JPS6030246Y2 - 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, that is, the material placement surface, and as a result, the conveyed material on the trough surface is transferred in a predetermined direction while repeating periodic jump movements. .

That is, as shown in Fig. 1, a vibration force is applied to the trough surface S in the direction of arrow A (inclined at an angle α with respect to the trough surface), and as a result, the material on the trough surface S is conveyed in the direction of arrow B. I'm going to be done.

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 trough surface S receives a force of P2. It landed on the trough surface S at the point P, which is equivalent to 21 points.
3, the material jumps again, and as shown by the dotted arrow in Figure 2, the material repeats the periodic jumping motion.
In FIG. 1, the material is transferred in the direction B.

However, bulk metal materials such as bolts, nuts, etc.
When transferring billets etc. using the vibrating conveyor mentioned above,
Because the material repeatedly jumps, when it collides with the trough surface (which is often made of metal), noise is emitted and, in some cases, it may cause a pollution problem.

Furthermore, when transporting fragile materials such as biscuits and senbei using a vibrating conveyor, periodic collisions with the trough surface may cause problems such as cracks and cracks. had some troublesome restrictions added to it.

Furthermore, when a material that tends to form lumps, such as a fine powder material, is transported by a vibrating conveyor, the lumps may be undesirable from a sanitary standpoint.

Further, conventional conveyors are generally of the resonant type, which not only have a complicated structure but also require troublesome design and adjustment to achieve synchronization.

・Also, without giving jumping motion to the conveyed material,
There is a so-called reciprocating conveyor that transports materials only by sliding and movement, but in this case, the driving part uses a crank mechanism with a complicated mechanical configuration, which is not only expensive but also causes damage to the foundation and the ground. There was a problem with vibration isolation.

The purpose of the present invention is to eliminate the drawbacks of the conventional vibrating conveyor described above. According to the present invention, a vibrated part extending in a predetermined direction and a vibrated part S an elastic member supported so as to be able to vibrate in a direction; The vibration mechanism is separated from a synchronization connecting member that connects the vibrating part to the vibrating part so as to be able to vibrate relative to the vibrating part, an unbalanced mass of a large-diameter gear fixed to a shaft end of the first rotating shaft that is coupled to rotate the front second rotating shaft in opposite directions at a speed that is an integral multiple of the first rotating shaft; and the large-diameter gear a small-diameter gear meshing with the gear and fixed to the shaft end of the second rotating shaft;
an electric motor that drives the first rotating shaft; The second unbalanced weight is fixed to the rotating shaft so as to be at the same angular position in opposite rotational directions, and the two front power distribution motors are connected to the first and second unbalanced weights of one of the vibrating parts. When the weight is started to be driven to rotate in directions opposite to the first and second unbalanced weights of the other vibrating section, the vibrating mechanism vibrates in a direction perpendicular to the predetermined direction. By doing so, the first and second unbalanced weights of one of the vibrating sections move at the same speed and the same speed in opposite directions as the first and second unbalanced weights of the other vibrating section. A vibrating conveyor characterized in that the vibration conveyor is synchronized to rotate in phase, so that centrifugal force components of the vibrating part in a direction perpendicular to the predetermined direction mutually cancel each other in the pair of vibrating parts. achieved.

With the above configuration, the above-mentioned problems of noise and material problems are solved, and since it is not a resonant type, the structure is simple and the design is not only easy. As the above-mentioned elastic member, an elastic member with a low spring constant is used, and a structure that can support the vibrated part can be achieved, so the vibration-proofing effect is good, the overall structure is lightweight, and the cost is reduced. I can do it.

Further, since the excitation force applied to the vibrated part in a predetermined direction changes continuously and is not impactful, it will not damage any parts.

In addition, in the above structure, since the excitation mechanism and the vibrated part are connected via the above-mentioned connecting member, it is necessary to synchronize one excitation part with the other excitation part. It does not require a pair of gears, making the structure simpler.

Below 1. The details of the present invention will be explained for each embodiment with reference to the drawings.

3 to 8 show a first embodiment of the present invention.

In the figure, the conveying trough 1 is made of steel, for example, and has a U-shaped cross section and a rectangular shape in plan view.The conveying material (for example, billets or bolts) is supplied at its left end, and its right end is open. 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 S, and the leaf springs 2 are attached to these in the longitudinal direction of the transport trough 1 (i.e., 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 P.

A synchronizing leaf spring mounting angle member 32 is fixed by welding or the like perpendicular to the longitudinal direction of the trough 1 at the bottom near the left end of the trough 1, and at the center of the front end of the vibration mechanism 6, which will be described in detail below. A synchronizing leaf spring mounting plate 34 is fixed in correspondence with the leaf spring mounting angle member 32.

Synchronizing leaf springs 30a, 30b are fixed to both ends of these mounting members 32, 34, respectively, by bolts, for example.

As described above, the mounting members 32 and 34 and the synchronization leaf spring 30
The trough 1 and the vibration mechanism 6 are connected via a connecting member C consisting of a and 30b.

The vibration mechanism 6 is further supported on the base 3 by a plurality of coil springs 36 so as to be stably supported.

The vibration mechanism 6 according to this embodiment is separated from a pair of vibration parts 6a and 6b, each having a rectangular parallelepiped-shaped mounting bracket 10a.
, 10b is a spacer plate 38 and the above-mentioned synchronizing leaf spring 34
are fixed to each other through.

Bearing housings lla, llb, 12at 12bt are installed on both sides of the mounting brackets 10a and 10b.
13at 13b and 14a, 14b are fixed,
One first rotating shaft 15a is supported at both ends by the bearing housings lla and 12a, and the other first rotating shaft 15b is supported at both ends by the bearing housings llb and 12b.

Similarly, one second rotating shaft 16a is supported at both ends by the bearing housings 13a and 14a, and the other second rotating shaft 16b is supported at both ends by the bearing bousings 13b and 14b.

As clearly shown in FIG. 5, first unbalanced weights 7a and 7b having a semicircular shape S are fixed to the first rotating shafts 15ay 15b with bolts or the like.

In this embodiment, the first unbalanced weights 7a and 7b are the fourth unbalanced weights 7a and 7b, respectively.
As shown in the figure, two identical unbalanced weights are used.

Furthermore, as clearly shown in FIG. 5, the second rotating shafts 16a and 16b have second unbalanced masses having a smaller diameter than the first unbalanced masses 7a and 7b, but which are also semicircular in shape. 8a and 8b are fixed with bolts or the like.

The pair of first unbalanced weights 7a and 7b have the same shape, and similarly the pair of second unbalanced weights 8a and 8b have the same shape.

The rear wall of the mounting brackets 10a and 10b has a characteristic S.
゛Similar pair of induction motors M□9M2 (e.g. rated 200
v, 20 4 poles) are fixed.

A small diameter pulley 18a is fixed to one end of the rotating shaft of one induction motor M, and a large diameter pulley 20a is fixed to one end of the first rotating shaft 15a.
A belt 22a is wound around 8a and 20a.

Similarly, a small-diameter pulley 18b having the same shape as the above-mentioned pulley 18a is fixed to one end of the rotating shaft of the other induction motor M2, and a small-diameter pulley 18b having the same shape as the above-mentioned pulley 18a is fixed to one end of the other first rotating shaft 15b. - Large diameter pulley 20b with the same shape as 20a
is fixed, and a belt 22b is wound around these pulleys 18b and 20b.

A pair of large diameter gears 24a, 24b are fixed to the other ends of the pair of first rotating shafts 15a, 15b, and a pair of second rotating shafts 1
A pair of small diameter gears 26a, 26 are provided at the other ends of 6a, 16b.
b is fixed.

In this embodiment, the ratio of the number of teeth between the large diameter gears 24a, 24b and the small diameter gears 26a, 26b is 2:1, and they mesh with each other.

Unbalanced weight 7 at 7 bv 8 at 8 b
are rotated by the drive of the electric motor M□9M2, and each generates a centrifugal force. According to the present invention, the synchronizing force after driving is applied to the rotating shafts 15a, 1 of the respective vibrating parts 6a, 6b.
5b, 16a, and 16b, the second and second unbalanced weights 7at8a of one vibrating part 6a act on the other vibrating part 6.
When a steady state is reached in which the second and second unbalanced weights 7b and 8b of b are rotated synchronously at the same speed in opposite directions, the centrifugal force of them is The unbalanced masses 7a, 7b are placed at angular positions such that the sum of the vertical components is always zero, as will be described later.

8a and 8b are rotating shafts 15a, 15b, 16a, respectively.
16b.

According to this embodiment, the phase relationship is fixed as shown in FIG.

The present embodiment is configured as described above, and its operation will be explained below.

When an electric power source is added to the electric motor M19M2 to rotate in opposite directions, the first rotating shaft 1
5a and 15b start rotating.

That is, one first rotating shaft 15a starts to rotate clockwise in FIG. 3, and the other first rotating shaft 15b starts rotating counterclockwise.

On the other hand, large diameter gears 24a, 24b and small diameter gear 26 at
26b, the first rotating shaft 15at
The rotational force of 15b is transmitted to the second rotating shafts 16a and 16b, and the second unbalanced weight 8at8b is driven by the gear ratio of 2:1.
The first unbalanced weights 7a and 7b begin to rotate in opposite directions at a rotational speed twice that of the first unbalanced weights 7a and 7b.

However, due to differences in the characteristics of the electric motors M19 and M2 and differences in the frictional force between the V-belt boots, the rotating shafts 15a and 15b and 16a and 16b are disconnected immediately after the power is turned on.
do not rotate synchronously at the same speed, and a combined centrifugal force in the direction perpendicular to the The opposite side vibrates in the vertical direction S.

That is, the leaf springs 30a and 30b exhibit rigidity in the longitudinal direction, that is, the elastic constant is extremely large, but
Since it is easy to bend in a direction perpendicular to this longitudinal direction, the vibration mechanism 6 can vibrate relative to the trough 1 in this direction.

On the other hand, the vibration force is also directly transmitted to the trough 1 in the X direction via the leaf springs 30a and 30b, and the vibration mechanism 6 vibrates together with the trough 1 in the X direction as well.

On the other hand, as the speeds of the rotating shafts rise to a predetermined rotational speed determined by the characteristics of the electric motor M In other words, the electric motor Ml? A mechanical synchronizing force is applied to M2, and eventually the electric motors M19M2 rotate synchronously in opposite directions at the same speed and in the same phase.

Regarding the above-mentioned synchronization power, for example, see Magazine 1 Yaskawa Electric, published July 1960, No. 2, No. 95, pages 274-28.
Page 2, 1 Uras Motor; Magazine 'OHM, April 1960 issue, pages 107 to 112, 1 Oscillating electric motors and their applications; 1 Transactions of the Japan Society of Mechanical Engineers, J3 No. 234 (Showa 4l);
-2) Self-synchronization of single-vibration machines on pages 184 to 193 has been theoretically proven, but if this is to be further implemented, the vibration mechanism 6 is connected to a pair of mounting brackets 10a. , 10b, and a rotating shaft 15ay supported thereon.
16ay 15av 16bs Unbalanced weight fixed to these rotating shafts 7at 8at 7bt 8b
1 Electric motor Mlt fixed to bracket lea, 10b
A pair of mounting brackets 10a and 1 are made of M2, etc.
0b are integrated via members 34 and 3B.

That is, the mounting brackets lea and 10b vibrate together.

This vibration in the X direction causes the unbalanced masses 7a, 8a, 7b to
, 8b act in opposite directions but in a synchronous manner.

That is, the electric motors M19 and M2 rotate synchronously.

Thus, the rotating shaft 15a in a steady state. 15b, 16a, 1
6b rotates, and the rotational phases of the unbalanced weights 7a, 7b, 8a, and 8b in this steady state will be explained below.

That is, as shown in FIGS. 6A to 6D, when one first unbalanced weight 7a rotates 90 degrees clockwise from the rotational phase shown in FIG. 6A, the other first unbalanced weight 7b rotates in the opposite direction. The second unbalanced weight 8a rotates 90 degrees clockwise, and the second unbalanced weight 8b rotates 180 degrees counterclockwise.
is rotated 180 degrees clockwise and becomes the state shown in FIG. 6B.

Similarly, one of the first unbalanced weights 7a is rotated 90 degrees clockwise.
When the first unbalanced weight 7a rotates once, the other unbalanced weights 7b, 8a, 8b take the rotational positions shown in FIGS. 6C and 6D, and when one first unbalanced weight 7a rotates once clockwise, The first unbalanced weight 7b rotates once in the counterclockwise direction, and the second unbalanced weights 8a and 8b rotate twice in opposite directions.
The unbalanced weights 7a, 7b, 8at8b each take their original rotational positions shown in FIG. 6A.

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

Note that the first unbalanced weight 7a. 7b is powered by two unbalanced weights of the same shape, as shown in Figure 4.
When one unbalanced weight 7a, 7b (however, the mass is twice that of one) is fixed at the center between two unbalanced weights as shown in Fig. 4. Since the sum of each resultant force is the same as in the case of two pieces, for convenience, in the following explanation of the resultant force, it is assumed that there is only one first unbalanced weight 7at7b.

That is, in the rotational phase shown in FIG. 6A, the centrifugal force F1 acting on the center of gravity G□, G2 of the first unbalanced weights 7a, 7b
．． F2 is equal in size and opposite in direction, and similarly centrifugal force f1 acts on the center of gravity g1° of the second unbalanced weight 8a*8b.
．． Since f2 is also equal in size and opposite in direction, the resultant force in the direction (Y direction) perpendicular to the direction X of the trough is zero, and the component in the direction
Since it is zero for 8a and ab, the resultant force in the X direction (horizontal direction) is also zero.

Next, in the rotational phase shown in FIG. 6B, the second unbalanced weight 8a
, 8b's centrifugal forces f□, f2 are opposite in direction and cancel each other out, but the centrifugal force F0., of the first unbalanced weight 7a*7b is F2
are each in the -X direction, and the resultant force F = F + F2 =
It becomes 2F 1.

However, since the Y direction components are each zero, the first unbalanced weight 7ag7bs, the second unbalanced weight 8a,
The resultant force of the centrifugal force in the Y direction of 8b is zero.

Similarly, it can be seen that in the rotational phases of FIGS. 6C and 6D, the resultant force of the centrifugal forces of the unbalanced weights 7a, 7b, 8a, and 8b in the Y direction is zero.

This can be explained with respect to a general rotational phase as follows.

That is, as shown in FIG. 7, the rotational phase of the sand diameter is considered in terms of time from the rotational phase shown in FIG. 6A.

Centrifugal force F of the first unbalanced weights 7a and 7b in this phase
The X-direction components of □ and F2 are −Fisinωt and −, respectively.
F2sinωt (however, ω represents the angular velocity, so the resultant force);'=-F□sinωt-F25in
ωt=−i1sinωt.

Further, the centrifugal force f1 of the second unbalanced weights 8a and 8b. f2 X
The direction components are f□5in2ωt and f2sin>, respectively.
6) Since t, their resultant force f = f1sin
2ωt +f2sin2ωt =2f1sin2ωt.

In the end, the resultant force in the X direction of the centrifugal force of the unbalanced weights 7at 7bt 8at 8b Fx = F + f = -S゛□s
inωt+ga□5in2ωt, which is the vibration mechanism 6
is added to trough 1.

Also, the centrifugal force F of the first unbalanced weights 7a and 7b, Y of F2
The direction components are −F1CO8ωt and F2CO3ωt, respectively.
Therefore, their resultant force F knee F1CO3ω is 10F2CO3ω1=0.

Further, the centrifugal force f1 of the second unbalanced weights 8a and 8b. Y of f2
The direction components are −f1CO32ωt and f2CO32, respectively.
Since ωt, their resultant force f=-f1CO82ω
t+f2cO52ωt=0.

Therefore, the resultant force Fy in the Y direction of the centrifugal force of the unbalanced weights 7a, 7b9, 8a, and ab is always zero.

In the end, trough 1 has only the X direction, the above Fx = -2F
A composite sum of 1 sin ωt + 5 in 2 ωt is applied from the vibration mechanism 6 via the leaf springs 30a and 30b.

A graph of this resultant force is shown in FIG. 8A.

In addition, in the illustration, F□=2f1.

That is, as shown in FIG. 8A, the second unbalanced weight 8a,
The resultant force f in the X direction of the centrifugal force due to the first unbalanced weight 7ay7b changes sinusoidally with a period twice the resultant force F in the X direction of the centrifugal force due to the first unbalanced weight 7ay7b, and the graph that combines these is Fx. be.

The vibrating conveyor according to this embodiment constitutes a consistent quantity system in terms of vibration, and the elastic constant of the entire leaf spring 2 and the mass supported by these (total mass of the trough 1, vibrating mechanism 6, etc.) The resonant frequency of this mass system is determined by this, but if the elastic constant of the entire leaf spring 2 is made sufficiently small and the trough 1 is vibrated at a driving frequency higher than the resonant frequency, as is clear from vibrational theory, , the excitation force of trough 1 is 180
It vibrates with a phase difference of degrees.

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

This graph S is obtained by inverting the graphs f and F with respect to the horizontal axis t (time axis), and then combining them.

Note that for the graph S, the vertical axis represents length.

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

By repeating such periodic movements of the trough 1, the material on the trough 1, for example, the billet, is transferred in the X direction.

In other words, in the high-speed backward movement region between I and ■ in FIG. Slippage occurs between the material and the floor surface.

Next, in the low speed forward region between ■ and ■, trough 1
The material on the floor of trough 1 advances 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 Figures 3 and 4. For example, billets (iron material to be fed to the furnace) are used as the conveying material, 1 stroke is about 8Trr! R to set the rotational speed of the rotating shafts 15a, 15b to about 500,000 yen.

m, the material is transferred at a rate of approximately 1277 L/min.

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

FIG. 9 is a side view of the main parts of a vibrating conveyor according to a second embodiment of the present invention, in which the synchronizing leaf springs 30a and 30b of the above-mentioned embodiment are used.

In place of the connecting member C consisting of the mounting members 32 and 34, a connecting member C consisting of a pair of support shafts 40a, 40b, 42a, 42b and a pair of connecting bars 44ay44b is used.

Since the other parts are exactly the same as those in the above-described embodiment, corresponding parts are given the same reference numerals and a description thereof will be omitted.

That is, in FIG. 9, a pair of support shafts 40a, 40b are fixed to both side surfaces near the rear end of the trough 1, and the synchronization plate of the above embodiment is attached to the connecting part of the vibrating parts 6a, 6b in the vibrating mechanism 6. A pair of support shafts 42at42b are fixed to positions corresponding to the spring mounting plate 34 so as to protrude laterally.

These support shafts 40at42a and 40b, 42b include
A pair of connecting bars 44at44b are pivotally connected at both ends thereof.

That is, the connecting bars 44a and 44b are connected to the support shaft 40at40.
b and 42a, 42b so as to be rotatable.

When power is applied to rotate the induction motor M□9M2 in opposite directions as in the first embodiment, in the initial state, the vibration mechanism 6 moves in the longitudinal direction of the trough 1, that is, in the direction Y perpendicular to the X direction. oscillates relative to trough 1.

On the other hand, the connecting bars 44a, 44 are also connected to the vibration mechanism 6 in the X direction.
Vibration force is applied via b, and the trough 1 and the vibration mechanism 6 vibrate integrally in the X direction.

For this reason, a synchronizing force is generated in the vibrating parts 6a and 6b, and as shown in FIG. 5, the first unbalanced weights 7a and 7b and the second A steady state is obtained in which the two unbalanced weights 8a and 8b rotate at the same speed in synchronization with each other in opposite directions.

Thereafter, the trough 1 vibrates in the X direction as shown in FIGS. 8A and 8B.

In addition, in the initial state immediately after the start of exercise, the connecting bar 44
a and 44b perform rocking motion around the support shafts 40a and 40b as shown by the broken lines in FIG. 9, and as a result, the vibration mechanism 6 vibrates in the direction perpendicular to the , this amplitude δ is normally on the order of 21, and is exaggerated in the figure.

Similarly, in the first embodiment, the amplitude of vibration in the vertical direction after the start of movement until reaching a steady state is about 20 rrrm.

FIGS. 10 and 11 show a third embodiment of the invention, and are a side view and a plan view of the main parts, respectively.

The above embodiment differs from the above embodiment in the connecting member C that connects the trough 1 and the vibration mechanism 6, but is otherwise the same, so parts corresponding to the above embodiment are given the same reference numerals.
Their explanation will be omitted.

10 and 11, a reinforcing member 46 is fixed to the rear end of the trough 1 with bolts, and a connecting bracket 48, which will be described in detail below, is fixed to this by welding.

That is, in the connecting bracket 48, a pair of mutually parallel rubber bushing mounting plates 50a and 50b are attached to the reinforcing member 46.
It is fixed by welding.

On the outer surfaces of the rubber bush mounting plates 50a and 50b, outer cylindrical parts 52a and 52b and ring-shaped rubber parts 54a and 54 are provided, respectively.
A rubber bushing consisting of b is fixed.

Both ends of a connecting rod 58 are fixed to the center holes of these rubber bushings as shown in FIG.

This connecting rod 58 has a pair of connecting plates 5 of S゛ triangle.
6a and 56b are fixed in parallel by welding at the top of each.

The pair of connecting portions 56a*56b are connected to the vibration mechanism 6 at their bottom portions.
Mounting bracket 1 for vibrating parts 6a and 6b on the front side of
It is also fixed to a common mounting plate 60 of 0a and 10b by welding.

In addition, as shown clearly in FIG. 11, the connecting rod 58 is
The rubber bushings are fixed to the center holes of the rubber bushes 54a*54b through openings formed in the mounting plates 50a and 50b,
The diameter of this opening is sufficiently larger than the diameter of the connecting rod 58.

The connecting member C between the trough 1 and the vibration mechanism 6 of this embodiment is configured as described above.

When power is applied to rotate the induction motor M19M2 in opposite directions as in the above embodiment, in the initial state, the vibration mechanism 6 is moved relative to the trough 1 in the longitudinal direction of the trough 1, that is, in the direction perpendicular to the X direction. Vibrate.

On the other hand, the connecting plate 56av56b1 is also connected to the vibration mechanism 6 in the X direction.
A vibration force is applied via the connecting rod 58 and the rubbers 54a and 54b, and the trough 1 and the vibration mechanism 6 vibrate integrally in the X direction.

For this reason, a synchronizing force is generated in the vibrating parts 6a and 6b, and eventually the rotating shaft 15a is moved as clearly shown in FIG.

A steady state is obtained in which the first unbalanced weights 7a and 7b and the second unbalanced weights 8a and 8b, which are fixed to 15b, 16a, and 16b, rotate in opposite directions synchronously and at the same speed.

Thereafter, the trough 1 vibrates in the X direction as shown in FIGS. 8A and 8B.

In addition, in the initial state immediately after the start of the movement, the ring-shaped rubber 54a, 54b of the rubber bush is twisted in its circumferential direction, so that the connecting plates 56a, 56b, that is, the vibration mechanism 6, vibrates as shown by δ in FIG. .

On the other hand, since the ring-shaped rubbers 54a and 54b have a large elastic constant in the X direction, that is, in the radial direction, they directly transmit the vibration force of the X direction component from the vibrating mechanism 6 to the trough 1. and vibrate integrally in this direction.

Note that since there is a considerable distance from the connecting rod 58 to the vibrating mechanism 6 as shown, the vibrating mechanism 6 can vibrate in the vertical direction S (the magnitude of δ is determined according to the above-mentioned implementation). As in the example, the figures are exaggerated.

) Figures 12 and 13 show a fourth embodiment of the present invention,
They are a side view and a plan view of essential parts, respectively.

This embodiment differs from the above embodiments in the connecting member C that connects the trough 1 and the vibration mechanism 6, but is otherwise the same, so parts corresponding to those in the above embodiments are designated by the same reference numerals. , their explanation will be omitted.

The connecting member C of this embodiment will be explained below.

In the figure, a reinforcing member 62 is fixed to the rear end of the trough 1 with bolts, and a rectangular mounting plate 64 is fixed thereto by welding.

On the other hand, on the front side of the vibration mechanism 6 are mounting brackets) 10a,
A rectangular mounting plate 66 is commonly fixed to 10b by welding.

Between the mounting plates 64 and 66, a pair of rubber plates 70a and 70b (not shown) are provided near both ends of the plates.
Fixed by

These rubber plates 70a and 70b are made by gluing a rectangular rubber piece between two rectangular iron plates in a sandwich-like manner, as is well known, and have elasticity in the shear direction, that is, in the vertical direction Y in FIG. Although the constant is relatively small,
In the compression direction, that is, in the horizontal direction X in FIG. 12, the elastic constant is extremely large.

A further pair of rubber plates 72a and 72b similar to these rubber plates 70a and 70b are attached to both ends of the mounting plate 66,
Band-shaped rubber plate mounting plates 6 arranged corresponding to both ends
8a and 68b by bolts (not shown).

The mounting plate 64 and the rubber plate mounting plates 68a and 68b are provided with a coupling member 74 having a U-shaped cross section at their upper and lower ends.
at74b, 76a, 76b are fixed with bolts etc., thereby connecting members 74 at 74b, 76
Mounting plate 64 and plate rubber mounting plate 68 via a, 76 b
a and 68b are integrated.

The connecting member C of this embodiment is constructed as described above.

In this embodiment as well, the electric motor M1
When power is applied to rotate 9M2 in opposite directions, the vibration mechanism 6 vibrates in the vertical direction Y relative to the trough 1 in the initial state.

On the other hand, in the horizontal direction
Since the elastic constant of 2b in the compression direction is extremely large, it is directly transmitted to the trough 1 via the rubber plates 70a, 70bt 72at 72b, and the vibration mechanism 6 and the trough vibrate integrally in the horizontal direction X.

In this embodiment as well, the vibration mechanism 6 vibrates in the vertical direction Y in the initial state or transient state from the start of driving to the steady state, as in the above-mentioned embodiments, but it also vibrates in the horizontal direction X. Rotating shaft 15 of vibrating parts 6a, 6b
A synchronizing force acts on at 15 b and 16 at 16 b, resulting in a steady state as shown in FIGS. 6A to 6D.

In the steady state, the trough 1 moves forward at a low speed and backward at a high speed, as described with reference to FIGS. 8A and 8B.

As a result, the material on the floor of the trough 1 is slid forward.

Although the vibrating conveyor according to each embodiment 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 7at7b
are made up of two unbalanced weights, but of course they may be made up of one unbalanced weight like the second unbalanced weights 8a and 8b, and the shape is also semicircular. Not limited to shape.

However, as in the above embodiment, the first unbalanced weight 7
If at7b were each made up of two unbalanced weights, the stress distribution on the rotating shafts 15a and 15b would be more preferable.

In this respect, the first unbalanced weights 7a, 7b may be configured to include a larger number of unbalanced weights.

The same can be said of the second unbalanced weights 8a and 8b.

In this specification, the eccentricity of an unbalanced weight means (distance from the axis of the rotating shaft to the center of gravity G or g of the unbalanced weight) x (mass of the unbalanced weight), and the first When the unbalanced weight or the second unbalanced weight is composed of a plurality of unbalanced weights, the sum of their eccentricities is the eccentricity of the first unbalanced weight or the second unbalanced weight.

Also, the rotation axis 1 of the unbalanced weights 7at 7b, 8a, 8b
5a, 15bt, 16at, and 16b are not limited to the above-described embodiments.

In other words, in the embodiment, the positions shown in FIG. Two unbalanced weights 7av 7b, 8a, ab are:
When the rotating shafts 15at, 15b, 16a, and 16b are rotated by the drive of the electric motor M□9M2, the centrifugal force component in the direction perpendicular to the direction X of the trough 1 in a steady state is as follows: 7b-8a,
8b should be fixed so that they cancel each other out.

For example, the first unbalanced weight 7a is placed at the angular position shown in FIG.
, 7b may be fixed to the rotating shafts 15a, 15b.

In this case, Y of centrifugal force F□ of one first unbalanced weight 7a
As is clear from the figure, the direction component is -F1sinβ, and the Y-direction component of the centrifugal force F2 of the other first unbalanced weight 7b is F25inβ, and it is clear that they cancel each other out in the Y direction. It is.

The second unbalanced weights 8a*8b are the same as those described in the above embodiment.

From the state shown in FIG. 14, it is clear that when rotated as described above, the Y-direction component is zero at any rotational phase.

Furthermore, in the embodiment described above, the first unbalanced weight 7a.

7b and the second unbalanced weight 8a*8b rotation speed ratio is 2:1
However, it is clear that a similar periodic asymmetric trough motion can be obtained even if the ratio is set to 3:1 or 4:1.

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 1 - frequency 70 (2
) If the angle of inclination of the leaf spring 2 with respect to the vertical direction is 20 degrees at 7 minutes, the material is transferred without jumping movements.

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.

Further, in the above embodiment, the trough 1 is supported on the base 3 by the leaf spring 2, and the vibration mechanism 6 is supported by the coil spring 36.
However, instead of this, the trough 1 is suspended by a leaf spring 2 from a stationary body fixed to a part of the building, and the trough 1 is suspended from a stationary body fixed to a part of the building by means of a coil spring of the vibration mechanism 6. Even if the structure is suspended, the same effect as explained in the above embodiment can be obtained.

In addition, in the vibration mechanism 6 of the above-described embodiment, the vibration part 6a,
Although the configuration is such that the electrodes 6b are arranged in the vertical direction, they may be arranged in the horizontal direction instead.

In this case, the connecting member C is rotated 90 degrees around the X direction of the trough 1 from the position shown in each example so that it can vibrate laterally (in a horizontal plane in a direction perpendicular to the X direction of the trough 1). It can be placed in a rotated position.

Since the present invention is constructed as described above, the structure is simple, and although the trough advances slowly in the conveying direction,
Since the return is rapid, unlike the conventional method in which the transported object jumps while colliding with the trough, the material slips (see Figure 8B), and there is no noise from the transported material, and the material does not get stuck. It doesn't cause any blemishes or blemishes, and it doesn't raise 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 the first 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, and Fig. 5 is - A sectional view in the V-line direction, FIGS. 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 illustrate the operation in the same manner. This is a graph to explain. Figure 9 shows a second embodiment of the vibrating conveyor of the present invention, a side view of the main parts thereof, and Figures 10 and 11 show a third embodiment of the vibrating conveyor of the present invention, side views of the main parts. 12 and 13 show a fourth embodiment of the vibrating conveyor of the present invention, and FIG. 14 shows a side view and a partially sectional plan view of the same essential parts. FIG. 3 is a side view of an unbalanced weight showing a modification of the mounting position of the unbalanced weight to the rotating shaft. In the figure, 1...trough, 2...
・Plate spring, 7a, 7b...First unbalanced weight, 8a, 8b...Second unbalanced weight, 24
a, 24 b, 26 a. 26b...Gear, Ml, M2...Induction motor, 30at3ob---,, synchronization plate spring, 40a, 40b. 42a, 42b... Support shaft, 44a, 44b.
...Connection bar, 48 ...Connection bracket, 52av52b ...Outer cylinder, 54a, 54b.
...Rubber, 58...Connection rod, 70
a, 70 b, 72 a, 72 b...
...Plate rubber.

Claims (1)

[Scope of utility model registration request] A vibrated part extending in a predetermined direction, an elastic member that supports the vibrated part so as to vibrate in the predetermined direction, an excitation mechanism, and an excitation mechanism that supports the excitation part in the predetermined direction. a synchronization connection that connects the vibrating mechanism to the vibrating part so as to vibrate integrally with the vibrating part and vibrate relative to the vibrating part in a direction perpendicular to the predetermined direction; The vibration mechanism has a first unbalanced weight with a large value of (eccentric radius x mass) and a second unbalanced weight with a small value of (eccentric radius x mass); a first rotating shaft and a second rotating shaft to which the weights are respectively fixed; these rotating shafts are coupled so as to rotate in opposite directions and the front second rotating shaft at a speed that is an integral multiple of the first rotating shaft; a large-diameter gear fixed to the shaft end of the first rotating shaft, and a small-diameter gear meshing with the large-diameter gear and fixed to the shaft end of the second rotating shaft; an electric motor for driving; The unbalanced weights are fixed to the rotating shaft so as to be at the same angular position in opposite rotational directions, and the first and second unbalanced weights of the vibrating section on one side are fixed to the rotating shaft so as to be at the same angular position in opposite rotational directions. When the first and second unbalanced weights of the vibrating unit are started to be driven so as to rotate in opposite directions, the vibrating mechanism vibrates in a direction perpendicular to the predetermined direction. The first and second unbalanced weights of one of the vibrating parts are synchronized to rotate in opposite directions at the same speed and in the same phase, thereby perpendicular to the predetermined direction of the vibrating part. A vibrating conveyor, characterized in that centrifugal force components in the directions cancel each other out in the pair of vibrating sections.