Variable load and support rigidity guide vane adjusting mechanism multifunctional test bench and test method

Abstract

The invention belongs to the technical field of dynamic characteristic testing of guide vane adjusting mechanisms, and particularly relates to a multifunctional test bed and a test method for a guide vane adjusting mechanism with variable load and support rigidity. The test bed comprises a supporting structure, an adjusting mechanism, a blade load torque adjusting system, a supporting rigidity adjusting system, a power driving system and a testing system. The invention provides a multifunctional test bench scheme and a test method, which can simulate the dynamic characteristics and the adjustment performance of a guide vane adjustment mechanism under the influence of key factors such as different driving modes, load sizes, support stiffness, joint gaps and the like, and research the influence of the key factors on the adjustment precision and the retarding force of the mechanism. Reliable experimental data is provided for optimizing the adjusting performance and the control strategy of the guide vane adjusting mechanism.

Description

Technical Field

[0001] The invention belongs to the technical field of dynamic characteristic testing of a guide vane regulating mechanism, and in particular relates to a multifunctional test bench and a testing method for a guide vane regulating mechanism with variable load and support stiffness. Background Art

[0002] The guide vane adjustment mechanism is a key component of an aero-engine, which is used to adjust the guide vane angle to expand the compressor stability margin and prevent stalling. However, as the working time increases, it often suffers from performance failures such as stuck and decreased adjustment accuracy due to factors such as excessive workload, variable working environment, deterioration of friction performance of joint contact interface, and increased wear. In practical applications, especially in aero-engines, the blades are subjected to the combined effects of complex conditions such as aerodynamic loads, high temperature, and high pressure, which makes the dynamic characteristics complex. Although there are related studies at home and abroad, there is a lack of complete dynamic characteristics simulation test equipment. The existing test bench has a single function and cannot fully simulate the real working conditions, especially in simulating aerodynamic loads, changes in support stiffness, and joint nonlinear factors. Therefore, it is of great significance to develop a multifunctional test bench for the guide vane adjustment mechanism that can simulate variable loads and support stiffness, which can provide reliable experimental data for studying the dynamic characteristics of the mechanism, optimizing the structural design, and improving the adjustment performance.

[0003] In actual operation of the guide vane adjustment mechanism, the aerodynamic load and mechanical load on the blades will change with the change of working conditions. For example, in different flight phases (such as take-off, cruising, and landing) of aircraft engines, the aerodynamic load and mechanical load on the blades vary greatly. Through variable load experiments, the blade load under different working conditions can be simulated, and the influence of load changes on the dynamic characteristics of the guide vane adjustment mechanism can be studied, providing a basis for optimizing the blade design and the control strategy of the adjustment mechanism.

[0004] Support stiffness is one of the important factors affecting the dynamic characteristics of the guide vane adjustment mechanism. Changes in support stiffness will affect the vibration characteristics and adjustment accuracy of the blades, especially under high loads and complex working conditions. Changes in support stiffness may cause the blade adjustment mechanism to become stuck or fail. Through variable support stiffness experiments, the dynamic characteristics of the guide vane adjustment mechanism under different support stiffness can be simulated, and the influence of support stiffness on adjustment accuracy and blocking force can be studied, providing a basis for optimizing the design of the support structure. Summary of the invention

[0005] The purpose of the present invention is to provide a multifunctional test bench and test method for a guide vane adjustment mechanism with variable load and support stiffness, which can simulate the dynamic characteristics of the guide vane adjustment mechanism under different working conditions, study the influence of load changes and support stiffness on the adjustment accuracy, and provide reliable experimental data for optimizing the structural design and control strategy of the guide vane adjustment mechanism.

[0006] The technical solution to achieve the purpose of the present invention is:

[0007] A multifunctional test bench for a guide vane regulating mechanism with variable load and support stiffness comprises a supporting structure, a blade load moment regulating system, a regulating mechanism, a support stiffness regulating system, a power drive system and a testing system.

[0008] Furthermore, the support structure includes an upper base 1, a lower base 2, an actuator support seat Ⅰ18 and an actuator support seat Ⅱ27. In the support structure, the blade load torque adjustment system, the adjustment mechanism, the support stiffness adjustment system and the power drive system of the guide vane adjustment mechanism multifunctional test bench are all installed on the upper base 1. The bottom end of the linkage ring equivalent structure 12 of the adjustment mechanism is hinged to the top end of the slider 13, and the slider 13 can move along the slide rail 14, and the slide rail 14 is fixed on the lower base 2. The guide vane adjustment mechanism body is fixed to the upper base 1 through the actuator support seat Ⅰ18 and the actuator support seat Ⅱ27.

[0009] Furthermore, the blade load torque adjustment system includes an upper blade clamp 3, a lower blade clamp 4, a blade 5, two blade resistance torque simulation devices 6, a blade shaft 8, and a damper rod 7; in the blade load torque adjustment system, the blade resistance torque simulation device 6 includes an upper damping plate 31 and a lower damping plate 32, and a friction plate 34 is arranged between the upper damping plate 31 and the lower damping plate 32; the hexagonal nut 33 passes through the upper damping plate 31, the friction plate 34, and the lower damping plate 32 in each blade resistance torque simulation device 6 in turn, and is connected as a whole. Among them, the lower damping plate 32 in the upper blade resistance torque simulation device 6 is fixed to the top surface of the blade 5 through the damper rod 7, and the blade rocker arm 9 passes through the middle of the damper rod 7. The upper damping plate 31 of the upper blade resistance torque simulation device 6 is fixed to the upper blade clamp 3 through six screws; the upper blade clamp 3 is fixed above the lower blade clamp 4, and the blade 5 is between the upper blade clamp 3 and the lower blade clamp 4; the upper damping plate 31 of the lower blade resistance torque simulation device 6 is fixed to the bottom surface of the blade 5 through the damper rod 7, and the lower damping plate 32 of the lower blade resistance torque simulation device 6 is fixed to the lower blade clamp 4 through six screws; during the experiment, the adjustment mechanism transmits the drive to the blade rocker arm 9, and the blade rocker arm 9 drives the lower damping plate 32 to rotate, so that relative movement is generated between the upper damping plate 31, the lower damping plate 32 and the friction plate 34, and friction occurs. Since the lower damping plate 32 cooperates with the blade 5 through the damper rod 7, a friction torque is provided for the rotation of the blade 5. The blade resistance moment simulation device 6 generates resistance moment after calibration to simulate the blade load under different working conditions.

[0010] Furthermore, the lower blade fixture 4 is fixed on the upper base 1 of the supporting structure.

[0011] Furthermore, the middle part of the blade shaft 8 is smooth and has threads at both ends. It passes through the hexagonal nut 33, the upper damping plate 31, the friction plate 34, and the lower damping plate 32 in the upper blade resistance torque simulation device 6 from top to bottom. The bottom end is rigidly connected to the blade 5 through threads, and the top end is rigidly connected to the angular displacement sensor 28 through threads.

[0012] Furthermore, the adjustment mechanism includes a blade rocker arm 9, a blade rocker 10, a linkage ring plate 11, a linkage ring equivalent structure 12, a slider 13, a slide rail 14, a pull rod 15, a rocker arm 16 and an actuator mounting seat Ⅰ17; the power drive system includes an actuator push rod 19, an actuator cylinder 20 and a coupling 30; in the adjustment mechanism and power drive system, the actuator cylinder 20 is rotatably connected to the actuator mounting seat Ⅱ21, and the actuator mounting seat Ⅱ21 is fixed on the elastic plate 22; the two ends of the coupling 30 are respectively connected to the actuator cylinder 20 and the force sensor 29; one end of the actuator push rod 19 is mounted on the force sensor 29 The other end is hinged to one end of the rocker arm 16 through a pin shaft, the middle part of the rocker arm 16 is hinged to the actuator mounting seat Ⅰ17, the actuator mounting seat Ⅰ17 is fixed to the actuator support seat Ⅰ18, the actuator support seat Ⅰ18 is fixed to the upper base 1, the other end of the rocker arm 16 is hinged to one end of the pull rod 15 through a joint bearing; the other end of the pull rod 15 is hinged to the top of the linkage ring equivalent structure 12 through a joint bearing; the linkage ring piece 11 is fixed to the upper part of the linkage ring equivalent structure 12, and a blade rocker 10 is arranged on the linkage ring piece 11, the blade rocker arm 9 is hinged to the blade rocker 10, and the end face of the blade rocker arm 9 is perpendicular to the axis of the linkage ring equivalent structure 12.

[0013] Furthermore, the linkage ring equivalent structure 12 is a rod with a length equal to the radius of the linkage ring of the guide vane adjustment mechanism, and the axial movement of the linkage ring is replaced by the bottom connecting rail 14. The linkage ring equivalent structure 12 can decompose the spiral movement of the linkage ring into the superposition of the rotational movement of the rod and the linear movement of the guide rail.

[0014] Furthermore, the support stiffness adjustment system includes an elastic plate 22, an elastic plate clamp, an elastic plate fixing slot plate 25 and a support fixing slot plate 26. In the support stiffness adjustment system, the elastic plate clamp includes an upper elastic plate clamp 23 and a lower elastic plate clamp 24, a cavity is formed between the two and fixed on the support fixing slot plate 26; a plurality of circular stop holes are provided on the elastic plate fixing slot plate 25 and the support fixing slot plate 26, and the support stiffness of the actuator is changed by changing the position of the elastic plate clamp installed on the support fixing slot plate 26; the elastic plate 22 passes through the cavity formed by the upper elastic plate clamp 23 and the lower elastic plate clamp 24, and is fixed on the support fixing slot plate 26 through the circular stop holes on the elastic plate fixing slot plate 25; the support fixing slot plate 26 is fixed to the upper base 1 through the actuator support seat II 27.

[0015] The present invention simulates typical joints of the guide vane adjustment mechanism in the following manner: the revolute pair is simulated by a pin and a hole, the ball pair is simulated by a spherical bearing, and the cylindrical pair is simulated by a linkage ring equivalent structure.

[0016] Optionally, for a specific joint, the clearance of the revolute pair can be simulated by changing the outer diameter of the pin to study the effect of the clearance kinematic pair on the dynamic characteristics of the mechanism.

[0017] During the experiment, the electric cylinder inside the actuator body 20 provides driving force to push the actuator push rod 19 to move, thereby providing motion drive for the entire adjustment mechanism. By using the electric cylinder controller, the motion drive characteristics of the actuator, including drive trajectory, speed, stroke and other parameters, are changed to explore the influence of different drive characteristics on the adjustment accuracy and blocking force of the mechanism.

[0018] Furthermore, there are five possible installation positions of the elastic plate clamp on the support and fixing slot plate 26. The support stiffness values ​​corresponding to the various installation positions are obtained through finite element analysis.

[0019] Furthermore, the test system includes an angular displacement sensor 28 and a force sensor 29. In the test system, the angular displacement sensor 28 is used to measure the real-time rotation angle of the blade 5 during the movement of the actuator; the force sensor 29 is used to measure the blocking force applied to the actuator during the experiment.

[0020] A multifunctional test method for a guide vane adjustment mechanism with variable load and support stiffness comprises the following steps:

[0021] Step 1: Assemble the blade load torque adjustment system and the support stiffness adjustment system on the test bench, calibrate the blade resistance torque simulation device 6, set the damping size, select the installation position of the elastic plate clamp, and set the support stiffness of the actuator.

[0022] Step 2: Start the actuator and set the driving parameters. The motion drive output by the actuator push rod 19 is transmitted to the blade 5 through the adjustment mechanism to control the blade 5 to adjust the angle.

[0023] Step 3: Measure the real-time rotation angle of the blade 5 and the magnitude of the actuator's blocking force during the movement of the actuator through the test system, and record the data.

[0024] Step 4: Design an experimental plan according to the experimental verification requirements, change the damping size of the blade resistance torque simulation device and the actuator support stiffness, repeat steps 2 and 3, and analyze the influence of different loads and support stiffness on the adjustment accuracy of blade 5 through data comparison.

[0025] The beneficial effects of the present invention are as follows:

[0026] 1. The present invention is a multifunctional test bench for a guide vane adjustment mechanism with variable load and support stiffness. By adjusting the blade load through a blade resistance torque simulation device, the blade load under different working conditions can be simulated, and the influence of load changes on the dynamic characteristics of the guide vane adjustment mechanism can be studied. By adjusting the support stiffness through a support stiffness adjustment system, the dynamic characteristics of the guide vane adjustment mechanism under different support stiffness can be simulated, and the influence of support stiffness on adjustment accuracy and blocking force can be studied.

[0027] 2. The blade load torque adjustment system includes two blade resistance torque simulation devices, which are installed at the upper and lower ends of the blade. Before the experiment, the torque sensor and special tooling are used for calibration. The friction torque provided by the blade resistance torque simulation device is adjusted by tightening the hexagonal nut. It has the advantages of flexible and adjustable friction torque, stable, compact structure and simple operation.

[0028] 3. The support stiffness adjustment system is characterized by a simple and compact structure, which saves material and processing costs. The stiffness of the actuator support can be changed by changing the position of the elastic plate clamp on the elastic plate.

[0029] 4. The support stiffness slot plate is provided with 5 installation positions of the elastic plate clamp, and the support stiffness can be adjusted in a wide range; the elastic plate clamp is composed of an upper elastic plate clamp and a lower elastic plate clamp, and bolts are passed through the holes on the elastic plate clamp to tightly fix one end of the elastic plate and the elastic plate clamp together. This test bench has the advantages of reliable installation and a wide adjustable range. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 Test bench axle measurement Figure 1 ;

[0031] Figure 2 Schematic diagram of blade load torque regulation system;

[0032] Figure 3 Exploded view of blade load moment adjustment system;

[0033] Figure 4 Schematic diagram of blade resistance moment simulation device;

[0034] Figure 5 Schematic diagram of the assembly of the blade drag moment simulation device and the upper blade fixture;

[0035] Figure 6 Axonometric drawing of the regulating mechanism and power drive system;

[0036] Figure 7 Axonometric drawing of support stiffness adjustment system;

[0037] Figure 8 Experimental flow chart;

[0038] Fig. 9 Test bench axle measurement Figure 2 .

[0039] Among them, 1. upper base, 2. lower base, 3. upper blade fixture, 4. lower blade fixture, 5. blade, 6. blade resistance torque simulation device, 7. damper rod, 8. blade shaft, 9. blade rocker arm, 10. blade rocker arm, 11. linkage ring piece, 12. linkage ring equivalent structure, 13. slide rail fixing, 14. slide rail, 15. pull rod, 16. rocker arm, 17. actuator mounting seat I, 18. actuator support seat I, 19. Actuator push rod, 20. Actuator body, 21. Actuator mounting seat II, 22. Elastic plate, 23. Upper elastic plate clamp, 24. Lower elastic plate clamp, 25. Elastic plate fixing slot plate, 26. Support fixing slot plate, 27. Actuator support seat II, 28. Angular displacement sensor, 29. Force sensor, 30. Coupling, 31. Upper damping plate, 32. Lower damping plate, 33. Hexagonal nut, 34. Friction plate. DETAILED DESCRIPTION

[0040] The examples of the present invention are further described in detail below in combination with the technical solutions and the accompanying drawings.

[0041] The present invention provides a multifunctional test bench and test method for a guide vane adjustment mechanism with variable load and support stiffness, which simulates the mechanical characteristics of the guide vane adjustment mechanism under different working conditions and studies the influence of load change and support stiffness on precision adjustment by changing the support stiffness of the actuator. The axonometric diagram of this test bench is shown in the attached figure. Figure 1 , Fig. 9 shown.

[0042] A multifunctional test bench for a guide vane regulating mechanism with variable load and support stiffness comprises a supporting structure, a blade load moment regulating system, a regulating mechanism, a support stiffness regulating system, a power drive system and a testing system.

[0043] The support structure includes an upper base 1, a lower base 2, an actuator support seat Ⅰ18 and an actuator support seat Ⅱ27. In the support structure, the blade load torque adjustment system, the adjustment mechanism, the support stiffness adjustment system and the power drive system of the guide vane adjustment mechanism multifunctional test bench are all installed on the upper base 1. The bottom end of the linkage ring equivalent structure 12 of the adjustment mechanism is hinged to the top end of the slider 13 through a joint bearing, and the slider 13 can move along the slide rail 14, and the slide rail 14 is fixed on the lower base 2. The guide vane adjustment mechanism body is fixed to the upper base 1 through the actuator support seat Ⅰ18 and the actuator support seat Ⅱ27.

[0044] The blade load moment adjustment system comprises an upper blade fixture 3, a lower blade fixture 4, a blade 5, two blade resistance moment simulation devices 6, a blade shaft 8, and a damper rod 7; as shown in the attached Figure 2-Figure 5As shown; in the blade load torque adjustment system, the blade resistance torque simulation device 6 includes an upper damping plate 31 and a lower damping plate 32, and a friction plate 34 is arranged between the upper damping plate 31 and the lower damping plate 32; the hexagonal nut 33 passes through the upper damping plate 31, the friction plate 34, and the lower damping plate 32 in each blade resistance torque simulation device 6 in turn, and is connected as a whole. Among them, the lower damping plate 32 in the upper blade resistance moment simulation device 6 is fixed to the top surface of the blade 5 through the damper rod 7, and the damper rod 7 passes through the blade rocker arm 9 in the middle. The upper damping plate 31 of the upper blade resistance moment simulation device 6 is fixed to the upper blade fixture 3 through six screws 7; the upper blade fixture 3 is fixed above the lower blade fixture 4, and the blade is between the upper blade fixture 3 and the lower blade fixture 4; the upper damping plate 31 of the lower blade resistance moment simulation device 6 is fixed to the bottom surface of the blade 5, and the lower damping plate 32 of the lower blade resistance moment simulation device 6 is fixed to the lower blade fixture 4 through six screws; the lower blade fixture 4 is fixed to the upper base 1 of the supporting structure through six bolts. The middle part of the blade shaft 8 is smooth and has threads at both ends. It passes through the hexagonal nut 33, the upper damping plate 31, the friction plate 34, and the lower damping plate 32 in the upper blade resistance moment simulation device 6 from top to bottom in sequence, and the bottom end is rigidly connected to the blade 5 through threads, and the top end is rigidly connected to the angular displacement sensor 28 through threads. In this mechanism, the blade resistance torque simulation device 6 is used to provide the resistance torque for the rotation of the blade 5. The resistance torque is generated by calibration before the experiment to simulate the load of the blade 5 under different working conditions.

[0045] According to the attached Figure 2-Figure 5 Taking the blade resistance torque simulation device 6 fixed to the upper blade fixture 3 as an example, the working principle of the blade resistance torque simulation device 6 is as follows: the blade resistance torque simulation device 6 is divided into two upper and lower damping plates, and a friction plate 34 made of wear-resistant material is placed between the upper and lower damping plates. The lower damping plate 32 cooperates with the blade 5 and the blade rocker arm 9 through three damper rods 7, and the upper damping plate 31 is fixed to the upper blade fixture 3 through six screws. During the experiment, the adjustment mechanism transmits the drive to the blade rocker arm 9, and the blade rocker arm 9 drives the lower damping plate 32 to rotate, so that the upper and lower damping plates and the friction plate 34 produce relative motion and friction. Since the lower damping plate 32 cooperates with the blade 5 through the damper rod 7, it provides friction torque for the rotation of the blade 5. The principle of the blade resistance torque 6 is the same for the upper and lower parts.

[0046] Before the experiment begins, it is necessary to calibrate the blade resistance torque simulation device and set the rotational torque required for the experiment. The calibration process of the blade resistance torque simulation device 6 is as follows: by tightening the hexagonal nut 33 above the blade resistance torque simulation device 6, the pressure at the contact interface between the upper and lower damping plates and the friction plate 34 is changed, thereby changing the value of the friction torque. Use a torque sensor and special tooling to calibrate the friction torque of the blade resistance torque simulation device 6 so that it reaches the torque value required by the experimental requirements. Similarly, the load torque is changed according to the experimental requirements, and the adjustment process is as follows: by tightening the hexagonal nuts 33 of the upper and lower damping plates, the pressure at the contact interface is changed, thereby changing the value of the friction torque.

[0047] The regulating mechanism comprises a blade rocker arm 9, a blade rocker lever 10, a linkage ring piece 11, a linkage ring equivalent structure 12, a slider 13, a slide rail 14, a pull rod 15, a rocker arm 16 and an actuator mounting seat Ⅰ 17; as shown in the attached Figure 6 As shown, the power drive system includes an actuator push rod 19, an actuator cylinder body 20 and a coupling 30; in the adjustment mechanism and power drive system, the actuator cylinder body 20 is rotatably connected to the actuator cylinder mounting seat II 21, and the actuator cylinder mounting seat II 21 is fixed to the elastic plate 22 by four screws; the two ends of the coupling 30 are respectively connected to the actuator cylinder body 20 and the force sensor 29; one end of the actuator push rod 19 is installed with the force sensor 29, and the other end is hinged with one end of the rocker arm 16 through a pin shaft, and the middle part of the rocker arm 16 is connected to the actuator cylinder mounting seat I 17 through The pin is hinged, the actuator mounting seat Ⅰ17 is fixed to the actuator support seat Ⅰ18, and the actuator support seat Ⅰ18 is fixed to the upper base 1. The other end of the rocker arm 16 is hinged to one end of the pull rod 15 through a joint bearing; the other end of the pull rod 15 is hinged to the top of the linkage ring equivalent structure 12 through a joint bearing; the linkage ring plate 11 is fixed to the upper part of the linkage ring equivalent structure 12 by two bolts, and the blade rocker 10 is arranged on the linkage ring plate 11. The blade rocker arm 9 is hinged to the blade rocker arm 10, and the end face of the blade rocker arm 9 is perpendicular to the axis of the linkage ring equivalent structure 12. The linkage ring equivalent structure 12 is a rod with a length equal to the radius of the linkage ring of the guide vane adjustment mechanism, and the axial movement of the linkage ring is replaced by the slide rail 14 connected at the bottom. The linkage ring equivalent structure 12 can decompose the spiral motion of the linkage ring into the superposition of the rotational motion of the rod and the linear motion of the guide rail. By using the controller of the electric cylinder, the motion driving characteristics of the actuator, including driving trajectory, speed, stroke and other parameters, are changed to explore the influence of different driving characteristics on the adjustment accuracy and blocking force of the mechanism.

[0048] The present invention simulates typical joints of the guide vane adjustment mechanism in the following manner: the revolute pair is simulated by a pin and a hole, the ball pair is simulated by a spherical bearing, and the cylindrical pair is simulated by a linkage ring equivalent structure.

[0049] Optionally, for a specific joint, the clearance of the revolute pair can be simulated by changing the outer diameter of the pin to study the effect of the clearance kinematic pair on the dynamic characteristics of the mechanism.

[0050] The support stiffness adjustment system includes an elastic plate 22, an elastic plate fixture, an elastic plate fixing slot plate 25 and a support fixing slot plate 26. Figure 7 As shown, in the support stiffness adjustment system, the elastic plate clamp includes an upper elastic plate clamp 23 and a lower elastic plate clamp 24, a cavity is formed between the two and fixed on the support fixed slot plate 26; a plurality of circular stop holes are provided on the elastic plate fixed slot plate 25 and the support fixed slot plate 26, and the supporting stiffness of the actuator is changed by changing the position of the elastic plate clamp installed on the support fixed slot plate 26; the elastic plate 22 passes through the cavity formed by the upper elastic plate clamp 23 and the lower elastic plate clamp 24, and is fixed to the support fixed slot plate 26 with 4 fastening bolts through the circular stop holes on the elastic plate fixed slot plate 25; the support fixed slot plate 26 is fixed to the upper base 1 through the actuator support seat Ⅱ 27.

[0051] During the experiment, the electric cylinder inside the actuator body 20 provides driving force to push the actuator push rod 19 to move, thereby providing motion drive for the entire adjustment mechanism. By using the electric cylinder controller, the motion drive characteristics of the actuator, including drive trajectory, speed, stroke and other parameters, are changed to explore the influence of different drive characteristics on the adjustment accuracy and blocking force of the mechanism.

[0052] In actual operation, the support stiffness of the actuator is changed by adjusting the relative position of the elastic plate fixture and the support fixed slot plate 26. Excluding a row of circular stop holes at the upper end of the fixed elastic plate 22, there are a total of 6 rows of slots on the support fixed slot plate 26 for the elastic plate fixture to be fixed. There are 5 installable positions for the elastic plate fixture on the support fixed slot plate 26. Through finite element mechanics analysis, the actuator support stiffness values ​​corresponding to each installable position are obtained and recorded. Before the experiment begins, the actuator support stiffness is selected according to the experimental requirements, and the fixed elastic plate is installed at the corresponding position.

[0053] The test system includes an angular displacement sensor 28 and a force sensor 29. In the test system, the angular displacement sensor 28 is installed above the blade resistance torque simulation device 6, and is rigidly connected to the blade shaft 8 through a thread, and is used to measure the real-time rotation angle of the blade 5 during the movement of the actuator; the force sensor 29 is installed on the top of the piston at the output end of the actuator, and is used to measure the resistance force of the actuator during the experiment.

[0054] The installation method of the support stiffness adjustment system is:

[0055] 1) Install the actuator support seat II 27 on the upper base 1 and fix it with hexagonal screws;

[0056] 2) Install the support and fixing groove plate 26 on the actuator mounting seat II 27 and fix it with hexagonal screws;

[0057] 3) Determine the actuator support stiffness value required for the experiment, and select the installation position of the elastic plate 22 and the elastic plate fixture according to the finite element stiffness range obtained by finite element analysis;

[0058] 4) After selecting the installation position, align the upper elastic plate fixture 3 and the lower elastic plate fixture 4 and install them at the determined position. Pass the elastic plate through the cavities of the upper and lower elastic plate fixtures and install it on the elastic plate fixing plate 25. Use bolts to tighten the elastic plate fixture and fix it to the supporting fixing slot plate 26. Use bolts to tighten the elastic plate 22 and the elastic plate fixing slot plate 25 and fix them to the supporting fixing slot plate 26.

[0059] The test system is mainly composed of an angular displacement sensor 28 and a force sensor 29. The specific installation position of the angular displacement sensor 28 is shown in the attached figure. Figure 1 As shown, the specific installation position of the force sensor 29 is as shown in the attached Figure 6 The angular displacement sensor 28 is installed on the blade shaft 8 through a thread, and during the experiment, the real-time rotation angle of the blade 5 is measured during the movement of the actuator; the force sensor 29 is installed on the top of the piston at the output end of the actuator to measure the blocking force of the actuator during the experiment.

[0060] The specific experimental steps of this test bench are:

[0061] 1) Before the experiment begins, assemble the blade load torque adjustment system and the support stiffness adjustment system onto the test bench, calibrate the blade resistance torque simulation device 6, and set the damping size. Select the installation position of the elastic plate fixture, correctly install and fix the elastic plate fixture and the elastic plate 22, and set the support stiffness of the actuator.

[0062] 2) After the preparation work is completed, the electric cylinder is started, the actuator begins to move, and the motion drive output by the actuator is transmitted to the blade 5 through the adjustment mechanism to control the angle adjustment of the blade 5. The real-time rotation angle of the blade 5 and the actuator blocking force during the movement of the actuator are measured by the test system, and the data are recorded.

[0063] 3) Design an experimental scheme according to the experimental verification requirements, change the friction torque of the blade resistance torque simulation device 6 by tightening the hexagonal nuts 33 of the upper and lower damping plates; change the support stiffness of the actuator by changing the installation position of the elastic plate clamp on the support fixed slot plate 26. Repeat steps 1 and 2, and analyze the influence of different loads and support stiffness on the adjustment accuracy of the blade 5 through data comparison.

[0064] The experimental steps flow chart is attached Figure 8 .

Claims

1. A multifunctional test bench for guide vane adjustment mechanism with variable load and support stiffness, characterized in that: It includes a supporting structure, a blade load torque adjustment system, an adjustment mechanism, a supporting stiffness adjustment system, a power drive system and a testing system.

2. The multifunctional test bench for guide vane adjustment mechanism with variable load and support stiffness according to claim 1, characterized in that: The support structure comprises an upper base (1), a lower base (2), an actuator support seat I (18) and an actuator support seat II (27); in the support structure, a blade load torque adjustment system, an adjustment mechanism, a support stiffness adjustment system and a power drive system of a guide vane adjustment mechanism multifunctional test bench are all installed on the upper base (1); the bottom end of the linkage ring equivalent structure (12) of the adjustment mechanism is hinged to the top end of a slider (13), the slider (13) can move along a slide rail (14), and the slide rail (14) is fixed on the lower base (2); the guide vane adjustment mechanism body is fixed to the upper base (1) through the actuator support seat I (18) and the actuator support seat II (27).

3. The multifunctional test bench for guide vane adjustment mechanism with variable load and support stiffness according to claim 1, characterized in that: The blade load torque adjustment system comprises an upper blade fixture (3), a lower blade fixture (4), a blade (5), two blade resistance torque simulation devices (6), a blade shaft (8), and a damper rod (7); in the blade load torque adjustment system, the blade resistance torque simulation device (6) comprises an upper damping plate (31) and a lower damping plate (32), and a friction plate (34) is arranged between the upper damping plate (31) and the lower damping plate (32); a hexagonal nut (33) passes through the upper damping plate (31), the friction plate (34), and the lower damping plate (32) in each blade resistance torque simulation device (6) in sequence, and is connected into a whole; wherein the lower damping plate (32) in the upper blade resistance torque simulation device (6) is fixed to the top surface of the blade (5) through the damper rod (7), the middle of the damper rod (7) passes through the blade rocker arm (9), and the upper damping plate (31) of the upper blade resistance torque simulation device (6) is connected to the upper blade by six screws. The upper blade fixture (3) is fixed above the lower blade fixture (4), and the blade (5) is located between the upper blade fixture (3) and the lower blade fixture (4); the upper damping plate (31) of the lower blade resistance torque simulation device (6) is fixed to the bottom surface of the blade (5) through the damper rod (7), and the lower damping plate (32) of the lower blade resistance torque simulation device (6) is fixed to the lower blade fixture (4) through six screws; during the experiment, the adjustment mechanism transmits the drive to the blade rocker arm (9), and the blade rocker arm (9) drives the lower damping plate (32) to rotate, so that relative movement is generated between the upper damping plate (31), the lower damping plate (32) and the friction plate (34) to generate friction. Since the lower damping plate (32) cooperates with the blade (5) through the damper rod (7), a friction torque is provided for the rotation of the blade (5); the blade resistance torque simulation device (6) generates a resistance torque after calibration to simulate the blade load under different working conditions.

4. The multifunctional test bench for guide vane adjustment mechanism with variable load and support stiffness according to claim 1, characterized in that: The regulating mechanism comprises a blade rocker arm (9), a blade rocker (10), a linkage ring plate (11), a linkage ring equivalent structure (12), a slider (13), a slide rail (14), a pull rod (15), a rocker arm (16) and an actuator mounting seat I (17); the power drive system comprises an actuator push rod (19), an actuator cylinder body (20) and a coupling (30); in the regulating mechanism and the power drive system, the actuator cylinder body (20) is rotationally connected to the actuator mounting seat II (21), and the actuator mounting seat II (21) is fixed on the elastic plate (22); the two ends of the coupling (30) are respectively connected to the actuator cylinder body (20) and the force sensor (29); one end of the actuator push rod (19) is mounted on the force sensor (29), The other end is hinged to one end of the rocker arm (16) through a pin shaft, the middle part of the rocker arm (16) is hinged to the actuator mounting seat I (17), the actuator mounting seat I (17) is fixed to the actuator support seat I (18), the actuator support seat I (18) is fixed to the upper base (1), the other end of the rocker arm (16) is hinged to one end of the pull rod (15) through a joint bearing; the other end of the pull rod (15) is hinged to the top of the linkage ring equivalent structure (12) through a joint bearing; the linkage ring plate (11) is fixed to the upper part of the linkage ring equivalent structure (12), a blade rocker (10) is arranged on the linkage ring plate (11), the blade rocker arm (9) is hinged to the blade rocker (10), and the end face of the blade rocker arm (9) is perpendicular to the axis of the linkage ring equivalent structure (12).

5. The multifunctional test bench for guide vane adjustment mechanism with variable load and support stiffness according to claim 1, characterized in that: The support stiffness adjustment system comprises an elastic plate (22), an elastic plate clamp, an elastic plate fixing groove plate (25) and a support fixing groove plate (26); in the support stiffness adjustment system, the elastic plate clamp comprises an upper elastic plate clamp (23) and a lower elastic plate clamp (24), a cavity is formed between the two and the two are fixed on the support fixing groove plate (26); a plurality of circular stop holes are arranged on the elastic plate fixing groove plate (25) and the support fixing groove plate (26), and the support stiffness of the actuator cylinder is changed by changing the position of the elastic plate clamp installed on the support fixing groove plate (26); the elastic plate (22) passes through the cavity formed by the upper elastic plate clamp (23) and the lower elastic plate clamp (24), and is fixed on the support fixing groove plate (26) through the circular stop holes on the elastic plate fixing groove plate (25); the support fixing groove plate (26) is fixed to the upper base (1) through the actuator cylinder support seat II (27).

6. The multifunctional test bench for guide vane adjustment mechanism with variable load and support stiffness according to claim 1, characterized in that: The test system comprises an angular displacement sensor (28) and a force sensor (29); in the test system, the angular displacement sensor (28) is used to measure the real-time rotation angle of the blade (5) during the movement of the actuator; The force sensor (29) is used to measure the blocking force applied to the actuator during the experiment.

7. A multifunctional test bench for guide vane adjustment mechanism with variable load and support stiffness according to any one of claims 1 to 6, characterized in that: The lower blade fixture (4) is fixed on the upper base (1) of the support structure; the middle part of the blade shaft (8) is smooth and has threads at both ends, and passes through the hexagonal nut (33), the upper damping plate (31), the friction plate (34), and the lower damping plate (32) in the upper blade resistance torque simulation device (6) in sequence from top to bottom, the bottom end is rigidly connected to the blade (5) through the threads, and the top end is rigidly connected to the angular displacement sensor (28) through the threads.

8. A multifunctional test bench for guide vane adjustment mechanism with variable load and support stiffness according to any one of claims 1 to 6, characterized in that: The linkage ring equivalent structure (12) is a rod with a length equal to the radius of the linkage ring of the guide vane adjustment mechanism, and is connected to a slide rail (14) at the bottom to replace the axial movement of the linkage ring; the linkage ring equivalent structure (12) can decompose the spiral movement of the linkage ring into the superposition of the rotational movement of the rod and the linear movement of the guide rail.

9. A multifunctional test bench for guide vane adjustment mechanism with variable load and support stiffness according to any one of claims 1 to 6, characterized in that: The elastic plate clamp has five installable positions on the supporting fixed slot plate (26); and the support stiffness value corresponding to each installation position is obtained through finite element analysis.

10. A multifunctional test method for a guide vane adjustment mechanism with variable load and support stiffness is carried out using a multifunctional test bench for a guide vane adjustment mechanism with variable load and support stiffness as described in any one of claims 1 to 9, characterized in that: The following steps are involved: Step 1: Assemble the blade load torque adjustment system and the support stiffness adjustment system on the test bench, calibrate the blade resistance torque simulation device (6), set the damping size, select the installation position of the elastic plate fixture, and set the support stiffness of the actuator; Step 2: Start the actuator and set the drive parameters. The motion drive output by the actuator push rod (19) is transmitted to the blade (5) through the adjustment mechanism, and the blade (5) is controlled to adjust the angle. Step 3: Using a test system to measure the real-time rotation angle of the blade (5) and the magnitude of the actuator's blocking force during the actuator's movement, and record the data; Step 4: Design an experimental plan according to the experimental verification requirements, change the damping size of the blade resistance torque simulation device and the actuator support stiffness, repeat steps 2 and 3, and analyze the influence of different loads and support stiffness on the blade (5) adjustment accuracy through data comparison.

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