WO2014057857A1

WO2014057857A1 - Vibrating parts transport device

Info

Publication number: WO2014057857A1
Application number: PCT/JP2013/076913
Authority: WO
Inventors: 石河　智海
Original assignee: Ntn株式会社
Priority date: 2012-10-10
Filing date: 2013-10-03
Publication date: 2014-04-17
Also published as: JP6153308B2; CN104736460B; TW201425181A; JP2014076881A; CN104736460A; TWI585018B; KR20150065707A

Abstract

A complex vibrating type parts transport device that can maintain the parts transport speed and suppress pitching motion of a parts transport member (1). After increasing the eigenfrequency of the rotational vibration (rotational vibration mode for vibration in the horizontal direction) generated in an intermediate vibrating body (4) and a base (3) to be greater than the eigenfrequency of a rotational vibration (rotational vibration mode for vibration in the vertical direction) generated in the parts transport member (1) and a upper vibrating body (2), the pitching motion of the parts transport member (1), viewed from the floor, can be suppressed and the parts transport speed can be maintained without a decrease in the eigenfrequency of a translational vibration mode for vibration in the horizontal direction by adjusting the mass of the base (3) so that the amplitude of the pitching motion (vibration level of the rotational vibration mode for vibration in the horizontal direction) of the base (3) is near the amplitude of the relative pitching motion (vibration level of the rotational vibration mode for vibration in the vertical direction) corresponding to the base (3) of the parts transport member (1).

Description

Vibrating parts conveyor

The present invention relates to a vibration type component conveying apparatus that conveys a component by vibrating a component conveying member by driving an excitation mechanism.

In the vibration type parts conveying device, a base and an intermediate vibrator installed on the floor with a horizontal vibration leaf spring directed in the vertical direction for the purpose of imparting an optimum vibration to the parts conveying member to the parts conveying And the component conveying member and the intermediate vibrating body are connected by a vertical vibration leaf spring directed in the horizontal direction, so that the horizontal vibration and the vertical vibration of the component conveying member can be adjusted respectively. There is a vibration type.

By the way, in such a composite vibration type component transport apparatus, a rotational motion (hereinafter referred to as “pitching motion”) around the center of gravity G of a component transport member (including an upper vibrator attached to the component transport member) occurs. Parts conveyance may become unstable, and in order to prevent this pitching movement, the vertical vibration leaf springs are made into one set, and arranged so as to constitute a ramen structure together with the parts conveying member and the intermediate vibrating body. Has been proposed (see Patent Document 1 below).

However, even if the arrangement of the vertical vibration leaf springs proposed in Patent Document 1 is used, if the component conveying member becomes longer or the mass increases due to the property of the component to be conveyed, the structure of the component supply partner, etc. Since the moment around the center of gravity G of the conveying member increases, a pitching motion may occur. Further, when the component conveying member has an asymmetric shape and the position of the center of gravity G is deviated from the attracting position of the electromagnet constituting the vibrating mechanism, the attraction force acts on the position deviated from the center of gravity G. A moment around the center of gravity G is generated by the force, and a pitching motion is generated.

On the other hand, the applicant of the present invention is that the pitching motion of the component transporting member is a relative pitching motion with respect to the base of the component transporting member (hereinafter also simply referred to as “relative pitching motion”), and a phase opposite to this. The weight of the base is adjusted so that the amplitude of the pitching motion of the base approaches the amplitude of the relative pitching motion of the parts conveying member. Thus, a technology for suppressing the pitching motion of the component conveying member was developed, and this was filed prior to this application (Japanese Patent Application No. 2011-243393).

Japanese Patent Laid-Open No. 2003-40418

In the above 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. The mass of the base should be increased to increase the amplitude of the pitching motion of the base. However, in this case, not only the component conveying member but also the mass of the base increases, so that the natural frequency in the horizontal direction, which is the same direction as the component conveying direction, decreases. Normally, the frequency (drive frequency) of the power supply voltage waveform applied to the electromagnet is set to a frequency in the vicinity of the natural frequency in the horizontal direction so that a horizontal vibration displacement requiring a large amplitude can be obtained efficiently. Since resonance vibration is generated, if the natural frequency in the horizontal direction is lowered, the drive frequency is also lowered, and the component conveying speed is reduced.

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

In order to solve the above problems, the present invention provides a component conveying member in which a component conveying path is formed, an upper vibrating body to which the component conveying member is attached, a base installed on a floor, and the upper vibrating body. An intermediate vibrating body provided between the base, a first elastic member connecting the intermediate vibrating body and the base, and a second elastic member connecting the upper vibrating body and the intermediate vibrating body. One of the first elastic member and the second elastic member 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 mechanism are used as parts. In the vibration-type component conveying apparatus that applies a horizontal vibration to the conveying member and applies a vertical vibration to the component conveying member by the vertical vibration elastic member and the second vibration mechanism. The natural frequency of the rotational vibration generated in the body and base Employing the configuration is larger than the natural frequency of the rotational vibration generated in the workpiece transport member and the upper vibration member. The reason why the present invention employs this configuration will be described below.

There are two types of vibration parts conveying devices in general: a mode that vibrates in translation and a mode that vibrates in rotation. It is the latter rotational vibration mode that causes the pitching motion, and its natural frequency is in the vicinity of the natural frequency of the translational vibration mode. Since the composite vibration type can vibrate in the horizontal direction and the vertical direction, there is a translational vibration mode and a rotational vibration mode for each vibration direction.

Fig. 7 shows a simplified model of a composite vibration type parts conveying device. The upper rigid body A in this simple model corresponds to a component conveying member (including the upper vibrating body). The spring Ka corresponds to an elastic member for vertical vibration, the lower rigid body B corresponds to an intermediate vibration body and a base, and the spring Kb corresponds to a vibration isolating member provided between the lower rigid body B and the floor surface F. 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 practice, the intermediate vibrating body and the base are connected by an elastic member for horizontal vibration, but the horizontal vibration elastic member does not act in the vertical direction and is not considered in this simple model.

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

The natural frequency of the translational vibration mode of horizontal vibration can be adjusted by changing the mass of the lower rigid body B and the configuration of the spring Kb. Similarly, the natural frequency of the translational vibration mode of the vertical vibration can be adjusted by changing the mass of the upper rigid body A and the configuration of the spring Ka. Note that the natural frequency of each rotational vibration mode follows the natural frequency of the translational vibration mode, but the relationship with the natural frequency of the translational vibration mode can be adjusted by changing the moment of inertia. However, since it is common to change the mass of the end to change the moment of inertia, there is a limit to the adjustment of the difference in natural frequency between the translational vibration mode and the rotational vibration mode.

Here, the natural frequency of the rotational vibration mode of horizontal vibration (rotational vibration generated in the lower rigid body B) is smaller than the natural frequency of the rotational vibration mode of vertical vibration (rotational vibration generated in the upper rigid body A). In this case, the relationship between the vibration frequency, vibration level, and phase is as shown in FIG. In FIG. 8, the vibration level of the rotational vibration mode of the horizontal vibration in FIG. 7 is the pitching motion at point B1 as viewed from the floor in FIG. 7, and the vibration level of the rotational vibration mode of the vertical vibration in FIG. Each shows the relative pitching motion. For simplification, the translational vibration mode of the vertical vibration is not shown. Further, since the driving frequency of the electromagnet is in the vicinity of the natural frequency of the translational vibration mode in the horizontal vibration, the phase of the vibration waveform of the rotational vibration mode of the horizontal vibration and the rotational vibration mode of the vertical vibration is substantially the same. Therefore, the pitching motion (absolute pitching motion at point A1 as viewed from the floor) of the component conveying member is the sum of the vibration level of the rotational vibration mode of horizontal vibration and the vibration level of the rotational vibration mode of vertical vibration.

Now, it is assumed that the pitching motion of the component conveying member is suppressed in the state of the solid line in FIG. When the component conveying member is replaced with one having a large mass and moment of inertia in this state, the natural frequency of the vertical vibration translation and the rotational vibration mode is reduced (broken line in FIG. 8). In practice, the natural frequency of the horizontal vibration translation and the rotational vibration mode also decreases, but is ignored here. At this time, since the vibration level in the rotational vibration mode of the vertical vibration at the drive frequency is increased, the pitching motion of the component conveying member is increased.

To suppress the amplification of the pitching motion described above, increase the natural frequency of the rotational vibration mode of the horizontal vibration to reduce the vibration level of the rotational vibration mode of the horizontal vibration at the drive frequency, or translate the horizontal vibration. It is conceivable to reduce the vibration level of the rotational vibration mode of the vertical vibration by lowering the natural frequency of the vibration mode (driving frequency of the electromagnet).

In the former case, in order to increase the natural frequency of the rotational vibration mode of horizontal vibration, the mass of the lower rigid body B is reduced to reduce the moment of inertia, but as described above, the translational vibration mode and the rotational vibration mode It is difficult to keep the natural frequency of Therefore, the natural frequency of the translational vibration mode of the horizontal vibration is also increased, and the driving frequency of the electromagnet is also increased accordingly. Therefore, the vibration level of the rotational vibration mode of the vertical vibration is further increased and the pitching motion is suppressed. It is difficult.

On the other hand, in the latter case, in order to reduce the natural frequency of the translational vibration mode of the horizontal vibration, the mass of the lower rigid body B is increased to increase the moment of inertia. At this time, as shown by the broken line in FIG. 9, the natural frequency of the rotational vibration mode of the horizontal vibration is also lowered, and the vibration level is almost the same, but the vibration level of the rotational vibration mode of the vertical vibration is lowered. Pitching motion can be suppressed. In this case, however, the drive frequency of the electromagnet is lowered, so that the component conveyance speed is lowered.

Next, the case where the natural frequency of the rotational vibration mode of horizontal vibration is made larger than the natural frequency of the rotational vibration mode of vertical vibration will be described. The relationship between the vibration frequency, vibration level and phase in this case is shown in FIG. At this time, the vibration waveforms of the rotational vibration mode of horizontal vibration and the rotational vibration mode of vertical vibration at the driving frequency of the electromagnet have opposite phases. Accordingly, the pitching motion of the component conveying member is represented by the difference between the vibration level in the horizontal vibration mode and the vertical vibration mode.

In the state of the solid line in FIG. 10, since the vibration level of the rotational vibration mode of horizontal vibration and the vibration level of the rotational vibration mode of vertical vibration at the driving frequency are the same, no pitching motion of the component conveying member occurs. When the component conveying member is replaced with one having a large mass and moment of inertia in this state, the natural frequency in the translational and rotational vibration modes of the vertical vibration is lowered (broken line in FIG. 10). In practice, the natural frequency of the horizontal vibration translation and the rotational vibration mode also decreases, but is ignored here. At this time, there is a difference between the vibration level of the rotational vibration mode of horizontal vibration and the vibration level of the rotation vibration mode of vertical vibration at the drive frequency, so that a pitching motion of the component conveying member occurs.

In order to suppress the above pitching motion, as shown by a broken line in FIG. 11, the natural frequency of the rotational vibration mode of the horizontal vibration is increased and the vibration level of the rotational vibration mode of the horizontal vibration at the driving frequency of the electromagnet is increased. And the vibration level in the rotational vibration mode of the vertical vibration may be set to the same level. At this time, the natural frequency of the translational vibration mode of the horizontal vibration also increases. However, as described above, the relationship between the natural frequency of the translational vibration mode and the rotational vibration mode can be slightly changed. It is possible to suppress the pitching motion by setting the vibration level in the rotational vibration mode to the same level. In addition, in this case, the natural frequency of the translational vibration mode of the horizontal vibration, that is, the driving frequency of the electromagnet does not decrease, so that the component conveyance speed can be maintained.

From the above, in the present invention, the natural frequency of the rotational vibration mode of horizontal vibration (rotational vibration generated in the lower rigid body B, that is, the intermediate vibration body and the base) in FIG. It is possible to suppress the pitching motion of the component conveying member while maintaining the component conveying speed by making it larger than the natural frequency of the upper rigid body A in FIG. 7, that is, the rotational vibration generated in the component conveying member and the upper vibrating body. It was.

In the above configuration, it is desirable to provide a weight on the base. This is because the natural frequency of the rotational vibration generated in the intermediate vibrator and the base can be easily adjusted by changing the mass of the weight.

When a vibration isolating member is provided between the base and the floor surface, the base is arranged so that the amplitude of the pitching motion of the base approaches the amplitude of the pitching motion relative to the base of the component conveying member. What is necessary is just to adjust the mass of.

Here, the weight is composed of a plurality of weight pieces, and the mass can be adjusted by increasing / decreasing the number of the weight pieces, and is preferably provided at the end of the base. This is because as the portion that changes the mass of the base is farther from the center of gravity, the influence of the increase / decrease in the mass on the amplitude of the pitching motion increases, and mass adjustment becomes easier.

Moreover, it is desirable to provide the weights at a plurality of locations. If the mass is changed at only one location on the base, the center of gravity of the base moves, and the center of the pitching movement is shifted, making adjustment difficult. However, if multiple weights are installed, the center of gravity of the base will not move. This is because the mass of the weight can be adjusted. Conversely, by adjusting the mass of the weights provided at a plurality of locations and moving the position of the center of gravity of the base to the vicinity of the center of the apparatus, it is possible to stabilize the transport behavior. Further, even if the installation position of the weight can be adjusted in the vertical direction, the center of gravity of the base can be moved to the vicinity of the center of the apparatus so that a stable transport behavior can be obtained.

The elastic member for horizontal vibration may be arranged such that the fixed position to the intermediate vibrator and the fixed position to the base or the upper vibrator are located on the same horizontal line orthogonal to the component conveying direction. In this way, the horizontal deformation of the horizontal vibration elastic member is not connected to the vertical displacement, and the occurrence of vertical vibration due to the horizontal vibration is suppressed. At this time, a plurality of the horizontal vibration elastic members are provided in the component conveying direction, and the positional relationship between the fixed position to the intermediate vibrating body and the fixed position to the base or the upper vibrating body alternately in the component conveying direction. If it arrange | positions so that it may replace | exchange, since the vibration of the direction orthogonal to a components conveyance direction can also be suppressed in a horizontal surface, a conveyance behavior can be stabilized further.

On the other hand, the elastic member for vertical vibration is fixed at two fixed positions on the same horizontal line orthogonal to the component conveying direction, or fixed at two fixed positions on the same horizontal line parallel to the component conveying direction. That's fine.

Each excitation mechanism is composed of an electromagnet and a movable iron core, a reference waveform generating means for generating a reference waveform of an applied voltage in an applied voltage setting circuit to one of the electromagnets, and an amplitude with respect to the reference waveform Waveform amplitude adjusting means for adjusting is provided, and the applied voltage setting circuit for the other electromagnet is generated by the phase difference adjusting means for generating a waveform having a predetermined phase difference with respect to the reference waveform, and the phase difference adjusting means By providing waveform amplitude adjustment means to adjust the amplitude of the waveform so that the waveform, period, phase difference and amplitude of the voltage applied to each electromagnet can be controlled freely, horizontal vibration and vertical vibration Can be easily brought close to the desired vibration.

In addition, the voltage setting circuit for applying voltage to the electromagnet of each of the excitation mechanisms is provided with PWM signal generating means for converting a waveform whose amplitude is adjusted by the waveform amplitude adjusting means into a PWM (Pulse Width Modulation) signal, Each excitation mechanism can be driven by the PWM method.

As described above, the vibration-type component conveying device of the present invention has a natural frequency of the rotational vibration generated in the intermediate vibrating body and the base more than the natural frequency of the rotational vibration generated in the component conveying member and the upper vibrating body. Since it is enlarged, the pitching motion of the component conveying member viewed from the floor can be suppressed while maintaining the component conveying speed, and as a result, desired vibration can be easily applied to the component conveying member and stable component conveying. Can be realized.

Partially cutaway front view of the component conveying apparatus of the embodiment Top view without trough in FIG. Side view of FIG. Schematic diagram of an applied voltage setting circuit of each excitation mechanism of the component conveying apparatus of FIG. FIG. 1 is a partially cutaway front view showing a modification of the arrangement of the vertical vibration leaf springs of FIG. Top view without trough in FIG. The front view of the simple model of the components conveying apparatus for demonstrating the effect | action of this invention Graph explaining the amplification behavior of the pitching motion of a general parts conveyor The graph explaining the suppression method of the pitching movement of FIG. The graph explaining the generation | occurrence | production behavior of the pitching motion of the components conveying apparatus of this invention The graph explaining the suppression method of the pitching movement of FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIG. 1 to FIG. 3, the vibration type component conveying apparatus has a trough (component conveying member) 1 in which a linear conveying path 1 a is formed attached to an upper surface of an upper vibrating body 2. An intermediate vibration body 4 is provided between the base 3 installed on the floor, the intermediate vibration body 4 and the base 3 are connected by two leaf springs 5 as first elastic members, and the upper vibration body 2 The intermediate vibrating body 4 is connected by four leaf springs 6 as second elastic members, and a horizontal vibration (component conveying direction, X direction in the figure) is generated between the intermediate vibrating body 4 and the base 3. The first vibration mechanism 7 is provided, and the second vibration 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 columnar leaf spring mounting portions 3a are erected at two diagonal corners of the base 3, and a vibration isolating rubber (vibration isolating member) 18 fixed to the floor surface F is provided. It is supported. In addition, you may use a coil spring etc. for a vibration proof member.

Further, weights 19 are provided at both ends of the base 3 in the component conveying direction. Each of these weights 19 includes a plurality of detachable weight pieces 19a, and the mass can be adjusted by increasing or decreasing the number of the weight pieces 19a. Here, although illustration is omitted, the method of attaching the weight 19 to the base 3 can be a method of providing a through hole in each weight piece 19a and screwing it with a bolt or the like. At this time, a plurality of screw holes provided in the base 3 are arranged in the height direction so that the mounting position of the weight 19 on the base 3 can be adjusted in the vertical direction, thereby stabilizing the transport behavior. It becomes possible to easily move the position of the center of gravity of the base 3 to the vicinity of the center of the apparatus and to avoid interference between the weight 19 and other equipment. In this embodiment, the weight 19 is composed of a plurality of weight pieces 19a, but a weight having a desired mass alone may be used.

The intermediate vibrating body 4 is formed in a rectangular frame shape, and two diagonal corners thereof are opposed to 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 is a lower portion of the upper vibrating body 2. Are arranged to face each other. Further, on the outer peripheral surface, a leaf spring mounting portion 4a is provided that protrudes in the component conveying direction (X direction) from two diagonal corners that do not face the leaf spring mounting portion 3a of the base 3.

The first leaf spring 5 has its one end at the leaf spring mounting portion of the base 3 so that the front and back surfaces are oriented in the component conveyance direction, and the fixed positions of both ends are located on the same horizontal line orthogonal to the component conveyance direction. The other end portion is fixed to the leaf spring mounting portion 4a of the intermediate vibrator 4 to 3a, thereby forming a horizontal vibration leaf spring (horizontal vibration elastic member) that supports the intermediate vibrator 4 so as to vibrate in the horizontal direction. Yes. Here, the two leaf spring mounting portions 3a of the base 3 and the two leaf spring mounting portions 4a of the intermediate vibrating body 4 intersect so that straight lines connecting the installation positions of the same mounting portion intersect in plan view. Since they are provided, the two horizontal vibration leaf springs 5 are arranged so that the positional relationship between the two fixed positions thereof is switched in the component conveying direction.

On the other hand, the second leaf spring 6 has one end at the bottom of the upper vibrator 2 so that the front and back surfaces are oriented vertically and the fixed positions of both ends are located on the same horizontal line perpendicular to the component conveying direction. The other end portion is fixed to the edge in the longitudinal direction of the intermediate vibrating body 4 to form a vertical vibration leaf spring (vertical vibration elastic member) that supports the upper vibrating body 2 so as to vibrate in the vertical direction.

The first vibrating mechanism 7 includes an AC electromagnet 9 installed on the base 3 and a movable iron core 10 attached to the intermediate vibrating body 4 so as to face the electromagnet 9 with a predetermined interval. It consists of Although the movable iron core 10 is attached to the intermediate vibrator 4 in this example, it may be attached to the upper vibrator 2. On the other hand, the second vibration mechanism 8 includes an AC electromagnet 11 installed on the base 3, and a movable iron core 12 attached to the upper vibrator 2 so as to face the electromagnet 11 with a predetermined interval. It consists of

When the electromagnet 9 of the first vibration mechanism 7 is energized, an intermittent electromagnetic attractive force acts between the electromagnet 9 and the movable iron core 10, and due to this electromagnetic attractive force and the restoring force of the horizontal vibration leaf spring 5, A horizontal vibration is generated in the intermediate vibrating body 4, and this vibration is transmitted to the upper vibrating body 2 and the trough 1 through the vertical vibration leaf spring 6. Further, when the electromagnet 11 of the second vibration mechanism 8 is energized, an intermittent electromagnetic attractive force acts between the electromagnet 11 and the movable iron core 12, and this electromagnetic attractive force and the restoring force of the vertical vibration leaf spring 6. As a result, vertical vibrations are generated in the upper vibrating body 2 and the trough 1. And the components supplied to the trough 1 are conveyed along the linear conveyance path 1a by this horizontal vibration and vertical vibration.

Therefore, the horizontal vibration and the vertical vibration of the trough 1 can be adjusted by separately setting the voltage applied to the

electromagnets

9 and 11 of the

vibration mechanisms

7 and 8.

FIG. 4 shows a circuit for setting an applied voltage to the

electromagnets

9 and 11 of the

vibration mechanisms

7 and 8. The circuit of the first vibration mechanism 7 is provided with a reference waveform generating means 13 for generating a reference waveform of the applied voltage. The reference waveform generation means 13 generates a reference waveform corresponding to the set value of the type of waveform (for example, sine wave) and the period (frequency) of the waveform. On the other hand, the circuit of the second excitation mechanism 8 is provided with phase difference adjusting means 14 for generating a waveform having a predetermined phase difference with respect to the reference waveform generated by the reference waveform generating means 13.

In each of the

excitation mechanisms

7 and 8, the waveform generated by the reference waveform generating means 13 or the phase difference adjusting means 14 is adjusted to a predetermined amplitude by the waveform amplitude adjusting means 15, and the PWM signal generating means 16 After conversion to a PWM signal, the voltage is amplified by the voltage amplifying means 17 and applied to the

electromagnets

9 and 11. Thus, the horizontal vibration and the vertical vibration can be adjusted by freely controlling the waveform, period, phase difference and amplitude of the voltage applied to the

electromagnets

9 and 11, respectively. Note that when each excitation mechanism is not driven by the PWM method, the PWM signal generating means 16 becomes unnecessary.

Further, as a whole device, the natural frequency of the rotational vibration (horizontal vibration rotational vibration mode) generated in the intermediate vibration body 4 and the base 3 is the rotational vibration generated in the trough 1 and the upper vibration body 2 ( It is adjusted to be larger than the natural frequency of the rotational vibration mode of vertical vibration. The natural frequency of the rotational vibration mode of the horizontal vibration is adjusted by changing the fixed length, thickness and number of the horizontal vibration leaf springs 5 and the moment of inertia of the base 3 and the intermediate vibration body 4. On the other hand, the natural frequency of the rotational vibration mode of the vertical vibration is adjusted by changing the fixed length, thickness and number of the vertical vibration leaf springs 6 and the moment of inertia of the trough 1 and the upper vibration body 2.

Actually, the trough 1 is often mounted at the customer, and it is difficult to change the specifications of the

leaf springs

5 and 6 and the moment of inertia of each member such as the upper vibrator 2. Therefore, before shipping, the above adjustment is performed within the range of the mass and the moment of inertia of the trough 1 that is assumed to be mounted at the customer, and the customer adjusts the weight 19 installed on the base 3 according to the trough 1 to be mounted. It is desirable that the pitching motion can be suppressed only by adjustment.

This vibration type component conveying apparatus has the above-described configuration, and when vibration is generated in the intermediate vibrating body 4 by driving the first vibrating mechanism 7, two fixed positions on the same horizontal line orthogonal to the component conveying direction. The horizontal vibration leaf spring 5 fixed in step S is repeatedly deformed only in the horizontal direction and returned to the original state. Thereby, the vibration generated in the intermediate vibrating body 4 hardly includes vertical vibration, and is substantially only in the horizontal direction. In addition, since the positional relationship between the fixed positions of the two horizontal vibration leaf springs 5 is arranged so as to be interchanged in the component conveyance direction, the direction in the direction perpendicular to the component conveyance direction (Y direction in FIGS. 2 and 3) in the horizontal plane Vibration can also be suppressed.

Then, a vibration isolating rubber 18 is provided between the base 3 and the floor surface F, a weight 19 including a plurality of weight pieces 19 a is provided on the base 3, and rotational vibration generated in the intermediate vibrator 4 and the base 3. Since the natural frequency of the trough 1 and the upper vibration body 2 are larger than the natural frequency of the rotational vibration, the base of the trough 1 in which the amplitude of the pitching motion of the base 3 is in the opposite phase to this By adjusting the mass of the base 3 by increasing / decreasing the number of the weight pieces 19a so as to approach the amplitude of the relative pitching motion with respect to 3, the pitching motion of the trough 1 seen from the floor can be reliably suppressed. , Stable component conveyance can be realized. Moreover, even when the mass of the base 3 is adjusted in order to suppress the pitching movement of the trough 1 in this way, the component conveyance speed can be maintained (see FIG. 11).

5 and 6 show a modification of the arrangement of the vertical vibration leaf springs 6 of the above-described embodiment. In this modification, the vertical vibration leaf spring 6 is moved in the short direction of the upper vibration body 2 and the intermediate vibration body 4 at two fixed positions on the same horizontal line parallel to the component conveying direction (X direction in the figure). It is fixed to the edge.

In the above-described embodiment, the first plate spring that connects the intermediate vibration body and the base is a horizontal vibration plate spring, and the second plate spring that connects the upper vibration body and the intermediate vibration body is the vertical vibration plate. In contrast to this, the first plate spring may be a vertical vibration plate spring, and the second plate spring may be a horizontal vibration plate spring. Further, one leaf spring is arranged at each location, but two or more leaf springs may be used as one.

In addition, although the horizontal vibration leaf springs are arranged in two places, they may be constituted by three or more places. In this case, the positional relationship between the fixed position to each intermediate vibrator and the fixed position to the base is a component. What is necessary is just to arrange | position so that it may alternate by the conveyance direction. On the other hand, the vertical vibration leaf springs are arranged at four locations, but may be configured at two or more locations.

Furthermore, in the embodiment, a leaf spring is used for the elastic member for horizontal vibration and the elastic member for vertical vibration, but an elastic member other than the leaf spring can also be used. Moreover, although each vibration mechanism uses what consists of an electromagnet and a movable iron core, it is not restricted to this, What is necessary is just an actuator which can generate | occur | produce the same vibration force.

1 trough (component conveying member)
2 Upper vibration body 3 Base 4 Intermediate vibration body 5 First leaf spring (leaf spring for horizontal vibration)
6 Second leaf spring (plate spring for vertical vibration)
7 First vibration mechanism 8

Second vibration mechanism

9, 11

Electromagnets

10, 12 Movable iron core 18 Vibration-proof rubber (vibration-proof member)
19 Weight 19a Weight piece

Claims

A component conveying member in which a component conveying path is formed, an upper vibrator to which the component conveying member is attached, a base installed on a floor, and an intermediate vibrator provided between the upper vibrator and the base; A first elastic member that connects the intermediate vibration body and the base, and a second elastic member that connects the upper vibration body and the intermediate vibration body, the first elastic member and the second elastic member. One of the elastic members is an elastic member for horizontal vibration, the other is an elastic member for vertical vibration, and the horizontal vibration elastic member and the first vibration mechanism impart horizontal vibration to the component conveying member, In the vibration-type component conveying apparatus in which the vertical vibration is applied to the component conveying member by the vertical vibration elastic member and the second vibration mechanism, the natural vibration of the rotational vibration generated in the intermediate vibrator and the base Numbers are generated in the parts conveying member and upper vibrating body Vibratory parts feeder characterized by being larger than the natural frequency of the rotational vibration that.
2. The vibration type component conveying apparatus according to claim 1, wherein a weight is provided on the base.
An anti-vibration member is provided between the base and the floor, and the mass of the base is adjusted so that the amplitude of the pitching motion of the base approaches the amplitude of the pitching motion relative to the base of the component conveying member. The vibration type component conveying apparatus according to claim 1 or 2, wherein
The horizontal vibration elastic member is arranged such that a fixed position to the intermediate vibrator and a fixed position to the base or the upper vibrator are located on the same horizontal line orthogonal to the component conveying direction. The vibration type component conveying apparatus according to any one of claims 1 to 3.
A plurality of the horizontal vibration elastic members are provided in the component conveying direction, and the positional relationship between the fixed position to the intermediate vibrating body and the fixed position to the base or the upper vibrating body is alternately switched in the component conveying direction. The vibration type parts conveying device according to claim 4, wherein
6. The vibration type component conveying apparatus according to claim 1, wherein the elastic member for vertical vibration is fixed at two fixed positions on the same horizontal line orthogonal to the component conveying direction.
6. The vibration type component conveying apparatus according to claim 1, wherein the elastic member for vertical vibration is fixed at two fixed positions on the same horizontal line parallel to the component conveying direction.
Each excitation mechanism is composed of an electromagnet and a movable iron core, a reference waveform generating means for generating a reference waveform of an applied voltage in an applied voltage setting circuit to one of the electromagnets, and an amplitude with respect to the reference waveform Waveform amplitude adjusting means for adjusting is provided, and the applied voltage setting circuit for the other electromagnet is generated by the phase difference adjusting means for generating a waveform having a predetermined phase difference with respect to the reference waveform, and the phase difference adjusting means 8. The vibration type component conveying apparatus according to claim 1, further comprising a waveform amplitude adjusting unit that adjusts an amplitude with respect to the waveform.
9. A circuit for setting a voltage applied to an electromagnet of each of the excitation mechanisms is provided with PWM signal generating means for converting a waveform whose amplitude is adjusted by each of the waveform amplitude adjusting means into a PWM signal. The vibratory component conveying device according to 1.