JPS5849442B2 - vibrating conveyor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vibrating conveyor that conveys various lumps, grains, powder materials or various parts by vibration.

Generally, in a vibrating conveyor, a vibrating force having a certain angle is applied to the trough material transfer bed, whereby the material on the transfer bed is transferred in a predetermined direction while repeating periodic jump movements.

That is, as shown in Figure 1, the transfer bed S of the trough is subjected to a vibration force in the direction of arrow A (inclined at an angle α with respect to the transfer bed S), and as a result, the material on the transfer bed S is moved in the direction of arrow B. It is transported in the direction.

The vibration force changes sinusoidally as shown in Figure 2, and at a point P1 where its vertical component exceeds the mass of the material x gravitational acceleration, the material jumps in the α direction, and the transfer bed S receives a force of P2. The material lands on the transfer bed S at the point P1, and jumps again at point P3, which corresponds to point P1.Hereafter, as shown by the dotted arrow in FIG. The material is transferred in the direction B as shown in the figure.

However, bulk metal materials such as bolts, nuts,
When transferring billets etc. using the vibrating conveyor mentioned above,
Due to the repeated jumping motion of the material, when it collides with the transfer bed (often made of metal), it produces noise and, in some cases, creates a pollution problem.

Furthermore, when fragile materials such as biscuits and senbei are transported using a vibrating conveyor, periodic collisions with the transport bed can cause problems such as cracks and cracks, which can be affected by the material of the transport bed and the vibration conditions. had some troublesome restrictions added to it.

Furthermore, when a material that easily generates dust, such as a finely powdered material, is transported by a vibrating conveyor, the dust may be undesirable from a sanitary standpoint.

Further, conventional vibrating conveyors are generally of the resonant type, and in this case, not only the structure is complicated, but also troublesome design and adjustment are required to achieve synchronization.

There is also a so-called reciprocating conveyor, which transports the material only by sliding motion without giving it a jumping motion, but in this case, a crank mechanism or a complicated mechanical structure is used as the drive unit. Not only was the cost high, but there were also difficulties in providing vibration isolation to the foundation and ground.

The purpose of the present invention is to eliminate the above-mentioned drawbacks of the conventional vibrating conveyor, and the purpose is to provide a vibrating part that extends in a predetermined direction, and a tenon that supports the vibrating part so that it can vibrate in the predetermined direction. an elastic member that vibrates the vibrating mechanism and the vibrated part integrally in the predetermined direction, and vibrates the vibrating mechanism and the vibrated part in a direction perpendicular to the predetermined direction; a vertical component absorbing connecting member that connects the vibrating mechanism and the vibrated part so as to vibrate relative to the vibrating part; and a second unbalanced weight having a small eccentric radius x mass, a first rotating shaft and a second rotating shaft to which these unbalanced weights are respectively fixed, a driving source, and the above-mentioned rotation by driving this driving source. When driven by a gear mechanism that connects both rotational shafts so that the shafts are rotated in opposite directions and the second rotational shaft is rotated at a speed that is an integral multiple of the first rotational shaft, the vibration mechanism is moved to the predetermined direction. By constantly vibrating in a direction perpendicular to the direction of This is achieved by a vibrating conveyor characterized in that the vibration is transmitted to the vibrating section via the vibrating section.

The structure described above not only solves the problems of noise and materials breaking and breaking, but also has a simple structure and easy design. As a result, while using a spring with a low spring constant, it is possible to create a structure that can support the vibrated part, so the vibration-proofing effect is good, and the overall structure is also lightweight, making it possible to reduce costs.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The details of the present invention will be described below with reference to embodiments and the drawings.

In the figure, the conveying trough 1 is made of steel, for example, and has a box-shaped cross section and a rectangular shape in plan view, and the conveying material (for example, billets or bolts) is supplied at its left end, and its open right end The conveyed material is discharged from the section and transferred to the next process by a conveyor (not shown) or the like.

This transport trough 1 is coupled to a base 3 by a plurality of leaf springs 2.

That is, a plurality of mounting angle members 4a and 4b are fixed to the bottom and top surfaces of the transport trough 1 and the base 3 at equal intervals, and the plate springs 2 are attached to these mounting angle members 4a and 4b in the longitudinal direction of the transport trough 1 (
In other words, it is fixed so as to be arranged perpendicularly to the transport direction.

The conveying trough 1 is thus supported by the leaf spring 2 so as to be able to vibrate in the direction of the arrow X.

According to the present invention, the above-mentioned transport trough 1 as a vibrated part
is connected to the supporting mechanism 6 via the connecting portion C.

That is, in the connecting portion C, a plate spring mounting angle member 30 having an L-shaped cross section is fixed to the rear end wall of the trough 1 with, for example, bolts, and on the other hand, the front side of the rectangular parallelepiped-shaped bracket 10 of the vibration mechanism 6 is fixed to the rear end wall of the trough 1. Similarly, a plate spring mounting angle member 32 having an L-shaped cross section is fixed to the portion with, for example, bolts.

A pair of vertical partial absorbing leaf springs 34a and 34b are fixed near both ends of the mounting angle members 30 and 32, respectively, with their longitudinal force directions parallel to the longitudinal direction of the trough 1, for example, by bolts.

The leaf springs 34a and 34b are made of steel or FRP (
It is made of fiber reinforced plastic and is easily deformed in the direction perpendicular to its longitudinal direction, that is, easily bent, but exhibits rigidity against compression and tension in the longitudinal direction and hardly deforms.

Although the connecting portion C according to the embodiment of the present invention is constructed as described above, the vibration mechanism 6 coupled to the trough 1 via this connecting portion C will be described in detail below.

That is, in the vibration mechanism 6, two pairs of bearing housings 11 and 12 are provided on both side walls of the mounting bracket 10.
and 13 and 14 are fixed.

Bearing housings 11 and 12 support the first rotating shaft 1
5 is supported at both ends thereof, and a second rotating shaft 16 is supported at both ends by bearing nozzles 13 and 14.

As clearly shown in FIG. 5, a first unbalanced weight 7 having a semicircular shape is fixed to the first rotating shaft 15 with bolts or the like.

Each of the first unbalanced masses 7 in this embodiment consists of two identical unbalanced masses, as is clearly shown in FIG.

Furthermore, as clearly shown in FIG. 5, a second unbalanced weight 8, which is smaller in diameter than the first unbalanced weight 7 but also semicircular in shape, is fixed to the second rotating shaft 16 with bolts or the like. Ru.

An induction motor M is fixed to the rear wall of the mounting bracket 10.

A small diameter pulley 18 is attached to one end of the rotating shaft of the induction motor M.
is fixed, and a large diameter pulley 2 is attached to one end of the first rotating shaft.
0 is fixed, and a belt 22 is wound around these boots IJ-18 and 20.

A large diameter gear 24 is fixed to the other end of the first rotating shaft 15,
A small diameter gear 26 is fixed to one end of the second rotating shaft 16.

In this embodiment, the ratio of the number of teeth between the large diameter gear 24 and the small diameter gear 26 is 2.
:1 and are mutually interlocking.

According to this embodiment, the first unbalanced weight 7 and the second unbalanced weight 8 are connected to the first rotation axis 15 and the second rotation axis 16, respectively, in a phase relationship as shown in FIG. are fixed, and as is known, their rotation causes centrifugal forces F and f (6th A
6D) is generated, and the sum of these centrifugal forces F and f becomes the vibration force generated from the vibration mechanism 6.

The magnitude of the centrifugal forces F and f is determined by the first and second unbalanced weights 7,
8, the distances from the axes of the rotation axes 15, 16 of the centers of gravity G and g of the rotary shafts 15, 16 are R, r, the masses of the first and second unbalanced weights 7, 8 are M, m, and the rotation axes 15, 16 The angular velocity of ω1, ω2
Then, F=MRω12 and f2mrω22, respectively.
becomes.

Further, according to this embodiment, the second rotating shaft 16 is the first rotating shaft 1.
Since it rotates at a speed twice as high as 5, ω2=2ω1.

Furthermore, according to this embodiment, the first unbalanced weight 7 is made up of two unbalanced weights of the same shape as shown in FIG. 4, but instead of this, one unbalanced weight of the same shape is used. Balanced weight (however, the mass is twice as large as in the case of two).

) is fixed to the rotating shaft 15 at the center position between the two unbalanced weights 7, 7 as shown in FIG. 4, and the centrifugal force is the same. is assumed to be between one and a certain number for the sake of simplicity.

Further, in this specification, the above-mentioned MR and mr will be referred to as the eccentricity of the unbalanced weight.

The vibration mechanism 6 configured as described above is supported on the base 3 by a plurality of coil springs 36 at the bottom wall of the bracket 10.

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

When power is applied to the electric motor M and it is driven once, the first rotating shaft 15 is rotated through the belt 22, for example, 800
r. p. It rotates clockwise at a rotational speed of m.

On the other hand, due to the meshing of the gears 24 and 26 fixed to one end of the first rotating shaft 15 and the second rotating shaft 16, the second rotating shaft 16 has a speed of, for example, 1600 r. p. It rotates counterclockwise at a rotational speed of m.

Hereinafter, each rotational phase of the unbalanced weights 7 and 8 will be explained. As shown in FIGS. 6A to 6D, the first unbalanced weight 7 is rotated 90 degrees clockwise from the rotational phase shown in FIG. 6A. When rotated, the second unbalanced weight 8 rotates 180 degrees counterclockwise, resulting in the state shown in FIG. 6B. When the first unbalanced weight 7 further rotates 90 degrees clockwise, the second unbalanced weight 8 8 is rotated 180 degrees counterclockwise to the state shown in FIG. 6C, and then returns from the state shown in FIG. 6D to the state shown in FIG. 6A.

That is, when the first unbalanced weight 7 shifts one rotation clockwise, the second unbalanced weight 8 rotates two rotations counterclockwise.

Thereafter, periodic rotational movements shown in FIGS. 6A to 6D are performed.

To explain the direction of the centrifugal force in each rotational phase described above, in the rotational position of FIG. 6A, the first unbalanced weight 7
The centrifugal force F acting on the center of gravity G of the second unbalanced weight 8 is
is in the same direction as the centrifugal force f exerted on
An excitation force f is generated.

Then, in the rotational phase of FIG. 6B, the first unbalanced weight 7
The centrifugal force F acting on the center of gravity G of the second unbalanced weight 8 is in the -X direction, but the centrifugal force f acting on the center of gravity g of the second unbalanced weight 8 is in the Y direction,
Excitation forces of −F and f are generated in the excitation mechanism 6 in the X direction and the Y direction, respectively.

Next, in the rotation phase of FIG. 6C, the first unbalanced weight 7
The centrifugal force F acting on the center of gravity G of the second unbalanced weight 8 is in the Y direction, but the centrifugal force f acting on the center of gravity G of the second unbalanced weight 8 is in the -Y direction.
The excitation mechanism 6 generates an excitation force F−f in the Y direction.

Then, in the rotational phase of FIG. 6D, the first unbalanced weight 7
The centrifugal force F acting on the center of gravity G of the second unbalanced weight 8 is in the X direction, but the centrifugal force f acting on the center of gravity g of the second unbalanced weight 8 is in the Y direction. F and f
generates an excitation force of

It has become clear that the above-mentioned excitation force is periodically generated in the excitation mechanism 6 in each rotational phase shown in FIGS. 6A to 6D. It is as follows.

That is, after time t from the rotational phase shown in FIG. 6A, the first unbalanced weight 7 and the second unbalanced weight 8 come to the rotational positions shown in FIG. 7, respectively.

In the general rotational phase shown in FIG. 7, the X-direction force of the centrifugal force F acting on the center of gravity G of the first unbalanced weight 7 is ps
inωt (ω; angular velocity), and the Y direction component is F co
It is sωt.

On the other hand, X of the centrifugal force f acting on the center of gravity g of the second unbalanced weight 8
The direction or minute is fsin2ωt, and the Y direction or minute is -f
cos 2ωt.

Therefore, the resultant force in the X direction of the centrifugal forces of the first and second unbalanced weights 7 and 8 is Fx=-Fsinωt+f sin
2ωt, and the resultant force in the Y direction is FyF cosω
t-fcos2ωt.

That is, the above-mentioned excitation force Fy is generated from the excitation mechanism 6 in the Y direction, and the above-mentioned excitation force Fx is generated in the X direction.

However, according to this embodiment, the vibration mechanism 6 includes the leaf springs 34a,
Since it is connected to the trough 1 via the trough 34b, the leaf springs 34a and 34b bend vertically as shown by broken lines due to the above-mentioned excitation force Fy, and the excitation mechanism 6 itself vibrates in the vertical direction.

Therefore, the Y-direction component of the force from the vibration mechanism 6 is hardly transmitted to the trough 1 side, and only the X-direction component is transmitted to the plate 3.
4a, 34b directly to the trough 1.

This is because the leaf springs 34a, 34b exhibit rigidity in this direction as described above.

That is, the vibration mechanism 6 sends Fx=Fsi to the trough 1.
Only the resultant force nωt+fsin2ωt is applied.

Figure 8A is a graphical representation of this combined force.

Note that in the illustration, F=2 f.

That is, the eccentric radius multiplied by the mass of the first unbalanced weight 7 is twice that of the second unbalanced weight 8.

That is, as shown in FIG. 8A, the X-direction fraction f' of the centrifugal force f by the second unbalanced weight 8 is twice the period of the X-direction fraction F' of the centrifugal force F by the first unbalanced mass 7. Q changes sinusoidally, and the graph that combines these changes is Q.

The vibration conveyor according to this embodiment has a single mass system in the X direction from a vibration perspective, and the elastic constant of the entire leaf spring 2 and the mass supported by these (the trough 1, the connecting part C1 excitation The resonant frequency of this mass system is determined by the total mass of the mechanism 6), but if the elastic constant of the entire leaf spring 2 is made sufficiently small and the trough 1 is excited at a driving frequency higher than the resonant frequency, vibration theory As is clear from the above, the trough 1 vibrates with a phase difference of 180 degrees from the excitation force.

Therefore, when excited with a resultant force Q as shown in FIG. 8A, the trough vibrates as shown in the graph S.

This graph S has graphs f' and F' on the horizontal axis t(
(time axis) and then combine them.

However, for graph S, the vertical axis represents displacement.

As understood from the graph S, the trough 1 moves forward at a low speed to point a, and then moves backward at a high speed from this forward position point a to point b.

Next, the vehicle moves forward at a low speed from the backward position point b to the forward position point a.

As the trough 1 repeats such periodic movements, the material on the transfer bed 1a of the trough 1, for example billet M, is transferred in the X direction.

In other words, in the high-speed backward motion region between ■ and ■ in FIG. 8A, the static friction between the material and the floor of the trough 1 is overcome, and only the trough 1 moves backward, causing the surface of the trough 1 to move backward. Slippage occurs between the material and the floor surface.

Next, in the low speed forward region between ■ and ■, trough 1
The material on the surface of the transfer bed 1a advances together with the trough 1.

That is, the trough 1 repeatedly moves forward and backward as shown in FIG. 8B.

By repeating this phenomenon, the material is transferred to the right on the floor of the trough 1 in FIG. 3 or 4.

For example, the conveying material is billet (iron material supplied to the furnace), and the rotational speed of the rotating shaft 15 is set to about 80 O r. p. m
In this case, the material is transported at a speed of 12 m/min.

Moreover, unlike conventional vibrating conveyors, there is no noise caused by the jumping movement of the material, and the material is transferred smoothly.

9 and 10 are a side view and a plan view of a portion of a vibrating conveyor according to another embodiment of the present invention.

This embodiment differs from the above-described embodiment only in the connecting portion C, and is otherwise the same, so corresponding parts are designated by the same reference numerals and description thereof will be omitted.

That is, in the connecting portion C of this embodiment, the plan view is [
A shaped reinforcing member 40 is fixed to the rear wall of the trough 1 by bolts or welding, and a pair of support shaft mounting plates 42a and 42b are fixed to this reinforcing member 40 by welding in parallel to the X direction at a predetermined interval. Ru.

On the other hand, a pair of spindle mounting plates 44a and 44b are also welded to the front wall of the mounting bracket 10 of the vibration mechanism 6 parallel to the X direction with the same spacing as the spacing between the mounting plates 42a and 42b on the trough 1 side. Fixed by

The above mounting plates 42a, 42b, 44a, 44b have vertical support shafts 46a, 46b, 48a, 48b, respectively.
is fixed by welding.

Connecting rods 50 and 52 are pivotally connected to these support shafts 46a and 48a and to 46b and 48b at both ends.

That is, the ring parts soa, sob and 52a, 52b formed at both ends of the connecting rods 50 and 52 connect to the support shaft 4.
6a, 48a and 46b, 48b so as to be rotatable.

As described above, the connecting portion C of this embodiment is constructed, and the above-mentioned vibration mechanism 6 and the trough 1 are connected through this. An excitation force Q is applied, and the trough 1 performs a similar movement.

That is, due to the Y-direction component of the excitation force from the vibration mechanism 6, the vibration mechanism 6 itself causes the connecting rods 50 and 52 to swing around the support shafts 46a and 46b, as shown by broken lines in FIG. Therefore, it vibrates relative to the trough 1 in the Y direction.

As a result, the Y direction from the vibration mechanism 6 or the trough 1
Only the X-direction command is transmitted to the trough 1 via the rigid connecting rods 50, 52, and the vibration mechanism 6 and the trough 1 are connected to each other in the X direction as shown in FIGS. 8A and 8B. Vibrate.

Therefore, the material M' on the floor surface 1a of the trough 1 is transferred to the floor surface 1a without making a jumping movement as described in the above embodiment.
It performs a periodic sliding movement on a and is transferred to the right end side of the trough 1.

Although the vibrating conveyor according to the embodiments of the present invention is constructed and operates as described above, the present invention is not limited to these embodiments, and various modifications can be made based on the technical idea of the present invention. It is.

For example, in the above embodiment, the first unbalanced weight 7 is restrained from two unbalanced masses, but of course, like the second unbalanced mass 8, the first unbalanced mass 7 is restrained from one unbalanced mass. The shape is not limited to a semicircular shape.

However, as in the above embodiment, the first unbalanced weight 7
The stress distribution due to the centrifugal force on the rotating shaft will be more favorable if the two unbalanced weights are used.

In this respect, the first unbalanced weight 7 may be configured to be dominated by a larger number of unbalanced weights.

The same can be said of the second unbalanced weight 8.

Furthermore, the fixed angular position of the unbalanced weights 7, 8 with respect to the rotating shaft 15, 16 is not limited to the above-described embodiment.

That is, in the embodiment, it is fixed at the position shown in FIG. 5 or 6A (the positions in FIGS. 6B to 6D are equivalent to FIG. 6A), but the present invention is not limited to this, for example,
The first unbalanced weight 7 and the second unbalanced weight 8 may be fixed to the rotating shafts 15 and 16, respectively, in the angular positional relationship shown in FIG. 11.

In this case, unbalanced weights 7 and 8 are used in the Y direction (
An excitation force of fFsinβ) is generated, and an excitation force of (-Fcosβ) is generated in the X direction, which causes the vibration mechanism 6 itself to move in the Y direction, and the vibration mechanism 6 and the trough 1 to move the vibration mechanism 6 and the trough 1 in the Y direction. It is clear that periodic excitation forces are generated in the Y and X directions by vibrating integrally in the X direction and rotating the rotating shafts 15 and 16 in opposite directions at a speed ratio of 1:2. , 8A and 8B, it is clear that a graph of the same trend, albeit with a slight deviation in phase and height, can be obtained for sliding material transport.

This also allows the transfer speed to be controlled.

Furthermore, in the above embodiment, the rotational speed ratio of the first unbalanced weight 7 and the second unbalanced weight 8 was set to 2:1, but even if this was set to 3:1 or 4:1, the same periodic effect would occur. It is clear that an asymmetric trough motion can be obtained.

Furthermore, in the above-described embodiment, the trough 1 is supported on the base 3 by a leaf spring, but it may be suspended from above via a leaf spring.

In this case, the vibration mechanism 6 is also suspended from above via a coil spring.

Furthermore, although the leaf springs 2 are arranged vertically in the above-described embodiments, they may also be arranged with some inclination in the vertical direction.

However, in this case, it is assumed that the vertical component of the vibrational acceleration of the trough 1 satisfies the condition of the gravitational acceleration (g) so that no jumping motion of the material occurs.

For example, the vibration stroke of trough 1 is 10, and the vibration frequency is 70.
When the angle of inclination of the plate 2 with respect to the vertical direction is 20 degrees at 0 times/min, the material is transferred without jumping movement.

In addition, in the above embodiment, the plate spring 34a is used as the connecting portion C.
, 34b or connecting rods 50, 52 hinged to the trough and the vibration mechanism at both ends are used, but the above-mentioned hinges may be replaced with rubber pushers, or plate rubber may be used for shearing. The same effect as described above can be obtained even if the direction is parallel to the Y direction and the compression direction is arranged in the X direction.

Furthermore, in the embodiment, the trough 1 that simply transfers the material was explained as the vibrated part, but the invention is not limited to this, and additional structures such as protrusions and grooves on the floor of the trough 1 may be used as is known in the art. In addition, actions such as sorting and sorting of materials may be performed while being transported.

In this case, for example, if the present invention is applied to a so-called pinking table used to manually select defective products such as materials or parts transferred on a conveyor, the material or parts will jump like in the past. This has the effect of reducing eye fatigue for the operator.

Since the present invention is constructed as described above, the structure is simple, and the trough as the vibrated part advances slowly in the conveying direction, but returns rapidly, so that the conveyed object can be easily moved compared to the conventional one. Unlike the method of jumping while colliding with the trough as shown in 5, the relationship is slipping (see Figure 8B).
.

There is no noise from the conveyed material, and there is no cracking or cracking on the material.
It does not generate dust and does not generate dust like conventional methods.

Furthermore, since it is not a resonant type, it does not require complicated design or adjustment, and provides various effects such as easy vibration isolation.

[Brief explanation of the drawing]

FIGS. 1 and 2 are schematic diagrams and graphs of a part of the vibrating section showing the principle of operation of a conventional vibrating conveyor, and FIGS.
FIG. 8 shows an embodiment of the vibrating conveyor of the present invention.
Fig. 3 is a side view of the vibrating conveyor, Fig. 4 is an enlarged plan view of the same part, Fig. 5 is a sectional view along the line ■-■ in Fig. 4,
6A to 6D and FIG. 7 are side views of each unbalanced weight for explaining the operation of the embodiment of the present invention, and FIGS. 8A and 8B are graphs similarly explaining the operation. FIGS. 9 and 10 show other embodiments of the vibrating conveyor of the present invention. FIG. 9 is a side view of the main parts, FIG. 10 is a plan view of the main parts, and FIG. FIG. 7 is a side view of an unbalanced weight showing a modification of the mounting position of the balanced weight to the rotating shaft. In the figure, 1...trough, 2...
・Plate spring, 7... First unbalanced weight, 8...
...Second unbalanced weight, 24, 26...Gear, M
...Induction motor, 34a, 34b...
Leaf spring, 50, 52...Connection rod.

Claims (1)

[Claims] 1 a vibrated part extending in a predetermined direction; an elastic member that supports the vibrated part so as to vibrate in the predetermined direction; The vibrating mechanism and the vibrated part are vibrated integrally with the vibrating part, and the vibrating mechanism is vibrated relative to the vibrated part in a direction perpendicular to the predetermined direction. and a connecting member for vertical absorption, and the vibration mechanism includes a first unbalanced weight having an eccentric radius x mass and a second unbalanced weight having a small eccentric radius x mass, and the unbalanced weight. A first rotating shaft, a second rotating shaft to which the weight is fixed, a driving source, and seven drives of this one driving source cause the two rotating shafts to rotate in opposite directions, and the second rotating shaft rotates in the first rotation. When driven by a gear mechanism that connects both rotating shafts so as to rotate at an integral multiple of the speed of the shaft, the vibration mechanism constantly vibrates in a direction perpendicular to the predetermined direction, thereby increasing the vertical direction of the vibration force. The vibration component is not transmitted to the vibrated part, and only the horizontal component of the excitation force is transmitted to the vibrated part via the vertical component absorption connecting member. Conveyor.