CN111539113A - Method for evaluating hydrodynamic safety of water wall of power station boiler under ultralow load - Google Patents
Method for evaluating hydrodynamic safety of water wall of power station boiler under ultralow load Download PDFInfo
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B37/00—Component parts or details of steam boilers
- F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
- F22B37/42—Applications, arrangements, or dispositions of alarm or automatic safety devices
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06Q—INFORMATION AND COMMUNICATION TECHNOLOGY [ICT] SPECIALLY ADAPTED FOR ADMINISTRATIVE, COMMERCIAL, FINANCIAL, MANAGERIAL OR SUPERVISORY PURPOSES; SYSTEMS OR METHODS SPECIALLY ADAPTED FOR ADMINISTRATIVE, COMMERCIAL, FINANCIAL, MANAGERIAL OR SUPERVISORY PURPOSES, NOT OTHERWISE PROVIDED FOR
- G06Q10/00—Administration; Management
- G06Q10/06—Resources, workflows, human or project management; Enterprise or organisation planning; Enterprise or organisation modelling
- G06Q10/063—Operations research, analysis or management
- G06Q10/0635—Risk analysis of enterprise or organisation activities
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06Q—INFORMATION AND COMMUNICATION TECHNOLOGY [ICT] SPECIALLY ADAPTED FOR ADMINISTRATIVE, COMMERCIAL, FINANCIAL, MANAGERIAL OR SUPERVISORY PURPOSES; SYSTEMS OR METHODS SPECIALLY ADAPTED FOR ADMINISTRATIVE, COMMERCIAL, FINANCIAL, MANAGERIAL OR SUPERVISORY PURPOSES, NOT OTHERWISE PROVIDED FOR
- G06Q10/00—Administration; Management
- G06Q10/06—Resources, workflows, human or project management; Enterprise or organisation planning; Enterprise or organisation modelling
- G06Q10/063—Operations research, analysis or management
- G06Q10/0639—Performance analysis of employees; Performance analysis of enterprise or organisation operations
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06Q—INFORMATION AND COMMUNICATION TECHNOLOGY [ICT] SPECIALLY ADAPTED FOR ADMINISTRATIVE, COMMERCIAL, FINANCIAL, MANAGERIAL OR SUPERVISORY PURPOSES; SYSTEMS OR METHODS SPECIALLY ADAPTED FOR ADMINISTRATIVE, COMMERCIAL, FINANCIAL, MANAGERIAL OR SUPERVISORY PURPOSES, NOT OTHERWISE PROVIDED FOR
- G06Q50/00—Systems or methods specially adapted for specific business sectors, e.g. utilities or tourism
- G06Q50/06—Electricity, gas or water supply
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/08—Thermal analysis or thermal optimisation
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
Abstract
The invention discloses an evaluation method of hydraulic safety of a spiral water wall of a supercritical power station boiler under ultra-low load, which comprises the following steps: (1) establishing an equivalent loop method calculation model and a single tube heat load calculation model of a spiral tube ring water-cooled wall flow pressure node; (2) calculating the flow pressure under the lowest operating condition; (3) correcting heat load distribution through the existing temperature measuring point data; (4) and performing hydrodynamic safety check under the ultra-low load parameter. The hydrodynamic force and spiral tube ring single tube heat load calculation model established by the invention better determines the operation condition of each tube in the water wall flow from the theoretical angle, corrects the heat load through the measured point data of the operated lowest working condition, can improve the accuracy of evaluation, and provides a basis for the analysis and evaluation of the hydrodynamic force safety of the water wall of the supercritical boiler under the ultra-low load working condition for the analysis and evaluation of the adaptability of the same type of unit to deep peak regulation operation feasibility analysis.
Description
The technical field is as follows:
the invention relates to the field of power station boiler water wall operation evaluation, in particular to an evaluation method for hydrodynamic safety of a power station boiler spiral tube ring water wall under ultralow load.
Background art:
in recent years, in order to greatly advance clean reformation of energy structures, the development speed of renewable energy is accelerated, and the development speed of thermal power is slowed down. However, the new energy has the characteristics of randomness, intermittence, instability and the like, after the proportion is increased to a certain degree, larger peak regulation pressure is inevitably brought to a power grid, the peak regulation capacity of the system needs to be fully excavated by the existing coal-electric unit, the flexibility and the adaptability of the system are enhanced, and the trend is the inevitable development trend of thermal power at present and in the future. The problems of deep peak regulation capability and low-load operation adaptability are important factors for restricting the flexibility improvement of the thermal power generating unit, and the load rate of the thermal power generating unit is required to be as low as 20-40% by deep peak regulation.
Because the supercritical unit usually only considers the normal operation of minimum 40-50% rated load at the beginning of design, the water cooling wall hydrodynamic force under the ultra-low load deviating from the design working condition has the safety problems of pulsation, multivalueness and the like. At present, the existing research is mostly directed to a vertical tube ring water-cooled wall boiler, and the research on the ultra-low load of less than 30 percent is less. In addition, the water-cooled wall structure of the spiral tube ring is complex, the number of connecting elbows between the tubes and the header is large, and the flow resistance is large; when the rated load operates, the mass flow rate of the working medium is large, and the influence of resistance is relatively small; during ultra-low load operation, the resistance disturbance is relatively large, and the hydrodynamic force is possibly influenced. Therefore, in the hydrodynamic calculation process, higher calculation accuracy is required, and the accuracy of a calculation result is directly related to a water wall flow pressure calculation model and a single-tube heat load calculation model. When the unit operates at low load, the flame filling degree in the hearth is different from the high load time difference, and the heat load distribution deviates from an empirical curve at the moment. Most of the existing hydrodynamic force calculation documents adopt empirical curves, the empirical curves are empirical methods, complete theoretical bases are lacked, and the curve is greatly influenced by changes of working conditions. The calculation problems directly influence the result of hydrodynamic calculation and bring difficulty to the operation evaluation of the ultra-low load water wall.
Disclosure of Invention
The invention aims to provide a more accurate evaluation method for the hydrodynamic safety of the water wall of the power station boiler under the ultralow load, which can give reference to the operation of a power station unit and effectively predict the adaptability of the ultralow load operation.
In order to solve the technical problem, the invention provides an evaluation method for the hydrodynamic safety of a water wall of a power station boiler under ultralow load, which comprises the following steps:
(1) establishing an equivalent branch method calculation model and a single-tube heat load calculation model of a spiral tube ring water-cooled wall flow pressure node;
(2) calculating the flow pressure under the lowest operating condition;
(3) correcting heat load distribution according to the existing temperature measuring point data;
(4) and performing hydrodynamic safety check under the ultra-low load parameter.
The method for evaluating the hydrodynamic safety of the water wall of the power station boiler under the ultralow load comprises the following steps that in the step (1), the equivalent branch method calculation model of the flow pressure node of the water wall of the spiral tube coil is used for enabling a water wall loop to be equivalent to a plurality of branches, and the calculation method of the reduced resistance coefficient of the equivalent branches is as shown in the formula (2-1) to the formula (2-3):
Kc＝∑Ki(2-2)
in the formula: g is the total flow of the pipeline in units: kg/s;
Giequivalent branch flow, unit: kg/s;
Kbthe total reduced resistance coefficient of the parallel pipelines;
Kcthe total reduced resistance coefficient for the series pipeline;
Kdxis the reduced resistance coefficient at equivalent flow.
The method for evaluating the hydrodynamic safety of the water wall of the power station boiler under the ultra-low load comprises the steps that the single-tube heat load calculation model in the step (1) adopts a spiral tube coil water wall single-tube enthalpy increase calculation method, the heat load of an inclined tube section is calculated by a infinitesimal analysis method based on line integral, and the final calculation equation is shown as a formula (3-1)
In the formula ηrqThe coefficient of uneven thermal load among walls is a constant value for the same furnace wall;
ηrhfor the coefficient of thermal load inequality in the height direction, it can be expressed as a 6 th-order polynomial F with respect to the relative height y of the furnace1(y)；
ηrbFor the coefficient of thermal load inequality in the width direction, it can be expressed as a 6 th-order polynomial F with respect to the relative width x of the furnace2(x)；
C is a correction coefficient;
qavthe average heat load of the heating surface of the water wall is as follows: kJ/m2/s；
FiIs the heating area of the pipe section, unit: m is3；
G is the pipe flow, unit: kg/s;
dL is the length of the micro-spool piece,
unit: m;
x, Y, X, Y are the width and length of the micro-element tube segment on absolute and relative scales, unit: m;
d is the pipe intercept, unit: m;
xinthe x coordinate of the position of the inlet of the tube relative to the width of the tube panel where the tube is positioned;
yinis a y coordinate of the position of the inlet of the tube relative to the height of the hearth;
α is the tube inclination, in units: (iv) DEG;
b is the width of the tube panel where the tube is located, unit: m;
h is the height of the hearth, unit: and m is selected.
The method has the advantages that the operation condition of each pipe in the water wall flow is better determined, the accuracy of hydrodynamic calculation can be improved, and the established method for analyzing and evaluating the hydrodynamic safety of the water wall of the supercritical boiler under the ultra-low load working condition can be suitable for analyzing the feasibility of the adaptive deep peak shaving operation of the same type of units.
Drawings
FIG. 1 is a schematic view of the equivalent bypass flow network of the water wall of the present invention
FIG. 2 is a physical model of a heated pipe section constructed in accordance with the present invention
FIG. 3 is a micro-element mathematical model of a spiral pipe section established by the invention
FIG. 4 is a result of the calculation of the temperature distribution of the outer wall of the outlet of the front wall of the spiral tube coil water wall according to the present invention
FIG. 5 is a result of calculating the temperature distribution of the outer wall of the outlet of the right wall of the water wall of the spiral tube coil according to the present invention
FIG. 6 shows the calculation results of the mass flow rate distribution of the spiral tube coil of the lower furnace
FIG. 7 shows the mass flow rate distribution calculation results of the vertical pipe line of the upper furnace
FIG. 8 shows the multi-valued evaluation result of the hydrodynamic force of the 149 number tube of the lower spiral tube coil of the present invention
Detailed Description
A method for evaluating the hydrodynamic safety of a water wall of a power station boiler under ultralow load comprises the following steps:
(1) establishing an equivalent branch method calculation model and a single-tube heat load calculation model of a spiral tube ring water-cooled wall flow pressure node;
(2) calculating the flow pressure under the lowest operating condition;
(3) correcting heat load distribution according to the existing temperature measuring point data;
(4) and performing hydrodynamic safety check under the ultra-low load parameter.
In step 1, an equivalent flow network method is adopted to simplify the water wall process into the combination of the header nodes and the pipelines between the headers, and fig. 1 is a schematic diagram of the equivalent branch flow network of the water wall. The pressure drop and flow relation equation of a single tube panel is known as
ΔPi＝Ki·Gi 2(1)
In the formula: kiThe single pipeline conversion resistance coefficient is 1/kg/m, and the local resistance conversion coefficient, the friction resistance conversion coefficient and the gravity differential pressure conversion coefficient are added; giSingle line flow, unit: kg/s; delta PiSingle line pressure drop, unit: pa.
The total conversion resistance coefficient of the parallel pipelines is obtained from the relationship of equal pressure drop of the parallel pipelines
The total conversion resistance coefficient of the series pipeline can be obtained by the relation that the flow of the series pipeline is equal
K＝∑Ki(3)
Due to the complexity of the spiral pipe ring structure, the outlet convergence header is usually at a cross joint, namely, a header passes through a plurality of pipelines in front and at the back, and at the moment, the flow of the pipelines in front and at the back of the header is unequal and cannot be equivalent to a loop. Therefore, by adopting the method of equivalent branches, a loop is equivalent to a plurality of branches, and the reduced resistance coefficient of the equivalent branches can be expressed as:
in the formula: g is the total flow of the pipeline in units: kg/s; giEquivalent branch flow, unit: kg/s; k' is the reduced resistance coefficient at equivalent flow.
The whole water wall loop can be equivalent to a loop by the methods of the formulas (1) to (4) and the series-parallel pipelines, so that the total pressure drop of the water wall is calculated.
In the step 1, the single spiral pipe coil pipe is different from the single vertical ascending pipeline pipe in that the heating of the pipe in the height direction and the width direction is changed, and the calculation of the heat load of the single spiral pipe coil pipe based on a line integral method is considered. Fig. 2 is a physical model of the heated pipe section established by the invention, and fig. 3 is a infinitesimal mathematical model of the spiral pipe section established by the invention.
The local thermal load non-uniformity coefficient of the micro-element tube segment is
ηi＝ηrq·ηrh·ηrb·C＝C′F1(y)F2(x) (6)
In the formula ηrqη is the coefficient of thermal load non-uniformity between walls, and the value of the coefficient can be regarded as a constant for the same furnace wallrhFor the coefficient of thermal load inequality in the height direction, it can be expressed as a 6 th-order polynomial F with respect to the relative height y of the furnace1(y)；ηrbFor the coefficient of thermal load inequality in the width direction, it can be expressed as a 6 th-order polynomial F with respect to the relative width x of the furnace2(x) (ii) a C is a correction coefficient.
For the micro-element section of the spiral pipe section, the enthalpy of the working medium is increased to
In the formula: q. q.savThe average heat load of the heating surface of the water wall is as follows: kJ/m2/s；FiIs the heating area of the pipe section, unit: m is3(ii) a G is the pipe flow, unit: kg/s; dL is the length of the micro-spool piece,
unit: m; x, Y, X, Y are the width and length of the micro-element tube segment on absolute and relative scales, unit: m; d is the pipe intercept, unit: and m is selected.
The length infinitesimal is converted into x and y coordinate infinitesimal, and the absolute scale is converted into the relative scale to obtain
In the formula: x is the number ofinX being the tube inlet position relative to the width of the tube panel on which the tube is locatedCoordinates; y isinIs the y coordinate of the position of the tube inlet relative to the height of the hearth, α is the inclination angle of the tube in unit degree, B is the width of the tube panel where the tube is located in unit m, and H is the height of the hearth in unit m.
And (3) integrating the formula (7) to obtain a calculation formula of the heat load of the single pipe of the spiral pipe section:
the independent heat load calculation can be carried out on each pipe of the spiral pipe coil by the calculation capability of the electronic computer through the formula (8), so that the heating condition of the single pipe is determined, and the accuracy of the pressure drop and flow relation of each pipe is ensured.
Example calculation results are obtained through steps 2, 3 and 4, fig. 4 is a calculation result of the temperature distribution of the outer wall of the outlet of the front wall of the water wall of the spiral tube coil of the invention, fig. 5 is a calculation result of the temperature distribution of the outer wall of the outlet of the right wall of the water wall of the spiral tube coil of the invention, fig. 6 is a calculation result of the mass flow rate distribution of the spiral tube coil of the lower hearth of the invention, fig. 7 is a calculation result of the mass flow rate distribution of the vertical pipeline of the upper hearth of the invention, and fig. 8 is a multivalued evaluation result of the water power of the No. 149 tube of the lower. The calculated value and the measured value of the wall temperature of the water-cooled wall of the spiral tube ring of the lower furnace hearth under the working condition of 40 percent TRL are basically at the same level and are consistent with the temperature distribution under the working condition of 100 percent BMCR, which shows that the hydrodynamic calculation model has better accuracy, and the total pressure drop of the water-cooled wall and the errors of all parameters of the separator are within an acceptable range.
The maximum mass flow rate of the spiral tube coil of the hearth under the water wall is 52 loops with the outlet on the left wall, and the flow rate is 739.03kg/s/m2The minimum is 12 loops at the front wall at the outlet, and the flow rate is 701.25kg/s/m2The deviation was 5.11%. In the water-cooled wall of the spiral tube coil, the vertical drop of each tube is the same, the maximum gravity pressure drop is 0.05728MPa, and the minimum gravity pressure drop is 0.05396 MPa. The position of the water-cooled wall where the mass flow rate of the vertical tube coil of the hearth is the maximum is a 43-loop of the right wall, and the flow rate is 399.689kg/s/m286 loops with the smallest left wall and a flow rate of 303.75kg/s/m2Deviation of 24.00% >, sideThe wall flow rate deviation is greater than the front and rear walls, as expected. Pressure drop flow rate dependence obtained by varying the tube flow rate figure 8 shows that the total pressure drop increases with increasing flow rate and is monotonically increasing. Therefore, the water wall of the spiral tube coil can be judged to have no multivalue phenomenon under the working condition of 30% BMCR. The method for analyzing and evaluating the hydraulic safety of the water-cooled wall of the supercritical boiler under the ultra-low load working condition, which is established by the invention, can be suitable for analyzing the feasibility of the adaptive deep peak shaving operation of the same type of units.
Claims (3)
1. A method for evaluating the hydrodynamic safety of a spiral water wall of a supercritical power station boiler under ultra-low load is characterized by comprising the following steps:
(1) establishing an equivalent branch method calculation model and a single-tube heat load calculation model of a spiral tube ring water-cooled wall flow pressure node;
(2) calculating the flow pressure under the lowest operating condition;
(3) correcting heat load distribution according to the existing temperature measuring point data;
(4) and performing hydrodynamic safety check under the ultra-low load parameter.
2. The method for evaluating the hydrodynamic safety of the spiral water wall of the supercritical power station boiler under the ultra-low load as claimed in claim 1, wherein the specific method of the equivalent branch method calculation model of the flow pressure node of the spiral tube coil water wall in the step (1) is as follows: one water wall loop is equivalent to a plurality of branches, and the calculation method of the equivalent resistance coefficient of the equivalent branches is as shown in the formulas (2-1) to (2-3):
Kc＝∑Ki(2-2)
in the formula: g is the total flow of the pipeline in units: kg/s;
Giequivalent branch flow, unit: kg/s;
Kbthe total reduced resistance coefficient of the parallel pipelines;
Kcthe total reduced resistance coefficient for the series pipeline;
Kdxis the reduced resistance coefficient at equivalent flow.
3. The method for evaluating the hydrodynamic safety of the spiral water-cooled wall of the supercritical power station boiler under the ultra-low load as claimed in claim 1, wherein the single-tube heat load calculation model in the step (1) adopts a single-tube enthalpy increase calculation method of the spiral tube coil water-cooled wall, the heat load of the inclined tube section is calculated by a infinitesimal analysis method based on line integral, and the final calculation equation is shown as the formula (3-1):
in the formula ηrqThe coefficient of uneven thermal load among walls is a constant value for the same furnace wall;
ηrhfor the coefficient of thermal load inequality in the height direction, it can be expressed as a 6 th-order polynomial F with respect to the relative height y of the furnace1(y)；
ηrbFor the coefficient of thermal load inequality in the width direction, it can be expressed as a 6 th-order polynomial F with respect to the relative width x of the furnace2(x)；
C is a correction coefficient;
qavthe average heat load of the heating surface of the water wall is as follows: kJ/m2/s；
FiIs the heating area of the pipe section, unit: m is3；
G is the pipe flow, unit: kg/s;
dL is the length of the micro-spool piece,
unit: m;
x, Y, X, Y are the width and length of the micro-element tube segment on absolute and relative scales, unit: m;
d is the pipe intercept, unit: m;
xinthe x coordinate of the position of the inlet of the tube relative to the width of the tube panel where the tube is positioned;
yinis a y coordinate of the position of the inlet of the tube relative to the height of the hearth;
α is the tube inclination, in units: (iv) DEG;
b is the width of the tube panel where the tube is located, unit: m;
h is the height of the hearth, unit: and m is selected.
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113434985A (en) * | 2021-07-08 | 2021-09-24 | 西安热工研究院有限公司 | State evaluation method for steam-water separator pipe seat and connecting pipe of supercritical or ultra-supercritical boiler |
| CN113532798A (en) * | 2021-08-10 | 2021-10-22 | 西安热工研究院有限公司 | Method for calculating minimum feed water flow of low load of supercritical power station boiler |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101013416A (en) * | 2007-02-06 | 2007-08-08 | 西安交通大学 | Hydrodynamic general design and checking method of boiler |
| CN103216812A (en) * | 2013-04-15 | 2013-07-24 | 王衡 | Method for on-line monitoring and alarming of convection heating face flue gas temperature field of power station boiler |
| CN105424746A (en) * | 2016-01-04 | 2016-03-23 | 华能南京金陵发电有限公司 | Monitoring system and method for heat transfer characteristic of water wall tube of utility boiler |
| CN105698156A (en) * | 2016-02-01 | 2016-06-22 | 上海发电设备成套设计研究院 | Online monitoring method and system for wall temperature of vertical water wall of ultra-supercritical boiler |
| CN106897547A (en) * | 2017-01-12 | 2017-06-27 | 西安交通大学 | A kind of general hydrodynamic calculation method of ultra-supercritical boiler |
-
2020
- 2020-04-27 CN CN202010342727.3A patent/CN111539113A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101013416A (en) * | 2007-02-06 | 2007-08-08 | 西安交通大学 | Hydrodynamic general design and checking method of boiler |
| CN103216812A (en) * | 2013-04-15 | 2013-07-24 | 王衡 | Method for on-line monitoring and alarming of convection heating face flue gas temperature field of power station boiler |
| CN105424746A (en) * | 2016-01-04 | 2016-03-23 | 华能南京金陵发电有限公司 | Monitoring system and method for heat transfer characteristic of water wall tube of utility boiler |
| CN105698156A (en) * | 2016-02-01 | 2016-06-22 | 上海发电设备成套设计研究院 | Online monitoring method and system for wall temperature of vertical water wall of ultra-supercritical boiler |
| CN106897547A (en) * | 2017-01-12 | 2017-06-27 | 西安交通大学 | A kind of general hydrodynamic calculation method of ultra-supercritical boiler |
Non-Patent Citations (1)
| Title |
|---|
| 董乐: "660MW超超临界循环流化床锅炉水动力及流动不稳定特性计算分析", 《中国电机工程学报》 * |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113434985A (en) * | 2021-07-08 | 2021-09-24 | 西安热工研究院有限公司 | State evaluation method for steam-water separator pipe seat and connecting pipe of supercritical or ultra-supercritical boiler |
| CN113532798A (en) * | 2021-08-10 | 2021-10-22 | 西安热工研究院有限公司 | Method for calculating minimum feed water flow of low load of supercritical power station boiler |
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