Abstract:
Provided is a vibration control device, which enables the vibrations of a vibrating body, such as a rotary machine, to automatically be suppressed, without installing a vibration detection sensor on the vibration control device or vibrating body, and without controlling the rotational speed or phase of the vibration control device. The vibration control device ( 1 ), which is installed on a vibrating body ( 2 ) and controls the vibrations of the vibrating body ( 2 ), comprises a rotating shaft ( 11 ), a mass body ( 12 ) that is fixed to the rotating shaft ( 11 ), and an activation apparatus ( 13 ) that adds the power of a rotational motion, which is centered on the rotating shaft ( 11 ), to the mass body ( 12 ).

Description:
TECHNICAL FIELD 
       [0001]    The present invention relates to a vibration control device mounted on a vibrating body and suppressing its vibration and a control method therefor. 
       BACKGROUND ART 
       [0002]    A rotary machine such as a hard disk of a personal computer, an electric fan, a cutting device, and a power generation turbine is preferably designed with its imbalance as small as possible, and careful balancing is performed before shipment. However, since there is a limit to balancing of the rotary machine, an external force of a centrifugal force type is generated during an operation, and vibration occurs. Furthermore, there are also machines which inevitably generate large imbalance during its operation due to its performances as in the case of an electric washing machine and reciprocating machines which inevitably generate vibration to some degree due to its structure as in the case of an engine. In order to suppress vibration of these machines (hereinafter referred to as a vibrating body), an automatic balancer and a vibration compensator are proposed (see Patent Literature 1, for example). 
         [0003]      FIG. 8  illustrates an example of an automatic balancer  1 X. This automatic balancer  1 X has a circumferential passage  30  having the same central axis as that of a rotary machine  32  (a centrifugal separator and the like, for example) and a balance modifier  31  movably arranged in the passage  30 . Here, outline arrows indicate vibration direction Z of the rotary machine  32 . 
         [0004]    Subsequently, an operation of the automatic balancer  1 X will be described. This automatic balancer  1 X can suppress vibration of the rotary machine  32  by passive movement of the balance modifier  31  in the rotating passage  30  and relative standstill in the passage  30  when vibration occurs in the rotary machine  32 . At this time, a position where the balance modifier  31  relatively stands still after it moves in the passage  30  is passively changed depending on an amplitude and a vibration frequency of the rotary machine  32 . 
         [0005]    On the other hand, the vibration compensator has a vibration detection sensor for detecting vibration of a machine such as a diesel engine and the like, a plurality of rotatable mass bodies arranged at appropriate positions in the machine, and a motor for changing a rotational speed or phase of each of the mass bodies. This vibration compensator can suppress vibration of the machine, by detecting vibration of the machine by the vibration detection sensor, by sending a control signal to each of the motors, and by changing the rotational speed or phase of each of the mass bodies. 
         [0006]    However, the above-mentioned automatic balancer and the vibration compensator have some problems. First, the automatic balancer has a problem in which it amplifies an amplitude of the machine in a region with a vibration frequency (frequency) lower than a resonant frequency (or a resonance point). 
         [0007]    Second, the automatic balancer has a problem in which self-excited vibration is generated in a region of a vibration frequency higher than the resonance point. That is, although the automatic balancer has a function of automatically suppressing vibration, the balance modifier and the like cannot be positively controlled, and thus vibration of the machine might be amplified in some cases. 
         [0008]    Third, the vibration compensator requires a precise motor or a complicated control mechanism, and thus has a problem of a high cost. 
       CITATION LIST 
     Patent Literature 
       [0000]    
       
         PTL 1: Japanese Patent Laid-Open No. 2001-304330 
       
     
       SUMMARY OF INVENTION 
     Technical Problem 
       [0010]    The present invention has been made in view of the above-mentioned problems and has an object to provide a vibration control device which can automatically suppress vibration of the vibrating body without installing a vibration detection sensor on a vibrating body such as a rotary machine, a reciprocating machine or the like, or the vibration control device, or without controlling a rotational speed or phase of the vibration control device. Furthermore, an object of the present invention is to provide a low-cost vibration control device. 
       Solution to Problem 
       [0011]    In order to achieve the above-mentioned object, a vibration control device according to the present invention, installed in a vibrating body and controlling vibration of the vibrating body includes a rotating shaft, a mass body fixed to the rotating shaft, and an activation apparatus which adds power of a rotational motion around the rotating shaft to the mass body. 
         [0012]    With this configuration, the vibration control device can automatically suppress vibration of the vibrating body without control of a rotational speed or phase. This vibration control device can automatically suppress vibration of the vibrating body by executing control of adding an initial velocity to the mass body only at start-up. 
         [0013]    In the above-mentioned vibration control device, the vibration control device has at least the two mass bodies which can rotate independently of each other and having a structure in which relative positions of the mass bodies in a rotating direction are automatically adjusted. With this configuration, the mass body of the vibration control device has its relative positional relationship automatically adjusted so as to be optimal for vibration control in accordance with an amplitude amount and frequency characteristics of the vibrating body. As a result, a vibration control performance of the vibration control device is largely enhanced. 
         [0014]    In the above-mentioned vibration control device, the vibration control device has a power assist mechanism for offsetting rotation resistance of the mass body, the power assist mechanism having a power source for adding the power to the rotating shaft or the mass body and a control device, the control device having a reading mechanism for detecting a vibration frequency of the vibrating body, a control map for determining the power the power source should add to the rotating shaft or the mass body from the vibration frequency of the vibrating body and an output control mechanism for outputting the determined power to the rotating shaft or the mass body from the power source. 
         [0015]    With this configuration, not only can a rotation period of the mass body in the vibration control device be synchronized with a vibration period of the vibrating body without a delay, but also the mass body can be rotated with an optimal phase, and the vibration control performance can be enhanced. This is because rotation resistance of the mass body can be offset by the power assist mechanism. 
         [0016]    A control method for the vibration control device according to the present invention in order to achieve the above-mentioned object is a control method for a vibration control device installed in a vibrating body and controlling vibration of the vibrating body and having a rotating shaft, a mass body fixed to the rotating shaft, an activation apparatus for adding power of a rotational motion around the rotating shaft to the mass body, and a power assist mechanism for offsetting rotation resistance of the mass body, the method including a reading step of reading a vibration frequency of the vibrating body by the power assist mechanism, an output determining step of determining the power to be added to the mass body from a control map prepared in advance, and an output control step of adding the power determined in the output determining step to the mass body. With this configuration, the same working effects as the above can be obtained. 
       Advantageous Effects of Invention 
       [0017]    According to the vibration control device according to the present invention, there can be provided a vibration control device which can automatically suppress vibration of a vibrating body without installing a vibration detection sensor on the vibrating body such as a rotary machine, a reciprocating machine or the like, or the vibration control device, or without controlling a rotational speed or phase of the vibration control device. Furthermore, a low-cost vibration control device can be provided. 
     
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         [0018]      FIG. 1  is a schematic diagram illustrating a vibration control device of an embodiment according to the present invention. 
           [0019]      FIG. 2  are plan views illustrating an operation of the vibration control device. 
           [0020]      FIG. 3  is a schematic diagram illustrating a vibration control device of another embodiment according to the present invention. 
           [0021]      FIG. 4  are plan views illustrating an operation when there are two mass bodies. 
           [0022]      FIG. 5  are schematic diagrams illustrating a vibration control device of still another embodiment according to the present invention. 
           [0023]      FIG. 6  is a schematic diagram illustrating a mass body of the vibration control device of still another embodiment according to the present invention. 
           [0024]      FIG. 7  is a graph illustrating a vibration control performance of the vibration control device. 
           [0025]      FIG. 8  is a diagram illustrating an outline of a prior-art automatic balancer. 
       
    
    
     DESCRIPTION OF EMBODIMENTS 
       [0026]    Hereinafter, a vibration control device of an embodiment according to the present invention will be described by referring to the attached drawings. Particularly, the vibration control device installed in a diesel engine for ships (hereinafter referred to as a vibrating body) will be described as an example.  FIG. 1  illustrates an outline of the vibration control device  1  of the embodiment according to the present invention. The vibration control device  1  has a rotating shaft  11 , a mass body  12  fixed to the rotating shaft  11 , a casing  15  for protecting the mass body  12 , a clutch  14  installed on the rotating shaft  11 , and an activation apparatus (an electric motor, for example)  13  for start-up of the mass body  12  via the clutch  14 . Furthermore, the vibration control device  1  has a bottom plate  16  and is installed on the vibrating body (a diesel engine, for example)  2  via this bottom plate  16 . The mass body  12  is formed into a thick fan shape (hereinafter referred to as a disk-shaped mass body). The clutch  14  is configured so as to control connection and releasing of the electric motor  13  and the rotating shaft  11 . Meanwhile, an arrow indicates a rotation direction of the rotating shaft  11  and the mass body  12 , and an outline arrow indicates a vibration direction Z generated in the vibrating body  2 . 
         [0027]    Here, a diesel engine for ships is assumed to have, for example, a longitudinal size of 5500 to 6700 mm, a lateral size of 3150 to 3800 mm, and a height of approximately 8500 to 10200 mm. Furthermore, the vibration control device  1  is assumed to have a diameter of 400 to 600 mm, a height of 500 to 700 mm, and a weight of approximately 400 to 500 kg, and a mass of the mass body  12  is assumed to be approximately 150 to 250 kg. Furthermore, the engine has, in many cases, a direction in which vibration is particularly strong (the x-axis direction in  FIG. 1 ) due to influences of the number and arrangement of pistons and the like, and its vibration frequency is assumed to be approximately 5 to 20 Hz. 
         [0028]    Subsequently, an operation of the vibration control device  1  will be described.  FIG. 2  schematically illustrate movement of the vibration control device  1 , a state of displacement of the vibrating body  2 , and a relationship of a vibration external force F acting on the vibrating body  2 . In the first place, when the diesel engine of a ship is started, for example, vibration is generated in the engine (vibrating body  2 ) (see  FIGS. 2A and 2B . After that, a signal for start-up is sent to the electric motor (activation apparatus)  13 , and start control is executed (starting step). This electric motor  13  is stopped after being used as the activation apparatus. At this time, the clutch  14  is released, and connection between the electric motor  13  and the rotating shaft  11  is released. 
         [0029]    The rotating shaft  11  and the mass body  12  having obtained an initial velocity maintains rotation by using vibration of the engine  2  as power (see a vibration controlling step and  FIGS. 2C to 2F ). At this time, the mass body  12  automatically rotates so as to cancel the vibration of the engine  2 . Specifically, the mass body  12  rotates at a vibration frequency equal to the vibration frequency of the vibration of the engine  2  and also rotates so that the center of gravity of the mass body  12  is in a direction opposite to that of the vibration external force F acting on the engine  2 . Meanwhile, as illustrated in  FIGS. 2D and 2E , the direction of the vibration external force F is opposite to the direction of displacement of the mass body  12 , which is a feature at a vibration frequency higher than a resonance point. Because of the above, even if the vibration frequency is changed with a change in the rotational speed of the engine  2 , the rotational speed of the mass body  12  is automatically changed in accordance with this vibration frequency. When the engine  2  is stopped, rotation of the mass body  12  is also automatically stopped, and the vibration control operation is finished (finishing step). 
         [0030]    With the above-mentioned configuration, the following working effects can be obtained. First, the vibration control device  1  can be kept stopped in a region where the vibrating body  2  has a vibration frequency lower than the resonance point. Therefore, the vibration control device  1  does not cause a problem, as in the prior-art automatic balancer, in which the amplitude of the vibrating body  2  is increased at the vibration frequency lower than the resonance point. That is because the vibration control device  1  is configured not to operate as long as the initial velocity is not given by the activation apparatus  13 . 
         [0031]    Second, in a region where the vibrating body  2  has a vibration frequency equal to or higher than the resonance point, the amplitude of the vibrating body  2  can be suppressed. This is because, even if the vibration frequency at which the vibrating body  2  vibrates is high, rotation of the mass body  12  follows the external force and the vibration of the vibrating body  2 , and balance can be maintained. 
         [0032]    Third, the vibration control device  1  can be provided at a low cost. That is because the vibration control device  1  does not require a sensor or a control device for complicated control. That is, as long as the initial velocity is given, the mass body  12  is automatically rotated at the most suitable rotational speed for suppressing the amplitude of the vibrating body  2  without control after that. 
         [0033]      FIG. 3  illustrates an outline of a vibration control device  1   a  of another embodiment according to the present invention. The vibration control device  1   a  has two mass bodies  12   a . These two mass bodies  12   a  are arranged so as to be next to each other in a perpendicular direction with respect to the rotating shaft  11 . Furthermore, the two mass bodies  12   a  are installed so as to rotate in a state independent of the rotating shaft  11 , respectively. Specifically, it can be configured such that the rotating shaft  11  is made into a double shaft composed of an inner shaft and an outer shaft having a common central axis, that the rotating shaft  11  is made into the double shaft and is further provided with a one-way clutch or the like installed, or that the rotating shaft is made into two independent rotating shafts having different center axes. The relative positional relationship of these two mass bodies  12   a  is configured so as to be automatically adjusted with the rotation of the mass bodies  12   a.    
         [0034]    Next, an operation of the vibration control device  1   a  having the two mass bodies  12   a  will be described.  FIG. 4  illustrate planar outlines in a state in which the two mass bodies  12   a  are rotating.  FIG. 4A  illustrates a state in which the two mass bodies  12   a  are automatically adjusted so that most of them overlap with each other in planer view, and  FIG. 4B  illustrates a state in which the two mass bodies  12   a  are automatically adjusted so that they are largely shifted in the rotating direction. 
         [0035]    When a vibration external force of the vibrating body  2  is large, as illustrated in  FIG. 4A , a configuration in which masses of the two mass bodies  12   a  are concentrated to one point is preferable. On the other hand, when the vibration external force of the vibrating body  2  is small, a configuration in which the masses of the two mass bodies  12   a  are distributed is preferable. This vibration control device  1   a  automatically realizes the two states as illustrated in  FIG. 4  depending on the magnitude of the vibration external force through the use of the two mass bodies  12   a , and even when the magnitude of the vibration external force is changed, the vibration control device  1   a  can respond to the change of the magnitude by automatic change of relative positions of the two mass bodies  12   a.    
         [0036]    Furthermore, in order to improve the vibration control performance of this vibration control device, the power assist mechanism is preferably installed. This power assist mechanism is a control mechanism for adding power from a power source (the electric motor  13 , for example) to the rotating shaft  11  or the mass body  12  in order to offset the rotation resistance generated in a bearing or the like between the rotating shaft  11  and the casing  15  and can be constituted by the power source (the electric motor  13 , for example) and the vibration control device. 
         [0037]    This control device has a reading mechanism for detecting a rotational speed of a diesel engine, a control map for determining the power to be added to the rotating shaft  11  or the mass body  12  from the engine rotational speed, and an output control mechanism for outputting the power to be added determined by the control map to the rotating shaft  11  or the mass body  12 . 
         [0038]    Subsequently, a specific control method for the power assist mechanism will be described. First, the rotational speed of the diesel engine monitored in an engine room is read by the reading mechanism of the power assist mechanism (reading step). Subsequently, from the control map prepared in advance, the power to be added by the electric motor to the rotating shaft with respect to the current engine rotational speed is determined (output determining step). Finally, the determined power to be added is outputted from the electric motor to the rotating shaft by the output control mechanism (output control step). With this configuration, the rotating shaft can apparently rotate without resistance. 
         [0039]    Meanwhile, the control device constituting the power assist mechanism may be installed in the vibration control device  1  or may be incorporated in the diesel engine control device or the like in the engine room. Furthermore, the power constituting the power assist mechanism is not limited to the electric motor but can be constituted by known power sources such as a hydraulic motor, an air motor and the like. Moreover, the power assist mechanism and the activation apparatus can make use of the same power source (motor and the like). 
         [0040]    With the above-mentioned configuration, the following working effects can be obtained. First, the vibration control performance of the vibration control device can be enhanced. This is because the rotation of the mass body of the vibration control device can be synchronized with the vibration of the vibrating body without a delay in phase. Namely, this is because frictional resistance or the like causing the delay in phase of the mass body can be offset. 
         [0041]    Second, the vibration control performance of the vibration control device can be enhanced with low cost. This is because the power source of the power assist mechanism can be shared as power of the activation apparatus. In addition, this is because, with the configuration in which the power to be added to the rotating shaft is estimated from the vibration frequency of the vibrating body (the rotational speed of the diesel engine), a sensor for detecting the rotational speed of the mass body of the vibration control device or a complicated control program is not needed. 
         [0042]      FIG. 5  illustrate an outline of the activation apparatus of a vibration control device  1   b  of still another embodiment according to the present invention.  FIG. 5A  illustrates a plan view of the vibration control device  1   b , and  FIG. 5B  illustrates a perspective view. This vibration control device  1   b  has a mass body  12   b  in which a dent portion  22  is formed on a side surface and an activation apparatus constituted by an air nozzle  21  fixed to the casing  15 . This vibration control device  1   b  has a configuration of supplying an air  23  via the air nozzle  21  at start-up and starting rotation of the mass body  12   b.    
         [0043]    With this configuration, the vibration control device  1   b  can add a motive power to a position (an outer peripheral side) away from the rotating shaft  11 , and thus even the vibration control device  1   b  on which the mass body  12   b  with a large mass is mounted can be easily started. 
         [0044]    In the case of the vibration control device  1   b  to be installed in the diesel engine for ships, as the air  23 , compressed air for engine start-up, scavenging air boosted by a turbocharger and the like can be used. In addition, it may be configured such that a fluid such as oil or the like is filled in the casing  15  and a flow in the rotating direction is added to this fluid. By the flow of this fluid, start-up of the mass body (activation apparatus) can be realized. Furthermore, the fluid such as the above-mentioned air  23 , oil or the like can also be used as the power source for offset of rotation resistance (power assist mechanism). 
         [0045]    Furthermore, it may be configured such that a plurality of the air nozzles  21  is installed along a circumference of the casing  15 . With this configuration, rotation resistance can be offset without being relatively interrupted, as the power source for the power assist mechanism. 
         [0046]      FIG. 6  illustrates a mass body of a vibration control device  1   c  of still another embodiment according to the present invention. This mass body  12   c  has a vertically long shape obtained by cutting a part of a pipe into an arc shape (hereinafter referred to as a vertical mass body). This mass body  12   c  is fixed to a rotating shaft  11   c  rotating independently so that a relatively free positional relationship can be taken. 
         [0047]    With this configuration, the following working effects can be obtained. First, by the configuration in which a rotation radius of the mass body  12   c  is made small, a high vibration control performance can be exerted for vibration with a high vibration frequency. Second, a high following performance can be exerted for a change in the vibration frequency of the vibrating body. For example, the rotational speed of the mass body of the vibration control device can be caused to follow the vibrating body whose rotational speed is frequently changed, such as an engine of an automobile. In the case of the vibrating body having little change in the rotational speed such as the diesel engine for ships, vibration can be sufficiently controlled even with the disk-shaped mass body as illustrated in  FIG. 1 . 
         [0048]      FIG. 7  illustrates a graph indicating the vibration control performance of the vibration control device. The ordinate is amplitude A (mm) of the vibrating body, and the abscissa is a frequency f (Hz). A broken line indicates a case where the vibration control device is not installed, a dashed line indicates a case where the vibration control device is installed, and a solid line indicates a case where the vibration control device having the power assist mechanism is installed. An activation point P indicates a vibration frequency when the mass body of the vibration control device is given the initial velocity to thereby start it, and reference character V denotes a resonant frequency. Meanwhile, the vibration control device may be started after the vibration frequency of the vibrating body (the rotational speed of the engine, for example) is rapidly raised and is caused to pass the resonant frequency V. 
         [0049]    As illustrated in  FIG. 7 , if the vibration control device is started at the activation point P, the amplitude A of the vibrating body is rapidly reduced. That is, the vibration of the vibrating body can be effectively suppressed. The vibration control device of the present invention can exert a high vibration control performance at the vibration frequency higher than the resonant frequency V particularly at which the vibration was difficult to be suppressed. Furthermore, with the use of the vibration control device having the power assist mechanism, an extremely high vibration control performance can be exerted. 
         [0050]    As described above, with the vibration control device of the present invention, the vibration of the vibrating body can be effectively suppressed. Meanwhile, the vibrating body to be targeted is not limited to the diesel engine for ships. Specifically, the vibration control device of the present invention can be also applied to a diesel power generator, a turbine for power generation, an electric washing machine, a cutting device, an electric fan, a hard disk and the like, for example. At this time, by using the external force acting on the vibrating body, the amplitude, the vibration frequency of the vibrating body and the like as parameters, the mass of the mass body of the vibration control device, a length from a fulcrum to the center of gravity of the mass body, an inertia moment of the mass body and the like are determined. 
       REFERENCE SIGNS LIST 
       [0000]    
       
         
           
               1 ,  1   a ,  1   b ,  1   c  vibration control device 
               2  vibrating body 
               11  rotating shaft 
               12 ,  12   a ,  12   b ,  12   c  mass body 
               13  activation apparatus (electric motor) 
               15  casing