EP2271827B1 - Turbomaschine mit schubausgleichskolben - Google Patents

Turbomaschine mit schubausgleichskolben Download PDF

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Publication number
EP2271827B1
EP2271827B1 EP09742020A EP09742020A EP2271827B1 EP 2271827 B1 EP2271827 B1 EP 2271827B1 EP 09742020 A EP09742020 A EP 09742020A EP 09742020 A EP09742020 A EP 09742020A EP 2271827 B1 EP2271827 B1 EP 2271827B1
Authority
EP
European Patent Office
Prior art keywords
pressure
pressure chamber
diameter
rotor
rotary machine
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
Application number
EP09742020A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2271827A1 (de
Inventor
Walter Gehringer
Richard Geist
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to PL09742020T priority Critical patent/PL2271827T3/pl
Publication of EP2271827A1 publication Critical patent/EP2271827A1/de
Application granted granted Critical
Publication of EP2271827B1 publication Critical patent/EP2271827B1/de
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
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like

Definitions

  • the invention relates to a rotary machine, in particular turbine, pump or compressor, with at least one rotor and at least one process fluid, which surrounds the rotor at least partially, wherein the rotor has at least one compensating piston, for influencing an axial thrust of the rotor, wherein the compensating piston at least one Diameter change of the rotor, wherein at least one shaft seal is provided which seals a first space in which a first pressure prevails of a second space in which a second pressure prevails such that at least temporarily a pressure difference between the first and the second space is applied and a first shaft seal is disposed on the balance piston such that a first change in diameter exposes the pressure of the first space and a second change in diameter exposes the pressure of the second space.
  • a gas turbine with high pressure and low pressure compensation piston is disclosed
  • Balancing pistons on rotary machines are part of the usual assemblies, especially in steam turbines.
  • a pressure build-up or a pressure reduction of the process fluid takes place along a relaxation or compression path in at least partially axial direction of the rotor, wherein the rotor itself or its associated element in areas of varying diameter, such as wave heels, exposed to the respective different applied pressures are.
  • rotating blades produce here as well as in the circumferential direction continuous shaft paragraphs an axial thrust that these elements transmit as axial force in the rotor.
  • a thrust bearing In order for a thrust bearing to be designed in a meaningful size under these operating conditions, it is necessary to compensate for these forces by corresponding opposing forces elsewhere.
  • a control set the pressure in the pressure chambers, so that the desired residual thrust is always formed.
  • the described balancing effect can only be achieved if either the pressures on the compensating piston have a particularly high difference or the compensating piston diameter is made very large.
  • the shaft seal provided on the compensating piston requires sufficiently large axial space to achieve the required sealing effect.
  • Both large diameter and large axial space cause on the one hand undesirable rotordynamic effects in the form of vibrations and on the other hand high costs due to the additional material requirements for both the rotor and the surrounding components, in particular for the housing.
  • the follow-up costs for the installation, transport and storage of large components are significant.
  • the invention has therefore taken on the task of developing a rotary machine with a balancing piston of the type mentioned in such a way that with the same thrust compensation only a reduced space is required.
  • the formation of the balancing piston having a plurality of spaces, each separated by shaft seals from each other to form a pressure difference and which spaces are limited by at least one change in diameter of the rotor, allows reducing the diameter of the balance piston without reducing the thrust balance potential.
  • multi-stage design of the balance piston where a stage of a balance piston is defined as an array of a shaft seal, a space with a certain pressure, and a diameter change of the rotor limiting that space), the required pressure per stage of the balance piston can be made smaller; so that the requirements for the corresponding shaft seal are reduced and this may optionally be formed with a smaller axial dimension.
  • an arrangement according to the invention can also have more than four of the above-defined stages, for example 5, 6, or more.
  • a compensating piston according to the invention even at high pressure differences per stage does not require a large axial space, it is expedient if the shaft seals are each formed between the pressure chambers as a brush seal or a mechanical seal. Compared to conventional labyrinth seals, these sealing shapes have a better sealing effect, so that higher pressure differences can be reduced by way of a smaller axial extent, and accordingly compensating pistons according to the invention have only a small space requirement, both radially and axially.
  • Particularly useful is the formation of pressure channels to the respective pressure chambers, so that can make the differential pressures required for the compensation by setting a certain pressure in the pressure chambers.
  • the actuator In order to enable an adaptation of the thrust balance to different operating conditions, it may additionally be useful to provide at least one actuator or a valve in at least one pressure channel, by means of which the pressure in the connected pressure chamber is adjustable.
  • the actuator allows a dynamic pressure regulation, which is preferably caused depending on the respective operating point of a central control.
  • the inventive stepwise design of the balance piston allows the use of identical shaft seals for different turbines, especially if a variation of the number of stages of the balance piston in their difference of the thrust balance exactly corresponds to the thrust difference of the corresponding types of rotary machine.
  • FIG. 1 shows a rotary machine 1, namely a steam turbine 2, is relaxed in the fed-in live steam 3 when flowing through a blading 4 on steam 5 a lower pressure level in the region of a discharge 80.
  • the axial thrust 8 is supported on a thrust bearing 9.
  • a compensating piston 10 is provided, which is designed as a shaft shoulder on the rotor 6.
  • FIGS. 2 and 3 show the detail X with the balance piston 10 in conventional construction or in the inventive design.
  • FIG. 2 illustrated balancing piston 10 in a conventional design has in the axial direction of the rotor 6 from left to right denotes a first pressure chamber 11, a first change in diameter 21, a first shaft seal 31, a second pressure chamber 12 with a second change in diameter 22.
  • Axially in front of this described arrangement is a shaft labyrinth seal 82, by means of which the first pressure chamber 11 is sealed to the atmosphere 51.
  • Axially behind the arrangement described as compensating piston 10, or on the part of the turbine interior facing end of this arrangement is another wave labyrinth seal 52, by means of which the second pressure chamber 12 is sealed to an inflow 54 out.
  • This wave labyrinth seal can be attributed to the balance piston 10.
  • the applied pressure in the second pressure chamber 22 is higher than that in the first pressure chamber 11, so that the resulting from a balance of forces of the balance piston thrust directed against the thrust from the blading 4.
  • FIG. 3 shows the arrangement according to the FIG. 2 or the detail X of the FIG. 1 with an inventive design of the balance piston 10.
  • the balance piston 10 is in this case formed with four pressure chambers 11, 12, 13, 14, each having a shaft seal 31, 32, 33 for separation from each other and at least one change in diameter 21, 22, 23, 24th of the rotor 6 are partially limited.
  • the shaft seals 31, 32, 33 are formed as brush seals, so that for a conventional construction ( Fig. 2 ) equivalent pressure difference between the pressure chambers 11, 12, 13, 14 is only a small axial space to spend.
  • the second pressure chamber 12 and the third pressure chamber 13 are connected to pressure channels 42, 43 in connection, so that the second pressure chamber 12 has a higher pressure than the third pressure chamber 13.
  • the first in the first Pressure chamber 11 and in the third pressure chamber 13 applied pressure and the voltage applied in the second pressure chamber 12 and the fourth pressure chamber 14 pressure identical. Due to the permeability of the shaft seals 31 - 33, a flow according to the arrows 61 - 66 results in each case due to the pressure differences between the individual pressure chambers fed by the pressure channels 42, 43rd
  • FIGS. 4 and 5 show the diameter provided on the rotor 6 in conjunction with various pressures in the pressure chambers 11-14 in cooperation with shaft seals 31-33 FIG. 4 the first pressure chamber 11 is connected via a pressure channel 71 with the outflow and the second pressure chamber 12 by means of a pressure channel 72 with a higher pressure level in the blading. 4
  • FIG. 5 shows that in addition to the first pressure chamber 11 and the second pressure chamber 12, a third pressure chamber 13 and a fourth pressure chamber 14 are also connected to the pressure levels at the outflow 80 and the blading 4 and in this way the double effect of the thrust compensation can be achieved , Otherwise, with the same design of the steam turbine 2, the diameter of the compensating piston 10 in the embodiment according to the invention would after FIG. 5 lower.
  • an actuator 100 or valve can be provided in the pressure channel 71, by means of which the pressure in the pressure chambers 12, 13, 14 can be adapted to the current operating conditions.
  • the actuator is controlled by a central controller 101.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Sealing Devices (AREA)
EP09742020A 2008-05-09 2009-04-30 Turbomaschine mit schubausgleichskolben Not-in-force EP2271827B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL09742020T PL2271827T3 (pl) 2008-05-09 2009-04-30 Maszyna wirnikowa z tłokiem wyrównawczym nacisku

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008022966.0A DE102008022966B4 (de) 2008-05-09 2008-05-09 Rotationsmaschine
PCT/EP2009/055271 WO2009135802A1 (de) 2008-05-09 2009-04-30 Turbomaschine mit schubausgleichskolben

Publications (2)

Publication Number Publication Date
EP2271827A1 EP2271827A1 (de) 2011-01-12
EP2271827B1 true EP2271827B1 (de) 2012-09-05

Family

ID=40935006

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09742020A Not-in-force EP2271827B1 (de) 2008-05-09 2009-04-30 Turbomaschine mit schubausgleichskolben

Country Status (9)

Country Link
EP (1) EP2271827B1 (ja)
JP (1) JP5086471B2 (ja)
CN (1) CN102016231B (ja)
BR (1) BRPI0912209A2 (ja)
DE (1) DE102008022966B4 (ja)
ES (1) ES2392322T3 (ja)
PL (1) PL2271827T3 (ja)
RU (1) RU2507399C2 (ja)
WO (1) WO2009135802A1 (ja)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH701914A1 (de) * 2009-09-30 2011-03-31 Alstom Technology Ltd Dampfturbine mit Entlastungsnut am Rotor im Bereich des Schubausgleichskolbens.
EP2554789A1 (de) * 2011-08-04 2013-02-06 Siemens Aktiengesellschaft Dampfturbine umfassend einen Schubausgleichskolben
DE102011087824A1 (de) * 2011-12-06 2013-06-06 Man Diesel & Turbo Se Turbine
JP5917324B2 (ja) * 2012-07-20 2016-05-11 株式会社東芝 タービンおよびタービン運転方法
ITCO20120066A1 (it) * 2012-12-20 2014-06-21 Nuovo Pignone Srl Metodo per bilanciare la spinta, turbina e motore a turbina
WO2014153345A1 (en) * 2013-03-18 2014-09-25 Onesubsea Ip Uk Limited Balance piston for multiphase fluid processing
EP2826960B1 (en) * 2013-07-19 2019-04-10 Siemens Aktiengesellschaft Sealing bush carrier for a steam turbine and steam turbine
WO2015043881A1 (de) * 2013-09-30 2015-04-02 Siemens Aktiengesellschaft Welle naxiallageranordnung und turbomaschine mit einer solchen
DE102014222057A1 (de) * 2014-10-29 2016-05-04 Siemens Aktiengesellschaft Turbine mit Axialdruckausgleich
EP3121450B1 (de) * 2015-07-23 2020-09-02 Sulzer Management AG Pumpe zum fördern eines fluids mit variierender viskosität
EP3397843A1 (de) * 2016-02-04 2018-11-07 Siemens Aktiengesellschaft Gasturbine mit axialschubkolben und radiallager
KR102322866B1 (ko) * 2020-05-13 2021-11-04 두산중공업 주식회사 가스 터빈용 베어링 제어 장치, 이를 포함하는 가스 터빈, 및 이를 이용한 베어링 제어 방법
CN113685236B (zh) * 2021-08-23 2022-10-14 华能铜川照金煤电有限公司 一种用于单缸、单列复速级背压汽轮机的平衡活塞装置
US11927105B1 (en) * 2022-09-16 2024-03-12 General Electric Company Thrust bearings to support axial thrust in pumps

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU808703A1 (ru) * 1979-02-19 1981-02-28 Chernenko Mikhail S Турбонасосный агрегат м.с.черненко
JPS56142231U (ja) * 1980-03-26 1981-10-27
JPS58148228U (ja) * 1982-03-31 1983-10-05 株式会社日立製作所 過給機の軸封装置
DE3424138A1 (de) * 1984-06-30 1986-01-09 BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau Luftspeichergasturbine
JPS62244000A (ja) * 1986-04-15 1987-10-24 Ebara Corp タ−ビン駆動圧縮機
RU2099567C1 (ru) * 1995-04-28 1997-12-20 Конструкторское бюро химавтоматики г.Воронеж Устройство для осевой разгрузки ротора турбонасосного агрегата
EP0891471B1 (de) * 1996-04-11 2002-06-26 Siemens Aktiengesellschaft Verfahren und vorrichtung zum schubausgleich bei einer turbomaschine
JPH10317903A (ja) * 1997-05-15 1998-12-02 Ishikawajima Harima Heavy Ind Co Ltd ガスタービンのベアリングスラスト力バランス構造
EP1035301A1 (de) * 1999-03-08 2000-09-13 Asea Brown Boveri AG Ausgleichskolben für den axialen Schubausgleich einer Welle von einer Turbine
DE19951570A1 (de) * 1999-10-27 2001-05-03 Abb Patent Gmbh Einrichtung zur Kompensierung des Axialschubs bei Turbomaschinen
JP2001140604A (ja) * 1999-11-19 2001-05-22 Ishikawajima Harima Heavy Ind Co Ltd 圧縮空気貯蔵型ガスタービンのスラスト調整装置及び方法
US6732502B2 (en) * 2002-03-01 2004-05-11 General Electric Company Counter rotating aircraft gas turbine engine with high overall pressure ratio compressor
EP1479875A1 (de) * 2003-05-23 2004-11-24 Siemens Aktiengesellschaft Lager für die axiale Lagerung eines Läufers einer Gasturbine
EP1624155A1 (de) * 2004-08-02 2006-02-08 Siemens Aktiengesellschaft Dampfturbine und Verfahren zum Betrieb einer Dampfturbine
US7195443B2 (en) * 2004-12-27 2007-03-27 General Electric Company Variable pressure-controlled cooling scheme and thrust control arrangements for a steam turbine
EP1780376A1 (de) * 2005-10-31 2007-05-02 Siemens Aktiengesellschaft Dampfturbine

Also Published As

Publication number Publication date
DE102008022966B4 (de) 2014-12-24
JP2011520063A (ja) 2011-07-14
RU2507399C2 (ru) 2014-02-20
EP2271827A1 (de) 2011-01-12
WO2009135802A1 (de) 2009-11-12
CN102016231A (zh) 2011-04-13
RU2010150344A (ru) 2012-06-20
ES2392322T3 (es) 2012-12-07
CN102016231B (zh) 2013-12-25
BRPI0912209A2 (pt) 2015-10-06
PL2271827T3 (pl) 2013-02-28
DE102008022966A1 (de) 2009-12-03
JP5086471B2 (ja) 2012-11-28

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