JP5739463B2 - Vibrating transfer device - Google Patents

Description

  The present invention relates to a vibratory transfer device, and more particularly to a mechanism for adjusting the transfer state of a transfer object.

  2. Description of the Related Art Generally, a vibratory transfer device is known for supplying electronic components and the like to an inspection device while aligning them on a transfer path in a manufacturing facility. In this case, since the processing speed of the conveyed product is determined in the supply destination apparatus such as the inspection apparatus arranged on the downstream side of the conveyance path, the downstream supply is performed at the supply end of the conveyance path of the vibration type conveyance apparatus. It is necessary to supply the conveyed product at a speed that matches the processing speed of the previous apparatus. Here, if the supply speed of the conveyed product is slower than the processing speed of the supply destination device, the processing efficiency of the entire manufacturing facility is reduced, and thus the processing capacity of the manufacturing facility cannot be fully utilized. Therefore, it is usually sufficient to set the supply speed of the conveyed product faster than the processing speed of the supply destination apparatus. However, if the supply speed is too high, the conveyed product stays on the conveying path in the vicinity of the supply end for a long time, so the conveyed item is worn on the conveying path or damaged by contact between the preceding and following conveyed items. Therefore, in practice, it is necessary to precisely adjust the conveyance speed of the vibration type conveyance device in accordance with the processing speed of the supply destination device.

  In the conventional vibratory transfer device, for example, as in Patent Document 1 below, the inclination angle of the driving leaf spring for vibrating the transfer body provided with the transfer path can be adjusted by the movable structure of the spacer or the mounting portion, etc. The composition is known. On the other hand, it is possible to adjust the inclination angle of the anti-vibration leaf spring for connecting the counterweight connected to the carrier to the base, instead of the driving leaf spring for vibrating the carrier. Patent Document 2 discloses a configuration in which the speed can be set.

Japanese Patent Publication No. 44-3778 JP-A-3-106711

  By the way, when installing a vibration type conveying apparatus in a manufacturing facility, various adjustment operations are required in relation to the upstream and downstream manufacturing facilities of the apparatus to be installed. In particular, the conveyance speed of the conveyed product must be adjusted within a range corresponding to the production line. However, in the method of adjusting the inclination angle of the driving leaf spring as in the above-mentioned conventional patent document 1, the vibration angle of the conveyance body is directly adjusted, so that the conveyance speed of the conveyance object can be greatly changed. Since the spring constant of the plate spring is large, changing the inclination angle greatly changes the resonance frequency and amplitude of the entire vibration system. For this reason, in order to precisely set the conveyance speed of the conveyed product to a desired value, complicated and delicate adjustment work is required in consideration of various conditions. Further, when the tilt angle of the driving leaf spring is adjusted, the posture and height of the transport body change greatly depending on the tilt angle. Since the required accuracy with respect to the height is high, it is necessary to readjust the posture and height of the conveyance path after adjusting the inclination angle, which further complicates the operation.

  On the other hand, in the conventional method of changing the inclination angle of the vibration isolating leaf spring as in Patent Document 2, the spring constant in the vibration direction of the vibration isolating leaf spring is usually smaller than the spring constant of the driving leaf spring. The influence on the resonance frequency and amplitude of the drive vibration system composed of the conveyance path and the counterweight connected via the drive leaf spring is small. Further, if the lower end portion of the vibration isolating leaf spring is moved, the inclination angle can be changed without changing the posture and height of the transport body. However, this method does not directly change the vibration mode of the carrier, but only changes the inclination angle of the vibration-proof plate spring that supports the counterweight. That is, it is intended to indirectly control the vibration mode of the conveying body that is elastically supported via the driving leaf spring by changing the elastic support characteristic of the counterweight. Therefore, unless the inclination angle of the vibration-proof leaf spring is changed to a certain extent, the conveyance speed of the conveyed product cannot be adjusted sufficiently, and if the inclination angle is changed greatly, the vibration mode becomes unstable. There is a problem. Further, in this method, since the support mode along the transport direction of the drive vibration system composed of the transport body and the counterweight connected via the driving leaf spring is greatly changed, the balance of the transport state of the entire transport body, For example, if it is attempted to set a uniform transfer speed over the entire length of the transfer path or appropriately change the transfer speed change direction along the transfer direction, it is necessary to consider the balance between the front and rear vibration-proof leaf springs. Adjustment work is often difficult. In addition, as described above, the method of adjusting the inclination angle of the vibration-damping leaf spring can keep the posture and height of the transport body substantially constant, but there are subtleties caused by the attachment and removal of bolts and screws. In order to cope with the increasing precision of the posture and height of the transported body in recent years with the miniaturization of transported objects, the posture and The complicated work for readjustment of the height cannot be omitted.

  Therefore, the present invention solves the above-described problems, and an object of the present invention is to realize a vibrating transfer device that can easily adjust the state of the transfer state along the transfer path. Another object is to realize a vibration type conveying apparatus that can eliminate the need for readjustment of the posture and height of the conveying path even if the inclination angle of the vibration-proof plate spring is adjusted.

  In view of such circumstances, the vibratory transfer device of the present invention includes a transfer body provided with a transfer path, a pair of driving leaf springs that respectively support the transfer body in the front and rear directions of the transfer path, and the pair of drive springs. A pair of connection bodies that are connected to the transport body via drive leaf springs and arranged separately in front and rear in the transport direction, and one end is connected to the pair of connection bodies in front and rear in the transport direction. A pair of piezoelectric driving bodies, a connecting member that connects the other ends of the pair of piezoelectric driving bodies, and a pair of vibration-proofing units that support the pair of connecting bodies on the installation surface before and after in the transport direction, respectively. A leaf spring and a spring angle adjusting mechanism configured to adjust an inclination angle of at least one of the anti-vibration leaf springs before and after the conveying direction.

  According to this invention, the vibration generated by the pair of piezoelectric driving bodies connected in common to the coupling member is transmitted to the corresponding driving leaf springs via the connecting bodies separately disposed before and after the conveying direction. As a result, the transport body is vibrated by the pair of drive leaf springs, and the transported material on the transport path is transported in the transport direction. At this time, the vibration-proof leaf spring that elastically supports the connection body reduces vibration energy that leaks to the installation surface side of the device such as the base.

  In addition, by changing the inclination angle of the anti-vibration leaf spring that elastically supports the connection body by the spring angle adjusting mechanism, the elastic support characteristic received by the connection body driven by the piezoelectric drive body also changes, so the vibration of the transport body Direction and amplitude can be varied. Therefore, it becomes possible to control the conveyance speed and other conveyance modes by the conveyance body by the spring angle adjusting mechanism.

  In particular, in the present invention, since a pair of vibration isolating leaf springs arranged before and after the conveying direction are respectively connected to connecting bodies separately arranged before and after the conveying direction, Even if the tilt angle is changed, the drive vibration system supported by the other vibration-proof leaf spring is basically not affected. Therefore, when the conveyance speed is adjusted on one of the front and rear sides in the conveyance direction, the conveyance speed and other conveyance modes are hardly changed on the other side, so that the adjustment operation can be performed significantly more easily than in the past.

  Here, by using the inertial mass corresponding to the mass of the transport body connected to the driving leaf spring as the connecting member, vibration energy leaking to the installation surface side via the vibration damping leaf spring can be further reduced. In addition, since the independence between the pair of driving vibration systems before and after the conveying direction can be further increased, it is possible to more easily control the vibration mode of the conveying body by adjusting the inclination angle of the vibration-proof leaf spring. It becomes possible.

  In the present invention, it is preferable that the spring angle adjusting mechanism is configured to be able to change an inclination angle of the vibration-proof plate spring in a state where the connection body is fixed. According to this, since the connection body elastically supports the transport body via the driving leaf spring, if the adjustment work is performed with the connection body fixed, the posture and height of the transport body can be changed. Without changing the inclination angle of the vibration-proof leaf spring. The connection body is fixed not only when the connection body itself is directly fixed, but indirectly, for example, by fixing the piezoelectric drive body, the driving leaf spring, the transport body, or the coupling member to the base. However, it can be performed by various methods that can fix the connection body. In this case, it is desirable to use a support fixing means described later.

In the present invention, the are respectively disposed before and after the transport direction, the drive plate spring, said connection member and a pair of driving vibration systems consisting of the piezoelectric driving body, the vibration center disposed on the piezoelectric driving body The connecting body is configured to vibrate in a manner of rotating around, and the spring angle adjusting mechanism is configured to connect at least one of the anti-vibration leaf springs before and after the conveying direction to the anti-vibration leaf spring. the piezoelectric driving body is connected to the connecting member and the driving plate spring, and the virtual center point on the side of the oscillation center of the driving vibration system consisting of the carrier which is connected to the driving plate spring The virtual center point is closer to the vibration center than the anti-vibration leaf spring is configured to be rotatable in a rotation direction around the rotation direction and to be held and fixed at a plurality of positions in the rotation direction. Set to position. According to this, at least one of the vibration-proof leaf springs can be rotated around the virtual center point of the piezoelectric driving body, and can be held and fixed at a plurality of positions in the rotation direction. Even if the inclination angle of the vibration isolating leaf spring is changed, the vibration angle of the connection body around the virtual center point changes, but the posture of the vibration isolating leaf spring viewed from the virtual center point does not change. The displacement of the vibration center of the drive vibration system and the fluctuation of the load on the piezoelectric drive body can be suppressed, and the fluctuation of the resonance frequency and the instability of the vibration mode of the drive vibration system can also be suppressed. In this case, the virtual center point is set at a position closer to the vibration center than the vibration-proof leaf spring . In particular, it is desirable that the virtual center point substantially coincides with the vibration center of the drive vibration system.

  In the present invention, the spring angle adjusting mechanism may include a first anti-vibration leaf spring guided by a first guide surface along a rotation direction around the virtual center point and a first connection between the connection body. The sliding contact portion, the first holding structure for positioning and holding the vibration-proof plate spring with respect to the connecting body in the rotation direction, and the second guide surface along the rotation direction guide the A second sliding contact portion between the vibration-proof plate spring and the installation surface; and a second holding structure for positioning and holding the vibration-proof plate spring in the rotation direction with respect to the installation surface. It is preferable to have.

  In this case, the spring angle adjusting mechanism includes a rotation operation means for rotating the vibration isolation plate spring in the rotation direction, and a vibration isolation plate spring set by the rotation operation means. It is desirable to further have an operation display part provided with a spring angle display means for displaying the inclination angle.

In the present invention, a base on which the lower end of the pair of the vibration isolating plate spring is connected, preferably further has a supporting and fixing means for fixing the position of the connecting member to directly or indirectly the base . When adjusting the inclination angle of the anti-vibration leaf spring by the spring angle adjusting means, the position of the connection body is fixed directly or indirectly to the base using the support fixing means, so that the drive leaf spring is connected to the connection body. Since the posture and height along the conveyance direction of the conveyance body elastically supported via the can be maintained, the work for resetting the posture and height of the conveyance body can be made unnecessary.

  According to the present invention, it is possible to realize a vibration type conveying apparatus that can easily adjust the state of the conveying state along the conveying path by the spring angle adjusting means. Further, it is possible to realize a vibration type conveying apparatus that can eliminate the need for adjusting the posture and height of the conveying path even if the inclination angle of the leaf spring is adjusted by the support fixing means.

It is a perspective view which shows the whole embodiment of the vibration type conveying apparatus concerning this invention from the front of a conveyance direction. It is a front view which shows a mode that the same embodiment was seen from the front of the conveyance direction. It is a left view which shows the state which removed the side surface coating plate of the embodiment. It is a left view which shows the state which removed the conveyance body fixing member of the embodiment further. It is a perspective view of a different posture of the embodiment. It is a right view which shows the state which removed the side surface coating plate of the embodiment. It is a perspective view which shows a mode that the state which removed the side surface coating plate of the embodiment was seen from the back of a conveyance direction. It is an enlarged view of the operation display part of the spring angle adjustment mechanism of the embodiment. It is a fragmentary sectional view which shows the internal structure of the spring angle adjustment mechanism of the embodiment. It is an expanded fragmentary sectional view which expands and shows the internal structure of the spring angle adjustment mechanism in the reference | standard state of the vibration isolating leaf spring. It is an expanded fragmentary sectional view which expands and shows the internal structure of the spring angle adjustment mechanism in the state which changed the inclination-angle of the vibration-proof leaf | plate spring. It is an expanded partial sectional view which expands and shows the internal structure of a spring angle adjustment mechanism in the vertical cross section orthogonal to the vertical cross section shown in FIG. It is structure explanatory drawing for demonstrating operation | movement of the spring angle adjustment mechanism of the embodiment. It is composition explanatory drawing which shows the whole structure of different embodiment.

  Next, embodiments of the present invention will be described in detail with reference to the accompanying drawings. 1 is a perspective view of the present embodiment, FIG. 2 is a front view thereof, FIG. 3 is a left side view showing a state in which a side cover plate is removed, and FIG. 4 is a left side view showing a state in which a carrier fixing member is further removed. 5 is another perspective view, FIG. 6 is a right side view showing a state in which the side cover plate is removed, and FIG. 7 is another perspective view in which the side cover plate is removed.

  The present embodiment is a vibration transfer device 10 that can be mounted with a transfer body (not shown) having a transfer path. The transport body includes a groove-shaped transport path according to the shape and size of the transported object (for example, an electronic component). In the illustrated example, a first trough 1F on which a first transport body (a transport body 10F described later) having a transport path extending linearly toward the transport direction F is mounted, and transport in the direction opposite to the transport direction F And a second trough 1B on which a second transport body having a transport path extending linearly in the direction B is mounted.

  The leaf springs 11 and 12 for driving are connected to the first trough 1F from below at two locations separated in the front and rear in the transport direction F, respectively. In addition, the driving leaf springs 13 and 14 are connected and fixed to the second trough 1B from below at two locations separated in the front and rear in the transport direction B, respectively. These plate springs 11 to 14 are flat in the illustrated example, and are attached in a posture substantially orthogonal to the vibration directions Fv and Bv directed obliquely upward in front of the conveyance directions F and R, respectively, as shown in FIG. It has been. That is, the normal lines of the drive leaf springs 11 and 12 are substantially parallel to the vibration direction Fv, and the normal lines of the drive leaf springs 13 and 14 are substantially parallel to the vibration direction Bv. In FIG. 3, the upper mounting normal Lfu and the lower mounting normal Lfd of the driving leaf springs 11 and 12 are both set in parallel with the vibration direction Fv, and the upper mounting normal Lbu and lower portion of the driving leaf springs 13 and 14 are set. The attachment normal Lbd is set in parallel with the vibration direction Bv.

  The lower ends of the drive leaf springs 11 to 14 are connected and fixed to the upper ends of a pair of connection bodies 15 and 16 disposed below the front and rear in the transport directions F and B, respectively. The connection body 15 is connected and fixed to a vibration-proof plate spring 17 extending downward, and the lower end of the vibration-proof plate spring 17 is connected and fixed to the base 19. The connection body 16 is connected and fixed to a vibration-proof plate spring 18 extending downward, and the lower end of the vibration-proof plate spring 18 is connected and fixed to a base 19. The anti-vibration leaf springs 17 and 18 are also formed in a flat plate shape in the illustrated example, and are basically attached in a posture substantially orthogonal to the vibration direction Fv. The anti-vibration leaf spring 17 is connected and fixed to the connecting body 15 at the upper mounting normal Ldu1, and is connected and fixed to the anti-vibration spring mounting member 21 of the spring angle adjusting mechanism 20 described later at the lower mounting normal Ldd1. Further, the vibration isolating leaf spring 18 is connected and fixed to the connection body 16 at the upper mounting normal Ldu2, and is connected and fixed to the base 19 at the lower mounting normal Ldd2. In the present embodiment, both the upper mounting normal line Ldu1 and the lower mounting normal line Ldd1 of the vibration isolating leaf spring 17 are made variable so that the inclination angle θ can be adjusted by the spring angle adjusting mechanism 20 described in detail later. Composed. On the other hand, the upper mounting normal line Ldu2 and the lower mounting normal line Ldd2 of the vibration isolating leaf spring 18 are fixed.

  The lower end of the piezoelectric driving body D1 extending upward is connected and fixed to the lower end of the connection body 15, and the upper end of the piezoelectric driving body D1 is connected and fixed to the front end of the connecting plate Cn. The lower end of the piezoelectric driving body D2 extending upward is connected and fixed to the lower end of the connection body 16, and the upper end of the piezoelectric driving body D2 is connected and fixed to the rear end of the connecting plate Cn. Therefore, the connecting plate Cn extends along the transport direction F, and connects the upper ends of the pair of piezoelectric driving bodies D1 and D2 before and after the connecting plate Cn. A weight block Cw is fixed to the lower part of the connecting plate Cn. The connection plate Cn and the weight block Cw correspond to the above-described connection members. In this embodiment, the inertia mass body (counterweight) connected to the opposite end of the pair of piezoelectric drive bodies D1 and D2 as a whole in this embodiment. ). This inertia mass body has a mass substantially equal to the total mass of the first trough 1F and the transport body mounted on the first trough 1F, and the vibration energy leaks to the base 19 side via the vibration isolating leaf springs 17 and 18. Reduce.

  The piezoelectric driving bodies D1 and D2 include a piezoelectric element composed of a leaf spring-like elastic substrate and a piezoelectric layer laminated on the surface of the substrate. By applying an alternating voltage to the front and back of the piezoelectric layer, the vibration direction Fv Deflection and deformation in a direction substantially along In the illustrated example, the piezoelectric driving bodies D1 and D2 are composed of only piezoelectric elements. However, a plate spring connected in series to the piezoelectric elements may be used. In both cases where the piezoelectric driving bodies D1 and D2 are composed only of piezoelectric elements and in which the leaf springs are connected in series, the piezoelectric driving bodies D1 and D2 are one in the above vibration system. Acts as two leaf springs. In the illustrated example, the piezoelectric driving bodies D1 and D2 are of a bimorph type in which piezoelectric bodies are laminated on both surfaces of an elastic substrate. The piezoelectric driving bodies D1 and D2 are formed in a plate shape as a whole, and are attached in a posture substantially orthogonal to the transport directions F and B. In particular, when the transport direction F is the supply direction, the vibration and the transport direction F are vibrated. It is preferable to attach with the attitude | position which has the normal line which faced the intermediate direction between the direction Fv.

  Side support plates Sx (shown by a two-dot chain line in FIG. 1) and Sy are attached to the base 19 on both the left and right sides. The side surface covering plates Sx and Sy extend upward from the base 19, respectively, and cover the side of the connecting plate Cn, preferably the vicinity of the lower portions of the first trough 1F and the second trough 1B from the left and right sides. ing. Further, the support fixing member 30 is attached to at least one of the left and right sides, that is, the left side in the illustrated example. The support fixing member 30 constitutes the support fixing means for fixing the connection body 15. In the illustrated example, the support fixing member 30 is attached and fixed to the side portion of the base 19 and the side portion of the connecting plate Cn from the outside so as to straddle the side surface covering plate Sx. In the state of being attached and fixed in this manner, the support fixing member 30 acts to fix the position of the connection body 15 as a result. In the illustrated example, a central screw hole Cna and front and rear concave holes Cnb are provided on the side of the connecting plate Cn, and a central screw hole 19a and front and rear concave holes 19b are also provided on the side of the base 19. . On the other hand, on the inner surface of the support fixing member 30, there are through holes through which bolts corresponding to the screw holes Cna and 19a can be inserted, and fitting protrusions corresponding to the concave holes Cnb and 19b, respectively. It is formed. The support fixing member 30 is attached by screwing the bolt 31 from the upper and lower through holes into the screw holes Cna and 10a in a state where the fitting protrusion is inserted into the concave holes Cnb and 19b. By attaching the support fixing member 30, the position of the connection body 15 to which the vibration isolating leaf spring 17 is connected is fixed. Therefore, even if the vibration isolating leaf spring 17 is moved or removed, the posture of the transport body or Height remains unchanged. In addition, since the support fixing member 30 is for maintaining the posture and height of the transport body in the end, it is sufficient that the position of the connection body 15 is fixed as a result, for example, the connection body 15 itself. May be fixed to the base 19, or the first trough 1 </ b> F or the transport body itself may be fixed to the base 19.

  A side frame 22 is attached to the base 19 at the lower part of the front end of the side surface to which the support fixing member 30 is attached. On the outer surface of the side frame 22, as shown in FIG. 8, a dial-type operation unit 22 a and a scale corresponding to the operation unit 22 a have a predetermined inclination angle θ of the anti-vibration leaf spring 17. A display unit 22b for displaying by a method is provided. In the illustrated example, the operation portion 22a is constituted by a straight groove formed on a convex curved rotary shaft head. The display portion 22b is composed of a scale formed around the rotary shaft head where the operation portion 22a is formed, and the scale position indicated by the operation portion 22a corresponds to the inclination angle of the vibration-proof leaf spring described later. It is supposed to be.

  In the vibration type conveying apparatus of the present embodiment, as shown in FIG. 3, the first troughs 1F and 1B, the driving leaf springs 11 to 13, the connecting bodies 15 and 16, the piezoelectric driving bodies D1 and D2, The connecting members Cn and Cw constitute a vibrating body structure that is elastically supported by the vibration-proof plate springs 17 and 18. More specifically, in the present embodiment, the connecting members Cn and Cw act as an inertial mass body, so that the driving plate spring 11, the connection body 15, and the piezoelectric driving body D1 are formed in front of the conveyance direction F. A drive vibration system is configured, and behind the transport direction F, a drive vibration system including the drive leaf spring 12, the connection body 16, and the piezoelectric drive body D2 is formed. In the present embodiment, since the connecting bodies 15 and 16 are separately provided, the two drive vibration systems may be regarded as a vibration system that is substantially independent as an action on the transport body (first trough 1F). is there.

  Next, the spring angle adjusting mechanism 20 will be described with reference to FIGS. Usually, the vibration system substantially vibrates in such a manner that it is rotated around a vibration center disposed in the piezoelectric driving bodies D1 and D2 by being given a vibration generating force by the piezoelectric driving bodies D1 and D2. However, in the strict sense, the vibration center includes the entire configuration of the pair of driving vibration systems before and after the conveyance direction F, the elastic support characteristics of the vibration damping leaf springs 17 and 18, and the driving vibration system before and after the conveyance direction F. It is difficult to specify an accurate location because it is affected by the size and rigidity of the connecting members (inertial mass bodies) Cn and Cw disposed between the balance and the two vibration systems. Therefore, as shown in FIG. 9, the spring angle adjusting mechanism 20 sets a virtual center point O1 that is assumed to be on the side where the actual vibration center exists as viewed from the vibration-proof leaf spring 17, and the virtual center point is set. An anti-vibration leaf spring 17 is configured to be rotatable around O1, and an inclination angle θ of the anti-vibration leaf spring 17 in the conveying direction F can be adjusted by this rotation. In the present embodiment, the virtual center point O <b> 1 is set at a position closer to the actual vibration center than the respective portions of the vibration-damping leaf spring 17 (position considered to be substantially the vibration center).

  As shown in FIG. 9, the connecting body 15 includes a connecting member 15A, an upper mounting structure 15B made of spacers, bolts, and the like for mounting the driving leaf spring 11 to the connecting member 15A, and the connecting member 15A. A lower mounting structure 15C composed of a spacer, a bolt or the like for mounting the piezoelectric driving body D1, and a vibration isolation composed of a spacer, a bolt, etc. for mounting the vibration isolating leaf spring 17 to the connecting member 15A. And a spring mounting structure 15D. The connection height of the anti-vibration leaf spring 17 to the connection member 15a by the anti-vibration spring attachment structure 15D is such that the drive leaf spring 11 is attached by the upper attachment structure 15B and the piezoelectric drive body D1 is attached by the lower attachment structure 15C. Configured to be between positions. Such a configuration brings about advantageous effects with respect to securing the arrangement space of the piezoelectric driving body D1, reducing the spring constant in the conveying direction F (vibration direction) of the vibration isolating plate spring 17, reducing the overall height of the apparatus, and the like. . The above-described configuration is the same for the connection body 16 as well.

  FIG. 10 shows a vibration isolating plate spring 17 in a posture parallel to the driving leaf spring 11 (inclination angle θ = 3.5 degrees, the value of the display unit 22b corresponding to the operation unit 22a is 1). 3 is a partial cross-sectional view showing a mounting structure of a leaf spring 17. FIG. The upper end of the anti-vibration leaf spring 17 is connected and fixed to the anti-vibration spring mounting structure 15 </ b> D of the connection body 15 constituting a part of the spring angle adjustment mechanism 20. The anti-vibration spring mounting structure 15D includes an arcuate portion 15a configured coaxially with the virtual center point O1 provided on the connection member 15A. Arc-shaped sliding contact surfaces formed coaxially with the virtual center point O1 are formed on both the inner and outer surfaces of the arc-shaped portion 15a. The anti-vibration spring mounting structure D has a structure for releasably holding the inner holding member 15b and the outer holding member 15c, which are spacers having sliding contact surfaces that are in sliding contact with both the inner and outer surfaces of the arcuate portion 15a. Have. Here, the anti-vibration spring mounting structure 15D includes the sliding contact surfaces on both the inner and outer sides of the arc-shaped portion 15a, the sliding contact surface on the outer surface of the inner holding member 15b, and the sliding contact surface on the inner surface of the outer holding member 15c. And a first holding structure constituted by a circular hole 15a and a through hole of the inner holding member 15b, a screw hole of the outer holding member 15c, a bolt, and the like. Here, the vibration isolating plate spring 17 is fixed to the connecting member 15A by tightening the bolt or the like of the first holding structure, and the vibration isolating plate spring 17 is removed by loosening the bolt or the like of the first holding structure. It is comprised so that it can be rotated around the virtual center point O1 along the sliding contact part.

On the other hand, the lower end of the anti-vibration leaf spring 17 is connected and fixed to an anti-vibration spring attachment member 21 constituting a part of the spring angle adjustment mechanism 20 by an anti-vibration spring attachment structure 21D made of a spacer, a bolt, or the like. The vibration-proof spring attachment member 21 protrudes toward the left side (the side of the later-described side frame 22), the upper and lower sides, the arcuate engagement surface formed coaxially about the virtual center O1 The provided engaging portion 21a, screw holes 21b formed on the left and right side surfaces for mounting bolts and the like, and a cam groove 21c opened on the left side surface are provided.

  Side frames 22 and 23 attached and fixed to the base 19 are arranged on both the left and right sides of the vibration-proof spring mounting member 21. As shown in FIG. 12, the side frames 22 and 23 are formed with through holes 22c and 23c, and the bolts 24 inserted into the through holes 22c and 23c are screwed into the screw holes 21b of the vibration-proof spring mounting member 21, thereby preventing the side frames 22 and 23. The vibration spring mounting member 21 can be fixed to the base 19. Here, the detachable fixing structure between the anti-vibration spring mounting member 21 and the side frames 22 and 23 via the bolts 24 corresponds to the second holding structure. Further, as shown in FIG. 10, a guide groove 22d is formed on the inner surface of the side frame 22 along the rotation direction around the virtual center point O1, and the engaging portion 21a is fitted into the guide groove 22d. The arcuate engagement surface is in sliding contact with the inner surface of the guide groove 22d, so that the anti-vibration spring mounting member 21 is guided in the rotational direction. This guide structure constitutes the second sliding contact portion. Furthermore, the cam groove 21c of the vibration-proof spring mounting member 21 is fitted with a columnar cam 25 that is connected and fixed so as to be eccentric with respect to the operation portion 22a protruding on the outer surface of the side frame 22. When the dial-type operation unit 22a is rotated, the cam 25 is eccentrically rotated, whereby the anti-vibration spring mounting member 21 is moved along the guide groove 22d. In this way, the vibration isolation spring mounting member 21 mounted and fixed to the lower end of the vibration isolation leaf spring 17 rotates around the virtual center point O1 by the guide groove 22d of the side frame 22 fixed to the base 19. Therefore, even if the vibration-proof plate spring 17 is rotated, the posture and height of the drive vibration system are basically maintained.

  Next, a method for adjusting the inclination angle θ of the vibration isolating leaf spring 17 using the spring angle adjusting mechanism 20 configured as described above and the operation of each part will be described. First, prior to starting the adjustment of the inclination angle θ of the vibration isolating plate spring 17, in order to maintain the posture and height of the first trough 1F (conveyance body), the support fixing member 30 is moved to the side of the connecting plate Cn. And fixed to the side of the base 19. As a result, the connection body 15 is fixed even when the holding and fixing state of the anti-vibration spring mounting structure 15D of the anti-vibration leaf spring 17, the anti-vibration spring mounting member 21 and the side frames 22 and 23 is released. The position does not change, and the posture and height of a carrier (not shown) mounted on the first trough 1F and the second trough 1B are not changed.

  Next, the anti-vibration spring mounting structure 15D is released by loosening a bolt or the like, and the fixing structure between the anti-vibration spring attachment member 21 and the side frames 22 and 23 is released by loosening the bolt 24. The first holding structure and the second holding structure are released to make the vibration-proof leaf spring 17 movable. In this way, the upper end of the anti-vibration leaf spring 17 has an imaginary center point by the first sliding contact portion constituted by the arcuate portion 15a of the anti-vibration spring mounting structure 15D, the inner holding member 15b, and the outer holding member 15c. A second sliding contact portion that is guided so as to be pivotable around O1 and that has a lower end of the vibration isolating leaf spring 17 constituted by an engaging portion 21a of the vibration isolating spring mounting member 21 and a guide groove 22d of the side frame 22. As a result, the center of the virtual center point O1 is guided to be rotatable.

  In this state, when the operation portion 22a on the outer surface of the side frame 22 is rotated, the anti-vibration spring mounting member 21 is guided as described above through the cam groove 21c of the second sliding contact portion by the eccentric rotation of the cam 25. Accordingly, the anti-vibration spring mounting structure 15D also rotates while being guided by the first sliding contact portion as described above, so that the anti-vibration leaf spring 17 fixed to the anti-vibration spring attachment member 21 is rotated. Rotates around the virtual center point O1. Therefore, the inclination angle θ of the vibration isolating leaf spring 17 shown in FIG. 9 changes according to the rotation operation of the operation portion 22a. For example, the reference state shown in FIG. 10 can be changed to the state shown in FIGS. Here, the inclination angle θ of the vibration-proof leaf spring 17 is preferably adjustable within a range of at least ± 1.5 degrees, and in particular, adjustable within a range of at least ± 3.0 degrees. Is desirable. In addition, it is preferable that the inclination angle θ is about 2.5 to 3.5 degrees as a standard value, and can be adjusted in either direction of increase or decrease. Furthermore, it is desirable to provide a scale appropriately set so as to have a predetermined correspondence with the tilt angle θ. In the illustrated display portion 22b, the reference state shown in FIG. 10 in which the vibration isolating plate spring 17 is parallel to the driving plate spring 11 is set to 0. From this reference state, the vibration isolating plate spring 17 is shown in the drawing. Are provided with scales 1 to 6 indicating the amount of change in angle (unit = degree), which takes a positive value in the direction of increasing the inclination angle θ in the horizontal direction. 1 to 8 show a state in which the operation unit 22a indicates the scale 6 of the display unit 22b. Further, the standard value may be set to 0, and the scale may be displayed in both plus and minus directions from the standard value.

  When the operation portion 22a is operated as described above and the posture of the vibration isolating leaf spring 17 is changed to the desired inclination angle θ, the bolt and the side frame 22 of the vibration isolating spring mounting structure 15D are arranged. The upper end and the lower end (anti-vibration spring mounting member 21) of the anti-vibration leaf spring 17 are fixed by tightening the bolts 24 on the outer surface of the anti-vibration plate 17 respectively. Finally, the support fixing member 30 is removed from the connecting plate Cn and the base 19.

  As described above, when the inclination angle θ of the vibration-proof plate spring 17 is adjusted, the conveyance mode along the conveyance direction of the conveyance body can be changed as follows. FIG. 13 is an explanatory diagram schematically showing the overall configuration of the vibratory transfer apparatus 10 of the present embodiment. Here, it is assumed that the transport body 10F is mounted on the first trough 1F. As shown in FIG. 13, in the present embodiment, the anti-vibration leaf spring 17 ′ having the inclination angle θ increased by adjusting the anti-vibration leaf spring 17 in the reference state (inclination angle θ = 3.5 degrees) can do. Here, the elastic support characteristic given to the connection body 15 by the vibration isolating plate spring 17 in the standard state has a minimum spring constant Sa in a direction orthogonal to the driving plate spring 11 and the anti-vibration leaf spring 17, and the driving plate. The spring constant Sb in the direction parallel to the spring 11 and the vibration isolating plate spring 17 is maximized. For this reason, the vibration generated by the vibration force of the piezoelectric driving body D1 is transmitted to the driving leaf spring 11 through the connection body 15 that is substantially elastically supported with the minimum spring constant Sa, so that the transport body 10F is driven. It vibrates efficiently in the vibration direction Fv perpendicular to the inclination angle of the plate spring 11.

  On the other hand, when the inclination angle θ increases, the elastic support characteristic that the vibration isolating leaf spring 17 gives to the connection body 15 is such that the direction having the minimum spring constant Sa ′ is in the transport direction F compared to Sa in the reference state. Since the displacement is further upwards toward the front, the connection body 15 driven by the piezoelectric driving body D1 vibrates slightly upward compared to the reference state, and its amplitude is also slightly smaller. Accordingly, the vibration direction Fv ′ of the transport body 10F also changes slightly upward as compared with the vibration direction Fv in the reference state, and the amplitude becomes small, so that the transport speed of the transport object W decreases. Further, generally speaking, by increasing or decreasing the inclination angle θ of the vibration isolating plate spring 17, the piezoelectric drive body 1 </ b> D, the connecting body 15, and the driving plate spring 11 corresponding to the vibration isolating plate spring 17 are formed. Since the vibration direction Fv given by the drive vibration system and the amplitude thereof can be changed, the conveyance speed and other conveyance states (such as posture stability during conveyance of the conveyance object W) can be adjusted.

  In the present embodiment, the vibration direction Fv can be adjusted by the inclination angle θ of the vibration-proof leaf spring 17 in the drive vibration system in the front in the transport direction F as described above. On the other hand, the driving vibration system behind the conveyance direction F, which is composed of the piezoelectric driving body D2, the connection body 16, and the driving leaf spring 12, is connected to the front driving vibration system via the connecting plate Cn and the weight block Cw. Therefore, although the vibration phase is synchronized, the vibration direction and amplitude act on the carrier 10F substantially independently. For this reason, if the inclination angle θ of the vibration isolating leaf spring 18 that elastically supports the connection body 16 does not change, the rear portion of the transport body 10F in the transport direction F still vibrates according to the vibration direction Fv and amplitude in the reference state. become. Therefore, as described above, the transport state of the transport object W arranged on the rear portion of the transport body 10F is a transport state different from the front portion of the transport body 10F. For example, in the above example, the conveyance speed is high in the rear part of the conveyance body 10F, and the conveyance speed is low in the front part. The independence of the driving vibration system before and after the conveying direction F can be obtained only by connecting the piezoelectric driving bodies D1 and D2 with the connecting plate Cn, but by a method such as connecting the weight block Cw as in the illustrated example. The higher the inertial mass on the other end side of the piezoelectric driving bodies D1 and D2, the higher the value.

  In this embodiment, the inclination angle θ of the vibration isolating leaf spring 17 is set so that the vibration isolating leaf spring 17 rotates around the virtual center point O1 on the vibration center side which is normally set inside the piezoelectric driving body D1. Since it is changed by being moved, the orientation of the vibration isolation leaf spring 17 viewed from the virtual center point O1 changes, but the posture of the vibration isolation leaf spring 17 viewed from the virtual center point O1 does not change. For this reason, the change in the inclination angle θ of the vibration isolating plate spring 17 brings about a change in the vibration mode caused by the change in the connection angle between the driving plate spring 11 and the vibration isolating plate spring 17, and the surroundings of the virtual center point O 1. The angle range (vibration direction) of the connection body 15 is changed, but the vibration around the virtual center point O1 is hardly affected. Therefore, even when the inclination angle θ is adjusted, if the angle range is small, it is possible to suppress the displacement of the vibration center and the variation of the load mode with respect to the piezoelectric driving body D1. For the same reason, it is possible to avoid fluctuations in the resonance frequency and instability of the vibration mode of the drive vibration system. Although it is desirable that the virtual center point O1 substantially coincides with the actual vibration center, the virtual center point O1 may be closer to the vibration center than each part of the vibration isolating leaf spring 17 even if it does not completely coincide. Equivalent effects can be obtained.

  Changing the transport speed before and after the transport body 10F as described above is effective in the following cases. For example, when another supply destination device 50 such as an inspection device is disposed downstream of the transport body 10F as shown in FIG. 13, the processing capability of the supply destination device 50 for the transported object W is maximized. Therefore, it is necessary to set the transport speed of the transported object W on the transport body 10F to be larger than the processing speed corresponding to the processing capacity. This is because the transported object W with an inappropriate transport posture or structural defect is removed from the transport path (in this embodiment, adjacent to the transport path for supplying the transport body 10F). Configured to discharge a part of the transported object W to the transport path for collecting the transported body.) When the transported object W is transported at a transport speed substantially corresponding to the processing capability, This is because by eliminating the conveyed product W, a substantial supply amount is insufficient and the processing capability of the supply destination apparatus 50 cannot be fully utilized. However, when the transport speed of the transport body 10F is set to be higher than the processing speed in this way, as shown in FIG. 13, the front end (supply end) in the transport direction F in which transfer is performed with the apparatus 50 of the transport body 10F. In the vicinity, the conveyed product W stays. Although such a staying state of the transported object W is necessary to some extent, if the staying state is prolonged, there is a possibility that the friction between the transported object W and the transport path, the damage due to the contact between the transported objects W, contamination, etc. may be caused. . Therefore, by increasing the conveyance speed on the upstream side (the rear portion in the conveyance direction F) and decreasing the conveyance speed on the downstream side (the front portion in the conveyance direction F), the substantial residence time of each conveyance object W is shortened. In addition, by reducing the conveyance energy itself given to the conveyed product W in the vicinity of the supply end, the degree of damage and contamination of the conveyed product W can be reduced.

  In the present embodiment, contrary to the above, it is also possible to control by the spring angle adjustment mechanism 20 so as to increase the conveyance speed from the rear part to the front part in the conveyance direction F of the conveyance body 10F. In order to obtain a uniform conveyance speed over the entire length of the conveyance body 10F, the spring angle adjusting mechanism 20 can be used.

  In the case of the present embodiment, the second trough 1B is also connected to the connection body 15 via the driving leaf spring 13, so that it is mounted on the second trough 1B by the spring angle adjusting mechanism 20. Concerning a transport body (not shown) (for example, a transport body having a recovery transport path for receiving the transport object W excluded from the transport body 10F, transporting the transport object W in the reverse direction, and returning it to the upstream side) The conveyance speed and other conveyance states can be controlled. However, since the conveyance direction B in this case is opposite to the conveyance direction F, the control state of the conveyance state along the conveyance direction is opposite to the conveyance body 10F.

  In FIG. 14, in addition to the spring angle adjusting mechanism 20 for adjusting the inclination angle θ of the vibration isolating plate spring 17, a spring angle adjusting mechanism 20 ′ for adjusting the inclination angle of the anti vibration isolating spring 18 is shown. The provided structure is shown. As described above, in this embodiment, the driving vibration system in front of the conveyance direction F and the driving vibration system in the rear act on the conveyance body 10F substantially independently. By providing the spring angle adjustment mechanisms 20 and 20 ', it is possible to more accurately and easily control the conveyance speed and other conveyance states across the conveyance direction F of the conveyance body 10F.

  Note that the vibratory conveyance device of the present invention is not limited to the above-described illustrated examples, and it is needless to say that various changes can be made without departing from the gist of the present invention. For example, the vibratory conveyance device of the above embodiment has a structure in which a conveyance body provided with a conveyance path for supply and a conveyance body equipped with a conveyance path for recovery can be arranged in parallel, but provided with a conveyance path for supply. It is good also as an apparatus structure which can mount only a conveyance body.

DESCRIPTION OF SYMBOLS 10 ... Vibration type conveying apparatus, 10F ... Conveyance body, 1F ... 1st trough, 1B ... 2nd trough, 11-14 ... Leaf spring for driving, 15, 16 ... Connection body, 15A ... Connection member, 15B ... Upper part Mounting structure, 15C: Lower mounting structure, 15D: Anti-vibration spring mounting structure, 15a ... Arc-shaped portion, 15b ... Inner holding member, 15c ... Outer holding member, 17, 18 ... Anti-vibration leaf spring, 19 ... Base, 20, 20 '... Spring angle adjustment mechanism, 21 ... Anti-vibration spring attachment member, 21D ... Anti-vibration spring attachment structure, 21a ... Engagement part, 21b ... Screw hole, 21c ... Cam groove, 22, 23 ... Side frame, 22a ... operation part, 22b ... display part, 22c, 23c ... through hole, 22d ... guide groove, 24 ... bolt, 25 ... camshaft, D1, D2 ... piezoelectric drive, Cn ... connecting plate, Cw ... weight block, F, B: transport direction, Fv, Fb: vibration direction, θ: inclination angle W ... work, 50 ... supply target device

Claims (5)

A transport body having a transport path;
A pair of drive leaf springs for supporting the transport body before and after the transport direction of the transport path;
A pair of connecting bodies respectively connected to the transport body via the pair of driving leaf springs and arranged in the front and back of the transport direction;
A pair of piezoelectric driving bodies each having one end connected to the pair of connecting bodies and arranged in front and rear in the transport direction;
A connecting member for connecting the other ends of the pair of piezoelectric driving members;
A pair of anti-vibration leaf springs for supporting the pair of connectors on the installation surface in the front-rear direction in the transport direction;
A spring angle adjustment mechanism capable of adjusting an inclination angle of at least one of the vibration-proof leaf springs before and after the conveying direction;
Equipped with,
A pair of drive vibration systems including the drive leaf spring, the connection body, and the piezoelectric drive body, which are respectively arranged before and after the conveyance direction, rotate around a vibration center disposed in the piezoelectric drive body. Each vibrate in a manner,
The spring angle adjusting mechanism is configured to connect at least one of the anti-vibration leaf springs before and after the conveying direction, the connection body connected to the anti-vibration leaf spring, and the piezoelectric drive connected to the connection body. body and the driving plate spring, and rotatably configured in the rotational direction about the imaginary center point on the side of the oscillation center of the driving vibration system consisting of the carrier which is connected to the driving plate spring vibration, and the holding fixably composed of a plurality of positions in the rotational direction, the virtual center point, characterized by Rukoto is set to a position closer to the vibration center than the vibration isolating plate spring Type conveyor.   The vibration type conveying apparatus according to claim 1, wherein the spring angle adjusting mechanism is configured to be able to change an inclination angle of the vibration-proof plate spring in a state where the connection body is fixed. The spring angle adjustment mechanism is
A first sliding contact portion between the anti-vibration leaf spring guided by the first guide surface along the rotation direction and the connection body;
A first holding structure for positioning and holding the anti-vibration leaf spring with respect to the connection body in the rotation direction;
A second sliding contact portion between the vibration isolating leaf spring guided by the second guide surface along the rotation direction and the installation surface;
A second holding structure for positioning and holding the vibration-proof plate spring in the rotation direction with respect to the installation surface;
The vibratory transfer device according to claim 1, wherein the vibration transfer device is provided. The spring angle adjusting mechanism displays a rotation operation means for rotating the vibration isolation plate spring in the rotation direction, and an inclination angle of the vibration isolation plate spring set by the rotation operation means. The vibratory conveyance device according to claim 2 , further comprising an operation display unit provided with a spring angle display means. Claims, characterized in that it further comprises a base on which the lower end of the pair of the vibration isolating plate springs are connected, and a support fixing means for fixing the position of the connecting member to directly or indirectly the base 5. The vibratory transfer device according to any one of 1 to 4 .

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