EP2567151B1 - Verfahren zum betreiben eines dampferzeugers - Google Patents

Verfahren zum betreiben eines dampferzeugers Download PDF

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Publication number
EP2567151B1
EP2567151B1 EP11714517.7A EP11714517A EP2567151B1 EP 2567151 B1 EP2567151 B1 EP 2567151B1 EP 11714517 A EP11714517 A EP 11714517A EP 2567151 B1 EP2567151 B1 EP 2567151B1
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EP
European Patent Office
Prior art keywords
flow
evaporator heating
flow medium
heating surface
steam
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.)
Active
Application number
EP11714517.7A
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German (de)
English (en)
French (fr)
Other versions
EP2567151A2 (de
Inventor
Jan BRÜCKNER
Joachim Brodesser
Martin Effert
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
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Siemens AG
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Priority to PL11714517T priority Critical patent/PL2567151T3/pl
Publication of EP2567151A2 publication Critical patent/EP2567151A2/de
Application granted granted Critical
Publication of EP2567151B1 publication Critical patent/EP2567151B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/06—Control systems for steam boilers for steam boilers of forced-flow type
    • F22B35/10—Control systems for steam boilers for steam boilers of forced-flow type of once-through type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D5/00—Controlling water feed or water level; Automatic water feeding or water-level regulators
    • F22D5/26—Automatic feed-control systems
    • F22D5/36—Automatic feed-control systems for feeding a number of steam boilers designed for different ranges of temperature and pressure

Definitions

  • the invention relates to a method for operating a steam generator having a combustion chamber with a plurality of evaporator heating surfaces connected in parallel on the flow medium side. It further relates to such a steam generator.
  • a steam generator is a closed, heated vessel or piping system designed to produce high pressure, high temperature steam for heating and service purposes (eg, for operation of a steam turbine).
  • water tube boilers are used, in which the flow medium - usually water - is located in steam generator tubes.
  • the combustion chamber in which the heat is generated by combustion of the respective raw material, can be arbitrarily designed by the arrangement of pipe walls.
  • Such a steam generator in the design of a water tube boiler thus comprises a combustion chamber, the surrounding wall is at least partially formed of tube walls, ie gas-tight welded steam generator tubes.
  • these steam generator tubes form, as evaporator heating surfaces, first an evaporator, into which the unevaporated medium is introduced and evaporated.
  • the evaporator is usually arranged in the hottest region of the combustion chamber. He is downstream of the flow medium side, where appropriate, a device for separating water and steam and a superheater, in which the steam is further heated above its evaporation temperature to in a subsequent heat engine such.
  • the evaporator can be upstream of the flow medium side, a pre-heater (so-called economizer), the feed water under Exploitation of waste or residual heat preheats and so also increases the efficiency of the entire system.
  • the US 5 293 842 A describes a method for operating a steam generating plant in which steam is generated from water by indirect heat exchange with hot flue gas, wherein condensed water is first preheated and then the preheated water is evaporated under high pressure.
  • the EP 0 359 735 A1 describes a heat recovery steam generator with a feedwater tank, which performs the function of a steam drum.
  • steam generator tubes can be arranged within the combustion chamber, which are connected on the flow medium side parallel to the steam generator tubes forming the enclosure walls. These can be summarized or welded to an inner wall, for example. Depending on the desired arrangement of evaporator heating surfaces or inner walls within the combustion chamber, it may be necessary to interconnect interior walls on the flow medium side in succession and to connect their steam generator tubes via an intermediate collector.
  • the object of the invention is therefore to provide a method for operating a steam generator of the type mentioned above and a steam generator, which allow a particularly long service life and a particularly low repair susceptibility of the steam generator.
  • the invention is based on the consideration that a particularly long service life and a particularly low repair susceptibility of an evaporator in a steam generator would be achievable by avoiding overheating of the steam generator tubes by excessively high vapor contents or enthalpies.
  • these high levels of steam occur in particular by the fact that in intermediate collectors already teilverdampftes flow medium is distributed unevenly to the downstream steam generator tubes. This unequal distribution should therefore be prevented by avoiding a two-phase mixture of water and steam in the intermediate collector.
  • this solution has constructive disadvantages. Therefore, rather, the temperature of the flow medium should be reduced at the entrance to the steam generator.
  • a preheater To improve the efficiency or to optimize the Schundanssen the entrances of the perimeter walls and the inner walls of a steam generator is preceded by a preheater.
  • This uses waste heat to preheat the flow medium. Due to the lower exhaust gas temperature generated by the use of waste heat so a higher overall efficiency of the steam generator is achieved.
  • a particularly simple construction of a steam generator is therefore possible by the different temperature at the inner wall and the peripheral wall of the steam generator is achieved by structural measures on the preheater, d. H. by providing media with different degrees of preheating.
  • a first part of the flow medium is conducted past the preheater. This can be done by means of a bridging line.
  • a bypass of the preheater of the preheater is achieved in a structurally simple manner and achieved a lower heat input into the bridged part of the flow medium. This can then be supplied to the entry of the first evaporator heating surface at a lower temperature.
  • the first part of the flow medium with a second fluid flow side after the Preheater diverted part to be mixed.
  • a particularly adapted reduction of the temperature of the first evaporator heating surfaces supplied flow medium is achieved.
  • the mass flow of the second partial flow is limited upwards.
  • This limitation can take place via a manual control or control valve for setting a flow rate limitation of the second control flow.
  • a directional boundary should be provided by a check valve to prevent the main flow of the preheater exit stream, from which the second partial flow is diverted, not to cool unintentionally.
  • the mass flow rate of the first substream should advantageously be regulated on the basis of thermodynamic parameters at a measuring point downstream of the inlet of the first evaporator heating surface.
  • a control valve can be arranged in the bypass line of the preheater. If the system is operated at supercritical pressures, where at no temperature water and steam can occur simultaneously and thus no phase separation is possible, there is no danger of segregation described above and the part of the flow medium passed by the preheater can be reduced to zero. If the steam generator operated with subcritical pressures in the evaporator, such. B. partial load operation of a modern Gleit horrkessels, it must be adhered to avoid segregation of the two media a certain supercooling, which is determined by means of thermodynamic parameters at a measuring point behind the first evaporator heating.
  • the measuring point should advantageously in one of the first evaporator heating surface downstream intermediate collector can be arranged.
  • thermodynamic parameters are carried out in an advantageous embodiment such that pressure and temperature are used as thermodynamic parameters, wherein the saturated steam temperature is determined from the measured pressure and the actual value of the subcooling is determined on the basis of the measured temperature.
  • pressure and temperature are used as thermodynamic parameters, wherein the saturated steam temperature is determined from the measured pressure and the actual value of the subcooling is determined on the basis of the measured temperature.
  • a setpoint value for the subcooling is advantageously set and controlled the mass flow of the first partial flow based on the deviation of the actual and setpoint of subcooling.
  • the mass flow rate of the first partial flow is increased at a lower actual value than the nominal value of the subcooling.
  • the mass flow of the second partial flow is advantageously controlled by the mass flow of the first evaporator heating supplied flow medium.
  • Further regulation of the mass flow rate of the flow medium supplied to the first evaporator heating surface can take place taking into account a water-steam separation device arranged downstream of the evaporator heating surfaces.
  • the current of the first evaporator heating surface fed medium regulated by the exit enthalpy of the evaporator.
  • the outlet enthalpy is determined on the basis of the temperature of the flow medium at the last evaporator heating surface downstream of the first evaporator heating surface and the pressure in the water-steam separator.
  • a control of the outlet enthalpy to the mean fluid enthalpy in the separator is a control of the outlet enthalpy to the mean fluid enthalpy in the separator.
  • the set point of the evaporator outlet enthalpy should be stored dependent on the load in the main control loop. In any case, the outlet temperature of the fluid se should be limited so that the maximum permissible material temperature is not exceeded.
  • the advantages achieved by the invention are in particular that the problem of water-steam segregation in the intermediate collector is reliably avoided by the use of two media with different degrees of supercooling for feeding the various evaporator parts (enclosing walls and inner walls).
  • the evaporator does not have to be increased or only slightly enlarged in order to ensure a sufficiently high outlet enthalpy at the evaporator.
  • a design of the steam generator as a once-through boiler has several advantages: forced-circulation steam generators can be used for both subcritical and supercritical pressure without changing the process technology. Only the wall thickness of the pipes and collectors must be dimensioned according to the intended pressure. Thus, the continuous flow principle meets the globally recognizable trend towards increasing efficiencies by increasing the steam conditions.
  • the steam generator 1 in a schematic representation according to the FIG. 1 is designed as a forced flow steam generator. It comprises a plurality of tube walls formed from steam generator tubes and flowed through from bottom to top, namely an enclosing wall 2 and symmetrically arranged, inclined aligned interior walls 4, to which an additional interior wall 8 is connected downstream via an intermediate collector 6 on the flow medium side.
  • the continuous steam generator 1 is thus designed in the so-called "pant-leg" design.
  • the intermediate walls 6 upstream inner walls 4 flow medium at a lower temperature is supplied as the Um Publishedswand 2.
  • first modifications of the preheater 16 are provided, the different heat inputs in ensure the different medium flows.
  • a branch point 18 is upstream of the flow medium side. A portion of the flow medium is thus passed around the preheater 16 in a bypass line 20.
  • the preheater 16 is first followed by a further branching point 22, from which a line is led to the inlets 10 of the surrounding wall 2. A part of the preheated flow medium is thus supplied to the enclosure wall 2. Another part of the preheated flow medium is guided in a line 24, which meets in a mixing point 26 with the bypass line 20.
  • a medium of lower temperature is achieved by the mixing of the medium streams, which is then fed to the inlets 12 of the inner walls 4.
  • a check valve 30 is arranged, which is an unwanted cooling by reflux in the branching point 22 prevented. Furthermore, a manual flow control valve 32 is provided, which limits the diverted mass flow preheated medium upwards.
  • the pressure p and the temperature T in the intermediate collector 6 serve as input variables for the automatic regulation in the flow control valve 28. From the pressure determined, the saturated steam temperature is initially determined whose difference to the determined temperature T results in the actual undercooling. In order to prevent segregation of water and steam in the intermediate collector 6, a target subcooling in the intermediate collector 6 is specified. If the actual subcooling exceeds the desired subcooling, the automatic flow control valve 28 is closed further, so that the temperature at the inlets 12 increases. In the opposite case, the flow control valve 28 is opened further. If pressure and temperature are above the critical point of the flow medium, the flow control valve 28 is completely closed, since at supercritical pressures at no temperature water and steam can occur simultaneously and thus no segregation in the intermediate collector 6 can occur more.
  • FIG. 2 An alternative embodiment of the invention shows FIG. 2 ,
  • the steam generator 1 is here except for the flow control valve 32 for FIG. 1 identical.
  • the flow control valve 32 is here as the control valve 28 automated. This makes it possible to regulate the amount of the inner walls 4 supplied medium.
  • the total flow F to the inlets 12, which is determined at a measuring point 34, serves as the input variable for the control. In this case, the total flow F is guided by means of a setpoint determined by design calculations.
  • FIG. 3 A further embodiment of the invention is in FIG. 3 shown.
  • the steam generator 1 to FIG. 2 identical, it However, further components are shown, namely the outlet 36 of the inner wall 8 and the outlet 38 of the enclosure wall 2.
  • the media streams from the outlets 36, 38 are brought together and fed into a water-steam separator 40.
  • the main control loop is shown, which controls the total amount of supplied flow medium in the steam generator 1 by means of a flow control valve 42.
  • pressure p and temperature T at the outlet on the steam side of the water-steam separator 40 serve as input variables for the regulation of the total medium flow.
  • the amount of flow medium supplied to the inner walls 4 via the inlets 12 is regulated as a function of the exit enthalpy of the inner wall 8. This is determined on the basis of the temperature T at the outlet 36 of the inner wall 8 and the pressure p in the water-steam separator 40. In this case, the average fluid enthalpy in the water-steam separator 40 is provided as a setpoint for the outlet enthalpy of the inner wall 8. In addition, the outlet temperature at the outlet 40 is limited beyond the maximum permissible material temperature.
  • FIG. 4 finally shows a state diagram for water / steam, in which the states of the flow medium are located in different areas of the steam generator.
  • the diagram plots the specific enthalpy h in kJ / kg against the pressure p in bar.
  • first lines of the same temperature T ie isotherms 44 are shown, whose respective temperature values are indicated on the right-hand axis of the graph in degrees Celsius.
  • the bump-shaped structure 46 on the left graphite side provides information about the vapor content of the water / steam mixture. Outside the structure 46, the medium is single-phase, ie, there is only medium in an aggregate state.
  • the tip of the structure 46 at about 2100 kJ / kg and 221 bar here marks the critical point 48. If the pressure rises above 221 bar, water and steam do not occur at any temperature.
  • Within structure 46 is a water-steam mixture.
  • the proportion of water and steam is shown with curves 50 in 10-percent intervals, from 0% vapor content at characteristic 52% to 100% vapor content at characteristic 54.
  • the curves 50, 52, 54 converge at the critical point 48.
  • the isotherms 44 are perpendicular to the pressure axis, so are also isobars. An energy input into the medium at constant pressure thus causes no higher temperature, but rather a shift of the water-steam content to more steam out.
  • the steam process within the steam generator 1 runs on different load characteristic curves 56, 58, 60, which are not isobars, since the pressure losses of the heating surfaces are represented.
  • the load essentially determines the pressure within the overall system.
  • Load curve 56 represents the steam process at 100% load
  • load curve 58 at 70% load
  • load curve 60 at 40% load.
  • points A, B, C, D in each case represent the state of the flow medium at different points of the steam generator 1, and first without the separate regulation according to the invention of the temperature at the inlets 12 of the inner walls 4: point A the state at the entrance of the Preheater 16, point B the state at the inlet 12 of the inner walls 4, point C the state in the intermediate collector 6 and point D the state at the outlet of the evaporator.
  • the steam generator is fully operated at 100% load in the supercritical range.
  • no point A, B, C, D on the load curve 56 is a distinction of water and steam possible, so that no segregation can occur.
  • the subcritical range is already reached, but only a small part of the load characteristic 58 is within the structure 46.
  • the points A, B, C of the load characteristic 58 are still below the structure 46, here is single-phase water. Again, it can not come to segregation in the intermediate collector 6.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP11714517.7A 2010-05-07 2011-04-07 Verfahren zum betreiben eines dampferzeugers Active EP2567151B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL11714517T PL2567151T3 (pl) 2010-05-07 2011-04-07 Sposób eksploatacji wytwornicy pary

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010028720A DE102010028720A1 (de) 2010-05-07 2010-05-07 Verfahren zum Betreiben eines Dampferzeugers
PCT/EP2011/055401 WO2011138116A2 (de) 2010-05-07 2011-04-07 Verfahren zum betreiben eines dampferzeugers

Publications (2)

Publication Number Publication Date
EP2567151A2 EP2567151A2 (de) 2013-03-13
EP2567151B1 true EP2567151B1 (de) 2016-09-28

Family

ID=44021942

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11714517.7A Active EP2567151B1 (de) 2010-05-07 2011-04-07 Verfahren zum betreiben eines dampferzeugers

Country Status (9)

Country Link
US (1) US9683733B2 (ko)
EP (1) EP2567151B1 (ko)
KR (1) KR101852642B1 (ko)
CN (1) CN103026136B (ko)
CA (1) CA2798366A1 (ko)
DE (1) DE102010028720A1 (ko)
DK (1) DK2567151T3 (ko)
PL (1) PL2567151T3 (ko)
WO (1) WO2011138116A2 (ko)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011076968A1 (de) * 2011-06-06 2012-12-06 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Umlauf-Abhitzedampferzeugers
DE102014222682A1 (de) 2014-11-06 2016-05-12 Siemens Aktiengesellschaft Regelungsverfahren zum Betreiben eines Durchlaufdampferzeugers

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL110085C (ko) * 1955-09-16
GB1052417A (ko) * 1963-03-25
DE3863153D1 (de) * 1987-09-21 1991-07-11 Siemens Ag Verfahren zum betreiben eines durchlaufdampferzeugers.
JPH01157551A (ja) 1987-09-24 1989-06-20 Hitachi Ltd ウェーハ・スケール集積回路
AT394100B (de) * 1988-09-14 1992-01-27 Sgp Va Energie Umwelt Abhitze-dampferzeuger
DE59300573D1 (de) * 1992-03-16 1995-10-19 Siemens Ag Verfahren zum Betreiben einer Anlage zur Dampferzeugung und Dampferzeugeranlage.
BE1010594A3 (fr) * 1996-09-02 1998-11-03 Cockerill Mech Ind Sa Procede de conduite d'une chaudiere a circulation forcee et chaudiere pour sa mise en oeuvre.
DE19651678A1 (de) * 1996-12-12 1998-06-25 Siemens Ag Dampferzeuger
UA42888C2 (uk) * 1997-06-30 2001-11-15 Сіменс Акціенгезелльшафт Парогенератор, який працює на відхідному теплі
DE19926326A1 (de) * 1999-06-09 2000-12-14 Abb Alstom Power Ch Ag Verfahren und Anlage zum Erwärmen eines flüssigen Mediums
US6460490B1 (en) * 2001-12-20 2002-10-08 The United States Of America As Represented By The Secretary Of The Navy Flow control system for a forced recirculation boiler
JP2003214601A (ja) * 2002-01-21 2003-07-30 Mitsubishi Heavy Ind Ltd ボイラの給水装置及び給水方法並びにボイラシステム
DE10354136B4 (de) * 2002-11-22 2014-04-03 Alstom Technology Ltd. Zirkulierender Wirbelschichtreaktor
US7243618B2 (en) * 2005-10-13 2007-07-17 Gurevich Arkadiy M Steam generator with hybrid circulation
CN1888531B (zh) * 2006-04-25 2010-08-11 黄昕旸 大型煤粉锅炉飞灰再循环燃烧方法及装置
CN200940824Y (zh) * 2006-08-18 2007-08-29 东方锅炉（集团）股份有限公司 带背靠背水冷壁中隔墙的循环流化床锅炉炉膛
CN1948831B (zh) * 2006-11-09 2010-05-12 上海锅炉厂有限公司 一种流化床锅炉分层流化布风板的布置方法
EP2034137A1 (de) * 2007-01-30 2009-03-11 Siemens Aktiengesellschaft Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage sowie dafür ausgelegte Gas- und Dampfturbinenanlage
WO2007133071A2 (en) * 2007-04-18 2007-11-22 Nem B.V. Bottom-fed steam generator with separator and downcomer conduit

Also Published As

Publication number Publication date
KR101852642B1 (ko) 2018-04-26
EP2567151A2 (de) 2013-03-13
CA2798366A1 (en) 2011-11-10
WO2011138116A2 (de) 2011-11-10
KR20130098856A (ko) 2013-09-05
PL2567151T3 (pl) 2017-06-30
CN103026136B (zh) 2015-03-25
US9683733B2 (en) 2017-06-20
CN103026136A (zh) 2013-04-03
DE102010028720A1 (de) 2011-11-10
WO2011138116A3 (de) 2013-01-17
US20130047938A1 (en) 2013-02-28
DK2567151T3 (en) 2017-01-09

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