JP3443719B2 - Dynamic balance measuring machine - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention measures the dynamic balance of a rotating body.
Related to machine relates to the dynamic balance measurement device suitably used for a polygon mirror or the like rotating at a high speed.

[0002]

2. Description of the Related Art Polygon mirrors that are lightweight and rotate at high speed
As described in JP-A-4-172227,
Vertical two-sided dynamic balance measuring machine for tires, that is, upper and lower sides of a lower motor case having tire mounting means on the upper side 2
The parts are connected to the machine body fixing part in a cantilever manner with a coil spring, etc., and the connecting surfaces are made to coincide with each other and the two parts are connected at the upper and lower parts via a vibration sensor of the case such as a load cell or a moving coil, so that the motor shaft and the tire are connected. The dynamic balance is measured with the same measuring machine that obtains the maximum amount of shake and the phase angle of the two upper and lower surfaces of the tire from the information of the phase sensor that detects the position mark of There is.

In the dynamic balance measuring machine, the coil spring has a large spring constant in order to support a motor or the like, which is much heavier than a polygon mirror, in a cantilever manner, and at the same high speed as when the polygon mirror is used. If the bearing is composed of a dynamic pressure bearing that has low frictional resistance to rotate, the air layer formed by the dynamic pressure bearing absorbs minute vibrations, which makes it difficult to use a highly sensitive vibration sensor. There is a problem in that it is not possible to measure such an unbalanced amount. Moreover, not only the force in the connecting direction of the motor case and the machine body fixed part but also the force in the perpendicular direction is applied to the vibration sensor, so the measurement including the component of the force unnecessary for the dynamic balance measurement is performed, and the measurement is unsuccessful. Another problem is that it tends to be accurate.

On the other hand, a driving board portion provided with a polygon mirror mounting means and a motor for rotating the polygon mirror is supported by a roller or the like so as to be horizontally movable in one direction, or the driving board portion is fixed to an upper body fixing portion. Influence of the weight of the drive board on the vibration in the direction perpendicular to the center of the motor rotation axis, such as hanging horizontally with four equal-length hanging strings from the four vertexes of the square centering on the center of the motor rotation axis There is also known a dynamic balance measuring machine which is designed to reduce as much as possible. However, such a measuring machine is a static balance measuring machine and cannot measure dynamic balance.

On the other hand, for example, the above-mentioned dynamic balance measuring machine can determine the vector [M] which gives the weight weight and the position phase angle to be added to the constant radius position for balance adjustment of the rotating body. However, even if [M] is given, if the weight to be added is large, or if the addition position is the same as the previous addition position, it is not possible to add a weight to the phase angle position that gives one point of the constant radius position. Instead, it will be attached to the spread position, so once given [M]
It is difficult to obtain a sufficient dynamic balance by adjusting the dynamic balance based on, and the dynamic balance measurement and the dynamic balance adjustment based on the result are repeated many times, which makes it difficult to adjust the dynamic balance. there were.

[0006]

[SUMMARY OF THE INVENTION The present invention has been made to solve the problems in the conventional dynamic balancing machines described above, a lightweight, such as a polygon mirror, yet using Bearing pressure Te and purpose to provide dynamic balancing machines which can accurately measure up small unbalance of the rotating body rotating at a high speed.

[0007]

SUMMARY OF THE INVENTION According to the present invention, there is provided a drive board portion on which an object to be measured is detachably mounted and rotated, and a lower portion of the drive board portion, which is integrally provided in a suspended state, for the rotation. A vibration detecting plate portion having a detected portion for detecting vibration in a direction perpendicular to the center line, and the vibration detecting plate portion and left and right machine body fixing portions in a direction perpendicular to the vibration direction at two locations separated vertically. A leaf spring that is perpendicular to the vibration direction to be connected, a vibration sensor that detects the vibration of the detected portion, a rotation phase sensor that detects the rotation phase of the measured object, and outputs of the rotation phase sensor and the vibration sensor. to achieve the pre-Symbol purpose by the maximum deflection amount and structure of the first invention of dynamic balancing machines, characterized in that it comprises a calculating means for calculating information related to the phase angle of the object to be measured based on the information.

[0008]

In other words, in the dynamic balance measuring machine of the present invention , the drive substrate portion on which the measured object is mounted and rotated is provided with the detected portion for detecting the vibration in the direction perpendicular to the lower rotation center line. The vibration detection plate part is supported by the leaf springs that are perpendicular to the vibration direction at the two left and right body fixing parts that are perpendicular to the vibration direction to be detected. If there is a disproportion,
The detected part of the vibration detection plate is sensitively and efficiently unbalanced and shakes the maximum at a phase angle with weight, and the calculation means accurately detects the deviation of the measured object based on the information of the vibration sensor and the rotation phase sensor that detect it. Gives information about the balance and its phase angle. By providing the detected portion of the vibration detecting plate and the vibration sensor at the upper and lower portions with this measuring device, the dynamic balance of any portion such as the upper and lower two surfaces of the measured object can be measured.

[0009]

[0010]

The present invention will be described below with reference to the drawings.

[0011] Figure 1 is schematic perspective view showing an example of a dynamic balance measuring machine of the present invention, FIG. 2 is a partial sectional view showing an example of a driving substrate of the present invention the dynamic balancing machine, FIG. 3 is dynamic balancing machine FIG. 4 is a plan view of an adjusted object showing an example of balance adjustment by a dynamic balance adjuster, and FIG. 5 is an adjusted object showing an example of balance adjustment by a dynamic balance adjuster. FIG. 6 is a partial perspective view of the body, and FIG. 6 is a plan view of the body to be adjusted showing another example of balance adjustment by the dynamic balance adjuster.

In FIG. 1, reference numeral 1 designates an object-to-be-measured mounting means 101, whose details are shown in FIG.
The drive board unit 2 having a motor 120 for rotating in the direction of the arrow is provided integrally with a lower portion of the drive board unit 1 in a suspended state, and detects vibration in a direction perpendicular to the rotation center line of the measured object P. The vibration detecting plate portions 3, 4 having the detected portions 21, 22 separated from each other in the vertical direction are the right and left body fixing portions 7, 8 and the vibration detecting plate in the direction perpendicular to the vibration direction of the vibration detecting plate portion 2. The leaf springs 5 and 6 perpendicular to the vibration direction of the vibration detecting plate portion 2 connecting the portion 2 to the upper portion also connect the left and right body fixing portions 7 and 8 and the vibration detecting plate portion 2 at the lower portion. The leaf springs 9 and 10 are the detected portions 21, 2 of the vibration detection plate portion 2.
2 is a vibration sensor using, for example, an acceleration pickup or a moving coil, which outputs shake information such as acceleration or shake amount, and the shake information output from these sensors passes only components synchronized with the rotation and other components. The noise is input to the control device 14 using a microcomputer via the amplifier circuits 11 and 12 including a filter circuit for removing the noise as necessary.

Reference numeral 13 denotes a reference position mark P1 provided on the object P to be measured or a reference position mark detection signal provided on a shaft for rotating the object P to be output to the control mounting 14, for example, a light emitting element and a photoelectric conversion element. Rotational phase sensor consisting of 1
Reference numeral 5 denotes an operation panel for outputting drive control information of the measuring machine, calculation control information input from the vibration sensors 9 and 10 and the rotation phase sensor 13 and a start signal to the control device 1.
Reference numeral 6 is a display of input / output control information of the control device 14 and calculation results.

In FIG. 2, the same reference numerals as those in FIG. 1 indicate the same functional members. In the dynamic balance measuring machine of the example of FIG. 2, the object-to-be-measured mounting means 101 of the driving board portion 1 is vertically supported by the driving board portion 1. The fixed core shaft 102, the lower thrust bearing 103, the radial bearing 105, and the upper thrust bearing 109 that are sequentially fitted to the core shaft 102, and the washer 118 screwed into the screw hole provided in the upper end surface of the core shaft 102. Through the upper thrust bearing 109, the radial bearing 105 and the lower thrust bearing 103.
Of the upper and lower thrust bearings 109, 1
03, the collar 107 fitted to the outer diameter of the radial bearing 105 maintains a gap of about 1 to 7 μm, and the length also has a collar 107 having a length that produces a similar gap between the upper and lower thrust bearings 109 and 103, The driven portion 114 integrally provided in a state fitted to the outer diameter of the collar 107 and having a large number of magnets 125 arranged in the circumferential direction on the lower surface side, and the collar 107 fitted to the outer diameter of the collar 107. A large number of reflecting surfaces 1 that are pressed against the driven part 114 and fixed to the collar 107 by a fixing member 117 that is screwed into a screw provided on the outer diameter of
15 is composed of a polygon mirror 116 formed on the outer periphery. The drive board unit 1 as shown in FIG. 2 is mounted with the measured object P and is driven by the stator coil 124.
When the collar 107 integrated with 14 and the polygon mirror 116 are rotated, a large number of spiral-shaped dynamic pressure generating grooves 121 having a depth of several μm formed in the upper surface of the lower thrust bearing 103 in the circumferential direction are lowered. Thrust bearing 103 and collar 107
After the collar 107 and the driven portion 114 are floated by flowing in the gap between the collar 107 and the driven portion 114 from the outer peripheral side, the gap between the radial bearing 105 and the collar 107 is raised to raise the collar 107.
An airflow is blown through the gap between the upper thrust bearing 109 and the upper thrust bearing 109 from the center side toward the outer peripheral direction, whereby the driven part 11
The rotating body from 4 to the polygon mirror 116 can be rotated at a high speed of 2 to 3 × 10 ⁴ rpm with a low frictional resistance. That is, a dynamic pressure bearing is formed between the upper and lower thrust bearings 109 and 103, the radial bearing 105 and the collar 107. These dynamic pressure bearing constituent members may be formed of any one of ceramics, preferably metal, which is excellent in wear durability, or may be formed of a resin that is lightweight, inexpensive and easily obtained.

Not only in the example of FIG. 2, not only the dynamic pressure generating groove 121 is provided only in the lower thrust bearing 103, but also the radial bearing 105 and the lower thrust bearing 103, or the radial bearing 105 and the lower thrust bearing 103 and the upper thrust. It may be formed on the bearing 109, the upper thrust bearing 109 may be omitted, and the washer 118 may directly press and fix the radial bearing 105 and may be opposed to the upper end surface of the collar 107. However, a simple metal bearing or a ball bearing which does not form a dynamic pressure bearing may be used.

The dynamic balance measurement by the measuring machine of FIG. 1 having the above-mentioned object mounting means 101 is carried out as follows.

The object to be measured P is mounted on the object to be measured mounting means 101 of the drive board unit 1 as described above, and the number of revolutions and the calculation program are designated on the operation panel 15 and then the apparatus is started to start the object to be measured. When P is rotated to the operating speed by the motor 120 including the stator coil 124 on the drive substrate 1 side and the magnet 125 on the driven part 114 side, which is controlled by the control device 14, the measured object P is unbalanced. The leaf springs 3 to 6 supported by the vibration detection plate portion 2
It oscillates in the direction perpendicular to the plane of and perpendicular to the center of rotation. The vibration sensors 9 and 10 detect the vibrations of the two detected portions 21 and 22 of the vibration detection plate 2, respectively, and the amplification circuit 11
The shake information is input to the control device 14 via 12, and the timing information at which the rotational phase sensor 13 detects the reference position mark P1 is input to the control device 14. As a result, the signal processing device portion of the control device 14 determines the maximum shake of the detected portions 21 and 22 from the shake information, the timing information, and the rotation speed information of the measured object P provided by a motor drive pulse counter (not shown) or a rotary encoder. The shake vectors [A ₁ ] and [A ₂ ] given by the quantities and their phase angles from the reference position mark P1 are obtained and stored.

Next, the weight of the weight and the weight of the vector [U ₁ ] given by the additional position phase are added at a constant radius position from the center of rotation to which the balance adjustment weight of the upper surface of the object to be measured P is added, and the same as above. Then, the shake vectors [B ₁₁ ] and [B ₂₁ ] given by the maximum shake amounts of the detected portions 21 and 22 and their phase angles from the reference position mark P1 are obtained and stored. Next, the weight of the weight and the weight of the vector [U ₂ ] given by the additional position phase are added at a constant radius position from the center of rotation to which the balance adjustment weight of the measured object P is added, and the detected portion is similarly added. The shake vectors [B ₁₂ ] and [B ₂₂ ] given by the maximum shake amounts of 21 and 22 and their phase angles from the reference position mark P1 are obtained,
([B ₁₁ ]-[A ₁ ]) / [U ₁ ] = [α ₁₁ ],
([B ₂₁ ]-[A ₂ ]) / [U ₁ ] = [α ₂₁ ],
([B ₁₂ ]-[A ₁ ]) / [U ₂ ] = [α ₁₂ ],
By ([B ₂₂ ]-[A ₂ ]) / [U ₂ ] = [α ₂₂ ], a shake correction coefficient vector [α ₁₁ ] due to an additional weight,
[Α ₂₁ ], [α ₁₂ ] and [α ₂₂ ] are calculated, and the weights to be added to the constant radius positions, which are the unbalanced amounts of the upper and lower two surfaces, for adjusting the dynamic balance of the measured object P from the following equations. The vectors [M ₁ ] and [M ₂ ] that give the weight and the position phase angle are obtained.

[0019]

[Equation 1]

The vectors [M ₁ ] and [M ₂ ] give the weight weight and the position phase angle to be added which can accurately adjust the dynamic balance of the object P to be measured. The object P to be measured in FIG. 2 is provided with circumferential grooves 116a and 114a for adding a balance weight by a dynamic balance adjuster as described later based on the information of the vectors [M ₁ ] and [M ₂ ]. . In the case of balancing by weight reduction instead of weight balancing, the position phase angle may be advanced by π to reduce the weight.

In FIG. 3, reference numeral 30 denotes an attaching / detaching means 31 for easily obtaining a rotational balance, which is composed of, for example, a mounting shaft having a screw hole or a bolt on an upper end surface thereof to which the body to be adjusted Q of the rotating body is attached and detached, and a washer and a tightening screw or a nut. And 32. The object rotating part having a rotating means such as a motor or a speed reducer for rotating the mounting shaft of the attaching / detaching means 31 to rotate the body Q to be adjusted around the rotating shaft, 32 is the attaching / detaching means. A weighting means for ejecting a liquid material such as an ultraviolet curable resin liquid, a molten resin liquid or a dissolved resin liquid from the nozzle 33a to adhere it to the surface of the body to be adjusted Q attached to 31 and to solidify it by ultraviolet irradiation, cooling or drying. 33 and a combination of a feed screw and a nut or a rack and a pinion of the illustrated example for moving the weighting means 33 to displace the discharge port position of the nozzle 33a in the radial direction of the rotation of the body to be adjusted. Alternatively weighted distribution portion having a radial moving means 34 consisting of a hydraulic plunger, etc., 35,
Information of the positions R and θ to be weighted on the surface of the body to be adjusted Q and the weight M, that is, for example, the above-mentioned vector [M ₁ ] or [M ₂ ]
The unbalanced information and the detection information of the reference mark sensor 36 for detecting the reference rotation phase mark Q1 of the object to be adjusted Q are input, and the turning means and the weight distribution of the turning means of the object turning part 30 are input. Movement of moving means 34 of section 32 and weighting means 3
3 is a control device using a microcomputer for controlling the discharge of the liquid material from the nozzle 33a.

The object to be adjusted Q in the illustrated example has a radius R from the center of rotation.
At the position of the circular groove 116a or 1 of the measured object P of FIG.
Since a circular groove Q2 having a radial width 2r for attaching a weight for dynamic balance adjustment is provided similarly to 14a, the control device 35 controls the weighting means 33 according to an instruction from an operation panel (not shown). After the nozzle 33a is moved to the radius R position of the circumferential groove Q2, the moving means 34 is stopped while the nozzle 33a is moved, for example, the weight M and the weighted position of the vector [M ₁ ] as described in the section of the action. When the phase angle θ is input through the operation panel, M / m = n + s (m is a predetermined weight within a range evenly distributed from one point that can be regarded as being added to one point, but in the illustrated example, the radial direction is the circumference. Since it is regulated by the groove width of the groove Q2, it is preferable that the weight is a predetermined weight within a range in which the distribution in the left and right in the circumferential direction can be kept uniform and the spread in the left and right in the circumferential direction is approximately r or less on one side. Is 0
Alternatively, the following control is performed according to the value of n, which is a positive integer and s is a decimal number.

When n is 0, the position of θ is weighted by s × m, and when n is 1, the positions of θ ± 2r / R are m / 2 and m (1-cos2r). / R) + m × s
, When n is 2, the weight is 2m (1-cosr / R) + m × s at two positions of θ ± r / R and at the positions of θ ± r / R, and when n is 3, θ ± r M at the two positions of / R and 2 at the two positions of θ ± 2r / R and 2m (1-cosr / R) + m (1-cos2r / at the positions of m / 2 and θ, respectively.
The discharge amount of the liquid material by the nozzle 33a of the weighting means 33 and the rotation by the rotating means of the adjusted body rotating portion 30 are controlled so as to perform the weighting of R) + m × s.

FIG. 4 shows the front surface of the body to be adjusted Q which has been weighted for balance adjustment by the control when n is 3, and the vector [M ₂ ] on the back surface side is obtained by the two-side balance adjustment.
If is also input, the balance adjustment is similarly weighted on the back side. By this weight adjustment, it is possible to obtain a rotating body having an excellent dynamic balance. However, the weight adjustment is not limited to this example, and even if the circumferential groove Q2 is controlled so as to perform weighting of continuous distribution as shown in FIG. 5 (A), it is flat as shown in FIG. 5 (B). The same effect can be obtained by controlling the surface of the object to be adjusted Q so as to apply a circular arc-shaped continuous distribution.

Further, the dynamic balance adjusting machine of the present invention is not limited to the one for adjusting the weight, and the weighting means 33 is replaced with a milling head using an end mill having a hole diameter of 2r.
As shown in Fig. 5, an arcuate groove having a depth h is excavated on the flat surface of the object to be adjusted Q, or a circle having a diameter 2r distributed in the circumferential direction with a radius R as described in the section of the action. The control for excavating the depression may be performed.

In the case of the continuous distribution of FIG. 5A, for example, the arc length s for filling the circumferential groove Q2 of the resin corresponding to the weight M to be added is s≈M / 2ρrh (ρ is the resin unit) Since the weight per volume, r and h are 1/2 of the groove width of the circumferential groove Q2 and the depth), the nozzle 33a is first (s-2r) / 2 outward from the position of θ ± 2r / R. The circular groove Q2 is filled with resin by rotating the arc length 2r relative to each other, and finally, the total amount of the filled resin is M in the arc length 2r portion at the R and θ positions.
By filling the shortage resin amount to achieve the above, it is possible to adjust the dynamic balance with high accuracy similar to the dot-like distribution of FIG. Moreover, in the case of the continuous distribution of FIG.
The deposition weight m per unit arc length may be obtained in advance, and the resin may be deposited such that the R and θ positions are the last by using s of s≈M / m. In the case of FIG. 5C, the center of the end mill is R, θ ± (M−ρπr
By excavating the groove of depth h by moving in the range of ² h) / 2ρrhR, the dynamic balance can be adjusted accurately no matter where the excavation starts.

Not limited to the example of weighting or unloading in the arc shape described above, weighting or unloading may be performed in the radial direction as shown in FIG. However, in this case,
It cannot be weighted in the groove and R _S = (R _L ²
-2MR / m) ^1/2 (where R _L is the specified maximum radius that allows weighting or unloading, and m is the radius R that satisfies the loading weight or excavating weight per unit radial direction length)
_It is possible to adjust the dynamic balance with high accuracy by performing the control of weighting or excavation weighting of m proportions on the plane between _S and _RL .

[0028]

As described above in detail, according to the dynamic balance measurement apparatus of the present invention, the drilling weight to be weight by weight and the position phase angle or removed to be added to the dynamic balance can be precisely adjusted in the object to be measured The position phase angle can be easily obtained.

[Brief description of drawings]

FIG. 1 is a schematic perspective view showing an example of a dynamic balance measuring machine of the present invention.

FIG. 2 is a partial cross-sectional view showing an example of a drive board portion of the dynamic balance measuring machine of the present invention.

FIG. 3 is a schematic perspective view showing an example of a dynamic balance adjuster.

FIG. 4 is a plan view of an adjusted body showing an example of balance adjustment by a dynamic balance adjuster.

FIG. 5 is a partial perspective view of an adjusted body showing an example of balance adjustment by a dynamic balance adjuster.

FIG. 6 is a plan view of an adjusted body showing another example of balance adjustment by a dynamic balance adjuster.

[Explanation of symbols]

1 Drive board part P DUT P1 reference position mark 2 Vibration detection plate 3, 4, 5, 6 leaf spring 7, 8 Body fixing part 9, 10 Vibration sensor 13 Rotational phase sensor 14, 35 Control device 15 Operation panel 21, 22 Detected part 101 Measured object mounting means 102 core shaft 103 Lower thrust bearing 105 radial bearing 107 colors 109 Upper thrust bearing 114 Driven part 116 polygon mirror 117 fixing member 119 Tightening screw 120 motor 121 Dynamic pressure generating groove 124 Stator coil 125 magnet 30 Adjustable body rotating part 31 Detaching means 32 Weighted distribution part 33 Weighting means 33a nozzle 34 means of transportation 36 Reference mark sensor

─────────────────────────────────────────────────── ─── Continuation of front page (58) Fields surveyed (Int.Cl. ⁷ , DB name) G01M 1/38 G01M 1/16 G01M 1/32 G02B 26/10 102

Claims (3)

(57) [Claims] 1. A drive substrate part on which an object to be measured is detachably mounted and rotated, and a lower part of the drive substrate part which is integrally provided in a suspended state to generate vibration in a direction perpendicular to the center line of rotation. A vibration detecting plate portion having a detected portion for detecting,
A leaf spring at right angles to the vibration direction that connects the vibration detection plate portion and left and right body fixing portions at right angles to the vibration direction at two vertically separated locations, and a vibration that detects the vibration of the detected portion. A sensor, a rotational phase sensor for detecting the rotational phase of the object to be measured, and an arithmetic means for calculating information about the unbalanced amount of the object to be measured and its phase angle based on the output information of the rotational phase sensor and the vibration sensor. A dynamic balance measuring machine characterized by being equipped. 2. The vibration detection plate portion has the detected portions at two upper and lower positions, and the vibration sensors are provided for the two detected portions, respectively, and the arithmetic means is an arbitrary measured object. The dynamic balance measuring machine according to claim 1, wherein the information regarding the unbalance amount of the portion and the phase angle thereof can be calculated. 3. A radial bearing in which the object to be measured is a polygon mirror unit and includes a magnet that receives a rotational force from a stator coil of the drive substrate section, and a means for mounting the object to be measured is a vertical radial bearing, and the radial bearing. The dynamic balance measuring machine according to claim 1 or 2, wherein a polygon mirror mounted with thrust bearings provided on the upper and lower end sides or the lower end side is rotatably supported by dynamic pressure bearings.