JPS5915850B2 - vibrating conveyor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vibrating conveyor, and particularly to a vibrating conveyor in which the vibration angle of a vibrated part is variable.

Generally, in a vibrating conveyor, a vibrating force in an oblique direction is applied to the trough as a vibrated part with respect to the material transfer surface, and the material is transferred. Regardless of the form of the source,
The trough is connected to the base or countermass by diagonally arranged leaf or coil springs.

The angle of inclination of this spring is determined based on the material or parts to be transferred.
or determined to obtain the optimum vibration direction for the desired action (e.g. drying or cooling the material during transport), but if the material, component or desired action changes. In some cases, it may be necessary to change the angle of inclination of the spring to optimize the direction of vibration.

In the above cases, the mounting angle of multiple leaf springs or coil springs with respect to the foundation or opposing mass and trough can be changed, but for this purpose, it is necessary to prepare another mounting block or to perform mounting work according to the number of springs. required and extremely troublesome;
Work efficiency is also poor.

Furthermore, depending on the vibration source, it is necessary to change the mounting angle of the spring with respect to the trough or the opposing mass, and since these vibration sources are generally very heavy, the work is very cumbersome.

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 vibrating conveyor that can easily change the vibration angle of the vibrated part.

According to the present invention, this object is achieved by an excitation mechanism having an excitation part extending in a predetermined direction and an unbalanced weight fixed to a pair of rotating shafts that are rotated at the same speed in opposite directions by a gear mechanism. , comprising a base part that fixes the vibration excitation mechanism and is supported so that it can vibrate, and an elastic unit that connects the base part and the vibrated part so that they can vibrate relatively, and the balanced weight is When the rotating shaft rotates, the vertical components of the vibrated parts with respect to the predetermined direction cancel each other out, and the elastic unit is fixed to the rotating shaft. and a rubber spring mounting plate, one surface of the rubber spring in the shearing direction is fixed to the rubber spring mounting plate, and the other surface is fixed to the vibrated part, and the rubber spring is mounted. This is achieved by a vibrating conveyor, characterized in that the plate is rotatably fixed to the base part so that the shearing direction of the rubber spring is in a desired direction with respect to the predetermined direction of the vibrated part. Ru.

Hereinafter, a vibrating conveyor according to an embodiment of the present invention will be described with reference to the drawings.

The vibrating conveyor according to this embodiment is an elongated conveyor, and the length and width of the trough 1, which has a J-shaped cross section, is, for example, 8 m and 10 crrl, and the trough 1 as a vibrated part are arranged at equal intervals in the longitudinal direction, and are elastically coupled to the base 4 by a plurality of elastic units 3, which will be described in detail later, via a plurality of support plates 2, which are also arranged at equal intervals.

The base 4 is long like the trough 1, and is supported on the ground by an anti-vibration spring 5.

As shown in FIGS. 2 and 4, the support plate 2, elastic unit 3, and base 4 welded and fixed to the trough 1 are symmetrically provided along the longitudinal direction, and the elastic units 3 are arranged at equal intervals. The number of support plates 2 is appropriately selected depending on the length of the trough 1.

A vibrator 1 is fixed to an end of the base 4 corresponding to the material supply side end 1a of the trough 1 via a mounting member 6.

That is, a mounting member 6 is fixed to the front end surface of a rectangular cylindrical frame 8 of the vibration exciter 7, and an end portion of the base 4 is fixed to this member 6.

Rotating shafts 9a arranged vertically within the frame 8
, 9b are supported at both ends by bearings 10a, 10b fixed to both sides of the frame 8, respectively, and semicircular unbalanced weights 11a, 11 are mounted in the center thereof.
b is fixed by a known method, although not shown.

Gears 12a and 12b having the same number of teeth and meshing with each other are fixed to one end of the rotating shafts 9a and 9b protruding from the frame 8, and a pulley 13 is fixed to the other end of the rotating shaft 9a. There is.

An electric motor 14 is fixed to the rear end surface of the frame 8, and a belt 16 is wound around a small pulley 15 fixed to one end of the rotating shaft and the above-mentioned large diameter pulley 13.

When the rotating shafts 9a and 9b are driven by the electric motor 14, they rotate at a constant speed in opposite directions as shown by the arrows in FIG. Unbalanced weights 11a, llb are attached to the rotating shafts 9a, 9b at angular positions such that they cancel each other out.
is fixed.

For example, they are fixed to rotating shafts 9a and 9b in a phase relationship as shown in FIG.

The vibration exciter γ in this embodiment is constructed as described above.Next, details of the elastic unit 3 will be explained with reference to FIGS. 1, 2, 4, and 5. The unit 3 mainly consists of a pair of rubber springs 30
．． 31, a connecting member 32 which is sandwiched between these rubber springs 30 and 31 and fixed by bolts, and a circular rubber spring mounting plate 33.

Rubber spring 30.31 is rectangular rubber 30c
, 31c, and a rectangular iron plate 30a vulcanized and fixed to these surfaces and lower surfaces.

31a, 30b, and 3ib, and the connecting member 32, which is clamped and fixed by rubber springs 30 and 31, includes a pair of upper and lower iron plates 32a, 32b, and these iron plates 32a.
It consists of a rectangular parallelepiped connecting block 32c fixed by welding at the center position between *32b.

A circular opening 33a is formed in the center of the circular rubber spring mounting plate 33 for adjusting the vibration angle, that is, for adjusting the mounting angle of the rubber spring 30°31.
A pair of arcuate openings 33b and 33c (see FIG. 1) are formed concentrically with a and radially opposed to each other.

By engaging the bolts 36 and 37 with these openings 33b and 33c (see Fig. 1) and screwing them into the screw holes formed in the base 4, the rubber spring mounting plate 33, that is, the elastic unit 3 is attached to the base. Fixed to 4.

The inner surface of the rubber spring mounting plate 33 has a central opening 33a.
A pair of flat plate-shaped mounting members 38 and 39 are welded and fixed in parallel to each other, and protrude inward from a circular opening 4a formed in the base 4 concentrically with the central opening 33a of the rubber spring 33.

Rubber springs 30 and 31 are attached to these mounting members 38 and 39.
iron plates 3Qa, 31b are fixed with bolts and nuts as shown in FIG.
A connecting member 32 is inserted in a crimped state between them, and its upper and lower iron plates 32a, 32b are connected to the iron plate 30 of the rubber spring 30, 31.
It is fixed with bolts and nuts as shown in 31a and 31b.

A connecting block 32c fixed to the center of the connecting member 32
As clearly shown in FIG. 4, a through hole 32d is formed in the
A bolt 34 is inserted through this.

The inner end face of the connecting block 32C abuts the support plate 2, so that the rubber springs 30, 31 are separated from the support plate 2 by a predetermined distance.

A round hole aligned with the through hole 32d of the connecting block 32c is formed in the support plate 2, and the end of the bolt 34 inserted through the through hole 32d is also inserted through this round hole, and the nut 35
is screwed onto this and tightened, thereby connecting member 3
2, thus one side of each of the rubber springs 30, 31 is fixed relative to the support plate 2, ie to the trough 1.

Note that the above-mentioned base 4 and the vibrator T1 rubber spring mounting plate 33 constitute the vibrating section of the present vibration conveyor, but by fixing the above-mentioned connecting member 32 to the support plate 2, it becomes the vibrated section. A relatively vibratory connection between the trough 1 and the vibrating part is established.

In order to give a desired vibration angle to the horizontally extending trough 1, each elastic unit 3 is attached at a corresponding angle β as shown in FIG. It is fixed to the base 4 so as to be inclined with respect to the direction H.

That is, in this inclination angle adjustment work, the connecting member 3
2 (bolt 34 inserted here and arcuate opening 33b)
, 33c are loosened, and the rubber spring mounting plate 33 is rotated clockwise or counterclockwise about the bolt 34 to obtain the above-mentioned desired angle β. Tighten the bolts 34, 36, and 37. The vibrating conveyor according to this embodiment is constructed as described above, and its operation will be explained next.

When a power source is connected to the electric motor 14, the rotating shafts 9as9b rotate in opposite directions at the same speed, as shown in FIG.

Therefore, the unbalanced weights 11a and llb fixed to the rotating shafts 9a and sb also rotate, and their centers of gravity? 1* Centrifugal force F, IF is generated at F2.

When the unbalanced weights 11a and 11b have the phase relationship shown in FIG. 6A, their centrifugal force F1sF is in the vertical direction (
Since the Y-direction) components are opposed to each other, the resultant force Fy in the vertical direction (assuming that the unbalanced weights 11a and 11b are equal in mass and shape) is 0, and their horizontal (X-direction) components are 0. Since is 0, the resultant force FX in the horizontal direction is also 0.

When rotated 90 degrees from the phase in Figure 6A, the unbalanced weight 11a
, llb have the phase relationship shown in FIG. 6B, and their centrifugal force F1 . Since the vertical component of F2 is 0, the resultant force FY in the vertical direction is also 0, but the resultant force FX in the horizontal direction is the centrifugal force F1. F2 is in the same direction, so FX
-F1+F2=2F (however, F, =F, =F).

When the phase is further rotated by 90 degrees from the phase shown in Figure 6B, the unbalanced weight 1
1a.

11b has the phase relationship shown in FIG. 6C.

In this phase, centrifugal force F8. Since F2 is in opposite directions in the vertical direction, the resultant force F in the vertical direction
The resultant force in the horizontal direction to Y= is FX=0.

When the phase relationship shown in FIG. 6C is further rotated by 90 degrees, the unbalanced weights 11a and llb have the phase relationship shown in FIG. 6D.

In this phase, the centrifugal force F1 of the unbalanced weights 11a and 11b. Since F2 is in the same direction in the horizontal direction, the resultant force in the horizontal direction is FX=F□10F,=2F, but the direction is opposite to the phase relationship in FIG. 6B.

The resultant force in the vertical direction is FY=O.

If the phase relationship shown in FIG. 6D is further rotated by 90 degrees, the phase relationship shown in FIG. 6A will be obtained, and the unbalanced masses 11a and 11b will each rotate once in opposite directions, and the above-mentioned phase relationship will be repeated. , it can be understood that vibration force is generated only in the horizontal direction from the vibrator T, but
This will be further explained generally with reference to FIG.

Now, after t seconds from the phase relationship shown in FIG. 6A, the unbalanced weight 11a
, 11b centrifugal force F1. Considering F, the X-direction component of the centrifugal force F1 of one unbalanced weight 11a is F1X
=-F1cosω (where ω is the angular frequency of the rotating shafts 9a, 9b), and X of the centrifugal force F2 of the other unbalanced weight iib
The directional component is F2X=-F2 co sωt.

Therefore, the resultant force in the X direction FX=FIX+F2X=
2FcosGJt.

On the other hand, centrifugal force F1. The Y-direction components of F, respectively, are Ft
Y=Flsinω and F2y−F2s in(d
t, so the resultant force in the Y direction is FY=FIY
+F2Y=O.

Therefore, from the vibrator T, FX=-2Fc only in the horizontal direction.
A sinusoidal vibration force osωt is generated.

The above-mentioned sinusoidal vibration force FX=-2Fcosωt is transmitted from the vibrator γ to the base 4, and vibrates the trough 1 through the elastic force of each elastic unit 3.Next, the vibration of the trough 1 will be explained. do.

The sinusoidal vibration force FX from the vibrator 1 is applied to the mounting members 38 and 39 fixed to the rubber spring mounting plate 33 of the elastic unit 3.
The rubber springs 30.3 are now deformed as shown in FIG.
1's shear direction is P, and the direction perpendicular to this, that is, the compression direction, is Q, and the displacements of the vibrated part and the vibrated part in each direction are x11X2 and y, #y2
In this case, the following equation of motion holds true.

In the above equation, m represents the total mass of the vibrating part consisting of the trough 1, support plate 2, etc., M represents the total mass of the vibrating part consisting of the base 4, the vibrator T, etc., and k represents the total mass The total spring constant of the rubber springs 30, 31 of the elastic unit 3 in the shear direction and K represent the total spring constant in the compression direction.

Further, Fxcosβ and -Fxsinβ represent components of the excitation force Fx of the vibrator T in the P direction and the Q direction.

In the above equation, the spring constant of the vibration isolation spring 5 is ignored because it is sufficiently smaller than the spring constant of the rubber springs 30 and 31 and K.

The above equations (1) to (4) are expressed as the vibration width of the excited part xl * Vm
Therefore, the excited part, that is, the trough 1, performs linear vibration having a component xl in the P direction and a component y□ in the Q direction.

y/l (1-λ')s for the P direction of this linear vibration
inβ ru gradient town 1 = (□−2・).

With o5β 1, trough 1 under the conditions of 2〈1 and λ′〈l
When driven, the linear vibration is slightly inclined from the P direction toward the horizontal direction H-H.

The spring constant of the rubber spring 30.31 in the shear direction is sufficiently smaller than the spring constant K in the compression direction, so
When the vibrating conveyor is driven with resonance in the shear direction, ζ, that is, when it is driven at λ=1, the trough 1 is P
direction, ie parallel to the shearing direction of the rubber springs 30.31.

In practice, considering the load of material fed into trough 1, λ
The conveyor is driven at 0.9, but under this condition β=4
Experimental data has been obtained in which the vibration angle of the trough 1 is about 30 degrees compared to 5 degrees.

The condition that λ is 0.9 is based on the mass of the vibrating part and the vibrated part and the rubber spring 30, which determines the resonant frequency ω0 of the entire vibration conveyor while keeping the drive frequency ω of the vibrator 1 constant.
It may be determined by an appropriate calculation such as the spring constant in the shear direction of 31, or the vibration conveyor which is the vibration system may be kept constant and the driving frequency of the vibrator T may be determined by some means, such as an inverter circuit, to supply power to the motor 14. It may also be determined by changing the frequency.

According to an embodiment of the invention, as mentioned above, the trough 1 vibrates at a desired angle with respect to the horizontal direction, i.e., at a desired vibration angle with respect to the longitudinal direction of the trough 1, as shown in FIG. 1 OA. However, if you want to change this vibration angle, each elastic unit 3 can be rotated.
After loosening the rubber springs 30.31 and rotating the mounting plate 33 to which the rubber springs 30.31 are attached around the bolts 34 to adjust the shearing direction of the rubber springs 30.31 to an angle corresponding to the desired vibration angle, remove the rubber springs 34. Since it is only necessary to tighten 36 and 37, the adjustment work for changing the vibration angle is extremely easy.

Moreover, the vibration exciter 1 is operated only in the horizontal direction, that is, in the trough 1
Since the excitation force is generated only in the longitudinal direction of the trough 1, even if the trough 1 is of a long type as in this embodiment, bending vibration in the first mode or the second mode hardly occurs.

In other words, the trough 1 itself generates almost no undulating vibrations along its length - this is not only favorable for the strength requirements of the trough 1, but also ensures a stable transfer of material. This is guaranteed.

Generally, in order to avoid vibrations in the first mode or second mode of the trough 1, the drive frequency of the trough 1 is designed to be as low as possible below the resonance frequency of these modes.

That is, the design is such that the resonant frequencies of these modes are as high as possible than the drive frequency, but according to this embodiment, since there is no vertical component in the excitation force, vibrations of these modes are extremely unlikely to occur.

Therefore, not only can the resonant frequencies of these modes be lowered to make the strength of the trough 1 as low as possible, but the trough 1 can also be The length can be made larger.

Furthermore, according to this embodiment, as described above, the driving frequency can be made close to the resonance frequency of the primary mode or secondary mode of the trough 1, so the driving frequency can be made higher for a given trough. Can be done.

For example, the frequencies of the first mode of trough 1 are 683r,p
, m, and the frequency of the secondary mode is 155 Or, p, m, and the driving frequency is 115°r, p, m. In other words, the driving frequency is the frequency of the primary mode of trough 1 and the frequency of the secondary mode. Experimental data has been obtained that shows that the trough 1 hardly causes any bending vibration even if it is set in between.

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 30 and 31 are used in each elastic unit 3, but the invention is not limited to this, and a plurality of rubber springs may be attached above and below the connecting member 32. You may also do so.

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

Further, in the above embodiment, the base 4 is supported on the foundation by the vibration isolating spring 5, but instead of this, the base 4 may be suspended and supported on a part of the building by the vibration isolating spring.

Furthermore, in the above embodiments, a long type vibrating conveyor was explained in which the width of the trough 1 was 1Ocrr1 and the length was 8m.
The present invention is of course applicable to short vibrating conveyors.

In this case, the number of elastic units 3 can be reduced compared to the embodiment, depending on the length of the trough.

Furthermore, it is also possible to configure a vibrating conveyor with one elastic unit 3.

In this case, for example, the elastic unit and the base may be provided along the center line along the longitudinal direction of the trough.

Further, a pair of arcuate openings 33b, 33 of the rubber spring mounting plate 33 in the elastic unit 3 in the above embodiments.
If the circumferential length of c is further increased, the shear direction of the rubber springs 30 and 31 of the elastic unit 3 can be changed up to 360 degrees, so the material on the trough 1 can be moved using the same vibration exciter T. The transport direction can be reversed.

Further, in the above embodiments, the longitudinal direction of the trough 1 is horizontal, but the present invention is also applicable to an inclined trough 1.

In this case, the vibration exciter T may be tilted according to the inclination angle of the trough 1 and fixed to the base 4.

The vibrating conveyor of the present invention has the configuration described above,
The vibration angle of the vibrated part can be easily changed, and moreover, bending vibration in the longitudinal direction of the vibrated part itself can be prevented from occurring.

[Brief explanation of the drawing]

FIG. 1 is a side view of a vibrating conveyor according to an embodiment of the present invention;
Fig. 2 is a plan view of the conveyor, Fig. 3 is an enlarged sectional view in the l-1 line direction in Fig. 2, and Fig. 4 is an IV in Fig. 1.
-IV line direction enlarged sectional view, FIG. 5 is V- in FIG.
6A to 6D are enlarged cross-sectional views in the V-line direction; It is a side view for generally explaining the excitation force generated by rotation of. In the figure, 1...... trough, 3...
...Elastic unit, 4...Base, 5...
・・Vibration isolation spring, 1・・・Vibration machine, 9as9
b... Rotating shaft, 11a. 11b...Unbalanced weight, 12a, 12b...
...Gear, 14...Electric motor, 30.31...
...Rubber spring, 33...Rubber spring mounting plate.

Claims (1)

[Claims] 1. An excitation mechanism that has an excited part that tilts in a predetermined direction, an unbalanced weight that is fixed to a pair of rotating shafts that are rotated at the same speed in opposite directions by a gear mechanism, and this excitation mechanism that is fixed. a base part supported so as to vibrate; and an elastic unit that connects the base part and the vibrated part so as to be able to vibrate relative to each other; The vibrated parts are each fixed to the rotating shaft so that their vertical components with respect to the predetermined direction cancel each other out, and the elastic unit is composed of a plate-shaped rubber spring and a rubber spring mounting plate. , with respect to the shearing direction of the rubber spring, one surface is fixed to the rubber spring mounting plate and the other surface is fixed to the vibrated part, and the rubber spring mounting plate is fixed in the shearing direction of the rubber spring. A vibrating conveyor, wherein the vibrating conveyor is rotatably fixed to the base part so that the direction is in a desired direction with respect to the predetermined direction of the vibrated part.