WO2023246273A1 - 旁路供热系统减温水调节阀超前控制方法及系统 - Google Patents

旁路供热系统减温水调节阀超前控制方法及系统 Download PDF

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Publication number
WO2023246273A1
WO2023246273A1 PCT/CN2023/089750 CN2023089750W WO2023246273A1 WO 2023246273 A1 WO2023246273 A1 WO 2023246273A1 CN 2023089750 W CN2023089750 W CN 2023089750W WO 2023246273 A1 WO2023246273 A1 WO 2023246273A1
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WIPO (PCT)
Prior art keywords
desuperheating water
bypass
regulating valve
water regulating
valve
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PCT/CN2023/089750
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English (en)
French (fr)
Inventor
张奔
杨荣祖
谢天
黄嘉驷
曾立飞
穆祺伟
王汀
翟鹏程
王耀文
于龙文
王宏武
Original Assignee
西安热工研究院有限公司
西安西热节能技术有限公司
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Publication of WO2023246273A1 publication Critical patent/WO2023246273A1/zh

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    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05B—CONTROL OR REGULATING SYSTEMS IN GENERAL; FUNCTIONAL ELEMENTS OF SUCH SYSTEMS; MONITORING OR TESTING ARRANGEMENTS FOR SUCH SYSTEMS OR ELEMENTS
    • G05B13/00—Adaptive control systems, i.e. systems automatically adjusting themselves to have a performance which is optimum according to some preassigned criterion
    • G05B13/02—Adaptive control systems, i.e. systems automatically adjusting themselves to have a performance which is optimum according to some preassigned criterion electric
    • G05B13/04—Adaptive control systems, i.e. systems automatically adjusting themselves to have a performance which is optimum according to some preassigned criterion electric involving the use of models or simulators
    • G05B13/042—Adaptive control systems, i.e. systems automatically adjusting themselves to have a performance which is optimum according to some preassigned criterion electric involving the use of models or simulators in which a parameter or coefficient is automatically adjusted to optimise the performance
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/70—Application in combination with
    • F05D2220/76—Application in combination with an electrical generator

Definitions

  • the present disclosure relates to the field of power generation technology, and in particular to a method and system for advance control of a desuperheating water regulating valve in a bypass heating system.
  • thermoelectric decoupling transformation of thermal power generating units According to the National Energy Administration's "14th Five-Year Plan" energy planning requirements, the installed capacity of new energy sources such as wind power and photovoltaics will continue to grow rapidly. In order to improve the power grid's ability to absorb new energy, it is required to improve the peak load regulation capacity of thermal power units and improve the operation of thermal power units. Flexibility and improve new energy consumption capacity. The flexibility transformation of thermal power units that has been implemented enables the units to have deep peak-shaving capabilities.
  • the main technologies include low-load stable combustion of boilers, low-load denitration, zero output of low-pressure cylinders, and bypass heating. Among them, bypass heating has the advantages of low investment, flexible operation, and high thermoelectric decoupling characteristics. It has become one of the important technologies for the current thermoelectric decoupling transformation of thermal power generating units. It has played an important role in improving the heating capacity of power plants and achieving deep peak shaving. significant role.
  • the present disclosure proposes a method for advance control of the desuperheating water regulating valve of high and low bypass heating systems, which includes the following steps: a simulation test is performed to obtain the advance control curve of the desuperheating water regulating valve of the bypass heating system; the controller controls the desuperheating water regulating valve according to the opening of the bypass valve. , the set temperature after the desuperheater and the advance control curve of the desuperheating water regulating valve control the opening of the desuperheating water regulating valve.
  • the controller controls the opening of the desuperheating water regulating valve of the high-bypass heating system according to the advance control curve of the desuperheating water regulating valve of the high-bypass heating system, and the controller controls the desuperheating water regulating valve opening of the high-bypass heating system according to the low-bypass heating system.
  • the lead control curve of the desuperheating water regulating valve of the road heating system controls the opening of the desuperheating water regulating valve of the low side valve heating system.
  • the controller includes a temperature setting module configured to set the post-desuperheater temperature.
  • the simulation test to obtain the advance control curve of the desuperheating water regulating valve of the bypass heating system includes the following steps: select at least 5 temperature point values between the upper and lower limits of the temperature design value after the desuperheater, and Select at least 5 valve opening points within the maximum valve opening range of the road valve; put into the bypass heating system to make the bypass heating system operate stably; adjust the bypass valve opening to a certain valve Opening point value, set the temperature behind the desuperheater to the selected temperature point value in sequence, adjust the opening degree of the desuperheating water regulating valve until the high and low bypass heating systems operate stably, and record each The desuperheating water regulating valve opening data under the combined operating conditions of the valve opening point value and the temperature point value; analyzing and processing the desuperheating water regulating valve opening data under each operating condition to obtain the desuperheating water regulating valve advance control curve.
  • the opening of the bypass valve is a certain value.
  • the opening degree is determined according to the adjacent temperature points.
  • the opening of the desuperheating water regulating valve corresponding to the value of the desuperheating water regulating valve and the adjacent temperature point value on the desuperheating water regulating valve advance control curve are determined under the known conditions of the bypass valve opening and the set post-desuperheater temperature. The opening of the hot water regulating valve.
  • the upper and lower limits of the design value of the temperature after the desuperheater in the low-side heating system are 260°C and 240°C, and 5 temperature points are selected between the upper and lower limits of the design value of the temperature after the desuperheater.
  • the values are 260°C, 255°C, 250°C, 245°C and 240°C respectively.
  • the maximum valve opening of the bypass valve in the low-bypass heating system is 90%, and 5 valve opening point values are selected within the maximum valve opening range of the bypass valve, which are 10%, 30%, 50%, 70%, 90%.
  • the maximum valve opening of the bypass valve in the high-bypass heating system is 50%, and five valve opening point values are selected within the maximum valve opening range of the bypass valve, which are 5%, 10%, 15%, 30%, 50%.
  • the present disclosure proposes a desuperheating water regulating valve advance control system for a bypass heating system, including: a desuperheater;
  • the temperature of the bypass steam is reduced under the action of desuperheating water after passing through the desuperheater.
  • the controller of the present disclosure controls the opening of the desuperheating water regulating valve according to the opening of the bypass valve, the set temperature after the desuperheater and the advance control curve of the desuperheating water regulating valve, thereby avoiding the need for desuperheating when adjusting the opening of the bypass valve.
  • Temperature reduction caused by delayed temperature change behind the reactor The water regulating valve responds to the lag in adjustment and the safety hazard caused by temperature fluctuations after the desuperheater, while ensuring the accuracy of the calculation of high and low side valve flow rates.
  • Figure 1 shows a typical high and low side heating system diagram
  • Figure 2 is a simplified diagram of the high (low) bypass system
  • Figure 3 is a schematic diagram of the advance control curve of the desuperheating water regulating valve of the low-bypass heating system
  • Figure 4 is a schematic diagram of the advance control curve of the desuperheating water regulating valve of the low-bypass heating system according to an embodiment of the present disclosure
  • Figure 6 is a schematic diagram of the control method of the control system of the present disclosure.
  • bypass heating causes the original proportion of steam entering the high- and medium-pressure cylinders to change, deviating from the design value. This will directly affect the axial thrust of the unit. Exceeding the axial thrust will cause the thrust of the unit to warp. The temperature, axial displacement, and expansion difference between high and medium pressure cylinders exceed the limits, which affects the safe and stable operation of the unit.
  • the typical high and low side heating system diagram is shown in Figure 1. To solve this problem, the existing solution is to obtain the high side valve flow rate and the low side valve flow rate based on the mass balance and energy balance, and then control the opening of the high side valve based on the calculated one-to-one correspondence between the two and the low side valve flow rate. Spend.
  • F 2 , P 1 , P 2 , P 3 , T 1 , T 2 , T 3 can be measured in real time, then F 1 and F 3 can be obtained according to the above formula, and then according to the high and low side
  • the relationship between F 1 of each path (calculated based on the thermal balance diagram and the axial thrust of the high and medium pressure rotor), adjust the high side F 1 by controlling the high side valve to match the low side F 1 ,
  • the axial thrust of the high and medium pressure rotor is within a safe range, ensuring safe and stable operation of the unit.
  • the disclosed advance control method of the desuperheating water regulating valve of the bypass heating system includes the following steps:
  • the simulation test is used to obtain the advance control curve of the desuperheating water regulating valve of the bypass heating system
  • the controller includes a temperature setting module, which is used to set the temperature after the desuperheater.
  • the bypass heating system desuperheating water regulating valve advance control curve includes a high bypass heating system desuperheating water regulating valve advance control curve and a low The bypass heating system desuperheating water regulating valve advance control curve, the controller controls the desuperheating water regulating valve opening of the high bypass heating system according to the high bypass heating system desuperheating water regulating valve advance control curve, the controller controls the desuperheating water regulating valve opening of the high bypass heating system according to the low bypass
  • the advance control curve of the desuperheating water regulating valve of the heating system controls the opening of the desuperheating water regulating valve of the low side valve heating system.
  • the opening of the bypass valve is adjusted to a certain valve opening point value
  • the temperature after the desuperheater is sequentially set to the selected temperature point value
  • the opening degree of the desuperheating water regulating valve is adjusted until the high and low bypass supply
  • the thermal system operates stably, and the opening data of the desuperheating water regulating valve under the combination of each valve opening point value and temperature point value is recorded. Specifically, five temperature point values are selected between the upper and lower limits of the temperature design value after the desuperheater.
  • the opening data record table of the desuperheating water regulating valve under the combination of each valve opening point value and the temperature point value is shown in Table 1.
  • Table 1 Example table of opening data recording of desuperheating water regulating valve under the combination of each valve opening point value and temperature point value.
  • the advance control curve of the desuperheating water regulating valve of the low-bypass heating system is shown in Figure 3.
  • the bypass valve opening is a certain value and the set temperature after the desuperheater is between two adjacent temperature points
  • the desuperheating water regulating valve will advance according to the adjacent temperature point values and the adjacent temperature point values.
  • the corresponding opening of the desuperheating water regulating valve on the control curve determines the opening of the desuperheating water regulating valve under the condition that the bypass valve opening and the set post-desuperheater temperature are known.
  • the low side desuperheating water regulating valve advance control parameter J can be automatically given to the low side desuperheating water regulating valve according to the low side heating system desuperheating water regulating valve advance control curve and the set temperature behind the desuperheater valve. If the constant temperature T 30 is between two adjacent T 3 (T 3a corresponds to J a and T 3b corresponds to J b as an example) test values, the following method can be used to determine J 0 :
  • the high side desuperheating water regulating valve advance control parameter J can be automatically given based on the high side heating system desuperheating water regulating valve lead control curve and the set temperature behind the desuperheater valve.
  • the upper and lower limits of the design value of the temperature after the desuperheater in the low-side heating system are 260°C and 240°C, and five temperature point values are selected between 260°C and 240°C, respectively 260°C, 255°C.
  • the maximum value of the low side valve opening is 90%, select 5 low side valve opening point values within the range of 90% of the low side valve opening, and the points are They are 10%, 30%, 50%, 70%, and 90%; put in the high and low side heating systems and run stably for 30 minutes; adjust the bypass valve to the opening point value of each valve, and at the same time set the desuperheater in sequence Temperature set value, then adjust the opening of the desuperheating water regulating valve until the system runs stably for 30 minutes, and record the final opening of the desuperheating water regulating valve, as shown in Table 2.
  • Table 2 is the desuperheating water regulating valve opening data record table under the combination of low valve opening point value and temperature point value.
  • the lead control curve of the desuperheating water regulating valve of the low-bypass heating system is obtained, as shown in Figure 4.
  • the upper and lower limits of the design value of the temperature after the desuperheater in the high side heating system are 290°C and 270°C.
  • Five temperature point values are selected between 290°C and 270°C, respectively 290°C, 285°C. °C, 280°C, 275°C, 270°C; the maximum opening of the high side valve is 50%.
  • Table 3 is the desuperheating water regulating valve opening data record table under the combination of high valve opening point value and temperature point value.
  • the high side desuperheated water regulating valve advance control parameter J g is automatically given according to the set temperature behind the desuperheater valve, such as the set temperature after the desuperheater valve
  • the advanced control system of the desuperheating water regulating valve of high and low bypass heating systems includes a desuperheating water regulating valve, a bypass valve, a desuperheater and a controller.
  • the desuperheating water regulating valve is set on the desuperheating water circulation pipeline, and the desuperheating water is used to adjust the desuperheating water flow;
  • the bypass valve is set upstream of the desuperheater to adjust the bypass opening; the bypass steam passes through the desuperheater and flows into the desuperheating water.
  • the temperature decreases under the action of the controller;
  • the controller includes a temperature setting module and a control module.
  • the temperature setting module, desuperheating water regulating valve and bypass valve are all electrically connected to the control module.
  • the control module of the controller obtains the bypass valve opening and the temperature after the desuperheater set by the temperature setting module, and controls the desuperheating water regulating valve according to the advance control curve of the desuperheating water regulating valve.
  • the opening degree avoids safety hazards caused by temperature fluctuations behind the desuperheater, and at the same time ensures the accuracy of calculations of high and low side valve flow rates.
  • references to the terms “one embodiment,” “some embodiments,” “an example,” “specific examples,” or “some examples” or the like means that specific features are described in connection with the embodiment or example.
  • structures, materials, or features are included in at least one embodiment or example of the present disclosure.
  • the schematic expressions of the above terms may be directed to different embodiments or examples.
  • the specific features, structures, materials or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
  • those skilled in the art may combine and combine different embodiments or examples and features of different embodiments or examples described in this specification unless they are inconsistent with each other.
  • first and second are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of indicated technical features. Therefore, the characteristics defined as “first” and “second” can be expressed or implied including at least one of these features.
  • “plurality” means at least two, such as two, three, etc., unless otherwise expressly and specifically limited.

Abstract

一种旁路供热系统减温水调节阀超前控制方法及系统。方法包括模拟试验获取旁路供热系统减温水调节阀超前控制曲线；控制器根据旁路阀开度、设定的减温器后温度以及减温水调节阀超前控制曲线控制减温水调节阀开度。

Description

旁路供热系统减温水调节阀超前控制方法及系统
相关申请的交叉引用
本申请基于申请号为202210716654.9、申请日为2022年06月23日的中国专利申请提出，并要求该中国专利申请的优先权，该中国专利申请的全部内容在此引入本申请作为参考。
技术领域
本公开涉及发电技术领域，尤其涉及一种旁路供热系统减温水调节阀超前控制方法及系统。
背景技术
根据国家能源局“十四五”能源规划要求，风电、光伏等新能源电力装机容量将快速持续增长，为了提高电网对新能源的消纳能力，要求提高火电机组调峰能力，提升火电机组运行灵活性，提高新能源消纳能力。现已实施的火电机组灵活性改造使得机组具备深度调峰的能力，主要技术包括锅炉低负荷稳燃、低负荷脱硝、低压缸零出力、旁路供热等。其中旁路供热具有投资少、运行灵活，高热电解耦特性等优势，已经成为目前火力发电机组热电解耦改造的重要技术之一，在提升电厂供热能力和实现深度调峰方面发挥了重大作用。
发明内容
本公开旨在至少在一定程度上解决相关技术中的技术问题之一。
为此，本公开的实施例提出一种旁路供热系统减温水调节阀超前控制方法及系统。
本公开提出了一种高、低旁路供热系统减温水调节阀超前控制方法，包括以下步骤：模拟试验获取旁路供热系统减温水调节阀超前控制曲线；控制器根据旁路阀开度、设定的减温器后温度以及所述减温水调节阀超前控制曲线控制减温水调节阀开度。
在一些实施例中，所述旁路供热系统减温水调节阀超前控制曲线包括高旁路供热系统减温水调节阀超前控制曲线和低旁路供热系统减温水调节阀超前控制曲线。
在一些实施例中，所述控制器根据所述高旁路供热系统减温水调节阀超前控制曲线控制高旁阀供热系统的减温水调节阀开度，所述控制器根据所述低旁路供热系统减温水调节阀超前控制曲线控制低旁阀供热系统的减温水调节阀开度。
在一些实施例中，所述控制器包括温度设定模块，所述温度设定模块用于设定所述减温器后温度。
在一些实施例中，所述模拟试验获取旁路供热系统减温水调节阀超前控制曲线包括以下步骤：在减温器后温度设计值的上下限之间选取至少5个温度点值，在旁路阀最大阀门开度范围内选取至少5个阀门开度点值；投入旁路供热系统，使所述旁路供热系统稳定运行；调节所述旁路阀开度为某一所述阀门开度点值，依次设定所述减温器后温度为选取的所述温度点值，调节所述减温水调节阀开度直至所述高、低旁路供热系统稳定运行，记录各所述阀门开度点值与所述温度点值组合工况下的减温水调节阀开度数据；分析处理各工况下的所述减温水调节阀开度数据获得所述减温水调节阀超前控制曲线。
在一些实施例中，所述减温器后温度设计值根据机组安全运行范围确定。
在一些实施例中，所述旁路阀开度为一定值，设定的所述减温器后温度在两个相邻的所述温度点值之间时，根据相邻的所述温度点值以及所述相邻的温度点值在减温水调节阀超前控制曲线上对应的减温水调节阀的开度确定在旁路阀开度、设定的减温器后温度已知条件下的减温水调节阀的开度。
在一些实施例中，所述旁路供热系统稳定运行运行时间为20-60min。
在一些实施例中，低旁供热系统中减温器后温度设计值的上下限为260℃和240℃，并且在所述减温器后温度设计值的上下限之间选取5个温度点值，分别为260℃、255℃、250℃、245℃、240℃。
在一些实施例中，低旁供热系统中旁路阀最大阀门开度为90％，并且在所述旁路阀最大阀门开度范围内选取5个阀门开度点值，分别为10％、30％、50％、70％、90％。
在一些实施例中，高旁供热系统中减温器后温度设计值的上下限为290℃和270℃，并且在所述减温器后温度设计值的上下限之间选取5个温度点值，分别为290℃、285℃、280℃、275℃、270℃。
在一些实施例中，高旁供热系统中旁路阀最大阀门开度为50％，并且在所述旁路阀最大阀门开度范围内选取5个阀门开度点值，分别为5％、10％、15％、30％、50％。
本公开提出了一种旁路供热系统减温水调节阀超前控制系统，包括：减温器；
减温水调节阀，所述减温水调节阀设置在减温水流通管路上，用于调节减温水流量；旁路阀，所述旁路阀设置在所述减温器上游，用于调节旁路开度；控制器，所述控制器包括温度设定模块和控制模块，所述温度设定模块、所述减温水调节阀和所述旁路阀均与所述控制模块电连接。
在一些实施例中，旁路蒸汽经过所述减温器后在减温水的作用下温度降低。
本公开的控制器根据旁路阀开度、设定的减温器后温度以及所述减温水调节阀超前控制曲线控制减温水调节阀开度，避免了调整旁路阀开度时，减温器后温度变化延迟造成的减温 水调节阀响应滞后调节的情况以及减温器后温度波动造成的安全隐患，同时保障了高旁阀流量与低旁阀流量计算的准确性。
附图说明
本公开上述的和/或附加的方面和优点从下面结合附图对实施例的描述中将变得明显和容易理解，其中：
图1为典型的高低旁供热系统图；
图2为高(低)旁路系统简图；
图3为示例性的低旁路供热系统减温水调节阀超前控制曲线示意图；
图4为本公开的一个实施例的低旁路供热系统减温水调节阀超前控制曲线示意图；
图5为本公开的一个实施例的高旁路供热系统减温水调节阀超前控制曲线示意图；
图6为本公开控制系统的控制方式示意图。
具体实施方式
下面详细描述本公开的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，旨在用于解释本公开，而不能理解为对本公开的限制。
在相关技术中，旁路供热使得蒸汽进入高、中压缸原有的比例发生变化，偏移设计值，这会直接影响机组的轴向推力，轴向推力的超限会导致机组推力瓦温、轴向位移、高中压缸胀差超限，影响机组安全稳定运行，典型的高低旁供热系统图如图1所示。针对该问题，现有的解决方法为：按照质量平衡与能量平衡得到高旁阀流量与低旁阀流量，再根据计算得到的二者一一对应关系以及低旁阀流量来控制高旁阀开度。控制思路为，首先调整低旁阀开度，满足供热需求，然后当低旁阀开度达到“阈值”时，开启高旁阀，保持高中压转子轴向推力平衡，机组安全运行。
高(低)旁路系统简图如图2所示，F1+F2＝f3；F1·H1+F2·H2＝F3·H3；H1＝f(P1,T1)；H2＝f(P2,T2)；H3＝f(P3,T3)，其中，F1、P1、T1为减温器前旁路蒸汽的流量(t/h)、压力(MPa)、温度(℃)；F2、P2、T2为减温水的流量(t/h)、压力(MPa)、温度(℃)；F3、P3、T3为减温器后旁路蒸汽的流量(t/h)、压力(MPa)、温度(℃)；H1为减温器前旁路蒸汽的焓；H2为减温水的焓；H3为减温器后旁路蒸汽的焓。对于高旁或低旁：可实时测得F2、P1、P2、P3、T1、T2、T3，则根据上式可得F1、F3，再根据高、低旁路各自的F1之间的关系(根据热平衡图以及高中压转子轴向推力核算得到)，通过控制高旁阀调节高旁F1来匹配低旁F1， 使得高中压转子轴向推力处于安全范围内，保证机组安全稳定运行。
然而，当机组实际运行时，会出现以下问题：在调整高旁阀(低旁阀)开度时，减温水调节阀会相应动作以保证减温器后温度处于安全范围，T3的变化会有较为明显的延迟，这是由于减温器后温度变化的测量(温度测量元件：热电偶/热电阻)本身存在延迟，且减温器后混合均匀需要一定的时间。进一步的，由于T3的变化会有较为明显的延迟，减温水调节阀也会出现响应的滞后调节情况，导致减温水流量调节滞后，最终导致T3会出现时间较长、幅度较大的波动，这会严重影响减温加压器后蒸汽温度的控制，影响机组安全运行，并且影响高旁阀流量与低旁阀流量计算的准确性。
为此，本公开的实施例提出一种旁路供热系统减温水调节阀超前控制方法及系统。
下面参照附图描述根据本公开实施例提出的旁路供热系统减温水调节阀超前控制方法及系统。
本公开的旁路供热系统减温水调节阀超前控制方法，包括以下步骤：
模拟试验获取旁路供热系统减温水调节阀超前控制曲线；
控制器根据旁路阀开度、设定的减温器后温度以及减温水调节阀超前控制曲线控制减温水调节阀开度。
控制器包括温度设定模块，温度设定模块用于设定减温器后温度，旁路供热系统减温水调节阀超前控制曲线包括高旁路供热系统减温水调节阀超前控制曲线和低旁路供热系统减温水调节阀超前控制曲线，控制器根据高旁路供热系统减温水调节阀超前控制曲线控制高旁阀供热系统的减温水调节阀开度，控制器根据低旁路供热系统减温水调节阀超前控制曲线控制低旁阀供热系统的减温水调节阀开度。
模拟试验获取旁路供热系统减温水调节阀超前控制曲线包括以下步骤：
(1)在减温器后温度设计值的上下限之间选取至少5个温度点值，在旁路阀最大阀门开度范围内选取至少5个阀门开度点值；
(2)投入高、低旁路供热系统，使高、低旁路供热系统稳定运行；
(3)调节旁路阀开度为某一阀门开度点值，依次设定减温器后温度为选取的温度点值，调节减温水调节阀开度直至高、低旁路供热系统稳定运行，记录各阀门开度点值与温度点值组合工况下的减温水调节阀开度数据；
(4)分析处理各工况下的减温水调节阀开度数据获得减温水调节阀超前控制曲线。
减温器后温度设计值根据机组安全运行范围确定，最大阀门开度根据机组实际运行过程中的阀门开度确定，另外，可以理解的是，温度点值和阀门开度点值选取的越多，试验结果越可靠。高、低旁路供热系统稳定运行运行时间为20-60min。
在一些实施例中，调节旁路阀开度为某一阀门开度点值，依次设定减温器后温度为选取的温度点值，调节减温水调节阀开度直至高、低旁路供热系统稳定运行，记录各阀门开度点值与温度点值组合工况下的减温水调节阀开度数据。具体为，在减温器后温度设计值的上下限之间依次选取5个温度点值，该温度点值分别为T3a、T3b、T3c、T3d、T3e，其中，T3a为最大值、T3e为最小值；根据机组实际运行过程中最大阀门开度选取，在最大阀门开度范围内选取5个阀门开度点值，该阀门开度点值分别为Ka、Kb、Kc、Kd、Ke；投入高、低旁供热系统，稳定运行30min；调整旁路阀为各阀门开度点值，同时依次设定减温器后温度设定值，然后调整减温水调节阀开度直至系统稳定运行30min，记录最终的减温水调节阀开度(J)。
在本公开实施例中，各阀门开度点值与温度点值组合工况下的减温水调节阀开度数据记录表如表1所示。
表1：各阀门开度点值与温度点值组合工况下的减温水调节阀开度数据记录示例表。
分析处理根据表1所记录的数据得到旁路供热系统减温水调节阀超前控制曲线。
在本公开实施例中，低旁路供热系统减温水调节阀超前控制曲线如图3所示。旁路阀开度为一定值，设定的减温器后温度在两个相邻的温度点值之间时，根据相邻的温度点值以及相邻的温度点值在减温水调节阀超前控制曲线上对应的减温水调节阀的开度确定在旁路阀开度、设定的减温器后温度已知条件下的减温水调节阀的开度。例如，低旁阀开度为D时，可根据低旁供热系统减温水调节阀超前控制曲线以及设定的减温器阀后温度自动给予低旁减温水调节阀超前控制参数J，如设定温度T30处于相邻两个T3(以T3a对应Ja、T3b为例对应Jb)试验值之间，则可以采用以下方法确定J0：
同理，高旁阀开度为G时，可根据高旁供热系统减温水调节阀超前控制曲线以及设定的减温器阀后温度自动给予高旁减温水调节阀超前控制参数J。
在一些实施例中，低旁供热系统中减温器后温度设计值的上下限为260℃和240℃，在260℃和240℃之间选取5个温度点值，分别为260℃、255℃、250℃、245℃、240℃；低旁阀阀门开度最大值为90％，在低旁阀阀门开度90％范围内选取5个低旁阀阀门开度点值，分 别为10％、30％、50％、70％、90％；投入高、低旁供热系统，稳定运行30min；调整旁路阀为各阀门开度点值，同时依次设定减温器后温度设定值，然后调整减温水调节阀开度直至系统稳定运行30min，记录最终的减温水调节阀开度，如表2所示。
表2各低阀门开度点值与温度点值组合工况下的减温水调节阀开度数据记录表。
分析处理表2中的数据，得到低旁路供热系统减温水调节阀超前控制曲线，如图4所示。曲线1、曲线2、曲线3、曲线4、曲线5分别对应T3a＝260℃、T3b＝255℃、T3c＝250℃、T3d＝245℃、T3e＝240℃时的减温水调节阀超前控制曲线。举例说明，根据图4，低旁阀开度为50％时，根据设定的减温器阀后温度自动给予低旁减温水调节阀超前控制参数Jd，如设定的减温器阀后温度为Td处于T3a＝260℃和T3b＝255℃之间，则据此可得Jd。
在一些实施例中，高旁供热系统中减温器后温度设计值的上下限为290℃和270℃，在290℃和270℃之间选取5个温度点值，分别为290℃、285℃、280℃、275℃、270℃；高旁阀阀门开度最大值为50％，在高旁阀阀门开度50％范围内选取5个高旁阀阀门开度点值，分别为5％、10％、15％、30％、50％；投入高、低旁供热系统，稳定运行30min；调整旁路阀为各阀门开度点值，同时依次设定减温器后温度设定值，然后调整减温水调节阀开度直至系统稳定运行30min，记录最终的减温水调节阀开度，如表3所示。
表3各高阀门开度点值与温度点值组合工况下的减温水调节阀开度数据记录表。
分析处理表3中的数据，得到高旁路供热系统减温水调节阀超前控制曲线，如图5所示。曲线6、曲线7、曲线8、曲线9、曲线10分别对应T31＝290℃、T32＝285℃、T33＝280℃、T34＝275℃、T35＝270℃时的减温水调节阀超前控制曲线。举例说明，根据图5，高旁阀开度为30％时，根据设定的减温器阀后温度自动给予高旁减温水调节阀超前控制参数Jg，如设定的减温器阀后温度为Tg处于T31＝290℃和T32＝285℃之间，则据此可得Jg。
高、低旁路供热系统减温水调节阀超前控制系统包括减温水调节阀、旁路阀、减温器和控制器。减温水调节阀设置在减温水流通管路上，减温水用于调节减温水流量；旁路阀设置在减温器上游，用于调节旁路开度；旁路蒸汽经过减温器后在减温水的作用下温度降低；控制器包括温度设定模块和控制模块，温度设定模块、减温水调节阀和旁路阀均与控制模块电连接。如图6所示，在控制过程中，控制器的控制模块获取旁路阀开度和温度设定模块设定的减温器后温度，根据减温水调节阀超前控制曲线控制减温水调节阀的开度，避免了减温器后温度波动造成的安全隐患，同时保障了高旁阀流量与低旁阀流量计算的准确性。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本公开的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述可以针对不同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含 地包括至少一个该特征。在本公开的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
尽管已经示出和描述了本公开的实施例，本领域的普通技术人员可以理解：在不脱离本公开的原理和宗旨的情况下可以对这些实施例进行多种变化、修改、替换和变型，本公开的范围由权利要求及其等同物限定。

Claims (14)

  1. 一种旁路供热系统减温水调节阀超前控制方法，包括：
    模拟试验获取旁路供热系统减温水调节阀超前控制曲线；
    控制器根据旁路阀开度、设定的减温器后温度以及所述减温水调节阀超前控制曲线控制减温水调节阀开度。
  2. 如权利要求1所述的方法，其中，所述旁路供热系统减温水调节阀超前控制曲线包括高旁路供热系统减温水调节阀超前控制曲线和低旁路供热系统减温水调节阀超前控制曲线。
  3. 如权利要求2所述的方法，其中，所述控制器根据所述高旁路供热系统减温水调节阀超前控制曲线控制高旁阀供热系统的减温水调节阀开度，所述控制器根据所述低旁路供热系统减温水调节阀超前控制曲线控制低旁阀供热系统的减温水调节阀开度。
  4. 如权利要求1所述的方法，其中，所述控制器包括温度设定模块，所述温度设定模块用于设定所述减温器后温度。
  5. 如权利要求1所述的方法，其中，所述模拟试验获取旁路供热系统减温水调节阀超前控制曲线包括以下步骤：
    在减温器后温度设计值的上下限之间选取至少5个温度点值，在旁路阀最大阀门开度范围内选取至少5个阀门开度点值；
    投入所述旁路供热系统，使所述旁路供热系统稳定运行；
    调节所述旁路阀开度为某一所述阀门开度点值，依次设定所述减温器后温度为选取的所述温度点值，调节所述减温水调节阀开度直至所述高、低旁路供热系统稳定运行，记录各所述阀门开度点值与所述温度点值组合工况下的减温水调节阀开度数据；
    分析处理各工况下的所述减温水调节阀开度数据获得所述减温水调节阀超前控制曲线。
  6. 如权利要求5所述的方法，其中，所述减温器后温度设计值根据机组安全运行范围确定。
  7. 如权利要求5所述的方法，其中，所述旁路阀开度为一定值，响应于设定的所述减温器后温度在两个相邻的所述温度点值之间，根据相邻的所述温度点值以及所述相邻的温度点值在减温水调节阀超前控制曲线上对应的减温水调节阀的开度确定在旁路阀开度、设定的减温器后温度已知条件下的减温水调节阀的开度。
  8. 如权利要求5所述的方法，其中，所述旁路供热系统稳定运行的运行时间为20-60min。
  9. 如权利要求5所述的方法，其中，低旁供热系统中减温器后温度设计值的上下限为260℃和240℃，并且在所述减温器后温度设计值的上下限之间选取5个温度点值，分别为 260℃、255℃、250℃、245℃、240℃。
  10. 如权利要求5所述的方法，其中，低旁供热系统中旁路阀最大阀门开度为90％，并且在所述旁路阀最大阀门开度范围内选取5个阀门开度点值，分别为10％、30％、50％、70％、90％。
  11. 如权利要求5所述的方法，其中，高旁供热系统中减温器后温度设计值的上下限为290℃和270℃，并且在所述减温器后温度设计值的上下限之间选取5个温度点值，分别为290℃、285℃、280℃、275℃、270℃。
  12. 如权利要求5所述的方法，其中，高旁供热系统中旁路阀最大阀门开度为50％，并且在所述旁路阀最大阀门开度范围内选取5个阀门开度点值，分别为5％、10％、15％、30％、50％。
  13. 一种旁路供热系统减温水调节阀超前控制系统，其中，用于实施如权利要求1-12中任一项所述的方法，包括：
    减温器；
    减温水调节阀，所述减温水调节阀设置在减温水流通管路上，用于调节减温水流量；
    旁路阀，所述旁路阀设置在所述减温器上游，用于调节旁路开度；
    控制器，所述控制器包括温度设定模块和控制模块，所述温度设定模块、所述减温水调节阀和所述旁路阀均与所述控制模块电连接。
  14. 如权利要求13所述的系统，其中，旁路蒸汽经过所述减温器后在减温水的作用下温度降低。
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CN115097730A (zh) * 2022-06-23 2022-09-23 西安热工研究院有限公司 高、低旁路供热系统减温水调节阀超前控制方法及系统

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030024248A1 (en) * 2001-07-31 2003-02-06 Stefan Klatt Method for controlling a low-pressure bypass system
CN111123770A (zh) * 2019-12-13 2020-05-08 山东中实易通集团有限公司 一种fcb工况下旁路模型开度确定方法及装置
CN111502787A (zh) * 2020-05-07 2020-08-07 西安西热节能技术有限公司 一种用于高、低旁联合供热机组中高旁阀实现自动控制的方法
CN111535879A (zh) * 2020-05-09 2020-08-14 国电南京电力试验研究有限公司 一种燃气-蒸汽联合循环机组旁路系统控制方法
CN111853906A (zh) * 2020-08-11 2020-10-30 西安热工研究院有限公司 一种火电机组供热高低压旁路阀自动调节方法及系统
CN113027550A (zh) * 2021-03-22 2021-06-25 西安热工研究院有限公司 一种满足调峰需求的高低压旁路系统及动态寻优控制方法
CN115097730A (zh) * 2022-06-23 2022-09-23 西安热工研究院有限公司 高、低旁路供热系统减温水调节阀超前控制方法及系统

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030024248A1 (en) * 2001-07-31 2003-02-06 Stefan Klatt Method for controlling a low-pressure bypass system
CN111123770A (zh) * 2019-12-13 2020-05-08 山东中实易通集团有限公司 一种fcb工况下旁路模型开度确定方法及装置
CN111502787A (zh) * 2020-05-07 2020-08-07 西安西热节能技术有限公司 一种用于高、低旁联合供热机组中高旁阀实现自动控制的方法
CN111535879A (zh) * 2020-05-09 2020-08-14 国电南京电力试验研究有限公司 一种燃气-蒸汽联合循环机组旁路系统控制方法
CN111853906A (zh) * 2020-08-11 2020-10-30 西安热工研究院有限公司 一种火电机组供热高低压旁路阀自动调节方法及系统
CN113027550A (zh) * 2021-03-22 2021-06-25 西安热工研究院有限公司 一种满足调峰需求的高低压旁路系统及动态寻优控制方法
CN115097730A (zh) * 2022-06-23 2022-09-23 西安热工研究院有限公司 高、低旁路供热系统减温水调节阀超前控制方法及系统

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