A continuous wind tunnel variable pressure control device and method based on double parameter compensation

Abstract

A continuous wind tunnel variable speed pressure control device and method based on double parameter compensation belong to the technical field of large-scale continuous wind tunnel test, and aim to solve the problem of difficult wind tunnel variable speed pressure adjustment. The device comprises a continuous wind tunnel body, a compressor group, a stable section, a nozzle section, a test section and a second throat arranged in sequence on the wind tunnel body, a test model arranged in the test section, a center body arranged in the second throat, a medium-pressure air source and an exhaust tower connected with the wind tunnel body between the compressor group and the stable section in sequence along the airflow flow direction, an air inlet adjusting valve arranged on the connecting pipeline of the medium-pressure air source and the wind tunnel body, an exhaust adjusting valve arranged on the connecting pipeline of the exhaust tower and the wind tunnel body, a total pressure measuring rake arranged on the stable section, and a static pressure measuring rake arranged on the test section. The center body is a variable rhombic tubular member composed of four wall plates hinged in sequence, and the flow area of the second throat is adjusted through the deformation of the center body, so that the speed pressure can be controlled through the real-time Mach number and total pressure.

Description

TECHNICAL FIELD

[0001] The present application belongs to the technical field of large-scale continuous wind tunnel test, and particularly relates to a continuous wind tunnel variable speed pressure control device and method based on double-parameter compensation. BACKGROUND

[0002] In large-scale continuous wind tunnel test, for specific test methods such as flutter test, it is often necessary to control the speed pressure under specified conditions, and to meet the precise control of a series of process variables such as Mach number and total pressure while precisely controlling the speed pressure. However, the driving device of the large-scale continuous wind tunnel often affects several process variables at the same time, such as the change of the speed of the compressor affecting the changes of the Mach number, total pressure and speed pressure, thereby making it difficult to achieve precise control of a single process variable or several process variables under specified conditions. In severe cases, it may cause control disorder, system overshoot, oscillation or loss of control, which puts high requirements on the control method of the wind tunnel flow field. SUMMARY

[0003] The purpose of the present application is to provide a continuous wind tunnel variable speed pressure control device and method based on double-parameter compensation to solve the problem that the driving device of the large-scale continuous wind tunnel often affects several process variables at the same time. The technical solution adopted by the present application is as follows:

[0004] A continuous wind tunnel variable speed pressure control device based on double-parameter compensation, comprising a continuous wind tunnel body, a compressor group, a stable section, a nozzle section, a test section and a second throat are sequentially arranged on the wind tunnel body, a test model is arranged in the test section, a center body is arranged in the second throat, a medium-pressure air source and an exhaust tower are sequentially connected with the wind tunnel body between the compressor group and the stable section in the airflow direction, an air inlet adjusting valve is arranged on the connecting pipeline between the medium-pressure air source and the wind tunnel body, an exhaust adjusting valve is arranged on the connecting pipeline between the exhaust tower and the wind tunnel body, a total pressure measuring rake is arranged on the stable section, and a static pressure measuring rake is arranged on the test section.

[0005] The second throat is a rectangular tubular member, an orbit extending forward and backward is arranged in the second throat, two sliding blocks are slidingly arranged on the orbit, the center body is a variable rhombus tubular member composed of four wall plates sequentially hinged, the center body is vertically arranged, the two ends of the center body are slidingly matched with the upper wall and the lower wall of the second throat respectively, a group of driving assemblies are arranged on the left wall and the right wall of the second throat, the driving assembly comprises a plurality of vertically arranged driving modules, the driving module comprises a servo motor, a speed reducer and an extension mechanism, the servo motor drives the extension mechanism to extend and retract left and right through the speed reducer, one diagonal of the center body is connected with two sliding blocks respectively, and the other diagonal of the center body is connected with two groups of extension mechanisms respectively.

[0006] Further, the variable speed pressure master control system and the compressor controller, the total pressure measuring rake and the static pressure measuring rake constitute a sensor acquisition system, the medium pressure gas source, the air inlet regulating valve, the exhaust tower and the exhaust regulating valve constitute a pressure control system, the plurality of drive modules, the track and the sliding block constitute a center body control system, the compressor controller is electrically connected with the compressor unit, the variable speed pressure master control system comprises a feedback calculation module, a motion state module, a Mach number control module and a total pressure control module, the feedback calculation module is electrically connected with the total pressure measuring rake and the static pressure measuring rake respectively, the feedback calculation module collects the actual total pressure of the stable section and the real-time static pressure P ct of the test section, and according to the real-time total pressure P ct and the real-time static pressure P m , the real-time Mach number M is calculated, the motion state module is electrically connected with the compressor controller and the plurality of drive modules respectively, the motion state module obtains the real-time rotating speed n of the compressor unit and the real-time distance d of the two driving ends of the center body, the Mach number control module adjusts the target rotating speed n m and the target distance d m of the two driving ends of the center body according to the difference between the real-time Mach number M and the target Mach number M 0m and the data obtained by the motion state module, the total pressure control module adjusts the opening degree of the air inlet regulating valve and the exhaust regulating valve according to the difference between the real-time total pressure P 0m and the target total pressure P m , so that the real-time total pressure P m tends to the target total pressure P m .

[0007] Further, each of the drive assemblies is composed of two drive modules arranged above and below.

[0008] The application also provides a continuous wind tunnel variable speed pressure control method based on double parameter compensation, which is realized by the above-mentioned continuous wind tunnel variable speed pressure control device based on double parameter compensation and comprises the following steps.

[0009] Step one, determining the target speed pressure Q m of the test section, and splitting the target speed pressure Q m into a target Mach number M m and a target total pressure P 0m , obtaining the relationship between the target speed pressure Q m , the target Mach number M m and the target total pressure P 0m .

[0010] The target speed pressure Q m is calculated by the following formula:

[0011] (1).

[0012] In the formula, P ctm is the target static pressure of the test section, the target static pressure Pctm The relationship between the target total pressure P 0m is as follows:

[0013] (2);

[0014] The simultaneous equations (1) and (2) can be obtained:

[0015] (3);

[0016] Step two, gradually increase the real-time rotational speed n of the compressor unit, so that the real-time total pressure P0 of the test section satisfies the following formula:

[0017] P0≥80% P 0m (4);

[0018] Then keep the real-time rotational speed n of the compressor unit constant;

[0019] Step three, obtain the relationship between the flow area A2 of the second throat and the real-time Mach number M of the test section:

[0020] (5);

[0021] In the formula, dA2 is the flow area change amount of the second throat, dM is the real-time Mach number change amount of the test section, P 0-2 is the total pressure of the second throat, and dP 0-2 is the total pressure change amount of the second throat;

[0022] The real-time Mach number M of the test section is calculated by the following formula:

[0023] (6);

[0024] According to the flow conservation relationship, the relationship between dA2 and dP 0-2 is as follows:

[0025] (7);

[0026] In the formula, C1 is a constant; C1 is calculated by the following formula:

[0027] (8);

[0028] In the formula, γ is the specific heat ratio of the gas in the wind tunnel body, and A1 is the flow area at the test model;

[0029] The relationship between dP 0-2 and dM is as follows:

[0030] (9);

[0031] Wherein, C2 is a constant; the constant C2 is calculated by the following formula:

[0032] (10);

[0033] Simultaneous equations (5) to (10), the relationship between dA2 and dM is as follows:

[0034] (11);

[0035] Step four, according to formula (11), under the specified real-time Mach number M and the second throat flow area A2, the second throat flow area change dA2 and the real-time Mach number change dM is proportional, then the control formula of the real-time Mach number M through the deformation PI control of the center body is:

[0036] (12);

[0037] Wherein, is the telescopic change of the telescopic mechanism at k time, is the proportional parameter of the center body deformation, is the integral parameter of the center body deformation, is the difference between the target Mach number M m and the real-time Mach number M at k time, is the difference between the target Mach number M m and the real-time Mach number M at k-1 time;

[0038] That is, when the two driving ends of the center body driven by the telescopic mechanism move to the target distance d m , the real-time Mach number M can reach the target Mach number M m through the corresponding flow area change of the second throat.

[0039] Step five, keep the target Mach number M m stable, and start to control the real-time total pressure P0, set the error band of the real-time total pressure P0 to ±δ;

[0040] When P 0m -P0≥δ, run the air supply mode, that is, close the exhaust regulating valve, and control the opening of the air inlet regulating valve through PI control and feedforward control, the control formula is:

[0041] (13);

[0042] Wherein, is the opening of the air inlet regulating valve, is the control proportional parameter of the air inlet regulating valve, is the control integral parameter of the air inlet regulating valve, The target total pressure P at time k in the gas replenishment mode. 0m The difference between the real-time total pressure P0 and the actual pressure. The target total pressure P at time k-1 in the gas replenishment mode. 0m The difference between the real-time total pressure P0 and the actual pressure. It is the compensation coefficient for the real-time speed n in the air replenishment mode;

[0043] When disturbances exist in the wind tunnel, P appears. m When P0 ≤ -δ, the exhaust mode is activated, meaning the intake regulating valve is closed, and the opening of the exhaust regulating valve is controlled via PI control and feedforward control. The control formula is as follows:

[0044] (14);

[0045] In the formula, The opening degree of the exhaust regulating valve. It is the control proportional parameter of the exhaust regulating valve. These are the integral control parameters of the exhaust regulating valve; e3(m) is the target total pressure P at time m in exhaust mode. 0m The difference between the real-time total pressure P0 and the actual pressure. The target total pressure P at time m-1 in exhaust mode. 0m The difference between the real-time total pressure P0 and the actual pressure. It is the compensation coefficient for the real-time speed n in exhaust mode.

[0046] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0047] The present invention discloses a continuous wind tunnel variable speed pressure control device and method based on dual-parameter compensation. To achieve variable speed pressure test conditions, the target speed pressure is decomposed into a target Mach number and a target total pressure. The flow area of ​​the second throat is adjusted by controlling the deformation of the control center body, thereby adjusting the real-time Mach number to approach the target Mach number. The real-time total pressure is increased to greater than or equal to 80% of the target total pressure by increasing the real-time speed of the compressor unit, providing a basis for subsequent real-time total pressure control. Through PI feedback control, parameter compensation, threshold switching and other means, the real-time total pressure is made closer to the target total pressure, thereby obtaining accurate real-time speed pressure. It has been well applied in experiments. Attached Figure Description

[0048] Figure 1 This is a schematic diagram of the structure of the device of the present invention;

[0049] Figure 2 This is a top view of the structure where the central body is installed inside the second throat.

[0050] Figure 3 This is a side view of the structure where the central body is installed inside the second throat.

[0051] Figure 4 This is a control principle diagram of the method of the present invention;

[0052] Figure 5 This is a control method diagram of the method of the present invention;

[0053] Figure 6 This is a control flowchart of the method of the present invention.

[0054] In the diagram, 1. Wind tunnel body, 2. Compressor unit, 3. Stabilization section, 4. Nozzle section, 5. Test section, 6. Second throat, 7. Test model, 8. Central body, 9. Medium-pressure air source, 10. Intake regulating valve, 11. Exhaust tower, 12. Exhaust regulating valve, 13. Total pressure measuring rake, 14. Static pressure measuring rake, 15. Drive module, 16. Servo motor, 17. Reducer, 18. Telescopic mechanism, 19. Track, 20. Wall panel, 21. Variable speed pressure main control system, 22. Sensor acquisition system, 23. Compressor controller, 24. Pressure control system, 25. Central body control system, 26. Feedback calculation module, 27. Motion state module, 28. Mach number control module, 29. Total pressure control module. Detailed Implementation

[0055] To make the objectives, technical solutions, and advantages of this invention clearer, the invention is described below with reference to specific embodiments shown in the accompanying drawings. However, it should be understood that these descriptions are merely exemplary and not intended to limit the scope of the invention. Furthermore, descriptions of well-known structures and technologies are omitted in the following description to avoid unnecessarily obscuring the concept of the invention.

[0056] The connections mentioned in this invention are divided into fixed connections and detachable connections. Fixed connections, also known as non-detachable connections, include but are not limited to conventional fixed connection methods such as folded connections, riveted connections, adhesive connections, and welded connections. Detachable connections include but are not limited to conventional disassembly methods such as bolted connections, snap-fit ​​connections, pin connections, and hinged connections. When a specific connection method is not explicitly defined, it is assumed that at least one existing connection method can be found to achieve this function, and those skilled in the art can choose according to their needs. For example, a welded connection can be chosen for fixed connections, and a bolted connection can be chosen for detachable connections.

[0057] The present invention will be further described in detail below with reference to the accompanying drawings. The following embodiments are explanations of the present invention, but the present invention is not limited to the following embodiments.

[0058] Example 1: As Figures 1-5As shown, a continuous wind tunnel variable speed pressure control device based on two-parameter compensation, including a continuous wind tunnel body 1, the wind tunnel body 1 is sequentially provided with a compressor set 2, a stable section 3, a nozzle section 4, a test section 5 and a second throat 6, the test section 5 is provided with a test model 7, the second throat 6 is provided with a center body 8, a medium pressure gas source 9 and an exhaust tower 11 are sequentially connected with the wind tunnel body 1 between the compressor set 2 and the stable section 3 along the airflow direction, the connecting pipeline of the medium pressure gas source 9 and the wind tunnel body 1 is provided with an air inlet regulating valve 10, the connecting pipeline of the exhaust tower 11 and the wind tunnel body 1 is provided with an exhaust regulating valve 12, the stable section 3 is provided with a total pressure measuring rake 13, and the test section 5 is provided with a static pressure measuring rake 14;

[0059] The second throat 6 is a rectangular tubular member, the second throat 6 is provided with a track 19 extending forward and backward, two sliding blocks are slidingly arranged on the track 19, the center body 8 is a variable rhombic tubular member composed of four wall plates 20 which are sequentially hinged, the center body 8 is vertically arranged, the two ends of the center body 8 are slidingly matched with the upper wall and the lower wall of the second throat 6 respectively, a group of driving assemblies are arranged on the left wall and the right wall of the second throat 6, the driving assembly includes a plurality of vertically arranged driving modules 15, the driving module 15 includes a servo motor 16, a speed reducer 17 and an extension mechanism 18, the servo motor 16 drives the extension mechanism 18 to extend and retract left and right through the speed reducer 17, one group of diagonals of the center body 8 are connected with two sliding blocks respectively, another group of diagonals of the center body 8 are connected with two groups of extension mechanisms 18 respectively, the diagonals of the center body 8 connected with the two groups of extension mechanisms 18 are active ends, and the diagonals connected with the two sliding blocks are passive ends, the two groups of extension mechanisms 18 are synchronously extended and retracted, so as to control the deformation of the center body 8, and then realize the change of the cross-sectional size of the center body 8 blocking the second throat 6, so as to realize the size adjustment of the flow area A2 of the second throat 6, so that the real-time Mach number M of the test section 5 has a corresponding relationship with the flow area of the second throat 6, that is, the real-time Mach number change of the test section can be realized by controlling the deformation of the center body 8, and the real-time total pressure P0 of the test section 5 can be realized by the medium pressure gas source 9 and the exhaust tower 11, and the real-time speed pressure Q has a corresponding relationship with the real-time Mach number M and the real-time total pressure, so that the real-time speed pressure Q can be obtained by controlling the real-time Mach number M and the real-time total pressure P0 through the device.

[0060] It also includes a variable-speed pressure main control system 21 and a compressor controller 23. The total pressure measuring rake 13 and the static pressure measuring rake 14 constitute a sensor acquisition system 22. The medium-pressure air source 9, the intake regulating valve 10, the exhaust tower 11, and the exhaust regulating valve 12 constitute a pressure control system 24. Several drive modules 15, the track 19, and the slider constitute a central body control system 25. The compressor controller 23 is electrically connected to the compressor unit 2. The variable-speed pressure main control system 21 includes a feedback calculation module 26, a motion state module 27, a Mach number control module 28, and a total pressure control module 29. The feedback calculation module 26 is electrically connected to the total pressure measuring rake 13 and the static pressure measuring rake 14, respectively. The feedback calculation module 26 collects the actual total pressure of the stable section 3 and the real-time static pressure P of the test section 5. ct The actual total pressure of the stable section 3 is taken as the real-time total pressure P0 of the test section 5, and based on the real-time total pressure P0 and the real-time static pressure P ct The motion state module 27 is electrically connected to the compressor controller 23 and several drive modules 15 respectively. The motion state module 27 obtains the real-time rotational speed n of the compressor unit 2 and the real-time distance d between the two active ends of the central body 8. The Mach number control module 28 calculates the real-time Mach number M and the target Mach number M. m The difference between the values ​​obtained and the data obtained from the motion state module 27 are used to adjust the target speed n of the compressor unit 2. m The target distance d between the two active ends of the central body 8 m The total pressure control module 29 controls the total pressure based on the real-time total pressure P0 and the target total pressure P. 0m The difference in pressure is used to adjust the opening of the intake regulating valve 10 and the exhaust regulating valve 12, thereby controlling the real-time total pressure P0 to move towards the target total pressure P. 0m .

[0061] Each set of drive components consists of two drive modules 15 arranged vertically.

[0062] Example 2: Figures 1-6 As shown, a continuous wind tunnel variable speed pressure control method based on dual-parameter compensation is implemented using a continuous wind tunnel variable speed pressure control device based on dual-parameter compensation as described in Example 1, and includes the following steps:

[0063] Step 1: Determine the target velocity pressure Q of test section 5. m and will target speed Q m Decomposed into target Mach number M m and target total pressure P 0m Obtain the target speed pressure Q m With the target Mach number M m and target total pressure P 0m Relationship;

[0064] Target speed Q m Calculated using the following formula:

[0065] (1) ;

[0066] P0= P ctm is the target static pressure of the test section 5, the target static pressure P ctm and the target total pressure P 0m have the following relationship:

[0067] (2) ;

[0068] By combining equation (1) and equation (2), we have:

[0069] (3) ;

[0070] Step two, gradually increase the real-time rotational speed n of the compressor unit 2, so that the real-time total pressure P0of the test section 5 satisfies the following equation:

[0071] P0≥80% P 0m (4) ;

[0072] Then keep the real-time rotational speed n of the compressor unit 2 constant;

[0073] Step three, obtain the relationship between the flow area A2of the second throat 6 and the real-time Mach number M of the test section 5:

[0074] (5) ;

[0075] In the equation, dA2is the flow area change amount of the second throat 6, dM is the real-time Mach number change amount of the test section 5, P 0-2 is the total pressure of the second throat 6, and dP 0-2 is the total pressure change amount of the second throat 6;

[0076] The real-time Mach number M of the test section 5 is calculated by the following equation:

[0077] (6) ;

[0078] According to the flow conservation relationship, the relationship between dA2and dP 0-2 is as follows:

[0079] (7) ;

[0080] In the equation, C1is a constant; C1is calculated by the following equation:

[0081] (8) ;

[0082] In the equation, γ is the specific heat ratio of the gas in the wind tunnel body 1, and A1is the flow area at the test model 7;

[0083] dP0-2 The relationship between dM is as follows:

[0084] (9);

[0085] In the formula, C2 is a constant; the constant C2 is calculated by the following formula:

[0086] (10);

[0087] Simultaneous equations (5) to (10), the relationship between dA2 and dM is as follows:

[0088] (11);

[0089] Step four, according to formula (11), under the specified real-time Mach number M and the second throat 6 flow area A2, the second throat 6 flow area change dA2 and the real-time Mach number change dM is proportional, then the control formula of the real-time Mach number M through the deformation PI control of the center body 8 is:

[0090] (12);

[0091] In the formula, is the telescopic change of the telescopic mechanism 18 at k time, is the proportional parameter of the center body 8 deformation, is the integral parameter of the center body 8 deformation, is the difference between the target Mach number M m and the real-time Mach number M at k time, is the difference between the target Mach number M m and the real-time Mach number M at k-1 time;

[0092] That is, when the two active ends of the center body 8 driven by the telescopic mechanism 18 are moved to the target distance d m , the real-time Mach number M can reach the target Mach number M m through the corresponding flow area change of the second throat 6.

[0093] Step five, keep the target Mach number M m stable, and start to control the real-time total pressure P0, set the error band of the real-time total pressure P0 to ±δ;

[0094] When P 0m -P0≥δ, run the air supplement mode, that is, close the exhaust regulating valve 12, and control the opening of the intake regulating valve 10 through PI control and feedforward control, the control formula is:

[0095] (13);

[0096] wherein, is the opening degree of the intake regulating valve 10, is the control proportional parameter of the intake regulating valve 10, is the control integral parameter of the intake regulating valve 10, is the difference between the target total pressure P 0m and the real-time total pressure P0 in the boost mode at time k, is the difference between the target total pressure P 0m and the real-time total pressure P0 in the boost mode at time k-1, is the compensation coefficient of the real-time rotating speed n in the boost mode.

[0097] When there is a disturbance in the wind tunnel, P m -P0≤-δ, the exhaust mode is run, that is, the intake regulating valve 10 is closed, and the opening degree of the exhaust regulating valve 12 is controlled by means of PI control and feedforward control, and the control formula is:

[0098] (14).

[0099] wherein, is the opening degree of the exhaust regulating valve 12, is the control proportional parameter of the exhaust regulating valve 12, is the control integral parameter of the exhaust regulating valve 12, e3(m) is the difference between the target total pressure P 0m and the real-time total pressure P0 in the exhaust mode at time m, is the difference between the target total pressure P 0m and the real-time total pressure P0 in the exhaust mode at time m-1, is the compensation coefficient of the real-time rotating speed n in the exhaust mode.

[0100] The continuous wind tunnel variable speed pressure control device and method based on double-parameter compensation provided by the application can realize the test working condition of variable speed pressure, split the target speed pressure Q m into a target Mach number M m and a target total pressure P 0m , adjust the flow area of the second throat 6 by controlling the deformation of the center body 8, and then adjust the real-time Mach number M to approach the target Mach number M m , improve the real-time rotating speed n of the compressor set 2 to improve the real-time total pressure P0 to be greater than or equal to 80% of the target total pressure P 0m , provide a basic condition for the subsequent control of the real-time total pressure P0, realize the real-time total pressure P0 approaching the target total pressure P 0m by means of PI feedback control, parameter compensation and threshold switching, and then obtain an accurate real-time speed pressure Q, and good application is achieved in the test.

[0101] The above examples are only illustrative of the present application and do not limit the protection scope thereof, and the person skilled in the art can also make partial changes thereto, as long as the changes do not exceed the spirit and essence of the present application and are within the protection scope of the present application.

Claims

1. A variable speed pressure control device for a continuous wind tunnel based on two-parameter compensation, characterized by: The wind tunnel body (1) comprises a continuous wind tunnel body (1), a compressor group (2), a stable section (3), a nozzle section (4), a test section (5) and a second throat (6) are sequentially arranged on the wind tunnel body (1), a test model (7) is arranged in the test section (5), a center body (8) is arranged in the second throat (6), a medium-pressure air source (9) and an exhaust tower (11) are sequentially connected with the wind tunnel body (1) between the compressor group (2) and the stable section (3) along the airflow direction, the connecting pipeline of the medium-pressure air source (9) and the wind tunnel body (1) is provided with an air inlet adjusting valve (10), the connecting pipeline of the exhaust tower (11) and the wind tunnel body (1) is provided with an exhaust adjusting valve (12), the stable section (3) is provided with a total pressure measuring rake (13), and the test section (5) is provided with a static pressure measuring rake (14); The second throat (6) is a rectangular tubular member, the second throat (6) is provided with a track (19) extending forward and backward, two sliding blocks are slidingly arranged on the track (19), the center body (8) is a variable rhombic tubular member formed by sequentially hingedly connecting four wall plates (20), the center body (8) is vertically arranged, the two ends of the center body (8) are slidingly matched with the upper wall and the lower wall of the second throat (6) respectively, a group of driving assemblies are arranged on the left wall and the right wall of the second throat (6), each driving assembly comprises a plurality of vertically arranged driving modules (15), the driving module (15) comprises a servo motor (16), a speed reducer (17) and an extension mechanism (18), the servo motor (16) drives the extension mechanism (18) to extend and retract leftward and rightward through the speed reducer (17), one group of opposite corners of the center body (8) are connected with the two sliding blocks correspondingly, and the other group of opposite corners of the center body (8) are connected with the two groups of extension mechanisms (18) correspondingly.

2. The variable pressure control device for a continuous wind tunnel based on dual parameter compensation according to claim 1, characterized in that: The variable speed pressure master control system (21) and the compressor controller (23), the total pressure measuring rake (13) and the static pressure measuring rake (14) constitute the sensor acquisition system (22), the medium pressure gas source (9), the air inlet regulating valve (10), the exhaust tower (11) and the exhaust regulating valve (12) constitute the pressure control system (24), a plurality of drive modules (15), the track (19) and the slider constitute the center body control system (25), the compressor controller (23) is electrically connected with the compressor unit (2), the variable speed pressure master control system (21) comprises a feedback calculation module (26), a motion state module (27), a Mach number control module (28) and a total pressure control module (29), the feedback calculation module (26) is electrically connected with the total pressure measuring rake (13) and the static pressure measuring rake (14), the feedback calculation module (26) collects the actual total pressure of the stable section (3) and the real-time static pressure P ct of the test section (5), the actual total pressure of the stable section (3) is taken as the real-time total pressure P0 of the test section (5), and the real-time total pressure P0 and the real-time static pressure P ct are used to calculate the real-time Mach number M, the motion state module (27) is electrically connected with the compressor controller (23) and the plurality of drive modules (15), the motion state module (27) obtains the real-time rotating speed n of the compressor unit (2) and the real-time distance d of the two driving ends of the center body (8), the Mach number control module (28) adjusts the target rotating speed n m of the compressor unit (2) and the target distance d m of the two driving ends of the center body (8) according to the difference between the real-time Mach number M and the target Mach number M m obtained by the motion state module (27), the total pressure control module (29) adjusts the opening degree of the air inlet regulating valve (10) and the exhaust regulating valve (12) according to the difference between the real-time total pressure P0 and the target total pressure P 0m , and controls the real-time total pressure P0 to tend to the target total pressure P 0m .

3. The variable pressure control device for a continuous wind tunnel based on dual parameter compensation according to claim 1, characterized in that: Each group of driving assemblies is composed of two driving modules (15) arranged above and below.

4. A continuous wind tunnel variable pressure control method based on double parameter compensation, relying on the continuous wind tunnel variable pressure control device based on double parameter compensation of claim 2, characterized in that, The following steps are included: Step one, determine the target speed pressure Q of the test section (5) m And the target speed pressure Q m Is split into target Mach number M m And target total pressure P 0m , get the relationship between target speed pressure Q m And target Mach number M m And target total pressure P 0m ; Target speed pressure Q m is calculated by the following equation: (1)； In the formula, P ctm is the target static pressure of the test section (5), the target static pressure P ctm is the target total pressure of the test section (5), and the target total pressure P 0m is related to the target static pressure P as follows. (2)； The simultaneous equations (1) and (2) can be obtained: (3)； Step two, gradually increase the real-time rotating speed n of the compressor group (2), so that the real-time total pressure P0 of the test section (5) satisfies the following formula: P0≥ 80% P 0m (4); Then keep the real-time rotating speed n of the compressor group (2) constant; Step three, obtain the relationship between the flow area A2 of the second throat (6) and the real-time Mach number M of the test section (5): (5)； In the formula, dA2 is the flow area variation of the second throat (6), dM is the real-time Mach number variation of the test section (5), P 0-2 is the total pressure of the second throat (6), dP 0-2 is the total pressure variation of the second throat (6); The real-time Mach number M of the test section (5) is calculated by the following formula: (6)； The relationship between dA2 and dP according to the flow conservation relationship is as follows: 0-2 dA2 = -dP (7)； In the formula, C1 is a constant; C1 is calculated by the following formula: (8)； In the formula, γ is the specific heat ratio of the gas in the wind tunnel body (1), and A1 is the flow area at the test model (7); dP 0-2 The relationship with dM is as follows: (9)； In the formula, C2 is a constant; the constant C2 is calculated by the following formula: (10)； By simultaneously solving equations (5) to (10), the relationship between dA2 and dM is as follows: (11)； Step four, according to formula (11), under the specified real-time Mach number M and the flow area A2 of the second throat (6), the flow area change amount dA2 of the second throat (6) is proportional to the real-time Mach number change amount dM, so the control formula for controlling the real-time Mach number M through the deformation PI of the center body (8) is as follows: (12)； In the formula, is the telescopic change amount of the telescopic mechanism (18) at time k, is a proportional parameter of the deformation of the central body (8), is an integral parameter of the deformation of the central body (8), is the difference between the target Mach number M m and the real-time Mach number M at time k, is the difference between the target Mach number M m and the real-time Mach number M at time k-1. That is, when several telescopic mechanisms (18) drive two active ends of the center body (8) to move to a target distance d m , the real-time Mach number M can reach the target Mach number M m by the corresponding change in the flow area of the second throat (6). Step five, keep target Mach number M m Stable, and start to control the real-time total pressure P0, set the error band of the real-time total pressure P0 as ±δ; When P 0m - When P0≥δ, run the air supplement mode, i.e. close the exhaust adjusting valve (12), and control the opening of the intake adjusting valve (10) by means of PI control and feedforward control, with the control formula being: (13)； In the formula, is the opening of the intake air regulating valve (10), is the control proportional parameter of the intake air regulating valve (10), is the control integral parameter of the intake air regulating valve (10), is the difference between the target total pressure P 0m and the real-time total pressure P0 in the k-1 moment of the supplementary air mode, is the difference between the target total pressure P 0m and the real-time total pressure P0 in the k-1 moment of the supplementary air mode, is the compensation coefficient of the real-time rotating speed n in the supplementary air mode. When there is disturbance in the wind tunnel, P m - When P0≤-δ, the exhaust mode is run, i.e. the intake regulating valve (10) is closed, and the opening of the exhaust regulating valve (12) is controlled by means of PI control and feedforward control, and the control formula is: (14)； In the formula, is the opening of the exhaust regulating valve (12), is the control proportional parameter of the exhaust regulating valve (12), is the control integral parameter of the exhaust regulating valve (12), e3(m) is the target total pressure P 0m of the difference between the real-time total pressure P0, is the target total pressure P 0m of the difference between the real-time total pressure P0, is the compensation coefficient of the real-time rotating speed n in the exhaust mode.

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