A control method for a variable-section supercharger control valve

Abstract

The present invention discloses a variable-section supercharger control valve control method, comprising: determining a required opening value based on an input initial required opening value; determining an opening deviation based on the required opening value and the actual opening value, and performing PID closed-loop control on the opening of the variable-section supercharger control valve based on a set closed-loop enabling condition to determine a first requested duty cycle; limiting the first requested duty cycle to obtain a second requested duty cycle; determining a friction compensation duty cycle based on the opening deviation; determining a compensation coefficient based on an actual system voltage and a set standard voltage; determining a final requested duty cycle based on the second requested duty cycle, the friction compensation duty cycle, and the compensation coefficient; and controlling the opening of the variable-section supercharger control valve using the final requested duty cycle. This method achieves precise control of the variable-section supercharger control valve.

Description

Technical Field

[0001] The present invention relates to the field of engine control, and in particular to a method for controlling a variable-section supercharger control valve. Background Art

[0002] A variable geometry turbocharger (VGT) uses guide vanes to control the vortex cross-section. These guide vanes are controlled by the engine control unit to control the airflow entering the turbocharger. Research has shown that VGT systems can increase boost pressure and turbocharger response speed, achieve lower speeds for maximum torque, allow for more turbocharger operation during engine MAP conditions, and improve engine thermal efficiency. This patent primarily addresses improving the control accuracy of the VGT valve, enhancing valve protection and control correction, thereby enhancing valve control precision.

[0003] Prior art CN113175378A discloses a control method, system, and automobile for a variable supercharger in an automobile engine. The method includes: determining an engine operating condition based on engine operating condition parameters; when the engine operating condition is a steady-state condition, obtaining a steady-state torque demand based on the operating condition parameters, querying a supercharger nozzle ring opening diagram based on the steady-state torque demand, and controlling the variable supercharger nozzle ring opening based on the query result; or when the engine operating state is a transient condition, obtaining an acceleration torque demand based on the operating condition parameters, and controlling the variable supercharger nozzle ring opening switching based on the acceleration torque demand and the variable supercharger control strategy.

[0004] The defects of the above-mentioned prior art are that: the protection of the VGT control valve motor, the speed control corresponding to different openings in the closed-loop control, and the influence of the system voltage are not taken into consideration, and the control accuracy is not high. Summary of the Invention

[0005] The object of the present invention is to provide a method for controlling a variable area supercharger control valve, so as to improve the control accuracy of the variable area supercharger.

[0006] To solve the above technical problems, the present invention provides a variable-section supercharger control valve control method, comprising:

[0007] Determine the required opening value according to the input initial required opening value;

[0008] Determining an opening deviation based on the required opening value and the actual opening value, and performing PID closed-loop control on the opening of the variable-area supercharger control valve based on a set closed-loop enabling condition to determine a first requested duty cycle;

[0009] Limiting the first requested duty cycle to obtain a second requested duty cycle;

[0010] Determine the friction force compensation duty cycle according to the opening deviation;

[0011] Determine the compensation coefficient based on the actual system voltage and the set standard voltage;

[0012] determining a final requested duty cycle according to the second requested duty cycle, the friction compensation duty cycle, and the compensation coefficient;

[0013] The opening of the variable-geometry supercharger control valve is controlled at the final requested duty ratio.

[0014] According to the above solution, the method for determining the required opening value based on the input initial opening request includes:

[0015] Determine the required position value based on the initial required opening value and the maximum position value and minimum position value obtained through self-learning;

[0016] Determine the required angle value based on the required position value and the set position angle coefficient;

[0017] Limit the rate of change of the required angle value to within the set range;

[0018] The required opening value is determined based on the limited required angle value.

[0019] According to the above solution, the method of limiting the rate of change of the required angle value to within a set range includes:

[0020] Determine the demand angle value deviation based on the limited demand angle value at the previous moment and the demand angle value at the current moment;

[0021] Perform table lookup and linear interpolation processing according to the demand opening value to determine the maximum limit rate and minimum limit rate of the demand angle value deviation, and limit the rate of change of the demand angle value deviation according to the maximum limit rate and minimum limit rate of the demand angle value deviation;

[0022] The single change gradient step length of the demand angle value is determined according to the change rate of the demand angle value deviation and the set calculation cycle.

[0023] According to the above scheme, the closed-loop enabling condition is:

[0024] a) an externally inputted boost pressure request value reaches a set boost pressure demand value; the boost pressure request value is obtained by obtaining the external input;

[0025] b) The intake air flow rate deviation exceeds the minimum limit value of the closed-loop control; the intake air flow rate deviation is determined based on the actual intake air flow rate;

[0026] The method of performing PID closed-loop control on the opening of the variable-area supercharger control valve based on the set closed-loop enabling condition to determine the first requested duty cycle includes:

[0027] According to the opening deviation and the required opening value, a table lookup and linear interpolation process are performed to determine the output duty cycle of item P;

[0028] Determine the P-item coefficient value based on the P-item output duty cycle and opening deviation;

[0029] According to the opening deviation and the opening deviation change rate, a table lookup and linear interpolation process are performed to determine the I-term integral single-step incremental gain coefficient; the opening deviation change rate is determined according to the opening deviation and the set calculation period;

[0030] Determining the first integral single-step increment based on the first integral single-step increment gain coefficient, the opening deviation, and the PID final duty cycle over-limit correction value; the PID final duty cycle over-limit correction value is determined based on the correction value and a set over-limit limit rate, and the correction value is determined based on the value of the first requested duty cycle in the previous calculation cycle and the set limit value;

[0031] Determine the I term coefficient value according to the value of the I term coefficient value in the previous calculation cycle, the I term integral single-step increment gain coefficient, and the I term integral single-step increment;

[0032] According to the opening deviation and the opening deviation change rate, a table lookup and linear interpolation process are performed to determine the D-term gain coefficient;

[0033] Determine the D-term coefficient value based on the D-term gain coefficient and the opening deviation change rate;

[0034] A first requested duty cycle is determined according to the P-term coefficient value, the I-term coefficient value, and the D-term coefficient value.

[0035] According to the above scheme, the method for determining the value of the coefficient value of item I in the previous calculation cycle is as follows:

[0036] When the set correction activation conditions are met, the value of the I coefficient in the previous calculation cycle is corrected;

[0037] The modification activation conditions include:

[0038] 1) The externally input boost pressure request value reaches the minimum required value for the normal and stable operation of the valve;

[0039] 2) The opening deviation is less than the set value;

[0040] 3) The opening deviation change rate is less than the set value;

[0041] The method for correcting the value of the coefficient value of item I in the previous calculation cycle includes:

[0042] When the single-step increment of the I-term integral is positive, the value of the I-term coefficient in the previous calculation cycle is reduced by a fixed step length;

[0043] When the single-step increment of the I-term integral is negative, the I-term coefficient value in the previous calculation cycle is increased by a fixed step length;

[0044] When the absolute value of the coefficient value of item I in the previous calculation cycle is less than the set value, the coefficient value of item I in the previous calculation cycle is set to 0.

[0045] According to the above scheme, the method for determining the coefficient value of item I includes:

[0046] Limit the I-term coefficient value to between the set maximum I-term coefficient value and the minimum I-term coefficient value;

[0047] The required opening value is zero, and the actual opening value is zero, so the I coefficient value is zero.

[0048] According to the above solution, the method of limiting the first requested duty cycle to obtain the second requested duty cycle includes:

[0049] When the first requested duty cycle is greater than the preset upper limit value, the maximum limit value is decreased by a set step size;

[0050] When the maximum limit value is greater than the set maximum limit value, the second duty cycle is made equal to the maximum limit value; when the maximum limit value is less than the set maximum limit value, the second duty cycle is made equal to the maximum limit value;

[0051] When the first requested duty cycle is less than the preset lower limit value, the minimum limit value is increased by a set step size;

[0052] When the minimum limit value is less than the set minimum limit value, the second duty cycle is equal to the minimum limit value; when the minimum limit value is greater than the set minimum limit value, the second duty cycle is equal to the minimum limit value.

[0053] According to the above scheme, the method for determining the friction force compensation duty cycle according to the opening deviation includes:

[0054] The friction compensation duty cycle is obtained by looking up a pre-calibrated table according to the opening deviation.

[0055] According to the above scheme, the method for determining the compensation coefficient according to the actual system voltage and the standard voltage includes:

[0056] Divide the actual system voltage by the standard voltage and use the result as the compensation coefficient.

[0057] According to the above solution, the method for determining the final requested duty cycle based on the second requested duty cycle, the friction compensation duty cycle, and the compensation coefficient includes:

[0058] The second requested duty cycle and the friction compensation duty cycle are added together and then multiplied by the compensation coefficient, and the obtained product is used as the final requested duty cycle.

[0059] The present invention has the following beneficial effects: by controlling the opening value through PID closed-loop control, the control accuracy of the variable-geometry supercharger control valve is improved, and dead-point speed limitation is achieved. Furthermore, the requested duty cycle is compensated based on friction and system voltage, further improving control accuracy. BRIEF DESCRIPTION OF THE DRAWINGS

[0060] Figure 1 This is a flow chart of a variable-section supercharger control valve control method according to a first embodiment of the present invention. DETAILED DESCRIPTION

[0061] To make the purpose, technical solutions, and advantages of the embodiments of the present disclosure more clear, the technical solutions of the embodiments of the present disclosure will be clearly and completely described below in conjunction with the accompanying drawings of the embodiments of the present disclosure. Obviously, the described embodiments are part of the embodiments of the present disclosure, not all of the embodiments. Based on the described embodiments of the present disclosure, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present disclosure.

[0062] Example 1:

[0063] See also Figure 1 This embodiment discloses a method for controlling a variable-section supercharger control valve, comprising the following steps:

[0064] S1. Determine the required opening value based on the input initial required opening value.

[0065] Specifically, S1 includes the following steps:

[0066] S101. Determine the required opening value Pos ab :

[0067] Pos ab =Pos raw 100% (Pos max -Pos min )+Pos min ;

[0068] Among them, Pos raw is the initial required opening value, Pos max The maximum opening position of the valve after self-learning (not necessarily 100%), Pos min The minimum opening position of the valve after self-learning (not necessarily 0%);

[0069] S102, the required opening value Pos ab Multiply by the corresponding angle position coefficient to convert to the required angle value Pos ang ;

[0070] S103, limiting the change rate of the required angle value to within a set range;

[0071] Specifically, S103 includes:

[0072] S1031, according to the required angle value Pos after the previous moment ang_ , the demand angle value Pos at this moment ang , determine the required angle value deviation is error = Pos ang -Pos ang_z ;

[0073] S1032, according to the required opening value Pos des Perform table lookup and linear interpolation processing to determine the maximum limit rate and minimum limit rate of the demand angle value deviation error, and limit the rate of change of the demand angle value deviation error based on the maximum limit rate and minimum limit rate of the demand angle value deviation error;

[0074] It should be understood that the change rate of the demand angle value deviation error multiplied by the duration of a single calculation cycle is the single change gradient step of the demand angle value deviation error. In this embodiment, the calculation cycle is 10ms.

[0075] S104: Reversely convert the required angle value after the limit to obtain the required opening value Pos des .

[0076] S2. Determine an opening deviation according to the required opening value and the actual opening value, and perform PID closed-loop control on the opening of the variable-area supercharger control valve based on a set closed-loop enabling condition to determine a first requested duty cycle.

[0077] Among them, the closed-loop enabling conditions are set as follows:

[0078] a) The externally inputted boost pressure request value reaches the set boost pressure demand value; the boost pressure request value is obtained by obtaining the external input; the boost pressure demand value is the minimum required value (relative pressure, in this example, 3 kPa) for achieving normal and stable operation of the valve;

[0079] b) The intake air flow deviation exceeds the minimum limit value of the closed-loop control; the intake air flow deviation is determined according to the actual intake air flow; in this embodiment, the intake air flow deviation Air err =Air act -Air min , of which Air act The actual current intake air flow rate can be obtained through conventional flow sensors or general speed density method. min is the set value, which is 0 in this embodiment;

[0080] Specifically, step S2 includes:

[0081] S201. Determine an opening deviation based on the required opening value and the actual opening value, that is, subtract the actual opening value from the required opening value to obtain the opening deviation, and further divide the opening deviation by the calculation period to obtain the opening deviation change rate;

[0082] S202, performing table lookup and linear interpolation processing based on the opening deviation and the required opening value to determine the P-term coefficient value;

[0083] The X-axis and Y-axis of the table are opening deviation POS err_ (In this example, -50 and 50 are used as the minimum and maximum values, respectively, with a fixed interval of 10 vector values) and the required opening value POS des_ (This embodiment uses 0 and 100 as the minimum and maximum values, respectively, with a fixed interval of 10 vector values), the Z axis is the preset P item output duty cycle P gain ; The table lookup and linear interpolation processing is specifically based on the current actual opening deviation POS err and the required opening value POS des Perform X, Y interpolation to determine the P item output duty cycle P gain , calculate the P coefficient value Pct P =POS err *P gain , ensuring that the control duty cycle is small when the valve is close to the dead center;

[0084] S203, performing table lookup and linear interpolation processing according to the opening deviation and the opening deviation change rate to determine the I-term integral single-step incremental gain coefficient;

[0085] The X-axis and Y-axis of the table are opening deviation POS err_ (In this example, -50 and 50 are used as the minimum and maximum values, respectively, with a fixed interval of 10 vector values) and the opening deviation change rate POS err__ (In this embodiment, -50 and 50 are used as the minimum and maximum values, respectively, with a fixed interval of 10 vector values), the Z axis is the preset I-term integral single-step incremental gain coefficient I gain ; The table lookup and linear interpolation processing is specifically based on the current actual opening deviation POS err and opening deviation change rate POS err_ Perform X, Y interpolation to determine the I-term integral single-step incremental gain coefficient I gain , can control the valve integration speed at different target deviations and action speeds;

[0086] S204, based on the I-term integral single-step incremental gain coefficient I gain , opening deviation POS errAnd the PID final duty cycle over-limit correction value, determine the I-term integral single-step increment;

[0087] Pct wind =Pct sat *K wind

[0088] In the above formula, Pct wind K is the PID final duty cycle over-limit correction value, wind is the limiting rate coefficient,

[0089] The larger the value, the faster the limit. It is a calibrable value. In this example, it is 0.1. Pct sat is the correction value;

[0090] Pct sat =Pct final_ -100%

[0091] In the above formula, Pct final_ is the value of the final requested duty cycle in the previous cycle, and 100% is the limit value taken in this embodiment;

[0092] I step =POS err -Pct wind

[0093] In the above formula, I step is the position deviation after correction;

[0094] Pct I_ =I gain *I step

[0095] In the above formula, Pct I_ is the single-step increment of the I-term integral.

[0096] S205, determining the value of item I according to the value of the coefficient of item I in the previous calculation cycle and the single-step increment of the integral of item I;

[0097] I-term coefficient value Pct I =Pct I_ +Pct I_ ; Among them, Pct I_ is the value of the coefficient of item I in the previous calculation cycle; on this basis, the coefficient value of item I is restricted as follows:

[0098] The I-term coefficient value is limited to between the set maximum I-term coefficient value (100% in this embodiment) and the minimum I-term coefficient value (-100% in this embodiment);

[0099] Furthermore, the shutdown control is performed on the coefficient value of item I:

[0100] When the required opening value is zero and the actual opening value is zero (i.e. the engine has stopped), the I coefficient value is set to zero; the valve is parked at zero position to prevent the engine from starting again and the integral term from affecting the control;

[0101] Furthermore, when the following activation correction conditions are met, the value Pct of the coefficient value of item I in the previous calculation cycle is I_ Make corrections:

[0102] 1) The externally input boost pressure request value reaches the set minimum required value for normal and stable valve operation (relative pressure, 3 kPa in this embodiment);

[0103] 2) Opening deviation POS err Less than the set value POS deadband (This embodiment takes 0.1);

[0104] 3) Opening deviation change rate POS err_ Less than the set value POS deadband (This embodiment takes 0.1);

[0105] The value Pct of the coefficient value of item I in the previous calculation cycle I_ The specific method for correction is:

[0106] When the I-term integral single-step increment Pct I_ When it is positive, the coefficient value of item I is equal to the value Pct of the previous calculation cycle. I_ Reduce the fixed step size; expressed as: Pct I__ =Pct I_ -I const ; Among them, Pct I__ Indicates the value of the revised I coefficient in the previous calculation period, I const Indicates the set fixed step size;

[0107] When the I-term integral single-step increment Pct I_ When it is negative, the coefficient value of item I is Pct of the previous calculation cycle. I_ Increase fixed step size I const ; Expressed as: Pct I__ =Pct I_ +I const

[0108] When the absolute value of the coefficient value of item I in the previous calculation cycle is less than the set value (0.1 in this embodiment, and can be set to a positive value close to 0 in other embodiments), the coefficient value of item I in the previous calculation cycle is set to 0.

[0109] S206, according to the opening deviation and the opening deviation change rate, the table lookup and linear interpolation are performed to determine the D-term gain coefficient; wherein the X-axis and Y-axis of the table are the opening deviation POSerr_ (In this example, -50 and 50 are used as the minimum and maximum values, respectively, with a fixed interval of 10 vector values) and the opening deviation change rate POS err__ (In this embodiment, -50 and 50 are used as the minimum and maximum values, respectively, with a fixed interval of 10 vector values), the Z axis is the preset D-term gain coefficient D gain ; The table lookup and linear interpolation processing is specifically based on the current actual opening deviation POS err and opening deviation change rate POS err_ Perform X, Y interpolation to determine the D gain coefficient D gain , in order to control the differential speed of the valve at different target deviations and action speeds. The specific method is to err The larger the D gain The larger the calibration, the faster the differential speed when the deviation is large.

[0110] S207, determining the D-term coefficient value according to the D-term gain coefficient and the opening deviation change rate;

[0111] D-term coefficient value Pct D =D gain *POS err_ .

[0112] S208, determine the first requested duty cycle according to the P-item coefficient value, the I-item coefficient value, and the D-item coefficient value; specifically, the P-item coefficient value, the I-item coefficient value Pct I 、D coefficient value Pct D Add and get the first requested duty cycle Pct PID

[0113] S3. Limit the first requested duty cycle to obtain a second requested duty cycle.

[0114] It can be understood that the VGT control valve is a PWM control valve. The characteristic of this valve is to change the switching period and duty cycle of the solenoid valve to control the duty cycle. Different valves from different manufacturers have different tolerance to large currents, so current protection is required, that is, control of the valve control duty cycle.

[0115] Specifically, S3 includes:

[0116] S301: When the first requested duty cycle Pct PID Greater than the preset upper limit Lim enbl (50% in this embodiment) when the maximum limit value Lim max Press the set step length Lim step Descending:

[0117] Lim max =Lim max_ -Lim step

[0118] In the above formula, Lim max_ is the value of the maximum limit value in the previous calculation cycle. The initial value of the maximum limit value is set to 100% in this embodiment;

[0119] When the maximum limit value Lim max Greater than the set maximum limit value Lim maxDC When the second duty cycle Pct out Equal to the maximum limit value Lim max , when the maximum limit value Lim max When the value is less than the set maximum limit value, Lim maxDC , so that the second duty cycle Pct out Equal to the maximum limit value Lim maxDC ; In this embodiment, the maximum limit value Lim maxDC Set to 40%;

[0120] S302, when the first request occupancy Pct PID Less than the preset lower limit Lim disb (This embodiment takes -50%), the minimum limit value Lim min Press the set step length Lim step Incremental:

[0121] Lim min =Lim min_ +Lim step

[0122] In the above formula, Lim min_ The value of the minimum limit value in the previous calculation cycle. The initial value of the minimum limit value is set to -100% in this embodiment.

[0123] When the minimum limit value Lim min Less than the set minimum limit value Lim minDC When the second duty cycle Pct out Equal to the minimum limit value Lim min , when the minimum limit value Lim min Greater than the set minimum limit value Lim minDC When the second duty cycle Pct out Equal to the minimum limit value.

[0124] S4. Determine the friction force compensation duty cycle according to the opening deviation.

[0125] It should be understood that friction compensation is determined by the characteristics of the valve body. When the deviation between the valve target position and the actual position is greater, the valve action is faster and greater friction compensation is required. Therefore, the valve characteristic curve is based on different valve position deviations.

[0126] In this embodiment, the opening deviation and friction compensation duty cycle Pct determined by calibration fric The relationship is as follows:

[0127] Opening deviation (%) -10 -5 0 5 10 Friction compensation duty cycle (%) -6 -3 0 3 6

[0128] S5. Determine the compensation coefficient based on the actual system voltage and the set standard voltage.

[0129] Compensation coefficient K = U real / U nom , where U real is the current actual system voltage, U nom is the set standard voltage, in this embodiment, U nom Take 12V.

[0130] S6. Determine a final requested duty cycle according to the second requested duty cycle, the friction compensation duty cycle, and the compensation coefficient.

[0131] Final duty cycle Pct final =(Pct out +Pct fric )*K.

[0132] S7. Control the opening of the variable-geometry supercharger control valve according to the final requested duty ratio.

[0133] It should be understood that the size of the serial numbers of the steps in the above embodiments does not mean the order of execution. The execution order of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of the embodiments of this application.

[0134] Example 2:

[0135] This embodiment discloses a computer device, which includes at least but not limited to: a memory and a processor that can be communicatively connected to each other via a system bus.

[0136] In this embodiment, the memory (i.e., readable storage medium) includes flash memory, hard disk, multimedia card, card-type memory (e.g., SD or DX memory), random access memory (RAM), static random access memory (SRAM), read-only memory (ROM), electrically erasable programmable read-only memory (EEPROM), and programmable read-only memory (PROM). The memory may also be an external storage device of a computer device, such as a plug-in hard disk equipped with the computer device, a smart memory card (SmartMedia Card, SMC), a secure digital (Secure Digital, SD) card, a flash card, etc. Of course, the memory may also include both the internal storage unit of the computer device and its external storage device. In this embodiment, the memory is generally used to store the operating system and various application software installed on the computer device, such as the program code for implementing the variable geometry supercharger control valve control method described in Example 1. In addition, the memory may also be used to temporarily store various types of data that have been output or are about to be output.

[0137] In some embodiments, the processor may be a central processing unit (CPU), a controller, a microcontroller, a microprocessor, or other data processing chip. The processor is generally used to control the overall operation of a computer device. In this embodiment, the processor is used to run program code stored in a memory or process data, such as the program code for implementing the variable area supercharger control valve control method described in Example 1 to achieve precise control of the variable area supercharger control valve.

[0138] Example 3:

[0139] This embodiment provides a computer-readable storage medium, such as a flash memory, a hard disk, a multimedia card, a card-type memory (e.g., an SD or DX memory), a random access memory (RAM), a static random access memory (SRAM), a read-only memory (ROM), an electrically erasable programmable read-only memory (EEPROM), a programmable read-only memory (PROM), a magnetic memory, a disk, an optical disk, a server, an App store, etc., on which a computer program is stored, and when the program is executed by a processor, a corresponding function is implemented. The computer-readable storage medium of this embodiment is used to implement the program code of the variable-section supercharger control valve control method described in Example 1, so as to achieve precise control of the variable-section supercharger control valve.

[0140] It should be pointed out that, according to the needs of implementation, the various steps / components described in this application can be split into more steps / components, or two or more steps / components or partial operations of steps / components can be combined into new steps / components to achieve the purpose of the present invention.

[0141] The above descriptions are merely embodiments of the present invention and are not intended to limit the patent scope of the present invention. Any equivalent structure or equivalent process transformation made using the contents of the present invention's description and drawings, or directly or indirectly applied in other related technical fields, are also included in the patent protection scope of the present invention.

Claims

1. A variable area supercharger control valve control method, characterized in that: include: Determine the required opening value according to the input initial required opening value; Determining an opening deviation based on the required opening value and the actual opening value, and performing PID closed-loop control on the opening of the variable-area supercharger control valve based on a set closed-loop enabling condition to determine a first requested duty cycle; Limiting the first requested duty cycle to obtain a second requested duty cycle; Determine the friction force compensation duty cycle according to the opening deviation; Determine the compensation coefficient based on the actual system voltage and the set standard voltage; determining a final requested duty cycle according to the second requested duty cycle, the friction compensation duty cycle, and the compensation coefficient; The opening of the variable-geometry supercharger control valve is controlled at the final requested duty ratio.

2. The variable area supercharger control valve control method according to claim 1, characterized in that: The method for determining the required opening value based on the input initial required opening value includes: Determine the required position value based on the initial required opening value and the maximum position value and minimum position value obtained through self-learning; Determine the required angle value based on the required position value and the set position angle coefficient; Limit the rate of change of the required angle value to within the set range; The required opening value is determined based on the limited required angle value.

3. The variable area supercharger control valve control method according to claim 2, characterized in that: The method for limiting the rate of change of the required angle value to within a set range includes: Determine the demand angle value deviation based on the limited demand angle value at the previous moment and the demand angle value at the current moment; Perform table lookup and linear interpolation processing according to the demand opening value to determine the maximum limit rate and minimum limit rate of the demand angle value deviation, and limit the rate of change of the demand angle value deviation according to the maximum limit rate and minimum limit rate of the demand angle value deviation; The single change gradient step length of the demand angle value is determined according to the change rate of the demand angle value deviation and the set calculation cycle.

4. The variable area supercharger control valve control method according to claim 2, characterized in that: The closed-loop enabling condition is: a) an externally inputted boost pressure request value reaches a set boost pressure demand value; the boost pressure request value is obtained by obtaining the external input; b) The intake air flow deviation exceeds the minimum limit value of the closed-loop control; the intake air flow deviation is determined based on the actual intake air flow; The method of performing PID closed-loop control on the opening of the variable-area supercharger control valve based on the set closed-loop enabling condition to determine the first requested duty cycle includes: According to the opening deviation and the required opening value, a table lookup and linear interpolation process are performed to determine the output duty cycle of item P; Determine the P-item coefficient value based on the P-item output duty cycle and opening deviation; According to the opening deviation and the opening deviation change rate, a table lookup and linear interpolation process are performed to determine the I-term integral single-step incremental gain coefficient; the opening deviation change rate is determined according to the opening deviation and the set calculation period; Determining the first integral single-step increment based on the first integral single-step increment gain coefficient, the opening deviation, and the PID final duty cycle over-limit correction value; the PID final duty cycle over-limit correction value is determined based on the correction value and a set over-limit limit rate, and the correction value is determined based on the value of the first requested duty cycle in the previous calculation cycle and the set limit value; Determine the I term coefficient value according to the value of the I term coefficient value in the previous calculation cycle, the I term integral single-step increment gain coefficient, and the I term integral single-step increment; According to the opening deviation and the opening deviation change rate, a table lookup and linear interpolation process are performed to determine the D-term gain coefficient; Determine the D-term coefficient value based on the D-term gain coefficient and the opening deviation change rate; A first requested duty cycle is determined according to the P-term coefficient value, the I-term coefficient value, and the D-term coefficient value.

5. The variable area supercharger control valve control method according to claim 4, characterized in that: The method for determining the value of the coefficient value of item I in the previous calculation cycle is as follows: When the set correction activation conditions are met, the value of the I coefficient in the previous calculation cycle is corrected; The modification activation conditions include: 1) The externally input boost pressure request value reaches the minimum required value for the normal and stable operation of the valve; 2) The opening deviation is less than the set value; 3) The opening deviation change rate is less than the set value; The method for correcting the value of the coefficient value of item I in the previous calculation cycle includes: When the single-step increment of the I-term integral is positive, the value of the I-term coefficient in the previous calculation cycle is reduced by a fixed step length; When the single-step increment of the I-term integral is negative, the I-term coefficient value in the previous calculation cycle is increased by a fixed step length; When the absolute value of the coefficient value of item I in the previous calculation cycle is less than the set value, the coefficient value of item I in the previous calculation cycle is set to 0.

6. The variable area supercharger control valve control method according to claim 4, characterized in that: The method for determining the coefficient value of item I includes: Limit the I-term coefficient value to between the set maximum I-term coefficient value and the minimum I-term coefficient value; The required opening value is zero, and the actual opening value is zero, so the I coefficient value is zero.

7. The variable area supercharger control valve control method according to claim 1, characterized in that: The method of limiting the first requested duty cycle to obtain the second requested duty cycle includes: When the first requested duty cycle is greater than a preset upper limit value, the maximum limit value is decreased by a set step size; when the maximum limit value is greater than the set maximum limit value, the second duty cycle is made equal to the maximum limit value; when the maximum limit value is less than the set maximum limit value, the second duty cycle is made equal to the maximum limit value; When the first requested duty cycle is less than the preset lower limit value, the minimum limit value is increased by the set step size; when the minimum limit value is less than the set minimum limit value, the second duty cycle is equal to the minimum limit value; when the minimum limit value is greater than the set minimum limit value, the second duty cycle is equal to the minimum limit value.

8. The variable area supercharger control valve control method according to claim 1, characterized in that: The method for determining the friction compensation duty cycle according to the opening deviation includes: The friction compensation duty cycle is obtained by looking up a pre-calibrated table according to the opening deviation.

9. The variable area supercharger control valve control method according to claim 1, characterized in that: The method for determining the compensation coefficient according to the actual system voltage and the standard voltage includes: Divide the actual system voltage by the standard voltage and use the result as the compensation coefficient.

10. The variable area supercharger control valve control method according to claim 1, characterized in that: The method for determining the final requested duty cycle according to the second requested duty cycle, the friction compensation duty cycle, and the compensation coefficient includes: The second requested duty cycle and the friction compensation duty cycle are added together and then multiplied by the compensation coefficient, and the obtained product is used as the final requested duty cycle.

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