CN103646176A - Comprehensive calculation method for energy-saving effect after steam turbine steam seal modification - Google Patents
Comprehensive calculation method for energy-saving effect after steam turbine steam seal modification Download PDFInfo
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Abstract
The invention discloses a comprehensive calculation method for an energy-saving effect after a steam turbine steam seal modification. In detail, the comprehensive calculation method includes the steps that pressure, temperature, flow and electric power test points are arranged on a steam turbine set thermal system; fed water flows, main steam flows, cold reheat steam flows and reheat steam flows are calculated; steam leakage amount of high pressure cylinder and intermediate pressure cylinder balance disc shaft seals of a set is calculated; the steam leakage amount of the high pressure cylinder and intermediate pressure cylinder shaft seals, the steam inlet amount of a low pressure cylinder shaft seal, pressure of the low pressure cylinder shaft seal and temperature rise of condensation water passing through a shaft seal heater are measured; the test heat rate of the set and a heat rate after a parameter modification are calculated; all parameters of a steam turbine are compared with design values prior to the steam shaft modification, so that the energy-saving effect of the steam turbine steam seal modification is evaluated. Through thermal performance testing performed on the steam turbine, the parameters of the thermal system are tested, and the evaluation and analyzing method for the energy-saving effect after the steam turbine steam seal modification are provided. The method is simple and reasonable, and the calculated result is more accurate.
Description
Technical field
The present invention relates to steam turbine field, relate in particular to the COMPREHENSIVE CALCULATING method of the rear energy-saving effect of a kind of turbine steam seal transformation.
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, 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 when judgement and evaluation turbine steam seal correctional effect, the most frequently used method is the foundation that is reduced to the raising of each cylinder efficiency of steam turbine and unit heat consumption rate.But the many factors that affects steam turbine cylinder efficiency, heat consumption rate, comprising: the transformation of (1) Turbine Flow Path; (2) turbine steam seal, retrofit of axial seal; (3) flow passage component fouling and scale removal; (4) inside and outside leakage of system etc.Because unit model is different, packing, shaft gland steam leakage are not quite similar on the impact of unit performance index, sometimes after turbine steam seal transformation, the improvement of cylinder efficiency and heat consumption rate is also not obvious, and wherein also comprise the overhaul effects such as improvement that leak outside in the scale removal of unit flow passage component, system, therefore only utilize the improvement of cylinder efficiency and heat consumption rate comprehensively to analyze turbine steam seal correctional effect.
Summary of the invention
Object of the present invention is exactly in order to address the above problem, and has proposed the COMPREHENSIVE CALCULATING method of the rear energy-saving effect of a kind of turbine steam seal transformation
To achieve these goals, the present invention adopts following technical scheme:
A COMPREHENSIVE CALCULATING method for energy-saving effect after turbine steam seal transformation, comprises the following steps:
Step 1: arrange some pressure, temperature, flow rate test point in Steam Turbine therrmodynamic system.
Step 2: the temperature rise of condensate of measuring respectively leakage steam flow amount, low pressure (LP) cylinder shaft seal admission flow, steam turbine monitor section parameter, gland heater steam inlet condition and the process gland heater of high pressure cylinder and intermediate pressure cylinder front and back shaft seal.
Step 3: carry out steam turbine and become steam temperature working condition tests, measure and calculate balancing frame steam loss number percent between height that high pressure cylinder and intermediate pressure cylinder be arranged symmetrically with structure, intermediate pressure cylinder.
Step 4: the actual efficiency of calculating respectively Steam Turbine high pressure cylinder, intermediate pressure cylinder and low pressure (LP) cylinder.
Step 5: calculate Steam Turbine test heat consumption rate, calculate the revised heat consumption rate of Steam Turbine parameter.
Step 6: by steam turbine monitor section parameter, 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, 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, the revised heat consumption rate of low pressure (LP) cylinder actual efficiency and unit parameter compares with the design value of the front manufacturing firm of packing transformation respectively, comprehensively judges the energy-saving effect of turbine steam seal transformation according to comparative result.
The concrete measuring method of described step 2 is:
(1) measure respectively high pressure cylinder, intermediate pressure cylinder gland packing leakage pressure P
1, high pressure cylinder, intermediate pressure cylinder gland packing leakage temperature t
1, low pressure (LP) cylinder shaft seal steam pressure P
2, low pressure (LP) cylinder shaft seal steam temperature t
2, steam turbine monitor section pressure P
3, steam turbine monitor section temperature t
3, gland heater initial steam pressure P
4, gland heater throttle (steam) temperature t
4, gland heater inflow temperature t
5, gland heater leaving water temperature t
6.
(2) utilize known Δ T=t
6-t
5calculate the solidifying water temperature liter through gland heater, wherein, t
5for gland heater inflow temperature, t
6for gland heater leaving water temperature.
(3) measure high, intermediate pressure cylinder antero posterior axis gland leak-off density p
1with low pressure (LP) cylinder shaft seal admission density p
2.
(4) calculate respectively opening diameter d high, intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device
t1opening diameter d with low pressure (LP) cylinder shaft seal admission flow restriction device
t2; Concrete formula is:
d
t1＝d
201×λ
d1×(t
1-20)
d
t2＝d
202×λ
d2×(t
2-20)
Wherein, d
201for high, the intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device opening diameter at 20 ℃ of design temperatures, λ
d1for linear expansion coefficient high, intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device, t
1for working temperature high, intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device; d
203for the opening diameter of low pressure (LP) cylinder shaft seal admission flow restriction device at 20 ℃ of design temperatures, λ
d3for low pressure (LP) cylinder shaft seal admission flow restriction device linear expansion coefficient, t
2working temperature for low pressure (LP) cylinder shaft seal admission flow restriction device.
(5) calculate respectively high, intermediate pressure cylinder antero posterior axis gland leak-off flow G
zfwith low pressure (LP) cylinder shaft seal admission flow G
dzf, concrete formula is:
G
zf＝0.126446×α
1×d
t1 2×ε
1×(ΔP
1×ρ
1)
1/2
G
dzf＝0.126446×α
2×d
t2 2×ε
2×(ΔP
2×ρ
2)
1/2
Wherein, α
1for coefficient of flow high, intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device, be known quantity, Δ P
1for when test is high, the differential pressure of the measured flow of intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device, the kPa of unit, ε
1for the expansion coefficient of measured medium, it is known quantity; α
2for coefficient of flow high, intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device, be known quantity, Δ P
2for when test is high, the differential pressure of the measured flow of intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device, the kPa of unit, ε
2for the expansion coefficient of measured medium, it is known quantity.
The concrete measuring method of described step 3 is:
(1) reduce respectively steam turbine main steam temperature and improve reheat temperature, and improve two working condition tests that steam turbine main steam temperature reduces reheat temperature, the deviation that makes main steam temperature and reheat temperature is 20～30 ℃, other parameter constants.
(2) difference MEASUREMENT OF STEAM turbine main steam enthalpy i
ms, reheated steam enthalpy i
rh, the final enthalpy that feeds water
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
32with generated output power Pe.
(3) measure the front feedwater flow G of boiler economizer entrance
fw, the equivalent flow G that changes of boiler drum level
b1, desuperheating water of superheater flow G
ss, reheater desuperheating water flow G
rs.
(4) calculate respectively the high steam flow amount G that adds of #1
e1, the high steam flow amount G that adds of #2
e2with the high steam flow amount G that adds of #3
e3, specific formula for calculation is as follows:
G
e1＝G
fw×(i
12-i
11)/(i
n1-i
s1)；
G
e2＝[G
fw×(i
22-i
21)-G
e1×(i
s1-i
s2)]/(i
n2-i
s2)；
G
e3＝[G
fw×(i
32-i
31)-(G
e1+G
e2)×(i
s2-i
s3)]/(i
n3-i
s3)；
Wherein, G
fwfor feedwater flow, i
11for #1 is high, add into water enthalpy, i
12for #1 is high, add water outlet enthalpy, i
21for #2 is high, add into water enthalpy, i
22for #2 is high, add water outlet enthalpy, i
31for #3 is high, add into water enthalpy, i
32for #3 is high, add water outlet enthalpy, i
s1for #1 HP heater drainage enthalpy, i
s2for #2 HP heater drainage enthalpy, i
s3for #3 HP heater drainage enthalpy, i
n1for #1 is high, add admission enthalpy, i
n2for #2 is high, add admission enthalpy, i
n3for #3 is high, add admission enthalpy.
(5) calculate respectively main steam flow G
ms, cold reheated steam flow G
chwith reheated steam flow G
rh, specific formula for calculation is as follows:
G
ms＝G
fw+G
b1+G
ss；
G
ch＝G
ms-G
g1-G
e1-G
e2-G
e3；
G
rh＝G
ch+G
rs；
Wherein, G
fwfor feedwater flow, G
b1for the equivalent flow that boiler drum level changes, G
ssfor desuperheating water of superheater flow; G
msfor main steam flow, G
g1for high pressure cylinder door bar and antero posterior axis gland steam leakage rate sum, by makers' thermodynamic property book, provided G
e1, G
e2and G
e3be respectively high steam flow amount, high steam flow amount and the high steam flow amount of adding of #3 added of #2 added of #1; G
rsfor reheater desuperheating water flow.
(6) measure gland packing leakage enthalpy i between high intermediate pressure cylinder
leak; Measure reheated steam pressure P
rh, measure intermediate pressure cylinder exhaust steam pressure P
ich, intermediate pressure cylinder exhaust enthalpy i
ich.
(7) establish 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, calculate shaft gland steam leakage and the mixed enthalpy i of reheated steam between high intermediate pressure cylinder
mix, specific formula for calculation is:
i
mix＝[G
rh×i
ich+i
leak×N×G
ms]/(G
rh+N×G
ms)；
Wherein, G
rhfor reheated steam flow, i
leakfor gland packing leakage enthalpy between high intermediate pressure cylinder, i
ichfor intermediate pressure cylinder exhaust enthalpy.
(8) calculate the actual enthalpy drop H of reheated steam in intermediate pressure cylinder
i, concrete formula is:
H
i＝i
mix-i
ich；
Wherein, i
mixfor shaft gland steam leakage between high intermediate pressure cylinder and the mixed enthalpy of reheated steam, i
ichfor intermediate pressure cylinder exhaust enthalpy.
(9) utilize the intermediate pressure cylinder initial steam pressure P measuring
rh, intermediate pressure cylinder admission enthalpy i
rhwith intermediate pressure cylinder exhaust steam pressure P
ichthe isentropic enthalpy drop, ideal enthalpy drop H of calculation of steam in intermediate pressure cylinder
0.
(10) calculate intermediate pressure cylinder actual efficiency η
iP, computing formula is:
η
IP＝H
i/H
0
Wherein, H
ifor the actual enthalpy drop of steam in intermediate pressure cylinder, H
0for the isentropic enthalpy drop, ideal enthalpy drop of steam in intermediate pressure cylinder.
(11) utilize the described computing method of step (2)-step (10) to calculate respectively and two intermediate pressure cylinder efficiency eta that become in steam temperature working condition experimentings of the middle steam turbine of plot step (1)
iPand the relation curve of shaft gland steam leakage number percent N between high intermediate pressure cylinder, in two relation curves of gained, the value of intersection point N is shaft gland steam leakage number percent between the high intermediate pressure cylinder of Steam Turbine reality.
The concrete grammar of described step 4 is:
(1) measure high pressure cylinder initial steam pressure P
ms, high pressure cylinder throttle (steam) temperature t
ms, high pressure cylinder admission enthalpy i
ms; Measure high pressure cylinder exhaust steam pressure P
ch, exhaust temperature of HP t
ch, high pressure cylinder exhaust enthalpy i
ch; Measure intermediate pressure cylinder initial steam pressure P
rh, intermediate pressure cylinder throttle (steam) temperature t
rh, intermediate pressure cylinder admission enthalpy i
rh; Measure intermediate pressure cylinder exhaust steam pressure P
ich, intermediate pressure cylinder exhaust temperature t
ich, intermediate pressure cylinder exhaust enthalpy i
ich; Measure low pressure (LP) cylinder initial steam pressure P
lp, low pressure (LP) cylinder throttle (steam) temperature t
lp, low pressure (LP) cylinder admission enthalpy i
lp; Measure low pressure (LP) cylinder exhaust steam pressure P
ex.
(2) the actual enthalpy drop H of difference calculation of steam in high pressure cylinder
hPactual enthalpy drop H with steam in intermediate pressure cylinder
iP, specific formula for calculation is as follows:
H
HP＝i
ms-i
ch；
H
IP＝i
rh-i
ich；
Wherein, i
msfor high pressure cylinder admission enthalpy, i
chfor high pressure cylinder exhaust enthalpy, i
rhfor intermediate pressure cylinder admission enthalpy, i
ichfor intermediate pressure cylinder exhaust enthalpy.
(3) utilize the high pressure cylinder initial steam pressure P measuring
ms, high pressure cylinder admission enthalpy i
mswith high pressure cylinder exhaust steam pressure P
chthe isentropic enthalpy drop, ideal enthalpy drop H of calculation of steam in high pressure cylinder
oHP; Utilize the intermediate pressure cylinder initial steam pressure P measuring
rh, intermediate pressure cylinder admission enthalpy i
rhwith intermediate pressure cylinder exhaust steam pressure P
ichthe isentropic enthalpy drop, ideal enthalpy drop H of calculation of steam in intermediate pressure cylinder
oIP; Utilize the low pressure (LP) cylinder initial steam pressure P measuring
lp, low pressure (LP) cylinder admission enthalpy i
lpwith low pressure (LP) cylinder exhaust steam pressure P
excalculation of steam is calculated the entropy enthalpy drop H in low pressure (LP) cylinder
oLP.
(4) utilize steam turbine energy budget method to calculate low pressure (LP) cylinder exhaust enthalpy i
ex.
(5) the actual enthalpy drop H of calculation of steam in low pressure (LP) cylinder
lP, computing formula is: H
lP=i
lP-i
ex.
(6) calculate respectively high pressure cylinder actual efficiency η
hP, intermediate pressure cylinder actual efficiency η
iPwith low pressure (LP) cylinder efficiency eta
lP, specific formula for calculation is as follows:
η
HP＝H
HP/H
OHP；
η
IP＝H
IP/H
OIP；
η
LP＝H
LP/H
OLP；
Wherein, H
hPfor the actual enthalpy drop of steam in high pressure cylinder, H
oHPfor the isentropic enthalpy drop, ideal enthalpy drop of steam in high pressure cylinder, H
iPfor the actual enthalpy drop of steam in intermediate pressure cylinder, H
oIPfor the isentropic enthalpy drop, ideal enthalpy drop in intermediate pressure cylinder, H
lPfor the actual enthalpy drop of steam in low pressure (LP) cylinder, H
oLPfor the entropy enthalpy drop in low pressure (LP) cylinder.
The concrete steps of described step 5 are:
(1) calculate unit test heat consumption rate H
t, computing formula is:
H
t＝((G
ms-G
ss)×(i
ms-i
fw)+G
ch×(i
rh-i
ch)+G
ss×(i
ms-i
ss)+G
rs×(i
rh-i
rs))/Pe；
Wherein, G
msfor main steam flow, G
ssfor desuperheating water of superheater flow, i
msfor high pressure cylinder admission enthalpy, i
fwfor final feedwater enthalpy, G
chfor cold reheated steam flow, i
rhfor intermediate pressure cylinder admission enthalpy, i
chfor high pressure cylinder exhaust enthalpy, i
ssfor desuperheating water of superheater enthalpy, G
rsfor reheater desuperheating water flow, i
rsfor reheater desuperheating water enthalpy, Pe is generator active power.
(2) calculate the revised heat consumption rate H of unit
r, computing formula is:
H
r＝H
t/(C
1×C
2×C
3×C
4×C
5)
Wherein, C
1, C
2, C
3, C
4, C
5respectively main steam pressure, main steam temperature, reheated steam crushing, reheat steam temperature and the correction factor of low pressure (LP) cylinder exhaust steam pressure to heat consumption rate, C
1, C
2, C
3, C
4, C
5be the known parameters that manufacturing plant provides.
The invention has the beneficial effects as follows:
(1) Steam Turbine of transforming for packing, can utilize high, medium and low cylinder pressure efficiency and unit heat consumption rate, and steam turbine is high, intermediate pressure cylinder shaft gland steam leakage, low pressure (LP) cylinder shaft seal throttle flow, axle add steam inlet condition, through parameters such as the solidifying water temperature liter of gland heater and axial seal pressure, supervision section temperature, carry out the effect of comprehensive evaluation turbine steam seal transformation.
(2) for steam turbine high, intermediate pressure cylinder reversed arrangement, become steam temperature working condition tests, reduce respectively main stripping temperature and improve reheat temperature, and improve the test that main stripping temperature reduces by two operating modes of reheat temperature, make the intermediate pressure cylinder efficiency eta of above two operating modes
iPand between high intermediate pressure cylinder, shaft gland steam leakage accounts for main steam G
msthe relation curve of number percent N, 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.
(3) by steam turbine monitor section parameter, high, intermediate pressure cylinder front and back shaft gland steam leakage, 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, intermediate pressure cylinder efficiency, low pressure (LP) cylinder efficiency, before the transformation of the revised heat consumption rate of unit parameter and packing, 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, result of calculation is accurate.
Accompanying drawing explanation
Fig. 1 is Steam Turbine therrmodynamic system measuring point arrangenent diagram of the present invention;
Fig. 2 (a) is the front intermediate pressure cylinder efficiency eta of packing transformation
iPrelation curve with high intermediate pressure cylinder shaft gland steam leakage number percent N;
Fig. 2 (b) is the rear intermediate pressure cylinder efficiency eta of packing transformation
iPrelation curve with high intermediate pressure cylinder shaft gland steam leakage number percent N.
Embodiment:
Below in conjunction with accompanying drawing and embodiment, the present invention will be further described:
Certain genco's 660MW steam turbine is overcritical, single shaft, three cylinders (senior middle school's pressing cylinder), four steam discharges, the Condensing Reheat Steam Turbine that Shanghai steam turbine plant is produced.After unit operation, heat consumption rate does not reach design load always, and hear rate is higher, and genco takes advantage of major overhaul chance, and the shaft seal of the axle head of steam turbine and flow passage component, packing are optimized to transformation.
Turbine steam seal modification scheme is:
(1) before and after high pressure, shaft seal transform honeycomb steam seal as; (2) low pressure shaft seal transform broach+contact packing (outer 2 circles and interior 1 circle transform contact packing as by broach packing) as; (3) low pressure positive and negative one to level Four blade tip seal transform honeycomb steam seal as; (4) change the inserted packing of high pressure nozzle of wearing and tearing; (5) all the other packings all adopt broach packing.
According to ASME PTC6-2004 < < Turbine Performance Test rules > >, carry out Steam Turbine Performance test, the layout of test measuring point is according to 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 #5, and in advance through there being the inspection center of qualification to demarcate.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.
The IMP discrete data acquisition device that all data acquisitions are produced with Shi Lunbaijie company, 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 raw data of unit packing transformation front and back 660MW operating mode and change steam temperature working condition tests, in table 2, list the result of calculation of unit packing transformation front and back 660MW working condition tests, in table 3, list the result of calculation that unit packing transformation front and back become steam temperature working condition tests.
660MW and change steam temperature working condition tests raw data before and after the transformation of table 1 unit packing
This test is usingd condensing water flow as calculating benchmark, calculate feedwater flow according to #1, #2, #3 high adding with thermal equilibrium and the mass balance of oxygen-eliminating device, 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, high, the middle pressure shaft gland steam leakage of low pressure (LP) cylinder shaft seal steam calculation of parameter measured, feeding of low-pressure shaft seal flow; According to the gland heater admission of measuring, Inlet and outlet water temperature parameter, calculate the parameters such as gland heater temperature rise, as shown in table 2.
660MW working condition tests result of calculation before and after the transformation of table 2 unit packing
After above supercritical 660MW unit packing transformation, under the operating mode of electric power 640MW, three homophony door standard-sized sheets, become steam temperature working condition tests, maintain the power of the assembling unit constant during test, main vapour pressure is constant, three valve standard-sized sheets.Reduce respectively main steam temperature and improve reheat steam temperature, improve the method that main steam temperature reduces reheat steam temperature, make the two poor 20-30 ℃, to determine shaft gland steam leakage and the real intermediate pressure cylinder efficiency value at balancing frame place between height, intermediate pressure cylinder.Between height, intermediate pressure cylinder, the result of calculation of the shaft gland steam leakage at balancing frame place test is in Table 3.
Before and after the overcritical 660MW turbine steam seal transformation of table 3, become steam temperature working condition tests result
Become the test findings of steam temperature operating mode: before packing transformation, the share that shaft gland steam leakage high, intermediate pressure cylinder balancing frame place accounts for main steam flow is 1.283%; After packing transformation, the share that shaft gland steam leakage high, intermediate pressure cylinder balancing frame place accounts for main steam flow is 0.8945%; .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 0.986%, and actual steam loss is larger than design steam loss, and the steam loss after packing Optimizing Reconstruction is less than the shaft gland steam leakage before packing Optimizing Reconstruction.Fig. 2 (a) is for before packing transformation, the relation curve of balancing frame place shaft gland steam leakage number percent N between Steam Turbine Through IP Admission efficiency and height, intermediate pressure cylinder; Fig. 2 (b) is for after packing transformation, the relation curve of balancing frame place shaft gland steam leakage number percent N between Steam Turbine Through IP Admission efficiency and height, intermediate pressure cylinder.
By table 2, table 3 experiment calculation result, can be found out, steam turbine axle head packing, and after flow passage component shaft seal and packing transformation, high pressure cylinder efficiency brings up to 85.048% by 82.29%, intermediate pressure cylinder efficiency brings 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, high pressure rear axle front cover section is reduced to 9315.4kg/h to the steam loss of intermediate pressure cylinder gland steam exhauster by 9474.5kg/h, and between height, intermediate pressure cylinder, balancing frame shaft gland steam leakage accounts for main steam flow number percent and is reduced to 0.8945% by 1.283%.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; After packing transformation, gland heater initial steam pressure is reduced to 0.109MPa by 0.142MPa, and the solidifying water temperature of process gland heater rises and is reduced to 1.7 ℃ by 1.988 ℃; Shaft gland steam leakage 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.
Although above-mentioned, by reference to the accompanying drawings the specific embodiment of the present invention is described; but be not limiting the scope of the invention; one of ordinary skill in the art should be understood that; on the basis of technical scheme of the present invention, those skilled in the art do not need to pay various modifications that creative work can make or distortion still in protection scope of the present invention.
Claims (5)
1. a COMPREHENSIVE CALCULATING method for energy-saving effect after turbine steam seal transformation, is characterized in that, comprises the following steps:
Step 1: arrange some pressure, temperature, flow rate test point in Steam Turbine therrmodynamic system;
Step 2: the temperature rise of condensate of measuring respectively leakage steam flow amount, low pressure (LP) cylinder shaft seal admission flow, steam turbine monitor section parameter, gland heater steam inlet condition and the process gland heater of high pressure cylinder and intermediate pressure cylinder front and back shaft seal;
Step 3: carry out steam turbine and become steam temperature working condition tests, measure and calculate balancing frame steam loss number percent between height that high pressure cylinder and intermediate pressure cylinder be arranged symmetrically with structure, intermediate pressure cylinder;
Step 4: the actual efficiency of calculating respectively Steam Turbine high pressure cylinder, intermediate pressure cylinder and low pressure (LP) cylinder;
Step 5: calculate Steam Turbine test heat consumption rate, calculate the revised heat consumption rate of Steam Turbine parameter;
Step 6: by steam turbine monitor section parameter, 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, 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, the revised heat consumption rate of low pressure (LP) cylinder actual efficiency and unit parameter compares with the design value of the front manufacturing firm of packing transformation respectively, comprehensively judges the energy-saving effect of turbine steam seal transformation according to comparative result.
2. the COMPREHENSIVE CALCULATING method of energy-saving effect after a kind of turbine steam seal transformation as claimed in claim 1, is characterized in that, the concrete measuring method of described step 2 is:
(1) measure respectively high pressure cylinder, intermediate pressure cylinder gland packing leakage pressure P
1, high pressure cylinder, intermediate pressure cylinder gland packing leakage temperature t
1, low pressure (LP) cylinder shaft seal steam pressure P
2, low pressure (LP) cylinder shaft seal steam temperature t
2, steam turbine monitor section pressure P
3, steam turbine monitor section temperature t
3, gland heater initial steam pressure P
4, gland heater throttle (steam) temperature t
4, gland heater inflow temperature t
5, gland heater leaving water temperature t
6;
(2) utilize known Δ T=t
6-t
5calculate the solidifying water temperature liter through gland heater, wherein, t
5for gland heater inflow temperature, t
6for gland heater leaving water temperature;
(3) measure high, intermediate pressure cylinder antero posterior axis gland leak-off density p
1with low pressure (LP) cylinder shaft seal admission density p
2;
(4) calculate respectively opening diameter d high, intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device
t1opening diameter d with low pressure (LP) cylinder shaft seal admission flow restriction device
t2; Concrete formula is:
d
t1＝d
201×λ
d1×(t
1-20)；
d
t2＝d
202×λ
d2×(t
2-20)；
Wherein, d
201for high, the intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device opening diameter at 20 ℃ of design temperatures, λ
d1for linear expansion coefficient high, intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device, t
1for working temperature high, intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device; d
203for the opening diameter of low pressure (LP) cylinder shaft seal admission flow restriction device at 20 ℃ of design temperatures, λ
d3for low pressure (LP) cylinder shaft seal admission flow restriction device linear expansion coefficient, t
2working temperature for low pressure (LP) cylinder shaft seal admission flow restriction device;
(5) calculate respectively high, intermediate pressure cylinder antero posterior axis gland leak-off flow G
zfwith low pressure (LP) cylinder shaft seal admission flow G
dzf, concrete formula is:
G
zf＝0.126446×α
1×d
t1 2×ε
1×(ΔP
1×ρ
1)
1/2；
G
dzf＝0.126446×α
2×d
t2 2×ε
2×(ΔP
2×ρ
2)
1/2；
Wherein, α
1for coefficient of flow high, intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device, be known quantity, Δ P
1for when test is high, the differential pressure of the measured flow of intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device, the kPa of unit, ε
1for the expansion coefficient of measured medium, it is known quantity; α
2for coefficient of flow high, intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device, be known quantity, Δ P
2for when test is high, the differential pressure of the measured flow of intermediate pressure cylinder antero posterior axis gland leak-off flow restriction device, the kPa of unit, ε
2for the expansion coefficient of measured medium, it is known quantity.
3. the COMPREHENSIVE CALCULATING method of energy-saving effect after a kind of turbine steam seal transformation as claimed in claim 1, is characterized in that, the concrete measuring method of described step 3 is:
(1) reduce respectively steam turbine main steam temperature and improve reheat temperature, and improve two working condition tests that steam turbine main steam temperature reduces reheat temperature, the deviation that makes main steam temperature and reheat temperature is 20～30 ℃, other parameter constants;
(2) difference MEASUREMENT OF STEAM turbine main steam enthalpy i
ms, reheated steam enthalpy i
rh, the final enthalpy that feeds water
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
32with generated output power Pe;
(3) measure the front feedwater flow G of boiler economizer entrance
fw, the equivalent flow G that changes of boiler drum level
b1, desuperheating water of superheater flow G
ss, reheater desuperheating water flow G
rs;
(4) calculate respectively the high steam flow amount G that adds of #1
e1, the high steam flow amount G that adds of #2
e2with the high steam flow amount G that adds of #3
e3, specific formula for calculation is as follows:
G
e1＝G
fw×(i
12-i
11)/
(i n1-i
s1)；
G
e2＝[G
fw×(i
22-i
21)-G
e1×(i
s1-i
s2)]/(i
n2-i
s2)；
G
e3＝[G
fw×(i
32-i
31)-(G
e1+G
e2)×(i
s2-i
s3)]/(i
n3-i
s3)；
Wherein, G
fwfor feedwater flow, i
11for #1 is high, add into water enthalpy, i
12for #1 is high, add water outlet enthalpy, i
21for #2 is high, add into water enthalpy, i
22for #2 is high, add water outlet enthalpy, i
31for #3 is high, add into water enthalpy, i
32for #3 is high, add water outlet enthalpy, i
s1for #1 HP heater drainage enthalpy, i
s2for #2 HP heater drainage enthalpy, i
s3for #3 HP heater drainage enthalpy, i
n1for #1 is high, add admission enthalpy, i
n2for #2 is high, add admission enthalpy, i
n3for #3 is high, add admission enthalpy;
(5) calculate respectively main steam flow G
ms, cold reheated steam flow G
chwith reheated steam flow G
rh, specific formula for calculation is as follows:
G
ms＝G
fw+G
b1+G
ss；
G
ch＝G
ms-G
g1-G
e1-G
e2-G
e3；
G
rh＝G
ch+G
rs；
Wherein, G
fwfor feedwater flow, G
b1for the equivalent flow that boiler drum level changes, G
ssfor desuperheating water of superheater flow; G
msfor main steam flow, G
g1for high pressure cylinder door bar and antero posterior axis gland steam leakage rate sum, by makers' thermodynamic property book, provided G
e1, G
e2and G
e3be respectively high steam flow amount, high steam flow amount and the high steam flow amount of adding of #3 added of #2 added of #1; G
rsfor reheater desuperheating water flow;
(6) measure gland packing leakage enthalpy i between high intermediate pressure cylinder
leak; Measure reheated steam pressure P
rh, measure intermediate pressure cylinder exhaust steam pressure P
ich, intermediate pressure cylinder exhaust enthalpy i
ich;
(7) establish 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, calculate shaft gland steam leakage and the mixed enthalpy i of reheated steam between high intermediate pressure cylinder
mix, specific formula for calculation is:
i
mix＝[G
rh×i
ich+i
leak×N×G
ms]/(G
rh+N×G
ms)；
Wherein, G
rhfor reheated steam flow, i
leakfor gland packing leakage enthalpy between high intermediate pressure cylinder, i
ichfor intermediate pressure cylinder exhaust enthalpy;
(8) calculate the actual enthalpy drop H of reheated steam in intermediate pressure cylinder
i, concrete formula is:
H
i＝i
mix-i
ich；
Wherein, i
mixfor shaft gland steam leakage between high intermediate pressure cylinder and the mixed enthalpy of reheated steam, i
ichfor intermediate pressure cylinder exhaust enthalpy;
(9) utilize the intermediate pressure cylinder initial steam pressure P measuring
rh, intermediate pressure cylinder admission enthalpy i
rhwith intermediate pressure cylinder exhaust steam pressure P
ichthe isentropic enthalpy drop, ideal enthalpy drop H of calculation of steam in intermediate pressure cylinder
0;
(10) calculate intermediate pressure cylinder actual efficiency η
iP, computing formula is:
η
IP＝H
i/H
0；
Wherein, H
ifor the actual enthalpy drop of steam in intermediate pressure cylinder, H
0for the isentropic enthalpy drop, ideal enthalpy drop of steam in intermediate pressure cylinder;
(11) utilize the described computing method of step (2)-step (10) to calculate respectively and two intermediate pressure cylinder efficiency eta that become in steam temperature working condition experimentings of the middle steam turbine of plot step (1)
iPand the relation curve of shaft gland steam leakage number percent N between high intermediate pressure cylinder, in two relation curves of gained, the value of intersection point N is shaft gland steam leakage number percent between the high intermediate pressure cylinder of Steam Turbine reality.
4. the COMPREHENSIVE CALCULATING method of energy-saving effect after a kind of turbine steam seal transformation as claimed in claim 1, is characterized in that, the concrete grammar of described step 4 is:
(1) measure high pressure cylinder initial steam pressure P
ms, high pressure cylinder throttle (steam) temperature t
ms, high pressure cylinder admission enthalpy i
ms; Measure high pressure cylinder exhaust steam pressure P
ch, exhaust temperature of HP t
ch, high pressure cylinder exhaust enthalpy i
ch; Measure intermediate pressure cylinder initial steam pressure P
rh, intermediate pressure cylinder throttle (steam) temperature t
rh, intermediate pressure cylinder admission enthalpy i
rh; Measure intermediate pressure cylinder exhaust steam pressure P
ich, intermediate pressure cylinder exhaust temperature t
ich, intermediate pressure cylinder exhaust enthalpy i
ich; Measure low pressure (LP) cylinder initial steam pressure P
lp, low pressure (LP) cylinder throttle (steam) temperature t
lp, low pressure (LP) cylinder admission enthalpy i
lp; Measure low pressure (LP) cylinder exhaust steam pressure P
ex;
(2) the actual enthalpy drop H of difference calculation of steam in high pressure cylinder
hPactual enthalpy drop H with steam in intermediate pressure cylinder
iP, specific formula for calculation is as follows:
H
HP＝i
ms-i
ch；
H
IP＝i
rh-i
ich；
Wherein, i
msfor high pressure cylinder admission enthalpy, i
chfor high pressure cylinder exhaust enthalpy, i
rhfor intermediate pressure cylinder admission enthalpy, i
ichfor intermediate pressure cylinder exhaust enthalpy;
(3) utilize the high pressure cylinder initial steam pressure P measuring
ms, high pressure cylinder admission enthalpy i
mswith high pressure cylinder exhaust steam pressure P
chthe isentropic enthalpy drop, ideal enthalpy drop H of calculation of steam in high pressure cylinder
oHP; Utilize the intermediate pressure cylinder initial steam pressure P measuring
rh, intermediate pressure cylinder admission enthalpy i
rhwith intermediate pressure cylinder exhaust steam pressure P
ichthe isentropic enthalpy drop, ideal enthalpy drop H of calculation of steam in intermediate pressure cylinder
oIP; Utilize the low pressure (LP) cylinder initial steam pressure P measuring
lp, low pressure (LP) cylinder admission enthalpy i
lpwith low pressure (LP) cylinder exhaust steam pressure P
excalculation of steam is calculated the entropy enthalpy drop H in low pressure (LP) cylinder
oLP;
(4) utilize steam turbine energy budget method to calculate low pressure (LP) cylinder exhaust enthalpy i
ex;
(5) the actual enthalpy drop H of calculation of steam in low pressure (LP) cylinder
lP, computing formula is: H
lP=i
lP-i
ex;
(6) calculate respectively high pressure cylinder actual efficiency η
hP, intermediate pressure cylinder actual efficiency η
iPwith low pressure (LP) cylinder efficiency eta
lP, specific formula for calculation is as follows:
η
HP＝H
HP/H
OHP；
η
IP＝H
IP/H
OIP；
η
LP＝H
LP/H
OLP；
Wherein, H
hPfor the actual enthalpy drop of steam in high pressure cylinder, H
oHPfor the isentropic enthalpy drop, ideal enthalpy drop of steam in high pressure cylinder, H
iPfor the actual enthalpy drop of steam in intermediate pressure cylinder, H
oIPfor the isentropic enthalpy drop, ideal enthalpy drop in intermediate pressure cylinder, H
lPfor the actual enthalpy drop of steam in low pressure (LP) cylinder, H
oLPfor the entropy enthalpy drop in low pressure (LP) cylinder.
5. the COMPREHENSIVE CALCULATING method of energy-saving effect after a kind of turbine steam seal transformation as claimed in claim 1, is characterized in that, the concrete steps of described step 5 are:
(1) calculate unit test heat consumption rate H
t, computing formula is:
H
t＝((G
ms-G
ss)×(i
ms-i
fw)+G
ch×(i
rh-i
ch)+G
ss×(i
ms-i
ss)+G
rs×(i
rh-i
rs))/Pe；
Wherein, G
msfor main steam flow, G
ssfor desuperheating water of superheater flow, i
msfor high pressure cylinder admission enthalpy, i
fwfor final feedwater enthalpy, G
chfor cold reheated steam flow, i
rhfor intermediate pressure cylinder admission enthalpy, i
chfor high pressure cylinder exhaust enthalpy, i
ssfor desuperheating water of superheater enthalpy, G
rsfor reheater desuperheating water flow, i
rsfor reheater desuperheating water enthalpy, Pe is generator active power;
(2) calculate the revised heat consumption rate H of unit
r, computing formula is:
H
r＝H
t/(C
1×C
2×C
3×C
4×C
5)
Wherein, C
1, C
2, C
3, C
4, C
5being the known parameters that manufacturing plant provides, is respectively main steam pressure, main steam temperature, reheated steam crushing, reheat steam temperature and the correction factor of low pressure (LP) cylinder exhaust steam pressure to heat consumption rate.
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