JPH0577254B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to an unbalance detection device for a rotating body, and more particularly to an unbalance detection device for a rotating body that can shorten the detection time of an unbalance in a rotating body.

<Prior art> There have been various unbalance correcting devices for rotating bodies. For example, Japanese Patent Application Laid-Open No. 132641/1983 discloses a method for positioning an unbalanced position of a rotating body at low cost and with high precision. A possible device is disclosed.

In this device, both shaft ends of the rotating body are rotatably supported by a pair of pivot parts having V-shaped grooves, but the pivot parts are orthogonal to the axial direction of the rotating body. They are each elastically supported via leaf springs so that they can reciprocate. Further, a displacement sensor is connected to the pivot part to detect its displacement, and a rotation angle sensor is connected to the rotating body, so that when the rotating body is rotated, there is a possibility that the rotating body is unbalanced. In this case, the rotating body vibrates as it rotates, and the pivot also vibrates, so both sensors can detect the unbalanced position.

However, if the rotational speed at the time of unbalance detection is higher than the natural frequency of the pivot, large vibrations will occur due to resonance when the rotation of the rotating body exceeds the natural frequency of the pivot. Therefore, after the natural frequency is exceeded and the steady rotational speed is reached at the time of unbalance detection, it takes a relatively long time for the vibration due to resonance to subside, resulting in a problem that the unbalance detection time becomes longer. .

<Problems to be Solved by the Invention> In view of the problems of the prior art, the main object of the present invention is to rotate a rotating body at a rotation frequency exceeding the natural frequency of the pivot part, It is an object of the present invention to provide an unbalance detection device for a rotating body that can shorten the detection time even when detecting unbalance of a body.

<Means for Solving the Problems> According to the present invention, the present invention provides a pivot part that rotatably supports both ends of a rotating body in the axial direction, and a support that supports the pivot part so that it can freely reciprocate. An unbalance detection device for a rotating body having a rotary member configured to generate a magnetic force between a magnet fixed to the pivot portion and the magnet in a direction to restore the pivot portion to a neutral position. A magnet coil is fixedly installed on the supporting portion side so as to face the magnet, and the magnet coil is energized so as to generate a relatively large magnetic force when the rotation speed of the rotating body is low. By providing an unbalance detection device for a rotating body, characterized in that the excitation current is supplied to the magnet coil so as to generate a smaller magnetic force when the rotational speed is high. achieved.

<Function> By doing this, when the rotational speed of the rotating body is low, a large magnetic force is generated in the direction of restoring the pivot to the neutral position with respect to the reciprocating movement of the pivot, thereby increasing the rigidity of the pivot. This is equivalent to the state in which the natural frequency of the pivot point is shifted to a high frequency range. Furthermore, since a relatively small magnetic force is generated when the rotational speed is high, this is equivalent to lowering the rigidity of the pivot, and the natural frequency of the pivot is shifted to a low frequency range. Therefore, when the rotational speed of the rotating body increases, the natural frequency of the pivot portion moves in the opposite direction to the direction in which the rotational speed increases, so it is possible to prevent the pivot portion from resonating significantly.

<Examples> Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

1 and 2 are a front view and a side view showing an unbalance correcting device for a rotating body according to the present invention. As clearly shown in FIGS. 1 and 2, an upper frame 2 is disposed above a lower frame 1 fixed to a foundation (not shown), and an upper frame 2 is provided between the frames 1 and 2. Interposed wall member 3
The upper frame 2 is fixed by the columnar members 4.

The upper frame 2 has a reciprocating cylinder 5,
A slide shaft 8 is supported via a rubber mount 6, is provided to stand upright on the upper frame 2, and is coaxially fixed to the piston of the cylinder 5.
is supported by a slide bearing 9 so as to be slidable in the vertical direction, and extends downward from the upper frame 2 . Further, a bracket 11 is fixed to the lower end of the slide shaft 8, and a rail member 12 is fixed to the lower end of the bracket 11 so as to extend in the horizontal direction (left-right direction in FIG. 2). has been done. A pair of prismatic arm members 13 are fixed to the rail member 12 so as to extend parallel to each other at a predetermined interval in the horizontal direction (left and right direction in FIG. 1) perpendicular to the rail member 12. There is.

The free end 14 side of the arm member 13 is formed to be thinner than the proximal end thereof, and a rectangular pipe-shaped slide member 15 is attached to the free end 14 in the axial direction of the free end 14 as shown in FIG. It is fitted so that it can freely reciprocate in the direction of arrow A. Note that compressed air is supplied to the arm member 13 by a compressed air supply means (not shown), and the free end portion 14 and the slide member 15
is formed as an air bearing of a known type, so that the slide member 15 can reciprocate very smoothly.

FIG. 3 is a perspective view showing the appearance of one slide member 15, and as clearly shown in FIGS. 1 to 3, an L-shaped hook 16 is integrally provided on the lower end surface of the slide member 15. It is installed vertically and has 1 hook.
A V-shaped groove 17 is formed at the upper edge of the arm portion at the lower end of the arm. Since the pair of arm members 13 are provided parallel to each other as described above,
The hooks 16 are also arranged in parallel, and as shown in the figure, the shaft 1 of the rotor 18 of the motor as a rotating body is inserted into the V-shaped groove 17 of the pair of hooks 16.
Both ends of 9 are rotatably supported.

A pair of magnets 20 are fixed to the upper end of the slide member 15 at a predetermined distance in the axial direction of the slide member 15. Further, above both magnets 20, there is an annular magnet coil 21.
It is fixed to the plate-shaped bracket 11 described above and to the free end of the extended bracket 22, so as to face both magnets 20. The magnetic force generated by exciting the magnet coil 21
In other words, when the slide member 15 moves in both directions of arrow A, it acts as a restoring force to return the slide member 15 to the neutral position.

Further, an L-shaped bracket 23 is fixed to the upper end surface of the slide member 15, and the arm member 13
An optical displacement sensor 24 is fixed at the base end of the bracket 23 so as to face the L-shaped bracket 23. By this displacement sensor 24, the L-shaped bracket 23
By irradiating light toward the L-shaped bracket 23 and receiving the reflected light from the L-shaped bracket 23, the displacement of the L-shaped bracket 23, that is, the displacement of the slide member 15 (as indicated by the arrow A in the figure)
displacement in both directions). Therefore, rotor 1
It is possible to detect the horizontal runout of both end faces in the axial direction of No. 8 without contact.

In this way, the slide member 15
8 is formed as a pivot support that rotatably supports it. Note that since the cylinder 5 is supported by the rubber mount 6 as described above, this slide member 15 is also supported elastically.
External vibrations transmitted via the frames 1 and 2 are prevented from affecting the slide member 15.

Further, in the bracket 11, the base end of the plate-shaped arm 27 is connected to the first base by a bearing (not shown).
It is rotatably supported in both directions indicated by arrow B in the figure. A swinging actuator 25 is integrally fixed on the left side of the bracket 11 in FIG.
The output shaft of the arm 27 is connected to the base end of the arm 27. Furthermore, the free end of the arm 27 extends toward the upper part of the rotor 18. Therefore, by driving the swinging actuator 25, the arm 2
The free end portion of 7 moves up and down in the direction of arrow B in FIG.

A pair of extensions 31 extend downward from the free end of the arm 27 and are integrally formed so as to sandwich the rotor 18 and face each other. large pulley 32 and small pulley 3
3 are arranged at each proximal end and distal end. Furthermore, an idle pulley 34 is disposed at the intermediate portion of the extending portion 31 on the free end side of the arm 27.
A rubber wire belt 35 is wrapped around each pulley 32-34. Further, a large pulley 32 on the base end side of the arm 27 is coaxially and integrally provided with a drive pulley 36 on the opposite side of the arm 27, and a drive motor 37 is provided on the base end of the arm 27. are integrally fixed, and a drive pulley 36 is rotationally driven by a drive motor 37 via a belt 38. Therefore, the arm 27
8, as shown in FIG. 1 and FIG. The belt 35 contacts the upper part of the outer peripheral surface of the rotor 18. By rotating the drive motor 37 in this state, the rotor 18 will rotate. Further, an encoder 39 is fixed to the free end of the arm 27, and is coaxially and integrally connected to the large pulley 32 on the free end side, and rotates in synchronization with the rotation of the rotor 18. The rotation angle of the rotor 18 can be detected.

In this way, a detection station for detecting unbalance of the rotor 18 is configured, and by driving the cylinder 5 in the vertical direction indicated by arrow D in FIG. 1, the rotor 18 is conveyed in the vertical direction. be done.

Although both arm members 13 are fixed to the rail member 12 as described above, the distance between the two arm members 13 can be adjusted as appropriate within the range of the longitudinal direction of the rail member 12. Since there is no limit to the length of the rotor, it can be applied to various types of rotors.

Further, above the rotor 18 of the upper frame 2, a rotor fixing cylinder 41 is fixedly installed so as to stand vertically, and a U-shaped attachment 42 is attached to the free end of the piston shaft. 1
It is installed vertically towards 8. By driving the rotor fixing cylinder 41, the attachment 4
2 moves up and down in the direction of arrow C in FIG.

The lower end surface of this attachment 42 is the rotor 18
The wire belt 35 is recessed so as not to press the wire belt 35 when the attachment 42 further descends and its lower end surface contacts the outer peripheral surface of the rotor 18. 35
A groove 43 is formed in a portion corresponding to (FIG. 2). By pushing down this attachment 42 toward the rotor 18, the rotor 18 is fixed in a state where it is pivotally supported in the V-shaped groove 17.
At this time, a locking piece 49 fixed to the attachment 42 locks the bracket 11 so that the hook 16 is not damaged by the pressing force of the rotor fixing cylinder 41.
The downward stroke of the attachment 42 is regulated by contact with a stopper 50 provided at the bottom.

A rotor fixing plate 44 is disposed at a predetermined position via a fixing base at a position corresponding to the lower part of the rotor 18 of the lower frame 1. A slot 45 is cut in the. A pair of disc-shaped cutters 46 are disposed within the lower frame 1 so as to face the slot 45 and at a predetermined interval along the slot 45. Both cutters 46 are rotationally driven by motors (not shown) via belts 47, and the cutter supports 48 of both cutters 46 are driven in forward and reverse directions by driving devices (not shown), so that the cutters 46 move in the direction of arrow E in FIG. It reciprocates in the direction indicated by. In this way, a correction station is configured below the rotor 18.

Next, the control in this embodiment will be described below with reference to the block diagram of FIG. The input terminal 51 has
The displacement signal from the displacement sensor 24 described above is input as a sine wave corresponding to the vibration caused by the unbalance of the rotor 18, and the displacement signal from the input terminal 51 is passed through the low-pass filter 52 and is combined with the output voltage of the low-pass filter 52. The deviation from the reference voltage from the input terminal 53 is input to the power amplifier 54, and an output corresponding to the deviation is supplied to the magnet coil 21 via the output terminal 55. Furthermore, rotor 1
When the rotational speed of the rotor 8 is low, the output voltage of the low-pass filter 52 is high and the deviation becomes large, so a relatively large excitation current is supplied to the magnet coil 21, and when the rotational speed of the rotor 18 is high,
Since the output of the low-pass filter 52 becomes lower and the deviation becomes smaller, the low-pass filter 52 is adjusted so that a smaller excitation current than the above is supplied to the magnet coil 21. In this way, the air bearing control section 56 is configured.

Next, the measuring section 69 will be explained below. The displacement signal from the input terminal 51 described above is passed through a bandpass filter 57, an absolute value amplifier 58, an averaging circuit 59, and an A/
The amount of displacement is inputted to the calculation control section 61 via the D converter 60. Further, the output from the band pass filter 57 is inputted to a timing generation circuit 63 via a zero cross detection circuit 62.
The timing generation circuit 63 and the interface circuit 65 exchange signals with each other. Further, a rotation angle signal from the encoder 39 is inputted from an input terminal 64 to the arithmetic control section 61 via an interface circuit 65. Therefore, the arithmetic control section 61 can detect the unbalanced position and amount of unbalance of the rotor 18, and also performs driving stop control of each of the drive devices described above. Further, the timing generation circuit 63 and the rotation instruction circuit 66 exchange signals with each other, and the rotation instruction signal from the rotation instruction circuit 66 is input to the servo amplifier 67, and the output of the servo amplifier 67 is sent to the output terminal 68. The signal is output to the drive motor 37 via.

Next, the operation procedure in this embodiment will be described below. First, the arm 27 is pivoted upward to the upper position indicated by arrow B in FIG. 1, and in this state, the rotor 18 is set on the hook 16 by rotor supply means (not shown). Next, the arm 27 rotates down to the state shown in FIG.
The drive motor 37 is driven to rotate the rotor 18 via the wire belt 38. At this time, if the rotor 18 is unbalanced, the slide member 15 will vibrate in the direction of arrow A in FIG.

In this embodiment, when the rotational speed of the rotor 18 is low, a relatively large excitation current is supplied to the magnet coil 21 as described above, so that a restoring force is generated in the direction of returning the slide member 15 to the neutral position. A large magnetic force is generated. Therefore, this is equivalent to a case where the rigidity of the slide member 15 becomes relatively high, and the natural frequency shifts to a higher frequency. Further, the rotational speed increases to reach a predetermined rotational speed for detecting unbalance, but when the rotational speed is high, a small excitation current is supplied to the magnet coil 21, so that Since a small magnetic force is generated, this is equivalent to a relatively low stiffness, and the natural frequency shifts to a lower frequency. Therefore, when the rotation speed increases,
Since the natural frequency of the slide member 15 quickly moves from the higher side to the lower side, the slide member 15 can be prevented from vibrating greatly without being affected by resonance, and the unbalance can be quickly resolved. It is possible to detect only vibration caused by

In this way, unbalance is detected at high rotational speeds, but at this time the magnetic force is small and it is possible to vibrate even for minute unbalances, so the unbalance can be detected with high precision. can do. In addition, both displacement sensors 24
The unbalance of both end faces of the rotor 18 is measured simultaneously, and the angle signal from the encoder 39 is used to measure the unbalance on both end faces of the rotor 18.
The amount of unbalance and the position of unbalance of the rotor 18 are detected.

After detecting the unbalance, the drive motor 37 is activated by the arithmetic control section 61 so that the unbalance position on one end surface side of the rotor 18 is directed downward.
A control signal is output to rotate the rotor 18 at a slow speed and position it. After the rotor 18 is stopped, the cylinder 5 is driven in a direction to move the rotor 18 downward, in order to transport the rotor 18 from the inspection station to the correction station. At the same time, the rotor fixing cylinder 41 is driven in a direction to lower the attachment 42, and when the rotor 18 comes into contact with the rotor fixing plate 44, the rotor 18 is pressed and fixed downward. In this way, the rotor 18 is fixed in the position shown by the imaginary lines in FIGS. 1 and 2.

Next, the cutter support base 48 is moved so that the cutter 46 cuts the end face on the side where the unbalanced position is directed downward according to the amount of unbalanced position. After the correction of one end surface is completed, the cylinder 5 is driven upward so that the rotor 18 is lifted from the rotor fixing plate 44, and the rotor fixing cylinder 41 is moved in a direction that releases the pressure fixation of the rotor 18. The drive motor 37 is controlled so as to direct the unbalanced position of the other end face downward.
Then, the rotor 18 is attached to the rotor fixing plate 4 again.
4, and modify in the same manner as above.

In this way, after the modification of the rotor 18 is completed, both cylinders 5 and 41 are driven to return the rotor 18 to its initial position, and the arm 27 is then driven.
is rotated upward, and the rotor 18 is moved to another station by a rotor moving device (not shown) to return to the initial state. Furthermore, in the case of this device, when it is confirmed that there is no unbalance after rotating the rotor 18, the rotor 18 can be moved immediately without entering the correction process, so that the rotor 18 can be corrected. Process efficiency can be improved.

If the hook 16 side is damaged due to an operational error when setting or removing the rotor 18 from the hook 16, for example, if a contact type displacement sensor such as a potentiometer type is used as the displacement sensor, the pick-up However, in this embodiment, a non-contact optical displacement sensor 24 is used as the displacement sensor, so that the displacement sensor 24 can be replaced.
Since no undesirable force is applied to the displacement sensor 24, damage to the displacement sensor 24 can be prevented.

<Effects of the Invention> As described above, according to the present invention, when the rotation speed of the rotating body is low, the rotation continues to increase without resonance due to the natural frequency of the pivot part transitioning to a high frequency range. In addition, when the rotational speed is high, the natural frequency shifts to a low frequency range, so there is no resonance even if the rotational speed increases. Therefore, when the steady rotation speed at the time of detection is reached, there is no large vibration due to resonance, so only the vibration due to unbalance can be quickly measured, and the time for detecting unbalance can be shortened. Therefore, the effect is extremely large.

[Brief explanation of the drawing]

FIG. 1 is a front view showing an unbalance correcting device for a rotating body according to the present invention. 2 is a side view of the unbalance correcting device for a rotating body shown in FIG. 1. FIG. FIG. 3 is a perspective view showing the pivot portion of the unbalance correction device for a rotating body. FIG. 4 is a block diagram showing control in this embodiment. 1...Lower frame, 2...Upper frame, 3
... Wall member, 4 ... Column member, 5 ... Cylinder,
6...Rubber mount, 8...Slide shaft, 9...
Slide bearing, 11...Bracket, 12...Rail member, 13...Arm member, 14...Free end portion, 15...Slide member, 16...Hook, 1
7... V-shaped groove, 18... Rotor, 19... Shaft, 2
0...Magnet, 21...Magnetic coil,
22... Bracket, 23... L-shaped bracket, 24... Displacement sensor, 25... Rocking type actuator, 27... Arm, 31... Extension portion, 3
2...Large pulley, 33...Small pulley, 34...Idle pulley, 35...Wire belt, 36...
Drive pulley, 37... Drive motor, 38... Belt, 39... Encoder, 41... Rotor fixing cylinder, 42... Attachment, 43...
Groove, 44...Rotor fixing plate, 45...Slot, 46...Cut, 47...Belt, 48...
... Cutting support base, 49 ... Locking piece, 50 ... Stopper, 51 ... Input terminal, 52 ... Low pass filter, 53 ... Input terminal, 54 ... Power amplifier, 55 ... Output terminal, 56 ... Air bearing control section, 57...Band pass filter, 58...
Absolute value amplifier, 59...Averaging circuit, 60...
A/D converter, 61... Arithmetic control unit, 62...
... Zero cross detection circuit, 63 ... Timing generation circuit, 64 ... Input terminal, 65 ... Interface circuit, 66 ... Rotation instruction circuit, 67 ... Servo amplifier, 68 ... Output terminal, 69 ... Meter side Department.

Claims (1)

[Scope of Claims] 1. An unbalance detection device for a rotating body, comprising a pivot part that rotatably supports both ends of the rotating body in the axial direction, and a support part that supports the pivot part so that it can reciprocate. , a magnet fixed to the support part so as to face the magnet in order to generate a magnetic force between the magnet fixed to the pivot part and the magnet in a direction to restore the pivot part to the neutral position; a magnet coil, and when the rotation speed of the rotating body is low, an excitation current is supplied to the magnet coil so as to generate a relatively large magnetic force, and when the rotation speed is high, the magnet coil is supplied with an excitation current that generates a relatively large magnetic force. An unbalance detection device for a rotating body, characterized in that an excitation current is supplied to the magnet coil so as to generate a small magnetic force.