EP0043602A1 - Steam turbine with steam extraction for heating - Google Patents

Steam turbine with steam extraction for heating Download PDF

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Publication number
EP0043602A1
EP0043602A1 EP81200621A EP81200621A EP0043602A1 EP 0043602 A1 EP0043602 A1 EP 0043602A1 EP 81200621 A EP81200621 A EP 81200621A EP 81200621 A EP81200621 A EP 81200621A EP 0043602 A1 EP0043602 A1 EP 0043602A1
Authority
EP
European Patent Office
Prior art keywords
steam
reaction
extraction
heating
turbine
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.)
Ceased
Application number
EP81200621A
Other languages
German (de)
French (fr)
Inventor
Hansueli Horber
Anton Dr. Roeder
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.)
BBC Brown Boveri AG Switzerland
Original Assignee
BBC Brown Boveri AG Switzerland
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BBC Brown Boveri AG Switzerland filed Critical BBC Brown Boveri AG Switzerland
Publication of EP0043602A1 publication Critical patent/EP0043602A1/en
Ceased legal-status Critical Current

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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
    • 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
    • F01D1/18—Non-positive-displacement machines or engines, e.g. steam turbines without stationary working-fluid guiding means
    • F01D1/20—Non-positive-displacement machines or engines, e.g. steam turbines without stationary working-fluid guiding means traversed by the working-fluid substantially axially
    • 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
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/141—Shape, i.e. outer, aerodynamic form
    • F01D5/142—Shape, i.e. outer, aerodynamic form of the blades of successive rotor or stator blade-rows

Definitions

  • the invention relates to a steam turbine with heating steam extraction according to the preamble of claim 1.
  • the axial thrust varies with the operating conditions in the heating network and can no longer be compensated for in every operating state with the compensating piston. Under certain operating conditions, an impermissibly high load on the comb bearing can occur.
  • the axial thrust is essentially caused by the axial flow forces on the rotor blades.
  • the axial thrust is largely determined by the static pressure difference between the inlet and outlet cross-sections of the impellers.
  • the heating steam is usually taken from the outlet of the medium pressure turbine. If the quantity withdrawn changes, the pressure also changes at the extraction point, which also results in a change in the axial thrust of the last row of blades before this extraction point. This change is much smaller with a lower degree of reaction of the stage. The axial thrust of the previous rows of blades, however, remains almost unchanged.
  • the present invention arose from the object of avoiding this behavior of the axial thrust, which is unfavorable for the load on the comb bearings, with changing quantities of heating steam being withdrawn.

Abstract

Steam turbine with steam extraction for heating, having reaction blading, the last stage before the extraction nozzle being configured with a smaller reaction level than the other stages of the blading, to reduce the change of the axial thrust on extraction of the steam. <IMAGE>

Description

Die Erfindung betrifft eine Dampfturbine mit Heizdampfentnahme nach dem Oberbegriff des Patentanspruchs l.The invention relates to a steam turbine with heating steam extraction according to the preamble of claim 1.

Bei einflutigen oder unsymmetrischen zweiflutigen Reaktionsturbinen wird der im Betrieb auftretende Axialschub durch dampfbeaufschlagte Ausgleichskolben kompensiert.In the case of single-flow or asymmetrical double-flow reaction turbines, the axial thrust that occurs during operation is compensated for by steam-compensating pistons.

Bei solchen Turbinen mit Heizdampfentnahme variiert der Axialschub mit den Betriebsbedingungen im Heiznetz und kann mit dem Ausgleichskolben nicht mehr bei jedem Betriebszustand ausgeglichen werden. Bei gewissen Betriebszuständen kann daher eine unzulässig hohe Belastung des Kammlagers auftreten.In such turbines with heating steam extraction, the axial thrust varies with the operating conditions in the heating network and can no longer be compensated for in every operating state with the compensating piston. Under certain operating conditions, an impermissibly high load on the comb bearing can occur.

Der Axialschub wird im wesentlichen durch die axialen Strömungskräfte an den Laufschaufeln verursacht. Bei Reaktionsturbinen ist der Axialschub grösstenteils durch die statische Druckdifferenz zwischen Ein- und Austrittsquerschnitt der Laufräder bestimmt.The axial thrust is essentially caused by the axial flow forces on the rotor blades. In reaction turbines, the axial thrust is largely determined by the static pressure difference between the inlet and outlet cross-sections of the impellers.

Bei herkömmlichen Heizkraftwerken entnimmt man den Heizdampf meist am Austritt der Mitteldruckturbine. Bei Aenderungen der Entnahmemenge ändert sich dabei auch der Druck an der Entnahmestelle, woraus auch eine Aenderung des Axialschubes der letzten Laufschaufelreihe vor dieser Entnahmestelle resultiert. Diese Aenderung ist bei kleinerem Reaktionsgrad der Stufe wesentlich kleiner. Der Axialschub der vorhergehenden Laufschaufelreihen bleibt dabei hingegen nahezu unverändert.In conventional thermal power plants, the heating steam is usually taken from the outlet of the medium pressure turbine. If the quantity withdrawn changes, the pressure also changes at the extraction point, which also results in a change in the axial thrust of the last row of blades before this extraction point. This change is much smaller with a lower degree of reaction of the stage. The axial thrust of the previous rows of blades, however, remains almost unchanged.

Die vorliegende, im kennzeichnenden Teil des Patentanspruchs 1 definierte Erfindung entstand aus der Aufgabe, dieses für die Kammlagerbelastung ungünstige Verhalten des Axialschubes bei sich ändernden Entnahmemengen von Heizdampf zu vermeiden.The present invention, defined in the characterizing part of patent claim 1, arose from the object of avoiding this behavior of the axial thrust, which is unfavorable for the load on the comb bearings, with changing quantities of heating steam being withdrawn.

Die Erfindung wird im folgenden unter Bezugnahme auf zwei in der Zeichnung schematisch dargestellte Ausführungsbeispiele beschrieben.The invention is described below with reference to two exemplary embodiments shown schematically in the drawing.

In der Zeichnung stellen dar:

  • Fig. 1 die Ausgestaltung des erfindungswesentlichen Teiles einer unsymmetrischen zweiflutigen Reaktionsturbine und
  • Fig. 2 dasselbe bei einer einflutigen Reaktionsturbine.
In the drawing:
  • Fig. 1 shows the configuration of the essential part of the invention of an asymmetrical double-flow reaction turbine and
  • Fig. 2 the same with a single-flow reaction turbine.

Bei der Ausführung nach Fig. 1 bezeichnen 1 den Eintrittskanal und 2 und 3 die Austrittskanäle einer unsymmetrischen zweiflutigen Mitteldruckreaktionsturbine. Die Zahlen unter den einzelnen Stufen bedeuten deren Reaktionsgrade. In der Regel werden alle Stufen mit dem optimalen Reaktionsgrad von 0,5 ausgeführt mit den eingangs beschriebenen nachteiligen Wirkungen bei Aenderungen der für Heiz-oder Prozesszwecke entnommenen Dampfmenge. Zur Vermeidung eines unzulässig hohen-Axialschubes aus den obengenannten Gründen werden gemäss der Erfindung die Endstufen 4 und 5 an den beiden Austrittskanälen 2 und 3 mit einem gegenüber den vorhergehenden Stufen, die mit dem optimalen Reaktionsgrad von 0,5 ausgelegt sind, reduzierten Reaktionsgrad, im gezeichneten Beispiel 0,35, ausgeführt, so dass der Axialschub im gesamten Betriebsbereich kleiner und daher zulässig wird. Es ist daher möglich, den Durchmesser des Ausgleichskolbens zu reduzieren. Die durch die Abweichung vom Optimum 0,5 bedingte Einbusse an Stufenwirkungsgrad wird dabei durch die geringeren Verluste am Ausgleichskolben ausgeglichen.1 designate 1 the inlet duct and 2 and 3 the outlet ducts of an asymmetrical double-flow medium pressure reaction turbine. The numbers below the individual stages indicate their degree of reaction. As a rule, all stages are carried out with the optimum degree of reaction of 0.5 with the disadvantageous effects described at the outset when the amount of steam removed for heating or process purposes is changed. To avoid an impermissibly high axial thrust from the above For this reason, according to the invention, the final stages 4 and 5 are carried out on the two outlet channels 2 and 3 with a reduced degree of reaction compared to the preceding stages, which are designed with the optimum degree of reaction of 0.5, in the example shown 0.35, so that the axial thrust becomes smaller in the entire operating range and is therefore permissible. It is therefore possible to reduce the diameter of the compensating piston. The loss in step efficiency caused by the deviation from the optimum 0.5 is compensated for by the lower losses at the compensating piston.

Bei der in Fig. 2 schematisch dargestellten Beschaufelung einer einflutigen Reaktionsturbine mit dem Eintrittskanal 6 unddemAustrittskanal 7 wird die angestrebte Reduktion des Axialschubes im ganzen Betriebsbereich durch einen kleineren Reaktionsgrad der einzigen Endstufe 8 erreicht. Hier wurde für deren Reaktionsgrad ebenfalls 0,35 gewählt, doch könnte dieser ebenso wie bei der zweiflutigen Turbine, je nach Auslegung der Anlage, auch andere Werte unter 0,5 aufweisen.In the blading of a single-flow reaction turbine with the inlet duct 6 and the outlet duct 7, which is shown schematically in FIG. Here, 0.35 was also chosen for the degree of reaction, but this, like the double-flow turbine, could also have other values below 0.5, depending on the design of the system.

BezeichnungslisteLabel list

  • 1 Einstrittskanal *1 entry channel *
  • 2 Austrittskanal2 outlet channel
  • 3 Austrittskanal3 outlet channel
  • 4 Endstufe4 power amplifier
  • 5 Endstufe5 power amplifier
  • 6 Eintrittskanal6 inlet channel
  • 7 Austrittskanal7 outlet channel
  • 8 Endstufe8 power amplifier

Claims (4)

1. Dampfturbine mit Heizdampfentnahme, mit einer Reaktionsbeschaufelung und Entnahmestutzen für den Dampf, dadurch gekennzeichnet, dass der Reaktionsgrad der jeweils letzten Stufe vor einem Entnahmestutzen kleiner ausgeführt ist als der Reaktionsgrad der übrigen, vorhergehenden Stufen.1. Steam turbine with heating steam extraction, with a reaction blading and extraction nozzle for the steam, characterized in that the degree of reaction of the last stage before a extraction nozzle is made smaller than the degree of reaction of the other, previous stages. 2. Dampfturbine nach Anspruch l, dadurch gekennzeichnet, dass die jeweils letzte Stufe vor den Entnahmestutzen mit einem Reaktionsgrad von 0,35 und die übrigen, vorhergehenden Stufen mit einem Reaktionsgrad von 0,5 ausgeführt sind.2. Steam turbine according to claim 1, characterized in that the last stage before the extraction nozzle with a degree of reaction of 0.35 and the remaining, previous stages are carried out with a degree of reaction of 0.5. 3. Dampfturbine nach Anspruch 2, dadurch gekennzeichnet, dass die Turbine zweiflutig ausgeführt ist und die beiden Fluten unterschiedlich viele Stufen aufweisen.3. Steam turbine according to claim 2, characterized in that the turbine is designed with two flows and the two floods have different numbers of stages. 4. Dampfturbine nach Anspruch 2, dadurch gekennzeichnet, dass die Turbine einflutig ausgeführt ist.4. Steam turbine according to claim 2, characterized in that the turbine is single-flow.
EP81200621A 1980-07-09 1981-06-05 Steam turbine with steam extraction for heating Ceased EP0043602A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH5248/80 1980-07-09
CH524880 1980-07-09

Publications (1)

Publication Number Publication Date
EP0043602A1 true EP0043602A1 (en) 1982-01-13

Family

ID=4290412

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81200621A Ceased EP0043602A1 (en) 1980-07-09 1981-06-05 Steam turbine with steam extraction for heating

Country Status (2)

Country Link
EP (1) EP0043602A1 (en)
DK (1) DK281181A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998031923A1 (en) * 1997-01-14 1998-07-23 Siemens Aktiengesellschaft Steam turbine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR376816A (en) * 1907-04-16 1907-08-22 Auguste Brien Method of balancing the axial thrust of compressible fluid turbines
GB293037A (en) * 1927-06-30 1928-10-04 International General Electric Company Incorporated
GB315370A (en) * 1928-07-12 1930-02-06 Gen Electric Improvements in and relating to means for balancing the axial thrust in a turbine installation
DE573542C (en) * 1931-03-15 1933-04-01 Bbc Brown Boveri & Cie Overpressure steam or gas turbine
FR851531A (en) * 1938-03-15 1940-01-10 Dual circulation turbine with internal admission
FR2361531A1 (en) * 1976-08-13 1978-03-10 Europ Turb Vapeur COMPRESSIBLE FLUID TURBINE

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR376816A (en) * 1907-04-16 1907-08-22 Auguste Brien Method of balancing the axial thrust of compressible fluid turbines
GB293037A (en) * 1927-06-30 1928-10-04 International General Electric Company Incorporated
GB315370A (en) * 1928-07-12 1930-02-06 Gen Electric Improvements in and relating to means for balancing the axial thrust in a turbine installation
DE573542C (en) * 1931-03-15 1933-04-01 Bbc Brown Boveri & Cie Overpressure steam or gas turbine
FR851531A (en) * 1938-03-15 1940-01-10 Dual circulation turbine with internal admission
FR2361531A1 (en) * 1976-08-13 1978-03-10 Europ Turb Vapeur COMPRESSIBLE FLUID TURBINE

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998031923A1 (en) * 1997-01-14 1998-07-23 Siemens Aktiengesellschaft Steam turbine
US6345952B1 (en) * 1997-01-14 2002-02-12 Siemens Aktiengesellschaft Steam turbine
CN1084822C (en) * 1997-01-14 2002-05-15 西门子公司 Steam turbine

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Publication number Publication date
DK281181A (en) 1982-01-10

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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Effective date: 19820319

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Effective date: 19831009

RIN1 Information on inventor provided before grant (corrected)

Inventor name: ROEDER, ANTON, DR.

Inventor name: HORBER, HANSUELI