—Machines or engines with axial-thrust balancing effected by working-fluid characterised by having one fluid flow in one axial direction and another fluid flow in the opposite direction
    • 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
    • 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
    • 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
    • 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
    • F01D9/041—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector using blades
    • 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
    • F01D9/06—Fluid supply conduits to nozzles or the like
    • 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
    • F01D9/06—Fluid supply conduits to nozzles or the like
    • F01D9/065—Fluid supply or removal conduits traversing the working fluid flow, e.g. for lubrication-, cooling-, or sealing fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2220/00—Application
    • F05B2220/30—Application in turbines
    • F05B2220/301—Application in turbines in steam turbines

Definitions

  • the invention relates to a turbomachine comprising a rotor rotatably supported about a rotation axis, rotor blades disposed on the rotor, a casing disposed around the rotor, vanes disposed on the casing, a flow passage interposed between formed in the housing and the housing is arranged for the inflow of steam, an inflow segment, which is arranged in the housing, inflow segment guide vanes, which are arranged in the inflow segment.
  • Turbomachines such as Steam turbines are used for example in the energy supply.
  • such turbomachines comprise a rotatably mounted rotor and a housing arranged around the rotatably mounted rotor.
  • the housing is divided into an inner housing and an outer housing arranged around the inner housing.
  • the rotors of such engineered turbomachines include blades that are disposed between vanes disposed on the inner shell and define a flow passage through which a flow medium flows.
  • steam is the flow medium.
  • the invention has set itself the task of specifying an improved turbomachine.
  • An essential feature here is that bores are carried out, which are arranged in the inflow segment and produce a fluidic connection between the inflow and a relief space, which is arranged between the inflow segment and the rotor.
  • the bores are designed in such a way that a part of an inflow steam is passed through the bores and part of the inflow steam through the inflow segment vanes.
  • the inflow segment has a hub-side ring segment, in which the bores are formed.
  • the bores are seen in the flow direction of the inflow vapor upstream of the inflow segment vanes arranged.
  • a portion of the steam can be discharged directly before flowing through the inflow ring. This allows better cooling.
  • the bores are inclined by an angle ⁇ which lies between 40 ° and 80 ° with respect to a radial direction passing through the axis of rotation. This allows optimal cooling effects to be achieved ; since the swirl of the steam flowing in under the inflow segment is essential for cooling as effectively as possible.
  • the inflow 11 is provided for the flow of steam and designed accordingly.
  • the inner housing 8 has in this area a projection 20 on which an inflow segment 21 is arranged.
  • the inflow segment 21 is substantially formed as a ring and installed in the inner housing 8. At the outer diameter of the inflow segment 21, the inflow segment 21 is fitted in a groove 22.
  • the inflow segment 21 has a hub-side ring segment 23 which is connected to the inner housing 8 via a second sealing element 24.
  • the hub-side ring segment 23 has a sealing groove 25 into which the second sealing element 24 is fitted.
  • the inner housing 8 also has a groove 26 in which the other end of the second sealing element 24 is arranged.
  • the inflow segment 21 has inflow segment vanes 27 integrally formed with the inflow segment 21.
  • FIG. 3 shows a sectional view through the inflow segment 21.
  • inflow segment vane is designated by reference numeral 27.
  • six holes 29 are executed, which are formed in a tangential direction to the discharge chamber 30 at an angle ⁇ .
  • the direction of rotation of the rotor 3 is counterclockwise.
  • the angle ⁇ is explained on the bore 29 in the twelve o'clock position. From the axis of rotation 2 from a reference line 35 is shown in the radial direction. At an angle ⁇ , which is between 40 ° and 80 °, a bore 29 is executed. Through this bore 29, the mass flow M 1 flows . Due to the applied twist of the steam undergoes a change in velocity and thus a reduction in the static temperature of the steam relative to the rotating system, which then leads to a cooling of the surface of the rotor 3 relative to the temperature of the mass flow M tot .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

Die Erfindung betrifft eine Strömungsmaschine, umfassend einen Rotor, der drehbar um eine Rotationsachse gelagert ist, Laufschaufeln, die auf dem Rotor angeordnet sind, ein Gehäuse, das um den Rotor angeordnet ist, Leitschaufeln, die am Gehäuse angeordnet sind, einen Strömungskanal, der zwischen dem Rotor und dem Gehäuse ausgebildet ist, eine Zuströmung, die im Gehäuse angeordnet ist und zum Zuströmen von Dampf ausgebildet ist, ein Einströmsegement, das im Gehäuse angeordnet ist, Einströmsegment-Leitschaufeln, die im Einströmsegment angeordnet sind.The invention relates to a turbomachine comprising a rotor rotatably supported about a rotation axis, rotor blades disposed on the rotor, a casing disposed around the rotor, vanes disposed on the casing, a flow passage interposed between formed in the housing and the housing is arranged for the inflow of steam, an inflow segment, which is arranged in the housing, inflow segment guide vanes, which are arranged in the inflow segment.

Strömungsmaschinen, wie z.B. Dampfturbinen, werden beispielsweise in der Energieversorgung eingesetzt. Im Wesentlichen umfassen solche Strömungsmaschinen einen drehbar gelagerten Rotor und ein um den drehbar gelagerten Rotor angeordnetes Gehäuse. In der Regel wird das Gehäuse in ein Innengehäuse und ein um das Innengehäuse angeordnetes Außengehäuse eingeteilt. Die Rotoren solch ausgeführter Strömungsmaschinen umfassen Laufschaufeln, die zwischen am Innengehäuse angeordneten Leitschaufeln angeordnet sind und einen Strömungskanal bilden, durch den ein Strömungsmedium strömt. In einer als Dampfturbine ausgebildeten Ausführungsform der Strömungsmaschine ist Dampf das Strömungsmedium.Turbomachines, such as Steam turbines are used for example in the energy supply. Essentially, such turbomachines comprise a rotatably mounted rotor and a housing arranged around the rotatably mounted rotor. As a rule, the housing is divided into an inner housing and an outer housing arranged around the inner housing. The rotors of such engineered turbomachines include blades that are disposed between vanes disposed on the inner shell and define a flow passage through which a flow medium flows. In an embodiment of the turbomachine designed as a steam turbine, steam is the flow medium.

Das in eine Strömungsmaschine einströmende Strömungsmedium weist vergleichsweise hohe Temperaturen auf. So ist bei Dampfturbinen als Ausführungsform einer Strömungsmaschine der Dampf derart erhitzt, dass der Dampf Temperaturen von über 600 C aufweisen kann. Solch hohe Temperaturen führen zu großen thermischen Belastungen der Strömungsmaschine. Insbesondere werden die Bauteile der Strömungsmaschine thermisch belastet, die im Einströmbereich des Strömungsmediums angeordnet sind. Darüber hinaus ist der Rotor ebenfalls besonders an der Stelle an der das Strömungsmedium in die Strömungsmaschine einströmt besonders thermisch belastet. Die Materialien müssen geeignet gewählt werden, damit die Strömungsmaschine betrieben werden kann.The flow medium flowing into a turbomachine has comparatively high temperatures. Thus, in the case of steam turbines as an embodiment of a turbomachine, the steam is heated in such a way that the steam can have temperatures of more than 600 ° C. Such high temperatures lead to large thermal loads on the turbomachine. In particular, the components of the turbomachine are thermally loaded, which are arranged in the inflow region of the flow medium. In addition, the rotor is also very special the point at which flows the flow medium in the turbomachine particularly thermally stressed. The materials must be chosen suitably so that the turbomachine can be operated.

Allerdings sind dadurch die Einsatzgrenzen eines Rotors begrenzt, da die thermische Belastung nur bis zu einem Grenzwert zulässig und möglich ist. Beispielsweise lassen die maßgeblichen Festigkeitskennwerte der eingesetzten Materialien bei zu hohen Temperaturen überproportional nach. Aus der Temperatur, die das Material des Rotors aufweist, ergeben sich beispielsweise die maximal zulässigen Wellendurchmesser, bezogen auf die Auslastung im Welleninneren oder auch maximal zulässige Fliehkräfte im randnahen Bereich von Rotoren, die besonders bei 60 Hz Anwendungen zur Einschränkung führen können. Abhilfe wird geschaffen durch Temperaturabsenkung, die durch Kühlung der Oberfläche erfolgen kann oder durch Kühlung des Welleninneren, die entweder eine Erweiterung der mechanischen Einsatzgrenzen des Rotors bei gegebenem Werkstoff erzielen oder in anderen Fällen ein Wechsel zu hochwertigeren und teureren Werkstoffen vermeiden.However, this limits the operating limits of a rotor, since the thermal load is only permissible and possible up to a limit value. For example, the relevant strength characteristics of the materials used at disproportionately lower at too high temperatures. From the temperature, which has the material of the rotor, resulting, for example, the maximum permissible shaft diameter, based on the load in the shaft interior or maximum permissible centrifugal forces in the near-edge region of rotors, which can lead to restrictions especially at 60 Hz applications. A remedy is provided by lowering the temperature, which can be done by cooling the surface or by cooling the shaft interior, which either achieve an extension of the mechanical limits of use of the rotor for a given material or avoid a change to higher quality and more expensive materials in other cases.

Derzeitige Strömungsmaschinen weisen ein Einströmsegment auf, das im Zuströmungskanal der Strömungsmaschine angeordne ist. Dieses Einströmsegment weist einen Leitschaufelring auf siehe z.B US 2 244 983 . Der in die Strömungsmaschine zuströmende Frischdampf trifft zunächst auf die Leitschaufeln dieses Einströmsegments. In der Regel wird dieses Einströmsegment am Innengehäuse angeordnet. Ein physikalischer Effekt, der mit dem Einströmsegment erzielt werden kann, ist, dass der Frischdampf einen erhöhten Drall aufweist und dadurch zu Temperaturabsenkungseffekten der Einströmentlastungsnut führt. Dadurch wird eine moderate Kühlung erreicht, die die thermische Auslastung der ersten Turbinenschaufelfüße als auch des Welleninneren reduziert. Solche Einströmsegmente werden auch als Diagonalstufen bezeichnet.Current turbomachines have an inflow segment which is arranged in the inflow passage of the turbomachine. This inflow segment has a vane ring, see eg US 2 244 983 , The fresh steam flowing into the turbomachine initially strikes the guide vanes of this inflow segment. As a rule, this inflow segment is arranged on the inner housing. A physical effect that can be achieved with the inflow segment is that the live steam has an increased swirl and thereby leads to temperature drop effects of the inflow relief groove. As a result, a moderate cooling is achieved, which reduces the thermal load of the first turbine blade feet and the shaft interior. Such inflow segments are also referred to as diagonal stages.

Die Erfindung hat es sich zur Aufgabe gemacht, eine verbesserte Strömungsmaschine anzugeben.The invention has set itself the task of specifying an improved turbomachine.

Erreicht wird dies durch eine Strömungsmaschine gemäß Anspruch 1.This is achieved by a turbomachine according to claim 1.

Ein wesentliches Merkmal hierbei ist, dass Bohrungen ausgeführt werden, die im Einströmsegment angeordnet sind und eine strömungstechnische Verbindung zwischen der Zuströmung und einem Entlastungsraum, der zwischen dem Einströmsegment und dem Rotor angeordnet ist, herstellt.An essential feature here is that bores are carried out, which are arranged in the inflow segment and produce a fluidic connection between the inflow and a relief space, which is arranged between the inflow segment and the rotor.

Erfindungsgemäß wird somit vorgeschlagen, die Temperatur an der Wellenoberfläche stärker abzusenken, indem Bohrungen, die als Tangentialbohrungen ausgeführt sind, angeordnet werden. Dadurch wird der Strömung des Strömungsmediums unterhalb des Einströmsegments eine vorgegebene Umfangsgeschwindigkeit aufgeprägt. Dadurch ergibt sich an der Wellenoberfläche der gewünschte Kühlungseffekt. Durch eine Benetzung des Bereichs der Wellenoberfläche in der Entlastungsnut mit Temperaturen unter der Frischdampf-Temperatur ergibt sich auch eine Temperaturabsenkung im Bereich der Wellenachse unter der ersten Laufschaufelklaue.According to the invention it is thus proposed to lower the temperature at the shaft surface stronger by holes that are designed as tangential holes are arranged. As a result, a predetermined peripheral speed is impressed on the flow of the flow medium below the inflow segment. This results in the desired cooling effect on the shaft surface. Wetting the region of the wave surface in the relief groove at temperatures below the live steam temperature also results in a temperature reduction in the region of the shaft axis under the first blade claw.

Vorteilhafte Weiterbildungen sind in den Unteransprüchen angegeben.Advantageous developments are specified in the subclaims.

So sind in einer ersten vorteilhaften Weiterbildung die Bohrungen derart ausgebildet, dass ein Teil eines Zuströmdampfes durch die Bohrungen und ein Teil des Zuströmdampfes durch die Einströmsegment-Leitschaufeln geführt wird.Thus, in a first advantageous development, the bores are designed in such a way that a part of an inflow steam is passed through the bores and part of the inflow steam through the inflow segment vanes.

In einer weiteren vorteilhaften Weiterbildung weist das Einströmsegment ein nabenseitiges Ringsegment auf, in dem die Bohrungen ausgebildet sind.In a further advantageous development, the inflow segment has a hub-side ring segment, in which the bores are formed.

Vorteilhafterweise sind die Bohrungen in Strömungsrichtung des Zuströmdampfes gesehen, vor den Einströmsegment-Leitschaufeln angeordnet. Dadurch kann ein Teil des Dampfes direkt vor dem Durchströmen durch den Einströmring abgeleitet werden. Dadurch ist eine bessere Kühlung möglich.Advantageously, the bores are seen in the flow direction of the inflow vapor upstream of the inflow segment vanes arranged. As a result, a portion of the steam can be discharged directly before flowing through the inflow ring. This allows better cooling.

Erfindungsgemäß sind die Bohrungen um einen Winkel α, der zwischen 40° und 80° liegt, gegenüber einer radialen Richtung, die durch die Rotationsachse geht, geneigt. Dadurch lassen sich optimale Kühlungseffekte erzielen; da der Drall des unter dem Einströmsegment einströmenden Dampfes wesentlich ist für eine möglichst effektive Kühlung.According to the invention, the bores are inclined by an angle α which lies between 40 ° and 80 ° with respect to a radial direction passing through the axis of rotation. This allows optimal cooling effects to be achieved ; since the swirl of the steam flowing in under the inflow segment is essential for cooling as effectively as possible.

In einer vorteilhaften Weiterbildung sind sechs Bohrungen ausgebildet, wobei die Anzahl von der jeweiligen Geometrie, Thermodynamik und Höhe des gewünschten Kühleffekts beeinflusst wird.In an advantageous development, six holes are formed, wherein the number of the respective geometry, thermodynamics and height of the desired cooling effect is influenced.

Die Erfindung wird anhand eines Ausführungsbeispiels anhand der schematisierten Zeichnungen näher erläutert.The invention will be explained in more detail with reference to an embodiment with reference to the schematic drawings.

Es zeigen:

Figur 1
eine schematische Schnittansicht durch einen Teil einer Strömungsmaschine;
Figur 2
eine teilperspektivische Ansicht eines Einströmrings;
Figur 3
eine Schnittansicht durch den Einströmring.
Show it:
FIG. 1
a schematic sectional view through a part of a turbomachine;
FIG. 2
a partial perspective view of an inflow ring;
FIG. 3
a sectional view through the inflow ring.

Die Figur 1 zeigt einen Ausschnitt einer Strömungsmaschine. Die in Figur 1 gezeigte Strömungsmaschine ist als eine Dampfturbine 1 ausgebildet. Die Dampfturbine 1 weist einen um eine Rotationsachse 2 drehbar gelagerten Rotor 3 auf. Der Rotor 3 weist verschiedene Durchmesser auf. Auf einer Rotoroberfläche 4 sind Laufschaufeln 5 angeordnet. Der Übersichtlichkeit wegen ist lediglich eine Laufschaufel 5 dargestellt. Die Laufschaufel 5 weist einen Laufschaufelfuß 6 auf, der in einer entsprechenden Rotornut 7 angeordnet ist. Das unmittelbar zum Laufschaufelfuß 6 benachbarte Rotormaterial wird auch als Laufschaufelklaue bezeichnet.The FIG. 1 shows a section of a turbomachine. In the FIG. 1 shown turbomachine is designed as a steam turbine 1. The steam turbine 1 has a rotor 3 rotatably mounted about a rotation axis 2. The rotor 3 has different diameters. On a rotor surface 4 blades 5 are arranged. For the sake of clarity, only one blade 5 is shown. The blade 5 has a blade root 6, which in a corresponding rotor groove 7 is arranged. The rotor material immediately adjacent to the blade root 6 is also referred to as a blade claw.

Um den Rotor 3 ist ein Innengehäuse 8 angeordnet, das im Wesentlichen und je nach Bauform aus einem oberen Innengehäuseteil und einem unteren Innengehäuseteil bei horizontaler Teilfuge oder entsprechend aus linkem und rechtem Innengehäuseteil bei vertikaler Teilfuge ausgebildet ist. Um das Innengehäuse 8 ist ein Außengehäuse 9 angeordnet. Zwischen dem Innengehäuse 8 und dem Außengehäuse 9 ist ein Dichtelement 10 angeordnet.To the rotor 3, an inner housing 8 is arranged, which is formed substantially and depending on the design of an upper inner housing part and a lower inner housing part with horizontal parting or correspondingly from the left and right inner housing part with vertical parting line. To the inner housing 8, an outer housing 9 is arranged. Between the inner housing 8 and the outer housing 9, a sealing element 10 is arranged.

Das Innengehäuse 8 ist derart ausgebildet, dass durch eine nicht näher dargestellte Dampfzuführung eine Zuströmung 11 ausgebildet ist. Durch diese Zuströmung 11 wird Frischdampf, der Temperaturen bis 650°C oder mehr aufweisen kann, zugeführt. Das Innengehäuse 8 trägt zudem Leitschaufeln 12, die über Leitschaufelfüße 13 in entsprechende Innengehäusenuten 14 angeordnet sind.The inner housing 8 is formed such that an inflow 11 is formed by a steam supply, not shown. By this inflow 11 is fresh steam, which may have temperatures of up to 650 ° C or more supplied. The inner housing 8 also carries guide vanes 12, which are arranged via guide blade feet 13 in corresponding inner housing grooves 14.

Der Übersichtlichkeit wegen ist lediglich eine Leitschaufel 12 dargestellt. Zwischen dem Innengehäuse 8 und dem Rotor 3 ist ein Strömungskanal 15 ausgeführt, der durch die Leitschaufeln 12 und Laufschaufeln 5 gebildet ist. Der Rotor 3 ist mit einem Schubausgleichskolben 16 ausgebildet, der im Wesentlichen einen größeren Durchmesser aufweist. Zwischen der Oberfläche 17 des Schubausgleichskolbens 16 und dem Innengehäuse 8 ist eine Wellendichtung 18 ausgebildet. In Rotationsrichtung gesehen vor dem Schubausgleichskolben 16 weist der Rotor 2 einen geringeren Durchmesser auf, wobei in diesem Abschnitt eine zweite Wellendichtung 19 angeordnet ist.For the sake of clarity, only one vane 12 is shown. Between the inner housing 8 and the rotor 3, a flow channel 15 is formed, which is formed by the guide vanes 12 and blades 5. The rotor 3 is formed with a thrust balance piston 16 having a substantially larger diameter. Between the surface 17 of the thrust balance piston 16 and the inner housing 8, a shaft seal 18 is formed. Seen in the direction of rotation in front of the thrust balance piston 16, the rotor 2 has a smaller diameter, wherein in this section a second shaft seal 19 is arranged.

Die Zuströmung 11 ist zum Zuströmen von Dampf vorgesehen und dementsprechend ausgebildet. Das Innengehäuse 8 weist in diesem Bereich einen Vorsprung 20 auf, an dem ein Einströmsegment 21 angeordnet ist. Das Einströmsegment 21 ist im Wesentlichen als Ring ausgebildet und in das Innengehäuse 8 eingebaut. Am äußeren Durchmesser des Einströmsegmentes 21 ist das Einströmsegment 21 in eine Nut 22 eingepasst. Das Einströmsegment 21 weist ein nabenseitiges Ringsegment 23 auf, das über ein zweites Dichtelement 24 mit dem Innengehäuse 8 verbunden ist. Dazu weist das nabenseitige Ringsegment 23 eine Dichtnut 25 auf, in die das zweite Dichtelement 24 eingepasst ist. Des Weiteren weist das Innengehäuse 8 ebenfalls eine Nut 26 auf, in der das andere Ende des zweiten Dichtelementes 24 angeordnet ist. Das Einströmsegment 21 weist Einströmsegment-Leitschaufeln 27 auf, die integral mit dem Einströmsegment 21 ausgebildet sind. Der Rotor 3 ist mit einer Entlastungsnut 28 ausgebildet, die sich im Wesentlichen durch einen geringeren Durchmesser auszeichnet und einen gewissen radialen Abstand zum Einströmsegment 21 aufweist, um den Entlastungsraum 30 auszubilden. Das Einströmsegment 21 im eingebauten Zustand stellt über die Dichtelemente und Einbausituation eine technisch dampfdichte Separierung des Zuströmkanals 11 zum Entlastungsraum 30 sicher. Bohrungen 29 sind im nabenseitigen Ringsegment 23 im Einströmsegment 21 angeordnet. Diese Bohrungen 29 stellen eine strömungstechnische Verbindung zwischen der Zuströmung 11 und einem Entlastungsraum 30 her, der zwischen dem Einströmsegment 21 und dem Rotor 3 ausgebildet ist.The inflow 11 is provided for the flow of steam and designed accordingly. The inner housing 8 has in this area a projection 20 on which an inflow segment 21 is arranged. The inflow segment 21 is substantially formed as a ring and installed in the inner housing 8. At the outer diameter of the inflow segment 21, the inflow segment 21 is fitted in a groove 22. The inflow segment 21 has a hub-side ring segment 23 which is connected to the inner housing 8 via a second sealing element 24. For this purpose, the hub-side ring segment 23 has a sealing groove 25 into which the second sealing element 24 is fitted. Furthermore, the inner housing 8 also has a groove 26 in which the other end of the second sealing element 24 is arranged. The inflow segment 21 has inflow segment vanes 27 integrally formed with the inflow segment 21. The rotor 3 is formed with a relief groove 28, which is characterized essentially by a smaller diameter and has a certain radial distance from the inflow segment 21 in order to form the relief space 30. The inflow segment 21 in the installed state ensures a technically vapor-tight separation of the inflow channel 11 to the relief space 30 via the sealing elements and installation situation. Holes 29 are arranged in the hub-side ring segment 23 in the inflow segment 21. These holes 29 establish a fluidic connection between the inflow 11 and a relief space 30, which is formed between the inflow segment 21 and the rotor 3.

Im Betrieb strömt ein Massenstrom (Mges) in die Zuströmung 11. Dieser Massenstrom teilt sich in einen kleineren Massenstrom (M1), der durch die Bohrungen 29 führt und in den Entlastungsraum 30 gelangt und in einen größeren Massenstrom (M2), der durch die Einströmsegment-Leitschaufel 27 strömt und danach durch den Strömungskanal 15 führt. Es gilt Mges=M1+M1, wobei M1 << M2. Des Weiteren teilt sich der Massenstrom M1, der durch die Bohrungen 29 führt, in einen Massenstrom M11 auf, der über die zweite Wellendichtung 19 in einen Schubausgleichskolben-Vorraum 31 gelangt. Ein anderer Teil des Massenstroms M1 gelangt als zweiter Massenstrom M12 am nabenseitigen Ringsegment 23 entlang in den Strömungskanal 15.In operation, a mass flow (M tot ) flows into the inflow 11. This mass flow is divided into a smaller mass flow (M 1 ), which passes through the bores 29 and enters the discharge space 30 and into a larger mass flow (M 2 ), the flows through the inflow segment vane 27 and then passes through the flow channel 15. We have Mg es = M 1 + M 1 , where M 1 << M 2 . Furthermore, the mass flow M 1 , which leads through the bores 29, is divided into a mass flow M 11 , which passes via the second shaft seal 19 into a thrust balance piston antechamber 31. Another part of the mass flow M 1 passes as a second mass flow M 12 on the hub-side ring segment 23 along in the flow channel 15th

Der Massenstrom M11 + M12 weist eine vergleichsweise geringere Temperatur auf als der von Mges und führt daher zu einer Abkühlung der Rotoroberfläche in der Entlastungsnut 28.The mass flow M 11 + M 12 has a comparatively lower temperature than that of M tot and therefore leads to a cooling of the rotor surface in the relief groove 28.

Die Bohrungen 29 sind in Strömungsrichtung 32 des Zuströmdampfes gesehen, vor den Einströmsegment-Leitschaufeln 27 angeordnet.The holes 29 are seen in the flow direction 32 of the inflow steam, arranged in front of the inflow segment guide vanes 27.

Die Figur 2 zeigt eine Teilansicht des Einströmsegments 21. In der in Figur 2 dargestellten Perspektive erfolgt ein Blick von der Rotationsachse 2 aus in radialer Richtung nach außen. In der dargestellten Perspektive sind mehrere Einströmsegment-Leitschaufeln 27 zu erkennen. Das nabenseitige Ringsegment 23 ist im Wesentlichen dreieckförmig ausgebildet und weist die Nut 25 zur Aufnahme des Dichtelementes 24 auf. Die Figur 2 zeigt eine Perspektive des Einströmelements 21, wobei eine innenseitige Oberfläche 33 des nabenseitigen Ringsegments 23 zu sehen ist. Der Austritt 34 der Bohrungen 29 ist auf dieser innenseitigen Oberfläche 33 ausgebildet.The FIG. 2 shows a partial view of the inflow segment 21. In the in FIG. 2 perspective shown takes a view from the axis of rotation 2 in the radial direction to the outside. In the illustrated perspective, multiple inflow segment vanes 27 can be seen. The hub-side ring segment 23 is substantially triangular in shape and has the groove 25 for receiving the sealing element 24. The FIG. 2 shows a perspective of the inflow member 21, wherein an inside surface 33 of the hub side ring segment 23 can be seen. The outlet 34 of the holes 29 is formed on this inside surface 33.

Die Figur 3 zeigt eine Schnittansicht durch das Einströmsegment 21. Der Übersichtlichkeit wegen ist lediglich eine Einströmsegment-Leitschaufel mit dem Bezugszeichen 27 versehen. Im gewählten Ausführungsbeispiel sind sechs Bohrungen 29 ausgeführt, die in einer tangentialen Richtung zum Entlastungsraum 30 im Winkel α ausgebildet sind. Die Drehrichtung des Rotors 3 erfolgt gegen den Uhrzeigersinn. Beispielhaft wird an der Bohrung 29 in der Zwölf-Uhr-Position der Winkel α erläutert. Von der Rotationsachse 2 aus ist in radialer Richtung eine Bezugslinie 35 dargestellt. Unter einem Winkel α, der zwischen 40° und 80° liegt, wird eine Bohrung 29 ausgeführt. Durch diese Bohrung 29 strömt der Massenstrom M1. Durch den ausgeübten Drall erfährt der Dampf eine Geschwindigkeitsänderung und damit eine Absenkung der statischen Temperatur des Dampfes bezogen auf das rotierende System, was dann zu einer Abkühlung der Oberfläche des Rotors 3 gegenüber der Temperatur des Massenstroms Mges führt.The FIG. 3 shows a sectional view through the inflow segment 21. For clarity, only one inflow segment vane is designated by reference numeral 27. In the selected embodiment, six holes 29 are executed, which are formed in a tangential direction to the discharge chamber 30 at an angle α. The direction of rotation of the rotor 3 is counterclockwise. By way of example, the angle α is explained on the bore 29 in the twelve o'clock position. From the axis of rotation 2 from a reference line 35 is shown in the radial direction. At an angle α, which is between 40 ° and 80 °, a bore 29 is executed. Through this bore 29, the mass flow M 1 flows . Due to the applied twist of the steam undergoes a change in velocity and thus a reduction in the static temperature of the steam relative to the rotating system, which then leads to a cooling of the surface of the rotor 3 relative to the temperature of the mass flow M tot .

Claims (7)

  1. Turbomachine, comprising
    - a rotor (3) which is mounted rotatably about an axis of rotation (2), rotor blades (5) which are arranged on the rotor (3),
    - a casing (8, 9) which is arranged about the rotor (3), guide vanes (12) which are attached inside the casing (8, 9),
    - a flow duct (15) which is formed between the rotor (3) and the casing (8, 9),
    - a supply line (11) which is arranged in the casing (8, 9) and is formed for supplying steam,
    - an inflow segment (21) which is arranged in the casing (8, 9),
    - inflow segment guide vanes (27) which are arranged in the inflow segment (21),
    bores (29) which are arranged in the inflow segment (21) and which establish a fluidic connection between the supply line (11) and a relief space (30) which is arranged between the inflow segment (21) and the rotor (3),
    characterized in that the bores (29) are inclined,
    with respect to a radial direction through the axis of rotation (2),
    by an angle α in the circumferential direction of between 40° and 80°.
  2. Turbomachine according to Claim 2,
    wherein the bores (29) are formed such that part of the supply steam is fed through the bores (29) and part of the supply steam is fed through the inflow segment guide vanes (27).
  3. Turbomachine according to Claim 1 or 2,
    wherein the inflow segment (21) has a hub-side ring segment (23) in which are formed the bores (29).
  4. Turbomachine according to Claim 1, 2 or 3,
    wherein the bores (29) are arranged upstream of the inflow segment guide vanes (27), as seen in the flow direction (32) of the supply steam.
  5. Turbomachine according to Claim 1,
    wherein six bores (29) are formed.
  6. Turbomachine according to one of the preceding claims,
    wherein the casing is formed as an inner casing (8) and an outer casing (9) is arranged around the inner casing (8).
  7. Turbomachine according to one of the preceding claims, formed as a steam turbine (1).
EP13739171.0A 2012-07-12 2013-07-09 Inlet segment for a flow machine Not-in-force EP2859192B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13739171.0A EP2859192B1 (en) 2012-07-12 2013-07-09 Inlet segment for a flow machine

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP12176161.3A EP2685051A1 (en) 2012-07-12 2012-07-12 Inlet segment for a flow machine
PCT/EP2013/064429 WO2014009333A1 (en) 2012-07-12 2013-07-09 Inflow segment for a turbomachine
EP13739171.0A EP2859192B1 (en) 2012-07-12 2013-07-09 Inlet segment for a flow machine

Publications (2)

Publication Number Publication Date
EP2859192A1 EP2859192A1 (en) 2015-04-15
EP2859192B1 true EP2859192B1 (en) 2016-05-25

Family

ID=48803516

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Application Number Title Priority Date Filing Date
EP12176161.3A Withdrawn EP2685051A1 (en) 2012-07-12 2012-07-12 Inlet segment for a flow machine
EP13739171.0A Not-in-force EP2859192B1 (en) 2012-07-12 2013-07-09 Inlet segment for a flow machine

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP12176161.3A Withdrawn EP2685051A1 (en) 2012-07-12 2012-07-12 Inlet segment for a flow machine

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US (1) US20150159486A1 (en)
EP (2) EP2685051A1 (en)
JP (1) JP5985748B2 (en)
KR (1) KR20150036474A (en)
CN (1) CN104471193B (en)
IN (1) IN2014DN10499A (en)
PL (1) PL2859192T3 (en)
WO (1) WO2014009333A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017114608A1 (en) * 2017-06-30 2019-01-03 Man Diesel & Turbo Se Turbine inlet housing of an axial turbine of a turbocharger

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2294983A (en) * 1941-04-29 1942-09-08 Westinghouse Electric & Mfg Co Steam turbine apparatus
US3429557A (en) * 1966-06-30 1969-02-25 Gen Electric Steam turbine rotor cooling arrangement
US3614255A (en) * 1969-11-13 1971-10-19 Gen Electric Thrust balancing arrangement for steam turbine
US4242041A (en) * 1979-01-15 1980-12-30 Westinghouse Electric Corp. Rotor cooling for double axial flow turbines
JPS59153901A (en) * 1983-02-21 1984-09-01 Fuji Electric Co Ltd Cooling device for rotor in steam turbine
JPH0734808A (en) * 1993-07-26 1995-02-03 Mitsubishi Heavy Ind Ltd Steam turbine
JPH0742508A (en) * 1993-08-02 1995-02-10 Mitsubishi Heavy Ind Ltd Rotor cooling device for steam turbine
JPH09125909A (en) * 1995-10-30 1997-05-13 Mitsubishi Heavy Ind Ltd Combined-cycle steam turbine
JP2004197696A (en) * 2002-12-20 2004-07-15 Kawasaki Heavy Ind Ltd Gas turbine equipped with whirling nozzle
CN100378308C (en) * 2006-07-07 2008-04-02 姜伟 Impeller-pressurizing rotor-injection type steam turbine
JP5558120B2 (en) * 2010-01-12 2014-07-23 株式会社東芝 Steam turbine rotor cooling device and steam turbine provided with this cooling device

Also Published As

Publication number Publication date
CN104471193A (en) 2015-03-25
EP2685051A1 (en) 2014-01-15
JP2015522130A (en) 2015-08-03
KR20150036474A (en) 2015-04-07
JP5985748B2 (en) 2016-09-06
PL2859192T3 (en) 2016-11-30
CN104471193B (en) 2016-08-24
WO2014009333A1 (en) 2014-01-16
US20150159486A1 (en) 2015-06-11
IN2014DN10499A (en) 2015-08-21
EP2859192A1 (en) 2015-04-15

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