EP2310636B1 - Procédé de conduite d'une turbine à vapeur - Google Patents

Procédé de conduite d'une turbine à vapeur Download PDF

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Publication number
EP2310636B1
EP2310636B1 EP09780710.1A EP09780710A EP2310636B1 EP 2310636 B1 EP2310636 B1 EP 2310636B1 EP 09780710 A EP09780710 A EP 09780710A EP 2310636 B1 EP2310636 B1 EP 2310636B1
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EP
European Patent Office
Prior art keywords
steam
turbine
low
inlet device
pressure
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
EP09780710.1A
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German (de)
English (en)
Other versions
EP2310636A1 (fr
Inventor
Jörg Eppendorfer
Bernd Leidinger
Markus Mantei
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Siemens AG
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Siemens AG
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Priority to PL09780710T priority Critical patent/PL2310636T3/pl
Publication of EP2310636A1 publication Critical patent/EP2310636A1/fr
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Publication of EP2310636B1 publication Critical patent/EP2310636B1/fr
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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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/08—Cooling; Heating; Heat-insulation
    • F01D25/12—Cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/18—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbine being of multiple-inlet-pressure type
    • F01K7/20—Control means specially adapted therefor
    • 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
    • F05D2260/00—Function
    • F05D2260/20—Heat transfer, e.g. cooling
    • F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
    • F05D2260/2322—Heat transfer, e.g. cooling characterized by the cooling medium steam
    • 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
    • F05D2270/00—Control
    • F05D2270/30—Control parameters, e.g. input parameters
    • F05D2270/303—Temperature
    • F05D2270/3032—Temperature excessive temperatures, e.g. caused by overheating

Definitions

  • the invention relates to a method for operating a steam turbine plant according to the preamble of claim 1.
  • a steam turbine the thermal energy supplied by the turbine steam is converted into mechanical work.
  • Such known steam turbines include a high-pressure side steam inlet and a low-pressure side steam outlet.
  • a control device for controlling at least the steam inlet, but usually also for controlling further plant components of a steam turbine-containing steam turbine plant is provided.
  • a shaft extending through the turbine, the so-called turbine rotor, is driven by means of turbine blades. By coupling the rotor with an electric generator allows a steam turbine z. B. the generation of electrical energy.
  • the rotor To drive the rotor typically blades and vanes are provided.
  • the blades are attached to the rotor and rotate therewith, whereas the blades are mostly stationary on a turbine housing.
  • the guide vanes z. B. be attached to a so-called vane carrier.
  • the vanes provide a favorable flow of steam through the turbine to achieve the most efficient energy conversion. In this reaction, both the temperature and the pressure of the steam are reduced in the course between the steam inlet and the steam outlet.
  • the steam which has already largely expanded and cooled in the preceding turbine parts is reheated in the low-pressure part (eg final stage) by the rotating rotor blades.
  • an additional steam supply optionally takes place via a further steam inlet device which is arranged in the turbine run between a high-pressure side steam inlet device and a low-pressure side steam outlet device of the steam turbine.
  • the inventive method is characterized in that in the presence of certain activation criteria, a special operating mode with a controlled steam supply via the further steam inlet device with simultaneous reduction or shutdown of the steam supply via the high-pressure steam inlet device is activated, which is deactivated again in the presence of certain deactivation criteria, with the the feed via the further steam inlet means is conditioned with values of temperature and pressure which are greater than those values of temperature and pressure which would result without the additional steam inlet at that point in the turbine run.
  • a further steam inlet is activated alternatively to the high-pressure steam inlet or in addition to the (in this case reduced) high-pressure steam inlet, in order to avoid excessive ventilation in particular, which advantageously hitherto associated with such ventilation temperature stress of the relevant Turbine components is reduced.
  • the life of these components can be advantageously extended.
  • the present inventors have recognized that a reduced temperature stress in the low pressure part the turbine advantageously allows the formation of turbine blades in lightweight construction, in particular z. B. using a fiber composite material such. CFK. Such materials have hitherto largely been considered unrealisable for the manufacture of these turbine blades.
  • a specially conditioned steam is provided for the supply via the further steam inlet device.
  • the steam supplied thereon as required is conditioned in terms of its temperature and pressure such that the values of temperature and pressure are greater than those values which would result without the additional steam inlet at this point in the turbine run.
  • the steam turbine plant may be, for example, an industrial steam turbine plant, in which the steam turbine is coupled to a generator for generating electrical energy, the power z. B. between about 2 MW and 50 MW.
  • the invention is also suitable for larger power plants, for example, for large-scale plants with a capacity greater than 100 MW.
  • the steam turbine plant can be, in particular, a condensation steam turbine plant in which the vapor discharged from the turbine on the low-pressure side is condensed and, for example, condensed. B. is then reheated in a cycle to produce the high pressure side to be admitted live steam.
  • Turbines are usually divided into several turbine stages to achieve the highest possible efficiency, such a stage consists of a row of vanes and a downstream adjacent row of blades.
  • the individual blades of a row extend here on common axial height, but angularly offset in the circumferential direction to each other in different radial directions.
  • stages provided on the high pressure side may be referred to as “high pressure part”, whereas one or more stages at the turbine end, ie low pressure side (output side) are usually referred to as “low pressure part” or “final stage (s)" of the turbine.
  • the entirety of the turbine stages arranged one behind the other can also be structurally or structurally divided into groups, each of which can have its own turbine housing ("drum") or are accommodated in a common turbine housing.
  • drum turbine housing
  • the naming system of the turbines and the general usage usually provide at least high pressure and low pressure stages. These may or may not, however, be arranged in their own housing (which may be connected, for example, by a pipeline to the adjacent housing).
  • the further steam inlet device is particularly preferably arranged in a low-pressure part of the turbine, in particular at the entrance of a "final stage".
  • the output of the last power amplifier can then z. B. may be connected directly to a condenser for condensing the low pressure side discharged steam.
  • the invention is of particular interest for steam turbines in which the pressure of the steam to be discharged via the low-pressure steam outlet device is smaller by at least a factor 10 2 than the pressure of the steam to be introduced via the high-pressure steam inlet device.
  • the high-pressure side admitted steam can z. B. have a pressure of more than 10 bar, whereas the steam to be discharged on the low pressure side may have a pressure of less than 0.5 bar.
  • the steam supplied via the further steam inlet means preferably has a pressure and a temperature which respectively lie between the corresponding values of the high-pressure side steam inlet and the low-pressure side steam outlet, the pressure and / or the temperature of the steam supplied via the further steam inlet device preferably being appreciably larger than which are at this point the turbine for the same operating condition of the turbine without such an additional steam inlet values to be expected.
  • a ventilation downstream of the further steam inlet can be reliably avoided.
  • the further steam inlet device which is preferably arranged at the inlet of a low-pressure part of the steam turbine, preferably comprises a controllable valve with which the steam supply as required can be controlled. Particularly preferred at this point is the use of a proportional valve, by means of which the vapor flow can be set exactly to a desired extent.
  • the steam supply is effected via the further steam inlet device.
  • a low-load operation can be detected, for example, based on an evaluation of a torque currently supplied by the turbine or a currently supplied rotary power (for example on a coupling of the turbine rotor).
  • the steam upon detection of a specific temperature increase in a low-pressure part of the steam turbine, the steam is supplied via the further steam inlet device.
  • a temperature increase can in the simplest case as exceeding a be defined predetermined temperature threshold.
  • the temperature increase can also be detected taking into account a current temperature change rate.
  • the high-pressure side steam inlet device may comprise a valve, for example a proportional valve.
  • a valve of the high-pressure side steam inlet device is closed and instead a valve of the further steam inlet device is opened.
  • valves mentioned can be infinitely adjustable with appropriate training and control.
  • the valve of the further steam inlet device can then be opened more or less as required, the valve of the high-pressure side steam inlet device preferably being closed more or less in a corresponding manner. So there is no need to make a sudden change in the steam supply.
  • Essential for the invention is triggered in response to currently detected operating parameters further steam supply, in which the high-pressure side steam supply is reduced.
  • the high-pressure side steam inlet is not completely closed even if the steam supply is appreciable via the further steam inlet device is, but z. B. at least the so-called "cooling steam amount" is passed through the high-pressure side part of the turbine. Otherwise there is a risk that the turbine runner driven by the steam supply in the low-pressure part leads to ventilation in the high-pressure part of the turbine.
  • the detected operating parameters comprise a torque measured at a turbine rotor.
  • the detected operating parameters include a temperature measured in a low-pressure part of the steam turbine.
  • further operating parameters of the system in particular the turbine can be measured, such.
  • B. a rotational speed or rotational speed of the turbine rotor. From detected torque and detected speed of the rotor can be z. B. derive a current rotational power of the turbine rotor.
  • the check for the existence of the activation criteria and deactivation criteria can, for. B. by means of suitable Software or be implemented by means of an electronically stored lookup table.
  • the criteria by which activation and deactivation of the special operating mode (“further steam inlet”) is triggered and / or other criteria may then be continuously checked during the special operating mode to control the turbine and / or other plant components in particular Operating mode.
  • an additional increase in the mechanical power consumption of the system components driven by the turbine is effected in the special operating mode.
  • this also includes the "connection" of specifically provided power consumers. It can therefore z. B. an additional power sensor can be integrated into the train, which absorbs power in idle mode and z. B. transformed into heat, which is dissipated. This also reduces the ventilation in the final stages.
  • power from an electric generator coupled to the turbine can be converted to heat via heating resistors.
  • the additional, provided by increasing the mechanical power consumption can, for. B. for heating the input side of the turbine and / or via the further steam inlet device supplied medium (eg., Water) can be used.
  • this power can be used to preheat the condensate in a circuit formed as a condensing steam turbine plant system.
  • a water injection in an outlet region of the Controlled turbine which can advantageously provide an additional cooling effect.
  • a safety monitoring takes place with respect to a temperature measured in a low-pressure part of the steam turbine, and the turbine fulfills predetermined uncertainty criteria (eg. excessive temperature and / or excessive Temperatursantrainstendenz) is switched off.
  • At least some of the components in a low-pressure part of the turbine, in particular moving blades and / or vanes, are manufactured in lightweight construction, for example using a fiber composite material (eg CFRP).
  • CFRP fiber composite material
  • Fig. 1 1 illustrates a steam turbine plant 10 with a steam turbine 12 and a control device 14 for controlling the steam turbine 12.
  • the turbine 12 comprises a high-pressure steam supply line 16 for supplying live steam via a controllable valve V1 and a low-pressure steam discharge 18, which leads in the illustrated embodiment to a (not shown) condenser of a steam cycle, from which after heating the condensate live steam is generated again.
  • live steam for example at a pressure of about 10 2 bar and a temperature of about 500 ° C
  • the supply line 16 at the input of the turbine 12 is supplied.
  • the vapor has a substantially reduced pressure and a substantially reduced temperature (eg, about 10 1 bar and about 200 ° C).
  • the steam expands further and emerges again at the outlet of the turbine 12 via the discharge line 18 at about 10 -1 bar and about 40 ° C. (eg 0.05 bar and 33 ° C.).
  • the thermal energy of the steam supplied to the turbine 12 is converted into mechanical turning work.
  • a turbine runner 22 extending through the turbine 12 is driven by blades 24 attached thereto and in turn drives an electrical generator 28 via an optional gear 26.
  • the turbine 12 could alternatively or additionally z.
  • Pumps or other units. Powerful pumps and / or compressors are z. B. often needed to implement large-scale industrial chemical processes.
  • the blades 24 alternate with vanes 30, which provide for a favorable flow of steam through the turbine.
  • the vanes 30 are secured to the inside of a turbine housing and project radially inwardly therefrom.
  • the turbine 12 in the exemplary embodiment illustrated comprises a total of six blade row pairs 30, 24.
  • FIG. 1 Rotor blades 24 of turbine 12 arranged on the right-hand side, which belong to a first expansion section or a low-pressure step group 12-2, whereas those in FIG Fig. 1 left blades are attributable to a second expansion section or a high-pressure stage group 12-1.
  • erosion-resistant blades 24 in the low-pressure part 12-2 or corresponding blade coatings fails in practice, however, because appropriate materials often have comparatively low allowable maximum temperatures, which can be easily exceeded in the turbine.
  • Turbine blades in the low pressure part of known turbines are therefore usually z. B. made of steel or titanium.
  • the blades 24 of the low-pressure stage group 12-2 can be very advantageously designed as lightweight vanes, optionally with a special coating.
  • control device 14 a plurality of measured variables are entered, such as a temperature T, which is detected by a arranged in the low-pressure stage 12-2 temperature sensor 42, a speed n and a torque TQ, which by a (not shown) sensors, for example in Range of the transmission 26 are detected.
  • a temperature T which is detected by a arranged in the low-pressure stage 12-2 temperature sensor 42
  • a speed n and a torque TQ which by a (not shown) sensors, for example in Range of the transmission 26 are detected.
  • the control device 14 By means of an evaluation of the supplied operating parameters T, n, TQ,..., The control device 14 generates a plurality of output signals for controlling various system components.
  • control signals sv1 and sv2 for example, the valves V1 and V2 designed as infinitely controllable are actuated at the steam supply lines 16 and 40.
  • valve V1 In a normal operation, such as under full load, the valve V1 is open and the valve V2 is closed.
  • the control device 14 detects on the basis of the detected operating parameters an excessive increase in temperature in the range of the output stage 12-2 and a low-load operation, which due to the effect of ventilation such a temperature increase to be afraid. In such a case, the control device 14 counteracts a temperature increase by a special operating mode, in which specially conditioned steam is introduced via the further steam supply line 40.
  • the relatively low power of the turbine 12 is thus largely or even substantially only by means of the supply line 40 subsequent low pressure part of the turbine 12 is generated.
  • a ventilation in this area is advantageously avoided and the temperature remains low (or decreases).
  • this particular mode of operation by simultaneously closing or essentially closing the valve V1, the high pressure side supplied steam flow and thus the power generation in the high pressure stage 12-1 can be switched off or reduced.
  • the effect achieved according to the invention can, for. B. by an additional water injection in the range of the final stage 12-2, especially in a so-called Abdampfgephinuses the power amplifier 12-2, are still supported.
  • a cooling water injection can, for. B. in the mentioned special operating mode of the control device 14 and (quantitatively) controlled, preferably in dependence on operating parameters, which are detected during this mode of operation on the turbine 12.
  • FIG. 3 is a flowchart for illustrating the turbine control effected by the control device 14, which can be realized for example by means of software running in the control device 14.
  • the processing starts in a step S10.
  • a torque (eg clutch torque) TQ is smaller than a predetermined threshold value TQa.
  • step S14 it is checked in a step S14 whether the temperature T measured in the output stage 12-2 is greater than a predetermined threshold value Ta.
  • step S12 if the torque TQ is comparatively small (step S12) or the temperature T is relatively large (step S14), the processing proceeds to step S16, in which the valve V1 is closed and the valve V2 is opened.
  • the "special operating mode" is activated, which counteracts the temperature increase in the final stage of the turbine 12.
  • step S18 This particular mode of operation is in the illustrated embodiment only deactivated again when both the torque TQ is greater than a predetermined threshold TQb (step S18) and the temperature T is less than a predetermined threshold Tb (step S20). Only if the result of both polls is positive, the processing proceeds to a step S22, at which the special operating mode is again deactivated by the valve V1 is opened again and the valve V2 is closed again. Then, the processing returns to step S12.
  • the "special operating mode" which in the simplest case is a switching of the steam supply from the high-pressure side supply via the line 16 to the intermediate supply via the line 40, can in practice be adapted in many ways to the respective requirements.
  • a control carried out as a function of the detected operating parameters in particular stepless control of the valves V1 and / or V2.
  • the possibility may be mentioned that, in particular on the basis of the measured temperature T, it is possible to control the system 10 with the aim of keeping this temperature T within a certain range or below a certain maximum temperature.
  • z. B. a temperature control can be provided.
  • Such a temperature control can, for. Example, consist of proportional, integral and differential components, and optionally have a pilot control in dependence on the torque or the rotational power.
  • the turbine 12 may be in the special operating mode z. B. controlled speed controlled or power controlled or regulated to certain characteristics of the driven system components (eg generator 28).
  • control device can control a water injection in order to achieve an additional cooling effect.
  • the design of the turbine 12 and its control advantageously allows a reduction or complete elimination of the ventilation in low load or idle mode, thus advantageously the occurring in such an operating condition temperature increase in the low pressure part can be avoided.
  • At least some of the rotor blades in the low-pressure part of the turbine are made of lightweight construction, in particular of fiber composite material (eg CFRP), optionally with a coating (to increase the resistance to drop impact erosion).
  • CFRP fiber composite material
  • a coating to increase the resistance to drop impact erosion.
  • Such a coating is necessary in practice, in particular for many fiber composite materials, since these materials z. B. have a lower drop resistance compared to hardened steel.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Turbines (AREA)

Claims (10)

  1. Procédé de conduite d'une installation de turbine à vapeur comprenant une turbine à vapeur (12) avec un dispositif d'admission de vapeur (16, V1) côté haute pression, un dispositif d'échappement de vapeur (18) côté basse pression et un autre dispositif d'admission de vapeur (40, V2) placé entre ces derniers sur le parcours, dans lequel un apport de vapeur est commandé par l'intermédiaire dudit autre dispositif d'admission de vapeur (40, V2) en fonction de paramètres de fonctionnement détectés (TQ, T), caractérisé en ce qu'en présence de critères d'activation déterminés un mode de fonctionnement spécial (S16) est activé, comprenant un apport de vapeur commandé par l'intermédiaire de l'autre dispositif d'admission de vapeur (40, V2) avec réduction ou coupure simultanée de l'apport de vapeur par l'intermédiaire du dispositif d'admission de vapeur (16, V1) côté haute pression, lequel mode est désactivé (S22) en présence de critères de désactivation déterminés, la vapeur prévue pour être apportée par l'intermédiaire de l'autre dispositif d'admission de vapeur (40, V2) étant conditionnée par des valeurs de température et de pression supérieures aux valeurs de température et de pression que l'on obtiendrait sans l'apport de vapeur supplémentaire à cet endroit du parcours de turbine.
  2. Procédé selon la revendication 1, dans lequel, lorsqu'un fonctionnement à faible charge de la turbine à vapeur (12) est détecté, l'apport de vapeur est effectué par l'intermédiaire de l'autre dispositif d'admission de vapeur (40, V2).
  3. Procédé selon l'une des revendications précédentes, dans lequel, lorsqu'une certaine augmentation de la température est détectée dans une partie basse pression (12-2) de la turbine à vapeur (12), l'apport de vapeur est effectué par l'intermédiaire de l'autre dispositif d'admission de vapeur (40, V2).
  4. Procédé selon l'une des revendications précédentes, dans lequel, dans le mode de fonctionnement spécial, l'apport de vapeur par l'intermédiaire du dispositif d'admission de vapeur (16, V1) côté haute pression et l'apport de vapeur supplémentaire par l'intermédiaire de l'autre dispositif d'admission de vapeur (40, V2) sont commandés en fonction d'une température (T) mesurée dans une partie basse pression (12-2) de la machine à vapeur (12).
  5. Procédé selon l'une des revendications précédentes, dans lequel les paramètres de fonctionnement détectés (TQ, T) comprennent un couple (TQ) mesuré sur un rotor de turbine (22).
  6. Procédé selon l'une des revendications précédentes, dans lequel les paramètres de fonctionnement détectés (TQ, T) comprennent une température (T) mesurée dans une partie basse pression (12-2) de la turbine à vapeur (12).
  7. Procédé selon l'une des revendications précédentes, dans lequel des composants (26, 28) de l'installation entrainés par la turbine à vapeur (12) sont commandés dans le mode de fonctionnement spécial (S16) pour augmenter la puissance mécanique absorbée.
  8. Procédé selon la revendication 7, dans lequel les composants (26, 28) de l'installation entrainés par la turbine à vapeur (12) sont prévus pour transformer, au moins partiellement, la puissance absorbée dans le mode de fonctionnement spécial en chaleur pour préchauffer le condensat dans un circuit de l'installation (10) conçue sous forme d'installation de turbine à vapeur à condensation.
  9. Procédé selon l'une des revendications précédentes, dans lequel une injection d'eau est également commandée dans une région de sortie de la turbine à vapeur (12) en fonction des paramètres de fonctionnement détectés (TQ, T).
  10. Procédé selon l'une des revendications précédentes, dans lequel une surveillance de sécurité par rapport à une température (T) mesurée dans une partie basse pression (12-2) de la turbine à vapeur (12) a lieu dans le mode de fonctionnement spécial (S16) et dans lequel la turbine à vapeur (12) est arrêtée lorsque des critères d'insécurité prédéterminés sont remplis.
EP09780710.1A 2008-07-16 2009-07-16 Procédé de conduite d'une turbine à vapeur Not-in-force EP2310636B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL09780710T PL2310636T3 (pl) 2008-07-16 2009-07-16 Sposób eksploatacji turbiny parowej

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810033402 DE102008033402A1 (de) 2008-07-16 2008-07-16 Dampfturbinenanlage sowie Verfahren zum Betreiben einer Dampfturbine
PCT/EP2009/059152 WO2010007131A1 (fr) 2008-07-16 2009-07-16 Installation de turbine à vapeur et procédé de conduite d'une turbine à vapeur

Publications (2)

Publication Number Publication Date
EP2310636A1 EP2310636A1 (fr) 2011-04-20
EP2310636B1 true EP2310636B1 (fr) 2016-08-31

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EP09780710.1A Not-in-force EP2310636B1 (fr) 2008-07-16 2009-07-16 Procédé de conduite d'une turbine à vapeur

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Country Link
US (1) US8770914B2 (fr)
EP (1) EP2310636B1 (fr)
DE (1) DE102008033402A1 (fr)
PL (1) PL2310636T3 (fr)
WO (1) WO2010007131A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102010004386B4 (de) * 2010-01-12 2015-05-13 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Dampfturbosatzes eines Kraftwerkes
US20130305720A1 (en) * 2012-05-15 2013-11-21 General Electric Company Systems and methods for active temperature control in steam turbine
JP5397560B1 (ja) * 2013-04-05 2014-01-22 富士電機株式会社 抽気蒸気タービン発電設備の保安運転方法および装置
CN103470317A (zh) * 2013-09-11 2013-12-25 上海电气电站设备有限公司 一种汽轮机联合阀门结构
JP5946976B2 (ja) 2014-06-06 2016-07-06 株式会社テイエルブイ 流体使用設備管理方法、又は、流体使用設備管理システム
CN107524478B (zh) * 2017-07-18 2024-05-28 华电电力科学研究院有限公司 用于抽凝背系统的低压缸冷却装置及其应用
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PL2310636T3 (pl) 2017-04-28
DE102008033402A1 (de) 2010-01-21
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US20110185732A1 (en) 2011-08-04
EP2310636A1 (fr) 2011-04-20

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