EP1957759B1 - Procédé de démarrage d'une installation de turbines à vapeur - Google Patents

Procédé de démarrage d'une installation de turbines à vapeur Download PDF

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Publication number
EP1957759B1
EP1957759B1 EP06763662.1A EP06763662A EP1957759B1 EP 1957759 B1 EP1957759 B1 EP 1957759B1 EP 06763662 A EP06763662 A EP 06763662A EP 1957759 B1 EP1957759 B1 EP 1957759B1
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EP
European Patent Office
Prior art keywords
steam
temperature
reference component
starting
transient
Prior art date
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Active
Application number
EP06763662.1A
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German (de)
English (en)
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EP1957759A2 (fr
Inventor
Edwin Godebrecht
Rainer Quinkertz
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Siemens AG
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Siemens AG
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Publication date
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Priority to EP06763662.1A priority Critical patent/EP1957759B1/fr
Priority to PL06763662T priority patent/PL1957759T3/pl
Publication of EP1957759A2 publication Critical patent/EP1957759A2/fr
Application granted granted Critical
Publication of EP1957759B1 publication Critical patent/EP1957759B1/fr
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Classifications

    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D19/00—Starting of machines or engines; Regulating, controlling, or safety means in connection therewith
    • F01D19/02—Starting of machines or engines; Regulating, controlling, or safety means in connection therewith dependent on temperature of component parts, e.g. of turbine-casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/165—Controlling means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/85—Starting

Definitions

  • the invention relates to a method for starting a steam turbine plant which has at least one steam turbine and at least one steam generating plant for generating steam which drives the steam turbine, the steam turbine plant having at least one reference component which has an initial temperature of greater than 250 ° C. at a starting time. wherein the temperature of the steam and the reference component is continuously measured, wherein the reference component of the steam turbine plant is subjected to steam from the start time.
  • document US-A-353232079 discloses, for example, a method for starting a large steam power plant after a temporary service interruption.
  • the steam generated in a heat recovery steam generator is initially not supplied to the steam turbine part of a steam turbine plant, but bypasses bypass stations on the turbine and fed directly to a condenser, which condenses the steam to water.
  • the condensate is then fed back as feed water to the steam generator or blown off a roof, if no diverter station is present.
  • certain steam parameters in the steam lines of the water-steam cycle or in the leading to the turbine part of the steam turbine plant steam lines, such as certain vapor pressures and temperatures are met, the steam turbine is switched on. The maintenance of these steam parameters should keep possible stresses in thick-walled components at a low level and avoid impermissible relative elongations.
  • the thick-walled components of the steam turbine still have high outlet temperatures after night shutdowns or even after weekend shutdowns.
  • Thick-walled components are in this case z.
  • control valves are currently kept closed in a steam turbine plant until the steam generator or boiler supplies steam at a correspondingly high temperature , These temperatures are in about 50 ° C above a starting temperature of individual thick-walled components.
  • the disadvantage here is considered the long waiting time until the availability of the steam turbine plant.
  • the object of the invention is to provide a method for starting a steam turbine plant of the type mentioned, which leads to a quick availability of the steam turbine plant.
  • This object is achieved by a method for starting a steam turbine plant having at least one steam turbine and at least one steam generating plant for generating the steam turbine driving steam, wherein the steam turbine plant has at least one reference component, the starting temperature at an outlet temperature of greater than 250 ° C, wherein the temperature of the steam and the reference member is continuously measured, wherein the reference member of the steam turbine plant is applied from the start time with steam, wherein the starting temperature of the steam is lower than the temperature of the reference component and the temperature of the Steam is increased with a start transient and the start temperature and the start transient are chosen such that the temperature change per unit time of the reference component is below a predetermined limit, the temperature of the reference component is initially lower until a minimum reached wi rd and then gets higher.
  • the temperature change per unit time of the reference component is in this case at values greater than or equal to 5K / min.
  • the invention is based on the recognition that the thick-walled components of a steam turbine plant, in spite of the high compared to the temperature of the steam outlet temperatures can be acted upon with the steam whose temperature is below the starting temperature of individual reference components.
  • the temperature of the steam must be increased with a sufficient transient, so that the average integral temperature of the thick-walled reference components undergoes only negligible cooling.
  • a transient is a change, in particular temperature change per unit time (° K / min). Whereas a gradient is to be understood as a change, in particular a change in temperature per distance (° K / min). As a result, even relative expansion problems can be excluded.
  • the invention is therefore based on the recognition that a very fast start time of the steam turbine plant possible is, although the requirement of a steam from the boiler or boiler of about 50 Kelvin is above the starting temperature of the reference components is omitted, and is acted upon by a vapor whose temperature is lower than the starting temperature of the reference components.
  • the steam outlet temperature must be increased after applying the reference components with a sufficient and suitable starting gradient.
  • Too low a start gradient would result in too little increase in the temperature of the steam and there is a risk that the thick-walled components will over-cool.
  • the temperature of the reference component is measured at a surface of the, which faces the steam.
  • a reference component initially cools on the surface, and the components lying further in the interior cool comparatively slowly. This leads to a temperature difference in the thickness of the reference components, which can lead to thermal stresses. Therefore, it is advantageous if the temperature of the component is measured directly on the surface facing the steam.
  • the method is extended to the effect that a further temperature is measured at a point of the reference component, which faces away from the steam, wherein the starting temperature and the starting gradient are selected such that a temperature difference between the temperature the surface and the further temperature is below a predetermined temperature difference limit.
  • the invention is based on the recognition that just a high temperature difference between the temperature of the surface of a reference component and the temperature at an adjacent location of the reference component is harmful.
  • the further temperature is measured at a surface of the reference component opposite to the surface acted upon by the steam.
  • the further temperature is measured substantially in the middle of the reference component. Since the thick-walled reference components of the steam turbine plant behave relatively sluggish with a temperature increase, which means that the temperature increase in the wall thickness direction is very slow, it is advantageous if the further temperature is measured substantially in the middle of the reference component. This allows very early monitoring of the temperature development of the thick-walled reference components.
  • the start transient is selected such that its value is greater than or equal to 5K / min.
  • the value can be constant or variable. This makes it possible to start a steam turbine plant with relatively simple procedural means.
  • the temperature of the vapor is increased after reaching a transfer limit value with a guide gradient, wherein the value of the guide gradient is lower than the value of the start gradient.
  • the invention is based on the idea that initially a cooler compared to the starting temperature of the reference component steam acts on the reference component. This leads to a cooling the steam facing surface of the reference component.
  • the starting temperature of the steam must not be too low compared to the starting temperature of the reference component.
  • the increase in the temperature of the steam must be done with a suitable transient. Too slow an increase in the temperature of the steam leads to damage to the reference components.
  • the thick-walled reference component initially cools until the temperature of the reference component reaches a minimum. After reaching this minimum, the temperature of the reference component increases.
  • the temperature of the steam is then increased with the start transient up to an acceptance limit value. After reaching the acceptance limit, the temperature of the vapor is further increased with a pilot transient, the value of the pilot transient being lower than the value of the start transient. Too rapid an increase in the temperature of the steam would cause the surface facing the steam to heat too quickly with respect to the surface of the reference component facing away from the vapor, thereby causing too great a temperature difference between the surface facing the steam and the surface Surface, which faces away from the steam, leads. This leads to undesirable damage to the reference component. By choosing a suitable guiding transient, which must be lower than the starting transient, a development of too great a temperature difference between the side facing the steam and the side facing away from the vapor is prevented.
  • the change of the temperature of the steam is carried out by external water injection. This provides a comparatively simple way of influencing the transient of the temperature increase.
  • the outlet temperatures of the reference components are between 300 ° to 450 ° C.
  • the starting temperature of the steam is up to 150 ° C below the Output temperature.
  • the value of the start transient is greater than or equal to 5 Kelvin per minute, in particular it is 13 Kelvin per minute.
  • the value of the guiding transient is between 0 and 15 Kelvin per minute, in particular the value is 1 Kelvin per minute. The inventors have recognized that these values are suitable in today's steam turbine construction to carry out the method described above.
  • FIG. 1 schematically shown combined gas and steam turbine plant 1 comprises a gas turbine plant 1a and a steam turbine plant 1b.
  • the gas turbine plant 1a is equipped with a gas turbine 2, a compressor 4 and at least one combustion chamber 6 connected between the compressor 4 and the gas turbine 2.
  • a gas turbine 2 By means of the compressor 4, fresh air L is sucked in, compressed and fed via the fresh air line 8 to one or more burners of the combustion chamber 6.
  • the supplied air is mixed with supplied via a fuel line 10 liquid or gaseous fuel B and ignited the mixture.
  • the resulting combustion exhaust gases form the working medium AM of the gas turbine plant 1a, which is the Gas turbine 2 is supplied, where it performs work under relaxation and coupled to the gas turbine 2 shaft 14 drives.
  • the shaft 14 is coupled in addition to the gas turbine 2 with the air compressor 4 and a generator 12 to drive this.
  • the expanded working medium AM is discharged via an exhaust pipe 34 to a heat recovery steam generator 30 of the steam turbine plant 1b.
  • the working medium discharged from the gas turbine 1a at a temperature of about 500 ° to 600 ° C. is used for generating and superheating steam.
  • the steam turbine plant 1b comprises, in addition to the heat recovery steam generator 30, which can be designed in particular as a forced flow system, a steam turbine 20 with turbine stages 20a, 20b, 20c and a condenser 26.
  • the heat recovery steam generator 30 and the condenser 26 together with condensate lines and feed water lines 35, 40 and with steam lines 48, 53, 64, 70, 80, 100, a steam system, which forms a steam circuit together with the steam turbine 20.
  • Water from a feedwater tank 38 is fed by means of a feedwater pump 42 to a high-pressure preheater 44, also called an economizer, and from there to an evaporator 46 connected to the economizer 44 and designed for a continuous operation.
  • the evaporator 46 is in turn connected on the output side via a steam line 48, in which a water separator 50 is connected to a superheater 52.
  • a steam line 43 the superheater 52 is connected on the output side to the steam inlet 54 of the high-pressure stage 20 a of the steam turbine 20.
  • the steam superheated by the superheater 52 drives the steam turbine before it is passed on via the steam outlet 56 of the high-pressure stage 20a to a reheater 58.
  • the steam is forwarded via a further steam line 81 to the steam inlet 60 of the medium-pressure stage 20b of the steam turbine 20, where it drives the turbine.
  • the steam outlet 62 of the medium-pressure stage 20b is connected via an overflow line 64 to the steam inlet 66 of the low-pressure stage 20c of the steam turbine 20. After flowing through the low-pressure stage 20c and the associated drives of the turbine, the cooled and expanded steam is output via the steam outlet 68 of the low-pressure stage 20c to the steam line 70, which leads it to the condenser 26.
  • the condenser 26 converts the incoming steam into condensate and transfers the condensate via the condensate line 35 by means of a condensate pump 36 to the feedwater tank 38.
  • this also includes a bypass line 100, the so-called high-pressure bypass, which branches off from the steam line 53 before it reaches the steam inlet 54 of the high-pressure stage 20a.
  • the high-pressure bypass 100 bypasses the high-pressure stage 20a and leads into the feed line 80 to the reheater 58.
  • Another bypass line, the so-called medium-pressure bypass 200 branches off the steam line 81 before it opens into the steam inlet 60 of the medium-pressure stage 20b.
  • the medium-pressure bypass 200 bypasses both the intermediate pressure stage 20b and the low-pressure stage 20c and opens into the vapor line 70 leading to the condenser 26.
  • a check valve 102, 202 are installed, with which they can be shut off.
  • shut-off valves 104, 204 are installed in the steam line 53 and in the steam line 81, respectively between the branch point the bypass line 100 or 200 and the steam inlet 54 of the high-pressure stage 20a and the steam inlet 60 of the medium-pressure stage 20a.
  • a shut-off valve is located in the steam line 53, between the branch point of the bypass line 100 and the steam inlet 54 of the high-pressure stage 20 a of the steam turbine 20.
  • bypass line 100 and the shut-off valves 102, 104 serve to divert a portion of the steam to bypass the steam turbine 2 during the startup of the combined cycle power plant 1.
  • the steam turbine installation 1b is in a cooled state and a hot or warm start is to be carried out.
  • a hot start is typically referred to as a start after a night shutdown of about 8 hours, whereas a start after a weekend shutdown of about 48 hours is referred to as a warm start.
  • the thick-walled components of the steam turbine 1b still have high outlet temperatures of 300 ° to about 500 ° C.
  • the thick-walled components can also be referred to as reference components. Thick-walled components are in this case z.
  • the reference component has a starting temperature greater than 250 ° C.
  • the temperature of the vapor and the reference component is continuously measured.
  • the steam turbine plant 1b is acted upon from a start time with steam.
  • the starting temperature of the steam is lower than the temperature of the reference component.
  • the temperature of the steam is then increased with a controllable start transient, wherein the starting temperature and the starting transient are selected such that the temperature change per Time unit of the reference component is below a predetermined limit, the temperature of the reference component is initially lower, until a minimum is reached and then higher.
  • the temperature profile of the steam 205 is shown as a function of time. Likewise, the temperature profile is shown on a steam-facing surface 202 of a thick-walled component. Also shown in FIG. 2 a mean integral temperature 204 of the thick-walled component.
  • integral temperature 204 is meant, for example, the temperature that prevails substantially in the middle of the reference component.
  • the temperature of the steam 205 is increased with a start-up transient, as described in FIG. 2 represented, constant, increased.
  • the constant start transient leads to a linear progression of the temperature up to an acceptance limit value 201.
  • the temperature of the vapor 205 is increased with a lead transient which is lower than the value of the start transient.
  • the starting temperature of the thick-walled reference component has a value of greater than 250 ° C and is in this embodiment at about 500 ° C.
  • the temperature of the thick-walled component becomes higher and increases comparatively strongly up to the point of time 206, when the temperature of the vapor reaches the acceptance limit value and is subsequently increased more moderately with the guidance transient.
  • the temperature of the steam can be influenced by water injection.
  • the mean integral temperature 204 of the reference component in principle follows the course as well as the designated 203 curve of the thick-walled component. First, the temperature drops until a minimum value 204 is reached. Then the temperature rises.
  • FIG. 3 is the availability or performance of such a gas and steam turbine plant according to the invention to see.
  • the dotted curves show the course of a conventional, existing according to the prior art gas and steam turbine plant.
  • the solid lines show the course of a gas and steam turbine plant, which was started by the method according to the invention.
  • the time is plotted on the X axis and the availability or the output of the steam turbine plant in percent on the Y axis.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Turbines (AREA)

Claims (12)

  1. Procédé de mise en fonctionnement d'une installation ( 1b ) de turbine à vapeur, qui a au moins une turbine ( 20a, 20b, 20c ) à vapeur et au moins une installation ( 30b, 30, 44, 46, 52, 50 ) de production de vapeur pour produire de la vapeur entraînant la turbine ( 20a, 20b, 20c ) à vapeur, dans lequel l'installation ( 1b ) de turbine à vapeur a au moins un élément de référence, qui, à l'instant de la mise en fonctionnement, a une température de sortie supérieure à 250°C,
    dans lequel on mesure en continu la température de la vapeur et de l'élément de référence,
    dans lequel on soumet à la vapeur l'élément de référence de l'installation ( 1b ) de turbine à vapeur à partir de l'instant de mise en marche,
    caractérisé en ce que
    la température de mise en marche de la vapeur est plus basse que la température de l'élément de référence et
    on élève la température de la vapeur par un transitoire de mise en marche et
    on choisit la température de mise en marche et le transitoire de mise en marche à ce que la variation de température par unité de temps de l'élément de référence soit inférieure à une valeur limite donnée à l'avance,
    dans lequel la température de l'élément de référence devient d'abord plus basse jusqu'à ce qu'un minimum soit atteint et ensuite devient plus haute.
  2. Procédé suivant la revendication 1,
    dans lequel on mesure la température de l'élément de référence à sa surface, qui est tournée vers la vapeur.
  3. Procédé suivant la revendication 2,
    dans lequel on mesure une autre température en un point de l'élément de référence, qui est éloigné de la vapeur, la température de mise en marche et le transitoire de mise en marche étant choisis de manière à avoir, avec une valeur limite de différence de température donnée à l'avance, une différence de température entre la température à la surface et l'autre température.
  4. Procédé suivant la revendication 3,
    dans lequel on mesure l'autre température à une surface de l'élément de référence, qui est opposée à la surface soumise à la vapeur.
  5. Procédé suivant la revendication 3,
    dans lequel on mesure l'autre température essentiellement au milieu de l'épaisseur de l'élément de référence.
  6. Procédé suivant l'une des revendications précédentes,
    dans lequel le transitoire de mise en marche est constant.
  7. Procédé suivant l'une des revendications précédentes,
    dans lequel on élève, avec un transitoire de conduite, la température de la vapeur après avoir atteint une valeur ( 201 ) limite de prise en charge,
    la valeur du transitoire de conduite étant plus petite que la valeur du transitoire de mise en marche.
  8. Procédé suivant l'une des revendications précédentes,
    dans lequel la variation de la température de la vapeur s'effectue par une injection d'eau extérieure.
  9. Procédé suivant l'une des revendications précédentes,
    dans lequel les températures initiales des éléments sont comprises entre 300°C et 400°C.
  10. Procédé suivant l'une des revendications précédentes,
    dans lequel la température de la vapeur à la mise en marche est inférieure de jusqu'à 150 K à la température initiale.
  11. Procédé suivant l'une des revendications précédentes,
    dans lequel le transitoire de mise en marche prend des valeurs supérieures ou égales à 5 K/min, notamment de 13 K/min.
  12. Procédé suivant l'une des revendications précédentes,
    dans lequel le transitoire de conduite prend des valeurs comprises entre 0 et 15 K/min, notamment de 1 K/min.
EP06763662.1A 2005-07-14 2006-06-13 Procédé de démarrage d'une installation de turbines à vapeur Active EP1957759B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP06763662.1A EP1957759B1 (fr) 2005-07-14 2006-06-13 Procédé de démarrage d'une installation de turbines à vapeur
PL06763662T PL1957759T3 (pl) 2005-07-14 2006-06-13 Sposób uruchamiania instalacji turbin parowych

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP05015350A EP1744020A1 (fr) 2005-07-14 2005-07-14 Procédé de démarrage d'une installation de turbines à vapeur
EP06763662.1A EP1957759B1 (fr) 2005-07-14 2006-06-13 Procédé de démarrage d'une installation de turbines à vapeur
PCT/EP2006/063135 WO2007006617A2 (fr) 2005-07-14 2006-06-13 Procede pour faire demarrer une installation de turbine a vapeur

Publications (2)

Publication Number Publication Date
EP1957759A2 EP1957759A2 (fr) 2008-08-20
EP1957759B1 true EP1957759B1 (fr) 2016-09-14

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EP05015350A Withdrawn EP1744020A1 (fr) 2005-07-14 2005-07-14 Procédé de démarrage d'une installation de turbines à vapeur
EP06763662.1A Active EP1957759B1 (fr) 2005-07-14 2006-06-13 Procédé de démarrage d'une installation de turbines à vapeur

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Application Number Title Priority Date Filing Date
EP05015350A Withdrawn EP1744020A1 (fr) 2005-07-14 2005-07-14 Procédé de démarrage d'une installation de turbines à vapeur

Country Status (10)

Country Link
US (1) US7805941B2 (fr)
EP (2) EP1744020A1 (fr)
JP (1) JP4762310B2 (fr)
CN (1) CN101305163B (fr)
BR (1) BRPI0613011A2 (fr)
CA (1) CA2615001C (fr)
ES (1) ES2607357T3 (fr)
PL (1) PL1957759T3 (fr)
RU (1) RU2370653C1 (fr)
WO (1) WO2007006617A2 (fr)

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JP4707927B2 (ja) * 2000-05-31 2011-06-22 シーメンス アクチエンゲゼルシヤフト 多段蒸気タービンの無負荷又は軽負荷運転時の運転方法と装置

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WO2007006617A2 (fr) 2007-01-18
RU2370653C1 (ru) 2009-10-20
US7805941B2 (en) 2010-10-05
JP2009501292A (ja) 2009-01-15
PL1957759T3 (pl) 2017-04-28
BRPI0613011A2 (pt) 2010-12-14
US20090126365A1 (en) 2009-05-21
CA2615001A1 (fr) 2007-01-18
CN101305163A (zh) 2008-11-12
CN101305163B (zh) 2012-11-14
CA2615001C (fr) 2012-05-08
WO2007006617A3 (fr) 2008-06-26
EP1744020A1 (fr) 2007-01-17
JP4762310B2 (ja) 2011-08-31
EP1957759A2 (fr) 2008-08-20

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