A hydraulically buffered electromagnetically driven rotary-static collision device and its test method

Abstract

This invention discloses a hydraulically buffered electromagnetically driven rotary-static collision device and test method, relating to the field of aero-engine blade collision testing technology. The device includes a housing, an electromagnetic coil disposed at the end of the housing, a hydraulic damper sequentially passing through the electromagnetic coil and the housing, a triaxial force sensor and a collision head sequentially disposed at the extension end of the hydraulic damper, a permanent magnet sleeved on the end of the hydraulic damper away from the housing, a first spring sleeved on the outer wall of the hydraulic damper with one end connected to the permanent magnet and the other end connected to the housing, and a PID controller electrically connected to the triaxial force sensor and used to control the current of the electromagnetic coil in real time. The collision head extends out of the housing away from the electromagnetic coil. The hydraulic damper provides a constant contact force to the collision head, preventing it from retracting. The PID controller can control the current of the electromagnetic coil in real time, thereby adjusting the attraction force of the electromagnetic coil to the permanent magnet to ensure the stability of the collision force.

Description

Technical Field

[0001] This invention relates to the field of aero-engine blade impact testing technology, specifically to a hydraulically buffered electromagnetically driven rotating-static impact testing device and test method. Background Technology

[0002] Rotor-to-station rubbing is a typical failure of aero-engines, potentially causing excessive rotor vibration, casing coupling resonance, and blade breakage or loss, severely impacting engine safety. Modern aero-engines' continuous pursuit of high thrust-to-weight ratio and low fuel consumption has led to increasingly smaller rotor-to-station clearances, resulting in a higher probability of rotor-to-station rubbing. Therefore, researching the rubbing mechanism is of great significance. Existing rotor-to-station rubbing devices mostly use servo motors to drive rigid rubbing heads, which has the following drawbacks: mechanical drive is prone to causing the rubbing head to retract due to reaction force upon impact, affecting measurement accuracy; and relying solely on mechanical structural clearances to absorb impact cannot adjust the rubbing force, leading to inconsistent rubbing forces and difficulty in handling high-frequency dynamic rubbing.

[0003] Therefore, it is necessary to develop and design a hydraulic buffer electromagnetic drive rotary-static collision device and test method to solve the problem of high-frequency vibration absorption and the problem of collision retraction of the collision head controlled by the stepper motor, so as to achieve stable collision force. This is a technical problem that urgently needs to be solved by those skilled in the art. Summary of the Invention

[0004] To address the aforementioned problems, this invention provides a hydraulically buffered electromagnetically driven rotary-static collision device and testing method, which solves the problems of high-frequency vibration absorption and the collision retraction of the stepper motor-controlled collision head, thereby achieving stable collision force.

[0005] To achieve the above objectives, the present invention provides the following solution:

[0006] A hydraulically buffered electromagnetically driven rotary-static collision device includes a housing, an electromagnetic coil disposed at the end of the housing, a hydraulic damper passing through the electromagnetic coil and the housing in sequence, a triaxial force sensor and a collision head disposed in sequence at the extension end of the hydraulic damper, a permanent magnet sleeved on the end of the hydraulic damper away from the housing, a first spring sleeved on the outer wall of the hydraulic damper with one end connected to the permanent magnet and the other end connected to the housing, and a PID controller electrically connected to the triaxial force sensor and used to control the magnitude of the current of the electromagnetic coil in real time. The collision head extends out of the housing at the end away from the electromagnetic coil.

[0007] Preferably, the hydraulic damper includes an outer tube, an inner tube sleeved inside the outer tube, an oil drain hole and a pressure accumulator sponge disposed in the inner tube, a piston built into the inner tube and a piston rod connected to the piston, a second spring disposed between the inner tube and the outer tube, and an adjuster for adjusting the damping force of the hydraulic damper. The outer tube is connected to the permanent magnet, and the piston rod is connected to the triaxial force sensor.

[0008] Preferably, the end of the triaxial force sensor away from the friction head is provided with a slider, the slider is used to slide along the inner wall of the housing, the slider is provided with a through hole for the piston rod to pass through, and the inner wall of the housing is provided with a slide rail that cooperates with the slider.

[0009] Preferably, the permanent magnet is fixedly connected to the outer tube via an aluminum mounting base.

[0010] Preferably, the friction head is snapped into place with the triaxial force sensor.

[0011] Preferably, the end of the housing away from the permanent magnet is fitted with the outer wall of the casing of the aero-engine to be measured, and the housing is provided with a bracket for fixing the housing to the casing of the aero-engine to be measured.

[0012] Preferably, an infrared temperature sensor for real-time monitoring of the temperature of the contact area is provided on one side of the bracket.

[0013] Preferably, the PID controller includes an ADC analog-to-digital converter and a DSP digital signal processor.

[0014] This invention also discloses a hydraulically buffered electromagnetic drive rotary-to-static collision test method, which uses the hydraulically buffered electromagnetic drive rotary-to-static collision device as described above, characterized by comprising the following steps:

[0015] Preset hydraulic damping parameters;

[0016] Replace and adjust the contact head according to the test requirements;

[0017] The control mode of the PID controller is preset based on the frequency domain characteristics of the force signal;

[0018] The PID controller controls the electromagnetic coil to operate, performs the impact test, and monitors the impact force to control its magnitude.

[0019] When the friction force exceeds the safety threshold, the PID controller reduces the output current.

[0020] Preferably, the PID controller operates in steady-state mode. Constant, PID parameters =2, =0.5, =0.1), Impact Mode (Automatic Increase) It can be either up to 1.5 (suppressing high-frequency disturbances) or a self-learning mode (optimizing PID parameters based on historical data).

[0021] The present invention achieves the following technical effects compared to the prior art:

[0022] By setting a hydraulic damper to provide a constant contact force to the friction head, the problem of friction head retraction is avoided. The friction force is monitored in real time by a triaxial force sensor, and the corresponding value is transmitted to the PID controller. The PID controller can control the current of the electromagnetic coil in real time, thereby adjusting the attraction force of the electromagnetic coil on the permanent magnet to ensure the stability of the friction force. Attached Figure Description

[0023] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0024] Appendix Figure 1 This is a schematic cross-sectional view of the hydraulic buffer electromagnetic drive rotary-static collision device disclosed in this invention.

[0025] Appendix Figure 2 This is a three-dimensional structural schematic diagram of the hydraulic buffer electromagnetic drive rotary-static collision device disclosed in this invention.

[0026] Appendix Figure 3 This is a schematic diagram of the structure of the hydraulic buffer electromagnetic drive rotary-static collision device disclosed in this invention installed on the casing of the aircraft engine to be measured.

[0027] Among them, 1. hydraulic damper; 2. mounting aluminum base; 3. permanent magnet; 4. first spring; 5. electromagnetic coil; 6. housing; 7. slider; 8. triaxial force sensor; 9. contact head. Detailed Implementation

[0028] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0029] The purpose of this invention is to provide a hydraulically buffered electromagnetically driven rotary-static collision device and test method, which solves the problem of high-frequency vibration absorption and the problem of collision retraction of the collision head controlled by the stepper motor, thereby achieving stable collision force.

[0030] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0031] Figures 1-3 The hydraulic buffer electromagnetic drive rotary-static collision device disclosed in this embodiment of the invention includes at least a housing 6. An electromagnetic coil 5 is disposed at one end of the housing 6. A hydraulic damper 1 is disposed inside the housing 6. The electromagnetic coil 5 is sleeved on the outer periphery of the hydraulic damper 1. The telescopic end of the hydraulic damper 1 extends into the housing 6 and is connected to the collision head 9 via a triaxial force sensor 8. A permanent magnet 3 is disposed at the end of the hydraulic damper 1 away from the housing 6. A first spring 4 is sleeved on the outer wall of the hydraulic damper 1, with one end of the first spring 4 fixedly connected to the permanent magnet 3 and the other end of the first spring 4 connected to the housing 6. The body 6 is fixedly connected and also includes a PID controller electrically connected to the triaxial force sensor 8. The PID controller is used to control the current of the electromagnetic coil 5 in real time, thereby controlling the magnetic force of the electromagnetic coil 5. By setting the hydraulic damper 1, a constant contact force is provided to the friction head 9 to avoid the problem of the friction head 9 retracting. The friction force is monitored in real time by the triaxial force sensor 8 and the corresponding value is transmitted to the PID controller. The PID controller can control the current of the electromagnetic coil 5 in real time, thereby adjusting the attraction force of the electromagnetic coil 5 on the permanent magnet 3 to ensure the stability of the friction force.

[0032] It should be noted that the electromagnetic coil 5 is ring-shaped and fixed to the end of the housing 6 near the permanent magnet 3. When energized, it generates an electromagnetic force that attracts the permanent magnet 3, which drives the hydraulic damper 1 to push the friction head 9 into the casing of the aircraft engine to be measured. The electromagnetic force is adjusted by controlling the current of the electromagnetic coil 5 through the PID controller. The electromagnetic coil 5 adopts a dual-winding coil. The main winding is responsible for conventional displacement control, and the secondary winding is dedicated to high-frequency fine adjustment. The response time of the secondary winding is <0.1ms, which is used to compensate for the lag of PID control.

[0033] The end of the housing 6 near the friction head 9 is open, and the end away from the friction head 9 has a hole for the hydraulic damper 1 to pass through. The housing 6 is a hollow cylinder, and openings are provided on both sides of the housing 6 to facilitate sensor wiring and observation.

[0034] The triaxial force sensor 8, the rubbing head 9, and the housing 6 are coaxial. There are gaps between the triaxial force sensor 8, the rubbing head 9 and the inner wall of the housing 6, and the rubbing head 9 extends from one end of the housing 6.

[0035] Figures 1-3In one embodiment, the hydraulic damper 1 includes an outer tube, an inner tube sleeved inside the outer tube, an oil drain hole and a pressure accumulator sponge disposed in the inner tube, a piston and a piston rod connected to the piston disposed inside the inner tube, a second spring disposed between the outer end of the inner tube and the inner end of the outer tube, and an adjuster for adjusting the damping force of the hydraulic damper 1. The outer tube is connected to a permanent magnet 3, and the piston rod is connected to a triaxial force sensor 8, and the piston rod is coaxial with the outer casing. When the piston rod is subjected to an impact force, the piston rod drives the piston to squeeze the hydraulic oil inside the inner tube, thus reducing the hydraulic pressure. After being pressurized, the oil is discharged one by one from the drain hole of the inner tube. Part of the discharged hydraulic oil flows back to the inner tube through the return hole, and the other part enters the accumulator sponge. After the external force disappears, the second spring quickly pushes the piston rod to reset, and a negative pressure is formed in the inner tube. The check valve set on the inner tube opens automatically, and the hydraulic oil quickly returns to the inner tube through the opened check valve. The damper returns to its initial state. Depending on different friction conditions, the oil pressure can be changed by controlling the oil flow through the regulator at the top of the hydraulic damper 1. The hydraulic damper 1 is existing technology and will not be described in detail here.

[0036] When the current in the electromagnetic coil 5 decreases or disappears, the hydraulic damper 1 and its connected triaxial force and friction head 9 are reset, thereby ending the friction.

[0037] Figures 1-3 As a preferred method, the end of the triaxial force sensor 8 away from the friction head 9 is provided with a slider 7. The slider 7 is used to slide along the inner wall of the housing 6. The slider 7 is provided with a through hole for the piston rod to pass through. The inner wall of the housing 6 is provided with a slide rail that cooperates with the slider 7. The cooperation between the slider 7 and the slide rail can guide the friction head 9 during the extension and retraction process, while reducing the friction between the slider 7 and the inner wall of the housing 6.

[0038] It should be noted that the inside of the slide is coated with grease, and the slider 7 is arranged in a ring inside the housing 6. The slider 7 is perpendicular to the axis of the housing 6, and one end is fixedly connected to the triaxial force sensor 8, so that it can slide freely along the axis inside the housing 6.

[0039] refer to Figures 1-3 The permanent magnet 3 is fixedly connected to the outer tube of the hydraulic damper 1 through the mounting aluminum base 2, ensuring the firmness of the permanent magnet 3.

[0040] refer to Figures 1-3 As a preferred method, the friction head 9 is snapped together with the triaxial force sensor 8, which facilitates the disassembly and assembly of the friction head 9 for replacement. When conducting different tests, a specific friction head 9 is selected.

[0041] It should be noted that the initial design of the contact head 9 is an arc-shaped contact surface with a radius of curvature approximately the same as that of the casing of the aircraft engine to be measured. The rear end is fixedly connected to the triaxial force sensor 8. At the same time, a library of contact heads in various materials (ceramic, titanium alloy) and shapes (arc, wedge) is provided to adapt to different testing needs.

[0042] The snap-fit ​​connection can be achieved by designing a flange on the end face of the triaxial force sensor 8, inserting the corresponding groove of the friction head 9, and then tightening it with circumferentially distributed high-strength bolts. Alternatively, the triaxial force sensor 8 can have built-in stainless steel elastic claws (such as Bainstein spring steel sheets). When the friction head 9 is pushed in, the claws expand and lock, and pressing the release ring enables quick disassembly.

[0043] refer to Figures 1-3 As a preferred method, the end of the housing 6 away from the permanent magnet 3 is engaged with the outer wall of the casing of the aero-engine to be measured, and a bracket is provided for fixing the housing 6 on the casing of the aero-engine to be measured. The bracket is used to fix the housing 6 on the casing of the aero-engine to be measured, so that the rubbing head 9 extends into the aero-engine to be measured and rubs against the blades of the aero-engine to be measured under the drive of the PID controller.

[0044] It should be noted that the mating end of the housing 6 with the casing of the aircraft engine to be measured is thickened and cut to the surface curvature of the casing in order to fix it on the casing.

[0045] refer to Figures 1-3 As one implementation method, an infrared temperature sensor is installed on one side of the bracket for real-time monitoring of the temperature of the rubbing area. The infrared temperature sensor is electrically connected to the PID controller. The infrared temperature sensor collects the temperature signal of the rubbing area and transmits the temperature signal to the PID controller. If the temperature exceeds the threshold temperature, the PID controller automatically shortens the duration of rubbing under high heat conditions.

[0046] refer to Figures 1-3 In one implementation, the PID controller includes an ADC analog-to-digital converter and a DSP digital signal processor. The ADC (sampling rate ≥10kHz) is responsible for converting the continuous analog signals (such as temperature, pressure, speed) detected by the sensor into discrete digital quantities for the processor to perform PID calculations. The DSP can perform the discretization calculation of the PID in real time.

[0047] The PID controller controls the current of the electromagnetic coil 5, thereby controlling the magnetic force to control the axial extension of the hydraulic damper 1 and the friction head 9. The PID controller integrates a high-precision ADC and DSP processor to acquire the axial force signal of the triaxial force sensor 8 in real time. The current drive circuit of the electromagnetic coil 5 uses PWM modulation, supporting continuous adjustment from 0-30A. Its control logic is as follows:

[0048] First set the target friction force Real-time current is calculated using a PID algorithm. :

[0049]

[0050] in This represents the error at the current time t, i.e., the difference between the target friction force and the actual friction force. ; The target friction force is set; The actual friction force measured at time t is the real-time friction force measured by the triaxial force sensor 8. Calculate the real-time current value output by the PID controller; This is the proportional gain coefficient, used to adjust the system's response to the current error; This is the integral gain coefficient, used to eliminate the steady-state error of the system by adjusting for the accumulation of past errors; The differential gain coefficient is used to predict future error trends, thereby suppressing system oscillations. , , These are adjustable parameters;

[0051] Simultaneously, based on the frequency domain characteristics of the force signal (such as the proportion of high-frequency components under impact conditions), the PID parameters are dynamically adjusted (e.g., increasing oscillation suppression). The PID controller has three preset modes: steady-state mode (…). Constant, PID parameters =2, =0.5, =0.1), Impact Mode (Automatic Increase) Up to 1.5, suppressing high-frequency disturbances) and self-learning mode (optimizing PID parameters based on historical data), different modes are selected for collision tests according to different test requirements.

[0052] This invention also discloses a hydraulically buffered electromagnetic drive rotary-to-static collision test method, which utilizes the aforementioned hydraulically buffered electromagnetic drive rotary-to-static collision device and includes the following steps:

[0053] Step 1), preset hydraulic damping parameters: adjust the regulator at the top of the hydraulic damper 1 according to the target impact intensity to control the oil port flow and change the oil pressure;

[0054] Step 2), Adjustment of the friction head 9: Replace the friction head 9 with one of different materials and shapes according to the test requirements to achieve spot friction and partial friction tests.

[0055] Step 3), PID controller mode preset: Based on the frequency domain characteristics of the force signal (such as the proportion of high-frequency components under impact conditions), the PID parameters are dynamically adjusted (such as increasing the suppression of oscillation). The control module presets three modes, namely steady-state mode ( Constant, PID parameters =2, =0.5, =0.1), Impact Mode (Automatic Increase) Up to 1.5, suppressing high-frequency disturbances) and self-learning mode (optimizing PID parameters based on historical data).

[0056] Step 4), the PID controller controls the electromagnetic coil 5 to be energized, so that the rubbing head 9 moves in the axial direction until the rubbing head 9 and the blade of the aero-engine to be measured rub against each other.

[0057] Step 5), the PID controller controls the electromagnetic coil 5 and monitors the friction force to make it move quantitatively in order to control the degree of friction;

[0058] Step 6): The PID controller controls the triaxial force sensor 8 to collect tangential and axial friction forces during the rubbing process, and controls the infrared sensor to collect the rubbing temperature signal.

[0059] Step 7) When the axial friction force exceeds the safety threshold, the PID controller controls the output current of the electromagnetic coil 5 to reduce the current, thus protecting the system. At the same time, based on the data from the infrared temperature sensor, the duration of friction under high-heat conditions is automatically shortened.

[0060] It should be noted that, for those skilled in the art, it is obvious that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from the spirit or essential characteristics of the invention. Therefore, the embodiments should be considered exemplary and non-limiting in all respects, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

Claims

1. A hydraulically buffered electromagnetically driven rotary-static collision device, characterized in that, The device includes a housing, an electromagnetic coil disposed at the end of the housing, a hydraulic damper that passes through the electromagnetic coil and the housing in sequence, a triaxial force sensor and a friction head disposed in sequence at the extension end of the hydraulic damper, a permanent magnet sleeved on the end of the hydraulic damper away from the housing, a first spring sleeved on the outer wall of the hydraulic damper with one end connected to the permanent magnet and the other end connected to the housing, and a PID controller electrically connected to the triaxial force sensor and used to control the magnitude of the current of the electromagnetic coil in real time. The friction head extends out of the housing at the end away from the electromagnetic coil. The hydraulic damper includes an outer tube, an inner tube sleeved inside the outer tube, an oil drain hole and a pressure accumulator sponge disposed in the inner tube, a piston built into the inner tube and a piston rod connected to the piston, a second spring disposed between the inner tube and the outer tube, and an adjuster for adjusting the damping force of the hydraulic damper. The outer tube is connected to the permanent magnet, and the piston rod is connected to the triaxial force sensor. The triaxial force sensor has a slider at the end away from the friction head. The slider is used to slide along the inner wall of the housing. The slider has a through hole for the piston rod to pass through. The inner wall of the housing has a slide rail that cooperates with the slider.

2. The hydraulic buffer type electromagnetic drive rotary-static collision device according to claim 1, characterized in that, The permanent magnet is fixedly connected to the outer tube by an aluminum mounting base.

3. The hydraulic buffer type electromagnetic drive rotary-static collision device according to claim 1, characterized in that, The friction head is engaged with the triaxial force sensor.

4. The hydraulic buffer type electromagnetic drive rotary-static collision device according to claim 1, characterized in that, The end of the housing away from the permanent magnet is fitted with the outer wall of the casing of the aero-engine to be measured, and the housing is provided with a bracket for fixing the housing to the casing of the aero-engine to be measured.

5. The hydraulic buffer type electromagnetic drive rotary-static collision device according to claim 4, characterized in that, An infrared temperature sensor is installed on one side of the bracket for real-time monitoring of the temperature of the contact area.

6. The hydraulic buffer type electromagnetic drive rotary-static collision device according to claim 1, characterized in that, The PID controller includes an ADC analog-to-digital converter and a DSP digital signal processor.

7. A hydraulically buffered electromagnetic drive rotary-to-static collision test method, using the hydraulically buffered electromagnetic drive rotary-to-static collision device as described in any one of claims 1-6, characterized in that, Includes the following steps: Preset hydraulic damping parameters; Replace and adjust the contact head according to the test requirements; The control mode of the PID controller is preset based on the frequency domain characteristics of the force signal; The PID controller controls the electromagnetic coil to operate, performs the impact test, and monitors the impact force to control its magnitude. When the friction force exceeds the safety threshold, the PID controller reduces the output current.

8. The hydraulic buffer electromagnetic drive rotary-static collision test method according to claim 7, characterized in that, The PID controller operates in one of the following modes: steady-state mode, impulse mode, and self-learning mode. The parameters of the steady-state mode are: Constant, PID parameters =2, =0.5, =0.1; The parameters of the impact mode are: automatic increase. Up to 1.5, suppressing high-frequency disturbances; The parameters of the self-learning mode are: PID parameters are optimized based on historical data.

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