KR100324942B1 - Balancing machine for rotor and method therefor - Google Patents

Abstract

Balancing Machine (1 ') of the rotating body according to the present invention is a frame (3') for supporting the rotor (Rotor) 2 'of the object to measure the unbalance amount (vibration) for supporting the experimental table (Isolator; 30), a vertical plate (Pedestal; 4 '), each provided on the experimental table (3') at regular intervals, and a guider device (Guider) for allowing the interval movement of the vertical plate (4 ') of one side ), A driving roller 5 'installed on the vertical plate 4' on one side, and a supporting roller 6 'installed on upper and lower portions of each vertical plate, to prevent axial fluctuations of the specimen. The height of the clamper (61 '), the cover (7') holding the upper support roller (6 '), and the size of the rotor (2') are prevented from falling out of the rotor (2 '). An upper roller jig 71 for adjusting, a fixing screw 72 for fixing the roller jig 71, a drive shaft 51 for transmitting rotational force to one end of the driving roller 5 ', Coupling 52 connecting the roller 5 'and the drive shaft 51, a drive wheel 8' connected to the outer side of the drive shaft 51, and the drive wheel 9 '. Pulley (10 ') for driving through the connection with the transmission (18) provided for rotating the rotating body 2' at high speed, AC motor (11 ') for connecting to the transmission, the experimental table ( 3 '), a non-contact gap sensor (12') required to measure the amount of swing vibration (amplitude and phase) of the rotating body 2 ', and a photo sensor necessary to set the time and phase reference. 13 '), the automatic shut-off device 19 which automatically cuts off power when the vibration amount of the rotating body reaches a limit value during operation, and the AC motor 11' to control the speed of the rotating body 2 '. A speed controller 14 'for controlling and an A / D converter for converting signals detected from the gap sensor 12' and the optical sensor 13 'into digital signals. r; 15 '), a computer analyzer 16' for processing measurement data converted through an A / D converter.

In addition, in the balancing method of the rotating body to find the unbalanced mass inherent in any specimen (rotator) itself placed on the test bench, to compensate the unbalance amount to maintain the balance of the rotating body, the modification of the specimen for balancing Set three or more faces to match the measurement face with the corrected face and rotate the specimen in each measurement face. And the trial weight on each crystal plane of the specimen Whirl movement of the specimen in every measurement plane By using the measured value, the equation based on the equation of motion [ ] Is the basic formula for equivalent unbalance in each correction plane To calculate, and to compensate for the unbalanced mass of the specimen.

Description

Balancing device and method of rotating body {BALANCING MACHINE FOR ROTOR AND METHOD THEREFOR}

The present invention relates to a technique for balancing an object, in particular for balancing a rotating machine rotor.

In general, a rotating body used in various machines generates vibrations in which the rotating body shakes abnormally when it rotates due to an unbalanced mass distributed within itself from the beginning of material formation. As a result, the machine does not operate smoothly and easily breaks down.

In general, as shown in FIG. 1, the balancing apparatus 1 includes a test bench 3 for supporting a rotating body 2 to measure an unbalance amount, and a vertical plate provided at regular intervals on the test bench 3 ( 4), the driving roller (5) installed on the vertical plate (4) on one side and the support roller (6) installed on the upper and lower portions of each vertical plate, the upper support roller (to prevent jumping out of the rotating body (2) 6) having a lid (7) holding, a drive wheel (8) for transmitting rotational force to one end of the drive roller (5), and a pulley (10) for driving the drive wheel through connection with the belt (9) It consists of a motor 11.

In addition, a force sensor (12) installed on the vertical plate (4) required to measure the vertical plate transfer force generated in the rotating body (2) placed on the test table (3), the optical sensor required to set the reference of the phase 13, the speed controller 14 for controlling the AC motor 11 to control the speed of the rotating body 2, and the signals detected from the force sensor 12 and the optical sensor 13 are digital signals. A / D converter 15 for converting the data into a computer, and a computer analyzer 16 for processing the measured data converted through the A / D converter, the data being a predetermined algorithm embedded in the computer analyzer 16. It is calculated through the unbalance calculation S / W.

Here, the unbalance calculation S / W is composed of a preprocessing S / W, a solver, and a postprocessing S / W, which are convenient for the user to operate. The preprocessing S / W is an algorithm developed using A / D conversion and motor control. The input data (amplitude and phase angle at three excitation frequencies) are obtained, and the solver performs a balancing algorithm developed to find the amount of unbalance. The post-processing S / W graphically displays the vibration characteristics and Mark the location.

In order to achieve balancing of any rotor, the experimenter first turns on the computer analyzer 16 and then opens the lid 7 and the rotor 2 on the lower rollers 5 and 6 of the bench 3. Position both ends of each to close the cover (7) and lock the latch. Of course, on the contrary, the computer analyzer 16 may be turned on after fixing both ends of the rotating body 2 to the rollers 5 and 6 of the test bench 3 first. Then, the driving wheel 8 is rotated by applying a current to the motor 11 so as to rotate the driving wheel 8 connecting the pulley 10 of the motor 11. The rotating body 2 can be rotated by friction.

Accordingly, the data measured from the force sensor 12 mounted in the vertical plate 4 of the bench 3 and the light sensor 13 which sets the phase reference is placed on the computer analyzer 16 placed on the support 17. It is calculated through the built-in unbalance calculation software.

In general, balancing techniques include (a) Influence Coefficient Method (ICM), (b) Modal Balancing Method (MBM) (b), and (c) Integrated Balancing Method (UBM); Unified Blancing Method), a technique using the influence coefficient method will be described first.

(a) Impact coefficient method (ICM)

Influence coefficient method is to first determine the influence coefficients and then calculate the unbalance amount based on the measured amount of alternating random trial masses that cause unbalance. At this time, the rotation speed should be fixed as one. The coefficient of influence method is called the exact point method (EPM) because the number of unknowns and the number of equations coincide. The exact point method is proposed to impose a sensor to improve the effect of measurement error (this is called the influence coefficient method that adopts Least-Squared error method (LSM)). As it is added, the incidental cost increases.

Another reason for the low accuracy of the influence coefficient method in the case of a large number of equilibrium surfaces is that only data per frequency of one rotational speed should be used. That is, the response signal contains the vibration characteristics from the first to the higher order, but if the rotation speed is fixed to one, it is impossible to obtain the vibration amount data sufficiently representing the higher order vibration characteristics.

In summary, the influence coefficient method is sensitive to measurement error because the measured vibration amount cannot be effectively used because the rotational speed must be fixed to one, and the number of unknowns and the number of equations are equal. In particular, as the number of equilibrium surfaces increases, it is very difficult to obtain reliable results because of the effects of measurement errors.

In the basic formula ,

Based on the assumption that the correlation between the unbalance and the vibration is linear,

here,

Influence Coefficient Matrix Is an asymmetric complex matrix that changes with rotational speed.

The unknown coefficient of influence matrix to be identified is 2n ² .

; The amount of vibration defined by magnitude and phase, expressed as a complex number. The amount of vibration is measured using n sensors.

; The distributed unbalance of the specimen equals the concentrated unbalance of the crystal plane, expressed as a complex number of magnitude and phase. The unknown number of unbalances is 2n.

In the balancing procedure ,

Step 1 selects the number of measuring planes and crystal planes of the specimen (object to be balanced) and assigns serial numbers to each of n.

Step 2 measures the whirl motion of the measurement surface after fixing the rotational speed, leaving the specimen 'as is'. Whirlwind motion is defined by amplitude and phase.

Step 3 measures the bending motion of each measurement plane by moving the trial mass from crystal plane # 1 to crystal plane #n in turn.

Step 4 calculates the unbalance for the modified plane using the coefficient of influence basic formula based on the values measured in steps 2 and 3.

Step 5 weighs the compensating weight offset from the calculated unbalance (magnitude and phase).

The coefficient of influence method is the most widely used formula because it is a basic formula based solely on the fact that the amount of vibration and the source of vibration are proportional to each other. Therefore, there is an advantage that can be easily applied to non-experts. Instead, firstly, an unknown number to be identified is set too much, making it sensitive to measurement errors, and secondly, since it does not reflect the principles of mechanics, it is impossible to use all the information of the rotor dynamics analysis.

(b) Mode Equilibrium (MBM)

Mode balancing is a technique of balancing based on the fact that the response characteristic is driven by the mode characteristic near the resonance of a specific mode. Mode balancing is based on the rotor dynamics model because it is a technique using vibration characteristics. Therefore, the mode balancing method is more effective than the coefficient of influence method for the flexible rotor which performs the balancing of more than three surfaces. However, it is not suitable for non-expert use because the vibration mode characteristics must be known in advance before balancing. In addition, there is a possibility that a problem caused by excessive vibration is caused because the driving near the dangerous speed.

Mode balancing is developed based on the fact that the unbalance response is governed by the vibration characteristics of the mode near the critical velocity. Since the vibration rapidly increases at the dangerous speed, the magnitude of the dangerous velocity is determined while observing the magnitude of the vibration during operation, and then the vibration mode is measured at the velocity. At this time, since the vibration characteristics of the rotating body are mainly shown, an unbalance amount is calculated using a mechanical relationship. Mode balancing is a technique that is mainly used for balancing a generator turbine or a machine tool spindle because the mode balancing is performed based on the principle of mechanics, so that even a relatively high order mode can be effectively performed.

However, mode balancing has the following fundamental problems.

1) Problem that occurs when the rotational speed matches the dangerous speed

① It is difficult to accurately measure the phase because the phase change is drastically in the danger velocity area.

Near the dangerous speed, the phase changes rapidly. Therefore, when the vibration amount is measured near the dangerous speed, the measurement error affects the phase sensitively.

② Due to severe vibration, there are many difficulties in working.

-The load of the roller support is very large, which can cause many problems in operation.

-If the limit of vibration amount is reached before the dangerous speed is reached, the accuracy is reduced because the balance must be balanced at the rotational speed which is contrary to the basic assumption of the mode balancing method.

2) Problems with Compensation Weight Installation

When balancing the k + 1th mode, the compensation weight must be calculated so as not to re-exit the kth mode. In order to meet these conditions, it is practically cumbersome and expensive to weigh the compensation weight accurately calculated in each mode.

In the basic formula ,

The relationship between vibration and unbalance is obtained using the inherent characteristics defined by the system's mode vector and eigenvalues.

here,

s; Number of vibration modes

Ω; Rotation speed

; mod vector of the i th mode

; adjoint modal vector of the i th mode

λ _i ; eigen value of the i th mode

If the rotational speed is close to the dangerous speed of the k-th mode, that is, Ω≡Im (λ _k ), equation (A-2) is approximately

Becomes The ultimate goal of balancing is to reduce the amount of vibration To satisfy Is reduced to the problem of finding.

To calculate the compensation weight to eliminate the kth mode, the amount of vibration at the dangerous velocity of the kth mode The mode vector of the and kth modes ( ) And the accompanying mode vector ( ) Should be measured.

In the balancing procedure ,

Step 1 defines the equilibrium rotation speed range.

Step 2 identifies the response characteristics while operating from the 'as is' state to the speed range.

Step 3 measures the most severe vibration at the first critical velocity and performs cross-sectional equilibrium.

Step 4 speeds up to the second dangerous speed and repeats the same process as step 3 at that speed.

Step 5 performs balancing in the dangerous speed region continuously up to the speed range.

In the balancing step in each mode, if the vibration is severe enough that the dangerous speed cannot be reached, the section balancing is performed at the rotational speed reaching the upper limit of vibration and repeated.

(c) Integrated Equilibrium (UBM)

Integrated balancing is a technique that integrates the shortcomings of the influence coefficient method and the mode balancing method. While influence coefficients have technical limitations that are sensitive to measurement errors, mode balancing is cumbersome in that vibration mode characteristics must be known in advance. The integrated equilibrium grading method is based on the mode equilibrium grading method using the vibration mode characteristics and obtains the mode influence coefficient for each mode by using the trial mass. However, because the method itself does not start from a new concept but is a mixture of the two methods, it does not show a big difference.

The integrated balancing method does not need to know the vibration mode in advance and is based on a mathematical model, so it is more convenient to use than the mode balancing method and more accurate than the influence coefficient method. Since the number of driving due to the trial mass increases, the cost is less economical than the mode balancing method.

Problems of the prior art,

In driving frequency by trial mass,

In the coefficient of influence method, for n-side equilibrium, 2n ² unknowns are always set in the coefficient of influence. Since the number of equations in the basic formula is 2n, except for the state as it is, when n trial masses are attached, the number of equations becomes 2n ^2, which is equal to the number of unknowns. Therefore, the minimum number of driving including the operation of the state as is is n + 1 times.

The mode balancing method is a method of sequentially performing balancing for each vibration mode starting from the first dangerous velocity. In this case, single plane balancing is performed at a dangerous speed, and two operations (as-is and one attempted mass attempt) are required to perform cross-balance. Therefore, the minimum driving frequency required for balancing up to the nth order mode is 2n.

The conventional technique is uneconomical because the number of attempts to balance is larger as the number of equilibrium planes increases.

In systematic errors ,

Since the influence coefficient method considers only general linear relations, structural error is a general model without structural errors other than modeling error due to linearization of nonlinear characteristics. There is a model error because the mode equilibrium method is based on a rotor dynamic mathematical model. There is also a truncation analysis because an approximate method is applied in the process of using Modal Analysis.

In installing calibration weights ,

Once the unbalance is identified, a compensating weight that eliminates it must be weighed. Influence counting measures the weight of compensation once after every measurement and analysis. The mode balancing method requires the correction mass to be applied each time vibration mode balancing is performed, which is very cumbersome.

An object of the present invention is to provide a method for calculating an unbalance amount and compensating for an unbalance amount by using a balance catching device and a rotating body dynamics that are economical and resistant to measurement errors, and which can effectively carry out high level mode balancing. .

1 is a schematic front view showing a conventional balancing device.

2 is a schematic front view showing a balancing apparatus of the present invention;

3 is a schematic diagram showing a rotating body (test piece) of a test object.

4 is a graph showing a system response curve of a rotating body.

5A is a scatter diagram showing an unbalance amount due to a measurement error by a conventional influence coefficient method.

5B is a scatter diagram showing the amount of unbalance due to measurement error by the method of the present invention.

6 is a graph showing the standard deviation of the unbalance amount according to the sampling operation speed by the conventional influence coefficient method and the method of the present invention, respectively.

<Description of the symbols for the main parts of the drawings>

1 ': balancing device 2': rotating body

3 ': Experiment Table 4': Vertical Plate

5 ': drive roller 6': support roller

7 ': cover 8': drive wheel

9 ': Belt 10': Pulley

11 ': AC motor 12': gap sensor

13 ': optical sensor 14': speed controller

15 ': A / D Converter 16': Computer Analyzer

18: Transmission 19: Automatic Shut Off

31: guider 51: drive shaft

52: coupling 71: upper roller jig

72: fixing screw 61: clamper

As shown in FIG. 2, when any specimen (rotator) placed on a frame 1 'is rotated, the amount of bending vibration (amplitude and phase) of the specimen is measured at various angles at three or more desired positions. Unbalancing mass detecting means,

And a computer analysis means incorporating an analysis algorithm (algorithm) capable of compensating for an unbalanced amount of the specimen in three or more planes from values measured at multiple angles through the unbalance amount detection means.

More specifically, the balancing machine (Balancing Machine) 1 'of the present invention is a frame (3') for supporting the rotor (Rotor) 2 'of the object to measure the unbalance amount (vibration) for supporting the test bench (Isolator; 30), a vertical plate (Pedestal; 4 '), each provided on the experimental table (3') at regular intervals, and a guider device (Guider) to enable the interval movement of the vertical plate (4 ') of one side ), A driving roller 5 'installed on the vertical plate 4' on one side, and a supporting roller 6 'installed on upper and lower portions of each vertical plate, to prevent axial fluctuations of the specimen. The height of the clamper (61 '), the cover (7') holding the upper support roller (6 '), and the size of the rotor (2') are prevented from falling out of the rotor (2 '). An upper roller jig 71 for adjusting, a fixing screw 72 for fixing the roller jig 71, a drive shaft 6 'for transmitting rotational force to one end of the driving roller 5', a sphere Coupling 52 connecting the roller 5 'and the drive shaft 51, a drive wheel 8' connected to the outer side of the drive shaft 51, and the drive wheel 9 '. And a pulley (10 ') for driving through a connection, a transmission (18) provided for rotating the rotating body (2') at high speed, and an AC motor (11 ') for connecting with the transmission.

In addition, as the unbalance amount detecting means, a non-contact gap sensor (12 '), time and phase required to measure the amount of swing vibration (amplitude and phase) of the rotating body 2' placed on the bench 3 '. Photo sensor (13 ') necessary to set the standard, the automatic shut-off device 19 and the speed of the rotating body 2' to automatically cut off the power when the vibration amount of the rotating body reaches the limit value during operation A speed controller 14 'for controlling the AC motor 11' for controlling, and an A / D converter for converting signals detected from the gap sensor 12 'and the optical sensor 13' into digital signals ( 15 '), a computer analyzer 16' which processes measured data converted through an A / D converter, and based on the data, a mathematical model of a rotating body dynamic system built into the computer analyzer 16 '. Unbalance calculation S / W consisting of algorithms based on By an unbalance (amplitude and phase) of the rotor (2 ') is calculated.

Operation of the rotating body balancing device of the present invention is performed as follows.

In order to achieve balancing of a certain rotor, the experimenter first turns on the computer analyzer 16 'and then guides the vertical plate 4' on one side of the bench 3 'appropriately to the length of the rotor. Fix the interval through (30). Then, open the cover 7 and place both ends of the rotor 2 'on the lower rollers 5' and 6 'fixed to the vertical plate 4' to close the cover 7 'and close the latch. Lock and secure. Then, the upper support roller 6 'is pushed through the upper roller jig 71 so that the rotating body 2' can be pressed from above and stabilized, and then fixed with the fixing screw 72. The clamper 61 is positioned at the end of the rotating body 2 'so as not to swing in the axial direction during operation. Then, the gap sensor 12 'of the unbalance detection means is brought close to the rotor 2' and fixed with a magnetic fastener. The reflective tape is attached to one side of the rotating shaft and the optical sensor 13 'is positioned perpendicular to the point. Subsequently, after adjusting the transmission 18 to determine the maximum driving speed, a current is applied to the motor 11 'to rotate the drive wheel 8' connected to the pulley 10 'of the motor 11'. By rotating the drive roller 5 'through the drive shaft 51 and the coupling 62, the rotor 2' can be rotated by friction.

Accordingly, the data measured from the gap sensor 12 'installed near the rotor 2' of the bench 3 'and the pulse data measured from the optical sensor 13' are transferred to the A / D converter 15 '. Is sent to the computer analyzer 16 '. In the computer analyzer 16 ', the vibration amount is calculated by the built-in data processing device, and the unbalance amount (magnitude and phase) inherent in the rotating body 2' through the built-in unbalanced S / W based on the calculated vibration amount. This is calculated.

At this time, the automatic shut-off device 19 for automatically turning off the AC motor 11 'when the rotating body 2' suddenly turns on the vibration and collides with the gap sensor is activated.

Further, in the feature of the balancing method of the present invention,

1) A method of simultaneously using measurement data of several rotational speeds,

-It has higher precision than the influence coefficient method and the mode balancing method.

2) a balancing method based on a mathematical model,

-Rotor dynamics analysis and measurement information are used for balancing.

3) It is possible to implement a simple method of work that reduces the number of trial masses.

In derivation of the equilibrium basic formula based on a mathematical model,

Assume that the rotation system is an isotropic rotor dynamic system.

The foundation is assumed to be a rigid body.

Where M, B, C, and K are mass, gyro, attenuation, and stiffness matrices, respectively. Is the whirl movement of the measuring point, Is a runout (wound motion when the rotating body is slowly rotated).

The unbalanced response is

Runout,

Substituting (2), (3) into (1),

M ₀ = M + B (4 ')

In the balancing method of the present invention,

The unknowns are the components of the K, M ₀ and C matrices and the concentration unbalance Are real and imaginary components.

-Based on Equation (4), attach a trial mass to a specific position of the specimen, measure the vibration amount each time, and identify the unknown.

Mass On the test specimen and measured at the rotational speed Ω _S about,

r = 0,1,2, ... R, s = 1,2, ..., S.,

Unknown If you sum up the equation (5),

; K, C, M ₀ and Real unknown vector of unknown components.

Real matrix defined by.

And a real vector defined by Ω _S , s = 1,2, ... S.

M; Number of equations

N; Number of unknowns

Using the least-squares method, Eq. (6) is calculated as

The balancing procedure of the present invention is as follows.

Step a displays the serial number by setting the number of measurement surfaces of the specimen to n, preferably three or more. The crystal plane coincides with the measurement plane.

Step b puts the specimen on the balancing machine, run out With respect to and S sampling rotational speeds Ω _S , rotate the specimen as it is, `` whirl motion '' in each measurement plane. Measure

Step c is the trial weight on crystal plane # 1 of the specimen And whirling as in step b Measure

Step d repeats step c each time transferring the trial mass from crystal plane # 1 to crystal plane #R (R <n).

Step e is equivalent equilibrium amount in the correction plane using the basic formula (Equation 8) of the present invention based on the values measured in the entire process of steps b to d To calculate.

Step f is the compensating imbalance that offsets the calculated unbalance Hangs

In comparison with the prior art

(1) Influence on dispersion error

For the influence coefficient method and the method of the present invention, the dispersion of the result due to the dispersion error of the measurement is compared by simulation (see FIGS. 5A and 5B).

1. Subjects of simulation

-Rotor-flexible shaft system for rigid bearing support

-Balance both sides

2. Dispersion Error of Measurement

-After the response was calculated by the finite element method, the vibration amount was imposed on the vibration amount calculated by random generation in consideration of the gap sensor, resolution, and straightness.

-The resolution of the gap sensor is 1 μm, the linearity is 0.5% up to 0.16mm, and 3.0% over 0,16mm.

3. Variance of Equilibrium Results for Variance Errors

-As a result of identifying the unbalance amount with the vibration amount obtained by the simulation, the dispersion degree as shown in FIGS. 5A and 5B is shown.

It can be seen that the standard deviation depends on the sampling rotation speed (see FIG. 6).

Rotational speed showed that the method of the present invention had a smaller standard deviation than the coefficient of influence method over the entire period (see FIG. 6).

Conventional devices use the influence coefficient method as the basic algorithm, so the sampling rate must be fixed to one. However, the apparatus of the present invention can measure vibration amounts for several speeds and use them both for balancing.

Therefore, the technique of the present invention is less affected by the measurement error than the conventional technique. In particular, since the rotation speed can be appropriately selected to a wide range in three or more plane balancing, the accuracy of the balancing can be improved.

(2) Type of sensor

Conventional devices use force sensors, but the devices of the present invention use gap sensors.

(3) Free choice of sensor position

The device of the present invention can measure by moving the sensor to the desired location of the specimen. In other words, it is possible to select a position advantageous for the measurement.

(4) the number of equilibrium faces

In the conventional apparatus using the force sensor, the sensor can be installed only at two bearing supports, so that it is impossible to equilibrate more than three surfaces. Since the apparatus of the present invention can install the desired number of sensors at a desired position, it is possible to equilibrate more than three surfaces with a simple apparatus.

(5) cost reduction

The more the trial mass is recovered, the more accurate the measurement result is. However, there is a cost problem, so it is necessary to equilibrate as few times as possible within the range of desired precision. Since the conventional apparatus is based on the influence coefficient method, the number of attempted masses must be at least as large as the number of equilibrium planes, apart from the expense.

The apparatus of the present invention may only recover the trial weight once if it falls within the range of desired precision. If the precision is not very high and you have to balance large quantities, you can save time and money by reducing the number of trial weights.

Comparison of Conventional Techniques and Techniques of the Invention Method Item Conventional method Method of the invention Usefulness and Effects of the Methods of the Invention Impact on measurement error Sensitive to Measurement Errors Robust to measurement error LSM can be used to compensate for measurement errors Multiple sampling rates can be used to obtain measurement data advantageous for higher-order mode balancing Sensor location Fixed to the support (two places) The user can freely select the position that is advantageous for the measurement It is advantageous to increase the precision because the accuracy of the measurement is improved by the position that is advantageous for the measurement. Equilibrium Surface Count Balance Both Sides Can equilibrate more than three sides Vibration displacement measurement method can increase the number of measuring points by 3 or more. Equilibrium can be balanced from a flexible body such as a machine tool spindle. Cost reduction The number of trial weights should be greater than or equal to the number of equilibrium faces Equilibrium can be achieved even with the number of trial weights below the number of planes Rapid parallelization of large quantities of products can simplify the process and reduce costs.

The method of the present invention is resistant to measurement errors because several rotational speeds can be arbitrarily selected throughout the operation of the work. .

The method of the present invention is not limited to maintaining the driving frequency more than a certain amount as in the case of the influence coefficient method or the mode balancing method. The method of the present invention may increase the number of driving to increase the number of equations, but there is also a method of matching the number of equations by increasing only the number of rotational speeds to be sampled in one operation.

It is a given that the accuracy is of course improved by balancing the trial mass several times. However, in consideration of economic aspects, there are many cases where it is necessary to reduce the number of operations within a range that satisfies a certain degree of precision. It is very advantageous from an economic point of view that the method of the present invention can freely control the recovery of attempted mass.

Since the method of the present invention starts from the equation of motion, there is a model error of the same degree as the mode equilibrium method. However, there is no cutting error.

As a result, the method of the present invention is an innovative technique having superiority in terms of economy, degree, or convenience compared to the existing commercially available influence coefficient method and mode balancing method.

Claims (5)

In the equilibrium device of the rotating body to find the unbalanced mass inherent in any specimen (rotator) itself placed on the bench, to compensate the unbalance amount to maintain the balance of the rotor, Unbalance amount sensing means for measuring the amount of oscillation vibration (amplitude and phase) of the test piece at various angles at three or more desired positions when the test piece (rotator) rotates; And a computer analysis means incorporating an analysis algorithm capable of compensating for an unbalance amount of the specimen in three or more correction surfaces from values measured at multiple angles through the unbalance amount detection means. 2. The apparatus of claim 1, wherein the sensing means comprises a gap sensor for measuring the amount of vibration of the rotating body placed on the bench. 3. The balancing device of claim 1 or 2, further comprising an automatic shut-off device which automatically shuts off power when the vibration amount of the rotating body reaches a limit value during operation. The apparatus of claim 1 or 2, further comprising a speed controller for controlling an AC motor to control the speed of the rotating body. In the method of balancing the rotating body to find the unbalanced mass inherent in any specimen (rotator) itself placed on the experiment table, to compensate the unbalance amount to maintain the balance of the rotor, By setting the crystal plane of the specimen to the number of three or more, to match the measurement plane with the crystal plane, the rotational movement of the specimen in each measurement plane And the trial weight at each crystal plane of the specimen Whirl movement of the specimen in every measurement plane By using the measured value, the equation based on the equation of motion [ ] Is the basic formula for equivalent unbalance in each correction plane Calculating and compensating for the unbalanced mass of the specimen.