EP2037086B1 - Mise en route d'une turbine à vapeur - Google Patents

Mise en route d'une turbine à vapeur Download PDF

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Publication number
EP2037086B1
EP2037086B1 EP07014816.8A EP07014816A EP2037086B1 EP 2037086 B1 EP2037086 B1 EP 2037086B1 EP 07014816 A EP07014816 A EP 07014816A EP 2037086 B1 EP2037086 B1 EP 2037086B1
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EP
European Patent Office
Prior art keywords
valve
steam turbine
open position
steam
rotation
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
EP07014816.8A
Other languages
German (de)
English (en)
Other versions
EP2037086A1 (fr
Inventor
Rudolf Dr. Keiper
Thomas Dr. Müller
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
Application filed by Siemens AG filed Critical Siemens AG
Priority to PL07014816T priority Critical patent/PL2037086T3/pl
Priority to EP07014816.8A priority patent/EP2037086B1/fr
Priority to PCT/EP2008/059241 priority patent/WO2009016029A2/fr
Publication of EP2037086A1 publication Critical patent/EP2037086A1/fr
Application granted granted Critical
Publication of EP2037086B1 publication Critical patent/EP2037086B1/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

Definitions

  • the invention relates to a method for starting a steam turbine at a synchronous speed, which is operated in a cogeneration system with a boiler and at least one arranged between the boiler and the steam turbine in a steam line valve with a controllable open position, wherein a live steam pressure upstream of the valve is measured.
  • the invention relates to a control unit of a cogeneration system, which cogeneration system comprises a boiler and at least one to be operated at a synchronous speed steam turbine, wherein between the steam turbine and the boiler at least one arranged in a steam line valve with adjustable open position is provided, wherein a live steam pressure upstream of the valve is measured.
  • different dynamic behavior of individual components such as the boiler and the steam turbine can lead to unexpected operating conditions.
  • the boiler in which the steam generation and overheating takes place, essentially follows thermal time constants
  • the steam turbine in which the generated and superheated steam is expanded, follows with their speed behavior much shorter time constants than the boiler.
  • a so-called quick-acting valve which in certain as Fault classified events the steam supply from the boiler to the steam turbine interrupts.
  • the steam generated in the boiler is fed in bypass to the steam turbine to a reducing station, which either relaxes the circulating medium into the environment or, after expansion, introduces a condenser integrated in the circuit.
  • US 4,258,424 discloses a computer controlled control system for determining steam flow characteristics of a steam turbine.
  • the control valves are fully opened to introduce steam from a boiler into a turbine.
  • the control valves may be individually controlled to provide thermal equilibrium on the rotor and reduce rotor blade stress.
  • the steam turbine may be controlled based on steam control, speed control, or load control to meet predetermined safety limits and protection limits.
  • GB 2 084 260 A discloses a steam turbine control for a steam turbine in a steam turbine power plant.
  • the steam turbine power plant has a high-pressure turbine and a low-pressure turbine.
  • a main control valve, a high pressure bypass valve, a control valve and a low pressure bypass valve control the respective turbines.
  • the control valves are controlled based on the speed and temperature of the turbine.
  • the invention has therefore set itself the task of preventing unwanted fast-closing events at a power cogeneration system mentioned above.
  • the valve with adjustable opening position according to the invention is usually a so-called control valve, which is often used in combination with a so-called quick-closing valve.
  • the running between the boiler and the steam turbine steam line is usually a so-called live steam line.
  • the invention finds particularly advantageous use in a boiler which is fired with solids, in particular by means of combustible organic material, since such systems have a particularly different dynamic behavior compared to that of the steam turbine. In principle, however, the method or regulation according to the invention can be used for all cycles of the type mentioned above. While quick-acting valves usually only allow the fully open or completely closed position and are optimized for a particularly fast closing process, control valves allow a continuously variable adjustment of the opening between 0% and 100%.
  • the method according to the invention has the significant advantage that conventionally necessary and very complex coordination work between the control behavior of the steam turbine and that of the boiler can be reduced to a minimum or eliminated altogether.
  • the controller of the valve position essentially takes over the pressure control of the boiler or supports this, so that an occurrence of a quick-closing criterion from a critical pressure behavior of the boiler out is highly unlikely.
  • this phase occurs simultaneously due to the opening of the valve or control valve an increase in the speed of the steam turbine.
  • the specification of the setpoint for the open position of the valve is no longer dependent on the live steam pressure, but on the speed of the steam turbine, which is regularly specified as the control criterion for the speed of the setpoint synchronous speed.
  • the time of the changeover of the control for the opening position of the valve or the speed difference to the synchronous speed can be determined depending on the system conditions, the difference is rather low, when the boiler is very sensitive to the opening of the control valve with pressure drop.
  • the method according to the invention is used when using particularly tolerant turbo sets, which do not require any special speed transients, especially in resonance ranges for damage-free starting.
  • the predetermined difference value to the synchronous speed in which the control of the valve position is switched by the dependence on the live steam pressure depending on the speed, may suitably be between 1% and 10% of the synchronous speed, so that at a synchronous speed of 3000 rev / min after reaching A speed of about 2900 rev / min is switched to a speed control.
  • the control criterion during the start-up phase in which the valve position is controlled by the live steam pressure is preferably a constant live steam pressure of, for example, 2.5 bar.
  • FIG. 1 shows a schematic overview of a cogeneration system 1 with a control according to the invention using the start-up method according to the invention.
  • the combined heat and power system 1 consists essentially of a boiler B, a steam turbine ST, a generator G, a condenser Cond and a feedwater pump PU.
  • the boiler B the water delivered by the feed water pump PU to a pressure of about 3.5 bar is heated, evaporated and superheated by means of a heat supply QF.
  • the superheated live steam passes through a main steam line FSL passing a quick-closing valve ESV and a control valve CV to relax in the steam turbine ST, where under production of technical work, the live steam is expanded to condenser pressure which technical work drives a generator G, the electric power P in a Network GR feeds.
  • the turbo set consisting of steam turbine ST and generator G rotates at a synchronous speed n sync of 3000 U / min.
  • the condenser Cond the relaxed steam is condensed with the removal of heat QC.
  • the condensed water is pumped by the pump PU receiving the technical work WT to the boiler pressure of 3.5 bar.
  • the fuel supply QF to the boiler B is controlled by means of a boiler controller PID, which regulates the supply of solid fuel in response to the live steam pressure PF with the aim of keeping the live steam pressure constant at 3.5 bar.
  • the live steam pressure PF in the Main steam line FSL is measured by means of a pressure sensor PS.
  • the position of the control valve CV is controlled by means of a regulator PI.
  • a speed sensor NS By means of a speed sensor NS, the speed n of the turbo set of steam turbine ST and generator G is measured.
  • the speed n and the live steam pressure PF are input to a control unit CM, which controls or controls, among other things, the opening position of the control valve CV and the fuel supply QF via the controller PI or PID.
  • the quick-closing valve ESV In a first phase of the startup of the combined heat and power system 1, the quick-closing valve ESV is closed and the boiler B generates live steam under fuel supply QF, which is fed under passage through a bypass valve VR via a reducing station directly into the condenser Cond. Upon reaching unspecified criteria, such as steam purity or stability over a period of time, closes the bypass valve VR.
  • the quick-closing valve ESV opens simultaneously with the closing of the bypass valve VR and the control valve CV opens so far that about 50% of the maximum open position of the control valve CV are reached.
  • the live steam pressure PF drops slightly and the speed n of the steam turbine ST increases.
  • the control unit CM regulates the live steam pressure to 3.5 bar by means of suitable control of the control valve CV and the speed n of the steam turbine ST increases as a result.
  • control valve initially simply remains in the first open position of about 50% without further control of the live steam pressure and also not guided by the turbine speed n.

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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 (11)

  1. Méthode de mise en route d'une turbine à vapeur (ST) sur une vitesse synchrone (nsync), laquelle turbine à vapeur fonctionne dans un système de production combinée de chaleur et d'électricité (1) comprenant une chaudière (B) et au moins une soupape (CV)avec position d'ouverture réglable, disposée dans une conduite de vapeur entre la chaudière (B) et la turbine à vapeur (ST), une pression de vapeur fraîche (PF) étant mesurée en amont de la soupape (CV),
    caractérisée par :
    a) ouverture de la soupape (CV) pendant une opération de mise en route de la turbine à vapeur (ST) sur une première position d'ouverture, un réglage de la position d'ouverture de la soupape (CV), après l'ouverture de la soupape (CV) sur la première position d'ouverture, ayant lieu en fonction de la pression de vapeur fraîche (PF) de manière à ce que la pression de vapeur fraîche (PF) ne dépasse pas une première limite inférieure,
    b) commutation du réglage de la position d'ouverture de la soupape (CV) en fonction de la vitesse (N), lorsque la vitesse (N) de la turbine à vapeur (ST) s'est approchée de la vitesse synchrone (nsync) jusqu'à une première valeur différentielle prédéterminée (Δn),
    c) réglage de la position d'ouverture de la soupape (CV) de manière à ce que la turbine à vapeur (ST) tourne à la vitesse synchrone (ngync).
  2. Méthode selon la revendication 1,
    caractérisée en ce que la première position d'ouverture est entre 25% et 75%.
  3. Méthode selon la revendication 1 ou 2,
    caractérisée en ce que la position d'ouverture avant la commutation du réglage de la position d'ouverture de la soupape (CV) est réglée en fonction de la vitesse (N), du réglage de la valeur théorique constante de la première position d'ouverture.
  4. Méthode selon la revendication 1, 2 ou 3,
    caractérisée en ce que
    la première valeur différentielle (Δn) est entre un pour cent et vingt pour cent de la vitesse synchrone (ngync).
  5. Méthode selon la revendication 1, 2, 3 ou 4 caractérisée en ce qu'
    avant la deuxième étape (étape b)) une valeur théorique de la pression de vapeur fraîche (PF) est constante.
  6. Méthode selon la revendication 1, 2, 3, 4 ou 5,
    caractérisée en ce que
    pendant ou après l'ouverture de la soupape de réglage (CV), une soupape de dérivation (VR) destinée à contourner la turbine à vapeur (ST) est complètement fermée, de sorte que la vapeur provenant de la chaudière (B) traverse totalement la turbine à vapeur (ST).
  7. Unité de réglage (CM) d'un système de production combinée de chaleur et d'électricité (1), lequel système de production combinée de chaleur et d'électricité présente une chaudière et au moins une turbine à vapeur (ST) à faire fonctionner à une vitesse synchrone (ngync), au moins une soupape (CV) avec position d'ouverture réglable, disposée dans une conduite de vapeur (FSL) entre la turbine à vapeur (ST) et la chaudière (B) étant ménagée, une pression de vapeur fraîche (PF) étant mesurée en amont de la soupape (CV),
    caractérisée en ce que
    l'unité de réglage (CM) est réalisée de manière à ce que
    a) dans une première étape de la mise en route du système de production combinée de chaleur et d'électricité (1), la soupape (CV) s'ouvre, et qu'après la première étape, pendant l'opération de mise en route de la turbine à vapeur, la position d'ouverture de la soupape (CV) soit réglée en fonction de la pression de vapeur fraîche (PF) mesurée, de telle manière que la pression de vapeur fraîche (PF) ne dépasse pas une première limite inférieure,
    b) dans une deuxième étape, une commutation du réglage de la position d'ouverture de la soupape (CV) soit réalisée en fonction de la vitesse (n), lorsque la vitesse (n) de la turbine à vapeur (nsync) s'est approchée de la vitesse synchrone (nsync) jusqu'à une valeur différentielle prédéterminée (Δn) et
    c) dans une troisième étape, la position d'ouverture de la soupape (CF) soit réglée de manière à ce que la turbine à vapeur (ST) tourne à la vitesse synchrone (nsync).
  8. Unité de réglage (CM) selon la revendication 7,
    caractérisée en ce que l'unité de réglage (CM) est réalisée de manière à ce que
    la première position d'ouverture soit entre 25% et 75%.
  9. Unité de réglage (CM) selon la revendication 7 ou 8,
    caractérisée en ce que l'unité de réglage (CM) est réalisée de manière à ce que
    la première valeur différentielle (Δn) soit entre un pour cent et vingt pour cent de la vitesse synchrone (nsync).
  10. Unité de réglage (CM) selon la revendication 7, 8 ou 9
    caractérisée en ce que l'unité de réglage (CM) est réalisée de manière à ce qu'
    à la première étape, une valeur théorique de la pression de vapeur fraîche (PF) soit constante.
  11. Unité de réglage (CM) selon la revendication 7,8, 9 ou 10
    caractérisée en ce que l'unité de réglage (CM) est réalisée de manière à ce que
    pendant ou après l'ouverture de la soupape de réglage (CV), une soupape de dérivation (VR) destinée à contourner la turbine à vapeur (ST) soit complètement fermée, de sorte que la vapeur provenant de la chaudière (B) traverse totalement la turbine à vapeur (ST).
EP07014816.8A 2007-07-27 2007-07-27 Mise en route d'une turbine à vapeur Active EP2037086B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PL07014816T PL2037086T3 (pl) 2007-07-27 2007-07-27 Rozruch turbiny parowej
EP07014816.8A EP2037086B1 (fr) 2007-07-27 2007-07-27 Mise en route d'une turbine à vapeur
PCT/EP2008/059241 WO2009016029A2 (fr) 2007-07-27 2008-07-15 Mise en marche d'une turbine à vapeur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07014816.8A EP2037086B1 (fr) 2007-07-27 2007-07-27 Mise en route d'une turbine à vapeur

Publications (2)

Publication Number Publication Date
EP2037086A1 EP2037086A1 (fr) 2009-03-18
EP2037086B1 true EP2037086B1 (fr) 2013-05-15

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07014816.8A Active EP2037086B1 (fr) 2007-07-27 2007-07-27 Mise en route d'une turbine à vapeur

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EP (1) EP2037086B1 (fr)
PL (1) PL2037086T3 (fr)
WO (1) WO2009016029A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9249691B2 (en) * 2012-01-06 2016-02-02 General Electric Company Systems and methods for cold startup of rankine cycle devices
WO2015028366A2 (fr) * 2013-08-28 2015-03-05 Siemens Aktiengesellschaft Procédé permettant de faire fonctionner un générateur de vapeur à circulation forcée chauffé par l'extérieur

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4258424A (en) 1972-12-29 1981-03-24 Westinghouse Electric Corp. System and method for operating a steam turbine and an electric power generating plant
US3879616A (en) * 1973-09-17 1975-04-22 Gen Electric Combined steam turbine and gas turbine power plant control system
US4329592A (en) 1980-09-15 1982-05-11 General Electric Company Steam turbine control
US4598551A (en) * 1985-10-25 1986-07-08 General Electric Company Apparatus and method for controlling steam turbine operating conditions during starting and loading

Also Published As

Publication number Publication date
WO2009016029A3 (fr) 2009-04-02
WO2009016029A2 (fr) 2009-02-05
EP2037086A1 (fr) 2009-03-18
PL2037086T3 (pl) 2013-10-31

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