JPWO2009078273A1 - Vibration transfer device - Google Patents

Abstract

The vibration conveyance device (1) is a device that conveys an article while vibrating the conveyance table (11), a first spring (121, 122), a second spring (131, 132), and a vibration. A source (14). Articles are placed on the transport table (11). The first springs (121, 122) are springs that give vibration to the transport table (11), and resonate at the first natural frequency (fc1). The second spring (131, 132) causes vibration in a direction (922) that is different from the direction of vibration (912) that the first spring (121, 122) imparts to the transport table (11). Which resonates at a second natural frequency (fc2) different from the first natural frequency (fc1). The vibration source (14) vibrates the first spring (121, 122) and the second spring (131, 132). Thereby, while enabling miniaturization of the apparatus and simplification of control, adjustment of the conveyance amount and conveyance in consideration of the property of the article are enabled.

Description

  The present invention relates to a vibration conveyance device, and more particularly to conveyance and adjustment of a conveyance amount in consideration of the properties of an article.

  Conventionally, a vibration transfer device such as a resonance-type vibration feeder (hereinafter referred to as “resonance-type vibration feeder”) is used to transfer articles to an automatic weighing machine or a weighing machine. Examples of articles conveyed by the resonant vibration feeder include snacks and confectionery such as candy, vegetables such as peppers, processed foods such as winners and frozen foods, and the like.

  The conventional resonance type vibration feeder adjusts the conveyance amount of the article to be conveyed by changing the amplitude or changing the operation time. Specifically, the carry amount increases by increasing the amplitude. In addition, the conveyance amount increases by extending the operation time. However, the above-described resonance type vibration feeder has a limit in increasing the amplitude. Further, the influence of the properties (properties, shapes, etc.) of the articles on the transport amount cannot be considered.

  When it is necessary to transport a large amount of articles or when it is necessary to consider the properties of the articles, it is necessary to take measures such as embossing the transport surface or tilting the transport surface. . When these measures are taken, it becomes difficult to transport a small amount of an article, so it is necessary to replace the transport surface according to the transport amount of the article. For this reason, the work becomes complicated, and as a result, the work time and cost increase due to an increase in the number of steps.

  Therefore, techniques such as Patent Document 1 and Patent Document 2 described below have been proposed. In any case, by adjusting the vibration direction of the transport surface, it is possible to adjust the transport amount and transport in consideration of the properties of the article, thereby preventing an increase in work time and cost.

  Specifically, Patent Document 1 discloses a vibration feeder including a rotatable support shaft and two shakers attached to the support shaft. The vibration exciter has a rotatable unbalanced rotor, and the rotation axis thereof is orthogonal to the support shaft. The vibration direction is adjusted by controlling the rotation of the support shaft and the rotation of the unbalanced rotor.

Patent Document 2 discloses an article conveying device including two vibration generating means. The two vibration generating units generate vibrations in the vertical direction and the horizontal direction with respect to the movable body. The vibration direction is adjusted by controlling the phase difference between the vertical vibration and the horizontal vibration.
JP 2006-52034 A Japanese Examined Patent Publication No. 7-98567

  However, since the vibration feeder of Patent Document 1 has a complicated structure, there is a problem that the vibration feeder is increased in size. Moreover, since the article conveyance apparatus of patent document 2 needs to control each of two vibration generators, there existed a problem that control became complicated.

  The present invention has been made in view of the above-described circumstances, and enables the adjustment of the conveyance amount and the conveyance in consideration of the properties of the article while enabling the miniaturization of the apparatus and the simplification of the control. It is aimed.

  A vibration transfer device according to a first invention is a device that transfers an article while vibrating the article, and includes a transfer stand, a first spring, a second spring, and a vibration source. Articles are placed on the transport table. The first spring is a spring that imparts vibration to the transport table, and resonates at the first natural frequency. The second spring is a spring that gives the carrier a vibration in a direction different from the direction of the vibration that the first spring gives to the carrier. The second natural frequency is different from the first natural frequency. Resonates at. The vibration source vibrates the first and second springs.

  According to the vibration transfer device of the first invention, the first and second natural frequencies are different from each other. Therefore, the first and second springs are vibrated at the same frequency by the vibration source, and the vibration frequency is reduced. The amplitude and phase difference of the vibrations of the first and second springs can be changed simply by changing them. Since the directions of vibration of the first and second springs are different from each other, the direction and amplitude of vibration applied to the transport table can be adjusted by changing the amplitude and phase difference of these vibrations. Therefore, it is possible to adjust the conveyance amount and carry the article in consideration of the properties of the article.

  In addition, the carrier can be vibrated with a desired amplitude in a desired direction simply by vibrating the first and second springs at a certain frequency. Therefore, the vibration carrier device can be downsized and the control can be simplified. Is possible.

  A vibration transfer device according to a second invention is the vibration transfer device according to the first invention, and further includes a control unit. The control unit adjusts at least one of the amplitude and phase of each of the first and second springs by changing the frequency of the vibration source.

  According to the vibration transfer device of the second invention, desired vibration can be applied to the transfer table by changing the frequency of the vibration source by the control unit.

  A vibration transfer device according to a third aspect of the present invention is the vibration transfer device according to the second aspect of the present invention, wherein the control unit changes the frequency of the vibration source based on the direction and amplitude of vibrating the transfer table.

  According to the vibration transfer device of the third invention, the transfer table can be vibrated in a desired direction with a desired amplitude by changing the frequency of the vibration source by the control unit.

  A vibration transfer device according to a fourth aspect of the present invention is the vibration transfer device according to any one of the first to third aspects, wherein the first spring is connected to the transfer table. The second spring is connected to the transport table via the first spring.

  According to the vibration transfer device of the fourth invention, since the second spring is connected via the first spring, the first and second springs vibrate at the same frequency with one vibration source. The frequency of the vibration can be changed.

  A vibration transfer device according to a fifth aspect of the present invention is the vibration transfer device according to any one of the first to fourth aspects of the invention, wherein the first and second springs are at least in phase with the vibration in the same phase. And can be selectively executed.

  According to the vibration conveyance device according to the fifth aspect of the invention, the vibration direction of the conveyance surface can be changed by selectively executing the vibration in the same phase and the vibration in the opposite phase.

  A vibration transfer device according to a sixth aspect of the present invention is the vibration transfer device according to any one of the first to fifth aspects, wherein the first and second springs have a first frequency relative to the frequency of the vibration source. A curve representing a change in the amplitude of the spring and a curve representing a change in the amplitude of the second spring with respect to the frequency intersect at a certain frequency.

  According to the vibration transfer device of the sixth aspect of the invention, the phase difference is reduced to 0 while changing the vibration frequencies of the first and second springs by changing the frequency applied to the first and second springs. It can be continuously changed between ° (in phase) and 180 ° (antiphase). Therefore, the vibration direction and amplitude of the conveying surface can be continuously changed, and thus the vibration direction and amplitude can be finely adjusted.

  A vibration transfer device according to a seventh aspect of the present invention is the vibration transfer device according to any one of the first to sixth aspects, wherein at least forward and reverse movements are selected for the transfer of the article placed on the transfer table. Can be executed automatically.

  According to the vibration transfer device of the seventh invention, the article on the transfer surface can be moved forward and backward. In addition, immediately before stopping the conveyance, the direction in which the article is moved can be controlled to be opposite to the direction in which the article has been moved. Thereby, when the conveyance is stopped, the article can be prevented from moving due to inertia.

  A vibration transfer device according to an eighth aspect of the present invention is the vibration transfer device according to the seventh aspect of the present invention, wherein the transfer table has a transfer surface on which articles are placed. The directions in which the first and second springs vibrate are inclined opposite to each other with respect to the direction perpendicular to the transport surface.

  According to the vibration transfer device according to the eighth aspect of the invention, the amplitude of the first spring is increased and the amplitude of the second spring is decreased, thereby moving (advancing) the article on the transfer surface in a predetermined direction. Can be made. On the other hand, by reducing the amplitude of the first spring and increasing the amplitude of the second spring, it is possible to move (reverse) in the direction opposite to the predetermined direction. Therefore, the article on the conveying surface can move forward and backward.

  Moreover, in any of the cases described above, the vibration having the vibration component in the direction perpendicular to the transport surface is generated, so that the article on the transport surface can be loosened or smoothed.

  A vibration transfer device according to a ninth aspect of the present invention is the vibration transfer device according to any one of the first to sixth aspects, wherein the transfer stand has a transfer surface on which an article is placed. The directions in which the first and second springs vibrate are inclined in the same direction with respect to the direction perpendicular to the transport surface.

  According to the vibration transfer device of the ninth aspect of the invention, since vibration in a direction perpendicular to the transfer surface can be increased, even when an adhesive article is transferred, Adhesion can be prevented.

  According to the vibration transfer device of the present invention, the first and second natural frequencies are different from each other. Therefore, the first and second springs are vibrated at the same frequency by the vibration source, and the frequency is changed. Only the amplitude and phase difference of the vibrations of the first and second springs can be changed. Since the vibration directions of the first and second springs are different from each other, it is possible to adjust the vibration direction and amplitude of the transport table by changing the amplitude and phase difference of these vibrations. Therefore, it is possible to adjust the conveyance amount and carry the article in consideration of the properties of the article.

  In addition, the carrier can be vibrated with a desired amplitude in a desired direction simply by vibrating the first and second springs at a certain frequency. Therefore, the vibration carrier device can be downsized and the control can be simplified. Is possible.

It is a figure which shows notionally the vibration conveying apparatus concerning 1st Embodiment. It is the conceptual diagram which looked at the vibration conveyance apparatus concerning the modification 2 of 1st Embodiment, and the modification of 2nd Embodiment from the conveyance direction downstream of the articles | goods. It is the conceptual diagram which looked at the vibration conveyance apparatus concerning the modification 2 of 1st Embodiment, and the modification of 2nd Embodiment from the conveyance direction downstream of the articles | goods. It is a figure which shows the relationship between the frequency f and the amplitude A with a graph. It is a figure which shows the relationship between the frequency f and the initial phase (phi) 0 with a graph. It is a figure which shows coordinate axis x1, x2. It is a figure which shows the relationship between time and the displacement of a spring with a graph. It is a figure which shows typically the vibration of a spring to a vibration conveyance apparatus. It is a figure which shows the synthetic | combination vibration given to a conveyance stand. It is a figure which shows the relationship between time and the displacement of a spring with a graph. It is a figure which shows typically the vibration of a spring to a vibration conveyance apparatus. It is a figure which shows the synthetic | combination vibration given to a conveyance stand. It is a figure which shows the relationship between time and the displacement of a spring with a graph. It is a figure which shows typically the vibration of a spring to a vibration conveyance apparatus. It is a figure which shows the synthetic | combination vibration given to a conveyance stand. It is a block diagram which shows notionally control of a vibration conveyance apparatus. It is a figure which shows notionally the vibration conveying apparatus concerning 2nd Embodiment. It is a figure which shows coordinate axis x3, x4. It is a figure which shows the relationship between time and the displacement of a spring with a graph. It is a figure which shows typically the vibration of a spring to a vibration conveyance apparatus. It is a figure which shows the synthetic | combination vibration given to a conveyance stand. It is a figure which shows the relationship between time and the displacement of a spring with a graph. It is a figure which shows typically the vibration of a spring to a vibration conveyance apparatus. It is a figure which shows the synthetic | combination vibration given to a conveyance stand. It is a figure which shows the relationship between time and the displacement of a spring with a graph. It is a figure which shows typically the vibration of a spring to a vibration conveyance apparatus. It is a figure which shows the synthetic | combination vibration given to a conveyance stand. It is a figure which shows notionally the automatic weighing machine concerning the Example of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Conveyance stand 11a Conveyance surface 14 Vibration source 90 Direction perpendicular | vertical to a conveyance surface 121-124 1st spring 131-134 2nd spring 172 Control part 912,922,914,924 Direction of vibration A Amplitude f Frequency fc1 1st 1 natural frequency fc2 2nd natural frequency

First Embodiment Structure of Vibration Conveying Device FIG. 1A is a diagram conceptually showing the vibration conveying device 1 according to the present embodiment. The vibration conveyance device 1 is a device that conveys articles such as confectionery, vegetables, and processed foods in the conveyance direction 93 while oscillating articles such as confectionery, vegetables, and processed foods. 131, 132, a vibration source 14, and a fixing unit 15. Hereinafter, the upper side and the lower side in the vertical direction 90 are simply expressed as “upper side” and “lower side”, respectively.

<Transportation platform>
The conveyance stand 11 has an upper surface as a conveyance surface 11a. Articles to be transported are placed on the transport surface 11a.

<First and second springs>
The first springs 121, 122 are springs that resonate at the first natural frequency fc <b> 1, and apply vibrations to the transport table 11. The second springs 131 and 132 are springs that resonate at a second natural frequency fc2 that is different from the first natural frequency fc1, and give vibration to the transport table 11. This will be specifically described below. In FIG. 1A, leaf springs are employed for both the first springs 121 and 122 and the second springs 131 and 132.

  The first springs 121 and 122 extend in a direction 911 inclined with respect to the vertical direction 90. The second springs 131 and 132 extend in a direction 921 inclined to the opposite side of the direction 911 with respect to the vertical direction 90. Note that the direction 911 and the direction 921 intersect each other. Hereinafter, the direction 911 and the direction 921 are referred to as an extending direction 911 and an extending direction 921, respectively.

  Upper ends 121 a and 122 a of the first springs 121 and 122 are connected to a connecting portion 161 fixed to the transport table 11. Lower ends 121b and 122b of the first springs 121 and 122 are connected to upper ends 131a and 132a of the second springs 131 and 132, respectively. Lower end portions 131 b and 132 b of the second springs 131 and 132 are connected to the fixed portion 15.

  Specifically, in FIG. 1A, the upper end portions 121a and 122a are coupled to the coupling portion 161 by being fixed to the coupling portion 161 with screws. The lower end part 121b and the upper end part 131a are connected to each other by being fixed to the connecting part 162 with screws. The lower end 122b and the upper end 132a are connected to each other by being fixed to the connecting portion 163 with a screw. The lower end portions 131b and 132b are connected to the fixing portion 15 by being fixed to the fixing portion 15 with screws.

  In view of the fact that the connecting portion 161 is fixed to the transport base 11, it can be understood that the upper end portions 121 a and 122 a are connected to the transport base 11 through the same connecting portion 161. Further, it can be understood that the second springs 131 and 132 are connected to the transport table 11 via the first springs 121 and 122 and the connecting portion 161, respectively.

  Due to the arrangement of the first and second springs described above, for the first springs 121 and 122, the upper ends 121a and 122a are perpendicular to the extending direction 911 with the lower ends 121b and 122b as fulcrums. Vibrates along. Therefore, the first springs 121 and 122 can impart vibrations in the direction 912 to the transport base 11.

  As for the second springs 131 and 132, the upper end portions 131a and 132a vibrate along a direction 922 perpendicular to the extending direction 921 with the lower end portions 131b and 132b as fulcrums. Therefore, the second springs 131 and 132 can apply vibrations in the direction 922 to the transport table 11 via the first springs 121 and 122, respectively.

  Considering that the extending direction 921 of the second springs 131 and 132 is inclined to the opposite side of the extending direction 911 of the first springs 121 and 122 with respect to the vertical direction 90, the direction 922 is changed to the next direction 922. Can be ascertained. That is, the direction 922 is a direction different from the direction 912 and is inclined to the opposite side of the direction 912 with respect to the vertical direction 90 (FIG. 1A).

  In FIG. 1A, the connecting portions 162 and 163 are connected to each other via the connecting portion 164. Specifically, both the connecting portions 162 and 163 are fixed to the same connecting portion 164. As a result, the vibrations of the first and second springs 121 and 131 and the vibrations of the first and second springs 122 and 132 can be easily synchronized. it can.

<Vibration source>
The vibration source 14 includes an electromagnetic coil 141 and a movable iron core 142 that interact with each other. Specifically, the electromagnetic coil 141 generates an oscillating magnetic field by alternating current flowing through itself, and vibrates the movable iron core 142. Then, by changing the amplitude and frequency of the alternating current flowing through the electromagnetic coil 141, the amplitude and the frequency f of the vibrating movable core 142 can be changed. In addition to alternating current, the applied current may be half-wave rectified alternating current, intermittent rectangular waves, PWM (Pulse Width Modulation) waves generated by an inverter, or the like.

  The vibration source 14 vibrates the first springs 121 and 122 and the second springs 131 and 132. Specifically, the movable iron core 142 of the vibration source 14 is coupled to the first springs 121 and 122 via the coupling portion 161. As a result, the vibration of the movable iron core 142 is transmitted to the first springs 121 and 122 via the connecting portion 161.

  The vibration transmitted to the first springs 121 and 122 is also transmitted to the second springs 131 and 132 connected to the first springs 121 and 122, respectively.

  Accordingly, the first springs 121 and 122 and the second springs 131 and 132 can be vibrated at the same frequency f by one vibration source 14.

<Modification 1>
In the vibration transfer device 1 described above, plate springs are used for the first springs 121 and 122 and the second springs 131 and 132, but springs other than the plate springs may be used. Moreover, you may employ | adopt what laminated | stacked several leaf | plate springs.

<Modification 2>
In the vibration transfer device 1 described above, the lower ends 121b and 122b of the first springs 121 and 122 are connected to the upper ends 131a and 132a of the second springs 131 and 132 via the connecting portions 162 and 163, respectively. However, the present invention is not limited to this, and the first springs 121 and 122 and the second springs 131 and 132 may be coupled in another manner.

  Further, the first springs 121 and 122 and the second springs 131 and 132 may be separately connected to the transport table 11 and the connecting portion 161.

  The positions where the lower ends 121b and 122b of the first springs 121 and 122 and the upper ends 131a and 132a of the second springs 131 and 132 are attached to the connecting portion 164 are the same position in the width direction of the connecting portion 164. (See FIG. 1B) or a position offset to the left and right (see FIG. 1C). 1B and 1C are views as seen from the downstream side in the conveyance direction of the article in the vibration conveyance device 1 shown in FIG. 1A.

<Modification 3>
In the vibration transfer device 1 described above, the electromagnetic coil 141 and the movable iron core 142 are employed as the vibration source 14, but, for example, a piezoelectric element may be employed. By adopting the piezoelectric element, the vibration source 14 can be reduced in size, and thus the vibration transfer device 1 can be reduced in size.

2. Characteristics of first and second springs <Relationship between frequency and amplitude>
FIG. 2 shows the relationship between the frequency f and the amplitude A by the graph 201 for the first springs 121 and 122 and by the graph 202 for the second springs 131 and 132.

  In the first springs 121 and 122, the amplitude A is the maximum when the frequency f is the first natural frequency fc1 (graph 201). That is, when the frequency f is the first natural frequency fc1, the first springs 121 and 122 are in resonance.

  The value of the amplitude A at the first natural frequency fc1 is determined by the amplitude of vibration applied from the vibration source 14 to the first springs 121 and 122. That is, by increasing (or decreasing) the amplitude of the movable iron core 142 that is vibrated by the vibration source 14, the value of the amplitude A at the first natural frequency fc1 can be increased (or decreased).

  In the second springs 131 and 132, the amplitude A becomes the maximum when the frequency f is the second natural frequency fc2 (graph 202). That is, when the frequency f is the second natural frequency fc2, the second springs 131 and 132 are in resonance.

  The value of the amplitude A at the second natural frequency fc2 is determined by the amplitude of vibration applied from the vibration source 14 to the second springs 131 and 132. That is, by increasing (or decreasing) the amplitude of the movable iron core 142 that is vibrated by the vibration source 14, the value of the amplitude A at the second natural frequency fc2 can be increased (or decreased).

  FIG. 2 shows a case where the first and second natural frequencies fc1 and fc2 are different from each other and the second natural frequency fc2 is larger than the first natural frequency fc1. Moreover, in FIG. 2, the high frequency side of the graph 201 and the low frequency side of the graph 202 intersect at a certain frequency f.

<Relationship between frequency and initial phase>
FIG. 3 shows the relationship between the frequency f and the initial phase φ0 by a graph 301 for the first springs 121 and 122 and a graph 302 for the second springs 131 and 132. The initial phase φ0 shown in FIG. 3 is obtained when the coordinate axes x1 and x2 are set along the vibration directions 912 and 922 as shown in FIG. Note that the origin O of each of the coordinate axes x1 and x2 is at the position of the center of vibration.

  From the graph 301, the initial phase φ0 changes from 0 (deg) to −180 (deg) in the vicinity of the first natural frequency fc1 for the first springs 121 and 122 as the frequency f increases. I understand. When the frequency f is the first natural frequency fc1, the initial phase φ0 is −90 (deg).

  From the graph 302, the initial phase φ0 of the second springs 131 and 132 changes from 0 (deg) to −180 (deg) in the vicinity of the second natural frequency fc2 as the frequency f increases. I understand. When the frequency f is the second natural frequency fc2, the initial phase φ0 is −90 (deg).

  Since the first and second natural frequencies fc1 and fc2 are different from each other, the phase when the first springs 121 and 122 vibrate and the second spring 131 are changed only by changing the frequency f. , 132 can be made the same or different in phase. This will be specifically described with reference to FIG. FIG. 3 shows a case where the second natural frequency fc2 is larger than the first natural frequency fc1, as in FIG.

  In the region R1 (FIG. 3) in which the frequency f is equal to or less than the frequency f1, the first springs 121 and 122 and the second springs 131 and 132 have the same initial phase φ0 (= 0 (deg)). Oscillate in the same phase. Note that, at the lower limit frequency f0 of the region R1, both the amplitude A of the first springs 121 and 122 and the amplitude A of the second springs 131 and 132 are substantially zero (FIG. 2).

  In the region R2 (FIG. 3) where the frequency f is between the frequency f1 and the frequency f3, the first springs 121 and 122 and the second springs 131 and 132 have different initial phases φ0. Vibrates at different phases. That is, a phase difference Δφ0 occurs between the phase when the first springs 121 and 122 vibrate and the phase when the second springs 131 and 132 vibrate. Specifically, as the frequency f increases from the frequency f1, the absolute value of the phase difference Δφ0 increases from 0 (deg) to 180 (deg) or the vicinity thereof, and then becomes 0 (deg) again.

  In a region R3 (FIG. 3) where the frequency f is equal to or higher than the frequency f3, the first springs 121 and 122 and the second springs 131 and 132 have the same initial phase φ0 (= −180 (deg)). So it vibrates in the same phase. Note that at the upper limit frequency f4 of the region R3, both the amplitude A of the first springs 121 and 122 and the amplitude A of the second springs 131 and 132 are substantially zero (FIG. 2).

3. Operation of Vibration Transfer Device In the vibration transfer device 1 described above, the transfer table 11 is provided with vibrations generated by the first springs 121 and 122 and vibrations generated by the second springs 131 and 132. That is, the carriage 11 is given a vibration (hereinafter referred to as “combined vibration”) obtained by combining the vibration along the direction 912 (coordinate axis x1) and the vibration along the direction 922 (coordinate axis x2). Hereinafter, operation | movement of a vibration conveying apparatus is demonstrated for every area | region R1-R3 (FIG. 3).

<Vibration in region R1>
A case where the first springs 121 and 122 and the second springs 131 and 132 are vibrated in the region R1 will be described. In this case, the first springs 121 and 122 and the second springs 131 and 132 all have an initial phase φ0 of 0 (deg) and vibrate in the same phase (FIG. 3). In addition, the amplitude A of the first springs 121 and 122 is significantly greater than the amplitude A of the second springs 131 and 132 (FIG. 2).

  Specifically, the vibrations of the first springs 121 and 122 and the second springs 131 and 132 at the frequency f1 will be described with reference to FIGS.

  FIG. 5 shows the relationship between time and spring displacement by a graph 501 for the first springs 121 and 122 and a graph 502 for the second springs 131 and 132. In FIG. 5, the coordinate axis x1 and the coordinate axis x2 are overlapped to clarify the relationship between the vibration of the first springs 121 and 122 and the vibration of the second springs 131 and 132, which will be described later. The same applies to FIGS. 8 and 11. Further, the amplitude of the first springs 121 and 122 is indicated by reference numeral A1, and the amplitude of the second springs 131 and 132 is indicated by reference numeral A2, and the same applies to FIGS.

  FIG. 6 is a diagram schematically showing the vibration of the first spring 121 (122) and the vibration of the second spring 131 (132) at the vibration frequency f1, respectively.

  As shown in FIGS. 5 and 6, at the frequency f1, the first springs 121 and 122 and the second springs 131 and 132 vibrate in the same phase (initial phase = 0 (deg)). When the springs 121 and 122 are displaced in the positive direction of the coordinate axis x1 (solid line vector 601), the second springs 131 and 132 are also displaced in the positive direction of the coordinate axis x2 (solid line vector 603). The solid line vector 601 represents the displacement of the first springs 121 and 122 in the positive direction and has the maximum displacement (FIG. 5). A solid line vector 603 represents the displacement of the second springs 131 and 132 in the positive direction and the displacement amount is maximum (FIG. 5).

  When the first springs 121 and 122 are displaced in the negative direction of the coordinate axis x1 (broken line vector 602), the second springs 131 and 132 are also displaced in the negative direction of the coordinate axis x2 (broken line vector 604). The broken line vector 602 represents the displacement of the first springs 121 and 122 in the negative direction and has the maximum displacement (FIG. 5). A broken line vector 604 represents the displacement of the second springs 131 and 132 in the negative direction and has the maximum displacement (FIG. 5).

  FIG. 7 is a diagram illustrating the combined vibration applied to the transport table 11 at the frequency f1. In FIG. 7, the direction and amplitude of the combined vibration are indicated by a combined vector 701. The combined vector 701 is a combination of a solid line vector 601 (FIG. 6) related to the vibration of the first springs 121 and 122 and a solid line vector 603 (FIG. 6) related to the vibration of the second springs 131 and 132. Represents the direction of the combined vibration, and the magnitude represents the amplitude of the combined vibration.

  The combined vector 701 includes a component vector that travels in the transport direction 93 and a component vector that travels in the direction 94 perpendicular to the transport surface 11a. This is because the first springs 121 and 122 and the second springs 131 and 132 vibrate in the same phase (FIG. 3) at the frequency f1 on the coordinate axes x1 and x2 (FIG. 6). This is because the amplitude of the springs 121 and 122 is significantly larger than the amplitude of the second springs 131 and 132 (FIG. 2).

  Therefore, when the frequency is f1, the article placed on the transport surface 11a can be moved in the transport direction 93. In addition, since the article can be vibrated in the direction 94 perpendicular to the conveyance surface 11a, the article can be loosened or leveled.

  The amplitude of the combined vibration (the magnitude of the combined vector 701) can be changed by changing the amplitude of the vibration generated in the vibration source 14. Specifically, the amplitude of the composite vibration is increased by increasing (or decreasing) the amplitude of the movable iron core 142 that is vibrated by the vibration source 14 and increasing (or decreasing) the amplitudes A1 and A2 (FIG. 5) ( Or smaller). The same applies to synthetic vibration (FIGS. 10 and 13) described later.

<Vibration in region R2>
A case where the first springs 121 and 122 and the second springs 131 and 132 are vibrated in the region R2 will be described. In this case, the first springs 121 and 122 and the second springs 131 and 132 have different initial phases φ0 and vibrate at different phases (FIG. 3). Moreover, the amplitudes of the first springs 121 and 122 and the amplitudes of the second springs 131 and 132 are approximately the same (FIG. 2).

  Specifically, the vibrations of the first springs 121 and 122 and the second springs 131 and 132 at the frequency f2 (FIG. 3) where the absolute value of the phase difference Δφ0 is 180 (deg) are shown in FIGS. 10 will be used for explanation.

  FIG. 8 shows the relationship between time and spring displacement with a graph 801 for the first springs 121 and 122 and a graph 802 for the second springs 131 and 132. FIG. 9 is a diagram schematically showing the vibration of the first spring 121 (122) and the vibration of the second spring 131 (132) at the vibration frequency f2, respectively.

  As shown in FIGS. 8 and 9, since the first springs 121 and 122 and the second springs 131 and 132 vibrate in opposite phases (absolute value of phase difference Δφ0 = 180 (deg)) at the frequency f2. When the first springs 121 and 122 are displaced in the positive direction of the coordinate axis x1 (solid line vector 901), the second springs 131 and 132 are displaced in the negative direction of the coordinate axis x2 (solid line vector 903). The solid line vector 901 represents the displacement of the first springs 121 and 122 in the positive direction and has the maximum displacement (FIG. 8). A solid line vector 903 represents the displacement of the second springs 131 and 132 in the negative direction and has the maximum displacement (FIG. 8).

  When the first springs 121 and 122 are displaced in the negative direction of the coordinate axis x1 (broken line vector 902), the second springs 131 and 132 are displaced in the positive direction of the coordinate axis x2 (broken line vector 904). The broken line vector 902 represents the displacement of the first springs 121 and 122 in the negative direction and has the maximum displacement (FIG. 8). A broken line vector 904 represents the displacement of the second springs 131 and 132 in the positive direction and has the maximum displacement (FIG. 8).

  FIG. 10 is a diagram illustrating the combined vibration applied to the transport table 11 at the frequency f2. In FIG. 10, the direction and amplitude of the combined vibration are indicated by a combined vector 1001. A combined vector 1001 is a combination of a solid line vector 901 (FIG. 9) related to the vibration of the first springs 121 and 122 and a solid line vector 903 (FIG. 9) related to the vibration of the second springs 131 and 132. Represents the direction of the combined vibration, and the magnitude represents the amplitude of the combined vibration.

  In the combined vector 1001, the magnitude of the component vector toward the conveyance direction 93 is more dominant than the magnitude of the component vector toward the direction 94 perpendicular to the conveyance surface 11a. This is because the first springs 121 and 122 and the second springs 131 and 132 are in antiphase (the absolute value of the phase difference Δφ0 = 180 (deg) at the frequency f2 on the coordinate axes x1 and x2 (FIG. 9). )) (FIG. 3), and the amplitudes of the first springs 121 and 122 and the amplitudes of the second springs 131 and 132 are approximately the same (FIG. 2).

  Therefore, the conveyance amount of the article placed on the conveyance surface 11a in the conveyance direction 93 can be increased at the frequency f2 than at the frequency f1.

<Vibration in region R3>
A case where the first springs 121 and 122 and the second springs 131 and 132 are vibrated in the region R3 will be described. In this case, the first springs 121 and 122 and the second springs 131 and 132 all have an initial phase φ0 of −180 (deg) and vibrate in the same phase (FIG. 3). In addition, the amplitude A of the second springs 131 and 132 is significantly greater than the amplitude A of the first springs 121 and 122 (FIG. 2).

  Specifically, the vibrations of the first springs 121 and 122 and the second springs 131 and 132 at the frequency f3 will be described with reference to FIGS.

  FIG. 11 shows the relationship between time and spring displacement by a graph 1101 for the first springs 121 and 122 and a graph 1102 for the second springs 131 and 132. FIG. 12 is a diagram schematically showing the vibration of the first spring 121 (122) and the vibration of the second spring 131 (132) at the vibration frequency f3 in the vibration conveyance device 1, respectively.

  As shown in FIGS. 11 and 12, since the first springs 121 and 122 and the second springs 131 and 132 vibrate in the same phase (initial phase = −180 (deg)) at the frequency f3. When the first springs 121 and 122 are displaced in the positive direction of the coordinate axis x1 (solid line vector 1201), the second springs 131 and 132 are also displaced in the positive direction of the coordinate axis x2 (solid line vector 1203). The solid line vector 1201 represents the displacement of the first springs 121 and 122 in the positive direction and has the maximum amount of displacement (FIG. 11). A solid line vector 1203 represents the displacement of the second springs 131 and 132 in the positive direction and has the maximum displacement (FIG. 11).

  When the first springs 121 and 122 are displaced in the negative direction of the coordinate axis x1 (broken line vector 1202), the second springs 131 and 132 are also displaced in the negative direction of the coordinate axis x2 (broken line vector 1204). The broken line vector 1202 represents the displacement of the first springs 121 and 122 in the negative direction and has the maximum displacement (FIG. 11). A broken line vector 1204 represents the displacement of the second springs 131 and 132 in the negative direction and has the maximum displacement (FIG. 11).

  FIG. 13 is a diagram illustrating the combined vibration applied to the transport table 11 at the frequency f3. In FIG. 13, the direction and amplitude of the combined vibration are indicated by a combined vector 1301. A combined vector 1301 is a combination of a solid line vector 1201 (FIG. 12) relating to the vibration of the first springs 121 and 122 and a solid line vector 1203 (FIG. 12) relating to the vibration of the second springs 131 and 132, and its direction. Represents the direction of the combined vibration, and the magnitude represents the amplitude of the combined vibration.

  The combined vector 1301 has a component vector that goes in the direction opposite to the transport direction 93. This is because the first springs 121 and 122 and the second springs 131 and 132 vibrate in the same phase (FIG. 3) when the frequency is f3 on the coordinate axes x1 and x2 (FIG. 12). This is because the amplitude of the springs 131 and 132 is significantly larger than the amplitude of the first springs 121 and 122 (FIG. 2).

  Therefore, when the frequency is f3, the article placed on the conveyance surface 11a can be moved in the direction opposite to the conveyance direction 93. Accordingly, in the conveyance direction 93, the article on the conveyance surface 11a can be moved forward. Backward is free.

  In addition, immediately before stopping the conveyance, the direction in which the article is moved can be controlled to be opposite to the direction in which the article has been moved. Thereby, when the conveyance is stopped, the article can be prevented from moving due to inertia. Therefore, it is not necessary to attach a gate for preventing the article from moving due to inertia to the vibration transfer device 1, and thus the vibration transfer device 1 can be simplified.

4). As described above, the amplitude A and the phase difference φ0 of the first springs 121 and 122 and the second springs 131 and 132 can be adjusted by changing the frequency f of the vibration source, Thus, the direction and amplitude of vibration (synthetic vibration) applied to the transport table 11 can be changed.

  Therefore, the amplitude and frequency f of the vibration generated in the vibration source 14 are controlled based on the direction and amplitude of the vibration (synthetic vibration) applied to the carriage 11. Thereby, the conveyance stand 11 can be vibrated with a desired amplitude in a desired direction.

  For example, the amplitude and frequency f of the vibration generated in the vibration source 14 are controlled as follows. That is, the amplitude and frequency of the current flowing through the electromagnetic coil 141 of the vibration source 14 are controlled. This will be specifically described with reference to FIG.

  FIG. 14 is a block diagram conceptually showing the above-described control. The vibration transfer device 1 further includes an inverter 171 and a control unit 172. In FIG. 14, an inverter 171, a control unit 172, and an electromagnetic coil 141 are shown in the vibration transfer device 1.

  The inverter 171 converts the current i1 input from the power source into a current i2 having a desired amplitude and a desired frequency, and outputs the current i2 to the electromagnetic coil 141.

  The control unit 172 is a table representing the relationship between the vibration direction and amplitude of the transport table 11 and the amplitude and frequency f of vibration that should be generated by the vibration source 14 in order to vibrate the transport table 11 with the direction and amplitude. Have.

  In order to vibrate the carriage 11 in a certain direction with a certain amplitude, a vibration direction command S1 is input as a direction command, and an amplitude command S2 is input as an amplitude command. Based on the table, the control unit 172 derives the vibration amplitude and the frequency f to be generated by the vibration source 14 from the input vibration direction command S1 and amplitude command S2.

  Then, the control unit 172 calculates a current i2 to be applied to the vibration source 14 in order to vibrate the vibration source 14 with the derived amplitude and frequency f, so that the current i1 input to the inverter 171 is converted into the current i2. Next, the inverter 171 is controlled.

5. Features of vibration transfer device <Vibration transfer device>
According to the vibration transfer device 1 described above, since the first and second natural frequencies fc1 and fc2 are different from each other, the first springs 121 and 122 and the second springs 131 and 132 are made to have the same frequency by the vibration source 14. The amplitude A and the phase difference Δφ0 of the first springs 121 and 122 and the second springs 131 and 132 can be changed only by changing the frequency f while vibrating at f.

  The vibration direction 912 (coordinate axis x1) of the first springs 121 and 122 and the vibration direction 922 (coordinate axis x2) of the second springs 131 and 132 are inclined to the opposite sides with respect to the vertical direction 90. Cross each other. For this reason, by changing the amplitude A and the phase difference Δφ0 of these vibrations, the direction and amplitude of the vibrations applied to the transport table 11 can be adjusted. Therefore, it is possible to adjust the conveyance amount and carry the article in consideration of the properties of the article.

  Specifically, by selecting vibrations with the same phase (phase difference Δφ0 = 0 (deg)), the article can be conveyed in the conveying direction 93 while loosening or leveling the article. On the other hand, by selecting vibration with an opposite phase (absolute value of phase difference Δφ0 = 180 (deg)), it is possible to increase the conveyance amount of the article in the conveyance direction 93. Also, the article placed on the conveyance surface 11a. With respect to the above-mentioned conveyance, forward and reverse can be selectively executed in the conveyance direction 93.

  Moreover, the carrier 11 can be vibrated at a desired frequency in a desired direction simply by vibrating the first springs 121 and 122 and the second springs 131 and 132 at a certain frequency f. It is possible to reduce the size of the transport device and simplify the control.

<Regarding the characteristics of the first and second springs>
A curve representing the relationship between the frequency f and the amplitude A for the first springs 121 and 122 (graph 201 in FIG. 2) and the relationship between the frequency f and the amplitude A for the second springs 131 and 132 are represented. The curve (graph 202 in FIG. 2) preferably intersects at a certain frequency f as shown in FIG.

  This is because the amplitude A1 of the first springs 121 and 122 and the amplitude A2 of the second springs 131 and 132 are changed by changing the frequency f applied to the first springs 121 and 122 and the second springs 131 and 132. This is because the phase difference Δφ0 can be continuously changed between 0 ° (same phase) and 180 ° (reverse phase) while changing. As a result, the direction and amplitude of the vibration (synthetic vibration) of the transport table 11 can be continuously changed, so that the direction and amplitude of the vibration (synthetic vibration) of the transport table 11 can be finely adjusted.

Second Embodiment Structure of Vibration Conveying Device FIG. 15 is a diagram conceptually showing the vibration conveying device 1A according to the present embodiment. The vibration transfer device 1 </ b> A includes a transfer table 11, first springs 123 and 124, second springs 133 and 134, a vibration source 14 (not shown), and a fixing unit 15.

  In the present embodiment, the arrangement of the first springs 123 and 124 and the second springs 133 and 134 is different from that of the first embodiment. Hereinafter, the arrangement of the first springs 123 and 124 and the second springs 133 and 134 will be specifically described. Other components are the same as those in the first embodiment, and thus the description thereof is omitted.

  As for the characteristics of the first springs 123 and 124 and the second springs 133 and 134, the first springs 121 and 122 and the second springs 131 and 132 described in the first embodiment (see FIGS. Since this is the same as FIG. In the present embodiment, as the initial phase φ0, the case where coordinate axes x3 and x4 are set along the vibration directions 914 and 924 as shown in FIG. 16 is adopted.

<Arrangement of first and second springs>
The first springs 123 and 124 extend in a direction 913 inclined with respect to the vertical direction 90. The second springs 133 and 134 extend in a direction 923 inclined to the same direction as the direction 913 with respect to the vertical direction 90. Note that the direction 913 and the direction 923 intersect each other. Hereinafter, the direction 913 and the direction 923 are referred to as an extending direction 913 and an extending direction 923, respectively.

  Upper ends 123 a and 124 a of the first springs 123 and 124 are connected to a connecting portion 161 fixed to the transport table 11. Lower ends 123b and 124b of the first springs 123 and 124 are connected to upper ends 133a and 134a of the second springs 133 and 134, respectively. Lower end portions 133 b and 134 b of the second springs 133 and 134 are connected to the fixing portion 15.

  Due to the arrangement of the first and second springs described above, for the first springs 123 and 124, the upper ends 123a and 124a are perpendicular to the extending direction 913 with the lower ends 123b and 124b as fulcrums. Vibrates along. Therefore, the first springs 123 and 124 can impart vibrations in the direction 914 to the transport base 11.

  As for the second springs 133 and 134, the upper end portions 133a and 134a vibrate along a direction 924 perpendicular to the extending direction 923, with the lower end portions 133b and 134b serving as fulcrums. Therefore, the second springs 133 and 134 can apply vibrations in the direction 924 to the transport table 11 via the first springs 123 and 124, respectively.

  In view of the fact that the extending direction 923 of the second springs 133, 134 is inclined in the same direction as the extending direction 913 of the first springs 123, 124 with respect to the vertical direction 90 and their directions are different. 924 can be grasped as follows. In other words, the direction 924 is different from the direction 923 and is inclined in the same direction as the direction 923 with respect to the vertical direction 90 (FIG. 15).

<Modification>
In the above-described vibration transfer device 1A, the lower ends 123b and 124b of the first springs 123 and 124 are connected to the upper ends 133a and 134a of the second springs 133 and 134, respectively. In this manner, the first springs 123 and 124 and the second springs 133 and 134 may be connected to each other.

  Further, the first springs 123 and 124 and the second springs 133 and 134 may be separately connected to the transport table 11 and the connecting portion 161.

  Similarly to the first embodiment, the positions at which the lower ends 123b, 124b of the first springs 123, 124 and the upper ends 133a, 134a of the second springs 133, 134 are attached to the connecting portion 164 are connected. It may be the same position in the width direction of the portion 164 (see FIG. 1B) or a position offset to the left and right (see FIG. 1C).

2. Operation of vibration transfer device <Vibration in region R1>
A case where the first springs 123 and 124 and the second springs 133 and 134 are vibrated in the region R1 will be described. In this case, each of the first springs 123 and 124 and the second springs 133 and 134 has an initial phase φ0 of 0 (deg) and vibrates in the same phase (FIG. 3). In addition, the amplitude A of the first springs 123 and 124 is significantly greater than the amplitude A of the second springs 133 and 134 (FIG. 2).

  Specifically, the vibrations of the first springs 123 and 124 and the second springs 133 and 134 at the frequency f1 will be described with reference to FIGS.

  FIG. 17 shows the relationship between time and spring displacement by a graph 511 for the first springs 123 and 124 and a graph 512 for the second springs 133 and 134. In FIG. 17, the coordinate axis x3 and the coordinate axis x4 are overlapped to clarify the relationship between the vibration of the first springs 123 and 124 and the vibration of the second springs 133 and 134, which will be described later. The same applies to FIG. 20 and FIG. Further, the amplitude of the first springs 123 and 124 is denoted by reference numeral A1, and the amplitude of the second springs 133 and 134 is denoted by reference numeral A2. The same applies to FIGS.

  FIG. 18 is a diagram schematically showing the vibration of the first spring 123 (124) and the vibration of the second spring 133 (134) at the vibration frequency f1, respectively, on the vibration transfer device 1A.

  As shown in FIGS. 17 and 18, the first springs 123 and 124 and the second springs 133 and 134 vibrate in the same phase (initial phase = 0 (deg)) at the frequency f1. When the springs 123 and 124 are displaced in the positive direction of the coordinate axis x3 (solid line vector 611), the second springs 133 and 134 are also displaced in the positive direction of the coordinate axis x4 (solid line vector 613). The solid line vector 611 represents the displacement of the first springs 123 and 124 in the positive direction and has the maximum displacement (FIG. 17). A solid line vector 613 represents the displacement of the second springs 133 and 134 in the positive direction and has the maximum displacement (FIG. 17).

  When the first springs 123 and 124 are displaced in the negative direction of the coordinate axis x3 (broken line vector 612), the second springs 133 and 134 are also displaced in the negative direction of the coordinate axis x4 (broken line vector 614). The broken line vector 612 represents the displacement of the first springs 123 and 124 in the negative direction and has the maximum displacement (FIG. 17). A broken line vector 614 represents the displacement of the second springs 133 and 134 in the negative direction and has the maximum displacement (FIG. 17).

  FIG. 19 is a diagram showing the combined vibration applied to the transport table 11 at the frequency f1. In FIG. 19, the direction and amplitude of the combined vibration are indicated by a combined vector 711. A combined vector 711 is a combination of a solid line vector 611 (FIG. 18) related to the vibration of the first springs 123 and 124 and a solid line vector 613 (FIG. 18) related to the vibration of the second springs 133 and 134. Represents the direction of the combined vibration, and the magnitude represents the amplitude of the combined vibration.

  The combined vector 711 includes a component vector that travels in the transport direction 93 and a component vector that travels in the direction 94 perpendicular to the transport surface 11a. This is because the first springs 123 and 124 and the second springs 133 and 134 vibrate in the same phase (FIG. 3) at the frequency f1 on the coordinate axes x3 and x4 (FIG. 18). This is because the amplitude of the springs 123 and 124 is significantly larger than the amplitude of the second springs 133 and 134 (FIG. 2).

  Therefore, when the frequency is f1, the article placed on the transport surface 11a can be moved in the transport direction 93. In addition, since the article can be vibrated in the direction 94 perpendicular to the conveyance surface 11a, the article can be loosened or leveled.

  The amplitude of the combined vibration (the magnitude of the combined vector 711) can be changed by changing the amplitude of the vibration generated in the vibration source 14. Specifically, the amplitude of the composite vibration is increased by increasing (or decreasing) the amplitude of the movable iron core 142 to be vibrated by the vibration source 14 and increasing (or decreasing) the amplitudes A1 and A2 (FIG. 17) ( Or smaller). The same applies to synthetic vibration (FIGS. 22 and 25) described later.

<Vibration in region R2>
A case where the first springs 123 and 124 and the second springs 133 and 134 are vibrated in the region R2 will be described. In this case, the first springs 123 and 124 and the second springs 133 and 134 have different initial phases φ0 and vibrate at different phases (FIG. 3). In addition, the amplitudes of the first springs 123 and 124 and the amplitudes of the second springs 133 and 134 are approximately the same (FIG. 2).

  Specifically, the vibrations of the first springs 121 and 122 and the second springs 131 and 132 at the frequency f2 (FIG. 3) where the absolute value of the phase difference Δφ0 is 180 (deg) are shown in FIGS. 22 will be described.

  FIG. 20 shows the relationship between time and spring displacement by a graph 811 for the first springs 123 and 124 and a graph 812 for the second springs 133 and 134. FIG. 21 is a diagram schematically showing the vibration of the first spring 123 (124) and the vibration of the second spring 133 (134) at the vibration frequency f2 in the vibration transfer device 1A.

  As shown in FIGS. 20 and 21, since the first springs 123 and 124 and the second springs 133 and 134 vibrate in the opposite phase (absolute value of phase difference Δφ0 = 180 (deg)) at the frequency f2. When the first springs 123 and 124 are displaced in the positive direction of the coordinate axis x3 (solid line vector 911), the second springs 133 and 134 are displaced in the negative direction of the coordinate axis x4 (solid line vector 913). The solid line vector 911 represents the displacement of the first springs 123 and 124 in the positive direction and has the maximum displacement (FIG. 20). A solid line vector 913 represents the displacement of the second springs 133 and 134 in the negative direction and has the maximum displacement (FIG. 20).

  When the first springs 123 and 124 are displaced in the negative direction of the coordinate axis x3 (broken line vector 912), the second springs 133 and 134 are displaced in the positive direction of the coordinate axis x4 (broken line vector 914). The broken line vector 912 represents the displacement of the first springs 123 and 124 in the negative direction and has the maximum displacement (FIG. 20). A broken line vector 914 represents the displacement of the second springs 133 and 134 in the positive direction and the displacement amount is maximum (FIG. 20).

  FIG. 22 is a diagram illustrating the combined vibration applied to the transport table 11 at the frequency f2. In FIG. 20, the direction and amplitude of the combined vibration are indicated by a combined vector 1011. A combined vector 1011 is a combination of a solid line vector 911 (FIG. 21) related to the vibration of the first springs 123 and 124 and a solid line vector 913 (FIG. 21) related to the vibration of the second springs 133 and 134. Represents the direction of the combined vibration, and the magnitude represents the amplitude of the combined vibration.

  In the combined vector 1011, the magnitude of the component vector toward the direction 94 perpendicular to the conveyance surface 11 a is more dominant than the magnitude of the component vector toward the conveyance direction 93. This is because the first springs 123 and 124 and the second springs 133 and 134 are in antiphase (absolute value of the phase difference Δφ0 = 180 (deg) at the frequency f2 on the coordinate axes x3 and x4 (FIG. 21). )) (FIG. 3), and the amplitudes of the first springs 123 and 124 and the amplitudes of the second springs 133 and 134 are substantially the same (FIG. 2).

  Therefore, the article placed on the conveying surface 11a can be loosened or smoothed at the frequency f2 than at the frequency f1. In addition, since the vibration in the direction 94 perpendicular to the transport surface 11a is strong, even when an adhesive article is transported, it is possible to prevent the article from adhering to the transport surface 11a.

<Vibration in region R3>
A case where the first springs 123 and 124 and the second springs 133 and 134 are vibrated in the region R3 will be described. In this case, the first springs 123 and 124 and the second springs 133 and 134 all have an initial phase φ0 of −180 (deg), and vibrate in the same phase (FIG. 3). In addition, the amplitude A of the second springs 133 and 134 is significantly greater than the amplitude A of the first springs 123 and 124 (FIG. 2).

  Specifically, the vibrations of the first springs 123 and 124 and the second springs 133 and 134 at the frequency f3 will be described with reference to FIGS.

  FIG. 23 shows the relationship between time and spring displacement by a graph 1111 for the first springs 123 and 124 and a graph 1112 for the second springs 133 and 134. FIG. 24 is a diagram schematically showing the vibration of the first spring 123 (124) and the vibration of the second spring 133 (134) at the vibration frequency f3 in the vibration transfer device 1A.

  As shown in FIGS. 23 and 24, at the frequency f3, the first springs 123 and 124 and the second springs 133 and 134 vibrate in the same phase (initial phase = −180 (deg)). When the first springs 123 and 124 are displaced in the positive direction of the coordinate axis x3 (solid line vector 1211), the second springs 133 and 134 are also displaced in the positive direction of the coordinate axis x4 (solid line vector 1213). The solid line vector 1211 represents the displacement of the first springs 123 and 124 in the positive direction and has the maximum displacement (FIG. 23). The solid line vector 1213 represents the displacement of the second springs 133 and 134 in the positive direction and has the maximum displacement (FIG. 23).

  When the first springs 123 and 124 are displaced in the negative direction of the coordinate axis x3 (broken line vector 1212), the second springs 133 and 134 are also displaced in the negative direction of the coordinate axis x4 (broken line vector 1214). The broken line vector 1212 represents the displacement of the first springs 123 and 124 in the negative direction and has the maximum displacement (FIG. 23). A broken line vector 1214 represents the displacement of the second springs 133 and 134 in the negative direction and has the maximum displacement (FIG. 23).

  FIG. 25 is a diagram illustrating the combined vibration applied to the transport table 11 when the frequency is f3. In FIG. 25, the direction and amplitude of the combined vibration are indicated by a combined vector 1311. The combined vector 1311 is a combination of the solid line vector 1211 (FIG. 24) relating to the vibration of the first springs 123 and 124 and the solid line vector 1213 (FIG. 24) relating to the vibration of the second springs 133 and 134, and its direction. Represents the direction of the combined vibration, and the magnitude represents the amplitude of the combined vibration.

  The combined vector 1311 has a larger component vector toward the transport direction 93 than the combined vector 711 (FIG. 19) in the region R1. This is because the first springs 123 and 124 and the second springs 133 and 134 vibrate in the same phase (FIG. 3) when the frequency f3 in the coordinate axes x3 and x4 (FIG. 24), and the second This is because the amplitude of the springs 133 and 134 is significantly larger than the amplitude of the first springs 123 and 124 (FIG. 2).

  Therefore, when the vibration frequency is f3, the amount of the articles placed on the conveyance surface 11a in the conveyance direction 93 can be increased.

3. Control of Vibration Conveying Device Also in this embodiment, the amplitudes of the first springs 123 and 124 and the second springs 133 and 134 are changed by changing the frequency f of the vibration source as in the first embodiment. A and the phase difference φ0 can be adjusted, so that the direction and amplitude of vibration (synthetic vibration) applied to the carriage 11 can be changed.

4). Characteristics of the Vibration Conveying Device According to the above-described vibration conveying device 1A, the first and second natural frequencies fc1 and fc2 are different from each other. The amplitude A and the phase difference Δφ0 of the first springs 123 and 124 and the second springs 133 and 134 can be changed simply by changing the frequency f while oscillating 134 at the same frequency f.

  The vibration direction 914 (coordinate axis x3) of the first springs 123 and 124 and the vibration direction 924 (coordinate axis x4) of the second springs 133 and 134 are inclined in the same direction with respect to the vertical direction 90. Cross each other. For this reason, by changing the amplitude A and the phase difference Δφ0 of these vibrations, the direction and amplitude of the vibrations applied to the transport table 11 can be adjusted. Therefore, it is possible to adjust the conveyance amount and carry the article in consideration of the properties of the article.

  Specifically, by selecting vibrations in the same phase (phase difference Δφ0 = 0 (deg)), the conveyance amount of the article in the conveyance direction 93 can be increased. On the other hand, by selecting vibration with an opposite phase (absolute value of phase difference Δφ0 = 180 (deg)), even when an adhesive article is conveyed, adhesion of the article to the conveyance surface 11a is prevented. be able to.

  In addition, the conveyance table 11 can be vibrated at a desired frequency in a desired direction by simply vibrating the first springs 123 and 124 and the second springs 133 and 134 at a certain frequency f. It is possible to reduce the size of the transport device and simplify the control.

  FIG. 26 is a diagram conceptually illustrating an automatic weighing machine 2 to which the vibration conveyance device 1 according to the first embodiment can be applied. The automatic weighing machine 2 includes a dispersion table 21, a vibration transfer device 1, a pool hopper 23, a weighing hopper 24, and a vibrator 25. In FIG. 26, the article is indicated by a symbol P, and the flow of the article is indicated by a solid arrow.

  The distribution table 21 has an umbrella shape and is arranged with the tip of the umbrella facing up. The dispersion table 21 is supported near the center by a vibrator 25, and vibrates when the vibrator 25 is driven. Thereby, the articles P placed on the upper surface of the dispersion table 21 are radially dispersed.

  A plurality of vibration transfer apparatuses 1 are arranged around the distribution table 21. The article P dispersed by the dispersion table 21 is placed on the vibration conveyance device 1. Then, the article P on the vibration conveyance device 1 moves toward the pool hopper 23 due to the vibration of the vibration conveyance device 1.

  There are a plurality of pool hoppers 23, and one pool hopper 23 is provided corresponding to each of the vibration transfer devices 1. Article P is put into the pool hopper 23 little by little from the corresponding vibration transfer device 1. Then, the pool hopper 23 temporarily stores the article P and puts it into the weighing hopper 24.

  There are a plurality of weighing hoppers 24, one for each of the pool hoppers 23. The weighing hopper 24 measures the weight of the article P put in from the corresponding pool hopper 23.

  The measured values (the weights of the articles) of the plurality of weighing hoppers 24 are selected and combined so that the total weight of the articles P becomes a predetermined value. Then, the articles are discharged only from the weighing hopper 24 showing the selected measurement value, and these are assembled. The combination can be determined by, for example, a combination calculation.

  Note that the vibration transfer device 1A according to the second embodiment can also be applied to the automatic weighing machine 2 as described above.

Claims (9)

An apparatus for conveying an article while vibrating the article,
A carriage on which the article is placed;
A first spring that vibrates the carrier and resonates at a first natural frequency;
A spring that gives the carrier a vibration in a direction that is different from the direction of the vibration that the first spring gives to the carrier; and a second natural frequency that is different from the first natural frequency. A resonating second spring;
A vibration conveying apparatus comprising: a vibration source that vibrates the first and second springs. The vibration conveyance device according to claim 1, further comprising a control unit that adjusts at least one of an amplitude and a phase of each of the first and second springs by changing a frequency of the vibration source.   The vibration conveyance device according to claim 2, wherein the control unit changes the frequency of the vibration source based on a direction and amplitude of vibrating the conveyance table. The first spring is coupled to the carrier;
The second spring is connected to the transport table via the first spring.
The vibration conveyance apparatus as described in any one of Claim 1 thru | or 3.   The vibration according to any one of claims 1 to 4, wherein the first and second springs can selectively execute at least vibration in the same phase and vibration in the opposite phase. Conveying device.   For the first and second springs, there are a curve representing a change in amplitude of the first spring with respect to the frequency of the vibration source and a curve representing a change in amplitude of the second spring with respect to the frequency. The vibration conveying device according to claim 1, wherein the vibration conveying device intersects at a certain frequency.   The vibration transfer device according to claim 1, wherein at least forward and reverse movements of the article placed on the transfer table can be selectively executed. The transport table has a transport surface on which the article is placed,
The vibration conveyance device according to claim 7, wherein directions in which the first and second springs vibrate are inclined to opposite sides with respect to a direction perpendicular to the conveyance surface. The transport table has a transport surface on which the article is placed,
The vibration according to any one of claims 1 to 6, wherein directions in which the first and second springs vibrate are inclined in the same direction with respect to a direction perpendicular to the conveyance surface. Conveying device.

Images