A quick cut blind plate valve control method and system

Abstract

The application relates to the field of blind plate valves, and discloses a quick-cut blind plate valve control method and system. The method comprises the following steps: acquiring real-time pressure monitoring data of the inlet side and the outlet side of a quick-cut blind plate valve in a pipeline system; calculating a pressure difference value between the inlet side and the outlet side of the quick-cut blind plate valve and obtaining a pressure difference change rate; obtaining a working condition type of the current pipeline system according to the numerical value of the pressure difference value and the positive and negative directions of the pressure difference change rate; generating a corresponding working condition identification signal based on the identified working condition type; generating a driving force control parameter suitable for the current working condition based on the working condition identification signal; and controlling a hydraulic driving system according to the driving force control parameter to drive the quick-cut blind plate valve to perform an opening or closing action. Through the technical scheme, the hydraulic driving system of the quick-cut blind plate valve can be controlled with adaptive control parameters under different working conditions.

Description

A quick-cut blind valve control method and system Technical Field

[0001] This application relates to the field of quick-cut blind valves, and more particularly to a control method and system for quick-cut blind valves. Background Technology

[0002] Hydraulic quick-cut blind valves are important pipeline control devices installed in pipeline lines to control the flow of fluid.

[0003] During operation, when the valve needs to be closed, the hydraulic system supplies pressurized oil to the drive unit, which moves the valve plate into the flow channel until the flow channel is completely cut off. When the valve needs to be opened, the hydraulic system controls the direction and flow rate of the pressurized oil to move the valve plate in the opposite direction, thereby opening the flow channel.

[0004] The working load of a hydraulic blind valve mainly comes from the fluid pressure in the pipeline system. When the pressure of the medium in the pipeline increases, the fluid thrust on the valve plate increases, requiring a greater driving force to close the valve. When the pressure of the medium in the pipeline decreases, the fluid thrust on the valve plate decreases, and the required driving force also decreases accordingly. Currently, the control system of hydraulic blind valves mainly adopts a fixed parameter control method, that is, the control parameters are set based on experience and remain unchanged throughout the entire operation, making it impossible to adjust the control strategy according to these changes in operating conditions.

[0005] Solving this technical problem is a technical challenge that needs to be overcome by those skilled in the art. Summary of the Invention

[0006] This application provides a quick-cut blind valve control method to at least partially solve the above-mentioned technical problems.

[0007] To achieve the above objectives, according to a first aspect of this application, a method for controlling a quick-cut blind valve is provided, comprising:

[0008] Acquire real-time pressure monitoring data at the inlet and outlet sides of quick-cut blind valves in the pipeline system;

[0009] Calculate the pressure difference between the inlet and outlet sides of the quick-cut blind valve and obtain the rate of change of pressure difference;

[0010] The current operating condition type of the pipeline system is obtained based on the magnitude of the differential pressure value and the positive or negative direction of the differential pressure change rate; a corresponding operating condition identification signal is generated based on the identified operating condition type.

[0011] Based on the operating condition identification signal, drive force control parameters adapted to the current operating condition are generated;

[0012] The hydraulic drive system is controlled according to the driving force control parameters to drive the quick-cut blind valve to perform opening or closing actions.

[0013] Optionally, the current operating condition type of the pipeline system is obtained based on the magnitude of the differential pressure value and the positive or negative direction of the differential pressure change rate, including:

[0014] The system includes preset thresholds for high and low differential pressure levels to define operating ranges, as well as a pressure boosting rate threshold to characterize the severity of differential pressure changes.

[0015] When the current value of the differential pressure is greater than the high threshold value of the differential pressure, the operating condition is determined to be a predetermined high-pressure operating condition.

[0016] When the current value of the differential pressure is between the low differential pressure threshold and the high differential pressure threshold and the rate of change of the differential pressure is greater than the pressure increase rate threshold, the operating condition is determined to be a trend-based high pressure warning operating condition.

[0017] When the current value of the differential pressure is between the low differential pressure threshold and the high differential pressure threshold and the rate of change of the differential pressure is not greater than the pressurization rate threshold, the operating condition is determined to be a stable and normal operating condition.

[0018] When the current value of the differential pressure is less than the low threshold of the differential pressure, the operating condition is determined to be a stable low-pressure operating condition.

[0019] The established high-voltage operating conditions and trend-based high-voltage early warning operating conditions are uniformly identified as high-voltage operating condition types;

[0020] The stable and normal operating condition is identified as a normal operating condition type;

[0021] The stable low-pressure operating condition is identified as a low-pressure operating condition type;

[0022] Based on the identified high-voltage operating condition type, normal operating condition type, or low-voltage operating condition type, a corresponding operating condition identification signal is generated.

[0023] Optionally, when the operating condition type is a high-pressure operating condition, the step of generating driving force control parameters adapted to the current operating condition includes:

[0024] Obtain the currently set output power of the hydraulic drive system;

[0025] The target performance parameter value is obtained by a lookup table algorithm based on the current value of the differential pressure and the rate of change of the differential pressure; the target performance parameter value is positively correlated with the differential pressure and the rate of change of the differential pressure.

[0026] Calculate the deviation between the target performance parameter value and the currently set output power of the hydraulic system, and generate a deviation signal;

[0027] The deviation signal is input into the PID controller to obtain the feedback adjustment amount used to correct the output power of the hydraulic system;

[0028] Calculate the power feedforward compensation amount based on the amplitude of the real-time differential pressure value;

[0029] The feedback adjustment amount and the power feedforward compensation amount are superimposed, and the superposition result is subjected to amplitude limiting processing to generate the driving force control parameters.

[0030] Optionally, the power feedforward compensation is calculated based on the amplitude of the real-time differential pressure value, including:

[0031] A preset power feedforward compensation mapping table is provided, which corresponds to the range of differential pressure values. The mapping table divides the differential pressure values ​​into multiple segmented ranges and configures a corresponding power feedforward compensation increment coefficient for each segmented range.

[0032] Input the current value of the pressure difference into the mapping table, and calculate the power feedforward compensation increment coefficient corresponding to the current pressure difference value;

[0033] The target power feedforward compensation amount is obtained by multiplying the power feedforward compensation increment coefficient with the currently set output power of the hydraulic drive system.

[0034] Optionally, the method further includes:

[0035] After completing the action of the quick-cut blind valve, record the performance indicators during this action. The performance indicators include: the actual response time of the valve plate reaching the target position and the peak output power of the hydraulic drive system during the entire action.

[0036] The performance indicators are compared with preset performance benchmarks to calculate the control effectiveness score for this action.

[0037] When the control performance score is lower than a preset threshold, it is determined that there is a deviation in the power feedforward compensation increment coefficient of the corresponding differential pressure amplitude range in the current mapping table.

[0038] Based on the direction of the deviation between the actual response time and the ideal response time and the degree of overshoot of the peak output power, the incremental coefficient corresponding to the differential pressure amplitude range in the mapping table is adjusted; if the actual response time exceeds the ideal response time and the peak output power does not reach the upper limit, the incremental coefficient of the power feedforward compensation in the corresponding segment range is increased; if the peak output power exceeds the safety limit, the incremental coefficient of the power feedforward compensation in the corresponding segment range is decreased.

[0039] Update the power feedforward compensation increment coefficient to the power feedforward compensation mapping table.

[0040] Optionally, when the operating condition type is a low-pressure operating condition, drive force control parameters adapted to the current operating condition are generated, including:

[0041] The target performance parameter value is obtained based on the current value of the differential pressure using a table lookup algorithm; wherein, the target performance parameter value is inversely correlated with the magnitude of the differential pressure and is not affected by the rate of change of the differential pressure;

[0042] Calculate the deviation between the target performance parameter value and the currently set output power of the hydraulic system, and generate a deviation signal;

[0043] The deviation signal is input into the PID controller to obtain the feedback adjustment amount used to correct the output power of the hydraulic system;

[0044] The power feedforward compensation is calculated based on the amplitude of the real-time differential pressure value, wherein the power feedforward compensation is negative or zero, and is used to reduce the output power of the hydraulic system.

[0045] The feedback adjustment amount and the power feedforward compensation amount are superimposed, and the superposition result is subjected to amplitude limiting processing. The output power of the hydraulic system is not lower than the preset minimum safety threshold, thereby generating the driving force control parameters.

[0046] Optionally, before inputting the deviation signal into the PID controller, the method further includes:

[0047] Based on the currently identified operating condition type, the corresponding PID control parameters are retrieved. The PID control parameters for the corresponding high-voltage operating condition type are configured such that the proportional gain coefficient is greater than that in the PID control parameters for the corresponding normal operating condition type, and the integral time constant is less than that in the PID control parameters for the corresponding normal operating condition type, in order to improve response speed and suppress overshoot. The PID control parameters for the corresponding low-voltage operating condition type are configured such that the proportional gain coefficient is less than that in the PID control parameters for the corresponding normal operating condition type, and the integral time constant is greater than that in the PID control parameters for the corresponding normal operating condition type, in order to reduce power fluctuations.

[0048] The retrieved PID control parameters are loaded into the PID controller.

[0049] According to a second aspect of this application, a quick-cut blind valve control system is provided, comprising:

[0050] The first processing module is used to: acquire real-time pressure monitoring data on the inlet and outlet sides of the quick-cut blind valve in the pipeline system;

[0051] The second processing module is used to: calculate the pressure difference between the inlet and outlet sides of the quick-cut blind valve and obtain the pressure difference change rate;

[0052] The third processing module is used to: obtain the current operating condition type of the pipeline system based on the magnitude of the differential pressure value and the positive or negative direction of the differential pressure change rate; and generate a corresponding operating condition identification signal based on the identified operating condition type.

[0053] The fourth processing module is used to: generate driving force control parameters adapted to the current working condition based on the working condition identification signal;

[0054] The fifth processing module is used to: control the hydraulic drive system according to the driving force control parameters, and drive the quick-cut blind valve to perform opening or closing actions.

[0055] In summary, the embodiments of this application, through the above technical solutions, control the valve control device according to the driving parameters under different working conditions, thereby realizing the intelligent control of pipeline hydraulics.

[0056] Other features and advantages of this application will be described in detail in the following detailed description section. Attached Figure Description

[0057] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0058] Figure 1 is a flowchart of a quick-cut blind valve control method provided in an exemplary embodiment of this application;

[0059] Figure 2 is a system schematic diagram of a quick-cut blind valve control system provided in an exemplary embodiment of this application;

[0060] Explanation of reference numerals in the attached drawings: 201, first processing module; 202, second processing module; 203, third processing module; 204, fourth processing module; 205, fifth processing module. Detailed Implementation

[0061] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the protection scope of this application.

[0062] This application provides a quick-cut blind valve control method. Referring to Figure 1, the quick-cut blind valve control method provided in this embodiment includes the following steps:

[0063] Step 101: Obtain real-time pressure monitoring data from the inlet and outlet sides of the quick-cut blind valve in the pipeline system.

[0064] Specifically, a quick-opening blind flange valve is a valve used to quickly cut off or isolate the flow of media in a pipeline system. It features a blind flange structure, enabling rapid opening and closing. A sensor array, composed of multiple pressure and flow sensors, is used to collect pressure values ​​at different locations within the pipeline system in real time, generating a raw monitoring dataset. Based on this raw monitoring dataset, data preprocessing is performed, employing filtering algorithms to remove noise interference from the pressure and flow velocity data, resulting in processed pressure and flow velocity data sequences. The filtering algorithm can be a Kalman filter or a moving average filter, used to eliminate random and system noise generated during sensor measurements.

[0065] Step 102: Calculate the pressure difference between the inlet and outlet sides of the quick-cut blind valve and obtain the pressure difference change rate.

[0066] Specifically, the differential pressure change rate refers to the rate at which the pressure difference between the inlet and outlet sides of the quick-cut blind valve changes over time.

[0067] Step 103: Obtain the current operating condition type of the pipeline system based on the magnitude of the differential pressure value and the positive or negative direction of the differential pressure change rate; generate a corresponding operating condition identification signal based on the identified operating condition type.

[0068] Step 104: Generate driving force control parameters adapted to the current working condition based on the working condition identification signal.

[0069] Step 105: Control the hydraulic drive system according to the driving force control parameters to drive the quick-cut blind valve to perform opening or closing actions.

[0070] Specifically, by monitoring the pressure data at the inlet and outlet sides of the quick-cut blind valve in the pipeline system in real time, calculating the differential pressure value and differential pressure change rate, the current operating condition type of the pipeline system is identified. Based on different operating condition types, corresponding operating condition identification signals are generated. Based on the operating condition identification signals, the driving force control parameters are adjusted. The hydraulic drive system controls the opening or closing action of the quick-cut blind valve according to the driving force control parameters. This enables the quick-cut blind valve to control the hydraulic drive system with appropriate control parameters under different operating conditions, effectively reducing the pressure loss and energy consumption of the pipeline system.

[0071] In some embodiments, the current operating condition type of the pipeline system is determined based on the magnitude of the differential pressure value and the positive or negative direction of the differential pressure change rate, including:

[0072] The system includes preset thresholds for high and low differential pressure levels to define operating ranges, as well as a pressure boosting rate threshold to characterize the severity of differential pressure changes.

[0073] When the current value of the differential pressure is greater than the high threshold value of the differential pressure, the operating condition is determined to be a predetermined high-pressure operating condition.

[0074] When the current value of the differential pressure is between the low differential pressure threshold and the high differential pressure threshold and the rate of change of the differential pressure is greater than the pressure increase rate threshold, the operating condition is determined to be a trend-based high pressure warning operating condition.

[0075] When the current value of the differential pressure is between the low differential pressure threshold and the high differential pressure threshold and the rate of change of the differential pressure is not greater than the pressurization rate threshold, the operating condition is determined to be a stable and normal operating condition.

[0076] When the current value of the differential pressure is less than the low threshold of the differential pressure, the operating condition is determined to be a stable low-pressure operating condition.

[0077] The established high-voltage operating conditions and trend-based high-voltage early warning operating conditions are uniformly identified as high-voltage operating condition types;

[0078] The stable and normal operating condition is identified as a normal operating condition type;

[0079] The stable low-pressure operating condition is identified as a low-pressure operating condition type;

[0080] Based on the identified high-voltage operating condition type, normal operating condition type, or low-voltage operating condition type, a corresponding operating condition identification signal is generated.

[0081] Specifically, the high differential pressure threshold is a pre-set upper limit standard for differential pressure value, used to define whether the pipeline system has entered a high-pressure state; the low differential pressure threshold is a pre-set lower limit standard for differential pressure value, used to define whether the pipeline system is in a low-pressure state; the pressure increase rate threshold is a pre-set critical value characterizing the degree of drastic change in differential pressure, used to determine whether the pipeline pressure is rising rapidly; the predetermined high-pressure condition is the operating state where the current differential pressure value of the pipeline system directly exceeds the high differential pressure threshold; the trend-based high-pressure warning condition refers to the state where the differential pressure value is in the normal range, but the rate of change of differential pressure exceeds the pressure increase rate threshold, indicating that the pressure is about to enter the high-pressure range; the stable normal condition refers to the operating state where the differential pressure value is in the normal range and the rate of change of differential pressure is stable.

[0082] Under high-pressure conditions, power enhancement ensures the reliability and timeliness of valve operation; under normal conditions, power maintenance ensures system stability; and under low-pressure conditions, energy-saving strategies reduce energy consumption. This avoids the problems of unsafe high-pressure operation and energy-inefficient low-pressure operation caused by single power control, improves the accuracy of quick-cut blind valve control, and extends the service life of hydraulic drive system and valve.

[0083] In some embodiments, when the operating condition type is a high-voltage operating condition type, the step of generating driving force control parameters adapted to the current operating condition includes:

[0084] Obtain the currently set output power of the hydraulic drive system;

[0085] The target performance parameter value is obtained by a lookup table algorithm based on the current value of the differential pressure and the rate of change of the differential pressure; the target performance parameter value is positively correlated with the differential pressure and the rate of change of the differential pressure.

[0086] Calculate the deviation between the target performance parameter value and the currently set output power of the hydraulic system, and generate a deviation signal;

[0087] The deviation signal is input into the PID controller to obtain the feedback adjustment amount used to correct the output power of the hydraulic system;

[0088] Calculate the power feedforward compensation amount based on the amplitude of the real-time differential pressure value;

[0089] The feedback adjustment amount and the power feedforward compensation amount are superimposed, and the superposition result is subjected to amplitude limiting processing to generate the driving force control parameters.

[0090] Specifically, the lookup table algorithm is a parameter matching algorithm based on a pre-set mapping table. It pre-stores the differential pressure value, differential pressure change rate, and corresponding target performance parameter values ​​as a mapping relationship. During runtime, the target performance parameter value is directly obtained by querying the mapping table. The target performance parameter value is the ideal output power reference value of the hydraulic drive system. Under high-pressure conditions, its magnitude is positively correlated with the differential pressure value and differential pressure change rate. The deviation signal is the difference between the target performance parameter value and the currently set output power of the hydraulic drive system. The PID controller, short for proportional-integral-derivative controller, performs proportional, integral, and derivative operations on the deviation signal to output a feedback adjustment, thereby correcting the system output. The feedback adjustment is the power correction value calculated by the PID controller based on the deviation signal, used to compensate for the deviation between the current output power and the target value. The power feedforward compensation is a power compensation amount pre-calculated based on the amplitude of the real-time differential pressure value. It is used to predict the impact of pressure changes on valve action under high-pressure conditions, adjust the power output in advance, and avoid control deviations caused by lag.

[0091] Amplitude limiting is a method of limiting the amplitude of the superposition result of feedback adjustment and power feedforward compensation to ensure that the final generated driving force control parameters do not exceed the safe operating range of the hydraulic drive system and avoid overload damage to the equipment.

[0092] By using a lookup table algorithm to quickly match target performance parameter values ​​that are positively correlated with differential pressure and differential pressure change rate, and by using feedforward compensation to anticipate power demand fluctuations caused by pressure changes, the lag defect of single feedback control is compensated for, effectively avoiding slow valve action due to insufficient power or energy waste and equipment impact due to excessive power under high pressure conditions.

[0093] In some embodiments, calculating the power feedforward compensation based on the magnitude of the real-time differential pressure includes:

[0094] A preset power feedforward compensation mapping table is provided, which corresponds to the range of differential pressure values. The mapping table divides the differential pressure values ​​into multiple segmented ranges and configures a corresponding power feedforward compensation increment coefficient for each segmented range.

[0095] Input the current value of the pressure difference into the mapping table, and calculate the power feedforward compensation increment coefficient corresponding to the current pressure difference value;

[0096] The target power feedforward compensation amount is obtained by multiplying the power feedforward compensation increment coefficient with the currently set output power of the hydraulic drive system.

[0097] Specifically, the differential pressure amplitude range is a series of continuous numerical ranges divided according to the magnitude of the differential pressure between the inlet and outlet sides of the quick-cut blind valve, used to distinguish the magnitudes of different pressure differences; the power feedforward compensation mapping table is a pre-set table that stores the correlation between differential pressure amplitude ranges and corresponding power feedforward compensation increment coefficients, facilitating quick lookup and matching; the power feedforward compensation increment coefficient is a proportional coefficient set for each segmented interval, reflecting the intensity of the power compensation demand for differential pressure within that interval; the target power feedforward compensation amount is the finally determined feedforward compensation power value, obtained by multiplying the power feedforward compensation increment coefficient by the current output power of the hydraulic drive system, used to compensate for the impact of pressure changes on valve operation in advance.

[0098] By using a pre-defined mapping table of differential pressure amplitude segments and incremental coefficients, the corresponding compensation intensity is matched according to the real-time differential pressure value, thus avoiding the inadequacy of a single compensation strategy for different pressure scenarios. The target compensation amount is calculated based on the product of the current output power and the incremental coefficient, so that the feedforward compensation amount is positively correlated with both the actual intensity of the differential pressure and the current power level of the system, thus avoiding the compensation amount from being out of touch with actual needs.

[0099] In some embodiments, the method further includes:

[0100] After completing the action of the quick-cut blind valve, record the performance indicators during this action. The performance indicators include: the actual response time of the valve plate reaching the target position and the peak output power of the hydraulic drive system during the entire action.

[0101] The performance indicators are compared with preset performance benchmarks to calculate the control effectiveness score for this action.

[0102] When the control performance score is lower than a preset threshold, it is determined that there is a deviation in the power feedforward compensation increment coefficient of the corresponding differential pressure amplitude range in the current mapping table.

[0103] Based on the direction of the deviation between the actual response time and the ideal response time and the degree of overshoot of the peak output power, the incremental coefficient corresponding to the differential pressure amplitude range in the mapping table is adjusted; if the actual response time exceeds the ideal response time and the peak output power does not reach the upper limit, the incremental coefficient of the power feedforward compensation in the corresponding segment range is increased; if the peak output power exceeds the safety limit, the incremental coefficient of the power feedforward compensation in the corresponding segment range is decreased.

[0104] Update the power feedforward compensation increment coefficient to the power feedforward compensation mapping table.

[0105] Specifically, the actual response time of the valve plate reaching the target position can be understood as the actual time elapsed from the issuance of the control command to the valve plate fully reaching the open or closed target position; the peak output power is the maximum output power of the hydraulic drive system during the entire operation; the performance benchmark can be understood as a pre-set standard value used to evaluate the effect of the action, including the ideal response time and the safety limit of the peak power. The control performance score is a quantitative score calculated based on the comparison between the actual performance indicators and the performance benchmark, reflecting the control quality of this action, such as whether the response speed meets the standard and whether the power is reasonable. The overshoot of the peak output power can be understood as the extent to which the actual peak output power exceeds the preset safety limit, reflecting the stability of the power control; the greater the overshoot, the higher the risk of equipment overload.

[0106] In some embodiments, when the operating condition type is a low-pressure operating condition type, driving force control parameters adapted to the current operating condition are generated, including:

[0107] The target performance parameter value is obtained based on the current value of the differential pressure using a table lookup algorithm; wherein, the target performance parameter value is inversely correlated with the magnitude of the differential pressure and is not affected by the rate of change of the differential pressure;

[0108] Calculate the deviation between the target performance parameter value and the currently set output power of the hydraulic system, and generate a deviation signal;

[0109] The deviation signal is input into the PID controller to obtain the feedback adjustment amount used to correct the output power of the hydraulic system;

[0110] The power feedforward compensation is calculated based on the amplitude of the real-time differential pressure value, wherein the power feedforward compensation is negative or zero, and is used to reduce the output power of the hydraulic system.

[0111] The feedback adjustment amount and the power feedforward compensation amount are superimposed, and the superposition result is subjected to amplitude limiting processing. The output power of the hydraulic system is not lower than the preset minimum safety threshold, thereby generating the driving force control parameters.

[0112] In some embodiments, the method further includes, before inputting the deviation signal to the PID controller:

[0113] Based on the currently identified operating condition type, the corresponding PID control parameters are retrieved. The PID control parameters for the corresponding high-voltage operating condition type are configured such that the proportional gain coefficient is greater than that in the PID control parameters for the corresponding normal operating condition type, and the integral time constant is less than that in the PID control parameters for the corresponding normal operating condition type, in order to improve response speed and suppress overshoot. The PID control parameters for the corresponding low-voltage operating condition type are configured such that the proportional gain coefficient is less than that in the PID control parameters for the corresponding normal operating condition type, and the integral time constant is greater than that in the PID control parameters for the corresponding normal operating condition type, in order to reduce power fluctuations.

[0114] The retrieved PID control parameters are loaded into the PID controller.

[0115] Specifically, the system retrieves the corresponding PID control parameters from the preset parameter library based on the currently identified operating condition type. For high-voltage conditions, the PID parameters are configured with a high proportional gain coefficient and a low integral time constant. The proportional gain is greater than that of the normal operating condition to enhance the rapid response to deviations, and the integral time is less than that of the normal operating condition to suppress overshoot. For low-voltage conditions, the PID parameters are configured with a low proportional gain coefficient and a high integral time constant. The proportional gain is less than that of the normal operating condition to slow down the adjustment speed and avoid drastic power fluctuations, and the integral time is greater than that of the normal operating condition to ensure smooth adjustment.

[0116] By matching differentiated PID control parameters to different operating conditions, under high-pressure conditions, the high proportional gain and low integral time can respond quickly to deviations and suppress overshoot, avoiding the risk of slow valve action or sudden power increase caused by adjustment lag, and ensuring the timeliness and safety of control in high-pressure scenarios. Under low-pressure conditions, the configuration of low proportional gain and high integral time slows down the adjustment speed, reduces power fluctuations, avoids increased energy consumption or unstable operation caused by frequent adjustments during energy saving, and ensures stable operation in low-pressure scenarios.

[0117] Referring to Figure 2, a second embodiment of the present invention provides a quick-cut blind valve control system, comprising:

[0118] The first processing module 201 is used to: acquire real-time pressure monitoring data of the inlet and outlet sides of the quick-cut blind valve in the pipeline system;

[0119] The second processing module 202 is used to: calculate the pressure difference between the inlet side and the outlet side of the quick-cut blind valve and obtain the pressure difference change rate;

[0120] The third processing module 203 is used to: obtain the current operating condition type of the pipeline system based on the magnitude of the differential pressure value and the positive or negative direction of the differential pressure change rate; and generate a corresponding operating condition identification signal based on the identified operating condition type.

[0121] The fourth processing module 204 is used to: generate driving force control parameters adapted to the current working condition based on the working condition identification signal;

[0122] The fifth processing module 205 is used to: control the hydraulic drive system according to the driving force control parameters, and drive the quick-cut blind valve to perform opening or closing actions.

[0123] It should be noted that the quick-cut blind valve control system provided in this embodiment of the invention is used to execute all the process steps of the quick-cut blind valve control method in the above embodiment. The working principle and beneficial effects of the two are one-to-one, so they will not be described again.

[0124] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0125] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0126] The embodiments, implementation methods, and related technical features of this application can be combined and substituted for each other without conflict.

[0127] The above are merely preferred embodiments of this application and are not intended to limit this application in any way. Any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of this application without departing from the scope of the technical solution of this application shall still fall within the scope of the technical solution of this application.

Claims

1. A method for controlling a quick-cut blind valve, characterized in that, include: Acquire real-time pressure monitoring data at the inlet and outlet sides of quick-cut blind valves in the pipeline system; Calculate the pressure difference between the inlet and outlet sides of the quick-cut blind valve and obtain the pressure difference change rate; determine the current operating condition type of the pipeline system based on the magnitude of the pressure difference and the positive or negative direction of the pressure difference change rate; generate a corresponding operating condition identification signal based on the identified operating condition type; generate driving force control parameters adapted to the current operating condition based on the operating condition identification signal; control the hydraulic drive system according to the driving force control parameters to drive the quick-cut blind valve to perform opening or closing actions; the current operating condition type of the pipeline system is determined based on the magnitude of the pressure difference and the positive or negative direction of the pressure difference change rate, including: pre- Define a high-pressure differential threshold and a low-pressure differential threshold to define the operating condition range, and a boosting rate threshold to characterize the drastic change in pressure differential. When the current value of the pressure differential is greater than the high-pressure differential threshold, the operating condition is determined to be a predetermined high-pressure operating condition. When the current value of the pressure differential is between the low-pressure differential threshold and the high-pressure differential threshold, and the rate of change of the pressure differential is greater than the boosting rate threshold, the operating condition is determined to be a trend-based high-pressure warning operating condition. When the current value of the pressure differential is between the low-pressure differential threshold and the high-pressure differential threshold, and the rate of change of the pressure differential is not greater than the boosting rate threshold... The operating condition is determined to be a stable normal operating condition; when the current value of the differential pressure is less than the low-level threshold of the differential pressure, the operating condition is determined to be a stable low-pressure operating condition; the established high-pressure operating condition and the trend-based high-pressure warning operating condition are uniformly identified as high-pressure operating condition types; the stable normal operating condition is identified as a normal operating condition type; the stable low-pressure operating condition is identified as a low-pressure operating condition type; based on the identified high-pressure operating condition type, normal operating condition type, or low-pressure operating condition type, a corresponding operating condition identification signal is generated; the step of generating driving force control parameters adapted to the current operating condition includes: obtaining the currently set output power of the hydraulic drive system. The target performance parameter value is obtained by looking up a table based on the current value of the differential pressure and the rate of change of the differential pressure. The target performance parameter value is positively correlated with the differential pressure and the rate of change of the differential pressure. The deviation between the target performance parameter value and the currently set output power of the hydraulic system is calculated to form a deviation signal. The deviation signal is input to the PID controller to obtain the feedback adjustment amount used to correct the output power of the hydraulic system. The power feedforward compensation amount is calculated based on the amplitude of the real-time differential pressure value. The feedback adjustment amount and the power feedforward compensation amount are superimposed and the superposition result is subjected to amplitude limiting processing to generate the driving force control parameters.

2. The method according to claim 1, characterized in that, The calculation of power feedforward compensation based on the amplitude of the real-time differential pressure value includes: a preset power feedforward compensation mapping table corresponding to the amplitude range of the differential pressure value; the mapping table divides the differential pressure value amplitude into multiple segmented intervals and configures a corresponding power feedforward compensation increment coefficient for each segmented interval; the current value of the differential pressure value is input into the mapping table to calculate the power feedforward compensation increment coefficient corresponding to the current differential pressure value; the target power feedforward compensation amount is obtained by multiplying the power feedforward compensation increment coefficient by the currently set output power of the hydraulic drive system.

3. The method according to claim 2, characterized in that, The method further includes: after completing the action of the quick-cut blind valve, recording the performance indicators during this action, including the actual response time of the valve plate reaching the target position and the peak output power of the hydraulic drive system during the entire action; comparing the performance indicators with a preset performance benchmark to calculate the control efficiency score of this action; when the control efficiency score is lower than a preset threshold, determining that there is a deviation in the power feedforward compensation increment coefficient of the corresponding differential pressure amplitude range in the current mapping table; adjusting the increment coefficient corresponding to the differential pressure amplitude range in the mapping table according to the deviation direction of the actual response time and the ideal response time and the overshoot of the peak output power; if the actual response time exceeds the ideal response time and the peak output power does not reach the upper limit, increasing the power feedforward compensation increment coefficient of the corresponding segment interval; if the peak output power exceeds the safety limit, decreasing the power feedforward compensation increment coefficient of the corresponding segment interval; and updating the adjusted power feedforward compensation increment coefficient to the power feedforward compensation mapping table.

4. The method according to claim 3, characterized in that, When the operating condition is a low-pressure operating condition, drive force control parameters adapted to the current operating condition are generated, including: obtaining a target performance parameter value based on the current value of the differential pressure using a lookup table algorithm; wherein the target performance parameter value is inversely correlated with the amplitude of the differential pressure and is not affected by the rate of change of the differential pressure; calculating the deviation between the target performance parameter value and the currently set output power of the hydraulic system to form a deviation signal; inputting the deviation signal into a PID controller to obtain a feedback adjustment amount for correcting the output power of the hydraulic system; calculating a power feedforward compensation amount based on the amplitude of the real-time differential pressure, wherein the power feedforward compensation amount is negative or zero, used to reduce the output power of the hydraulic system; superimposing the feedback adjustment amount and the power feedforward compensation amount, and performing amplitude limiting processing on the superposition result, ensuring that the output power of the hydraulic system is not lower than a preset minimum safety threshold, to generate drive force control parameters.

5. The method according to claim 4, characterized in that, Before inputting the deviation signal into the PID controller, the method further includes: retrieving the corresponding PID control parameters according to the currently identified operating condition type; the PID control parameters corresponding to the high-voltage operating condition type are configured such that the proportional gain coefficient is greater than the proportional gain coefficient in the PID control parameters corresponding to the normal operating condition type, and the integral time constant is less than the integral time constant in the PID control parameters corresponding to the normal operating condition type, in order to improve the response speed and suppress overshoot; the PID control parameters corresponding to the low-voltage operating condition type are configured such that the proportional gain coefficient is less than the proportional gain coefficient in the PID control parameters corresponding to the normal operating condition type, and the integral time constant is greater than the integral time constant in the PID control parameters corresponding to the normal operating condition type, in order to reduce power fluctuation; and loading the retrieved PID control parameters into the PID controller.

6. A quick-cut blind valve control system, characterized in that, include: The first processing module is used to: acquire real-time pressure monitoring data on the inlet and outlet sides of the quick-cut blind valve in the pipeline system; The second processing module is used to: calculate the pressure difference between the inlet and outlet sides of the quick-cut blind valve and obtain the pressure difference change rate; the third processing module is used to: obtain the current operating condition type of the pipeline system based on the magnitude of the pressure difference and the positive or negative direction of the pressure difference change rate; and generate a corresponding operating condition identification signal based on the identified operating condition type; the fourth processing module is used to: generate driving force control parameters adapted to the current operating condition based on the operating condition identification signal. The fifth processing module is used to: control the hydraulic drive system according to the driving force control parameters to drive the quick-cut blind valve to perform opening or closing actions; obtain the current pipeline system operating condition type according to the magnitude of the differential pressure value and the positive or negative direction of the differential pressure change rate, including: preset differential pressure high threshold and differential pressure low threshold for defining the operating condition range, and a pressure increase rate threshold for characterizing the severity of differential pressure change; when the current value of the differential pressure value is greater than the differential pressure high threshold, determine the operating condition as a predetermined high-pressure operating condition; when the current value of the differential pressure value is between the differential pressure low threshold and the differential pressure high threshold and the differential pressure change rate is greater than the pressure increase rate threshold, determine the operating condition as a trend-based high-pressure warning operating condition; when the current value of the differential pressure value is between the differential pressure low threshold and the differential pressure high threshold and the differential pressure change rate is not greater than the pressure increase rate threshold, determine the operating condition as a stable normal operating condition; when the current value of the differential pressure value is less than the differential pressure low threshold, determine the operating condition as a stable low-pressure operating condition; and change the predetermined high-pressure operating condition... The process of uniformly identifying high-pressure warning conditions and trend-based high-pressure conditions as high-pressure conditions; identifying stable normal conditions as normal conditions; identifying stable low-pressure conditions as low-pressure conditions; generating corresponding condition identification signals based on the identified high-pressure, normal, or low-pressure conditions; and generating drive force control parameters adapted to the current condition includes: obtaining the currently set output power of the hydraulic drive system; obtaining the target performance parameter value based on the current value of the differential pressure and the rate of change of the differential pressure using a lookup table algorithm; the target performance parameter value being positively correlated with the differential pressure and the rate of change of the differential pressure; calculating the deviation between the target performance parameter value and the currently set output power of the hydraulic system to form a deviation signal; inputting the deviation signal into a PID controller to obtain a feedback adjustment amount for correcting the output power of the hydraulic system; calculating the power feedforward compensation amount based on the amplitude of the real-time differential pressure; superimposing the feedback adjustment amount and the power feedforward compensation amount and performing amplitude limiting processing on the superposition result to generate drive force control parameters.

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