JP6322090B2 - Shaker - Google Patents

Description

  The present invention relates to a vibrator.

  Conventionally, as a vibration exciter, for example, a vibration table, an actuator, a spring interposed between the actuator and the vibration table, and a spring interposed between the base and the vibration table are provided. (For example, refer to Patent Document 1).

  Since this vibration exciter forms a spring mass system with the vibration exciter and the spring, it is small enough to vibrate the exciter with a large amplitude if the actuator is vibrated at the natural frequency. The advantage is that it only takes power.

JP 2014-009943 A

  In the conventional shaker, the shaking table can be vibrated greatly with a small force. However, when stopping the shaking table, it is necessary to apply vibrations in the opposite phase to the shaking table with the actuator. You have to show a lot of power compared to sometimes. The actuator may not be stopped by the actuator, but may wait for the vibration table to naturally stop by the frictional force generated by the spring and the sliding portion, but this method is not rational.

  In this way, the actuator must exert a large force so that the shaking table can be safely stopped, so a large actuator must be used, and a resonance that gives a large vibration with a small force is used. Cannot enjoy the benefits of a shaker.

  Accordingly, the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a vibration exciter that enables use of an actuator having a small output.

  In order to achieve the above-described object, the vibration exciter in the problem solving means of the present invention includes a damper element capable of suppressing the reciprocating motion of the vibration table, so that the damping force generated by the damper element generates vibration of the vibration table. Can stop safely. Therefore, the linear actuator is not required to have a high output for stopping the vibration table.

  According to the vibration exciter of the second aspect, the vibration table is provided with a vibration floor on which the reciprocating motion is loaded, and the spring element transmits the reciprocating motion of the movable portion of the linear actuator to the vibration floor. The second spring that transmits the reciprocating motion of the spring and the vibration bed to the vibration table, the damper element is a first damper capable of suppressing the reciprocation of the vibration bed, and the second spring capable of suppressing the reciprocation of the vibration table. Because the vibration exciter is a system with two degrees of freedom, the vibration table can be vibrated at different frequencies in the primary and secondary modes, and testing at multiple frequencies is possible. Is possible. Further, since the vibration table is reciprocated on the vibration floor, the lateral width of the vibration exciter can be made compact.

  According to the shaker of claim 3, the movable part side damper in which the damper element is interposed between the excitation table and the movable part, and the base in which the damper element is interposed between the excitation table and the base Since the side damper is provided, the vibration table can be safely stopped even if an abnormality occurs in the movable part side damper or the base side damper.

  According to the vibrator of Claim 4, the 1st movable part side spring interposed between a vibration floor and a movable part, and the 1st base side interposed between a vibration floor and a base A first shaking table spring interposed between the spring, one end of the shaking table and the vibrating bed, and a second shaking table spring interposed between the other end of the shaking table and the vibrating bed Therefore, the vibration exciter becomes a system of two degrees of freedom. Therefore, the vibration table can be vibrated at different frequencies in the primary mode and the secondary mode, and a test at a plurality of frequencies can be performed. Moreover, since the vibration exciter is reciprocated on the vibration floor, the lateral width of the vibration exciter becomes compact. Furthermore, a first movable part side damper interposed between the vibration floor and the movable part, a first base side damper interposed between the vibration floor and the base, and one end of the vibration table And the first vibration table damper interposed between the other end of the vibration table and the vibration floor. The shaking table can be safely stopped even if an abnormality occurs in the part.

  According to the vibration exciter of the fifth aspect, since the damper element includes the switching unit that can be switched between a state in which the damping element does not exhibit the damping force and a state in which the damping force is exerted, When oscillating, it is possible to oscillate the oscillating table without energy loss by preventing the damper element from exerting a damping force, and the energy consumption of the oscillating device can be reduced.

  According to the vibration exciter of the sixth aspect, since the damper element is provided with the damping force variable portion that makes the damping force variable when expanding and contracting variable, the damping force can be changed and the amplitude of the shaking table can be controlled. . Further, when the damping force is increased at the stroke end, the damper element can be used as a stopper for restricting an excessive stroke of the vibration table.

  According to the vibrator of the present invention, an actuator with a small output can be used.

It is a side view of the vibration exciter in a first embodiment. It is a schematic sectional drawing of the damper as a damper element. It is a side view of the vibration exciter in 2nd embodiment. It is a side view of the vibration exciter in 3rd embodiment. It is a side view of the vibration exciter in 4th embodiment.

  The present invention will be described below based on the embodiments shown in the drawings. As shown in FIG. 1, the vibration exciter K <b> 1 in the first embodiment includes a base 2, a linear actuator 3, the vibration exciter 4, a spring element 5, and a damper element 6. The spring element 5 and the damper element 6 are interposed between the linear actuator 3 and the vibration table 4. In this vibration exciter K 1, the linear actuator 3 is driven to vibrate the vibration exciter 4 via the spring element 5.

  Hereinafter, each part of the vibration exciter K1 of 1st embodiment is demonstrated in detail. In this embodiment, the base 2 includes a traveling floor 2a on which the vibration table 4 travels and a holding portion 2b that stands up from the traveling floor 2a and holds the linear actuator 3. The traveling floor 2a is provided with at least two guide rails 2c arranged in parallel with each other.

  In this embodiment, the linear actuator 3 is a hydraulic cylinder. The cylinder 3a is held by the holding portion 2b of the base 2, the piston 3b is slidably inserted into the cylinder 3a, and the cylinder 3a. The hydraulic oil is supplied to and discharged from the piston rod 3c, which is movably inserted into the piston 3b and connected to the piston 3b, and the rod side chamber R1 and the piston side chamber R2 partitioned by the piston 3b in the cylinder 3a. On the other hand, a hydraulic pump 3d that relatively moves the piston 3b in the axial direction is provided. In the linear actuator 3, the hydraulic oil is supplied to the rod side chamber R1 by the hydraulic pump 3d, the hydraulic oil is discharged from the piston side chamber R2, and the piston 3b and the piston rod 3c connected thereto are connected. Move to the right in FIG. Further, in the linear actuator 3, the hydraulic oil is discharged from the rod side chamber R1, the hydraulic oil is supplied to the piston side chamber R2, and the piston 3b and the piston rod 3c connected thereto are moved leftward in FIG. Let That is, in this embodiment, the movable part M in the linear actuator 3 is composed of the piston 3b and the piston rod 3c connected to the piston 3b, and enables the movable part M to reciprocate in the axial direction. .

  Note that the linear actuator 3 may be a pneumatic cylinder that uses a fluid other than the working oil, for example, a gas, as the working fluid. In addition to such a cylinder-type actuator, a linear motor or a rotary type may be used. A linear actuator including a motor and a feed screw mechanism may be used. And if it is a linear motor, it is comprised with a magnet and an electromagnet, and what is necessary is just to make any one into a movable part. Even if it exists in the linear actuator which consists of a rotary motor and a feed screw mechanism, a motor or a feed screw mechanism A member that exhibits a linear motion in the above may be used as a movable portion.

  On the other hand, the vibration table 4 includes a base body 4a to which a test piece (not shown) can be attached, and a plurality of bearings 4b that are provided in the lower part of the base body 4a and run on the guide rail 2c. The bearing 4b and the guide rail 2c constitute a linear guide, and the vibration table 4 is guided by the linear guide and moves on the traveling floor 2a of the base 2 described above in the horizontal direction in FIG. The vehicle can travel in a direction that matches the expansion / contraction direction. Therefore, in this embodiment, at least two or more guide rails 2c are provided in parallel, and the vibration table 4 can reciprocate on the base 2 without tilting.

  In this embodiment, a linear guide is provided so that the exciter 4 can reciprocate in the direction in which the vibration table 4 coincides with the expansion / contraction direction of the linear actuator 3 on the traveling floor 2a of the base 2, but a linear guide is provided. Alternatively, the vibration table 4 may be provided with wheels that can travel on the traveling floor 2a so that the vibration table 4 can travel on the traveling floor 2a, or a guide is provided on the traveling floor 2a side of the base 2. A rod may be provided, and a bush slidably contacting the guide rod may be attached to the vibration table 4 to guide the movement of the vibration table 4 in a direction that matches the expansion / contraction direction of the linear actuator 3. Alternatively, a number of balls may be arranged on the lower surface of the floor body 4a of the vibration table 4 or the upper surface of the traveling floor 2a of the base 2 so that the vibration table 4 travels on the traveling floor 2a. Furthermore, a large number of rollers may be arranged on the traveling floor 2a, and the rollers 4 may be caused to travel on the rollers, and the traveling floor 2a and the vibration table 4 are formed with a low friction material amount. The contact surface may be smoothed and the exciter 4 may be slid on the traveling floor 2a. Since the base 2 only needs to be able to hold the linear actuator 3, the traveling floor 2 a is not essential, but as described above, the provision of the traveling floor 2 a can provide an environment suitable for traveling of the vibration table 4. Therefore, smooth movement of the vibration table 4 can be realized. Moreover, it may replace with installation of the driving | running | working floor 2a, and you may provide the slide mechanism which slides the shaking table 4 non-contacting using an air pressure or hydraulic pressure.

  In this case, the spring element 5 is a coil spring, and one end is connected to the vibration table 4 and the other end is connected to the piston rod 3 c of the linear actuator 3. And if the linear actuator 3 is driven, the spring element 5 can be expanded-contracted and the vibration of the vibration exciter 4 can be implement | achieved. That is, the reciprocating motion of the movable part M of the linear actuator 3 can be transmitted to the vibration table 4 via the spring element 5. The spring element 5 is not limited to a coil spring, and may be an elastic body that expands and contracts by receiving an external force and generates a reaction force that opposes the external force along with the expansion and contraction.

  In this case, as shown in FIG. 2, the damper element 6 is constituted by a single hydraulic damper, and in detail, this hydraulic damper is slidably inserted into the cylinder 6a and the cylinder 6a. A piston 6b, a piston rod 6c that is movably inserted into the cylinder 6a and connected to the piston 6b in the middle, an extension side chamber 6d, a compression side chamber 6e, and an extension side chamber 6d partitioned by the piston 6b in the cylinder 6a. A passage 6f that communicates with the pressure side chamber 6e, a bypass passage 6g that communicates between the extension side chamber 6d and the pressure side chamber 6e, and a damping force that is provided in the middle of the passage 6f and that can change the resistance applied to the flow of liquid passing therethrough The variable valve 6h is provided with an opening / closing valve 6i that is provided in the middle of the bypass passage 6g and opens and closes the bypass passage 6g. Although the damping force variable valve 6h is illustrated as an electromagnetic valve that can change the flow path area by driving the valve body with a solenoid, it may be a valve that drives the valve body with an actuator other than the solenoid. Good. The open / close valve 6i is also an electromagnetic valve that opens and closes the flow path by driving the valve body with a solenoid, but may be a valve that drives the valve body with an actuator other than the solenoid. . The damping force variable valve 6h and the opening / closing valve 6i are connected to the control device C, and can be controlled as instructed by the control device C.

  In the damper element 6, when the open / close valve 6i is closed and extended by an external force, the compression side chamber is expanded from the compressed expansion side chamber 6d through the passage 6f and the damping force variable valve 6h. The liquid moves to 6e. Since the damping force variable valve 6h provides resistance to the passage of the liquid and generates a differential pressure in the extension side chamber 6d and the pressure side chamber 6e, the damper element 6 exhibits a damping force that prevents extension. Since the damping force in the damper element 6 is adjusted by changing the resistance given to the liquid flow by the damping force variable valve 6h, the damping force exerted by the damper element 6 can be made variable.

  In the damper element 6, when the opening / closing valve 6i is closed and contracted by an external force, the expansion side chamber is expanded from the compression side chamber 6e through the passage 6f and the damping force variable valve 6h. The liquid moves to 6d. Since the damping force variable valve 6h applies resistance to the passage of the liquid and generates a differential pressure in the compression side chamber 6e and the expansion side chamber 6d, the damper element 6 exhibits a damping force that prevents contraction. Since the damping force in the damper element 6 is adjusted by changing the resistance given to the liquid flow by the damping force variable valve 6h, the damping force exerted by the damper element 6 can be made variable. Therefore, the damping force variable valve 6h functions as a damping force variable unit that varies the damping force that the damper element 6 exerts during expansion and contraction.

  On the other hand, in a state where the opening / closing valve 6i is opened and the bypass passage 6g is opened, when the damper element 6 is expanded and contracted by an external force, the liquid preferentially passes through the bypass passage 6g having a smaller resistance than the damping force variable valve 6h. Therefore, the damper element 6 is in a state where it hardly exhibits the damping force that prevents expansion and contraction. Therefore, the bypass 6g and the opening / closing valve 6i function as a switching unit that can be switched between a state in which the damper element 6 does not exhibit a damping force during expansion and contraction and a state in which the damping force is exhibited.

  As described above, in the case of the present embodiment, the damper element 6 does not exhibit a damping force when the on-off valve 6i is opened, and does not interfere with the expansion and contraction of the spring element 5. On the contrary, when the on-off valve 6i is closed, the damping force Is exerted to prevent expansion and contraction of the spring element 5.

  The above-described structure of the damper element 6 is an example, and the structure of the structure can be arbitrarily changed, and other structures can be adopted. For example, as described above, the damper element 6 is a so-called double rod type damper in which the piston rod 6c is inserted into both the expansion side chamber 6d and the compression side chamber 6e, but may be a single rod type damper. In addition to the hydraulic damper, a pneumatic damper may be used. Further, the damper element 6 may be a biflow type damper or a uniflow type damper. Further, as the working fluid, water, an aqueous solution, an electromagnetic viscous fluid, or an electroviscous fluid may be used in addition to the working oil. When an electromagnetic viscous fluid is used, a coil that applies a magnetic field to the passage 6f may be used for the damping force variable portion. When an electrorheological fluid is used, an electric field can be applied to the passage 6f. That's fine.

  In the vibration exciter K1 configured as described above, when the piston 3b and the piston rod 3c which are the movable portions M of the linear actuator 3 are reciprocated, the spring element 5 expands and contracts. Since the vibration of the movable part M is transmitted to the vibration table 4 via the spring element 5, the vibration device K1 can move the vibration table 4 relative to the base 2. . When the vibration table 4 is vibrated, the opening / closing valve 6i, which is a switching portion of the damper element 6, is opened to enable the bypass path 6g so that the damper element 6 does not exert a damping force. In this way, the damper element 6 does not hinder the vibration of the vibration table 4 driven by the linear actuator 3, so that the kinetic energy of the linear actuator 3 can be used for vibration of the vibration table 4 without loss. Therefore, if the switching element is provided in the damper element 6, the energy consumption of the vibration exciter K1 can be reduced. Note that even if the damper element 6 does not include a switching unit and the damping element 4 can continue to exhibit a damping force during expansion and contraction, the vibration table 4 can be excited, and the damper element does not include the switching unit. Can also be used.

  If the mass of the spring element 5 is ignored, the natural frequency determined by the mass of the vibration table 4 and the mass of a test piece (not shown) attached to the vibration table 4 and the spring constant of the spring element 5, that is, the vibration table 4 When the movable part M of the linear actuator 3 is reciprocated at the natural frequency in the system of the spring element 5, the spring element 5 expands and contracts at the natural frequency and the excitation table 4 resonates. The amplitude of M is amplified and transmitted to the movable floor 4. When the vibration table 4 is vibrated at a frequency that matches the natural frequency in this way, the thrust of the linear actuator 3 is small, and even if the amplitude of the vibration table 4 is small at first, the vibration table 4 is gradually increased. The vibration table 4 vibrates greatly.

  Subsequently, when the vibration table 4 is stopped, the opening / closing valve 6i of the damper element 6 is closed to shut off the passage 6g so that the damper element 6 exhibits a damping force. In this case, the linear actuator 3 may be stopped, but may be actively expanded and contracted in a phase opposite to that of the vibration of the vibration table 4. The vibration of the vibration table 4 is suppressed by the damping force generated by the expansion and contraction of the damper element 6. The kinetic energy of the vibration table 4 and the elastic energy of the spring element 5 are converted into heat by the damper element 6. Will stop safely. Further, when it is desired to control the amplitude of the vibration table 4, the damper element 6 can exert a damping force to suppress the vibration of the vibration table 4, so that the amplitude of the vibration table 4 can be controlled. Specifically, the desired amplitude of the vibration table 4 can be realized by adjusting the damping force of the damper element 6 while driving the linear actuator 3.

  Thus, in the vibration exciter K1 of the present invention, the amplitude of the movable part M of the linear actuator 3 can be amplified, and the vibration of the vibration table 4 can be realized with a large amplitude. Thereby, in the vibration exciter K1, the linear actuator 3 having a stroke length shorter than the amplitude of the vibration table 4 can be used. And in the shaker K1 of this invention, when stopping the vibration stand 4, the damping force which the damper element 6 generate | occur | produces can be utilized, and it is not necessary for the linear actuator 3 to exhibit a big thrust. Therefore, according to the shaker K1 of the present invention, it is possible to use an actuator with a small output. In addition, since it is sufficient to use the linear actuator 3 having a small output, it is possible to receive the maximum merit of the vibration exciter using the resonance, which can reduce the power consumption without increasing the size of the device. . Further, since the damping force of the damper element 6 can be changed, it is not necessary to control the amplitude of the vibration table 4 by exerting a large output by the linear actuator 3, and the vibration table 4 can be changed by changing the damping force of the damper element 6. Can be controlled.

  The damper element 6 is interposed between the linear actuator 3 and the vibration table 4 so as to be connected to both. However, the damper element 6 can also be interposed between the base 2 and the vibration table 4. . When the damping force variable valve 6h is installed on the cylinder 6a side, the cylinder 6a can be connected to the base 2 considering the insertion of the damper element 6 between the base 2 and the vibration table 4. For example, since the damping force variable valve 6h is connected to the base 2 side and does not vibrate, the wiring to the solenoid can be easily performed.

  In addition, the damper element 6 can change the resistance given to the flow of the liquid passing through the passage 6f by the damping force variable valve 6h as described above. However, when the damper element 6 is displaced to the vicinity of the stroke end, the stroke beyond the damper element 6 can be changed. The damper element 6 can function as a stopper for restricting the excessive amplitude of the vibration table 4 by restricting or blocking the passage 6f against the displacement toward the end side. Specifically, as shown in FIG. 2, ports 6j and 6k connected to the passage 6f are provided in the vicinity of both ends of the cylinder 6a, and the piston 6b is displaced to the vicinity of the stroke end on the extension side with respect to the cylinder 6a. Then, it reaches the port 6j and gradually shuts off the port 6j against further displacement of the extension side toward the stroke end side, so that the damping force exerted by the damper element 6 increases. Yes. On the contrary, when the piston 6b is displaced to the vicinity of the pressure side stroke end with respect to the cylinder 6a, the port 6k is approached, and the port 6k is gradually blocked against any further displacement toward the pressure side stroke end. Thus, the damping force exerted by the damper element 6 is increased. If the damper element 6 is configured in this way, the damper element 6 can be provided with a stopper function to restrict excessive amplitude of the vibration table 4. Thus, in addition to the damping force variable valve 6h, the damping force changing unit may be configured to include a mechanism for blocking the ports 6j and 6k by the piston 6b. The structure for increasing the damping force when the damper element 6 is displaced to the vicinity of the stroke end is not limited to the above-described structure. For example, the damper element 6 flows when the damper element 6 is displaced to the vicinity of the stroke end by controlling the damping force variable valve 6h. The stopper area can be realized by reducing the road area. The damper element 6 is not provided with a stopper function, but as shown by a broken line in FIG. 1, when the vibration table 4 makes a maximum stroke on the base 2, the stroke in the same direction beyond that of the vibration table 4 is reached. You may make it provide stopper S1, S2 which regulates.

  The spring element 5 is composed of one spring provided between the vibration table 4 and the linear actuator 3 as shown in FIG. 1, but the second embodiment shown in FIG. Like the vibrator K2 of the embodiment, the movable part side spring 51 having a spring element interposed between the vibration base 4 and the linear actuator 3, and the spring receiving part 2d provided on the vibration base 4 and the base 2 You may comprise by the base side spring 52 interposed between these. In this case, the excitation table 4 is sandwiched between the movable part side spring 51 and the base side spring 52. The movable part side spring 51 and the base side spring 52 may be interposed in a compressed state, or may be interposed in a natural length or in an extended state. Further, the spring constants of the movable part side spring 51 and the base side spring 52 may be the same or different, but if the spring constant is set so that the natural frequency at which the vibration base 4 is easily vibrated is set. Good.

  The damper element is also provided between the movable part side damper 61 in which the damper element is interposed between the vibration table 4 and the linear actuator 3, and the spring receiving part 2 d provided on the vibration table 4 and the base 2. You may comprise with the base side damper 62 interposed. The movable portion side damper 61 and the base side damper 62 may be configured in the same manner as the specific configuration of the damper element 6 in the first embodiment described above, but may be a damper having other configurations. Moreover, the above-described various variations described in the damper element 6 in the first embodiment can be applied. Since the damper element is composed of the movable part side damper 61 and the base side damper 62, even if any one of the dampers 61, 62 is found to be abnormal, the other normal damper is used to make the vibration table 4 It can be stopped safely.

  Further, in this case, a damper having a damping force variable portion is provided only for one of the movable portion side damper 61 or the base side damper 62, and the damping force varying portion is provided when controlling the amplitude of the vibration table 4. Only the damping force may be changed to control the amplitude. Instead of connecting one end of the movable portion side damper 61 to the linear actuator 3, the vibration of the vibration table 4 relative to the base 2 may be attenuated by connecting to the base 2. In addition, as long as the vibration table 4 can be safely stopped by the damping force generated by one of the movable part side damper 61 or the base side damper 62, only one of them may be provided as a damper element.

  Even in the vibration exciter K2 of the second embodiment configured as described above, the vibration of the exciter 4 can be realized by amplifying the amplitude of the movable portion M of the linear actuator 3. Therefore, according to the shaker K2 of the present invention, it is possible to use an actuator with a small output. Further, since it is sufficient to use the linear actuator 3 having a small output, the apparatus is not increased in size, and the merit of the vibration exciter using the resonance that can reduce the power consumption can be maximized.

  The vibration exciter K3 in 3rd embodiment is demonstrated. As shown in FIG. 4, the vibration exciter K <b> 3 includes a base 2, a vibration floor 7 on which the vibration exciter 4 is reciprocally loaded, and a reciprocating motion of the movable portion M in the linear actuator 3. A first spring 10 for transmitting, a second spring 11 for transmitting the reciprocating motion of the vibration floor 7 to the vibration exciter 4, a first damper 12 capable of suppressing the reciprocating motion of the vibration floor 7, and a vibration exciter 4 and a second damper 13 capable of suppressing the reciprocating motion of 4.

  In this embodiment, the vibration floor 7 includes a floor main body 7a on which the vibration table 4 travels, a spring receiving portion 7b rising from both ends of the floor main body 7a, and a guide rail provided at the upper end of the floor main body 7a in FIG. 7c and a plurality of bearings 7d that travel on the guide rail 2c provided on the traveling floor 2a of the base 2 are configured. In the vibration exciter K1 according to the first embodiment, the guide rail 2c of the traveling floor 2a is caused to travel on the bearing 4b provided on the vibration exciter 4, and the linear guide is configured. The guide rail 2 c is caused to travel on a bearing 7 d provided on the floor 7, and the vibration floor 7 can reciprocate on the traveling floor 2 a in the extending and contracting direction of the linear actuator 3. In addition, instead of the linear guide, the vibration floor 7 can be provided with traveling wheels capable of traveling on the traveling floor 2a. The vibration table 4 of the first embodiment is arranged on the traveling floor 2a of the base 2. This is the same as described for the traveling structure.

  The vibration table 4 is provided with a bearing 4b that is loaded on the floor body 2a of the vibration floor 7 and travels on the guide rail 7c. A linear guide is constituted by the bearing 4c and the guide rail 7c, and the vibration table 4 can reciprocate on the guide rail 7c provided on the vibration floor 7 via the bearing 4b. The guide rail 7 c and the guide rail 2 c are provided along the same direction, and the vibration exciter 4 can reciprocate on the vibration floor 7 in the extending and contracting direction of the linear actuator 3. Since two or more guide rails 7c are provided in parallel, the vibration table 4 can reciprocate on the vibration floor 7 without tilting. In addition, instead of the linear guide, the vibration table 4 can be provided with traveling wheels capable of traveling on the vibration floor 7 because the vibration table 4 of the first embodiment is on the traveling floor 2a of the base 2. This is the same as described for the structure for traveling.

  In the vibration exciter K3 of the third embodiment, the spring element is composed of the first spring 10 and the second spring 11 described above. In this case, the first spring 10 is a coil spring, and is interposed between the movable part M and the vibration floor 7 in the linear actuator 3. When the movable part M is driven to reciprocate, This reciprocating motion is transmitted to the vibration floor 7. In this case, the second spring 11 is a coil spring, and is interposed between the spring receiving portion 7b of the vibration floor 7 and the vibration table 4. The reciprocating motion of the vibration floor 7 is the vibration table. 4 is transmitted. Accordingly, since the linear actuator 3 is driven to reciprocate the drive unit M, the first spring 10 and the second spring 11 that are spring elements expand and contract, and the vibration table 4 vibrates. That is, even in the vibration exciter K3 of the third embodiment, the reciprocating motion of the movable portion M of the linear actuator 3 can be transmitted to the vibration exciter 4 via the spring element. In addition, the 1st spring 10 and the 2nd spring 11 are not limited to a coil spring, What is necessary is just an elastic body which expands and contracts by receiving external force, and generate | occur | produces the reaction force which opposes external force with the said expansion / contraction. The spring constants of the first spring 10 and the second spring 11 may be the same or different. However, if the spring constant is set so that the vibration table 4 has a natural frequency that is easy to vibrate. Good.

  In the vibration exciter K3 of the third embodiment, the damper element includes the first damper 12 and the second damper 13 described above. In this case, the first damper 12 has the same configuration as the damper as the damper element 6 in the vibration exciter K1 of the first embodiment described above, and the movable portion M and the vibration floor 7 in the linear actuator 3 are provided. It is intervened between. The first damper 12 can be switched between a state where the damping force is exerted and a state where the damping force is not exhibited, and the damping force can be changed in a state where the damping force is exerted. When the first damper 12 exhibits a damping force, the relative vibration between the movable portion M and the vibration floor 7 is suppressed by the damping force, and when the first damper 12 does not exhibit a damping force, the linear actuator 3. The vibration of the vibrating floor 7 is not disturbed. The first damper 12 may be interposed between the base 2 and the vibration floor 7, and even in the first damper 12, the damping force is increased at the stroke end in the same manner as the damper element 6. Thus, it may be configured to function as a stopper for restricting an excessive stroke of the vibration floor 7. Note that the first damper 12 may also be a passive damper that cannot switch between changing the damping force and enabling / disabling the damping force.

  In this case, the second damper 13 has the same configuration as the damper as the damper element 6 in the vibration exciter K1 of the first embodiment described above, and is provided between the vibration floor 7 and the vibration table 4. Is intervened. Specifically, the second damper 13 is interposed between the spring receiving portion 7 b of the vibration floor 7 and the vibration table 4. The second damper 13 can be switched between a state where the damping force is exerted and a state where the damping force is not exhibited, and the damping force can be changed in a state where the damping force is exerted. When the second damper 13 exhibits a damping force, the relative vibration between the vibration floor 7 and the vibration table 4 is suppressed by the damping force, and when the second damper 13 does not exhibit a damping force, the linear actuator The excitation of the vibration table 4 by the vibration floor 7 driven by 3 is not disturbed. The second damper 13 may be interposed between the base 2 and the vibration table 4, and even in the second damper 13, the damping force at the stroke end is the same as that of the damper element 6. May be configured to function as a stopper that restricts an excessive stroke of the vibration floor 7 by enlarging. The second damper 13 may also be a passive damper that cannot switch between changing the damping force and enabling / disabling the damping force. When the second damper 13 is interposed between the base 2 and the vibration table 4, the first damper 12 can be omitted unless the damping force is insufficient.

  In the vibration exciter K3 configured as described above, when the piston 3b and the piston rod 3c, which are the movable part M of the linear actuator 3, are reciprocated, the first spring 10 expands and contracts to move to the vibration floor 7. The reciprocating motion of the part M is transmitted and the vibration floor 7 vibrates. The vibration of the vibration floor 7 causes the second spring 11 to expand and contract and the vibration table 4 also vibrates. Thus, the vibration of the movable part M is transmitted to the vibration table 4 via the first spring 10 and the second spring 11 which are the spring elements, and the vibration exciter K3 It can move relative to the base 2. When the vibration table 4 is vibrated, if the first damper 12 and the second damper 13 which are the damper elements do not exhibit a damping force, the kinetic energy generated by driving the linear actuator 3 is lost without loss. 4 can be vibrated. In the case of this embodiment, two mass points of the vibration floor 7 and the vibration table 4 are provided, and a first spring 10 is interposed between the linear actuator 3 and the vibration floor 7, and the vibration floor 7 and the vibration table 4. Since the second spring 11 is interposed between the first mode and the second mode, the system has two natural frequencies of a primary mode and a secondary mode having a higher frequency than the primary mode. In the primary mode, the vibration directions of the vibration floor 7 and the vibration table 4 are the same, and in the secondary mode, the vibration directions of the vibration floor 7 and the vibration table 4 are opposite. If the vibration table 4 is vibrated at the natural frequency of the primary mode or the secondary mode, vibration with a large amplitude can be obtained. In the vibration in the primary mode, the vibration floor 7 and the vibration table 4 vibrate in the same direction, so that there is an advantage that the amplitude of the vibration table 4 can be easily increased compared with the vibration in the secondary mode. Even if the first damper 12 and the second damper 13 which are damper elements are not provided with a switching portion and are passive dampers that continue to exhibit a damping force during expansion and contraction, the vibration of the vibration table 4 Is possible and usable.

  When the vibration table 4 is vibrated at a frequency that matches the natural frequency in this way, the thrust of the linear actuator 3 is small, and even if the amplitude of the vibration table 4 is small at first, the vibration table 4 is gradually increased. The vibration table 4 can vibrate greatly.

  Subsequently, when the vibration table 4 is stopped, the vibrations of the vibration table 4 and the vibration floor 7 are attenuated by the damping force generated by the first damper 12 and the second damper 13 which are damper elements. The stand 4 and the vibration floor 7 can be safely stopped. Even in the vibration exciter K3 of this embodiment, the kinetic energy of the vibration table 4 and the vibration floor 7 and the elastic energy of the spring element are converted into heat by the damper element, and the vibration table 4 can be safely stopped. In the two-mass-point two-degree-of-freedom system, the vibration frequency of the linear actuator 3 is such that the vibration of the vibration bed 7 can be stopped or the amplitude can be reduced. When driven, the vibration of the vibration table 4 can be quickly stopped.

  In addition, even when it is desired to control the amplitude of the vibration table 4, the first damper 12 and the second damper 13, which are damper elements, exhibit a damping force, so that the vibration of the vibration table 4 is suppressed. The amplitude of the vibration table 4 can be controlled. Specifically, while driving the linear actuator 3, the damping force of one or both of the first damper 12 and the second damper 13, which are damper elements, is adjusted to achieve the desired amplitude of the vibration table 4. it can. When the second damper 13 is interposed between the base 2 and the vibration table 4 and the first damper 12 is omitted, the vibration can be obtained by adjusting the damping force of the second damper 13. The amplitude of the table 4 can be controlled.

  As described above, in the vibration exciter K3 of the present invention, the amplitude of the movable portion M of the linear actuator 3 can be amplified to realize vibration with a large amplitude of the vibration table 4. Thereby, in the vibrator K3, the linear actuator 3 having a stroke length shorter than the amplitude of the vibration table 4 can be used. In the shaker K3 of the present invention, the damping force generated by the damper element can be used when the amplitude of the shaking table 4 is controlled or stopped, and the linear actuator 3 needs to exert a large thrust. There is no. Therefore, according to the shaker K3 of the present invention, it is possible to use an actuator with a small output. In addition, since it is sufficient to use the linear actuator 3 having a small output, it is possible to maximize the merit of the vibration exciter using resonance, which can reduce the power consumption without increasing the size of the device.

  Further, since the vibration exciter K3 has the vibration exciter 4 mounted on the vibration floor 7 so as to be able to reciprocate, the lateral width of the vibration exciter K3 in FIG. 4 can be shortened. Can be compact.

  Further, since the shaker K3 is a two-mass point two-degree-of-freedom system, the vibration of the vibration table 4 can be realized at different frequencies in the primary mode and the secondary mode. The vibration test can be executed.

  If the first damper 12 is connected to the base 2 and the vibration floor 7 and the second damper 13 is connected to the vibration table 4 and the vibration floor 7, the first damper Wiring to the solenoid in the switching part and the damping force variable part of the 12 and the second damper 13 becomes easy. Rather than providing the first damper 12 and the second damper 13 with a stopper function, as shown by the broken line in FIG. The stoppers S3 and S4 for restricting the stroke in the same direction as described above may be provided, and the stoppers S5 and S6 for restricting the maximum stroke of the vibration table 4 may be provided on the vibration floor 7.

  The first spring 10 is composed of one spring provided between the vibration floor 7 and the linear actuator 3 as shown in FIG. 4, but the fourth embodiment shown in FIG. And the first movable portion side spring 71 interposed between the vibration floor 7 and the movable portion M of the linear actuator 3, and the spring receiving portion provided on the vibration floor 7 and the base 2. You may comprise with the 1st base side spring 72 interposed between 2d. In this case, the vibration floor 7 is sandwiched between the first movable part side spring 71 and the first base side spring 72. The first movable part side spring 71 and the first base side spring 72 may be interposed in a compressed state, or may be interposed in a natural length or an extended state.

  Further, the second spring 11 is composed of one spring provided between the vibration floor 7 and the vibration table 4 as shown in FIG. 4, but the fourth spring 11 shown in FIG. Like the vibrator K4 of the embodiment, the first vibration base spring 73 interposed between the spring receiving portion 7b provided at one end of the vibration floor 7 and the vibration base 4, and the other end of the vibration floor 7 You may comprise with the 2nd vibration stand spring 74 interposed between the spring receiving part 7e and the vibration stand 4 provided in this. In this case, the vibration table 4 is sandwiched between the first vibration table spring 73 and the second vibration table spring 74. The first vibration base spring 73 and the second vibration base spring 74 may be interposed in a compressed state, or may be interposed in a natural length or in an extended state. Further, the spring constants of the first movable part side spring 71, the first base side spring 72, the first vibration base spring 73, and the second vibration base spring 74 may be the same or different. What is necessary is just to set the said spring constant so that it may become the natural frequency which the stand 4 is easy to vibrate.

  Further, the first damper 12 is composed of one damper provided between the vibration floor 7 and the linear actuator 3 as shown in FIG. 4, but the fourth embodiment shown in FIG. And the first movable part side damper 81 interposed between the vibration floor 7 and the movable part M of the linear actuator 3, and the spring receiving part provided on the vibration floor 7 and the base 2. You may comprise with the 1st base side damper 82 interposed between 2d. In this case, the first movable part side damper 81 can be interposed between the base 2 and the vibration floor 7.

  Further, the second damper 13 is composed of one damper provided between the vibration floor 7 and the vibration table 4 as shown in FIG. 4, but the fourth damper 13 shown in FIG. Like the vibration exciter K4 of the embodiment, the first vibration table damper 83 interposed between the spring receiving portion 7b provided at one end of the vibration bed 7 and the vibration table 4, and the other end of the vibration bed 7 You may comprise by the 2nd vibration stand damper 84 interposed between the spring receiving part 7e and the vibration stand 4 which were provided in this.

In this case, the first vibration table damper 83 and the second vibration table damper 84 can be interposed between the base 2 and the vibration table 4.
The first movable portion side damper 81, the first base side damper 82, the first vibration table damper 83, and the second vibration table damper 84 are the specific configuration of the damper element 6 in the first embodiment described above. The damper may be configured similarly, but may be a damper having other configurations, and the above-described various variations described in the damper element 6 in the first embodiment are applicable.

  Further, in this case, a damping force variable portion is provided only for one of the first movable part side damper 81 and the first base side damper 82 and only one of the first vibration base damper 83 and the second vibration base damper 84. In controlling the amplitude of the vibration table 4, the amplitude control may be performed by changing the damping force only for the damper having the damping force variable section. Even if an abnormality is observed in one of the first movable part side damper 81 and the first base side damper 82 and one of the first vibration base damper 83 and the second vibration base damper 84, a normal damper is used. Thus, the vibration table 4 can be safely stopped.

  Even in the vibration exciter K4 of the fourth embodiment configured as described above, since it is a two-mass point two-degree-of-freedom system, similarly to the vibration generator K3 of the third embodiment, the primary mode or If vibration is performed at the natural frequency of the secondary mode, the amplitude of the movable part M of the linear actuator 3 can be amplified to realize vibration with a large amplitude of the vibration table 4. Therefore, according to the shaker K4 of the present invention, it is possible to use an actuator with a small output. In addition, since it is sufficient to use the linear actuator 3 having a small output, it is possible to maximize the merit of the vibration exciter using resonance, which can reduce the power consumption without increasing the size of the device.

  Furthermore, since the vibration exciter K4 has the vibration exciter 4 mounted on the vibration floor 7 so as to be able to reciprocate, the lateral width of the vibration exciter K4 in FIG. 5 can be shortened. Can be compact.

  This is the end of the description of the embodiments of the present invention, but the scope of the present invention is not limited to the details shown or described.

2 base, 3 linear actuator, 4 vibration table, 5 spring element, 6 damper element, 6h variable damping force valve (damping force variable part), 6i on-off valve (switching part), 7 vibrating bed, 10 first spring 11 Second spring, 12 First damper, 13 Second damper, 51 Movable part side spring, 52 Base side spring, 61 Movable part side damper, 62 Base part damper, 71 First movable part side spring 72 First base side spring, 73 First vibration base spring, 74 Second vibration base spring, 81 First movable part side damper, 82 First base side damper, 83 First vibration base damper, 84 Second shaker damper, K1, K2, K3, K4 shaker, M movable part

Claims (6)

A linear actuator having a movable part capable of reciprocating in a linear direction;
A spring element that expands and contracts by reciprocating movement of the movable part;
A vibration table coupled to the spring element;
A vibration exciter comprising: a damper element coupled to the vibration exciter in parallel with the spring element and capable of suppressing reciprocation of the exciter. The vibration table includes a vibration floor on which reciprocation is loaded,
The spring element is
A first spring that transmits the reciprocating motion of the movable part to the vibrating floor;
A second spring that transmits the reciprocating motion of the vibration floor to the vibration table,
The damper element is
A first damper capable of suppressing reciprocation of the vibrating floor;
The vibration exciter according to claim 1, further comprising: a second damper capable of suppressing reciprocation of the vibration exciter. A base on which the linear actuator is mounted;
The spring element is
A movable part-side spring interposed between the excitation table and the movable part;
A base-side spring interposed between the vibration table and the base;
The damper element is
A movable part side damper interposed between the excitation table and the movable part;
The vibration exciter according to claim 1, further comprising a base-side damper interposed between the vibration exciter and the base. A base on which the linear actuator is mounted and the vibrating floor is reciprocally loaded;
The first spring is
A first movable part-side spring interposed between the vibrating floor and the movable part;
A first base side spring interposed between the vibration floor and the base;
The second spring is
A first vibration table spring interposed between one end of the vibration table and the vibration floor;
A second shaking table spring interposed between the other end of the shaking table and the vibrating floor,
The first damper is
A first movable part side damper interposed between the vibrating floor and the movable part;
A first base side damper interposed between the vibration floor and the base;
The second damper is
A first vibration table damper interposed between one end of the vibration table and the vibration floor;
The vibration exciter according to claim 2, further comprising a second vibration exciter damper interposed between the other end of the vibration exciter and the vibration floor. 5. The additive according to claim 1, wherein the damper element includes a switching portion that can be switched between a state in which a damping force is not exerted during expansion and contraction and a state in which the damping force is exerted. Shake. 6. The vibration exciter according to claim 1, wherein the damper element includes a damping force varying unit that varies a damping force exerted during expansion and contraction.

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