CN103900819A - Method for testing and evaluating energy conservation effect of modified steam seal of flow passage part of steam turbine unit - Google Patents
Method for testing and evaluating energy conservation effect of modified steam seal of flow passage part of steam turbine unit Download PDFInfo
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Abstract
The invention relates to a method for testing and evaluating an energy conservation effect of a modified steam seal of a flow passage part of a steam turbine unit. According to pressure, temperature and flow data obtained in a thermal performance test of the steam turbine unit,, parameters like steam loss of shaft seals of balance disks of high and intermediate pressure cylinders, steam loss of shaft seals of high and intermediate pressure cylinders, steam feeding quantity of a shaft seal of a low pressure cylinder, pressure of a low pressure shaft seal, and condensed water temperature raising of a shaft seal heater after upgrading and modification of the steam seal of the flow passage part of the steam turbine unit are calculated, all the above parameters are compared with values of the steam seal before modification and design values of a manufacturer, and the energy conservation effect of the steam seal of the circulation part of the steam turbine unit after upgrading and modification is evaluated.
Description
Technical field
The present invention relates to the detection technique of rotary regenerative air heater in fuel-burning power plant, in particular to a kind of energy-saving effect test and evaluation method of Steam Turbine flow passage component packing transformation.
Background technology
Since the nineties in 20th century, along with continuous introduction Design of Steam Turbine manufacturing technology, internal vapor turbine designing and manufacturing level is improved significantly, and steam turbine internal efficiency also reaches higher level.But in actual motion, the steam turbine of various capacity and different parameters, internal efficiency does not generally reach design load, affects the economy of unit operation.The factor that affects turbine efficiency is a lot, wherein the dynamic and static leaf packing of Turbine Flow Path and gland packing leakage, shaft end gland seal leakage vapour are the major reasons that causes turbine efficiency to reduce, particularly turbine parameters is more and more higher, under identical seal clearance, increases by the flow of interstage gland.Leaking vapour not only affects the moving-stator blade of bypass acting, and causes the disturbance of next stage sprue steam flow, and dual counter productive affects stage efficiency.In order to reduce to leak the impact of vapour, the design and use effect of packing plays more and more important effect.
The most frequently used packing of modern steam turbine is still comb-tooth-type structure, in recent years, along with the development of technology, from the external various new packing of having introduced, more typically has: Honeycomb steam seal, brush steam seal, adjustable steam seal, contact packing, side tooth packing etc.Although these gland seal structure forms are not quite similar, but deviser's guiding theory is by increasing the number of teeth, reduce gap, increasing resistance, improve sealing effectiveness, reduce to leak the loss that vapour causes, Novel steam seal is widely used in Turbine Flow Path packing and shaft end gland seal upgrading at present.
Turbine steam seal transformation can significantly improve Steam Turbine economic target, and in the time of judgement and evaluation turbine steam seal correctional effect, the most frequently used method is the foundation that is reduced to the raising of the each cylinder efficiency of steam turbine and unit heat consumption rate.But for flow passage component upgrading unit, due to unit body retrofit of Flow, the each cylinder efficiency of steam turbine and heat consumption rate are greatly improved, and much larger than the energy-saving effect of packing transformation, therefore the improvement of steam turbine cylinder efficiency and heat consumption rate is not suitable for the effect of evaluating turbine steam seal transformation.
The Chinese invention patent that for example application number is 201310214133.4, it discloses the appraisal procedure of the through-flow level of a kind of steam turbine sound seal leakage to steam turbine power loss, it first utilizes packing flow rate calculation formula to calculate respectively the leakage rate of steam turbine through-flow level interstage gland and blade tip seal, then calculate the through-flow blade tip seal leakage rate of steam turbine, finally calculate the power of the assembling unit loss causing due to the through-flow level of steam turbine seal leakage, adopt the method can assess each through-flow blade sound part labyrinth clearance and change the influence degree to steam turbine overall performance, the size that finally can affect steam turbine power to through-flow blade labyrinth clearance is carried out quantitative assessment and evaluation.In the method, adopting certain through-flow level seal leakage amount of assessment to assess the power of whole Steam Turbine, is obviously to have limitation, and the data that draw are inaccurate.
The Chinese invention patent that for example application number is 201110158913.2 again, it discloses a kind of method of diagnosing Turbine Flow Path gland seal system state, it is according to the current existing measuring point test of power plant, do not need to increase measuring point and surveying instrument, variation by parameter is calculated, grasp the variable quantity calculating after unit operation a period of time, diagnose the sudden change situation of the gland seal system of steam turbine.The method adopts existing measuring point to test, and the accuracy of its data is not high, causes changing the steam turbine power loss causing to labyrinth clearance and carries out quantitative evaluation.
Summary of the invention
The above-mentioned technological deficiency existing in order to solve prior art, the object of the present invention is to provide a kind of energy-saving effect test and evaluation method of Steam Turbine flow passage component packing transformation, the pressure recording according to Steam Turbine thermal performance test, temperature, data on flows, calculate the improved height of packing upgrading of Steam Turbine flow passage component, intermediate pressure cylinder balancing frame shaft gland steam leakage, high, intermediate pressure cylinder shaft gland steam leakage, low pressure (LP) cylinder shaft seal throttle flow, low pressure shaft seal steam pressure, the parameters such as the temperature rise of condensate of gland heater, and by numerical value before above numerical value and packing transformation, the design load of manufacturing firm compares, evaluate the improved energy-saving effect of flow passage component upgrading unit packing.
According to the energy-saving effect test and evaluation method of Steam Turbine flow passage component packing transformation of the present invention, comprise the steps:
The first step, arranges the measuring point of several pressure, temperature, flow, electric power in Steam Turbine therrmodynamic system;
Second step, calculates high, intermediate pressure cylinder front and back shaft gland steam leakage, and low pressure (LP) cylinder shaft seal throttle flow, calculates the temperature rise of condensate through gland heater;
The 3rd step, carries out steam turbine and becomes steam temperature working condition tests, calculates balancing frame steam loss between height high, that intermediate pressure cylinder is arranged symmetrically with structure, intermediate pressure cylinder;
The 4th step: by balancing frame steam loss between height, intermediate pressure cylinder, before shaft gland steam leakage before and after high, intermediate pressure cylinder, low pressure (LP) cylinder shaft seal throttle flow, gland heater initial steam pressure, throttle (steam) temperature, temperature rise of condensate and packing transformation, the design value of manufacturing firm compares, and evaluates the energy-saving effect that turbine steam seal is transformed.
Preferably, second step is divided into five little steps:
The first step, measures high, medium and low cylinder pressure gland packing leakage pressure P zf, gland packing leakage temperature t zf, gland packing leakage flow differential pressure △ Pzf; Measure gland heater initial steam pressure Pzj, gland heater throttle (steam) temperature tzj, gland heater inflow temperature tzj1, #1 low-pressure heater inflow temperature t1dj1;
Second step, rises by △ T=(t1dj1-tzj1 through the solidifying water temperature of gland heater) calculate;
The 3rd step, measures high, medium and low cylinder pressure gland packing leakage density p;
The 4th step, calculate the opening diameter dt of measuring sensor under working temperature by formula dt=d20 × λ d × (t-20), the linear expansion coefficient (known) that in formula, λ d is measuring sensor, the opening diameter (known) that d20 is measuring sensor at 20 ℃ of design temperatures, t is working temperature (known);
The 5th step, utilizes formula Gzf=0.126446 × α × dt2 × ε × (Δ Pzf × ρ) 1/2 to calculate high, intermediate pressure cylinder shaft gland steam leakage, and low pressure (LP) cylinder shaft seal throttle flow, in formula: the coefficient of flow (known) that α is measuring sensor; Dt is the opening diameter mm of measuring sensor under working temperature; Δ Pzf is measuring sensor measured gland packing leakage flow differential pressure of when test, kPa; ε is the expansion coefficient (known) of measured medium.
In above-mentioned arbitrary scheme, preferably, third step is divided into 15 little steps:
The first step, carry out steam turbine and become steam temperature working condition tests, reduce respectively main stripping temperature and improve reheat temperature, and improve main stripping temperature and reduce by two operating condition of test of reheat temperature, the temperature difference reaches 25-30 ℃, and other parameters are as identical in generator load, main vapour pressure, pitch aperture etc.;
Second step, measures main steam enthalpy ims, reheated steam enthalpy irh, finally feeds water that enthalpy ifw, cold reheated steam enthalpy ich, desuperheating water of superheater enthalpy iss, reheater desuperheating water enthalpy irs, #1 are high adds that admission enthalpy in1, #1 HP heater drainage enthalpy is1, #2 are high adds that admission enthalpy in2, #2 HP heater drainage enthalpy is2, #3 are high to be added high adding into water enthalpy i11, #1 are high of admission enthalpy in3, #3 HP heater drainage enthalpy is3, #1 and add high adding into water enthalpy i21, #2 are high of water outlet enthalpy i12, #2 and add that water outlet enthalpy i22, #3 are high adds high water outlet enthalpy i32, the generated output power Pe of adding into water enthalpy i31, #3;
The 3rd step, measures equivalent flow Gbl, desuperheating water of superheater flow Gss, the reheater desuperheating water flow Grs of feedwater flow Gfw, boiler drum level variation;
The 4th step, calculate the #3 high high high steam flow amount Ge3 that adds of steam flow amount Ge2, #1 that adds of steam flow amount Ge1, #2 that adds, #3 is high add steam flow amount by formula Ge1=Gfw × (i32-i31)/(in3-is3) calculates, the high steam flow amount of adding of #2 is by formula Ge2=[Gfw × (i22-i21)-Ge1(is3-is2)]/(in2-is2) calculates, the high steam flow amount of adding of #1 is by formula Ge3=[Gfw × (i12-i11)-(Ge1+Ge2) × (is2-is1)]/(in1-is1) calculate;
The 5th step, utilizes formula Gms=Gfw+Gbl+Gss to calculate main steam flow Gms;
The 6th step, high pressure cylinder door bar and antero posterior axis gland steam leakage rate sum Ggl calculate according to makers' thermodynamic property;
The 7th step, calculates cold reheated steam flow Gch according to formula Gch=Gms-Ggl-Ge1-Ge2-Ge3;
The 8th step, calculates reheated steam flow Grh according to formula Grh=Gch+Grs;
The 9th step, measures gland packing leakage enthalpy ileak between high intermediate pressure cylinder;
The tenth step, if the number percent N that between high intermediate pressure cylinder, shaft gland steam leakage Gleak accounts for main steam flow Gms is respectively 0,2,4,6,8,10, the mixed enthalpy imix of shaft gland steam leakage and reheated steam is according to formula imix=[Grh × irh+ (ileak-irh) × N × Gms]/[Grh+N × Gms] obtain;
The 11 step, measures reheated steam pressure P rh, measures intermediate pressure cylinder exhaust steam pressure Pex, intermediate pressure cylinder exhaust enthalpy iex;
The 12 step, the actual enthalpy drop Hi of steam in intermediate pressure cylinder, is calculated by formula Hi=imix-iex;
The 13 step, utilizes intermediate pressure cylinder steam inlet condition Prh, the imix and the isentropic enthalpy drop, ideal enthalpy drop H0 of exhaust steam pressure Pex calculation of steam in intermediate pressure cylinder that measure;
The 14 step, intermediate pressure cylinder actual efficiency is η IP=Hi/H0;
The 15 step, makes the relation curve of shaft gland steam leakage number percent between above two intermediate pressure cylinder efficiency eta IP that become steam temperature operating modes and high intermediate pressure cylinder, and the value of gained intersection point is shaft gland steam leakage number percent between the high intermediate pressure cylinder of unit reality.
In above-mentioned arbitrary scheme, preferably, between described height, intermediate pressure cylinder, balancing frame packing adopts six circle brushes, broach packing and six circle broach packings.
In above-mentioned arbitrary scheme, preferably, described high pressure cylinder rear shaft seal adopts ten circle Honeycomb steam seals.
In above-mentioned arbitrary scheme, preferably, described intermediate pressure cylinder rear shaft seal adopts seven circle Honeycomb steam seals.
In above-mentioned arbitrary scheme, preferably, before and after described low pressure (LP) cylinder, shaft seal is each adopts broach packing in three circles to contact outer broach packing with two circles.
In above-mentioned arbitrary scheme preferably, described electric power measurement, generator power is measured at 0.02 grade of qualified WT3000 power transducer of the outlet termination verification of generator.
In above-mentioned arbitrary scheme preferably, described flow measurement, condensing water flow adopts throat's pressure Long Nozzle of standard and 0.075 grade of 3051 differential pressure transmitter to measure, condensing water flow nozzle is contained on the low horizontal pipeline adding between outlet and oxygen-eliminating device import of #4, and demarcates through the inspection center that has qualification in advance.
In above-mentioned arbitrary scheme, preferably, described superheater, reheater desuperheating water flow are measured with standard orifice plate; High, intermediate pressure cylinder gland packing leakage flow utilizes standard orifice plate to measure; Low pressure (LP) cylinder shaft seal steam flow is measured with standard orifice plate.
In above-mentioned arbitrary scheme preferably, described pressure survey, 0.1 grade of 3051 pressure transmitter measurement for all pressure-measuring-points.
In above-mentioned arbitrary scheme preferably, described temperature survey, industrial one-level E calibration armoured thermocouple for all temperature points.
In above-mentioned arbitrary scheme preferably, above all data acquisitions discrete data acquisition device, adapted portable computer gathers, collection period is 30 seconds.
In sum, in such scheme for the Steam Turbine of flow passage component upgrading, no longer only utilize the improvement of high, medium and low cylinder pressure efficiency and unit heat consumption rate to judge the effect of turbine steam seal transformation, but utilize high, intermediate pressure cylinder shaft gland steam leakage, low pressure (LP) cylinder shaft seal throttle flow, rise and the parameter such as shaft seal steam pressure judges and evaluates the energy-saving effect that turbine steam seal is transformed through the solidifying water temperature of gland heater; For steam turbine high, intermediate pressure cylinder reversed arrangement, become steam temperature working condition tests, reduce respectively main stripping temperature and improve reheat steam temperature degree, and the test that improves two operating modes of main stripping temperature reduction reheat steam temperature degree, make shaft gland steam leakage between the intermediate pressure cylinder efficiency eta IP of above two operating modes and high intermediate pressure cylinder and account for the relation curve of the number percent N of main steam flow Gms, obtain shaft gland steam leakage number percent between the high intermediate pressure cylinder of unit reality, evaluate the effect of balancing frame packing transformation between high, intermediate pressure cylinder; By shaft gland steam leakage before and after height, intermediate pressure cylinder, before low pressure shaft seal throttle flow, low pressure shaft seal steam pressure, gland heater initial steam pressure, gland heater throttle (steam) temperature, the temperature rise of condensate and the packing that add through axle are transformed, the design load of manufacturing firm compares, evaluate the energy-saving effect of turbine steam seal transformation, the easy measurements and calculations of parameter, method simple possible.
Accompanying drawing explanation
Fig. 1 is according to Steam Turbine therrmodynamic system measuring point arrangenent diagram in the energy-saving effect test and evaluation method of Steam Turbine flow passage component packing transformation of the present invention.
Fig. 2 is according to the relation curve of shaft gland steam leakage number percent N between intermediate pressure cylinder efficiency eta IP and high intermediate pressure cylinder in rotary regenerative air heater on-line performance diagnostic system of the present invention and method thereof.
Embodiment
The following description is only exemplary and be not in order to limit the disclosure, application or purposes in essence.The embodiment of the energy-saving effect test and evaluation method below in conjunction with Figure of description to Steam Turbine flow passage component packing transformation of the present invention is further described.
The present invention adopts following technical scheme: a kind of energy-saving effect test and evaluation method of flow passage component upgrading unit packing transformation, and concrete steps are:
Step 1: arrange some pressure, temperature, flow measuring point in Steam Turbine therrmodynamic system;
Step 2: calculate shaft gland steam leakage before and after high, intermediate pressure cylinder, low pressure (LP) cylinder shaft seal throttle flow; Calculate the temperature rise of condensate through gland heater;
Step 3: carry out steam turbine and become steam temperature working condition tests, calculate balancing frame steam loss between height high, that intermediate pressure cylinder is arranged symmetrically with structure, intermediate pressure cylinder;
Step 4: by balancing frame steam loss between high intermediate pressure cylinder, high, intermediate pressure cylinder front and back shaft gland steam leakage, low pressure (LP) cylinder shaft seal throttle flow, before gland heater initial steam pressure, throttle (steam) temperature, temperature rise of condensate and packing transformation, the design value of manufacturing firm compares, and evaluates the energy-saving effect of turbine steam seal transformation.
The concrete steps of above-mentioned steps two are:
(2-1) measure high, medium and low cylinder pressure gland packing leakage pressure P zf, gland packing leakage temperature t zf, gland packing leakage flow differential pressure △ Pzf; Measure gland heater initial steam pressure Pzj, gland heater throttle (steam) temperature tzj, gland heater inflow temperature tzj1, #1 low-pressure heater inflow temperature t1dj1.
(2-2) rise by △ T=(t1dj1-tzj1 through the solidifying water temperature of gland heater) calculate;
(2-3) measure high, medium and low cylinder pressure gland packing leakage density p;
(2-4) calculate the opening diameter dt of measuring sensor under working temperature by formula dt=d20 × λ d × (t-20), the linear expansion coefficient (known) that in formula, λ d is measuring sensor, the opening diameter (known) that d20 is measuring sensor at 20 ℃ of design temperatures, t is working temperature (known);
(2-5) utilize formula Gzf=0.126446 × α × dt2 × ε × (Δ Pzf × ρ) 1/2 to calculate high, intermediate pressure cylinder shaft gland steam leakage, low pressure (LP) cylinder shaft seal throttle flow, in formula: the coefficient of flow (known) that α is measuring sensor; Dt is the opening diameter of measuring sensor under working temperature; Δ Pzf is measuring sensor measured gland packing leakage flow differential pressure of when test, kPa; ε is the expansion coefficient (known) of measured medium.
The concrete steps of above-mentioned steps three are:
(3-1) carry out steam turbine and become steam temperature working condition tests, reduce respectively main stripping temperature and improve reheat temperature, and improve main stripping temperature and reduce by two operating condition of test of reheat temperature, the temperature difference reaches 25-30 ℃, and other parameters are as identical in generator load, main vapour pressure, pitch aperture etc.;
(3-2) measure main steam enthalpy ims, reheated steam enthalpy irh, final feedwater enthalpy ifw, cold reheated steam enthalpy ich, desuperheating water of superheater enthalpy iss, reheater desuperheating water enthalpy irs, the high admission enthalpy in1 that adds of #1, #1 HP heater drainage enthalpy is1, the high admission enthalpy in2 that adds of #2, #2 HP heater drainage enthalpy is2, the high admission enthalpy in3 that adds of #3, #3 HP heater drainage enthalpy is3, #1 is high to be added into water enthalpy i11, the high water outlet enthalpy i12 that adds of #1, #2 is high to be added into water enthalpy i21, the high water outlet enthalpy i22 that adds of #2, #3 is high to be added into water enthalpy i31, the high water outlet enthalpy i32 that adds of #3, generated output power Pe,
(3-3) measurement feedwater flow Gfw, boiler drum level change equivalent flow Gbl, desuperheating water of superheater flow Gss, reheater desuperheating water flow Grs;
(3-4) #3 high add steam flow amount Ge1, #2 high add steam flow amount Ge2, #1 high add steam flow amount Ge3 by #3 highly add, #2 highly adds, high the heat Balance Calculation adding obtains #1; #3 is high, and the steam flow amount of adding is calculated by formula Ge1=Gfw × (i32-i31)/(in3-is3); The high steam flow amount of adding of #2 is by formula Ge2=[Gfw × (i22-i21)-Ge1(is3-is2)]/(in2-is2) calculate; The high steam flow amount of adding of #1 is by formula Ge3=[Gfw × (i12-i11)-(Ge1+Ge2) × (is2-is1)]/(in1-is1) calculate;
(3-5) utilize formula Gms=Gfw+Gbl+Gss to calculate main steam flow Gms;
(3-6) high pressure cylinder door bar and antero posterior axis gland steam leakage rate sum Ggl calculate according to makers' thermodynamic property;
(3-7) calculate cold reheated steam flow Gch according to formula Gch=Gms-Ggl-Ge1-Ge2-Ge3;
(3-8) calculate reheated steam flow Grh according to formula Grh=Gch+Grs;
(3-9) measure gland packing leakage enthalpy ileak between high intermediate pressure cylinder;
(3-10) establish the number percent N that shaft gland steam leakage Gleak between high intermediate pressure cylinder accounts for main steam flow Gms and be respectively 0,2,4,6,8,10, the mixed enthalpy imix of shaft gland steam leakage and reheated steam is according to formula imix=[Grh × irh+ (ileak-irh) × N × Gms]/[Grh+N × Gms] obtain;
(3-11) measure reheated steam pressure P rh, measure intermediate pressure cylinder exhaust steam pressure Pex, intermediate pressure cylinder exhaust enthalpy iex,
(3-12) the actual enthalpy drop Hi of steam in intermediate pressure cylinder calculated by formula Hi=imix-iex;
(3-13) utilize intermediate pressure cylinder steam inlet condition Prh, the imix and the isentropic enthalpy drop, ideal enthalpy drop H0 of exhaust steam pressure Pex calculation of steam in intermediate pressure cylinder that measure;
(3-14) intermediate pressure cylinder actual efficiency is η IP=Hi/H0;
(3-15) make the relation curve of shaft gland steam leakage number percent N between above two intermediate pressure cylinder efficiency eta IP that become steam temperature operating modes and high intermediate pressure cylinder, the N value of gained intersection point is shaft gland steam leakage number percent between the high intermediate pressure cylinder of unit reality.
In such scheme for the Steam Turbine of flow passage component upgrading, no longer only utilize the improvement of high, medium and low cylinder pressure efficiency and unit heat consumption rate to judge the effect of turbine steam seal transformation, but utilize high, intermediate pressure cylinder shaft gland steam leakage, low pressure (LP) cylinder shaft seal throttle flow, rise and the parameter such as shaft seal steam pressure judges and evaluates the energy-saving effect that turbine steam seal is transformed through the solidifying water temperature of gland heater; For steam turbine high, intermediate pressure cylinder reversed arrangement, become steam temperature working condition tests, reduce respectively main stripping temperature and improve reheat steam temperature degree, and the test that improves two operating modes of main stripping temperature reduction reheat steam temperature degree, make shaft gland steam leakage between the intermediate pressure cylinder efficiency eta IP of above two operating modes and high intermediate pressure cylinder and account for the relation curve of the number percent N of main steam flow Gms, obtain shaft gland steam leakage number percent between the high intermediate pressure cylinder of unit reality, evaluate the effect of balancing frame packing transformation between high, intermediate pressure cylinder; By shaft gland steam leakage before and after height, intermediate pressure cylinder, before low pressure shaft seal throttle flow, low pressure shaft seal steam pressure, gland heater initial steam pressure, gland heater throttle (steam) temperature, the temperature rise of condensate and the packing that add through axle are transformed, the design load of manufacturing firm compares, evaluate the energy-saving effect of turbine steam seal transformation, the easy measurements and calculations of parameter, method simple possible.
Carry out Steam Turbine Performance test according to GB/T8117.1-2008 " steam turbine performance reception test rules ", the layout of test measuring point as shown in Figure 1.
Unit measuring system and measurement instrument: (1) electric power measurement: generator power is measured at 0.02 grade of qualified WT3000 power transducer of the outlet termination verification of generator.(2) flow measurement: condensing water flow adopts throat's pressure Long Nozzle of standard and 0.075 grade of 3051 differential pressure transmitter to measure, condensing water flow nozzle is contained on the low horizontal pipeline adding between outlet and oxygen-eliminating device import of #4, and demarcates through the inspection center that has qualification in advance.Superheater, reheater desuperheating water flow are measured with standard orifice plate; High, intermediate pressure cylinder gland packing leakage flow utilizes standard orifice plate to measure; Low pressure (LP) cylinder shaft seal steam flow is measured with standard orifice plate.(3) pressure survey: 0.1 grade of 3051 pressure transmitter measurement for all pressure-measuring-points.(4) temperature survey: industrial one-level E calibration armoured thermocouple for all temperature points.
All data acquisitions discrete data acquisition device, adapted portable computer gathers, and collection period is 30 seconds.The test raw data collecting is carried out to arithmetic mean calculating by the metastable one continuous recording period of operating mode, and pressure-measuring-point carries out absolute altitude and atmospheric pressure correction.The measured value of the multiple measuring point of same parameters in test, gets its arithmetic mean.
In table 1, list the test raw data under unit flow passage component and packing transformation front and back 330MW operating mode, in table 2, list the experiment calculation result under the 330MW operating mode of unit packing transformation front and back.
330MW working condition tests raw data before and after table 1 unit flow passage component and packing transformation
This test is using condensing water flow as calculating benchmark, calculate feedwater flow according to #1, #2, high adding with thermal equilibrium and the mass balance of oxygen-eliminating device of #3, then calculate main steam flow, reheated steam flow, high pressure cylinder exhaust steam flow (cold reheated steam flow); According to height, middle last item gland leak-off, low pressure (LP) cylinder shaft seal steam calculation of parameter gland packing leakage flow, the shaft seal steam flow measured; According to the parameter such as gland heater admission, the temperature rise of Inlet and outlet water calculation of parameter gland heater of measuring, as shown in table 2.
330MW working condition tests result of calculation before and after table 2 unit flow passage component and packing transformation
Learnt by table 2 experiment calculation result, subcritical 330MW unit, after Turbine Flow Path and packing transformation, cylinder efficiency and heat consumption rate all have clear improvement, but this can not transform as turbine steam seal the Basic Evaluation foundation of energy-saving effect, because the raising of cylinder efficiency and the reduction of heat consumption rate, should mainly give the credit to flow passage component upgrading, therefore to flow passage component upgrading unit, the parameters such as the temperature rise of condensate that the energy-saving effect of turbine steam seal transformation should add by shaft gland steam leakage, shaft seal steam amount, shaft seal steam pressure, process axle are evaluated judgement.
After above 330MW unit flow passage component and packing transformation, under three valve point operating modes, become steam temperature working condition tests, maintain the power of the assembling unit close when test, main vapour pressure is close, three valve standard-sized sheets.Adopt and reduce respectively the method that main steam temperature improves reheat steam temperature, improves main steam temperature reduction reheat steam temperature, make the two poor 25-30 ℃, to determine height, intermediate pressure cylinder balancing frame place's gland leak-off amount and real intermediate pressure cylinder efficiency value.The result of calculation high, intermediate pressure cylinder balancing frame place's gland leak-off amount is tested is in table 3.
After table 3 330MW Steam Turbine flow passage component and packing transformation, become steam temperature working condition tests result
The test findings that becomes steam temperature operating mode into: the share that shaft gland steam leakage high, intermediate pressure cylinder balancing frame place accounts for main steam flow is 1.02%.And THA operating condition design data, the share that shaft gland steam leakage high, intermediate pressure cylinder balancing frame place accounts for main steam flow is 1.503%, actual steam loss is less than design steam loss.Fig. 2 is Steam Turbine Through IP Admission efficiency and relation curve high, intermediate pressure cylinder balancing frame place's gland leak-off amount number percent N, and the N value of gained intersection point is shaft gland steam leakage number percent between the high intermediate pressure cylinder of unit reality.Drawn by Fig. 2, ratio and intermediate pressure cylinder efficiency that the height in steam turbine, middle pressure shaft gland steam leakage account for main steam flow are inversely proportional to.
Learnt by table 2, table 3 experiment calculation result, the high, medium and low cylinder pressure shaft end gland seal of steam turbine, and after flow passage component shaft seal and packing transformation, high, intermediate pressure cylinder shaft gland steam leakage reduces, high, intermediate pressure cylinder rear axle front cover section is reduced to 3912.6kg/h to oxygen-eliminating device steam loss from 4642kg/h, and high pressure shaft seal to low pressure shaft seal steam loss is reduced to 475.4t/h from 499.8t/h; Under running on the lower load, shaft seal steam pressure decreased, feeding of low-pressure shaft seal flow reduces, and can not meet the self-packing requirement of unit; Temperature rise of condensate through gland heater is reduced to 2.41 ℃ from 4.4 ℃; Gland leak-off amount high, intermediate pressure cylinder balancing frame place is less than design load.Above data declaration, the energy-saving effect of turbine steam seal transformation is good.
It will be apparent to those skilled in the art that the energy-saving effect test and evaluation method of Steam Turbine flow passage component packing transformation of the present invention comprises the combination in any of each several part in this instructions.As space is limited and in order to make instructions simple and clear, these combinations to be introduced one by one in detail at this, but seen after this instructions, the scope of the present invention that the combination in any of the each several part being made up of this instructions forms is self-evident.
Claims (10)
1. an energy-saving effect test and evaluation method for Steam Turbine flow passage component packing transformation, comprises the steps:
The first step, arranges the measuring point of several pressure, temperature, flow, electric power in Steam Turbine therrmodynamic system;
Second step, calculates high, intermediate pressure cylinder front and back shaft gland steam leakage, and low pressure (LP) cylinder shaft seal throttle flow, calculates the temperature rise of condensate through gland heater;
The 3rd step, carries out steam turbine and becomes steam temperature working condition tests, calculates balancing frame steam loss between height high, that intermediate pressure cylinder is arranged symmetrically with structure, intermediate pressure cylinder;
The 4th step: by balancing frame steam loss between height, intermediate pressure cylinder, before shaft gland steam leakage before and after high, intermediate pressure cylinder, low pressure (LP) cylinder shaft seal throttle flow, gland heater initial steam pressure, throttle (steam) temperature, temperature rise of condensate and packing transformation, the design value of manufacturing firm compares, and evaluates the energy-saving effect that turbine steam seal is transformed.
2. the energy-saving effect test and evaluation method of Steam Turbine flow passage component packing transformation as claimed in claim 1, is characterized in that, second step is divided into five little steps:
The first step, measures high, medium and low cylinder pressure gland packing leakage pressure P
zf, gland packing leakage temperature t
zf, gland packing leakage flow differential pressure △ P
zf; Measure gland heater initial steam pressure P
zj, gland heater throttle (steam) temperature t
zj, gland heater inflow temperature t
zj1, #1 low-pressure heater inflow temperature t
1dj1;
Second step, rises by △ T=(t through the solidifying water temperature of gland heater
1dj1-t
zj1) calculate;
The 3rd step, measures high, medium and low cylinder pressure gland packing leakage density p;
The 4th step, by formula dt=d
20× λ d × (t-20) calculates the opening diameter dt of measuring sensor under working temperature;
The 5th step, utilizes formula G
zf=0.126446 × α × dt
2× ε × (Δ P
zf× ρ)
1/2calculate high, intermediate pressure cylinder shaft gland steam leakage, low pressure (LP) cylinder shaft seal throttle flow.
3. the energy-saving effect test and evaluation method of Steam Turbine flow passage component packing transformation as claimed in claim 1, is characterized in that, third step is divided into 15 little steps:
The first step, carry out steam turbine and become steam temperature working condition tests, reduce respectively main stripping temperature and improve reheat temperature, and improve main stripping temperature and reduce by two operating condition of test of reheat temperature, the temperature difference reaches 25-30 ℃, and other parameters are as identical in generator load, main vapour pressure, pitch aperture etc.;
Second step, measures main steam enthalpy i
ms, reheated steam enthalpy i
rh, the final enthalpy i that feeds water
fw, cold reheated steam enthalpy i
ch, desuperheating water of superheater enthalpy i
ss, reheater desuperheating water enthalpy i
rs, the high admission enthalpy i that adds of #1
n1, #1 HP heater drainage enthalpy i
s1, the high admission enthalpy i that adds of #2
n2, #2 HP heater drainage enthalpy i
s2, the high admission enthalpy i that adds of #3
n3, #3 HP heater drainage enthalpy i
s3, #1 is high adds into water enthalpy i
11, the high water outlet enthalpy i that adds of #1
12, #2 is high adds into water enthalpy i
21, the high water outlet enthalpy i that adds of #2
22, #3 is high adds into water enthalpy i
31, the high water outlet enthalpy i that adds of #3
32, generated output power Pe;
The 3rd step, measures feedwater flow G
fw, boiler drum level change equivalent flow G
bl, desuperheating water of superheater flow G
ss, reheater desuperheating water flow G
rs;
The 4th step, calculates the high steam flow amount G that adds of #3
e1, the high steam flow amount G that adds of #2
e2, the high steam flow amount G that adds of #1
e3, the high steam flow amount of adding of #3 is by formula G
e1=G
fw× (i
32-i
31)/(i
n3-i
s3) calculate, the high steam flow amount of adding of #2 is by formula G
e2=[G
fw× (i
22-i
21)-G
e1(i
s3-i
s2)]/(i
n2-i
s2) calculate, the high steam flow amount of adding of #1 is by formula G
e3=[G
fw× (i
12-i
11)-(G
e1+ G
e2) × (i
s2-i
s1)]/(i
n1-i
s1) calculate;
The 5th step, utilizes formula G
ms=G
fw+ G
bl+ G
sscalculate main steam flow G
ms;
The 6th step, high pressure cylinder door bar and antero posterior axis gland steam leakage rate sum G
glcalculate according to makers' thermodynamic property;
The 7th step, according to formula G
ch=G
ms-G
gl-G
e1-G
e2-G
e3calculate cold reheated steam flow G
ch;
The 8th step, according to formula G
rh=G
ch+ G
rscalculate reheated steam flow G
rh;
The 9th step, measures gland packing leakage enthalpy i between high intermediate pressure cylinder
leak;
The tenth step, establishes shaft gland steam leakage G between high intermediate pressure cylinder
leakaccount for main steam flow G
msnumber percent N be respectively 0,2,4,6,8,10, the mixed enthalpy i of shaft gland steam leakage and reheated steam
mixaccording to formula i
mix=[G
rh× i
rh+ (i
leak-i
rh) × N × G
ms]/[G
rh+ N × G
ms] obtain;
The 11 step, measures reheated steam pressure P
rh, measure intermediate pressure cylinder exhaust steam pressure P
ex, intermediate pressure cylinder exhaust enthalpy i
ex;
The 12 step, the actual enthalpy drop H of steam in intermediate pressure cylinder
i, by formula H
i=i
mix-i
excalculate;
The 13 step, utilizes the intermediate pressure cylinder steam inlet condition Prh, the i that measure
mixwith exhaust steam pressure P
exthe isentropic enthalpy drop, ideal enthalpy drop H of calculation of steam in intermediate pressure cylinder
0;
The 14 step, intermediate pressure cylinder actual efficiency is η
iP=H
i/ H
0;
The 15 step, makes above two intermediate pressure cylinder efficiency eta that become steam temperature operating modes
iPand the relation curve of shaft gland steam leakage number percent between high intermediate pressure cylinder, the value of gained intersection point is shaft gland steam leakage number percent between the high intermediate pressure cylinder of unit reality.
4. the energy-saving effect test and evaluation method of the transformation of the Steam Turbine flow passage component packing as described in any one in claim 1-3, is characterized in that: between described height, intermediate pressure cylinder, balancing frame packing adopts six circle brushes, broach packing and six circle broach packings.
5. the energy-saving effect test and evaluation method of the transformation of the Steam Turbine flow passage component packing as described in any one in claim 1-3, is characterized in that: described high pressure cylinder rear shaft seal adopts ten circle Honeycomb steam seals.
6. the rotary regenerative air heater on-line performance diagnostic method as described in claim 1-3, is characterized in that: described intermediate pressure cylinder rear shaft seal adopts seven circle Honeycomb steam seals.
7. the rotary regenerative air heater on-line performance diagnostic method as described in claim 1-3, is characterized in that: before and after described low pressure (LP) cylinder, shaft seal is each adopts broach packing in three circles to contact outer broach packing with two circles.
8. rotary regenerative air heater on-line performance diagnostic method as claimed in claim 1, is characterized in that: described electric power measurement, generator power is measured at 0.02 grade of qualified WT3000 power transducer of the outlet termination verification of generator.
9. rotary regenerative air heater on-line performance diagnostic method as claimed in claim 1, it is characterized in that: described flow measurement, condensing water flow adopts throat's pressure Long Nozzle of standard and 0.075 grade of 3051 differential pressure transmitter to measure, condensing water flow nozzle is contained on the low horizontal pipeline adding between outlet and oxygen-eliminating device import of #4, and demarcates through the inspection center that has qualification in advance.
10. rotary regenerative air heater on-line performance diagnostic method as claimed in claim 3, is characterized in that: described superheater, reheater desuperheating water flow standard orifice plate are measured.
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| CN110672315A (en) * | 2019-06-14 | 2020-01-10 | 国网浙江省电力有限公司电力科学研究院 | Steam turbine regulating valve state evaluation method based on valve rod steam leakage |
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