CN103382860A - Control method for steam turbine power generation and heat supply system - Google Patents
Control method for steam turbine power generation and heat supply system Download PDFInfo
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Abstract
A control method for a steam turbine power generation and heat supply system comprises the following steps: unit start-up control, boiler automatic protection, bypass alarming, low voltage safety oil protection, power generator water cut-off protection, and automatic water supply regulation, wherein the unit start-up control comprises inspection before unit start-up, preparation before unit ignition, and ignition and pressure-boosting control.
Description
Technical field
The present invention relates to a kind of controlling method, specifically, relate to a kind of steam turbine power generation heating system controlling method.
Background technique
Along with improving constantly of living standards of the people, area of heat-supply service is constantly developed, and heating load constantly increases, and as the heat supply work of one of government's " people's livelihood " engineering, relates to huge numbers of families' quality of life, is day by day paid attention to.Become so develop new heat supply process the good exploration that ensures reliability of heat-supply system, have important social effect.
At present China's heat supply present situation is take extraction for heat supply and little unit rough vacuum back pressure heat supply process as main, and the minority region has and utilizes earth source heat pump to implement for the cold-peace heat supply.Continuous expansion and Plant reconstruction plant modernization due to area of heat-supply service lags behind in addition, and the boiler heat supplying mode that occupies a narrow space still exists, and this heat-supplying mode not only environmental pollution is serious, and the Economy extreme difference.
The heat supply of large-scale unit back pressure is current better heat-supplying mode, but the unit of operation at non-heat supply phase Economy extreme difference, causes annual economic benefit unsatisfactory in this way.
Extraction for heat supply is to use at present maximum heat-supplying modes, and utilization ratio is hanged down and the larger phenomenon of cold source energy but its existence is drawn gas.Although little unit rough vacuum back pressure heat supply process cold source energy is zero, but because little unit operation parameter is lower, generation load and boiler caloric receptivity ratio are less, limited generation load, economic benefit is still undesirable, because little unit heat capacity is limited, can't satisfy extensive heat demand simultaneously.
From the heating form analysis of the cogeneration units of present operation, the following unit of 50MW generally generally adopts adjustable drawing gas or the heat supply of back pressure unit.The basic sucking condensing type heating form that all adopts of 100MW and above unit.Performance driving economy under its heat supply running operating mode of sucking condensing type heat supply unit and back pressure type unit is far apart.Analyze according to rough vacuum circulating water heating reforming design scheme, under the heating operating mode, its gross coal consumption rate can reach below 150g/kWh in the winter time, and takes out solidifying heat supply unit best level also more than 240g/kWh with capacity.Back pressure type unit or rough vacuum circulating water heating unit are compared with the sucking condensing type unit, the basic difference of its economical effect of heat-supply just is: when back pressure (or rough vacuum circulating water heating) unit moves under supplying thermal condition, its cold source energy all is utilized, and the sucking condensing type unit only has part to draw gas and be used to heat supply, the turbine discharge share reduces to some extent, but still has larger cold source energy.
For this reason, a kind of cold source energy minimum of searching, generation load and boiler recept the caloric, and ratio is higher, heat-supplying mode that satisfy simultaneously extensive heat demand is the task of top priority.In addition, for present existing heat supply process, for extensive district heating,, generation load few in the urgent need to a kind of investment cost restriction is relatively little, energy-conservation and economic benefit large, Site Implementation strong adaptability, technology that safety reliability is high.To this, the invention provides i.e. " pure condensate-back pressure double-mode " heating system of a kind of " the two back pressure double rotors of low pressure (LP) cylinder exchange " heating system, for this heating system, need to provide the controlling method for this heating system.
Summary of the invention
Some embodiment who is equivalent in primitive request scope of the present invention does following summary.These embodiments are unrestricted claimed invention scope also, but attempts to provide the brief overview of multiple possibility form of the present invention.In fact, the present invention can comprise and is similar to or is different from the multi-form of the embodiment that proposes below.
The invention provides a kind of steam turbine power generation heating system controlling method; comprise that unit starting is controlled, boiler is protected automatically, bypass warning, low-voltage safety oil guard, generator water cut-off protection, feedwater automatic control; wherein unit starting is controlled and is comprised the front inspection of unit starting, the front preparation of unit igniting, igniting and boosting rectifier control; wherein the inspection before unit starting comprises; check whether there is following situations, forbid unit starting when having any in following situations:
(1) undesired or main inlet throttle-stop valve, throttle of emergency overspeed governor action, the non-return flap that draws gas are not closed completely;
(2) speed control system can not be controlled rotating speed after can not keeping idle running or removal of load;
(3) the turbine rotor bending break number surpasses cold conditions reference value ± 0.02mm, and wherein the cold conditions reference value is measured load after unit installation or overhaul;
(4) the Turbo-generator Set sound partly has obvious grating;
(5) high, the upper and lower temperature difference of IP inner casing surpasses 35 ℃, and the upper and lower temperature difference of outer shell is over 50 ℃;
(6) the high intermediate pressure cylinder differential expansion is greater than reference value 6mm or less than reference value 1mm;
(7) turbine oil and fire-resistant oil oil and turbidity test are defective or the turbine oil temperature lower than 25 ℃;
(8) main table meter (rotating speed, axial displacement, relative expansion, important meals temperature point etc.) is malfunctioning;
(9) protection power source and automatic safety device are not normal;
(10) Boiler Furnace Safeguard Supervisory System, digital electro-hydraulic control system, Steam Turbine Safety Monitoring System, steam turbine trip protection system and device can not normally drop into;
(11) the control system action is undesired, affects unit starting and normal operation;
(12) the boiler drum level protection is imperfect.
Description of drawings
To describe now according to preferred but nonrestrictive embodiment of the present invention, these and other features of the present invention, aspect and advantage will become apparent when the reference accompanying drawing is read following detailed description, wherein:
Fig. 1 is the structural representation of the present invention during with the pure condensate rotor operation.
Fig. 2 is the structural representation of the present invention during with back pressure heat supply rotor operation.
Fig. 3 is power generation and heat supply system construction drawing of the present invention.
Fig. 4 is start-up curve of generating unit figure.
Embodiment
The following description is only exemplary and be not in order to limit the disclosure, application or purposes in essence.Should be understood that, in whole accompanying drawings, corresponding reference character represents identical or corresponding parts and feature.
Fig. 1 is the structural representation when inventing with the pure condensate rotor operation.In figure, high pressure rotor 5 by steam turbine connects low pressure rotor one end by the second coupling 4, and the low pressure rotor the other end connects generator 1 by the first coupling 2 and carries out power generation and heat supply, saves at non-heating season, low pressure rotor adopts pure condensate rotor 3, is used for the unit generation of non-heating season.In heating season, pure condensate rotor 3 is replaced by back pressure heat supply rotor 6.
Fig. 2 is the structural representation of the present invention during with back pressure heat supply rotor operation.At Heating Season, untie the first coupling 2 and the second coupling 4, pure condensate rotor 3 is replaced by back pressure heat supply rotor 6, connect the first coupling 2 and the second coupling 4, be used for the generating electricity in winter heat supply.Finish at Heating Season, back pressure heat supply rotor 6 is more gained pure condensate rotor 3, be used for generating.Be specially adapted to the to go into operation transformation of big-and-middle-sized unit of this steam turbine.Through the unit of transformation, adopt back pressure heat supply rotor 6 at Heating Season, steam turbine moves in the back pressure mode, can obtain good economic benefit.This equipment has also overcome the shortcoming that large-scale back pressure unit can not move at non-heating season.Adopt pure condensate rotor 3 at non-heating season, steam turbine will move in the pure condensate mode, guarantee power benefit.
Fig. 3 is power generation and heat supply system construction drawing of the present invention.As seen from the figure, power generation and heat supply of the present invention system comprises vapour condenser, heat exchangers for district heating, pumps for hot water supply net, cooling tower, circulating water pump, pumps for hot water supply net etc.Fig. 4 is start-up curve of generating unit figure, wherein shows main stripping temperature, main vapour pressure, the trend over time of loading.
Hereinafter working procedure of the present invention will be described.
1, basic principle
" the two back pressure double rotors of low pressure (LP) cylinder exchange " circulating water heating technology, namely, the high back pressure low pressure rotor that uses newly-designed rotor and stator blade progression relatively to reduce when the heat supply running operating mode, vapour condenser operation high back pressure (30～45kPa), corresponding exhaust temperature is increased to 80 ℃ of left and right, carries out circulating water heating; At non-heating period, more former pure condensate rotor is recovered, exhaust pressure returns to 4.9kPa, returns to former pure condensate unit operation operating mode fully.Like this, unit has namely been realized " double-mode " of " pure condensate-back pressure ".
Heat exchange requirement for As soon as possible Promising Policy first-degree heating network and secondary heat supply network, the rough vacuum circulating water heating adopts the tandem type two-stage heating system, at first heat supply network circulating water heat for the first time through vapour condenser, absorb the low pressure (LP) cylinder exhausted spare heat, and then complete heating for the second time through heat supply initial station steam heater, generate high-temperature-hot-water, deliver to hot water pipe net and carry out heat exchange by secondary heat exchange station and secondary heat supply network circulating water, return unit condenser after high-temperature-hot-water is cooling, consisting of a complete circulation waterway, draws gas for unit mesolow cross over pipe in steam source, heat supply initial station.
When rough vacuum circulating water heating operating mode is moved during heating, under unit pure condensate operating mode, needed cooling column and circulating water pump are out of service, the circulation of vapour condenser is switched to the hot water pipe net circulating water loop that pumps for hot water supply net is set up, form new " heat-water " exchange system.Circulating water loop switch complete after, the water flow that enters vapour condenser is down to 6000-9000t/h, back pressure of condenser rises to 30～45kPa by 5～7 kPa left and right, the low pressure (LP) cylinder exhaust temperature rises to 69～78 ℃ (saturation temperature that back pressure is corresponding) by 30～40 ℃.Heating for the first time through vapour condenser, heat supply network circulating water return water temperature is promoted to 66～75 ℃ (3 ℃ of condenser terminal differences) by 60 ℃, then send into the initial station heat exchangers for district heating after pumps for hot water supply net boosts, feed to heat supply network one time after the heat supply network supply water temperature further is heated to 85-90 ℃.
When unit moves in the pure condensate operating mode, withdraw from the operation of pumps for hot water supply net and heat exchangers for district heating, recover the operation of former circulating water pump and cooling tower, back pressure of condenser returns to 5～7kPa.
Systematic parameter from design rough vacuum circulating water heating technology, because steam turbine operation steady in a long-term is subjected to exhaust temperature not higher than the restriction of 80 ℃, consider condenser terminal difference, the circulating water water-exit temperature of Heat Supplying with Low Vacuum is not generally higher than 75 ℃, water supply, return water temperature scope are generally 60 ℃～75 ℃ of water supply, 50 ℃～60 ℃, backwater, and corresponding operation back pressure is 25～45kPa.
Need to prove, for the rough vacuum circulating water heating, should reduce as far as possible the circulating water return water temperature, farthest to utilize the low pressure (LP) cylinder exhaust steam heat, otherwise not only the low pressure (LP) cylinder heat exhaust can not obtain high efficiency utilization, also can cause low pressure (LP) cylinder exhaust temperature overtemperature, the safe and reliable operation of steam turbine is brought considerable influence.
Consider the variation actual conditions of vapour condenser operating conditions, the design philosophy of determining transformation is: under the prerequisite that realizes Heating Period and non-heating period thermal procession, Heating Period guarantees the Security of vapour condenser equipment, and non-heating period (being the pure condensate operating mode) guarantees the Economy of vapour condenser equipment.Although the Operational Limits of the Operational Limits of circulating water heating phase vapour condenser during far above the pure condensate operating mode, the running state of Steam Side of Condenser and water side (fluid properties, heat exchange mode, pressure, temperature grade) does not have the change of matter.So the throat of the existing vapour condenser of reservation, shell, bottom support etc. are feasible to condenser retrofit on this basis fully.Restrain simultaneously and arrange according to high back pressure transformation situation and carried out targeted design, to satisfy the long-time running under heating and pure condensate operating mode.
The below introduces the steam-turbine unit running.
1, the startup of unit
1.1 forbid unit starting under following situations
(1) undesired or main inlet throttle-stop valve, throttle of emergency overspeed governor action, the non-return flap that draws gas are not closed completely;
(2) speed control system can not be controlled rotating speed after can not keeping idle running or removal of load;
(3) the turbine rotor bending break number surpasses cold conditions reference value ± 0.02mm, and wherein the cold conditions reference value is measured load after unit installation or overhaul;
(4) the Turbo-generator Set sound partly has obvious grating;
(5) high, the upper and lower temperature difference of IP inner casing surpasses 35 ℃, and the upper and lower temperature difference of outer shell is over 50 ℃;
(6) the high intermediate pressure cylinder differential expansion is greater than reference value 6mm or less than reference value 1mm;
(7) turbine oil and fire-resistant oil oil and turbidity test are defective or the turbine oil temperature lower than 25 ℃;
(8) main table meter (rotating speed, axial displacement, relative expansion, important meals temperature point etc.) is malfunctioning;
(9) protection power source and automatic safety device are not normal.
(10) Boiler Furnace Safeguard Supervisory System (FSSS, Furnace Safety Supervision System), digital electro-hydraulic control system (DEH, Digital Electro-Hydraulic Control System), Steam Turbine Safety Monitoring System (TSI, Turbine Supervisory Instrumentation), steam turbine trip protection system (ETS, Emergency trip system) device can not normally drop into;
(11) the control system action is undesired, affects unit starting and normal operation;
(12) the boiler drum level protection is imperfect.
When above-mentioned all situations does not exist, allow unit starting.
1.2 the inspection before unit starting
Prepare before the unit igniting
(1) confirm that under all machine supplying powders, the powder plate washer in off position.
(2) start condensate pump.
(3) start feed water pump to boiler feed water, when steam water-level proceed to-during 300mm, close the adjustment doors that respectively feeds water, isolation door, stop feed water pump, close the total door of feedwater, open the economizer recirculation door.
(4) start circulating water pump, circulation puts into operation.
(5) start water-jet pump, open main and auxiliary air ejector air gate.
(6) check that condenser vacuum rises to 13.33kPa.
1.3 light a fire and boost
(1) start the preheater oil pump, start preheater.
(2) start suction, gas fan, adjust and inhale air output, keep combustion chamber draft-50Pa, keep the 30% above air quantity of rated load.(3) confirm that each oil gun angle valve closes tightly, start fuel pump, adjust oil pressure to more than 2.6MPa, determine the fuel leakage pass the test.
(4) start fire inspection cooling blower normal after, the purging condition satisfies, and carries out furnace purge.
(5) after burner hearth " purging is completed ", open oil-feed quick-break valve.
(6) open oil gun oil-feed door, each oily angle valve, close recirculation door, drop into grease gun igniting.
(7) check that small oil gun catches fire stable.
(8) drop into main, steam by-pass system again, adjust condenser vacuum.
(9) when saturated vapour pressure rises to 0.15～0.2MPa, rinse the steam water-level meter.
(10) when saturated vapour pressure rises to 0.3～0.5MPa, flushing pressure table pipe and the tight drum screw of boiler maintenance heat.
(11) hydrophobic cutting to behind the door before electronic main shutter, open electronic main shutter.
(12) when saturated vapour pressure rises to 0.5MPa, stop adjacent stove heating.
(13) when the reheater inlet pressure reaches 0.1～0.3MPa, close reheater cold junction draining valve.
(14) control rate of rise 0.05MPa/min, 1 ℃/min of main steam temperature warming velocity and drum wall temperature difference up and down are not more than 40 ℃.
(15) according to exhaust temperature, cylinder water spray after dropping into.
(16) persistent surveillance cylinder temperature, the tight situation of inspection high pressure main inlet throttle-stop valve, throttle, reheat stop interceptor valve, high-pressure cylinder steam discharge non-return flap.
(17) main vapour pressure rises to 0.1MPa, and gland seal system is taken out female pipe vapour source heating coil to surge tank with three.
(18) adjust the coagulator water level.
(19) open water cooled furnace wall lower collecting box sewage door, be interrupted blowdown, each one is heated evenly, set up as early as possible water circulation.
(20) during steam water-level+50mm, start the feed water pump boiler feed water, close economizer recirculation.In time drop into cooling water.
(21) main steam pressure reaches 1.86～2.06MPa, and steam temperature is more than 370 ℃, and reheat steam temperature is more than 250 ℃.
(22) send vapour to shaft seal, operation vacuum breaking door keeps condenser vacuum 59-75 kPa.
2, boiler is protected automatically
Boiler protection automatically is the automatic Protection of taking in the middle of boiler operatiopn equipment, when the abnormal accident, reports to the police or arrestment operation automatically.
Boiler protects the action launching condition to comprise automatically:
A tripping operation in (1) two suction fan
A tripping operation in (2) two gas fans
A tripping operation in (3) two mill exhausters and dropping into without oil gun
(4) steam water-level also continues 10 seconds greater than reference value 250mm
(5) steam water-level also continues 10 seconds less than reference value 250mm
(6) furnace pressure is higher than reference value 1000Pa
(7) furnace pressure is lower than reference value 800Pa
(8) failure of fuel
(9) furnace flame is lost
(10) steam turbine chaser
3, the warning of bypass
When one of following situations occurring, bypath system is sent warning
The valves such as (1) high other decompression, low other decompression, high other desuperheat, low other desuperheat are simultaneously during standard-sized sheet.
(2) high branch mouth temperature and definite value deviation are greater than predetermined value
(3) low branch mouth temperature and definite value deviation are greater than predetermined value
(4) bypass pressure valve fastener communication failure
(5) high side pressure valve instruction feedback deviation is greater than predetermined value
(6) high other spray water valve instruction feedback deviation is greater than predetermined value
7) low side pressure valve instruction feedback deviation is large
8) low other spray water valve instruction feedback deviation is large
9) the by-pass reducing valve is opened, the desuperheat valve do not open.
10) automatic switching is fashionable, when instruction, feedback deviation greater than 30% the time.
4, low-voltage safety oil guard
Low-voltage safety oil (turbine oil) when oil pressure is down to 0.45MPa membrane valve open, venting high voltage control oil is closed height, intermediate pressure main stop valve, throttle, the non-return flap that draws gas at different levels.
5, generator water cut-off protection
is reduced to 10t/h when generator amature or stator flow of inlet water, and pressure decreased is to 0.049MPa, and when continuing 30 seconds, carries out the action of generator water cut-off protection, the tripping operation of generator main oil switch, steam turbine tripping operation simultaneously.
6, the adjustment of steam water-level
Boiler is normally in service, and water level should remain on 0, and normal fluctuation range is ± 50mm.
Boiler water level should be as the criterion with the drum pressure difference water gauge, and operation is adjusted take the drum electric contact as foundation, and with reference to table meters such as feedwater, steam flows.Require the boiler of sending into of feedwater continuous uniform, avoid large adjustment.
The steam water-level meter should be clear, and sufficiency of illumination is without leaking vapour, water leakage phenomenon.Mica water-level gauge water line is answered slight fluctuations, if water level does not fluctuate or sheet mica when smudgy, should in time rinse, and magnetic turnover panel water-level gauge magnetic turnover panel is consistent continuously, processes otherwise should contact maintenance.
Fashionable when the feedwater automatic switching, should often monitor the indication of each table meter, when water level surpasses ± 50mm and when continuing to change, should in time switch to manual adjustment, prevent from sternly not causing the full lack of water of boiler because monitoring.
When one of following situations occurs, feedwater automatic control will withdraw from automatically:
(1) the steam water-level signal is malfunctioning
(2) the main steam flow signal is malfunctioning
(3) the feedwater flow signal is malfunctioning
(4) feed water pump instruction and feedback deviation are greater than 15%
(5) steam water-level is higher than reference value 110mm
(6) steam water-level is lower than reference value 100mm
(7) steam water-level and setting value deviation are greater than ± 80mm
After feedwater is withdrawed from automatically voluntarily, should in time carry out manual tune.After water level is normal, then drop into feedwater automatically.
Each water level gauge meter must indicating correct, per tour and twice of water-level gauge check and correction on the spot.The high and low alarm signal of steam water-level is reliable, regularly carries out per month verification.
Meet following situations, should strengthen supervision and the adjustment of steam water-level, prevent from lacking, full water.
1) in igniting process, when red switch, raising speed, side by side, during load up.
2) during safety valve action.
3) feedwater is automatic when malfunctioning.
4) feed water pump work is undesired, or feed water pump coupler scoop tube bite.
5) the accident wicket is not closed tight.
6) pressure-containing member leaks serious.
7) during periodical blowdown.
When 8) vapour pressure or load have than great fluctuation process.
9) height adds the throwing stopping time.
10) feed water by-pass switches or when switching feed water pump.
This specification at length discloses the present invention, comprises optimal mode, and also can make related domain anyone put into practice the present invention, comprise the method for making and using any equipment or system and carry out any introducing.Protection scope of the present invention is limited by accessory claim, and can be included in pin various modification made for the present invention, remodeling and equivalents in the situation that does not break away from protection domain of the present invention and spirit.
Claims (8)
1. steam turbine power generation heating system controlling method; comprise that unit starting is controlled, boiler is protected automatically, bypass warning, low-voltage safety oil guard, generator water cut-off protection, feedwater automatic control; wherein unit starting is controlled and is comprised the front inspection of unit starting, the front preparation of unit igniting, igniting and boosting rectifier control; wherein the inspection before unit starting comprises; check whether there is following situations, forbid unit starting when having any in following situations:
(1) undesired or main inlet throttle-stop valve, throttle of emergency overspeed governor action, the non-return flap that draws gas are not closed completely;
(2) speed control system can not be controlled rotating speed after can not keeping idle running or removal of load;
(3) the turbine rotor bending break number surpasses cold conditions reference value ± 0.02mm, and wherein the cold conditions reference value is measured load after unit installation or overhaul;
(4) the Turbo-generator Set sound partly has obvious grating;
(5) high, the upper and lower temperature difference of IP inner casing surpasses 35 ℃, and the upper and lower temperature difference of outer shell is over 50 ℃;
(6) the high intermediate pressure cylinder differential expansion is greater than reference value 6mm or less than reference value 1mm;
(7) turbine oil and fire-resistant oil oil and turbidity test are defective or the turbine oil temperature lower than 25 ℃;
(8) main table meter (rotating speed, axial displacement, relative expansion, important meals temperature point etc.) is malfunctioning;
(9) protection power source and automatic safety device are not normal;
(10) Boiler Furnace Safeguard Supervisory System, digital electro-hydraulic control system, Steam Turbine Safety Monitoring System, steam turbine trip protection system and device can not normally drop into;
(11) the control system action is undesired, affects unit starting and normal operation;
(12) the boiler drum level protection is imperfect.
2. the method for claim 1, is characterized in that, prepares to comprise before described unit igniting:
(1) confirm that under all machine supplying powders, the powder plate washer in off position;
(2) start condensate pump;
(3) start feed water pump to boiler feed water, when steam water-level proceed to-during 300mm, close the adjustment doors that respectively feeds water, isolation door, stop feed water pump, close the total door of feedwater, open the economizer recirculation door;
(4) start circulating water pump, circulation puts into operation;
(5) start water-jet pump, open main and auxiliary air ejector air gate;
(6) check that condenser vacuum rises to 13.33kPa;
The method of claim 1 is characterized in that, described igniting and boosting rectifier control comprise:
(1) start the preheater oil pump, start preheater;
(2) start suction, gas fan, adjust and inhale air output, keep combustion chamber draft-50Pa, keep the 30% above air quantity of rated load; (3) confirm that each oil gun angle valve closes tightly, start fuel pump, adjust oil pressure to more than 2.6MPa, determine the fuel leakage pass the test;
(4) start fire inspection cooling blower normal after, the purging condition satisfies, and carries out furnace purge;
(5) after burner hearth " purging is completed ", open oil-feed quick-break valve;
(6) open oil gun oil-feed door, each oily angle valve, close recirculation door, drop into grease gun igniting;
(7) check that small oil gun catches fire stable;
(8) drop into main, steam by-pass system again, adjust condenser vacuum;
(9) when saturated vapour pressure rises to 0.15～0.2MPa, rinse the steam water-level meter;
(10) when saturated vapour pressure rises to 0.3～0.5MPa, flushing pressure table pipe and the tight drum screw of boiler maintenance heat;
(11) hydrophobic cutting to behind the door before electronic main shutter, open electronic main shutter;
(12) when saturated vapour pressure rises to 0.5MPa, stop adjacent stove heating;
(13) when the reheater inlet pressure reaches 0.1～0.3MPa, close reheater cold junction draining valve;
(14) control rate of rise 0.05MPa/min, 1 ℃/min of main steam temperature warming velocity and drum wall temperature difference up and down are not more than 40 ℃;
(15) according to exhaust temperature, cylinder water spray after dropping into;
(16) persistent surveillance cylinder temperature, the tight situation of inspection high pressure main inlet throttle-stop valve, throttle, reheat stop interceptor valve, high-pressure cylinder steam discharge non-return flap;
(17) main vapour pressure rises to 0.1MPa, and gland seal system is taken out female pipe vapour source heating coil to surge tank with three;
(18) adjust the coagulator water level;
(19) open water cooled furnace wall lower collecting box sewage door, be interrupted blowdown, each one is heated evenly, set up as early as possible water circulation;
(20) during steam water-level+50mm, start the feed water pump boiler feed water, close economizer recirculation; In time drop into cooling water;
(21) main steam pressure reaches 1.86～2.06MPa, and steam temperature is more than 370 ℃, and reheat steam temperature is more than 250 ℃;
(22) send vapour to shaft seal, operation vacuum breaking door keeps condenser vacuum 59-75 kPa.
3. the method for claim 1, is characterized in that, described boiler automatically protection comprises, takes the automatic Protection to equipment in the middle of boiler operatiopn, during at least one in following situations occurs, reports to the police or arrestment operation automatically:
A tripping operation in (1) two suction fan;
A tripping operation in (2) two gas fans;
A tripping operation in (3) two mill exhausters and dropping into without oil gun;
(4) steam water-level also continues 10 seconds greater than reference value 250mm;
(5) steam water-level also continues 10 seconds less than reference value 250mm;
(6) furnace pressure is higher than reference value 1000Pa;
(7) furnace pressure is lower than reference value 800Pa;
(8) failure of fuel;
(9) furnace flame is lost;
(10) steam turbine chaser.
4. the method for claim 1, is characterized in that, the warning of described bypass comprises, when one of following situations occurring, bypath system is sent warning:
The valves such as (1) high other decompression, low other decompression, high other desuperheat, low other desuperheat are simultaneously during standard-sized sheet;
(2) high branch mouth temperature and definite value deviation are greater than predetermined value;
(3) low branch mouth temperature and definite value deviation are greater than predetermined value;
(4) bypass pressure valve fastener communication failure;
(5) high side pressure valve instruction feedback deviation is greater than predetermined value;
(6) high other spray water valve instruction feedback deviation is greater than predetermined value;
(7) low side pressure valve instruction feedback deviation is large;
(8) low other spray water valve instruction feedback deviation is large;
(9) the by-pass reducing valve is opened, the desuperheat valve do not open.
5. (10) automatic switching is fashionable, when instruction, feedback deviation greater than 30% the time.
6. the method for claim 1, is characterized in that, described low-voltage safety oil guard comprises, when low-voltage safety oil oil pressure is down to 0.45MPa, membrane valve is opened, and venting high voltage control oil is closed height, intermediate pressure main stop valve, throttle, the non-return flap that draws gas at different levels.
7. the method for claim 1; it is characterized in that; described generator water cut-off protection comprises; when generator amature or stator flow of inlet water are reduced to 10t/h; pressure decreased is to 0.049MPa; and when continuing 30 seconds, carry out the action of generator water cut-off protection, the tripping operation of generator main oil switch, steam turbine tripping operation simultaneously.
8. the method for claim 1, is characterized in that, described generator water cut-off protection comprises, when one of following situations occurs, feedwater automatic control will withdraw from automatically:
(1) the steam water-level signal is malfunctioning;
(2) the main steam flow signal is malfunctioning;
(3) the feedwater flow signal is malfunctioning;
(4) feed water pump instruction and feedback deviation are greater than 15%;
(5) steam water-level is higher than reference value 110mm;
(6) steam water-level is lower than reference value 100mm;
(7) steam water-level and setting value deviation are greater than ± 80mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310208872.2A CN103382860B (en) | 2013-05-24 | 2013-05-30 | Steam turbine power generation heating system controlling method |
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| CN201320301786.1U Expired - Fee Related CN203374325U (en) | 2013-05-24 | 2013-05-29 | Connecting structure between condenser throat portion and steam turbine exhaust port |
| CN201320301788.0U Expired - Fee Related CN203374321U (en) | 2013-05-24 | 2013-05-29 | Moving blade of low-pressure rotor |
| CN201310206163.0A Expired - Fee Related CN103291391B (en) | 2013-05-24 | 2013-05-29 | A kind of steam turbine power generation heating system with double-mode |
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| CN201320301482.5U Expired - Fee Related CN203374324U (en) | 2013-05-24 | 2013-05-29 | Low-pressure circulating component |
| CN201310206093.9A Expired - Fee Related CN103306758B (en) | 2013-05-24 | 2013-05-29 | A kind of control method of monitored parameter under high back pressure supplies thermal condition |
| CN201310206097.7A Expired - Fee Related CN103292383B (en) | 2013-05-24 | 2013-05-29 | A kind of operation control operation method of circulating water heating unit |
| CN201320301790.8U Expired - Fee Related CN203374322U (en) | 2013-05-24 | 2013-05-29 | Low-pressure separating board for steam turbine double-rotor exchanging circulating water heat supply |
| CN201320301712.8U Expired - Fee Related CN203374326U (en) | 2013-05-24 | 2013-05-29 | Optimized rear cylinder water spray system |
| CN201310208872.2A Expired - Fee Related CN103382860B (en) | 2013-05-24 | 2013-05-30 | Steam turbine power generation heating system controlling method |
| CN201310208998.XA Expired - Fee Related CN103306753B (en) | 2013-05-24 | 2013-05-30 | A kind of steam turbine set cooling water system and chilled(cooling) water supply (CWS) method |
| CN201320355675.9U Expired - Fee Related CN203374329U (en) | 2013-05-24 | 2013-06-21 | Low pressure through-flow structure |
| CN201320355671.0U Expired - Fee Related CN203374328U (en) | 2013-05-24 | 2013-06-21 | Clapboard combination structure for steam turbine |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201320301788.0U Expired - Fee Related CN203374321U (en) | 2013-05-24 | 2013-05-29 | Moving blade of low-pressure rotor |
| CN201310206163.0A Expired - Fee Related CN103291391B (en) | 2013-05-24 | 2013-05-29 | A kind of steam turbine power generation heating system with double-mode |
| CN201320301484.4U Expired - Fee Related CN203374323U (en) | 2013-05-24 | 2013-05-29 | Low-pressure front-back shaft sealing parts |
| CN201320301505.2U Expired - Fee Related CN203374320U (en) | 2013-05-24 | 2013-05-29 | Low-pressure rotor for steam turbine double-rotor exchanging circulating water heat supply |
| CN201320301482.5U Expired - Fee Related CN203374324U (en) | 2013-05-24 | 2013-05-29 | Low-pressure circulating component |
| CN201310206093.9A Expired - Fee Related CN103306758B (en) | 2013-05-24 | 2013-05-29 | A kind of control method of monitored parameter under high back pressure supplies thermal condition |
| CN201310206097.7A Expired - Fee Related CN103292383B (en) | 2013-05-24 | 2013-05-29 | A kind of operation control operation method of circulating water heating unit |
| CN201320301790.8U Expired - Fee Related CN203374322U (en) | 2013-05-24 | 2013-05-29 | Low-pressure separating board for steam turbine double-rotor exchanging circulating water heat supply |
| CN201320301712.8U Expired - Fee Related CN203374326U (en) | 2013-05-24 | 2013-05-29 | Optimized rear cylinder water spray system |
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| CN201310208998.XA Expired - Fee Related CN103306753B (en) | 2013-05-24 | 2013-05-30 | A kind of steam turbine set cooling water system and chilled(cooling) water supply (CWS) method |
| CN201320355675.9U Expired - Fee Related CN203374329U (en) | 2013-05-24 | 2013-06-21 | Low pressure through-flow structure |
| CN201320355671.0U Expired - Fee Related CN203374328U (en) | 2013-05-24 | 2013-06-21 | Clapboard combination structure for steam turbine |
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| CN104633638A (en) * | 2014-09-01 | 2015-05-20 | 国家电网公司 | Comprehensive control method for function of machine halt without boiler shutdown in power plant FCB |
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| CN111412025A (en) * | 2020-03-26 | 2020-07-14 | 华润电力技术研究院有限公司 | Method and system for monitoring state of high-side system of steam turbine |
| CN111412025B (en) * | 2020-03-26 | 2022-08-02 | 华润电力技术研究院有限公司 | Method and system for monitoring state of high-side system of steam turbine |
| CN111425274A (en) * | 2020-04-16 | 2020-07-17 | 京能(赤峰)能源发展有限公司 | Combined heat and power generation system capable of meeting resident and industrial heat supply requirements during deep peak shaving |
| CN113217119A (en) * | 2021-05-11 | 2021-08-06 | 中国大唐集团科学技术研究院有限公司中南电力试验研究院 | Stability judgment method for steam turbine speed regulating system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN203374325U (en) | 2014-01-01 |
| CN103306753A (en) | 2013-09-18 |
| CN203374321U (en) | 2014-01-01 |
| CN103291391B (en) | 2016-08-10 |
| CN103292383B (en) | 2016-03-23 |
| CN103291391A (en) | 2013-09-11 |
| CN103382860B (en) | 2015-12-02 |
| CN103306753B (en) | 2015-08-12 |
| CN203374329U (en) | 2014-01-01 |
| CN103292383A (en) | 2013-09-11 |
| CN203374326U (en) | 2014-01-01 |
| CN203374320U (en) | 2014-01-01 |
| CN203374328U (en) | 2014-01-01 |
| CN103306758B (en) | 2016-06-01 |
| CN103306758A (en) | 2013-09-18 |
| CN203374323U (en) | 2014-01-01 |
| CN203374324U (en) | 2014-01-01 |
| CN203374322U (en) | 2014-01-01 |
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