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
  • F01D19/00—Starting of machines or engines; Regulating, controlling, or safety means in connection therewith
  • F01D19/02—Starting of machines or engines; Regulating, controlling, or safety means in connection therewith dependent on temperature of component parts, e.g. of turbine-casing
• • 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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
  • F01K7/165—Controlling means specially adapted therefor

Definitions

• the invention relates to a method for anticipatory, also referred to as predictive, start-up of steam turbines and a module for carrying out the method according to claims 1 and 23 and is particularly suitable for An ⁇ fahroptimierung of steam turbines with and without Darnpf reheating.
• the plant operator incurs increased own costs, since the power generation takes place after the synchronization of the generator with the electrical supply network with a greatly reduced thermal efficiency compared to the operation of the turbine with the rated steam parameters.
• the power plant blocks are operated according to the power requirement of the electrical supply network. If the power requirement of the supply network is low, selected power plant blocks must even be completely switched off. On the other hand, if the power consumption increases again, the power plant blocks are started again and switched to the electrical supply network. For the power plant operator, this startup process is costly and, in particular, depending on the downtime of a power plant block, the startup costs increase steadily.
• the start of the boiler includes only a relatively small portion of the ge entire startup process of a power plant block.
• the start-up period in which the costs are influenced by the boiler, is limited to the rapid provision of steam for the turbine start.
• the starting parameters such as the live steam temperature and the inlet temperature of the superheated steam into the turbine, are usually selected according to the instantaneous metal temperature of the respective turbine parts.
• the amount of steam supplied by the boiler via the diverting stations and the starting steam pressure of the boiler are decisively influenced by the structural design of the boiler.
• start-up diagram for the shortest startup duration from the boiler and turbine suppliers, starting with the shortest startup duration can only be parameterized with the start steam set, such as the start steam temperature, the start steam pressure and the start metal temperature of the critical turbine components. For a cost-effective startup of the turbine and thereby also the power plant block thus the following two conditions must be met.
• the first necessary condition for the cost-effective startup of the turbine and thus also of the power plant block is that the allowances of the allowable stress on the turbine metals are fully utilized for achieving the shortest turbine run.
• the second necessary condition for the cost-effective startup of the turbine and thereby also of the power plant block is achieved by optimizing the increase of the inlet vapor pressure into the turbine.
• the stress on the turbine metal in particular in the turbine rotors and the housing wall of the turbine, has hitherto been regulated by means of a so-called limit regulation, which becomes active only in the region above the allowable stress of the turbine.
• This limit regulation corrects only for a short time the gradient of the inlet steam temperature of the turbine, if the stress of the turbine metal exceeds the permissible loading limit.
• no regulation takes place on a nominal value of the stress in the range below the allowable stress of the turbine core.
• the border control With the use of the border control, the shortest starting time of the turbine, and thereby also of the entire power plant block, which the power plant operator strives for is not achievable.
• the increases in the steam parameters such as the steam temperatures and the steam pressures at the turbine inlet, as well as the speed-up of the turbine are exclusively pre-programmed. Assuming that the shortest startup duration is ensured after a startup diagram, only the startup steam temperatures predefined in the startup diagram and the vapor pressure increase defined in the startup diagram apply.
• the invention has the object, a method and a module for carrying out the method for predictive Determination of optimum steam parameters at the turbine inlet, but also at Kesselaus ⁇ , specify for a cost-efficient startup of steam turbines, which is used in particular for the initial optimization of steam turbines with and without reheating, and thus an improved start-up strategy of the power plant block can be achieved with minimal cost.
• thermodynamic behavior of the real turbine system is replicated stationary and dynamic and accelerated compared to the behavior of the real plant accelerated by a multiple , with which the operator of the power plant block advantageously has the preview of the required steam parameters for the starting process of the turbine within a very short time.
• the acceleration factor can be set as large as desired by means of an adjuster placed on the predictive approach module.
• the inlet steam parameters refer to the live steam temperature and the live steam pressure for turbines without reheating and to the fresh steam steam temperature, the live steam pressure and also on the inlet steam temperature and the inlet steam pressure in turbines with reheat.
• the desired start steam temperature and the desired start steam pressure are also determined and made available to the boiler control for implementation be put.
• thermodynamic parameters determined with the module according to the invention are compared with the current parameters of the real turbine.
• the device for determining the reference voltage requires no measuring probe, which advantageously eliminates a costly design of the probe for detecting the stress of the critical turbine components, in particular in the double-housing design of a high-pressure turbine part due to the different housing expansions.
• a device for the operational detection of the stress in the critical metal components of the turbine, ie of the turbine metal, which is introduced, for example, on a special probe introduced from the outside into the turbine, preferably at a critical metal point, to determine the Steam tempera ture is located.
• the invention is furthermore provided as an alternative to detecting the three-dimensional stresses of the critical turbine components and the resulting results Comparative stresses, only the tangential thermal stresses of the outer and inner fibers of the critical point of the turbine component to be determined, namely on the basis of the simulated temperature difference between the respective metal fiber and the so-called integral mean temperature of the radial temperature distribution in the respective turbine component.
• the tangential thermal stresses of the outer and inner fibers of the critical point of the turbine component are displayed to the operating personnel in addition to the current reference stresses of the outer and inner fibers.
• the determined temperature differences only the tangential heat stress at the critical points of the turbine component, without taking into account the influence of the vapor pressure and the rotor speed, and thus represent only a part of tan ⁇ gentialen component of the existing three-dimensional voltage in the metal fiber
• the determined temperature difference than Control variable used instead of the determined comparison voltage and thus advantageously a better Re ⁇ gel quality compared to the use of the determined reference voltage as Regel ⁇ size achieved.
• the controlled variable with respect to the temperature difference is thus favorably influenced in terms of control technology when there is a change in the steam temperature as a result of the control variables changed by the controller, such as the opening speed of the control valves in turbines without reheating, the opening speed of the interception valves in turbines with reheat and the rate of change of the inlet steam temperature at the turbine inlet.
• the stress is applied to the critical points of the turbine, preferably the turbine rotors. but also the housing wall of the turbine, regulated to an optimally rising Beanspru ⁇ chungs setpoint in the closed loop until it reaches its zulässi ⁇ gen stress limit and further to the identical with the allowable stress value, which is also referred to as stress control.
• stress control As a manipulated variable, the opening speed of criz ⁇ valves and after reaching the maximum position of the control valves is used as a manipulated variable, the rate of increase of the inlet temperature at the turbine inlet.
• the module for predictive start optimization comprises a dynamic model of the steam pipelines between the boiler and the turbine, whereby the corresponding steam temperatures at the boiler outlet are determined on the basis of the determined optimum course of the respective inlet steam temperature into the turbine can be determined.
• the stress of the critical turbine metal is consistently exploited up to the permissible limit for achieving the shortest starting process, thereby fulfilling the first necessary condition for achieving the most cost-effective turbine startup is.
• the second necessary condition for achieving the most cost-effective turbine start-up is to ensure a monotonous increase in live steam enthalpy, taking into account the maintenance of a uniform steam cycle. Ferzeugung fills by means of a proposed limit control of the live steam enthalpy.
• the limit control of the monotone enthalpy increase uses the rate of change of the live steam pressure as the manipulated variable.
• the resulting temporal course of the live steam pressure is determined here as the optimum course for the start-up process with simultaneously satisfied secondary conditions with respect to the monotonous increase in live steam enthalpy.
• the enthalpy increase based on the fresh temperature increase is optimized as a percentage of the ratio of the differences between the live steam enthalpies and the live steam temperatures between their start and nominal values.
• the minimum cost is always determined by calculating the calculated cost K shown in the following formula (1) taking into account the specific purchase price of the fuel ⁇ ßR.th. the specific selling price of the electric current ⁇ elStr and the difference ⁇ of the energy in the fuel ThE ⁇ e and the energy E Tu converted with the turbine at the conclusion of the starting process according to the following formula
• the module according to the invention comprises a model for simulating stationary and dynamic behavior the real turbine system including the connecting pipe to the boiler, which simulates a much accelerated working model for the relevant physical variables, such as steam, metal temperatures, Dampfdrü ⁇ bridge, turbine speed by switching on the acceleration factor Be ⁇ .
• Another peculiarity of the model for simulating the real turbine installation, including the connecting pipe to the boiler, as well as the preview model is that with these models the starting process using a start-up diagram for utilizing the available at the beginning of the starting process Exemptions of the allowable stress of the turbine metal is verifiable.
• the resulting start-up costs by means of the above-mentioned Ekocons when starting after a start-up diagram can be determined with the preview model.
• a comparison when starting the turbine after a start-up diagram using the Vorschaumodells with the method described above is possible.
• the module for carrying out the method according to the invention for the predictive start of steam turbines of a turbine system comprises a preview model for determining the optimum steam parameters, such as the live steam pressure and the live steam temperature in front of the HP turbine in turbines without reheating and additionally the steam pressure and the Steam temperature of the superheated steam in turbines with reheating, at the turbine inlet and at the boiler outlet before each start of the turbine taking into account the complete Utilization of the allowable stress of the turbine metal, wherein the preview model the allowable stress of the turbine metal on an optimally rising stress setpoint until the allowable size of the Beanspru ⁇ tion of the turbine metal and continue until the end of the turbine approach to the permissible size of Regulates the stress limit of the turbine metal in a closed loop.
• the preview model for determining the optimum steam parameters, such as the live steam pressure and the live steam temperature in front of the HP turbine in turbines without reheating and additionally the steam pressure and the Steam temperature of the superheated steam in turbines with reheating, at the turbine inlet
• a model for simulating the stationary and dynamic behavior of the real turbine system which in particular the steam generator, is used to check the functions of the module according to the invention turbine, the piping, the bypass stations and the devices for operational recording of the rotor stress of the turbine simulates integrated into the module for predictive Anfahroptimierung.
• the model for simulating the real turbine system is set up to simulate the turbine metal temperatures of the critical turbine parts, in particular for determining the tangential heat stresses of the critical turbine metal, and to feed the preview model for further processing.
• the model for simulating the real turbine system comprises a partial model of the turbine, a partial model of diverter stations, a submodel of kausdampfrohr ⁇ lines between the boiler and the turbine to determine the heat and pressure loss in the steam pipe between the boiler and turbine and a module for determining the thermal stress on the critical components of the turbine.
• an arbitrary acceleration factor for the preview model and the model for simulating the real turbine system for realizing a short determination duration of the steam parameter for starting the turbine system are set by means of an adjuster.
• the turbine when the preview model is switched off, the turbine can be started up according to predetermined startup diagrams taking into account the time profiles of the entry steam parameters determined using the model for simulating the real turbine system.
• the Vorschaumodell to determine the most cost-effective temporal course of the steam parameters at the turbine inlet and the boiler outlet processed before the start of the turbine, the predetermined measurement signals of the real turbine, taking into account the boiler usually minimally realizable starting steam temperature and the start-inlet temperature of the superheated steam, as well as the start entry steam pressures.
• the described anticipatory determination of optimized steam parameters for cost-efficient startup of the turbine with the pre-expansion model can be activated not only before the turbine start, but also during the startup process of the real turbine in order to obtain the most favorable time profiles for the remaining part of the startup process To determine entry steam parameters and the operating staff to submit as default increases for the optimal start-up continuation.
• the preview model and / or the model for modeling the behavior of the real turbine system default parameters, such as parameters that can be taken from thermal diagrams of the real steam temperatures and pressures, material values of the turbine rotors and / or the turbine housing and permissible Process comparative stresses on critical turbine metal parts.
• the most cost-effective time profiles of the live steam parameters are advantageously obtained; in the case of steam turbines with overheating also the courses of the parameters of the temporarily superheated inlet steam. not only at the turbine inlet but also at the boiler outlet before each start of the turbine plant, taking into account the permissible stress of the turbine components, many times faster - in comparison with the duration of the real turbine start-up.
• the startup process is thus characterized by a minimal start-up cost and also by a higher economic efficiency.
• the method and system according to the invention with the characteristics described above can also be used for the predictive drive optimization of steam turbines of a turbine plant.
• 1 is an exemplary representation of the module according to the invention for the determination of a predictive low-cost startup of a steam turbine
• FIG. 2 shows a detailed representation of the module according to the invention for the determination of the anticipatory cost-effective startup of the steam turbine.
• FIG 3 shows an exemplary embodiment of the module according to the invention for determining a predictive low-cost startup of the steam turbine in online operation, the relevant physical process data of the real turbine being supplied to the module for predictive start optimization for carrying out the functions of the module for predictive start optimization.
• FIG. 4 shows a further exemplary embodiment of the module according to the invention for determining a prospective cost-effective startup of the steam turbine in offline operation, the relevant physical process data being the real turbine by means of a model for simulating the stationary turbine for executing the functions of the module according to the invention and dynamic behavior of the real turbine system
• 5 shows a representation for the verification of the startup of the turbine after a start-up diagram by means of the model for simulating the stationary and dynamic behavior of the real turbine system
• FIG. 4 shows a further exemplary embodiment of the module according to the invention for determining a prospective cost-effective startup of the steam turbine in offline operation, the relevant physical process data being the real turbine by means of a model for simulating the stationary turbine for executing the functions of the module according to the invention and dynamic behavior of the real turbine system
• 5 shows a representation for the verification of the startup of the turbine after a start-up diagram by means of the model for simulating the stationary and dynamic behavior of the real turbine system
• FIG. 4 shows a further exemplary embodiment of the
• Fig. 6 shows the optimal time courses of the steam parameters and to these the corresponding curves of the stress when starting the turbine after a 48 hours standstill.
• FIG. 1 shows an exemplary representation of the module 1 according to the invention for carrying out the method for determining a predictive cost-effective drive of a steam turbine, wherein optimum time profiles of the steam parameters at the turbine inlet and at the boiler outlet, in particular before each, are achieved by means of the module 1 according to the invention Startup of the turbine, taking into account the full utilization of the allowable stress of the turbine metal, hereinafter also called Metall ⁇ claiming determined.
• the steam parameters relate to the fresh steam pressure upstream of the HP turbine (PFD. V H D) and at the boiler outlet (p a ⁇ ) and the fresh steam temperature upstream of the HP Turbi ⁇ ne (TFD. V HDT) and at the boiler outlet (T a ⁇ ) for turbines without reheating or to the live steam pressure before the HD turbine (PFD V HD) and at the boiler outlet (p a ⁇ ), the live steam temperature (TFD.VHDT) before the HP turbine and at the boiler outlet (T a ⁇ ) Steam pressure in front of the MD turbine (PZÜ.VMD) and at the boiler outlet (p a zü) and the steam temperature upstream of the MD turbine (TZÜ.VMDT) and at the boiler outlet (T a zü) for turbines with reheat.
• the metal stress is controlled in a closed loop with the change in the opening speed of the control valves as manipulated variable YHD until the maximum control valve position. After reaching the maximum position of the control valves, the metal load in the closed loop is controlled with the change in the rate of increase of the live steam temperature as manipulated variable TFD.
• the change in the stress at the critical point of the turbine metal which occurs only due to a change in the heat transfer coefficient, is recognized by the module 1 according to the invention and the proportion of the activity of the above-mentioned control according to the remaining requirements of the regulated Be ⁇ reduced demand.
• the metal stress is controlled in turbines with reheating of the turbine part for the reheated steam in the closed loop with the change in the opening speed of the interceptor valves as manipulated variable YMD until reaching the maximum intercept valve position.
• the metal stress of the turbine part for the reheated steam is controlled with the change in the rate of increase of the inlet temperature of the reheated steam as control variable TZ Ü D.
• the reduction of the activity of the above-mentioned control is initiated when the load is due only to the change in the heat coefficient.
• the optimum time profiles of the steam parameters at the turbine inlet and at the boiler outlet determined by the module 1 for predictive start optimization are, in particular, the steam temperature profile TvT (t) upstream of the HP (high pressure) partial turbine and MD (partial pressure) partial turbine, the temporal vapor pressure curve pvT (t) before the HP turbine section and MD turbine, the thermal turbine power and / or generator power P (t), the comparison stresses ⁇ v (t) of the critical metal locations of the turbine, which are determined from the outer fiber tension ⁇ v, a (t) of the critical metal locations of the turbine and the inner-fiber stress ⁇ v, i (t) of the critical metal locations of the turbine are determined, the allowable reference stresses ⁇ v, zul (t) of the critical metal locations of the turbine, which are from the permissible Outside fiber tension and the permissible inner fiber tension ⁇ v, zul (t) of the critical metal locations of the turbine are determined, the characterizing ⁇ the metal temperature differences .DELTA.T (t) the comparison stresses ⁇
• the module 1 for predictive start-up optimization is provided to provide further time profiles Va1, Va2, such as the live steam enthalpy at the turbine inlet, for an optimized and cost-effective approach of the turbine.
• the module 1 for predictive start optimization processes in addition to the operationally detected temperature field in the turbine rotor and / or in the turbine housing G1, the start boiler pressure K1 and limit signals K2 from the boiler 2.
• the acceleration factor for connection to the module 1 by means of an adjuster 5, can be set arbitrarily large, so that the operating staff of the power plant block vor ⁇ in some advantageous way the preview of the required time profiles of Dampfparame ⁇ ter for the startup process of the turbine is present within a very short time.
• Art measurement signals R1 other parameters for determining the time profiles of the steam parameters are st from the real turbine 3, in particular the minimum realizable from the boiler start temperature T HD, HD and HD start pressure p s tart, HD, or the start - MD temperature T s tart, MD and start MD pressure p s tart, MD.
• the turbine speed n the steam pressure in the turbine before the HD blading P V HDB and before the MD blading P VM DB in a turbine with reheat, which for determining the time course of the live steam parameters - for steam turbines with reheat and the Increases in the parameters of the superheated steam - not only at the turbine inlet but also at the boiler outlet before each start of the turbine system are processed.
• the module 1 for predictive start optimization comprises a preview model 10 which, for example, determines the allowable stress of the turbine metal in FIG a closed control loop to an optimal, up to the value of the permissible stress guided setpoint controls and then complies with the allowable stress regulated until reaching the rated steam parameters.
• the manipulated variables are first the opening speed of the control valves and, after reaching the maximum position of the control valves, the rate of rise of the inlet temperature at the turbine inlet.
• the preview model comprises 10 partial models P1-P15.
• the submodels include, for example:
• thermodynamic model of the steam turbine P1 including the regenerative feed water heating, the bypass stations and the pressure dynamics of the reheater, in the case of turbines with reheating,
• the allowable stress X1 of the turbine from a database 11 of the module 1, the operationally detected turbine metal temperatures G1 from the device 4 for operational detection of the temperature field in Turbinenro ⁇ gate and / or in the turbine housing and the steam parameters R1 from the real turbine 3 the Vorschaumodell 10 for determining the optimized time profiles of the Dampf ⁇ parameters (TvT (t), pvT (t), P (t), ⁇ v (t), ⁇ v, zul (t), ⁇ T (t), ⁇ v , zul (t), Tstart.wu, the ekofactor and the entrainment enthalpy) at the turbine inlet and at the boiler outlet and these parameters (TvT (t), pvT (t), P (t), ⁇ v (t), ⁇ v, zul ( t), ⁇ T (t), ⁇ v, zul (t), Tstart.wu, the ekofactor and the entrainment enthalpy) at the outputs 01 to O9.
• the pre-foam model 10 receives measurement signals R1 from the real turbine 3 at a first input In1 and the operationally determined temperature field at a further input In2 from the device 4 in the turbine rotor and / or in the turbine housing G1.
• the switches A1 and A2 are in the upper position Ao.
• the starting boiler pressure K1 which corresponds to the minimum starting fresh steam pressure to be realized by the boiler 2 or the superheated pressure - in the case of a turbine with intermediate superheating - and the limiting signals K2 from the critical metal points in the boiler 2 are transmitted via a third input In3 and a fourth input In4 the Vorschaumodell 10 for taking into account the increases of the inlet steam parameters of the turbine supplied.
• the measurement signals simulated by the model 12 for simulating the turbine installation are fed to the preview model 10 for further processing at the exit M2.
• the measurement signals from the real turbine 3 are reproduced by means of the model 12 for simulating the turbine system and the preview model 10 is simulated as measurement signals M1 at the first input. gear In1.
• the switches A1 and A2 are in the lower position Au, the switch B in the upper position Bo, the switch A2 in the lower position Au and the switch C in the upper position Co.
• the model 12 is used to model the real turbine system.
• the signals R1 and G1 which are otherwise measured on the real turbine 3 are simulated and transmitted to the preview model 10 at the output M2 for further processing at the second input In2.
• the preview model 10 and / or the model 12 for simulating the turbine system also process default parameters X1, such as design temperatures provided by a heat circuit diagram, material values of the turbine rotors and / or the turbine housing and the permissible limit of the comparison stresses on the critical metal parts which are preferably stored in a database 11 of the module 1 and are supplied to the preview model 10 at a fifth input In5 and to the model 12 for simulating the real turbine system at a sixth input In6.
• default parameters X1 such as design temperatures provided by a heat circuit diagram, material values of the turbine rotors and / or the turbine housing and the permissible limit of the comparison stresses on the critical metal parts which are preferably stored in a database 11 of the module 1 and are supplied to the preview model 10 at a fifth input In5 and to the model 12 for simulating the real turbine system at a sixth input In6.
• the startup of the turbine is based on a start-up diagram integrated in module 1 and with the aid of the frequently accelerated preview model 10 and / or the model 12 for the simulation of the turbine system with respect to the utilization of the permissible limits of the stress on the critical turbine metal (See Fig. 5), verified and allows a comparison with the approach to the Vorschaum model.
• the switches B and A2 are in the lower positions Bu and Au and the switch C in the upper position Co and the temporal profiles of the Ein ⁇ vaporized vapor parameters according to startup diagram, which at the outputs D1 and D2 a Start-up diagram generator 13 are present, are transmitted by means of the input signals at Ers ⁇ th input In1 the preview model 10 and the seventh input In7 the model 12 for performing the verification.
• the switch C is in the lower position Cu, taking into account the currently measured metal temperatures at critical points of the turbine metal, the "desired start steam temperature" for the HP or MD turbine inlet of the boiler control is presented as specification for the realization and for the "desired start steam temperature” for the HD or MD turbine entry, the start-up preview is determined with the aid of the preview model 10.
• the module 1 shows an exemplary embodiment of the module 1 according to the invention for determining the anticipatory cost-effective startup of the steam turbine, wherein the measured process data from the real sub-turbine, such as temperatures and vapor pressures, of the functions of the module 1 for predictive start optimization, for example real turbine 3, the preview model 10 are supplied and thus present with these measurement signals of the turbine module 1.
• the measured process data from the real sub-turbine such as temperatures and vapor pressures
• the preview model 10 are supplied and thus present with these measurement signals of the turbine module 1.
• the allowable stress of the turbine is determined by means of the temperature field in the turbine metal operatively detected by the device 4 and fed to the preview model 10 at the second input In2 from the output G1 of the device 4 for operational detection of the temperature field in the turbine engine and / or in the turbine housing for further processing.
• connection of the measured values of the real turbine 3 to the module 1 for predictive startup optimization furthermore has the effect that at the first input In1 of the preview model 10, measurement signals R1 from the real turbine 3 are applied to the preview model for further processing.
• the preview model 10 further processes the default parameters X1 from the database 11, which are fed to the preview model at the fifth input In5.
• the preview model 10 processes, in addition to the detected metal temperatures G1, such as the outside temperature, mean temperature and internal temperature of the turbine metal, the starting boiler pressure K1 and limiting signals K2 from the boiler 2, which corresponds to the preview model at the third input In3 and at the fourth input In4 be supplied.
• the preview model 10 provides the optimized time profiles of the steam parameters for the optimized approach to the outputs 01-09 of the turbine and the further courses of the preselected physical quantities from the startup process at the output Va1.
• the stress of the critical turbine metal for the increase of the inlet steam temperature is fully used up to its permissible limit and the course of the increase of the live steam pressure and / or of the superheated pressure - in the case of turbines with reheatening runs optimally to the nominal values of the pressure, by regulating the stress in the turbine rotors in the closed loop and correcting the rise gradient of the inlet temperature even in the range below the permissible stress limits according to the above-described control method in the closed loop on a nominal value.
• the live steam pressure and the steam pressure in front of the turbine part optimally increase for the intermediate superheated steam.
• the optimum increase of the respective Eneries steam temperature is realized at the lowest start-up costs of the turbine in an advantageous manner.
• the module 1 shows a further exemplary embodiment of the module 1 according to the invention for determining a prospective cost-effective startup of the steam turbine, wherein the real turbine 3 is simulated by the model 12 for simulating the stationary and dynamic behavior of the turbine system and for executing the functions of the module 1 predictive start-up optimization when the real turbine 3 is switched off, the stationary and dynamic behavior of the real turbine 3 is simulated.
• the verification of the functions of the preview model is thus carried out by means of the model 12 contained in the module 1 for simulating the real turbine system, so that no signals from the real turbine 3 are required.
• the permissible stress of the turbine is simulated by means of the model 12 and used to determine the optimized time profiles of the steam parameters (TvT (t), pvT (t), P (t), ⁇ T (t), ⁇ Tzul (t), Tstart.wu, of the ekofactor and the live steam enthalpy) at the turbine inlet and at the boiler outlet are supplied to the preview model 10 as simulated physical quantities M2 at the second inlet In2 for the further processing described above.
• the model 12 for simulating the real turbine system also processes default parameters X1, such as the temperatures from a thermal map, Materi ⁇ alhong the turbine rotors and / or the turbine housing and the allowable limit of the comparison stresses on the critical metal parts, the sixth on ⁇ gear In6 the model 12 to replicate the real turbine system are supplied.
• default parameters X1 such as the temperatures from a thermal map, Materi ⁇ alen the turbine rotors and / or the turbine housing and the allowable limit of the comparison stresses on the critical metal parts, the sixth on ⁇ gear In6 the model 12 to replicate the real turbine system are supplied.
• the required measurement signals from the real turbine 3 are reproduced by the model 12 and transmitted to the preview model 10 as simulated measurement signals M1 at the first input In1.
• FIG. 5 shows an illustration for the verification of the startup of the turbine according to one of the startup diagrams by means of the startup diagram generator 13, wherein when the preview model 10 is switched off, the turbine starts up according to predefined approach diagrams, taking into account the model 12 Replica of the real turbine system determined time profiles of the entry steam parameters D2 is executed.
• the time profiles of the inlet steam parameters D2 according to the approach diagram generated with the startup diagram generator 13 are transmitted to the model 12 for modeling the real turbine system at the seventh input In7 in order to simulate the turbine startup according to the respective startup diagram with the model 12.
• FIG. 6a shows, by way of example, the optimum time profiles of the steam parameters
• FIG. 6b shows the corresponding curves of the stress of the turbine metal during startup of the HP turbine part after a forty-eight hour turbine standstill, taking into account the permissible stressing of the critical points of the turbine metal by means of the module 1 according to the invention.
• Fig. 6a the turbine speed n, the curves of the manipulated variable for the FD control valves YRD, the live steam pressure upstream of the HD turbine part PFD.
• V HDT the steam pressures before blading of the HP sub-turbine P V HDB, at the boiler outlet p a ⁇ , and behind the HP sub-turbine P hHDT , and the temperature profiles of the radial temperature distribution in the critical turbine component with the outer fiber T a , the integral Mean temperature T m and the inner fiber Tj and the curves of the temperatures in front of the HD turbine part TFD.
• the course of the steam mass flows IDHDT, rn MD ⁇ through the HD and MD turbine and the steam mass flow ITIHDBP through the HD diverter station and the generator power Pe e n for the optimized approach is shown.
• FIG. 6b shows the curves of the stress of the turbine metal corresponding to FIG. 6a, the time profiles of the admissible comparative stresses ⁇ a , zui, ⁇ j, zui of the critical metal locations of the turbine being shown.
• the permissible comparative stresses ⁇ a, Z ui, CFJ, ZU I refer to the outer fiber stress ⁇ a and inner fiber stress ⁇ i of the critical metal locations of the turbine in the corresponding permissible limit of the characteristic temperature differences ⁇ T i2UL , ⁇ T a to L as difference .DELTA.T a, ⁇ Tj between the integral mean temperature T m of the radial Tempera ⁇ turverotti in the turbine component and the temperature of the outer fiber T a, or the integral mean temperature T m of the radial temperature distribution in the Turbinen ⁇ component and the temperature of the inner fiber Tj of the metal turbine component.
• G1 output signals based on the determined temperature field of the turbine rotor and / or the turbine housing
• In1 Input signals as measurement signals to be adjusted from the real turbine In2 Input signals for metal temperatures to be matched from the model for the simulation of the turbine system or measurement signals from the real turbine
• In5 input signals such as the real steam temperatures or
• In6 input signals such as the real steam temperatures or
• M1 reproduced measured signals for the preview model by means of the model for simulating the turbine system
• Va 1 output signals of the preview model as further relevant data for the time profiles of the entry parameters from the determined start-up of the respective sub-turbine
• TFD Manipulated variable for the rate of change of the live steam inlet steam temperature at the turbine inlet in turbines without intermediate overheating
• ⁇ T aZUL permissible temperature differences as difference ⁇ Tj between the integra ⁇ len mean temperature T m of the radial temperature distribution in the Turbi ⁇ nenkomponente and the temperature of the inner fiber Tj

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Control Of Turbines (AREA)
• Production Of Liquid Hydrocarbon Mixture For Refining Petroleum (AREA)

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• 2004
  • 2004-12-02 DE DE102004058171A patent/DE102004058171A1/de not_active Withdrawn
• 2005
  • 2005-09-08 EP EP05785118A patent/EP1797284B1/fr not_active Not-in-force
  • 2005-09-08 DE DE502005003245T patent/DE502005003245D1/de active Active
  • 2005-09-08 AT AT05785118T patent/ATE389097T1/de not_active IP Right Cessation
  • 2005-09-08 PL PL05785118T patent/PL1797284T3/pl unknown
  • 2005-09-08 WO PCT/EP2005/009640 patent/WO2006037417A1/fr active IP Right Grant
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