A wind tunnel rotor airfoil high-frequency dynamic test drive system and optimization control method

Abstract

A high-frequency dynamic test drive system and optimization control method for a wind tunnel rotor airfoil belongs to the field of wind tunnel testing technology. To solve the problem of high-precision control of the amplitude and phase of high-frequency sinusoidal motion, the present invention fixes a high-frequency hydraulic swing cylinder on the first support seat, and the rotating shaft of the high-frequency hydraulic swing cylinder is connected to one end of the airfoil test piece through a tightening sleeve, and the free end of the airfoil test piece is supported on the second support seat; a first photoelectric encoder is installed on the high-frequency hydraulic swing cylinder, and a second photoelectric encoder is installed on the free end of the airfoil test piece; the hydraulic oil of the hydraulic oil source pump station acts on the high-frequency hydraulic swing cylinder through an electro-hydraulic servo valve, and the hydraulic oil in the bearing chamber of the high-frequency hydraulic swing cylinder is discharged into the hydraulic oil source pump station through an oil pump; the electro-hydraulic servo valve, the first photoelectric encoder, the second photoelectric encoder, and the hydraulic oil source pump station are respectively connected to a hydraulic controller, and the hydraulic controller is connected to a host control computer. The present invention effectively improves the control accuracy of high-frequency sinusoidal motion.

Description

Technical Field

[0001] The present invention belongs to the technical field of wind tunnel testing, and in particular relates to a high-frequency dynamic test drive system for a wind tunnel rotor airfoil and an optimization control method. Background Art

[0002] During helicopter flight, the rotor blades are constantly exposed to a typical unsteady, asymmetric aerodynamic environment, which can produce significant dynamic stall and, in severe cases, stall flutter, affecting rotor life and flight safety. With the continuous development of my country's helicopter technology and the continuous improvement of helicopter performance, rotor motion has become more complex and the unsteady aerodynamic forces it is subject to have become more severe. Therefore, the future development of my country's high-end helicopter equipment requires systematic analysis of rotor dynamic stall and research on its mechanisms.

[0003] At present, wind tunnel dynamic testing technology for rotor airfoils remains an important technical means for conducting dynamic stall analysis and mechanism research on rotors. Research on dynamic test technology for rotor airfoils has been carried out in Europe and the United States for a long time. The test equipment capabilities basically meet the research needs for unsteady aerodynamic forces on rotors. The model oscillation motion indicators can meet the simulation of high-order vibration modes of helicopter rotors, with oscillation frequencies exceeding 70Hz and amplitudes reaching 5°. Existing domestic airfoil dynamic test equipment generally uses servo motors + speed bumps / cam mechanisms for driving. These devices have disadvantages such as complex drive mechanisms, low motion indicators, and low control accuracy. The dynamic test frequency is often within 20Hz, making it impossible to carry out high-frequency vibration test research. The test capabilities cannot meet the research needs of dynamic stall analysis of rotor airfoils. Summary of the Invention

[0004] The problem to be solved by the present invention is to achieve high-precision control of the amplitude and phase of high-frequency sinusoidal motion, and propose a high-frequency dynamic test drive system for a wind tunnel rotor airfoil and an optimization control method.

[0005] To achieve the above object, the present invention is implemented through the following technical solutions:

[0006] A high-frequency dynamic test drive system for a wind tunnel rotor airfoil includes a high-frequency hydraulic swing cylinder, an electro-hydraulic servo valve, a first photoelectric encoder, a locking sleeve, a second photoelectric encoder, a second support base, a first support base, a hydraulic oil source pump station, an oil pump, a host control computer, and a hydraulic controller.

[0007] A high-frequency hydraulic swing cylinder is fixedly mounted on the first support seat, the rotating shaft of the high-frequency hydraulic swing cylinder is connected to one end of the airfoil test piece via a tightening sleeve, the other end of the airfoil test piece is supported on the second support seat, and a second photoelectric encoder is mounted on the other end of the airfoil test piece; the first photoelectric encoder is mounted on the high-frequency hydraulic swing cylinder;

[0008] The oil outlet of the high-frequency hydraulic swing cylinder is connected to the electro-hydraulic servo valve, the electro-hydraulic servo valve is connected to the hydraulic oil source pump station, the hydraulic oil source pump station is connected to the oil pump, and the oil pump is connected to the oil inlet of the high-frequency hydraulic swing cylinder;

[0009] The high-frequency hydraulic swing cylinder, the first photoelectric encoder, the second photoelectric encoder, and the hydraulic oil source pump station are respectively connected to a hydraulic controller, and the hydraulic controller is connected to a host control computer.

[0010] Furthermore, the hydraulic oil source pump station provides hydraulic oil with a constant pressure of 21 MPa.

[0011] Furthermore, the electro-hydraulic servo valve is a three-position, four-way, high-frequency response electro-hydraulic servo valve.

[0012] An optimization control method for a high-frequency dynamic test drive system for a wind tunnel rotor airfoil is implemented based on the aforementioned high-frequency dynamic test drive system for a wind tunnel rotor airfoil, and includes the following steps:

[0013] S1. Construct a position closed-loop control model for the drive system of a high-frequency dynamic test of a rotor airfoil in a wind tunnel;

[0014] S2. Based on the position closed-loop control model constructed in step S1, a high-frequency sinusoidal motion amplitude and phase adaptive compensation control method is constructed to obtain an optimized control model with an amplitude and phase adaptive compensation algorithm;

[0015] S3. Based on the optimized control model with the amplitude and phase adaptive compensation algorithm obtained in step S2, a control strategy for the start and stop of the high-frequency hydraulic swing cylinder of the wind tunnel rotor airfoil high-frequency dynamic test drive system is set up with a constant-amplitude variable-frequency sinusoidal motion slow start and stop control strategy. This results in the final optimized optimized control method for the wind tunnel rotor airfoil high-frequency dynamic test drive system.

[0016] Furthermore, the expression of the position closed-loop control model of the drive system for the high-frequency dynamic test of the wind tunnel rotor airfoil in step S1 is:

[0017] ;

[0018] in, To control the output, is the control input, To control the error, is the first-order velocity feedforward gain, is the second-order acceleration feedforward gain, is the proportionality coefficient, is the integration coefficient, is the differential coefficient, and t is the time.

[0019] Furthermore, the specific implementation method of the amplitude and phase adaptive compensation control algorithm in step S2 includes the following steps:

[0020] S2.1. Constructing an amplitude adaptive compensation control method:

[0021] The sinusoidal motion function expression of the high-frequency hydraulic swing cylinder is defined as:

[0022] ;

[0023] in, is the position of the swing cylinder at time t, is the amplitude, is the oscillation frequency, is the phase, is the oscillation equilibrium position;

[0024] definition is the input command amplitude, is the target amplitude, is the actual amplitude of the sinusoidal motion of the high-frequency hydraulic swing cylinder, is the maximum value of sinusoidal motion; is the minimum value of sinusoidal motion; is the amplitude difference between the actual amplitude and the target amplitude; is the amplitude proportional gain, satisfying ;

[0025] The actual amplitude of the sinusoidal motion of the high-frequency hydraulic swing cylinder is expressed as:

[0026] ;

[0027] The difference between the actual amplitude and the target amplitude is expressed as:

[0028] ;

[0029] Add a proportional control link to the amplitude of the sinusoidal motion, and adjust the set amplitude adaptively through the proportional link to continuously adjust After a cycle, the amplitude difference When the deviation is within the allowable range, the adjustment is stopped and the expression of the input command amplitude is:

[0030] ;

[0031] Where, i is the i-th cycle;

[0032] S2.2. Constructing a phase adaptive compensation control method:

[0033] definition is the target frequency, is the target phase, To set the phase, is the time difference between the actual motion curve and the command curve over the oscillation equilibrium position, is the phase difference between the actual motion curve and the command curve, is the phase proportional gain, satisfying , then the phase difference The expression is:

[0034] ;

[0035] in, satisfy ;

[0036] Based on the phase difference, the phase of the sinusoidal motion is increased by proportional control, and the phase is adaptively adjusted through the proportional link to continuously adjust the phase. After a cycle, the phase difference If the deviation is within the allowable range, stop adjusting.

[0037] The final expression for setting the phase of the sinusoidal command is:

[0038] ;

[0039] Where, j is the jth cycle;

[0040] S2.3. When executing the amplitude adaptive compensation control method and the phase adaptive compensation control method, the amplitude difference and phase difference are automatically calculated in each cycle. The proportional control link adjusts and updates the set amplitude and phase of the sinusoidal motion, so that the actual motion curve gradually approaches the command curve until it enters the allowable deviation range. The final position of the high-frequency hydraulic swing cylinder after compensation at time t is expressed as:

[0041] ;

[0042] in, is the position of the high-frequency hydraulic swing cylinder at time t.

[0043] Furthermore, the specific implementation method of step S3 includes the following steps:

[0044] Make the sinusoidal motion with the initial frequency =0.8Hz starts to move, and the frequency increases with each sine cycle =0.2Hz, the sinusoidal motion of the high-frequency hydraulic swing cylinder in slow start / slow stop mode can be expressed as:

[0045] ;

[0046] in, For the A sinusoidal motion cycle, is the initial frequency, is the variable frequency step;

[0047] The following conditions are met:

[0048] ;

[0049] in, is the target frequency;

[0050] Set up a high-frequency hydraulic swing cylinder to fix the amplitude ,frequency =0.8Hz to start the sinusoidal motion, and the frequency increases by 0.2Hz for each sinusoidal cycle until the oscillation frequency reaches the target frequency After that, a stable sinusoidal motion is performed at the target frequency;

[0051] After data collection is completed, the deceleration and stop process is also to reduce the frequency by 0.2Hz per sine cycle until it reaches the initial frequency. Then stop exercising.

[0052] Beneficial effects of the present invention:

[0053] The wind tunnel rotor airfoil high-frequency dynamic test drive system described in the present invention adopts a high-frequency hydraulic swing cylinder as the drive device, which is rigidly connected to the airfoil test piece through a clamping sleeve. The high torque and high-frequency response characteristics of the hydraulic swing cylinder are utilized to achieve a dynamic test frequency index of 70Hz. At the same time, an amplitude / phase adaptive compensation control algorithm is designed based on the composite feedforward + PID control algorithm to achieve high-precision control of the amplitude / phase of high-frequency sinusoidal motion.

[0054] The drive system for high-frequency dynamic testing of wind tunnel rotor airfoils described in this invention utilizes a hydraulic oscillating cylinder with a hydrostatic support seal as the drive device. Based on the hydrostatic support seal's characteristics of zero friction, zero viscosity, high frequency response, and high operating speed, it is coupled with a high-frequency electro-hydraulic servo valve and a hydraulic oil source pump station with sufficient flow to achieve 70Hz / 5° high-frequency sinusoidal motion, meeting the equipment requirements for high-frequency dynamic testing of airfoils. A clamping sleeve is used to rigidly connect the hydraulic oscillating cylinder's output shaft to the airfoil test piece, allowing the oscillating cylinder to directly drive the airfoil test piece, avoiding the problems of transmission backlash and test piece motion phase lag that can occur during high-frequency reciprocating motion with transmission methods such as cam mechanisms or elastic couplings.

[0055] The optimized control method for a high-frequency dynamic test drive system for wind tunnel rotor airfoils, described in this paper, effectively improves the control accuracy of high-frequency sinusoidal motion. Combined with the controller's ultra-high cycle time of 0.125µs, it achieves ultra-high-precision curve following with an amplitude difference of no more than 1% and a phase difference of no more than 3° when executing 70Hz / 5° motion targets. The designed constant-amplitude variable-frequency slow start and stop control strategy effectively addresses the significant overload shock associated with high-frequency sinusoidal motion reaching the test frequency instantaneously, ensuring that the test equipment safely and smoothly achieves its motion targets without damaging the equipment. BRIEF DESCRIPTION OF THE DRAWINGS

[0056] Figure 1 This is a schematic structural diagram of a wind tunnel rotor airfoil high-frequency dynamic test drive system;

[0057] Figure 2 This is the principle block diagram of the composite feedforward + PID control algorithm;

[0058] Figure 3 This is a comparison diagram between the actual curve and the command curve before using the amplitude / phase adaptive compensation control algorithm;

[0059] Figure 4 This is a comparison diagram between the actual curve and the command curve after using the amplitude / phase adaptive compensation control algorithm;

[0060] Figure 5 This is a comparison chart of the actual curve and command curve of high-frequency sinusoidal motion under the 70Hz / 5° indicator;

[0061] Figure 6 This is a schematic diagram of a constant amplitude variable frequency slow start / slow stop motion (taking 5° / 2Hz sinusoidal motion as an example);

[0062] Figure 7 This is a flowchart for initializing the drive system for a high-frequency dynamic test of a wind tunnel rotor airfoil;

[0063] Among them, 1 is a high-frequency hydraulic swing cylinder, 2 is an electro-hydraulic servo valve, 3 is the first photoelectric encoder, 4 is a expansion sleeve, 5 is an airfoil test piece, 6 is a second photoelectric encoder, 7 is a second support seat, 8 is a first support seat, 9 is a hydraulic oil source pump station, 10 is a pumping pump, 11 is a host control computer, and 12 is a hydraulic controller. DETAILED DESCRIPTION

[0064] In order to make the objectives, technical solutions, and advantages of the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are only intended to explain the present invention and are not intended to limit the present invention. That is, the specific embodiments described herein are only some embodiments of the present invention, not all embodiments. Generally, the components of the specific embodiments of the present invention described and illustrated in the drawings herein can be arranged and designed in various different configurations, and the present invention can also have other embodiments.

[0065] Therefore, the following detailed description of the specific embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the invention as claimed, but is merely representative of selected specific embodiments of the present invention. All other specific embodiments obtained by those skilled in the art based on the specific embodiments of the present invention without making any creative efforts shall fall within the scope of protection of the present invention.

[0066] In order to further understand the content, features and effects of the present invention, the following specific embodiments are given as examples, and the attached Figure 1 -Attached Figure 7 The detailed instructions are as follows:

[0067] Example 1:

[0068] A high-frequency dynamic test drive system for a wind tunnel rotor airfoil comprises a high-frequency hydraulic swing cylinder 1, an electro-hydraulic servo valve 2, a first photoelectric encoder 3, a locking sleeve 4, a second photoelectric encoder 6, a second support base 7, a first support base 8, a hydraulic oil source pump station 9, an oil pump 10, a host control computer 11, and a hydraulic controller 12.

[0069] A high-frequency hydraulic swing cylinder 1 is fixedly mounted on the first support 8. The rotating shaft of the high-frequency hydraulic swing cylinder 1 is connected to one end of the airfoil test piece 5 via a tightening sleeve 4. The other end of the airfoil test piece 5 is supported on the second support 7. A second photoelectric encoder 6 is mounted on the other end of the airfoil test piece 5. A first photoelectric encoder 3 is mounted on the high-frequency hydraulic swing cylinder 1.

[0070] The oil outlet of the high-frequency hydraulic swing cylinder 1 is connected to the electro-hydraulic servo valve 2, the electro-hydraulic servo valve 2 is connected to the hydraulic oil source pump station 9, the hydraulic oil source pump station 9 is connected to the oil pump 10, and the oil pump 10 is connected to the oil inlet of the high-frequency hydraulic swing cylinder 1;

[0071] The high-frequency hydraulic swing cylinder 1 , the first photoelectric encoder 3 , the second photoelectric encoder 6 , and the hydraulic oil source pump station 9 are respectively connected to a hydraulic controller 12 , and the hydraulic controller 12 is connected to a host control computer 11 .

[0072] Furthermore, the hydraulic oil source pump station 9 provides hydraulic oil with a constant pressure of 21 MPa.

[0073] Furthermore, the electro-hydraulic servo valve 2 is a three-position, four-way, high-frequency response electro-hydraulic servo valve.

[0074] Furthermore, the hydraulic controller 12 implements position closed-loop control of the high-frequency hydraulic swing cylinder 1 based on an optimized position closed-loop control method.

[0075] Furthermore, based on the angle signal of the other end of the airfoil test piece 5 measured by the second photoelectric encoder 6, the angle signal of the driving end is measured by the first photoelectric encoder 3, and the angle difference between the driving end and the other end is used to judge the degree of torsional deformation of the airfoil test piece 5 in high-frequency sinusoidal motion.

[0076] Example 2:

[0077] An optimization control method for a high-frequency dynamic test drive system for a wind tunnel rotor airfoil is implemented based on the high-frequency dynamic test drive system for a wind tunnel rotor airfoil described in Example 1, and includes the following steps:

[0078] S1. Construct a position closed-loop control model for the drive system of a high-frequency dynamic test of a rotor airfoil in a wind tunnel;

[0079] Further, such as Figure 2 As shown in FIG, the basic position closed-loop control model of the drive system for the high-frequency dynamic test of the wind tunnel rotor airfoil in step S1 is expressed as follows:

[0080] ;

[0081] in, To control the output, is the control input, To control the error, is the first-order velocity feedforward gain, is the second-order acceleration feedforward gain, is the proportionality coefficient, is the integration coefficient, is the differential coefficient, and t is the time.

[0082] S2. Based on the position closed-loop control model constructed in step S1, a high-frequency sinusoidal motion amplitude and phase adaptive compensation control method is constructed to obtain an optimized control model with an amplitude and phase adaptive compensation algorithm;

[0083] Furthermore, the specific implementation method of step S2 includes the following steps:

[0084] S2.1. Constructing an amplitude adaptive compensation control method:

[0085] The sinusoidal motion function expression of the high-frequency hydraulic swing cylinder is defined as:

[0086] ;

[0087] in, is the position of the swing cylinder at time t, is the amplitude, is the oscillation frequency, is the phase, is the oscillation equilibrium position;

[0088] definition is the input command amplitude, is the target amplitude, is the actual amplitude of the sinusoidal motion of the high-frequency hydraulic swing cylinder, is the maximum value of sinusoidal motion; is the minimum value of sinusoidal motion; is the amplitude difference between the actual amplitude and the target amplitude; is the amplitude proportional gain, satisfying ;

[0089] The actual amplitude of the sinusoidal motion of the high-frequency hydraulic swing cylinder is expressed as:

[0090] ;

[0091] The difference between the actual amplitude and the target amplitude is expressed as:

[0092] ;

[0093] Add a proportional control link to the amplitude of the sinusoidal motion, and adjust the set amplitude adaptively through the proportional link to continuously adjust After a cycle, the amplitude difference When the deviation is within the allowable range, the adjustment is stopped and the expression of the input command amplitude is:

[0094] ;

[0095] Where, i is the i-th cycle;

[0096] S2.2. Constructing a phase adaptive compensation control method:

[0097] definition is the target frequency, is the target phase, To set the phase, is the time difference between the actual motion curve and the command curve over the oscillation equilibrium position, is the phase difference between the actual motion curve and the command curve, is the phase proportional gain, satisfying , then the phase difference The expression is:

[0098] ;

[0099] in, satisfy ;

[0100] Based on the phase difference, the phase of the sinusoidal motion is increased by proportional control, and the phase is adaptively adjusted through the proportional link to continuously adjust the phase. After a cycle, the phase difference If the deviation is within the allowable range, stop adjusting.

[0101] The final expression for setting the phase of the sinusoidal command is:

[0102] ;

[0103] Where, j is the jth cycle;

[0104] Furthermore, when performing sinusoidal motion, Figure 4 As shown in the figure, after the amplitude adaptive compensation control method and the phase adaptive compensation control method are executed, the controller will automatically calculate the amplitude difference and phase difference in each cycle (0.1us), adjust and update the set amplitude and set phase of the sinusoidal motion through proportional control, optimize the actual motion curve of the swing cylinder, and make the actual motion curve gradually close to the command curve until it enters the allowable deviation range; Figure 5 As shown in the figure, after the introduction of the amplitude adaptive compensation control method and the phase adaptive compensation control method, the amplitude difference of the 70Hz / 5° sinusoidal motion is less than 0.2%, and the phase difference is less than 1.5°, which meets the proposed requirements of amplitude difference ≤1% and phase difference ≤3°.

[0105] S3. Based on the optimized control model with the amplitude and phase adaptive compensation algorithm obtained in step S2, a control strategy for the start and stop of the high-frequency hydraulic swing cylinder of the wind tunnel rotor airfoil high-frequency dynamic test drive system is set up with a constant-amplitude variable-frequency sinusoidal motion slow start and stop control strategy. This results in the final optimized optimized control method for the wind tunnel rotor airfoil high-frequency dynamic test drive system.

[0106] Furthermore, the specific implementation method of step S3 includes the following steps:

[0107] Make the sinusoidal motion with the initial frequency =0.8Hz starts to move, and the frequency increases with each sine cycle =0.2Hz, the sinusoidal motion of the high-frequency hydraulic swing cylinder in slow start / slow stop mode can be expressed as:

[0108] ;

[0109] in, For the A sinusoidal motion cycle, is the initial frequency, is the variable frequency step;

[0110] The following conditions are met:

[0111] ;

[0112] in, is the target frequency;

[0113] Set up a high-frequency hydraulic swing cylinder to fix the amplitude ,frequency =0.8Hz to start the sinusoidal motion, and the frequency increases by 0.2Hz for each sinusoidal cycle until the oscillation frequency reaches the target frequency After that, a stable sinusoidal motion is performed at the target frequency;

[0114] After data collection is completed, the deceleration and stop process is also to reduce the frequency by 0.2Hz per sine cycle until it reaches the initial frequency. Then stop exercising.

[0115] Further, such as Figure 6 As shown in the figure, the slow start and slow stop motion process is introduced with an amplitude of 5° and a frequency of 2Hz as an example: the swing cylinder starts a sinusoidal motion at 5° / 0.8Hz. According to formula 9, the frequency increases by 0.2Hz for each sinusoidal cycle until the target frequency is reached. After data acquisition is complete, the frequency is reduced by 0.2 Hz per sine cycle until it reaches the initial frequency of 0.8 Hz, at which point the motion stops.

[0116] like Figure 7 As shown, the initialization operation of a high-frequency dynamic test drive system for a wind tunnel rotor airfoil is as follows:

[0117] Before normal testing, system initialization is required. The main purpose is to raise the hydraulic oil temperature to above 30°C and remove air from the hydraulic lines, so that the dynamic performance of the drive system for a high-frequency dynamic test of a wind tunnel rotor airfoil is optimized. The specific steps are as follows:

[0118] Step 1: Check the hardware equipment. If no abnormality is found, power on the hydraulic oil source pump station and control system.

[0119] Step 2: System operation, including: running the upper control computer to sequentially start the hydraulic oil source pump station, operate at a low pressure of 2MPa, enter the closed-loop control mode, increase the pressure of the hydraulic oil source pump station to 21MPa, and start the oil pump;

[0120] Step 3: Sinusoidal motion: input amplitude 30°, frequency 0.5Hz, equilibrium position 0°. After the motion parameters are sent to the hydraulic controller, the sinusoidal motion command is executed to make the high-frequency hydraulic swing cylinder perform continuous sinusoidal motion with large amplitude and low frequency.

[0121] Step 4: When the hydraulic oil temperature exceeds 30°C and the static positioning accuracy is better than 0.01°, the heating and exhaust work can be considered completed, the sinusoidal motion is stopped, the constant temperature cooling system is started, and the initialization operation is considered completed.

[0122] After the initialization operation is completed, high-frequency dynamic testing of the wind tunnel rotor airfoil can be carried out.

[0123] It should be noted that relational terms such as "first" and "second" are used only to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations. Moreover, the terms "comprises," "comprising," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus comprising a series of elements includes not only those elements, but also other elements not explicitly listed, or elements inherent to such process, method, article, or apparatus. In the absence of further limitations, an element defined by the phrase "comprising a ..." does not exclude the presence of additional identical elements in the process, method, article, or apparatus comprising the element.

[0124] Although the present application has been described above with reference to specific embodiments, various modifications may be made thereto and components may be substituted with equivalents without departing from the scope of the present application. In particular, as long as there are no structural conflicts, the various features of the embodiments disclosed herein may be combined with each other in any manner, and the omission of an exhaustive description of these combinations in this specification is solely for the sake of space and resource conservation. Therefore, the present application is not limited to the specific embodiments disclosed herein, but includes all technical solutions within the scope of the claims.

Claims

1. A high-frequency dynamic test drive system for rotor airfoils in a wind tunnel, characterized in that: It includes a high-frequency hydraulic swing cylinder (1), an electro-hydraulic servo valve (2), a first photoelectric encoder (3), a tightening sleeve (4), a second photoelectric encoder (6), a second support base (7), a first support base (8), a hydraulic oil source pump station (9), an oil pump (10), an upper control computer (11), and a hydraulic controller (12); A high-frequency hydraulic swing cylinder (1) is fixedly mounted on the first support seat (8); a rotating shaft of the high-frequency hydraulic swing cylinder (1) is connected to one end of the airfoil test piece (5) via a tightening sleeve (4); the other end of the airfoil test piece (5) is supported on the second support seat (7), and a second photoelectric encoder (6) is mounted on the other end of the airfoil test piece (5); a first photoelectric encoder (3) is mounted on the high-frequency hydraulic swing cylinder (1); The oil outlet of the high-frequency hydraulic swing cylinder (1) is connected to the electro-hydraulic servo valve (2), the electro-hydraulic servo valve (2) is connected to the hydraulic oil source pump station (9), the hydraulic oil source pump station (9) is connected to the oil pump (10), and the oil pump (10) is connected to the oil inlet of the high-frequency hydraulic swing cylinder (1); The high-frequency hydraulic swing cylinder (1), the first photoelectric encoder (3), the second photoelectric encoder (6), and the hydraulic oil source pump station (9) are respectively connected to a hydraulic controller (12), and the hydraulic controller (12) is connected to a host control computer (11).

2. A wind tunnel rotor airfoil high frequency dynamic test drive system according to claim 1, characterized in that: The hydraulic oil source pump station (9) provides hydraulic oil at a constant pressure of 21 MPa.

3. A wind tunnel rotor airfoil high frequency dynamic test drive system according to claim 1 or 2, characterized in that: The electro-hydraulic servo valve (2) is a three-position, four-way, high-frequency response electro-hydraulic servo valve.

4. A method for optimizing and controlling a drive system for a high-frequency dynamic test of a wind tunnel rotor airfoil, implemented by the drive system for a high-frequency dynamic test of a wind tunnel rotor airfoil according to any one of claims 1 to 3, characterized in that: The steps include: S1. Construct a position closed-loop control model for the drive system of a high-frequency dynamic test of a rotor airfoil in a wind tunnel; S2. Based on the position closed-loop control model constructed in step S1, a high-frequency sinusoidal motion amplitude and phase adaptive compensation control method is constructed to obtain an optimized control model with an amplitude and phase adaptive compensation algorithm; S3. Based on the optimized control model with the amplitude and phase adaptive compensation algorithm obtained in step S2, a control strategy for the start and stop of the high-frequency hydraulic swing cylinder of the wind tunnel rotor airfoil high-frequency dynamic test drive system is set up with a constant-amplitude variable-frequency sinusoidal motion slow start and stop control strategy. This results in the final optimized optimized control method for the wind tunnel rotor airfoil high-frequency dynamic test drive system.

5. The optimization control method for a high-frequency dynamic test drive system for a wind tunnel rotor airfoil according to claim 4, characterized in that: The expression of the position closed-loop control model of the drive system for the high-frequency dynamic test of the wind tunnel rotor airfoil in step S1 is: ； in, To control the output, is the control input, To control the error, is the first-order velocity feedforward gain, is the second-order acceleration feedforward gain, is the proportionality coefficient, is the integration coefficient, is the differential coefficient, and t is the time.

6. The optimization control method for a high-frequency dynamic test drive system for a wind tunnel rotor airfoil according to claim 5, characterized in that: The specific implementation method of step S2 includes the following steps: S2.

1. Constructing an amplitude adaptive compensation control method: The sinusoidal motion function expression of the high-frequency hydraulic swing cylinder is defined as: ； in, is the position of the swing cylinder at time t, is the amplitude, is the oscillation frequency, is the phase, is the oscillation equilibrium position; definition is the input command amplitude, is the target amplitude, is the actual amplitude of the sinusoidal motion of the high-frequency hydraulic swing cylinder, is the maximum value of sinusoidal motion; is the minimum value of sinusoidal motion; is the amplitude difference between the actual amplitude and the target amplitude; is the amplitude proportional gain, satisfying ; The actual amplitude of the sinusoidal motion of the high-frequency hydraulic swing cylinder is expressed as: ； The difference between the actual amplitude and the target amplitude is expressed as: ； Add a proportional control link to the amplitude of the sinusoidal motion, and adjust the set amplitude adaptively through the proportional link to continuously adjust After a cycle, the amplitude difference When the deviation is within the allowable range, the adjustment is stopped and the expression of the input command amplitude is: ； Where, i is the i-th cycle; S2.

2. Constructing a phase adaptive compensation control method: definition is the target frequency, is the target phase, To set the phase, is the time difference between the actual motion curve and the command curve over the oscillation equilibrium position, is the phase difference between the actual motion curve and the command curve, is the phase proportional gain, satisfying , then the phase difference The expression is: ； in, satisfy ; Based on the phase difference, the phase of the sinusoidal motion is increased by proportional control, and the phase is adaptively adjusted through the proportional link to continuously adjust the phase. After a cycle, the phase difference If the deviation is within the allowable range, stop adjusting. The final expression for setting the phase of the sinusoidal command is: ； Where, j is the jth cycle; S2.

3. When executing the amplitude adaptive compensation control method and the phase adaptive compensation control method, the amplitude difference and phase difference are automatically calculated in each cycle. The proportional control link adjusts and updates the set amplitude and phase of the sinusoidal motion, so that the actual motion curve gradually approaches the command curve until it enters the allowable deviation range. The final position of the high-frequency hydraulic swing cylinder after compensation at time t is expressed as: ； in, is the position of the high-frequency hydraulic swing cylinder at time t.

7. The optimization control method for a wind tunnel rotor airfoil high-frequency dynamic test drive system according to claim 6, characterized in that: The specific implementation method of step S3 includes the following steps: Make the sinusoidal motion with the initial frequency =0.8Hz starts to move, and the frequency increases with each sine cycle =0.2Hz, the sinusoidal motion of the high-frequency hydraulic swing cylinder in slow start / slow stop mode is expressed as: ； in, For the A sinusoidal motion cycle, is the initial frequency, is the variable frequency step; The following conditions are met: ； in, is the target frequency; Set up a high-frequency hydraulic swing cylinder to fix the amplitude ,frequency =0.8Hz to start the sinusoidal motion, and the frequency increases by 0.2Hz for each sinusoidal cycle until the oscillation frequency reaches the target frequency After that, a stable sinusoidal motion is performed at the target frequency; After data collection is completed, the deceleration and stop process is also to reduce the frequency by 0.2Hz per sine cycle until it reaches the initial frequency. Then stop exercising.

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