JPS5913406B2 - 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 leaf 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 such as the above, the mounting angles of the multiple leaf springs relative to the container and base can be changed, but this requires the preparation of separate mounting blocks and mounting work according to the number of leaf springs. This is extremely 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 tedious.

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 parts transport track, a drive part, a mounting base for the drive part on which the drive part is fixed and is supported so as to be able to vibrate; a plurality of elastic units that are coupled to the first drive mounting base so as to be able to vibrate relative to each other; These vibrating electric motors are arranged at a predetermined distance in the axial direction of the rotating shaft (and at a predetermined distance in a horizontal plane in a direction perpendicular to the rotating shaft (disposed on the drive unit mounting base). Balance weights are fixed to the outer ends of the two rotating shafts so as to be at the same angular position with respect to the rotational direction, and gears having the same number of teeth are fixed to the inner ends of each of the rotating shafts. The gears are in mesh with each other, the plurality of elastic units are arranged around the drive section, each elastic unit is composed of a plate-shaped rubber spring and a rubber spring mounting plate, and the elastic units are configured to shear the rubber spring. In terms of direction, one surface is fixed to the rubber spring mounting plate, and 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 as desired with respect to the drive unit mounting base. This is achieved by a vibrating parts conveying machine, which is fixed to the one drive unit mounting base so as to be rotatably adjustable in the same direction.

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 a vibrating parts conveying machine according to this embodiment, and this parts conveying machine is equipped with a dish-shaped container, that is, a ball 1.

The ball 1 is provided with a helical transport track 2, as clearly shown in FIG.

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 is a rectangular movable plate 6, 7.8°9 (third
(see figure) are fixed by welding or the like at positions corresponding to the four sides of a roughly regular hexagon.

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

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 arranged opposite to such a movable part, and is supported on a foundation by a plurality of vibration isolation springs 30.

A drive unit 11 is fixed to the center of the base 10, which is clearly shown in FIGS. 3 and 4 and consists of a pair of vibrating electric motors M9M2, which will be described in detail later.

Furthermore, rectangular base fixing plates 12 and 13 are provided on the base 10.
．． 14.15 are fixed by welding or the like at positions corresponding to the four sides of the 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 22.

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 are openings for symmetrically arranging the rubber springs 20, 21 with respect to the base fixing plate 12, 13, 14, and 15 as shown in FIG. 23a and 12a.

13a, 14a, and 15a (of which only 13a is shown) are formed.

The opening 23a of the rubber spring mounting plate 23 has a Y rectangular shape as clearly shown in FIG. 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 between these rubber springs 20 and 21 in a crimped state, and the upper and lower iron plates 22a, 22b
are fixed to the iron plates 20b, 21a of the rubber springs 20.21 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 movable plates 6, 7, 8.9 (only 7 is shown in FIG. 5), so that the rubber spring 20.21 is in contact with the movable plates 6, 7, 8.9.
It is separated by a predetermined distance.

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 ends of the connecting member 22 are further inserted into this round hole, and the nut 25 is screwed thereto, so that the connecting member 22 is connected to the movable plates 6, 7,
It is fixed at 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, and 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 above-mentioned base fixing plate 12 * 13° 14.15
The openings 12a, 13a, 14a, and 15a (only 13a is shown) are circular, and their diameter is equal to the diameter of the circle that includes the arcuate side of the opening 23a of the rubber spring mounting plate 23 and the arcuate opening. It is located in the middle of the circle of which 23b and 23c are part.

Rubber spring mounting plate 230 arc-shaped openings 23b, 23
The bolts 26.27 are engaged with the bolts 26.27, respectively, and the bolts 26.27 are connected to the base fixing plates 12, 13, 14.
The elastic unit 16 is fixed to the base fixing plates 12, 13, 14, and 15 by screwing into the screw holes formed in the base fixing plates 12, 13, 14, and 15.

This fixing is carried out in such a way that the longitudinal direction of the rubber spring 20.21, that is, the shear 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.

Loosen the bolts 26 and 27 engaged with the bolts 23c, rotate the rubber spring mounting plate 23 in the desired direction around the bolts 24, and when the desired angle β is obtained, rotate the bolts 24 and 26. 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.

The book 1 drive unit 11 is arranged at the center of the base 10,
The vibration electric motor M19M2 has a mounting leg 32a.

It is fixed to the base 10 via bolts 33a, 32b and 33b.

Unbalanced weights 34a, 34b are fixed to the spaced apart shaft ends of the rotating shafts 35a, 35b of the vibration electric motor M19M2.

The unbalanced weights 34a, 34b have a known shape, and are semicircular in shape, with their centers of gravity G1. , G2 is the rotation axis 3
5a The rotating shafts 3 are arranged so that they are at the same angular position with respect to the rotation direction of the tatami 35b (mutually opposite directions as described later).
5a and 35b.

Gears 36a and 36 having the same number of teeth are provided at adjacent shaft ends of the rotating shafts 35a and 35b of the vibration electric motor M19M2.
b are fixed, and these are intermeshing with each other.

The meshing parts of the gears 36a and 36b are located on the vertical center line A-A of the conveyor as shown in FIG. 4, and their radial direction is on the horizontal axis of the conveyor as shown in FIG. Center line B-
8, the gears 35a, 36b, vibrating electric motors M1-M2, are arranged on the base 10.

The vibration electric motor M19M2 has a terminal box T1. T
2 are provided respectively, and a power supply cable (
(not shown) are led out, and these cables are connected to a power source so that the vibrating motor M19M2 rotates in the opposite 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 vibration motor M19M2, the unbalanced weights 34a and 34b rotate counterclockwise and clockwise as shown in FIGS. 6A to 6D.

This rotation causes their center of gravity G1. Centrifugal force F is generated in G2.

Electric motor M, M20 rotating shaft 35a. SuG, k L+-
jflF IF Vehicle weight '2Ca '2GklffP
Since they are operated synchronously from the beginning, they always rotate while maintaining the same angular position in the direction of rotation.

Figures 6A to 6D show unbalanced weights 34a and 34b.
It shows each rotation phase at 90° intervals during rotation, and in Fig. 6D, the centrifugal force F1 generated at the center of gravity G1 of the unbalanced weight 34a of one vibrating motor M1 is in the -y direction (Fig. 6A). ~ In Fig. 6D, the Y direction is the horizontal direction, that is, the direction parallel to the line B-B, and the X direction is the vertical direction, that is, the direction parallel to the line A-A. Centrifugal force F2 (Fl-F2X or Y direction) generated at the center of gravity G2 of the unbalanced weight 34b.

As is clear from FIG. 3, unbalanced weights 34a and 34b
Since the distance between the centers of gravity G1 and G2 is l in the horizontal plane in the direction perpendicular to the line B-B, this pair of forces F1. F2
As a result, a rotational moment M-Fl (F1=F2=F) is generated, which causes the base 10 and the base fixing plate 12°13.
14 and 15.

Moreover, in the rotation phase of FIG. 6D, the unbalanced weights 34a,
34b centrifugal force F1. Since the X direction component of F2 is 0, the base 10 and the base fixing plate 12, 13.14.1
5, the vertical component of the excitation force is 0.

Furthermore, unbalanced weights 34a and 34b are added from the state shown in FIG. 6D.
are rotated by 90° in opposite directions, resulting in a rotational phase as shown in FIG. 6A.

That is, in this rotational phase, the centrifugal force F1 of the unbalanced weight 34a is in the -X direction, and the centrifugal force F2 of the other unbalanced weight 34b is also in the -X direction.

Therefore, these combined forces F1+F2-2F(Fl-F2
) is the base 10 and base fixing plates 12, 13, 14.1
5 and becomes a vertical excitation force.

Note that in this rotational phase, the centrifugal force F1. The Y-direction component of F2 is O, and the base 10 and base fixing plates 12, 13,
The rotational moment to 14.15 is O.

When the unbalanced weights 34a and 34b are further rotated by 90 degrees in opposite directions from the rotational phase shown in FIG. 6A, the rotational phase shown in FIG. 6B is obtained.

In this phase, the centrifugal force F1 of one unbalanced weight 34a
is in the Y direction, but the centrifugal force F2 of the other unbalanced weight 34b is in the -Y direction.

Therefore, this pair of forces F1. F2 causes a rotational moment) M--Fl in the opposite direction to that in Fig. 6D, which causes the base 10 and the base fixing plate 12°
5.

In this rotation phase, the X-direction component of the centrifugal force F1°F2 of the unbalanced masses 34a and 34b is O, so the vertical excitation force of the base 10 and base fixing plates 12, 13, 14, and 15 is It is O.

9 further in opposite directions from the rotational phase in Fig. 6B.
When rotated by 0°, the unbalanced weights 34a, 34b assume the rotational phase shown in FIG. 6D.

In this rotational phase, the centrifugal force F of one unbalanced weight 34a]
is in the +X direction, and the centrifugal force F of the other unbalanced weight 34b
2 is also in the +X direction, and the Y direction components are each 0.

Therefore, the base 10 and the base fixing plates 12, 13, 14
．． 15, an upward vertical excitation force 2F is transmitted.

When the unbalanced weights 34a and 34b are further rotated by 90 degrees in the opposite direction from the rotational phase shown in FIG. 6C, the unbalanced weights 34a and 34b assume the rotational phase shown in FIG. 6D.

Thus, the unbalanced weights 34a, 34b rotate once, and the above-mentioned state is repeated.

From the above explanation, it is clear that the vibration electric motor M1. By M20 rotation,
It will be understood that a vibratory rotational moment in the horizontal plane and a vibratory force in the vertical direction are generated from the drive unit 11, and the temporal changes in the vibratory rotational moment (M) and the vertical vibratory force V will be further considered.

Now, the unbalanced weight 3 after L seconds from the rotational phase shown in Fig. 6D.
Considering the angular positions of 4a and 34b, it becomes as shown in FIG.
The Y-direction component of the centrifugal force F1 of the other unbalanced weight 34b is F1y--Flco^t, and the Y-direction component of the centrifugal force F2 of the other unbalanced weight 34b is F2y-F2Co8GJt.

(Here, ω is the rotating shaft 35a of the vibration electric motor M11M20.

35b).

Also, the X direction components are F and X needle 1sirYJ)
and F2X--F2s i rKI)t.

Therefore, the pair of Y-direction components F1y and F2V described above yield a rotational moment of M = 1F cosot7z, and the combination of the X-direction components F1X and F2x yields a vertical vibration force V of V=F1x+F2x=-2Fsitmt based on the base 10. , the base fixed plates 12, 13, 14゜15, the elastic unit 16 and the movable plates 6, 7, 8゜9. The angle β of the shearing direction with respect to the horizontal direction is sufficiently smaller than 90 degrees, and the vertical vibration force V is transmitted to the ball 1 through the spring constant of the magum spring 20, 21 in the compression direction.

Since the spring constant of the rubber springs 20 and 21 in the compression direction is very large, the entire conveying machine receives this vibration force V as a unit.

The spring constant of the vibration isolating spring 30 that supports the entire carrier is sufficiently small and can be ignored, so if the mass of the entire carrier is m, then the vertical F of the entire carrier Become.

Therefore, the ball 1 also vibrates with an amplitude X in the vertical direction.

On the other hand, the vibration rotational moment M, that is, the torsional vibration force M
is transmitted to the movable plates 6.7, 8.9, that is, the ball 1, via the base 10, the base fixed plates 12.13° 14.15, and the elastic unit 16. Next, this torsional vibration force M causes the ball to The reason why 1 vibrates in an ellipse will be approximately analyzed with reference to FIG.

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 shear direction P of the rubber springs 20 and 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=Mcosβ, and the component in the compression direction −Msinβ.

Now, the moment of inertia of the movable parts including the ball 1, the movable plates 6, 7, 8.9, etc. about an axis passing through the center of gravity of the movable parts and parallel to the direction Q is I(11, the base 10, the drive part 11, etc.) IC12 is the moment of inertia of the fixed part around an axis that passes through the center of gravity of the fixed part and is parallel to direction Q, Ipl is the moment of inertia of the movable part around an axis that passes through the center of gravity of the movable part and is parallel to direction P. If the moment of inertia of the fixed part around the axis passing through the center of gravity and parallel to direction P is Ip2, the torsional spring constant in the rubber spring 20°210 shear direction is Kp, and the torsional spring constant in the compression direction is Kq, then The equation of motion is established as follows.

Ip1'o'1-Kq(θ2fJ1)=0 ・-""(
1) Engineering p2'0°, 2 +Kq (θ2-01) -M
sinβ・・・・・・(2) Iq word, −Kp(α2−α
1)=0・・・・・・・・・・・・(3)Iq1'cc
2+Kp(a2-α1)-Mcosβ...smell)
Here, 01 is the rotation angle of the movable part around an axis that passes through the center of gravity of the movable part and is parallel to direction P, θ2 is the rotation angle of the fixed part around an axis that passes through the center of gravity of the fixed part and is parallel to direction P, and α1 is The rotation angle of the movable part around an axis passing through the center of gravity of the movable part and parallel to the direction Q, 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 the 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.

Here, R represents the distance from the axis passing through the center of gravity of the movable part and parallel to the direction Q to the point S, and R' represents the distance from the axis passing through the center of gravity of the movable part and parallel to the direction P to the point S.

From the above equation (5X6), it can be seen that due to the torsional vibration force M, the container Q
1(■q1+Iq2) (1) Point S on the top performs linear vibration with a slope of Recognize.

On the other hand, as mentioned above, the ball 1 is subjected to 6 vibrations in the vertical direction 0, --; ys i rut by the vertical vibration F.
Vibration with a phase difference of 0 degrees is added, and as a result, the ball 1 vibrates in an ellipse.

That is, the amplitude of the linear vibration with the gradient Qt mentioned above is D
1, then this linear vibration U = D cos ωL, and the vibration component due to the vibration force V perpendicular to this is V = E sin
It is expressed as ωL.

Note that the vibration component due to the vibration force V in the direction parallel to the linear vibration]) COSωL is ignored because the shear direction β of the rubber spring 20.21 is sufficiently smaller than 90 degrees.

By performing calculations to eliminate ωL from the above, the following relational expression can be obtained.

2v2 −−1− − = 1 2E2 This is the equation of an ellipse.

Therefore ball 1 on 1 The point S is a straight line with a slope of - and 1 perpendicular to it. Elliptical vibration with a major axis and a minor axis in the direction is performed.

However, on the other hand, in the equations of motion (1) to (4), the viscosity coefficient of the rubber spring 20. Since the carrier is driven at close angular frequencies, a phase difference of approximately 90° is actually generated between the above-mentioned θ1 and α1, as is clear from vibration engineering.

Therefore, when expressed as θ1-A5inωL, α1=Bc
1, which can be expressed as osωL (where A and B are each Ip
ll Ip21 I(lx tI+121ω, a constant determined by the viscosity coefficient of the rubber spring 20.21, etc.).

Therefore, in this case Pl and Ql are each P
1 = RBcosωt, Ql-R'ASinωt, and by calculating to eliminate ωL from these, the following relational expression can be obtained.

p2 Q Ki □＋□＝ (RB)2 (R’A)2 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 g resonance, (λ': l: 1) RB>R'A tear, so the long axis is in the P direction. It can be seen that elliptical vibration occurs.

Note that when the carrier is driven at an angular frequency very close to the natural vibration angular frequency in the shear direction of the rubber springs 20, 21, the vibration component due to the vertical vibration force V may be ignored.

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 vibration component due to the vertical vibration force V also changes. relatively large,
The direction of the major axis of the elliptical vibration changes depending on these factors, but one of the experimental results is that when λ'-=0.9, β=
300, the inclination angle γ of the long axis of the elliptical vibration of the ball 1 with respect to the horizontal direction was about 20 mo.

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 applies to 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, as shown in FIG. 9, the elastic unit 16 may be rotated counterclockwise by an angle 2β and fixed at this position.

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 directly to the drive unit 11 of k, 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 actual embodiment of the present invention, even if the winding direction of the ball transport track changes, the 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 even when changing the part or material and setting new optimal conditions, the mounting angle β of the elastic unit 16 can be easily adjusted. It can be changed.

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 above embodiment, two rubber springs 20 and 21 are used in the elastic unit 16, but the invention is not limited to this, and a plurality of rubber springs may be installed above and below the connecting member 22. 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.

Further, in the above actual case, 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 by a vibration isolating spring on a part of the building.

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 explanation of drawings]

Fig. 1 is a plan view of a vibrating parts conveying machine according to an actual case of the present invention, Fig. 2 is a side view of the same conveying machine, Fig. 3 is a plan view of the same conveying machine excluding the balls, and Fig. 4 is a plan view of the same conveying machine. FIG. 5 is a cross-sectional side view taken along the V-V direction in FIG. 3, and FIGS. 6A and 6D explain each angular position of the unbalanced weight and the action of the conveyor. FIG. 7 is a front view for explaining the action of the unbalanced weight, FIG. 8 is a partial side view for explaining the action of the conveyor, and FIG. Figure 9 is a partial side view for explaining the action of the same conveyor with the elastic unit installed at a different angle, and Figure 10 is a plan view of the ball in which the winding direction of the conveyor track is opposite to that in Figure 1. be. In addition, in the figure, 1, 1'... ball, 10...
base, 11... drive unit, 16... elastic unit),
20° 21...Rubber spring, 23...Rubber spring mounting plate, 34a, 34b-Unbalanced weight, 36a. 36b...Gear, Ml, M2...Vibration electric motor.

Claims (1)

[Claims] 1. A container equipped with a spiral parts 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 drive section mounting base relative to each other. and a plurality of elastic units vibrably coupled to the drive unit, the drive unit comprising a pair of vibrating electric motors that rotate in opposite directions and generate centrifugal force in a vertical plane, and the driving unit comprises a pair of vibrating electric motors that rotate in opposite directions and generate centrifugal force in a vertical plane. The unbalanced weights of these vibrating motors are arranged on the drive unit mounting base at a predetermined distance apart (and at a predetermined distance in a direction perpendicular to the rotational axis in a horizontal plane), and the unbalanced weights of these vibration motors are The gears are fixed to the outer ends of the two rotating shafts so as to be at the same angular position, and the gears having the same number of teeth are fixed to the inner ends of each of the rotating shafts, and these gears mesh with each other. , the plurality of elastic units are arranged around the driving part, each of the elastic units is composed of a plate-shaped rubber spring and a rubber spring mounting plate, and one of the plurality of elastic units is arranged around the rubber spring mounting plate with respect to the shearing direction of the rubber spring. the other side is fixed to the container, and the rubber spring mounting plate is attached to the drive unit mounting base so that the shearing direction of the rubber spring is in a desired direction with respect to the drive unit mounting base. A vibrating parts conveying machine characterized by being fixed in a rotationally adjustable manner.