Electromagnetic rotary vibration for rotary body and damper using the same rotary body

Abstract: An apparatus for electromagnetically and rotationally vibrating a rotary body supported by bearings. The apparatus comprises a ring-shaped magnet (10) bipolarly magnetized and mounted on a shaft (18) of the rotary body coaxially, a ring-shaped stator (12) having a coil and adapted to generate a rotating magnetic field by controlling an electric current supplied to the coil, and a frequency-variable vibration power source (14) adapted to supply alternating electric power to the coil in the stator. The magnet and the stator have different magnetic radii and are disposed so as to be opposed to each other in a direction identical with the magnetization direction of the magnet. Thus the rotational exciting force is applied to the rotary body by an interaction of the rotating magnet field generated by the stator with the magnet. This electro-magnetic rotary vibrator can be applied to a damper for offsetting the unbalanced vibration of a rotary body.

Description: This invention relates to the techniques for electromagnetically and rotationally vibrating a rotary body supported by bearings, and more particularly to an electromagnetic rotary vibrator for a rotary body, adapted to apply a rotational exciting force to the rotary body by a bipolarly magnetized ring-shaped magnet and a ring-shaped stator adapted to generate a rotating magnetic field by controlling an electric current supplied to a coil; and a damper for a rotary body which uses such a vibrator. A rotary machine has a critical speed at which a vibration amplitude increases suddenly when a revolution velocity thereof increases to coincide with a natural frequency. A rotary body used without having it pass a critical speed is subjected to a test for the purpose of minimizing a vibration amplitude generated by the influence of such a use, thereby evaluating the balance of the vibration of the rotary body and carrying out a suitable balancing operation. Especially, the rotary machines (first-order passing type to N-th order passing type) adapted to pass critical speeds to reach a rated revolution velocity are subjected to tests so as to pass the critical speeds, in the same manner as the above-mentioned rotary body, and a suitable balancing operation is carried out; otherwise a rated revolution velocity cannot be attained. A balancing operation for a rotary body is necessarily carried out in this manner. According to the conventional balancing techniques, a rotary body is installed in a practical rotary machine, and unbalanced vibration is measured with the rotary machine operated. On the basis of the result of measurement, a balance weight is attached to the rotary body, or conversely, the rotary body is shaved, whereby the vibration of the rotary body is suppressed. In an actual rotation test, the determining of vibration amplitude and the calculating and correcting of balance have to be done at each critical speed. Namely, very complicated operations requiring much labor and time have to be carried out. In recent years, a displacement feedback control method using a controlling type magnetic bearing has been studies as one method of solving these problems. A controlling type magnetic bearing is originally adapted to apply a force to a rotary shaft so that the rotary shaft is retained constantly in a neutral position in the same bearing. In a damping operation using this controlling type magnetic bearing, an exciting force offsetting an unbalanced vibration of a rotary body and synchronous with the rotation thereof is applied in a superposed manner to the controlling type magnetic bearing to suppress the vibration and have the vibration to pass critical speeds, whereby the balance evaluation is carried out. Such a method is disclosed in, for example, Japanese Patent Laid-Open Specification No. 4-351348/1992. A controlling type magnetic bearing is basically adapted to attract a rotary shaft of a magnetic substance to electromagnetic actuators and retain the same in a neutral position in the bearing. The electromagnetic actuators, the attractive force of two poles of which acts on one position, are used by arranging them in four directions of XY plane (a plane perpendicular to a direction Z in which the rotary shaft extends). In order to generate a rotating magnetic field for applying a exciting force to a rotary body, rotational synchronous single-phase electric power of sine and cosine waves is generated by using a personal computer-controlled DSP (digital signal processor) or a tracking filter circuit, and the thus generated rotational synchronous single-phase electric power is superposed to the neutral position retaining-electric power of the electromagnetic actuators arranged in the XY plane. However, since the controlling type magnetic bearings are originally adapted to apply a force to and control a rotary shaft so that the rotary shaft is retained constantly in a neutral position in the bearings as mentioned above, an exciting force offsetting unbalanced vibration and synchronous with the rotation of the rotary body constitutes disturbance to the magnetic bearings and causes the action of the bearings to become unstable. Namely, an exciting force due to the effect of the attractive rotating magnetic field of the controlling type magnetic bearings is generated for obtaining a spring effect by displacement feedback and a damping effect by speed feedback, and the original function of the controlling type magnetic bearings work so as to offset this disturbance (exciting force). Therefore, a specially difficult control operation is required. The function of the electromagnetic actuators attracting the rotary shaft of the magnetic substance and arranged in four directions of XY plane works only solely at an instant, and does not work with full power, so that an exciting force is small. This causes the dimensions of the electromagnetic actuators to increase. Regarding a control operation, problems such as a feedback delay occur. Although the electromagnetic actuators basically work so as to attract the rotary body, an unnecessary rotational force also occurs, and this causes whirling (self-excited vibration). Moreover, in view of the DSP response characteristics, the attainment of a high revolution velocity and the passage of a high-order critical speed are difficult. US-A-4806835 discloses an electromagnetic device which comprises at least one compensation ring placed in the vicinity of the fluid bearing and mounted relative to the rotor by means of an active radial magnetic bearing whose electromagnet windings are powered as a function firstly of the signals delivered by a position detector for detecting the position of the compensation ring relative to the rotor, and secondly of the signals delivered by at least two vibration detectors disposed on the casing of the machine and having non-parallel sensitivity axes which are perpendicular to the axis of the rotor. The signals delivered by the vibration detectors are applied to a high-gain narrow-band selective feedback circuit whose central frequency is synchronized with a reference frequency fo. The compensation ring is of relatively small mass and serves to exert a rotary compensation force on the rotor via the radial magnetic bearing, which force is equal to the centrifugal force due to the out-of-balance mass of the rotor but which is 180° out of phase relative thereto, thereby reducing casing vibration while expending little energy. An object of the present invention is to provide an apparatus capable of electromagnetically applying a rotational exciting force of an arbitrary frequency to a rotary body efficiently. Another object of the present invention is to provide a damper for a rotary body, adapted to offset the unbalanced vibration of the rotary body by electromagnetically applying vibration of an amplitude equal to that of the unbalanced vibration and of a phase opposite to that thereof to the rotary body. According to the present invention, there is provided an apparatus for electromagnetically and rotationally vibrating a rotary body supported by bearings, comprising a ring-shaped magnet bipolarly magnetized and mounted on a shaft of said rotary body coaxially, a ring-shaped stator having a coil and adapted to generate a magnetic field rotating about the axis of the shaft by controlling an electric current supplied to said coil, and a frequency-variable vibration power source adapted to supply alternating electric power to said coil in said stator, the distances between the axis of the shaft and the position in which a magnetic pole is formed in said magnet and said stator being different so that said magnet and said stator have different magnetic radii, and said magnet and said stator being disposed so as to be geometrically opposed to each other in a direction identical with the magnetization direction of said magnet to thereby apply the rotational exciting force to said rotary body by an interaction of the rotating magnetic field generated by said stator with said magnet. The ring-shaped magnet may be mounted directly on the rotary shaft, or on a static portion of a bearing mounted on the rotary shaft. The magnet is preferably a permanent magnet, and may be an electromagnet. For example, there is a structure in which an axially bipolarly magnetized permanent magnet constituting the ring-shaped magnet, and a stator are disposed so that the magnet and the stator are axially opposed to each other. Such a structure may also be employed that has a radially bipolarly magnetized permanent magnet constituting the ring-shaped magnet, and a stator which are disposed so as to be opposed to each other radially in the same plane. According to the present invention, there is also provided a damper using the above-described electromagnetic rotary vibrator for a rotary body and adapted to offset unbalanced vibration of the rotary body supported by bearings. This damper comprises an electromagnetic rotary vibrator provided with a ring-shaped magnet bipolarly magnetized and mounted on a shaft of the rotary body coaxially, and a ring-shaped stator having a coil and adapted to generate a rotating magnetic field by controlling an electric current supplied to the coil, the magnet and the stator having different magnetic radii and being disposed so as to be opposed to each other in a direction identical with the magnetization direction of the magnet to thereby apply the rotational exciting force to the rotary body by an interaction of the rotating magnetic field generated by the stator with the magnet; a meter provided with a rotation sensor for detecting a revolution velocity of the rotary body; and a damping power source adapted to generate a sine wave signal of a frequency synchronous with the rotation of the rotary body by an output pulse from the rotation sensor and supply a driving output, which is obtained by controlling the phase and amplitude of the sine wave signal, to the coil of the stator. Thus vibration of a phase opposite to that of unbalanced vibration of the rotary body and of an amplitude substantially equal to that of the unbalanced vibration thereof is generated by the electromagnetic rotary vibrator. In this damper for a rotary body, the meter is preferably provided, in addition to the rotation sensor for detecting a revolution velocity of the rotary body, with a vibration sensor for detecting the vibration of the rotary body, and a measuring instrument for determining the phase and amplitude of the vibration on the basis of outputs from the two sensors. The damping power source is provided with a phase synchronizing loop adapted to generate a signal of a frequency synchronous with the rotation of the rotary body by an output pulse from the rotation sensor, a sine ROM storing sine wave data therein, a D/A converter adapted to carry out D/A conversion on the basis of the sine wave data read from the sine ROM, and a phase-voltage controller adapted to control the sine wave data, which are outputted from the sine ROM, in such a manner that the phase of the sine wave data becomes opposite to that of the unbalanced vibration of the rotary body obtained from the measuring instrument, and control an output from the D/A converter in such a manner that the amplitude of the output from the D/A converter substantially corresponds to that of the unbalanced vibration of the rotary body. In the electromagnetic vibrator for a rotary body, the magnet and the stator have different magnetic radii and are disposed so as to be opposed to each other in a direction identical with the magnetization direction of the magnet, so that a resultant force based on the interaction, i.e. repulsion and attraction of the magnetic field generated by the stator and the magnet, is exerted in a plane perpendicular to the axial direction of the rotary shaft. This resultant force rotates in accordance with the rotating magnetic field generated by the stator. Consequently, the rotational exciting force is exerted on the rotary body. The rotational exciting force can be controlled freely on the basis of the value, frequency and phase of the alternating current supplied to the stator. When vibration having a phase opposite to that of the unbalanced vibration of the rotary body and an amplitude substantially equal to the unbalanced vibration is applied electromagnetically to the rotary body, the unbalanced vibration is offset. For example, a typical example is shown schematically in Figs. 1 and 2. When an electromagnetic vibrational response shown by a broken line is applied to an unbalanced vibrational response shown by a solid line in a simple harmonic vibration waveform on a time axis in Fig. 1, a synthesized waveform of the solid line and broken line constitutes an offset waveform. Fig. 2 is a Nyquist diagram representative of what is shown in Fig. 1, and indicates that a synthesized vibrational response in which an unbalanced vibrational response and an electmagnetic vibrational response the phase of which is opposite to that of the unbalanced vibrational response are combined offsets these unbalanced vibration and electromagnetic vibration each other. The passage of an N-order critical speed can be carried out by practicing the above-described operation each time the rotary body passes a critical speed. Fig. 1 is an explanatory drawing showing a vibration waveform in the vicinity of a critical speed. Fig. 2 is an explanatory drawing showing an example of a Nyquist diagram in the vicinity of a critical speed. Fig. 3 is a schematic explanatory drawing showing an embodiment of the electromagnetic rotary vibrator according to the present invention. Fig. 4 is an explanatory drawing showing another embodiment of the electromagnetic rotary vibrator according to the present invention. Fig. 5 is an explanatory drawing showing still another embodiment of the electromagnetic rotary vibrator according to the present invention. Fig. 6 is a schematic block diagram showing an embodiment of the damper according to the present invention. Fig. 7 is an explanatory drawing showing an example of vibration spectra before and after a vibration offsetting operation. Fig. 3 is a basic construction diagram showing an embodiment of an electromagnetic rotary vibrator for a rotary body according to the present invention. This apparatus is adapted to apply a rotational exciting force to an arbitrary rotary body supported rotatably by a passive bearing (not shown), and comprises a ring-shaped permanent magnet 10, a ring-shaped stator 12 having a coil and a vibration power source 14. The permanent magnet 10 is axially bipolarly magnetized in the axicial direction, and mounted on the rotary body 16 (a shaft 18 of the rotary body in this embodiment) coaxially. The stator 12 may have the same construction as a regular induction motor, and is adapted to generate a substantially bipolar rotating magnetic field with an electric current supplied to the coil thereof and controlled properly. The permanent magnet 10 and the stator 12 have different magnetic radii (distance between a position in which a magnetic pole is formed and the axis of the rotary body shaft 18, the magnetic radii of the permanent magnet and the stator being represented by symbols R 1 , R 2 respectively), and are disposed so as to be opposed to each other in the axial direction. The vibration power source 14 is a frequency-variable inverter for supplying an alternating electric power to the coil of the stator 12. In the rotary vibrator structure of Fig. 3, the ring-shaped permanent magnet 10 is magnetized so that, for example, the upper and lower surfaces thereof have an N-pole and an S-pole respectively. Assume that an S- pole and an N-pole occur at a certain instant in the right and left side portions respectively in the drawing of the stator 12 due to a current supplied to the coil. Consequently, a left-upward electromagnetic force due to the repulsive force of the S-poles occurs in the right side portion in the drawing, while a left-downward electromagnetic force due to an attractive force between the N- and S-poles occurs in the left side portion in the drawing. If they are synthesized, the components in the axial direction of the permanent magnet 10 are in opposite directions and are therefore offset each other but the components F 1 , F 2 in the direction (in a horizontal plane in the drawing) perpendicular to the axial direction are in the same direction and are therefore summed up to turn into an eccentric force. The direction of a magnetic field occurring in the stator 12 changes circularly in accordance with the frequency of the alternating electric power supplied from the vibration power source 14, so that the direction of an electromagnetic eccentric force supplied to the permanent magnet 10 also changes circularly. This eccentric force can be controlled on the basis of the frequency and value of the alternating current supplied to the stator 12. Namely, owing to the interaction of the rotating magnetic field generated in the stator 12 with the permanent magnet 10, a desired level of rotational exciting force can be applied to the rotary body 16, and an electric input generates a high-quality exciting force of a rotational vibration vector. The inverter used as the vibration power source 14 is generally set to be rectangular wave voltage-frequency variable by temporarily turning the commercial electric current into a direct current, and carrying out the positive-negative voltage switching in accordance with the frequency. Such a rectangular wave inverter is commercially available and can be obtained easily at a low price. The waveform of the vibrating AC power may be a sine waveform in addition to a rectangular waveform. However, a sine wave inverter is expensive and not general. It is considered that the above-described rotary vibrator for a rotary body according to the present invention is an optimum embodiment but a structure for applying a rotational exciting force to a rotary body is not limited to the embodiment. Although a permanent magnet is used as the ring-shaped magnet in the above embodiment, it may be replaced by an electromagnet. In this case, a structure having a winding around a magnetic core (not shown) may be mounted on the shaft of the rotary body by supplying an electric current to'the winding via a brush as used in a conventional DC motor. It is also possible that a magnet and a stator be disposed in the same plane. An example of such an arrangement is shown in Fig. 4. A ring-shaped permanent magnet 20 is radially bipolarly magnetized (the outer circumferential surface has an S-pole, and the inner circumferential surface an N-pole) and mounted on a rotary body 21. The rotary body 21 is rotatably supported by a bearing 22. A stator 23 is ring-shaped, and adapted to generate a rotating magnetic field with an electric current, which is supplied to a coil and controlled properly. The permanent magnet 20 and stator 23 are disposed in the same plane so as to be opposed to each other in the radial direction (i.e., the permanent magnet 20 is positioned on the inner side of the stator 23). If a magnetic field generated by the stator in this structure at a certain instant is in the condition, for example, as shown in Fig. 4, an attractive force of different poles occurs in a left portion of the rotary body 21, while a repulsive force of the same poles occurs in a right portion of the rotary body. Consequently, a leftward force is exerted on the rotary body 21. Since this force rotates with the rotating magnetic field generated by the stator 23, the rotary body 21 receives a rotational exciting force. Although the magnet is mounted directly on the rotary body in both of the above-described examples as shown in Figs. 3 and 4, it may be mounted via a bearing. Such an example is shown in Fig. 5. A ball bearing 26 is mounted on a rotary body 25, and a ring-shaped permanent magnet 27 on a static portion of the bearing 26. In this example, the permanent magnet is axially bipolarly magnetized just as the permanent magnet shown in Fig. 3. A ring-shaped stator 28 is disposed so as to be opposed axially to the permanent magnet 27. Such an arrangement of the magnet mounted via a bearing has the advantage that the magnet does not receive rotational stress, so that an electromagnet is easily installed. However, since a load is imparted to the bearing, it is necessary that consideration be given to the prevention of the seizure of the bearing. There is a damper for a rotary body as one of applied examples of the above-described electromagnetic rotary vibrator for a rotary body. An example of schematic construction of the damper is shown in Fig. 6. A rotary body 30 to which the damper is applied is supported in a horizontal plane (XY directions) by upper and lower bearings 32, 34 each of which has a spring and a damping member, and in a vertical plane (Z direction) by a thrust bearing 36 also having a spring and a damping member. The rotary body 30 further has a driving motor 42 comprising a permanent magnet 38 and a stator 40, and is rotated at a desired speed by supplying an electric current from driving inverter 44 to the stator 40. The damper for the rotary body according to the present invention is provided with an electromagnetic rotary vibrator 46, a meter 48 and a damping power source 50, and formed so as to offset the unbalanced vibration of the rotary body by generating by the electromagnetic rotary vibrator vibration the phase of which is opposite to that of the unbalanced vibration of the rotary body, and the amplitude of which is substantially equal to that thereof. The construction of the electromagnetic rotary vibrator 46 may be basically identical with that of the rotary vibrator shown in Fig. 3, and is provided with a ring-shaped permanent magnet axially and bipolarly magnetized and mounted on a shaft 52 of the rotary body, and a ring-shaped stator 62 having a coil and adapted to generate a rotating magnetic field with an electric current supplied to the coil thereof and controlled properly. The permanent magnet 60 and the stator 62 have different magnetic radii, and are disposed so as to be opposed to each other axially. A rotational exciting force is applied to the rotary body by an interaction of the rotating magnetic field generated by the stator with the permanent magnet. The meter 48 is provided with a rotation sensor 70 for detecting a revolution velocity of the rotary body, a vibration sensor 72 for detecting the vibration of the rotary body, and a measuring instrument 74, such as an oscilloscope or a FFT (high-speed Fourier transformer) adapted to determine the phase and amplitude of vibration on the basis of outputs from these two sensors 70, 72. The damping power source 50 generates a sine wave signal of a frequency synchronous with the rotation of the rotary body by an output pulse from the rotation sensor 70, and supply a driving output, which is obtained by controlling the phase and amplitude of the mentioned signal, to the coil of the stator 62 in the electromagnetic rotary vibrator 46. The damping power source in this embodiment is provided with a phase synchronizing loop (PLL) 80 adapted to generate a signal of a frequency synchronous with the rotation of the rotary body by an output pulse from the rotation sensor 70, a sine ROM 82 storing sine wave data therein, a D/A converter 84 adapted to carry out D/A conversion in accordance with the sine wave data read out from the sine ROM 82, and a phase-voltage controller 86 adapted to control the sine wave data outputted from the sine ROM 86, in such a manner that the phase of the sine wave data becomes opposite to that of the unbalanced vibration of the rotary body obtained from the measuring instrument 74, and control an output from the D/A converter 74 in such a manner that the amplitude of the output from the D/A converter substantially corresponds to that of the unbalanced vibration of the rotary body. The phase-voltage controller 86 controls the D/A converter 84 on the basis of a signal synchronous with the rotation of the rotary body and obtained from the phase synchronizing loop 80 and a vibrational response which can be determined by the measuring instrument 74. In this damper, the vibration condition is grasped by the measuring instrument 48, and a damping force corresponding to the unbalanced vibration of the rotary body is outputted from the electromagnetic rotary vibrator 46 on the basis of the power from the damping power source 50, whereby the damping of the rotary body is done. This damper is of a closed loop control system, and can also be applied to a damper of an open loop control system. The vibration of the rotary body is grasped by measuring the same with the measuring instrument. The damping of the rotary body can be done by controlling the phase and voltage manually by the phase-voltage controller on the basis of the measured vibration. As long as the whole of the vibration of the rotary body has been grasped in advance, the damping operation can be carried out by program-controlling the phase-voltage controller even when a damper which does not have a meter is used. The outline of the results of application of this kind of damper to a fourth-order flexural critical speed passing type rotary body is schematically shown in Fig. 7. In the damper used in an experiment, a manual control operation of an open loop control system was carried out in a stepped manner for the convenience' sake. Fig. 7A shows the outline of a vibration spectrum before the offsetting of vibration, and Fig. 7B the outline of a vibration spectrum after the offsetting of vibration. It is understood that the vibration is damped to a level not higher than an allowable limit of vibration with respect to the first order flexural critical speed a to the fourth order flexural critical speed d by a very simple damper controlling operation. The electromagnetic rotary vibrator for a rotary body according to the present invention can be not only applied to such a damper but also used as a rotation balancer in which the amount of unbalanced vibration is calculated and the balancing of vibration is then done by a modal method based on the conventional techniques. The electromagnetic rotary vibrator can also be applied to the vibration evaluation in a rotating field (for example, the evaluation of bearing yield strength or critical speed variation in a rotating field). In a conventional method of evaluating the yield strength of a bearing, unbalanced vibration is applied as a test weight to a rotary body, the amount thereof is increased gradually, and a rotation test is conducted each time. Therefore, the number of conducting rotation tests increases, and many process steps are required. When a rotary body is rotationally vibrated by using the electromagnetic rotary vibrator according to the present invention, the vibration amplitude can be increased at each critical speed, i.e., a vibrational response can be attained arbitrarily. This enables a load imparting parameter to be set by one rotation test under high-quality conditions based on the imparting of a dynamic load under the limit conditions of use of a bearing, and the yield strength of the bearing to be efficiently evaluated. When the electromagnetic rotary vibrator according to the present invention is used in a rotating field, the variation of resonance point in accordance with an increase in the revolution velocity of a rotary body can be detected, and the results of the detection can be reflected upon the evaluation of the structure designing of the rotary body. The waveform of the vibrating alternating electric power supplied from the vibrating-damping power source may be a rectangular waveform or a sine waveform as mentioned above. The vibration evaluation is carried out for obtaining a vibrational response. Accordingly, the level of an input may be low, and the waveform thereof may be a rectangular waveform since data are picked up in an arbitrary frequency band. However, especially when the alternating electric power is applied to a damping operation, it is desirable that the electric power has a sine waveform of a single frequency. Vibrating a rotary body with alternating electric power having a rectangular waveform becomes a complex vibrating operation of a basic frequency and an odd number-multiplied frequency (vibrating a rotary body with alternating electric power having a waveform other than a sine waveform becomes a vibrating operation similar to this vibrating operation), so that, when a critical speed exists in an odd number-multiplied frequency during a vibrating operation with a target basis frequency, a vibrational response is made. When an inverter of a rectangular waveform is used, voltage of odd number-multiplied frequencies become smaller in the order of the multiples, and the levels of exciting force become inversely proportional to the frequency, so that a vibrational response is small. However, it should be noted that a region in which the basic frequency is swept becomes wide. Conversely, if these characteristics are utilized, a vibrating operation in a high frequency region can be carried out. The vibrating-damping power source is not limited to only the structure shown in Fig. 6. Besides the above-described method of converting an output from a rotary body, there is a method in which a vibration waveform is amplified by an amplifier through a synchronizing filter and a phase converter. The methods of vibrating a rotary body on the basis of a vibration-pulse output include (1) a DSP vibrating method using a host personal computer, (2) a vibrating method using an oscillator operated synchronously with a trigger, and (3) a vibrating method using an inverter controlled by a personal computer. Rotating magnetic field power can be obtained by an arbitrary method out of such methods as described above. In these methods, it is necessary that the function of regulating the phase and the amount of electric power of a rotating magnetic field is provided. The above description is of a case where the rotary body makes a vibrational response independently at each critical speed as shown in Figs, 1 and 2. However, depending upon a structure of a rotary body, there is a case in which a plurality of critical speeds approach, so that the rotary body vibrates in a coupled manner at the same revolution velocity. When a rotary body makes such a coupled vibrational response, it is difficult to carry out an excellent damping operation by a single electromagnetic rotary vibrator. In such a case, by providing electromagnetic rotary vibrators in a plurality of arbitrary places and by carrying out control operations separately, an excellent damping operation can be accomplished. As described above, the present invention is of a system in which a rotary body is directly vibrated, and capable of applying a high-quality rotational exciting force of an arbitrary frequency to the rotary body electromagnetically and efficiently. Therefore, the present invention can be used as a rotation balancer for calculating the amount of unbalanced vibration and balancing the vibration by a modal method based on the conventional techniques. The present invention is also capable of setting a load imparting parameter by one rotation test, and being utilized as an efficient method of evaluating the yield strength of a bearing. It is further possible to grasp the variation of a resonance point occurring in accordance with an increase in the revolution velocity of a rotary body, and reflect the results upon the designing and evaluating of the construction of a rotary body. Since the present invention is formed so that vibration having an amplitude equal to that of the unbalanced vibration of a rotary body and a phase opposite to that thereof is applied electromagnetically to the rotary body, it is possible to damp the vibration by offsetting the unbalanced vibration of the rotary body without substantially requiring a control operation. The performance of this apparatus up to the stage of the passage of the existing fourth order flexural critical speed has already been proven excellent. This apparatus can also be applied to an N-order critical speed passing type rotary body having increased critical speed, and is very effective for an elastic rotary body which is rotated at a high speed. This damper apparatus can also sufficiently deal with transitional vibration and unreproducible vibration, such as thermal unbalance due to a temperature rise during the rotation of a rotary body, deformation unbalance due to rotational stress and fluid unbalance.

Claims: An apparatus for electromagnetically and rotationally vibrating a rotary body supported by bearings, comprising a ring-shaped magnet (10) bipolarly magnetized and mounted on a shaft (18) of said rotary body coaxially, a ring-shaped stator (12) having a coil and adapted to generate a magnetic field rotating about the axis of the shaft by controlling an electric current supplied to said coil, and a frequency-variable vibration power source (14) adapted to supply alternating electric power to said coil in said stator, the distances between the axis of the shaft (18) and the position in which a magnetic pole is formed in said magnet and said stator being different so that said magnet (10) and said stator (12) have different magnetic radii, and said magnet (10) and said stator (12) being disposed so as to be geometrically opposed to each other in a direction identical with the magnetization direction of said magnet to thereby apply the rotational exciting force to said rotary body by an interaction of the rotating magnetic field generated by said stator with said magnet. An apparatus for electromagnetically and rotationally vibrating a rotary body according to claim 1, wherein said ring-shaped magnet (10) is a permanent magnet bipolarly magnetized in the axial direction, said permanent magnet (10) and said stator (12) being disposed so as to be geometrically opposed to each other in the axial direction. An apparatus for electromagnetically and rotationally vibrating a rotary body according to claim 1, wherein said ring-shaped magnet (20) is a permanent magnet bipolarly magnetized in the radial direction, said permanent magnet (20) and said stator (23) being disposed so as to be geometrically opposed to each other radially in the same plane. An apparatus for electromagnetically and rotationally vibrating a rotary body according to claim 1, wherein a bearing (26) having a static portion is mounted on said shaft of said rotary body, said ring-shaped magnet (27) being mounted on said static portion of said bearing (26). A damper for a rotary body adapted to offset unbalanced vibration of a rotary body supported by bearings, comprising: an apparatus for electromagnetically and rocationally vibrating a rotary body according to claim 1, a meter (48) provided with a rotation sensor (70) for detecting a revolution velocity of said rotary body, and a dampening power source (50) adapted to generate a sine wave signal of a frequency synchronous with the rotation of said rotary body by an output pulse from said rotation sensor, and to supply a driving output, which is obtained by controlling the phase and amplitude of said sine wave signal, to said coil of said stator, whereby a vibration of a phase opposite to that of an unbalanced vibration of said rotary body and of an amplitude substantially equal to that of the unbalanced vibration thereof can be generated by said electromagnetic rotary vibrator. A damper for a rotary body according to claim 5, wherein said meter (48) is provided, in addition to said rotation sensor (70) for detecting a revolution velocity of said rotary body, with a vibration sensor (72) for detecting the vibration of said rotary body, and a measuring instrument (74) for determining the phase and amplitude of the vibration on the basis of outputs from said two sensors, said dampening power source (50) being provided with a phase synchronizing loop (80) adapted to generate a signal of a frequency synchronous with the rotation of said rotary body by an output pulse from said rotation sensor, a sine ROM (82) storing sine wave data therein, a D/A converter (84) adapted to carry out D/A conversion on the basis of the sine wave data read out from said sine ROM, and a phase-voltage controller (86) adapted to control the sine wave data, which are outputted from said sine ROM, in such a manner that the phase of said sine wave data becomes opposite to that of the unbalanced vibration of said rotary body obtained from said measuring instrument, and control an output from said D/A converter in such a manner that the amplitude of said output from said D/A converter substantially corresponds to that of the unbalanced vibration of said rotary body.

Inventors: GUNJI KIYOSHI, KIKUCHI KIYOTAKA, GUNJI, KIYOSHI, KIKUCHI, KIYOTAKA, Gunji, Kiyoshi 2556, Narita-cho, Kikuchi, Kiyotaka 1700-1, Shirakata
Applicants: JAPAN NUCLEAR CYCLE DEV INST, JAPAN NUCLEAR CYCLE DEVELOPMENT INSTITUTE
Application year: 1996
Main classification: G01M1
IPC codes: F16F15, H02K7, G05D19, F16C32, G01M7, G01M1