EP0842350A1 - Systeme de regulation du regime d'une turbine et procede de regulation du regime d'une turbine pendant un delestage - Google Patents

Systeme de regulation du regime d'une turbine et procede de regulation du regime d'une turbine pendant un delestage

Info

Publication number
EP0842350A1
EP0842350A1 EP96924760A EP96924760A EP0842350A1 EP 0842350 A1 EP0842350 A1 EP 0842350A1 EP 96924760 A EP96924760 A EP 96924760A EP 96924760 A EP96924760 A EP 96924760A EP 0842350 A1 EP0842350 A1 EP 0842350A1
Authority
EP
European Patent Office
Prior art keywords
speed
turbine
control
controller
value
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.)
Granted
Application number
EP96924760A
Other languages
German (de)
English (en)
Other versions
EP0842350B1 (fr
Inventor
Bernhard Jerye
Alfred Schwope
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
Publication of EP0842350A1 publication Critical patent/EP0842350A1/fr
Application granted granted Critical
Publication of EP0842350B1 publication Critical patent/EP0842350B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • 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
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/20—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted
    • F01D17/22—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted the operation or power assistance being predominantly non-mechanical

Definitions

  • the invention relates to a control system for speed control of a turbine for generating electrical current with a first control structure, which is used for speed control during idle and / or island operation of the turbine, and a method for controlling the speed of a turbine during load shedding.
  • load jump devices can be realized.
  • these load jump devices bring about an immediate closing of a control valve regulating the rotational speed, the duration of the control valve's keeping closed from the level of the load shedding, that is to say from the reduction in the electrical power generated by the turbine and the associated generator , depends.
  • the speed control of the turbine is taken over by the speed controller. This regulates the speed during idle operation and during island operation of the turbine, that is to say in the case in which no electrical power is delivered to a power supply network.
  • the turbine is coupled to the generator, so that the speed of the turbine is determined by the nominal speed (synchronous speed) and the speed controller of the control, for example the combustion Supply of material in a gas turbine or the supply of steam in a steam turbine.
  • DE-AS 1 296 657 describes an electrohydraulic controller for the main steam valve of a steam turbine.
  • the main steam valve is regulated by an opening regulator depending on its position.
  • Either a variable dependent on the speed or a variable dependent on the power serves as the setpoint of the control.
  • a load step relay not specified, is used for this.
  • GB 2 011 126 A describes a control system of a gas turbine in which a fuel supply valve is controlled with a PI controller.
  • This is a control system which is the leader in the purely network operation of the gas turbine system and is designed in such a way that it ensures appropriate readjustment in the event of load changes.
  • Such control systems have the conflict that the integral part requires a long time constant for a good quality of the control and a short time constant for a reaction as quickly as possible to a change in the load of the gas turbine.
  • Speed ie the speed is adjusted as quickly as possible to the required constant speed by superimposing the speed difference signal on a constant signal. This accelerates the integrator's response to the difference signal.
  • the function generator number difference signal .an For the regulation of the speed, the function generator thus reduces the speed to a change corresponding to the non-zero speed difference signal, so that the quantity of fuel supplied is reduced via the fuel supply valve.
  • DE 26 27 591 B2 specifies a control device for turbines with a speed controller and a power controller.
  • the two controllers are connected to a minimum selection structure and are tracked one after the other while the turbine is operating.
  • the minimum selection structure selects the respectively smaller value of the speed controller or the power controller and feeds it to a proportional element which generates a valve control value.
  • the speed controller is designed so that when a sudden load cut-off occurs, the resulting increase in the speed of the turbine is kept small, so that there is in particular an increase of only about 1% compared to the operating speed.
  • the only embodiment specifically described is a speed controller which has a proportional, an integral and a differential component.
  • the output of the speed controller is immediately controlled downwards via the differential component, and the turbine is adjusted to a defined number of revolutions.
  • the number of revolutions increased during load shedding is thus immediately reduced again by the differential part.
  • the line frequency is fed directly to the differential part and only the proportional and the integral part the difference between the set frequency and the line frequency.
  • the object of the invention is to provide a uniform and simple control system without an additional load step device for a turbine, which prevents the turbine from closing quickly when a load is shed.
  • Another task of The invention consists in specifying a method for regulating the speed when a turbine is shedding loads.
  • the first-mentioned object is achieved by a control system for controlling the speed of a turbine for generating electrical current with a first control structure with a PI controller, which can be connected to an actuator serving to control the speed and when the engine is idling and / or isolated Turbine is used for speed control and, in the event of a load shedding, supplies the actuator with a closing signal, the first control structure being able to be supplied with a deviation signal which is dependent on the difference between the setpoint value and the actual value of the speed.
  • the P controller of the first control structure preferably has a proportionality constant such that when the deviation signal is present with a predefinable minimum size, the output signal of the I controller assumes the value zero.
  • control system with the first control structure ensures that without additional devices or electrical
  • the PI controller is suitable both for speed control of the turbine during idling and / or island operation and also for control of the actuator, so that after a load shedding, this is brought into a predefinable position immediately by a closing signal.
  • the actuator remains in this position for a period of time determined by the amount of load shedding, and after this period of time it is adjusted to a position required for idling and / or island operation by an increase in the output signal of the first control structure.
  • a corresponding deviation signal it can be achieved that the integrator is integrated down to the value zero and remains at this value during the grid operation of the turbine.
  • the first control structure does not control the actuator, but constantly receives a non-zero deviation signal, which means that the first control structure is in an overdriven state.
  • the output signal of the first control structure is limited by a predeterminable maximum output signal value. This maximum output signal value is dominated by the output signal of the P controller. If the proportionality constant K1 of the P controller is selected such that the product of the proportionality constant and the deviation signal is greater than or equal to the maximum output signal of the first control structure, the output signal of the I controller is automatically limited to zero. This ensures that the integral portion of the first control structure has the value zero when a load shedding occurs.
  • the first control structure delivers an output signal immediately after the load shedding occurs, which also has the value zero.
  • This "zero" output signal is therefore also immediately present after the load shedding on the actuator, which thereby immediately assumes its predetermined position, in particular a closed position.
  • the deviation signal is made zero, for example, by setting the setpoint value of the speed to the value of the synchronous speed, which corresponds to the actual value of the speed during mains operation and when a load shedding occurs:
  • the speed is regulated via the first control structure.
  • the time period in which the actuator remains in the predeterminable position, in particular a closed position depends on the level of the load shedding, in particular which are proportional to this.
  • the first control structure executes a speed control in such a way that the predetermined target value, in particular the synchronous speed of the turbine, is reached. After a load shedding, the speed of the turbine rises above the synchronous speed and drops again after reaching a maximum value.
  • the actuator is actuated via the first control structure, for example a control valve is opened again, so that the rotational speed is dependent on the parameters and the control algorithm (PI algorithm) of the first control structure Synchronous speed is adjusted.
  • PI algorithm control algorithm
  • the control system preferably has a second control structure and a correction value structure.
  • the correction value structure is connected to the first control structure ⁇ and to the second control structure ⁇ so that, when idling and / or isolated operation, the output signal of the second control structure is updated to the value of the output signal of the first control structure.
  • the output signals of the first and second control structures are identical at all times during idle and / or isolated operation, so that when switching to mains operation, the actuator, which is connected to the second control structure in network operation and to the first control structure in island operation , that the same output signal is supplied.
  • the second object is achieved by a method for regulating the speed of a turbine in the event of a load shedding, in that a first control structure, which serves to regulate the speed during idle and / or island operation and which has a PI controller, receives a deviation signal during network operation - is carried out so that the output signal of the I controller assumes the value zero, and if a load shedding occurs, the deviation signal is set to the value zero and the output signal Signal of the PI controller is fed to an actuator for regulating the speed.
  • the method has the advantage that the speed is used in a single control structure, both at idle and / or in-line operation and when shedding loads, to avoid a rapid shutdown of the turbine.
  • a suitable choice of the parameters of the PI controller ensures that the deviation signal applied to the first control structure during network operation overrides the first control structure in such a way that the portion of the I controller in the output signal of the first control structure is zero.
  • the actuator can be, for example, a control valve which, when an input signal with the value zero is present, goes into a minimum opening position, so that the speed of the turbine is limited to a value which is below the maximum permissible value. This effectively prevents the turbine from closing quickly when the load is shed.
  • the method is suitable for both gas and steam turbines, wherein in a gas turbine the actuator controlled by the first control structure is a control valve which serves to regulate the fuel supply.
  • the actuator is a control valve which serves to regulate the steam supply. Exemplary embodiments for the control system and for the method for controlling the speed of a turbine are described in more detail with reference to the drawing.
  • FIG. 1 gives a schematic structure of the control system
  • FIG. 2 shows the course over time of the setpoint value of the speed, the actual value of the speed and the stroke of a control valve serving to regulate the speed.
  • the control system 1 shows a control system 1 for controlling a gas turbine in network operation and in the event of load shedding and idling and / or island operation.
  • the control system 1 has a first control structure 2 which contains a PI controller 4 and which consists of a P controller 5 (proportionality constant K1) and an I controller 6.
  • the control system 1 also contains a second control structure 7, which has a P controller (proportionality constant K2).
  • the first control structure 2 and the second control structure 7 are each connected to a generator power switch 9, which is connected via a minimum selection device 11 to an actuator 3 for regulating the speed of the turbine.
  • the first control structure 2 is also connected to a correction value structure 8.
  • a limit signal Y 3MI N is also present at the minimum selection device 11, which limits the actuation of the actuator 3.
  • the power control takes place via the second control structure 7.
  • the power switch 9 switches the second control structure 7 to the actuator 3 via the device 11.
  • the speed of the gas turbine is thus at its synchronous value.
  • the power control takes place in such a way that the difference x from a setpoint value W2 of the speed and from the actual value W1, the synchronous value, is supplied to the second control structure 7.
  • This difference value x represents a deviation signal.
  • the first control structure 2 and supplied to both controllers 5,6.
  • This deviation signal leads to an overload of the first control structure 2, which is limited by its limiting value Y1max.
  • the output signals Y p , Yi of the P controller 5 or de I controller 6 are added.
  • the sum forms the output signal Y1 of the first control structure 2.
  • the output signal Yp of the P controller 5 corresponds precisely to the restriction value Ylmax of the first control structure 2.
  • the I controller 6 By overdriving and / or the choice of the proportionality constant K1 is integrated by the I controller 6 towards zero, so that its initial value Yi becomes zero.
  • the difference between this setpoint W2 and the actual value Wl is amplified by the P controller 7 and fed to the actuator 3.
  • the setpoint W2 can be preset to the synchronous speed of the turbine via a setpoint switch 12.
  • the setpoint value W2 of the rotational speed is set to the synchronous value, so that the actual value W1 and the setpoint value W2 match, so that the difference x between the two values, that is to say the deviation signal, is just zero.
  • the power switch 9 is switched so that the first control structure 2 is connected to the actuator 3.
  • the control structure 2 which is constantly on standby during network operation, thus takes over the speed control of the gas turbine. Since the deviation signal X has the value zero immediately after the load shedding has been recognized, an input signal with the value zero is present both at the P controller 5 and at the I controller 6.
  • the output signal Yp of the P controller 5 thus has also the value zero; the output signal Yi of the I controller 6 has the value zero anyway due to the foregoing.
  • the output signal Y1 of the first control structure 2 thus also has the value zero.
  • This value zero is fed to the actuator 3 as an input signal.
  • This actuator 3 is a control valve which controls the fuel supply to the gas turbine. When the "zero" output signal of the first control structure 2 is applied, it goes to a minimum opening position that has been set in advance.
  • FIG. 2 does not show the temporal course of the setpoint W2 of the speed, the actual value Wl of the speed and the stroke Z of the control valve 3, not shown to scale.
  • all three values are constant, with the setpoint W2 the speed is greater than the actual value (the synchronous value).
  • the setpoint value W2 is suddenly reduced to the synchronous value (corresponds to the actual value W1 at this time).
  • the setpoint switch 12 is closed.
  • the stroke Z of the control valve 3, as described above also drops almost suddenly to a predetermined value.
  • the stroke Z of the control valve 3 remains limited to the predetermined minimum value in a controlled manner via the first control structure 2.
  • the deviation signal X becomes positive and the first control structure 2 begins, the stroke Z of the control valve 3 to be changed so that the speed is adjusted to the synchronous value.
  • the output signal Y1 of the first control structure 2 is supplied to the correction setpoint structure 8, a correction setpoint dw formed therein being additionally supplied to the deviation signal X of the second control structure 7.
  • the structure 8 has a P controller 13, whose proportionality constant I / k2 has the reciprocal value of the proportionality constant K2 of the P controller of the second control structure 7.
  • the output value of the P controller 13 is fed to a holding element 14, so that when the mains switch (not shown) and generator circuit breaker 9 are switched on simultaneously for mains operation of the turbine, the output value is recorded.
  • the hold signal emitted to the hold element 14 is generated via a logic “and” element 15, which is supplied with a control signal 16, 17 in accordance with the respective position of the power switch and the generator power switch 9. It is hereby achieved that the output signal of the second control structure 7 is kept constantly at the value of the output signal Y1 of the first control structure 2 during idle and / or island operation of the gas turbine. When the power switch 9 is switched to mains operation, it is thus ensured that the speed is not changed by the switching, in particular no speed jump occurs.
  • control system 1, the first control structure 2, the correction value structure 8 and the second control structure 7 can be implemented as electrical or electronic components, as integrated circuits and / or software circuits.
  • the invention is characterized in that the mastery of load shedding is achieved without an additional load shedding device.
  • the control after detection of a load shedding is fully constantly adopted by the first rule structure. This also serves to control the speed of the turbine during idling and / or island operation.
  • the control structure has a PI controller, the integral part of which is pressed to the value zero during normal network operation. This is preferably achieved in that the first control structure is continuously controlled during the network operation by a deviation signal which corresponds to the deviation between a predetermined target and actual value of the speed. This deviation signal is set to the value zero when a load shedding occurs, so that the input and the output signal of the first control structure are also just zero.
  • the output signal of the first control structure is transmitted to an actuator of the turbine, which is used to regulate the speed and, when the output signal is present, goes to a predetermined minimum control position with the value zero.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
  • Control Of Eletrric Generators (AREA)

Abstract

Ce système (1) de régulation du régime d'une turbine génératrice de courant électrique comprend une première structure de régulation (1) qui peut être reliée à un organe de régulation (3) qui sert à réguler le régime de la turbine pendant sa marche à vide et/ou isolée. Un signal d'écart (X) dépendant de la différence entre la valeur nominale (W2) et la valeur réelle (W1) du régime peut en outre être transmis à la structure de régulation (2). Pendant un délestage, la première structure de régulation (2) transmet un signal de fermeture à l'organe de régulation (3) en fonction du signal d'écart (X). La première structure de régulation (2) associe ainsi la fonction de régulation du régime pendant la marche à vide et/ou isolée de la turbine à une fonction évitant l'arrêt rapide de la turbine pendant un délestage. L'invention concerne également un procédé de régulation du régime d'une turbine pendant un délestage.
EP96924760A 1995-08-03 1996-07-22 Systeme de regulation du regime d'une turbine et procede de regulation du regime d'une turbine pendant un delestage Expired - Lifetime EP0842350B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19528601A DE19528601C2 (de) 1995-08-03 1995-08-03 Regeleinrichtung zur Drehzahlregelung einer Turbine sowie Verfahren zur Regelung der Drehzahl einer Turbine bei Lastabwurf
DE19528601 1995-08-03
PCT/DE1996/001342 WO1997006351A1 (fr) 1995-08-03 1996-07-22 Systeme de regulation du regime d'une turbine et procede de regulation du regime d'une turbine pendant un delestage

Publications (2)

Publication Number Publication Date
EP0842350A1 true EP0842350A1 (fr) 1998-05-20
EP0842350B1 EP0842350B1 (fr) 1999-01-20

Family

ID=7768639

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96924760A Expired - Lifetime EP0842350B1 (fr) 1995-08-03 1996-07-22 Systeme de regulation du regime d'une turbine et procede de regulation du regime d'une turbine pendant un delestage

Country Status (6)

Country Link
EP (1) EP0842350B1 (fr)
JP (1) JP4073956B2 (fr)
CZ (1) CZ29998A3 (fr)
DE (2) DE19528601C2 (fr)
RU (1) RU2156865C2 (fr)
WO (1) WO1997006351A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6116853A (en) * 1998-11-13 2000-09-12 Siemens Aktiengesellschaft Method and apparatus for checking the operating reliability of a turbine during load shedding
DE10328932A1 (de) * 2003-06-27 2005-01-13 Alstom Technology Ltd Verfahren und Vorrichtung zum Erfassen eines Lastabwurfes zwischen einer elektrische Energie erzeugenden Rotationsmaschine und einem zur Stromversorgung an die Rotationsmaschine angeschlossenen Versorgungsnetzwerkes
DE102007045167B4 (de) 2007-09-20 2020-07-02 Man Energy Solutions Se Regelsystem und -verfahren zur Regelung einer Dampfturbine
JP5888947B2 (ja) * 2011-11-25 2016-03-22 三菱日立パワーシステムズ株式会社 弁制御装置、ガスタービン、及び弁制御方法
RU2625552C1 (ru) * 2016-06-17 2017-07-14 федеральное государственное бюджетное образовательное учреждение высшего образования "Национальный исследовательский университет "МЭИ" (ФГБОУ ВО "НИУ "МЭИ") Способ регулирования газовых турбин при глубоких снижениях частоты в энергосистеме
RU2669146C1 (ru) * 2017-10-31 2018-10-08 Акционерное общество "Проектно-конструкторское бюро "Автоматика" Электрогидравлическая система автоматического регулирования частоты вращения ротора паровой турбины привода электрогенератора судовой гребной электрической установки
RU2670470C1 (ru) * 2017-11-13 2018-10-23 Акционерное общество "Проектно-конструкторское бюро "Автоматика" Гидросистема управления клапанами паровой турбины

Family Cites Families (6)

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DE1401456A1 (de) * 1962-03-15 1968-10-24 Siemens Ag Einrichtung fuer Drehzahlregelung von Turbinen
NL296751A (fr) * 1962-08-18 1900-01-01
DE1601849C3 (de) * 1968-01-11 1975-04-24 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt Regeleinrichtung für Turbinen mit Drehzahl- und Leistungsregelung
DE2627591B2 (de) * 1976-06-19 1981-04-16 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Regeleinrichtung für Turbinen mit Drehzahl- und Leistungsregelung
JPS5487319A (en) * 1977-12-23 1979-07-11 Nissan Motor Co Ltd Fuel control equipment of gas turbine
US4280059A (en) * 1979-12-26 1981-07-21 United Technologies Corporation Detecting power loss in free turbines

Non-Patent Citations (1)

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Title
See references of WO9706351A1 *

Also Published As

Publication number Publication date
DE19528601A1 (de) 1997-02-06
RU2156865C2 (ru) 2000-09-27
DE19528601C2 (de) 1998-07-09
JPH11510579A (ja) 1999-09-14
WO1997006351A1 (fr) 1997-02-20
JP4073956B2 (ja) 2008-04-09
DE59601196D1 (de) 1999-03-04
EP0842350B1 (fr) 1999-01-20
CZ29998A3 (cs) 1998-05-13

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