JP2004045392A - Apparatus for measuring rotation balance of rotor and method therefor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an apparatus for measuring a balance of a rotor, which precisely measures a dynamic unbalance of a rotor, and facilitates the automation of measurement thereof. <P>SOLUTION: The apparatus for measuring the rotation balance of the rotor has a rotation sensor for detecting rotation of the rotor, an excitation means for exciting the rotor, and a vibration sensor for detecting vibration of the rotor. The excitation means excites the rotor in synchronism with the rotation of the rotor, which is detected by the rotation sensor. The excitation is applied so as to cancel the vibration corresponding to a predetermined dynamic unbalance to be left in the rotor. The vibration sensor detects composite vibration generated in the rotor by the rotation of the rotor and excitation of the excitation means. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to an apparatus and a method for measuring a dynamic imbalance of a rotating body, and more particularly, to measure a deviation of a dynamic imbalance that a rotating body actually has with respect to a predetermined dynamic imbalance that the rotating body should have. Apparatus and method.
[0002]
[Prior art]
A rotating body that rotates at a high speed during operation has a risk of generating a large vibration if it has a dynamic imbalance, and is usually designed and manufactured so as not to have a dynamic imbalance. However, some rotating bodies are required to leave a certain dynamic imbalance so that a device incorporating the rotating body does not generate vibration, noise, and the like as a whole. A typical example of such a rotating body is an engine crankshaft. The crankshaft is provided with a piston, a connecting rod and the like in the engine. For this reason, even if the rotational balance of the crankshaft alone is perfectly balanced, the entire mechanism combining the crankshaft and the piston, etc., has a dynamic imbalance and generates significant vibration during operation of the engine. Become. In order to suppress such vibration, the crankshaft is generally manufactured to have a certain dynamic imbalance that cancels out the dynamic imbalance caused by the piston or the like.
[0003]
Meanwhile, whether or not a rotating body such as the above-described crankshaft has the actually required dynamic unbalance must be confirmed by actually measuring the dynamic unbalance of the rotating body. Conventionally, there have been roughly three methods for performing such a measurement.
[0004]
The first method is a method in which a weight that cancels the required dynamic unbalance is attached to the rotating body, and in that state, the dynamic unbalance of the rotating body is measured by the rotation balance measuring device. For example, when the rotating body is a crankshaft, a weight (dummy ring) equivalent to a piston is attached to each crankpin, and dynamic imbalance of the crankshaft is measured by a rotation balance measuring device in that state. If the crankshaft has the required predetermined dynamic imbalance, the dynamic imbalance is canceled by a dummy ring attached to each crankpin and measured by a rotational balance measuring device. Dynamic imbalance is zero. On the other hand, if the crankshaft does not have the desired ideal dynamic imbalance, a dynamic imbalance corresponding to a deviation from the ideal dynamic imbalance is measured by the rotation balance measuring device. It will be.
[0005]
In the second method, instead of directly attaching the dummy ring to the rotating body, a spindle (dummy weight) that balances with a predetermined dynamic unbalance to be left on the rotating body is attached to a spindle of a rotation balance measuring device that rotationally drives the rotating body. ) Is attached, and dynamic imbalance of the rotating body is measured in this state. Also in this second method, if the rotating body does not have the desired ideal dynamic unbalance, the difference between the actual dynamic unbalance of the rotating body and the ideal dynamic unbalance is obtained. Is measured.
[0006]
In the third method, the rotating body itself is rotated without attaching a dummy ring or a dummy weight, and vibration generated at this time is detected by a vibration pickup. Next, from the output signal of the vibration pickup, the signal output from the vibration pickup is electrically removed if the rotating body has an ideal dynamic imbalance. As a result, a signal indicating a deviation between the actual dynamic unbalance of the rotating body and the ideal dynamic unbalance is obtained, and based on the signal, whether the rotating body has the appropriate dynamic unbalance It is possible to determine whether or not.
[0007]
From the measurement results obtained by the above method, the contents of the correction to be applied to the measured rotating body can be determined in order to give the measured dynamic body an ideal dynamic imbalance. For example, when the rotating body is a crankshaft, the correction is performed by forming an appropriate drill hole at an appropriate position of a counterweight provided on the crankshaft.
[0008]
[Problems to be solved by the invention]
By the way, in the first method, it is necessary to attach / detach a dummy ring for each rotating body to be measured. For this reason, it was difficult to automate the measurement. In addition, when trying to measure multiple types of rotating bodies using the same measuring device, there is another problem that a different dummy ring must be prepared for each model.
[0009]
Also in the second method, when trying to measure many types of rotating bodies with the same measuring machine, different dummy weights must be prepared for each model, and the dummy weight must be replaced every time the model changes. However, there is a problem that automation is difficult.
[0010]
The third method has an advantage that it is easy to automate the measurement because there is no need to attach and detach the dummy ring and the dummy weight. However, in the third method, the amplitude of the vibration that must be detected is large in order to detect a large vibration caused by rotating the rotating body without suppressing the vibration using a dummy ring or the like. On the other hand, since the deviation of the actual dynamic unbalance of the rotating body from the ideal dynamic unbalance is relatively small, the influence of such a deviation on the vibration is relatively small. Therefore, in order to detect the effect due to the deviation of the dynamic imbalance, it is necessary to measure the vibration with high accuracy, but it is difficult to measure a large amplitude with high accuracy. It has not always been easy to accurately measure the deviation of the actual dynamic unbalance of the rotating body from the ideal dynamic unbalance.
[Object of the invention]
In view of the circumstances described above, an object of the present invention is to provide a rotating body balance measuring apparatus and a measuring method that can accurately measure the deviation of the dynamic unbalance of the rotating body and that can easily automate the measurement. .
[0011]
[Means for Solving the Problems]
In order to achieve the above object, an apparatus for measuring the rotation balance of a rotating body according to the present invention includes a rotation sensor that detects rotation of the rotating body, a vibration unit that vibrates the rotating body, And a vibration sensor for detecting
[0012]
In the above device, the vibration unit vibrates the rotating body in synchronization with the rotation of the rotating body detected by the rotation sensor. The vibration is performed so as to cancel vibration corresponding to a predetermined dynamic imbalance to be left on the rotating body. The vibration sensor detects a combined vibration generated in the rotating body due to the rotation of the rotating body and the vibration of the vibration means. The detected synthetic vibration is a small-amplitude vibration corresponding to the deviation of the dynamic unbalance that the rotating body actually has with respect to the predetermined dynamic unbalance, that is, the initial unbalance of the rotating body. Therefore, the vibration sensor can detect the vibration corresponding to the initial imbalance with high accuracy, for example, by appropriately adjusting its dynamic range to the amplitude of the synthetic vibration. Based on the detected vibration, the initial unbalance of the rotating body can be detected. Can also be determined with high accuracy. In addition, in the above-described device, there is no need to attach or detach a so-called dummy ring or the like to / from the rotating body, so that the entire measurement can be easily automated.
[0013]
The vibration means includes a memory means for storing reference vibration information relating to a reference vibration generated by the rotation of the reference rotating body having a predetermined dynamic imbalance, and a vibration means for generating a vibration signal based on the reference vibration information. It may be configured to include a vibration signal generation unit and a vibrator such as a piezoelectric actuator that vibrates the rotating body so as to cancel the reference vibration based on the vibration signal.
[0014]
In the above case, the reference vibration information stored in the memory means is, for example, rotating the reference rotating body having a predetermined dynamic imbalance without applying vibration, detecting the rotation angle of the reference rotating body, and detecting the detected rotation angle. In synchronization with the rotation angle, the vibration generated by the rotation of the reference rotator can be detected, and the vibration can be generated based on the detected vibration.
[0015]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. 1 and 2 show a front view and a side view, respectively, of a measuring section of a crankshaft balance measuring device for measuring the balance of a crankshaft as a rotating body according to an embodiment of the present invention. In the following description, the vertical direction in FIG. 1 is defined as the Y-axis direction, and the direction perpendicular to both the vertical direction and the rotation axis direction of the crankshaft is defined as the X-axis direction.
[0016]
The device frame of the measuring unit 1 of the crankshaft balance measuring device includes a base 13, a plurality of springs 14 extending vertically upward from the base 13, and a table 15 supported by the springs 14. Drive shaft bearings 12a and 12b are attached to the lower surface of the table 15. The drive shaft 5 is rotatably supported by the drive shaft bearings 12a and 12b. As shown in FIG. 2, a first side wall 13a (left side in FIG. 2) and a second side wall 13b, which can be regarded as substantially rigid, extend vertically upward from both ends of the base 13 in the X-axis direction. I have.
[0017]
The motor 2 is attached to the base 13. A pulley 3 is attached to a drive shaft 2 a of the motor 2. On the other hand, a first pulley 6 is attached to one end of the drive shaft 5, and a first endless belt 4 is passed between the first pulley 6 and the pulley 3 attached to the drive shaft 2 a of the motor 2. By driving the motor 2, the drive shaft 5 can be rotationally driven via the first endless belt 4.
[0018]
Further, a first table side wall 17a and a second table side wall 17b which are parallel to each other vertically from the upper surface of the table 15 are fixed. The first table side wall 17a and the second table side wall 17b are rigid bodies having extremely high rigidity as compared with the spring constant of the spring 14. The driven shaft bearings 16a and 16c are fixed to the first table side wall 17a, and the driven shaft bearings 16b and 16d are fixed to the second table side wall 17b. FIG. 1 shows only the driven shaft bearings 16a and 16b, and the driven shaft bearings 16c and 16d are arranged on the inner side in FIG. 1 of the driven shaft bearings 16a and 16b, respectively. The driven shaft bearings 16a, 16b, 16c and 16d rotatably support the driven shafts 10a, 10b, 10c and 10d (only 10a and 10b are shown in FIG. 1).
[0019]
Pulleys 9a, 9b, 9c, 9d are attached to one ends of the driven shafts 10a, 10b, 10c, 10d, respectively. Further, second pulleys 7 a and 7 b are attached to a portion of one end of the drive shaft 5 adjacent to the pulley 6 and the other end of the drive shaft 5. Pulley 9a attached to second pulley 7a and driven shaft 10a and pulley 9c attached to driven shaft 10c, pulley 9b attached to second pulley 7b and driven shaft 10b, and pulley attached to driven shaft 10d. The second endless belts 8a and 8b are respectively passed to 9d. Therefore, when the drive shaft 5 rotates, its power is transmitted to the driven shafts 10a and 10c via the second endless belt 8a, and as a result, the driven shafts 10a and 10c rotate. Power from the drive shaft 5 is also transmitted to the driven shafts 10b and 10d via the second endless belt 8b, and as a result, the driven shafts 10b and 10d also rotate.
[0020]
Rollers 11a, 11b, 11c and 11d are attached to the other ends of the driven shafts 10a, 10b, 10c and 10d, respectively. One end 110a of the rotating shaft of the crankshaft 100 is mounted on the rollers 11a and 11c, and the other end 110b of the rotating shaft of the crankshaft 100 is mounted on the rollers 11b and 11d. The crankshaft 100 rotates following the rotation of the rollers 11a, 11b, 11c, 11d. That is, the crankshaft 100 can be rotated by driving the motor 2.
[0021]
A keyway 102 is formed at one end of the crankshaft 100. The measurement unit 1 of the rotation balance device further includes a sensor D for detecting the keyway 102.
[0022]
As shown in FIGS. 1 and 2, vibration pickups VDL and VDR are mounted between the first side wall 13 a of the base 13 and the table 15. Crankshaft 100 having dynamic imbalance oscillates when rotated. In the crankshaft balance measuring device of the present embodiment, the vibration of the crankshaft 100 is transmitted to the table 15 via the rollers 11a, 11b, 11c, 11d, the first and second table side walls 17a, 17b, and the like. The vibration pickups VDL and VDR detect the vibration transmitted from the rotating crankshaft 100 to the table 15. In other words, the vibration pickups VDL and VDR detect a change in load applied by the rotating crankshaft 100 to the rollers 11a, 11b, 11c, and 11d.
[0023]
The vibration pickups VDL and VDR are acceleration sensors that measure acceleration of two components (X-axis direction and Y-axis direction) perpendicular to the rotation axis of the crankshaft 100, respectively. The vibration pickup VDL is mounted on the same XY plane as the first table side wall 17a, and the vibration pickup VDR is mounted on the same XY plane as the second table side wall 17b.
[0024]
Further, between the second side wall 13b of the base 13 and the table 15, piezoelectric actuators VL and VR are attached. The piezoelectric actuator VL is mounted on the same XY plane as the first table side wall 17a, and the piezoelectric actuator VR is mounted on the same XY plane as the second table side wall 17b. The piezoelectric actuator is a member that is displaced in accordance with the magnitude of the applied voltage. Therefore, the table 15 can be vibrated freely by controlling signals input to the piezoelectric actuators VL and VR.
[0025]
FIG. 3 is a block diagram of the control unit 200 of the crankshaft balance measuring device according to the embodiment of the present invention.
[0026]
The control unit 200 includes a CPU 202, a memory 204, an input / output port (I / O port) 214, and first, second, third, and fourth D / A converters 206, 208, 210, and 212. The controller 200 further includes first and second amplifiers 216 and 218, first and second A / D converters 220 and 222, first and second digital filters 224 and 226, and a CPU data bus 228. Have.
[0027]
The first and second amplifier circuits 216 and 218 amplify the analog output signals of the vibration pickups VDR and VDL, respectively. The first and second A / D converters 220 and 222 convert analog output signals of the first and second amplifier circuits 216 and 218 into digital signals, respectively. The first and second digital filters 224 and 226 reduce the noise of the digital signals from the first and second A / D converters 220 and 222, respectively, and then send them to the CPU data bus 228.
[0028]
The CPU 202 stores the data on the CPU data bus 228 in the memory 204. Further, the CPU 202 generates an excitation signal based on the data stored in the memory 204. The generated excitation signal is sent to the left and right piezoelectric actuators VL and VR via the I / O port 214 and the first to fourth D / A converters 206, 208, 210 and 212. Thereby, the CPU 202 controls the operation of the piezoelectric actuators VL and VR, and thus controls the vibration of the table 15. Further, the CPU 202 generates a control signal for controlling the motor 2.
[0029]
Hereinafter, the operation of the crankshaft balance measuring device according to the present embodiment will be described. The crankshaft balance measuring device according to the present embodiment has two operation modes. The two operation modes are a reference vibration data sampling mode and a measurement mode. In the reference vibration data sampling mode, a measurement of a reference crankshaft having an ideal dynamic unbalance is performed, and the resulting data is stored in the memory 204. On the other hand, in the measurement mode, the deviation of the dynamic imbalance of the test crankshaft from the ideal dynamic imbalance is measured.
[0030]
In the reference vibration data sampling mode, the reference crankshaft is mounted on the rollers 11a, 11b, 11c, 11d. Next, by driving the motor 2, the rollers 11a, 11b, 11c and 11d are rotated, thereby rotating the reference crankshaft. At this time, the CPU 202 controls the motor 2 based on the pulse signal from the sensor D so that the reference crankshaft rotates at a predetermined rotation speed N (rpm).
[0031]
The rotating reference crankshaft oscillates due to its dynamic imbalance. The vibration of the reference crankshaft is transmitted to the table 15 via the rollers 11a, 11b, 11c, 11d and the first and second table side walls 17a and 17b. As a result, the table 15 vibrates. The vibration generated on the table 15 by the reference crankshaft in this manner is hereinafter referred to as “reference vibration”.
[0032]
In the reference vibration data sampling mode, the left and right piezoelectric actuators VL and VR are not driven so that the table 15 vibrates only by the vibration of the reference crankshaft.
[0033]
The reference vibration of the table 15 is detected by the vibration pickups VDL and VDR. The CPU 202 receives reference vibration data corresponding to one rotation of the reference crankshaft from the left and right vibration pickups VDR and VDL via the first and second A / D converters 220 and 222, and stores the data in a memory. 204.
[0034]
More specifically, the vibration pickup VDL located on the left side in FIG. 1 detects the acceleration of the table 15 in the X and Y directions near the first table side wall 17a, and detects the detected acceleration in the X and Y directions. And X and Y analog vibration signals WLX and WLY corresponding to. The X and Y analog vibration signals W _LX and W _LY are input to a second A / D converter 222 after passing through a second amplifier circuit 218, and are converted into X and Y digital vibration signals W ′ _LX and W ′ _LY . Is done. Next, the X and Y digital vibration signals W ′ _LX and W ′ _LY are _denoised by the digital filter 226 and sent to the CPU data bus 228. Thereby, the CPU 202 can acquire the data of the digital vibration signals W ′ _LX and W ′ _LY .
[0035]
Similarly, the vibration pickup VDR located on the right side in FIG. 1 detects the acceleration of the table 15 in the X and Y directions near the second table side wall 17b, and detects the X and Y analog vibration signals W _RX and W. _RY is sent to the first A / D converter 220 via the first amplifier circuit 216. In the first A / D converter 220, the X and Y analog vibration signals W _RX and W _RY are converted into the X and Y digital vibration signals W ′ _RX and W ′ _RY . The obtained X and Y digital vibration signals W ′ _RX and W ′ _RY are sent to the CPU data bus 228 via the digital filter 224. Thereby, the CPU 202 can acquire the data of the X and Y digital vibration signals W ′ _RX and W ′ _RY .
[0036]
The CPU 202 monitors the pulse signal generated by the sensor D and stores the data of each digital signal W ′ _LX , W ′ _LY , W ′ _RX and W ′ _{RY in} the memory 204 during a period between two consecutive pulse signals. To be stored. As a result, the CPU 202 generates four sets of digital data in the memory 204. Two sets of the four sets of digital data represent waveforms for one cycle of vibration detected in the X and Y directions by the vibration pickup VDL. Hereinafter, these two sets of data will be referred to as X and Y first reference vibration data, respectively. On the other hand, the other two sets represent waveforms of one cycle of the vibration detected in the X and Y directions by the vibration pickup VDR. Hereinafter, these two sets of data will be referred to as X and Y second reference vibration data, respectively.
[0037]
In the measurement mode, the test crankshaft whose dynamic imbalance is unknown is mounted on the rollers 11a, 11b, 11c and 11d and rotated at a predetermined rotation speed N (rpm). As a result, the test crankshaft vibrates due to its dynamic imbalance, and as a result, the table 15 also vibrates.
[0038]
The CPU 202 generates first and second vibration signals for controlling the operation of the piezoelectric actuator VL in the X and Y directions, respectively. The generated first and second excitation signals are sent to the piezoelectric actuator VL via the first and second D / A converters 206 and 208, respectively. Further, the CPU 202 generates third and fourth vibration signals for controlling the operations of the piezoelectric actuator VR in the X and Y directions, respectively. The generated third and fourth excitation signals are sent to the piezoelectric actuator VR via the third and fourth D / A converters 210 and 212, respectively.
[0039]
The first, second, third and fourth excitation signals are stored in the table 15 based on the X and Y first reference vibration data and the X and Y second reference vibration data stored in the memory 204, respectively. It is generated so as to generate a vibration opposite to the reference vibration, and is transmitted to the piezoelectric actuators VL and VR in synchronization with a pulse signal from the sensor D. That is, if the reference vibration represents a function f = (θ) (where θ represents the phase of vibration (or the rotation angle of the crankshaft)), the first, second, third, and fourth vibration signals are The piezoelectric actuators VL and VR are operated so that a vibration represented by the function f = −f (θ) is generated in the table 15.
[0040]
While the piezoelectric actuators VL and VR vibrate the table 15 as described above, the vibration pickups VDL and VDR detect the vibration of the table 15.
[0041]
If the test crankshaft has the same dynamic imbalance as the reference crankshaft, the vibrations caused by the test crankshaft will be canceled by the opposite vibrations generated by the piezoelectric actuators VL and VR. Therefore, the vibration pickups VDL and VDR do not detect any vibration from the table 15.
[0042]
If the dynamic imbalance of the test crankshaft is different from that of the reference crankshaft, the vibration generated by the test crankshaft will not be completely canceled by the piezoelectric actuators VL and VR. Accordingly, vibration corresponding to the dynamic imbalance between the test crankshaft and the reference crankshaft is generated on the table 15.
[0043]
The vibration pickups VDR and VDL detect the vibration generated on the table 15 due to the deviation of the dynamic imbalance of the test crankshaft from the dynamic imbalance of the reference crankshaft, and generate an analog signal corresponding to the detected vibration. The generated analog signal is then amplified by first and second amplifier circuits 216 and 218, and further converted into a digital signal by first and second A / D converters 220 and 222. Next, the CPU 202 stores in the memory 204 the digital data sent from the A / D converters 202 and 222 during a period between two consecutive pulse signals generated by the sensor D according to the rotation of the test crankshaft. I do.
[0044]
As described above, the data indicating the deviation of the dynamic imbalance of the test crankshaft from the dynamic imbalance of the reference crankshaft is stored in the memory 204. From the data obtained, the corrections to be made to the test crankshaft in order to match the dynamic imbalance of the test crankshaft with the dynamic imbalance of the reference crankshaft, i.e. at what position on the correction surface and how much It can be calculated whether the mass of the mass should be added or removed.
[0045]
While the crankshaft balance measuring device according to one embodiment of the present invention has been described above, the crankshaft balance measuring device can be variously modified. For example, the vibration applied to the table using the piezoelectric actuator may be generated in consideration of the rotational position (phase) of each of the test crankshafts.
[0046]
The above can be realized, for example, as follows. First, a correction plane for correcting the dynamic imbalance of the crankshaft is defined at the position of each crankpin of the reference crankshaft. Next, a vibration (hereinafter, referred to as "partial vibration") generated on the reference crankshaft due to dynamic imbalance of the reference crankshaft defined on each correction plane is obtained, and further, a waveform for one cycle of each partial vibration is expressed. A plurality of pieces of vibration information are stored in a memory. On the other hand, the crankshaft balance measuring device is provided with one crankpin sensor for each crankpin. Each crankpin sensor is provided in the crankshaft balance measuring device so as to detect the position of the corresponding crankpin. Next, an excitation signal for canceling each partial vibration is generated from each vibration information in the memory. Further, each vibration signal is sent to the piezoelectric actuator in synchronization with the output signal of the corresponding crankpin sensor. As a result, the piezoelectric actuator applies vibration to the table in consideration of the rotational direction position (phase) of each crankpin of the test crankshaft.
[0047]
【The invention's effect】
As described above, according to the present invention, the dynamic imbalance of the rotating body can be accurately measured, and the measurement can be easily automated.
[Brief description of the drawings]
FIG. 1 is a front view of a measuring unit of a crankshaft balance measuring device according to an embodiment of the present invention.
FIG. 2 is a side view of a measuring unit of the crankshaft balance measuring device according to the embodiment of the present invention.
FIG. 3 is a block diagram of a control unit of the crankshaft balance measuring device according to the embodiment of the present invention.
[Explanation of symbols]
13 Base 14 Spring 15 Table 100 Crankshaft 200 Control unit 202 CPU
206, 208, 210, 212 D / A converters 216, 218 A / D converter D Sensor VDL, VDR Vibration pickup VD, VR Piezoelectric actuator

Claims (9)

A rotation sensor for detecting rotation of the rotating body,
In synchronization with the rotation of the rotating body detected by the rotation sensor, vibration means for vibrating the rotating body so as to cancel vibration corresponding to a predetermined dynamic imbalance to be left in the rotating body,
A rotation balance measuring device for a rotating body, comprising: a vibration sensor for detecting a combined vibration generated in the rotating body by the rotation of the rotating body and the vibration of the vibration means. The vibrating means,
Memory means for storing reference vibration information relating to a reference vibration generated by rotation of the reference rotating body having the predetermined dynamic imbalance;
Excitation signal generation means for generating an excitation signal based on the reference vibration information,
A vibrator that vibrates the rotating body so as to cancel the reference vibration based on the vibration signal,
The rotational balance measuring device according to claim 1, further comprising: The rotation balance measuring device for a rotating body according to claim 2, wherein the vibrator is a piezoelectric actuator. The rotating body is rotatably mounted on a table that is installed on a base via a spring so as to be able to vibrate,
4. The rotation balance measuring device for a rotating body according to claim 2, wherein the vibrator is installed in contact with both the table and the base. 5. 5. The rotation balance measuring device for a rotating body according to claim 1, wherein the rotating body is a crankshaft. Detects the rotation of the rotating body,
In synchronization with the detected rotation of the rotating body, vibrating the rotating body to cancel vibration corresponding to a predetermined dynamic imbalance to be left in the rotating body,
A method for measuring the rotational balance of a rotating body, comprising detecting a combined vibration generated in the rotating body due to the rotation of the rotating body and the vibration. The vibration of the rotating body is
Reading the reference vibration information about the reference vibration generated by the rotation of the reference rotating body having the predetermined dynamic unbalance from the storage unit,
Based on the read reference vibration information, generate an excitation signal,
7. The method according to claim 6, wherein the method is performed by vibrating the rotating body so as to cancel the reference vibration based on the vibration signal. Rotating the reference rotating body without applying vibration,
Detecting the rotation of the reference rotator,
In synchronization with the detected rotation of the rotating body, to detect the reference vibration caused by the rotation of the reference rotating body,
Generating the reference vibration information based on the detected reference vibration,
The method according to claim 7, wherein the generated reference vibration information is stored in the storage unit. 9. The method according to claim 6, wherein the rotating body is a crankshaft.

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