JP2001171827A - Vibrating mechanism for parts aligner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To effectively prevent vibration of a shaking table from being transmitted to the circumference. SOLUTION: This vibrating mechanism for a parts aligner is provided with a motor M fixed to the shaking table 8, an eccentric cam 54 fitted to the rotary shaft 53 of the motor M, a rotating ring 57 rotatably fitted around the outer circumference of the eccentric cam 54, and the shaking table 4 connected to the rotating ring 57. A balancer 70 for offsetting the vibration by shaft whirling movement of the eccentric cam 54 is attached to the rotary shaft 53 and a selectively detachable weight 72 is installed in a holder 71 of the balancer 70.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration mechanism of a component aligner for aligning electronic components, precision mechanical components, and the like on a component alignment pallet.

[0002]

2. Description of the Related Art When handling a large amount of small parts such as electronic parts and precision machine parts, for example, if they are stored separately in a cardboard case or the like, it is difficult to handle and accidents such as breakage are liable to occur. It is difficult to perform effective production management.

[0003] As a specific example, regarding precision equipment such as ICs and watches, these parts are mass-produced except for special ones, and the number of parts handled in the manufacturing process and distribution process is enormous. Become. For example, the manufacture of ICs is performed as a series of operations, and in the manufacture, necessary parts such as frames and packages of a predetermined lot number must be supplied in an aligned state for each process. However, it is not possible to manually arrange a huge amount of small parts one by one due to work efficiency.

Therefore, conventionally, small parts have been arranged on a parts arrangement pallet by a swinging part arrangement machine and supplied to a manufacturing process. Although there are various types of configurations of the swinging type component aligning machine, an example of the configuration will be described below with reference to FIG.

[0005] The schematic structure of the oscillating component aligner 1 shown in FIG. 8 will be described. An alignment pallet 2 for aligning desired components.
And a collection pallet 3 which can be called a dust removal shape is mounted on the vibration table 4.
The recovery pallet 3 on one end side is supported by the stopper 5,
The other end is sandwiched by another collection pallet 3 and the fixed lever 7 urged in the direction of the stopper 5 by the compression spring 6 is opened and closed (movements in the directions of arrows A and B).

The vibration table 4 oscillates eccentrically about a rotation axis extending in the vertical direction in the figure while maintaining a horizontal state with respect to the swing table 8. Also,
The vibration table 4 is configured to swing with the lower swing table 8 in the directions of arrows C and D in the figure, and the swing table 8 is connected to the swing drive unit 11 via the connection unit 9. ing.

The swing drive unit 11 is provided on a base 12,
For example, the rocking table 8 is rocked in the directions of arrows C and D at a constant cycle by a motor and a cam mechanism. The swing cycle can be freely adjusted according to the shape and weight of the components to be aligned.

In order to align the components, the components are placed on the alignment pallet 2 and the vibration table 4 is swung in the directions of arrows C and D while eccentrically oscillating. As a result, the parts reciprocate between the collection pallets 3 while vibrating on the arrangement pallets 2, and during this time, they fit into, for example, concave molds formed on the arrangement pallets 2 according to the shapes of the parts. And align. When the components are accommodated in the mold, that is, when the alignment of the components is completed, the swinging of the swingable component aligner 1 is stopped, and the collection pallet 3 is pulled from the vibration table 4 while pulling the fixing lever 7. Then, the parts alignment pallet 2 is removed from the vibration table 4. Then, the empty component alignment pallet 4 is mounted on the vibration table 4 in preparation for the next component alignment, and the process proceeds to the next component alignment work.

Having described the configuration example of the oscillating component aligner 1 and the component alignment operation, an example of the vibration mechanism of the vibration table 4 will be described next. 9 to 11 show the vibration mechanism 21.
An example is shown below. As shown in FIG. 9, two pairs of shaft holders 22a and 22b are fixed to the four corners of the swing table 8, and a pair of slide shafts 23 are mounted between the shaft holders 22a and 22b. FIG. 9 is a cross-sectional view along the line EE in FIG. 10, and the swing table 8 is not shown.

A slide shaft 2 is provided on the bottom of the vibration table 4.
3 is fixed, so that the entire vibrating table 4 reciprocates in the directions of arrows F and G while being guided by the slide shaft 23, and another slide shaft orthogonal to the slide shaft 23. Reciprocating in a direction perpendicular to the arrows F and G while being guided by (not shown). That is, the vibration table 4 can perform eccentric vibration about the motor shaft 25.

On the other hand, a motor M is fixed to the swing table 8, and an eccentric cam 26 is attached to the motor shaft 25 as shown in an enlarged manner in FIG. A rotating ring 28 having a bearing 27 is attached to the outer periphery of the eccentric cam 26, and a connecting member 29 is attached to one end of the outer periphery of the rotating ring 28. A ball joint 30 is provided on the bottom surface of the vibration table 4 in an upright manner.
Is attached to the ball joint 30.

In the vibration mechanism 21 having such a configuration, the eccentric cam 26 rotates when the motor M is rotated, but the eccentric cam 26 rotates with the shaft eccentric because the shaft center is shifted. At this time, the rotating ring 28 itself is
Does not rotate due to the action of, but its position makes a circular motion. Since the motor M is fixed to the swing table 8, the vibration table 4 is moved in the directions orthogonal to the directions of the arrows F and G and the directions of the arrows F and G via the connecting member 29 and the ball joint 30. Reciprocating, the oscillating table 4 eccentrically vibrates while swinging.

The vibration width of the vibration table 4 is 2L, where L is the distance between the center of the eccentric cam 26 and the center of the motor shaft 25. This vibration width can be freely changed. Further, the speed of the vibration can be freely changed by controlling the number of rotations of the motor M.

By the way, as an environmental condition in which this type of oscillating parts aligning machine is installed, various devices such as precision machines are installed around the oscillating parts aligning machine. In addition, the whole swinging part alignment machine vibrates,
If the vibration is propagated to various devices around the automatic machine provided for the assembly line work, there is a risk that the work requiring precision, such as the reading operation of the image processing device, may be hindered. Therefore, preventing the propagation of the vibration may be an indispensable condition in designing the swinging type component aligning machine.

[0015]

Conventionally, some measures against vibrations have been taken into consideration, such as setting the weight of a gantry provided at the lower part of the oscillating type component aligner to be larger than necessary. No anti-vibration measures were taken, and fundamental measures were requested.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and has as its object to provide a vibration mechanism of a component aligning machine capable of effectively preventing the vibration of a vibration table from propagating to the surroundings. To provide.

[0017]

According to one aspect of the present invention, there is provided a motor fixed to a base, an eccentric cam mounted on a rotating shaft of the motor, and
A rotating ring rotatably fitted to the outer periphery of the eccentric cam; and a vibration table coupled to the rotating ring. In the vibration mechanism of the component aligning machine for applying vibration to the vibration table, a balancer for canceling vibration caused by the shaft oscillating motion of the eccentric cam is attached to the rotating shaft.

According to the present invention, the vibration transmitted to the base can be canceled by the simple configuration of mounting the balancer for canceling the vibration to the motor shaft caused by the shaft runout of the eccentric cam on the rotary shaft. Propagation to the surroundings can be effectively prevented.

According to a second aspect of the present invention, in the first aspect, the balancer is provided with a vibration canceling ability adjusting means.

Methods for adjusting the vibration canceling ability of the balancer include, for example, a method of changing the unbalanced mass and a method of changing the radius of the center of gravity. Either one of the unbalanced mass and the radius of the center of gravity may be changed, or both may be changed simultaneously. There is a need to adjust the vibration canceling ability when the amount of shaft runout of the eccentric cam is changed, and the adjustment can minimize the propagation of vibration.

According to a third aspect of the present invention, in the second aspect, as the means for adjusting the vibration canceling ability, an unbalanced mass that can be selectively attached to and detached from the balancer body is provided.

As described above, by making the unbalanced mass body detachable with respect to the main body of the balancer, the vibration canceling ability of the balancer can be adjusted by selecting and mounting the unbalanced mass body. . In this case, since it is only necessary to prepare mass bodies having different masses, the adjustment can be easily performed.

[0023]

Embodiments of the present invention will be described below in detail with reference to the drawings. Hereinafter, an embodiment of a swing type component aligner to which the present invention is applied will be described with reference to FIGS.

FIG. 1 is a sectional view showing the structure of the vibration mechanism of the vibration table, and FIGS. 2 (a) and 2 (b) are views as viewed from the direction of the arrow II in FIG. FIG. 3 is an exploded perspective view of a balancer of the vibration mechanism, FIG. 4 is a plan view of a holder (main body) of the balancer, FIG. 5 is a bottom view showing a bottom configuration of the vibration table and a part of the vibration mechanism, and FIG. It is a side view which shows the structure of a mechanism. In the description of the embodiments, the drawings and reference numerals used in the description of the conventional example are appropriately used.

The configuration of the vibration mechanism 41 in the present embodiment can be broadly divided into a support portion for rotating the vibration table 4 in a horizontal state and a cam mechanism. First, the schematic configuration of the support portion will be described. As shown in FIG. 5, a slide bearing 24 that moves along a slide shaft 23 is provided on the bottom surface of the vibration table 4, and a pair of slide bearings is provided in a direction intersecting the slide shaft 23. A slide shaft 42 is provided, and an end of each slide shaft 42 is fixed to the swing table 8 by fixed stays 43a and 43b. And the slide shaft 23
Are fixed to slide bearings 44a and 44b that move along each slide shaft 42.

According to such a support structure, the vibration table 4 reciprocates in the X direction shown in FIG. 5 by the slide bearing 24 which moves along the slide shaft 23. Although the slide bearings 44a and 44b are configured to move along the slide shaft 42, the vibration table 4
, The vibration table 4 reciprocates in the X direction and reciprocates in the Y direction by the action of the slide shaft 42 and the slide bearings 44a and 44b. As a result, when the vibration table 4 is urged in the X direction and the Y direction by the cam mechanism 51 described later, the vibration table 4 rotates in a biaxial direction on a horizontal plane, but reciprocating motion is included in the biaxial direction. Vibrates in a state.

Next, the structure of the cam mechanism 51 will be described.
1 is provided. The cam mechanism 51 includes a motor M fixed to a swing table (base) 8 as shown in FIG.
A rotating shaft 53 fixed to the motor shaft 52, an eccentric cam 54 provided on the rotating shaft 53, a rotating ring 57 rotatably fitted to the outer periphery of the eccentric cam 54 via a bearing 56,
It is constituted by a balancer 70 attached to the rotating shaft 53 and the like.

As shown in FIG. 2, the eccentric cam 54 comprises an eccentric cam main body 54a formed integrally with the rotating shaft 53 and an eccentric amount adjusting collar 54b fitted on the outer periphery thereof. By adjusting the relative rotational position of the main body 54a, the amount of eccentricity is reduced from the minimum value (zero) shown in FIG.
It can be adjusted within the range of the maximum value shown in FIG. In addition, the collar 5
4b is provided with a lock bolt 54c.

The balancer 70 is for canceling the vibration to the motor shaft caused by the shaft oscillating movement of the eccentric cam 54. As shown in FIG.
1 and the weight attached to and detached from it (unbalanced mass body)
72. The holder 71 has a fitting hole 73 for the rotating shaft 53 and a mounting hole 74 for the weight 72. The fitting hole 73 and the mounting hole 74 are formed at predetermined intervals on both end sides of the holder 71, and on the peripheral wall of the fitting hole 73,
A lock bolt 75 (FIGS. 3 and 4) for locking the holder 71 to the rotating shaft 53 with the fitting hole 73 fitted to the rotating shaft 53.
Are provided only with screw holes), and a lock bolt 76 for locking the weight 72 to the holder 71 with the weight 72 mounted in the mounting hole 74 is provided on the peripheral wall of the mounting hole 74.
(Shown only in the screw holes in FIGS. 3 and 4).

The weight 72 has a body 72a fitted into the mounting hole 74 and a circular head 72b larger than the mounting hole 74. For example, by changing the height H of the circular head 72b, the weight 72 becomes heavy. There are several types with different masses.

According to the cam mechanism 51 thus configured, the eccentric cam 5 is driven by rotating the motor M.
4 rotates around the motor shaft 52. As a result, the rotation ring 57 itself does not rotate, but its position is
, And if the motor shaft 52 rotates clockwise, for example, the entire rotating ring 57 moves clockwise, in other words, rotates. Since the rotating ring 57 is fixed to the vibration table 4, the rotation of the vibration table 4
Is exerted to rotate.

Here, recalling the support structure of the vibration table 4, the vibration table 4 is configured to be able to reciprocate in the X and Y directions by the support portion. Therefore, when the cam mechanism 51 is driven as described above, the vibration table 4
Rotates in the direction of arrow H in FIG.

When vibration is generated by the cam mechanism 51, the balancer 70 is attached to the rotary shaft 53 to cancel the vibration to the motor shaft caused by the shaft oscillating motion of the eccentric cam 54. The vibration transmitted to the table 8 can be canceled, and the vibration can be effectively prevented from being propagated to the surroundings.

When the axial runout of the eccentric cam 54 is changed, the weight 72 of the balancer 70 is adjusted accordingly.
, The propagation of vibration can be suppressed to the utmost. In this case, the adjustment can be easily performed simply by replacing the weight 72, which is the unbalanced mass body, with the holder 71 of the balancer 70.

The swing table 8 is mounted on the swing type component aligner 1 as described with reference to FIG.
In addition, it is swung in the directions of arrows C and D by the action of the swing drive unit 11. At the same time, when the cam mechanism 51 is driven as described above, the vibration table 4 swings in the directions of arrows C and D,
And it vibrates as shown by arrow H in FIG. As a result,
A rotational force is applied to the components to be aligned of the vibration table 4, and the components can be positioned and aligned in the radial direction. Also,
Parts having a high coefficient of friction, such as rubber products, can be efficiently aligned.

It should be noted that the present invention is not limited to the above-described embodiments, and appropriate modifications and improvements can be made. For example, in the above-described embodiment, a plurality of weights 72 having different weights are prepared, and selectively mounted on the holder 71 to adjust the vibration canceling ability of the balancer 70. The radius R of the center of gravity of the balancer 70 shown in FIG.
The same effect can be obtained by changing.

In practice, as shown in FIG. 7, the radius of the center of gravity can be changed by shifting the position of the head 72b with respect to the body 72a. In the case of the weight 72 in (a), the center L of the trunk 72a and the center of gravity G of the head 72b are matched, and the center of gravity radius with respect to the head 72b is R.
1, but the weights 72B, 7B in FIGS.
In the case of 2C, the center of gravity G of the head 72b is eccentric with respect to the center L of the body 72a, and the radius of the center of gravity with respect to the head 72b is R.
2, R3. Therefore, as shown in (d), for example, if the weight 72D in which the head 72b is eccentric with respect to the trunk 72a is created, the radius of the center of gravity can be easily changed.

[0038]

As described above, according to the first aspect of the present invention, the propagation of vibration to the surroundings can be prevented by a simple structure in which the balancer is attached to the rotation shaft of the eccentric cam.

According to the second aspect of the present invention, since means for adjusting the vibration canceling ability of the balancer is provided, effective vibration suppression can be performed even when the amount of shaft runout of the eccentric cam is changed. .

According to the third aspect of the present invention, the vibration canceling ability of the balancer can be adjusted by replacing the unbalanced mass body with the balancer body, so that the adjustment is simple.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a main part of a vibration mechanism according to an embodiment of the present invention.

FIGS. 2A and 2B are diagrams illustrating a case where an eccentric cam is adjusted to a minimum eccentric amount, and FIG. 2B is a diagram illustrating a case where the eccentric cam is adjusted to a maximum eccentric amount.

FIG. 3 is an exploded perspective view of a balancer provided in the vibration mechanism.

FIG. 4 is a plan view of a holder of the balancer.

FIG. 5 is a bottom view showing a supporting structure of a vibration table of the swing type component aligner to which the vibration mechanism of the present invention is applied.

FIG. 6 is a side view illustrating a configuration of a vibration mechanism.

FIGS. 7A to 7C are explanatory views of how to adjust the radius of the center of gravity of the balancer according to another embodiment of the present invention, wherein FIGS. 7A to 7C are side views of weights having different centers of gravity, and FIG. FIG. 4 is a perspective view of the weight seen from below.

FIG. 8 is a side view showing a configuration of a conventional swing type component aligning machine.

FIG. 9 is a bottom view of a vibration table of a conventional vibration mechanism.

FIG. 10 is a side view showing the configuration of the vibration mechanism.

FIG. 11 is an enlarged sectional view showing a configuration of an eccentric cam in the vibration mechanism.

[Explanation of symbols]

4 Vibration Table 8 Swing Table (Base) 41 Vibration Mechanism 54 Eccentric Cam 57 Rotation Ring 53 Rotation Shaft 70 Balancer 71 Holder (Main Body) 72, 72B, 72C, 72D Weight (Unbalanced Mass Body) M Motor

Claims (3)

[Claims] 1. A motor fixed to a base, an eccentric cam mounted on a rotation shaft of the motor, a rotation ring rotatably fitted on an outer periphery of the eccentric cam, and coupled to the rotation ring. A vibration table and a vibration mechanism of a component aligning machine that vibrates the vibration table via the rotation ring by a shaft runout movement of the eccentric cam due to rotation of the rotation shaft, wherein the rotation shaft includes the eccentric cam. A vibration mechanism for a parts aligning machine, characterized by mounting a balancer for canceling vibrations caused by shaft runout motion of the parts. 2. The vibration mechanism for a component aligning machine according to claim 1, wherein the balancer is provided with a means for adjusting a vibration canceling ability. 3. The vibration mechanism of a component aligning machine according to claim 2, wherein an unbalanced mass body selectively detachable from a main body of the balancer is provided as the adjusting means.