EP0065408A2 - Systèmes de commande pour générateurs de vapeur - Google Patents

Systèmes de commande pour générateurs de vapeur Download PDF

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Publication number
EP0065408A2
EP0065408A2 EP82302398A EP82302398A EP0065408A2 EP 0065408 A2 EP0065408 A2 EP 0065408A2 EP 82302398 A EP82302398 A EP 82302398A EP 82302398 A EP82302398 A EP 82302398A EP 0065408 A2 EP0065408 A2 EP 0065408A2
Authority
EP
European Patent Office
Prior art keywords
boiler
phase
pressure
valve
valve means
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
EP82302398A
Other languages
German (de)
English (en)
Other versions
EP0065408B1 (fr
EP0065408A3 (en
Inventor
Thomas D. Russell
Robert R. Walker
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.)
Babcock and Wilcox Co
Original Assignee
Babcock and Wilcox Co
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 Babcock and Wilcox Co filed Critical Babcock and Wilcox Co
Publication of EP0065408A2 publication Critical patent/EP0065408A2/fr
Publication of EP0065408A3 publication Critical patent/EP0065408A3/en
Application granted granted Critical
Publication of EP0065408B1 publication Critical patent/EP0065408B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/06—Control systems for steam boilers for steam boilers of forced-flow type
    • F22B35/10—Control systems for steam boilers for steam boilers of forced-flow type of once-through type
    • F22B35/105—Control systems for steam boilers for steam boilers of forced-flow type of once-through type operating at sliding pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/06—Control systems for steam boilers for steam boilers of forced-flow type
    • F22B35/10—Control systems for steam boilers for steam boilers of forced-flow type of once-through type
    • 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
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/18—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters
    • F01K3/20—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters with heating by combustion gases of main boiler
    • F01K3/22—Controlling, e.g. starting, stopping

Definitions

  • the present invention relates to control systems for boilers.
  • variable pressure boiler system In a variable pressure boiler system, the throttle pressure varies with the load. In its ideal form, the throttle valves on the turbine are left wide open and the throttle pressure varies directly with the load. Such variable pressure operation is desirable since it can increase the efficiency of the turbine.
  • the primary incentive for variable pressure operation is that it can increase the number of times that the turbine can be loaded and unloaded. This is because, with variable pressure operation, the change in the first stage steam exit temperature in the turbine is relatively minor, thus minimising thermal stress in the metal comprising the turbine.
  • the first stage steam exit temperature is load dependent. This can result in a greater change in temperature for the turbine which, in turn, can cause excessive metal fatigue.
  • a control system for a boiler being characterised by first valve means operable during a first phase of operation of the system, second valve means in fluidic communication with the first valve means and operable to open to a predetermined position during the first phase of operation of the system, and third valve means in fluidic communication with the second valve means and operable to vary the flow of steam from the boiler in response to the load imposed on the system during a second phase of operation of the system.
  • a preferred embodiment of the present invention described below solves or at least alleviates the aforementioned problems associated with the prior art by providing a boiler control system in which variable throttle pressure operation can be introduced at as low a load as possible and can be utilised for most of the load operating range. This is accomplished by opening a turbine valve to approximately 70 percent of its fully open position as soon as possible as the system is being loaded, utilising a flash tank while this is occurring unti the load demand exceeds minimum feedwater flow requirements, and then allowing the system to assume the variable throttle pressure mode of operation as the load is increased until throttle pressure approximates a designed operating pressure, at which time the turbine valve is regulated to meet load requirements.
  • the preferred system provides for variable pressure operation from approximately 20 percent to 75 percent of load and also provides for smooth transition from low load operation to the variable pressure mode of operation, and from the variable pressure mode of operation to a full pressure mode of operation.
  • a control coordinator is provided to monitor and correct steam flow, firing rate and feedwater flow. In this manner, the system can automatically adjust and compensate for deviations in these parameters from that which is desired.
  • the preferred control system thus permits variable throttle pressure operation of a once-through boiler, enables a once-through boiler to be operated in a variable pressure mode of operation over a wide load range, and provides a smooth transition in a once-through boiler from a low load type of operation to a variable pressure mode of operation and from the variable pressure mode of operation to a full pressure mode of operation.
  • FIG. 1 is a schematic drawing of a system 10 embodying the present invention.
  • the system 10 comprises primarily a furnace 12 whose output is connected to an input to a primary superheater 14, a flash tank 16, a secondary superheater 18 whose output is connected to an input to a turbine 20 via a turbine valve 22, a generator 23, and a condenser 24.
  • the condenser 24 is connected to an input to the furnace 12 via a low pressure heater 26, deaerator 28, a boiler feed pump 30, and a high pressure heater 32.
  • the primary superheater 14 is connected to an input to the flash tank 16 via a valve 34 and the flash tank 16 is connected to the secondary superheater 18 via a valve 36.
  • a pair of valves 38 and 40 are conected in parallel across the input to the valve 34 and an output of the valve 36.
  • a valve 42 is provided between the flash tank 16 and the condenser 24 and controls the flow of water from the flash tank 16 to the condenser.
  • a superheated steam attemperator valve 44 is provided between the output of the secondary superheater 18 and the flash tank 16.
  • FIG. 2 The principle of operation of the system is shown in Figure 2.
  • percentage pressure or valve opening is plotted versus percentage load, and flash tank pressure, furnace pressure, turbine valve position and throttle pressure are illustrated.
  • the objective is to obtain variable .throttle pressure at as low a load as possible, provide a smooth transition from low load operation to once-through operation, and incorporate the capabilities of a control coordinator 50, shown in Figure 3, during a variable throttle pressure phase of operation. This is accomplished by opening the turbine valve 22 as soon as possible, by operating the flash tank 16 until it is dry, and by using the valves 38 and 40 between the primary superheater 14 and the secondary superheater 18 as throttle valves, as wil hereinafter be described.
  • a unique feature of this control strategy is that throttle pressure is not directly controlled, except at minimum pressure, but is permitted to float to whatever level is required for the desired load. Thus, variable pressure operation is achieved over a very substantial portion of the load range.
  • an incoming control signal is applied to a unit load demand development function 52, an output of which is directed to the control coordinator 50 and to a turbine valve program 54, a steam flow modifier 56, a firing rate modifier 58, a feedwater modifier 60, and controls for the valve 36.
  • the turbine valve program 54 controls the operation of the turbine valve 22
  • the steam flow modifier 56 controls the operation of the valves 38 and 40
  • the firing rate modifier 50 controls the fuel and air mixture in the system
  • the feedwater modifier 60 regulates the flow of feedwater throughout the system.
  • a pressure transmitter 62 is connected to both the control coordinator 50 and the control valve 34, and an electrical transmitter 64, a feedwater temperature transmitter 66 and a superheater temperature transmitter 68 are also connected as inputs to the control coordinator 50 which, in turn, regulates the steam flow modifier 56, the firing rate modifier 58 and the feedwater modifier 60 by means of control signals generated therein.
  • the control system has basically three modes of operation: low load operation, once-through variable pressure operation, and full pressure operation.
  • Low load operation occurs when the boiler feedwater flow is limited to a minimum flow rate.
  • Once-through variable pressure operation occurs when the feedwater flow rate exceeds its minimum flow rate and continues until throttle pressure reaches a full design pressure, i.e. furnace pressure.
  • Full pressure operation occurs when the throttle pressure has reached full design pressure and continues until full load is achieved.
  • the throttle pressure is maintained constant and the turbine valve 22 is rapidly opened to approximately 70 percent of its fully open position, as shown in Figure 2.
  • the valves 38 and 40 are closed and the valves 34 and 36, along with the turbine valve 22, are opened.
  • the valve 34 controls the furnace pressure
  • the valve 36 controls the throttle pressure.
  • the valve 42 is also opened and regulates the water level in the flash tank 16.
  • all flow from the furnace 12 is directed to the flash tank 16 and starts as water and, as firing is increased, becomes steam.
  • the flash tank 16 acts as a steam and water separator and directs the water to the condenser 24 and the steam to the turbine 20.
  • the valve 40 opens and the valves 34 and 36 start closing, stopping the flow to the flash tank 16. This occurs at approximately 25 percent of load and starts the next phase of operation, i.e. the variable throttle pressure phase or once-through variable pressure phase of operation.
  • variable pressure phase or variable throttle pressure phase of operation the turbine valve 22 is maintained at approximately 70 percent of its fully open position by the turbine valve program 54.
  • steam flow control is regulated by the valve 40 and this valve, in essence, acts as a remote throttle valve.
  • the feedwater flow is given the responsibility of controlling steam temperature, whereas the firing rate controls the load, and throttle pressure is permittted to float to whatever value is necessary to satisfy the load requirements.
  • the control coordinator 50 assumes an important function in this phase of operation since it produces error or correction signals to the steam flow modifier 56, the firing rate modifier 58 and the feedwater modifier 60.
  • error or correction signals are as follows: a megawatt error minus a furnace pressure error control signal which is directed to the steam flow modifier 56, a megawatt error plus a furnace pressure error control signal which is directed to the firing rate modifier 58, and a superheat temperature error plus a feedwater temperature control signal which is directed to the feedwater modifier 60.
  • the feedwater flow can be adjusted to maintain steam temperature while the steam flow and the firing rate can be corrected to maintain proper furnace pressure and megawatts.
  • valve 38 When the valve 40 approaches its fully open position, the valve 38 starts opening and the turbine valve 22 is permitted to start opening further from its 70 percent open position. This commences the next phase of operation, i.e. the full pressure phase of operation.
  • control system produces a number of benefits. For example, by using variable pressure the first stage steam temperature can be closely controlled, which permits rapid loading of the turbine without creating excessive thermal stress.
  • the foregoing system provides for quickly achieving variable pressure operation, turbine metal temperature matching, and a smooth transition to once-through operation.
  • control coordinator regulates and controls the overall operation of the system in the variable pressure phase of operation and adjusts the system components to compensate for various operational deviations.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Control Of Turbines (AREA)
EP82302398A 1981-05-12 1982-05-11 Systèmes de commande pour générateurs de vapeur Expired EP0065408B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US26284481A 1981-05-12 1981-05-12
US262844 1981-05-12

Publications (3)

Publication Number Publication Date
EP0065408A2 true EP0065408A2 (fr) 1982-11-24
EP0065408A3 EP0065408A3 (en) 1983-11-16
EP0065408B1 EP0065408B1 (fr) 1986-04-23

Family

ID=22999306

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82302398A Expired EP0065408B1 (fr) 1981-05-12 1982-05-11 Systèmes de commande pour générateurs de vapeur

Country Status (8)

Country Link
EP (1) EP0065408B1 (fr)
JP (1) JPS57198902A (fr)
KR (1) KR870001505B1 (fr)
AU (1) AU556280B2 (fr)
CA (1) CA1211324A (fr)
DE (1) DE3270729D1 (fr)
ES (1) ES512051A0 (fr)
MX (1) MX152206A (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1985002667A1 (fr) * 1983-12-06 1985-06-20 Vsesojuzny Nauchno-Issledovatelsky I Proektno-Kons Dispositif de recirculation d'un milieu dans une chaudiere
KR102210866B1 (ko) * 2019-09-18 2021-02-04 한국에너지기술연구원 플래쉬탱크를 이용한 발전사이클시스템 및 그 제어방법
CN113432105A (zh) * 2021-07-14 2021-09-24 鞍山阿尔肯科技发展有限公司 一种物联网构架下燃气锅炉热能管理系统

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3286466A (en) * 1964-04-24 1966-11-22 Foster Wheeler Corp Once-through vapor generator variable pressure start-up system
US3572036A (en) * 1968-10-21 1971-03-23 Foster Wheeler Corp Vapor generator start-up system
US4241585A (en) * 1978-04-14 1980-12-30 Foster Wheeler Energy Corporation Method of operating a vapor generating system having integral separators and a constant pressure furnace circuitry

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3286466A (en) * 1964-04-24 1966-11-22 Foster Wheeler Corp Once-through vapor generator variable pressure start-up system
US3572036A (en) * 1968-10-21 1971-03-23 Foster Wheeler Corp Vapor generator start-up system
US4241585A (en) * 1978-04-14 1980-12-30 Foster Wheeler Energy Corporation Method of operating a vapor generating system having integral separators and a constant pressure furnace circuitry

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1985002667A1 (fr) * 1983-12-06 1985-06-20 Vsesojuzny Nauchno-Issledovatelsky I Proektno-Kons Dispositif de recirculation d'un milieu dans une chaudiere
US4608945A (en) * 1983-12-06 1986-09-02 Vsesojuzny Nauchno-Issledovatelsky Institut Atomnogo Energeticheskogo Mashinostroenia Apparatus for recirculating boiler fluid
KR102210866B1 (ko) * 2019-09-18 2021-02-04 한국에너지기술연구원 플래쉬탱크를 이용한 발전사이클시스템 및 그 제어방법
WO2021054586A1 (fr) * 2019-09-18 2021-03-25 한국에너지기술연구원 Système de cycle de production d'énergie utilisant un réservoir de détente et son procédé de commande
CN113432105A (zh) * 2021-07-14 2021-09-24 鞍山阿尔肯科技发展有限公司 一种物联网构架下燃气锅炉热能管理系统

Also Published As

Publication number Publication date
AU8357282A (en) 1982-11-18
JPS57198902A (en) 1982-12-06
EP0065408B1 (fr) 1986-04-23
ES8400580A1 (es) 1983-11-01
AU556280B2 (en) 1986-10-30
DE3270729D1 (en) 1986-05-28
JPS6252122B2 (fr) 1987-11-04
KR830010338A (ko) 1983-12-30
ES512051A0 (es) 1983-11-01
MX152206A (es) 1985-06-07
EP0065408A3 (en) 1983-11-16
KR870001505B1 (ko) 1987-08-19
CA1211324A (fr) 1986-09-16

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