A valve control method, device, unit and medium based on dynamic sub-ranges

Abstract

The embodiment of the application discloses a valve control method, device, unit and medium based on dynamic split range. The method comprises the following steps: when it is determined that a turbine unit is connected to a power grid and is in a power control mode event, obtaining a flow control parameter of the turbine unit, and determining a static split range point of a gas supplement valve corresponding to each turbine expander according to a turbine expander type included in the turbine unit, a total pipeline valve flow function and an actual total pipeline flow; determining a dynamic split range point rate limit value according to an actual deviation of turbine power, and determining a current dynamic split range point target value according to the dynamic split range point rate limit value, a historical dynamic split range point original value and the static split range point; determining a valve position output corresponding to each gas supplement valve according to the flow control parameter, the current dynamic split range point target value and a valve characteristic corresponding to each gas supplement valve, and controlling the operation of the gas supplement valve according to the valve position output. The method guarantees the stability of turbine power, and further meets the operation requirements of a compressed air energy storage system.

Description

Technical Field

[0001] The embodiments of the present invention relate to the field of compressed air energy storage technology, and in particular to a valve control method, device, unit and medium based on dynamic split range. Background Technology

[0002] Compressed air energy storage releases high-pressure gas from the storage device during the energy release phase. The gas is heated by a heat exchanger and then delivered to the turbine unit, which drives the generator to produce electricity. During this process, turbine power is typically adjusted by regulating valves associated with the turbine unit, such as throttle valves or make-up air valves.

[0003] However, since the adjustment of the make-up air valve is generally determined based on the make-up air pressure, while the turbine power adjustment is determined when the turbine inlet air temperature is lower than the rated design parameters, the make-up air valve will not automatically open and close due to the need to adjust the turbine power. Therefore, the control strategy for the make-up air valve cannot adjust the turbine power at this time, resulting in a continuous decrease in turbine power, which in turn fails to meet the operating requirements of the compressed air energy storage system. Summary of the Invention

[0004] This invention provides a valve control method, device, unit, and medium based on dynamic split-range. This method ensures the stability of turbine power, thereby meeting the operational requirements of compressed air energy storage systems.

[0005] In a first aspect, embodiments of the present invention provide a valve control method based on dynamic split-range. The compressed air energy storage system includes a turbine unit, an air storage device, a make-up air valve, and a load control unit. The turbine unit and the air storage device are connected via a main pipeline. The turbine unit includes at least one turbine expander, and each turbine expander corresponds to one make-up air valve, which is connected between the turbine expander and the air storage device via a branch pipeline. The load control unit is electrically connected to each turbine expander, the air storage device, and the make-up air valve. The method is applied to the load control unit and includes: When the turbine unit is connected to the grid and is in power control mode, the flow control parameters of the turbine unit are obtained, and the static split point of the make-up air valve corresponding to each turbine expander is determined according to the turbine expander type, the flow function of the main pipeline valve and the actual total pipeline flow.

[0006] The dynamic split point rate limit is determined based on the actual deviation of turbine power, and the current dynamic split point target value is determined based on the dynamic split point rate limit, the original value of the historical dynamic split point, and the static split point.

[0007] Based on the flow control parameters, the current dynamic split point target value, and the valve characteristics corresponding to each air supply valve, determine the valve position output corresponding to each air supply valve, and control the air supply valve to work according to the valve position output.

[0008] The valve control method based on dynamic tripping provided in this invention, after the compressed air energy storage system enters power control mode, can select the corresponding main pipeline valve flow function according to the type of turbine expander included in the turbine unit, and determine the static tripping point of the make-up air valve corresponding to each turbine expander using the actual total pipeline flow and the selected main pipeline valve flow function. This ensures that the flow characteristic curve of the entire system is smooth and continuous in different control intervals to avoid sudden flow changes. It can determine the turbine power deviation based on the turbine power demand value (turbine power setpoint) and the actual turbine power value (turbine power feedback value), and then determine the compensation value (dynamic tripping point rate limit) for selecting the dynamic tripping point based on the turbine power deviation. Finally, it determines the current dynamic tripping point target value based on the dynamic tripping point rate limit, the historical dynamic tripping point original value, and the static tripping point. This achieves a reasonable and accurate calculation of the current dynamic tripping point target value based on the actual turbine power deviation and the calculated static tripping point. First, based on the target value of the current dynamic split point and the flow control parameters corresponding to each valve, the flow distribution output is reasonably allocated to each valve. Then, the valve position output after allocating this amount of flow is calculated using the valve characteristics of each valve. This solves the problem that the adjustment of the air supply valve is currently determined only by the air supply pressure, which makes it impossible to control the air supply valve when the turbine power needs to be adjusted. It realizes the calculation of the valve position output parameters that each air supply valve should be adjusted according to the actual deviation of the turbine power, ensuring the stability of the turbine power and thus meeting the operating requirements of the compressed air energy storage system.

[0009] Secondly, embodiments of the present invention also provide a valve control device based on dynamic split-range. The compressed air energy storage system includes a turbine unit, an air storage device, a make-up air valve, and a load control unit. The turbine unit and the air storage device are connected via a main pipeline. The turbine unit includes at least one turbine expander, and each turbine expander corresponds to one make-up air valve, which is connected between the turbine expander and the air storage device via a branch pipeline. The load control unit is electrically connected to each turbine expander, the air storage device, and the make-up air valve. The device is applied to the load control unit and includes: The static trip module is used to obtain the flow control parameters of the turbine unit when the turbine unit is connected to the grid and is in power control mode. Based on the turbine expander type, the flow function of the main pipeline valve and the actual total pipeline flow, it determines the static trip point of the air supply valve corresponding to each turbine expander.

[0010] The dynamic split-point module is used to determine the dynamic split-point rate limit based on the actual deviation of turbine power, and to determine the current dynamic split-point target value based on the dynamic split-point rate limit, the original value of the historical dynamic split-point, and the static split-point.

[0011] The control module is used to determine the valve position output corresponding to each air supply valve based on the flow control parameters, the current dynamic split point target value and the valve characteristics corresponding to each air supply valve, and control the air supply valve to work according to the valve position output.

[0012] Thirdly, embodiments of the present invention also provide a load control unit, the load control unit comprising: At least one processor; and A memory that is communicatively connected to at least one processor; wherein, The memory stores a computer program that can be executed by at least one processor, such that the at least one processor is able to execute the valve control method based on dynamic splitting according to any embodiment of the present invention.

[0013] Fourthly, embodiments of the present invention also provide a computer-readable storage medium storing computer instructions that, when executed by a processor, implement the valve control method based on dynamic range of any embodiment of the present invention.

[0014] Fifthly, embodiments of the present invention also provide a computer program product, including a computer program that, when executed by a processor, implements the valve control method based on dynamic splitting of any embodiment of the present invention.

[0015] It should be noted that the aforementioned computer instructions may be stored, in whole or in part, on a computer-readable storage medium. This computer-readable storage medium may be packaged together with the processor of the dynamically segmented valve control device, or it may be packaged separately from the processor of the dynamically segmented valve control device; this application does not impose any limitations on this.

[0016] The descriptions of the second, third, fourth, and fifth aspects in this application can be referred to the detailed description of the first aspect; and the beneficial effects of the descriptions of the second, third, fourth, and fifth aspects can be referred to the analysis of the beneficial effects of the first aspect, which will not be repeated here.

[0017] In this application, the name of the aforementioned valve control device based on dynamic split-range does not limit the device or functional module itself. In actual implementation, these devices or functional modules may appear under other names. As long as the function of each device or functional module is similar to that of this application, it falls within the scope of the claims of this application and its equivalents.

[0018] These or other aspects of this application will become more readily apparent in the following description. Attached Figure Description

[0019] To more clearly illustrate the technical solutions in the embodiments of the present invention, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 A schematic flowchart of a valve control method based on dynamic split-range provided in an embodiment of the present invention; Figure 2 A schematic flowchart of another valve control method based on dynamic split-range provided in an embodiment of the present invention; Figure 3 A schematic diagram illustrating the process structure of compressed air energy storage provided in an embodiment of the present invention; Figure 4 An example diagram illustrating the flow distribution of a valve provided in an embodiment of the present invention; Figure 5 A schematic diagram of a valve control device based on dynamic split-range provided in an embodiment of the present invention; Figure 6 This is a schematic diagram of a load control unit provided in an embodiment of the present invention. Detailed Implementation

[0021] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, the accompanying drawings show only the parts relevant to the present invention, and not all of the structures.

[0022] In this article, the term "and / or" is merely a description of the relationship between related objects, indicating that there can be three relationships. For example, A and / or B can represent three situations: A exists alone, A and B exist simultaneously, and B exists alone.

[0023] The terms "first" and "second," etc., used in the specification and drawings of this application are used to distinguish different objects or to distinguish different treatments of the same object, rather than to describe a specific order of objects.

[0024] Furthermore, the terms "comprising" and "having," and any variations thereof, used in the description of this application are intended to cover non-exclusive inclusion. For example, a process, method, system, product, or apparatus that includes a series of steps or units is not limited to the steps or units listed, but may optionally include other steps or units not listed, or may optionally include other steps or units inherent to such process, method, product, or apparatus.

[0025] Before discussing the exemplary embodiments in more detail, it should be noted that some exemplary embodiments are described as processes or methods depicted as flowcharts. Although the flowcharts describe the operations (or steps) as sequential processes, many of these operations can be performed in parallel, concurrently, or simultaneously. Furthermore, the order of the operations can be rearranged. The process can be terminated when its operation is completed, but may also have additional steps not included in the figures. The process can correspond to a method, function, procedure, subroutine, subroutine, etc. Moreover, without conflict, the embodiments and features in the embodiments of the present invention can be combined with each other.

[0026] It should be noted that in the embodiments of this application, the words "exemplary" or "for example" are used to indicate examples, illustrations, or explanations. Any embodiment or design scheme described as "exemplary" or "for example" in the embodiments of this application should not be construed as being more preferred or advantageous than other embodiments or design schemes. Specifically, the use of the words "exemplary" or "for example" is intended to present the relevant concepts in a specific manner.

[0027] In the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0028] Figure 1 This is a flowchart illustrating a valve control method based on dynamic range division provided by an embodiment of the present invention. This embodiment is applicable to dynamically determining the valve position output of each make-up air valve based on the current turbine power. This method can be executed by a valve control device based on dynamic range division, which can be implemented in hardware and / or software and can be configured in a load control unit. In this embodiment, the load control unit is the main control unit of the compressed air energy storage system. In this embodiment, the compressed air energy storage system includes a turbine unit, an air storage device, make-up air valves, and a load control unit. The turbine unit and the air storage device are connected through a main pipeline. The turbine unit includes at least one turbine expander, and each turbine expander corresponds to one make-up air valve, which is connected between the turbine expander and the air storage device through a branch pipeline. The load control unit is electrically connected to each turbine expander, air storage device, and make-up air valve. (Continue to refer to...) Figure 1 This embodiment specifically includes: S101. When it is determined that the turbine unit is connected to the grid and is in power control mode, the flow control parameters of the turbine unit are obtained, and the static split point of the air supply valve corresponding to each turbine expander is determined according to the turbine expander type, the flow function of the main pipeline valve and the actual total pipeline flow.

[0029] The turbine unit grid connection event is the closing of the output circuit breaker of the generator unit, directly connecting it electrically to the external power grid and initiating power exchange. The power control mode event refers to the event of switching the turbine unit from other control modes (such as speed control and pressure control) to power control mode. Flow control parameters are parameters used to control the turbine flow rate. In this embodiment, the turbine expander type can include high-pressure, medium-pressure, and low-pressure types. The total pipeline valve flow function characterizes the quantitative relationship between the flow function corresponding to each valve, the actual total pipeline flow rate, and the static split point. The actual total pipeline flow rate is the real-time total pipeline flow rate. The static split point in this embodiment is used to ensure that the flow characteristic curve of the entire compressed air energy storage system is smooth and continuous within different control intervals to avoid sudden flow changes.

[0030] Specifically, after the compressed air energy storage system enters the turbine grid connection event, if it receives a mode switching command from the operator (switching to power control mode event), or if it automatically detects that a mode switch can be performed, it switches the current mode to power control mode event. At this time, existing methods can be used, such as calculating the power control output parameters based on the turbine unit's control power parameters and target control power parameters using incremental proportional-integral-derivative control, and using the power control output parameters as the turbine unit's flow control parameters. Simultaneously, since the number and type of turbine expanders included in different turbine units vary, it is necessary to determine the types of turbine expanders included in each turbine unit. Then, based on the types of turbine expanders included in the turbine unit, the corresponding main pipeline valve flow function is selected, and the actual total pipeline flow is obtained. Substituting the actual total pipeline flow into the selected main pipeline valve flow function, the static split point of the make-up air valve corresponding to each turbine expander can be determined.

[0031] In this embodiment, after the compressed air energy storage system enters the power control mode, the corresponding total pipeline valve flow function can be selected according to the type of turbine expander included in the turbine unit. The static split point of the air supply valve corresponding to each turbine expander can be determined by using the actual total pipeline flow and the selected total pipeline valve flow function. This ensures that the flow characteristic curve of the entire system is smooth and continuous in different control intervals to avoid sudden changes in flow, and also provides a static data basis for the subsequent determination of the dynamic split point.

[0032] S102. Determine the dynamic split point rate limit based on the actual deviation of turbine power, and determine the current dynamic split point target value based on the dynamic split point rate limit, the historical dynamic split point original value, and the static split point.

[0033] The actual turbine power deviation characterizes the discrepancy between the setpoint turbine power and the actual feedback turbine power. The dynamic split point rate limit is used to dynamically compensate for the split point value. The historical dynamic split point raw value is the dynamic split point value initially calculated during the historical process. The dynamic split point target value is the final dynamic split point value determined after comparing it with the static split point after the initial dynamic split point value is calculated.

[0034] Specifically, after calculating the actual turbine power deviation using the setpoint and feedback value of the actual turbine power, the actual turbine power deviation can be compared with a pre-set power limit, and the dynamic split point speed limit can be determined based on the comparison. Furthermore, after obtaining the dynamic split point speed limit, the current dynamic split point original value can be calculated based on the dynamic split point speed limit and historical dynamic split point original values. The current dynamic split point original value is then compared with the static split point to finally determine the current dynamic split point target value.

[0035] In this embodiment, the turbine power deviation can be determined based on the required turbine power value (turbine power setpoint) and the actual turbine power value (turbine power feedback value). Then, the compensation value (dynamic split point rate limit) used to select the dynamic split point is determined based on the turbine power deviation. Finally, the current dynamic split point target value is determined based on the dynamic split point rate limit, the historical dynamic split point original value, and the static split point. This realizes the reasonable and accurate calculation of the current dynamic split point target value based on the actual turbine power deviation and the calculated static split point, providing a basis for the subsequent precise adjustment of the valve position output of the air supply valve.

[0036] S103. Based on the flow control parameters, the current dynamic split point target value, and the valve characteristics corresponding to each air replenishment valve, determine the valve position output corresponding to each air replenishment valve, and control the air replenishment valve to work according to the valve position output.

[0037] Valve characteristics characterize the relationship between the degree of valve opening and closing and the relative flow rate through the valve. Valve position output is a control output parameter used to control the degree of valve opening and closing.

[0038] Specifically, the flow distribution output for each valve can be determined first based on the target value of the current dynamic split point and the flow control parameters corresponding to each valve; then, based on the flow distribution output for each valve and the valve characteristics corresponding to that valve, the valve position output corresponding to each valve can be determined; finally, the valve can be controlled to operate according to the valve position output so that the valve opening degree reaches the required opening degree.

[0039] In this embodiment, the flow distribution output is first reasonably allocated to each valve based on the current dynamic split point target value and flow control parameters corresponding to each valve. Then, the valve position output after allocating this amount of flow is calculated using the valve characteristics corresponding to each valve. This solves the problem that the adjustment of the air supply valve is currently determined only by the air supply pressure, which makes it impossible to control the air supply valve when the turbine power needs to be adjusted. It realizes the calculation of the valve position output parameters that each air supply valve should be adjusted based on the actual deviation of the turbine power, ensuring the stability of the turbine power and thus meeting the operating requirements of the compressed air energy storage system.

[0040] The valve control method based on dynamic tripping provided in this invention, after the compressed air energy storage system enters power control mode, can select the corresponding main pipeline valve flow function according to the type of turbine expander included in the turbine unit, and determine the static tripping point of the make-up air valve corresponding to each turbine expander using the actual total pipeline flow and the selected main pipeline valve flow function. This ensures that the flow characteristic curve of the entire system is smooth and continuous in different control intervals to avoid sudden flow changes. It can determine the turbine power deviation based on the turbine power demand value (turbine power setpoint) and the actual turbine power value (turbine power feedback value), and then determine the compensation value (dynamic tripping point rate limit) for selecting the dynamic tripping point based on the turbine power deviation. Finally, it determines the current dynamic tripping point target value based on the dynamic tripping point rate limit, the historical dynamic tripping point original value, and the static tripping point. This achieves a reasonable and accurate calculation of the current dynamic tripping point target value based on the actual turbine power deviation and the calculated static tripping point. First, based on the target value of the current dynamic split point and the flow control parameters corresponding to each valve, the flow distribution output is reasonably allocated to each valve. Then, the valve position output after allocating this amount of flow is calculated using the valve characteristics of each valve. This solves the problem that the adjustment of the air supply valve is currently determined only by the air supply pressure, which makes it impossible to control the air supply valve when the turbine power needs to be adjusted. It realizes the calculation of the valve position output parameters that each air supply valve should be adjusted according to the actual deviation of the turbine power, ensuring the stability of the turbine power and thus meeting the operating requirements of the compressed air energy storage system.

[0041] Figure 2 This is a flowchart illustrating another valve control method based on dynamic split-range provided by an embodiment of the present invention. This embodiment adds control of the throttle valve to the above embodiment, and specifies the steps of calculating the static split-range point, determining the dynamic split-range point rate limit, determining the current dynamic split-range point target value, and determining the valve position output corresponding to each air supply valve. Further, the turbine unit structure in this embodiment will be briefly introduced first. Figure 3 This is an example diagram of the process structure for compressed air energy storage provided in an embodiment of the present invention. Figure 3As shown, a compressed air energy storage system may include: a low-pressure turbine 101, a medium-pressure turbine 102, and a high-pressure turbine 103 in a turbine unit, as well as a heat exchanger 90, a low-pressure main valve 301 corresponding to the low-pressure turbine, a medium-pressure main valve 302 corresponding to the medium-pressure turbine, a throttle valve 303 corresponding to the high-pressure turbine, a main valve 91, an outlet shut-off valve 50, an air storage device 60, a heat storage tank 701, a cold storage tank 702, a second-stage air supply valve 801, and a first-stage air supply valve 802 (in actual air energy storage systems, N stages of air supply valves will be set according to the type and number of turbine expanders; only the second-stage air supply valve is shown here).

[0042] In existing technologies, one control method employs a "throttling + gas replenishment regulation" turbine control. In this method, the turbine power is adjusted by sequentially opening the throttling valve and the gas replenishment valve to regulate the intake flow. When the intake pressure approaches the gas replenishment pressure point and the turbine needs to rapidly change load, the throttling valve's flow characteristics require a large stroke to change the turbine intake flow, reducing the turbine's load-changing capability. Another turbine control method uses a throttling valve to control turbine power and a gas replenishment valve to control the gas replenishment pressure. However, when the turbine intake temperature is below the rated design parameters, the throttling valve is fully open before the gas storage pressure drops to the gas replenishment pressure point. In this case, the gas replenishment pressure control strategy cannot adjust the turbine power, causing a continuous decrease in turbine power and failing to meet system operating requirements. Therefore, this embodiment proposes the following specific solution, which will be referred to further. Figure 2 In this embodiment, the method specifically includes: S201. When it is determined that the turbine unit is connected to the grid and is in power control mode, the flow control parameters of the turbine unit are obtained.

[0043] Specifically, the flow control parameters of the turbine unit can be calculated using existing technology, such as the following calculation formula: ; ; Among them, OP PIC_OUT (n) represents the output value of the power proportional-integral-derivative control for the current cycle, which is also the flow control parameter in this embodiment, OP. PIC_OUT (n-1) represents the output value of the power proportional-integral-derivative control in the previous cycle, ΔU(n) represents the increment of the deviation effect in the current cycle, and X P T represents the proportional coefficient of the incremental proportional-integral-derivative (PID) control, e(n) represents the control deviation of the PID control in the current cycle, and e(n-1) represents the control deviation of the PID control in the previous cycle. I T is the integral time constant of incremental proportional-integral-derivative control. S The sampling period is the incremental proportional-integral-derivative control.

[0044] S202. Determine whether the turbine expander types included in the turbine unit include medium-pressure turbines; if so, proceed to S203; if not, proceed to S204.

[0045] Specifically, if the turbine expander type includes a medium-pressure turbine, S203 can be executed directly; otherwise, S204 can be executed directly.

[0046] Optionally, in this embodiment, when the turbine unit only includes a high-pressure turbine, its corresponding air supply valve is a first-stage air supply valve. In this case, the turbine air distribution method is "throttle valve + first-stage air supply valve", and the static split point is the first static split point. When the turbine unit includes a medium-pressure turbine and a high-pressure turbine, its corresponding air supply valve is a second-stage air supply valve. In this case, the turbine air distribution method is "throttle valve + first-stage air supply valve + second-stage air supply valve", and the static split points are the first static split point and the second static split point.

[0047] It is worth noting that this embodiment only assumes the presence of one medium-pressure turbine and one high-pressure turbine. Actual configurations may require adjustments based on the turbine unit's structure.

[0048] S203. Determine the existence of a first-stage air supply valve corresponding to the high-pressure turbine, a first static split point corresponding to the first-stage air supply valve, a second-stage air supply valve corresponding to the medium-pressure turbine, and a second static split point corresponding to the second-stage air supply valve. Obtain the first static split point by differentiating the piecewise function of the main pipeline valve flow rate corresponding to the first static split point. Obtain the second static split point by differentiating the piecewise function of the main pipeline valve flow rate corresponding to the second static split point.

[0049] Specifically, after determining that the turbine unit contains one high-pressure turbine and one medium-pressure turbine, it can be determined that the high-pressure turbine corresponds to a first-stage air supply valve, and this first-stage air supply valve corresponds to a first static split point; the medium-pressure turbine corresponds to a second-stage air supply valve, and this second-stage air supply valve corresponds to a second static split point. At this point, for each of the two static split points, the specific values ​​can be obtained by differentiating the corresponding piecewise flow function of the main pipeline valves. The specific calculation is as follows: First, based on the principle of linear superposition, the maximum total turbine intake flow rate is the sum of the maximum flow rates of the throttle valve and the supplementary air valve, while the minimum flow rate is the minimum adjustable flow rate of a single valve. Therefore, the piecewise function can be obtained as follows: ; Where C(fr) represents the flow function of the main pipeline valves; fr is the actual total pipeline flow, the specific value of which is generally a variable between 0 and 100%, corresponding to 0% to 100% of the total pipeline flow; Cv0(fr) is the flow function of the throttle valve; Cv1(fr) is the flow function of the first-stage air supply valve; Cv2(fr) is the flow function of the second-stage air supply valve; Cv 0，max Cv is the maximum flow rate of the throttle valve. 1，max Cv is the maximum flow rate of a section of the air supply valve. 2，max D1 is the maximum flow rate of the two-stage air supply valve; D2 is the first static split point corresponding to the first-stage air supply valve; and D3 is the second static split point corresponding to the two-stage air supply valve. In this embodiment, the quantities to be determined are D1 and D2. The unknown quantity is C(fr). All others are known quantities, which are either pre-set or determined based on the system properties of the compressed air energy storage system. In this embodiment, all known quantities are either pre-set or determined through testing or experiments based on equipment performance.

[0050] Furthermore, according to mathematical theory, the left and right derivatives of a piecewise function are equal at the point of division. Therefore, the following formula can be derived: ; ; Based on the above two formulas, the specific values ​​of D1 and D2 can be derived, thus determining the first static split point and the second static split point.

[0051] S204. Determine that there is only a gas supply valve corresponding to the high-pressure section turbine and the first static split point corresponding to the gas supply valve, and obtain the first static split point by differentiating the piecewise function of the main pipeline valve flow rate corresponding to the first static split point.

[0052] Specifically, if it is determined that only a high-pressure turbine exists, then it can be determined that only one air supply valve exists in the compressed air energy storage system, and the first static split point corresponding to this air supply valve can be determined. Therefore, the value of D1 can be calculated using the formula above, that is, by taking the derivatives of the first two formulas in the piecewise function and making them equal, the value of the first static split point can be obtained.

[0053] It is worth noting that in this embodiment, steps S203 or S204 can be selected to be executed depending on whether a medium-pressure turbine is included. Furthermore, after the execution is completed, step S205 is executed directly.

[0054] In this embodiment, by distinguishing the different types of turbine expanders included in the turbine unit to determine the static split point, the number and type of valves present in the turbine unit can be accurately determined based on the type of turbine expander in the turbine unit. Then, the static split point is reasonably allocated according to the different number and type of valves, providing an accurate data basis for the subsequent determination of the dynamic split point.

[0055] S205. Determine the actual deviation of turbine power based on the turbine power setpoint and the turbine power feedback value.

[0056] The turbine power setpoint is the pre-set turbine power demand value. The turbine power feedback value is the control feedback value obtained by real-time monitoring of the turbine unit's operating status during actual operation.

[0057] Specifically, the turbine power setpoint can be obtained, and the turbine power feedback value can be determined based on real-time monitoring parameters; then, the turbine power setpoint is subtracted from the turbine power feedback value, and the absolute value of the difference is obtained. The actual deviation of the turbine power can be obtained after obtaining the absolute value.

[0058] For example, the actual turbine power deviation can be calculated using the following formula: ; Among them, POWER k This refers to the actual deviation of turbine power; POWER SP This is the turbine power setpoint; POWER PV This is the turbine power feedback value.

[0059] S206. Determine the relationship between the actual deviation of turbine power, the minimum limit of turbine power, and the maximum limit of turbine power.

[0060] Specifically, obtain the preset minimum and maximum turbine power limits, and determine the relationship between the actual turbine power deviation and these two limits. Based on this relationship, select any one of steps S207-S209 to execute.

[0061] S207. If the actual deviation of turbine power is less than the minimum limit of turbine power, then the dynamic split point speed limit is determined to be the minimum limit of dynamic split point speed.

[0062] Specifically, if the actual deviation of turbine power is less than the minimum limit of turbine power, then the dynamic split point rate limit can be determined to be the preset minimum limit of dynamic split point rate.

[0063] S208. If the actual deviation of turbine power is greater than the maximum limit of turbine power, then the dynamic split point speed limit is determined to be the maximum limit of dynamic split point speed.

[0064] Specifically, if the actual deviation of turbine power is greater than the maximum limit of turbine power, then the dynamic split point rate limit can be determined to be the preset maximum limit of dynamic split point rate.

[0065] S209. If the actual deviation of turbine power is less than or equal to the maximum limit of turbine power and the actual deviation of turbine power is greater than or equal to the minimum limit of turbine power, then the dynamic split point speed limit is determined to be zero.

[0066] Specifically, if it is determined that the actual deviation of turbine power is less than or equal to the maximum limit of turbine power, and is greater than or equal to the minimum limit of turbine power, then the dynamic split point rate limit can be set to zero.

[0067] It is worth noting that in this embodiment, S207-S209 are parallel steps; in actual execution, only one will be selected for execution, and after any one step is completed, S210 will continue to be executed.

[0068] In this embodiment, the current turbine power adjustment (i.e., actual turbine power deviation) is determined by calculating the difference between the turbine power setpoint and the feedback value, thus quantifying the required turbine power adjustment. Furthermore, the dynamic split-point speed limit is determined based on the actual turbine power deviation and the preset turbine power limit, providing a basis for subsequently determining the original dynamic split-point value to compensate for the power deviation.

[0069] S210. Determine the previous dynamic split point original value from the historical dynamic split point original values, and sum the previous dynamic split point original value with the dynamic split point speed limit to obtain the current dynamic split point original value.

[0070] The original value of the previous dynamic split point is the "original value of the current dynamic split point" obtained in the previous execution cycle. In this embodiment, if the current execution cycle is the initial execution cycle, the original value of the previous dynamic split point is a preset value or zero.

[0071] Specifically, the original value of the previous dynamic split point is obtained, and then the original value of the current dynamic split point is obtained by summing the original value of the previous dynamic split point with the dynamic split point rate limit.

[0072] For example, continuing the above example, if the turbine unit includes a medium-pressure turbine, then the original value of the previous dynamic split point can be determined to include both the first original value of the previous dynamic split point and the second original value of the previous dynamic split point. Furthermore, the first original value of the current dynamic split point can be obtained by adding the dynamic split point rate limit to the first original value of the previous dynamic split point; the second original value of the current dynamic split point can be obtained by adding the dynamic split point rate limit to the second original value of the previous dynamic split point. Similarly, if the turbine unit only includes a high-pressure turbine, then only the first original value of the current dynamic split point can be calculated, that is, by adding the dynamic split point rate limit to the first original value of the previous dynamic split point.

[0073] In this embodiment, the dynamic split point rate limit is used as a compensation parameter when determining the dynamic split point, and the original value of the dynamic split point is determined, thereby realizing fine-tuning of the static split point based on the deviation of turbine power.

[0074] S211. Determine the target value of the current dynamic split point based on the numerical relationship between the static split point, the minimum static split point value, and the original value of the current dynamic split point.

[0075] Specifically, after determining the original value of the current dynamic split point, the original value of the current dynamic split point can be compared with the static split point. If the original value of the current dynamic split point is greater than the static split point, the target value of the current dynamic split point can be determined to be the value of the static split point. If the original value of the current dynamic split point is less than the minimum limit of the static split point, the target value of the current dynamic split point can be determined to be the value of the minimum limit of the static split point.

[0076] For example, continuing the above example, if the turbine unit includes a medium-pressure turbine, then when the original value of the first current dynamic range point is greater than the first static range point, the target value of the current dynamic first range point is determined to be the value of the first static range point; when the original value of the first current dynamic range point is less than the minimum limit of the first static range point, the target value of the current dynamic first range point is determined to be the value of the minimum limit of the first static range point. Furthermore, when the original value of the second current dynamic range point is greater than the second static range point, the target value of the current dynamic second range point is determined to be the value of the second static range point; when the original value of the second current dynamic range point is less than the minimum limit of the second static range point, the target value of the current dynamic second range point is determined to be the value of the minimum limit of the second static range point. If the turbine unit only includes the high-pressure section turbine, then there is only the original value of the first current dynamic split point. Therefore, when the original value of the first current dynamic split point is greater than the first static split point, the target value of the current dynamic first split point is determined to be the value of the first static split point. When the original value of the first current dynamic split point is less than the minimum value of the first static split point, the target value of the current dynamic first split point is determined to be the value of the minimum value of the first static split point.

[0077] In this embodiment, the minimum limit of the static split point and the static split point are used as limits, and the calculated original value of the dynamic split point is compared with them. The value closest to the original value of the dynamic split point is used as the final target value of the dynamic split point. This enables the dynamic adjustment of the split point according to the actual turbine power, providing a basis for the smooth and continuous flow characteristic curve of the entire system, and also providing a basis for the subsequent reasonable determination of the valve output of each valve.

[0078] S212. Determine the valve position output corresponding to the throttle valve based on the flow control parameters, the current dynamic split point target value, and the valve characteristics corresponding to the throttle valve.

[0079] In this embodiment, the compressed air energy storage system also includes a throttle valve, which is installed between the turbine unit and the air storage device; the load control unit is electrically connected to the throttle valve.

[0080] Specifically, for a throttle valve, after determining the current dynamic split point target value, the flow distribution output parameters corresponding to the throttle valve can be determined first based on the current dynamic split point target value and the flow control parameters. For example, dividing the flow control parameters by the current dynamic first split point target value yields the flow distribution output parameters corresponding to the throttle valve. Then, multiplying the flow distribution output parameters corresponding to the throttle valve by the valve characteristics corresponding to the throttle valve yields the valve position output corresponding to the throttle valve.

[0081] For example, based on the flow control parameters, the current dynamic split point target value, and the valve characteristics corresponding to the throttle valve, the valve position output corresponding to the throttle valve can be determined using the following formula: ; Among them, VALVE OUT_0 (n) represents the valve position output corresponding to the throttle valve. OP PIC_OUT (n) / DP1(n) is the flow distribution output parameter corresponding to the throttle valve, that is, the flow control parameter OP. PIC_OUT (n) is obtained by dividing the current dynamic first split point target value DP1(n). F0(x) is the valve characteristic corresponding to the throttle valve; all valve characteristics in this embodiment can be obtained through valve properties in experiments or tests.

[0082] S213. Control the operation of the throttle valve according to the valve position corresponding to the throttle valve.

[0083] Specifically, the load control unit can control the operation of the throttle valve according to the valve position output of the throttle valve.

[0084] It is worth noting that in this embodiment, S212-S213 are the control logic steps for the throttle valve, and S214-S216 are the control logic steps for the air supply valve. In actual execution, the throttle valve is generally controlled first, and then the air supply valve is controlled; optionally, the two can be executed simultaneously.

[0085] S214. Determine the flow distribution output parameters of each air supply valve based on the flow control parameters and the target value of the current dynamic split point corresponding to each air supply valve.

[0086] Specifically, when the turbine expander types included in the turbine unit include a high-pressure turbine, a first-stage air supply valve corresponding to the high-pressure turbine, a medium-pressure turbine, and a second-stage air supply valve corresponding to the medium-pressure turbine, the flow distribution output parameters of each air supply valve are determined, including: (i) For a single-stage air supply valve, calculate the first difference between the flow control parameter and the target value of the current dynamic first split point, calculate the second difference between the target value of the current dynamic second split point and the target value of the current dynamic first split point, and calculate the ratio of the first difference to the second difference to obtain the flow distribution output parameter of the single-stage air supply valve.

[0087] Specifically, for a single-stage air supply valve, its flow distribution output parameters are determined based on the flow control parameters and their corresponding current dynamic split point target value, and can be calculated using the following formula: ; Where n represents the nth execution round; OP PIC_OUT (n) represents the flow distribution output parameter corresponding to the gas replenishment valve in the nth execution round; OP OUT DP(n) represents the flow control parameters in the nth execution round; DP1(n) represents the target value of the current dynamic first split point; DP2(n) represents the target value of the current dynamic second split point. OP OUT DP1(n) is the first difference; DP2(n)-DP1(n) is the second difference.

[0088] (ii) For the two-stage air supply valve, calculate the third difference between the flow control parameter and the target value of the current dynamic second split point, calculate the fourth difference between the first value and the target value of the current dynamic second split point, and calculate the ratio of the third difference to the fourth difference to obtain the flow distribution output parameter of the two-stage air supply valve.

[0089] Specifically, for the two-stage air supply valve, its flow distribution output parameters are determined based on the flow control parameters and their corresponding current dynamic split point target value, and can be calculated using the following formula: ; Where n represents the nth execution round; OP OUT_2 (n) represents the flow distribution output parameter corresponding to the second-stage air supply valve in the nth execution round; OP OUT DP(n) represents the flow control parameters in the nth execution round; DP1(n) represents the target value of the current dynamic first split point; DP2(n) represents the target value of the current dynamic second split point. OP OUT (n)-DP2(n) is the third difference; 1-DP2(n) is the fourth difference.

[0090] S215. Multiply the flow distribution output parameter of each air replenishment valve by the valve characteristic corresponding to each air replenishment valve to obtain the valve position output corresponding to each air replenishment valve.

[0091] In this embodiment, the output range of the valve position output is 0~100%.

[0092] Specifically, for a single-stage air supply valve, the valve characteristic corresponding to the single-stage air supply valve can be directly multiplied by the flow distribution output parameter corresponding to the single-stage air supply valve to obtain the valve position output of the single-stage air supply valve in the nth round. For a two-stage air supply valve, the valve characteristic corresponding to the two-stage air supply valve can be directly multiplied by the flow distribution output parameter corresponding to the two-stage air supply valve to obtain the valve position output of the two-stage air supply valve in the nth round.

[0093] S216. Control the operation of the air supply valve according to the valve position output.

[0094] Specifically, the operation of each air supply valve is controlled according to the valve position output.

[0095] In this embodiment, by simultaneously controlling the throttle valve and each gas supply valve, the turbine power can be adjusted based on the throttle + gas supply distribution method. Dynamic split-range control is used to adjust and control the throttle valve and the gas supply valve, which solves the problem of slow turbine power response under the conditions of changes in intake parameters and rapid load changes, and realizes stable turbine load output within the full sliding pressure range of the gas storage device.

[0096] Furthermore, in this embodiment, if the turbine expander types included in the turbine unit include a high-pressure turbine, a first-stage air supply valve corresponding to the high-pressure turbine, a medium-pressure turbine, and a second-stage air supply valve corresponding to the medium-pressure turbine, then the flow distribution between the throttle valve and the air supply valve can be as follows: Figure 4 As shown. Figure 4 This diagram illustrates the flow distribution of valves according to an embodiment of the present invention. Specifically, the horizontal axis represents the flow distribution, and the vertical axis represents the valve flow rate. The original flow distribution of the throttle valve is from 0 to D1, the original flow distribution of the first-stage air supply valve is from D1 to D2 (i.e., two static split points), and the original flow distribution of the second-stage air supply valve is from D2 to 100% (the flow distribution lines corresponding to the original throttle valve, first-stage air supply valve, and second-stage air supply valve in the diagram are represented by thick straight lines and thick dashed lines, respectively). After recalculating the dynamic split points in the above manner, the flow distribution process between the throttle valve, first-stage air supply valve, and second-stage air supply valve can be tightly integrated, that is, the throttle valve, first-stage air supply valve, and second-stage air supply valve can be controlled simultaneously to regulate the power of the turbine unit. Therefore, after recalculating the dynamic split points, the control of the throttle valve can be determined based on the current target value DP1 of the first dynamic split point; the control of the first-stage air supply valve can be determined based on the current target value DP1 of the first dynamic split point and the current target value DP2 of the second dynamic split point; and the control of the second-stage air supply valve can be determined based on the current target value DP2 of the second dynamic split point (as shown by the thin dashed line and thin dotted line in the figure). Wherein, point D... 1_MIN With point D 2_MINThese are the minimum limits for the first static split point and the second static split point, respectively. Using this method, dynamic split-range control of the valve flow rates of the throttle valve, the first-stage air supply valve, and the second-stage air supply valve can be achieved simultaneously.

[0097] Optionally, in this embodiment, the valve position outputs of the throttle valve and the air supply valve are processed by a servo card using proportional-integral calculations to output standard electrical signal commands. These electrical signals are then converted into hydraulic signals by an electro-hydraulic converter, which in turn drives the throttle actuator, causing the lever to open the throttle valve. Optionally, the throttle valve and the air supply valve can be hydraulically operated or electrically operated.

[0098] Figure 5 This is a schematic diagram of a valve control device based on dynamic split-range, provided as an embodiment of the present invention. The compressed air energy storage system includes a turbine unit, an air storage device, a make-up air valve, and a load control unit; the turbine unit and the air storage device are connected via a main pipeline; the turbine unit includes at least one turbine expander, and each turbine expander corresponds to one make-up air valve, which is connected between the turbine expander and the air storage device via a branch pipeline; the load control unit is electrically connected to each turbine expander, air storage device, and make-up air valve; the device is applied to the load control unit; as shown... Figure 5 As shown, the device includes: The static split-range module 501 is used to obtain the flow control parameters of the turbine unit when the turbine unit is connected to the grid and is in power control mode. Based on the turbine expander type, the flow function of the main pipeline valve and the actual total pipeline flow, the static split-range point of the air supply valve corresponding to each turbine expander is determined.

[0099] The dynamic split-point module 502 is used to determine the dynamic split-point rate limit based on the actual deviation of turbine power, and to determine the current dynamic split-point target value based on the dynamic split-point rate limit, the original value of the historical dynamic split-point, and the static split-point.

[0100] The control module 503 is used to determine the valve position output corresponding to each air supply valve based on the flow control parameters, the current dynamic split point target value and the valve characteristics corresponding to each air supply valve, and to control the air supply valve to work according to the valve position output.

[0101] Based on the above embodiments, the compressed air energy storage system also includes a throttle valve, which is installed between the turbine unit and the air storage device; the load control unit is electrically connected to the throttle valve; after determining the current dynamic split point target value, the dynamic split module 502 is further used for: Based on the flow control parameters, the current dynamic split point target value, and the valve characteristics corresponding to the throttle valve, determine the valve position output corresponding to the throttle valve; control the operation of the throttle valve according to the valve position output corresponding to the throttle valve.

[0102] Based on the above embodiments, the static split-process module 501 is specifically used for: Determine whether the turbine expander types included in the turbine unit include a medium-pressure turbine. If the turbine expander types included in the turbine unit include a medium-pressure turbine, then determine the existence of a first-stage air supply valve corresponding to the high-pressure turbine, a first static split point corresponding to the first-stage air supply valve, a second-stage air supply valve corresponding to the medium-pressure turbine, and a second static split point corresponding to the second-stage air supply valve. The first static split point is obtained by differentiating the piecewise function of the main pipeline valve flow rate corresponding to the first static split point, and the second static split point is obtained by differentiating the piecewise function of the main pipeline valve flow rate corresponding to the second static split point. If the turbine expander types included in the turbine unit do not include a medium-pressure turbine, then determine that only the air supply valve corresponding to the high-pressure turbine and the first static split point corresponding to the air supply valve exist. The first static split point is obtained by differentiating the piecewise function of the main pipeline valve flow rate corresponding to the first static split point.

[0103] Based on the above embodiments, the dynamic splitting module 502 is specifically used for: The actual deviation of turbine power is determined based on the turbine power setpoint and the turbine power feedback value; Determine the relationship between the actual turbine power deviation, the minimum turbine power limit, and the maximum turbine power limit; if the actual turbine power deviation is less than the minimum turbine power limit, then the dynamic split point speed limit is determined to be the minimum dynamic split point speed limit; if the actual turbine power deviation is greater than the maximum turbine power limit, then the dynamic split point speed limit is determined to be the maximum dynamic split point speed limit; if the actual turbine power deviation is less than or equal to the maximum turbine power limit and the actual turbine power deviation is greater than or equal to the minimum turbine power limit, then the dynamic split point speed limit is determined to be zero.

[0104] Based on the above embodiments, the dynamic splitting module 502 is specifically used for: Determine the previous dynamic split point original value from the historical dynamic split point original values, and sum the previous dynamic split point original value with the dynamic split point speed limit to obtain the current dynamic split point original value; determine the current dynamic split point target value based on the numerical relationship between the static split point, the static split point minimum limit and the current dynamic split point original value.

[0105] Based on the above embodiments, the control module 503 is specifically used for: The flow distribution output parameter of each air supply valve is determined based on the flow control parameters and the target value of the current dynamic split point corresponding to each air supply valve; the flow distribution output parameter of each air supply valve is multiplied by the valve characteristic corresponding to each air supply valve to obtain the valve position output corresponding to each air supply valve.

[0106] Based on the above embodiments, when the turbine expander types included in the turbine unit include a high-pressure turbine, a first-stage air supply valve corresponding to the high-pressure turbine, a medium-pressure turbine, and a second-stage air supply valve corresponding to the medium-pressure turbine, the control module 503 is specifically used for: For a single-stage air supply valve, calculate the first difference between the flow control parameter and the current dynamic first split point target value, calculate the second difference between the current dynamic second split point target value and the current dynamic first split point target value, and calculate the ratio of the first difference to the second difference to obtain the flow distribution output parameters of the single-stage air supply valve. For a two-stage air supply valve, calculate the third difference between the flow control parameter and the current dynamic second split point target value, calculate the fourth difference between the first difference and the current dynamic second split point target value, and calculate the ratio of the third difference to the fourth difference to obtain the flow distribution output parameters of the two-stage air supply valve.

[0107] The valve control device based on dynamic range provided in the embodiments of the present invention can execute the valve control method based on dynamic range provided in any embodiment of the present invention, and has the corresponding functional modules and beneficial effects of the method.

[0108] It is worth noting that in the above embodiments of the valve control device based on dynamic split-range, the various units and modules included are only divided according to functional logic, but are not limited to the above division, as long as the corresponding functions can be achieved; in addition, the specific names of each functional unit are only for easy differentiation and are not used to limit the scope of protection of the present invention.

[0109] Figure 6 This is a schematic diagram of a load control unit provided in an embodiment of the present invention. Figure 6 A block diagram of an exemplary load control unit suitable for implementing embodiments of the present invention is shown. Figure 6 The load control unit shown is merely an example and should not be construed as limiting the functionality and scope of use of the embodiments of the present invention.

[0110] like Figure 6 As shown, the load control unit 11 is represented in the form of a general-purpose computing electronic device. The components of the load control unit may include, but are not limited to: one or more processors or processing units 16, system memory 28, and a bus 18 connecting different system components (including system memory 28 and processing unit 16).

[0111] Bus 18 represents one or more of several bus architectures, including a memory bus or memory controller, a peripheral bus, a graphics acceleration port, a processor, or a local bus using any of the various bus architectures. For example, these architectures include, but are not limited to, the Industry Standard Architecture (ISA) bus, the Micro Channel Architecture (MAC) bus, the Enhanced ISA bus, the Video Electronics Standards Association (VESA) local bus, and the Peripheral Component Interconnect (PCI) bus.

[0112] Load control units typically include a variety of computer-readable media. These media can be any available media that can be accessed by the load control unit, including volatile and non-volatile media, and removable and non-removable media.

[0113] System memory 28 may include computer system readable media in the form of volatile memory, such as random access memory (RAM) 30 and / or cache memory 32. The load control unit may further include other removable / non-removable, volatile / non-volatile computer system storage media. By way of example only, storage system 34 may be used to read and write non-removable, non-volatile magnetic media (…). Figure 6 Not shown; usually referred to as a "hard drive"). Although Figure 6 As not shown, disk drives for reading and writing to removable non-volatile disks (e.g., "floppy disks") and optical disc drives for reading and writing to removable non-volatile optical discs (e.g., CD-ROMs, DVD-ROMs, or other optical media) may be provided. In these cases, each drive may be connected to bus 18 via one or more data media interfaces. System memory 28 may include at least one program product having a set (e.g., at least one) of program modules configured to perform the functions of the embodiments of the present invention.

[0114] A program / utility 40 having a set (at least one) of program modules 42 may be stored, for example, in system memory 28. Such program modules 42 include, but are not limited to, an operating system, one or more application programs, other program modules, and program data. Each or some combination of these examples may include an implementation of a network environment. Program modules 42 typically perform the functions and / or methods described in the embodiments of the present invention.

[0115] The load control unit can also communicate with one or more external devices 14 (e.g., keyboard, pointing device, display 24, etc.), and with one or more devices that enable a user to interact with the load control unit, and / or with any device that enables the load control unit to communicate with one or more other computing devices (e.g., network card, modem, etc.). This communication can be performed via input / output (I / O) interface 22. Furthermore, the load control unit can also communicate with one or more networks (e.g., local area network (LAN), wide area network (WAN), and / or public networks, such as the Internet) via network adapter 20. Figure 6 As shown, network adapter 20 communicates with other modules of the load control unit via bus 18. It should be understood that, although... ​ As not shown, it can be used in conjunction with the load control unit and other hardware and / or software modules, including but not limited to: microcode, device drivers, redundancy processing units, external disk drive arrays, RAID systems, tape drives, and data backup storage systems.

[0116] The processing unit 16 executes various functional applications and page displays by running programs stored in the system memory 28, such as implementing the valve control method based on dynamic range provided in this embodiment. Of course, those skilled in the art will understand that the processor can also implement the technical solutions of the valve control method based on dynamic range provided in any embodiment of this invention.

[0117] This invention provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements, for example, the valve control method based on dynamic splitting provided in this invention.

[0118] The computer storage medium of this invention can be any combination of one or more computer-readable media. A computer-readable medium can be a computer-readable signal medium or a computer-readable storage medium. A computer-readable storage medium can be, for example, but not limited to, an electrical, magnetic, optical, electromagnetic, infrared, or semiconductor system, apparatus, or device, or any combination thereof. More specific examples of computer-readable storage media (a non-exhaustive list) include: an electrical connection having one or more wires, a portable computer disk, a hard disk, random access memory (RAM), read-only memory (ROM), erasable programmable read-only memory (EPROM or flash memory), optical fiber, portable compact disk read-only memory (CD-ROM), optical storage device, magnetic storage device, or any suitable combination thereof. In this document, a computer-readable storage medium can be any tangible medium that contains or stores a program that can be used by or in conjunction with an instruction execution system, apparatus, or device.

[0119] Computer-readable signal media may include data signals propagated in baseband or as part of a carrier wave, carrying computer-readable program code. Such propagated data signals may take various forms, including but not limited to electromagnetic signals, optical signals, or any suitable combination thereof. Computer-readable signal media may also be any computer-readable medium other than computer-readable storage media, capable of sending, propagating, or transmitting programs for use by or in connection with an instruction execution system, apparatus, or device.

[0120] Program code contained on a computer-readable medium may be transmitted using any suitable medium, including but not limited to: wireless, wire, optical fiber, RF, etc., or any suitable combination thereof.

[0121] This invention also provides a computer program product, including a computer program that, when executed by a processor, implements the valve control method based on dynamic splitting as provided in any embodiment of this invention.

[0122] Computer program code for performing the operations of this invention can be written in one or more programming languages ​​or a combination thereof. Programming languages ​​include object-oriented programming languages ​​such as Java, Smalltalk, and C++, as well as conventional procedural programming languages—such as the "C" language or similar programming languages. The program code can be executed entirely on the user's computer, partially on the user's computer, as a standalone software package, partially on the user's computer and partially on a remote computer, or entirely on a remote computer or server. In cases involving remote computers, the remote computer can be connected to the user's computer via any type of network, including a local area network (LAN) or a wide area network (WAN), or it can be connected to an external computer (e.g., via the Internet using an Internet service provider).

[0123] Those skilled in the art will understand that the modules or steps of the present invention described above can be implemented using general-purpose computing devices. They can be centralized on a single computing device or distributed across a network of multiple computing devices. Optionally, they can be implemented using computer-executable program code, thereby allowing them to be stored in a storage device for execution by a computing device, or they can be fabricated as separate integrated circuit modules, or multiple modules or steps can be fabricated as a single integrated circuit module. Thus, the present invention is not limited to any particular combination of hardware and software.

[0124] Furthermore, the acquisition, storage, use, and processing of data in the technical solution of this invention all comply with the relevant provisions of national laws and regulations.

[0125] Note that the above description is merely a preferred embodiment of the present invention and the technical principles employed. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein, and various obvious changes, readjustments, and substitutions can be made without departing from the scope of protection of the present invention. Therefore, although the present invention has been described in detail through the above embodiments, the present invention is not limited to the above embodiments, and may include many other equivalent embodiments without departing from the concept of the present invention, the scope of which is determined by the scope of the appended claims.

Claims

1. A valve control method based on dynamic split-range, characterized in that, The compressed air energy storage system includes a turbine unit, an air storage device, an air replenishment valve, and a load control unit; the turbine unit and the air storage device are connected via a main pipeline; the turbine unit includes at least one turbine expander, and each turbine expander corresponds to one air replenishment valve, which is connected between the turbine expander and the air storage device via a branch pipeline; the load control unit is electrically connected to each turbine expander, the air storage device, and the air replenishment valve respectively; The method is applied to a load control unit, and the method includes: When it is determined that the turbine unit is connected to the grid and is in power control mode, the flow control parameters of the turbine unit are obtained, and the static split point of the air supply valve corresponding to each turbine expander is determined according to the turbine expander type, the flow function of the main pipeline valve and the actual total pipeline flow of the turbine unit. The dynamic split point rate limit is determined based on the actual deviation of turbine power, and the current dynamic split point target value is determined based on the dynamic split point rate limit, the historical dynamic split point original value, and the static split point. Based on the flow control parameters, the current dynamic split point target value, and the valve characteristics corresponding to each of the replenishing valves, the valve position output corresponding to each replenishing valve is determined, and the replenishing valve is controlled to work according to the valve position output.

2. The method according to claim 1, characterized in that, The compressed air energy storage system also includes a throttle valve, which is disposed between the turbine unit and the air storage device; the load control unit is electrically connected to the throttle valve; After determining the target value of the current dynamic split point, the method also includes: Based on the flow control parameters, the current dynamic split point target value, and the valve characteristics corresponding to the throttle valve, determine the valve position output corresponding to the throttle valve; The throttle valve is controlled to operate according to the valve position output corresponding to the throttle valve.

3. The method according to claim 1, characterized in that, The step of determining the static trip point of the make-up air valve corresponding to each turbine expander based on the turbine expander type included in the turbine unit, the flow function of the main pipeline valves, and the actual total pipeline flow includes: Determine whether the turbine expander types included in the turbine unit include medium-pressure turbines; If the turbine expander type included in the turbine unit is a medium-pressure turbine, then it is determined that there is a first-stage air supply valve corresponding to the high-pressure turbine, a first static split point corresponding to the first-stage air supply valve, a second-stage air supply valve corresponding to the medium-pressure turbine, and a second static split point corresponding to the second-stage air supply valve. The first static split point is obtained by differentiating the piecewise function of the main pipeline valve flow rate corresponding to the first static split point, and the second static split point is obtained by differentiating the piecewise function of the main pipeline valve flow rate corresponding to the second static split point. If the turbine expander type included in the turbine unit does not include a medium-pressure turbine, then it is determined that only the air supply valve corresponding to the high-pressure turbine and the first static split point corresponding to the air supply valve exist. The first static split point is obtained by differentiating the piecewise function of the main pipeline valve flow rate corresponding to the first static split point.

4. The method according to claim 1, characterized in that, The determination of the dynamic split-point rate limit based on the actual deviation of turbine power includes: The actual deviation of the turbine power is determined based on the turbine power setpoint and the turbine power feedback value; Determine the relationship between the actual deviation of turbine power, the minimum limit of turbine power, and the maximum limit of turbine power; If the actual deviation of the turbine power is less than the minimum limit of the turbine power, then the dynamic split point rate limit is determined to be the minimum limit of the dynamic split point rate. If the actual deviation of the turbine power is greater than the maximum limit of the turbine power, then the dynamic split point rate limit is determined to be the maximum limit of the dynamic split point rate. If the actual deviation of the turbine power is less than or equal to the maximum limit of the turbine power and the actual deviation of the turbine power is greater than or equal to the minimum limit of the turbine power, then the dynamic split point rate limit is determined to be zero.

5. The method according to claim 1, characterized in that, The step of determining the current dynamic split point target value based on the dynamic split point rate limit, historical dynamic split point original values, and the static split point includes: The previous dynamic split point original value is determined from the historical dynamic split point original values, and the previous dynamic split point original value is summed with the dynamic split point rate limit to obtain the current dynamic split point original value; The target value of the current dynamic split point is determined based on the numerical relationship between the static split point, the minimum static split point value, and the original value of the current dynamic split point.

6. The method according to claim 1, characterized in that, The step of determining the valve position output corresponding to each air supply valve based on the flow control parameters, the current dynamic split point target value, and the valve characteristics corresponding to each air supply valve includes: The flow distribution output parameters of each air supply valve are determined based on the flow control parameters and the target value of the current dynamic split point corresponding to each air supply valve. Multiply the flow distribution output parameter of each of the air replenishment valves by the valve characteristics corresponding to each air replenishment valve to obtain the valve position output corresponding to each air replenishment valve.

7. The method according to claim 6, characterized in that, When the turbine expander types included in the turbine unit include a high-pressure turbine, a first-stage air supply valve corresponding to the high-pressure turbine, a medium-pressure turbine, and a second-stage air supply valve corresponding to the medium-pressure turbine, the step of determining the flow distribution output parameter of each air supply valve based on the flow control parameters and the current dynamic split point target value corresponding to each air supply valve includes: For the aforementioned air replenishment valve, calculate the first difference between the flow control parameter and the current dynamic first split point target value, calculate the second difference between the current dynamic second split point target value and the current dynamic first split point target value, and calculate the ratio of the first difference to the second difference to obtain the flow distribution output parameter of the aforementioned air replenishment valve; For the two-stage air supply valve, calculate the third difference between the flow control parameter and the current dynamic second split point target value, calculate the fourth difference between the first value and the current dynamic second split point target value, and calculate the ratio of the third difference to the fourth difference to obtain the flow distribution output parameter of the two-stage air supply valve.

8. A valve control device based on dynamic split-range, characterized in that, The compressed air energy storage system includes a turbine unit, an air storage device, an air replenishment valve, and a load control unit; the turbine unit and the air storage device are connected via a main pipeline; the turbine unit includes at least one turbine expander, and each turbine expander corresponds to one air replenishment valve, which is connected between the turbine expander and the air storage device via a branch pipeline; the load control unit is electrically connected to each turbine expander, the air storage device, and the air replenishment valve respectively; The device is applied to a load control unit, and the device includes: The static trip module is used to obtain the flow control parameters of the turbine unit when it is determined that the turbine unit is connected to the grid and is in power control mode. Based on the turbine expander type, the flow function of the main pipeline valve and the actual total pipeline flow of the turbine unit, the static trip point of the air supply valve corresponding to each turbine expander is determined. The dynamic split-range module is used to determine the dynamic split-point rate limit based on the actual deviation of turbine power, and to determine the current dynamic split-point target value based on the dynamic split-point rate limit, the historical dynamic split-point original value, and the static split-point. The control module is used to determine the valve position output corresponding to each of the replenishing valves based on the flow control parameters, the current dynamic split point target value and the valve characteristics corresponding to each replenishing valve, and to control the replenishing valve to work according to the valve position output.

9. A load control unit, characterized in that, include: One or more processors; Memory, used to store one or more programs. When the one or more programs are executed by the one or more processors, the one or more processors implement the valve control method based on dynamic splitting as described in any one of claims 1 to 7.

10. A computer-readable storage medium having a computer program stored thereon, characterized in that, When the program is executed by the processor, it implements the valve control method based on dynamic splitting as described in any one of claims 1 to 7.

Images