CN112446097A - Multi-objective optimization method for volume and load of steam generator - Google Patents

Multi-objective optimization method for volume and load of steam generator Download PDF

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CN112446097A
CN112446097A CN202011410167.7A CN202011410167A CN112446097A CN 112446097 A CN112446097 A CN 112446097A CN 202011410167 A CN202011410167 A CN 202011410167A CN 112446097 A CN112446097 A CN 112446097A
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刘政
王成
方园
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Wuhan No 2 Ship Design Institute No 719 Research Institute of China Shipbuilding Industry Corp
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Abstract

The invention relates to a multi-objective optimization method for volume and load of a steam generator, which comprises the following steps of setting an objective function of multi-objective optimization design of the steam generator: minySG＝FSG(x)＝(fV_SG(x),fQ_SG(x) In the formula, f)V_SG(x) As a function of SG volume with respect to decision variables; f. ofQ_SG(x) As a function of SG thermal power with respect to decision variables, fQ_SG(x) Is QSGThe values obtained by inversion are: f. ofQ_SG(x)＝‑QSG(x)；QSG(x) As a function of thermal power with respect to decision variables. Book (I)The method of the invention realizes that a smaller steam generator is used for bearing larger load, thereby gradually realizing the miniaturization of the nuclear power device.

Description

Multi-objective optimization method for volume and load of steam generator
Technical Field
The invention relates to multi-objective optimization of a steam generator, in particular to a multi-objective optimization design method for volume and load of a natural circulation type steam generator.
Background
The miniaturization of the nuclear power device is one direction of the development of the nuclear power device of the current ship, the volume and the power level of the nuclear power device are important factors influencing the performance of a nuclear power ship, the volume of the nuclear power device needs to be reduced as far as possible on the premise of meeting the safety, and meanwhile, the output power level of the device is ensured not to be reduced. The nuclear power device is a complex system composed of various nuclear power devices, the optimization of the nuclear power devices in the nuclear power device is the basis for realizing the system optimization of the nuclear power device, and the optimization design aiming at the nuclear power devices can provide reference and guidance for realizing the optimization of the nuclear power device at the system level.
Steam generators are key pieces of equipment in nuclear power plants, and one typical design goal is to carry large loads with a small steam generator volume. The traditional multi-objective optimization method mostly adopts a weighting method, namely, each objective is allocated with a weight and then converted into a single objective problem, but the method depends heavily on weighting factors selected by designers, different weighting factors generally correspond to different optimization results, the setting of the weights of the objectives has subjectivity because the weights of the objectives cannot be quantized, and in order to avoid introducing artificial subjectivity during multi-objective operation of the steam generator, a method capable of objectively performing multi-objective optimization on the volume and the load of the steam generator is necessary to be researched.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a multi-objective optimization method of the volume and the load of a steam generator, which realizes that the volume of the steam generator is smaller to bear larger load, thereby gradually realizing the miniaturization of a nuclear power plant.
The technical scheme adopted for realizing the aim of the invention is a multi-objective optimization method of volume and load of a steam generator, which comprises the following steps:
setting an objective function of multi-objective optimization design of the steam generator:
MinySG＝FSG(x)＝(fV_SG(x),fQ_SG(x))
in the formula (I), the compound is shown in the specification,fV_SG(x) As a function of SG volume with respect to decision variables; f. ofQ_SG(x) As a function of SG thermal power with respect to decision variables, fQ_SG(x) Is QSGThe values obtained by inversion are: f. ofQ_SG(x)＝-QSG(x)；QSG(x) As a function of thermal power with respect to decision variables;
the function of the decision vector is:
x＝[P,Tin,Tout,G,Psg,v,dtube_out,Rpitch]
wherein P is the operating pressure of the reactor, TinIs the inlet temperature, T, of the reactoroutOutlet temperature for reactivity, G mass flow of primary reactor coolant, PsgIs the secondary pressure of the steam generator, v is the flow velocity of the coolant in the tubes of the steam generator, dtube0outIs the outer diameter of the heat transfer pipe, RpitchIs the pitch diameter ratio of the heat transfer pipe.
In the above technical solution, the steam generator volume and load multi-objective optimization method further includes constraint conditions, where the constraint conditions include a value range of a decision variable, and upper and lower limits of a constraint variable.
In the technical scheme, the NSGA-II algorithm is utilized to solve ySGMinimum value of (1), i.e. Min ySG。
Further, according to the solved Min ySGAnd obtaining a Pareto optimal solution set of the volume and the load of the steam generator, and selecting a proper solution from the solution set according to actual requirements.
In the above technical solution, said fV_SG(x) And fQ_SG(x) Calculated by building a mathematical model of the steam generator.
And further, collecting key parameters of the female equipment, comparing the key parameters with the calculation result of the mathematical model, verifying the reliability of the mathematics of the equipment and the developed evaluation program, and checking the accuracy of the calculation result of the equipment program, wherein the key parameters of the female equipment comprise the diameter of a bent pipe section, the number of heat transfer pipes, the total heat transfer area, the height of a steam generator, the height of a straight pipe section, the wall thickness of the heat transfer pipes, the inner diameter of an upper barrel, the wall thickness of the upper barrel and the wall thickness of a lower barrel.
The traditional multi-objective optimization method mostly adopts a weighting method, namely, each objective is assigned with a weight and then is converted into a single objective problem, but the method depends heavily on weighting factors selected by designers, different weighting factors generally correspond to different optimization results, and the setting of the weights of the objectives is subjective because the weights of the objectives cannot be quantized. It can be seen that the traditional optimization method has large workload and strong subjectivity, the quality of the final scheme depends on the past design experience to a great extent, and the optimal design scheme can be determined only from a plurality of candidate schemes. The invention adopts a non-dominating thought, provides a method for objectively carrying out multi-objective optimization on the volume and the load of a steam generator, and can obtain a Pareto optimal solution set of the volume and the load of the steam generator by using an NSGA-II algorithm and combining a mathematical model of the steam generator and setting the volume and the load as optimization targets, so that a designer can select an optimal solution according to actual needs, and finally realize that a smaller volume of the steam generator bears a larger load, thereby gradually realizing the miniaturization of a nuclear power device.
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FIG. 1 is a flow chart of a steam generator volume and load multi-objective optimization method of the present invention.
FIG. 2 is a flow chart of the mathematical model for the steam generator in the optimization method of the present invention.
Detailed Description
The invention is described in further detail below with reference to the figures and the specific embodiments.
As shown in FIG. 1, the multi-objective optimization method of volume and load of the steam generator of the invention comprises the following steps:
and S1, establishing a mathematical model of the steam generator, as shown in the attached figure 2.
S1.1, analyzing and designing a mathematical model of the steam generator mainly from the aspects of heat transfer, flow, structure and the like. The basic structural form and thermal parameters of the steam generator are needed when thermal calculation is carried out, and the purpose is to calculate the heat transfer area of the heat transfer pipe for structural design and hydraulic calculation.
S1.1.1, calculating the heat transfer temperature difference between the primary side and the secondary side according to a formula (2-1), namely:
Figure BDA0002815158380000031
in the formula: Δ tmaxAnd Δ tminThe maximum temperature difference and the minimum temperature difference at two ends of the heat exchange area are respectively DEG C.
S1.1.2, calculating the primary side flow rate G according to the formula (2-2)sg：
Figure BDA0002815158380000032
In the formula: h isliThe enthalpy of the inlet of a heat transfer pipe of the steam generator is J/kg; h isloIs the enthalpy of the outlet of the heat transfer tube of the steam generator, J/kg; etasgHeat transfer efficiency of the primary side and the secondary side; qsgIs the steam generator thermal power, W.
S1.1.3, calculating the forced convection heat transfer coefficient alpha of the primary coolant in the heat transfer pipe to the pipe wall by combining the formula (2-2)1:
Figure BDA0002815158380000041
In the formula: lambda [ alpha ]1Is the thermal conductivity of the coolant, W/(m.K); diIs the inner diameter of the heat transfer pipe, m; refIs the Reynolds number, Pr, of the coolantfIs the prandtl number of the coolant. Re is a dimensionless number of standard heat transfer theory, and G is calculated according to the prior art using the formula (2-2)sgRe can be calculated.
S1.1.4, calculating the boiling heat transfer coefficient of the heat transfer type on the secondary side according to the formula (2-4).
α2＝5Psg 0.2q0.7 (2-4)
In the formula: psgThe operating pressure of the secondary side, Pa; q is the heat flow density of the heat transfer tube, W/m2。
S1.1.5, calculating the thermal resistance R of the pipe wall according to the formula (2-5)ωThe heat transfer tube material used in this example was Incoloy-800, whose heat transfer coefficient was calculated according to the formula recommended by KWU:
λ＝11.628+1.57*10-2tw (2-5)
in the formula: t is twThe temperature of the tube wall is measured in degrees centigrade.
S1.1.6, calculating the heat transfer coefficient k between the primary side and the secondary side by combining the formulas (2-3), (2-4) and (2-5):
Figure BDA0002815158380000042
in the formula: doAnd diThe outer diameter and the inner diameter m of the heat transfer pipe respectively; rωIs the thermal resistance of the tube wall, (m)2·℃)/W；RsIs the thermal resistance of heat transfer tube wall fouling, (m)2·℃)/W。
S1.1.7, calculating the heat transfer area of the heat transfer pipe by combining the formulas (2-1) and (2-6):
Figure BDA0002815158380000043
in the formula: the reserve coefficient C taken in this example is 1.1; qsgW is the heat exchange amount; delta t is a secondary side heat transfer temperature difference, DEG C; k is the heat transfer coefficient of the primary and secondary sides, W/(m)2·℃)。
S1.2, after the heat transfer area of the heat transfer pipe is obtained through thermodynamic calculation, the detailed calculation of the internal structure can be carried out, and the structural calculation aims to obtain parameters such as the number of the heat transfer pipes, the diameter of a pipe bundle and the height of a straight pipe section and is used for the next hydraulic calculation.
S1.2.1, calculating the number of heat transfer areas of the heat transfer tubes according to a formula (2-8):
Figure BDA0002815158380000051
in the formula: diIs the inner diameter of the heat transfer tube, m; u. oflThe flow velocity of the working medium in the heat transfer pipe is m/s; rholIs the density of working medium in the heat transfer pipe, kg/m3；GsgThe primary flow rate is kg/s.
S1.2.2, in combination with equation (2-8), calculate the tube bundle diameter:
Figure BDA0002815158380000052
in the formula: when the heat transfer pipes are arranged in a square shape, b takes a value of 1.19; b takes a value of 1.1 when arranged in a triangle; n is the number of the pull rods; s is the pitch of the heat transfer tubes, m; b ═ 1 to 1.5 d0。
S1.2.3, in combination with equation (2-8), calculating the height of the straight section of the steam generator heat transfer tube bundle:
Figure BDA0002815158380000053
in the formula: l istotalIs the total length of the U-shaped tube, m;
Figure BDA0002815158380000054
is the average diameter, m, of the tubes in the elbow region.
And S1.3, performing hydraulic calculation after thermal calculation and structural design calculation of the steam generator are completed, and aiming at determining the circulation multiplying power and the circulation speed of the secondary side. The hydraulic calculation of the steam generator comprises the calculation of flow resistance of a primary side and the calculation of a secondary side movement pressure head and circulation resistance, wherein the primary side resistance calculation aims to provide a reference basis for the design of a primary circulation pump, and the secondary side hydraulic calculation needs to set circulation multiplying power to balance the movement pressure head and the flow resistance of a circulation loop. The hydraulic calculation of the secondary side needs to be combined with the design processes of heating power, structure and the like to carry out iterative solution until convergence; the primary side resistance calculation needs to be calculated after the design of the steam generator is determined;
(1) primary side resistance calculation
S1.3.1, on the primary side of the steam generator, the resistance includes the frictional resistance and the local resistance in the heat transfer tubes, taking into account the reserve coefficient, which is 1.1 times the total calculated resistance.
Calculating the frictional resistance in the heat transfer tube according to the formula (2-11):
Figure BDA0002815158380000055
in the formula: rho is the density of the coolant, kg/m3(ii) a u is the flow velocity of the coolant in the heat transfer pipe, m/s; lavgIs the average length of the heat transfer tubes, m.
S1.3.2, local resistance calculated according to equation (2-12):
Figure BDA0002815158380000061
in the formula: xiiIs the local drag coefficient.
(2) Secondary hydraulic calculation
The moving pressure head is generated by different densities of working media in a descending space and an ascending space in the steam generator, water in the descending space is single-phase supercooled water, and because the supercooling degree is generally lower, the density difference between the supercooled water and saturated water is usually ignored in actual calculation, and the calculation is uniformly carried out according to the saturation water density; in the secondary side ascending section, the single-phase water absorbs heat and becomes saturated water until boiling, and the density is reduced.
S1.3.3, calculating the moving pressure head of the secondary side of the steam generator according to the formula (2-13):
Pm＝(ρs-ρm)gHr (2-13)
in the formula: rhosIs the density of saturated water, kg/m3；ρmIs the average density of the steam-water mixture, kg/m3；HrIs the height of the steam-containing section, m.
S1.3.4, combining the formulas (2-11), (2-12) and (2-13), adjusting the cyclic resistance so that the cyclic motion head and the flow resistance at the secondary side of the steam generator are equal:
Pm＝ΔPr+ΔPs+ΔPd (2-14)
in the formula: delta Pd、ΔPrAnd Δ PsRespectively the resistance of the secondary side descending section, the ascending section and the steam-water separator.
S1.4, the flow, heat transfer and structure calculations are not mutually independent, the calculations need to be repeatedly and alternately carried out until the calculation result is converged, and in the invention, the balance between the flow resistance of the secondary side and the circulating pressure head is taken as a convergence condition, so that the circulating multiplying power needs to be continuously adjusted.
S1.5, the interior of the steam generator is in a high-pressure state, and the pressure bearing capacity needs to be designed so as to ensure the operation safety of the steam generator. After the internal detailed structure of the steam generator is determined, intensity calculation can be carried out, and the thicknesses of the cylinder body and the end socket are determined, so that the external structural parameters of the steam generator can be determined. Wall thickness was calculated using ASME design specifications.
And S2, after the mathematical model of the steam generator is established according to the step S1, in order to verify the reliability of the device mathematics and the developed evaluation program, the accuracy of the device program calculation result can be checked, and the program calculation result is compared with the key parameters of the female device. Specifically, the parameters include the diameter of the bent pipe section, the number of heat transfer pipes, the total heat transfer area, the height of the steam generator, the height of the straight pipe section, the wall thickness of the heat transfer pipe, the inner diameter of the upper cylinder, the wall thickness of the lower cylinder and the like.
S3, establishing a multi-objective optimization algorithm
And compiling an NSGA-II algorithm, and reserving variable interfaces such as decision variables, target variables, constraint variables, solution algebra, population number and the like.
S4 steam generator optimization model
S4.1, objective function
Setting the objective function of the multi-objective optimization design of the steam generator as follows:
Min ySG＝FSG(x)＝(fV_SG(x),fQ_SG(x)) (2-15)
in the formula: f. ofV_SG(x) As a function of SG volume with respect to decision variables; f. ofQ_SG(x) As a function of SG thermal power with respect to decision variables, fQ_SG(x) Is QSGThe values obtained by inversion are: f. ofQ_SG(x)＝-QSG(x)；QSG(x) As a function of thermal power with respect to decision variables.
S4.2, decision variables
Design parameters influencing the objective function are determined according to the design process of the steam generator, and the design parameters comprise both thermal aspects and structural aspects. The thermal parameters include the operating pressure P of the reactor and the inlet temperature T of the reactorinAnd the outlet temperature ToutMass flow G of primary coolant in reactor, secondary pressure P of steam generatorsgThe flow velocity v of the coolant in the heat transfer tubes of the steam generator; the structural parameters mainly comprise the outer diameter do of the heat transfer pipe and the pitch-diameter ratio R of the heat transfer pipepitchAnd the decision vector is specifically:
x＝[P,Tin,Tout,G,Psg,v,dtube_out,Rpitch] (2-16)
s4.3, setting constraint conditions
In order to enable the steam generator to meet the requirements of actual engineering, constraint conditions need to be added, wherein the constraint conditions specifically comprise a value range of a decision variable and upper and lower limits of the constraint variable, the value range of the decision variable is determined according to the specific steam generator and is generally set to be a value near an original value, and the larger the set range is, the wider the design requirements on the steam generator are; the range of the constraint variables is dependent on the specific steam generator and the needs of the designer, with no specific range.
S5 setting a solution model
Assigning values to variables in the NSGA-II algorithm by using a reserved variable interface in the NSGA-II algorithm, specifically a decision variable x and a target variable f in a steam generator optimization modelV_SGConstraint variable C, solution algebra T, population number N and the like.
After the solution is completed, a Pareto optimal solution set of the volume and the load of the steam generator is obtained, a plurality of groups of optimization schemes are provided, and a proper solution is selected from the solution set according to actual requirements.

Claims (6)

1. A multi-objective optimization method for steam generator volume and load is characterized in that: setting an objective function of multi-objective optimization design of the steam generator:
MinySG＝FSG(x)＝(fV_SG(x),fQ_SG(x))
in the formula (f)V_SG(x) As a function of SG volume with respect to decision variables; f. ofQ_SG(x) As a function of SG thermal power with respect to decision variables, fQ_SG(x) Is QSGValue obtained by inversion, QSG(x) As a function of thermal power with respect to decision variables;
the decision variables are:
x＝[P,Tin,Tout,G,Psg,v,dtube_out,Rpitch]
wherein P is the operating pressure of the reactor, TinIs the inlet temperature, T, of the reactoroutIs the reactor outlet temperature, G is the reactor primary coolant mass flow, PsgIs the secondary pressure of the steam generator, v is the flow velocity of the coolant in the tubes of the steam generator, dtube_outIs the outer diameter of the heat transfer pipe, RpitchIs the pitch diameter ratio of the heat transfer pipe.
2. Method for multiobjective optimization of steam generator volume and load according to claim 1, characterized in that: and the constraint conditions comprise the value range of the decision variables and the upper and lower limits of the constraint variables.
3. Method for multiobjective optimization of steam generator volume and load according to claim 2, characterized in that: solving for y using NSGA-II algorithmSGMinimum value of (1), i.e. Min ySG。
4. Method for multiobjective optimization of steam generator volume and load according to claim 3, characterized in that: according to the Min y of solutionSGObtaining Pareto optimal solution set of volume and load of the steam generator, and selecting proper solution set according to actual demandThe solution of (1).
5. Method for the multiobjective optimization of steam generator volume and load according to any one of claims 1 to 4, characterized in that fV_SG(x) And fQ_SG(x) Calculating by establishing a mathematical model of the steam generator, including:
calculating the heat transfer temperature difference between the primary side and the secondary side according to the formula (2-1), namely:
Figure FDA0002815158370000011
in the formula: Δ tmaxAnd Δ tminRespectively the maximum temperature difference and the minimum temperature difference at the two ends of the heat exchange area;
calculating the primary side flow rate G according to the formula (2-2)sg：
Figure FDA0002815158370000021
In the formula: h isliFor the inlet enthalpy, h, of the heat transfer tubes of the steam generatorloIs the outlet enthalpy, eta, of the heat transfer tubes of the steam generatorsgFor the heat transfer efficiency between the primary side and the secondary side, QSGHeating power for the steam generator;
calculating the forced convection heat transfer coefficient alpha of the primary side coolant in the heat transfer pipe to the pipe wall according to the formula (2-2)1：
Figure FDA0002815158370000022
In the formula: lambda [ alpha ]1Is the heat conductivity of the coolant, diIs the inner diameter of the heat transfer tube, RefIs the Reynolds number, Pr, of the coolantfIs the prandtl number of the coolant;
calculating the boiling heat transfer coefficient of the heat transfer type of the secondary side according to the formula (2-4):
α2＝5Psg 0.2q0.7 (2-4)
in the formula: psgThe operating pressure of the secondary side is shown, and q is the heat flux density of the heat transfer pipe;
when the thermal resistance of the pipe wall is calculated according to the formula (2-5), the heat conductivity coefficient formula is calculated:
λ＝11.628+1.57*10-2tw (2-5)
in the formula: t is twIs the tube wall temperature;
calculating the heat transfer coefficients k of the primary side and the secondary side by combining the formulas (2-3), (2-4) and (2-5):
Figure FDA0002815158370000023
in the formula: doAnd diRespectively the outer diameter and the inner diameter, R, of the heat transfer pipeωIs the thermal resistance of the tube wall, RsThermal resistance to fouling of the heat transfer tube walls;
and (3) calculating the heat transfer area of the heat transfer pipe by combining the formulas (2-1) and (2-6):
Figure FDA0002815158370000024
in the formula: c is the reserve coefficient, QsgDelta t is a secondary side heat transfer temperature difference, and k is a secondary side heat transfer coefficient;
calculating the number of heat transfer areas of the heat transfer tubes according to the formula (2-8):
Figure FDA0002815158370000031
in the formula: diIs the inner diameter of the heat transfer tube ulIs the flow velocity of working medium in the heat transfer pipe, rholIs the density of the working medium in the heat transfer tube, GsgIs the primary side flow;
and (3) calculating the diameter of the tube bundle by combining the formula (2-8):
Figure FDA0002815158370000032
in the formula: when the heat transfer pipes are arranged in a square shape, the value of b is 1.19, and when the heat transfer pipes are arranged in a triangular shape, the value of b is 1.1; n is the number of the pull rods; s is the pitch of the heat transfer tube, b ═ 1 to 1.5 d0；
Calculating the height of the straight section of the heat transfer tube bundle of the steam generator according to the formula (2-10):
Figure FDA0002815158370000033
in the formula: l istotalThe total length of the U-shaped tube,
Figure FDA0002815158370000034
the average diameter of the heat transfer tubes in the elbow region;
calculating the frictional resistance in the heat transfer tube according to the formula (2-11):
Figure FDA0002815158370000035
in the formula: ρ is the coolant density, u is the coolant flow velocity in the heat transfer tube, lavgIs the average length of the heat transfer tubes;
local resistance calculated according to equation (2-12):
Figure FDA0002815158370000036
in the formula: xiiIs the local resistance coefficient;
calculating the moving pressure head of the secondary side of the steam generator according to the formula (2-13):
Pm＝(ρs-ρm)gHr (2-13)
in the formula: rhosDensity of saturated water, pmIs a mixture of soda waterAverage density of matter, HrIs the height of the steam-containing section;
and (3) combining the formulas (2-11), (2-12) and (2-13), adjusting the circulating resistance so that the circulating movement pressure head and the flow resistance of the secondary side of the steam generator are equal:
Pm＝ΔPr+ΔPs+ΔPd (2-14)
in the formula: delta Pd、ΔPrAnd Δ PsRespectively the resistance of the secondary side descending section, the ascending section and the steam-water separator.
6. Method for multiobjective optimization of steam generator volume and load according to claim 5, characterized in that: collecting key parameters of the female equipment, comparing the key parameters with the calculation result of the mathematical model, verifying the reliability of the mathematics of the equipment and the developed evaluation program, and checking the accuracy of the calculation result of the equipment program, wherein the key parameters of the female equipment comprise the diameter of a bent pipe section, the number of heat transfer pipes, the total heat transfer area, the height of a steam generator, the height of a straight pipe section, the wall thickness of the heat transfer pipes, the inner diameter of an upper barrel body, the wall thickness of the upper barrel body and the wall thickness of a lower barrel body.
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113251322A (en) * 2021-05-28 2021-08-13 华能(广东)能源开发有限公司海门电厂 Method and system for drain valve leakage judgment and steam leakage loss

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20140033906A (en) * 2012-09-11 2014-03-19 한국수력원자력 주식회사 Apparatus and method of steam generator tube plugging analysis using pressure drop and heat-transfer performance
CN110795857A (en) * 2019-11-06 2020-02-14 哈尔滨工程大学 Volume optimization method for secondary loop main equipment of floating nuclear power plant
WO2020041883A1 (en) * 2018-08-29 2020-03-05 Carleton University Enabling wireless network personalization using zone of tolerance modeling and predictive analytics
CN110879620A (en) * 2019-11-19 2020-03-13 中广核工程有限公司 Liquid level control method and system for vertical steam generator of nuclear power station
CN111311638A (en) * 2020-02-11 2020-06-19 中国人民解放军军事科学院评估论证研究中心 Dynamic multi-objective optimization method based on segmentation multi-directional prediction strategy

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20140033906A (en) * 2012-09-11 2014-03-19 한국수력원자력 주식회사 Apparatus and method of steam generator tube plugging analysis using pressure drop and heat-transfer performance
WO2020041883A1 (en) * 2018-08-29 2020-03-05 Carleton University Enabling wireless network personalization using zone of tolerance modeling and predictive analytics
CN110795857A (en) * 2019-11-06 2020-02-14 哈尔滨工程大学 Volume optimization method for secondary loop main equipment of floating nuclear power plant
CN110879620A (en) * 2019-11-19 2020-03-13 中广核工程有限公司 Liquid level control method and system for vertical steam generator of nuclear power station
CN111311638A (en) * 2020-02-11 2020-06-19 中国人民解放军军事科学院评估论证研究中心 Dynamic multi-objective optimization method based on segmentation multi-directional prediction strategy

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
顾雪平;赵宝斌;刘文轩: "结合多目标优化与灰色关联决策的负荷恢复方法", 电力自动化设备, vol. 35, no. 9, pages 6 - 13 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113251322A (en) * 2021-05-28 2021-08-13 华能(广东)能源开发有限公司海门电厂 Method and system for drain valve leakage judgment and steam leakage loss

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