EP0690204A2 - Turbine à vapeur ayant au moins deux joint pour assurer l'étanchéité du carter - Google Patents

Turbine à vapeur ayant au moins deux joint pour assurer l'étanchéité du carter Download PDF

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Publication number
EP0690204A2
EP0690204A2 EP95109678A EP95109678A EP0690204A2 EP 0690204 A2 EP0690204 A2 EP 0690204A2 EP 95109678 A EP95109678 A EP 95109678A EP 95109678 A EP95109678 A EP 95109678A EP 0690204 A2 EP0690204 A2 EP 0690204A2
Authority
EP
European Patent Office
Prior art keywords
seal
turbine
condensation
seals
steam
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
EP95109678A
Other languages
German (de)
English (en)
Other versions
EP0690204A3 (fr
EP0690204B1 (fr
Inventor
Karl Urlichs
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.)
Alstom SA
Original Assignee
ABB Patent GmbH
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 ABB Patent GmbH filed Critical ABB Patent GmbH
Publication of EP0690204A2 publication Critical patent/EP0690204A2/fr
Publication of EP0690204A3 publication Critical patent/EP0690204A3/fr
Application granted granted Critical
Publication of EP0690204B1 publication Critical patent/EP0690204B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • F01D11/04—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type using sealing fluid, e.g. steam
    • F01D11/06—Control thereof
    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages

Definitions

  • the invention relates to a steam turbine according to the preamble of claim 1.
  • One type of steam turbine is used as a counter-pressure turbine if the output steam is to be used in a heating network at elevated pressure.
  • a condensation turbine the heat content of the steam is exploited through its complete expansion up to a negative pressure in relation to the atmosphere. The consequence of this is that the outer seals of a condensation turbine must be suitable for preventing air from penetrating into the turbine housing, which is filled with steam.
  • seals W1 of the turbine housing of a condensation turbine are designed in the form of labyrinths without contact.
  • suitable precautions must be taken to improve the sealing effect. In general, this occurs on the fresh and exhaust side through a further seal W2 which is arranged from the interior of the housing behind the actual shaft seal W1 and through an annular chamber S which is between W1 and W2 and is acted on with sealing steam S1, S2.
  • the pressure for this steam becomes just chosen so large that in all cases there is a flow to the outside and thus the entry of air is excluded.
  • a leakage vapor L1 flowing through the outer seal must in turn be prevented from escaping into the atmosphere by suitable annular chambers L and labyrinth seals W3.
  • a chamber W ensures that the remaining leakage vapor / air mixture can be safely extracted.
  • a seal structure which is especially suitable for the compensating piston of a steam turbine is known from DE-35 33 829 A1.
  • An application of this seal instead of an inner balancing piston labyrinth in a steam turbine is described.
  • a lifting device is intended to prevent damage from occurring in the area of the seal during the heating and condensation phase of the steam.
  • the lifting device is also suitable for securing the standstill and turning operation of a turbine.
  • the object of the invention is to provide a condensation turbine according to the preamble of claim 1, which does not need expensive sealing steam devices, numerous pipelines and condensation devices and yet prevents the break-in of outside air into the negative pressure turbine interior.
  • a mechanical seal that is designed or installed in such a way that the gas lubrication can flow through the mechanical seal from the outside atmosphere into the interior of the housing enables the construction of a condensation turbine in which at least one seal is designed as a gas-lubricated mechanical seal both on the fresh steam side and on the exhaust side is.
  • the outermost mechanical seals on the fresh steam side and on the exhaust steam side are assigned separate sealing spaces which are acted upon by a compensating line AG with the same negative pressure lying below the atmospheric external pressure.
  • the construction of the condensation turbine is considerably simplified by using a mechanical seal of the type mentioned, since the steam space is protected from air ingress in all operating conditions. In particular, this also applies to the standstill and the so-called gymnastics operation, in which the turbine shaft is protected against warping by one-sided heating by slow rotation with a suitable device.
  • the outer labyrinth consisting of several labyrinth seals can be replaced on the fresh steam and exhaust steam sides by a mechanical seal, which reliably fulfills its tasks in all operating states.
  • Expensive barrier steam devices numerous pipelines and condensation devices can be dispensed with.
  • the arrangement of a vapor extraction W is carried out - if necessary - as in the conventional embodiment according to Fig.3.
  • the mechanical seal can be installed in the condensation turbine in such a way that its sealing gap is flowed through either from the inner to the outer diameter of this mechanical seal or vice versa. Accordingly, it is provided that in the mechanical seals an aerodynamically effective pattern is integrated into their sealing surfaces, the direction of their action with the intended flow of the mechanical seals from the outer atmosphere corresponds to the housing interior.
  • a compensating piston seal is inserted on the fresh steam side behind the outermost mechanical seal, which is also constructed as a mechanical seal.
  • the object of the invention can also be achieved by the features of claim 6.
  • a mechanical seal acting as a compensating piston seal also seals the shaft passage through the turbine housing on the fresh steam side saves a mechanical seal and thus an expensive component.
  • the axial bearing can be dimensioned so that it can absorb these forces. It is possible to dimension the axial bearing of the turbine shaft for both axial directions so that it optimally accommodates the thrusts at full load and when idling.
  • a major problem with the mechanical seal is that at very low speeds of the turbine rotor, such as occur during start-up operation or sometimes even during gymnastics operation, the aerodynamic expansion of the sealing gap is not carried out or is insufficient, and the sealing surfaces are therefore subject to increased abrasion. It is therefore advantageous to provide aids which ensure adequate sealing of the sealing gap in the start-up mode or in the turn mode.
  • the aids required for the spreading can be built up from mechanically acting elements, and then allow the sealing gap to be opened to the required width during start-up or gymnastics operation.
  • the aids required for the expansion can also be constructed to have an aerodynamic effect, steam being fed into a sealing space surrounding the compensating piston seal, which can be controlled via a valve and can thus be switched off in normal operation if the sealing space has a sufficient overpressure. This is particularly necessary in the case of condensation turbines, in which the seal would not be flowed through sufficiently for its own cooling in vacuum operation.
  • a conventional labyrinth seal downstream of the fresh steam side mechanical seal serves the same purpose as an emergency seal.
  • a further safety measure can consist in that the pressure difference in front of and behind this seal is measured on at least one labyrinth seal which acts as an emergency seal and that the steam turbine is triggered quickly when a predetermined limit value is exceeded.
  • Deformations impairing the sealing effect of the mechanical seal can be avoided by not dividing the mechanical seal and a seal housing receiving it, but rather by pushing it on the turbine rotor as closed ring parts during assembly.
  • the mechanical seal suitable for high temperatures has a non-rotating mechanical seal 2 which is movably connected to the turbine housing TG or the sealing housing 10 by a secondary seal 3.
  • the slide ring 2 is pressed by springs 4 via a secondary seal 3 onto a rotating counter ring 1 or the turbine shaft TW itself.
  • the counter ring 1 rotating with the turbine shaft TW can also be carried by a precision intermediate ring. It is centered with an elastically acting centering element 7 and held by a fastening element 8.
  • a sealing ring 9 prevents leakage between the slide ring 2 and the rotor R.
  • the sealing gap DS of the mechanical seal By designing the sealing gap DS of the mechanical seal with a special pattern on the opposing sealing surfaces, through which gap-opening pockets with a depth of a few micrometers are created, a hydrodynamic expansion of the sealing gap is achieved and, with the support of the rotation of the counter ring 1, small quantities are obtained of the fluid to be sealed conveyed through the seal.
  • the amount of passage In comparison to conventional non-contact labyrinth seals, the amount of passage is so small that it does not interfere with turbine operation. It can be removed in the condenser by a suction system.
  • the condensation turbine shown in Fig. 1 enables an almost complete compensation of the axial pressure forces.
  • a rotor R with its blades B is located in a turbine housing TG and is located on both sides in a slide bearing GL with its turbine shaft TW. It has at least one axial bearing AL to catch remaining axial thrust.
  • the supply of live steam FD and the removal of exhaust steam AD are also indicated.
  • the condensation turbine has three mechanical seals Wa, Wb, Wc, of which the two outer Wa, Wb seal the passage of the turbine shaft TW through the turbine housing TG. Sealing spaces DRa, DRb belonging to these mechanical seals Wa, Wb are connected to one another via a compensating line AL and have a negative pressure of approximately 0.04 bar. Due to this negative pressure, it is necessary to construct or arrange the mechanical seals, in contrast to the use in other turbomachinery, in such a way that an inflow of the sealing gap DS causes gas lubrication from outside to inside and the flow medium in this case is not steam but air.
  • mechanical seals Wa, Wb are flowed through in the direction from their inner to their outer diameter, so that the aerodynamically acting pattern must be arranged accordingly.
  • the mechanical seals Wa, Wb can also be used differently, e.g. as shown in Fig. 2b, install.
  • the respective direction of flow at the sealing gap DS is identified by an arrow.
  • the condensation turbine described is provided with a compensating piston for pressure compensation, the effect of which is ensured by a third mechanical seal acting as a compensation piston seal Wc.
  • Their structure corresponds to that of the other two mechanical seals Wa, Wb, but their installation is in accordance with a conventional arrangement in which the air flows from the inside to the outside. Under normal operating conditions, there is an overpressure in the associated seal chamber DRc, which, however, applies to gymnastics Vacuum can drop.
  • a steam supply K1 is provided, with the aid of which an overpressure sufficient for the flow can be established again.
  • a valve V enables the steam pressure to be controlled or the steam supply to be switched off in normal operation.
  • An emergency seal 5 upstream of the compensating piston seal Wc and a downstream emergency seal 6 are provided so that the fresh-steam side mechanical seals Wa, Wc do not lead to undesired steam leakage. Also to increase safety, pressure differences of the pressures Pw and Pk upstream and downstream of the emergency seals 5,6 are recorded, which can trigger a rapid shutdown of the turbine if the permissible limit values are exceeded.
  • the basic structure of the condensation turbine according to FIG. 2 corresponds to that of FIG. 1, so that repetitions in this regard can be dispensed with.
  • a decisive difference is that a compensating piston seal Wd also takes over the sealing of the shaft passage on the fresh steam side, so that the mechanical seal Wa according to FIG. 1 is saved. However, this is bought due to the lack of hydrostatic pressure compensation of the condensation part. In order to absorb these pressures, the axial bearing AL must be dimensioned accordingly.

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)
EP95109678A 1994-06-28 1995-06-22 Turbine à vapeur ayant au moins deux joint pour assurer l'étanchéité du carter Expired - Lifetime EP0690204B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4422594 1994-06-28
DE4422594A DE4422594A1 (de) 1994-06-28 1994-06-28 Kondensationsturbine mit mindestens zwei Dichtungen zur Abdichtung des Turbinengehäuses

Publications (3)

Publication Number Publication Date
EP0690204A2 true EP0690204A2 (fr) 1996-01-03
EP0690204A3 EP0690204A3 (fr) 1997-11-19
EP0690204B1 EP0690204B1 (fr) 2002-10-23

Family

ID=6521707

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95109678A Expired - Lifetime EP0690204B1 (fr) 1994-06-28 1995-06-22 Turbine à vapeur ayant au moins deux joint pour assurer l'étanchéité du carter

Country Status (6)

Country Link
US (1) US5577885A (fr)
EP (1) EP0690204B1 (fr)
JP (1) JP3696657B2 (fr)
DE (2) DE4422594A1 (fr)
DK (1) DK0690204T3 (fr)
FI (1) FI112108B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2262101A1 (fr) * 2009-06-12 2010-12-15 Siemens Aktiengesellschaft Procédé et agencement destinés à la rotation d'un ensemble turbo

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29806905U1 (de) * 1998-04-16 1998-07-09 Feodor Burgmann Dichtungswerke GmbH & Co, 82515 Wolfratshausen Gleitringdichtungsanordnung, insbesondere für die Flüssiggasabdichtung
DE19831988A1 (de) * 1998-07-16 2000-01-20 Abb Patent Gmbh Turbomaschine mit Gleitringdichtungen
DE19951570A1 (de) * 1999-10-27 2001-05-03 Abb Patent Gmbh Einrichtung zur Kompensierung des Axialschubs bei Turbomaschinen
US9363481B2 (en) * 2005-04-22 2016-06-07 Microsoft Technology Licensing, Llc Protected media pipeline
US8146922B2 (en) * 2008-06-25 2012-04-03 Dresser-Rand Company Shaft isolation seal
US20110164965A1 (en) * 2010-01-06 2011-07-07 General Electric Company Steam turbine stationary component seal
US9790863B2 (en) 2013-04-05 2017-10-17 Honeywell International Inc. Fluid transfer seal assemblies, fluid transfer systems, and methods for transferring process fluid between stationary and rotating components using the same
EP3517787B1 (fr) * 2017-02-02 2021-05-26 Mitsubishi Heavy Industries Compressor Corporation Compresseur

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3533829A1 (de) 1985-09-23 1987-04-02 Aeg Kanis Turbinen Dichtungsvorrichtung mit einer gasgeschmierten gleitringdichtung

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DE706180C (de) * 1938-12-30 1941-05-20 I G Farbenindustrie Akt Ges Stopfbuechse
US3392983A (en) * 1965-10-22 1968-07-16 Atomic Energy Commission Usa Safety control device for use with mechanical seals
DE3119467C2 (de) * 1981-05-15 1983-09-01 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Gleitringdichtung mit gasdynamischer Schmierung für hochtourige Strömungsmaschinen, insbesondere Gasturbinentriebwerke
US4557664A (en) * 1983-04-13 1985-12-10 Dresser Industries, Inc. Control of steam turbine shaft thrust loads
JPS59192803A (ja) * 1983-04-14 1984-11-01 Mitsubishi Heavy Ind Ltd 蒸気タ−ビンのグランドシ−リング装置
JPS59226206A (ja) * 1983-06-06 1984-12-19 Hitachi Ltd 蒸気タ−ビンの保護装置
DE3815679A1 (de) * 1988-05-07 1989-11-16 Kuehnle Kopp Kausch Ag Radialturbine
CA1326476C (fr) * 1988-09-30 1994-01-25 Vaclav Kulle Compresseur a gaz muni de joints de gaz sec
JPH04187897A (ja) * 1990-11-21 1992-07-06 Hitachi Ltd ドライガスシールの異常時のバックアップシステム
JPH05231103A (ja) * 1992-02-24 1993-09-07 Fuji Electric Co Ltd 復水タービンの軸封圧力制御装置
DE4216006C1 (fr) * 1992-05-12 1993-04-29 Mannesmann Ag, 4000 Duesseldorf, De
CH686525A5 (de) * 1992-07-02 1996-04-15 Escher Wyss Ag Turbomaschine .
US5375853B1 (en) * 1992-09-18 1998-05-05 Crane John Inc Gas lubricated barrier seal

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3533829A1 (de) 1985-09-23 1987-04-02 Aeg Kanis Turbinen Dichtungsvorrichtung mit einer gasgeschmierten gleitringdichtung

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2262101A1 (fr) * 2009-06-12 2010-12-15 Siemens Aktiengesellschaft Procédé et agencement destinés à la rotation d'un ensemble turbo
WO2010142486A1 (fr) * 2009-06-12 2010-12-16 Siemens Aktiengesellschaft Procédé et agencement pour le fonctionnement vireur d'un turbogénérateur
US9595900B2 (en) 2009-06-12 2017-03-14 Siemens Aktiengesellschaft Method and assembly for the turning gear operation of a turbo set

Also Published As

Publication number Publication date
DK0690204T3 (da) 2002-12-02
DE4422594A1 (de) 1996-01-04
EP0690204A3 (fr) 1997-11-19
EP0690204B1 (fr) 2002-10-23
US5577885A (en) 1996-11-26
FI953171A (fi) 1995-12-29
FI953171A0 (fi) 1995-06-27
JPH0849503A (ja) 1996-02-20
FI112108B (fi) 2003-10-31
JP3696657B2 (ja) 2005-09-21
DE59510430D1 (de) 2002-11-28

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