CN101864994B - Correction method for optimization of sliding pressure of large steam turbine - Google Patents
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Abstract
The invention discloses a correction method for optimization of sliding pressure of a large steam turbine generator set of a power plant. The current research on optimization of the sliding pressure of the large steam turbine generator set operating under the low load to ensure that the generator set can operate with excellent performance under the sliding pressure during the low-load operation has great significance in improvement of the operating efficiency of the generator set. The correction method is characterized in that correction factors are adopted to correct the sliding pressure control curve of the generator set, that is, the relevance relation of the load of the generator set, the main steam pressure and the opening of the high-pressure regulating valve is expressed as Cn*Ng varies as Cp*P0*Cv. Since the specific correction factors are introduced for control elements, the load of the generator set and the main steam pressure of the control curve of the generator set under the sliding pressure in the sliding pressure deviation factor correction method, the invention ensures that the steam turbine generator is in the mode of operating under the best sliding pressure, and can maintain the high operating efficiency of the generator set all the time.
Description
Technical field
The present invention relates to a kind of method for correcting of large turbo-type generator group optimization of sliding pressure of thermal power plant.
Background technique
Because socioeconomic development, society is to the resource requirement rapid growth, and it is nervous that electric coal supply also is tending towards, and the continuous rise of coal price has directly caused the increase of cost of electricity-generating, and Electricity Tariff Linkage mechanism is subjected to the impact of national macroeconomic environment and lag behind.Everything has all caused huge operated pressure to electricity power enterprise, and enterprise profit declines to a great extent even loss occurs.The work that electricity power enterprise can carry out is exactly to reduce specific energy consumption, reduce cost of electricity-generating as far as possible.Therefore, the energy saving in running of fired power generating unit consumption reduction has become the desirability of Business survival.
The large turbo-type generator group in thermal power plant can be taked the hybrid sliding-pressure operation mode usually in daily variable load operation process: take the fixed pressure operation mode in high load region, mainly rely on the change of high-pressure governing valve valve position to regulate unit load; Take the sliding pressure operation mode at low load region, mainly rely on the change of main steam pressure to regulate unit load, the high-pressure governing valve valve position is then substantially constant.To each unit, manufactory generally can provide the steam turbine hybrid sliding-pressure operation control curve of a design, realizes above-mentioned hybrid sliding-pressure operation mode, thereby guarantees that unit is in the more excellent state of performance driving economy.Yet; in steam turbine day-to-day operation process; along with the conversion in season causes that condenser pressure changes or because the external extraction for heat supply of unit causes main steam flow increase etc.; the high-pressure governing valve aperture that steam turbine control system is provided departs from the best sliding pressure valve position of anticipation, and this will produce adverse influence to unit sliding pressure operation efficient.
At present, along with 600, the impact that puts into operation successively of the large capacity unit such as 1000MW, the unit average load rate of each electricity power enterprise further descends, the underrun time increases thereupon, therefore, carry out the optimization of sliding pressure method research in large turbo-type generator group underrun stage, keep unit to be in the more excellent sliding pressure operation mode of performance in low load stage, be of great significance improving unit operation efficiency situation tool.
Summary of the invention
Technical problem to be solved by this invention is to overcome the defective that above-mentioned prior art exists, the sliding pressure drift correction method in a kind of large-size steam turbine load operation stage is provided, unit load operation phase sliding pressure operation control curve is revised, make steam turbine under actual sliding pressure mode, can keep best sliding pressure valve position, to reach energy-saving and cost-reducing purpose always.
For a concrete Turbo-generator Set, in the situation that unit operation parameter and thermodynamic system running state all change little, unit load becomes one to one variation relation with main steam flow, and main steam flow is regulated porthole aperture, main steam pressure variation relation in direct ratio with turbine high-pressure, and relation interrelated between unit load, main steam pressure and this three of high-pressure governing valve aperture, mutual restriction explained in the formulistic language below adopting:
N
g∝P
0×C
v (1)
In the formula (1), N
gBe unit load, P
0Be main steam pressure, C
vBe the instruction of high-pressure governing valve aperture, it can see a linearization as, the reflection several high-pressure regulation porthole apertures comprehensive parameters.
Can find out from top relation, unit load is proportional to main steam pressure and high-pressure regulation porthole aperture is long-pending, and this can see the primary relationship formula of steam turbine load control as.Yet, in the steam turbine actual moving process, along with the change of all kinds of operating conditionss of unit, if unit load N
gWith main steam pressure P
0Between continue to keep fixing linear corresponding relation, then turbine high-pressure is regulated the porthole aperture larger change will be occured, and departs from the best sliding pressure valve position of anticipation, thereby unit sliding pressure operation efficient is produced adverse influence.
For this reason, the technical solution used in the present invention is: utilize correction factor that unit sliding pressure control curve is revised, thus, the incidence relation formula between unit load, main steam pressure and this three of high-pressure governing valve aperture of explaining of formula (1) can be transformed into:
C
n×N
g∝C
p×P
0×C
v (2)
In the formula (2), C
nBe the total correction factor of unit operation parameter variation to unit load,
C
n=C
N1* C
N2* ... * C
Nk, C
NkRepresent that every Operational Limits deviation is to the correction factor of unit load.
C
PBe the total correction factor of unit thermodynamic system running state variation to main steam pressure,
C
P=C
P1* C
P2* ... * C
Pk, C
PkRepresent that every thermodynamic system deviation is to the correction factor of main steam pressure.
Introduce the computational methods that Operational Limits is revised the load of sliding pressure control curve, be exactly the condenser pressure during according to the steam turbine actual motion, main stripping temperature, reheat temperature etc. and the deviation situation of design load, calculate every Operational Limits and change the correction factor C that causes the unit load respective change
N1, C
N2... C
Nk, product and the unit actual motion load of these correction factors multiplied each other, just can calculate revised unit load C
n* N
g, with this as the abscissa in the unit sliding pressure control curve.
Similarly, introduce the thermodynamic system running state and change the computational methods that the main steam pressure of sliding pressure control curve is revised, every running statees such as the situation that externally puts into operation for heat flow, boiler cooling water flow and heater according to actual set exactly change the amplitude of variation that causes main steam flow, try to achieve each the partial factors coefficient C to main steam pressure (when the pitch aperture is constant, main steam pressure and main steam flow variation relation in direct ratio)
P1, C
P2... C
Pk, multiply by with these correction factors and from unit sliding pressure control curve, to look into main steam pressure (y coordinate parameter) P that gets
0, just can calculate revised unit main steam pressure C
P* P
0, and with this sliding pressure operation main steam pressure control desired value as unit CCS.
The above is the universal method for correcting of unit optimization of sliding pressure control curve, after using this method for correcting, steam turbine control system can be adjusted automatically along with the operating conditions change corresponding relation between main steam pressure and the unit load, thereby guarantees that steam turbine is in the more excellent sliding pressure operation mode of performance always.When specifically being applied in certain operating unit, can suitably simplify according to the unit actual operating state.For example, when carrying out every Operational Limits adjustment in the whole low-load sliding pressure operation stage, main steam temperature, reheat steam temperature generally all with rating value as control target, amplitude of variation is little, only have condenser pressure along with the ambient temperature change in winter, summer larger variation to be arranged, so get condenser pressure as main variable effect factor, unit load revised.In addition, the equipment such as the heater of unit thermodynamic system, feed water pump generally all are in normal running state, and for other operation thermodynamic system changing factors, whether the external heat supply of unit may be greater on the impact of steam turbine main steam pressure (not becoming controlled conditions with the pitch aperture), so the heat supply changes in flow rate is revised main steam pressure as main influence factor.
One, change the adverse effect that unit sliding pressure control curve is used in order effectively to get rid of condenser pressure, in the unit sliding pressure control, introduce " condenser pressure modifying factor ", and with C
N1Expression " condenser pressure modifying factor ", C
N1Can be calculated by following formula:
C
n1＝1+ΔP
c×C
0 (3)
In formula (3),
Δ P
cBe the difference of vapour condenser operating pressure and reference pressure, usually get Condenser Design pressure as reference pressure; The vapour condenser operating pressure can obtain by actual measurement, also can convert by the exhaust temperature of steam turbine and obtain, the site test comparison shows: this replacing method of asking for condenser pressure has enough precision, can satisfy the needs that calculate " condenser pressure modifying factor " in the unit sliding pressure operation control procedure fully.
C
0For the correction factor of the every variation of condenser pressure 1kPa to unit output, can choose according to the design data that manufactory provides, also can obtain by actual tests.
Two, the adverse effect of in order effectively to get rid of the heat supply changes in flow rate unit sliding pressure control curve being used is introduced in the unit sliding pressure control " the heat supply flow correction factor ", and with C
P1Expression " the heat supply flow correction factor ", C
P1Can be calculated by following formula:
C
P1＝1+(F
gr/F
ms)×C
h(4)
In formula (4),
(F
Gr/ F
Ms) for account for the percentage of main steam flow for heat flow;
C
hFor for heat flow to the steam turbine initial steam pressure (under fixing pitch aperture, be equivalent to steam turbine admission flow) correction factor, namely account for the every increase by 1% of percentage of main steam flow, cause the scaling factor that steam turbine admission flow increases, this scaling factor can calculate by " Equivalent Entropy Drop Method " and obtain.
In addition, if carry out unit heat supply and the not actual comparative test of Heating State, then can directly obtain comparatively definite main steam pressure correction factor C
P1
The present invention adopts sliding pressure bias factor revised law that unit load and the main steam pressure control key element of unit sliding pressure operation control curve are introduced specific correction factor, make the control system of steam turbine set can adapt to the variation of extraneous operating conditions, in time change its sliding pressure operation control parameter, thereby guarantee that steam turbine is in best sliding pressure operation mode, thereby realize that unit is in higher operational efficiency always.
Take the present invention can make unit be in the sliding pressure operation mode of comparatively optimizing, the net coal consumption rate of saving Turbo-generator Set reaches 1g/kWh, by a normal operating load rate conversion of 600MW unit, can save the coal-fired cost expense every year and reach 1,800,000 yuan, obtain good energy-saving run effect.
Below in conjunction with the explanation the drawings and specific embodiments substantive distinguishing features of the present invention is described further.
Description of drawings
Fig. 1 is that the present invention is applied on the Supercritical 600 MW Steam Turbine group, consideration season in summer (winter) condenser pressure changes the optimization of sliding pressure control curve of revising.
Fig. 2 is that the present invention is applied on the 125MW steam turbine set, considers the optimization of sliding pressure control curve that the heat supply flow correction is forward and backward.
Embodiment
The application of embodiment's 1 condenser pressure modifying factor
In unit optimization of sliding pressure control, introduce " condenser pressure modifying factor ", be equivalent to original fixing, unalterable sliding pressure control curve is become as changing self-adjusting cluster sliding pressure control curve according to condenser pressure at any time.Correspondingly, unit is fixed, sliding pressure transition point load also is in and constantly adjusts state, is in " best sliding pressure valve position " state to guarantee turbine high-pressure governing valve.The situation that the below changes with condenser vacuum take fixed, the sliding pressure transition point of an overcritical 600MW unit illustrates application process and the effect of " condenser pressure modifying factor " as example.
This unit has drawn unit sliding pressure control curve by the optimization of sliding pressure test, determines that unit is fixed, the unit load of sliding pressure turning point is 570MW.In test result computational process, the unit output of each operating condition of test has all been carried out the corrected Calculation of Operational Limits (comprising condenser pressure) off-design value.Therefore, calmly, sliding pressure turning point load 570MW is definite take Condenser Design pressure 5.5kPa as basis of reference.
When unit moves at the 600MW rated loan condition, the every variation of turbine back pressure 1kPa, unit output, heat consumption rate amplitude of variation are about 0.954%; When unit moves at the 300MW load condition, the every variation of turbine back pressure 1kPa, unit output, heat consumption rate amplitude of variation are about 1.247%.According to this test result, when this type unit is carried out the correction of sliding pressure control curve, can choose approx condenser pressure and change the correction factor C that exerts oneself corresponding to 1kPa
0=1% this fixing correction factor.
As can be seen from Figure 1, when this unit during at the summer condition rated load operation, along with the rising of ambient temperature, circulating water temperature can rise to about 40 ℃, and the actual turbine low pressure cylinder exhaust temperature that records is especially up to 46 ℃.Can detect according to the corresponding relation between condenser pressure and the exhaust temperature, the condenser pressure of this moment should be 10kPa, and 5.5kPa compares with Condenser Design pressure, obviously higher 4.5kPa.Get this unit vacuum and change correction factor C
0=1%, then can calculate " condenser pressure modifying factor " C of this operating conditions according to formula (3)
N1=1.045.Correspondingly, through revised unit " nominal load " be: C
N1* N
g=1.045 * 570=596MW.Result of calculation shows thus, and under summer condition high back pressure operating conditions, unit is fixed, the unit load of sliding pressure turning point should move to 596MW from 570MW.
As can be seen from Figure 1, when unit operating mode when operation in the winter time, the actual turbine low pressure cylinder exhaust temperature that records is 27 ℃, and corresponding condenser pressure should be 3.5kPa, and 5.5kPa compares with Condenser Design pressure, 2kPa obviously on the low side.Adopt formula (3) can calculate " condenser pressure modifying factor " C
N1=0.98, revised unit " nominal load " is: C
N1* N
g=0.98 * 570=558MW.Namely in the winter time under the operating mode condenser pressure actual motion condition on the low side, unit is fixed, the unit load of sliding pressure turning point should be displaced downwardly to 558MW from 570MW.
Can find out from top result of calculation owing to being subjected to the impact that significantly changes in summer, winter condition condenser vacuum, unit fixed, the sliding pressure turning point of summer, winter condition need to move, move down total amplitude of variation will be up to 38MW.
By above comparative analysis result as can be known, for summer, the larger operating conditions of condenser pressure deviation amplitude in winter, by introducing " condenser pressure modifying factor ", the actual set load of unit sliding pressure control curve can be revised to Condenser Design pressure, can realize the suitable translation of unit sliding pressure control curve, thereby guarantee that corresponding relation between turbine high-pressure governing valve aperture and the unit load can replicate test or the state during design.
The application of embodiment's 2 heat supply flow correction factors
As shown in Figure 2, the fine line among the figure is two valve standard-sized sheet sliding pressure operation main steam pressure change curves under the Heating State not, and the fitting formula of this sliding pressure curve is: Y=0.11927X+0.755, wherein Y is main steam pressure, units MPa, X is unit load, the MW of unit; Dotted line has represented the main steam pressure change curve of two valve standard-sized sheet sliding pressure operations of the external heat supply 16t/h of this unit state, and corresponding two valve sliding pressure master vapour pressure fitting formulas are: Y=0.12003X+1.120.After two curves among the figure are compared as can be known, when the same unit operation electric load of tape splicing, the main steam pressure setting value of unit Heating State will be higher than not Heating State, and average higher amplitude is about 4%, can calculate thus unit " the heat supply flow correction factor " C
P1=1.04.Do not obtain main steam pressure P if do not look into the two valve sliding pressure operations control curve of Heating State from unit
0, multiply by again this " heat supply flow correction factor " C
P1, can obtain this unit and finish for the revised main steam pressure control value of heat affecting: C
P1* P
0=1.04P
0It can also be seen that from Fig. 2, the intersection point load of heat supply, these two sliding pressure operation lines of not heat supply and fixed pressure operation line is respectively 104MW and 107MW, has reflected the change conditions that unit is fixed, the meeting of sliding pressure transition point load decreases owing to external heat supply.
By above comparative analysis result as can be known, practical operation situation for unit heat supply, not heat supply, introducing " the heat supply flow correction factor " is carried out corrected Calculation to the main steam pressure of unit sliding pressure control curve, can guarantee under the precondition that the turbine high-pressure governing valve aperture remains unchanged, by suitable raising main steam pressure, satisfy the main steam flow demand of cogeneration of heat and power.
Claims (7)
1. the method for correcting of an optimization of sliding pressure of large steam turbine is characterized in that utilizing correction factor that unit sliding pressure control curve is revised, and the incidence relation formula that is about between unit load, main steam pressure and this three of high-pressure governing valve aperture is expressed as: C
n* N
g∝ C
p* P
0* C
v, in the formula, C
nBe the total correction factor of unit operation parameter variation to unit load, C
n=C
N1* C
N2* ... * C
Nk, C
NkRepresent that every Operational Limits deviation is to the correction factor of unit load; C
PBe the total correction factor of unit thermodynamic system running state variation to main steam pressure, C
P=C
P1* C
P2* ... * C
Pk, C
PkRepresent that every thermodynamic system deviation is to the correction factor of main steam pressure.
2. the method for correcting of optimization of sliding pressure of large steam turbine according to claim 1 is characterized in that introducing condenser pressure modifying factor C in the unit sliding pressure control when the conversion in season causes that significantly changing appears in the condenser pressure of large-size steam turbine
N1, C
N1Calculated by following formula: C
N1=1+ Δ P
c* C
0, the Δ P in the formula
cBe the difference of vapour condenser operating pressure and reference pressure, get Condenser Design pressure as reference pressure, C
0Be the correction factor of the every variation of condenser pressure 1kPa to unit output.
3. the method for correcting of optimization of sliding pressure of large steam turbine according to claim 2 is characterized in that condenser pressure obtains or obtains by actual measurement by the exhaust temperature conversion of steam turbine.
4. according to claim 2 or the method for correcting of 3 described optimization of sliding pressure of large steam turbine, it is characterized in that C
0The design data that provides according to manufactory is chosen or is obtained by actual tests.
5. the method for correcting of optimization of sliding pressure of large steam turbine according to claim 1 and 2 is characterized in that introducing heat supply flow correction factor C in the unit sliding pressure control when large-size steam turbine is externally done significantly to adjust because of the hot user's in the external world requirement for heat flow
P1, steam turbine control system can be according to the corresponding relation of automatically adjusting for the situation of change of heat flow between main steam pressure and the unit load, C
P1Calculated by following formula: C
P1=1+ (F
Gr/ F
Ms) * C
h, (the F in the formula
Gr/ F
Ms) for account for the percentage of main steam flow, C for heat flow
hFor supplying heat flow to the correction factor of steam turbine initial steam pressure, the every increase by 1% of percentage that namely accounts for main steam flow causes the scaling factor that steam turbine admission flow increases.
6. the method for correcting of optimization of sliding pressure of large steam turbine according to claim 5 is characterized in that C
hCalculate acquisition by Equivalent Entropy Drop Method.
7. the method for correcting of optimization of sliding pressure of large steam turbine according to claim 5 is characterized in that when carrying out the comparative test of unit heat supply and Heating State not, then the direct comparatively definite main steam pressure correction factor C of acquisition
P1
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| CN108646558A (en) * | 2018-05-10 | 2018-10-12 | 湖南省湘电试验研究院有限公司 | A kind of Energy-saving for Thermal Power Units type sliding pressure real-time optimization method and system |
| CN111352400B (en) * | 2020-03-13 | 2021-05-07 | 中国大唐集团科学技术研究院有限公司华东电力试验研究院 | Heat supply unit sliding pressure operation optimization method and sliding pressure operation control system |
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| CN111927576B (en) * | 2020-07-29 | 2022-07-12 | 杭州意能电力技术有限公司 | Method for testing no-load energy consumption of steam turbine generator unit |
| CN114961890B (en) * | 2022-06-02 | 2024-02-13 | 国网河北能源技术服务有限公司 | Sliding pressure operation optimization method for steam turbine unit in heat supply period |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101079199A (en) * | 2006-05-22 | 2007-11-28 | 三菱重工业株式会社 | Gas turbine output learning circuit and combustion control device for gas turbine |
| CN101446807A (en) * | 2008-08-15 | 2009-06-03 | 中国电力科学研究院 | Realization method for heat-engine plant speed regulating system model in power system simulation |
| CN101504135A (en) * | 2009-03-06 | 2009-08-12 | 华北电力大学 | Steam pressure equalization controller for boiler-turbine unit |
-
2009
- 2009-11-16 CN CN 200910153856 patent/CN101864994B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101079199A (en) * | 2006-05-22 | 2007-11-28 | 三菱重工业株式会社 | Gas turbine output learning circuit and combustion control device for gas turbine |
| CN101446807A (en) * | 2008-08-15 | 2009-06-03 | 中国电力科学研究院 | Realization method for heat-engine plant speed regulating system model in power system simulation |
| CN101504135A (en) * | 2009-03-06 | 2009-08-12 | 华北电力大学 | Steam pressure equalization controller for boiler-turbine unit |
Non-Patent Citations (1)
| Title |
|---|
| 孙永平.600MW机组滑压运行方式优化的试验研究.《热力发电》.2007, * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103850726A (en) * | 2014-03-28 | 2014-06-11 | 苏州华瑞能泰发电技术有限公司 | Method for quickly determining stationary sliding pressing optimization curve of steam turbine |
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