EP0808440B1 - Verfahren und vorrichtung zum anfahren eines durchlaufdampferzeugers - Google Patents

Verfahren und vorrichtung zum anfahren eines durchlaufdampferzeugers Download PDF

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Publication number
EP0808440B1
EP0808440B1 EP96900860A EP96900860A EP0808440B1 EP 0808440 B1 EP0808440 B1 EP 0808440B1 EP 96900860 A EP96900860 A EP 96900860A EP 96900860 A EP96900860 A EP 96900860A EP 0808440 B1 EP0808440 B1 EP 0808440B1
Authority
EP
European Patent Office
Prior art keywords
throughput
evaporator
load
fuel
percentage
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.)
Expired - Lifetime
Application number
EP96900860A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0808440A1 (de
Inventor
Joachim Franke
Eberhard Wittchow
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
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
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Application filed by Siemens AG filed Critical Siemens AG
Publication of EP0808440A1 publication Critical patent/EP0808440A1/de
Application granted granted Critical
Publication of EP0808440B1 publication Critical patent/EP0808440B1/de
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Classifications

    • 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
    • F22B35/14—Control systems for steam boilers for steam boilers of forced-flow type during the starting-up periods, i.e. during the periods between the lighting of the furnaces and the attainment of the normal operating temperature of the steam boilers

Definitions

  • the invention relates to a method for starting a Continuous steam generator with a number of burners for a fossil fuel combustion chamber, whose gastight surrounding wall is at least approximately vertical extending evaporator tubes is formed, which are penetrated from bottom to top on the medium side. she further relates to a device for performing the Procedure.
  • the flow of the evaporator is the Continuous steam generator - and often also one in the continuous steam generator arranged smoke gas heated preheater or Economizer - a circulating current is superimposed during startup, order by correspondingly high speeds in the Pipes to cool them safely.
  • The is from pass current and superimposed circulating current existing minimum current with vertically arranged pipes in the surrounding walls the combustion chamber between 25% and 50% of the full load flow. This means that the steam generator load when starting only be increased to at least 25% to 50% must, before the efficient continuous operation with its high steam outlet temperatures.
  • start-up process comprehensive efficiency Power plant especially by realizing high and highest steam conditions, there is therefore a reduction in start-up losses increased importance too.
  • start-up process Circulation circuit to be installed which is usually at least one circulation pump with appropriate accessories or comprises a drain heat exchanger with a high technical Effort and therefore high investment costs required.
  • the invention is therefore based on the object of a method and a device for operating a once-through steam generator to be indicated with low start-up losses. This is said to a device suitable for carrying out the method can be achieved with little technical effort.
  • this object is achieved according to the invention solved in that the evaporator throughput depending of the or each burner supplied per unit of time Fuel amount is set, the evaporator throughput proportional to the heat output in the combustion chamber is set.
  • the evaporator throughput i.e. the amount of the evaporator supplied per unit of time and this medium flowing through, with the procedure according to the invention within a narrow tolerance band.
  • the invention is based on the knowledge that a Continuous steam generator also with a rapidly increasing fire output can be approached because its proportionate thin-walled components have high rates of temperature change allow. Due to the low storage mass of the evaporator uses a rapid steam formation, which leads to Overheating heating surfaces provided generated steam be chilled well.
  • the conventional start-up procedure for continuous steam generators was based on the assumption that the evaporator tubes of highly heated combustion chamber can only be cooled well if the medium flow in the pipes is turbulent, which is a corresponding high mass flow density in the pipes even during of the start-up process.
  • the invention is based on the consideration that also very low mass flow densities and at the same time high heat flow densities a very good heat transfer from a pipe wall to the flow medium when there is a so-called Ring flow forms.
  • Recent studies on the inside Heat transfer in vertical pipes has surprisingly training even at very low mass flow densities of such a ring flow confirmed in the always a large proportion of water in a water-water / Steam mixture formed flow medium to the pipe wall is transported. This also leads to a below about 25% of the full load current, i.e. the evaporator throughput at 100% load, minimum current lies to the good mentioned Heat transfer.
  • the described thermal engineering phenomenon is used in the process to operate a continuous steam generator during the start-up was implemented particularly cheaply, if based on a minimum evaporator throughput of less than 15%, preferably less than 10%, e.g. 5% of Full load throughput the evaporator throughput only in one narrow range from the percentage, related to full load Furnace heat output deviates.
  • the evaporator throughput is expediently limited to 5% to 10% of full load throughput. This ensures a steady upward flow right from the start guaranteed in all evaporator tubes.
  • the evaporator throughput set that related to full load throughput percentage evaporator throughput within a certain Bandwidth equal to the percentage based on full load Firing heat output is.
  • the range extends preferably between 3 to 8% above and between 2 to 3% below the percentage increase over time Firing heat output. This condition is asymmetrical Bandwidth applies in particular to a heating output, which ensures stable combustion is.
  • the device for starting a continuous steam generator with a number of burners for a fossil Combustion chamber with fuel its gas-tight Surrounding wall made of at least approximately vertical arranged evaporator tubes is formed, the medium side can flow from bottom to top, is called Task solved by a controller module for setting the Amount of medium supplied to the evaporator per unit of time depending on the or each burner per unit of time amount of fuel supplied.
  • the manipulated variable determined by the controller block determines the evaporator throughput rate proportional to the determined from the amount of fuel Fire heat output.
  • the controller block is included connected to a feed water line leading into the evaporator switched actuator and with one in one connected to the or each burner leading fuel line second flow sensor.
  • a device is indeed from the document EP-A-0 308 596 for regulating the amount of feed water in a natural circulation steam generator system known in which a controller block a characterizing the amount of fuel filtered into the burner Measured value can be fed.
  • a controller block a characterizing the amount of fuel filtered into the burner Measured value can be fed.
  • a setpoint determined by the controller block for the amount of feed water depend on the heat output could.
  • the controlled variable is expediently the evaporator throughput, i.e. the amount of the evaporator on the medium side per unit of time fed feed water.
  • The is advantageous Controller module with one connected to the feed water line Flow sensor connected.
  • the vertical throttle cable of the steam generator 1 according to FIG. 1 with rectangular cross section is formed by a surrounding wall 2, at the bottom of the throttle cable into a funnel-shaped Floor 3 merges.
  • Evaporator tubes 4 of the surrounding wall 2 are gas-tightly connected on their long sides, e.g. welded.
  • the bottom 3 includes a not shown Discharge opening 3a for ashes.
  • the lower region of the surrounding wall 2 forms the one with Number of burners 5 provided combustion chamber 6 of the continuous steam generator 1.
  • the medium side i.e. of feed water or a water / water-steam mixture, parallel from bottom to top - or in the case of evaporator tube groups one behind the other - evaporator tubes flowed through 4 of the surrounding wall 2 are with their entry ends to an inlet header 8 and with its outlet ends connected to an outlet header 10.
  • the entry collector 8 and the outlet collector 10 are located outside the throttle cable and are e.g. each by an annular Tube formed.
  • the inlet header 8 is via a line 12 and one Collector 14 with the output of a high pressure preheater or Economizers 15 connected.
  • the heating surface of the economizer 15 is in a room above the combustion chamber 6 Surrounding wall 2 arranged.
  • the economizer 15 is on the input side via a collector 16 with a feed water tank 18 connected, in a manner not shown connected to a steam turbine via a condenser and is thus connected in their water-steam cycle.
  • the outlet header 10 is via a water-steam separation vessel 20 and a line 22 connected to a high pressure superheater 24, the inside the perimeter wall 2 between the economizer 15 and the combustion chamber 5 is arranged.
  • the high pressure superheater 24 is on the output side during operation via a collector 26 with a high-pressure part of the steam turbine connected.
  • Between the high pressure superheater 24 and the Economizer 15 is an intermediate superheater within the surrounding wall 2 28 provided, the collector 30, 32 between the high pressure part and a medium pressure part of the steam turbine is switched.
  • feed water line 17 In the feed water line 17 are in the direction of flow Feed water S from the feed water tank 18 in a row a motor-operated feed water pump 34 and a means Steam D heated heat exchanger 36 for preheating the feed water as well as a valve 38 and a flow sensor 40 switched.
  • the flow sensor 40 is used to determine the per unit time amount fed through the feed water line 17 Feed water S.
  • the per unit of time conducted via line 17 Amount of feed water S corresponds to that from the Evaporator tubes 4 feed water quantity supplied to existing evaporators and thus the evaporator throughput.
  • Another flow sensor 42 is in a fuel line 44 switched, the partial lines 46 in the burner 5 opens.
  • a valve 48 is provided in the fuel line 44 Setting of the or each burner 5 supplied per unit of time Amount of fuel B switched.
  • the flow sensors 40 and 42 are via signal lines 50 and 52, into which transducers 51 and 53 are connected, with one Controller block 54 connected.
  • the controller block 54 is over a line 56 is connected to the valve 38.
  • the controller block 54 can alternatively also be shown with a dashed line Line 56 'with the motor-operated feed water pump 34 be connected.
  • the controller block 54 and the flow sensor 40, 42 and that to adjust the amount of Feed water S serving valve 38 are part of a control device 58 for starting the once-through steam generator 1.
  • the feed water pump 34 can also be used even by changing their speed to adjust the Amount of the feed water fed through the feed water line 17 S can be used.
  • the control device 58 is used to adjust the evaporator throughput depending on the or each burner 5 amount of fuel supplied per unit of time during a start-up process.
  • the controller block 54 via the signal line 50 the measured by means of the flow sensor 40 current value of the amount of the evaporator, i.e. the Evaporator tubes 4, amount of the supplied per unit of time Feed water S supplied.
  • This the controller block 54 of the value supplied to the flow sensor 42 corresponds to the current one Evaporator throughput VD ( Figure 2).
  • the Controller block 54 the current value via the signal line 52 the combustion heat output FW (FIG. 2) in the combustion chamber 6 fed.
  • the Amount of the burners 5 via the fuel line 44 to current time supplied fuel B determined.
  • This Fuel throughput is converted into the converter 53 corresponding combustion heat output FW converted.
  • the controller block 54 becomes a comparison of the current combustion heat output FW and the current evaporator throughput VD determines a manipulated variable SG, which via line 56 or 56 'the valve 38 or the speed of the feed water pump 34 controls.
  • the evaporator throughput VD serves as a control variable.
  • a minimum throughput of less than 15% of the throughput at 100% load is preferably already set.
  • this minimum throughput is within a bandwidth BD of 5% to 10% of the throughput at 100% load, ie the maximum evaporator throughput VD.
  • This minimum throughput of 5% to 10% of the maximum evaporator throughput VD is set at the start of the start-up process.
  • the first burner 5 is ignited at a point in time t 1 , the heating output FW initially rising suddenly.
  • the combustion heat output FW initially increases gradually. From a furnace heat output FW of approximately 6% of the maximum furnace heat output, the furnace heat output FW increases continuously over time t. With the continuous increase in the combustion heat output FW, the evaporator throughput VD is also continuously increased.
  • the evaporator throughput VD is preferably set such that the percentage evaporator throughput VD related to the throughput at full load within the bandwidth BD of 5% to 10% of the throughput at full load is equal to the percentage firing heat output FW related to full load, ie 100% load .
  • the bandwidth BD, within which the evaporator throughput VD increases with the thermal output FW over time, is limited by an upper limit line OG and a lower limit line UG.
  • the evaporator throughput VD is preferably set to increase in time with the combustion heat output FW during the start-up process.
  • the bandwidth BD - as can be seen in FIG. 2 - is asymmetrical, a deviation of the percentage evaporator throughput VD from the percentage combustion heat output upwards by 3% to 8% and downwards by 2% to 3% of the throughput at 100% load is permissible is.
  • the bandwidth BD is 5% in the exemplary embodiment, so that a deviation A o from the thermal output FW upwards by 3% and a deviation A u from the thermal output FW downwards by 2% is permissible.
  • a minimum throughput of less than 15% i.e. also at a limitation of the evaporator throughput VD at the beginning of the Starting process to preferably 5% to 10% of the throughput at full load there is an even upward flow in all Evaporator tubes 4 guaranteed.
  • Start-up losses are kept particularly low because the most efficient in terms of efficiency even at low loads Continuous operation is achieved.
  • Circulation pumps or waste heat exchangers commonly used up to now can be omitted with this start-up procedure.
  • the water-steam separation vessel 20 shown in FIG Water can be pumped directly via a pump Return line 62, in which a valve 63 is connected, in the feed water tank 18 and thus in the water-steam cycle to be led back. Since there is also a return of the feed water S from the water-steam separation vessel 20 in the flow direction of the feed water S in front of the evaporator 4 or in front of the economizer 15 and thus behind the feed water tank 18 can be omitted, a particularly simple regulation of the start-up process reached.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
EP96900860A 1995-02-09 1996-01-29 Verfahren und vorrichtung zum anfahren eines durchlaufdampferzeugers Expired - Lifetime EP0808440B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19504308A DE19504308C1 (de) 1995-02-09 1995-02-09 Verfahren und Vorrichtung zum Anfahren eines Durchlaufdampferzeugers
DE19504308 1995-02-09
PCT/DE1996/000115 WO1996024803A1 (de) 1995-02-09 1996-01-29 Verfahren und vorrichtung zum anfahren eines durchlaufdampferzeugers

Publications (2)

Publication Number Publication Date
EP0808440A1 EP0808440A1 (de) 1997-11-26
EP0808440B1 true EP0808440B1 (de) 1999-08-18

Family

ID=7753570

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96900860A Expired - Lifetime EP0808440B1 (de) 1995-02-09 1996-01-29 Verfahren und vorrichtung zum anfahren eines durchlaufdampferzeugers

Country Status (9)

Country Link
US (1) US5839396A (ja)
EP (1) EP0808440B1 (ja)
JP (1) JP3836139B2 (ja)
KR (1) KR100427125B1 (ja)
CN (1) CN1119554C (ja)
CA (1) CA2212517C (ja)
DE (2) DE19504308C1 (ja)
IN (1) IN186814B (ja)
WO (1) WO1996024803A1 (ja)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19717158C2 (de) 1997-04-23 1999-11-11 Siemens Ag Durchlaufdampferzeuger und Verfahren zum Anfahren eines Durchlaufdampferzeugers
DE19907451A1 (de) * 1999-02-22 2000-08-24 Abb Alstom Power Ch Ag Verfahren zum Anfahren eines Zwangdurchlauf-Abhitzekessels und Vorrichtung zur Durchführung des Verfahrens
EP2065641A3 (de) * 2007-11-28 2010-06-09 Siemens Aktiengesellschaft Verfahren zum Betrieben eines Durchlaufdampferzeugers sowie Zwangdurchlaufdampferzeuger
EP2119880A1 (de) 2008-02-15 2009-11-18 Siemens Aktiengesellschaft Verfahren zum Anfahren eines Durchdampferzeugers
EP2180250A1 (de) * 2008-09-09 2010-04-28 Siemens Aktiengesellschaft Durchlaufdampferzeuger
EP2182278A1 (de) * 2008-09-09 2010-05-05 Siemens Aktiengesellschaft Durchlaufdampferzeuger
US9541282B2 (en) * 2014-03-10 2017-01-10 International Paper Company Boiler system controlling fuel to a furnace based on temperature of a structure in a superheater section
DE102014222682A1 (de) 2014-11-06 2016-05-12 Siemens Aktiengesellschaft Regelungsverfahren zum Betreiben eines Durchlaufdampferzeugers
DE102017205382A1 (de) * 2017-03-30 2018-10-04 Siemens Aktiengesellschaft Wasserrückführung in vertikalen Zwangdurchlaufdampferzeugern
CN110006025A (zh) * 2019-03-19 2019-07-12 广东美智智能科技有限公司 一种基于pid的蒸汽发生器压力调控方法、设备及存储介质

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1593128A (ja) * 1967-12-09 1970-05-25
BE756407A (fr) * 1969-09-23 1971-03-22 Sulzer Ag Procede de mise en marche d'un generateur de vapeur
CH632331A5 (de) * 1978-10-03 1982-09-30 Sulzer Ag Verfahren zum anfahren eines zwanglaufdampferzeugers.
FI68458C (fi) * 1980-12-23 1985-09-10 Sulzer Ag Tvaongsstyrdaonggeneratoranlaeggning
CH673697A5 (ja) * 1987-09-22 1990-03-30 Sulzer Ag
ATE122137T1 (de) * 1990-01-31 1995-05-15 Siemens Ag Dampferzeuger.
US5396865A (en) * 1994-06-01 1995-03-14 Freeh; James H. Startup system for power plants

Also Published As

Publication number Publication date
JPH10513543A (ja) 1998-12-22
WO1996024803A1 (de) 1996-08-15
DE19504308C1 (de) 1996-08-08
CA2212517C (en) 2001-04-10
CA2212517A1 (en) 1996-08-15
IN186814B (ja) 2001-11-17
KR19980702020A (ko) 1998-07-15
US5839396A (en) 1998-11-24
CN1168172A (zh) 1997-12-17
JP3836139B2 (ja) 2006-10-18
DE59602799D1 (de) 1999-09-23
EP0808440A1 (de) 1997-11-26
CN1119554C (zh) 2003-08-27
KR100427125B1 (ko) 2004-08-02

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