TW201425181A - Vibrating type parts conveyance device - Google Patents

Abstract

The present invention can maintain parts conveyance speed and at the same time suppresses pitching motion of a parts conveyance member in a compound vibrating type parts conveyance device. By setting the natural vibration value of rotational vibration (rotational vibration mode of vibration in a horizontal direction) generated in an intermediate vibration body and a base to be greater than the natural vibration value of rotational vibration (rotational vibration mode of vibration in a vertical direction) generated by a parts conveyance member and an upper vibration body, pitching motion of the parts conveyance member that is observed from ground can be suppressed without reducing the natural vibration values of a translational vibration mode of vibration in the horizontal direction so as to maintain the parts conveyance speed by adjusting the mass of the base in such a way that an amplitude (vibration level of the rotation vibration mode of vibration in the horizontal direction) of the pitching motion of the base is close to an amplitude (vibration level of rotational vibration mode of vibration in the vertical direction) of the relative pitching motion of the parts conveyance member with respect to the base.

Description

Vibrating parts conveying device

The present invention relates to a vibrating component conveying apparatus that vibrates a component conveying member by a driving of a vibration mechanism to convey a component.

In the vibrating component conveying device, the composite vibrating type is configured to provide the component conveying member with the vibration suitable for the component conveying, and the horizontal vibration is connected to the ground by the leaf spring in the vertical direction. In the base and the intermediate vibrating body, the component transfer mechanism and the intermediate vibrating body are connected by the leaf spring for the vertical vibration in the horizontal direction, and the vibration of the component transfer member in the horizontal direction and the vibration in the vertical direction can be adjusted.

However, in the composite vibration type component transporting apparatus, there is a rotational motion (hereinafter referred to as "pitch motion") around the center of gravity G of the component transporting member (including the upper vibrating body or the like). In the case where the component conveyance is unstable, it is proposed to arrange the two pieces of the leaf spring for the vertical vibration in order to prevent the pitching motion, and to arrange the frame structure together with the component conveying member and the intermediate vibrating body ( Reference is made to Patent Document 1) below.

However, even if the arrangement of the leaf springs for the vertical vibration proposed in the patent document 1 is increased or the mass is increased depending on the properties of the components to be conveyed or the structure of the components to be transported, etc., the parts are transported. The moment of the member around the center of gravity G becomes large, so there is still a situation in which the pitching motion is generated. Further, when the component transporting member has an asymmetrical shape and the position of the center of gravity G is shifted from the attraction position of the electromagnet constituting the oscillating mechanism, the attractive force acts on the position shifted from the center of gravity G, so that it attracts The force produces a moment about the center of gravity G, which produces a pitching motion.

On the other hand, the applicant of the present invention considered that the pitching motion of the component conveying member is a relative pitching motion of the component conveying member with respect to the base (hereinafter also referred to simply as "relative tilting motion") and the opposite phase. The pitching motion of the platform is combined to develop a hammer on the base, and the mass of the base is adjusted in such a manner that the amplitude of the pitch motion of the base is close to the amplitude of the relative pitch motion of the component transporting member, thereby suppressing The technique of the pitching motion of the component transporting member has been applied to this prior to the present application (Japanese Patent Application No. 2011-243393).

[Previous Technical Literature]

[Patent Literature]

[Patent Document 1] Japanese Patent Laid-Open Publication No. 2003-40418

In the above-mentioned prior application, when the moment of inertia acting on the component conveying member is large (when the component conveying member is long or the mass is large), the amplitude of the relative pitching motion of the component conveying member becomes large. Therefore, as long as the mass of the base is increased, the amplitude of the pitch motion of the base can be increased. However, in this case, since the mass of the base member is increased not only by the mass of the component conveying member but also, the number of natural vibrations in the horizontal direction in the same direction as the component conveying direction is lowered. Further, since the vibration displacement in the horizontal direction requiring a large amplitude is generally efficiently obtained, the frequency (drive frequency) of the power supply voltage waveform applied to the electromagnet is set to a frequency near the natural vibration number in the horizontal direction. Since the resonance vibration is generated, if the number of natural vibrations in the horizontal direction is lowered, the driving frequency is also lowered, and the component conveying speed is slow.

Therefore, an object of the present invention is to suppress the pitching motion of the component conveying member while maintaining the component conveying speed in the composite vibration type component conveying device.

In order to solve the above problems, the vibrating component conveying device of the present invention adopts the following structure In addition, the method includes: a component conveying member having a component conveying path; an upper vibrating body to which the component conveying member is attached; a base disposed on the ground; and an intermediate vibrating body disposed on the upper vibrating body and a first elastic member that connects the intermediate vibrating body and the base; and a second elastic member that connects the upper vibrating body and the intermediate vibrating body; and the first elastic member and the second elastic member One of the elastic members for horizontal vibration and the elastic member for vertical vibration are provided by the horizontal vibration elastic member and the first oscillating mechanism to impart vibration in the horizontal direction to the component conveying member. The elastic member for the vertical vibration and the second oscillating mechanism impart vibration in the vertical direction to the component conveying member, and the number of natural vibrations of the rotational vibration generated in the intermediate vibrating body and the base is larger than the component conveying member and the upper vibration. The number of natural vibrations of the rotational vibration generated in the body. Hereinafter, the reason why the present invention adopts the configuration will be described.

In a general vibrating parts conveying device, there are both a translational vibration mode and a rotational vibration mode. The main cause of the pitching motion is the latter's rotational vibration mode, and the natural vibration number is in the vicinity of the natural vibration number of the translational vibration mode. Further, in the composite vibration type, since it can vibrate in the horizontal direction and the vertical direction, there are a translational vibration mode and a rotational vibration mode with respect to the respective vibration directions.

Fig. 7 shows a simplified model of the composite vibrating part conveying device. The upper rigid body A of the simple model corresponds to a component transport mechanism (including an upper vibrating body). Further, the spring Ka corresponds to an elastic member for vertical vibration, the lower rigid body B corresponds to the intermediate vibrating body and the base, and the spring Kb corresponds to an anti-vibration member provided between the lower rigid body B and the floor F. Further, the center of gravity Ga represents the center of gravity of the upper rigid body A, and the center of gravity Gb represents the center of gravity of the lower rigid body B. In addition, the intermediate vibrating body and the base are actually connected by the horizontal vibration elastic member. However, since the horizontal vibration elastic member does not act in the vertical direction, it is not considered in the simple model.

In the above simple model, the pitch motion of the lower rigid body B around the center of gravity Gb is a rotational vibration mode of horizontal vibration, and the pitch motion of the upper rigid body A around the center of gravity Ga becomes a rotational vibration mode of vertical vibration. On the other hand, the driving frequency of the electromagnet is as above As described above, the vicinity of the natural vibration number of the translational vibration mode in the horizontal vibration is described.

The natural vibration number of the translational vibration mode in the horizontal direction vibration can be adjusted by changing the mass of the lower rigid body B and the configuration of the spring Kb. Similarly, the natural vibration number of the translational vibration mode in the vertical direction vibration can also be adjusted by changing the mass of the upper rigid body A and the configuration of the spring Ka. Further, although the number of natural vibrations of each of the rotational vibration modes follows the natural vibration number of the translational vibration mode, the relationship between the natural vibration and the natural vibration number of the translational vibration mode can be adjusted by changing the inertia moment. However, since the change of the moment of inertia is generally performed by changing the mass of the end portion, the adjustment of the difference between the natural vibration numbers of the translational vibration mode and the rotational vibration mode is limited.

Here, the natural vibration number of the rotational vibration mode (the rotational vibration generated in the lower rigid body B) in the horizontal direction is smaller than the natural vibration number of the rotational vibration mode (the rotational vibration generated in the upper rigid body A) in the vertical direction vibration. The relationship between the number of vibrations and the vibration level and phase is shown in Fig. 8. The vibration level of the rotational vibration mode in the horizontal direction vibration in Fig. 8 represents the pitch motion of the B1 point observed from the ground in Fig. 7, and the vibration level of the rotational vibration mode in the vertical direction vibration is shown in Fig. 7 The relative pitch motion of point A1 observed at point B1. Further, the translational vibration mode in the vertical direction vibration is not shown for simplification. Further, since the driving frequency of the electromagnet is near the natural frequency of the translational vibration mode in the horizontal vibration, the rotational vibration mode of the horizontal vibration is substantially the same as the phase of the vibration waveform of the rotational vibration mode of the vertical vibration. Therefore, the pitch motion of the component transport member (the absolute pitch motion of the A1 point observed from the ground) is the vibration level of the rotational vibration mode of the horizontal vibration and the vibration level of the rotational vibration mode of the vertical direction vibration. with.

At present, in the state of the solid line in Fig. 8, the pitching motion of the component conveying member is suppressed. When the component transfer member is replaced with a larger mass and moment of inertia in this state, the number of natural vibrations in the translational vibration and the rotational vibration mode in the vertical direction vibration is lowered (broken line in FIG. 8). Furthermore, although the number of natural vibrations in the translational and rotational vibration modes of the horizontal vibration is actually lowered, it is ignored here. At this time, due to the vertical direction vibration in the driving frequency Since the vibration level of the moving rotary vibration mode becomes large, the pitching motion of the component conveying member becomes large.

In order to suppress the increase of the pitching motion, it is considered to increase the natural vibration number of the rotational vibration mode in the horizontal direction vibration, and to reduce the vibration level of the rotational vibration mode of the horizontal direction vibration in the driving frequency, or to reduce the translation of the horizontal vibration. The natural vibration number of the vibration mode (the driving frequency of the electromagnet) is lowered, and the vibration level of the rotational vibration mode that vibrates in the vertical direction is lowered.

In the case of the former, in order to increase the number of natural vibrations of the rotational vibration mode in the horizontal direction vibration, the mass of the lower rigid body B is reduced and the moment of inertia is reduced, but as described above, it is difficult to largely separate the translational vibration mode from the rotational vibration mode. The number of natural vibrations. Therefore, the number of natural vibrations of the translational vibration mode in the horizontal direction vibration is also increased, and as the driving frequency of the electromagnet is also increased, the vibration level of the rotational vibration mode in the vertical direction vibration is further increased, and it is difficult to suppress the pitching motion.

On the other hand, in the latter case, in order to reduce the number of natural vibrations of the translational vibration mode of the horizontal vibration, the mass of the lower rigid body B is increased and the moment of inertia is increased. At this time, as shown by the broken line in FIG. 9, the number of natural vibrations of the rotational vibration mode in the horizontal direction vibration also decreases, and the vibration level thereof is almost constant, but the vibration level of the rotational vibration mode in the vertical direction vibration is lowered. Therefore, the pitching motion can be suppressed. However, in this case, since the driving frequency of the electromagnet is lowered, the component conveying speed is lowered.

Next, a case where the number of natural vibrations in the rotational vibration mode in the horizontal direction vibration is larger than the number of natural vibrations in the rotational vibration mode in the vertical direction vibration will be described. The relationship between the number of vibrations and the vibration level and phase in this case is shown in FIG. At this time, the vibration waveform of the horizontal vibration in the driving frequency of the electromagnet and the vibration waveform of the rotational vibration mode in the vertical direction are opposite phases. Therefore, the pitch motion of the component conveying member is expressed by the difference between the vibration level of the rotational vibration mode in the horizontal direction vibration and the vibration level of the rotational vibration mode in the vertical direction vibration.

In the state of the solid line in FIG. 10, the vibration level of the rotational vibration mode of the horizontal direction vibration in the drive frequency is the same as the vibration level of the rotational vibration mode of the vertical direction vibration, so that the pitch motion of the component transport member is not generated. . When the component conveying member is replaced with a larger mass and the moment of inertia in this state, the natural vibration number of the translational vibration and the rotational vibration mode in the vertical direction vibration becomes low (broken line in FIG. 10). Furthermore, the number of natural vibrations of the translational and rotational vibration modes of the horizontally driven drive is also reduced, but it is ignored here. At this time, since the vibration level of the rotational vibration mode in the horizontal direction vibration in the driving frequency is different from the vibration level of the rotational vibration mode in the vertical direction vibration, the pitch motion of the component conveying member occurs.

In order to suppress the above-described pitching motion, as shown by the broken line in FIG. 11, the number of natural vibrations of the rotational vibration mode in the horizontal direction vibration is increased, and the vibration level of the rotational vibration mode in the horizontal direction vibration of the driving frequency of the electromagnet is made. The vibration level of the rotational vibration mode vibrating in the vertical direction may be the same level. At this time, the natural vibration number of the translational vibration mode in the horizontal direction vibration is also improved, but as described above, the relationship between the translational vibration mode and the natural vibration number of the rotational vibration mode is slightly changed, so that the horizontal direction vibration and the vertical direction vibration can be performed. The vibration level of the rotary vibration mode is set to the same level, and the pitch motion is suppressed. Further, in this case, since the number of natural vibrations of the translational vibration mode in the horizontal direction vibration, that is, the driving frequency of the electromagnet is not lowered, the component conveying speed can be maintained.

According to the above, in the present invention, the number of natural vibrations in the rotational vibration mode in which the horizontal direction vibrates (the rigid body B in the lower portion of FIG. 7 is the rotational vibration generated in the intermediate vibrating body and the base) is larger than the rotation in the vertical direction. The number of natural vibrations in the vibration mode (the rigid body A in the upper part of FIG. 7 , that is, the rotational vibration generated in the component conveying member and the upper vibrating body) can suppress the pitching motion of the component conveying member while maintaining the component conveying speed.

In the above configuration, it is preferable to provide a hammer on the base. The reason is that the number of natural vibrations of the rotational vibration generated in the intermediate vibrating body and the base can be easily adjusted by changing the mass of the hammer.

In the case where the vibration-proof member is provided between the base and the ground, the base is adjusted so that the amplitude of the pitch motion of the base approaches the amplitude of the relative pitch motion of the component transport member relative to the base. The quality of the station can be.

Here, the hammer may be formed by including a plurality of hammers, and the mass can be adjusted by increasing or decreasing the number of the hammers, and is preferably provided at the end of the base. The reason is that the farther the mass of the abutment changes from the center of gravity, the greater the influence of the increase and decrease of the mass on the amplitude of the pitching motion, and the easier the quality adjustment.

Further, it is preferable that the hammer is provided in a plurality of portions. The reason is that if only the mass of one part of the base is changed, the center of gravity of the base moves, and the center of the pitch motion is shifted, which makes it difficult to adjust. However, if the number of the hammers is set to plural, the base can be used. The center of gravity does not move to adjust the quality of the hammer. Conversely, by adjusting the mass of the hammer provided at a plurality of locations, the position of the center of gravity of the base is moved to the vicinity of the center of the apparatus, and the transport behavior can be stabilized. Further, even if the installation position of the hammer can be adjusted to the vertical direction, the center of gravity of the base can be moved to the vicinity of the center of the apparatus to obtain a stable conveyance behavior.

The horizontal vibration elastic member may be disposed such that the fixed position of the intermediate vibrating body and the fixed position of the base or the upper vibrating body are located on the same horizontal line orthogonal to the component transport direction. In this case, the horizontal direction deformation of the elastic member for horizontal vibration is independent of the displacement in the vertical direction, and the vibration in the vertical direction due to the vibration in the horizontal direction is suppressed. In this case, a plurality of the horizontal vibration elastic members are provided in the component conveying direction, and the positional relationship between the fixed position of the intermediate vibrating body and the fixed position of the base or the upper vibrating body is carried out on the parts. When the directions are arranged in a staggered manner, the vibration in the direction orthogonal to the component conveying direction in the horizontal plane can be suppressed, so that the conveying behavior can be made more stable.

On the other hand, the elastic member for vertical vibration may be fixed at two fixed positions on the same horizontal line orthogonal to the component conveying direction, or may be fixed at two fixed positions on the same horizontal line parallel to the component conveying direction.

The electromagnet and the movable iron core constitute the above-mentioned respective vibration oscillating mechanisms, and in the voltage application circuit for one of the electromagnets, a reference wavelength generating device that generates a reference waveform for applying a voltage, and a waveform for adjusting the amplitude of the reference waveform are provided. The amplitude adjusting device is configured to provide a phase difference adjusting device that generates a waveform having a specific phase difference with respect to the reference waveform, and a waveform for adjusting a waveform amplitude generated by the phase difference adjusting device in an applied voltage setting circuit for another electromagnet The amplitude adjusting device can freely control the waveform, period, phase difference, and amplitude of the applied voltage to each electromagnet, and thus, the horizontal vibration and the vertical vibration can be easily brought close to the desired vibration.

Further, in the voltage application circuit for the electromagnets of the respective vibration oscillating mechanisms, a PWM for converting a waveform whose amplitude has been adjusted by the respective waveform amplitude adjustment devices into a PWM (Pulse Width Modulation) signal is provided. The signal generating device can drive the vibration absorbing mechanisms in a PWM manner.

In the vibration type component conveying apparatus of the present invention, the number of natural vibrations of the rotational vibration generated in the intermediate vibrating body and the base is larger than the number of natural vibrations generated by the component conveying member and the upper vibrating body as described above, so that it can be maintained The component transport speed suppresses the pitch motion of the component transport member as viewed from the ground, and the desired vibration can be easily imparted to the component transport member, thereby achieving stable component transport.

1‧‧‧ slot (part transfer member)

1a‧‧‧Transportation path

2‧‧‧Upper vibrating body

3‧‧‧Abutment

3a‧‧‧ leaf spring installation

4‧‧‧Intermediate vibrating body

4a‧‧‧ leaf spring installation

5‧‧‧1st leaf spring (spring spring for horizontal vibration)

6‧‧‧2nd leaf spring (leaf spring for vertical vibration)

7‧‧‧1st vibration-increasing mechanism

8‧‧‧2th damper mechanism

9‧‧‧Electromagnet

10‧‧‧ movable iron core

11‧‧‧Electromagnet

12‧‧‧ movable iron core

13‧‧‧Reference waveform generating device

14‧‧‧ phase difference adjustment device

15‧‧‧ Waveform amplitude adjustment device

16‧‧‧PWM signal generating device

17‧‧‧Voltage Amplifier Parts

18‧‧‧Anti-vibration rubber (anti-vibration member)

19‧‧‧ Hammer

19a‧‧‧ Hammer

A‧‧‧Upper rigid body

B‧‧‧Lower rigid body

F‧‧‧ Ground

Ga‧‧‧ center of gravity

Gb‧‧‧ center of gravity

Ka‧‧ ‧ spring

Kb‧‧ spring

Fig. 1 is a partially cutaway front elevational view of the component transport apparatus of the embodiment.

Figure 2 is a plan view of the groove other than the groove of Figure 1.

Figure 3 is a side view of Figure 1.

Fig. 4 is a schematic view showing an applied voltage setting circuit of each of the oscillating mechanisms of the component transporting apparatus of Fig. 1.

Fig. 5 is a partially cutaway front elevational view showing a modification of the arrangement of the leaf spring for the vertical vibration of Fig. 1.

Figure 6 is a plan view of the groove other than the groove of Figure 5.

Fig. 7 is a front view showing a simplified model of the component transporting apparatus for explaining the action of the present invention.

Fig. 8 is a graph showing the amplification behavior of the pitching motion of the general component conveying device.

Fig. 9 is a graph showing the method of suppressing the pitching motion of Fig. 8.

Fig. 10 is a graph showing the behavior of the pitching motion of the component transporting apparatus of the present invention.

Fig. 11 is a graph showing the method of suppressing the pitching motion of Fig. 10.

Hereinafter, embodiments of the present invention will be described based on the drawings. As shown in FIG. 1 to FIG. 3, the vibrating component conveying apparatus is such that a groove (part conveying member) 1 in which a linear conveying path 1a is formed is attached to the upper surface of the upper vibrating body 2, and the upper vibrating body is attached. 2, the intermediate vibrating body 4 is provided between the base 3 provided on the ground, and the intermediate vibrating body 4 and the base 3 are connected by two leaf springs 5 as the first elastic members, and four plates are used as the second elastic members. The spring 6 connects the upper vibrating body 2 and the intermediate vibrating body 4, and the first vibrating mechanism 7 that generates vibration in the horizontal direction (the component conveying direction and the X direction in the drawing) is provided between the intermediate vibrating body 4 and the base 3. A second vibration absorbing mechanism 8 that generates vibration in the vertical direction (Z direction in the drawing) is provided between the upper vibrating body 2 and the base 3.

The base 3 is formed in a rectangular shape, and a columnar leaf spring mounting portion 3a is provided at two corners of the diagonal, and is supported by a vibration-proof rubber (anti-vibration member) 18 fixed to the floor surface F. Further, a spiral spring or the like can also be used as the vibration isolating member.

Further, a hammer 19 is provided at each of both ends of the component 3 in the conveying direction of the base 3. Each of the hammers 19 is constituted by a plurality of hammer pieces 19a that are detachable, and the mass adjuster can be realized by increasing or decreasing the number of the hammer pieces 19a. Here, although the illustration is omitted, the method of attaching the hammer 19 to the base 3 may be a method in which a through hole is provided in each of the hammer pieces 19a and screwed by a bolt or the like. At this time, will The plurality of screw holes provided in the base 3 are arranged in the height direction, and the mounting position of the hammer 19 to the base 3 can be adjusted in the vertical direction, whereby the position of the center of gravity of the base 3 can be easily moved to the vicinity of the center of the device. Or avoid interference between the hammer 19 and other machines in order to stabilize the transport behavior. Further, in this embodiment, the hammer 19 is constituted by a plurality of hammer pieces 19a, but a hammer having a desired mass of a single body may be used.

The intermediate vibrating body 4 is formed in a rectangular frame shape, and the opposite corners thereof face the upper end portion of the leaf spring mounting portion 3a of the base 3 on the outer peripheral side, and the inner peripheral surface faces the lower portion of the upper vibrating body 2 The way it is configured. Further, a leaf spring mounting portion 4a that protrudes from the opposite corners of the leaf spring mounting portion 3a of the base 3 in the component conveying direction (X direction) is provided on the outer peripheral surface thereof.

The first leaf spring 5 is a horizontally driven leaf spring (horizontal vibration elastic member), that is, the front and back surfaces are oriented toward the component transporting direction, and the fixed positions of the both ends are located on the same horizontal line orthogonal to the component transporting direction. In this manner, the one end portion is fixed to the leaf spring mounting portion 3a of the base 3, and the other end portion is fixed to the leaf spring mounting portion 4a of the intermediate vibrating body 4, and the intermediate vibrating body 4 is supported to be vibrated in the horizontal direction. Here, the two leaf spring attachment portions 3a of the base 3 and the two leaf spring attachment portions 4a of the intermediate vibrating body 4 are disposed such that the straight lines connecting the installation positions of the same mounting portion are arranged in a plan view, so that two levels are provided. The vibration leaf spring 5 is disposed so as to be staggered in the component conveying direction in a positional relationship between the two fixed positions.

On the other hand, the second leaf spring 6 is a leaf spring for vertical drive (elastic member for vertical vibration), that is, the front and back faces are oriented in the vertical direction, and the fixed positions at both ends are located in the direction in which the components are conveyed. One end portion is fixed to the lower portion of the upper vibrating body 2, and the other end portion is fixed to the longitudinal direction edge portion of the intermediate vibrating body 4, and the upper vibrating body 2 is supported in the vertical direction. vibration.

Further, the first vibration absorbing mechanism 7 is composed of an alternating current electromagnet 9 provided on the base 3 and a movable iron core 10 attached to the intermediate vibrating body 4 so as to face the electromagnet 9 at a predetermined interval. Furthermore, the movable iron core 10 is attached to the intermediate vibrating body 4 in this example, but it can also be mounted. Mounted on the upper vibrating body 2. On the other hand, the second vibration absorbing mechanism 8 is composed of an alternating current electromagnet 11 provided on the base 3 and a movable iron core 12 attached to the upper vibrating body 2 so as to face the electromagnet 11 at a predetermined interval. .

When the electromagnet 9 of the first oscillating mechanism 7 is energized, an intermittent electromagnetic attraction force acts between the electromagnet 9 and the movable iron core 10, and the restoring force of the electromagnetic attraction force and the horizontal vibration leaf spring 5 is exerted. On the other hand, the intermediate vibrating body 4 generates vibration in the horizontal direction, and the vibration is transmitted to the upper vibrating body 2 and the groove 1 via the vertical vibration plate spring 6. When the electromagnet 11 of the second vibration absorbing mechanism 8 is energized, an intermittent electromagnetic attraction force acts between the electromagnet 11 and the movable iron core 12, and the electromagnetic attraction force and the leaf spring 6 for vertical vibration are utilized. The restoring force generates vibration in the vertical direction in the upper vibrating body 2 and the groove 1. Further, the components supplied to the groove 1 are conveyed along the linear transport path 1a by the vibration in the horizontal direction and the vibration in the vertical direction.

Therefore, by setting the voltages applied to the electromagnets 9 and 11 of the respective oscillating mechanisms 7 and 8, the vibration in the horizontal direction and the vibration in the vertical direction of the groove 1 can be adjusted.

Fig. 4 shows a circuit for applying a voltage to the electromagnets 9, 11 of the respective oscillating mechanisms 7, 8. In the circuit of the first oscillating mechanism 7, a reference waveform generating device 13 that generates a reference waveform of an applied voltage is provided. The reference waveform generating device 13 generates a reference waveform corresponding to the type of the waveform (for example, a sine wave) and the set value of the period (frequency) of the waveform. On the other hand, in the circuit of the second vibration absorbing mechanism 8, a phase difference adjusting device 14 that generates a waveform having a specific phase difference with respect to the reference waveform generated by the reference waveform generating device 13 is provided.

Further, in the circuits of the respective vibration oscillating mechanisms 7, 8, the waveform generated by the reference waveform generating device 13 or the phase difference adjusting device 14 is adjusted to a specific amplitude by the waveform amplitude adjusting device 15, and is converted by the PWM signal generating device 16. After being the PWM signal, it is boosted by the voltage amplifying device 17 and applied to the respective electromagnets 9, 11. Thereby, the waveform, the period, the phase difference, and the amplitude of the applied voltage to the electromagnets 9 and 11 can be freely controlled, and the vibration in the horizontal direction and the vibration in the vertical direction can be adjusted. Furthermore, the PWM signal generating device 16 is not required when the vibration absorbing mechanisms are not driven by the PWM method.

Further, as a whole of the apparatus, the number of natural vibrations of the rotational vibration (rotational vibration mode of the horizontal vibration) generated in the intermediate vibrating body 4 and the base 3 is adjusted to be larger than the rotational vibration generated in the groove 1 and the upper vibrating body 2 The number of natural vibrations (rotational vibration mode in the vertical direction vibration). The natural vibration number of the rotational vibration mode in the horizontal direction vibration is adjusted by changing the fixed length, the thickness, the number of sheets of the horizontal vibration leaf spring 5, or the moment of inertia of the base 3 and the intermediate vibrating body 4. On the other hand, the natural vibration number of the rotational vibration mode in the vertical direction vibration is changed by the fixed length, the thickness, the number of sheets, or the inertia moment of the groove 1 and the upper vibrating body 2 of the leaf spring 6 for the vertical vibration. Adjustment.

In addition, in many cases, since the groove 1 is mounted by a customer, it is difficult to change the inertia moment of each member such as the specifications of the leaf springs 5 and 6 or the upper vibrating body 2 . Therefore, it is preferable to perform the above-described adjustment in the range of the mass and the moment of inertia of the tank 1 assumed to be mounted by the customer before shipment, and to install only the base 3 according to the slot 1 mounted by the customer. The adjustment of the hammer 19 can achieve the suppression of the pitching motion.

In the above-described configuration, the vibrating component transporting device is configured to be horizontally vibrated at two fixed positions on the same horizontal line orthogonal to the component transporting direction when the intermediate vibrating body 4 vibrates by the driving of the first vibrating mechanism 7. The leaf spring 5 is repeatedly subjected to an action of deforming only in the horizontal direction and returning to the original state. Thereby, the vibration generated in the intermediate vibrating body 4 hardly includes the vibration in the vertical direction, and is substantially only the vibration in the horizontal direction. In addition, since the positional relationship between the fixed positions of the two horizontal vibration leaf springs 5 is staggered in the component conveying direction, the direction orthogonal to the component conveying direction in the horizontal plane can be suppressed (Y in FIGS. 2 and 3). Direction) vibration.

Further, since the vibration-proof rubber 18 is provided between the base 3 and the floor F, the hammer 19 including the plurality of hammer pieces 19a is provided on the base 3, and the rotational vibration generated in the intermediate vibrating body 4 and the base 3 is provided. Since the number of natural vibrations is larger than the number of natural vibrations of the rotational vibration generated in the groove 1 and the upper vibrating body 2, the amplitude of the pitching motion of the base 3 is close to the opposite side of the groove 1 relative to the base 3 The amount of the hammer piece 19a is increased or decreased by the amplitude of the pitching motion to adjust the base The mass of the table 3 can surely suppress the pitching motion of the groove 1 observed from the ground, and can realize stable parts transportation. Further, when the mass of the base 3 is adjusted to suppress the pitching motion of the groove 1, the component transport speed can be maintained (see FIG. 11).

Fig. 5 and Fig. 6 show a variation of the arrangement of the leaf springs for the vertical vibration of the above embodiment. In this modification, the leaf spring 6 for vertical vibration is fixed to the short side of the upper vibrating body 2 and the intermediate vibrating body 4 at two fixed positions on the same horizontal line parallel to the component conveying direction (X direction in the drawing). Direction edge.

In the above-described embodiment, the first leaf spring that connects the intermediate vibrating body and the base is used as a leaf spring for horizontal vibration, and the second leaf spring that connects the upper vibrating body and the intermediate vibrating body is used as a leaf spring for vertical vibration. On the other hand, the first leaf spring is a leaf spring for vertical vibration, and the second leaf spring is a leaf spring for horizontal vibration. Further, the leaf springs are disposed in each unit in units of one sheet, but one or two or more sheets may be used as one.

Further, the horizontal vibration leaf springs are disposed at two locations, but may be configured in three or more locations. In this case, the positional relationship between the fixed position of the intermediate vibrating body and the fixed position of the base is also in the component transport direction. It can be configured in a staggered manner. On the other hand, the leaf spring for the vertical vibration is disposed at four locations, but it may be configured of two or more locations.

Further, in the embodiment, the leaf spring is used for the horizontal vibration elastic member and the vertical vibration elastic member, but of course, an elastic member other than the leaf spring may be used. Further, each of the damper mechanisms includes an electromagnet and a movable iron core. However, the present invention is not limited thereto, and any actuator that generates the same oscillating force may be used.

Claims (9)

A vibrating component conveying device comprising: a component conveying member having a component conveying path; an upper vibrating body to which the component conveying member is attached; a base provided on the floor; and an intermediate vibrating body provided on the above Between the upper vibrating body and the base; the first elastic member connecting the intermediate vibrating body and the base; and the second elastic member connecting the upper vibrating body and the intermediate vibrating body; and the first elastic member and the first elastic member One of the second elastic members is a horizontal vibration elastic member, and the other is a vertical vibration elastic member, and the horizontal vibration elastic member and the first vibration absorbing mechanism impart vibration in the horizontal direction to the component transfer member. The vertical vibration member and the second vibration absorbing mechanism apply vibration to the component conveying member in the vertical direction. The vibration type component conveying device is characterized in that the intermediate vibration body and the rotary vibration generated in the base are The number of natural vibrations is set to be larger than the number of natural vibrations of the rotational vibration generated in the component transporting member and the upper vibrating body. The vibrating part conveying device of claim 1, wherein the base is provided with a hammer. The vibrating component conveying device of claim 1 or 2, wherein an anti-vibration member is disposed between the base and the ground, wherein an amplitude of the pitching motion of the base is close to a relative longitudinal direction of the component conveying member relative to the base The mass of the base is adjusted by shaking the amplitude of the motion. The vibrating component conveying apparatus according to claim 1 or 2, wherein the horizontal vibration elastic member is located orthogonal to the component conveying direction such that the fixed position of the intermediate vibrating body and the fixed position of the base or the upper vibrating body are orthogonal to the component conveying direction Configured on the same horizontal line. The vibrating component conveying device according to claim 4, wherein the horizontal vibration elastic member is provided in plural in the component conveying direction, and each of the intermediate vibrations is provided The positional relationship between the fixed position of the movable body and the fixed position of the base or the upper vibrating body is arranged to be staggered in the component conveying direction. The vibrating component conveying device according to claim 1 or 2, wherein the vertical vibration elastic member is fixed to two fixed positions on the same horizontal line orthogonal to the component conveying direction. The vibrating component conveying apparatus according to claim 1 or 2, wherein the vertical vibration elastic member is fixed to two fixed positions on the same horizontal line parallel to the component conveying direction. The vibrating component conveying device according to claim 1 or 2, wherein the electromagnet and the movable iron core constitute the respective vibration oscillating mechanisms, and in a voltage setting circuit for one of the electromagnets, a reference waveform for generating an applied voltage is provided. a reference waveform generating device and a waveform amplitude adjusting device for adjusting an amplitude of the reference waveform; and a phase difference adjusting device for generating a waveform having a specific phase difference with respect to the reference waveform, in an applied voltage setting circuit for another electromagnet, And a waveform amplitude adjusting device for adjusting the amplitude of the waveform generated by the phase difference adjusting device. The vibrating component transporting apparatus according to claim 8, wherein the applied voltage setting circuit of the electromagnets of the respective vibrating mechanisms is provided with a waveform for converting amplitudes adjusted by the respective waveform amplitude adjusting devices into PWM signals. PWM signal generating device.