CN103646176B - The comprehensive calculation method of energy-saving effect after turbine steam seal transformation - Google Patents
The comprehensive calculation method of energy-saving effect after turbine steam seal transformation Download PDFInfo
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Abstract
The invention discloses the comprehensive calculation method of energy-saving effect after a kind of turbine steam seal is transformed, concretely comprise the following steps: arrange pressure, temperature, flow, electrical power test point in Steam Turbine therrmodynamic system；Calculate feedwater flow, main steam flow, cold reheated steam flow and reheated steam flow；Four: calculate unit height, intermediate pressure cylinder balancing frame shaft gland steam leakage；Measure height, intermediate pressure cylinder shaft gland steam leakage, low pressure cylinder shaft seal throttle flow, low pressure shaft seal pressure, through the temperature rise of condensate of gland heater；Calculate unit test heat consumption rate, the heat consumption rate after parameters revision；Each for steam turbine parameter is compared with design value before packing transformation, evaluates the energy-saving effect of turbine steam seal transformation.This method passes through Thermal Performance Test of Steam Turbine, tests therrmodynamic system parameter, provides energy-saving effect evaluation and analysis method after turbine steam seal transformation, and method advantages of simple, the result calculated is more accurate.
Description
Technical field
The present invention relates to steam turbine field, particularly relate to the COMPREHENSIVE CALCULATING side of energy-saving effect after a kind of turbine steam seal is transformed
Method.
Background technology
The most frequently used packing of modern steam turbine is still comb-tooth-type structure, in recent years, along with the development of technology, draws from abroad
Having entered various new packing, more typical have: Honeycomb steam seal, brush steam seal, adjustable steam seal, contact packing, side tooth packing
Deng.Although these gland seal structure forms are not quite similar, but the guiding theory of designer is by increasing the number of teeth, reducing gap, increasing
Adding resistance, improve sealing effectiveness, reduce the loss that leakage vapour is caused, Novel steam seal is now widely used in Turbine Flow Path
In packing and shaft end gland seal upgrading.
Turbine steam seal transformation can significantly improve Steam Turbine economic indicator, is judging and is evaluating turbine steam seal transformation
During effect, most common method be the raising with steam turbine each cylinder efficiency and unit heat consumption rate be reduced to foundation.But impact
Cylinder of steam turbine efficiency, heat consumption rate factor numerous, transform including: (1) Turbine Flow Path；(2) turbine steam seal, axle envelope change
Make；(3) flow passage component fouling and scale removal；(4) the inside and outside leakage of system etc..Owing to unit model is different, packing, shaft gland steam leakage
Impact on unit performance index is not quite similar, and after turbine steam seal transformation sometimes, the improvement of cylinder efficiency and heat consumption rate is not
Substantially, and the overhaul effects such as improvement that leak outside in the most also including unit flow passage component scale removal, system, therefore imitate just with cylinder
Turbine steam seal correctional effect cannot comprehensively be analyzed by the improvement of rate and heat consumption rate.
Summary of the invention
The purpose of the present invention is contemplated to solve the problems referred to above, it is proposed that energy-saving effect after the transformation of a kind of turbine steam seal
Comprehensive calculation method
To achieve these goals, the present invention adopts the following technical scheme that
The comprehensive calculation method of energy-saving effect after the transformation of a kind of turbine steam seal, comprises the following steps:
Step one: arrange some pressure, temperature, flow rate test point in Steam Turbine therrmodynamic system；
Step 2: measure high pressure cylinder respectively and the leakage steam flow amount of intermediate pressure cylinder antero posterior axis envelope, low pressure cylinder shaft are sealed into steam flow amount, vapour
Turbine monitors section parameter, gland heater steam inlet condition and the temperature rise of condensate through gland heater；
Step 3: carry out steam turbine and become steam temperature working condition tests, measure and calculate high pressure cylinder and intermediate pressure cylinder is arranged symmetrically with structure
Height, balancing frame steam loss percentage between intermediate pressure cylinder；
Step 4: calculate the actual efficiency of Steam Turbine high pressure cylinder, the nominal efficiency of intermediate pressure cylinder and low pressure (LP) cylinder respectively
Actual efficiency；
Step 5: calculate Steam Turbine test heat consumption rate, calculate the heat consumption rate after Steam Turbine parameters revision；
Step 6: by steam turbine monitor section parameter, balancing frame steam loss between high intermediate pressure cylinder, high, intermediate pressure cylinder antero posterior axis leak sealing
Vapour amount, low pressure cylinder shaft envelope throttle flow, low pressure (LP) cylinder shaft seal steam pressure, gland heater initial steam pressure, throttle (steam) temperature and condensation water
Temperature rise, high pressure cylinder actual efficiency, intermediate pressure cylinder actual efficiency, low pressure (LP) cylinder actual efficiency and the revised heat consumption rate of unit parameter divide
The design value of not front with packing transformation manufacturing firm compares, according to the transformation of comparative result comprehensive descision turbine steam seal
Energy-saving effect；
The concrete measuring method of described step 2 is:
(1) high pressure cylinder, intermediate pressure cylinder gland packing leakage pressure P are measured respectively1, high, intermediate pressure cylinder antero posterior axis gland leak-off flow throttling
Operating temperature t of device1, low pressure (LP) cylinder shaft seal steam pressure P2, low pressure cylinder shaft seals operating temperature t into steam flow amount throttling arrangement2,
Steam turbine monitor section pressure P3, steam turbine monitor section temperature t3, gland heater initial steam pressure P4, gland heater throttle (steam) temperature
t4, gland heater inflow temperature t5, gland heater leaving water temperature t6；
(2) known Δ T=t is utilized6-t5Calculate the solidifying water temperature liter through gland heater, wherein, t5For gland heater
Inflow temperature, t6For gland heater leaving water temperature；
(3) high, intermediate pressure cylinder antero posterior axis gland leak-off density p is measured1Seal into vapour density ρ with low pressure cylinder shaft2；
(4) height, the opening diameter d of intermediate pressure cylinder antero posterior axis gland leak-off flow throttling arrangement are calculated respectivelyt1Seal with low pressure cylinder shaft
Enter the opening diameter d of steam flow amount throttling arrangementt2；Concrete formula is:
dt1=d201×λd1×(t1-20)；
dt2=d202×λd2×(t2-20)；
Wherein, d201For high, the perforate at design temperature 20 DEG C of the intermediate pressure cylinder antero posterior axis gland leak-off flow throttling arrangement is straight
Footpath, λd1For high, the linear expansion coefficient of intermediate pressure cylinder antero posterior axis gland leak-off flow throttling arrangement, t1For high, intermediate pressure cylinder antero posterior axis envelope
The operating temperature of leakage steam flow amount throttling arrangement；d202Seal into steam flow amount throttling arrangement at design temperature 20 DEG C for low pressure cylinder shaft
Opening diameter, λd2Seal into steam flow amount throttling arrangement linear expansion coefficient, t for low pressure cylinder shaft2Seal for low pressure cylinder shaft and save into steam flow amount
The operating temperature of stream device；
(5) height, intermediate pressure cylinder antero posterior axis gland leak-off flow G are calculated respectivelyzfSeal into steam flow amount G with low pressure cylinder shaftdzf, specifically public
Formula is:
Gzf=0.126446 × α1×dt1 2×ε1×(ΔP1×ρ1)1/2；
Gdzf=0.126446 × α2×dt2 2×ε2×(ΔP2×ρ2)1/2；
Wherein, α1For high, the discharge coefficient of intermediate pressure cylinder antero posterior axis gland leak-off flow throttling arrangement, for known quantity, Δ P1For examination
The differential pressure of flow, unit kPa, ε measured by height, intermediate pressure cylinder antero posterior axis gland leak-off flow throttling arrangement when testing1For measured medium
The coefficient of expansion, for known quantity；α2For the discharge coefficient of low pressure (LP) cylinder antero posterior axis gland leak-off flow throttling arrangement, for known quantity, Δ P2
The differential pressure of flow, unit kPa, ε measured by low pressure (LP) cylinder antero posterior axis gland leak-off flow throttling arrangement during test2For measured medium
The coefficient of expansion, for known quantity.
The concrete measuring method of described step 3 is:
(1) carry out reducing steam turbine main steam temperature respectively and improve reheat temperature, and improve steam turbine main steam temperature
Reducing by two working condition tests of reheat temperature, making main steam temperature is 20～30 DEG C with the deviation of reheat temperature, and other parameters are not
Become；
(2) high pressure cylinder steam admission enthalpy i is measured respectivelyms, intermediate pressure cylinder steam admission enthalpy irh, final feedwater enthalpy ifw w, high pressure cylinder exhaust enthalpy
ich, desuperheating water of superheater enthalpy iss, reheater desuperheating water enthalpy irs, #1 height add steam admission enthalpy in1, #1 HP heater drainage enthalpy is1, #2 height adds
Vapour enthalpy in2, #2 HP heater drainage enthalpy is2, #3 height add steam admission enthalpy in3, #3 HP heater drainage enthalpy is3, #1 height adds into water enthalpy i11, #1 height adds
Water enthalpy i12, #2 height adds into water enthalpy i21, #2 height add water outlet enthalpy i22, #3 height adds into water enthalpy i31, #3 height add water outlet enthalpy i32And generator
Active-power P e；
(3) feedwater flow G before boiler economizer entrance is measuredfw, boiler drum level change equivalent flow Gb1, overheated
Device attemperation water flow Gss, reheater attemperation water flow Grs；
(4) calculate #1 height respectively and add steam flow amount Ge1, #2 height add steam flow amount Ge2Steam flow amount G is added with #3 heighte3, specifically
Computing formula is as follows:
Ge1=Gfw×(i12-i11)/(in1-is1)；
Ge2=[Gfw×(i22-i21)-Ge1×(is1-is2)]/(in2-is2)；
Ge3=[Gfw×(i32-i31)-(Ge1+Ge2)×(is2-is3)]/(in3-is3)；
Wherein, GfwFor feedwater flow, i11Add into water enthalpy, i for #1 height12Water outlet enthalpy, i is added for #1 height21Add into water for #2 height
Enthalpy, i22Water outlet enthalpy, i is added for #2 height31Add into water enthalpy, i for #3 height32Water outlet enthalpy, i is added for #3 heights1For #1 HP heater drainage enthalpy, is2
For #2 HP heater drainage enthalpy, is3For #3 HP heater drainage enthalpy, in1Steam admission enthalpy, i is added for #1 heightn2Steam admission enthalpy, i is added for #2 heightn3Add for #3 height
Steam admission enthalpy；
(5) main steam flow G is calculated respectivelyms, cold reheated steam flow GchWith reheated steam flow Grh, specifically calculate public affairs
Formula is as follows:
Gms=Gfw+Gb1+Gss；
Gch=Gms-Gg1-Ge1-Ge2-Ge3；
Grh=Gch+Grs；
Wherein, GfwFor feedwater flow, Gb1For the equivalent flow of boiler drum level change, GssFor desuperheating water of superheater stream
Amount；GmsFor main steam flow, Gg1For high pressure cylinder door rod and antero posterior axis gland steam leakage rate sum, by the thermodynamic property of manufactory
Book is given, Ge1、Ge2And Ge3Respectively #1 height adds steam flow amount, #2 height adds steam flow amount and #3 height adds steam flow amount；GrsFor reheating
Device attemperation water flow；
(6) gland packing leakage enthalpy i between high intermediate pressure cylinder is measuredleak；Measure intermediate pressure cylinder initial steam pressure Prh, measure intermediate pressure cylinder steam discharge pressure
Power Pich, intermediate pressure cylinder exhaust enthalpy iich；
(7) shaft gland steam leakage G between high intermediate pressure cylinder is setleakAccount for main steam flow GmsPercentage N be respectively 0,2,4,6,8,
10, calculate shaft gland steam leakage and reheated steam mixed enthalpy i between high intermediate pressure cylindermix, specific formula for calculation is:
imix=[Grh×iich+ileak×N×Gms]/(Grh+N×Gms)；
Wherein, GrhFor reheated steam flow, ileakFor gland packing leakage enthalpy between high intermediate pressure cylinder, iichFor intermediate pressure cylinder exhaust enthalpy；
(8) reheated steam actual enthalpy drop H in intermediate pressure cylinder is calculatedi, concrete formula is:
Hi=imix-iich；
Wherein, imixFor shaft gland steam leakage between high intermediate pressure cylinder and the mixed enthalpy of reheated steam, iichFor intermediate pressure cylinder steam discharge
Enthalpy；
(9) the intermediate pressure cylinder initial steam pressure P measured is utilizedrh, intermediate pressure cylinder steam admission enthalpy irhWith intermediate pressure cylinder exhaust steam pressure PichCalculate
Steam isentropic enthalpy drop, ideal enthalpy drop H in intermediate pressure cylinder0；
(10) intermediate pressure cylinder actual efficiency η is calculatedIP, computing formula is:
ηIP=Hi/H0；
Wherein, HiFor steam actual enthalpy drop in intermediate pressure cylinder, H0For steam isentropic enthalpy drop, ideal enthalpy drop in intermediate pressure cylinder；
(11) computational methods described in step (2)-step (10) are utilized to calculate respectively and steam turbine two in plot step (1)
IP efficiency η in individual change steam temperature working condition experimentingIPAnd the relation curve of shaft gland steam leakage percentage N, gained between high intermediate pressure cylinder
Article two, in relation curve, the value of intersection point N is shaft gland steam leakage percentage between the high intermediate pressure cylinder that Steam Turbine is actual.
Described step 4 method particularly includes:
(1) high pressure cylinder initial steam pressure P is measuredms, high pressure cylinder throttle (steam) temperature tms, high pressure cylinder steam admission enthalpy ims；Measurement high pressure cylinder is arranged
Steam pressure Pch, exhaust temperature of HP tch, high pressure cylinder exhaust enthalpy ich；Measure intermediate pressure cylinder initial steam pressure Prh, intermediate pressure cylinder throttle (steam) temperature
trh, intermediate pressure cylinder steam admission enthalpy irh；Measure intermediate pressure cylinder exhaust steam pressure Pich, intermediate pressure cylinder exhaust temperature tich, intermediate pressure cylinder exhaust enthalpy iich；Survey
Amount low pressure (LP) cylinder initial steam pressure Plp, low pressure (LP) cylinder throttle (steam) temperature tLp, low pressure (LP) cylinder steam admission enthalpy ilp；Measure low pressure (LP) cylinder exhaust steam pressure Pex；
(2) steam actual enthalpy drop H in high pressure cylinder is calculated respectivelyHPWith steam actual enthalpy drop H in intermediate pressure cylinderIP, tool
Body computing formula is as follows:
HHP=ims-ich；
HIP=irh-iich；
Wherein, imsFor high pressure cylinder steam admission enthalpy, ichFor high pressure cylinder exhaust enthalpy, irhFor intermediate pressure cylinder steam admission enthalpy, iichFor intermediate pressure cylinder
Exhaust enthalpy；
(3) the high pressure cylinder initial steam pressure P measured is utilizedms, high pressure cylinder steam admission enthalpy imsWith high pressure cylinder exhaust steam pressure PchCalculate and steam
Vapour isentropic enthalpy drop, ideal enthalpy drop H in high pressure cylinderOHP；Utilize the intermediate pressure cylinder initial steam pressure P measuredrh, intermediate pressure cylinder steam admission enthalpy irhAnd intermediate pressure cylinder
Exhaust steam pressure PichCalculate steam isentropic enthalpy drop, ideal enthalpy drop H in intermediate pressure cylinderOIP；Utilize the low pressure (LP) cylinder initial steam pressure P measuredlp, low pressure (LP) cylinder
Steam admission enthalpy ilpWith low pressure (LP) cylinder exhaust steam pressure PexCalculate steam and calculate entropy enthalpy drop H in low pressure (LP) cylinderOLP；
(4) steam turbine energy budget method is utilized to calculate low pressure (LP) cylinder exhaust enthalpy iex；
(5) steam actual enthalpy drop H in low pressure (LP) cylinder is calculatedLP, computing formula is: HLP=ilp-iex；
(6) high pressure cylinder actual efficiency η is calculated respectivelyHP, intermediate pressure cylinder name efficiency etaIPMWith low pressure (LP) cylinder efficiency etaLP, specifically calculate
Formula is as follows:
ηHP=HHP/HOHP；
ηIPM=HIP/HOIP；
ηLP=HLP/HOLP；
Wherein, HHPFor steam actual enthalpy drop in high pressure cylinder, HOHPFor steam isentropic enthalpy drop, ideal enthalpy drop in high pressure cylinder, HIPFor
The steam nominal enthalpy drop in intermediate pressure cylinder, HOIPFor the nominal isentropic enthalpy drop, ideal enthalpy drop in intermediate pressure cylinder, HLPFor steam reality in low pressure (LP) cylinder
Enthalpy drop, HOLPFor the isentropic enthalpy drop, ideal enthalpy drop in low pressure (LP) cylinder.
Concretely comprising the following steps of described step 5:
(1) unit test heat consumption rate H is calculatedt, computing formula is:
Ht=((Gms-Gss)×(ims-ifw)+Gch×(irh-ich)+Gss×(ims-iss)+Grs×(irh-irs))/Pe；
Wherein, GmsFor main steam flow, GssFor desuperheating water of superheater flow, imsFor high pressure cylinder steam admission enthalpy, ifwFor finally giving
Water enthalpy, GchFor cold reheated steam flow, irhFor intermediate pressure cylinder steam admission enthalpy, ichFor high pressure cylinder exhaust enthalpy, issFor desuperheating water of superheater
Enthalpy, GrsFor reheater attemperation water flow, irsFor reheater desuperheating water enthalpy, PeFor generator active power；
(2) unit revised heat consumption rate H is calculatedr, computing formula is:
Hr=Ht/(C1×C2×C3×C4×C5)
Wherein, C1、C2、C3、C4、C5It is the known parameters that manufactory provides, is main steam pressure, main steam temperature respectively
Degree, reheated steam crushing, reheat steam temperature and the low pressure (LP) cylinder exhaust steam pressure correction factor to heat consumption rate.
The invention has the beneficial effects as follows:
(1) for the Steam Turbine of packing transformation, it is possible to use high, medium and low cylinder pressure efficiency and unit heat consumption rate, and vapour
Turbine height, intermediate pressure cylinder shaft gland steam leakage, low pressure cylinder shaft envelope throttle flow, axle add steam inlet condition, solidifying water temperature through gland heater
Rise and the parameter such as axial seal pressure, supervision section temperature carrys out the effect that overall merit turbine steam seal is transformed.
(2) for high, the steam turbine of intermediate pressure cylinder reversed arrangement, carry out becoming steam temperature working condition tests, carry out respectively reducing main vapour
Temperature improves reheat temperature, and raising Stream temperature degree reduces the test of two operating modes of reheat temperature, makes two above operating mode
IP efficiency ηIPAnd shaft gland steam leakage accounts for main steam G between high intermediate pressure cylindermsThe relation curve of percentage N, obtain unit real
Shaft gland steam leakage percentage between the high intermediate pressure cylinder on border, evaluates the effect of balancing frame packing transformation between height, intermediate pressure cylinder.
(3) by steam turbine monitor section parameter, shaft gland steam leakage before and after height, intermediate pressure cylinder, low pressure shaft seal throttle flow, low pressure shaft seal
Pressure, gland heater initial steam pressure, gland heater throttle (steam) temperature, solidifying water temperature liter, high pressure cylinder efficiency, IP efficiency is low
Cylinder pressure efficiency, before the revised heat consumption rate of unit parameter and packing are transformed, the design load of manufacturing firm compare, evaluate steamer
The energy-saving effect of machine packing transformation, parameter easily measures and calculates, and method simple possible, result of calculation is accurate.
Accompanying drawing explanation
Fig. 1 is the Steam Turbine therrmodynamic system point layout figure of the present invention；
Fig. 2 (a) is IP efficiency η before packing transformationIPRelation curve with high intermediate pressure cylinder shaft gland steam leakage percentage N；
Fig. 2 (b) is IP efficiency η after packing transformationIPRelation curve with high intermediate pressure cylinder shaft gland steam leakage percentage N.
Detailed description of the invention
The present invention will be further described with embodiment below in conjunction with the accompanying drawings:
Certain genco 660MW steam turbine be Shanghai steam turbine plant produce overcritical, single shaft, (the senior middle school's pressing of three cylinders
Cylinder), four steam discharges, a Condensing Reheat Steam Turbine.After unit operation, heat consumption rate does not reaches design load always, and heat consumption is inclined
Height, genco takes advantage of major overhaul chance, and axle head and the axle envelope of flow passage component, packing to steam turbine are optimized transformation.
Turbine steam seal modification scheme is:
(1) high pressure antero posterior axis envelope transform honeycomb steam seal as；(2) low pressure shaft seal transform comb+contact packing as (outward
2 circles and interior 1 circle are transform as contact packing by comb packing)；(3) low pressure positive and negative one to level Four blade tip seal transform honeycomb as
Formula packing；(4) the inserted packing of high pressure nozzle of abrasion is changed；(5) remaining packing all uses comb packing.
Steam Turbine Performance test is carried out according to ASME PTC6-2004 " Turbine Performance Test code ", test measuring point
Arrange according to as shown in Figure 1.
Unit measurement system and measuring instruments: (1) electric power measurement: generator power terminates verification in the outlet of generator
0.02 grade of qualified WT3000 power transducer is measured.(2) flow measurement: condensing water flow uses throat's pressure long-neck of standard
Nozzle and 0.075 grade of 3051 differential pressure transmitter are measured, and condensing water flow nozzle is contained in that #5 is low to be added between outlet and oxygen-eliminating device import
Horizontal pipeline on, and in advance through there being the inspection center of qualification to demarcate.Superheater, reheater attemperation water flow standard orifice plate
Measure；High, intermediate pressure cylinder gland packing leakage flow utilizes standard orifice plate to measure；Low pressure (LP) cylinder shaft seal steam flow standard orifice plate is measured.
(3) pressure measxurement: all pressure-measuring-points are with 0.1 grade of 3051 pressure transmitter measurement.(4) temperature survey: all temperature points are used
Industry one-level E indexing armoured thermocouple.
The IMP discrete data acquisition device that all data acquisitions Shi Lunbaijie company produces, adapted portable computer is carried out
Gathering, collection period is 30 seconds.To the test initial data collected by the operating mode metastable one continuous record period
Carrying out arithmetic mean of instantaneous value calculating, pressure-measuring-point carries out absolute altitude and atmospheric pressure correction.The survey of the multiple measuring point of same parameters in test
Value, takes its arithmetic mean of instantaneous value.
Table 1 is listed 660MW operating mode and the initial data of change steam temperature working condition tests before and after the transformation of unit packing, table 2 arranges
Go out the result of calculation of 660MW working condition tests before and after unit packing is transformed, before and after table 3 is listed the transformation of unit packing, become steam temperature operating mode
The result of calculation of test.
660MW and change steam temperature working condition tests initial data before and after the transformation of table 1 unit packing
This test, using condensing water flow as calculating benchmark, adds the thermal balance with oxygen-eliminating device and quality according to #1, #2, #3 height
EQUILIBRIUM CALCULATION FOR PROCESS obtains feedwater flow, is then calculated main steam flow, reheated steam flow, high pressure cylinder exhaust steam flow (cold again
Vapours flow)；Last item gland leak-off high, middle is calculated according to the last item gland leak-off high, middle measured, low pressure (LP) cylinder shaft seal steam parameter
Amount, feeding of low-pressure shaft seal flow；Enter vapour according to the gland heater measured, Inlet and outlet water temperature parameter calculates gland heater temperature rise
Etc. parameter, as shown in table 2.
660MW working condition tests result of calculation before and after the transformation of table 2 unit packing
Above supercritical 660MW unit packing transformation after, electrical power 640MW, three homophony door standard-sized sheets operating mode under enter
Row becomes steam temperature working condition tests, maintains the power of the assembling unit constant during test, and main vapour pressure is constant, three valve standard-sized sheets.Reduce main steam respectively
Temperature improves reheat steam temperature, improves the method that main steam temperature reduces reheat steam temperature, makes the two difference 20-30 DEG C, with
Determine between height, intermediate pressure cylinder the shaft gland steam leakage at balancing frame and real IP efficiency value.Between height, intermediate pressure cylinder at balancing frame
The result of calculation of shaft gland steam leakage test is shown in Table 3.
Steam temperature working condition tests result is become before and after the transformation of table 3 overcritical 660MW turbine steam seal
Become the result of the test of steam temperature operating mode: before packing transformation, the shaft gland steam leakage at height, intermediate pressure cylinder balancing frame accounts for main steam
The share of flow is 1.283%；After packing transformation, the shaft gland steam leakage at height, intermediate pressure cylinder balancing frame accounts for part of main steam flow
Volume is 0.8945%；.And THA operating condition design data, the shaft gland steam leakage at height, intermediate pressure cylinder balancing frame accounts for part of main steam flow
Volume is 0.986%, and actual steam loss is bigger than design steam loss, and the steam loss after packing Optimizing Reconstruction is less than before packing Optimizing Reconstruction
Shaft gland steam leakage.Before Fig. 2 (a) is packing transformation, gland packing leakage at balancing frame between Steam Turbine Through IP Admission efficiency and height, intermediate pressure cylinder
The relation curve of amount percentage N；After Fig. 2 (b) is packing transformation, between Steam Turbine Through IP Admission efficiency and height, intermediate pressure cylinder at balancing frame
The relation curve of shaft gland steam leakage percentage N.
By table 2, table 3 experiment calculation result it can be seen that steam turbine shaft end gland seal, and flow passage component axle envelope and packing change
After making, high pressure cylinder efficiency is brought up to 85.048% by 82.29%, and IP efficiency is brought up to 91.724% by 90.151%,
The revised heat consumption rate of unit parameter is reduced to 7642.052kJ/kW.h by 7910.408kJ/kW.h, and high pressure rear shaft seal one section arrives
The steam loss of intermediate pressure cylinder gland steam exhauster is reduced to 9315.4kg/h, balancing frame shaft gland steam leakage between height, intermediate pressure cylinder by 9474.5kg/h
Account for main steam flow percentage and be reduced to 0.8945% by 1.283%.In low-load conditions, shaft seal steam pressure reduces, low
Last item gland sealing steam supply flow-reduction, it is impossible to meet the self-packing requirement of unit；Packing transformation after, gland heater initial steam pressure by
0.142MPa is reduced to 0.109MPa, and the solidifying water temperature through gland heater rises and is reduced to 1.7 DEG C by 1.988 DEG C；High, intermediate pressure cylinder
Shaft gland steam leakage at balancing frame is less than design load.Data above illustrates, the energy-saving effect of turbine steam seal transformation is good.
Although the detailed description of the invention of the present invention is described by the above-mentioned accompanying drawing that combines, but not the present invention is protected model
The restriction enclosed, one of ordinary skill in the art should be understood that on the basis of technical scheme, and those skilled in the art are not
Need to pay various amendments or deformation that creative work can make still within protection scope of the present invention.
Claims (4)
1. a comprehensive calculation method for energy-saving effect after turbine steam seal transformation, is characterized in that, comprise the following steps:
Step one: arrange some pressure, temperature, flow rate test point in Steam Turbine therrmodynamic system；
Step 2: measure high pressure cylinder respectively and the leakage steam flow amount of intermediate pressure cylinder antero posterior axis envelope, low pressure cylinder shaft are sealed into steam flow amount, steam turbine
Monitor section parameter, gland heater steam inlet condition and the temperature rise of condensate through gland heater；
Step 3: carry out steam turbine and become steam temperature working condition tests, measure and calculate high pressure cylinder and intermediate pressure cylinder be arranged symmetrically with structure height,
Balancing frame steam loss percentage between intermediate pressure cylinder；
Step 4: calculate the actual efficiency of Steam Turbine high pressure cylinder, the actual efficiency of intermediate pressure cylinder and the reality of low pressure (LP) cylinder respectively
Efficiency；
Step 5: calculate Steam Turbine test heat consumption rate, calculate the heat consumption rate after Steam Turbine parameters revision；
Step 6: by steam turbine monitor section parameter, balancing frame steam loss between high intermediate pressure cylinder, shaft gland steam leakage before and after high, intermediate pressure cylinder,
Low pressure cylinder shaft envelope throttle flow, low pressure (LP) cylinder shaft seal steam pressure, gland heater initial steam pressure, throttle (steam) temperature and temperature rise of condensate,
High pressure cylinder actual efficiency, intermediate pressure cylinder actual efficiency, low pressure (LP) cylinder actual efficiency and the revised heat consumption rate of unit parameter respectively with
Before packing transformation, the design value of manufacturing firm compares, energy-conservation according to the transformation of comparative result comprehensive descision turbine steam seal
Effect；
The concrete measuring method of described step 2 is:
(1) high pressure cylinder, intermediate pressure cylinder gland packing leakage pressure P are measured respectively1, high, intermediate pressure cylinder antero posterior axis gland leak-off flow throttling arrangement
Operating temperature t1, low pressure (LP) cylinder shaft seal steam pressure P2, low pressure cylinder shaft seals operating temperature t into steam flow amount throttling arrangement2, steam turbine
Monitor section pressure P3, steam turbine monitor section temperature t3, gland heater initial steam pressure P4, gland heater throttle (steam) temperature t4, axle seals
Heater inflow temperature t5, gland heater leaving water temperature t6；
(2) known Δ T=t is utilized6-t5Calculate the temperature rise of condensate through gland heater；
(3) high, intermediate pressure cylinder antero posterior axis gland leak-off density p is measured1Seal into vapour density ρ with low pressure cylinder shaft2；
(4) height, the opening diameter d of intermediate pressure cylinder antero posterior axis gland leak-off flow throttling arrangement are calculated respectivelyt1Seal into vapour with low pressure cylinder shaft
The opening diameter d of flow throttling arrangementt2；Concrete formula is:
dt1=d201×λd1×(t1-20)；
dt2=d202×λd2×(t2-20)；
Wherein, d201For high, intermediate pressure cylinder antero posterior axis gland leak-off flow throttling arrangement opening diameter at design temperature 20 DEG C, λd1
For high, the linear expansion coefficient of intermediate pressure cylinder antero posterior axis gland leak-off flow throttling arrangement, d202Seal for low pressure cylinder shaft and throttle into steam flow amount
Device opening diameter at design temperature 20 DEG C, λd2Seal into steam flow amount throttling arrangement linear expansion coefficient for low pressure cylinder shaft；
(5) height, intermediate pressure cylinder antero posterior axis gland leak-off flow G are calculated respectivelyzfSeal into steam flow amount G with low pressure cylinder shaftdzf, concrete formula is:
Gzf=0.126446×α1×dt1 2×ε1×(ΔP1×ρ1)1/2；
Gdzf=0.126446×α2×dt2 2×ε2×(ΔP2×ρ2)1/2；
Wherein, α1For high, the discharge coefficient of intermediate pressure cylinder antero posterior axis gland leak-off flow throttling arrangement, for known quantity, Δ P1During for test
The differential pressure of flow, unit kPa, ε measured by height, intermediate pressure cylinder antero posterior axis gland leak-off flow throttling arrangement1Swollen for measured medium
Swollen coefficient, for known quantity；α2For the discharge coefficient of low pressure (LP) cylinder antero posterior axis gland leak-off flow throttling arrangement, for known quantity, Δ P2For examination
The differential pressure of flow, unit kPa, ε measured by low pressure (LP) cylinder antero posterior axis gland leak-off flow throttling arrangement when testing2Swollen for measured medium
Swollen coefficient, for known quantity.
After a kind of turbine steam seal the most as claimed in claim 1 transformation, the comprehensive calculation method of energy-saving effect, is characterized in that, institute
The concrete measuring method stating step 3 is:
(1) carry out reducing steam turbine main steam temperature respectively and improve reheat temperature, and improve the reduction of steam turbine main steam temperature
Two working condition tests of reheat temperature, making main steam temperature is 20～30 DEG C with the deviation of reheat temperature, other parameter constants；
(2) high pressure cylinder steam admission enthalpy i is measured respectivelyms, intermediate pressure cylinder steam admission enthalpy irh, final feedwater enthalpy ifw, high pressure cylinder exhaust enthalpy ich, mistake
Hot device desuperheating water enthalpy iss, reheater desuperheating water enthalpy irs, #1 height add steam admission enthalpy in1, #1 HP heater drainage enthalpy is1, #2 height add steam admission enthalpy
in2, #2 HP heater drainage enthalpy is2, #3 height add steam admission enthalpy in3, #3 HP heater drainage enthalpy is3, #1 height adds into water enthalpy i11, #1 height add water outlet enthalpy
i12, #2 height adds into water enthalpy i21, #2 height add water outlet enthalpy i22, #3 height adds into water enthalpy i31, #3 height add water outlet enthalpy i32And generated power
Power P e；
(3) feedwater flow G before boiler economizer entrance is measuredfw, boiler drum level change equivalent flow Gb1, superheater desuperheat
Discharge Gss, reheater attemperation water flow Grs；
(4) calculate #1 height respectively and add steam flow amount Ge1, #2 height add steam flow amount Ge2Steam flow amount G is added with #3 heighte3, specifically calculate
Formula is as follows:
Ge1=Gfw×(i12-i11)/(in1-is1)；
Ge2=[Gfw×(i22-i21)-Ge1×(is1-is2)]/(in2-is2)；
Ge3=[Gfw×(i32-i31)-(Ge1+Ge2)×(is2-is3)]/(in3-is3)；
(5) main steam flow G is calculated respectivelyms, cold reheated steam flow GchWith reheated steam flow Grh, specific formula for calculation is such as
Under:
Gms=Gfw+Gb1+Gss；
Gch=Gms-Gg1-Ge1-Ge2-Ge3；
Grh=Gch+Grs；
Wherein, Gg1For high pressure cylinder door rod and antero posterior axis gland steam leakage rate sum, the thermodynamic property book of manufactory be given；
(6) gland packing leakage enthalpy i between high intermediate pressure cylinder is measuredleak；Measure intermediate pressure cylinder initial steam pressure Prh, measure intermediate pressure cylinder exhaust steam pressure
Pich, intermediate pressure cylinder exhaust enthalpy iich；
(7) shaft gland steam leakage G between high intermediate pressure cylinder is setleakAccount for main steam flow GmsPercentage N be respectively 0,2,4,6,8,10, meter
Calculate shaft gland steam leakage and reheated steam mixed enthalpy i between high intermediate pressure cylindermix, specific formula for calculation is:
imix=[Grh×iich+ileak×N×Gms]/(Grh+N×Gms)；
(8) reheated steam actual enthalpy drop H in intermediate pressure cylinder is calculatedi, concrete formula is:
Hi=imix-iich；
(9) the intermediate pressure cylinder initial steam pressure P measured is utilizedrh, shaft gland steam leakage and the mixed enthalpy of reheated steam between high intermediate pressure cylinder
imixWith intermediate pressure cylinder exhaust steam pressure PichCalculate reheated steam isentropic enthalpy drop, ideal enthalpy drop H in intermediate pressure cylinder0；
(10) intermediate pressure cylinder actual efficiency η is calculatedIP, computing formula is:
ηIP=Hi/H0；
(11) computational methods described in step (2)-step (10) are utilized to calculate respectively and two, steam turbine change in plot step (1)
Intermediate pressure cylinder actual efficiency η in steam temperature working condition experimentingIPAnd the relation curve of shaft gland steam leakage percentage N, gained between high intermediate pressure cylinder
Article two, in relation curve, the value of intersection point N is shaft gland steam leakage percentage between the high intermediate pressure cylinder that Steam Turbine is actual.
After a kind of turbine steam seal the most as claimed in claim 1 transformation, the comprehensive calculation method of energy-saving effect, is characterized in that, institute
State step 4 method particularly includes:
(1) high pressure cylinder initial steam pressure P is measuredms, high pressure cylinder throttle (steam) temperature tms, high pressure cylinder steam admission enthalpy ims；Measure high pressure cylinder steam discharge pressure
Power Pch, exhaust temperature of HP tch, high pressure cylinder exhaust enthalpy ich；Measure intermediate pressure cylinder initial steam pressure Prh, intermediate pressure cylinder throttle (steam) temperature trh、
Intermediate pressure cylinder steam admission enthalpy irh；Measure intermediate pressure cylinder exhaust steam pressure Pich, intermediate pressure cylinder exhaust temperature tich, intermediate pressure cylinder exhaust enthalpy iich；Measure low
Cylinder pressure initial steam pressure Plp, low pressure (LP) cylinder throttle (steam) temperature tLp, low pressure (LP) cylinder steam admission enthalpy ilp；Measure low pressure (LP) cylinder exhaust steam pressure Pex；
(2) steam actual enthalpy drop H in high pressure cylinder is calculated respectivelyHPWith steam actual enthalpy drop H in intermediate pressure cylinderi, specifically count
Calculation formula is as follows:
HHP=ims-ich；
Hi=imix-iich；
Wherein, imixFor shaft gland steam leakage between high intermediate pressure cylinder and the mixed enthalpy of reheated steam；
(3) the high pressure cylinder initial steam pressure P measured is utilizedms, high pressure cylinder steam admission enthalpy imsWith high pressure cylinder exhaust steam pressure PchCalculate steam to exist
Isentropic enthalpy drop, ideal enthalpy drop H in high pressure cylinderOHP；
Utilize the intermediate pressure cylinder initial steam pressure P measuredrh, shaft gland steam leakage and reheated steam mixed enthalpy i between high intermediate pressure cylindermix
With intermediate pressure cylinder exhaust steam pressure PichCalculate reheated steam isentropic enthalpy drop, ideal enthalpy drop H in intermediate pressure cylinder0；
Utilize the low pressure (LP) cylinder initial steam pressure P measuredlp, low pressure (LP) cylinder steam admission enthalpy ilpWith low pressure (LP) cylinder exhaust steam pressure PexCalculating steam calculates
Entropy enthalpy drop H in low pressure (LP) cylinderOLP；
(4) steam turbine energy budget method is utilized to calculate low pressure (LP) cylinder exhaust enthalpy iex；
(5) steam actual enthalpy drop H in low pressure (LP) cylinder is calculatedLP, computing formula is: HLP=ilp-iex；
(6) high pressure cylinder actual efficiency η is calculated respectivelyHP, intermediate pressure cylinder actual efficiency ηIPWith low pressure (LP) cylinder actual efficiency ηLP, specifically calculate
Formula is as follows:
ηHP=HHP/HOHP；
ηIP=Hi/H0；
ηLP=HLP/HOLP。
After a kind of turbine steam seal the most as claimed in claim 2 transformation, the comprehensive calculation method of energy-saving effect, is characterized in that, institute
State concretely comprising the following steps of step 5:
(1) unit test heat consumption rate H is calculatedt, computing formula is:
Ht=((Gms-Gss)×(ims-ifw)+Gch×(irh-ich)+Gss×(ims-iss)+Grs×(irh-irs))/Pe；
(2) unit revised heat consumption rate H is calculatedr, computing formula is:
Hr=Ht/(C1×C2×C3×C4×C5)
Wherein, C1、C2、C3、C4、C5It is the known parameters that manufactory provides, is main steam pressure, main steam temperature, more respectively
Vapours crushing, reheat steam temperature and the low pressure (LP) cylinder exhaust steam pressure correction factor to heat consumption rate.
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