JPS591645B2 - Vibrating parts conveyor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vibrating parts conveying machine, and more particularly to a vibrating parts conveying machine whose vibration direction is variable.

Generally, vibrating parts conveyors are also called parts feeders, and those having various structures are known.

For example, in an electromagnet-driven parts feeder, a dish-shaped container with a spiral track inside and a base supported by an anti-vibration spring are arranged in a plurality of parts inclined at a predetermined angle and arranged at equal angular intervals. They are coupled by a leaf spring so that they can relatively vibrate torsionally, and when a half-wave rectified alternating current is applied to the coil of the electromagnet, the container torsionally vibrates in a direction perpendicular to the longitudinal direction of the leaf spring.

The direction of this torsional vibration is relative to the parts and materials to be transported.
Alternatively, the plate springs are arranged at an angle to optimize the required action, but if the components, materials, or required action change, the direction of torsional vibration of the container may be optimized. You may have to change this.

In cases like the above, the mounting angles of multiple leaf springs relative to the container and base can be changed, but this requires the preparation of separate mounting blocks and the installation work according to the number of leaf springs, which is extremely time consuming. It is troublesome and has poor work efficiency.

In addition, as a parts feeder of another structural type, two vibrating electric motors are mounted on a container (often configured as a spiral elevator) supported on a foundation by vibration isolating springs and tilted at a predetermined angle in opposite directions. In this case, in order to change the direction of torsional vibration of the container, the mounting bolts of the two vibrating motors to the container must be loosened to obtain the desired torsional vibration angle. I have to adjust the slope.

However, vibrating electric motors are generally very heavy, and this inclination adjustment is very troublesome.

The present invention has been made in view of the above-mentioned points, and an object of the present invention is to provide a completely new parts conveying machine that can easily change the vibration angle of a container.

This object is achieved according to the invention by providing a container with a helical component transport track, a drive, a drive mounting base on which the drive is fixed and is supported in a vibrating manner, the container and the drive. A plurality of elastic units are coupled to a mounting base of one drive unit so as to be able to vibrate relatively. The unbalanced weights of the vibration electric motor are fixed to the rotating shafts so as to be at angular positions different from each other by 180 degrees with respect to the rotation direction, and gears having the same number of teeth are fixed to one shaft end of each of the rotating shafts. , these gears are respectively meshed with a pair of gears having an equal number of teeth fixed to a rotatably supported connecting shaft, and the plurality of elastic units are arranged around the drive section, and each of the elastic units is arranged around the drive section. It consists of a plate-shaped rubber spring and a rubber spring mounting plate, one surface of the rubber spring in the shearing direction is fixed to the rubber spring mounting plate,
The other surface is fixed to the container, and the rubber spring mounting plate is rotatably fixed to the base so that the shearing direction of the rubber spring is in a desired direction with respect to the base. This is achieved by a vibrating parts conveyor, which

Hereinafter, details of the present invention will be explained based on illustrated embodiments.

1 and 2 are a plan view and a side view of the vibrating parts conveyor according to this embodiment. As clearly shown in FIG. 1, a helical transport track 2 is provided.

This is a known structure, in which the parts or materials fed into the center of the ball 1 are gradually raised while being transferred clockwise in the figure on the transfer track 2 while being subjected to known torsional vibrations. is supplied to the next process.

The ball 1 as described above is fixed to the circular bottom plate 4 by welding or by a nut 5 as shown in FIG.

On the bottom of the bottom plate 4 are rectangular movable plates 6, 7, 8°9 (third
(see figure) are fixed by welding or the like at positions corresponding to the four sides of the y-regular hexagon.

The movable plates 6, 7 and 8, 9 each form a pair and are fixed by welding W'.

These movable plates 6, 7, 8.9, balls 1, and bottom plate 4 constitute a movable part of the present vibrating parts conveyor.

A circular base 10 is disposed opposite to such a movable part, and is supported on a foundation supported by a plurality of vibration isolation springs 30.

A drive section 11, which is clearly shown in FIGS. 3 and 4 and also includes a pair of vibrating electric motors M1 and M2, which will be described in detail later, is fixed to the center of the base 10.

Furthermore, rectangular base fixing plates 12 and 13 are provided on the base 10.
, 14 and 15 are fixed by welding or the like at positions corresponding to the four sides of the y-regular hexagon.

This hexagonal shape is concentric with the hexagonal shape for the movable plates 6, 7° 8.9 described above, and therefore the base fixed plates 12, 13,
14, 15 are arranged parallel to the movable plates 6°, 7, 8, and 9, respectively.

The base fixing plates 12.13 and 14.15 each form a pair, and are fixed by welding W at the vertical sides that abut each other.

An elastic unit 16 is fixed to each base fixing plate 12, 13, 14.15.

Each elastic unit 16 mainly consists of a pair of rubber springs 2
0, 21 (see Figure 5), these rubber springs 20.
21, and a circular rubber spring mounting plate 23.

Rubber spring 20.21 is rectangular rubber 20c
.

21c, and rectangular iron plates 20a, 21a, 20b, 21b fixed by vulcanization on the upper and lower surfaces thereof.The connecting member 22, which is clamped and fixed by rubber springs 20.21, is a pair of upper and lower iron plates 22a, 22b. It also consists of a rectangular parallelepiped connecting block 22c fixed by welding to the center position between these iron plates 22a and 22b.

Center part of rubber spring mounting plate 23 and base fixing plate 1
2, 13, 14, and 15 have openings in the center for symmetrically arranging the rubber springs 20, 21 with respect to the base fixing plates 12, 13, 14, and 15, as clearly shown in FIG. 23a, 12a, 13a, 14a, and 15a (of which only 13a is shown) are formed.

As clearly shown in FIG. 2, the opening 23a of the rubber spring mounting plate 23 has a rectangular shape, but its short sides are arcuate and its long sides are straight. Mounting plate 28 for attaching rubber springs 20 and 21 to
．． 29 is fixed by welding.

The iron plates 20a and 21b of the rubber springs 20 and 21 are fixed to these mounting plates 28 and 29 with bolts as shown in the figure, and the connecting member 22 is inserted in a crimped state between these rubber springs 20 and 21, and the upper and lower iron plates 22a, 22b is fixed to the steel plates 20b and 21a of the rubber springs 20 and 21 with bolts as shown.

A connecting block 22c fixed to the center of the connecting member 22
A through hole as shown in FIG. 5 is formed in the through hole, into which the bolt 24 is inserted.

The connecting block 22c is in contact with the movable plates 6, 7, 8.9 (only 7 is shown in FIG. 5), so that the rubber spring 20.21 is spaced a predetermined distance from the movable plates 6, 7, 8.9. Can be used.

The movable plates 6, 7, 8.9 that come into contact with the connecting block 22c have round holes that align with the through holes of the connecting block 22c, and the bolts 24 inserted into the connecting block 22c.
The connecting member 22 is connected to the movable plates 6 and 7 by further inserting the end portion into this round hole and screwing the nut 25 thereto.
, 8.9.

Although the above-mentioned base 10, drive section 11, and rubber spring mounting plate 23 constitute the fixed section of the vibrating component conveyor, the main section is fixed by fixing the connecting member 22 to the movable plates 6, 7, 8.9. A relatively vibratory connection between the movable part and the fixed part of the vibrating parts transport machine is provided.

The rubber spring mounting plate 23 is further formed with a pair of arc-shaped openings 23b and 23c facing each other around the through hole of the connecting block 22c of the connecting member 22.

In addition, the openings 12a, 13a, 14a, 15a of the base fixing plate 12, 13° 14.15 described above.

(only 13a is shown) is circular, and its diameter is the diameter of the circle that includes the arcuate side of the opening 23a of the rubber spring mounting plate 23 and the circle that includes the arcuate openings 23b and 23c. It is located midway between the diameter of

Rubber spring mounting plate 230 arc-shaped opening 23b, 2
3c are respectively engaged with bolts 26.27, and these bolts 26.27 are attached to the base fixing plates 12.13, 14.1.
The elastic unit 16 is fixed to the base fixing plates 12, 13, 14, 15 by screwing into the screw holes formed in the elastic unit 5.

This fixing is carried out in such a way that the longitudinal direction of the rubber spring 20.21, that is, the shearing direction, is inclined by a certain angle β with respect to the horizontal direction H, as clearly shown in FIG.

That is, in the adjustment work for such fixing, the bolt 24 and the arcuate opening 23b inserted through the connecting member 22.

23c, and rotate the rubber spring mounting plate 23 in the desired direction around the bolt 24 to obtain the above-mentioned desired angle β. Tighten the .27.

Next, details of the drive section 11 of the present vibrating parts conveyor will be explained with reference to FIGS. 3 and 4.

In the drive unit 11, a pair of vibration motor mounting plates 32a
, 32b are connected at a predetermined distance by a connecting pipe 33, and each is fixed perpendicularly to the base 10 by welding or the like.

Vibration electric motors M1 and M2 having a known structure are fixed to the mounting plates 32a and 32b via poles K.

Further, bearing housings 34a, 34b are fixed to the mounting plates 32a, 32b at their upper ends via angle members 40a, 40b, and a connecting shaft 35 is rotatably supported by the bearing housings 34a, 34b. ing.

Bevel gears 36a and 36b having the same number of teeth are fixed to both ends of the connecting shaft 350.

A pair of unbalanced weights 38a, 38b are fixed to both shaft ends of the rotating shafts 37a, 37b of the vibrating electric motors M1, M2.

The unbalanced weights 38a and 38b have a known shape, and are y
It has a semicircular shape, and its centers of gravity G1 and G2 are the rotation axis 3.
7a and 37b are fixed to the rotating shafts 37a and 37b so as to be at angular positions separated by 180 degrees from each other in the rotational direction.

The rotating shafts 37a, 37b rotate in the same direction as shown by the arrows in FIG. 3, and for example, the unbalanced weights 38a, 38b are connected to the rotating shaft 37a in the angular positional relationship shown in FIG.

37b.

Bevel gears 39a and 39b having the same number of teeth are further fixed to the upper shaft ends of the rotating shafts 37a and 37b, and a bevel gear 36a is fixed to both ends of the connecting shaft 350.
, 36b.

The bevel gears 39a, 39b and 36a, 36b have the same number of teeth.

Vibration electric motors M1 and M2 are equipped with terminal boxes T1 and T.
2 are provided respectively, and the power supply cable (
(not shown) are led out, and these cables are connected to a power source 5 so that the vibrating motors M1, M2 rotate in the same direction.

The parts conveyor according to the embodiment of the present invention is constructed as described above, and its operation will be explained next.

When a power source is connected to the vibrating motors M1 and M2, the unbalanced weights 38a and 38b rotate counterclockwise as shown in FIG.

This rotation generates centrifugal force F at their centers of gravity G1 and G2.

The unbalanced weights 38a and 38b each consist of a pair of upper and lower unbalanced weights of the same shape.1. Since they have the same shape and the same mass, centrifugal force F of the same magnitude is generated.

In this N, the centrifugal force F is the resultant force of the centrifugal force generated in each of the pair of upper and lower unbalanced weights.

Since the rotating shafts 37a and 37b of the electric motors Ml and M2 are forcibly operated in synchronization with each other by bevel gears 36a, 36b, 39a and 39b, regarding the rotation direction,
Rotate while maintaining a 180° phase difference.

FIG. 7 shows each rotational phase of the unbalanced masses 38a and 38b at 90° intervals until they make one rotation from the angular position shown in FIG. 3, and FIG. ,
Since the centrifugal forces F1 and F2 (F1=F2=F) generated at the centers of gravity G1 and G2 of the unbalanced weights 38a and 38b are in opposite directions in the Y direction, the resultant force in this direction is zero.

Also, since the component in each direction is 0, the mounting base 1
The translational motion component relative to 0 is 0 in both the X direction and the Y direction.

However, since the unbalanced weights 38a and 38b are fixed to the rotating shafts 37a and 37b of the vibration electric motors M1 and M2, respectively, at a predetermined distance l in the X direction, the base 1
0 is given a rotational moment of M=Fl.

That is, in the rotation phase shown in FIG. 7A, a clockwise rotational force is applied to the base 10.

When rotated 90 degrees from the angular position shown in Figure 7A, the unbalanced weight 3
8a and 38b assume the angular positions shown in FIG. 7B.

In this rotation phase, the unbalanced weight 38a. Centrifugal force F of 38b
1 and F2 are in opposite directions in the X direction, so the resultant force in this direction is O.

Also, in the Y direction, each component is O, so the mounting base 1
The translational motion component relative to 0 is 0 in both the X direction and the Y direction.

In this case, the rotational moment is M-0.

When the unbalanced masses 38a, 38b are then rotated 90 degrees from the angular position shown in FIG. 7B, they assume the angular position shown in FIG. 7C.

In this rotation phase, the unbalanced weight 38a. Centrifugal force F of 38b
1 and F2 are in opposite directions in the Y direction, so the resultant force in this direction is 0.

Also, in the X direction, each component is O, so the mounting base 1
The translational motion component with respect to 0 is O in both the X direction and the Y direction.

However, a rotational moment of M=-Fl is applied to the base 10.

That is, a rotational force in a direction opposite to the rotational phase shown in FIG. 7A is applied to the base 10.

When the unbalanced masses 38a, 38b are then rotated 90 degrees from the angular position shown in FIG. 7C, they assume the angular position shown in FIG. 7D.

In this rotation phase, the unbalanced weight 38a. Centrifugal force F of 38b
1 and F2 are in opposite directions in the X direction, so the resultant force in this direction is O.

Also, in the Y direction, each component is O, so the mounting base 1
The translational motion component relative to 0 is 0 in both the X direction and the Y direction.

In this case, the tail is a rotational moment) M=O.

Next, when the unbalanced weights 38a and 38b are rotated by 90 degrees, the rotation phase becomes as shown in FIG. 7A, and the unbalanced weights 38a and 38b make one rotation each time.

From the above explanation, it will be understood that the torsional vibration force is applied to the base 10 by the first drive unit 11, but this can be further explained in general as follows.

That is, the centrifugal forces F1 and F2 of the centers of gravity G1 and G2 of the unbalanced weights 38a and 38b after t seconds from the rotational phase in FIG. 7A
X direction component FIX, F2X and Y direction component FIY
F2Y is FIX=F154. ωt (ω is the angular velocity of the rotating shafts 37a and 37b), F2X = F 2
Si nωt, FIY knee F1CO8ωt, F2y=
=:F2CO3ωt.

Therefore, the resultant force of the X direction component F1x-t F2X=FI
Sinωt-F251nω1=0, and the resultant force of the Y-direction component F 1y+F2Y=-F ICO5ωt+F2C
O3ωt=0.

Also, rotational moment) M= F'1- y X 4 (
4 is the rotation axis 37 from the center O between the rotation axes 37a and 37b.
a.

37b) - F2Yx length = FlCO5ωt (F
1=F2=F).

As is clear from the above, 1. No translational force is applied to the base 10 by the drive unit 11, and M--Fl
Only the torsional vibration force of CO8ωt is applied.

This torsional vibration force M is applied to the base 10, the base fixing plate 12,
13, 14.15 and the elastic unit 16 to the movable plates 6, 7, 8.9, that is, the ball 1.Next, we will explain why the ball 1 vibrates in an ellipse due to this torsional vibration force M. Approximate analysis will be performed with reference to Figure 6.

A torsional vibration force M is applied to the rubber spring mounting plate 23 of each elastic unit 16 in the horizontal direction H, but this is now applied to the shearing direction P of the rubber springs 20° 21 and the direction perpendicular to this, that is, the compression direction Q. When divided into components in the shear direction P, the component Mp=MCO5β, and the component in the compression direction MQ=MSinβ.

Now, the moment of inertia of the movable parts around the axis parallel to the direction Q passing through the center of gravity of the movable parts including the ball 1, the movable plates 6, 7, 8, 9, etc.) Iq, including the base 10, the drive part 11, etc. The moment of inertia of the fixed part around the axis passing through the center of gravity of the fixed part and parallel to the direction Q is Iq, and the moment of inertia of the moving part around the axis passing through the center of gravity of the moving part and parallel to the direction P.
pl, the moment of inertia of the fixed part around the axis passing through the center of gravity of the fixed part and parallel to the direction P is Ip2, the torsional spring constant of the rubber spring 20゜21 in the shear direction is Kp, and the screw spring constant in the compression direction is Kq, the following operating equation holds true.

Ip1°σ, -Kp(θ2-θ1)=0...
・・・・・・・・・(1) Ip2°θ'2+Kp(θ2
−θ1 ) = Mcos β (2) I
(11'(!1 K(1(α2-α1)-〇...
・・・・・・・・・・・・ (3) ■q1'cj2 +
Kq(αz −a□) =MSinβ・・・・・・・・・
- In (4) and N, θ1 is the rotation angle of the movable part around the axis that passes through the center of gravity of the movable part and is parallel to direction P, and θ2 is the rotation angle of the fixed part around the axis that passes through the center of gravity of the fixed part and is parallel to direction P. Rotation angle, α1
α2 represents the rotation angle of the movable part around an axis passing through the center of gravity of the movable part and parallel to direction Q, and α2 represents the rotation angle of the fixed part around an axis passing through the center of gravity of the fixed part and parallel to direction Q.

Note that the spring constant of the vibration isolation spring 30 that supports the base 10 on the foundation is ignored because it is sufficiently smaller than the spring constant of the rubber springs 20 and 21.

By solving the above equations (1) to (4), the amplitudes P1 and Ql in the P direction and Q direction at one point S on the outer peripheral surface of the ball 1 are obtained as follows.

In this tile, R represents the distance from the axis passing through the center of gravity of the movable part and parallel to direction Q to point S, and Bi represents the distance from the axis passing through the center of gravity of the movable part and parallel to direction P to point S.

From the above equation (5X6), point S on container ■ is in direction P and Q
1(Ip1+Ip2)(1-λ'2) It can be seen that linear vibration with a Pl(Iq1+Iq2X1-λ2)sinβ-R gradient of 12□ is performed with respect to CO5β·bi.

However, in the equations of motion (1) to (4), the viscosity coefficient of the rubber spring 20.21 is ignored, and in reality it is very close to the natural vibration angular frequency in the P direction, that is, the shear direction of the rubber spring 30.31. In order to drive the carrier at an angular frequency, a phase difference of approximately 90° is actually generated between the above-mentioned θ2 and α1, as is clear from vibration engineering.

Therefore, when expressed as θ1=ASinωt, α1−βC
It can be expressed as OSωt.

Here, A and B are respectively Ip], Ip2, Iql,
It is a constant determined by Iq2, ω, the viscosity coefficient of the rubber spring 20.21, etc.

Therefore, in this case Pl and Ql are respectively P,:
RBCO5ωt, Ql-bia ASinωt, and by calculating to eliminate ωt from these, the following relational expression is obtained.

This is the equation of an ellipse.

In this equation, since the vibration angular frequency of the rubber spring 20.21 in the shear direction is driven by y resonance, (λ'21)RB>R'A, and therefore the long axis is in the P direction. It can be seen that elliptical vibration occurs.

At the resonance point in the shear direction, the above-mentioned elliptical vibration occurs, but as the drive frequency deviates from the resonance point, the phase difference between α1 and θ1 deviates from 90°, and the long axis of the elliptical vibration changes accordingly. However, one of the experimental results is that when λ' is 0.9, the inclination angle γ of the long axis of the elliptical vibration of ball 1 with respect to the horizontal direction is approximately 20° for β = 300. Met.

Under the elliptical vibrations described above, the parts or materials are transferred clockwise on the transfer track 2 within the ball 1, and are discharged from the track end 3 and guided to the next process.

Although FIG. 1 shows a ball 1 with a clockwise winding transport track 2, the same is true for a ball 1' with a counterclockwise winding transport track 51 as shown in FIG. The drive unit 11 is applied as is.

That is, in this case, the elastic unit 16 may be rotated counterclockwise by an angle of 2β and fixed at this position, as shown in FIG.

This angle adjustment work can be carried out extremely easily since it is only necessary to loosen the bolts 24, 26 and 27 and rotate the entire elastic unit 16 around it while being supported by the bolt 24.

There is no need to replace with a dedicated mounting block or move a heavy drive unit as in the past.

After the adjustment work, if power is supplied to the drive unit 11 as it is, the ball 1 will vibrate in an elliptical direction with its long axis at an inclination angle of γ in the opposite direction to the horizontal direction as shown in FIG. The material is transported counterclockwise on track 51 at the same transport speed as in FIG.

As described above, according to the embodiment of the present invention, even if the winding direction of the ball transport track changes, adjustment work can be performed very easily.

In the above, the case where a constant transfer speed is obtained for the same part or material has been explained, but if the part or material is changed and the optimum conditions are newly found and the escape is made, the mounting angle β of the elastic unit 16 can be easily changed. be able to.

Although the embodiments of the present invention have been described above, the present invention is of course not limited thereto, and various modifications can be made based on the technical idea of the present invention.

For example, in the nest embodiment described above, two rubber springs 20 and 21 are used in the elastic unit 16, but the invention is not limited to this. You can also do this.

It is also possible to configure the elastic unit using only one rubber spring.

In this case, for example, the upper iron plate of the rubber spring may be fixed to the base fixed plate, and the lower iron plate may be fixed to the movable plate.

Moreover, in the above embodiment, the bevel gear 36a.

Although the numbers of teeth of 36b, 39a, and 39b are the same, the number of teeth is not limited to this.

Bevel gear 39a fixed to rotating shafts 37a and 37b
, 39b and the bevel gears 36a, 36b fixed to the connecting shaft 35 only need to have the same number of teeth.

Further, in the above embodiment, the base 10 is supported on the foundation by the vibration isolating spring 30, but instead of this, the base 10 may be suspended and supported on a part of the building by the vibration isolating spring.

As described above, the vibration angle of the vibrating parts conveyor according to the present invention can be changed very easily, and even if the winding direction of the ball transfer track changes, this can be dealt with very easily. play.

[Brief Description of the Drawings] Fig. 1 is a plan view of a vibrating parts conveying machine according to an embodiment of the present invention, Fig. 2 is a side view of the same conveying machine, and Fig. 3 is a plan view of the same conveying machine excluding the balls. , FIG. 4 shows the same transport machine. A side view of the drive unit, FIG. 5 is a cross-sectional side view in the V-■ direction in FIG. Fig. 7E is a plan view of the unbalanced weight in the drive section to explain the action of the same conveyor, and Fig. 8 is a partial side view of the same transporter with different mounting angles of the elastic unit. 9 and 9 are plan views of the ball in which the winding direction of the transport track is opposite to that of FIG. 1. In addition, in the figure, 1, 1'... ball, 10
... Base, 11 ... Drive section, 16.
...Elastic unit, 20.21...Rubber spring, 23...Rubber spring mounting plate,
35...Connection shaft, 36a, 36b,
39a, :39b...Bevel gear, 38a
, 38b... Unbalanced weight, Ml, M2...
...Vibration electric motor.

Claims (1)

[Claims] 1. A container equipped with a spiral component transfer track, a drive section, a drive section mounting base on which the drive section is fixed and supported so as to be able to vibrate, and the container and the front drive section mounting base are relatively connected to each other. and a plurality of elastic units vibrably coupled to the drive unit, and the drive unit includes a pair of vibrating electric motors that rotate in the same direction and generate centrifugal force in the horizontal direction, and the unbalanced weight of these vibrating electric motors rotates in the direction of rotation. 180° to each other
Gears having an equal number of teeth are fixed to one shaft end of each rotating shaft at different angular positions, and these gears have teeth fixed to a rotatably supported connecting shaft. The plurality of elastic units are arranged around the driving section, and each elastic unit is composed of a plate-shaped rubber spring and a rubber spring mounting plate. Regarding the shearing direction of the rubber spring, one surface is fixed to the rubber spring mounting plate, the other surface is fixed to the container, and the rubber spring mounting plate is fixed so that the shearing direction of the rubber spring is fixed to the drive unit mounting base. 1. A vibrating parts conveying machine, wherein the vibrating parts conveying machine is rotatably fixed to the drive unit mounting base so as to be oriented in a desired direction.