CN103954321A - Novel method and novel device for testing gas leaking quantity of shaft seal between cylinders of turbine with combination cylinder of high and intermediate pressure cylinder - Google Patents
Novel method and novel device for testing gas leaking quantity of shaft seal between cylinders of turbine with combination cylinder of high and intermediate pressure cylinder Download PDFInfo
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- CN103954321A CN103954321A CN201410175326.8A CN201410175326A CN103954321A CN 103954321 A CN103954321 A CN 103954321A CN 201410175326 A CN201410175326 A CN 201410175326A CN 103954321 A CN103954321 A CN 103954321A
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Abstract
The invention discloses a novel method and a novel device for testing the gas leaking quantity of a shaft seal between cylinders of a turbine with a combination cylinder of a high and an intermediate pressure cylinder. The method comprises the following steps: step 1, measuring the steam parameters of the turbine under the work conditions of 100% and 50% loads; step 2, calculating the through-flow efficiency function of the intermediate pressure cylinder with the gas leaking ratio LR of the shaft seal as a variable under the work conditions of 100% and 50% loads; step 3, calculating the gas leaking ratio LR and the actual gas leaking quantity FL. The invention further discloses the test device. The method and the device have the beneficial effects that data collected by the test method and device are easy to measure, the structure is simple, the data collected on site can be remotely transmitted to a computer through a wireless network, and the implementation is easy.
Description
Technical field
Patent of the present invention belongs to generating mechanical field, is specifically related to a kind of novel high intermediate pressure cylinder and closes gland packing leakage weight testing method and device between cylinder steam turbine cylinder.
Background technology
Steam turbine, as most important mechanical rotation equipment in power plant, is being born the function that power plant's heat energy is converted into mechanical energy.Along with electric power unit develops to large capacity high parameter, in power plant, steam turbine serviceability is increasing to the economic influence of power plant.And the size of the shaft gland steam leakage of steam turbine directly affects again normal capacity for work and the performance of moving of steam turbine.
Between power plant steam turbine cylinder in shaft seal operational factor, between cylinder, the leakage flow of shaft seal has reflected the duty of shaft seal the most intuitively, under identical running boundary condition, between senior middle school's pressing cylinder steam turbine cylinder, shaft gland steam leakage is lower, represents that the running status of shaft seal between cylinder is better.
Taking a certain subcritical 600MW Direct Air-cooled Unit steam turbine as example, under 100% operating load, to close shaft gland steam leakage design load between cylinder steam turbine cylinder be 10t/h to high intermediate pressure cylinder, and on-the-spot test value may exceed one times of design load, directly increase the about 0.6g/kWh of power plant's gross coal consumption rate.
Therefore, should adopt between senior middle school's pressing cylinder steam turbine cylinder shaft gland steam leakage as the leading indicator that judges shaft seal running status between senior middle school's pressing cylinder steam turbine cylinder, but current power plant high intermediate pressure cylinder closes shaft gland steam leakage between cylinder steam turbine cylinder and cannot directly measure, also there is no special monitoring device and monitoring method, the state that therefore cannot close gland packing leakage between cylinder steam turbine cylinder to power plant's high intermediate pressure cylinder is comprehensively monitored.
Therefore more accurate in the urgent need to a kind of measurement data, method of testing relatively simple for structure and device solve current problem.
Summary of the invention
One of object of the present invention be to provide a kind of data accurately, the method for testing calculating efficient high intermediate pressure cylinder and close shaft gland steam leakage between cylinder steam turbine cylinder.
Technical scheme provided by the invention is:
A kind of novel high intermediate pressure cylinder closes gland packing leakage weight testing method between cylinder steam turbine cylinder, and it comprises following steps:
step 1, the steam parameter of mensuration steam turbine under 100% and 50% load condition:
(1) unit is under the basic method of operation of 100% load, remove unit primary frequency modulation and AGC function, steam turbine import main steam temperature, intermediate pressure cylinder inlet steam temperature keep ratings, and keep power generator turbine admission valve position certain, steam parameter p after the Control Stage of Steam Turbine of collection unit under this steady state (SS) after unit operation is stable
1and t
1, steam parameter p before intermediate pressure cylinder main inlet throttle-stop valve
2and t
2, steam parameter p on cross over pipe between mesolow cylinder
3and t
3, intermediate pressure cylinder is through-flow level before a steam parameter p
4;
Wherein, symbol p represents pressure, units MPa; T represents temperature, unit DEG C; Index number represents different measuring position;
(2) unit is under the basic method of operation of 50% load, remove unit primary frequency modulation and AGC function, steam turbine import main steam temperature, intermediate pressure cylinder inlet steam temperature keep ratings, and keep power generator turbine admission valve position certain, steam parameter p ' after the Control Stage of Steam Turbine of collection unit under this steady state (SS) after unit operation is stable
1and t '
1, steam parameter p ' before intermediate pressure cylinder main inlet throttle-stop valve
2and t '
2, steam parameter p ' on cross over pipe between mesolow cylinder
3and t '
3, intermediate pressure cylinder is through-flow level before a steam parameter p '
4;
Wherein, symbol p represents pressure, units MPa; T represents temperature, unit DEG C; Index number represents different measuring position; Subscript " ' " for distinguishing the parameter of step 1 (1);
step 2, calculate under 100% and 50% load condition taking gland packing leakage the intermediate pressure cylinder flow efficiency function as variable than LR:
(1) calculate intermediate pressure cylinder flow efficiency function under 100% load condition:
A) data of step 1 collection are brought into formula (1-1) ~ (8-1) and calculate following state point thermal parameter:
Steam enthalpy h after governing stage
1=f
1(p
1, t
1) formula (1-1)
Steam entropy s after governing stage
1=f
2(p
1, t
1) formula (2-1)
Before intermediate pressure cylinder main inlet throttle-stop valve, steam enthalpy is h
2=f
1(p
2, t
2) formula (3-1)
Steam entropy s before intermediate pressure cylinder main inlet throttle-stop valve
2=f
2(p
2, t
2) formula (4-1)
Between mesolow cylinder, on cross over pipe, steam enthalpy is h
3=f
1(p
3, t
3) formula (5-1)
Steam entropy s on cross over pipe between mesolow cylinder
3=f
2(p
3, t
3) formula (6-1)
Steam enthalpy h before level that intermediate pressure cylinder is through-flow
4=(h
2+ LR × h
1the formula of)/(1+LR) (7-1)
Steam entropy s before level that intermediate pressure cylinder is through-flow
4=f
4(p
4, h
4) formula (8-1)
In formula (1-1) ~ (8-1), function f
1for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam enthalpy, function f
2for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam entropy; Function f
4for the known pressure of international water and steam characteristic association and the computing formula of enthalpy calculation of steam entropy;
Wherein, h is steam enthalpy, the kJ/kg of unit; S is steam entropy, the kJ/kg.K of unit; LR be shaft gland steam leakage with design point under the ratio of intermediate pressure cylinder inlet steam flow;
B) calculate the intermediate pressure cylinder flow efficiency taking LR as variable according to formula (9-1)
η lfunction:
formula (9-1)
In formula (9-1),
H
4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam enthalpy, the kJ/kg of unit,
H
3represent LR leak vapour than time low pressure (LP) cylinder between steam enthalpy on cross over pipe, the kJ/kg of unit,
H
srepresent LR leak vapour than time intermediate pressure cylinder through-flow constant entropy steam discharge steam enthalpy, the kJ/kg of unit,
H
sadopt formula (10-1) to calculate:
H '
s=f
3(p '
3, s '
4) formula (10-1)
In formula (10-1),
s 4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam entropy, the kJ/kg of unit;
Function f
3for the known pressure of international water and steam characteristic association and the computing formula of steam entropy calculation of steam enthalpy;
(2) calculate intermediate pressure cylinder flow efficiency function under 50% load condition:
A) data of step 1 collection are brought into formula (1-2) ~ (8-2) and calculate following state point thermal parameter:
Steam enthalpy h ' after governing stage
1=f
1(p '
1, t '
1) formula (1-2)
Steam entropy s ' after governing stage
1=f
2(p '
1, t '
1) formula (2-2)
Before intermediate pressure cylinder main inlet throttle-stop valve, steam enthalpy is h '
2=f
1(p '
2, t '
2) formula (3-2)
Steam entropy s ' before intermediate pressure cylinder main inlet throttle-stop valve
2=f
2(p '
2, t '
2) formula (4-2)
Between mesolow cylinder, on cross over pipe, steam enthalpy is h '
3=f
1(p '
3, t '
3) formula (5-2)
Steam entropy s ' on cross over pipe between mesolow cylinder
3=f
2(p '
3, t '
3) formula (6-2)
Steam enthalpy h ' before level that intermediate pressure cylinder is through-flow
4=(h '
2+ LR × h '
1the formula of)/(1+LR) (7-2)
Steam entropy s ' before level that intermediate pressure cylinder is through-flow
4=f
4(p '
4, h '
4) formula (8-2)
In formula (1-2) ~ (8-2), function f
1for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam enthalpy, function f
2for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam entropy; Function f
4for the known pressure of international water and steam characteristic association and the computing formula of enthalpy calculation of steam entropy;
Wherein, h ' is steam enthalpy, the kJ/kg of unit; S ' is steam entropy, the kJ/kg.K of unit; LR be shaft gland steam leakage with design point under the ratio of intermediate pressure cylinder inlet steam flow;
B) calculate the intermediate pressure cylinder flow efficiency taking LR as variable according to formula (9-2)
η ' lfunction:
formula (9-2)
In formula (9-2),
H '
4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam enthalpy, the kJ/kg of unit,
H '
3represent LR leak vapour than time low pressure (LP) cylinder between steam enthalpy on cross over pipe, the kJ/kg of unit,
H '
srepresent LR leak vapour than time intermediate pressure cylinder through-flow constant entropy steam discharge steam enthalpy, the kJ/kg of unit,
H '
sadopt formula (10-2) to calculate:
H '
s=f
3(p '
3, s '
4) formula (10-2)
In formula (10-2),
S '
4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam entropy, the kJ/kg of unit;
Function f
3for the known pressure of international water and steam characteristic association and the computing formula of steam entropy calculation of steam enthalpy;
step 3, calculating are leaked vapour than LR and actual steam loss
f
l
:
(1) adopt following methods to ask and calculate LR:
A) appoint and get a larger LR
maxvalue, makes
, make x2=LR
max;
B) during due to LR=0
, make x1=0;
C) calculate and leak vapour ratio
time
value,
1. as
, calculate and finish,
;
for calculating departure;
2. as
, repeating step calculating c), wherein, the x value obtaining while making x2=computing last time, x1 is constant;
3. as
, repeating step calculating c), wherein, the x value obtaining while making x1=computing last time, x2 is constant;
(2) try to achieve Lou vapour than LR after, adopt formula (11) to calculate actual steam loss
f l:
formula (11)
In formula (11),
f lfor the actual steam loss of shaft seal between high intermediate pressure cylinder, the t/h of unit;
f d2for intermediate pressure cylinder inlet steam flow under design point, the t/h of unit, is known parameters, is checked in by producer's design data.
Preferably, rule of thumb, in a) step of step 3 of the present invention (1), LR
max=10%.
Preferably, according to universal experience, in the c) step of step 3 of the present invention (1),
be 0.0006.
It should be noted that, novel high intermediate pressure cylinder provided by the invention closes between cylinder steam turbine cylinder in gland packing leakage weight testing method, (1) of step 1 and (2) sequence of steps can be exchanged, no matter first the steam parameter under 50% load condition is measured, still first the steam parameter under 100% load condition is measured, can be realized the object of the invention; In like manner, (1) of step 2 and (2) sequence of steps can be exchanged, and no matter first the intermediate pressure cylinder flow efficiency under intermediate pressure cylinder flow efficiency or 100% load condition under 50% load condition are calculated, and can realize the object of the invention.
Another technical matters that patent of the present invention will solve be to provide a kind of simple in structure, data accurately novel high intermediate pressure cylinder close gland packing leakage between cylinder steam turbine cylinder and measure electricity testing device.
For solving the problems of the technologies described above, the technical scheme that patent of the present invention is taked is:
Novel high intermediate pressure cylinder of the present invention closes the novel high intermediate pressure cylinder that between cylinder steam turbine cylinder, gland packing leakage weight testing method adopts and closes a gland packing leakage measurement electricity testing device between cylinder steam turbine cylinder, it is characterized in that: comprise DATA REASONING terminal, data acquisition process equipment and display device;
Described DATA REASONING terminal comprises the first pressure transducer and the first temperature sensor that are arranged on after Control Stage of Steam Turbine, be arranged on the second pressure transducer and the second temperature sensor before intermediate pressure cylinder main inlet throttle-stop valve, be arranged on the 3rd pressure transducer and three-temperature sensor on cross over pipe between mesolow cylinder, be arranged on the 4th pressure transducer before the through-flow level of intermediate pressure cylinder;
The output terminal of described the first pressure transducer, the first temperature sensor, the second pressure transducer, the second temperature sensor, the 3rd pressure transducer, three-temperature sensor, the 4th pressure transducer connects respectively the respective input of data acquisition process equipment;
The output terminal of described data acquisition process equipment connects the respective input of described display device by data line, or is connected with display device by wireless network;
Wherein, described parameter h
1and h '
1recorded described parametric t by described the first pressure transducer
1and t '
1recorded described parameter h by described the first temperature sensor
2and h '
2recorded described parametric t by described the second pressure transducer
3and t '
3recorded described parameter h by described the second temperature sensor
3and h '
3recorded described parametric t by described the 3rd pressure transducer
3and t '
3recorded described parameter h by described three-temperature sensor
4and h '
4recorded by described the 4th pressure transducer.
Further, novel high intermediate pressure cylinder of the present invention closes gland packing leakage between cylinder steam turbine cylinder and measures in electricity testing device, and described data acquisition process equipment is the one in single-chip microcomputer, embedded computer system, industrial computer.
Preferably, novel high intermediate pressure cylinder of the present invention closes gland packing leakage between cylinder steam turbine cylinder and measures in electricity testing device, and described single-chip microcomputer model is OM-DAQPRO-5300.
Further, novel high intermediate pressure cylinder of the present invention closes gland packing leakage between cylinder steam turbine cylinder and measures in electricity testing device, and described display device is computing machine.
Further, novel high intermediate pressure cylinder of the present invention closes gland packing leakage between cylinder steam turbine cylinder and measures in electricity testing device, and the communication module of described wireless network is zigbee wireless communication module.
The principle of below novel high intermediate pressure cylinder of the present invention being closed to gland packing leakage weight testing method between cylinder steam turbine cylinder is described below:
In the time not considering the factor of shaft gland steam leakage between high intermediate pressure cylinder (being LR=0), intermediate pressure cylinder flow efficiency with load variation as shown in curve in Fig. 11.As seen from Figure 1, while not considering between cylinder shaft gland steam leakage, the intermediate pressure cylinder flow efficiency curve 1 of acquisition is irrational, and intermediate pressure cylinder flow efficiency should remain unchanged with the variation of load.
In the gas leakage of reality test, than under LR, the intermediate pressure cylinder flow efficiency value that two kinds of trystates (100% load condition and 50% load condition) obtain should equate,
, that is to say, leak vapour than under LR in required theory, intermediate pressure cylinder flow efficiency presents as shown in curve in Fig. 12 with the variation of load.
The present invention utilizes above principle, to the mensuration of the steam parameter to related locus under different working conditions, bring correlation parameter into formula, calculate the intermediate pressure cylinder flow efficiency value function taking LR as variable under two kinds of different load working conditions of height, then calculate in a certain error range
level off to the LR value of 1 o'clock, close shaft gland steam leakage between cylinder steam turbine cylinder thereby try to achieve high intermediate pressure cylinder.
The beneficial effect that adopts technique scheme to produce is:
(1) patent of the present invention adopts mode externally measured and that calculate, mainly by measuring and the through-flow relevant parameter such as pressure, temperature of intermediate pressure cylinder, after obtaining heating power data, pass through data acquisition process device processes, finally in display device, realize and calculate and show, can solve the measurement problem of shaft gland steam leakage between senior middle school of normal power plant in service pressing cylinder steam turbine high intermediate pressure cylinder by simple measurement, provide quantitative data accurately for power plant moves and overhauls; By shaft gland steam leakage between senior middle school's pressing cylinder steam turbine high intermediate pressure cylinder is monitored continuously, can monitor in real time the operation irregularity state of shaft seal between high intermediate pressure cylinder, meet the needs that economy of power plant is analyzed;
(2) the data ratio that patent data measuring terminals of the present invention gathers is easier to measure, and the data of collection in worksite can be passed through to wireless network remote transmission to computing machine, is convenient to implement and apply.
Brief description of the drawings
Fig. 1 intermediate pressure cylinder flow efficiency with load change curve:
Wherein, 1 is flow efficiency characteristic curve under theoretical LR, 2 characteristic curvees of flow efficiency while being LR=0;
The functional block diagram of Fig. 2 patent working example of the present invention;
Fig. 3 apparatus of the present invention structural representation,
Wherein, 1 first pressure transducer, 2 first temperature sensors, 3 second pressure transducers, 4 second temperature sensors, 5 the 3rd pressure transducers, 6 three-temperature sensors, 7 the 4th pressure transducers, 8 intermediate pressure cylinders, 9 high pressure cylinders, 10 high pressure main stop valves and variable valve, press stop valve and variable valve in 11,12, main steam steam delivery tube road, 13, reheated steam steam delivery tube road, 14 high pressure cylinder blow-off lines, 15 intermediate pressure cylinder blow-off lines.
Embodiment
Below in conjunction with the drawings and specific embodiments, patent of the present invention is described in further detail.
Embodiment
Referring to Fig. 1 and Fig. 2, according to determinator provided by the invention and method, shaft gland steam leakage between certain #10 of genco steam turbine cylinder is measured.
1, tested steam turbine: subcritical, the resuperheat, the twin-cylinder double flow steam extraction and condensing formula steam turbine that adopt east steam turbine company limited to manufacture, model C 300/246-16.7/0.35/537/537; According to producer's design data, intermediate pressure cylinder inlet steam flow under design point at full capacity
f d2for 742t/h.
2, the proving installation that installs novel high intermediate pressure cylinder of the present invention additional and close shaft gland steam leakage between cylinder steam turbine cylinder on tested steam turbine, this proving installation is made up of DATA REASONING terminal, data acquisition process equipment and display device;
Described DATA REASONING terminal comprises the first pressure transducer 1 and the first temperature sensor 2 that are arranged on after Control Stage of Steam Turbine, be arranged on the second pressure transducer 3 and the second temperature sensor 4 before intermediate pressure cylinder main inlet throttle-stop valve, be arranged on the 3rd pressure transducer 5 on cross over pipe and three-temperature sensor 6 between mesolow cylinder, be arranged on the 4th pressure transducer 7 before the through-flow level of intermediate pressure cylinder;
The output terminal of described the first pressure transducer 1, the first temperature sensor 2, the second pressure transducer 3, the second temperature sensor 4, the 3rd pressure transducer 5, three-temperature sensor 6, the 4th pressure transducer 7 connects respectively the respective input of data acquisition process equipment;
The output terminal of described data acquisition process equipment connects the respective input of described display device by data line, or passes through wireless communication with display device, and wireless network adopts zigbee wireless communication module to complete.
Described data acquisition process equipment is single-chip microcomputer, and model is OM-DAQPRO-5300; Described display device is computing machine; The communication module of described wireless network is zigbee wireless communication module.
In addition, as an alternative, described data acquisition process equipment also can be selected embedded computer system, industrial computer etc.
In the sensor, the pressure p that the first pressure transducer records
1represent, corresponding, the parameter that second and third and four pressure transducers record is p
2, p
3, p
4; The temperature that first, second, and third temperature sensor records is t
1, t
2and t
3.
3, adopt patent of the present invention to measure the step of calculating as follows:
(1) data input: the data that the first pressure transducer 1, the first temperature sensor 2, the second pressure transducer 3, the second temperature sensor 4, the 3rd pressure transducer 5, three-temperature sensor 6, the 4th pressure transducer 7 are gathered input in computing machine.
(2) utilize shaft gland steam leakage between following step test steam turbine cylinder:
step 1, the steam parameter of mensuration steam turbine under 100% and 50% load condition:
(1) unit is under the basic method of operation of 100% load, remove unit primary frequency modulation and AGC function, steam turbine import main steam temperature, intermediate pressure cylinder inlet steam temperature keep ratings, and keep power generator turbine admission valve position certain, steam parameter p after the Control Stage of Steam Turbine of collection unit under this steady state (SS) after unit operation is stable
1and t
1, steam parameter p before intermediate pressure cylinder main inlet throttle-stop valve
2and t
2, steam parameter p on cross over pipe between mesolow cylinder
3and t
3, intermediate pressure cylinder is through-flow level before a steam parameter p
4;
Wherein, symbol p represents pressure, units MPa; T represents temperature, unit DEG C; Index number represents different measuring position;
(2) unit is under the basic method of operation of 50% load, remove unit primary frequency modulation and AGC function, steam turbine import main steam temperature, intermediate pressure cylinder inlet steam temperature keep ratings, and keep power generator turbine admission valve position certain, steam parameter p ' after the Control Stage of Steam Turbine of collection unit under this steady state (SS) after unit operation is stable
1and t '
1, steam parameter p ' before intermediate pressure cylinder main inlet throttle-stop valve
2and t '
2, steam parameter p ' on cross over pipe between mesolow cylinder
3and t '
3, intermediate pressure cylinder is through-flow level before a steam parameter p '
4;
Wherein, symbol p represents pressure, units MPa; T represents temperature, unit DEG C; Index number represents different measuring position; Subscript " ' " for distinguishing the parameter of step 1 (1).
Carried out the parameter testing of 100% load and 50% load condition according to said method, the data that test obtains are in table 1:
Table 1 steam parameter test result
step 2, calculate under 100% and 50% load condition taking gland packing leakage the intermediate pressure cylinder flow efficiency function as variable than LR:
(1) calculate intermediate pressure cylinder flow efficiency function under 100% load condition:
A) data of step 1 collection are brought into formula (1-1) ~ (8-1) and calculate following state point thermal parameter:
Steam enthalpy h after governing stage
1=f
1(p
1, t
1) formula (1-1)
Steam entropy s after governing stage
1=f
2(p
1, t
1) formula (2-1)
Before intermediate pressure cylinder main inlet throttle-stop valve, steam enthalpy is h
2=f
1(p
2, t
2) formula (3-1)
Steam entropy s before intermediate pressure cylinder main inlet throttle-stop valve
2=f
2(p
2, t
2) formula (4-1)
Between mesolow cylinder, on cross over pipe, steam enthalpy is h
3=f
1(p
3, t
3) formula (5-1)
Steam entropy s on cross over pipe between mesolow cylinder
3=f
2(p
3, t
3) formula (6-1)
Steam enthalpy h before level that intermediate pressure cylinder is through-flow
4=(h
2+ LR × h
1the formula of)/(1+LR) (7-1)
Steam entropy s before level that intermediate pressure cylinder is through-flow
4=f
4(p
4, h
4) formula (8-1)
In formula (1-1) ~ (8-1), function f
1for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam enthalpy, function f
2for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam entropy; Function f
4for the known pressure of international water and steam characteristic association and the computing formula of enthalpy calculation of steam entropy;
Wherein, h is steam enthalpy, the kJ/kg of unit; S is steam entropy, the kJ/kg.K of unit; LR be shaft gland steam leakage with design point under the ratio of intermediate pressure cylinder inlet steam flow;
B) calculate the intermediate pressure cylinder flow efficiency taking LR as variable according to formula (9-1)
η lfunction:
formula (9-1)
In formula (9-1),
H
4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam enthalpy, the kJ/kg of unit,
H
3represent LR leak vapour than time low pressure (LP) cylinder between steam enthalpy on cross over pipe, the kJ/kg of unit,
H
srepresent LR leak vapour than time intermediate pressure cylinder through-flow constant entropy steam discharge steam enthalpy, the kJ/kg of unit,
H
sadopt formula (10-1) to calculate:
H '
s=f
3(p '
3, s '
4) formula (10-1)
In formula (10-1),
s 4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam entropy, the kJ/kg of unit;
Function f
3for the known pressure of international water and steam characteristic association and the computing formula of steam entropy calculation of steam enthalpy;
(2) calculate intermediate pressure cylinder flow efficiency function under 50% load condition:
A) data of step 1 collection are brought into formula (1-2) ~ (8-2) and calculate following state point thermal parameter:
Steam enthalpy h ' after governing stage
1=f
1(p '
1, t '
1) formula (1-2)
Steam entropy s ' after governing stage
1=f
2(p '
1, t '
1) formula (2-2)
Before intermediate pressure cylinder main inlet throttle-stop valve, steam enthalpy is h '
2=f
1(p '
2, t '
2) formula (3-2)
Steam entropy s ' before intermediate pressure cylinder main inlet throttle-stop valve
2=f
2(p '
2, t '
2) formula (4-2)
Between mesolow cylinder, on cross over pipe, steam enthalpy is h '
3=f
1(p '
3, t '
3) formula (5-2)
Steam entropy s ' on cross over pipe between mesolow cylinder
3=f
2(p '
3, t '
3) formula (6-2)
Steam enthalpy h ' before level that intermediate pressure cylinder is through-flow
4=(h '
2+ LR × h '
1the formula of)/(1+LR) (7-2)
Steam entropy s ' before level that intermediate pressure cylinder is through-flow
4=f
4(p '
4, h '
4) formula (8-2)
In formula (1-2) ~ (8-2), function f
1for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam enthalpy, function f
2for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam entropy; Function f
4for the known pressure of international water and steam characteristic association and the computing formula of enthalpy calculation of steam entropy;
Wherein, h ' is steam enthalpy, the kJ/kg of unit; S ' is steam entropy, the kJ/kg.K of unit; LR be shaft gland steam leakage with design point under the ratio of intermediate pressure cylinder inlet steam flow;
B) calculate the intermediate pressure cylinder flow efficiency taking LR as variable according to formula (9-2)
η ' lfunction:
formula (9-2)
In formula (9-2),
H '
4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam enthalpy, the kJ/kg of unit,
H '
3represent LR leak vapour than time low pressure (LP) cylinder between steam enthalpy on cross over pipe, the kJ/kg of unit,
H '
srepresent LR leak vapour than time intermediate pressure cylinder through-flow constant entropy steam discharge steam enthalpy, the kJ/kg of unit,
H '
sadopt formula (10-2) to calculate:
H '
s=f
3(p '
3, s '
4) formula (10-2)
In formula (10-2),
S '
4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam entropy, the kJ/kg of unit;
Function f
3for the known pressure of international water and steam characteristic association and the computing formula of steam entropy calculation of steam enthalpy;
step 3, calculating are leaked vapour than LR and actual steam loss
f
l
:
(1) adopt following methods to ask and calculate LR:
A) make x2=LR
max=10%, make
;
B) during due to LR=0
, make x1=0;
C) calculate and leak vapour ratio
time
value,
1. as
, calculate and finish,
;
be 0.0006;
2. as
, repeating step calculating c), wherein, the x value obtaining while making x2=computing last time, x1 is constant;
3. as
, repeating step calculating c), wherein, the x value obtaining while making x1=computing last time, x2 is constant;
(2) try to achieve Lou vapour than LR after, adopt formula (11) to calculate actual steam loss
f l:
formula (11)
In formula (11),
f lfor the actual steam loss of shaft seal between high intermediate pressure cylinder, the t/h of unit;
f d2for intermediate pressure cylinder inlet steam flow under design point, the t/h of unit, is known parameters, is checked in by producer's design data.
Above-mentioned result of calculation is in table 2:
Table 2 leaks gas than the result of calculation of LR
The above results is known, and in the time leaking vapour than LR=5.3%, the flow efficiency calculated value deviation of two kinds of operating modes is 0.005%, meets the requirement that departure is less than 0.0006.Therefore, the final leakage vapour obtaining is 5.3% than LR.
According to formula (11), can calculate the actual steam loss of shaft seal between high intermediate pressure cylinder and be:
F L?=?742×5.3%?=?39.33t/h。
The above embodiment is only the preferred embodiments of the present invention, and is not the exhaustive of the feasible enforcement of the present invention.For persons skilled in the art, any apparent change of under the prerequisite that does not deviate from the principle of the invention and spirit, it having been done, within all should being contemplated as falling with claim protection domain of the present invention.
Claims (8)
1. novel high intermediate pressure cylinder closes a gland packing leakage weight testing method between cylinder steam turbine cylinder, it is characterized in that comprising following steps:
step 1, the steam parameter of mensuration steam turbine under 100% and 50% load condition:
(1) unit is under the basic method of operation of 100% load, remove unit primary frequency modulation and AGC function, steam turbine import main steam temperature, intermediate pressure cylinder inlet steam temperature keep ratings, and keep power generator turbine admission valve position certain, steam parameter p after the Control Stage of Steam Turbine of collection unit under this steady state (SS) after unit operation is stable
1and t
1, steam parameter p before intermediate pressure cylinder main inlet throttle-stop valve
2and t
2, steam parameter p on cross over pipe between mesolow cylinder
3and t
3, intermediate pressure cylinder is through-flow level before a steam parameter p
4;
Wherein, symbol p represents pressure, units MPa; T represents temperature, unit DEG C; Index number represents different measuring position;
(2) unit is under the basic method of operation of 50% load, remove unit primary frequency modulation and AGC function, steam turbine import main steam temperature, intermediate pressure cylinder inlet steam temperature keep ratings, and keep power generator turbine admission valve position certain, steam parameter p ' after the Control Stage of Steam Turbine of collection unit under this steady state (SS) after unit operation is stable
1and t '
1, steam parameter p ' before intermediate pressure cylinder main inlet throttle-stop valve
2and t '
2, steam parameter p ' on cross over pipe between mesolow cylinder
3and t '
3, intermediate pressure cylinder is through-flow level before a steam parameter p '
4;
Wherein, symbol p represents pressure, units MPa; T represents temperature, unit DEG C; Index number represents different measuring position; Subscript " ' " for distinguishing the parameter of step 1 (1);
step 2, calculate under 100% and 50% load condition taking gland packing leakage the intermediate pressure cylinder flow efficiency function as variable than LR:
(1) calculate intermediate pressure cylinder flow efficiency function under 100% load condition:
A) data of step 1 collection are brought into formula (1-1) ~ (8-1) and calculate following state point thermal parameter:
Steam enthalpy h after governing stage
1=f
1(p
1, t
1) formula (1-1)
Steam entropy s after governing stage
1=f
2(p
1, t
1) formula (2-1)
Before intermediate pressure cylinder main inlet throttle-stop valve, steam enthalpy is h
2=f
1(p
2, t
2) formula (3-1)
Steam entropy s before intermediate pressure cylinder main inlet throttle-stop valve
2=f
2(p
2, t
2) formula (4-1)
Between mesolow cylinder, on cross over pipe, steam enthalpy is h
3=f
1(p
3, t
3) formula (5-1)
Steam entropy s on cross over pipe between mesolow cylinder
3=f
2(p
3, t
3) formula (6-1)
Steam enthalpy h before level that intermediate pressure cylinder is through-flow
4=(h
2+ LR × h
1the formula of)/(1+LR) (7-1)
Steam entropy s before level that intermediate pressure cylinder is through-flow
4=f
4(p
4, h
4) formula (8-1)
In formula (1-1) ~ (8-1), function f
1for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam enthalpy, function f
2for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam entropy; Function f
4for the known pressure of international water and steam characteristic association and the computing formula of enthalpy calculation of steam entropy;
Wherein, h is steam enthalpy, the kJ/kg of unit; S is steam entropy, the kJ/kg.K of unit; LR be shaft gland steam leakage with design point under the ratio of intermediate pressure cylinder inlet steam flow;
B) calculate the intermediate pressure cylinder flow efficiency taking LR as variable according to formula (9-1)
η lfunction:
formula (9-1)
In formula (9-1),
H
4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam enthalpy, the kJ/kg of unit,
H
3represent LR leak vapour than time low pressure (LP) cylinder between steam enthalpy on cross over pipe, the kJ/kg of unit,
H
srepresent LR leak vapour than time intermediate pressure cylinder through-flow constant entropy steam discharge steam enthalpy, the kJ/kg of unit,
H
sadopt formula (10-1) to calculate:
H '
s=f
3(p '
3, s '
4) formula (10-1)
In formula (10-1),
s 4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam entropy, the kJ/kg of unit;
Function f
3for the known pressure of international water and steam characteristic association and the computing formula of steam entropy calculation of steam enthalpy;
(2) calculate intermediate pressure cylinder flow efficiency function under 50% load condition:
A) data of step 1 collection are brought into formula (1-2) ~ (8-2) and calculate following state point thermal parameter:
Steam enthalpy h ' after governing stage
1=f
1(p '
1, t '
1) formula (1-2)
Steam entropy s ' after governing stage
1=f
2(p '
1, t '
1) formula (2-2)
Before intermediate pressure cylinder main inlet throttle-stop valve, steam enthalpy is h '
2=f
1(p '
2, t '
2) formula (3-2)
Steam entropy s ' before intermediate pressure cylinder main inlet throttle-stop valve
2=f
2(p '
2, t '
2) formula (4-2)
Between mesolow cylinder, on cross over pipe, steam enthalpy is h '
3=f
1(p '
3, t '
3) formula (5-2)
Steam entropy s ' on cross over pipe between mesolow cylinder
3=f
2(p '
3, t '
3) formula (6-2)
Steam enthalpy h ' before level that intermediate pressure cylinder is through-flow
4=(h '
2+ LR × h '
1the formula of)/(1+LR) (7-2)
Steam entropy s ' before level that intermediate pressure cylinder is through-flow
4=f
4(p '
4, h '
4) formula (8-2)
In formula (1-2) ~ (8-2), function f
1for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam enthalpy, function f
2for the known pressure of international water and steam characteristic association and the computing formula of temperature computation steam entropy; Function f
4for the known pressure of international water and steam characteristic association and the computing formula of enthalpy calculation of steam entropy;
Wherein, h ' is steam enthalpy, the kJ/kg of unit; S ' is steam entropy, the kJ/kg.K of unit; LR be shaft gland steam leakage with design point under the ratio of intermediate pressure cylinder inlet steam flow;
B) calculate the intermediate pressure cylinder flow efficiency taking LR as variable according to formula (9-2)
η ' lfunction:
formula (9-2)
In formula (9-2),
H '
4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam enthalpy, the kJ/kg of unit,
H '
3represent LR leak vapour than time low pressure (LP) cylinder between steam enthalpy on cross over pipe, the kJ/kg of unit,
H '
srepresent LR leak vapour than time intermediate pressure cylinder through-flow constant entropy steam discharge steam enthalpy, the kJ/kg of unit,
H '
sadopt formula (10-2) to calculate:
H '
s=f
3(p '
3, s '
4) formula (10-2)
In formula (10-2),
S '
4represent LR leak vapour than time intermediate pressure cylinder through-flow level before steam entropy, the kJ/kg of unit;
Function f
3for the known pressure of international water and steam characteristic association and the computing formula of steam entropy calculation of steam enthalpy;
step 3, calculating are leaked vapour than LR and actual steam loss
f
l
:
(1) adopt following methods to ask and calculate LR:
A) appoint and get a larger LR
maxvalue, makes
, make x2=LR
max;
B) during due to LR=0
, make x1=0;
C) calculate and leak vapour ratio
time
value,
1. as
, calculate and finish,
;
for calculating departure;
2. as
, repeating step calculating c), wherein, the x value obtaining while making x2=computing last time, x1 is constant;
3. as
, repeating step calculating c), wherein, the x value obtaining while making x1=computing last time, x2 is constant;
(2) try to achieve Lou vapour than LR after, adopt formula (11) to calculate actual steam loss
f l:
formula (11)
In formula (11),
f lfor the actual steam loss of shaft seal between high intermediate pressure cylinder, the t/h of unit;
f d2for intermediate pressure cylinder inlet steam flow under design point, the t/h of unit, is known parameters, is checked in by producer's design data.
2. novel high intermediate pressure cylinder as claimed in claim 1 closes gland packing leakage weight testing method between cylinder steam turbine cylinder, it is characterized in that in a) step of step 3 (1) LR
max=10%.
3. novel high intermediate pressure cylinder as claimed in claim 1 closes gland packing leakage weight testing method between cylinder steam turbine cylinder, it is characterized in that in the c) step of step 3 (1),
be 0.0006.
4. the novel high intermediate pressure cylinder as described in any one in claim 1 ~ 3 closes the novel high intermediate pressure cylinder that between cylinder steam turbine cylinder, gland packing leakage weight testing method is adopted and closes gland packing leakage measurement electricity testing device between cylinder steam turbine cylinder, it is characterized in that: comprise DATA REASONING terminal, data acquisition process equipment and display device;
Described DATA REASONING terminal comprises the first pressure transducer and the first temperature sensor that are arranged on after Control Stage of Steam Turbine, be arranged on the second pressure transducer and the second temperature sensor before intermediate pressure cylinder main inlet throttle-stop valve, be arranged on the 3rd pressure transducer and three-temperature sensor on cross over pipe between mesolow cylinder, be arranged on the 4th pressure transducer before the through-flow level of intermediate pressure cylinder;
The output terminal of described the first pressure transducer, the first temperature sensor, the second pressure transducer, the second temperature sensor, the 3rd pressure transducer, three-temperature sensor, the 4th pressure transducer connects respectively the respective input of data acquisition process equipment;
The output terminal of described data acquisition process equipment connects the respective input of described display device by data line, or is connected with display device by wireless network;
Wherein, described parameter h
1and h '
1recorded described parametric t by described the first pressure transducer
1and t '
1recorded described parameter h by described the first temperature sensor
2and h '
2recorded described parametric t by described the second pressure transducer
3and t '
3recorded described parameter h by described the second temperature sensor
3and h '
3recorded described parametric t by described the 3rd pressure transducer
3and t '
3recorded described parameter h by described three-temperature sensor
4and h '
4recorded by described the 4th pressure transducer.
5. novel high intermediate pressure cylinder as claimed in claim 4 closes gland packing leakage between cylinder steam turbine cylinder and measures electricity testing device, it is characterized in that described data acquisition process equipment is the one in single-chip microcomputer, embedded computer system, industrial computer.
6. novel high intermediate pressure cylinder as claimed in claim 5 closes gland packing leakage between cylinder steam turbine cylinder and measures electricity testing device, it is characterized in that described single-chip data acquisition treatment facility model is OM-DAQPRO-5300.
7. novel high intermediate pressure cylinder as claimed in claim 4 closes gland packing leakage between cylinder steam turbine cylinder and measures electricity testing device, it is characterized in that described display device is computing machine.
8. novel high intermediate pressure cylinder as claimed in claim 4 closes gland packing leakage between cylinder steam turbine cylinder and measures electricity testing device, and the communication module that it is characterized in that described wireless network is zigbee wireless communication module.
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| CN117029910A (en) * | 2023-07-26 | 2023-11-10 | 秦皇岛秦热发电有限责任公司 | Enthalpy exergy monitoring device for thermodynamic system |
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| CN108090663B (en) * | 2017-12-11 | 2020-06-26 | 囯网河北省电力有限公司电力科学研究院 | Evaluation method and system for deep peak shaving minimum output of heat supply unit |
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