WO2012110330A2 - Procédé pour faire fonctionner un générateur de vapeur à récupération de chaleur héliothermique - Google Patents

Procédé pour faire fonctionner un générateur de vapeur à récupération de chaleur héliothermique Download PDF

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Publication number
WO2012110330A2
WO2012110330A2 PCT/EP2012/051850 EP2012051850W WO2012110330A2 WO 2012110330 A2 WO2012110330 A2 WO 2012110330A2 EP 2012051850 W EP2012051850 W EP 2012051850W WO 2012110330 A2 WO2012110330 A2 WO 2012110330A2
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WO
WIPO (PCT)
Prior art keywords
evaporator
steam generator
bypass line
solar
flow
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.)
Ceased
Application number
PCT/EP2012/051850
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German (de)
English (en)
Other versions
WO2012110330A3 (fr
Inventor
Jan BRÜCKNER
Joachim 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
Publication of WO2012110330A2 publication Critical patent/WO2012110330A2/fr
Anticipated expiration legal-status Critical
Publication of WO2012110330A3 publication Critical patent/WO2012110330A3/fr
Ceased legal-status Critical Current

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Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G6/00—Devices for producing mechanical power from solar energy
    • F03G6/06—Devices for producing mechanical power from solar energy with solar energy concentrating means
    • F03G6/065—Devices for producing mechanical power from solar energy with solar energy concentrating means having a Rankine cycle
    • F03G6/067—Binary cycle plants where the fluid from the solar collector heats the working fluid via a heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G6/00—Devices for producing mechanical power from solar energy
    • F03G6/071—Devices for producing mechanical power from solar energy with energy storage devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/007—Control systems for waste heat boilers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S20/00—Solar heat collectors specially adapted for particular uses or environments
    • F24S20/20—Solar heat collectors for receiving concentrated solar energy, e.g. receivers for solar power plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S40/00—Safety or protection arrangements of solar heat collectors; Preventing malfunction of solar heat collectors
    • F24S40/50—Preventing overheating or overpressure
    • F24S40/55—Arrangements for cooling, e.g. by using external heat dissipating means or internal cooling circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S80/00—Details, accessories or component parts of solar heat collectors not provided for in groups F24S10/00-F24S70/00
    • F24S80/60—Thermal insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S23/00—Arrangements for concentrating solar-rays for solar heat collectors
    • F24S23/70—Arrangements for concentrating solar-rays for solar heat collectors with reflectors
    • 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

  • the invention relates to a method for operating a solar thermal heat recovery steam generator with an evaporator, an economizer with a number of EconomizerSystemflachen and with a medium to a number of EconomizerSystemflachen flow medium side parallel bypass line.
  • Solar thermal power plants are an alternative to conventional electricity generation ago ⁇ .
  • running solar thermal power plants with parabolic trough collectors or Fres nel collectors Another option is the direct or indirect evaporation in so-called solar tower power plants.
  • this tower power plant is heated in a so-called receiver Conversely ⁇ ambient air.
  • the hot air generated in this way releases its energy in a downstream heat recovery steam generator (AHDE) to the feed water coming from the condenser.
  • AHDE heat recovery steam generator
  • the generated steam is fed to a steam turbine. This is known as indi ⁇ rect solar evaporation.
  • a metallic or ceramic sponge also referred to as a volumetric absorber
  • the radiation is absorbed both on the surface and in the interior of a porous body and converted to heat.
  • Ambient air which is sucked inwards by the sponge, heats up to over 800 ° C and then serves to generate steam for a conventional steam power plant.
  • the advantage over tube bundle absorbers is that the heat does not have to be transmitted through a wall. As a result, higher energy flux densities, operating temperatures and efficiencies are possible. By concentrating the Blasted light in the absorber is expected to have very high heat flux densities.
  • Heat recovery steam generator can be categorized based on a variety of criteria: Based on the direction of flow of the gas stream can be divided heat recovery steam generator, for example, in Vertika ⁇ le and horizontal types. Furthermore, there are steam generator with a plurality of pressure stages with different thermal states of the water-steam mixture contained in each case.
  • this usually comprises a feedwater pre-heater or economizer.
  • This consists of several economizer heating surfaces, which form the last heating surfaces after a number of evaporator, superheater and reheater heating surfaces in the hot gas path.
  • the Econo ⁇ mizer is upstream of the evaporator heating and superheater and uses the residual heat in the hot gases to preheat the feed water.
  • the hot gas flows through the economizer in re ⁇ tively low temperatures.
  • a suffi ⁇ sponding sub-cooling of the flow medium is at the evaporator inlet in principle be secured (ie, the temperature of the flow medium should have a reaching distance from the saturation temperature from ⁇ have).
  • ⁇ measures are required in the lower load range.
  • a partial flow of the flow medium is usually led around one or more economizer heating surfaces in a bypass line via a corresponding arrangement and then mixed again with the main flow, for example at the inlet of the last economizer.
  • the partial flow is through the economizer bypass line usually being adjusted so that in steady state operation a is maintained under ⁇ cooling at the evaporator inlet, for example, at least 3 Kelvin (K) in the corresponding load range.
  • K Kelvin
  • a temperature and pressure measurement at the evaporator inlet is provided, with the aid of which a difference formation the actual supercooling can be determined at any time.
  • a valve in the economizer bypass line is actuated when the minimum subcooling is undershot. This valve receives an opening pulse of, for example
  • the valve receives a closing pulse of for example 1 s.
  • the opening in the rule for a longer period of time (for example, 600 s) remains before after renewed comparison between setpoint and actual value, the same operation is repeated, the sub-cooling at the evaporator inlet should still RESIZE ⁇ SSER than 6 K and the valve is not yet completely closed.
  • comparatively large time intervals are selected here in order to avoid vapor formation in the economizer.
  • the invention is therefore based on the object of specifying a method of operating a solar thermal heat recovery steam generator of the above type as well as a solar thermal heat recovery steam generator, which allow a higher operating Si ⁇ certainty and reliability in the control of the solar-heat steam generator ⁇ mix.
  • this object is achieved according to the invention by using a characteristic variable which is characteristic of the solar thermal waste heat steam generator for controlling or regulating the flow rate of the bypass line.
  • the invention is based on the consideration that a higher operational safety and reliability in the control of the solar thermal heat recovery steam generator would be possible if a formation of a water-steam mixture at Ein ⁇ occurs the evaporator could be reliably avoided ver ⁇ in all load conditions.
  • the risk of steam generation is relatively large during rapid load changes, in particular, since a relatively rapid change in the Unterküh ⁇ lung is present at the inlet of the evaporator. In these cases, the hitherto provided regulation of subcooling by influencing the Economizerbypass diesselmenge reacts too slowly. So it should be provided a faster responding control or regulation.
  • the flow rate of the bypass line is reduced with an increase in the characteristic.
  • the flow rate of the bypass line can be adjusted accordingly even if the heat energy supplied to the heat recovery steam generator increases, and thus even before the measurement of an actual change in temperature or subcooling at the inlet of the evaporator.
  • Increases namely in today's operation of the solar thermal heat recovery steam generator, the solar thermal waste heat steam generator supplied heat this is associated with an increase in other thermodynamic (state) sizes of the flow medium (such as feedwater mass flow, pressure, medium temperatures), which due to physical laws directly with an increase associated with the entry subcooling. Therefore, in this case, the flow rate of the bypass line is reduced, so that the tempera ⁇ tur increases at the outlet of the economizer and thus the Unterküh ⁇ ment is reduced at the evaporator inlet.
  • bypass line runs, for example, parallel to a number of economizer and after the mixing point of bypass line and flow through them Economizer heating surfaces are followed by one or more additional economizer heating surfaces.
  • the previously used temperature signal for controlling the flow rate of the bypass line is measured at the outlet of the last EconomizerAlbflache and thus at the inlet of the evaporator.
  • this signal which summarizes the temperature difference caused by changes in the flow ⁇ amount of the bypass line ER, delayed by one hand, the time required for the flow ⁇ medium for flowing through the last, not provided with a bypass line EconomizerSystemflachen, on the other hand by Storage processes of thermal energy in the pipe walls of these heating surfaces, the heat capacity is also taken into account. Therefore, a further Ver ⁇ improving the speed of the control or regulation might take place if the temperature is advantageously used at the mixing point at the outlet of the bypass line for controlling or regulating the flow rate of the bypass line. Thus, even more reliable and faster control or prevention of vapor formation at the inlet of the evaporator is possible.
  • the evaporator inlet subcooling is still significantly influenced by fluctuations in the saturation temperature in the evaporator. Since the saturation temperature in the evaporator is essentially influenced by the pressure in the pipe system, z. B. at rapid system pressure changes (for example, when dissolving a throttle reserve), a sharp decline in the occurrence of sub-cooling occur. This change in the inlet subcooling is independent of the thermal energy supplied to the solar thermal heat recovery steam generator. To consider such a scenario, beneficial ⁇ way legally saturation temperature should be used in the evaporator to control or regulate the flow rate of the bypass line.
  • control quality for the economizer bypass can be further improved in the event of a rapid pressure change in the evaporator.
  • An even better control quality of the flow rate of the bypass line can continue to be achieved if an even better, for the solar thermal heat recovery steam generator supplied heat energy characteristic parameter is used in the STEU ⁇ tion or regulation.
  • the power signal of the upstream air receiver can not ensure sufficient quality, as this signal may not be sufficiently correlated with the introduced into the solar thermal heat recovery steam generator heat, on the other hand, this signal is not available in applications without pre ⁇ switched air receiver.
  • the balanced hot gas heat of the evaporator should be used as characteristic for the thermal energy supplied to the solar heat recovery steam generator heat ⁇ cal characteristic.
  • the balanced hot gas heat is determined essentially from the mass flow of the hot gas on the one hand and the enthalpy difference at the hot gas inlet and at the outlet of the evaporator.
  • the inlet temperature is measured and the outlet temperature approximated by the saturation temperature of the evaporator and both temperature values calculated in an associated H exertgasenthalpie to ⁇ .
  • This practically allows a direct measurement of the heat flow introduced into the evaporator.
  • this signal is in control equipment for solar thermal heat from ⁇ steam generators often before, because it can be used to feed water control. By using this signal, the quality of the control or regulation can be further improved and sufficient subcooling at the inlet of the evaporator can be ensured even better.
  • the object is achieved by a solar thermal waste heat steam generator with an evaporator, with an economizer with a number of Economizersammlung lake, with a flow medium to a number of Economizersammlung lake parallel ge ⁇ switched bypass line with a flow control or flow control valve, with a temperature and pressure measurement Device at the evaporator inlet and optionally a temperature measuring device at the mixing point at the outlet of the bypass line and a data controller connected to the aforementioned measuring devices and the flow control or flow control valve control device, which is designed to carry out said method.
  • Such a heat recovery steam generator is advantageously used in a steam turbine plant.
  • the requiredußun ⁇ supercooling the flow medium at Verdampfereintrit can be sure ⁇ placed in a tower power plant with integrated heat recovery steam generator even during transient events.
  • a corresponding Eco-bypass control concept can be kept relatively constant during transient processes in addition to ensuring a minimum subcooling, so that by this measure first steam formation at the evaporator inlet still untrue ⁇ apparent and secondly the control quality of the Suitewasserre- concept by the almost constant evaporator ⁇ supercooling is positively influenced.
  • FIG. 1 shows a solar tower power plant with an open air receiver a designed as a volumetric absorber air receiver
  • 5 is a schematic representation of the control method, taking into account the balanced hot gas heat of the evaporator and the change in the saturation ⁇ temperature in the evaporator.
  • FIG. 1 shows a solar tower installation 129.
  • the solar tower installation 129 has a tower 132, on whose vertical upper end an air receiver 133 is arranged.
  • the air receiver 133 has a volumetric absorber 135.
  • a heliostat field 130 is placed on the ground near the tower around tower 132.
  • the heliostat field 130 has a plurality of heliostats 131 which are individually positionable or alignable.
  • the entire heliostat field 130 is aligned so that the direct solar radiation I s is focused, so that concentrated solar radiation I c is formed by optical reflection at the heliostat field 130, wherein the concentrated solar radiation I c on the air receiver 133, respectively the volumetric absorber 135th , is bundled.
  • ambient air L which flows into the air receiver 133, by means of the volumetric absorber 135 by the concentrated solar radiation I c is very strongly heated.
  • the highly heated or superheated air L can be used as heating air L 'or
  • the volumetric absorber 135 has a Ge ⁇ housing 134, which is equipped kitchens ⁇ tet with thermal insulation 140th
  • the thermal insulation 140 can be made, for example, of a porous ceramic material or a metal foam. hen, so that a good heating of the volumetric absorber 135 is given in sunlight.
  • the volumetric absorber 135 has an inlet 138 and an outlet 139. The inlet 138 and the outlet 139 are fluidically connected with each other.
  • the front side of the volumetric absorber 135 has a curved Quarzglasfens ⁇ ter 136, which is fitted into the housing 134.
  • Seit ⁇ Lich the quartz glass window 136 is a water-cooled
  • Protective cover 137 is provided which protects the end face of the volumetric absorber 135 against overheating and the
  • FIG. 3 shows a solar power ⁇ plant system 149, which consists of a solar part S and a power ⁇ plant part P, which integrates into an overall system is.
  • the solar part S has a solar tower system 129 - in ana ⁇ loger manner as described in FIG 1 - on. This comprises a heliostat field 130 and the solar tower 132 with the Lucasre ⁇ DCver 133, which is arranged at the top of the tower and containing the volumetric absorber 135.
  • the power plant section P includes a steam turbine 145 and an integrally ⁇ coupled to the steam turbine generator 146 for generating electrical energy.
  • a condenser 147 is connected to the steam turbine 145.
  • a feed water pump 148 delivers feedwater in the water-steam cycle 150 of the steam turbine plant.
  • the heating air flow L ' is connected via a feed 142 to the solar thermal waste heat steam generator 1.
  • connection line in the form of a return flow 141 between the solar thermal heat recovery steam generator 1 and the air receiver 133 of the solar tower 132 is provided.
  • blower 144 are turned on in the return.
  • the solar thermal heat recovery steam generator 1 has an evaporator 4 and an over ⁇ hitzersammlung Design 8th So that during operation the desired live steam temperature and the desired live steam pressure can be generated.
  • a hot-gas reservoir or buffer tank 143 con- nects the lead 141 to the return line 142 so that demand ⁇ as hot air L 'into the hot gas storage 143 can be branched off, are required, popped from the hot gas memory 143 from the buffer tank 143 and fed into the return line 141 can.
  • the solar part S and the power plant part P are integrated by this interconnection into an overall system, the solar thermal waste heat steam generator 1 with its heating surfaces being connected into the hot air flow L 'of the air receiver 133.
  • the heating surfaces of the solar thermal heat recovery steam generator 1 with hot gas L ' are applied, so that live steam F is generated.
  • the hot gas L ' has a temperature of 680 ° C and a pressure of 1 bar.
  • live steam F with a temperature of 480 ° C and a pressure of 26 bar is generated.
  • the steam turbine is F aufschlagt 145 loading, so that the steam in the steam turbines ⁇ F 145 ne work bringing relaxed and drives the turbine.
  • the steam turbine 145 in turn drives the electric Genera ⁇ tor 146, so that electrical energy is generated.
  • the vapor condenses in the condenser 147 and is in turn fed via the feed water pump 148 into the preheating section of the solar thermal waste heat steam generator 1.
  • FIG. 4 shows selected components of a schematically presented Darge ⁇ solar thermal heat recovery steam generator 1.
  • flow medium flows, driven by a non-illustrated pump initially at the inlet 2 in the cycle, wherein firstly a bypass line 3 branches off.
  • a flow control valve 6 is provided which can be regulated by a motor 7. It may also be a simple control valve is provided, however, a better adjustment of the subcooling at the evaporator inlet is possible by a fast-acting control valve.
  • a part of the flow medium thus flows depending on the position of the flow control valve 6 in the bypass line 3, another part flows into a first economizer 10.
  • a first economizer 10 There may be provided parallel to the bypass line 3 and other economizer heating.
  • the flow medium from the bypass line 3 and the economizer heating surface 10 is mixed at a mixing point 12.
  • the mixing point 12 is followed by a further economizer heating surface 14.
  • the evaporator 16 which may also consist of a number of heating surfaces, further components such as a water-vapor separator and further superheater heating surfaces are connected downstream.
  • the economizer heating surfaces 10, 14 and the evaporator 16 are possible on the hot gas side.
  • the economizer heating surfaces 10, 14 are downstream of the evaporator 16 on the hot gas side, since the economizers are designed to carry the comparatively coldest flow medium and to utilize the residual heat in the hot gas duct.
  • a suffi ⁇ sponding hypothermia that is a sufficient difference of actual temperature to saturation temperature in the evaporator are present, so that only liquid medium flow is present.
  • a pressure measuring device 20 and a temperature measuring device 22 are provided at this point.
  • Another, faster-reacting temperature signal which is not delayed by the through ⁇ term of flow medium through the economizer 14 is provided by a further temperature measuring device 24 at the mixing point 12th
  • a supercooling set point 26 is initially set at the evaporator inlet 18. This may for example be 3 K, ie, the temperature at the evaporator inlet 18 should be 3 K below the saturation temperature in the evaporator 16. From the pressure determined at the pressure measuring device 20, the saturation temperature 28 in the evaporator 16 is initially determined, since this is a direct function of the pressure prevailing in the evaporator 16. This saturation temperature 28 is then added in an adder 30 to the negative supercooling setpoint 26. In a further adder 32, the temperature measured at the temperature measuring device 22 at the evaporator inlet 18 is withdrawn thereon. This results in a suitable control value for a control of the flow control valve 6.
  • the power 34 of the heat recovery steam generator solar thermal upstream air receiver is used as an input signal.
  • the power 34 serves as an input signal for a differentiating element of the first order (DTI element) 36, which generates a correspondingly scaled output signal when the power 34 changes.
  • This output signal is added in a further adder 38 to the ge ⁇ measured deviation of the sub-cooling at the evaporator inlet to the setpoint.
  • Entry into the further economizer heating surface 14 detects what, in the case of only one temperature measuring device 22 at the evaporator inlet 18 or outlet of the economizer heating surface 14 as a result of the throughput time through the economizer heating surface 14, could take place only with a corresponding time delay.
  • These measurement ⁇ information is added to the negative control value in an adder 44th
  • the time delay behavior of the economizer heating surface 14 must be taken into account so that control operations already carried out (triggered by the change in the flow control temperature at the inlet of the economizer heating surface 14) are not subject to any further control intervention (after the temperature change arrived at the outlet of the economizer 14).
  • the temperature signal of the temperature measuring device 24 is processed after the addition in a PTn element 40, which simulates the time delay behavior of the economizer 14.
  • the resulting output signal is added in a further adder 42 to the previous control value and thus compensates for a double consideration again.
  • control value thus determined is passed to a ⁇ controller 46 further, which drives the motor 7 of the flow control valve 6 of the bypass line.
  • FIG 5 shows a schematic representation of a variant of the control circuit of Figure 1.
  • the balance ⁇ ed hot gas heat 48 is used as input signal for the DTL-member 36 instead of the output 34 of the air receiver 133rd
  • the carrying hot gas heat 48 is determined from the difference of the H adoptedgasenthalpie at the evaporator inlet 18 and the H adoptedgasenthalpie at the evaporator outlet (see Be ⁇ scription earlier) and through the hot gas mass flow.
  • the reported hot gas heat 48 a more direct In ⁇ indicator of the the solar thermal heat recovery steam generator 1 supplied heat quantity as the hot gas output 34 of the connected upstream air receiver 133.
  • Re ⁇ gelung the temperature at the evaporator inlet 18 is possible.
  • FIG. 5 shows a further DTL element 50, which generates an output signal when the saturation temperature in the evaporator 16 changes. This output signal is fed to the control loop in the adder ⁇ member 38. Characterized a sufficient sub-cooling can also be used in egg ⁇ ner stationary heat supply in the solar thermal heat recovery steam generator 1 at a rapid change in the pressure and the saturation temperature in the evaporator 28 16 at the evaporator inlet 18 technicallyge ⁇ represents.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Sustainable Development (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)

Abstract

L'invention concerne un procédé permettant de faire fonctionner un générateur de vapeur à récupération de chaleur (1) héliothermique, qui comprend un évaporateur (16) et un économiseur muni d'une pluralité de surfaces chauffantes (10, 14) d'économiseur et d'une conduite de dérivation (3) montée en parallèle avec une pluralité de surfaces chauffantes (10) d'économiseur côté fluide d'écoulement. Le but de l'invention est de permettre une fiabilité et une sécurité de fonctionnement accrues lors de la commande du générateur de vapeur à récupération de chaleur héliothermique. A cet effet, une grandeur caractéristique de l'énergie calorifique apportée au générateur de vapeur à récupération de chaleur (1) héliothermique est utilisée pour commander ou réguler le débit dans la conduite de dérivation (3).
PCT/EP2012/051850 2011-02-17 2012-02-03 Procédé pour faire fonctionner un générateur de vapeur à récupération de chaleur héliothermique Ceased WO2012110330A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011004280A DE102011004280A1 (de) 2011-02-17 2011-02-17 Verfahren zum Betreiben eines solarthermischen Abhitzedampferzeugers
DE102011004280.6 2011-02-17

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WO2012110330A3 WO2012110330A3 (fr) 2013-12-05

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CH715206A2 (de) * 2018-07-27 2020-01-31 Eni Spa Verfahren zur Isolation einer Prozesseinheit und Prozesseinheit mit einem isolierenden Bereich.
CN114543058B (zh) * 2022-02-25 2023-07-21 中国科学院电工研究所 一种基于太阳能的高温蒸汽发生器
EP4345399A1 (fr) * 2022-09-28 2024-04-03 ETH Zurich Récepteur solaire pour applications à haute température

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US20150240792A1 (en) * 2014-02-24 2015-08-27 Alstom Technology Ltd Solar thermal power system
US9995285B2 (en) * 2014-02-24 2018-06-12 Alstom Technology Ltd. Method for operating a solar thermal power system with an economizer recirculation line

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DE102011004280A1 (de) 2012-08-23

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