US20150083111A1 - Method and apparatus for operating a solar thermal power plant - Google Patents

Method and apparatus for operating a solar thermal power plant Download PDF

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Publication number
US20150083111A1
US20150083111A1 US14/391,746 US201314391746A US2015083111A1 US 20150083111 A1 US20150083111 A1 US 20150083111A1 US 201314391746 A US201314391746 A US 201314391746A US 2015083111 A1 US2015083111 A1 US 2015083111A1
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US
United States
Prior art keywords
steam
heat transfer
transfer medium
solar
exit
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.)
Abandoned
Application number
US14/391,746
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English (en)
Inventor
Jan Brückner
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
Original Assignee
Siemens AG
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Filing date
Publication date
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Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BRÜCKNER, Jan, THOMAS, FRANK
Publication of US20150083111A1 publication Critical patent/US20150083111A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S10/00—Solar heat collectors using working fluids
    • F24J2/04—
    • 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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/006—Methods of steam generation characterised by form of heating method using solar heat
    • F24J2/402—
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S50/00—Arrangements for controlling solar heat collectors
    • F24S50/40—Arrangements for controlling solar heat collectors responsive to temperature
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y02E10/44—Heat exchange systems
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y02E10/46—Conversion of thermal power into mechanical power, e.g. Rankine, Stirling or solar thermal engines

Definitions

  • Solar thermal power plants now represent an alternative to conventional electricity generation.
  • One power plant concept already known in this field is the so-called parabolic trough power plant.
  • thermal oil is conventionally used as a heat transfer medium, which flows through the parabolic troughs and thereby absorbs the heat provided by the sun.
  • the heat absorbed in this way by the heat transfer medium is subsequently used to generate steam in a steam generator.
  • the heat transfer medium flows around the steam generator tubes filled with water vapor in the steam generator, in such a way that it delivers its heat to the cooler steam generator tubes.
  • the steam thus generated in the tubes then drives a conventional steam turbine.
  • intermediate superheating of the steam is conventionally provided. That is to say, the cooled steam leaving an HD turbine stage is delivered to a further heat exchanger also heated by the heat transfer medium, and brought again to a higher temperature.
  • this intermediate superheater steam now flows around the intermediate superheater tubes, through which the heat transfer medium flows, in such a way that this steam is heated according to the strongly heated tubes carrying the heat transfer medium. Owing to the relatively large volume flows of the intermediate superheater steam, the pressure losses for the steam are kept within acceptable limits with such an intermediate superheater design.
  • the amount of heat transfer medium supplied may in this case be regarded as a free parameter. That is to say, the intermediate superheater only needs to be supplied with enough heat transfer medium so that, for a predetermined steam mass flow coming from the HD turbine, the desired final temperature of the intermediate superheater steam is reached. This final temperature can therefore be used as a regulating quantity for the amount of heat transfer medium to be supplied.
  • An aspect relates to a method and an apparatus for regulation of the amount of heat transfer medium to be supplied to the intermediate superheater.
  • Embodiments of the invention make use of an amount of heat transfer medium adapted to the system state and ascertained predictively. Specifically, this means that, at any given time, the mass flow of the heat transfer medium necessary in order to reach the final temperature of the intermediate superheater steam is ascertained on the basis of system-specific parameters in a predictive way.
  • the essential parameter used here is the heat flux required in order to reach the final temperature of the intermediate superheater steam, which is to be transferred from the heat transfer medium, for example thermal oil, to the steam in the intermediate superheater by means of correspondingly arranged tubes.
  • the temperature and the pressure of the steam at the entry of the intermediate superheater are measured and converted into an associated actual entry enthalpy.
  • an associated setpoint exit enthalpy is likewise determined with measured steam pressure and a desired temperature setpoint value to be adjusted.
  • the heat flux required for heating the steam is known. If the entry and exit temperatures as well as their associated pressures of the heat transfer medium are likewise measured, and with known substance values of the heat transfer medium are converted into associated enthalpies, then here again it is possible to determine an enthalpy difference of the heat transfer medium between the entry and exit. If the heat demand calculated for the steam is divided by this enthalpy difference of the heat transfer medium, then the required mass flow of the heat transfer medium is known at any given time for the steady system state.
  • the method according to embodiments of the invention, or the apparatus according to embodiments of the invention it is also possible to regulate the final temperature of the intermediate superheater with the least possible fluctuations even during very unsteady system states of the parabolic trough power plant.
  • system-specific parameters for example measurement quantities
  • the mass flow requirement for the heat transfer medium may be precalculated for any given system state at any time.
  • an externally imposed perturbation for example a change in the steam mass flow
  • the method according to embodiments of the invention, and the apparatus according to embodiments of the invention already react predictively to an expected change in the exit temperature of the intermediate superheater, and therefore already counteract such a change in advance.
  • the method according to embodiments of the invention and the apparatus according to embodiments of the invention are integrated into a solar-thermal parabolic trough power plant with an intermediate superheater so as to ensure steam temperatures which are as constant as possible at the exit of the intermediate superheater even for very unsteady operating states, such as occur with increased frequency in solar-heated power plants (for example as a result of cloud movement).
  • the availability of the overall power plant system can be improved by a concept which is economical in terms of material.
  • embodiments of the invention are employed in solar thermal power plants in which thermal oil is used as the heat transfer medium.
  • the concept according to embodiments of the invention may, however, in principle also be used in systems with different heat transfer media, assuming that the system has a separate intermediate superheater, not integrated into the steam generator, as a further heat exchanger. Furthermore, the concept according to embodiments of the invention are also suitable without significant modifications for use in combination with other components, for example final injection coolers or comparable measures for stabilizing the feed water mass flow in the steam generator of a solar thermal parabolic trough power plant.
  • FIG. 1 schematically shows a regulating concept
  • FIG. 2 schematically shows an enhanced regulating concept.
  • FIG. 1 schematically shows a possible regulating concept for the steady state operation of a solar thermal parabolic trough power plant.
  • the intermediate superheater Z Represented here are the intermediate superheater Z, a regulating device K for adjusting and correcting the mass flow of the heat transfer medium W, and a corresponding mass flow setpoint value control device for driving and therefore controlling the regulating device K as a function of an ascertained enthalpy difference of the heat transfer medium W between its entry and exit into and out of the intermediate superheater Z and an ascertained enthalpy difference of the steam D between its exit and entry out of and into the intermediate superheater Z.
  • the intermediate superheater Z is connected on the steam side to corresponding lines for conveying the steam D, and on the heat transfer medium side to corresponding tubes for conveying the heat transfer medium W.
  • the regulating device K for adjusting the mass flow of the heat transfer medium W comprises a motor actuator, a throttle valve driven by the motor actuator, and a measuring device arranged before the throttle valve for ascertaining the respective current mass flow of the heat transfer medium W. Together with a correspondingly formed regulating element, the measuring device, the motor actuator and the throttle valve form a control loop for modifying the currently adjusted mass flow of the heat transfer medium W according to a predetermined mass flow setpoint value.
  • the regulating device K is controlled by a mass flow setpoint value control device, which specifies the desired mass flow setpoint value.
  • the mass flow setpoint value control device is formed according to embodiments of the invention so that, during operation of a solar thermal power plant in which steam D is heated in the intermediate superheater Z in the water/steam circuit by a solar-thermally heated heat transfer medium W to an adjustable setpoint temperature value at the exit, in order to heat the steam D to an adjusted setpoint temperature value, a mass flow of the heat transfer media W entering the intermediate superheater Z is correspondingly modified as a function of an ascertained enthalpy difference of the heat transfer medium W between its entry and exit into and out of the intermediate superheater Z and an ascertained enthalpy difference of the steam D between its exit and entry out of and into the intermediate superheater Z.
  • the mass flow setpoint value control device comprises a first and a second module 10 and 11 for ascertaining the enthalpy of the heat transfer medium W at the entry and exit, as well as a third and a fourth module 20 and 21 for ascertaining the enthalpy of the steam D at the entry and exit.
  • This determination is carried out on the basis of measurement values of correspondingly arranged pressure sensors WP10, WP11, DP20 and DP21, and correspondingly arranged temperature sensors WT10, WT11 and DT20, for measuring the pressure and the temperature both of the steam D and of the heat transfer medium W.
  • These sensors are preferably arranged directly at the entry and exit of the steam D and of the heat transfer medium W into the intermediate superheater Z, so as to be able to ascertain as accurately as possible the system-specific parameters currently prevailing in the intermediate superheater Z.
  • the intermediate superheater Z Since the amount of heat transfer medium supplied can be regarded as a free parameter in an intermediate superheater Z physically separated from the steam generator, the intermediate superheater Z only needs to be supplied with as much heat transfer medium W as is necessary in order to reach a desired setpoint temperature of the intermediate superheater steam. This setpoint temperature at the exit of the steam D from the intermediate superheater Z is then intended to be used as a regulating quantity for adjusting the optimal mass flow of the heat transfer medium W. In order to adjust this optimal setpoint temperature, a controlling element 22 is therefore provided, by which a selected setpoint value can be specified for the fourth module 21 .
  • the mass flow setpoint value control device comprises a first subtractor element 24 for subtracting the ascertained steam entry enthalpy from the ascertained steam exit enthalpy, as well as a second subtractor element 12 for subtracting the ascertained heat transfer medium entry enthalpy from the ascertained heat transfer medium exit enthalpy.
  • a parameter characterizing a mass flow of the incoming steam D is ascertained.
  • this characteristic parameter is multiplied by the difference from the first subtractor element 24 , and in a subsequent divider element 30 the product from the multiplier element 25 is divided by the difference from the second subtractor element 12 .
  • the result of this divider element 30 is delivered as an ascertained mass flow setpoint value, then as a regulating quantity to the regulating device K for modifying the currently adjusted mass flow of the heat transfer medium W.
  • FIG. 2 shows another configuration according to embodiments of the invention, in which the amounts of heat stored in or released from the tube material of the intermediate superheater Z, as well as the amounts of heat stored in or released from the heat transfer medium located in the intermediate superheater Z, are additionally taken into account for the unsteady state case.
  • a greater or lesser heat supply by the heat transfer medium is consequently necessary compared with the heat flux determined for the quasi-steady state.
  • the flow of the heat transfer medium through the intermediate superheater Z needs to be adapted.
  • the characteristic temperature parameter ascertained for the material may in this case be used.
  • This may, for example, be the average material temperature of all the tubes.
  • the heat flux stored in the tube material or released from the tube material could be quantified in more detail by suitable measures, and appropriately taken into account when the required heat transfer mass flow is ascertained.
  • a sixth module 50 is provided for taking into account thermal energy stored in or released from tube walls of the intermediate heater Z, the output value of which is added to the product from the multiplier element 25 by an adder element 60 before the divider element 30 .
  • the change in the average material temperature of the tube material is in this case to be evaluated by means of a first-order differencing element.
  • a suitable time constant Tm and a suitable gain Km of this differencing element an approximately exact precalculation of the amounts of stored heat is possible.
  • a seventh module 55 may be provided for taking into account a thermal energy stored in or released from the heat transfer medium W, the output value of which is added to the product from the multiplier element 25 by an adder element 60 before the divider element 30 .
  • the change in the average temperature of the heat transfer medium is to be evaluated by means of a first-order differencing element.
  • the product of the mass and heat capacity is preferably to be used in the first case of the tube material, and in the second case of the heat transfer medium.
  • this product is also to be divided by the time constant of the associated differencing element.
  • the time constant of the two differencing elements may be different, and is preferably to be coupled to the flow time of the steam, of the heat transfer medium or a suitable combination of the two quantities.
  • additional regulation 70 may be superordinated to this method with predictive nature, as represented in FIG. 2 , which regulation, in the event of a steady state deviation of the steam temperature ascertained by means of a temperature sensor DT 70 at the exit of the intermediate superheater Z from the temperature setpoint value specified by the controlling element 22 , constantly eliminates this deviation. It is, however, to be taken into account that this superordinate regulation 70 may only intervene correctively, and must therefore have a relatively slow regulating behavior in relation to the overall regulating task.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Sustainable Development (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Turbines (AREA)
US14/391,746 2012-04-19 2013-04-11 Method and apparatus for operating a solar thermal power plant Abandoned US20150083111A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102012206466A DE102012206466A1 (de) 2012-04-19 2012-04-19 Verfahren und Vorrichtung zum Betrieb eines solarthermischen Kraftwerks
DE102012206466.4 2012-04-19
PCT/EP2013/057541 WO2013156375A1 (fr) 2012-04-19 2013-04-11 Procédé et dispositif pour faire fonctionner une centrale héliothermique

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US20150083111A1 true US20150083111A1 (en) 2015-03-26

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US14/391,746 Abandoned US20150083111A1 (en) 2012-04-19 2013-04-11 Method and apparatus for operating a solar thermal power plant

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US (1) US20150083111A1 (fr)
EP (1) EP2825736B1 (fr)
AU (1) AU2013248442B2 (fr)
DE (1) DE102012206466A1 (fr)
ES (1) ES2604818T3 (fr)
PT (1) PT2825736T (fr)
WO (1) WO2013156375A1 (fr)

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3269921A (en) * 1961-07-03 1966-08-30 Phillips Petroleum Co Computing and controlling the enthalpy of a process stream
US4574870A (en) * 1980-09-12 1986-03-11 Jacob Weitman Method and apparatus for controlling a counter-flow heat exchanger
US5363905A (en) * 1992-03-06 1994-11-15 Bayer Aktiengesellschaft Method of controlling heat exchangers using enthalpy flow as the correcting variable
US20060032606A1 (en) * 2002-10-15 2006-02-16 Claus Thybo Method and a device for detecting an abnormality of a heat exchanger and the use of such a device
US7007473B2 (en) * 2001-09-28 2006-03-07 Honda Giken Kogyo Kabushiki Kaisha Temperature control device of evaporator
US20060112682A1 (en) * 2002-08-09 2006-06-01 Honda Giken Kogyo Kabushiki Kaisha Working medium supply control system in heat exchanger
US20070157614A1 (en) * 2003-01-21 2007-07-12 Goldman Arnold J Hybrid Generation with Alternative Fuel Sources
US20100078011A1 (en) * 2008-09-25 2010-04-01 Peter Feher Ultra-compact, linear, solar-thermal steam generator
US20100212318A1 (en) * 2007-09-11 2010-08-26 Siemens Concentrated Solar Power Ltd. Solar thermal power plants
US20130213041A1 (en) * 2012-02-16 2013-08-22 Ormat Technologies Inc. Apparatus and method for increasing power plant efficiency at partial loads

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4217626A1 (de) * 1992-05-27 1993-12-02 Siemens Ag Zwangdurchlaufdampferzeuger
EP1614962A1 (fr) * 2004-07-09 2006-01-11 Siemens Aktiengesellschaft Méthode pour l'opération d'une chaudière à vapeur à passage unique
DE102007005562A1 (de) * 2007-01-24 2008-08-07 Deutsches Zentrum für Luft- und Raumfahrt e.V. Verfahren zum Betreiben eines solarthermischen Kraftwerks und solarthermisches Kraftwerk
EP2187051A1 (fr) * 2008-11-12 2010-05-19 Siemens Aktiengesellschaft Procédé et dispositif destinés à la surchauffe intermédiaire dans une centrale thermique solaire à l'aide d'une évaporation indirecte
WO2011104328A2 (fr) * 2010-02-26 2011-09-01 Siemens Aktiengesellschaft Dispositif et procédé de production vapeur d'eau surchauffée par l'énergie solaire selon le concept de circulation naturelle et utilisation de cette vapeur d'eau surchauffée
DE102010027226A1 (de) * 2010-05-06 2011-11-10 Siemens Aktiengesellschaft Solarer Kraftwerksteil einer solarthermischen Kraftwerksanlage und solarthermische Kraftwerksanlage mit Sonnenkollektorflächen für Wärmeträgermedium und Arbeismedium
DE102010040210A1 (de) * 2010-09-03 2012-03-08 Siemens Aktiengesellschaft Verfahren zum Betreiben eines solarbeheizten Durchlaufdampferzeugers sowie solarthermischer Durchlaufdampferzeuger
DE102010040623A1 (de) * 2010-09-13 2012-03-15 Siemens Aktiengesellschaft Verfahren zur Regelung einer kurzfristigen Leistungserhöhung einer Dampfturbine

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3269921A (en) * 1961-07-03 1966-08-30 Phillips Petroleum Co Computing and controlling the enthalpy of a process stream
US4574870A (en) * 1980-09-12 1986-03-11 Jacob Weitman Method and apparatus for controlling a counter-flow heat exchanger
US5363905A (en) * 1992-03-06 1994-11-15 Bayer Aktiengesellschaft Method of controlling heat exchangers using enthalpy flow as the correcting variable
US7007473B2 (en) * 2001-09-28 2006-03-07 Honda Giken Kogyo Kabushiki Kaisha Temperature control device of evaporator
US20060112682A1 (en) * 2002-08-09 2006-06-01 Honda Giken Kogyo Kabushiki Kaisha Working medium supply control system in heat exchanger
US20060032606A1 (en) * 2002-10-15 2006-02-16 Claus Thybo Method and a device for detecting an abnormality of a heat exchanger and the use of such a device
US20070157614A1 (en) * 2003-01-21 2007-07-12 Goldman Arnold J Hybrid Generation with Alternative Fuel Sources
US20100212318A1 (en) * 2007-09-11 2010-08-26 Siemens Concentrated Solar Power Ltd. Solar thermal power plants
US20100078011A1 (en) * 2008-09-25 2010-04-01 Peter Feher Ultra-compact, linear, solar-thermal steam generator
US20130213041A1 (en) * 2012-02-16 2013-08-22 Ormat Technologies Inc. Apparatus and method for increasing power plant efficiency at partial loads

Also Published As

Publication number Publication date
WO2013156375A1 (fr) 2013-10-24
EP2825736B1 (fr) 2016-08-24
ES2604818T3 (es) 2017-03-09
AU2013248442B2 (en) 2016-06-30
PT2825736T (pt) 2016-12-14
AU2013248442A1 (en) 2014-10-23
DE102012206466A1 (de) 2013-10-24
EP2825736A1 (fr) 2015-01-21

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