CN103382860B - Steam turbine power generation heating system controlling method - Google Patents
Steam turbine power generation heating system controlling method Download PDFInfo
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- CN103382860B CN103382860B CN201310208872.2A CN201310208872A CN103382860B CN 103382860 B CN103382860 B CN 103382860B CN 201310208872 A CN201310208872 A CN 201310208872A CN 103382860 B CN103382860 B CN 103382860B
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Abstract
A kind of steam turbine power generation heating system controlling method; comprise that unit starting controls, boiler protects automatically, bypass warning, low-voltage safety oil guard, generator water cut-off protection, feedwater automatic control, wherein unit starting prepare before controlling the inspection before comprising unit starting, unit ignition, igniting and boosting rectifier 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 the quality of life of huge numbers of families, is day by day paid attention to.So develop new heat supply process to become the good exploration ensureing reliability of heat-supply system, there is important social effect.
Current China heating subsidy is based on extraction for heat supply and little unit rough vacuum back pressure heat supply process, and minority region has and utilizes earth source heat pump to implement for cold-peace heat supply.In addition due to the continuous expansion of area of heat-supply service and Plant reconstruction plant modernization delayed, the boiler heat supplying mode that occupies a narrow space still exists, and this heat-supplying mode not only environmental pollution is serious, and Economy extreme difference.
The heat supply of Large-scale machine set back pressure is current better heat-supplying mode, but the unit run in this way is at non-heat supply phase Economy extreme difference, causes annual economic benefit unsatisfactory.
Extraction for heat supply at present uses maximum heat-supplying modes, but it exists the low and larger phenomenon of cold source energy of utilization ratio of drawing 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 the boiler ratio that recepts the caloric is less, limit generation load, economic benefit is still undesirable, simultaneously because little unit heat capacity is limited, extensive heat demand cannot be met.
From the heating form analysis of the cogeneration units run at present, below 50MW unit generally generally adopts adjustable drawing gas or back pressure unit heat supply.100MW and above unit substantially all adopt sucking condensing type heating form.Performance driving economy under sucking condensing type thermal power plant unit and its heat supply running operating mode of back pressure type unit is far apart.Analyze according to rough vacuum circulating water heating reforming design scheme, in the winter time under heating operating mode, its gross coal consumption rate can reach below 150g/kWh, and takes out solidifying thermal power plant unit best level also at more than 240g/kWh with capacity.Back pressure type unit or rough vacuum circulating water heating unit are compared with sucking condensing type unit, the basic difference of its economical effect of heat-supply is just: back pressure (or rough vacuum circulating water heating) unit is for when running under thermal condition, its cold source energy is all utilized, and sucking condensing type unit only has part to draw gas and be used to heat supply, turbine discharge share reduces to some extent, but still there is larger cold source energy.
For this reason, find that a kind of cold source energy is minimum, generation load and the boiler ratio heat-supplying mode that is higher, that simultaneously meet extensive heat demand that recepts the caloric is the task of top priority.In addition, for current existing heat supply process, for large-scale area heat supply, the technology few in the urgent need to a kind of investment cost, generation load restriction is relatively little, energy-conservation and economic benefit large, Site Implementation strong adaptability, safety reliability are high.To this, the invention provides one " the two back pressure double rotor of low pressure (LP) cylinder exchanges " heating system i.e. " pure condensate-back pressure double-mode " heating system, for this heating system, need the controlling method provided for this heating system.
Summary of the invention
Some embodiment be equivalent within the scope of primitive request of the present invention does following summary.These embodiments unrestricted claimed invention scope, but attempt to provide of the present invention multiple may the brief overview of form.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 controls, boiler protects automatically, bypass warning, low-voltage safety oil guard, generator water cut-off protection, feedwater automatic control; wherein unit starting prepares before controlling the inspection before comprising unit starting, unit ignition, lights a fire and boosting rectifier control; inspection wherein before unit starting comprises; check whether to there is following situations, when depositing in the following cases any one, forbid unit starting:
(1) emergency overspeed governor action abnormal or main inlet throttle-stop valve, throttle, the non-return flap that draws gas are not closed completely;
(2) speed control system can not control rotating speed after can not maintaining idle running or removal of load;
(3) turbine rotor bending break number exceedes cold conditions reference value ± 0.02mm, and wherein cold conditions reference value is measured load after units' installation or overhaul;
(4) Turbo-generator Set sound part has obvious grating;
(5) height, the upper and lower temperature difference of IP inner casing are more than 35 DEG C, and the upper and lower temperature difference of outer shell is more than 50 DEG C;
(6) high intermediate pressure cylinder differential expansion is greater than reference value 6mm or is less than reference value 1mm;
(7) turbine oil and fire-resistant oil oil and turbidity test are defective or turbine oil temperature lower than 25 DEG C;
(8) meter (rotating speed, axial displacement, relative expansion, important meals temperature point etc.) is mainly shown malfunctioning;
(9) protection power source and automatic safety device 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) control system action is abnormal, affects unit starting and normally runs;
(12) boiler drum level protection is imperfect.
Accompanying drawing explanation
To describe according to preferred but nonrestrictive embodiment of the present invention now, these and other features of the present invention, aspect and advantage will become apparent when reading following detailed description in detail with reference to accompanying drawing, wherein:
Fig. 1 is that the present invention is with structural representation during pure condensate rotor operation.
Fig. 2 is that the present invention is with structural representation during 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 to limit the disclosure, application or purposes in essence.Should be understood that, in whole accompanying drawing, corresponding reference character represents identical or corresponding parts and feature.
Fig. 1 is that invention is with structural representation during pure condensate rotor operation.In figure, connect low pressure rotor one end by the High inter case 5 of steam turbine by the second coupling 4, 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, 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 that the present invention is with structural representation during 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, for generating electricity in winter heat supply.Terminate at Heating Season, back pressure heat supply rotor 6 is more gained pure condensate rotor 3, for generating.This steam turbine is specially adapted to go into operation the transformation of big-and-middle-sized unit.Through the unit of transformation, adopt back pressure heat supply rotor 6 at Heating Season, steam turbine runs in back pressure mode, can obtain good economic benefit.This equipment also overcomes the shortcoming that large-scale back pressure unit can not run at non-heating season.Adopt pure condensate rotor 3 at non-heating season, steam turbine will run in pure condensate mode, ensure 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 system of the present invention 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, illustrated therein is Stream temperature degree, main vapour pressure, load trend over time.
Hereafter working procedure of the present invention will be described.
1, basic principle
" the two back pressure double rotor of low pressure (LP) cylinder exchanges " circulating water heating technology, namely, the high back pressure low pressure rotor that newly-designed rotor and stator blade progression reduces relatively is used when heat supply running operating mode, vapour condenser runs high back pressure (30 ~ 45kPa), corresponding exhaust temperature is increased to about 80 DEG C, carries out circulating water heating; At non-heating period, then recovered by former pure condensate rotor, exhaust pressure returns to 4.9kPa, returns to former pure condensate unit operation operating mode completely.Like this, namely unit achieves " double-mode " of " pure condensate-back pressure ".
For the heat transfer requirements of As soon as possible Promising Policy first-degree heating network and secondary heat networks, rough vacuum circulating water heating adopts tandem type two-stage heating system, first heat supply network circulating water carry out first time heating through vapour condenser, absorb low pressure (LP) cylinder exhausted spare heat, and then complete second time heating 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 networks circulating water, unit condenser is returned after high-temperature-hot-water cooling, form a complete circulation waterway, heat supply initial station steam source is that unit mesolow cross over pipe draws gas.
When during heating, rough vacuum circulating water heating operating mode is run, cooling column required under unit pure condensate operating mode and circulating water pump 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.After circulating water loop has switched, the water flow entering vapour condenser is down to 6000-9000t/h, and back pressure of condenser rises to 30 ~ 45kPa by about 5 ~ 7kPa, and low pressure (LP) cylinder exhaust temperature rises to 69 ~ 78 DEG C (saturation temperature that back pressure is corresponding) by 30 ~ 40 DEG C.Heat through the first time of vapour condenser, heat supply network circulating water return water temperature is promoted to 66 ~ 75 DEG C (condenser terminal differences 3 DEG C) by 60 DEG C, then after pumps for hot water supply net boosting, send into initial station heat exchangers for district heating, after heat supply network supply water temperature is heated to 85-90 DEG C further, feed to a heat supply network.
Unit, when pure condensate operating mode is run, exits pumps for hot water supply net and heat exchangers for district heating operation, and recover former circulating water pump and cooling tower operation, back pressure of condenser returns to 5 ~ 7kPa.
From the systematic parameter of design rough vacuum circulating water heating technology, because steam turbine long-term stability is run by exhaust temperature not higher than the restriction of 80 DEG C, consider condenser terminal difference, the circulating water water-exit temperature of Heat Supplying with Low Vacuum is general not higher than 75 DEG C, water supply, return water temperature scope are generally water supply 60 DEG C ~ 75 DEG C, 50 DEG C ~ 60 DEG C, backwater, and corresponding operation back pressure is 25 ~ 45kPa.
It should be noted that, for rough vacuum circulating water heating, circulating water return water temperature should be reduced as far as possible, farthest to utilize low pressure (LP) cylinder exhaust steam heat, otherwise not only low pressure (LP) cylinder heat exhaust can not obtain high efficiency utilization, also can cause low pressure (LP) cylinder exhaust temperature overtemperature, considerable influence is brought to the safe and reliable operation of steam turbine.
Consider the change actual conditions of vapour condenser operating conditions, determine that the design philosophy transformed is: under the prerequisite realizing Heating Period and non-heating period thermal procession, Heating Period ensures the Security of vapour condenser equipment, and non-heating period (i.e. pure condensate operating mode) ensures the Economy of vapour condenser equipment.Although the Operational Limits of circulating water heating phase vapour condenser is far above Operational Limits during pure condensate operating mode, the running state (fluid properties, heat exchange mode, pressure, temperature grade) of Steam Side of Condenser and water side does not have the change of matter.So retaining the throat, shell, bottom support etc. of existing vapour condenser, is feasible to condenser retrofit on this basis completely.Restrain simultaneously and arrange that transforming situation according to high back pressure has carried out targeted design, to meet the long-time running under heating and pure condensate operating mode.
Introduce steam-turbine unit running below.
1, the startup of unit
Unit starting is forbidden under 1.1 following situations
(1) emergency overspeed governor action abnormal or main inlet throttle-stop valve, throttle, the non-return flap that draws gas are not closed completely;
(2) speed control system can not control rotating speed after can not maintaining idle running or removal of load;
(3) turbine rotor bending break number exceedes cold conditions reference value ± 0.02mm, and wherein cold conditions reference value is measured load after units' installation or overhaul;
(4) Turbo-generator Set sound part has obvious grating;
(5) height, the upper and lower temperature difference of IP inner casing are more than 35 DEG C, and the upper and lower temperature difference of outer shell is more than 50 DEG C;
(6) high intermediate pressure cylinder differential expansion is greater than reference value 6mm or is less than reference value 1mm;
(7) turbine oil and fire-resistant oil oil and turbidity test are defective or turbine oil temperature lower than 25 DEG C;
(8) meter (rotating speed, axial displacement, relative expansion, important meals temperature point etc.) is mainly shown malfunctioning;
(9) protection power source and automatic safety device not normal.
(10) Boiler Furnace Safeguard Supervisory System (FSSS, FurnaceSafetySupervisionSystem), digital electro-hydraulic control system (DEH, DigitalElectro-HydraulicControlSystem), Steam Turbine Safety Monitoring System (TSI, TurbineSupervisoryInstrumentation), steam turbine trip protection system (ETS, Emergencytripsystem) device can not normally drop into;
(11) control system action is abnormal, affects unit starting and normally runs;
(12) boiler drum level protection is imperfect.
When above-mentioned all situations does not exist, allow unit starting.
Inspection before 1.2 unit startings
Prepare before unit ignition
(1) under confirming all machine supplying powders, powder plate washer in off position.
(2) condensate pump is started.
(3) start feed water pump to boiler feed water, when steam water-level proceed to-300mm time, close each feedwater adjustment doors, isolation door, stop feed water pump, close the total door of feedwater, open 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 igniting and boosting
(1) start preheater oil pump, start preheater.
(2) start suction, gas fan, air output is inhaled in adjustment, maintains combustion chamber draft-50Pa, keeps the above air quantity of 30% rated load.(3) confirm that each oil gun angle valve is closed tight, start fuel pump, adjustment oil pressure, to more than 2.6MPa, determines fuel leakage pass the test.
(4) start fire inspection cooling blower normal after, the condition that purges meets, and carries out furnace purge.
(5), after burner hearth " purging completes ", oil-feed quick-break valve is opened.
(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) master, again steam by-pass system is dropped into, adjustment condenser vacuum.
(9) when saturated vapour pressure rises to 0.15 ~ 0.2MPa, steam water-level meter is rinsed.
(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) hydrophobicly before electronic main shutter be switched to behind the door, open electronic main shutter.
(12) when saturated vapour pressure rises to 0.5MPa, adjacent stove is stopped to heat.
(13) when reheater inlet pressure reaches 0.1 ~ 0.3MPa, reheater cold junction draining valve is closed.
(14) control rate of rise 0.05MPa/min, Stream temperature warming velocity 1 DEG C/min and drum up-draft gasifier are not more than 40 DEG C.
(15) according to exhaust temperature, cylinder water spray after dropping into.
(16) persistent surveillance cylinder temperature, checks the tight situation of high-pressure main throttle 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 takes out female pipe vapour source heating coil to surge tank with three.
(18) coagulator water level is adjusted.
(19) open water cooled furnace wall lower collecting box sewage door, interrupted blow down, makes each portion be heated evenly, sets up water circulation as early as possible.
(20) during steam water-level+50mm, start feed water pump boiler feed water, close economizer recirculation.Timely input cooling water.
(21) main steam pressure reaches 1.86 ~ 2.06MPa, steam temperature more than 370 DEG C, reheat steam temperature more than 250 DEG C.
(22) send vapour to shaft seal, operation vacuum breaking door, keeps condenser vacuum 59-75kPa.
2, boiler is protected automatically
It is take the automatic Protection to equipment in the middle of boiler operatiopn that boiler is protected automatically, when there is abnormal accident, reports to the police or arrestment operation automatically.
The automatic protection act starting condition of boiler comprises:
A tripping operation in (1) two suction fan
A tripping operation in (2) two gas fans
One in (3) two mill exhausters is tripped and drops into without oil gun
(4) steam water-level is greater than reference value 250mm and continues 10 seconds
(5) steam water-level is less than reference value 250mm and continues 10 seconds
(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
Occur that following situations for the moment, bypath system sends warning
(1) while of the valves such as high other decompression, the decompression of low side, high other desuperheat, low other desuperheat during standard-sized sheet.
(2) high other outlet temperature and definite value deviation are greater than predetermined value
(3) low other outlet 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) by-pass reducing valve is opened, desuperheat valve do not open.
10) automatic switching is fashionable, when instruction, feedback deviation are greater than 30%.
4, low-voltage safety oil guard
When low-voltage safety oil (turbine oil) oil pressure is down to 0.45MPa, membrane valve is opened, venting high voltage control oil, closes high, intermediate pressure main stop valve, throttle, the non-return flap that draws gas at different levels.
5, generator water cut-off protection
works as generator amature or stator flow of inlet water is reduced to 10t/h, and Pressure Drop is low to moderate 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 in normal operation, and water level should remain on 0, and normal fluctuation range is ± 50mm.
Boiler water level should be as the criterion with drum pressure difference water gauge, and combustion adjustment, and to be counted with reference to the table such as feedwater, steam flow for foundation with drum electric contact.Require the feeding boiler of feedwater continuous uniform, avoid large adjustment.
Steam water-level meter should be clear, sufficiency of illumination, without leaking vapour, water leakage phenomenon.Mica water-level gauge water line answers slight fluctuations, if when water level does not fluctuate or sheet mica is smudgy, should rinse in time, magnetic turnover panel water-level gauge magnetic turnover panel is consistent continuously, otherwise should contact overhaul plan.
When feedwater automatic switching is fashionable, often should monitor the instruction of each table meter, when water level exceed ± 50mm and continue change time, manual adjustment should being switched in time, preventing from causing the full lack of water of boiler because monitoring tight.
When there is following situations for the moment, feedwater automatic control will exit automatically:
(1) steam water-level signal is malfunctioning
(2) main steam flow signal is malfunctioning
(3) 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
Feedwater should carry out manual tune after automatically exiting voluntarily in time.After water level is normal, then drop into feedwater automatically.
Each water level gauge meter must indicate correctly, and per tour and local water level meter are proofreaded twice.The high and low alarm signal of steam water-level is reliable, monthly regularly verifies.
Meet following situations, supervision and the adjustment of steam water-level should be strengthened, prevent from lacking, full water.
1) in igniting process, when red switch, raising speed, side by side, load up time.
2) during safety valve action.
3) feed water automatic malfunctioning time.
4) feed water pump work is abnormal, or feed water pump coupler scoop tube bite.
5) accident wicket is not closed tight.
6) pressure-containing member leaks serious.
7) during periodical blowdown.
8) when vapour pressure or load have a larger fluctuation.
9) height adds the throwing stopping time.
10) when feed water by-pass switches or switches feed water pump.
This specification disclose in detail the present invention, comprises optimal mode, and anyone that also can make related domain puts into practice the present invention, comprises the method manufacturing and use any equipment or system and perform any introducing.Protection scope of the present invention by appended claims, and can be included in the various modification made for the present invention of pin when not departing from scope and spirit, remodeling and equivalents.
Claims (6)
1. a steam turbine power generation heating system controlling method; comprise that unit starting controls, boiler protects automatically, bypass warning, low-voltage safety oil guard, generator water cut-off protection, feedwater automatic control; wherein unit starting prepares before controlling the inspection before comprising unit starting, unit ignition, lights a fire and boosting rectifier control; inspection wherein before unit starting comprises; check whether to there is following situations, when depositing in the following cases any one, forbid unit starting:
(1) emergency overspeed governor action abnormal or main inlet throttle-stop valve, throttle, the non-return flap that draws gas are not closed completely;
(2) speed control system can not control rotating speed after can not maintaining idle running or removal of load;
(3) turbine rotor bending break number exceedes cold conditions reference value ± 0.02mm, and wherein cold conditions reference value is measured load after units' installation or overhaul;
(4) Turbo-generator Set sound part has obvious grating;
(5) height, the upper and lower temperature difference of IP inner casing are more than 35 DEG C, and the upper and lower temperature difference of outer shell is more than 50 DEG C;
(6) high intermediate pressure cylinder differential expansion is greater than reference value 6mm or is less than reference value 1mm;
(7) turbine oil and fire-resistant oil oil and turbidity test are defective or turbine oil temperature lower than 25 DEG C;
(8) main table meter is malfunctioning;
(9) protection power source and automatic safety device 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) control system action is abnormal, affects unit starting and normally runs;
(12) boiler drum level protection is imperfect;
Described low-voltage safety oil guard comprises, and when low-voltage safety oil oil pressure is down to 0.45MPa, membrane valve is opened, venting high voltage control oil, closes high, intermediate pressure main stop valve, throttle, the non-return flap that draws gas at different levels;
Described generator water cut-off protection comprises, and when generator amature or stator flow of inlet water are reduced to 10t/h, Pressure Drop is low to moderate 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.
2. the method for claim 1, is characterized in that, prepares to comprise before described unit ignition:
(1) under confirming all machine supplying powders, powder plate washer in off position;
(2) condensate pump is started;
(3) start feed water pump to boiler feed water, when steam water-level proceed to-300mm time, close each feedwater adjustment doors, isolation door, stop feed water pump, close the total door of feedwater, open 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.
3. the method for claim 1, is characterized in that, described boiler is automatically protected and comprised, and takes the automatic Protection to equipment in the middle of boiler operatiopn, when there is at least one in following situations, to report to the police or arrestment runs automatically:
A tripping operation in (1) two suction fan;
A tripping operation in (2) two gas fans;
One in (3) two mill exhausters is tripped and drops into without oil gun;
(4) steam water-level is greater than reference value 250mm and continues 10 seconds;
(5) steam water-level is less than reference value 250mm and continues 10 seconds;
(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, described bypass is reported to the police and comprised, and occur that following situations is for the moment, bypath system sends warning:
(1) high other pressure loading valve, low other pressure loading valve, high other desuperheat valve, low other desuperheat valve simultaneously standard-sized sheet time;
(2) high other outlet temperature and definite value deviation are greater than predetermined value;
(3) low other outlet 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) by-pass reducing valve is opened, desuperheat valve do not open;
(10) automatic switching is fashionable, when instruction, feedback deviation are greater than 30%.
5. the method for claim 1, is characterized in that, described igniting and boosting rectifier control comprise:
(1) start preheater oil pump, start preheater;
(2) start suction, gas fan, air output is inhaled in adjustment, maintains combustion chamber draft-50Pa, keeps the above air quantity of 30% rated load; (3) confirm that each oil gun angle valve is closed tight, start fuel pump, adjustment oil pressure, to more than 2.6MPa, determines fuel leakage pass the test;
(4) start fire inspection cooling blower normal after, the condition that purges meets, and carries out furnace purge;
(5), after burner hearth " purging completes ", oil-feed quick-break valve is opened;
(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) master, again steam by-pass system is dropped into, adjustment condenser vacuum;
(9) when saturated vapour pressure rises to 0.15 ~ 0.2MPa, steam water-level meter is rinsed;
(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) hydrophobicly before electronic main shutter be switched to behind the door, open electronic main shutter;
(12) when saturated vapour pressure rises to 0.5MPa, adjacent stove is stopped to heat;
(13) when reheater inlet pressure reaches 0.1 ~ 0.3MPa, reheater cold junction draining valve is closed;
(14) control rate of rise 0.05MPa/min, Stream temperature warming velocity 1 DEG C/min and drum up-draft gasifier are not more than 40 DEG C;
(15) according to exhaust temperature, cylinder water spray after dropping into;
(16) persistent surveillance cylinder temperature, checks the tight situation of high-pressure main throttle 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 takes out female pipe vapour source heating coil to surge tank with three;
(18) coagulator water level is adjusted;
(19) open water cooled furnace wall lower collecting box sewage door, interrupted blow down, makes each portion be heated evenly, sets up water circulation as early as possible;
(20) during steam water-level+50mm, start feed water pump boiler feed water, close economizer recirculation; Timely input cooling water;
(21) main steam pressure reaches 1.86 ~ 2.06MPa, steam temperature more than 370 DEG C, reheat steam temperature more than 250 DEG C;
(22) send vapour to shaft seal, operation vacuum breaking door, keeps condenser vacuum 59-75kPa.
6. the method for claim 1, is characterized in that, described feedwater automatic control comprises, and when there is following situations for the moment, feedwater automatic control will exit automatically:
(1) steam water-level signal is malfunctioning;
(2) main steam flow signal is malfunctioning;
(3) 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 |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310197546 | 2013-05-24 | ||
| CN201310197546.6 | 2013-05-24 | ||
| CN201310208872.2A CN103382860B (en) | 2013-05-24 | 2013-05-30 | Steam turbine power generation heating system controlling method |
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| Publication Number | Publication Date |
|---|---|
| CN103382860A CN103382860A (en) | 2013-11-06 |
| CN103382860B true CN103382860B (en) | 2015-12-02 |
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| Application Number | Title | Priority Date | Filing Date |
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| 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 |
| 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 |
| 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 |
| CN201320301482.5U Expired - Fee Related CN203374324U (en) | 2013-05-24 | 2013-05-29 | Low-pressure circulating component |
| CN201320301788.0U Expired - Fee Related CN203374321U (en) | 2013-05-24 | 2013-05-29 | Moving blade of low-pressure rotor |
| CN201320301484.4U Expired - Fee Related CN203374323U (en) | 2013-05-24 | 2013-05-29 | Low-pressure front-back shaft sealing parts |
| CN201320301786.1U Expired - Fee Related CN203374325U (en) | 2013-05-24 | 2013-05-29 | Connecting structure between condenser throat portion and steam turbine exhaust port |
| 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 |
| CN201320301712.8U Expired - Fee Related CN203374326U (en) | 2013-05-24 | 2013-05-29 | Optimized rear cylinder water spray system |
| 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 |
| 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 |
| CN201310208872.2A Expired - Fee Related CN103382860B (en) | 2013-05-24 | 2013-05-30 | Steam turbine power generation heating system controlling 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 |
Family Applications Before (11)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| 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 |
| 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 |
| 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 |
| CN201320301482.5U Expired - Fee Related CN203374324U (en) | 2013-05-24 | 2013-05-29 | Low-pressure circulating component |
| CN201320301788.0U Expired - Fee Related CN203374321U (en) | 2013-05-24 | 2013-05-29 | Moving blade of low-pressure rotor |
| CN201320301484.4U Expired - Fee Related CN203374323U (en) | 2013-05-24 | 2013-05-29 | Low-pressure front-back shaft sealing parts |
| CN201320301786.1U Expired - Fee Related CN203374325U (en) | 2013-05-24 | 2013-05-29 | Connecting structure between condenser throat portion and steam turbine exhaust port |
| 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 |
| CN201320301712.8U Expired - Fee Related CN203374326U (en) | 2013-05-24 | 2013-05-29 | Optimized rear cylinder water spray system |
| 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 |
| 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 |
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| Application Number | Title | Priority Date | Filing Date |
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| 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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Also Published As
| Publication number | Publication date |
|---|---|
| CN203374321U (en) | 2014-01-01 |
| CN203374324U (en) | 2014-01-01 |
| CN103291391B (en) | 2016-08-10 |
| CN103382860A (en) | 2013-11-06 |
| CN103291391A (en) | 2013-09-11 |
| CN103292383A (en) | 2013-09-11 |
| CN203374325U (en) | 2014-01-01 |
| CN203374320U (en) | 2014-01-01 |
| CN203374326U (en) | 2014-01-01 |
| CN103306758A (en) | 2013-09-18 |
| CN203374329U (en) | 2014-01-01 |
| CN203374328U (en) | 2014-01-01 |
| CN103306753A (en) | 2013-09-18 |
| CN103306758B (en) | 2016-06-01 |
| CN203374322U (en) | 2014-01-01 |
| CN203374323U (en) | 2014-01-01 |
| CN103306753B (en) | 2015-08-12 |
| CN103292383B (en) | 2016-03-23 |
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