A resonance control method and device for a rotating machinery vibration measurement system

Abstract

The application discloses a resonance control method and device of a rotating machinery vibration measurement system, and relates to the technical field of rotating machinery vibration measurement and control. The method comprises the following steps: acquiring the corresponding rotating speed and vibration amplitude of each bearing of the rotating machinery in real time; after judging that the vibration amplitude of a bearing suddenly exceeds the sum of the amplitude threshold and the amplitude threshold tolerance under the corresponding rotating speed, analyzing the amplitude of each frequency multiplication component of the vibration, and if the 0.5 times frequency and / or 1 times frequency amplitude proportion is lower than a preset proportion, sending a resonance elimination signal to the stiffness adjustment structure of the corresponding bearing vibration measurement system to perform stiffness adjustment until the vibration amplitude drops into the amplitude threshold. The application can effectively analyze and identify the resonance of the rotating machinery vibration measurement system, and can avoid the resonance by optimizing and adjusting the pre-tightening force of the vibration probe installation fixing rod, changing the installation stiffness of the vibration measurement system, changing the inherent frequency of the vibration measurement system, and ensuring the authenticity of the vibration measurement data.

Description

Technical Field

[0001] This invention relates to the field of vibration measurement and control technology for rotating machinery, and specifically to a resonance control method and device for a vibration measurement system for rotating machinery. Background Technology

[0002] Rotating machinery is the core equipment of modern industry, the power source of industrial production, the foundation for large-scale standardized production, and a pillar of the economy and industrial chain. Its performance directly determines production efficiency, safety, and economy. Vibration measurement is a crucial link in the production and maintenance of rotating machinery. Vibration signals can reflect abnormalities such as wear, imbalance, and loosening of mechanical components (such as bearings, gears, and rotors). Sustained excessive vibration can lead to serious failures such as equipment breakage, bearing burnout, and rotor breakage, resulting in catastrophic consequences. Therefore, accurate vibration measurement is an important means to ensure the monitoring of equipment health status and fault prevention, and to extend equipment life. Vibration spectrum analysis can identify fault characteristic frequencies, avoiding sudden damage. Vibration monitoring can optimize maintenance cycles, reduce unnecessary downtime and disassembly, and reduce mechanical wear and fatigue damage. Vibration measurement can also prevent resonance in rotating machinery, maintain stable production process parameters, ensure production safety and stability, and ensure the safety of personnel and the environment. Vibration trend analysis enables predictive maintenance rather than reactive repairs, reducing unplanned downtime. Vibration data, employing techniques such as spectrum analysis and time-domain waveform analysis, can differentiate fault types (e.g., imbalance, misalignment, poor lubrication), accurately pinpointing the fault source, avoiding blind component replacement, and reducing maintenance costs. Furthermore, vibration data provides a basis for "condition-based maintenance," preventing over-maintenance (e.g., premature replacement of normal components) or under-maintenance (e.g., ignoring potential hazards), thus reducing maintenance waste. Many industries (such as power, petrochemical, and aviation) mandate vibration monitoring of critical equipment to ensure safe operation. Vibration data is a crucial basis for equipment performance acceptance and warranty liability determination, especially indispensable in high-end equipment manufacturing (e.g., wind turbines).

[0003] In summary, vibration measurement is a core tool for "equipment health management" of rotating machinery, and the accuracy and reliability of vibration measurements are fundamental to ensuring the safe operation of mechanical equipment. Precise measurement data accurately reflects the equipment's operating status, providing a scientific basis for fault diagnosis and performance evaluation, and avoiding misjudgments or missed detections due to errors. High reliability ensures consistent measurement results under different operating conditions, helping to detect potential problems such as imbalance and bearing wear early, and preventing sudden accidents. Simultaneously, it provides reliable data support for industrial automation and intelligent monitoring systems, which is crucial for improving production safety, economy, and the level of intelligent equipment management.

[0004] However, vibration measurement systems for rotating machinery (typically including vibration sensors such as vibration probes, signal conditioners, and analysis and display units) possess inherent frequencies due to their physical structure. When the external excitation frequency approaches a certain natural frequency of the measurement system, the system may absorb vibration energy and resonate. This resonance not only leads to data distortion and equipment damage but can also amplify the vibration risk of the measured object through coupling effects, potentially triggering a chain reaction of failures. Therefore, effectively analyzing and identifying the resonance in vibration measurement systems for rotating machinery and taking effective measures to reduce resonance interference and ensure the accuracy of vibration measurement data is currently lacking in the field of mechanical engineering and is urgently needed. This has immense economic value and social benefits for achieving safety, economy, and intelligent equipment management in related production processes. Summary of the Invention

[0005] The purpose of this invention is to overcome the shortcomings of the prior art and propose a resonance control method and device for a rotating machinery vibration measurement system. This method can effectively analyze and identify resonance interference in the rotating machinery vibration measurement system, and optimize the preload of the vibration probe mounting rod by adjusting the probe stiffness adjustment structure, thereby changing the installation stiffness of the vibration measurement system, changing the natural frequency of the vibration measurement system, avoiding resonance, and ensuring the authenticity of the vibration measurement data.

[0006] The technical solution adopted by this invention to solve its technical problem is:

[0007] On the one hand, a resonance control method for a rotating machinery vibration measurement system includes:

[0008] The corresponding rotational speed and vibration amplitude of each bearing in the rotating machinery are acquired in real time; the vibration amplitude is collected by a vibration probe.

[0009] The vibration amplitude of the bearing is compared with the sum of the amplitude threshold and the amplitude threshold tolerance;

[0010] After determining that the vibration amplitude of a bearing suddenly exceeds the sum of the amplitude threshold and the amplitude threshold tolerance at the corresponding rotational speed, the amplitude of each harmonic component of the vibration is analyzed. If the proportion of the amplitude of the 0.5 harmonic and / or 1 harmonic is lower than the preset ratio, a resonance cancellation signal is sent to the stiffness adjustment structure of the vibration measurement system of the corresponding bearing for stiffness adjustment until the vibration amplitude drops to within the amplitude threshold.

[0011] Methods for adjusting the stiffness of the vibration measurement system by sending resonance cancellation signals to the corresponding bearing stiffness adjustment structure include:

[0012] A first resonance cancellation signal is sent to the first-stage adjustment unit of the vibration measurement system stiffness adjustment structure of the corresponding bearing for the first stiffness adjustment. If the vibration amplitude decreases beyond the preset amplitude, the stiffness adjustment ends. If the vibration amplitude decreases less than the preset amplitude, a second resonance cancellation signal is sent to the second-stage adjustment unit of the vibration measurement system stiffness adjustment structure of the corresponding bearing for the second stiffness adjustment. If the vibration amplitude decreases beyond the preset amplitude, the stiffness adjustment ends. If the vibration amplitude decreases less than the preset amplitude, a third resonance cancellation signal is sent to the third-stage adjustment unit of the vibration measurement system stiffness adjustment structure of the corresponding bearing for the third stiffness adjustment. If the vibration amplitude decreases beyond the preset amplitude, the stiffness adjustment ends; otherwise, the instrument air intake pressure is increased, and a new round of stiffness adjustment is performed. The first-stage, second-stage, and third-stage adjustment units are cascaded composite adjustment units. The stiffness of the vibration measurement system after the second stiffness adjustment is a composite superposition of the stiffness of the first and second stiffness adjustments, and the stiffness of the vibration measurement system after the third stiffness adjustment is a composite superposition of the stiffness of all three stiffness adjustments.

[0013] A preferred method for determining whether the vibration amplitude of a bearing suddenly exceeds the sum of the amplitude threshold and the amplitude threshold tolerance at the corresponding rotational speed is as follows:

[0014] ;

[0015] in, This represents the vibration amplitude at a specific moment. Indicates rotational speed The corresponding amplitude threshold; This indicates the amplitude threshold tolerance set based on experience; This represents a typical time domain of 0.1s; This indicates that the instantaneous change exceeds the average value; This indicates that the bearing's vibration amplitude exceeds the sum of the amplitude threshold and the amplitude threshold tolerance at the corresponding rotational speed.

[0016] Preferably, the proportion of 0.5 harmonic and / or 1 harmonic amplitudes is lower than a preset ratio, as shown below:

[0017] ;

[0018] ;

[0019] ;

[0020] in, This indicates the percentage of amplitude at 0.5 harmonics; This represents the amplitude of the 0.5 harmonic vibration. This represents the vibration amplitude in a certain frequency band; max represents the maximum analysis frequency. , , Indicates the preset ratio; Indicates the percentage of amplitude at the first harmonic; This represents the amplitude of the first harmonic vibration. This indicates the percentage of amplitude at 0.5 harmonic and 1 harmonic.

[0021] Preferably, the preset ratio is a typical threshold corresponding to different application scenarios.

[0022] Preferably, the first, second, and third stiffness adjustments are specifically made by adjusting the air pressure of the pneumatic spring in the stiffness adjustment structure of the vibration measurement system to adjust the stiffness of the pneumatic spring; the pneumatic spring is installed on the mounting rod of the vibration probe to adjust the stiffness of the rotating machinery vibration measurement system.

[0023] Preferably, the stiffness of the pneumatic spring after the first stiffness adjustment , means as follows:

[0024] k1 = γ × C × P1;

[0025] Where γ represents the spring constant of the pneumatic spring; C represents the structural coefficient of the pneumatic spring; k1 represents the stiffness of the pneumatic spring after the first stiffness adjustment; P1 represents the air pressure value of the pneumatic spring after the first stiffness adjustment, and P1 is less than the maximum allowable air pressure of the pneumatic spring.

[0026] Stiffness of the pneumatic spring after the second stiffness adjustment , means as follows:

[0027] k2 = γ × C × P2;

[0028] Where k2 represents the pneumatic spring stiffness after the second stiffness adjustment; P2 represents the pneumatic spring air pressure value after the second stiffness adjustment, and P2 is less than the maximum allowable air pressure of the pneumatic spring.

[0029] Stiffness of the pneumatic spring after the third stiffness adjustment , means as follows:

[0030] k3 = γ × C × P3;

[0031] Where k3 represents the pneumatic spring stiffness after the third stiffness adjustment; P3 represents the pneumatic spring air pressure value after the third stiffness adjustment, and P3 is less than the maximum allowable air pressure of the pneumatic spring.

[0032] The natural frequency of the system after adjusting the stiffness of the pneumatic spring , means as follows:

[0033] , ;

[0034] in, Indicates the effective mass of the vibration measurement system; The maximum allowable air pressure for each pneumatic component of the stiffness adjustment structure, where n represents the nth pneumatic component; The system safety factor is set between 1.5 and 2.5 based on application scenarios and empirical data. This represents the system's natural frequency after the first stiffness adjustment; This represents the system's natural frequency after the second stiffness adjustment; This represents the system's natural frequency after the third stiffness adjustment.

[0035] On the other hand, a resonance control device for a rotating machinery vibration measurement system includes: a control processing unit and a stiffness adjustment structure; the control processing unit is used to implement the resonance control method of the rotating machinery vibration measurement system; the stiffness adjustment structure is fixed on the mounting rod of the vibration probe or installed independently.

[0036] Preferably, the stiffness adjustment structure includes a pneumatic spring, a first-stage adjustment unit, a second-stage adjustment unit, and a third-stage adjustment unit; the pneumatic spring is fixedly mounted on the mounting rod of the vibration probe; the air inlet of the pneumatic spring is connected to the first-stage adjustment unit, the second-stage adjustment unit, and the third-stage adjustment unit respectively via an air pipe; each of the first-stage adjustment unit, the second-stage adjustment unit, and the third-stage adjustment unit includes a corresponding level three-way solenoid valve and a cylinder, the cylinder being a cylinder with a piston and a spring; the three-way solenoid valve is electrically connected to the control processing unit to receive resonance cancellation signals. The first end of the three-way solenoid valve is connected to the instrument air via an air pipe, the second end of the solenoid valve is connected to the cylinder via an air pipe, and the third end of the solenoid valve is connected to the pneumatic spring via an air pipe. When the three-way solenoid valve does not receive a resonance elimination action signal, it is not energized. At this time, the instrument air is connected to the corresponding level cylinder via the air pipe, and the cylinder-to-pneumatic spring passage is closed. When the three-way solenoid valve receives a resonance elimination action signal, it is energized. At this time, the instrument air and the corresponding level cylinder passage are closed, and the cylinder-to-pneumatic spring passage is opened. At this time, the spring piston in the cylinder moves to push compressed air into the pneumatic spring.

[0037] Preferably, the pneumatic spring is inserted into the mounting rod of the vibration probe and secured by a locking nut.

[0038] Preferably, the control processing unit includes a programmable logic controller (PLC), a distributed control system (DCS), or an industrial computer.

[0039] As can be seen from the above description of the present invention, compared with the prior art, the present invention has the following beneficial effects:

[0040] (1) The present invention can automatically correct the vibration measurement system during the speed increase and decrease and operation of rotating machinery, without having to remove the measuring device for automatic correction;

[0041] (2) The present invention only analyzes the amplitude of each harmonic component of the vibration after a sudden increase in the vibration amplitude of a certain bearing is detected. Only when it is determined that the proportion of the 0.5 harmonic and / or 1 harmonic amplitude is lower than the preset ratio, the stiffness adjustment structure is activated to adjust the stiffness, so as not to trigger false adjustment and ensure accurate control.

[0042] (3) The present invention uses a three-level adjustment unit of stiffness adjustment structure to gradually increase the stiffness of the rotating machinery vibration measurement system. Each adjustment is performed and the vibration amplitude is judged, so as not to cause over-adjustment.

[0043] (4) The stiffness adjustment structure of the present invention, which includes a pneumatic spring, a first-stage adjustment unit, a second-stage adjustment unit and a third-stage adjustment unit, is simple in structure and easy to install, and will not affect the existing rotating machinery vibration measurement system. Attached Figure Description

[0044] Figure 1 This is a flowchart of the resonance control method of the rotating machinery vibration measurement system according to an embodiment of the present invention;

[0045] Figure 2 This is a schematic diagram of a stiffness adjustment structure according to an embodiment of the present invention;

[0046] Figure 3 This is a schematic diagram of another stiffness adjustment structure according to an embodiment of the present invention;

[0047] Figure 4 This is a structural framework diagram of the resonance control device of the rotating machinery vibration measurement system according to an embodiment of the present invention;

[0048] Reference numerals: 20-Control processing unit, 21-Stiffness adjustment structure, 210-Pneumatic spring, 211-First stage adjustment unit, 2110-First solenoid valve, 2111-First cylinder, 212-Second stage adjustment unit, 2120-Second solenoid valve, 2121-Second cylinder, 213-Third stage adjustment unit, 2130-Third solenoid valve, 2131-Third cylinder, 22-Vibration probe, 23-Mounting rod, 24-Extension cable, 25-Instrument air. Detailed Implementation

[0049] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0050] In the description of this invention, it should be noted that the terms "comprising," "including," or any other variations thereof are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0051] like Figure 1 As shown, the present invention provides a resonance control method for a rotating machinery vibration measurement system, comprising:

[0052] S101, real-time acquisition of the corresponding rotational speed and vibration amplitude of each bearing of the rotating machinery; the vibration amplitude is acquired by a vibration probe;

[0053] S102, compare the vibration amplitude of the bearing with the sum of the amplitude threshold and the amplitude threshold tolerance;

[0054] S103: After determining that the vibration amplitude of a bearing suddenly exceeds the sum of the amplitude threshold and the amplitude threshold tolerance at the corresponding rotational speed, the amplitude of each harmonic component of the vibration is analyzed. If the proportion of the amplitude of the 0.5 harmonic and / or 1 harmonic is lower than the preset ratio, a resonance cancellation signal is sent to the stiffness adjustment structure of the vibration measurement system of the corresponding bearing for stiffness adjustment until the vibration amplitude drops to within the amplitude threshold.

[0055] In this embodiment, the execution entity of the resonance control method for a rotating machinery vibration measurement system can be a control processing unit, specifically a control processing unit with data calculation, processing, and storage functions, such as a programmable logic controller (PLC), a distributed control system (DCS), or an advanced industrial computer. The corresponding rotational speeds of each bearing in the rotating machinery can be obtained directly by the control processing unit or indirectly by the corresponding sensors; this embodiment does not impose any limitations.

[0056] Furthermore, in step S102, the method for obtaining the amplitude threshold at the corresponding rotational speed is as follows:

[0057] Based on the rotational speed and vibration values ​​under different operating conditions of rotating machinery (including acceleration, constant speed, deceleration, etc.), a historical database of the correlation between rotational speed and vibration is established, and the upper limit threshold corresponding to different rotational speeds (using the historical upper limit value under different operating conditions as the vibration upper limit threshold under that rotational speed) is obtained as the vibration threshold.

[0058] Furthermore, in S102, the amplitude threshold tolerance is a preset value based on empirical values.

[0059] In S102, the method for determining that the vibration amplitude of a bearing suddenly exceeds the sum of the amplitude threshold and the amplitude threshold tolerance at the corresponding rotational speed is expressed as follows:

[0060] ;

[0061] in, This represents the vibration amplitude at a specific moment. Indicates rotational speed The corresponding amplitude threshold; This indicates the amplitude threshold tolerance set based on experience; This represents a typical time domain of 0.1s; This indicates that the instantaneous change exceeds the average value; This indicates that the bearing's vibration amplitude exceeds the sum of the amplitude threshold and the amplitude threshold tolerance at the corresponding rotational speed.

[0062] Furthermore, in S103, the preset ratio is set to a typical threshold corresponding to different application scenarios. The core of vibration analysis for rotating machinery is spectrum analysis, and the harmonics in the spectrum are the most important clues for diagnosing faults. Typically, in vibration analysis, the 0.5 harmonic is an important indicator of bearing oil film whirl or dynamic-static friction, and the 1st harmonic amplitude is the most significant indicator of rotor imbalance. Therefore, based on the 0.5 and 1st harmonics, the most likely faults and risks in rotating machinery can be analyzed. In addition, since the alarm value is generally half the trip value, the preset ratio can be set to 0.5. Of course, this preset ratio can also be adjusted according to the actual situation for different application scenarios.

[0063] In this embodiment, the proportion of 0.5 harmonic and / or 1 harmonic amplitudes is lower than a preset ratio, as shown below:

[0064] ;

[0065] ;

[0066] ;

[0067] in, This indicates the percentage of amplitude at 0.5 harmonics; This represents the amplitude of the 0.5 harmonic vibration. This indicates the vibration amplitude in a certain frequency band; max represents the maximum analysis frequency, which is determined based on the rotational speed and potential fault characteristics of the object under test. In general rotating machinery vibration analysis, the most common and safe starting point is to set the maximum analysis frequency to 10 to 100 times the machine rotational frequency. , , Indicates the preset ratio; Indicates the percentage of amplitude at the first harmonic; This represents the amplitude of the first harmonic vibration. This indicates the percentage of amplitude at 0.5 harmonic and 1 harmonic.

[0068] like Figure 2 , Figure 3 and Figure 4 As shown, the stiffness adjustment structure 21 described in this embodiment includes a pneumatic spring 210, a first-stage adjustment unit 211, a second-stage adjustment unit 212, and a third-stage adjustment unit 213. The pneumatic spring 210 is fixedly mounted on the mounting rod 23 of the vibration probe 22. The extension cable 24 of the vibration probe 22 passes through the mounting rod 23 and is electrically connected to the control processing unit 20. The air inlet of the pneumatic spring 210 is connected to the first-stage adjustment unit 211, the second-stage adjustment unit 212, and the third-stage adjustment unit 213 respectively through an air pipe. The first-stage adjustment unit 211, the second-stage adjustment unit 212, and the third-stage adjustment unit 213 each include a three-way solenoid valve and a cylinder. The cylinder is a cylinder with a piston and a spring. The solenoid valve is electrically connected to the control processing unit 20 to receive resonance cancellation signals. The first end of the solenoid valve is connected to the instrument air 25 through an air pipe, the second end of the solenoid valve is connected to the cylinder through an air pipe, and the third end of the solenoid valve is connected to the pneumatic spring 210 through an air pipe.

[0069] Specifically, the pneumatic spring 210 is inserted into and fixed on the mounting rod 23 of the vibration probe 22 and secured by a locking nut 214. The first-stage adjustment unit 211 includes a first solenoid valve 2110 and a first cylinder 2111; the second-stage adjustment unit 212 includes a second solenoid valve 2120 and a second cylinder 2121; the third-stage adjustment unit 213 includes a third solenoid valve 2130 and a third cylinder 2131. When the solenoid valves 2110, 2121, and 2130 are not energized, the instrument air and the corresponding cylinder passage are opened, and the pneumatic spring 210 passage is closed. The instrument air compresses the corresponding cylinder spring piston. When the solenoid valves 2110, 2121, and 2130 receive a resonance cancellation signal, they become energized, closing the instrument air and the corresponding cylinder passage and opening the cylinder and the pneumatic spring 210 passage. At this time, the cylinder spring pushes the piston to force gas into the pneumatic spring 210.

[0070] Furthermore, such as Figure 2As shown, the three cylinders can be respectively fixed to the mounting rod 23 of the vibration probe 22. Alternatively, as... Figure 3 and Figure 4 As shown, the three cylinders are not fixed to the mounting rod 23 of the vibration probe 22. If the stiffness adjustment structure 21 is placed in a protective box, the three cylinders can be fixed to the inner wall of the protective box or other positions, as long as they can be fixed. This embodiment does not impose any specific restrictions. Figure 2 and Figure 3 The structural difference lies in the fact that, in cases where the pre-tightening adjustment system has a smaller adjustment range, the device has a higher degree of integration and can employ... Figure 2 In cases where the pre-tightening adjustment system has a large adjustment range, resulting in a large device size and weight, integrating it with the vibration measurement system would affect the overall counterweight and adjustment effect of the device. Therefore, a different approach can be adopted. Figure 3 The method involves setting it externally to the vibration measurement system. Furthermore, when calculating the system's natural frequencies, Figure 3 The effective quality of the system is Figure 2 On top of that, the mass of three cylinders needs to be added.

[0071] In this embodiment, the method of sending a resonance cancellation signal to the stiffness adjustment structure 21 of the corresponding bearing in the vibration measurement system to adjust the stiffness of the vibration probe 22, in conjunction with the above-mentioned stiffness adjustment structure 21, includes:

[0072] A first resonance cancellation signal is sent to the first-stage adjustment unit 211 of the corresponding bearing's stiffness adjustment structure 21 for the first stiffness adjustment. If the vibration amplitude decreases beyond a preset amplitude, the stiffness adjustment ends. If the vibration amplitude decreases less than the preset amplitude, a second resonance cancellation signal is sent to the second-stage adjustment unit 212 of the corresponding bearing's stiffness adjustment structure 21 for the second stiffness adjustment. If the vibration amplitude decreases beyond the preset amplitude, the stiffness adjustment ends. If the vibration amplitude decreases less than the preset amplitude, a third resonance cancellation signal is sent to the third-stage adjustment unit 213 of the corresponding bearing's stiffness adjustment structure 21 for the second stiffness adjustment. The third stiffness adjustment is performed. If the vibration amplitude decreases by more than the preset amplitude, the stiffness adjustment ends. Otherwise, the instrument air intake pressure is increased (by a preset ratio or by a preset increment), and a new round of stiffness adjustment is performed. Among them, the first-level adjustment unit 211, the second-level adjustment unit 212, and the third-level adjustment unit 213 are cascaded composite three-level adjustment units. After the second stiffness adjustment, the stiffness of the rotating machinery vibration measurement system is the composite superposition of the first and second stiffness adjustments. After the third stiffness adjustment, the stiffness of the rotating machinery vibration measurement system is the composite superposition of the stiffness of the three probe stiffness adjustments.

[0073] Specifically, when the control processing unit detects that stiffness adjustment is needed, it sends a first resonance cancellation signal to the solenoid valve of the first-stage adjustment unit 211, thereby controlling the cylinder of the first-stage adjustment unit 211 to move. The air pressure in the cylinder chamber enters the pneumatic spring 210, thereby increasing the stiffness of the pneumatic spring. The working principles of the second-stage adjustment unit 212 and the third-stage adjustment unit 213 are similar. It should be noted that the cylinder models of the first-stage adjustment unit 211, the second-stage adjustment unit 212, and the third-stage adjustment unit 213 can be the same or different. That is, the air pressure output to the pneumatic spring 210 when the first-stage adjustment unit 211, the second-stage adjustment unit 212, and the third-stage adjustment unit 213 are activated can be the same or different, depending on the application. This embodiment does not impose any restrictions.

[0074] Based on the resonance characteristics, the resonance amplitude can be 2 to 10 to 20 times, or even more than 50 times, the normal vibration amplitude. Therefore, in this embodiment, the preset amplitude can be set to 50% of the vibration amplitude.

[0075] Specifically, the stiffness of the pneumatic spring after the first stiffness adjustment , means as follows:

[0076] k1 = γ × C × P1;

[0077] Where γ represents the spring constant of the pneumatic spring; C represents the structural coefficient of the pneumatic spring; k1 represents the stiffness of the pneumatic spring after the first stiffness adjustment; and P1 represents the air pressure value of the pneumatic spring after the first stiffness adjustment.

[0078] The total stiffness of the pneumatic spring after the second stiffness adjustment , means as follows:

[0079] k2 = γ × C × P2;

[0080] Where k2 represents the pneumatic spring stiffness after the second stiffness adjustment; P2 represents the pneumatic spring air pressure value after the second stiffness adjustment.

[0081] The total stiffness of the pneumatic spring after the third stiffness adjustment , means as follows:

[0082] k3 = γ × C × P3;

[0083] Where k3 represents the pneumatic spring stiffness after the third stiffness adjustment; P3 represents the pneumatic spring air pressure value after the third stiffness adjustment.

[0084] The natural frequency of the system after adjusting the stiffness of the pneumatic spring , means as follows:

[0085] , ;

[0086] in, Indicates the effective mass of the vibration measurement system; The maximum allowable air pressure for each pneumatic component of the stiffness adjustment structure, where n represents the nth pneumatic component; The system safety factor is generally set between 1.5 and 2.5, based on application scenarios and empirical data. This represents the system's natural frequency after the first stiffness adjustment; This represents the system's natural frequency after the second stiffness adjustment; This represents the system's natural frequency after the third stiffness adjustment.

[0087] like Figure 4 As shown, the present invention also discloses a resonance control device for a rotating machinery vibration measurement system, comprising: a control processing unit 20 and a stiffness adjustment structure 21; the control processing unit 20 is used to implement the resonance control method of the rotating machinery vibration measurement system.

[0088] like Figures 2-4 As shown, the stiffness adjustment structure 21 described in this embodiment includes a pneumatic spring 210, a first-stage adjustment unit 211, a second-stage adjustment unit 212, and a third-stage adjustment unit 213. The pneumatic spring 210 is fixedly mounted on the mounting rod 23 of the vibration probe 22. The extension cable 24 of the vibration probe 22 passes through the mounting rod 23 and is electrically connected to the control processing unit 20. The air inlet of the pneumatic spring 210 is connected to the first-stage adjustment unit 211, the second-stage adjustment unit 212, and the third-stage adjustment unit 213 respectively through an air pipe. The first-stage adjustment unit 211, the second-stage adjustment unit 212, and the third-stage adjustment unit 213 each include a three-way solenoid valve and a cylinder. The cylinder is a cylinder with a piston and a spring. The solenoid valve is electrically connected to the control processing unit 20 to receive resonance cancellation signals. The first end of the solenoid valve is connected to the instrument air 25 through an air pipe, the second end of the solenoid valve is connected to the cylinder through an air pipe, and the third end of the solenoid valve is connected to the pneumatic spring 210 through an air pipe.

[0089] Specifically, the pneumatic spring 210 is inserted into the mounting rod 23 of the vibration probe 22 and fixed by a locking nut 214. The first-stage adjustment unit 211 includes a first solenoid valve 2110 and a first cylinder 2111; the second-stage adjustment unit 212 includes a second solenoid valve 2120 and a second cylinder 2121; the third-stage adjustment unit 213 includes a third solenoid valve 2130 and a third cylinder 2131. When the solenoid valves 2110, 2121, and 2130 are not energized, the instrument air and the corresponding cylinder passage are opened, and the pneumatic spring 210 passage is closed. The instrument air compresses the corresponding cylinder spring piston. When the solenoid valves 2110, 2121, and 2130 receive a resonance cancellation signal, they become energized, closing the instrument air and the corresponding cylinder passage and opening the cylinder and the pneumatic spring 210 passage. At this time, the cylinder spring pushes the piston to force gas into the pneumatic spring 210.

[0090] For details not described in the resonance control device of a rotating machinery vibration measurement system, please refer to the resonance control method of a rotating machinery vibration measurement system. This embodiment will not repeat the description.

[0091] It should be noted that the resonance control device in this embodiment is based on the existing vibration measurement systems 22, 23 and 24. This vibration measurement system is the most typical vibration measurement device for rotating machinery, and will not be described in detail in this embodiment.

[0092] The above embodiments have illustrated the basic principles and implementation methods of the present invention, aiming to help understand the core concept and key steps of the invention. It should be understood that these embodiments are merely examples and do not limit the scope of application of the present invention. Those skilled in the art, based on their understanding of the concept of the present invention, can make various equivalent improvements to specific steps, parameter configurations, or device structures. These improvements also fall within the protection scope of the present invention, as defined in the appended claims.

Claims

1. A resonance control method of a rotating machinery vibration measurement system, characterized by, include: The corresponding rotational speed and vibration amplitude of each bearing in the rotating machinery are acquired in real time; the vibration amplitude is collected by a vibration probe. The vibration amplitude of the bearing is compared with the sum of the amplitude threshold and the amplitude threshold tolerance; After determining that the vibration amplitude of a bearing suddenly exceeds the sum of the amplitude threshold and the amplitude threshold tolerance at the corresponding rotational speed, the amplitude of each harmonic component of the vibration is analyzed. If the proportion of the 0.5 harmonic and / or 1 harmonic amplitude is lower than the preset ratio, a resonance cancellation signal is sent to the stiffness adjustment structure of the vibration measurement system of the corresponding bearing to adjust the stiffness, so as to adjust the natural frequency of the system until the vibration amplitude drops to within the amplitude threshold. Methods for adjusting the stiffness of the vibration measurement system by sending resonance cancellation signals to the corresponding bearing stiffness adjustment structure include: A first resonance cancellation signal is sent to the first-stage adjustment unit of the vibration measurement system stiffness adjustment structure of the corresponding bearing for the first stiffness adjustment. If the vibration amplitude decreases beyond the preset amplitude, the stiffness adjustment ends. If the vibration amplitude decreases less than the preset amplitude, a second resonance cancellation signal is sent to the second-stage adjustment unit of the vibration measurement system stiffness adjustment structure of the corresponding bearing for the second stiffness adjustment. If the vibration amplitude decreases beyond the preset amplitude, the stiffness adjustment ends. If the vibration amplitude decreases less than the preset amplitude, a third resonance cancellation signal is sent to the third-stage adjustment unit of the vibration measurement system stiffness adjustment structure of the corresponding bearing for the third stiffness adjustment. If the vibration amplitude decreases beyond the preset amplitude, the stiffness adjustment ends; otherwise, the instrument air intake pressure is increased, and a new round of stiffness adjustment is performed. The first-stage, second-stage, and third-stage adjustment units are cascaded composite adjustment units. The stiffness of the vibration measurement system after the second stiffness adjustment is a composite superposition of the first and second stiffness adjustments, and the stiffness of the vibration measurement system after the third stiffness adjustment is a composite superposition of the three stiffness adjustments. The method for determining whether the vibration amplitude of a bearing suddenly exceeds the sum of the amplitude threshold and the amplitude threshold tolerance at the corresponding rotational speed is expressed as follows: ； wherein, represents the vibration amplitude at a certain time; represents the rotation speed corresponding amplitude threshold value; represents the amplitude threshold value tolerance set empirically; represents a typical time domain of 0.1 s; represents that the instantaneous change exceeds the average value; represents that the vibration amplitude of the bearing exceeds the sum of the amplitude threshold value and the amplitude threshold value tolerance at the corresponding rotation speed.

2. The method of claim 1, wherein If the percentage of amplitude at 0.5 harmonics and / or 1 harmonics is lower than the preset ratio, it is indicated as follows: ； ； ； wherein, represents 0.5 times frequency amplitude proportion; represents 0.5 times frequency vibration amplitude; represents a certain frequency band vibration amplitude; max represents the maximum analysis frequency; , , represents a preset proportion; represents 1 times frequency amplitude proportion; represents 1 times frequency vibration amplitude; represents 0.5 times frequency and 1 times frequency amplitude proportion.

3. The method of claim 1, wherein The preset ratio is a typical threshold corresponding to different application scenarios.

4. The method of claim 1, wherein The first, second, and third stiffness adjustments specifically involve adjusting the air pressure of the pneumatic spring in the stiffness adjustment structure of the vibration measurement system to adjust the stiffness of the pneumatic spring. The pneumatic spring is mounted on the mounting rod of the vibration probe to adjust the stiffness of the rotating machinery vibration measurement system.

5. The method of claim 4, wherein the resonance control method is a method of controlling resonance of a rotating machinery vibration measurement system, characterized by, the stiffness of the aerodynamic spring after the first stiffness adjustment is represented as follows: k1 = γ × C × P1; Where γ represents the spring constant of the pneumatic spring; C represents the structural coefficient of the pneumatic spring; k1 represents the stiffness of the pneumatic spring after the first stiffness adjustment; P1 represents the air pressure value of the pneumatic spring after the first stiffness adjustment, and P1 is less than the maximum allowable air pressure of the pneumatic spring. Stiffness of the aerodynamic spring after the second stiffness adjustment is represented as follows: k2 = γ × C × P2; Where k2 represents the pneumatic spring stiffness after the second stiffness adjustment; P2 represents the pneumatic spring air pressure value after the second stiffness adjustment, and P2 is less than the maximum allowable air pressure of the pneumatic spring. Stiffness of the aerodynamic spring after the third stiffness adjustment is represented as follows: k3 = γ × C × P3; Wherein, k3 represents the third stiffness adjustment of the aerodynamic spring stiffness; P3 represents the third stiffness adjustment of the aerodynamic spring pressure value, P3 is less than the maximum allowable pressure of the aerodynamic spring; System natural frequency after pneumatic spring stiffness adjustment is represented as follows: ， ； wherein, represents the effective mass of the vibration measurement system; is the maximum allowable air pressure of each pneumatic element of the stiffness adjustment structure, and n represents the nth pneumatic element; is the system safety factor, which is set to be between 1.5 and 2.5 according to the application scenario and experience data; represents the system natural frequency after the first stiffness adjustment; represents the system natural frequency after the second stiffness adjustment; represents the system natural frequency after the third stiffness adjustment.

6. A resonance control device for a rotating machinery vibration measurement system, characterized in that, Comprise: The control processing unit is used to realize the resonance control method of the rotating machinery vibration measurement system as claimed in any one of claims 1-5; and the stiffness adjustment structure is fixed on the mounting fixed rod of the vibration probe or is independently mounted.

7. The rotating machine vibration measurement system resonance control device according to claim 6, characterized by The stiffness adjustment structure comprises an aerodynamic spring, a first-stage adjusting unit, a second-stage adjusting unit and a third-stage adjusting unit; the aerodynamic spring is fixedly mounted on the mounting fixed rod of the vibration probe; the air inlet of the aerodynamic spring is connected with the first-stage adjusting unit, the second-stage adjusting unit and the third-stage adjusting unit through air pipes respectively; the first-stage adjusting unit, the second-stage adjusting unit and the third-stage adjusting unit each comprise a corresponding three-way electromagnetic valve and a cylinder, the cylinder is a cylinder with a piston and a spring; the three-way electromagnetic valve is electrically connected with the control processing unit to receive the resonance elimination signal, the first end of the three-way electromagnetic valve is connected with the instrument air through an air pipe, the second end of the electromagnetic valve is connected with the cylinder through an air pipe, and the third end of the electromagnetic valve is connected with the aerodynamic spring through an air pipe; the three-way electromagnetic valve is not electrified when it does not receive the resonance elimination action signal, at this time, the instrument air is connected with the corresponding cylinder through an air pipe, and the cylinder to the aerodynamic spring passage is closed; the three-way electromagnetic valve is electrified when it receives the resonance elimination action signal, at this time, the instrument air to the corresponding cylinder passage is closed, and the cylinder to the aerodynamic spring passage is opened, at this time, the spring piston in the cylinder acts to push the compressed air into the aerodynamic spring.

8. The rotating machine vibration measurement system resonance control device according to claim 7, characterized by The aerodynamic spring is inserted and mounted on the mounting fixed rod of the vibration probe and is fixed through a locking nut.

9. The rotating machine vibration measurement system resonance control apparatus according to claim 6, wherein The control processing unit comprises a programmable logic controller (PLC), a distributed control system (DCS) or an industrial computer. The control processing unit comprises a programmable logic controller (PLC), a distributed control system (DCS) or an industrial computer.

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