EP2065641A2 - Procédé de fonctionnement d'un générateur de vapeur en flux continu, ainsi que générateur de vapeur en flux à sens unique - Google Patents

Procédé de fonctionnement d'un générateur de vapeur en flux continu, ainsi que générateur de vapeur en flux à sens unique Download PDF

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Publication number
EP2065641A2
EP2065641A2 EP07023081A EP07023081A EP2065641A2 EP 2065641 A2 EP2065641 A2 EP 2065641A2 EP 07023081 A EP07023081 A EP 07023081A EP 07023081 A EP07023081 A EP 07023081A EP 2065641 A2 EP2065641 A2 EP 2065641A2
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EP
European Patent Office
Prior art keywords
evaporator
flow
characteristic
mass flow
enthalpy
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.)
Withdrawn
Application number
EP07023081A
Other languages
German (de)
English (en)
Other versions
EP2065641A3 (fr
Inventor
Jan BRÜCKNER
Joachim Dr. Franke
Frank Thomas
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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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, Siemens Corp filed Critical Siemens AG
Priority to EP07023081A priority Critical patent/EP2065641A3/fr
Priority to MYPI2010002487A priority patent/MY154744A/en
Priority to CA2706794A priority patent/CA2706794C/fr
Priority to JP2010535331A priority patent/JP5318880B2/ja
Priority to CN200880116657.7A priority patent/CN102216685B/zh
Priority to ES08853664T priority patent/ES2402842T3/es
Priority to RU2010126182/06A priority patent/RU2010126182A/ru
Priority to PT88536644T priority patent/PT2212618E/pt
Priority to PCT/EP2008/065522 priority patent/WO2009068446A2/fr
Priority to AU2008328934A priority patent/AU2008328934B2/en
Priority to PL08853664T priority patent/PL2212618T3/pl
Priority to EP08853664A priority patent/EP2212618B1/fr
Priority to US12/743,881 priority patent/US9482427B2/en
Priority to BRPI0819844-6A priority patent/BRPI0819844A2/pt
Priority to TW097145590A priority patent/TWI465674B/zh
Priority to ARP080105181A priority patent/AR069453A1/es
Publication of EP2065641A2 publication Critical patent/EP2065641A2/fr
Priority to ZA201001475A priority patent/ZA201001475B/xx
Publication of EP2065641A3 publication Critical patent/EP2065641A3/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/38—Determining or indicating operating conditions in steam boilers, e.g. monitoring direction or rate of water flow through water tubes

Definitions

  • the invention relates to a method for operating a continuous steam generator with a Verdampferlik Structure, wherein a device for adjusting the feedwater mass flow ⁇ a setpoint ⁇ s for the feedwater mass flow ⁇ is supplied. It further relates to a forced once-through steam generator for carrying out the method.
  • the heating of a number of steam generator tubes which together form an evaporator heating surface, leads to a complete evaporation of a flow medium in the steam generator tubes in one pass.
  • the flow medium - usually water - is usually before its evaporation to the Verdampferlik Structure flow medium side upstream preheater, commonly referred to as economizer, fed and preheated there.
  • the feedwater mass flow is regulated in the evaporator heating surface.
  • the evaporator flow should be changed as synchronously as possible to the heat input into the evaporator, because otherwise a deviation of the specific enthalpy of the flow medium at the outlet of the evaporator from the target value can not be reliably avoided.
  • Such an undesirable deviation of the specific enthalpy makes it difficult to regulate the temperature of the live steam emerging from the steam generator and moreover leads to high material loads and thus to a reduced service life of the steam generator.
  • the feedwater flow control can be designed in the manner of a so-called predictive or predictive design.
  • the required feedwater desired values should also be provided during load changes as a function of the current or expected future operating state.
  • a continuous-flow steam generator in which the feedwater flow is controlled by a preliminary calculation of the required feedwater quantity.
  • the basis for the calculation method is the heat flow balance of the evaporator heating surface into which the feedwater mass flow should enter, in particular at the inlet of the evaporator heating surface.
  • the desired value for the feedwater mass flow is determined from the ratio of the heat flow currently transferred to the flow medium by the heating gas in the evaporator heating surface and a desired enthalpy increase of the flow medium in the evaporator heating surface given with respect to the desired live steam state.
  • the measurement of the feedwater mass flow directly at the entrance of the evaporator heating surface proves to be technically complex and not reliably feasible in any operating condition.
  • the feedwater mass flow at the inlet of the preheater is alternatively measured and included in the calculations of the feedwater quantity, which however is not always equal to the feedwater mass flow at the inlet of the evaporator heating surface.
  • Both of these concepts for a predictive mass flow control are based as essential input variable on the setpoint value for the steam generator power, from which the characteristic values flowing into the actual setpoint determination are calculated on the basis of stored correlations and in particular by recourse to previously obtained calibration or reference measurements.
  • this requires sufficiently stable and clearly attributable to a firing capacity overall system properties, as is usually the case with fired steam generators.
  • other systems such as in a design of the continuous steam generator as a waste heat boiler for heat recovery from the flue gas of an upstream gas turbine, such conditions are not available.
  • a firing capacity can not be used to the same extent as a free parameter as in directly fired boilers, as in an interconnection as waste heat boiler usually considered as the primary criterion for controlling the entire system operation of the gas turbine, the system state of the be adapted to other components.
  • the invention is therefore an object of the invention to provide a method for operating a steam generator of the type mentioned above, with a comparatively low cost even when operating the steam generator as a waste heat boiler a particularly well adapted to the current or expected heat input into the evaporator heating adjustment of the feedwater mass flow allowed by the evaporator heating. Furthermore, a particularly suitable for the implementation of the method forced circulation steam generators should be specified.
  • this object is achieved according to the invention by determining the heat flow transferred from the heating gas to the flow medium taking into account a temperature characteristic value characteristic of the actual temperature of the heating gas at the evaporator inlet and a mass flow characteristic characteristic of the current mass flow of the heating gas.
  • the invention is based on the consideration that a useful, sufficiently reliable predictive mass flow control should also be adapted to the particular features of the waste heat boiler as well as for waste heat boiler switched steam generator.
  • the firing capacity is not a suitable parameter that allows a sufficiently reliable conclusion on the underlying heat flow balance.
  • gas turbine internal parameters may occur, so that on the basis of these sizes no acceptable conclusion on the enthalpy when entering the heating gas in the flue gas duct the steam generator is possible.
  • the heat flow balance used to determine the required feedwater flow should therefore be based on other, particularly suitable parameters.
  • the heating gas temperature when entering the evaporator and the mass flow of the heating gas are provided.
  • a pilot-controlled calculation of the required feedwater quantity is made possible on the basis of a heat flow balance of the evaporator, which may optionally also optionally include subsequent superheater heating surfaces.
  • the temperature characteristic characteristic of the actual temperature of the heating gas at the evaporator inlet it is possible in particular to determine a particularly reliable characteristic value for the heating gas enthalpy at the evaporator inlet taking into account the heating gas enthalpy at the evaporator outlet, which in turn can be calculated from the mass flow characteristic characteristic of the current mass flow, and thus a particularly reliable and needs-based determination of the current heat supply. or carry-over from the fuel gas to the feed water.
  • the desired value -Enthalpieerhöhung the flow medium can be determined in the evaporator, wherein from the ratio of these sizes a suitable setpoint for the feedwater mass flow can be calculated.
  • a characteristic value which is particularly representative of the current situation is preferably taken into account.
  • Such characteristic values can be suitably determined on the basis of currently available measurement data and can be made available in a suitable manner, in particular with recourse to stored memory characteristic values.
  • a particularly reliable evaluation of the heat flow balance and thus the determination of a particularly precisely calculated feedwater desired value is made possible by advantageously taking into account in each case a currently measured value as a characteristic temperature characteristic and / or as a characteristic mass flow characteristic.
  • the transferred from the heating gas to the flow medium heat flow is advantageously based on a heat flow balance determined, in which the enthalpy difference of the hot gas between evaporator inlet and evaporator outlet is used as the essential input variable.
  • a particularly reliable characteristic calculation is also considered in a further advantageous embodiment but also that reproduced by this enthalpy difference lowering of the energy content in the flue gas when passing through the Verdampfersammlung description on the one hand to an enthalpy in the flow medium within the Verdampfershirts Chemistry, on the other hand also to Energyein- and / or Aussticher binen in the components of the evaporator, ie in particular in the steam generator tubes and other metallic components, can lead.
  • this aspect of the energy input and / or outflow of heat in the metal masses is suitably taken into account as a characteristic correction value by which the enthalpy difference of the heating gas is suitably modified.
  • the current enthalpy of the hot gas at the evaporator outlet is advantageously taken into account by being determined on the basis of the pressure of the flow medium at the evaporator inlet taking into account the characteristic mass flow characteristic value for the current mass flow of the hot gas.
  • the mass flow characteristic which is preferably present in the form of a measured value, but alternatively can also be calculated indirectly via further parameters by using stored correlation or other characteristic values, is advantageously first in the so-called "pinch point" of the steam generator, ie in the temperature difference converted between the outlet temperature of the flue gas and the boiling temperature of the flow medium at the evaporator inlet, said temperature difference advantageously added to a determined based on the pressure at the evaporator inlet boiling temperature of the flow medium and from this sum the enthalpy of the heating gas at the evaporator outlet is determined.
  • the determination of the desired enthalpy increase of the flow medium in the evaporator heating surface is advantageously based, on the one hand, on the basis of suitable measured values, for example the pressure and the temperature of the flow medium at the evaporator inlet, the determined actual enthalpy.
  • suitable measured values for example the pressure and the temperature of the flow medium at the evaporator inlet
  • the determined actual enthalpy is specified.
  • the continuous steam generator can be operated in a so-called "Benson control mode".
  • the "Benson control mode” at the outlet of the evaporator heating surface overheating of the flow medium is present.
  • the overfeeding of a water storage tank connected downstream of the evaporator heating surface can be accepted, and the subsequent heating surfaces can still be partially supplied with unevaporated flow medium, so that complete evaporation of the flow medium takes place only in the subsequent heating surfaces.
  • the setting of a setpoint temperature for the flow medium at the outlet of the evaporator lying above the saturation temperature of the flow medium by a predetermined temperature difference of, for example, 35 ° C.
  • the saturation temperature of the flow medium can be specified in particular as the desired steam parameter.
  • This is advantageously in the specification of the target value for the enthalpy the flow medium at the outlet of the evaporator heating considered a current cooling demand in the evaporator heating downstream injection coolers.
  • the desired live steam temperature should therefore be achieved in particular as far as possible by a suitable adjustment of the feedwater flow, so that the additional cooling requirement in the injection coolers can be kept particularly low.
  • the enthalpy setpoint of the flow medium at the evaporator outlet are suitably increased, so that a correspondingly small amount of feed water is supplied via the thus changed setpoint for the feedwater mass flow.
  • the steam generator can also be operated in a so-called "level control mode" in which the water level is varied and readjusted in a water storage tank connected downstream of the evaporator heating surface, wherein overflow of the water storage tank should be avoided as far as possible.
  • level control mode in which the water level is varied and readjusted in a water storage tank connected downstream of the evaporator heating surface, wherein overflow of the water storage tank should be avoided as far as possible.
  • the water level within the water reservoir is kept as far as possible in a predetermined desired range, in an advantageous embodiment for the setpoint for the feedwater mass flow, a level correction value is taken into account, which characterizes the deviation of the actual level of the fill in the water storage of an associated setpoint.
  • the stated object is achieved by designing a feedwater flow control system assigned to a device for adjusting the feedwater mass flow for specifying the desired value for the feedwater mass flow on the basis of said method.
  • the forced-circulation steam generator is designed in a particularly advantageous manner as a heat recovery steam generator, which is acted upon the hot gas side with the exhaust gas from an associated gas turbine plant.
  • the advantages achieved by the invention are, in particular, that a predictive or preventive determination of the anticipated need is particularly far-reaching by the specific consideration of a characteristic of the current temperature of the flue gas when entering the Schugaskanal and / or for the current mass flow of the flue gas oriented feedwater mass flow set point is possible, whereby even in the case of use of the steam generator as a waste heat boiler and consequently only a lack of correlation of the corresponding enthalpy characteristics with the power or delivery characteristic of the system a particularly reliable and stable control behavior can be achieved.
  • the once-through steam generator 1, 1 'according to the FIG. 1 . 2 each have a designated as economizer preheater 2 for intended as a flow medium feed water, which is located in a throttle cable, not shown.
  • the preheater 2 is on the flow medium side, a feedwater pump 3 upstream and a Verdampferrois Structure 4 downstream.
  • On the output side the Verdampferrois Chemistry 4 flow medium side via a water reservoir 6, which may be configured in particular as a water separator or Abscheideflasche connected to a number of downstream superheater 8, 10, 12, which in turn may be provided for adjusting the steam temperatures and the like with injection coolers 14, 16.
  • the forced once-through steam generator 1, 1 ' is configured in each case as a waste heat boiler or heat recovery steam generator, wherein the heating surfaces, ie in particular the preheater 2, the evaporator 4 and the superheater 8, 10, 12 are arranged in a hot gas channel acted upon by the gas from an associated gas turbine plant in a hot gas side.
  • the once-through steam generator 1, 1 ' is designed for a regulated admission with feed water.
  • the feedwater pump 3 is followed by a controlled by a servomotor 20 throttle valve 22, so that via suitable control of the throttle valve 22, the funded by the feedwater pump 3 in the direction of the preheater 2 feed water quantity or the feedwater mass flow is adjustable.
  • the throttle valve 22 is followed by a measuring device 24 for determining the feedwater mass flow ⁇ through the feedwater line.
  • the servo motor 20 is controlled via a control element 28, the input side is acted upon by a supplied via a data line 30 setpoint ⁇ s for the feedwater mass flow ⁇ and determined by a measuring device 24 actual value of the feedwater mass flow ⁇ .
  • a tracking requirement is transmitted to the controller 28, so that in the case of a deviation of the actual from the nominal value, a corresponding tracking of the throttle valve 22 takes place via the activation of the motor 20.
  • the input line 30 with an input for setting the set value ⁇ s for the feedwater mass flow Spe feedwater flow control 32, 32 'connected.
  • This is designed to determine the setpoint ⁇ s for the feedwater mass flow ⁇ based on a heat flow balance in the evaporator 4, wherein the setpoint ⁇ s for the feedwater mass flow ⁇ based on the ratio of the currently transferred in the evaporator 4 from the heating gas to the flow medium heat flow on the one hand and a desired enthalpy increase of the flow medium in the evaporator heating surface 4 predetermined with regard to the desired live steam state is predetermined on the other hand.
  • a use of such a concept of providing a target value for the feedwater mass flow on the basis of a heat balance even for a once-through steam generator 1, 1 'in construction as a waste heat boiler is in the embodiments according to FIG. 1 .
  • FIG. 2 in particular achieved in that the transferred from the heating gas to the flow medium heat flow is determined taking into account a characteristic of the current temperature of the heating gas at the evaporator inlet temperature characteristic and a characteristic of the current mass flow of the heating gas mass flow characteristic.
  • the feedwater flow control 32 to a divider 34, the numerator as a suitable characteristic for the currently transmitted in the evaporator 4 from the heating gas to the flow medium heat flow and as a denominator with respect to the desired live steam condition predetermined predetermined characteristic value for the desired desired enthalpy of the Flow medium is supplied in the evaporator 4.
  • the divider 34 is connected on the input side to a function module 36, which is based on a supplied, characteristic of the current temperature of the hot gas at the evaporator inlet temperature characteristic value as output value outputs a value for the enthalpy of the hot gas at the evaporator inlet.
  • the supply of a measured value characteristic of the current temperature of the heating gas at the evaporator inlet is provided as a temperature characteristic value.
  • the characteristic value which is characteristic of the enthalpy of the heating gas at the evaporator inlet is output to a subtractor 38, from which characteristic value a characteristic value for the enthalpy of the gas at the evaporator outlet provided by a function module 40 is subtracted.
  • the sum of two temperature values is formed on the input side of the functional element 40 by a summing element 42.
  • the saturation temperature of the flow medium determined on the basis of the pressure of the flow medium at the evaporator inlet is taken into account via a functional element 44, which is connected on the input side to a pressure sensor 46.
  • a functional element 48 which in turn is fed via a further functional element 50 for the current mass flow of the fuel gas characteristic mass flow characteristic, the so-called "pinch point", namely the determined from the mass flow of the fuel gas temperature difference of the heating gas temperature at the evaporator outlet minus the boiling point the flow medium at the evaporator inlet, considered. From these two temperature contributions added via the summing element 42, the enthalpy of the heating gas at the evaporator outlet, optionally with reference to suitable tables, diagrams or the like, is thus provided by the function module 40.
  • the subtracting element 38 thus supplies the enthalpy difference or balance of the heating gas, that is to say the difference between the heating gas enthalpy at the evaporator inlet and the enthalpy of the heating gas at the evaporator outlet.
  • This enthalpy difference is forwarded to a multiplier 52, which is also supplied with the characteristic mass flow characteristic value, which, incidentally, can be present as a currently measured value.
  • the multiplier 52 thus provides a characteristic value for the output from the flue gas to the evaporator 4 heat output.
  • a correction for heat input and / or accumulation effects in the components of the evaporator heating surface 4, in particular in the metal masses, is initially provided.
  • said characteristic value for the heat output emitted by the heating gas is first supplied to a subtracting element 54, where a correction value characteristic of the heat input or withdrawal into the evaporator components is subtracted.
  • a functional element 56 On the input side, this is in turn subjected to the output value of a further functional element 58, in that a mean temperature value for the metal masses of the evaporator heating surface 4 is determined.
  • the further functional member 58 is connected on the input side to a pressure sensor 60 arranged in the water reservoir 6, so that the further functional member 58, the average temperature of the metal masses based on the pressure of the flow medium, for. B. by equating with the boiling temperature associated with this pressure in the water tank 6 can determine.
  • the subtracting member 54 On the output side, the subtracting member 54 thus transfers a heat output for the heating gas, reduced by the thermal power stored in the metal of the evaporator heating surface 4, and thus a characteristic characteristic of the heat output to be delivered to the flow medium.
  • This characteristic is used in the divider 34 as a counter, which is divided there by a denominator, the one in the With regard to the desired live steam state, the predetermined desired enthalpy increase of the flow medium in the evaporator heating surface 4 corresponds, so that from this division or this ratio the desired value ⁇ s for the feedwater mass flow ⁇ can be formed.
  • the divider 34 is connected on the input side to a subtractor 70. This is acted on the input side with a provided by a functional element 72 characteristic value for the desired setpoint for the enthalpy of the flow medium at the evaporator outlet.
  • the subtracting element 70 is acted upon on the input side by a characteristic value or actual value for the current enthalpy of the flow medium at the evaporator inlet which is subtracted in the subtracter 70 from the characteristic value for the enthalpy at the evaporator outlet.
  • the function module 74 is connected to the pressure sensor 46 and to a temperature sensor 76 in order to form the characteristic value for the actual enthalpy at the evaporator inlet.
  • the once-through steam generator 1 and the once-through steam generator 1 'according to the FIG. 1 or 2 differ with regard to the design of their feedwater flow control 32, 32 'in particular with respect to the formation of the setpoint for the enthalpy at the evaporator outlet and thus with respect to the input-side loading of the functional module 72nd
  • the forced flow steam generator 1 according FIG. 1 is designed for operation in the so-called "Level Control Mode", in which the water level is regulated in the water reservoir 6, wherein the superheater 8, 10, 12 connected downstream of the evaporator heating surface 4 exclusively Steam is passed, and the evaporator outlet side still entrained water in the water reservoir 6 is deposited.
  • the function module 72 is acted on the input side, on the one hand, with a measured value, supplied by the pressure sensor 60, for the pressure in the water reservoir 6.
  • the function module 72 is supplied via an associated input 78 with a parameter characteristic of the desired live steam condition, for example a desired steam content at the evaporator outlet. From this parameter together with the mentioned pressure characteristic value, the desired value for the enthalpy of the flow medium at the evaporator outlet is subsequently formed in the function module 72.
  • the divider 34 supplies, on the output side, a desired value for the feedwater mass flow which is aligned and determined on the basis of the heat balance mentioned.
  • This setpoint value is subsequently corrected in a subsequent adder 80 by a correction value which reproduces a desired change in the water level in the water reservoir 6 via the feedwater inflow.
  • the water level in the water reservoir 6 is detected by a level sensor 82.
  • This actual value for the fill level is subtracted in a subtractor 84 from a stored or otherwise presettable setpoint for the fill level in the water reservoir 6.
  • an effective feedwater mass flow value is determined in a subsequent actuator 86, with which the water reservoir 6 is to be acted upon to correct its fill level.
  • This correction value is added in the adder 80 to the reference value for the feedwater mass flow determined on the basis of the heat flow balance, so that a value composed of the two proportions is output as setpoint value ⁇ s for the feedwater mass flow.
  • the forced once-through steam generator 1 ' according to FIG. 2 designed for operation in the so-called "Benson Control Mode", in which an overfeed of the intended as a water separator 6 and the complete evaporation of the flow medium only in the following superheater 8, 10, 12 is possible.
  • the functional element 72 via which the setpoint value for the enthalpy of the flow medium is to be output at the evaporator outlet, likewise receives on the input side the pressure value in the water separator 6 determined by the pressure sensor 60 on the input side.
  • the function module 72 is preceded on the input side by another functional module 90, which determines a suitable setpoint for the temperature of the flow medium in the water reservoir 6 on the basis of a stored functionality or the desired live steam condition based on the actual pressure in the water reservoir 6 determined by the pressure sensor 60.
  • a temperature value may be stored as the setpoint for the temperature, which corresponds to the saturation temperature of the flow medium at the determined pressure plus a predetermined minimum superheat of, for example, 35 ° C.
  • the function module 72 determines from said setpoint value for the temperature, taking into account the current pressure value, said setpoint value for the enthalpy of the flow medium at the evaporator outlet.
  • This setpoint which is provided by the function module 72 and is essentially oriented on the properties of the flow medium as such, is subsequently changed in a downstream adder 92 by a further correction value.
  • This further correction value supplied by a function module 94 essentially takes into account, in the manner of a trim function, the deviation of the currently detected live steam temperature from the live steam temperature actually desired in view of the desired live steam condition. A Such a deviation can be made noticeable in particular by the fact that, if the live steam temperature is too high, cooling demand arises in the injection coolers 14, 16, and thus the admission of the injection coolers 14, 16 with cooling medium is required.
  • the functional module 94 shifts this cooling demand away from the injection coolers 14, 16 and towards an increased feedwater supply.
  • the desired enthalpy of the flow medium at the evaporator outlet is correspondingly lowered in the function module 94, in order to minimize the cooling requirement.
  • the enthalpy setpoint is increased via the correction value provided by the function module 94 and its addition in the adder module 92.
  • a downstream direct control loop in which a value for the enthalpy of the flow medium at the evaporator outlet is determined in a function module 100 on the basis of the measured values in the water reservoir 6 and compared in a differentiation module 102 with the desired enthalpy, ie with the desired enthalpy value.
  • the setpoint-actual deviation is ascertained, which is superimposed, via a downstream regulator 104 in an adder 106, on the desired value for the feedwater mass flow provided by the divider 34.
  • This superimposition is suitably delayed in time and damped, so that this control intervention only in case of need, so too rough control deviation, intervenes.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Air Conditioning Control Device (AREA)
  • Central Heating Systems (AREA)
EP07023081A 2007-11-28 2007-11-28 Procédé de fonctionnement d'un générateur de vapeur en flux continu, ainsi que générateur de vapeur en flux à sens unique Withdrawn EP2065641A3 (fr)

Priority Applications (17)

Application Number Priority Date Filing Date Title
EP07023081A EP2065641A3 (fr) 2007-11-28 2007-11-28 Procédé de fonctionnement d'un générateur de vapeur en flux continu, ainsi que générateur de vapeur en flux à sens unique
AU2008328934A AU2008328934B2 (en) 2007-11-28 2008-11-14 Method for operating a once-through steam generator and forced-flow-once-through steam generator
PL08853664T PL2212618T3 (pl) 2007-11-28 2008-11-14 Sposób eksploatacji przepływowej wytwornicy pary oraz wytwornica pary z przepływem wymuszonym
JP2010535331A JP5318880B2 (ja) 2007-11-28 2008-11-14 貫流ボイラの運転のための方法ならびに強制貫流ボイラ
CN200880116657.7A CN102216685B (zh) 2007-11-28 2008-11-14 直流式锅炉的运行方法及强制式直流锅炉
ES08853664T ES2402842T3 (es) 2007-11-28 2008-11-14 Procedimiento para el funcionamiento de un generador de vapor de paso así como generador de vapor de paso único
RU2010126182/06A RU2010126182A (ru) 2007-11-28 2008-11-14 Способ эксплуатации прямоточного парогенератора и парогенератор с принудительной циркуляцией
PT88536644T PT2212618E (pt) 2007-11-28 2008-11-14 Método para funcionamento de um gerador de vapor contínuo e de um gerador de vapor de consumo forçado
PCT/EP2008/065522 WO2009068446A2 (fr) 2007-11-28 2008-11-14 Procédé d'utilisation d'un générateur de vapeur à circulation et générateur de vapeur à circulation forcée
MYPI2010002487A MY154744A (en) 2007-11-28 2008-11-14 Method for operating a once-through steam generator and forced-flow steam generator
CA2706794A CA2706794C (fr) 2007-11-28 2008-11-14 Procede d'utilisation d'un generateur de vapeur a circulation et generateur de vapeur a circulation forcee
EP08853664A EP2212618B1 (fr) 2007-11-28 2008-11-14 Procédé de fonctionnement d'un générateur de vapeurà passage unique, ainsi que générateur de vapeur à passage unique
US12/743,881 US9482427B2 (en) 2007-11-28 2008-11-14 Method for operating a once-through steam generator and forced-flow steam generator
BRPI0819844-6A BRPI0819844A2 (pt) 2007-11-28 2008-11-14 Método de operação de um gerador de vapor de passagem única e gerador de vapor de fluxo forçado
TW097145590A TWI465674B (zh) 2007-11-28 2008-11-26 運轉直流式蒸汽產生器之操作方法及強制式直流蒸汽產生器
ARP080105181A AR069453A1 (es) 2007-11-28 2008-11-28 Procedimiento para la operacion de un generador de vapor de circulacion continua, asi como generador de vapor de circulacion continua forzada
ZA201001475A ZA201001475B (en) 2007-11-28 2010-03-01 Method for operating a once-through steam generator and forced-flow steam generator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07023081A EP2065641A3 (fr) 2007-11-28 2007-11-28 Procédé de fonctionnement d'un générateur de vapeur en flux continu, ainsi que générateur de vapeur en flux à sens unique

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EP2065641A2 true EP2065641A2 (fr) 2009-06-03
EP2065641A3 EP2065641A3 (fr) 2010-06-09

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EP07023081A Withdrawn EP2065641A3 (fr) 2007-11-28 2007-11-28 Procédé de fonctionnement d'un générateur de vapeur en flux continu, ainsi que générateur de vapeur en flux à sens unique
EP08853664A Active EP2212618B1 (fr) 2007-11-28 2008-11-14 Procédé de fonctionnement d'un générateur de vapeurà passage unique, ainsi que générateur de vapeur à passage unique

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CA2706794A1 (fr) 2009-06-04
CA2706794C (fr) 2016-03-22
AU2008328934A1 (en) 2009-06-04
ES2402842T3 (es) 2013-05-09
PT2212618E (pt) 2013-05-24
JP5318880B2 (ja) 2013-10-16
WO2009068446A3 (fr) 2010-07-15
JP2011504996A (ja) 2011-02-17
TW200936957A (en) 2009-09-01
TWI465674B (zh) 2014-12-21
ZA201001475B (en) 2010-10-27
EP2212618A2 (fr) 2010-08-04
EP2065641A3 (fr) 2010-06-09
US9482427B2 (en) 2016-11-01
AU2008328934B2 (en) 2013-05-23
MY154744A (en) 2015-07-15
PL2212618T3 (pl) 2013-09-30
RU2010126182A (ru) 2012-01-10
US20100288210A1 (en) 2010-11-18
WO2009068446A2 (fr) 2009-06-04
AR069453A1 (es) 2010-01-20
EP2212618B1 (fr) 2013-04-03
BRPI0819844A2 (pt) 2015-06-16
CN102216685A (zh) 2011-10-12
CN102216685B (zh) 2014-10-22

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