Large-diameter vibration reduction circular seam type pressure regulating valve device for subsonic-transonic-supersonic wind tunnel and using method

Abstract

The invention provides a large-diameter vibration reduction circular seam type pressure regulating valve device for a sub-span-supersonic wind tunnel and a using method, the large-diameter vibration reduction circular seam type pressure regulating valve device comprises an outer conical cylinder, an air inlet grille is arranged at an air inlet of the outer conical cylinder, and the outer conical cylinder and an inner conical cylinder form a circulation area; an inlet of the pressure regulating molded surface cone is connected with the outer cone cylinder, and the inner molded surface of the pressure regulating molded surface cone is an arc surface and a multi-section index combined molded surface; a piston is arranged between the inner cone cylinder and the pressure regulating profile cone, a main seal and an auxiliary seal are arranged at the end of the piston, and the piston is in sliding connection with the inner cone cylinder through a servo driving device. A plurality of diagonal draw bars are arranged between the servo driving device and the piston, the two ends of each diagonal draw bar are hinged to the servo driving device and the piston respectively, and the two ends of the shock absorber are hinged between the diagonal draw bars and the servo driving device respectively. According to different wind tunnel experiment requirements, pressure distribution of a flow field can be accurately adjusted, mechanical impact and noise of the valve can be effectively reduced, and vibration generated by rapid movement is relieved through coupling between the damping device and the diagonal draw bar.

Description

Technical Field

[0001] The present invention relates to the technical field of fluid control equipment, and in particular to a sub-span super wind tunnel large-caliber vibration-damping annular gap type pressure regulating valve device and a use method thereof. Background Art

[0002] As an important aerodynamic experiment method, wind tunnel experiments are widely used in aerospace, automobile industry, construction engineering and other fields. In wind tunnel experiments, it is very important to adjust the pressure of the airflow inside the wind tunnel. Conventional pressure regulating valve devices have problems such as turbulent airflow, excessive noise, and easy vibration of the structure while meeting the requirements of accuracy and stability.

[0003] At present, the flow regulation accuracy of conventional industrial pressure regulating valves is only 1-5%, and the noise is as high as 170dB or more, which is difficult to meet the requirements of precise pressure regulation and low noise in wind tunnel experiments. Traditional wind tunnel pressure regulating valves mostly use annular gap pressure regulating structures, but they have defects such as easy separation of airflow, high valve noise, and easy sealing leakage, which cannot achieve accurate flow field pressure regulation and low noise requirements. Summary of the invention

[0004] The purpose of the present invention is to provide a sub-span super wind tunnel large-diameter vibration-damping annular gap type pressure regulating valve device and a method of use, aiming to solve the problems of airflow turbulence, high noise, seal leakage, structural vibration, etc. existing in the prior art, thereby realizing precise regulation of flow field pressure in wind tunnel experiments, and being able to effectively reduce noise, reduce gas leakage, and avoid wind tunnel resonance.

[0005] According to one purpose of the present invention, the present invention provides a sub-span super wind tunnel large-diameter vibration-damping annular gap type pressure regulating valve device, comprising an outer cone, an inner cone, a pressure regulating profile cone, a piston, a servo drive device, a diagonal tie rod and a shock absorber, wherein the air inlet of the outer cone is provided with an air inlet grille, the inner cone is arranged inside the outer cone, and the outer cone and the inner cone form a flow area; the inlet of the pressure regulating profile cone is connected to the outer cone, the outlet of the pressure regulating profile cone is connected to the outlet flange, and the inner profile of the pressure regulating profile cone is a circular arc surface and a multi-segment index combination profile; a piston is arranged between the inner cone and the pressure regulating profile cone, a primary seal and a secondary seal are arranged at the end of the piston, and the piston is slidably connected to the inner cone through a servo drive device; a plurality of diagonal tie rods are arranged between the servo drive device and the piston, and the two ends of the diagonal tie rod are respectively hingedly connected to the servo drive device and the piston, and the two ends of the shock absorber are respectively hingedly connected between the diagonal tie rod and the servo drive device.

[0006] Furthermore, the air intake grille is composed of multiple layers of sintered metal mesh blocks, the mesh number of the air intake grille ranges from 10 to 300 meshes, the noise reduction frequency of the sintered metal mesh block noise reduction arc plate is 0 to 40,000 Hz, and the air permeability is 30% to 100%.

[0007] Furthermore, the servo drive device includes a servo hydraulic cylinder, a hydraulic rod, a spline shaft, a spline sleeve and a displacement sensor. The spline shaft is fixed to the inner cone through a support. The spline shaft and the spline sleeve form a high-torque ball spline. Spherical hinge seats are provided at both ends of the diagonal tie rod. The two spherical hinge seats are connected to the diagonal tie rod through self-locking trapezoidal threads, and the rotation directions of the self-locking trapezoidal threads of the spherical hinge seats at both ends are opposite. An anti-loosening device is provided between the spherical hinge seat and the diagonal tie rod. One end of the diagonal tie rod is connected to the piston through the spherical hinge seat, and the other end of the diagonal tie rod is hinged to the spline sleeve. The spline sleeve is driven by the hydraulic rod to slide back and forth relative to the spline shaft, and finally the diagonal tie rod is driven to drive the piston to move axially.

[0008] Furthermore, the servo hydraulic cylinder is a double-acting servo hydraulic cylinder, which adopts dual servo hydraulic valves to coarse and fine control the flow to achieve precise pressure regulation and emergency shutdown functions. The servo hydraulic cylinder adopts a double closed-loop PID servo control strategy based on the valve characteristics, with the outer loop as the total pressure and the inner loop as the valve position. The parabolic speed curve method is used to optimize the valve core switching vehicle, thereby avoiding the rapid impact and damage of the valve core to the valve structure.

[0009] Furthermore, the profile of the outer cone is designed as a cylinder-cone-cylinder structure, the cone angle of the outer cone is less than 30°, the outer cone is connected to the inner cone via an even number of support ribs, and the cone angle of the inner cone is less than 60°.

[0010] Furthermore, the primary seal is a T-shaped structure with an inflation port and a draft angle, and the secondary seal is a U-shaped structure. The primary seal and the secondary seal can be arranged in multiples to increase the sealing redundancy and reliability.

[0011] Furthermore, the piston is made of cast aluminum structure or steel, and the outlet of the piston is evenly distributed with tiny pores connected to the main seal.

[0012] Furthermore, the shock absorber adopts a permanent magnet adjustable magnetorheological damper or a viscous fluid damper, a magnetorheological damper or a viscous shear damper.

[0013] Furthermore, the number of the shock absorbers is n, where n is any integer between 1 and 4, and the shock absorbers are used in pairs with the diagonal tie rods, and the center lines of the shock absorbers and the diagonal tie rods are perpendicular to each other.

[0014] According to another object of the present invention, the present invention provides a method for using the above-mentioned sub-span super wind tunnel large-diameter vibration-damping annular gap type pressure regulating valve device, comprising the following steps:

[0015] The two ends of the pressure regulating profile cone are respectively connected to the outer cone cylinder and the outlet flange, and the inner cone cylinder and the outer cone cylinder form a fluid flow area;

[0016] The servo drive device axially drives the spline sleeve to drive the inclined rod and finally drives the piston to move axially. The displacement sensor feeds back the axial position of the piston in real time. The change in the channel cross-sectional area of ​​the piston and the pressure regulating profile cone caused by the change in the axial displacement of the piston and the pressure regulating profile cone realizes the precise adjustment of the flow field pressure.

[0017] The air intake grille at the air inlet stabilizes the flow and reduces air flow pulsation. The flow field outlet has no support to avoid structural vibration caused by flow separation. The spline sleeve avoids circumferential vibration of the piston. The shock absorber avoids bending and deformation of the inclined rod and achieves vibration reduction. The main seal and auxiliary seal of the piston use pipeline gas to achieve inflation sealing.

[0018] The technical solution of the present invention can adjust the flow field pressure in real time according to the needs of the wind tunnel experiment, has good fluid mechanics performance and structural durability, and can still ensure precise control and stable operation, especially under high-frequency adjustment operation, and can accurately adjust the pressure distribution of the flow field through simple adjustment and control according to different wind tunnel test needs. When adjusting high flow, it can effectively reduce the mechanical impact and noise of the valve, and the vibration reduction device can reduce the vibration caused by rapid movement through coupling with the inclined rod, thereby ensuring the long-term stability and reliability of the equipment. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the specific implementation methods of the present invention or the technical solutions in the prior art, the drawings required for use in the specific implementation methods or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some implementation methods of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0020] Figure 1 It is a schematic cross-sectional view of the overall structure of an embodiment of the present invention;

[0021] Figure 2 It is a schematic diagram of a side view of the overall structure of an embodiment of the present invention in the direction of P;

[0022] Figure 3 This is a schematic diagram of the overall structure 3 / 4 of an embodiment of the present invention;

[0023] Figure 4 This is a schematic diagram of the main and auxiliary seal structures of the piston with detachable ends according to an embodiment of the present invention;

[0024] In the figure: 1. air intake grille; 2. inlet flange; 3. outer cone; 4. supporting ribs; 5. shock absorber; 6. diagonal tie rod; 7. diagonal tie rod support; 8. pressure regulating cone; 8. outlet flange; 10. auxiliary sealing cover plate; 11. auxiliary seal; 12. main sealing pressure plate; 13. first main sealing panel; 14. second main sealing panel; 15. main seal; 16. piston; 17. spline sleeve; 18. spline shaft; 19. support; 20. inner cone; 21. servo hydraulic cylinder; 22. hydraulic rod; 23. displacement sensor; 24. protective cover. DETAILED DESCRIPTION

[0025] The technical solution of the present invention will be clearly and completely described below in conjunction with the embodiments. Obviously, the described embodiments are part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0026] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0027] In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "multiple" means two or more, unless otherwise clearly and specifically defined. In addition, the terms "installed", "connected" and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal connection of two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0028] Example 1

[0029] like Figure 1-Figure 4 As shown,

[0030] A sub-span super wind tunnel large-caliber vibration-damping annular gap type pressure regulating valve device, comprising an outer cone 3, an inner cone 20, a pressure regulating profile cone 8, a piston 16 and a servo drive device, wherein:

[0031] An air inlet grille 1 is provided at the air inlet of the outer cone 3, and an inlet flange 2 is provided at the end of the outer cone 3. The inlet flange 2 is a standard gas pressure-bearing flange structure.

[0032] One end of the pressure regulating profile cone 8 is connected to the outer cone 3, and the other end of the pressure regulating profile cone 8 is connected to the outlet flange 9. The inner profile of the pressure regulating profile cone 8 is a circular arc surface and a multi-segment index combination profile, and its inlet is connected to the outer cone 3 by welding or flange, and the outlet is connected to the outlet flange 9. The inlet flange 2 and the outlet flange 9 are determined according to the flow rate and pressure regulating characteristics of the sub-span super wind tunnel, and preferably have the same diameter.

[0033] The inner cone 20 is arranged inside the outer cone 3. The outer cone 3 and the inner cone 20 form a flow area. The profile design of the outer cone 3 and the inner cone 20 is a cylinder-cone-cylinder structure. The cone angle of the outer cone 3 is less than 30°, ensuring that the airflow flows smoothly in the channel. The outer cone 3 is connected to the inner cone 20 through an even number of support ribs 4. The inner cone 20 is a cone-cylinder structure. The cone angle of the inner cone 20 is less than 60°. The flow channel area formed by them is equivalent to the inlet area.

[0034] A piston 16 is provided at the inner end of the inner cone 20. The piston 16 is slidably connected to the inner cone 20 through a servo drive device. The piston 16 is arranged between the inner cone 20 and the pressure regulating profile cone 8. The change in the axial displacement of the piston 16 and the pressure regulating profile cone 8 causes the change in the channel cross-sectional area of ​​the piston 16 and the pressure regulating profile cone 8 to achieve precise adjustment of the flow field pressure.

[0035] Specifically, the servo drive device includes a servo hydraulic cylinder 21 , a hydraulic rod 22 and a displacement sensor 23 . The servo hydraulic cylinder 21 is fixed at the middle of the inner cone 20 . The hydraulic rod 22 is connected to the servo hydraulic cylinder 21 , and performs linear reciprocating motion under the drive of the servo hydraulic cylinder 21 .

[0036] In this embodiment, the pressure regulating profile cone 8 is used to adjust the flow field pressure, and the servo hydraulic cylinder 21 is used to drive the piston 16 to accurately adjust the pressure. The servo hydraulic cylinder 21, the hydraulic rod 22 and the displacement sensor 23 form a servo drive device, which adjusts the valve position through a precise PID control strategy, optimizes the opening and closing process of the valve core, and avoids impact damage to the valve.

[0037] A support 19 is also fixed inside the inner cone 20, a spline shaft 18 is fixed on the support 19, a spline sleeve 17 is slidably connected to the spline shaft 18, and the spline sleeve 17 is fixedly connected to the end of the hydraulic rod 22. The spline sleeve 17 can be driven by the hydraulic rod 22 to slide back and forth relative to the spline shaft 18.

[0038] A plurality of inclined tie rods 6 are hingedly connected to the outer wall of the spline sleeve 17, and the other end of the inclined tie rod 6 is hingedly connected to the piston 16. The servo drive device composed of a servo hydraulic cylinder 21 and a hydraulic rod 22 axially drives the spline sleeve 17 to drive the inclined tie rod 6 and finally drives the piston 16 to move axially. The axial position of the piston 16 is fed back in real time through the displacement sensor 23.

[0039] In this embodiment, the inclined tie rod 6 is a rod with spherical hinged ears at both ends, and the ears are connected to the rod by trapezoidal threads, which have the functions of self-locking and length adjustment. The self-locking trapezoidal threads connecting the spherical hinged ears at both ends and the inclined tie rod have opposite rotation directions and are equipped with anti-loosening devices. There are even numbers of them along the circumference (6 in this embodiment), one end is connected to the piston 16 through the inclined tie rod support 7, and the other end is connected to the spline sleeve 17.

[0040] The servo hydraulic cylinder 21 drives the spline sleeve 17 through the hydraulic rod 22, so that it drives the movement between the inclined tie rod 6 and the piston 16. The position of the piston is accurately adjusted through the displacement sensor 23 with real-time feedback, thereby adjusting the channel cross-sectional area of ​​the pressure-regulating profile cone to achieve precise control of the flow field pressure.

[0041] The servo hydraulic cylinder 21, hydraulic rod 22, and displacement sensor 23 form a piston drive device. The servo hydraulic cylinder 21 and hydraulic rod 22 are double-acting servo hydraulic cylinders, which use dual servo hydraulic valves to control the flow rate coarse and fine adjustment to achieve precise pressure regulation and emergency shutdown functions. Based on the valve characteristics, the outer ring is the total pressure and the inner ring is the valve position. The double closed-loop PID servo control strategy uses a parabolic speed curve to optimize the valve core switch, avoiding the valve core from quickly impacting and damaging the valve structure. One end of the hydraulic rod 22 is connected to the spline sleeve 17, and the other end is connected to the displacement sensor 23. The displacement sensor 23 monitors the position of the piston in real time.

[0042] A protective cover 24 is provided in front of the position sensor 23 to protect the position sensor 23 from the impact of airflow.

[0043] In this embodiment, the air intake grille 1 is used to stabilize the flow and reduce the pulsation of the air flow. There is no support at the outlet of the flow field to avoid structural vibration caused by flow separation. The air intake grille 1 adopts a multi-layer sintered metal mesh block with a mesh size of 10-300, which can effectively stabilize the flow and reduce the pulsation of the air flow. The noise reduction frequency of the sintered metal mesh block noise reduction arc plate is 0-40000Hz, and the air permeability of the sintered metal mesh block noise reduction arc plate is 30%-100%.

[0044] In this embodiment, the spline sleeve 17 can prevent the circumferential vibration of the piston 16. The piston 16 is preferably a cast aluminum structure to reduce the weight. When the large structure exceeds the processing capacity of cast aluminum, it can be made of ordinary steel. The outlet is evenly distributed with tiny pores connected to the main seal 15 to realize two-way inflation sealing using high-pressure gas in the pipeline.

[0045] The spline sleeve 17 and the spline shaft 18 form a high-torque ball spline. The rolling friction reduces the friction coefficient by about one order of magnitude compared with the sliding friction, thereby improving the torsion resistance of the piston 16 and avoiding the circumferential vibration of the piston 16.

[0046] In order to reduce valve noise, especially at large flow, a shock absorber 5 is provided between the diagonal tie rod 6 and the spline sleeve 17, and the shock absorber 5 is used to reduce the deformation of the diagonal tie rod 6. The shock absorber 5 is a permanent magnet adjustable magnetorheological damper, or a viscous fluid damper, a magnetorheological damper or a viscous shear damper, which can effectively reduce the vibration and noise of the wind tunnel. The number of shock absorbers 5 installed is n, and n is any integer between 1 and 4. It is used in pairs with the diagonal tie rod 6, and the center lines are perpendicular to each other.

[0047] In this embodiment, the end of the piston 16 is provided with a primary seal 15 and a secondary seal 11, and the primary seal 15 and the secondary seal 11 of the piston 16 are inflated and sealed by pipeline gas. The primary seal 15 is a T-shaped structure with an inflation port and a draft angle, and the sealing is enhanced by high-pressure gas to avoid leakage. The secondary seal 11 is a U-shaped structure, and is inflated and sealed by pipeline gas. The primary seal and the secondary seal can be arranged in multiples to increase the sealing redundancy and reliability.

[0048] like Figure 4 As shown, the secondary seal 11 is a U-shaped structure, and the main seal 15 is a T-shaped structure with an inflatable port and an inclined surface. High-pressure gas passes through the inflatable port to make the secondary seal 11 and the main seal 15 fit more closely to the sealing surface to avoid overpressure leakage. In this embodiment, the secondary seal cover plate 10, the main seal pressure plate 12, the first main seal type panel 13, and the second main seal type panel 14 are all detachable and replaceable in circumferential sections. The main seal pressure plate 12, the first main seal type panel 13, the second main seal type panel 14 and the main seal 15 form a two-way sealing structure, which can be used for rapid on-off sealing of pipelines.

[0049] The invention avoids the vibration of the pressure regulating valve and realizes the accurate closed-loop control of the flow field pressure. The whole device is provided with necessary supports and lifting ears for easy installation and storage.

[0050] The present invention aims to solve the problems that the existing wind tunnel pressure regulating valve has no flow stabilization measures at the inlet, has valve core support at the outlet, resulting in poor uniformity of inlet airflow, and large flow separation caused by outlet support interference. The present invention sets a sintered wire mesh air intake grille at the inlet to stabilize the flow, and has no support at the outlet for separation, thereby ensuring a stable flow field.

[0051] The present invention uses a servo hydraulic cylinder to drive a high-torque ball spline servo drive device to axially drive a spline sleeve to drive a diagonal tie rod and finally drive the piston to move axially. Rolling friction is used instead of sliding friction, while improving the torsion resistance of the piston. The shock absorber avoids the bending deformation of the diagonal tie rod and achieves vibration reduction. The displacement sensor feeds back the axial position of the piston in real time, and the change in the channel cross-sectional area of ​​the piston and the pressure-regulating profile cone caused by the change in the axial displacement of the piston and the pressure-regulating profile cone realizes the precise adjustment of the flow field pressure.

[0052] The piston secondary seal of the present invention is a U-shaped structure, and the main seal is a T-shaped structure with an inflating port and an inclined surface. High-pressure gas passes through the inflating port to make the secondary seal and the main seal fit more closely to the sealing surface, thereby avoiding overpressure leakage. A two-way sealing structure is formed, which can be used for rapid on-off sealing of pipelines.

[0053] The pressure regulating valve driving device of the present invention adopts dual servo hydraulic valves to achieve precise pressure regulation and emergency shutdown functions for coarse and fine flow control. Based on the double closed-loop PID servo control strategy of the valve characteristics, the outer ring is the total pressure and the inner ring is the valve position. The parabolic speed curve method is adopted to optimize the valve core switching vehicle, thereby avoiding the rapid impact and damage of the valve core to the valve structure.

[0054] The present invention includes the following innovative features:

[0055] Flow stabilization measures: A multi-layer sintered metal mesh air intake grille is set at the air inlet to reduce air flow pulsation and improve the uniformity of the inlet air flow; there is no support at the outlet to avoid structural vibration caused by air flow separation.

[0056] Precise pressure regulation: A servo drive device consisting of a servo hydraulic cylinder, a hydraulic rod and a displacement sensor is used to drive the spline sleeve to drive the inclined rod and finally drive the piston to move axially. Through the axial displacement change of the piston and the pressure regulating profile cone, the channel cross-sectional area is precisely adjusted to achieve precise regulation of the flow field pressure.

[0057] Vibration reduction design: The vibration reducer is designed to avoid the bending deformation of the inclined tie rod, while reducing vibration and improving the stability of the pressure regulating valve.

[0058] Bidirectional sealing structure: It adopts a bidirectional sealing structure with U-shaped secondary seal and T-shaped main seal, and uses pipeline gas for inflation sealing to avoid overpressure leakage and achieve rapid pipeline on-off sealing.

[0059] Servo hydraulic control: The servo hydraulic valve performs coarse and fine control on the flow rate, adopts a double closed-loop PID control strategy, optimizes the valve core's switching process through a parabolic speed curve, avoids the impact of the valve core on the valve structure, and extends its service life.

[0060] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or replace some or all of the technical features therein with equivalents. However, these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A large-caliber vibration-damping annular gap type pressure regulating valve device for a sub-span super wind tunnel, characterized in that: It includes an outer cone cylinder, an inner cone cylinder, a pressure regulating profile cone, a piston, a servo drive device, a diagonal tie rod and a shock absorber, the air inlet of the outer cone cylinder is provided with an air inlet grille, the inner cone cylinder is arranged inside the outer cone cylinder, and the outer cone cylinder and the inner cone cylinder form a circulation area; the inlet of the pressure regulating profile cone is connected to the outer cone cylinder, the outlet of the pressure regulating profile cone is connected to the outlet flange, and the inner profile of the pressure regulating profile cone is a combination of an arc surface and a multi-segment index surface; a piston is arranged between the inner cone cylinder and the pressure regulating profile cone, a primary seal and a secondary seal are arranged at the end of the piston, and the piston is slidably connected to the inner cone cylinder through a servo drive device; a plurality of diagonal tie rods are arranged between the servo drive device and the piston, and the two ends of the diagonal tie rod are respectively hingedly connected to the servo drive device and the piston, and the two ends of the shock absorber are respectively hingedly connected between the diagonal tie rod and the servo drive device.

2. The sub-span super wind tunnel large-diameter vibration-damping annular gap type pressure regulating valve device according to claim 1 is characterized in that: The air intake grille is composed of multiple layers of sintered metal mesh blocks, the mesh number of the air intake grille ranges from 10 to 300 meshes, the noise reduction frequency of the noise reduction arc plate of the sintered metal mesh block is 0 to 40000 Hz, and the air permeability is 30% to 100%.

3. The sub-span super wind tunnel large-diameter vibration-damping annular gap type pressure regulating valve device according to claim 1 is characterized in that: The servo drive device includes a servo hydraulic cylinder, a hydraulic rod, a spline shaft, a spline sleeve and a displacement sensor. The spline shaft is fixed to the inner cone through a support. The spline shaft and the spline sleeve form a high-torque ball spline. Spherical hinge seats are provided at both ends of the diagonal tie rod. The two spherical hinge seats are connected to the diagonal tie rod through self-locking trapezoidal threads, and the rotation directions of the self-locking trapezoidal threads of the spherical hinge seats at both ends are opposite. An anti-loosening device is provided between the spherical hinge seat and the diagonal tie rod. One end of the diagonal tie rod is connected to the piston through the spherical hinge seat, and the other end of the diagonal tie rod is hinged to the spline sleeve. The spline sleeve is driven by the hydraulic rod to slide back and forth relative to the spline shaft, and finally the diagonal tie rod is driven to drive the piston to move axially.

4. The sub-span super wind tunnel large-diameter vibration-damping annular gap type pressure regulating valve device according to claim 3 is characterized in that: The servo hydraulic cylinder is a double-acting servo hydraulic cylinder. The servo hydraulic cylinder adopts dual servo hydraulic valves to control the flow rate coarse and fine adjustment to achieve precise pressure regulation and emergency shutdown functions. The servo hydraulic cylinder adopts a double closed-loop PID servo control strategy based on the valve characteristics, with the outer ring as the total pressure and the inner ring as the valve position. The parabolic speed curve method is used to optimize the valve core switching car, thereby avoiding the valve core from quickly impacting and damaging the valve structure.

5. The sub-span super wind tunnel large-diameter vibration-damping annular gap type pressure regulating valve device according to claim 1 is characterized in that: The profile of the outer cone is designed as a cylinder-cone-cylinder structure, the cone angle of the outer cone is less than 30°, the outer cone is connected to the inner cone via an even number of support ribs, and the cone angle of the inner cone is less than 60°.

6. The sub-span super wind tunnel large-diameter vibration-damping annular gap type pressure regulating valve device according to claim 1 is characterized in that: The main seal is a T-shaped structure with an inflation port and a draft angle, and the secondary seal is a U-shaped structure.

7. The sub-span super wind tunnel large-diameter vibration-damping annular gap type pressure regulating valve device according to claim 1 is characterized in that: The piston is made of cast aluminum or steel, and the outlet of the piston is evenly distributed with tiny pores connected to the main seal.

8. The sub-span super wind tunnel large-diameter vibration-damping annular gap type pressure regulating valve device according to claim 1 is characterized in that: The shock absorber adopts a permanent magnet adjustment type magnetorheological damper or a viscous fluid damper, a magnetorheological damper or a viscous shear type damper.

9. The sub-span super wind tunnel large-diameter vibration-damping annular gap type pressure regulating valve device according to claim 1 is characterized in that: The number of the shock absorbers is n, where n is any integer between 1 and 4. The shock absorbers are used in pairs with the diagonal tie rods, and the center lines of the shock absorbers and the diagonal tie rods are perpendicular to each other.

10. The method for using the large-diameter vibration-damping annular gap type pressure regulating valve device for a sub-span super wind tunnel according to claim 1 is characterized in that: The steps include: The two ends of the pressure regulating profile cone are respectively connected to the outer cone cylinder and the outlet flange, and the inner cone cylinder and the outer cone cylinder form a fluid flow area; The servo drive device axially drives the spline sleeve to drive the inclined rod and finally drives the piston to move axially. The displacement sensor feeds back the axial position of the piston in real time. The change in the channel cross-sectional area of ​​the piston and the pressure regulating profile cone caused by the change in the axial displacement of the piston and the pressure regulating profile cone realizes the precise adjustment of the flow field pressure. The air intake grille at the air inlet stabilizes the flow and reduces air flow pulsation. The flow field outlet has no support to avoid structural vibration caused by flow separation. The spline sleeve avoids circumferential vibration of the piston. The shock absorber avoids bending and deformation of the inclined rod and achieves vibration reduction. The main seal and auxiliary seal of the piston use pipeline gas to achieve inflation sealing.

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