JPH07119661B2 - Unbalance correction method and its apparatus in rotating body apparatus - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to an unbalance correction method and a device thereof in a rotary device. Here, the rotating body device means a device including a rotating body in which unbalance is a problem.

(Prior Art) Since an apparatus equipped with a rotating body such as a rotary grinding wheel cannot perform accurate machining if the rotating body has an imbalance, various means for eliminating the unbalance of the rotating body in an operating state compared to the conventional art. One of them is to attach a plurality of correction weights to a rotating body so as to be movable and fixed around a rotation center axis.

When correcting the imbalance of the rotating body in such a device,
First, temporarily fix the correction weight to an appropriate position of the rotating body, judge the static balance if it does not rotate unbalanced by rotating the rotating body by hand in that state, then rotate it in normal use By repeating the process of checking the dynamic balance, the unbalance of the rotating body was finally kept within a certain allowable range.

(Problems to be Solved by the Invention) In the above-mentioned one, since the operator determines the position of the counterweight by repeated trials depending on the feeling, it takes a lot of time and effort (in some cases, several hours) to correct the imbalance. However, it is almost impossible for even an expert to make highly accurate imbalance correction.

The present invention has been made in view of the above problems, and provides an unbalance correction method and a device thereof in a rotating device capable of easily and quickly performing unbalance correction of a rotating body without requiring skill. The purpose is to provide.

(Means for Solving the Problems) In the unbalance correction method in the rotating body device according to the present invention, a plurality of counterweights provided so as to be movable and fixed around a fixed radius with respect to the rotating body are provided at arbitrary fixed positions. The unbalance vector of the entire rotating body is measured while the same rotating body is rotated at a predetermined speed, and then at least one of the weights is fixed to any other fixed position of the rotating body. In this case, the unbalanced vector of the entire rotator is measured again while the rotator is rotated in the same manner, while each centrifugal force vector to be generated by a plurality of counterweights in each state is set to an arbitrary value. Numerical values proportional to the weight or mass of each counterweight, each simulated composite vector scaled at a fixed ratio is calculated based on the revolution speed, and then the displacement vector and the displacement vector obtained as the difference between the unbalanced vectors in each state. The rate of change, which is the ratio to the simulated displacement vector obtained as the difference between the simulated composite vectors in each state, was calculated, and thus, there was no balance weight from the information of the unbalance vector, the simulated composite vector and the rate of change described above. It is characterized in that a unique unbalance vector of the rotating body is calculated, and a fixed position of each counterweight for eliminating the unique unbalance vector is calculated as an angle around the rotation center axis.

Then, the unbalance correction device in the rotating body device includes a plurality of counterweights that are movable and fixed around the center of rotation with respect to the rotor and an angle scale for determining the fixed angle of these counterweights. On the other hand, the phase signal obtained from the detector for detecting the rotational phase of the rotating body and the vibration waveform signal obtained from the detector for detecting the vibration of the rotating body are directly input to the micro. Attach a computer,
Further, the microcomputer corrects the imbalance of the rotating body by each signal information detected by each of the detectors, the fixed angle information of the counterweight input from the operation keys of the computer control device, and the previously input material. It is characterized in that the angle information of the counterweight is output.

(Operation) The operator temporarily fixes the counterweight at an arbitrary position around the center axis of the rotating body, reads the fixed angle of each counterweight, and then rotates the rotor in the same manner as in the use state. Operate the computer so that the vibration state of the rotating body at is directly input to the computer. As a result, information about the unbalance vector of the entire rotating body in this state can be obtained.

After this, once stop the rotating body, temporarily fix the counterweight to a different position, read the fixed angle of each counterweight as described above, and then rotate the rotor again in the same manner as in use. Operate the computer so that the vibration status of the rotating body is directly input to the computer. As a result, information about the unbalance vector of the entire rotating body in this state can be obtained.

About the fixed angle information of each weight and the vibration information of the rotating body (that is, information about the unbalance vector of the entire rotating body) obtained as described above, and the revolution radius, weight or weight ratio (or mass etc.) of each weight It is operated so as to output the fixed angle information of each counterweight for eliminating the imbalance from the material information of (1) to the computer.

Then, the operator fixes each counterweight at a predetermined position in accordance with the fixed angle information output from the computer to eliminate the unbalance vector of the rotating body.

If each counterweight is two and the revolution radius and weight are the same, handling and processing will be simplified.

Further, in order to correct the imbalance with higher accuracy, the procedure equivalent to the above is repeated several times, whereby the magnitude of the imbalance vector of the rotating body rapidly converges toward 0. To do.

(Example) Hereinafter, one specific example of the present invention will be described in detail with reference to the drawings.

FIG. 1 shows a grinder which is an example of a rotating body apparatus according to the present invention, in which 1 is a working table and 2 is a rotating body in which a rotary polishing grindstone 3 is assembled, which rotates at a high speed around a rotation center axis 4.

Then, a circular groove 5 is formed on the end face of the portion formed integrally with the rotation center shaft 4 so as to center around the rotation center shaft 4, and a plurality of counterweights W ₁ , are formed in the groove 5. W ₂ is fitted around the rotation center axis 4 so that it can be moved and fixed freely. In this example, the weights W ₁ and W ₂ are only two and have the same weight (or the same mass). Further, as shown in FIG. 2, a reference mark 6 is attached to the peripheral edge of the circular groove 5 at an appropriate fixed position, and an angular scale for setting the mark 6 to 0 degree is used for the weight.
It is provided so that the angular positions of W ₁ and W ₂ can be easily discriminated. In this example, the operating screws 7 provided on the counterweights W ₁ and W ₂
The balance weights W ₁ and W ₂ can be changed between a fixed state and a movable state only by rotating the.

Reference numeral 8 is a microcomputer integrated with an operation panel for the grinding machine. Here, the microcomputer 8 includes a computer control device, an output device and the like in addition to the arithmetic processing device and the storage device. Front side 8a of the computer 8
In addition to the control switches of the grinder, various function keys of the computer control device, a display and a printer as an output device of the computer are arranged. Although not shown, as an input device directly connected to the computer, a vibration detector adapted to detect the vibration of the rotating body through its bearings and the rotational phase of the rotating body by light or magnetism. And a phase detection device adapted to detect (for this, Japanese Patent Laid-Open No. 60-2599).
(See Japanese Patent No. 27).

Next, an example of handling the above-described rotating body device and the contents of processing performed by the microcomputer 8 will be described according to the flow.
In addition, here, there are only two fishing weights W ₁ and W ₂ and both have the same revolution radius and the same weight (or mass).
Even if there are three or more and different revolution radiuses, weights, etc., the processing is only troublesome and the basic idea does not change.

The handling and processing flow of the apparatus is as shown in FIG. 3, and each step will be described below.

* First step: Initial measurement _First , fix the counterweights W ₁ and W ₂ at arbitrary positions, read the fixed angular positions of the weights W ₁ and W _{2 on} the scale, and use the operation keys to read the information from the microcomputer 8 To enter.

After that, the rotating body 2 is rotated at the normally used rotation speed by operating the operation panel, and the vibration displacement and phase of the rotating body 2 in this state are directly measured by the microcomputer through the vibration detector and the phase detector. And remember it.

The information obtained here is shown in Fig. 4, where a ₁ is the fixed angle of _one counterweight W ₁ , a ₂ is the fixed angle of the other counterweight W ₂ , and μ _1V is It is an unbalanced vector of the entire rotating body. Therefore, the magnitude of μ _1V shows the variable displacement of the rotating body, and θ ₁ shows its phase angle.

* Second step: The counterweights W ₁ and W ₂ are moved and fixed by operating the fixed operation panel, the rotation of the rotating body 2 is temporarily stopped, and the counterweight is adjusted.
Fix W ₁ and W ₂ at arbitrary fixed positions different from those in the first step. At this time, it is optional to move only one of the balance weights W ₁ and W ₂ or to move both of the balance weights W ₁ and W ₂ , but here, in order to simplify the handling, _one of the balance weights is moved. Only the weight W ₂ will be moved and fixed. The counterweight W ₂ after being moved will be referred to as W ₂ ′ hereinafter.

Here, the fixed angle of the counterweight W ₂ ′ is read and the information is input to the microcomputer 8 by the operation keys.

That is, the positions of the counterweights W ₁ and W ₂ ′ are as shown in FIG. 5, and a ₂ ′ is the fixed angle after the change of the counterweight W ₂ ′.

* Third step: Second measurement After the second step is completed, the rotating body 2 is rotated again in the normal use state by operating the operation panel, and the vibration displacement and phase of the rotating body 2 in the state are described above. Similarly, it is measured and stored in the microcomputer 8.

The measured information is shown in FIG. 6, where the vector μ _2V is the unbalanced vector of the entire rotor 3 and its magnitude indicates the vibration displacement of the rotor 2, and θ
₂ indicates the phase angle.

* Fourth step: unbalance correction of operation where the previous Dzu, the counterweight W _1, W ₂ of the weight is evident from the outset and (or by weight), the information obtained in the above step, i.e. " a ₁ (fixed angle of counterweight W ₁ ), a ₂ (fixed angle of counterweight W ₂ ), a ₂ ′ (fixed angle of counterweight W ₂ after moving), μ _1V (in the first step) The obtained unbalance vector of the entire rotating body), θ ₁ (phase angle of μ _1V ), μ _2V (the unbalance vector of the entire rotating body 2 obtained in the third step), and θ ₂ (phase angle of μ _2V ) The microcomputer 8 is caused to calculate the magnitude and phase of the unbalance vector unique to the rotating body 3 based on various information including ".
Here, the unbalance vector peculiar to the rotating body 3 is an unbalanced weight.
W _1, it is to refer to unbalance vector of the rotating body 2 and having no W _2.

Then, the order of the calculation is as follows.

A: Each counterweight W ₁ , W _{2 in} the normal use state of the rotating body ₂
An imaginary simulation vector related to the centrifugal force where is generated is determined based on the weight (or mass) of these weights W ₁ and W ₂ . That is, what is needed here is not a vector of the centrifugal force itself generated by W ₁ and W ₂ , but a simulation vector that has a similar relationship to these vectors, as will become apparent from the later description. The vector of the centrifugal force itself is scaled at an arbitrary fixed ratio.

Therefore, considering the ratio of these centrifugal forces in advance to obtain these simulated vectors, in this example, since W ₁ and W ₂ are promised to have the same weight, the actual centrifugal forces generated based on this are As long as the number of rotations and the radius of rotation of W ₁ and W ₂ are the same, the ratio is the same, and the ratio of both is “1: 1”.

Therefore, by deciding one of the simulated vectors to have a magnitude of 1 (this corresponds to the centrifugal force generated by W ₁ or W ₂ scaled at an arbitrary fixed ratio), the other simulated vector is determined. Can be determined to be 1.

Then, when these simulated vectors are illustrated, as shown in FIG. 7, that is, W _1V is a simulated vector relating to the centrifugal force generated based on the counterweight W ₁ , and W _2V is the counterweight W ₂
Is a simulated vector related to the centrifugal force generated based on

A) Obtain a simulated combined vector (= F _1V ) that is a combination of these simulated vectors W _1V and W _2V .

This is illustrated in FIG. 8, and R ₁ is the phase angle of F _1V .

From this point on, the horizontal line passing through the origin is the x-axis, and the vertical line passing through the origin is the y-axis.
Assume the xy coordinates for the axes.

Then, _{assuming that} the x component of W _1V is X ₁ and the y component thereof is Y ₁ , X ₁ = COS (a ₁ ) Y ₁ = SIN (a ₁ ).

Further, if the x-component of W _2V is X ₂ and the y-component is Y ₂ , then X ₂ = COS (a ₂ ) Y ₂ = SIN (a ₂ ).

However, the simulated composite vector (= F _1V ) to be obtained is F _1V = W _1V + W _2V , so if the x and y components of F _1V are F _1X and F _1Y , then F _1X = X ₁ + X ₂ = COS (A ₁ ) + COS (a ₂ ) F _1Y = Y ₁ + Y ₂ = SIN (a ₁ ) + SIN (a ₂ ).

Therefore The phase angle F _1V (= R _{1) ^{is, R 1 = TAN -1 (F}} 1Y / F 1X) = TAN -1 _{[SIN (a 1) + SIN (} a 2) / COS (a 1) + COS
(A ₂ )].

C) Next, in the normal use state of the rotating body 2, the counterweight W ₂ ′
The simulated vector related to the centrifugal force where
When expressed in the same scale as the simulated vector to be cut into W ₁ and W ₂ , since the weight (or mass) and the radius of gyration of W ₂ ′ are the same as W ₁ , its size can be determined to be 1.

That is, the simulated vector relating to the counterweight W ₂ ′ is shown in FIG.
It can be expressed as W ₂ ′ _V.

D) A simulated synthetic vector (= F _2V ) is obtained by synthesizing the simulated vector W _1V and the simulated vector W ₂ ′ _V. This is illustrated in FIG. 9, where R ₂ is the phase angle of F _2V .

Here, the x component (= X ₁ ) of W _1V is COS (a ₁ ) and the y component (= X ₁ )
As mentioned above, Y ₁ ) is SIN (a ₁ ).

On the other hand, assuming that the x component of W ₂ ′ _V is X ₃ and the y component is Y ₃ , X ₃ = COS (a ₂ ′) Y ₃ = SIN (a ₂ ′).

However, the above-mentioned simulated composite vector (= F _2V ) to be obtained is F _2V = W _1V + W ₂ ′ _V , so that if the x and y components of F _2V are F _2X and F _2Y , then F _2X = X ₁ + X _{3 = COS (a 1) +} COS (a 2 ') F 2Y = Y 1 + Y 3 = SIN (a 1) + SIN (a 2') and expressed.

Therefore, Becomes

And the phase angle (= R ₂ ) of F _2V is R ₂ = TAN ^-1 (F _2Y / F _2X ) ＝ TAN ^-1 [SIN (a ₁ ) + SIN (a ₂ ′) / COS (a ₁ ) + COS
(A ₂ ′)].

(E) An imaginary simulated displacement vector (= F ₂₁ ) is obtained by subtracting the simulated composite vector F _1V from the simulated composite vector F _2V . Here, what is needed is the magnitude of F _21, is shown in FIG. 10 To illustrate the F _21.

Then, because F ₂₁ = F _2V −F _1V , Becomes

F) Actual displacement vector (= μ ₂₁ ) obtained by subtracting the unbalance vector μ _{1V of the} entire rotor 2 obtained from the measurement result of step 1 from the unbalance vector μ _{2V of the} entire rotor 2 obtained from the measurement result of step 3 Ask for.

Here again, what is required is the size of μ ₂₁ , which is illustrated in FIG. 11.

Therefore, the displacement vector (= μ ₂₁ ) is expressed as μ ₂₁ = μ _2V −μ _1V . The phase angle of μ _2V is θ ₂ from the measurement result of step 3, and the phase angle of μ _1V is θ ₁ from the measurement result of step 1.

Here, if the x and y components of μ _2V are μ _2X and μ _2Y , then μ _2X = μ _2V COS (θ ₂ ) μ _2Y = μ _2V SIN (θ ₂ ) and the x and y components of μ _1V are μ _{If 1X} and μ _1Y , μ _1X = μ _1V COS (θ ₁ ) μ _1V = μ _1V SIN (θ ₁ )

Therefore, Is expressed as

G) The change vector μ ₂₁ is replaced with the simulated change vector F ₂₁
Divide by to obtain the change rate (= k).

k = μ ₂₁ / F ₂₁ Here, the meaning of k will be clarified with reference to FIG.

In the figure, C ₁ indicates a circle with a radius of 1, and C _K has a radius of 1 ×
Denote a circle that is k ', or k'. The vector represented by the line segments Y ₁ and Y ₃ is the actual synthetic vector generated by the counterweights W ₁ and W _{2 when the} rotating body 2 is rotated in the normal use state, and is the simulated synthetic vector F _1V described above. Let it be multiplied by the above-mentioned k'which is an arbitrary number. The vector represented by the line segments Y ₁ and Y ₂ is the counterweight when rotating the rotating body 2 in the normal use state.
It is assumed that the above-mentioned simulated combined vector F _2V is multiplied by the above k ′ by the actual combined vector generated by W ₁ and W ₂ ′. Thus counterweight W _1, W rotating body 2 specific unbalance vector _{when 2} 'is that there is no (subject trying this Calculate now) is W _1V described above if represented by U _V, W _2V ,
W ₂ ′ _V , F _1V , F _2V , F ₂₁ , μ _1V , μ _2V and μ ₂₁ must have a relative relationship as shown in the figure. The unbalance vector U _V cannot depend on the position of the counterweight. In such a case, the triangle S ₁ S ₂ S ₃ and the triangle Y ₁ Y ₂ Y ₃ are congruent, and the triangle Y ₁ Y ₂ Y ₃ and the triangle Y ₁ Y ₂₁ Y ₃₁ are similar. Therefore the displacement vector μ
_The vector represented by ₂₁ and the line segment Y ₂・ Y ₃ has the same direction and size, and the value obtained by dividing the vector represented by the line segment Y ₂・ Y ₃ by the simulated displacement vector F ₂₁ is the displacement vector. It is equal to μ ₂₁ divided by the simulated displacement vector F ₂₁ , and its value is the same as k ′. That is, this is the change rate (=
This means that finding k) is equivalent to finding k'in this figure.

H) However, as can be easily understood with reference to FIG. 12, the following relationship is established.

That is, U _V + k · F _1V = μ _1V U _V + k · F _2V = μ _{2V, so} U _V = μ _2V −k · F _2V・ ・ ・ f ₁ μ _1V = μ _2V −k · F _2V + k · F _1V ... f ₂ By the way, when measuring the imbalance of the rotating body, a delay error is generally generated due to the response characteristics of the device, the distortion of members, and the like. Therefore, the error must be taken into account in order to make the calculation accurate using the measurement results.

Therefore, the delay angle (= δθ) is obtained in advance.

Now, in order to calculate the delay angle (= δθ), the phase angle (= θ ₁ ′) of μ _{1V in} the calculation is calculated by using the above f ₁ formula.

That is, On the other hand, since the phase angle of μ _1V is now θ ₁ ′, μ _1V
Is represented as follows.

Then, by setting f ₃ and f ₄ equal,
θ ₁ ′ can be obtained.

That is, θ ₁ ′ = TAN ⁻¹ [μ _2V SIN (θ ₂ ) / − kSIN (a ₂ ′) + kSIN (a ₂ ) / μ _2V COS (θ ₂ ) −kCOS (a ₂ ′) + kCOS (a ₂ ). ] Becomes

The value of θ ₁ ′ thus obtained is a value different from that in theory, though it should be θ ₁ . That is, the error is an error that may occur due to the response characteristics of the device or the distortion of the members as described above.

Therefore, the delay angle (= δθ) is expressed as δθ = θ ₁ −θ ₁ ′.

Li) Then, the target unbalance vector U _V peculiar to the rotating body 2 is obtained by using the f ₁ equation.

That is, from U _V = μ _2V −k · F _2V , the following is obtained.

Note that here, μ _2V is taken into consideration in consideration of the delay angle (= δθ).
The phase angle of is defined as “θ ₂ + δθ”.

And the phase angle (= θ ₃ ) of U _V is as follows.

Therefore, θ ₃ TAN ^-1 {[μ _2V SIN (θ ₂ + δθ) −k SIN (a ₂ ′) + k · SIN (a ₁ ) / [μ _2V COS (θ ₂ + δθ) −k · COS (a ₂ ′) + k COS (a ₁ )]} Next, the fixed angle of each of the counterweights W ₁ and W ₂ that balances the unbalance vector U _V unique to the rotating body 2 obtained as described above is calculated.

Here, as shown in FIG. 13, the counterweights W ₁ and W ₂ are 18 more from the position of U _V , which is at the point θ ₃ from the reference point 0 °.
With the position P ₁ advanced by 0 degrees as a reference, it is bound to a position fixed at a position displaced by the same angle γ in opposite directions.

The procedure for calculating the fixed angles of the counterweights W ₁ and W ₂ is as follows.

A) It is generated by the counterweights W ₁ and W ₂ when the counterweights W ₁ and W ₂ are _first fixed to the position of γ and the rotating body 2 is rotated in the normal use state. Calculate the magnitude of the centrifugal force vector.

In FIG. 13, W _1VK and W _2VK are the vectors, and when γ is used, the magnitude is as follows.

That is, W _1VK = W _2VK = [W ₁ or W ₂ is a simulated vector (= 1) related to the centrifugal force generated in the normal use state of the rotating body] × k = k.

Here, k is the above-mentioned rate of change b) and the angle γ is obtained from the relationship between the vectors W _1VK and W _2VK and the unbalance vector U _V peculiar to the rotating body.

That is, the relationship between them is −U _V = W _1VK + W _2VK .

Therefore, | U _V | = (1 × k) · COS (γ) + (1 + k) · COS (γ) = 2k · COS (γ).

Therefore, the fixed angle (= γ) of the counterweights W ₁ and W ₂ is γ = COS ^-1
(U _V / 2k).

C) Furthermore, the fixed angle of each counterweight W ₁ , W ₂ (= γ1 or γ
When 2) is displayed at the reference position 6, that is, at an angle from 0 degree, the following calculation is performed.

The angle scale is set to be positive in the counterclockwise direction fm.

That is, a fixed angle of the counterweight W ₁ (= γ1) is expressed by γ1 = θ ₃ +180 °-gamma, a fixed angle (= .gamma.2) of the other counterweight W ₂ is a γ2 = θ ₃ +180 degrees + gamma expressed.

* Fifth step: Imbalance correction Fixed angle (= γ1 or γ2) obtained as described above
According to the information, the balance weights W ₁ and W ₂ are moved and fixed.

* Sixth step: Confirmation measurement Similarly to step 3, the vibration displacement and phase of the rotating body 2 are measured.

If the unbalance vector (= μ _2V ) of the entire rotating body 2 measured in the step is acceptable, the unbalance correction work is completed.

However, if it is unacceptable, press the operation key to adjust each counterweight W ₁ , at the time when the fifth step is completed,
The microcomputer 8 is made to continue the processing again by inputting the fixed angle information of W ₂ .

As a result, the microcomputer 8 obtains a new change rate (= k), a delay angle (= δθ), etc. from the measurement result of the sixth step and the measurement result of the third step according to the above-mentioned fourth step. Then, the highly accurate fixed angle information is calculated and output.

Therefore, the operation corresponding to the fifth step is again performed, that is, the balance weights w ₁ and W ₂ are moved and fixed again according to the fixed angle information, and then the operation corresponding to the sixth step is performed again. , After this, the unbalance vector (= μ _2V ).
The same operation and processing are repeated until the value becomes an allowable size.

Next, a record of actual imbalance correction using the apparatus of the present invention will be shown.

First fixed angle a ₁ input obtained in step information counterweight w _1: 50 ° counterweight w ₂ fixed angle a _2: 280-degree rotation member 2 overall unbalance size, i.e. the rotary body No. 2 vibration displacement μ _1V : 6.86 μm μ _1V phase angle θ ₁ : 327 degrees 2nd step operation The fixed angle of only the counterweight w ₂ was reduced by 20 degrees.

Input information obtained in the 3rd step Fixed angle of counterweight w ₁ a ₁ : 50 degrees Fixed angle of counterweight w ₂ ′ a ₂ ′: 260 degrees Unbalanced size of the entire rotor 2 μ _{2 V} That is, the vibration displacement of the rotating body 2: 5.17 μm μ _{2 V} phase angle θ ₂ : 323 degrees Output information obtained in the fourth step The magnitude of the unbalance U _V peculiar to the rotating body 2, that is, the vibration displacement of the rotating body 2: 2.64 μm U _V phase angle θ ₃ : 352.9 degrees Fixed angle of counterweight w ₁ γ ₁ : 98.9 degrees Fixed angle of counterweight w ₂ γ ₂ : 246.9 degrees Operation in the 5th step Each counterweight w ₁ , w ₂ was fixed again according to the fixed angle information γ1 and γ2 obtained in the fourth step.

Information obtained in the sixth step Size of unbalanced μ _{2 V} of the entire rotating body 2, that is, vibration displacement of the rotating body 2. Phase angle θ ₂ : 238 degrees of 1.98 μm μ _{2 V} Here, vibration of the rotating body 2 Displacement (ie unbalance vector μ
The size ( _2V ) is 1.98 μm, which is not yet satisfactory, so the next step was performed.

As a result, fixed angle information γ1 and γ2 of the balance weights w ₁ and w ₁ for correcting the balance with higher accuracy was obtained as follows.

Fixed angle of counterweight w ₁ γ ₁ : 56.6 degrees Fixed angle of counterweight w ₂ γ ₂ : 204.6 degrees Therefore, according to the operation corresponding to the fifth step, that is, the fixed angle information, each counterweight w ₁ , w ₂ The fixing angle of was fixed again.

Then, the operation corresponding to the sixth step was performed again, and the following result was obtained.

The magnitude of the unbalanced μ _2V of the entire rotating body 2, that is, the vibration displacement of the rotating body 2: 0.69 μm The phase angle θ ₂ : 132 degrees of μ _{2V The} vibration displacement of the rotating body 2 in this state is 0.69 μm. Since it was satisfactory, the balance correction work was completed.

(Effects of the Invention) According to the present invention described in detail above, most of the work for determining the fixed position of the counterweight, which was the most difficult in the imbalance correction, can be performed by a predetermined calculation. Since unbalance correction is possible, and the initial placement of the counterweight can be arbitrary when correcting the unbalance, handling is convenient, and the fixed position of each counterweight is calculated based on the rate of change. Even if the weighing of the counterweight and the measurement of the unbalance vector of the rotating body are weighed by different weighing means, the error caused by this does not occur at all, and from another viewpoint, Even if the unit for measuring the weight of the counterweight and the unit for measuring the magnitude of the unbalance vector are different, there is no problem and the versatility is excellent.

Further, according to the device of the present invention, the rotation and stop of the rotating body are repeated several times, the work of moving the counterweight around the rotation center axis of the rotor and fixing it is repeated several times, and the counterweight. Due to the limited human work consisting of handling the operation keys to input the fixed angle information, etc., it becomes possible to obtain the final fixed angle information of the counterweight to eliminate the imbalance of the entire rotating body, Moreover, each counterweight can be easily positioned according to the fixed angle information while observing the angle scale of the rotating body. Therefore, any skill is required for the unbalance correction work which has required a great deal of work in the past. This is extremely simple and can be performed in a short time without doing so.

[Brief description of drawings]

FIG. 1 is an overall front view of the device of the present invention, FIG. 2 is a front view of a rotating body, FIG. 3 is a flow chart of handling and processing, FIGS. 4 to 12 are diagrams showing vectors, and FIG. 13 is fishing. It is a figure explaining the fixed angle of a weight. 2 ... Rotator, 4 ... Rotation center axis, 8 ... Microcomputer, μ _1V and μ _2V …… Unbalance vector of the whole rotor, μ ₂₁ …… Displacement vector, k …… Change rate, F _1V and F _2V
…… Simulated composite vector, F ₂₁ …… Simulated displacement vector, U _V
…… Unbalance vector peculiar to rotating body, W ₁ and W ₂ …… Balance weight.

Claims (2)

[Claims] 1. A whole rotary body in a state in which a plurality of counterweights provided so as to be movable and fixed about a fixed radius with respect to the rotary body are fixed at arbitrary positions and the rotary body is rotated at a predetermined speed. The unbalance vector μ1V of the entire rotating body is measured again with the rotating body similarly rotated with at least one of the weights fixed to any other fixed position of the rotating body. On the other hand, each simulated composite vector in which each centrifugal force is scaled at an arbitrary fixed ratio so as to be generated by a plurality of counterweights in each of the states is performed.
F2V, F1V is calculated based on the numerical value proportional to the weight or mass of each counterweight and the fixed position or revolution speed of the same weight, and then the displacement vector μ21 and each state obtained as the difference of the unbalance vector of each state Change rate k, which is the ratio to the simulated displacement vector F21 obtained as the difference of the simulated combined vector of
Then, based on the information of the above-mentioned unbalance vector, simulated composite vector, and rate of change, the unbalance vector peculiar to the rotating body with no balance weight is calculated, and the unique unbalance vector is eliminated. A method for correcting imbalance in a rotating body apparatus, wherein a fixed position of each counterbalance weight is calculated as an angle around a rotation center axis of the rotating body. 2. A plurality of counterweights, which are movable and fixed around a center axis of rotation with respect to a rotating body, and an angle scale for discriminating a fixed angle of these counterweights. On the other hand, the rotating body rotates. Attach a microcomputer that the phase signal obtained from the detector for detecting the phase and the vibration waveform signal obtained from the detector for detecting the vibration of the rotating body are directly input, Moreover, the microcomputer determines that the counterweights are arranged differently from the signal information detected by the respective detectors, the fixed angle information of the counterweights input from the operation keys of the computer control device, and the previously input material. Simulated synthetic vector in which the unbalanced vector μ1V, μ2V during rotation of the rotating body in each arranged state and the centrifugal force to be generated by the counterweight in each arranged state are scaled at an arbitrary constant ratio. The change rate k, which is the ratio of the displacement vector μ21 obtained as the difference between the unbalanced vectors F1V and F2V and the unbalanced vector and the simulated displacement vector F21 obtained as the difference between the simulated combined vectors, is calculated, and based on these information An unbalance correction device for a rotating body device, wherein the angle information of the counterweight for correcting the unbalance of the rotating body is output.