CN110646138A - Dynamic balance method and analysis device for rotary machine without key phase and trial weight - Google Patents
Dynamic balance method and analysis device for rotary machine without key phase and trial weight Download PDFInfo
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Abstract
The embodiment of the invention provides a rotating machinery dynamic balance method without key phase and trial weight and an analysis device. The pulse signal sensor and the vibration sensor are introduced, and a key phase is not required to be introduced, but a specific blade is selected as a virtual key phase. Determining a pulse signal of a virtual key phase as a starting pulse and carrying out data backtracking, eliminating (n-1) pulse signals by using a signal processing method to obtain pulse signal data generated by the virtual key phase every revolution of a shaft, namely a key phase signal, carrying out parameter identification on the unbalanced vibration of the rotor by taking the key phase signal as reference, and solving the unbalanced vibration fault of the rotor by using a non-trial-weight dynamic balance method. The method is suitable for the working condition that the rotary machine cannot install the key phase or the key phase is inaccurate in reference, reduces the installation workload and the monitoring cost, expands the application range of the non-trial-weight field dynamic balance method of the rotary machine rotor, and provides a new direction for the dynamic balance of the rotary machine rotor.
Description
Technical Field
The invention relates to a dynamic balance method and an analysis device for a rotary machine without a key phase and a trial weight, and belongs to the technical field of vibration monitoring of rotary machines.
Background
The rotary machine is a common key device in various industries and is an important device widely applied in national economy and national defense industry of China. The rotary machine is greatly influenced by materials, and the rotor system of the machine is unbalanced and has faults caused by impact, corrosion, abrasion and coking. Wherein the mass imbalance of the rotor system is the main cause of the same-frequency vibration failure of the rotating machinery. Statistical data show that the vibration fault of the unit, which occurs on site, belongs to the mass unbalance of the rotor and accounts for more than 75 percent.
When the rotating machine has an unbalanced fault, the existing solution is as follows: dynamic balancing, on-site dynamic balancing and online dynamic balancing. Engineering practice shows that the advantages of on-site dynamic balance in solving the vibration fault of the unit are the greatest. The existing field dynamic balance technology generally needs to test the original vibration condition of a rotor system and the vibration condition after weight addition to diagnose the size and the phase of the original unbalance, and then balance correction is carried out, so that the aim of reducing vibration is fulfilled. The trial-weighing process of the method is often repeated for many times, thereby causing multiple startup and shutdown. This causes difficulties in the normal and continuous operation of the production in the enterprise, and for large-scale plants, the economic loss of each start-up and shut-down is enormous, sometimes even the conditions are not allowed. To solve the above problems, a trial-weight-free dynamic balance technique has appeared. The dynamic balancing technology without trial weight is a branch of the field dynamic balancing technology, and can solve the problem of unbalance of the rotating machinery. The technology solves the problem of repeated weight test in the field dynamic balance technology, does not need weight test, and can directly calculate the balance weight according to the vibration size.
In the conventional rotor dynamic balance method and the non-trial-weight rotor dynamic balance method, a key phase is introduced as a reference to obtain the amplitude and the phase angle of the unbalanced vibration of the rotor so as to calculate the counterweight mass and the counterweight phase angle. However, in an actual rotating machine set, there are often cases where the key phase cannot be installed due to a narrow space, or where the key phase reference is inaccurate, and effective calculation and weighting cannot be performed.
Disclosure of Invention
In view of the above, the present invention provides a dynamic balance method and an analysis apparatus for a rotary machine without a key phase and without a trial weight. The rotor unbalance phenomenon of the rotating machine is conveniently identified by parameters, the purpose of completing dynamic balance by starting the vehicle at one time under the condition of no key phase installation is realized, and the cost is reduced.
The embodiment of the invention provides a rotating machinery keyless phase non-trial-and-error dynamic balance method, which comprises the following steps:
combining a pulse signal sensor with a vibration sensor, monitoring a rotating machine in real time, and acquiring related signals including pulse signals, vibration signals and the like in the working process of a rotor system at a certain specific rotating speed R within a working rotating speed range;
and determining a specific rotating blade on the rotating machine as a reference blade according to the acquired pulse signals, wherein the rotating blades on the rotating machine except the reference blade are conventional blades. Treating the reference leaf as a "virtual key phase";
processing the acquired pulse signals to obtain key phase signals generated by the reference blade every revolution of the shaft, namely pulse signals generated by the virtual key phase;
comparing the key phase signal with the vibration signal, and determining the phase angle of the positive peak point of the synchronous component of the vibration signal relative to the vibration sensor probe, namely the unbalanced vibration phase angle theta1；
And (3) carrying out action balance and verifying the counterweight effect by combining a non-trial-weight field dynamic balance method: according to the obtained maximum amplitude value A1And unbalance vibration phase angle theta1Calculating to obtain the mass M of the counterweight and the phase angle of the counterweight
The balance weight is finished when the vehicle stops;
and starting the vehicle, detecting the operation of the vehicle at a specific rotating speed R, and verifying the counterweight effect.
Further, the pulse signal sensor combines together with vibration sensor, carries out real-time supervision to the rotating machinery, and relevant signal including in the collection rotor system working process: starting the vehicle, keeping the vehicle to a certain specific rotating speed R within the working rotating speed range, acquiring pulse signals of each rotating blade through a pulse signal sensor, acquiring vibration signals of a rotor by the vibration sensor, and acquiring synchronous vibration components caused by unbalance of the rotor through the vibration signals; and stopping the machine, and keeping the acquisition of the pulse signal and the vibration signal until the rotor completely stops.
Further, the determination of the "virtual key phase" is: the pulse number of the obtained pulse signal is the same as the number n of the rotating blades when the rotor rotates for one circle, after the rotor completely stops, if the pulse signal sensor is rotating the rotating blades, the obtained signal is a continuous high-voltage signal, and if the pulse signal sensor is staggered with the rotating blades, the obtained signal is a low-voltage signal; if the signal obtained after the complete stop is a continuous high voltage signal, the rotating blade opposite to the pulse signal sensor is selected as a reference blade, namely a virtual key phase, and if the signal is a low voltage signal after the complete stop, the rotating blade corresponding to the last pulse signal is selected as the reference blade, namely the virtual key phase.
Further, the collected pulse signals are processed, the pulse signals of the virtual key phase are determined to be used as initial pulses and data are traced back, the (n-1) pulse signals generated by the conventional blades are eliminated, and the key phase signals generated by the reference blades in each rotation of the shaft, namely the pulse signals generated by the virtual key phase, are obtained.
Further, the obtained key phase signal and the vibration signal are used as a 0-degree reference and are corresponded according to the synchronous time point, and the phase angle of the positive peak point of the synchronous component of the vibration signal relative to the vibration sensor probe is further determined, namely the phase angle theta of unbalanced vibration is determined1。
Further, the dynamic balance method for the non-trial-weight field comprises the following steps:
starting the vehicle, keeping the vehicle at a certain specific rotating speed R within the working rotating speed range, and recording the amplitude A of the highest point of vibration1And phase angle theta1。θ1The vibration phase of the same frequency of the rotor, namely the unbalance vibration phase, is measured by a measuring instrument.
Establishing a finite element model of a rotor bearing system of the rotary machine, and analyzing and judging the unbalance sensitive position of a vibration point as a balance plane according to the vibration mode and the unbalance response of the rotor;
correcting a rotor-bearing system by correcting the rigidity and the damping of a bearing in a rotor-bearing finite element model, so that the calculated critical rotating speed of the rotor finite element model has higher goodness of fit with the actual critical rotating speed of the rotor;
applying an unbalance amount with the mass of m g-mm & lt 0 DEG on a node of a corresponding balance plane of the finite element model;
the change of the vibration at the actual vibration measuring point along with the rotating speed is obtained through simulation calculation, and the corresponding vibration amplitude A of the actual vibration measuring point at the rotating speed R is obtained2And the phase angle of vibration theta2Vibration phase angle θ2Namely the lag angle;
phase of exciting forceEqual to the vibration displacement vector phase angle theta1And lag angle theta2To sum, i.e.
Counterweight phase
Phase with exciting forceOn the contrary, i.e.
Calculating the counterweight mass M according to the actual counterweight radius r of the rotor and the linear relationship of the amplitude, i.e.
And (5) stopping the vehicle, and selecting the counterweight mass according to the actual condition.
The embodiment of the invention also provides a rotary machine keyless phase and non-trial-weight dynamic balance analysis device, which comprises a rotary machine unbalance parameter acquisition device, a rotary machine unbalance parameter analysis device and an application server:
the rotating machine unbalance parameter acquisition device monitors the rotating machine in real time and acquires related signals including pulse signals, vibration signals and the like in the working process of the rotor system. And the information acquired by the rotating machinery unbalance parameter acquisition device is transmitted to the rotating machinery unbalance parameter analysis device. And the rotating machinery unbalance parameter analysis device processes the acquired information. The rotating machinery unbalance parameter analysis device is connected with the application server through a wireless network. And the information processed by the rotating machinery unbalance parameter analysis device is transmitted to the application server.
Furthermore, the rotating machinery unbalance parameter acquisition device comprises a pulse signal sensor and a vibration sensor. The pulse signal sensor is mounted on an external casing corresponding to the rotating blade. The vibration sensor is arranged at the supporting position of the rotor of the rotary machine and can be circumferentially provided with a plurality of pieces of vibration information which are measured in different directions.
The pulse signal sensor is an eddy current sensor, a capacitance sensor, a laser sensor or a microwave sensor, and is inserted into the casing to be opposite to the top end of the blade during installation. The pulse signal sensor can also be arranged on the outer surface of the casing or outside the casing when the pulse signal sensor is an eddy current sensor, and when the blade top passes through the sensor mounting position, namely the blade passes through the eddy current sensor, a pulse signal is generated.
The pulse signal sensor can also utilize the existing hole probing hole on the rotating mechanical casing, the sensor is stretched into from the hole probing hole to align the side edge of the rotating blade, the side edge of the measuring blade passes through the probe to obtain a pulse signal, and the phase of unbalanced vibration is obtained by comparing the synchronous components of the vibration signal.
Further, the rotating machine imbalance parameter analysis device comprises a signal processing module such as an oscillator, a filter and a demodulator, and a wireless transceiver, and processes the pulse signal, the vibration signal and the like and transmits the processed pulse signal, the vibration signal and the like to the application server.
Further, the application server is connected with the rotating machine unbalance parameter analysis device through a wireless network. The application server further processes and analyzes the signals processed by the rotating machine unbalance parameter analysis device, and comprises the steps of processing the pulse signals into key phase signals, determining a virtual key phase, obtaining the maximum amplitude value, the phase angle and the like of unbalance vibration, and monitoring the operating state of the rotating machine. The application server can call various data, such as various operation data of the rotary machine, and the like, and the application server can also collect various data of the rotary machine, such as basic data, use data, operation data and the like of the rotary machine, and can also modulate and control the rotary machine, and the like.
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In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present application and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained from the drawings without inventive effort.
FIG. 1 is a schematic view of a key-phase-free trial-weight-free dynamic balance analysis apparatus for a rotary machine;
FIG. 2 is a diagram of a pulse signal for measuring the rotation of a rotating blade by a pulse signal sensor;
FIG. 3 is a schematic diagram of the processing of a pulse signal;
FIG. 4 is a schematic diagram illustrating the corresponding determination of the unbalanced vibration phase according to the synchronization time point;
fig. 5 is a schematic diagram of the installation position of the pulse signal sensor.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all the embodiments. The components of the embodiments of the present application, generally described and illustrated in the figures herein, can be arranged and designed in a wide variety of different configurations. Thus, the following detailed description of the embodiments of the present application, presented in the accompanying drawings, is not intended to limit the scope of the claimed application, but is merely representative of selected embodiments of the application. All other embodiments, which can be derived by a person skilled in the art from the embodiments of the present application without making any creative effort, shall fall within the protection scope of the present application.
First, an application scenario to which the present application is applicable will be described. The application can be applied to national defense and industrial systems, monitors the vibration condition of the rotary mechanical rotor, so as to monitor the unbalance condition of the rotary mechanical rotor in advance and achieve the purpose of fault early warning. Referring to fig. 1, fig. 1 is a system diagram in the application scenario. As shown in fig. 1, the system includes a rotating machine imbalance parameter acquisition device, a rotating machine imbalance parameter analysis device, and an application server. The rotating machinery unbalance parameter acquisition device comprises a pulse signal sensor, a vibration sensor and other sensors. And the information acquired by the rotating machinery unbalance parameter acquisition device is transmitted to the rotating machinery unbalance parameter analysis device. The rotating machine unbalance parameter analysis device is connected with the application server through a wireless network, various data such as various operation data of the rotating machine can be called from the application server, the application server can collect various data of the rotating machine such as basic data, use data and operation data of the rotating machine, and the rotating machine can be modulated and controlled. In the above example, the rotating machine imbalance parameter analyzing device is connected to the application server to retrieve data from the application server, but the present invention is not limited to this, and in another example, the rotating machine imbalance parameter analyzing device may be connected to the application server, directly connected to each rotating machine, or connected to a database or the like to retrieve data of the rotating machine.
Research shows that most of the monitoring of the unbalance phenomenon of the rotor of the rotary machine is in a mode of monitoring the vibration of the position of the bearing, and a key phase value is introduced as a reference of a theoretical value. However, in an actual rotating machine set, a key phase sensor for acquiring a key phase value is difficult to install (such as an aircraft engine and the like are provided with a keyless phase sensor), and due to the influence of factors such as environment and the like, the accuracy of a monitoring result is not ideal, and additional cost is increased. The process of adding the weight by the field dynamic balance method not only needs to be repeated for many times, but also can cause multiple startup and shutdown. This causes difficulties for the normal production and continuous operation of the enterprise, and for large-scale equipment, the economic loss of each start-up and shut-down is huge, sometimes even the conditions are not allowed. To solve the above problems, a trial-weight-free dynamic balance technique has appeared. The non-trial-weight technology solves the problem of repeated trial weights in the field dynamic balance technology, does not need trial weights, and can directly calculate the balance weight according to the vibration size.
Based on the above, the embodiment of the invention provides a key-phase-free trial-weight-free dynamic balance method and an analysis device for a rotary machine, which can save the complexity of mounting a key-phase sensor in a rotor vibration monitoring system, facilitate parameter identification of the rotor unbalance phenomenon of the rotary machine, improve the monitoring accuracy, realize the completion of dynamic balance by starting a vehicle once, and reduce the cost.
The invention provides a rotating machinery dynamic balance method without key phase and trial weight, which comprises the following steps:
combining a pulse signal sensor with a vibration sensor, monitoring a rotating machine in real time, and acquiring related signals including pulse signals, vibration signals and the like in the working process of a rotor system at a certain specific rotating speed R within a working rotating speed range;
and determining a specific rotating blade on the rotating machine as a reference blade according to the acquired pulse signals, wherein the rotating blades on the rotating machine except the reference blade are conventional blades. Treating the reference leaf as a "virtual key phase";
processing the acquired pulse signals to obtain key phase signals generated by the reference blade every revolution of the shaft, namely pulse signals generated by the virtual key phase;
comparing the key phase signal with the vibration signal, and determining the phase angle of the positive peak point of the synchronous component of the vibration signal relative to the vibration sensor probe, namely the unbalanced vibration phase angle theta1；
Combined with no trialThe heavy field dynamic balance method performs dynamic balance and verifies the counterweight effect: according to the obtained maximum amplitude value A1And unbalance vibration phase angle theta1Calculating to obtain the mass M of the counterweight and the phase angle of the counterweight
The balance weight is finished when the vehicle stops;
and starting the vehicle, detecting the operation of the vehicle at a specific rotating speed R, and verifying the counterweight effect.
Further, the pulse signal sensor combines together with vibration sensor, carries out real-time supervision to the rotating machinery, and relevant signal including in the collection rotor system working process: starting the vehicle, keeping the vehicle to a certain specific rotating speed R within the working rotating speed range, acquiring pulse signals of each rotating blade through a pulse signal sensor, acquiring vibration signals of a rotor by the vibration sensor, and acquiring synchronous vibration components caused by unbalance of the rotor through the vibration signals; and stopping the machine, and keeping the acquisition of the pulse signal and the vibration signal until the rotor completely stops.
Further, the determination of the "virtual key phase" is: the pulse number of the obtained pulse signal is the same as the number n of the rotating blades when the rotor rotates for one circle, after the rotor completely stops, if the pulse signal sensor is rotating the rotating blades, the obtained signal is a continuous high-voltage signal, and if the pulse signal sensor is staggered with the rotating blades, the obtained signal is a low-voltage signal; if the signal obtained after the complete stop is a continuous high voltage signal, the rotating blade opposite to the pulse signal sensor is selected as a reference blade, namely a virtual key phase, and if the signal is a low voltage signal after the complete stop, the rotating blade corresponding to the last pulse signal is selected as the reference blade, namely the virtual key phase. The pulse signal sensors are located at different positions of the rotating blade to obtain pulse signals as shown in figure 2.
Further, the collected pulse signals are processed, the pulse signals of the virtual key phase are determined to be used as initial pulses and data are traced back, the (n-1) pulse signals generated by the conventional blades are eliminated, and the key phase signals generated by the reference blades in each rotation of the shaft, namely the pulse signals generated by the virtual key phase, are obtained. The signal processing diagram is shown in fig. 3.
Further, as shown in fig. 4, a key phase signal and a vibration signal synchronous component are obtained, the key phase signal is used as a 0 ° reference, and the correspondence is performed according to a synchronous time point, so as to determine a phase angle of a positive peak point of the vibration signal synchronous component relative to the synchronous vibration sensor probe, that is, an unbalanced vibration phase angle θ1。
Further, the dynamic balance method for the non-trial-weight field comprises the following steps:
starting the vehicle, keeping the vehicle at a certain specific rotating speed R within the working rotating speed range, and recording the amplitude A of the highest point of vibration1And phase angle theta1。θ1The vibration phase of the same frequency of the rotor, namely the unbalance vibration phase, is measured by a measuring instrument.
Establishing a finite element model of a rotor bearing system of the rotary machine, and analyzing and judging the unbalance sensitive position of a vibration point as a balance plane according to the vibration mode and the unbalance response of the rotor;
correcting a rotor-bearing system by correcting the rigidity and the damping of a bearing in a rotor-bearing finite element model, so that the calculated critical rotating speed of the rotor finite element model has higher goodness of fit with the actual critical rotating speed of the rotor;
applying an unbalance amount with the mass of m g-mm & lt 0 DEG on a node of a corresponding balance plane of the finite element model;
the change of the vibration at the actual vibration measuring point along with the rotating speed is obtained through simulation calculation, and the corresponding vibration amplitude A of the actual vibration measuring point at the rotating speed R is obtained2And the phase angle of vibration theta2Vibration phase angle θ2Namely the lag angle;
phase of exciting force
Equal to the vibration displacement vector phase angle theta1And lag angle theta2To sum, i.e.
Counterweight phase
Phase with exciting forceOn the contrary, i.e.
Calculating the counterweight mass M according to the actual counterweight radius r of the rotor and the linear relationship of the amplitude, i.e.
And (5) stopping the vehicle, and selecting the counterweight mass according to the actual condition.
The embodiment of the invention also provides a rotary machine keyless phase and non-trial-weight dynamic balance analysis device, which comprises a rotary machine unbalance parameter acquisition device, a rotary machine unbalance parameter analysis device and an application server:
the rotating machine unbalance parameter acquisition device monitors the rotating machine in real time and acquires related signals including pulse signals, vibration signals and the like in the working process of the rotor system. And the information acquired by the rotating machinery unbalance parameter acquisition device is transmitted to the rotating machinery unbalance parameter analysis device. And the rotating machinery unbalance parameter analysis device processes the acquired information. The rotating machinery unbalance parameter analysis device is connected with the application server through a wireless network. And the information processed by the rotating machinery unbalance parameter analysis device is transmitted to the application server. The overall device is shown in figure 1.
Furthermore, the rotating machinery unbalance parameter acquisition device comprises a pulse signal sensor and a vibration sensor. The pulse signal sensor is mounted on an external casing corresponding to the rotating blade. The vibration sensor is arranged at the supporting position of the rotor of the rotary machine and can be circumferentially provided with a plurality of pieces of vibration information which are measured in different directions.
The pulse signal sensor is an eddy current sensor, a capacitance sensor, a laser sensor or a microwave sensor, and is inserted into the casing to be opposite to the top end of the blade during installation. The pulse signal sensor can also be arranged on the outer surface of the casing or outside the casing when the pulse signal sensor is an eddy current sensor, and when the blade top passes through the sensor mounting position, namely the blade passes through the eddy current sensor, a pulse signal is generated.
The pulse signal sensor can also utilize the existing hole probing hole on the rotating mechanical casing, the sensor is stretched into from the hole probing hole to align the side edge of the rotating blade, the side edge of the measuring blade is subjected to probe to obtain a pulse signal, and the phase position of unbalanced vibration is obtained by comparing the vibration signal. The relative rotary vane mounting positions of the different pulse signal sensors are shown in fig. 5.
Further, the rotating machine imbalance parameter analysis device comprises a signal processing module such as an oscillator, a filter and a demodulator, and a wireless transceiver, and processes the pulse signal, the vibration signal and the like and transmits the processed pulse signal, the vibration signal and the like to the application server.
Further, the application server is connected with the rotating machine unbalance parameter analysis device through a wireless network. The application server further processes and analyzes the signals processed by the rotating machine unbalance parameter analysis device, and comprises the steps of processing the pulse signals into key phase signals, determining a virtual key phase, obtaining the maximum amplitude value, the phase angle and the like of unbalance vibration, and monitoring the operating state of the rotating machine. The application server can call various data, such as various operation data of the rotary machine, and the like, and the application server can also collect various data of the rotary machine, such as basic data, use data, operation data and the like of the rotary machine, and can also modulate and control the rotary machine, and the like.
An embodiment of the present invention further provides an electronic device, including: a processor, a memory and a bus, the memory storing machine readable instructions executable by the processor, the processor and the memory communicating over the bus when the electronic device is operating, the machine readable instructions when executed by the processor performing the steps of the rotating machine keyless phase trial and error balance analysis method as described above.
Embodiments of the present invention further provide a computer-readable storage medium, where a computer program is stored on the computer-readable storage medium, and when the computer program is executed by a processor, the steps of the keyless phase and non-trial-and-error dynamic balance analysis method for a rotating machine are performed.
In the embodiments provided in the present application, it should be understood that the apparatus and methods set forth may be implemented in other ways. The above-described apparatus embodiments are merely illustrative. The functions, if implemented in the form of software functional units and sold or used as a stand-alone product, may be stored in a non-volatile computer-readable storage medium executable by a processor. Based on such understanding, the technical solution of the present application or portions thereof that substantially contribute to the prior art may be embodied in the form of a software product stored in a storage medium and including instructions for causing a computer device (which may be a personal computer, a server, or a network device) to execute all or part of the steps of the method according to the embodiments of the present application. And the aforementioned storage medium includes: various media capable of storing program codes, such as a usb disk, a removable hard disk, a Read-Only Memory (ROM), a Random Access Memory (RAM), a magnetic disk, or an optical disk.
Finally, it should be noted that: the above-mentioned embodiments are only specific embodiments of the present application, and are used for illustrating the technical solutions of the present application, but not limiting the same, and the scope of the present application is not limited thereto, and although the present application is described in detail with reference to the foregoing embodiments, those skilled in the art should understand that: any person skilled in the art can modify or easily conceive the technical solutions described in the foregoing embodiments or equivalent substitutes for some technical features within the technical scope disclosed in the present application; such modifications, changes or substitutions do not depart from the spirit and scope of the exemplary embodiments of the present application, and are intended to be covered by the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.
Claims (10)
1. A rotary machine key phase-free trial-weight-free dynamic balance method is characterized in that a specific blade is selected as a virtual key phase without introducing a key phase, and the virtual key phase is used as a reference to carry out the trial-weight-free dynamic balance of a rotary machine rotor, and comprises the following steps:
combining a pulse signal sensor with a vibration sensor, monitoring a rotating machine in real time, and acquiring related signals including pulse signals, vibration signals and the like in the working process of a rotor system at a certain specific rotating speed R within a working rotating speed range;
and determining a specific rotating blade on the rotating machine as a reference blade according to the acquired pulse signals, wherein the rotating blades on the rotating machine except the reference blade are conventional blades. Treating the reference leaf as a "virtual key phase";
processing the acquired pulse signals to obtain key phase signals generated by the reference blade every revolution of the shaft, namely pulse signals generated by the virtual key phase;
comparing the key phase signal with the vibration signal, and determining the phase angle of the positive peak point of the synchronous component of the vibration signal relative to the vibration sensor probe, namely the unbalanced vibration phase angle theta1；
And (3) carrying out action balance and verifying the counterweight effect by combining a non-trial-weight field dynamic balance method: according to the obtained maximum amplitude value A1And unbalance vibration phase angle theta1Calculating to obtain the mass M of the counterweight and the phase angle of the counterweight
The balance weight is finished when the vehicle stops;
and starting the vehicle, detecting the operation of the vehicle at a specific rotating speed R, and verifying the counterweight effect.
2. A rotary machine keyless dynamic balancing method according to claim 1 wherein the determination of the "virtual key phase" is: the pulse number of the obtained pulse signal is the same as the number n of the rotating blades when the rotor rotates for one circle, after the rotor completely stops, if the pulse signal sensor is rotating the rotating blades, the obtained signal is a continuous high-voltage signal, and if the pulse signal sensor is staggered with the rotating blades, the obtained signal is a low-voltage signal; if the signal obtained after the complete stop is a continuous high voltage signal, the rotating blade opposite to the pulse signal sensor is selected as a reference blade, namely a virtual key phase, and if the signal is a low voltage signal after the complete stop, the rotating blade corresponding to the last pulse signal is selected as the reference blade, namely the virtual key phase.
3. The method of claim 1, wherein the key phase signal is obtained by: and processing the acquired pulse signals, determining pulse signals of a virtual key phase as initial pulses and performing data backtracking, and eliminating (n-1) pulse signals generated by the conventional blade to obtain key phase signals generated by the reference blade when the shaft rotates for one circle, namely the pulse signals generated by the virtual key phase.
4. A rotary machine keyless phase non-trial dynamic balancing method according to claim 1, wherein the acquisition of the unbalanced vibration phase: the obtained key phase signal and the vibration signal are used as a 0-degree reference and are corresponded according to the synchronous time point, and the phase angle of the positive peak point of the synchronous component of the vibration signal relative to the synchronous vibration sensor probe is further determined, namely the phase angle theta of unbalanced vibration is determined1。
5. The keyless phase non-trial dynamic balancing method for the rotary machine according to claim 1, wherein the non-trial-weight field dynamic balancing method comprises:
starting the vehicle, keeping the vehicle at a certain specific rotating speed R within the working rotating speed range, and recording vibrationAmplitude of dynamic peak A1And phase angle theta1。θ1The vibration phase of the same frequency of the rotor, namely the unbalance vibration phase, is measured by a measuring instrument.
Establishing a finite element model of a rotor bearing system of the rotary machine, and analyzing and judging the unbalance sensitive position of a vibration point as a balance plane according to the vibration mode and the unbalance response of the rotor;
correcting a rotor-bearing system by correcting the rigidity and the damping of a bearing in a rotor-bearing finite element model, so that the calculated critical rotating speed of the rotor finite element model has higher goodness of fit with the actual critical rotating speed of the rotor;
applying unbalance with the mass of mg · mm & lt 0 DEG on the node of the corresponding balance plane of the finite element model;
the change of the vibration at the actual vibration measuring point along with the rotating speed is obtained through simulation calculation, and the corresponding vibration amplitude A of the actual vibration measuring point at the rotating speed R is obtained2And the phase angle of vibration theta2Vibration phase angle θ2Namely the lag angle;
phase of exciting force
Equal to the vibration displacement vector phase angle theta1And lag angle theta2To sum, i.e.
Counterweight phase
Phase with exciting force
On the contrary, i.e.
Calculating the counterweight mass M according to the actual counterweight radius r of the rotor and the linear relationship of the amplitude, i.e.
And (5) stopping the vehicle, and selecting the counterweight mass according to the actual condition.
6. A rotary machine keyless phase and non-trial dynamic balance analysis device is characterized in that a required analysis device comprises: the system comprises a rotating machine unbalance parameter acquisition device, a rotating machine unbalance parameter analysis device and an application server;
the rotating machine unbalance parameter acquisition device monitors the rotating machine in real time and acquires related signals including pulse signals, vibration signals and the like in the working process of the rotor system. And the information acquired by the rotating machinery unbalance parameter acquisition device is transmitted to the rotating machinery unbalance parameter analysis device. And the rotating machinery unbalance parameter analysis device processes the acquired information. The rotating machinery unbalance parameter analysis device is connected with the application server through a wireless network. And the information processed by the rotating machinery unbalance parameter analysis device is transmitted to the application server.
7. The apparatus according to claim 6, wherein the apparatus for acquiring imbalance parameters of a rotating machine comprises a pulse signal sensor and a vibration sensor. The pulse signal sensor is mounted on an external casing corresponding to the rotating blade. The vibration sensor is arranged at the supporting position of the rotor of the rotary machine and can be circumferentially provided with a plurality of pieces of vibration information which are measured in different directions.
8. The apparatus according to claim 6, wherein the pulse signal sensor is an eddy current displacement sensor, a capacitance sensor, a laser sensor or a microwave sensor, and is inserted into the casing to face the blade tip;
the eddy current sensor can also be arranged on the outer surface of the casing or on the outer part of the casing, which is opposite to the blade top end. The existing hole probing hole on the casing of the rotating machine can be utilized, the sensor is extended into the hole probing hole to align with the side edge of the rotating blade, and the side edge of the measuring blade passes through the probe to obtain a pulse signal.
9. The apparatus according to claim 6, wherein the apparatus comprises a signal processing module such as an oscillator, a filter, a demodulator, and a wireless transceiver.
10. The keyless phase non-trial-and-error dynamic balance analysis device according to claim 6, wherein the application server is connected to the imbalance parameter analysis device via a wireless network, and the application server further processes and analyzes the signal processed by the imbalance parameter analysis device, processes and stores the signal. The signal processing comprises processing the pulse signals into key phase signals, determining a virtual key phase, acquiring the maximum amplitude, the phase angle and the like of the unbalanced vibration, and further realizing the monitoring of the running state of the rotating machine. The application server can call and store various data of the rotating machine, and can modulate and control the rotating machine.
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