WO2018007464A1 - Turbine speed and acceleration limiter - Google Patents

Turbine speed and acceleration limiter Download PDF

Info

Publication number
WO2018007464A1
WO2018007464A1 PCT/EP2017/066817 EP2017066817W WO2018007464A1 WO 2018007464 A1 WO2018007464 A1 WO 2018007464A1 EP 2017066817 W EP2017066817 W EP 2017066817W WO 2018007464 A1 WO2018007464 A1 WO 2018007464A1
Authority
WO
WIPO (PCT)
Prior art keywords
speed
acceleration
turbine
steam
threshold 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.)
Ceased
Application number
PCT/EP2017/066817
Other languages
French (fr)
Inventor
Rémi Soriano
Xavier Callier
Jean Luc LABRUNIE
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.)
GE Vernova GmbH
Original Assignee
General Electric Technology GmbH
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 General Electric Technology GmbH filed Critical General Electric Technology GmbH
Priority to US16/315,798 priority Critical patent/US20190301307A1/en
Priority to CN201780042546.5A priority patent/CN109415949A/en
Priority to JP2018567616A priority patent/JP2019525050A/en
Publication of WO2018007464A1 publication Critical patent/WO2018007464A1/en
Anticipated expiration legal-status Critical
Ceased 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
    • 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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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
    • F01K7/26—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 the turbines having inter-stage steam accumulation
    • F01K7/28—Control means specially adapted therefor
    • 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
    • F01D17/02—Arrangement of sensing elements
    • F01D17/08—Arrangement of sensing elements responsive to condition of working-fluid, e.g. pressure
    • 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
    • F01D21/02—Shutting-down responsive to overspeed
    • 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
    • F01D21/12—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for responsive to temperature
    • 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
    • F01K1/00—Steam accumulators
    • F01K1/08—Charging or discharging of accumulators with steam
    • 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
    • F01K1/00—Steam accumulators
    • F01K1/16—Other safety or control means
    • 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
    • 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
    • F01K7/18—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 the turbine being of multiple-inlet-pressure type
    • F01K7/20—Control means specially adapted therefor
    • 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
    • F01K7/22—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 the turbines having inter-stage steam heating
    • F01K7/24—Control or safety means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
    • F02C9/26—Control of fuel supply
    • F02C9/28—Regulating systems responsive to plant or ambient parameters, e.g. temperature, pressure, rotor speed
    • 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

Definitions

  • the present invention generally relates to power plant steam turbines and more particularly to a method for controlling steam admission into such a steam turbine.
  • a power plant steam turbine is a device which converts thermal energy o f pressurized steam to mechanical energy.
  • the thermal energy is obtained by the production of steam by a boiler.
  • the resulting steam flow is thus supplied to the steam turbine at the required pressure and temperature.
  • the turbine converts the steam flow into a torque which is used for driving a rotor of an electric generator for the production of electrical energy.
  • the rotor of the electric generator is driven by means of a turbine shaft that interconnects the rotor with the steam turbine.
  • the electric generator is coupled with an alternating current electrical grid for distributing the produced electrical energy to the consumers through a plurality o f transmission lines.
  • the electrical generator and the electrical grid are synchronized such that the frequency o f the electrical generator matches the frequency of the electrical grid.
  • the steam supplied by the boiler, enters a high pressure steam casing.
  • the admission in the high pressure casing is done through stop valves and control valves .
  • the steam After steam expansion in the high pressure casing, the steam is sent to moisture-separator reheaters pulling moisture and reheating the steam for preventing corrosion and erosion.
  • the dried and reheated steam is thus admitted in a reduced pressure casing, which is generally an intermediate pressure steam casing, through intermediate pressure stop and control valves, and then admitted in one or more low pressure steam casings .
  • Certain steam turbines are not provided with intermediate pressure casing and the steam passes directly from the moisture-separator reheaters to the low pressure casings through low pressure stop and control valves .
  • the resistive torque applied by the electric generator decreases or disappears and the steam flow passing through the turbine leads to an acceleration of the turbine.
  • the turbine overspeed trip caused by the torque unbalance between the thermal power and the electrical lo ad can lead to mechanical constraints on the shaft line and to an unavailability o f the turbine- generator group .
  • Another so lution consists in sending closing and re-opening orders to the control valves.
  • the disadvantage of this so lution lies on the time to recover as well as the control valves stress .
  • the present invention intends to overcome these disadvantages by providing a method for controlling admission steam into power plant steam turbine, the method being able to prevent an excessive speed and/or acceleration o f the turbine which may lead to the turbine unavailability for the grid.
  • the present invention thus proposes a method for controlling steam admission into a steam turbine, the turbine comprising a high pressure casing, at least one reduced pressure casing and an admission steam control system, the high pressure casing and at least one reduced pressure casing comprising control valves for steam admission.
  • the steam admission control system manages the fo llowing steps : determining at least one o f the speed and the acceleration o f the turbine; comparing the determined speed and/or acceleration respectively with a predefined speed thresho ld value and a predefined acceleration threshold value; when the determined speed and/or acceleration are superior to the predefined threshold value, the control system activates a speed and acceleration limiter.
  • the activated speed and acceleration limiter may impose control valve opening setpoints, depending on the determined speed and/or acceleration values, to the high pressure and reduced pressure control valves in order to regulate the steam admission into the turbine .
  • the speed and acceleration limiter can act by a fast and appropriate response.
  • control valve opening setpoints to the control valves may be performed through control valve position-loop cards.
  • control valve opening setpoints may depend on the turbine steam flow demand.
  • the steam flow demand is determined using parameters including at least one of the rotating speed of the turbine, the load, the live steam pressure and the turbine operating mode .
  • the speed threshold value may be chosen according to the turbine nominal speed.
  • the acceleration threshold value may be chosen according to the turbine maximum acceleration.
  • the speed and acceleration limiter is deactivated when the turbine speed and acceleration drop below the thresho ld value since the situation is normalized.
  • control system may be activated during a transient o f the turbine during which an excessive speed and/or acceleration are the mo st likely to occur.
  • Another obj ect of the invention relates to a steam turbine comprising a high pressure casing, at least one reduced pressure casing and a steam admission control system, the high pressure casing and at least one reduced pressure casing comprising control valves for steam admission.
  • the steam admission control system is configured to determine at least one of the speed and the acceleration o f the turbine, compare the determined speed and/or acceleration respectively with a predefined speed thresho ld value and a predefined acceleration thresho ld value, and activate a speed and acceleration limiter when the determined speed and/or acceleration are superior to the threshold value
  • hydraulic actuators are provided to perform the opening and closing of the control valves, the hydraulic actuators comprising an electro-hydraulic amplifier.
  • hydraulic actuators are provided to perform the opening and the closing of the control valves, the hydraulic actuators comprising a hydraulic fast closing device for emergency closing o f the associated control valves.
  • Figure 1 is a schematic view o f a power plant steam turbine for use in a method according to an embodiment o f the invention.
  • Figure 2 illustrates the steps performed by a steam admission control system of the steam turbine of figure 1 .
  • a power plant steam turbine 1 comprises a high pressure steam casing 2 and at least on reduced pressure casings.
  • the reduced pressure casings correspond to an intermediate steam casing 3 and three low pressure steam casings 4, 5 and 6.
  • the steam turbine is also provided with stop valves 7 and control valves 8 upstream o f the high pressure casing 2, and stop valves 9 and control valves 10 upstream of the intermediate pressure casing 3.
  • Two moisture-separator reheaters 1 1 and 12 are located upstream o f the intermediate pressure stop valves 9 and control valves 10.
  • the steam supplied by a boiler (not shown here), enters the high pressure steam casing 2.
  • the admission in the high pressure casing is done through high pressure stop valves 7 and high pressure control valves 8.
  • the steam is sent to moisture-separator reheaters 1 1 and 12.
  • the steam is thus admitted in the intermediate pressure casing 3 , through the intermediate pressure stop valves 9 and the intermediate pressure control valves 10 , and then admitted in the low pressure casings 4, 5 and 6.
  • the steam turbine 1 comprises a steam admission control system 13 which, when the turbine is running and advantageously when a transient occurs, is activated.
  • control system 1 3 determines one or both of the turbine speed 14 and the turbine acceleration 15.
  • control system 13 compares the determined speed with a predefined speed threshold value 16 and compares the determined acceleration with a predefined acceleration thresho ld value 17.
  • the control system 13 activates a speed and acceleration limiter 20.
  • the activated speed and acceleration limiter 20 imposes advantageously control valves opening setpoints 21 , 22 to the high pressure control valves 8 and to the reduced pressure control valves which are, in that examp le, the intermediate pressure control valves 10.
  • the control valves opening setpoints 21 , 22 are preferably elaborated depending on the turbine steam flow demand 23.
  • control system 13 may determine a steam flow demand 23 in function of various turbine parameters 24 and the determined speed and/or acceleration values.
  • the parameters 24 may include, for example, the rotating speed o f the turbine, the load, the live steam pressure, the turbine operating mode, limitations and runbacks, and allows the determination o f a speed and/or load demand.
  • the steam admission control system 13 comprises one position-loop card per control valve.
  • the position-loop cards 26 for the high pressure contro l valves 8 and the position-loop cards 27 for the intermediate pressure control valves 10 are respectively configured to perform the steps of imposing the opening setpoint 21 to the high pressure control valves 8 and imposing the opening setpoint 22 to the intermediate pressure control valves 10.
  • control valves 8, 10 are preferably performed by hydraulic actuators comprising an electro- hydraulic amplifier for the control of the valves and a hydraulic fast closing device for emergency closing of the valves 8, 10. Then the turbine may be configured to close the control valves 8, 10 either by the electro- hydraulic amplifier or the hydraulic fast closing device.
  • the speed and acceleration limiter 20 is preferably deactivated, and the control valves 8, 10 positions may be determined by the steam flow demand 23, itself determined by the parameters 24.
  • the turbine 1 In contrast, during a transient such as a load variation, a grid fault or a switch to house load operating mode, leading to a torque unbalance between the electrical load and the thermal power, the turbine 1 generally accelerates and its speed increases.
  • the speed and acceleration limiter 20 is only activated if the speed and/or acceleration values exceed the predefined speed and acceleration threshold values.
  • the speed and acceleration limiter 20 limits the speed and acceleration advantageously by imposing control valves opening setpoints 21, 22 and thus quickly closing the high pressure control valves 8 and the intermediate pressure control valves 10.
  • the speed and acceleration limiter 20 may be configured to derivate the speed continuously in order to calculate the corresponding acceleration and compares the obtained value with the predefined threshold value.
  • the acceleration predefined threshold value is around 50% of the turbine maximum acceleration.
  • the speed and acceleration limiter 20 decreases the steam flow demand 23 according to the deviation between the determined acceleration and the acceleration threshold value.
  • the speed and acceleration limiter 20 compares the turbine speed with the speed threshold value. Typically, the speed threshold value is 107% of the turbine nominal speed. Thus, the speed and acceleration limiter 20 decreases the steam flow demand 23 according to the deviation between the determined speed and the speed threshold value. Once the situation is normalized, the speed and acceleration values dropped below the speed and acceleration threshold. Thus the speed and acceleration limiter 20 may be deactivated and thus no longer control the high pressure control valves 8 and the intermediate pressure control valves 10.
  • the present invention provides a method allowing regulation of the steam supplied to the high pressure, intermediate pressure and low pressure casings 2 , 3 , 4, 5 , 6, and thus avoiding an excessive speed of the turbine 1 which could lead to the turbine unavailability for the grid.
  • the method allows ensuring the safety of the shaft line o f the turbine 1 by controlling the shaft-line speed, the lo ad of the turbo-generator and the live steam pressure by a fast and appropriate response.
  • the speed and acceleration limiter 20 realizes a realistic analysis by checking the speed variations, that is to say the result of the unbalance between the power and the lo ad. This improves the availability o f the turbine 1 by making the corrective actions on the result rather than a prediction.

Landscapes

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

Abstract

Method for controlling steam admission into a steam turbine (1), the turbine (1) comprising a high pressure casing (2), at least one reduced pressure casing (3, 4, 5, 6) and an admission steam control system (13), the high pressure casing (2) and at least one reduced pressure casing (3) comprising control valves (8, 10) for steam admission. The steam admission control system (13) manages the following steps: determining at least one of the speed (14) and the acceleration (15) of the turbine (1); comparing the determined speed and/or acceleration respectively with a predefined speed threshold value (16) and a predefined acceleration threshold value (17); when the determined speed and/or acceleration are superior to the predefined threshold value (18, 19), the control system (13) activates a speed and acceleration limiter (20).

Description

Turbine speed and acceleration limiter
The present invention generally relates to power plant steam turbines and more particularly to a method for controlling steam admission into such a steam turbine.
Typically, a power plant steam turbine is a device which converts thermal energy o f pressurized steam to mechanical energy. The thermal energy is obtained by the production of steam by a boiler. The resulting steam flow is thus supplied to the steam turbine at the required pressure and temperature.
The turbine converts the steam flow into a torque which is used for driving a rotor of an electric generator for the production of electrical energy. Particularly, the rotor of the electric generator is driven by means of a turbine shaft that interconnects the rotor with the steam turbine.
Commonly, the electric generator is coupled with an alternating current electrical grid for distributing the produced electrical energy to the consumers through a plurality o f transmission lines. In order to obtain a delivery of electrical energy from the electric generator to the electrical grid, it is important that the electrical generator and the electrical grid are synchronized such that the frequency o f the electrical generator matches the frequency of the electrical grid.
The steam, supplied by the boiler, enters a high pressure steam casing. The admission in the high pressure casing is done through stop valves and control valves .
After steam expansion in the high pressure casing, the steam is sent to moisture-separator reheaters pulling moisture and reheating the steam for preventing corrosion and erosion.
The dried and reheated steam is thus admitted in a reduced pressure casing, which is generally an intermediate pressure steam casing, through intermediate pressure stop and control valves, and then admitted in one or more low pressure steam casings . Certain steam turbines are not provided with intermediate pressure casing and the steam passes directly from the moisture-separator reheaters to the low pressure casings through low pressure stop and control valves . In case of a transient, such as a switch to house load turbine operating mo de, a switch to load rej ection or when a grid short circuit occurs, the resistive torque applied by the electric generator decreases or disappears and the steam flow passing through the turbine leads to an acceleration of the turbine.
The turbine overspeed trip caused by the torque unbalance between the thermal power and the electrical lo ad can lead to mechanical constraints on the shaft line and to an unavailability o f the turbine- generator group .
In the state of the art, solutions consists in keeping the intermediate pressure admission valves, or low pressure admission valves if there is no intermediate pressure casing, open from turbine start-up from a load between 5 to 40 % of the nominal lo ad. Predefined load profiles are used to reduce instability. Nevertheless, only a limited number o f profiles to characterize the transient are defined. The torque unbalance transients are often sudden, unpredictable and their magnitudes and pro files are difficult to characterize. Consequently, this so lution does not allow to respond to all type o f transient.
Another so lution consists in sending closing and re-opening orders to the control valves. However, the disadvantage of this so lution lies on the time to recover as well as the control valves stress .
Furthermore, these so lutions are not appropriate or sufficient for turbines with large dead vo lumes downstream intermediate pressure valves, especially between moisture-separator reheaters and intermediate pressure casing, and between intermediate pressure casing and low pressure casing.
Consequently, the present invention intends to overcome these disadvantages by providing a method for controlling admission steam into power plant steam turbine, the method being able to prevent an excessive speed and/or acceleration o f the turbine which may lead to the turbine unavailability for the grid.
The present invention thus proposes a method for controlling steam admission into a steam turbine, the turbine comprising a high pressure casing, at least one reduced pressure casing and an admission steam control system, the high pressure casing and at least one reduced pressure casing comprising control valves for steam admission.
The steam admission control system manages the fo llowing steps : determining at least one o f the speed and the acceleration o f the turbine; comparing the determined speed and/or acceleration respectively with a predefined speed thresho ld value and a predefined acceleration threshold value; when the determined speed and/or acceleration are superior to the predefined threshold value, the control system activates a speed and acceleration limiter.
Advantageously, the activated speed and acceleration limiter may impose control valve opening setpoints, depending on the determined speed and/or acceleration values, to the high pressure and reduced pressure control valves in order to regulate the steam admission into the turbine . The speed and acceleration limiter can act by a fast and appropriate response.
More advantageously, the step of imposing control valve opening setpoints to the control valves may be performed through control valve position-loop cards.
Besides, the control valve opening setpoints may depend on the turbine steam flow demand.
Preferably, the steam flow demand is determined using parameters including at least one of the rotating speed of the turbine, the load, the live steam pressure and the turbine operating mode .
In another embodiment, the speed threshold value may be chosen according to the turbine nominal speed.
Advantageously, the acceleration threshold value may be chosen according to the turbine maximum acceleration.
More advantageously, the speed and acceleration limiter is deactivated when the turbine speed and acceleration drop below the thresho ld value since the situation is normalized.
Besides, the control system may be activated during a transient o f the turbine during which an excessive speed and/or acceleration are the mo st likely to occur.
Another obj ect of the invention relates to a steam turbine comprising a high pressure casing, at least one reduced pressure casing and a steam admission control system, the high pressure casing and at least one reduced pressure casing comprising control valves for steam admission.
Besides, the steam admission control system is configured to determine at least one of the speed and the acceleration o f the turbine, compare the determined speed and/or acceleration respectively with a predefined speed thresho ld value and a predefined acceleration thresho ld value, and activate a speed and acceleration limiter when the determined speed and/or acceleration are superior to the threshold value
Preferably, hydraulic actuators are provided to perform the opening and closing of the control valves, the hydraulic actuators comprising an electro-hydraulic amplifier.
More preferably, hydraulic actuators are provided to perform the opening and the closing of the control valves, the hydraulic actuators comprising a hydraulic fast closing device for emergency closing o f the associated control valves.
Other advantages and features of the invention will appear from the detailed description of an embodiment of the invention, which is a non limiting example, illustrated on the appended drawings of which:
Figure 1 is a schematic view o f a power plant steam turbine for use in a method according to an embodiment o f the invention; and
Figure 2 illustrates the steps performed by a steam admission control system of the steam turbine of figure 1 .
As shown on Figure 1 , a power plant steam turbine 1 comprises a high pressure steam casing 2 and at least on reduced pressure casings. In the illustrated examp le, the reduced pressure casings correspond to an intermediate steam casing 3 and three low pressure steam casings 4, 5 and 6.
The steam turbine is also provided with stop valves 7 and control valves 8 upstream o f the high pressure casing 2, and stop valves 9 and control valves 10 upstream of the intermediate pressure casing 3.
Two moisture-separator reheaters 1 1 and 12 are located upstream o f the intermediate pressure stop valves 9 and control valves 10.
The steam, supplied by a boiler (not shown here), enters the high pressure steam casing 2. The admission in the high pressure casing is done through high pressure stop valves 7 and high pressure control valves 8. After steam expansion in the high pressure casing 2, the steam is sent to moisture-separator reheaters 1 1 and 12.
The steam is thus admitted in the intermediate pressure casing 3 , through the intermediate pressure stop valves 9 and the intermediate pressure control valves 10 , and then admitted in the low pressure casings 4, 5 and 6.
Furthermore, the steam turbine 1 comprises a steam admission control system 13 which, when the turbine is running and advantageously when a transient occurs, is activated.
As illustrated in figure 2, in a first step, the control system 1 3 determines one or both of the turbine speed 14 and the turbine acceleration 15.
In a second step, the control system 13 compares the determined speed with a predefined speed threshold value 16 and compares the determined acceleration with a predefined acceleration thresho ld value 17.
When the determined speed is superior to the predefined speed thresho ld value 1 8 and/or the determined acceleration is superior to the predefined acceleration thresho ld value 19 , the control system 13 activates a speed and acceleration limiter 20.
In order to regulate the steam admission into the turbine 1 and drop the speed and/or acceleration below the thresho ld values, the activated speed and acceleration limiter 20 imposes advantageously control valves opening setpoints 21 , 22 to the high pressure control valves 8 and to the reduced pressure control valves which are, in that examp le, the intermediate pressure control valves 10. The control valves opening setpoints 21 , 22 are preferably elaborated depending on the turbine steam flow demand 23.
In this regard, the control system 13 may determine a steam flow demand 23 in function of various turbine parameters 24 and the determined speed and/or acceleration values. The parameters 24 may include, for example, the rotating speed o f the turbine, the load, the live steam pressure, the turbine operating mode, limitations and runbacks, and allows the determination o f a speed and/or load demand.
In the illustrated embodiment, the steam admission control system 13 comprises one position-loop card per control valve. The position-loop cards 26 for the high pressure contro l valves 8 and the position-loop cards 27 for the intermediate pressure control valves 10 are respectively configured to perform the steps of imposing the opening setpoint 21 to the high pressure control valves 8 and imposing the opening setpoint 22 to the intermediate pressure control valves 10.
Moreover, the opening and closing of the control valves 8, 10 are preferably performed by hydraulic actuators comprising an electro- hydraulic amplifier for the control of the valves and a hydraulic fast closing device for emergency closing of the valves 8, 10. Then the turbine may be configured to close the control valves 8, 10 either by the electro- hydraulic amplifier or the hydraulic fast closing device.
In normal operation, the speed and acceleration limiter 20 is preferably deactivated, and the control valves 8, 10 positions may be determined by the steam flow demand 23, itself determined by the parameters 24.
In contrast, during a transient such as a load variation, a grid fault or a switch to house load operating mode, leading to a torque unbalance between the electrical load and the thermal power, the turbine 1 generally accelerates and its speed increases. The speed and acceleration limiter 20 is only activated if the speed and/or acceleration values exceed the predefined speed and acceleration threshold values. As a response, the speed and acceleration limiter 20 limits the speed and acceleration advantageously by imposing control valves opening setpoints 21, 22 and thus quickly closing the high pressure control valves 8 and the intermediate pressure control valves 10.
The speed and acceleration limiter 20 may be configured to derivate the speed continuously in order to calculate the corresponding acceleration and compares the obtained value with the predefined threshold value. Typically, the acceleration predefined threshold value is around 50% of the turbine maximum acceleration. Thus, the speed and acceleration limiter 20 decreases the steam flow demand 23 according to the deviation between the determined acceleration and the acceleration threshold value.
Furthermore, the speed and acceleration limiter 20 compares the turbine speed with the speed threshold value. Typically, the speed threshold value is 107% of the turbine nominal speed. Thus, the speed and acceleration limiter 20 decreases the steam flow demand 23 according to the deviation between the determined speed and the speed threshold value. Once the situation is normalized, the speed and acceleration values dropped below the speed and acceleration threshold. Thus the speed and acceleration limiter 20 may be deactivated and thus no longer control the high pressure control valves 8 and the intermediate pressure control valves 10.
Hence, the present invention provides a method allowing regulation of the steam supplied to the high pressure, intermediate pressure and low pressure casings 2 , 3 , 4, 5 , 6, and thus avoiding an excessive speed of the turbine 1 which could lead to the turbine unavailability for the grid.
The method allows ensuring the safety of the shaft line o f the turbine 1 by controlling the shaft-line speed, the lo ad of the turbo-generator and the live steam pressure by a fast and appropriate response.
The speed and acceleration limiter 20 realizes a realistic analysis by checking the speed variations, that is to say the result of the unbalance between the power and the lo ad. This improves the availability o f the turbine 1 by making the corrective actions on the result rather than a prediction.

Claims

1. Method for controlling steam admission into a steam turbine (1), the turbine (1) comprising a high pressure casing (2), at least one reduced pressure casing (3, 4, 5, 6) and an admission steam control system (13), the high pressure casing (2) and at least one reduced pressure casing (3) comprising control valves (8, 10) for steam admission, characterized in that the steam admission control system (13) manages the following steps:
determining at least one of the speed (14) and the acceleration (15) of the turbine (1);
comparing the determined speed and/or acceleration respectively with a predefined speed threshold value (16) and a predefined acceleration threshold value (17);
when the determined speed and/or acceleration are superior to the predefined threshold value (18, 19), the control system (13) activates a speed and acceleration limiter (20).
2. Method according to claim 1, wherein the activated speed and acceleration limiter (20) imposes control valve opening setpoints
(21, 22), depending on the determined speed and/or acceleration values, to the high pressure and reduced pressure control valves (8, 10) in order to regulate the steam admission into the turbine (1).
3. Method according to claim 2, wherein the control valve opening setpoints (21, 22) depend on the turbine (1) steam flow demand
(23).
4. Method according to claim 3, wherein, the steam flow demand (23) is determined using parameters (24) including at least one of the rotating speed of the turbine (1), the load, the live steam pressure and the turbine (1) operating mode.
5. Method according to claim 2, wherein the step of imposing control valve opening setpoints (21, 22) to the control valves (8, 10) is performed through control valve position-loop cards (26, 27).
6. Method according to any preceding claim, wherein the speed threshold value is chosen according to the turbine (1) nominal speed.
7. Method according to any preceding claim, wherein the acceleration threshold value is chosen according to the turbine ( 1 ) maximum acceleration.
8. Method according to any preceding claim, wherein the speed and acceleration limiter (20) is deactivated when the turbine ( 1 ) speed and acceleration drop below the threshold value.
9. Method according to any preceding claim, wherein the control system ( 13) is activated during a transient of the turbine ( 1 ) .
10. Steam turbine comprising a high pressure casing (2), at least one reduced pressure casing (3 , 4, 5 , 6) and a steam admission control system ( 13), the high pressure casing (2) and at least one reduced pressure casing (3) comprising control valves (8 , 10) for steam admission, characterized in that the steam admission control system ( 1 3 ) is configured to determine at least one of the speed ( 14) and the acceleration ( 15) of the turbine ( 1 ), compare the determined speed and/or acceleration respectively with a predefined speed threshold value ( 16) and a predefined acceleration threshold value ( 17), and activate a speed and acceleration limiter (20) when the determined speed and/or acceleration are superior to the threshold value ( 1 8 , 19) .
11. Steam turbine according to claim 10, wherein hydraulic actuators are provided to perform the opening and clo sing o f the contro l valves (8 , 10), the hydraulic actuators comprising an electro-hydraulic amplifier.
12. Steam turbine according to claim 10 or 1 1 , wherein hydraulic actuators are provided to perform the opening and the closing o f the control valves (8 , 10), the hydraulic actuators comprising a hydraulic fast closing device for emergency closing o f the associated control valves.
PCT/EP2017/066817 2016-07-08 2017-07-05 Turbine speed and acceleration limiter Ceased WO2018007464A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US16/315,798 US20190301307A1 (en) 2016-07-08 2017-07-05 Turbine speed and acceleration limiter
CN201780042546.5A CN109415949A (en) 2016-07-08 2017-07-05 Turbine trip speed and acceleration restrictor
JP2018567616A JP2019525050A (en) 2016-07-08 2017-07-05 Turbine speed acceleration limiter

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP16290133.4A EP3266987A1 (en) 2016-07-08 2016-07-08 Turbine speed and acceleration limiter
EP16290133.4 2016-07-08

Publications (1)

Publication Number Publication Date
WO2018007464A1 true WO2018007464A1 (en) 2018-01-11

Family

ID=56609822

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/066817 Ceased WO2018007464A1 (en) 2016-07-08 2017-07-05 Turbine speed and acceleration limiter

Country Status (5)

Country Link
US (1) US20190301307A1 (en)
EP (1) EP3266987A1 (en)
JP (1) JP2019525050A (en)
CN (1) CN109415949A (en)
WO (1) WO2018007464A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3049652B1 (en) * 2016-03-31 2020-03-06 Safran Aircraft Engines AIRCRAFT TURBOMACHINE WITH DISCHARGE DEVICE
US11428115B2 (en) * 2020-09-25 2022-08-30 General Electric Company Control of rotor stress within turbomachine during startup operation

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4412780A (en) * 1981-03-27 1983-11-01 General Electric Company Rate initial pressure limiter
EP2378083A2 (en) * 2010-04-13 2011-10-19 General Electric Company Double flow low-pressure steam turbine
GB2524582A (en) * 2014-03-28 2015-09-30 Mitsubishi Hitachi Power Sys Combined cycle gas turbine plant

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5167804A (en) * 1974-12-11 1976-06-11 Hitachi Ltd JOKITAABINNOKASOKUBOSHIHOHO OYOBI SONOSOCHI
US4166221A (en) * 1978-02-09 1979-08-28 Westinghouse Electric Corp. Overspeed protection controller employing interceptor valve speed control
JPS54155303A (en) * 1978-05-29 1979-12-07 Toshiba Corp Overspeed preventer for turbine
JP3166972B2 (en) * 1989-02-22 2001-05-14 株式会社日立製作所 Power plant control method and apparatus, and power plant
JP2854665B2 (en) * 1990-04-05 1999-02-03 株式会社東芝 Steam turbine controller
JPH10222203A (en) * 1997-02-10 1998-08-21 Mitsubishi Heavy Ind Ltd Digital controller
US20080098881A1 (en) * 2006-10-30 2008-05-01 General Electric Company Closed loop manual control system and method for an electrically operated hydraulic amplifier
CN100474201C (en) * 2007-01-30 2009-04-01 北京和利时系统工程有限公司 Method and device for restricting overspeed of a speed adjustment system
KR20130024537A (en) * 2011-08-31 2013-03-08 한국전력공사 Device and method for controlling overspeed of turbine
JP2013148040A (en) * 2012-01-20 2013-08-01 Toshiba Corp Apparatus and method for controlling steam turbine
CN103806959B (en) * 2012-11-14 2015-06-24 中国广东核电集团有限公司 Method and device for preventing disturbances to a steam turbine control system in a nuclear power plant
EP2848774A1 (en) * 2013-09-17 2015-03-18 Siemens Aktiengesellschaft Method for testing an overspeed protection system of a single-shaft system
CN103590858B (en) * 2013-11-19 2015-12-02 中国神华能源股份有限公司 Prevent the system and method that Power Plant turbine speed is ascended to heaven

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4412780A (en) * 1981-03-27 1983-11-01 General Electric Company Rate initial pressure limiter
EP2378083A2 (en) * 2010-04-13 2011-10-19 General Electric Company Double flow low-pressure steam turbine
GB2524582A (en) * 2014-03-28 2015-09-30 Mitsubishi Hitachi Power Sys Combined cycle gas turbine plant

Also Published As

Publication number Publication date
EP3266987A1 (en) 2018-01-10
CN109415949A (en) 2019-03-01
US20190301307A1 (en) 2019-10-03
JP2019525050A (en) 2019-09-05

Similar Documents

Publication Publication Date Title
CN101989745B (en) Method for early detection and anticipatory control of consumer-end load shedding in an electrical grid, and apparatus for carrying out the method
US20120183413A1 (en) Reactor Feedwater Pump Control System
US20120174584A1 (en) Power plant system having overload control valve
US9309779B2 (en) Steam turbine governing system for maintaining synchronization and process for performing the same
CA1193454A (en) Turbine high pressure bypass pressure control system
JP2015081589A (en) Steam turbine plant activation method
JP6396599B2 (en) Turbine control unit with thermal stress control device as main control device
JP2005520086A (en) Turbine operation method
CA2588879C (en) Steam turbine plant
US20190301307A1 (en) Turbine speed and acceleration limiter
EP2508719B1 (en) Method for starting a turbomachine
CN106030054B (en) Combine cycle combustion turbine equipment
JP2017506312A5 (en)
KR102196876B1 (en) Steam turbine overspeed prevention apparatus
US10871072B2 (en) Systems and methods for dynamic balancing of steam turbine rotor thrust
US12203395B2 (en) Turbine control valves dynamic interaction
CN103806959A (en) Method and device for preventing turbine control system of nuclear power station from generating disturbance
US20200040866A1 (en) Improvements to Hydraulic Machines During Grid Disconnections
US10167742B2 (en) Steam cycle, and method for operating a steam cycle
JPH0642368A (en) Control method for gas turbine compressor
Refan et al. Role of acceleration control in heavy duty gas turbines during load rejection
JPS6014965B2 (en) How to control pump groups
Bennauer et al. Optimized steam turbine governor controlling single or multiple grid faults

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17737546

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2018567616

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17737546

Country of ref document: EP

Kind code of ref document: A1