JPH11311582A - Excitation power measuring device of vibrator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To accurately measure the excitation power for a vibrator based on the detection value of vibration due to a known excitation power, the characteristic value of a system, and the detection value of vibration when operating the vibrator. SOLUTION: A sample 1 is supported by a fixture 2 and vibration equipment 8 is operated, thus vibrating a system consisting of the fixture 2 and the sample 1. the frequency characteristics of vibration are detected by an impedance head 7 and are inputted to a transfer function-creating equipment 20 through an amplifier 18 and an FFT analyzer 19, thus creating a transfer function. Then, the sample 1 is rotated while it is connected to the fixture. Acceleration and vibration power in this case is detected by the head 7 and inputted to an excitation power operator 21. In this case, acceleration or vibration power according to the sample 1 is divided by the transfer function and actual excitation power that is generated due to the rotation of the sample is obtained. When the speed of the sample 1 continuously changes, the correction of the acceleration according to the characteristics of an entire vibration system including the fixture 2 is made, thus obtaining the acceleration essential to the sample 1.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for measuring an exciting force generated by a vibration generator that generates vibration by operating an internal combustion engine, a transmission, a propeller shaft, or the like, and an operating state in which the number of revolutions changes. The present invention relates to an apparatus for measuring an exciting force of a continuously changing vibration generator.

[0002]

2. Description of the Related Art A rotating device such as an internal combustion engine, a transmission, or a propeller shaft generates vibrations due to weight imbalance and a driving structure that causes the operation. Therefore, when the rotating operation is performed, for example, an exciting force acting in the radial direction or the axial direction is generated. Here, the excitation force is a load that acts on an object having an infinite mass out of the excitation force that causes vibration. As a method of measuring the excitation force, a vibration generator such as an engine, that is, a test sample is fixed to a jig such as a test bench, and the test sample is operated, and then the test sample and a predetermined fixed portion are connected. A method of electrically detecting the load by using a sensor disposed in the sensor can be adopted.

[0003] Japanese Patent Application Laid-Open No. Hei 5-87697 discloses that
A vibration test apparatus is described in which a sample such as an engine is fixed to a jig and the output is absorbed by a motor or a dynamometer. In this test apparatus, a vibration is applied to an input shaft by a vibrator in order to simulate drive shaft vibration in a high rotation range.

Further, Japanese Patent Application Laid-Open No. 7-318415 describes an excitation force estimating apparatus which aims at obtaining a strong estimation result with high stability against noise. That is, the device described in this publication is a device for performing a vibration test by a so-called impact vibration method,
While calculating based on the vibration response when the target device is vibrated with an impulse hammer, etc., the vibration response when the target device is operated is stored, and the excitation force is estimated based on these calculation results and the stored contents. It is configured to be.

[0005]

When the excitation force of the vibration generator is measured as described above, the excitation force is received by a jig, and the excitation force is applied as a stress between the specimen and the jig in that state. Will be detected. As a result, the jig vibrates under the exciting force of the test piece, and as a result, the detected excitation force includes a change in the load due to the vibration of the jig. More specifically, the detection value changes in accordance with the vibration characteristics of the jig, and the obtained detection value is the excitation force applied to the jig used for the measurement. The vibrating force applied to the jig varies depending on the operation of the sample. That is, it is impossible to obtain the actual value of the exciting force, that is, the exciting force when the jig is a completely rigid body.

[0006] This is because the jig vibrates together with the test piece. Therefore, it is conceivable to increase the weight of the jig to suppress the vibration. That is, the weight of the jig is made relatively large with respect to the weight of the specimen, and this is supported by an appropriate support including a damper, or fixed to a foundation,
It is conceivable to mount and operate the specimen on it and measure the excitation force at that time.

Further, in the usual method, the characteristics of the jig are affected. As a countermeasure, the acceleration frequency characteristics in the measurement frequency range are stabilized by extremely increasing the jig weight and lowering the jig-side resonance point. A method is also conceivable. However, in that case, the weight of the jig required is several hundred tons or more, so it is difficult to realize. Even if it can be realized, a certain level of acceleration is generated, so that the measurement accuracy of the excitation force is reduced.

The apparatus described in Japanese Patent Application Laid-Open No. Hei 5-87697 does not take such technical problems into consideration, so that it is not adopted to measure the true excitation force of the specimen. Can not. In addition, Japanese Patent Application Laid-Open No. 7-31
The device described in Japanese Patent No. 8415 discloses the use of the term “excitation force”, but since there is no process of measuring or detecting the response of vibration to an infinite mass body, the so-called excitation force Since the estimation is performed, the true excitation force generated by the test specimen (vibration generator) cannot be measured. Also, the above-described internal combustion engine and transmission, etc.
Although the rotation speed always changes during practical use, the devices described in any of the above publications are configured to measure the vibration of the specimen in a steady state, and therefore,
Vibration and excitation force in a practical state could not be measured.

After all, conventionally, the vibration of the jig cannot be avoided, and the vibration is measured while the operating state of the test piece is kept constant. Therefore, a signal corresponding to the characteristic of the jig is included. The measured value is used as a value specifying the jig, and the relative evaluation must be performed by comparing it with the existing measured value.Furthermore, the excitation force of the vibration generator whose rotation speed changes continuously is accurate. There was a disadvantage that it could not be measured.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a measuring apparatus capable of accurately measuring an exciting force of a vibration generator that generates vibration by rotation or the like. Is what you do.

[0011]

Means for Solving the Problems and Action Therefor To achieve the above object, the invention according to claim 1 supports a vibration generator by a jig and uses a vibration caused by the operation of the vibration generator. In an excitation force measuring device for a vibration generator for measuring an excitation force, a vibrator for applying vibration to the vibration generator via the jig, and a jig supporting the vibration generator are applied by the vibrator. A vibrator exciting force measuring means for measuring the exciting force of the vibrator when vibrating, and detecting the vibrating force or acceleration when the jig supporting the vibration generator is vibrated by the vibrator. Operating the vibration generator supported by the jig, changing the operating state to a predetermined operating state, and changing the operating state after reaching the predetermined operating state. Exciting force or vibration A second detecting means for detecting a maximum value of the velocity and obtaining an exciting force or an acceleration of the vibration by the vibration generator based on the detected maximum value; an exciting force exciting force measuring means and a first detecting means; And an exciting force detecting means for detecting an exciting force of the vibration generator based on a measured value or a detected value obtained by each of the second detecting means.

Therefore, according to the first aspect of the present invention, the frequency characteristics of the excitation force or the vibration acceleration of the system including the jig and the vibration generator supported by the jig when the vibration is excited by the known excitation force are detected. The transfer function of a jig or a system including the jig is obtained based on these known excitation forces and the excitation force or vibration acceleration when vibrated by the excitation force. Then, if the vibration is generated by operating the vibration generator without changing the characteristics of the system, there is a relationship represented by the transfer function between the excitation force or the acceleration of the vibration and the excitation force at that time. Then, the excitation force or the frequency characteristic of the acceleration of the vibration is detected, and the excitation force is measured based on the detected value and the transfer function. In other words, according to the first aspect of the present invention, there are three values of the detected value of the vibration when the excitation is performed by the known excitation force, the characteristic value of the system from which these are obtained, and the detected value of the vibration when the vibration generator is operated. , The excitation force of the vibration generator is determined. Further, according to the first aspect of the present invention, even when the operation state of the vibration generator continuously changes, the actual excitation is performed based on the vibration excitation force or the maximum value of the acceleration according to the specific operation state. Since the acceleration of the force or the vibration is obtained, it is possible to accurately measure the excitation force of the vibration generator while excluding the influence of the change in the operation state.

According to a second aspect of the present invention, in the first aspect of the present invention, the second detecting means detects a vibration detected when a known reference vibration is input to a jig supporting the vibration generator. A predetermined relationship between the time lag with respect to the reference vibration and the deviation of the exciting force or the acceleration of the vibration,
Means for calculating the excitation force or acceleration of the vibration by the vibration generator based on the maximum value and a delay time from when the predetermined operation state is reached to when the maximum value is detected. It is characterized by having.

Therefore, according to the second aspect of the present invention, the exciting force or the acceleration of the vibration by the vibration generator whose operation state changes continuously is detected without the influence of the continuous change of the operation state. . Therefore, similarly to the first aspect of the present invention, it is possible to accurately measure the excitation force of the vibration generator while eliminating the influence of the change in the operation state.

According to a third aspect of the present invention, the vibration generator is supported by a jig at a plurality of support points, and the vibration generated by the operation of the vibration generator is supported by the jig. In a vibration generator excitation force measuring device that detects the vibration at the point and measures the excitation force by the vibration generator based on the detected value, the vibration generator and the vibration generator are fixed at support points other than the support point for detecting the vibration. An elastic member having a low resonance frequency for suppressing propagation of vibration is disposed between the elastic member and the tool.

Therefore, according to the third aspect of the present invention, the influence of the vibration characteristics of the jig supporting the vibration generator on the test object is avoided or suppressed. It is possible to accurately detect the exciting force or the acceleration of the vibration of the generator, and thus accurately measure the excitation force of the vibration generator.

According to a fourth aspect of the present invention, there is provided an apparatus for measuring an excitation force of a vibration generator, comprising a vibrator for supporting the vibration generator by a jig and vibrating the vibration generator via the jig. A vibration propagation suppressing mechanism in which an output member of the vibrator is connected to the jig and the propagation of vibration between a main body of the vibrator and the jig supporting the vibration generator is suppressed. Is provided.

According to the fourth aspect of the present invention, the vibration generated by the vibrator is transmitted only to the vibration generator via the output member, and the vibration is transmitted to the vibration generator via the jig. Thus, it is possible to avoid or suppress vibrations from a plurality of points, or to form a coupled system of the vibration generator, the jig, and the vibrator. As a result, the exciting force or the acceleration of the vibration of the vibration generator can be accurately detected, and the excitation force of the vibration generator can be accurately measured.

According to a fifth aspect of the present invention, there is provided an apparatus for measuring an excitation force of a vibration generator, comprising a vibrator for supporting the vibration generator by a jig and vibrating the vibration generator via the jig. An output member of the vibrator is connected to the jig, and a main body of the vibrator is held in a floating state with respect to a jig supporting the vibration generator. Is what you do.

According to the invention of claim 5, also in claim 4
Similarly to the invention of the third aspect, the vibration generated by the vibrator is transmitted only to the vibration generator via the output member, and therefore, the vibration is transmitted to the vibration generator via the jig to receive the vibration from a plurality of points. It is avoided or suppressed that the vibration generator, the jig, and the vibrator form a coupled system.
As a result, the excitation force of the vibration generator or the acceleration of the vibration can be accurately detected, and the excitation force of the vibration generator can be accurately measured.

According to a sixth aspect of the present invention, there is provided a vibration generator for detecting a vibration generated by operating a vibration generator supported by a jig, and measuring an excitation force by the vibration generator based on the detected vibration. In the excitation force measuring device of the above, the vibration of the vibration generator when operating the vibration of the vibration and the cross spectrum of the acceleration of the vibration and the acceleration of the vibration, based on the power spectrum of the vibration generating the power of the vibration It is characterized in that it is provided with a means for obtaining acceleration.

Therefore, according to the invention of claim 6, it is possible to accurately detect the vibration exciting force or the vibration acceleration when the vibration generator is operated by removing the electrical or mechanical noise, and furthermore, Excitation force can be measured accurately.

According to a seventh aspect of the present invention, the vibration generator is supported by a jig at a plurality of support points, and the excitation force of the vibration generator is measured by measuring the vibration generated by the vibration of the vibration generator. In the measurement device, a vibrator that applies vibration to the vibration generator through the jig at any of the support points, and a holding mechanism that holds the vibrator in a floating state with respect to the jig, An elastic member having a low resonance frequency that suppresses propagation of vibration interposed between the vibration generator and the jig at a support point other than the support point that transmits vibration between the vibration generator and the jig, A vibrator exciting force measuring means for measuring an exciting force of the vibrator when the jig supporting the vibration generating body is vibrated by the vibrator; and a jig supporting the vibrating body. First detection to detect the excitation force or vibration acceleration when the vibration is applied by the vibrator Means for operating the vibration generator supported by the jig and changing the operation state to a predetermined operation state, and a frequency corresponding to the operation state after the predetermined operation state is reached Detecting the maximum value of the acceleration of the vibration of the vibration based on the cross spectrum of the force that causes the vibration and the acceleration of the vibration and the power spectrum of the force, and based on the detected maximum value of the vibration generator Detecting means for obtaining an exciting force or acceleration of vibration by means of vibration, and generating a vibration based on a measured value or a detected value obtained by each of the exciter exciting force measuring means, the first detecting means and the second detecting means. And an exciting force detecting means for detecting an exciting force of the body.

Therefore, according to the present invention, the influence of the vibration characteristics of the jig and the transmission of the vibration of the vibrator to the vibration generator via the jig are eliminated to reduce the vibration generator. Vibration can be performed by a vibrator, and electrical or mechanical noise can be excluded from the detected data. As a result, vibration of the vibration generator can be accurately detected. Further, similarly to the first aspect of the present invention, even when the operation state of the vibration generator continuously changes, the actual vibration force or the maximum value of the acceleration according to the specific operation state is determined based on the actual value. Since the excitation force or the acceleration of the vibration is obtained, it is possible to accurately measure the excitation force of the vibration generator while excluding the influence of a change in the operation state.

[0025]

Next, the present invention will be described more specifically with reference to the drawings. FIG. 1 schematically shows an overall configuration of a measuring apparatus according to the present invention, in which a jig 2 for supporting a specimen 1 is arranged on a surface plate 3. The specimen 1 is a rotating body that rotates in an engine, a transmission, a propeller shaft, a differential, or another use state, and a jig 2 that supports the rotating body is, for example, so as to support horizontal and vertical loads. It is arranged at an angle of 45 degrees. The jig 2 is configured to support the specimen 1 at a plurality of locations. Specifically, specimen 1
Is fixed directly to the jig 2, and the other portion is connected to the jig 2 via the vibration isolator 6.
The vibration isolator 6 is provided to prevent the vibration characteristics of the jig 2 from affecting the vibration characteristics of the specimen 1, and is equal to or lower than the frequency of the vibration to be measured (preferably, 1 / (1) of the lowest frequency to be measured). (4 or less).

An impedance head 7 is attached to a predetermined location where the test sample 1 is fixed to the jig 2, on the opposite side of the jig 2 with respect to the predetermined location. It is connected. As shown in FIG. 2, for example, the vibrator 8 arranges an armature 10 around which a coil 9 is wound at a central portion of a permanent magnet 11 and sets the armature 10 by an elastic body 12 such as a coil spring or a leaf spring. The armature 10 is arranged so as to be aligned with the axis of the impedance head 7, that is, in a state extending in a direction perpendicular to the jig 2, It is fixed to the platen 3. In other words, the vibrator 8
And the specimen 1 are arranged on the same axis with the impedance head 7 and the jig 2 interposed therebetween.

As a device for driving the vibrator 8, a signal generator 14 and a vibrator driver 15 are provided. That is, a signal of an arbitrary frequency is transmitted by the signal transmitter 14, and a driving current corresponding to the signal is applied from the vibrator driver 15 to the coil 9 of the vibrator 8, so that the vibrator 8 is transmitted to the jig 2. Exciting force is applied. The vibrator driver 15 is, for example, capable of performing constant-current vibration and adjusting the vibration input level arbitrarily. An IVR measuring device 16 is connected to the output side of the exciter driver 15 to measure and output a current value, a voltage value, and an impedance for each frequency. In FIG. 1, reference numeral 17 denotes output data schematically showing an example of the resistance value R for each frequency ω measured by the measuring device 16.

On the other hand, the impedance head 7 has an amplifier 18 for measuring the exciting force or the exciting force and the acceleration.
It is connected to the. Further, the output side of the amplifier 18 is
An FT (fast Fourier transform) analyzer 19 is connected. The FFT analyzer 19 is connected to a transfer function generator 20 via a local maximum value calculator 19A, while being connected to an excitation force calculator 21. Note that this F
The FT analyzer 19 corresponds to the first detecting means in claims 1 and 7, and the local maximum value calculator 19A corresponds to the second detecting means in claims 1 and 7.

The transfer function generator 20 is for obtaining a transfer function of the jig 2 from a known input to the jig 2 and a frequency characteristic of an acceleration or a vibrating force corresponding thereto. Or a personal computer. Here, the known input is an exciting force to the specimen 1 when the exciter 8 is operated, and is a value obtained by correcting the exciting force generated by the exciter 8 by the characteristic of the jig 2.

More specifically, first, a force generated when a substantially infinite mass body is vibrated by the vibrator 8 is obtained. This is performed, for example, by vibrating the jig 2 by the vibrator 8 and detecting the acceleration and the vibrating force by the impedance head 7 on the vibrator 8 side. Then, the excitation force at the frequency where the acceleration existing between the resonance points is almost zero is plotted on the detection data, and such an operation is performed for a plurality of zero acceleration points,
Intermediate values of the excitation force thus obtained are interpolated by an approximate curve. An example of the approximate expression is

(Equation 1) Ω0, ζ, FK4j (0)
Determine the two unknowns. Note that ω0 is the vibrator armature resonance frequency, ζ is the vibrator armature attenuation coefficient, FK4j
(0) is the zero intercept of the excitation force (force), and these are treated as unknowns in Equation 1.

The excitation force when a substantially infinite mass is excited increases as the frequency increases up to a certain frequency. Therefore, the line connecting the excitation force at the point of zero acceleration as described above is obtained. Represents the excitation force at each frequency when a substantially infinite mass is excited. The excitation force when such an infinite mass is excited is obtained for each of a plurality of excitation input levels. An example of the excitation force F thus obtained for each frequency ω is indicated by reference numeral 22 in FIG. This function corresponds to the exciter excitation force measuring means of the present invention.

Next, as shown in FIG. 1, the jig 2 supporting the specimen 1 is vibrated by the vibrator 8. This is performed, for example, by random excitation (white noise excitation). The excitation input level is set in the same manner as when the above-described substantially infinite mass is excited. The excitation force and acceleration in that case are detected by the impedance head 6 on the specimen 1 side. When the entire system is vibrated in this manner, the whole system including the jig 2 and the test specimen 1 resonates at a predetermined frequency ω, and near the resonance point, the vibrator 8 is excited by self-excited vibration of the system. A back electromotive force may be generated in the coil 9 and the current value may decrease even when the constant current control is performed. The frequency range in such a situation is a portion where the impedance of the vibrator 8 has changed from the case where there is no resonance. Therefore, the change of the current is converted into the force generated by the coil 9 in all frequency ranges, and the exciting force when the substantially infinite mass is excited as described above is corrected.

Specifically, the correction is performed by vibrating the jig 2 supporting the specimen 1 and the frequency characteristic of the current of the main circuit of the vibrator 8 when the exciting force of the vibrator 8 is obtained in advance. The frequency characteristics of the current when vibrated by the detector 8 are compared with each other at the same frequency.
Then, these ratios are multiplied by the excitation force of the vibrator 8 obtained in advance to obtain the excitation force of the vibrator 8 when the jig 2 supporting the specimen 1 is vibrated. Note that when the capacity and control ability of the exciter driver 15 are sufficiently large and control accuracy such as constant current control can be maintained even during system resonance, the above correction need not be performed.

In this manner, the actual excitation force by the vibrator 8 when the jig 2 is vibrated is obtained. In FIG. 1, a frequency characteristic line obtained by superimposing the exciting force and the exciting force is indicated by reference numeral 2.
Shown as 3.

The specimen 1 is supported by the jig 2 and the vibrator 8 is stopped as described above while the specimen 1 is stopped.
When the jig 2 is vibrated, the frequency characteristics of the acceleration and the vibrating force are obtained by the amplifier 18 and the FFT analyzer 19 as the output of the impedance head 7. Therefore, the input from the exciter 8 to the system, that is, the excitation force by the exciter 8 and the output associated therewith, that is, the frequency characteristic of the system, are known, and the transfer function is obtained from the relationship between them. Specifically, the transfer function is obtained as a ratio between the acceleration or the excitation force of the system and the excitation force by the exciter 8. This becomes a three-dimensional transfer function because it depends on the excitation input level. The transfer function generator 20 is configured to perform such an operation to obtain a transfer function. Therefore, the transfer function creator 20 constitutes a vibrator exciting force measuring unit, a frequency characteristic detecting unit, and a transfer function detecting unit in the vibration generator exciting force measuring system.

Further, the excitation force calculator 21 has the F
An FT analyzer 19 and a transfer function generator 20 are connected. From the FFT analyzer 19, when the specimen 1 is rotated while the exciter 8 is stopped,
The data detected by the impedance head 7 on the side, that is, the frequency characteristics of acceleration or excitation force are input. In this case, the number of revolutions of the specimen 1 is continuously changed within a predetermined range of the number of revolutions, and the acceleration or the exciting force is calculated to a maximum value with respect to a predetermined operating state, that is, vibration of a frequency corresponding to the number of revolutions. This is calculated by the unit 19A. The details will be described later. The excitation force acting on the jig 2 from the specimen 1 when the specimen 1 is rotated by calculating based on the frequency characteristics of the vibration acceleration or the exciting force thus determined and the transfer function described above. Is required.
The excitation force calculator 21 performs these calculations, and more specifically, divides the frequency characteristic input from the FFT analyzer 19 in the frequency band to be measured by the transfer function.

FIG. 1 shows the impedance head 7.
The typical frequency characteristics of the excitation force F obtained by the above are indicated by reference numeral 24, and the typical frequency characteristics of the excitation force F by the specimen 1 as the calculation result are indicated by reference numeral 25. Therefore, the transfer function generator 20 and the excitation force calculator 21
Corresponds to the exciting force detecting means of claim 1.

Next, the operation of the above-described device will be described. As described above, since the excitation force generated by the vibrator 8 is not related to the structure of the specimen or jig, it is measured and determined in advance using an appropriate jig or structure. Is also good. In this case, there is no problem even if the jig 2 for supporting the specimen 1 is used.
In the apparatus having the configuration shown in FIG. 7, the jig 2 is vibrated by the vibrator 8, and the frequency characteristics of the acceleration and the vibrating force in that case are obtained. Then, the excitation force at the point where the acceleration is substantially zero is connected to determine the frequency characteristic of the excitation force, that is, the excitation force F. This is shown schematically in FIG. 1 at 22.
Exciting force F when exciting a substantially infinite mass body, that is, exciting force F.

Next, the specimen 1 is supported by the jig 2. The exciter 8 is operated with the specimen 1 stopped to vibrate the jig 2 and the system composed of the specimen 1 supported thereby. In this case, the input from the vibrator 8 is, for example, random vibration (white noise vibration), and the input level is the input level when the excitation force of the vibrator 8 is measured, that is, a substantially infinite mass body. Is the same as the input level when the excitation force for exciting is measured.

The frequency characteristic of the vibration caused by the random excitation is detected by the impedance head 7, signal-processed by the amplifier 18 and the FFT analyzer 19, and input to the transfer function generator 20. In that case, the exciting force by the vibrator 8 near the resonance point is corrected, and the correction value is adopted as the actual exciting force given by the vibrator 8. Then, a transfer function is created based on the exciting force and the frequency characteristics of the acceleration or the exciting force detected by the impedance head 7. Specifically, the ratio between the acceleration or the excitation force obtained via the impedance head 7 and the actual excitation force (corrected value) of the exciter 8 is obtained.

Next, the specimen 1 is rotated (operated). In that case, the vibrator 8 is stopped and remains connected to the jig 2. This is because the vibration characteristics of the system are not changed. The specimen 1, which is not provided with a drive source such as a transmission or a propeller shaft, is driven by an engine or a motor, and absorbs a load by a dynamometer or the like.

The acceleration and the exciting force in this case are detected by the impedance head 7 on the vibrator 8 side, and are subjected to signal processing by the amplifier 18 and the FFT analyzer 19 to determine the frequency characteristics thereof. 21. Since the so-called raw data includes the vibration of the jig 2, the excitation force has a large fluctuation as shown by a reference numeral 24 in FIG. 1, for example. The excitation force calculator 21 performs calculation based on the transfer function input from the transfer function generator 20 and the frequency characteristics of the excitation force by the specimen 1 input from the FFT analyzer 19. Specifically, the excitation force by the specimen 1 is obtained by dividing the acceleration or the excitation force by the specimen 1 by the transfer function. This is the actual excitation force generated when the specimen 1 rotates.

When the specimen 1 is a vibration generator having a structure in which the number of revolutions is continuously changed, the following processing is performed. FIG. 3 conceptually shows the result of order ratio analysis of vibration acceleration A when the rotation speed of a vibration generator such as a transmission is continuously changed, and FIG.
4 conceptually shows the measurement result of the acceleration A for the vibration of Hz. As shown in these figures, the measured value (the detected acceleration) is smaller than the original value of the acceleration A (the value when the response delay of the action system and the measurement system is zero). This is considered to be due to the delay or damping effect of the vibration of the vibration system that constitutes the measuring device such as the jig 2. As shown in FIG. 4, the original value has the maximum value at the frequency QHz corresponding to the rotation speed. (S point), but the measured value is later than that,
The measured value (point K) at the time of the maximum value of the original value becomes a small value. The measured value also shows the maximum value (point P) immediately after that, but becomes smaller than the original maximum value (point S).

Then, the specimen 1 set on the jig 2 is operated, and the acceleration A is measured at a specific frequency PHz corresponding to the specific operation. For example, the primary vibration of rotation at 3000 rpm is 50 Hz, and 1800 rpm
Since the primary vibration of the rotation is 30 Hz, the acceleration A is measured for the vibration of these frequencies. When the number of revolutions of the specimen 1 is continuously changing, the acceleration is detected behind the vibration of the specimen 1 due to a response delay of the entire vibration system including the jig 2.

Then, as shown in FIG. 5, when the acceleration of the vibration at the frequency corresponding to the specific operation state (rotational speed) is measured, the original value of the actual acceleration A at the time t0 when the rotational speed reaches the maximum value is obtained. Where the detected acceleration (point K) is
The value becomes smaller than the actual value (original value: point S). Thereafter, a maximum value (point P) of the measured value appears at time t1 after a predetermined delay time Δt. Here, by observing the time change of the acceleration A after the time point t0 when the specific operation state is reached, it is possible to know the delay time Δt at the time point t1 at which the measured value becomes a maximum. The deviation ΔA between the delay time Δt and the acceleration A
Therefore, by correcting the acceleration A by the acceleration deviation ΔA based on the delay time Δt for each frequency, the order ratio analysis value shown in FIG. 6 can be obtained.

This will be described in more detail.
A simulated triangular wave vibration (indicated by a thick solid line in FIG. 7) whose frequency RHz and input level are known is input to the jig 2 on which is set. The acceleration A in that case is measured. The measured value is shown by a thin solid line in FIG. 7. As is known from FIG. 7, as the change of the acceleration A of the inputted vibration is sharper, the vibration is detected later and the detected value is smaller. Become. FIG. 8 is a diagram schematically showing the relationship between the delay time Δt at which the local maximum value appears and the deviation ΔA of the local maximum value for the vibration of the specific frequency RHz and the input level. In addition,
The correlation between the delay time Δt and the deviation ΔA of the acceleration is
As shown in FIG. 9, the relationship between the input level, the delay time Δt, and the acceleration deviation ΔA is determined for a specific frequency. A plurality of frequencies including the resonance frequency R1 Hz, R2 Hz, R3 Hz,...
About the vibration of

Therefore, as shown in FIG. 5, when the delay time Δt at which the maximum value of the measured value (point P) appears for the vibration of a specific frequency is detected, the known data shown in FIG. 8 or FIG. The deviation ΔA of the maximum value corresponding to the detected time delay Δt is determined based on the correlation between the deviation ΔA of the maximum value and the deviation ΔA of the maximum value. And the deviation Δ
By adding A to the measured maximum value (point P), the original value of acceleration A (point S) can be obtained. FIG. 6 shows the order ratio analysis value (original value: point S) and the measured value (point K) thus obtained. By performing such processing, it is possible to accurately detect the acceleration A due to the specimen 1 in which the number of revolutions changes continuously. The calculation for the delay time Δt and the deviation ΔA of the maximum value is performed by the maximum value calculator 19A.

When the number of revolutions of the specimen 1 changes continuously, the FFT analyzer 19 corrects the measured value of the acceleration A and calculates the order ratio analysis value. In the excitation force calculator 21, the frequency characteristic of the transfer function input from the transfer function generator 20 and the excitation force by the specimen 1 input from the FFT analyzer 19 (order ratio analysis value)
The calculation is performed based on Specifically, the acceleration or the exciting force by the specimen 1 is divided by the transfer function,
Excitation force (order ratio analysis data) by the specimen 1 is obtained.
This is the actual excitation force generated when the specimen 1 rotates.

Therefore, according to the above-described measuring device, the characteristics of the system that influences the measurement of the excitation force are grasped as a transfer function, and the excitation force generated with the rotation and vibration of the test sample 1 is determined. Since the calculation is performed using the transfer function, the excitation force actually generated by the rotation of the specimen 1 can be accurately measured. In particular, in the above-described apparatus or method, the excitation force generated by the vibrator 8 when a substantially infinite mass is excited is obtained from the excitation force at the point where the acceleration is zero, and this is determined by the jig. When the system composed of the specimen 2 and the specimen 1 is vibrated, correction is performed using the detected value of the vibrator current near the resonance point, so that the transfer function of the system becomes accurate, and the specimen is obtained by using the transfer function. The correct forcing by 1 can be obtained. Further, even when the operation state (for example, the number of rotations) of the test piece changes continuously, the acceleration is corrected in accordance with the characteristics of the vibration system as a whole of the measuring device including the jig 2 and the test piece is corrected. Since the original acceleration due to the operation of the device is obtained, the excitation force of the specimen having the acceleration / deceleration can be accurately measured.

In the above-described example, since the specimen 1, the impedance head 7, and the vibrator 8 are arranged on the same axis via the jig 2, the acceleration can be detected by the single impedance head 7. However, when the test piece 1 and the vibrator 8 are not arranged on the same axis, the effect of the jig 2 occurs. Therefore, an impedance head is also arranged on the test piece 1 side, and the impedance head is used by the impedance head. The vibration acceleration by the shaker is detected, and the vibration by the specimen is detected by the impedance head on the shaker side. That is, the measurement based on the reciprocity theorem is performed. In that case, it is necessary to make the specimen 1 and the jig 2 substantially connected at only one point,
Therefore, for example, it is preferable that the specimen 1 be supported by the jig 2 via a slide mechanism as shown in FIG.
That is, a saddle 5 that moves back and forth in a direction perpendicular to the jig 2 is engaged with a receiving member 4 fixed to the jig 2,
The specimen 1 is fixed to the saddle 5. Then, an impedance head 7a is arranged at the center between the saddle 5 and the receiving member 4, so that the vibration of the specimen 1 acts vertically on the impedance head 7a.

The present invention can be applied to the case where the excitation force of a device that generates vibration by operation is measured. The vibration generator to be measured is not limited to the above-mentioned rotating body. For example, the present invention can be applied to the case where the excitation force of a device that generates vibration by reciprocating motion is measured.

As described above, when measuring the excitation force or acceleration by the vibration generator, it is necessary to minimize the influence of the equipment used for the measurement. In the example shown in FIG.
For this purpose, the specimen 1 was supported by the jig 2 via the vibration isolator 6. The example shown in FIG. 11 is an example in which the air spring unit 30 is used as the vibration isolator. More specifically, the jig shown here is mainly composed of a pair of columns 32 standing upright on the surface plate 31 so as to face each other. A shaker 33 is attached downward by a bracket 34. A cantilever-shaped fixing plate 35 extending horizontally from the pedestal portion of the bracket 34 is disposed below the vibrator 33, and a distal end of an armature 36 which is an output unit of the vibrator 33 is provided. Alternatively, the tip of a connecting rod 36 integrated with the armature is connected to the upper surface of the fixed plate 35.

One mounting portion of the specimen 1 is integrally connected to the lower surface of the fixing plate 35. The connection point of the specimen 1 to the fixing plate 35 is set on the axis of the vibrator 33, that is, on the center axis of the armature or a connecting rod 36 integrated therewith. An impedance head 37 for detecting vibration is disposed at a position where the specimen 1 is fixed to the fixing plate 35. More specifically, an impedance head 37 is provided between the fixed plate 35 and the specimen 1 on the central axis of the armature or the connecting rod 36 integrated therewith.
Has been fixed.

A horizontally extending base jig 38 is integrated at a lower position of the side wall part of the other support part 32, and an air spring unit is mounted on the upper surface of the base jig 38 via a receiving metal 39. 30 is fixed. A hanging member 41 is fixed to the upper movable plate 40 of the air spring unit 30, and a support portion on the non-measurement side of the specimen 1 is attached to the hanging member 41. Therefore, the test specimen 1 is supported and suspended at two right and left locations in FIG. This is for approximating the support form of the specimen 1 shown here in practical use.

The air spring unit 30 will be described in further detail. The air spring unit 30 is an elastic member that seals air in a retractable airtight container and utilizes the compressibility of air. The height and elastic force of the movable plate 40 can be adjusted by adjusting the pressure. Further, the movable plate 40 is configured to be elastically movable in a predetermined size range not only in the vertical direction but also in the horizontal direction. The resonance point on the non-measurement side including the air spring unit 30 is set to be equal to or lower than the lower limit of the vibration measurement frequency of the test sample 1.
More preferably, the resonance frequency is set to a frequency of about １ ／ of the measurement frequency or lower.

When the excitation force by the specimen 1 is measured by the measuring device shown in FIG.
The specimen 1 is held horizontally by adjusting the height to zero.
In this state, the vibrator 33 is operated and the specimen 1 is operated to detect the vibration acceleration or the exciting force by the impedance head 37. In this case, the resonance point of the air spring unit 30 is sufficiently low with respect to the frequency of the vibration for measuring the excitation force of the specimen 1, and is low enough that the restraining force of the specimen 1 does not affect the measurement of the excitation force. That is, the excitation force of the specimen 1 can be accurately measured. In particular, when comparing the air spring unit 30 with an elastic body such as a metal spring or rubber, the air spring unit 30 has a sufficiently low resonance point, the level adjustment of the specimen 1 is easy and accurate, and the vertical direction In addition, since the prevention effect in the horizontal direction is excellent, the measurement accuracy of the excitation force is increased. Therefore, the elastic member 6 and the air spring unit 30 correspond to an elastic member of the present invention.

When measuring the vibration characteristics including the excitation force of the vibration generator, it is necessary to excite the specimen, that is, to input the vibration to the specimen so that only predetermined vibration is input. . The example shown in FIG. 12 is an example of an excitation force measuring device configured to more accurately excite a specimen. That is, the support portion 42 is erected on the surface plate 43, and the pedestal jig 44 is provided on the side surface of the support portion 42.
Are mounted in a state of extending horizontally. A T-shaped jig 45 having a T-shaped cross section is provided upright on the upper surface on the distal end side of the pedestal jig 44. The specimen 1 is fixed in a suspended state on the opposite side of the T-shaped jig 45 from the column portion 42. A vibrator 46 is connected to the T-shaped jig 45 via an impedance head 47 on a side opposite to a fixing point of the specimen 1. That is, the armature of the vibrator 46 or the distal end of the connecting rod 48 integrated therewith is connected to the T-shaped jig 45 with the impedance head 47 interposed therebetween.

On the other hand, the vibrator 46 is held in a non-contact state with respect to the support 42 and the pedestal jig 44.
This is to prevent vibrations from being transmitted from the main body of the vibrator 46 to the specimen 1 via the pedestal jig 44 and the T-shaped jig 45, so that a so-called coupled system is not formed. Has become. More specifically, the support column 49
A pulley unit 51 having a beam portion 50 extending horizontally from an upper end of the pulley unit is provided on a surface plate 43 via an air spring unit 52. The tip of the beam part 50 is
The sheaves 53 are attached to the distal end portion and the base end portion (upper end portion of the support column 49) of the beam portion 50, respectively, and the wire 54 is wound around the sheaves 53.

Hooks 55 are attached to both ends of the wire 54, and one hook 55 is hooked on the vibrator 46. A counter weight 56 is suspended from the other hook 55. The counter weight 56 is lightly fixed to the supporting column 49 so as not to swing. The weight of the counterweight 56 is substantially equal to the weight of the vibrator 46, and therefore, the vibrator 46 is suspended in a so-called floating state. Note that a damper mass 57 is attached to the vibrator 46 in order to prevent the vibrator 46 from being largely displaced when the vibrator 46 is operated. That is, the vibrator 46 is separated as a vibration system from the T-shaped jig 45, the pedestal jig 44, and the column 42 to which the test sample 1 is attached.
Although not particularly shown, the other mounting portion of the specimen 1 is supported via an elastic member having a low resonance point such as an air spring unit as shown in FIG. 11 described above.

The measurement of the excitation force of the specimen 1 by the measuring device shown in FIG. 12 is performed in the same manner as described with reference to FIG. When the vibrator 46 is operated in the course of the measurement, the vibrating force is transmitted to the specimen 1 via the T-shaped jig 45 and at the same time, transmitted from the T-shaped jig 45 to the pedestal jig 44. Is done. However, since the vibrator 46 is kept in a non-contact state with the pedestal jig 44, the vibrating force does not circulate from the T-shaped jig 45 to the vibrator 46. Therefore, the specimen 1 can be excited by the exciter 46 in a state where there is no so-called disturbance.
The vibration characteristics or the excitation force of the specimen 1 can be measured with high accuracy.

In particular, in the configuration shown in FIG. 12, a pulley unit 51 including a support column 49 and a beam portion 50 for holding the vibrator 46 in a so-called floating state is connected to a platen via an air spring unit 52. Since it is installed on the base 43, transmission of vibrations from the base 43 and the floor (not shown) on which the base 43 is placed to the support columns 49 is suppressed. Also in this respect, the disturbance factor can be removed, so that the vibration characteristics or the excitation force of the specimen 1 can be measured with high accuracy.

The example shown in FIG. 12 is an example in which the vibrator 46 is held in a non-contact state or a floating state with respect to a jig to which the specimen 1 is fixed. Although a wire and a counterweight are used to hold the vibration exciter, a vibrator may be held by using a balance method instead. That is, a vibrator is suspended at one end of a balance supported swingably at a fulcrum, and a counterweight that is in equilibrium with the vibrator is suspended at the other end of the balance. The vessel may be held in a so-called floating state. The mechanism for suspending the vibrator 46 and bringing the vibrator 46 out of contact with the jig in this way corresponds to a vibration propagation suppressing mechanism according to claim 4.

As described with reference to FIG. 1, the excitation force measuring apparatus according to the present invention vibrates the test piece on the jig by a vibrator having a known excitation force, and outputs the known excitation force (input). ) And acceleration (output) as a transfer function, and further, the excitation force of the specimen is determined from the acceleration and the transfer function by operating the specimen on the jig. Therefore, it is essential to detect the acceleration of the vibration when the exciter is operated and the acceleration of the vibration when the specimen is operated. In this case, it is necessary to remove noise (noise) to increase the measurement accuracy.
In the apparatus shown in FIG. 1 or FIG. 12, the configuration of the measuring apparatus is devised to remove noise. Instead of such an improvement in the configuration of the device, or in addition to the improvement in the configuration of the device, the signal processing method can be improved to reduce errors due to noise.

That is, the transfer function is basically a function indicating the relationship between the input and the output of the signal transmission system. However, noise is mixed in the output signal of the observable input signal and output signal. Also, the transfer function of the system can be obtained as a ratio between the input and output cross spectra and the power spectrum of the input signal at each discrete frequency. A device for detecting a signal for performing such an operation is specifically as shown in FIG. 13, and includes a connection point of the vibrator 46 to the T-shaped jig 45 and a supply to the T-shaped jig 45. Load cells 55 and 56 for detecting a load and outputting as an electric signal are interposed at each of the connection points of the specimen 1, and an acceleration sensor for detecting acceleration due to vibration in the T-type jig 45 and outputting as an electric signal. 57 are provided. Other configurations are the same as those of the apparatus shown in FIG. 12, and the same reference numerals as in FIG. 13 denote the same parts in FIG. 13, and a description thereof will be omitted.

The output signals of the load cells 55 and 56 and the acceleration sensor 57 are input to the FFT analyzer 19 via the force / acceleration measuring amplifier 18 shown in FIG. The cross spectrum of the excitation force and the acceleration at the time of excitation and the excitation power spectrum are obtained by the FFT analyzer 19. Then, a transfer function is created by the transfer function creating unit 20 as a ratio between the cross spectrum of the exciting force and the acceleration and the power spectrum of the exciting force. Further, the acceleration is calculated based on the transfer function and the excitation force spectrum obtained by the FFT analyzer 19, that is, the acceleration is calculated as a product of them. This calculation can be performed by the excitation force calculator 21 or a computer (not shown), and the cross spectrum of the excitation force and the acceleration is calculated by Wxy
(k), the power spectrum of the exciting force is Wxx (k), and the exciting force spectrum is X (k), the acceleration spectrum V (k)
Is V (k) = (Wxy (k) / Wxx (k)). X (k).

Therefore, a transfer function is obtained from the cross spectrum of the exciting force and the acceleration and the exciting power spectrum using the measuring apparatus having the configuration shown in FIG. 13, and further based on the transfer function and the exciting force spectrum. If the acceleration is detected, it is possible to obtain an acceleration from which noise has been removed. If the excitation force is calculated using the vibration acceleration as described with reference to FIG. 1, an excitation force with a small error can be obtained. That is, measurement accuracy is improved. Therefore, the excitation force calculator 21 and a computer (not shown) correspond to the means for calculating the acceleration according to claim 6.

It should be noted that the force causing the vibration is not limited to the vibrating force detected by the load cells 55 and 56 described above, and the load acting on the T-type jig 45 is employed as a force replacing the vibrating force. can do. The apparatus shown in FIG. 14 is configured to detect the load acting on the T-shaped jig 45, and the both sides of the surface of the T-shaped jig 45 on the vibrator 46 side and the surface of the specimen 1 side. Is mounted with a strain gauge 60. The specimen 1 is fixed to a T-shaped jig 45 via a predetermined metal fitting, and an acceleration sensor 61 is interposed between the vibrator 46 and the T-shaped jig 45. That is, the acceleration sensor 61 is fixed in close contact with the T-shaped jig 45, and the vibrator 46 is connected to the acceleration sensor 61.

According to the apparatus having the configuration shown in FIG. 14, when the vibration exciter 46 is operated and when the specimen 1 is operated, the stress by the strain gauge 60 is detected instead of the excitation force. . Therefore, the transfer function is obtained by dividing the cross spectrum between the output of the strain gauge 60 and the acceleration by the output power spectrum of the strain gauge 60, and the acceleration spectrum can be obtained from the value and the output spectrum of the strain gauge 60. Also in that case, an acceleration from which noise has been removed can be obtained, and as a result, the excitation force of the test sample 1 can be measured with high accuracy.

In the above description, the acceleration is detected. However, in the present invention, the excitation force may be measured in the same manner as described in the above example, in which the excitation force is detected instead of the acceleration. can do.

[0070]

As described above, according to the first aspect of the present invention, a detected value of vibration when a known excitation force is applied, a characteristic value of a system from which the detected value is obtained, and the operation of the vibration generator. The excitation force of the vibration generator is obtained based on the three detected values of the vibration at the time of the vibration, and even when the operation state of the vibration generator continuously changes, the vibration according to the specific operation state is determined. Since the actual excitation force or acceleration of vibration is calculated based on the maximum value of the excitation force or acceleration, the effect of the change in the operating state must be excluded to accurately measure the excitation force of the vibration generator. Can be.

Further, according to the second aspect of the present invention, it is possible to detect the excitation force or the acceleration of the vibration by the vibration generator whose operating state changes continuously, excluding the influence of the continuous change of the operating state. Therefore, similarly to the first aspect of the present invention, it is possible to accurately measure the excitation force of the vibration generator while eliminating the influence of a change in the operating state.

According to the third aspect of the present invention, the influence of the vibration characteristics of the jig supporting the vibration generator on the vibration generator, which is the specimen, is avoided or suppressed. It is possible to accurately detect the exciting force or the acceleration of vibration on the body, and thus accurately measure the exciting force of the vibration generator.

According to the invention of claim 4, the vibration generated by the vibrator is transmitted to only the vibration generator via the output member,
Therefore, the vibration is transmitted from the plurality of points to the vibration generator via the jig, and the vibration generator, the jig, and the vibrator are prevented from forming an coupled system. . As a result, the exciting force or the acceleration of the vibration of the vibration generator can be accurately detected, and the excitation force of the vibration generator can be accurately measured.

According to the fifth aspect of the present invention, similarly to the fourth aspect of the invention, the vibration generated by the vibrator is transmitted only to the vibration generator via its output member. Vibration is transmitted via a plurality of points to receive vibration from a plurality of points, or a vibration generator, a jig, and a vibrator constitute an coupled system. As a result, the excitation force of the vibration generator or the acceleration of the vibration can be accurately detected, and the excitation force of the vibration generator can be accurately measured.

According to the sixth aspect of the invention, it is possible to accurately detect the vibration exciting force or the vibration acceleration when the vibration generator is operated by removing the electrical or mechanical noise,
Consequently, the excitation force can be accurately measured.

According to the seventh aspect of the present invention, the influence of the vibration characteristics of the jig and the transmission of the vibration of the vibrator to the vibration generator via the jig are eliminated. Can be vibrated by the vibrator, and electrical or mechanical noise can be excluded from the detected data, and as a result, the vibration of the vibration generator can be accurately detected. Further, similarly to the first aspect of the present invention, even when the operation state of the vibration generator continuously changes, the actual vibration force or the maximum value of the acceleration according to the specific operation state is determined based on the actual value. Since the excitation force or the acceleration of the vibration is obtained, it is possible to accurately measure the excitation force of the vibration generator while excluding the influence of a change in the operation state.

[Brief description of the drawings]

FIG. 1 is a block diagram schematically showing an example of the device of the present invention.

FIG. 2 is a schematic diagram illustrating an example of the structure of a vibrator.

FIG. 3 is a schematic diagram conceptually showing a change in acceleration by order ratio analysis when the number of revolutions of the vibration generator is continuously changed.

FIG. 4 is a diagram conceptually showing a change between an original value and a measured value of acceleration for vibration of a specific frequency when the rotation speed of a vibration generator is continuously changed.

FIG. 5 is a schematic diagram for explaining a deviation and a delay time between a maximum value of an acceleration and a maximum value of a measured value thereof at a specific frequency of a vibration generator whose operating state changes.

FIG. 6 is a schematic diagram conceptually showing a value obtained by correcting a vibration acceleration by order ratio analysis when the number of revolutions of the vibration generator is continuously changed.

FIG. 7 is a diagram illustrating a measurement result of a deviation and a delay time of a maximum value between an original value and a measured value of vibration acceleration by a simulated triangular wave.

FIG. 8 is a diagram showing a measurement result of a deviation with respect to a delay time between an original value of vibration acceleration and a measured value.

FIG. 9 is a diagram illustrating an example of a three-dimensional map of a delay time and a deviation between an original value and a measured value of the vibration acceleration for each frequency, and an input level.

FIG. 10 is a schematic view showing an example of a structure of a connecting portion between a jig and a test piece.

FIG. 11 is a diagram illustrating an example of a measuring device having a configuration in which a portion other than a measuring point is supported by an air spring unit.

FIG. 12 is a diagram showing an example of a measuring device having a configuration in which a vibrator is held in a so-called floating state.

FIG. 13 is a diagram showing a part of a measuring device configured to obtain a cross spectrum of an exciting force and an acceleration.

FIG. 14 is a diagram showing a part of an apparatus configured to obtain a cross spectrum of stress and acceleration of a T-shaped jig.

[Explanation of symbols]

1 Specimen, 2 Jig, 6 Vibration-proof material, 7, 37,
47: Impedance head, 8: Exciter, 18:
Amplifier 19 FFT analyzer 20 Transfer function generator 21 Excitation force calculator 30 Air spring unit 51 Pulley unit 56 Counterweight 55 55 Load sensor 57 61
... acceleration sensor, 60 ... strain gauge.

Claims (7)

[Claims] 1. An apparatus for measuring an excitation force of a vibration generator, wherein the vibration generator is supported by a jig, and an excitation force due to vibration caused by the operation of the vibration generator is measured. A vibrator that applies vibration to the generator, a vibrator excitation force measuring unit that measures an excitation force of the vibrator when the jig supporting the vibration generator is vibrated by the vibrator, First detecting means for detecting a vibrating force or acceleration of vibration when a jig supporting a vibration generator is vibrated by the vibrator; and operating the vibration generator supported by the jig and Changing the operating state to a predetermined operating state, detecting a maximum value of an exciting force or an acceleration of a vibration having a frequency corresponding to the operating state after the predetermined operating state is reached, and Based on the detected maximum value, Detecting means for obtaining an exciting force or acceleration of vibration, and generating vibration based on a measured value or a detected value obtained by each of the exciter exciting force measuring means, the first detecting means and the second detecting means. An exciting force measuring device for a vibration generator, comprising: an exciting force detecting means for detecting an exciting force of the body. 2. The method according to claim 1, wherein the second detecting means inputs a known reference vibration to a jig supporting the vibration generator, and a time delay and vibration force of the detected vibration with respect to the reference vibration. Alternatively, the vibration generation may be performed based on a predetermined relationship with a deviation of the acceleration of the vibration, the maximum value, and a delay time from when the predetermined operation state is reached to when the maximum value is detected. 2. The apparatus according to claim 1, further comprising: means for obtaining an exciting force or vibration acceleration by a body.
An apparatus for measuring an excitation force of a vibration generator according to claim 1. 3. A vibration generator is supported by a jig at a plurality of support points, and vibration generated by the operation of the vibration generator is detected at any one of the support points supported by the jig, In an excitation force measuring device for a vibration generator that measures an excitation force by the vibration generator based on the detected value, at a support point other than the support point for detecting the vibration, An excitation force measuring device for a vibration generator, wherein an elastic member having a low resonance frequency for suppressing propagation of vibration is disposed. 4. An apparatus for measuring an excitation force of a vibration generator, comprising: a vibration generator which supports the vibration generator by a jig and which vibrates the vibration generator via the jig. Is connected to the jig, and a vibration propagation suppression mechanism is provided for suppressing propagation of vibration between the main body of the vibrator and the jig supporting the vibration generator. An apparatus for measuring the excitation force of a vibration generator. 5. An apparatus for measuring an excitation force of a vibration generator, comprising: a vibration generator that supports the vibration generator by a jig and vibrates the vibration generator through the jig. Wherein the output member of the vibration generator is connected to the jig, and the main body of the vibrator is held in a floating state with respect to a jig supporting the vibration generator. Excitation force measuring device. 6. An excitation force measuring device for a vibration generator for detecting a vibration generated by operating a vibration generator supported by a jig and measuring an excitation force by the vibration generator based on the detected vibration. In the means for obtaining the acceleration of the vibration based on the cross spectrum of the force that causes the vibration of the vibration and the acceleration of the vibration when the vibration generator is operated, and the power spectrum of the force that generates the vibration An excitation force measuring device for a vibration generator, comprising: 7. An excitation force measuring device for a vibration generator, wherein the vibration generator is supported by a jig at a plurality of support points, and an excitation force due to vibration accompanying the operation of the vibration generator is measured. A vibrator that applies vibration to the vibration generator via the jig at the support point of the vibrator, a holding mechanism that holds the vibrator in a floating state with respect to the jig, the vibration generator and the jig An elastic member having a low resonance frequency that suppresses propagation of vibration interposed between the vibration generator and the jig at a support point other than the support point that transmits vibration between the vibration generator and the vibration generator. A vibrator exciting force measuring means for measuring an exciting force of the vibrator when the jig is vibrated by the vibrator; and when the jig supporting the vibration generator is vibrated by the vibrator. First detecting means for detecting the exciting force or acceleration of Operating the vibration generator and changing the operation state to a predetermined operation state, a force and an acceleration that generate vibration at a frequency according to the operation state after reaching the predetermined operation state Detecting the maximum value of the acceleration of the vibration based on the cross spectrum and the power spectrum of the force, and obtaining the excitation force or the acceleration of the vibration by the vibration generator based on the detected maximum value. Means, and an exciting force detecting means for detecting an exciting force of the vibration generator based on a measured value or a detected value obtained by each of the exciter exciting force measuring means, the first detecting means, and the second detecting means. An excitation force measuring device for a vibration generator, comprising: