CN103196523A - Steam turbine performance test standard flow calibration method based on auxiliary flow measurement - Google Patents

Steam turbine performance test standard flow calibration method based on auxiliary flow measurement Download PDF

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CN103196523A
CN103196523A CN2013101106494A CN201310110649A CN103196523A CN 103196523 A CN103196523 A CN 103196523A CN 2013101106494 A CN2013101106494 A CN 2013101106494A CN 201310110649 A CN201310110649 A CN 201310110649A CN 103196523 A CN103196523 A CN 103196523A
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pressure heater
flow rate
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杨海生
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State Grid Corp of China SGCC
Electric Power Research Institute of State Grid Hebei Electric Power Co Ltd
Hebei Electric Power Construction Adjustment Test Institute
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State Grid Corp of China SGCC
Electric Power Research Institute of State Grid Hebei Electric Power Co Ltd
Hebei Electric Power Construction Adjustment Test Institute
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Abstract

本发明提供了一种基于辅助流量测量的汽轮机性能试验基准流量的校验方法，其可以根据加热器至除氧器管道上实测的疏水流量数据及其它相关热力参数，计算出对应的给水流量及凝结水流量，最终可以对汽轮机性能试验的基准流量提供校验的手段和方法。可以为准确确定汽轮机性能试验的基准流量提供依据，为电厂运行经济性指标的计算提供准确数据，并为电厂的节能降耗提供依据。对电厂汽轮机性能试验的基准流量进行连续或定期的校验，保证其测量的准确性。

Figure 201310110649

The invention provides a verification method of the benchmark flow rate of the steam turbine performance test based on auxiliary flow measurement, which can calculate the corresponding feedwater flow rate and Condensed water flow can finally provide means and methods for verifying the benchmark flow of steam turbine performance test. It can provide the basis for accurately determining the benchmark flow rate of the steam turbine performance test, provide accurate data for the calculation of the economic index of the power plant operation, and provide the basis for the power plant's energy saving and consumption reduction. Carry out continuous or periodic calibration on the reference flow rate of the steam turbine performance test in the power plant to ensure the accuracy of its measurement.

Figure 201310110649

Description

Test the method for calibration of standard flow based on the steam turbine performance of auxiliary flow measurement
Technical field
The present invention relates to a kind of steam turbine performance of measuring based on auxiliary flow and test the method for calibration of standard flow.
Background technology
In the steam turbine performance test, standard flow adopts feedwater flow or condensing water flow usually, and power plant's feedwater flow measurement mechanism all is in High Temperature High Pressure and measures state, and its accuracy is difficult to guarantee behind the long-play.Though condensing water flow measurement mechanism measuring condition is better relatively, calculated by condensing water flow in the process of feedwater flow, also be subjected to the influence of other measurement parameter.If the accuracy of standard flow can be carried out verification by a kind of extra method, then can significantly improve the accuracy of standard flow in the performance test.
This important parameter of standard flow generally lacks the verification means in the steam turbine performance test at present, guarantees its accuracy.Therefore definite a kind of steam turbine performance of measuring based on auxiliary flow is tested the method for calibration of standard flow, and is necessary.
Summary of the invention
The object of the present invention is to provide a kind of steam turbine performance of measuring based on auxiliary flow to test the method for calibration of standard flow, hydrophobic data on flows and other associated hot force parameter that it can be surveyed to the oxygen-eliminating device pipeline according to well heater, calculate corresponding feedwater flow and condensing water flow, means and the method for verification finally can be provided the standard flow of steam turbine performance test.
The present invention solves its technical matters and adopts following technical scheme:
A kind of steam turbine performance of measuring based on auxiliary flow is tested the method for calibration of standard flow, and it comprises that step is as follows:
Step 1: to the hydrophobic pipeline of oxygen-eliminating device flow measuring sensor is installed at high-pressure heater, the installation of sensor should guarantee that its upstream and downstream have enough straight lengths; Utilize flow measuring sensor, the actual measurement high-pressure heater enters the hydrophobic flow W of oxygen-eliminating device 5d
Step 2: according to energy and the mass balance equation of oxygen-eliminating device and each high-pressure heater, adopt alternative manner to calculate corresponding to the hydrophobic flow W of actual measurement 5dFeedwater flow W fAnd condensing water flow W c
Step 3: the feedwater flow W that relatively calculates fAnd measured performance test benchmark feedwater flow W FtIf there is bigger deviation, to measured performance test benchmark feedwater flow W FtRevise;
Step 4: the condensing water flow W that relatively calculates cAnd measured performance test benchmark condensing water flow W CtIf there is bigger deviation, to measured performance test benchmark condensing water flow W CtRevise.
As a further improvement on the present invention, described step 2 is calculated by following formula:
Figure 89326DEST_PATH_IMAGE001
Wherein:
W f---feedwater flow, the t/h of unit;
W 8---No. eight high-pressure heater admission flows, the t/h of unit;
W 7---No. seven high-pressure heater admission flows, the t/h of unit;
W 6---No. six high-pressure heater admission flows, the t/h of unit;
W 5---oxygen-eliminating device admission flow, the t/h of unit;
W 5d---high-pressure heater is to the hydrophobic flow of oxygen-eliminating device, the t/h of unit;
W Dout---oxygen-eliminating device water flow, the t/h of unit;
W Level---the equivalent flow that deaerator level changes, the t/h of unit; Water level when rising be on the occasion of, be negative value during water level decline;
W Ss---superheater desuperheating water flow, the t/h of unit;
W Rs---reheater desuperheating water flow, the t/h of unit;
W Si---Sealing Water for Feedwater Pump flow of inlet water, the t/h of unit;
W So---Sealing Water for Feedwater Pump water flow, the t/h of unit;
W c---oxygen-eliminating device incoming condensing water flow, the t/h of unit;
h Fo8---No. eight high-pressure heater outlet Enthalpy of Feed Water, the kJ/kg of unit;
h Fo7---No. seven high-pressure heater outlet Enthalpy of Feed Water, the kJ/kg of unit;
h Fo6---No. six high-pressure heater outlet Enthalpy of Feed Water, the kJ/kg of unit;
h Fo5---oxygen-eliminating device outlet Enthalpy of Feed Water, the kJ/kg of unit;
h Fi8---No. eight high-pressure heater import Enthalpy of Feed Water, the kJ/kg of unit;
h Fi7---No. seven high-pressure heater import Enthalpy of Feed Water, the kJ/kg of unit;
h Fi6---No. six high-pressure heater import Enthalpy of Feed Water, the kJ/kg of unit;
h Fi5---oxygen-eliminating device incoming condensing water enthalpy, the kJ/kg of unit;
h 8---No. eight high-pressure heater inlet steam enthalpies, the kJ/kg of unit;
h 7---No. seven high-pressure heater inlet steam enthalpies, the kJ/kg of unit;
h 6---No. six high-pressure heater inlet steam enthalpies, the kJ/kg of unit;
h 5---oxygen-eliminating device inlet steam enthalpy, the kJ/kg of unit;
h 8d---No. eight hydrophobic enthalpies of high-pressure heater, the kJ/kg of unit;
h 7d---No. seven hydrophobic enthalpies of high-pressure heater, the kJ/kg of unit;
h 6d---No. six hydrophobic enthalpies of high-pressure heater, the kJ/kg of unit.
The good effect of invention is as follows: the hydrophobic data on flows and other associated hot force parameter that adopt the inventive method to survey to the oxygen-eliminating device pipeline according to well heater, finally calculate corresponding feedwater flow and condensing water flow, means and the method for verification finally can be provided the standard flow of steam turbine performance test.
Solve the check problem based on standard flow in the steam turbine performance test, can provide foundation for the standard flow of accurately determining the steam turbine performance test, for the calculating of power plant's performance driving economy index provides accurate data, and be the energy-saving and cost-reducing foundation that provides of power plant.Standard flow to the power plant steam turbine performance test carries out continuous or periodic verification, guarantees the accuracy of its measurement.
Description of drawings
Accompanying drawing 1 is the hydrophobic flow sensor arrangenent diagram of the present invention.
Accompanying drawing 2 is for the present invention relates to the synoptic diagram of oxygen-eliminating device and high-pressure heater system.
In the accompanying drawing: 1, high-pressure heater 2, oxygen-eliminating device 3, hydrophobic flow sensor 4, hydrophobic operation valve 5, No. six high-pressure heaters 6, No. seven high-pressure heaters 7, No. eight high-pressure heaters.
Embodiment
At first on-the-spot high-pressure heater 1 is arranged to the hydrophobic pipeline of oxygen-eliminating device 2 and carried out suitable change, increase hydrophobic flow sensor 3.Hydrophobic flow sensor 3 is installed in before the hydrophobic operation valve 4, and the flow development length Lu before the hydrophobic flow sensor 3 are no less than 25 times of pipe diameter length, and hydrophobic flow sensor 3 backs are not less than 10 times of calibers to hydrophobic operation valves distance, and namely L is no less than 35 times of calibers.Can be referring to accompanying drawing 1.
Computing method and the step of standard flow are as follows:
Typical oxygen-eliminating device and high-pressure heater system as shown in Figure 2.There are following quality and energy-balance equation.
To No. eight high-pressure heaters 7, exist:
Figure 424492DEST_PATH_IMAGE002
(1)
Wherein:
W f---feedwater flow, the t/h of unit;
W 8---No. eight high-pressure heater admission flows, the t/h of unit;
h Fo8---No. eight high-pressure heater outlet Enthalpy of Feed Water, the kJ/kg of unit;
h Fi8---No. eight high-pressure heater import Enthalpy of Feed Water, the kJ/kg of unit;
h 8---No. eight high-pressure heater inlet steam enthalpies, the kJ/kg of unit;
h 8d---No. eight hydrophobic enthalpies of high-pressure heater, the kJ/kg of unit.
To No. seven high-pressure heaters 6, exist:
(2)
Wherein:
W 7---No. seven high-pressure heater admission flows, the t/h of unit;
h Fo7---No. seven high-pressure heater outlet Enthalpy of Feed Water, the kJ/kg of unit;
h Fi7---No. seven high-pressure heater import Enthalpy of Feed Water, the kJ/kg of unit;
h 7---No. seven high-pressure heater inlet steam enthalpies, the kJ/kg of unit;
h 7d---No. seven hydrophobic enthalpies of high-pressure heater, the kJ/kg of unit.
To No. six high-pressure heaters 5, exist:
Figure 356862DEST_PATH_IMAGE004
(3)
Wherein:
W 6---No. six high-pressure heater admission flows, the t/h of unit;
h Fo6---No. six high-pressure heater outlet Enthalpy of Feed Water, the kJ/kg of unit;
h Fi6---No. six high-pressure heater import Enthalpy of Feed Water, the kJ/kg of unit;
h 6---No. six high-pressure heater inlet steam enthalpies, the kJ/kg of unit;
h 6d---No. six hydrophobic enthalpies of high-pressure heater, the kJ/kg of unit.
Figure 792523DEST_PATH_IMAGE005
(4)
Wherein:
W 5d---high-pressure heater is to the hydrophobic flow of oxygen-eliminating device, the t/h of unit.
To oxygen-eliminating device 2, exist:
Figure 564170DEST_PATH_IMAGE006
(5)
Figure 701759DEST_PATH_IMAGE007
(6)
Wherein:
W 5---oxygen-eliminating device admission flow, the t/h of unit;
W Dout---oxygen-eliminating device water flow, the t/h of unit;
W Dlevel---the equivalent flow that deaerator level changes, the t/h of unit; Water level when rising be on the occasion of, be negative value during water level decline;
W Ss---superheater desuperheating water flow, the t/h of unit;
W Rs---reheater desuperheating water flow, the t/h of unit;
W Si---Sealing Water for Feedwater Pump flow of inlet water, the t/h of unit;
W So---Sealing Water for Feedwater Pump water flow, the t/h of unit;
h Fo5---oxygen-eliminating device outlet Enthalpy of Feed Water, the kJ/kg of unit;
h Fi5---oxygen-eliminating device incoming condensing water enthalpy, the kJ/kg of unit;
h 5---oxygen-eliminating device inlet steam enthalpy, the kJ/kg of unit.
To condensing water flow, mass balance exists:
(7)
Wherein:
W c---oxygen-eliminating device incoming condensing water flow, the t/h of unit.
Calculation procedure is as follows:
Step 1: suppose a feedwater flow, according to other known thermal parameter, find the solution W by formula (1) respectively 8Find the solution W by formula (2) 7Find the solution W by formula (3) 6Find the solution W by formula (4) 5d
Step 2: the value W that relatively calculates 5dHydrophobic flow value W with actual measurement 5dtIn allowed band, then Jia Ding feedwater flow is the calculated value of feedwater flow as both errors; If error is bigger, then suppose feedwater flow again, go on foot from (1) and recomputate;
Step 3: according to the feedwater flow calculating value of determining, according to other known thermal parameter, find the solution W by formula (5) and formula (6) 5Find the solution condensing water flow W by formula (7) c
The verification of standard flow is carried out as follows:
(1) the feedwater flow W that relatively calculates fAnd measured performance test benchmark feedwater flow W FtIf there is bigger deviation, to measured performance test benchmark feedwater flow W FtRevise;
(2) the condensing water flow W that relatively calculates cAnd measured performance test benchmark condensing water flow W CtIf there is bigger deviation, to measured performance test benchmark condensing water flow W CtRevise.
Embodiment 1:
Certain 600MW unit, measured data is as shown in the table, and the symbol implication is the same in the table:
Symbol Unit Numerical value
W 5d t/h 305.521
W level t/h -0.366
W ss t/h 78.303
W rs t/h 6.338
W si t/h 4.500
W so t/h 4.500
h fo8 kJ/kg 1216.304
h fo7 kJ/kg 1092.593
h fo6 kJ/kg 942.794
h fo5 kJ/kg 791.557
h fi8 kJ/kg 1092.593
h fi7 kJ/kg 942.794
h fi6 kJ/kg 831.159
h fi5 kJ/kg 604.018
h 8 kJ/kg 2999.451
h 7 kJ/kg 2930.802
h 6 kJ/kg 3406.405
h 5 kJ/kg 3232.877
h 8d kJ/kg 1112.492
h 7d kJ/kg 954.210
h 6d kJ/kg 861.701
Suppose different feedwater flow values, calculate according to abovementioned steps, until calculating W 5d, compare with measured value in the above-mentioned table; Repeat to revise the feedwater flow value, until the W that calculates 5dCoincide with the measured value in the above-mentioned table.Each flow rate calculation value that obtain this moment is as follows:
Symbol Unit Final calculated value
W f t/h 1745.643
W 8 t/h 114.446
W 7 t/h 123.131
W 6 t/h 67.944
W 5 t/h 100.596
W dout t/h 1830.284
W c t/h 1424.533
The performance test benchmark feedwater flow W of field measurement FtValue is 1762.4t/h, therefore the performance test benchmark feedwater flow W of actual measurement FtCorrection be: 1745.64-1762.4=-16.76t/h;
The performance test benchmark condensing water flow W of field measurement CtValue is 1432.36t/h, therefore the performance test benchmark feedwater flow W of actual measurement FtCorrection be: 1424.533-1432.36=-7.83t/h.
Above embodiment is only unrestricted in order to technical scheme of the present invention to be described, although with reference to preferred embodiment the present invention is had been described in detail, those of ordinary skill in the art is to be understood that, can make amendment or be equal to replacement technical scheme of the present invention, and not breaking away from the spirit and scope of technical solution of the present invention, it all should be encompassed in the middle of the claim scope of the present invention.

Claims (2)

1.一种基于辅助流量测量的汽轮机性能试验基准流量的校验方法，其特征在于其包括如下步骤： 1. A method for verifying the performance test reference flow of a steam turbine based on auxiliary flow measurement, characterized in that it may further comprise the steps: 步骤一：在高压加热器至除氧器的疏水管路上安装流量测量传感器，传感器的安装应保证其上游及下游具有足够的直管段；利用流量测量传感器，实测高压加热器进入除氧器的疏水流量W5d； Step 1: Install a flow measurement sensor on the drain pipeline from the high-pressure heater to the deaerator. The installation of the sensor should ensure that there are enough straight pipe sections upstream and downstream; use the flow measurement sensor to measure the drain flow of the high-pressure heater into the deaerator. flow W 5d ; 步骤二：根据除氧器及各高压加热器的能量及质量平衡方程，采用迭代方法计算出对应于实测疏水流量W5d的给水流量Wf及凝结水流量Wc； Step 2: According to the energy and mass balance equations of the deaerator and each high-pressure heater, the iterative method is used to calculate the feedwater flow W f and the condensate flow W c corresponding to the measured hydrophobic flow W 5d ; 步骤三：比较计算出的给水流量Wf及其实测性能试验基准给水流量Wft；如果存在较大的偏差，对实测性能试验基准给水流量Wft进行修正； Step 3: Compare the calculated feedwater flow W f with its measured performance test benchmark feedwater flow W ft ; if there is a large deviation, correct the measured performance test benchmark feedwater flow W ft ; 步骤四：比较计算出的凝结水流量Wc及其实测性能试验基准凝结水流量Wct；如果存在较大的偏差，对实测性能试验基准凝结水流量Wct进行修正。 Step 4: Compare the calculated condensate flow rate W c with its measured performance test reference condensate flow rate W ct ; if there is a large deviation, correct the measured performance test reference condensate flow rate W ct . 2.根据权利要求1所述的一种基于辅助流量测量的汽轮机性能试验基准流量的校验方法，其特征在于，所述步骤二通过下列公式计算： 2. the verification method of a kind of steam turbine performance test reference flow based on auxiliary flow measurement according to claim 1, is characterized in that, described step 2 is calculated by following formula:
Figure 490246DEST_PATH_IMAGE001
Figure 490246DEST_PATH_IMAGE001
 其中： in: Wf ——给水流量，单位t/h； W f ——feed water flow rate, unit t/h; W8——八号高压加热器进汽流量，单位t/h； W 8 ——inlet steam flow rate of No. 8 high-pressure heater, unit t/h; W7——七号高压加热器进汽流量，单位t/h； W 7 ——inlet steam flow rate of No. 7 high pressure heater, unit t/h; W6——六号高压加热器进汽流量，单位t/h； W 6 ——inlet steam flow rate of No. 6 high pressure heater, unit t/h; W5——除氧器进汽流量，单位t/h； W 5 —— steam flow rate of deaerator, unit t/h; W5d——高压加热器至除氧器的疏水流量，单位t/h； W 5d ——The hydrophobic flow rate from the high pressure heater to the deaerator, unit t/h; Wdout ——除氧器出水流量，单位t/h； W dout ——water flow rate of deaerator, unit t/h; Wdlevel ——除氧器水位变化的当量流量，单位t/h；水位上升时为正值，水位下降时为负值； W dlevel ——the equivalent flow rate of the water level change of the deaerator, unit t/h; when the water level rises, it is a positive value, and when the water level drops, it is a negative value; Wss——过热器减温水流量，单位t/h； W ss ——superheater desuperheating water flow rate, unit t/h; Wrs——再热器减温水流量，单位t/h； W rs ——reheater desuperheating water flow rate, unit t/h; Wsi ——给水泵密封水进水流量，单位t/h； W si ——feedwater pump sealing water inlet flow rate, unit t/h; Wso ——给水泵密封水出水流量，单位t/h； W so ——the outlet flow rate of the sealing water of the feedwater pump, unit t/h; Wc——除氧器进口凝结水流量，单位t/h； W c ——Condensate flow at the inlet of the deaerator, unit t/h; hfo8——八号高压加热器出口给水焓值，单位kJ/kg； h fo8 ——Enthalpy value of feedwater at the outlet of No. 8 high-pressure heater, unit kJ/kg; hfo7——七号高压加热器出口给水焓值，单位kJ/kg； h fo7 ——Enthalpy value of feedwater at the outlet of No. 7 high pressure heater, unit kJ/kg; hfo6——六号高压加热器出口给水焓值，单位kJ/kg； h fo6 ——Enthalpy value of feedwater at the outlet of No. 6 high-pressure heater, unit kJ/kg; hfo5——除氧器出口给水焓值，单位kJ/kg； h fo5 - enthalpy value of feedwater at the outlet of deaerator, unit kJ/kg; hfi8——八号高压加热器进口给水焓值，单位kJ/kg； h fi8 ——The enthalpy value of feed water at the inlet of No. 8 high-pressure heater, unit kJ/kg; hfi7——七号高压加热器进口给水焓值，单位kJ/kg； h fi7 ——Enthalpy value of feed water at the inlet of No. 7 high-pressure heater, unit kJ/kg; hfi6——六号高压加热器进口给水焓值，单位kJ/kg； h fi6 ——Enthalpy value of feed water at the inlet of No. 6 high pressure heater, unit kJ/kg; hfi5——除氧器进口凝结水焓值，单位kJ/kg； h fi5 ——enthalpy value of condensed water at the inlet of deaerator, unit kJ/kg; h8——八号高压加热器进口蒸汽焓值，单位kJ/kg； h 8 ——enthalpy value of steam at the inlet of No. 8 high-pressure heater, unit kJ/kg; h7——七号高压加热器进口蒸汽焓值，单位kJ/kg； h 7 ——Enthalpy value of the inlet steam of No. 7 high-pressure heater, unit kJ/kg; h6——六号高压加热器进口蒸汽焓值，单位kJ/kg； h 6 ——enthalpy value of steam at the inlet of No. 6 high-pressure heater, unit kJ/kg; h5——除氧器进口蒸汽焓值，单位kJ/kg； h 5 ——enthalpy value of steam at the inlet of deaerator, unit kJ/kg; h8d——八号高压加热器疏水焓值，单位kJ/kg； h 8d —— Hydrophobic enthalpy value of No. 8 high pressure heater, unit kJ/kg; h7d——七号高压加热器疏水焓值，单位kJ/kg； h 7d —— Hydrophobic enthalpy value of No. 7 high pressure heater, unit kJ/kg; h6d——六号高压加热器疏水焓值，单位kJ/kg。 h 6d —— Hydrophobic enthalpy value of No. 6 high pressure heater, unit kJ/kg.
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CN107576373A (en) * 2017-08-17 2018-01-12 浙江邦业科技股份有限公司 A kind of synthesis ammonia system raw gas flow accuracy of detection judges and antidote
CN109141541A (en) * 2018-07-10 2019-01-04 中北大学 A kind of coal-fired power station boiler reheater working medium flow on-line correction method
CN110516363A (en) * 2019-08-28 2019-11-29 西安西热节能技术有限公司 A method of for determining Turbine Performance Test duration
CN110516363B (en) * 2019-08-28 2022-12-06 西安西热节能技术有限公司 Method for determining performance test duration of steam turbine
CN113204847A (en) * 2021-05-11 2021-08-03 三门核电有限公司 Comparison method for nuclear turbine performance test

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