JPS5913405B2 - 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.

In the conventionally widely known vibrating conveyor, a diagonal vibration force is applied to the transfer surface on which various materials are placed, causing the materials on the transfer surface to make a jumping motion (repeatedly moving in one direction). being transported.

In this case, the vibration force changes sinusoidally over time, and the material periodically repeats the jumping motion and impinges on the transport surface.

However, when metal materials such as bolts, nuts, billets, etc. are transported by the above-mentioned vibrating conveyor, the material repeatedly jumps, so when it collides with the transport surface (which is often made of metal), , generate noise and, in some cases, become a pollution problem.

In addition, when fragile materials such as biscuits and senbei are transported using a vibrating conveyor, periodic collisions with the transport surface may cause problems such as "cracks" and "breaks", and this is due to the nature of the material of the transport surface and the vibration conditions. 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.

There is also a vibrating conveyor called a reciprocating conveyor, which transfers the material only by sliding motion, without giving jump motion to the material being conveyed, but in this case, a crank mechanism or complicated mechanical structure is used as the drive unit. Not only was the cost high, but there were also difficulties in providing vibration protection to the foundation and ground.

In order to eliminate the above-mentioned drawbacks of the conventional vibrating conveyor, the present applicant previously proposed the following vibrating conveyor in Japanese Patent Application No. 53-164167.

In other words, this vibrating conveyor includes a vibrating part extending in a predetermined direction, an elastic member supporting the vibrating part so as to be able to vibrate substantially in the predetermined direction, and a vibrating mechanism. The excitation mechanism is configured to vibrate integrally with the vibrated part in the direction, and vibrate relative to the vibrated part in a direction perpendicular to the predetermined direction. The vibration mechanism is composed of a first and second unbalanced weight having different degrees of eccentricity, a rotating shaft for fixing these unbalanced masses, and a connecting member that connects these rotating shafts to each other. It consists of a pair of vibrating parts each having a drive source and a gear mechanism coupled to rotate at a predetermined speed ratio in opposite directions, and the driving source is connected to the first and second components of one of the vibrating parts. When the balanced weight starts to be driven so as 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. After that, the first and second unbalanced weights of one of the vibrating parts rotate at the same speed in opposite directions to the first and second unbalanced weights of the other vibrating part. In this case, the first and second unbalanced weights are synchronized so that centrifugal force components of the vibrating part perpendicular to the predetermined direction cancel each other out in the pair of vibrating parts. It is characterized in that weights are fixed to each of the rotating shafts.

The above-mentioned vibrating conveyor solves the above-mentioned problems of noise and material breaking and breaking, and since it is not a resonant type, it has a simple structure and is not only easy to design. , While using the above-mentioned elastic member with a low spring constant, it is possible to create a structure that can support the vibrated part, resulting in a good vibration-proofing effect (the overall structure is also lightweight and costs are reduced). be able to.

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.

An object of the present invention is to achieve the above-mentioned effects and further improve the material transfer speed to the maximum.

According to the present invention, the above object is to create a vibrated part (for example, a trough with a linear cross section and a rectangular plan view) that extends in a predetermined direction.
an elastic member (e.g., a leaf spring) that supports the vibrated part so as to be able to vibrate in substantially a predetermined direction; and an excitation mechanism that is integral with the vibrated part in the predetermined direction. and a connecting member (for example, a leaf spring) that connects the vibrating mechanism to the vibrated part so as to vibrate relative to the vibrated part in a direction perpendicular to the predetermined direction. , the vibration mechanism includes first and second unbalanced weights having different degrees of eccentricity, rotating shafts to which these unbalanced weights are respectively fixed, and rotating these rotating shafts in mutually opposite directions.
It consists of a pair of vibrating parts each having a gear mechanism and a driving source coupled to rotate at a speed ratio of 2, and each of the driving sources is connected to a first and a second unbalanced weight 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, and then , the first and second unbalanced weights of one of the vibrating parts rotate at the same speed in opposite directions to the first and second unbalanced weights of the other vibrating part, respectively. In this case, the first and second unbalanced weights are placed at angular positions such that centrifugal force components of the vibrating part in a direction perpendicular to the predetermined direction cancel each other out in the pair of vibrating parts. are respectively fixed to the rotating shaft, and the centrifugal force component of the first unbalanced weight of the both vibration parts in the predetermined direction is expressed as A sin ωt, and the centrifugal force component of the second unbalanced weight of the second unbalanced weight is The centrifugal force component in the direction Bs1
When expressed as n (2ω is one α) (where ω is the angular velocity,
t is time, A and B are constants determined by the angular velocity and eccentricity of the unbalanced weight, respectively, and α is determined by the relative mounting angle position of the first unbalanced weight with respect to the second unbalanced weight. (the force is determined by the direction of rotation of the first and second unbalanced weights), the first and second unbalanced weights are such that α is approximately 0° or 180°. This is achieved by means of a vibrating conveyor, characterized in that it is fixed to said rotating shaft in each angular position.

The vibrating conveyor configured as described above allows a sufficiently high material transfer speed to be obtained, and also provides the above-mentioned effects.

Hereinafter, details of the present invention will be explained for each embodiment with reference to the drawings.

1 to 6 show a first embodiment of the present invention.

In the figure, the conveying trough 1 is made of steel, for example, and has a 1"-shaped cross section, and is rectangular in plan view. Materials to be conveyed (for example, billets and bolts) are 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 approximately equal intervals, and the leaf springs 2 are attached to these 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 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 and 30b are fixed to both ends of these mounting members 32 and 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 stably supported and further supported on the base 3 by a plurality of coil springs 36.

The vibration mechanism 6 according to this embodiment includes a pair of vibration parts 6a.

6b, each rectangular parallelepiped-shaped mounting bracket)
10a and 10b are fixed to each other via a spacer plate 38 and the above-mentioned synchronizing leaf spring mounting plate 34.

Bearing housings 11a, 11b are provided on both sides of the mounting brackets 10a, 10b.

12a, 12b, 13a, 13b and 14a.

14b is fixed and the bearing housings 11a and 1
One first rotating shaft 15a is supported at both ends by bearings 11b and 12b, and the other first rotating shaft 15b is supported at both ends by bearings 11b 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 housings 13b and 14b.

As shown in FIG. 3, the first unbalanced weights 7ay 7b each have a substantially semicircular shape.
is fixed with bolts etc.

The first unbalanced masses 7ay, 7b in this embodiment each consist of two identical unbalanced masses, as clearly shown in FIG.

Furthermore, as clearly shown in FIG. 3, the second rotating shafts 16a, 16b have a second unbalanced weight 8a, which has a smaller diameter than the first unbalanced weights 7a, 7b, but also has a substantially semicircular shape. 8b is fixed with a bolt 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.

According to the present invention, the first and second unbalanced masses 7a, 8a of one vibrating section 6a and the second and second unbalanced masses 7b, 8b of the other vibrating section 6b. are rotational axes 15a, 16a, 15b at mutually symmetrical angular positions, respectively.
, 16b, and the first and second unbalanced weights 7a, 8a of one of the vibrating parts 6a are fixed to the respective rotation axes 15a, 16 in the direction perpendicular to the longitudinal direction X of the trough 1.
the second and second unbalanced weights 7b of the other vibrating section 6b, which are fixed to the rotating shafts 15a and 16a so as to be located below a;
8b is fixed so as to be located below the respective rotating shafts 15b, 16b in a direction perpendicular to the longitudinal direction X of the trough 1.

A pair of induction motors M12M2 (for example, rated at 200 V
, 200w 4 poles) are fixed.

A small diameter boo')-18a is fixed to one end of the rotating shaft of one induction motor M1, a large diameter boo')-20a is fixed to one end of the first rotating shaft 15a, and these pulleys 18a , 20a are wound with a V-belt 22a.

Similarly, the above-mentioned Boo! is also applied to one end of the rotating shaft of the other induction motor M2. j = 18a is a small diameter boo of the same shape! j-18
b is fixed, and a large diameter pulley 20 having the same shape as the above-mentioned pulley 20a is attached to one end of the other first rotating shaft 15b.
b is fixed, and a V-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 small-diameter gears 26a, 24b are fixed to the other ends of the pair of second rotating shafts 16b, 16a.
6b is fixed.

Large diameter gears 24a, 24b and small diameter gears 26a, 2
The tooth number ratio of 6b is 2:1 and they mesh with each other.

Unbalanced weight 7ay 7b, 8ay sb is electric motor M1
9M2, and generate centrifugal force. According to the present invention, the synchronizing force after driving is applied to the rotating shafts 15a of the respective vibrating parts 6a and 6b.

15b, 16a, 16b, one of the vibrating parts 6a
A steady state in which the first and second unbalanced weights 7a and 8a of the other excitation section 6b rotate synchronously at the same speed in opposite directions with the second and second unbalanced weights 7b and 8b of the other excitation section 6b. state, the resultant force of the component in the direction perpendicular to the X direction (horizontal direction) of these centrifugal forces is always zero as described later, and according to this example, the first imbalance Weight 7a, 7
b and the second unbalanced weights 8a, 8b are in the same direction perpendicular to the longitudinal direction X of the trough 1, that is, the center of gravity G0 of the first unbalanced weight 7a and the second unbalanced weight 8a The center of gravity g1 of the first unbalanced weight 7b and the center of gravity g2 of the second unbalanced weight 8b are located directly below the respective rotational axes 15a and 16a, and the center of gravity g2 of the other first unbalanced weight 7b and the second unbalanced weight 8b are located directly below the respective rotational axes 15a and 16a.
The unbalanced weights 7a7b, 8a, 8b are located at angular positions directly above the rotating shafts 15at15b, respectively.
.

16a and 16b.

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

When power is applied to the electric motors M, M2 to rotate in opposite directions, the first rotating shaft 15 is
a and 15b begin to rotate.

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 gears 26a, 26
The rotational force of the first rotating shafts 15a, 15b is transmitted to the second rotating shafts 16a, 16b due to the engagement with the first rotating shafts 15a, 15b, and the second unbalanced weights 8a, 8b are transferred to the first unbalanced weights due to the gear ratio of 2:1. The weights 7ay and 7b begin to rotate at twice the rotational speed of the weights 7b in opposite directions.

However, electric motor M1. Due to the difference in the characteristics of M2 and the difference in the frictional force between the V-belt and the pulley, the rotating shafts 15a and 15b and 16a and 16b are disconnected immediately after power is turned on.
do not rotate synchronously at the same speed, and a synthetic centrifugal force component in the direction perpendicular to the Vibrate vertically.

That is, the leaf springs 30 a and 30 b exhibit rigidity in their longitudinal direction, that is, their elastic constants are extremely large, but they are easy to bend in a direction perpendicular to this longitudinal direction, so the excitation mechanism 6 is bent in this direction. It can vibrate relative to the trough 1.

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 speed of these rotating shafts rises to a predetermined rotational speed determined by the characteristics of the electric motor M19M2, as can be theoretically proven, the vibration of the above-mentioned vibration mechanism 6 causes
A mechanical synchronizing force acts on the rotating shafts 15a, 15b and 16a, 16b, that is, the electric motor M12M2, and eventually the electric motor M19M2 rotates synchronously at the same speed in opposite directions.

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

That is, as shown in FIGS. 4A to 4D, when one first unbalanced weight 7a rotates 90 degrees clockwise from the rotational phase shown in FIG. 4A, the other first unbalanced weight 7b rotates. One second unbalanced weight 8a rotates 180 degrees counterclockwise, and the other second unbalanced weight 8a rotates 90 degrees counterclockwise.
b is rotated 180 degrees clockwise to the state shown in FIG. 4B.

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, 8a8b take the rotational positions shown in FIGS. 4C and 4D, and when one first unbalanced weight 7a rotates once clockwise, the other The unbalanced weight 7b rotates once in the counterclockwise direction, and the second unbalanced weight 8ay sb rotates twice in the opposite direction.
The unbalanced weights 7at7b, 8a, 8b each take their original rotational positions shown in FIG. 4A.

Thereafter, periodic rotational movements shown in FIGS. 4A to 4D are performed.

Note that the first unbalanced masses 7a and 7b each consist of two unbalanced masses having the same shape as shown in FIG.
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 Figure 2. Since the sum of each resultant force is the same as when each resultant force is composed of two, for convenience, in the following description of the resultant force, the first unbalanced weights 7a and 7b will be explained as being composed of one.

That is, in the rotational phase shown in FIG. 4A, the center of gravity G1. of the first unbalanced masses 7a, 7b. Centrifugal force F1 acting on G2
．． F2 is equal in size and opposite in direction, and centrifugal forces f□ and f2 acting on the center of gravity grt g2 of the second unbalanced weights 8a and 8b are also equal in size and opposite in direction, so the direction of the trough is The resultant force in the vertical direction (Y direction) is zero, and the component in the direction
7 b t 8 a.

Since it is zero for 8b, similarly the X direction (horizontal direction)
The resultant force of is also zero.

Next, in the rotational phase shown in FIG. 4B, the first unbalanced weight 7a
, sb centrifugal force f1. The directions of f2 are opposite and cancel each other out, but the centrifugal forces F, F2 of the first unbalanced weights 7a and 7b are each in the -X direction, and the resultant force F=F1+F2=2 F
.

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

Similarly, it can be seen that in the rotational phases of FIGS. 4C and 4D, 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 the rotational phase of the -carrier as follows.

That is, as shown in FIG. 5, consider the rotational phase seconds after the rotational phase shown in FIG. 4A.

Centrifugal force F of the first unbalanced weights 7a and 7b in this phase
1. ．． The X-direction component of F2 is −F1sinωt, respectively.
, -F2 sinωt (where ω represents the angular velocity), so their resultant force F=-F1 sinωt-F
sinωt=−2F1 sinωt.

Further, the centrifugal force f1 of the second unbalanced weights 8a and 8b. f2 X
The direction components are flsin 2ωt and f2 5i, respectively.
Since n2ωt, their resultant force f=f15in2
ωt+f2 5in2ωt=2f 1 sin 2ωt
It is.

In the end, the centrifugal force of unbalanced weights 7a, 7b, 8a, and ab
Resultant force in the direction Fx ”'F + f = -2”5
sincc+t+2f, 5in2ωt, which is applied to the trough 1 by the vibration mechanism 6.

Moreover, the centrifugal force F1 of the first unbalanced weights 7a and 7b. F2 Y
The direction components are −FI CO8ωt and F2cosω, respectively.
t, so their resultant force F=-F1 cosωt
+F2cosω1=0.

Also, the centrifugal force f of the second unbalanced weights 8a and 8b, Y of f2
The direction components are −f1 cos2ωt and f2 c, respectively.
Since os2ωt, their resultant force f=-f1co
s2ωt+f2 cos2ω1=0.

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

After all, trough 1 has only the X direction, as described above = -2F1s
A resultant force of inωt+2f15in2ωt is applied from the vibration mechanism 6 via the leaf springs 30a and 30b.

A graph of this resultant force is shown in FIG. 6A.

In addition, in the illustration, it is set as F□-2f1.

That is, as shown in FIG. 6A, the second unbalanced weight 8a,
The resultant force f in the X direction of the centrifugal force due to the first unbalanced weights 7a and 8b changes sinusoidally with a period twice as large as the resultant force F in the X direction of the centrifugal force due to the first unbalanced weights 7a and 7b, and the graph that combines them is It's to.

The vibrating conveyor according to this embodiment constitutes a one-mass system in terms of vibration, and the elastic constant of the entire leaf spring 2 and the mass supported by these (the total mass of the trough 1, the vibrating mechanism 6, etc.) The resonant frequency of this mass system (plate spring 3
The elastic constants of 0a and 30b are assumed to be infinite in the longitudinal direction, and the elastic constant of the coil spring 36 that supports the vibration mechanism 6 can be considered to be zero.

) is determined, 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 resonance frequency, it is clear from vibrational theory that the trough 1 will be affected by the excitation force. vibrates with a phase difference of 180 degrees.

Therefore, when excited with a resultant force as shown in FIG. 6A, the trough vibrates as shown in the graph shown by 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.

That is, in FIG. 6A, in the high-speed backward movement region between ■ and ■, only the trough 1 moves backward by overcoming the static friction force between the material and the floor surface of the trough 1, and the floor surface of the trough 1 Slippage occurs between the material above and the floor surface.

Next, in the low speed forward region between ■ and ■, trough 1
Almost all of the material on the floor of (very small in comparison).

That is, the trough 1 moves forward and backward as shown in FIG. 6B.

Due to the repetition of such phenomena, the material is transferred to the right on the floor surface of the trough 1 in FIG. 1 or 2.

For example, billet (iron material supplied to the furnace) is used as the conveying material, and the stroker of the trough 1 is about 8 mm, and the rotating shaft 15a,
When the rotation speed of 15b is approximately 1000 r, p, m,
The material is transported at a speed of approximately 12 m/min.

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

Next, changes in the excitation force F and the trough displacement S depending on the attachment angle positions of the second unbalanced masses 8a, 8b to the rotation shafts 16a, 16b relative to the first unbalanced masses 7a, 7b will be explained. .

Figure 7 shows a case where the mounting angle position of the second unbalanced masses 8a, 8b is set 45° in the opposite direction to the rotation direction of the first unbalanced masses 7a, 7b, away from the position shown in Figure 4A. shows.

In this case, the first and second unbalanced weights 7ay 7b
, 8a, 8b take the rotational positions shown in FIG. 8 after time t, and the respective X-direction resultant forces F and f are F=-2F1
sin ω and f=−2f1 cos(2ωt+
), therefore, the total resultant force Fz = F + f = -2F1
sinωt-2f1cos (2ω is 10-).

If these are shown in a graph, it will look like Figure 9.

In the illustration, F1=2f1.

The trough displacement S is obtained by inverting the excitation force F with respect to the time axis t, but in this case as well, the vertical axis X represents the length with respect to the trough displacement S, as in the case of FIG. 6A ( (Same for the graphs below).

As can be seen by comparing Figures 6A and 9, the excitation force and trough displacement S change in almost the same way, but they differ in detail, so the material transport speed is approximately the same or less. It is estimated that the following is true (because there is a partial high-speed forward movement region in the sections ■ to ■).

As a result of the experiment, as shown in FIG.
6a and 16b, and the conditions were the same as in the previous case, the material transport speed was 9 m/min.

That is, the transport speed decreased from 12 m/min to 9 m/min.

Next, FIG. 10 shows that the second unbalanced masses 8a, 8b are installed at an angle of 90 degrees in the opposite direction to the rotation direction of the first unbalanced masses 7a, 7b, away from the position shown in FIG. 4A. Indicates the case where

In this case, the first and second unbalanced weights 7a, 7b, 8
After time t, a and 8b assume the rotational positions shown in FIG. 11, and their respective X-direction resultant forces F and f are F=-2F1si.
nω and f = 2f1 cos2ω・t, so the total resultant force FX =F+f=-2F1 sinωt-
2f1cos2ωt.

If these and the trough displacement S are shown in a graph, it will be as shown in FIG.

As can be seen from FIG. 12, in this case, the trough 1 remains at the forward position for a while, and the transfer speed from the forward position a to the reverse position a and from the reverse position to the forward position a are Similarly changes from the symmetry of the graph with respect to .

Therefore, it is assumed that the transport speed of the material is extremely low.

The results of the experiment were also negative.

Furthermore, FIG. 13 shows that the mounting angle position of the second unbalanced masses 8a, 8b with respect to the first unbalanced masses 7a, 7b is 135° in the opposite direction to the rotation direction thereof, away from the position shown in FIG. 4A. Indicates the case where

In this case, the first and second unbalanced weights 7a, 7b, 8
After time t, a and 8b assume the rotational positions shown in FIG. 14, and their X-direction resultant forces F and f are F=-2F.

sin ω and f−−2f1 5in(2ωt+−)
Therefore, the total resultant force F, =F+f=-2F1 si
nωt-2fl 5in (2ωt+).

If these and the trough displacement S are shown in a graph, it will be as shown in FIG. 15.

As can be seen from FIG. 15, in this case, the trough 1 moves from the forward position a to the reverse position at a relatively low speed, and from the reverse position to the forward position a at a relatively high speed. Moreover, when comparing Figures 9 and 15,
It can be seen that if the directions of the time axes are reversed, the two graphs match.

Therefore, it is assumed that the transport velocity of the material is the same in magnitude as in FIG. 9, although the direction is opposite.

As a result of the experiment, the transport speed was 8 m/min, which was almost the same as 9 m/min in the case of FIG. 9, although the direction was opposite.

Further, FIG. 16 shows that the second unbalanced weights 8a, 8b are attached to the first unbalanced weights 7a, 7b by 180° in the opposite direction to the rotational direction, away from the position shown in FIG. 4A. Indicate the case.

In this case, the first and second unbalanced weights 7a, 7b, 8
After time t, a and 8b assume the rotational positions shown in FIG. 17, and their X-direction resultant forces F and f are F=-2F.

sinω and f=-2f1 cos(2ω becomes 0-, so the total resultant force FX =F+f=-2F1 si
nω becomes -2f1 sin2ωt.

If these and the trough displacement S are shown in a graph, it will be as shown in FIG.

As can be seen from FIG. 18, in this case, the trough 1 moves from the forward position a to the reverse position at a relatively low speed, and from the reverse position to the forward position a at a relatively high speed. Moreover, when comparing FIG. 6A and FIG. 18, it can be seen that if the directions of the time axes are reversed, the two graphs match.

Therefore, it is assumed that the transport velocity of the material is the same in magnitude as in Figure 6A, although the direction is opposite.

As a result of the experiment, the transport speed was 13 m/min, which was almost the same as the 12 m/min in the case of FIG. 6A, although the direction was opposite.

In addition, FIG. 19 shows the case where the mounting angle position of the second unbalanced weights 8a, 8b with respect to the first unbalanced weights 7a, 7b is set 45° in the direction of rotation, away from the position shown in FIG. 4A. .

In this case, the first and second unbalanced weights 7a, 7b, 8
at sb has the rotational position shown in FIG. 20 after time t, and the respective X-direction resultant forces F and f are F=-2F
1 sin ω and f=+2f15in(2ωt+
), so the total resultant force FX =F+f=-2F,
sin ωt+2f, 5in (2°t+7)A becomes・2
1 and the trough displacement S are shown in a graph as shown in FIG.

As can be seen by comparing the graph in Figure 15 and the graph in Figure 21, the graphs of trough displacement S become the same if they are reversed with respect to the time axis t, so the transport speed is the same and the directions are mutually It turns out that the opposite is true.

Furthermore, in the above explanation, the rotation direction of the first unbalanced weight 7a is clockwise, therefore the rotation direction of the first unbalanced weight 7b is counterclockwise, and the rotation direction of the second unbalanced weights 8a, 8b is are counterclockwise and clockwise, respectively, but if these rotation directions are reversed, the graphs representing the excitation force F and trough displacement S can be obtained by reversing the above graphs with respect to the time axis t. can get.

Therefore, as shown in FIG. 4A, FIG. 7, FIG. 10, FIG. 13, and FIG. 16, the first and second unbalanced weights 7a7b,
8a, 8b are rotating shafts 15a, 15b, 16a.

It is clear that in each case fixed at 16b, the transport speed is the same as described above, but the transport direction is reversed.

The excitation force explained above can be generally expressed as follows.

That is, FX = Asin ωt±Bs1n(2ωt
-a) Here, A = 2F, , B = 2f1, and α is the direction opposite to the rotation direction of the second unbalanced weights 8a, 8b with reference to their mounting positions in Fig. 4A. It represents the deviation angle from the first unbalanced weights 7a, 7b.

Also, the symbols are unbalanced weights 7 a y 7 b, 8
It is determined by the rotation direction of a t8b.

For example, as shown in FIG. 4A, unbalanced weight 7 a y7b
, 8a and 8b are each fixed to the rotating shaft,
As is clear from Fig. 6A, the excitation force FX = A si
It is expressed as n ωt+B 5in (2(7) t −0).

When fixed as shown in Fig. 7, as is clear from Fig. 9, FX = A sin ω is 1 B 5 in (2 ω
-45°), and when fixed as shown in Figs. 10, 13, and 16, Figs. 12 and 15 respectively.
As is clear from Fig. 18, FX = A si
nωt + B sin (2GJ t −90°),
F, =A sin ωt+B 5in(2ωt −1
35°), FX = A sin ωt+ B 5in
(20) t −180° ).

Furthermore, as shown in FIG. 19, unbalanced weights 7ay 7b
, 8ay sb is fixed to the rotating shaft, the second
As is clear from Figure 1, FX = A sinωt + B
5 inches (expressed as 2ωt-1-45°).

That is, in the case of FIG. 19, the second unbalanced weights 8a, s
The mounting position of b is different from the position shown in Fig. 4A by 45° in the direction of rotation, so
The above α is negative.

In addition, unbalanced weights 7a, 7t>, 8a8b
When the direction of rotation is reversed from the above explanation, in each graph, the combined excitation force f
Since the graph representing
ω is 10 B 5in (ω is 1 α + π) = A sin ωt-
Bs1n(ωt-α).

As is clear from the above explanation, the maximum transport speed is α=0
It can be seen that it can be obtained at 180° or 180°.

Note that even when α=45° or 135°, a transport speed quite close to the maximum transport speed can be obtained as described above, so
In practice, it is sufficient to attach the unbalanced weight 7at 7bt8ay ab to the rotary firing α-〇 or α=180°.

The first embodiment of the present invention is configured as described above, and each embodiment to which the present invention is applied will be described below.

FIG. 22 is a side view of the main parts of a vibrating conveyor according to a second embodiment of the present invention.
A pair of support shafts 40a, 40 instead of the connecting member C consisting of
b, 42a, 42b and a pair of connecting bars 44a, 44b
A connecting member C consisting of the following is used.

Since the other parts are exactly the same as those of the above-described embodiment, corresponding parts are given the same reference numerals and explanations will be omitted.

That is, in FIG. 22, a pair of support shafts 40 at 40 b are fixed to both side surfaces near the rear end of the trough 1, and in the vibration mechanism 6, the synchronization plate of the above embodiment is attached to the connecting portion of the vibration parts 6 & 6b. A pair of support shafts 42a and 42b are fixed to positions corresponding to the spring mounting plate 34 so as to protrude laterally.

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

That is, the connecting bars 44a, 44b are the support shafts 40a40b.
and 42a, 42b so as to be rotatable.

When power is applied to rotate the induction motor M12M2 in opposite directions as in the first embodiment, in the initial state, the vibration mechanism 6 moves the trough 1 in the longitudinal direction of the trough 1, that is, in the direction Y perpendicular to the X direction. vibrate relative to.

On the other hand, the connection bar 44 at
Vibration force is applied via 44b, 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. After 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, the trough 1 vibrates in the X direction as shown in FIGS. 6A and 6B.

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 broken lines in FIG. 22, and as a result, the vibration mechanism 6 vibrates in the direction perpendicular to the , this amplitude δ is normally about 20 mTIL, and is exaggerated in the figure.

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

FIGS. 23 and 24 show a third embodiment of the present invention, and are a side view and a plan view of essential 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. Therefore, the same reference numerals are given to the parts corresponding to the above embodiment, and the description thereof will be omitted. Omitted.

23 and 24, 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 yakugyo.

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 clearly in FIG.

This connecting rod 58 has a pair of approximately triangular connecting plates 56.
a and 56b are fixed in parallel at their respective tops by welding.

The pair of connecting plates 56a and 56b are connected to the vibration mechanism 6 at the bottom thereof.
At the front part of the mounting platen No.
It is also fixed to the common mounting plate 60 of a and 10b by welding.

In addition, as shown clearly in FIG. 24, 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, 50b,
The diameter of this opening shall be sufficiently larger than the diameter of the connecting rod 58.
A connecting member C is constructed.

Similar to the above embodiment, induction motor M1. When power is applied to rotate M2 in opposite directions, the vibration mechanism 6 vibrates relative to the trough 1 in the longitudinal direction of the trough 1, that is, in the direction perpendicular to the X direction in the initial state.

On the other hand, also in the X direction, connecting plates 56a, 5 are connected from the vibration mechanism 6.
6b, 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, as shown clearly in FIG. 3 (rotating shaft 15a).

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, 15a, and 16b, rotate in opposite directions synchronously and at the same speed.

Hereinafter, the trough 1 vibrates in the X direction as shown in FIGS. 6A and 6B. In the initial state immediately after the start of the movement, the ring-shaped rubbers 54a and 54b of the rubber bushing are connected by twisting in the circumferential direction. Plate 56a.

56b, that is, the vibration mechanism 6 vibrates as shown by δ in FIG.

On the other hand, a ring-shaped rubber 54a. 54b has a large elastic constant in the X direction, that is, in its radial direction, so the vibration force of the X direction component is directly transmitted from the vibrating mechanism 6 to the trough 1, and the vibrating mechanism 6 and the trough 1 are integrated in this direction. vibrates.

Note that since there is a considerable distance from the connecting rod 58 to the vibrating mechanism 6 as shown in the figure, the vibrating mechanism 6 can vibrate almost vertically (the magnitude of δ is similar to that in the above embodiment). Similarly, FIGS. 25 and 26 (which are exaggerated in the figures) show a fourth embodiment of the present invention, and 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, there is a mounting bracket 10% l on the front part of the vibration mechanism 6.
A rectangular mounting plate 66 is commonly fixed to l and 10b by welding.

A pair of rubber plates 70a and 70b are fixed between the mounting plates 64 and 66 near both ends thereof with bolts (not shown).

As is well known, these rubber plates 70a and 70b are made of a rectangular rubber sandwiched between two rectangular iron plates, and their elastic constants are relatively low in the shear direction, that is, in the vertical direction Y in FIG. Although small, the elastic constant is extremely large in the compression direction, that is, in the horizontal direction X in FIG.

A further pair of rubber plates 72a and 72b similar to such rubber plates 70a and 70b are provided at both ends of the mounting plate 660, and a band-shaped rubber plate mounting plate 68a disposed corresponding to both ends of the mounting plate 660.
Although not shown, it is fixed with a bolt between it and 68b.

The mounting plate 64 and the rubber plate mounting plate 68a68b are provided with a coupling member 74a having a cross-section shaped like an opening at their upper and lower ends.
, 74b and 76a, 76b are fixed with bolts or the like, whereby the mounting plate 64 and the rubber plate mounting plates 68a, 68b are integrated via the coupling members 74a, 74b, 76a, 76b.

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

In this embodiment as well, the electric motor M,
, M2 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 X, the X-direction component of the excitation force from the excitation mechanism 6 is the rubber plate 70a, 70b, 72a.

Since the elastic constant of 72b in the compression direction is extremely large, it is directly connected to the trough 1 via the rubber plates 70a, 70b, 72a, 72b.
is transmitted, and the vibration mechanism 6 and the trough 1 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 15a of vibration part 6a, 6b
, 15b, 16a.

A synchronizing force acts on 16b, which causes the
The goal is to obtain a steady state as shown in Figure D.

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. 6A and 6B.

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 possible.

For example, in the above embodiment, the first unbalanced weights 7a, 7b
are each made up of two unbalanced weights, and of course these are referred to as the second unbalanced weight 8a.

Similarly to 8b, it may be composed of one unbalanced weight, and the shape is not limited to the semicircular shape.

However, as in the above embodiment, the first unbalanced weight 7
If a and 7b were each composed 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 8ay8b.

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 15 of the unbalanced weights 7ay 7b, 8a, 8b
The fixed angular positions of a, 15b, 16a, and 16b are not limited to the illustrated embodiments described above.

That is, in each of the embodiments, it is fixed at the position shown in FIG. 3 or 4A (the positions in FIGS. 4B to 4D are equivalent to FIG. 4A), but the present invention is not limited thereto.

For example, as shown in FIG. 16, the first unbalanced weight 7a,
7b center of gravity G1. G2 are rotating shafts 15a and 15b, respectively.
When the second unbalanced weight 8a is directly below and directly above the
Unbalanced weight 7at7b such that y sb is located directly above and directly below rotating shafts 16a and 16b, respectively.

8a and 8b may be fixed.

That is, the above-mentioned α may be fixed at 180 degrees.

However, in this case, in order to transfer the material from the left side to the right side of the trough 1, their rotational direction must be opposite to that shown in FIG.

For this purpose, simply change the connection of the induction motor M□2M2 to the power supply.

It is not necessary to fix the unbalanced weight to the rotating shaft so that the angle is exactly α-0 or α-180°.
It will be clear from the above description that the angle 1 may be fixed to α-180°.

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 mm, and the vibration frequency is 7.
00 times/min, the angle of inclination of the plate spring 2 with respect to the vertical direction is 20
In this case, 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.

Furthermore, in the above embodiment, the trough 1 is supported on the base 3 by the plate spring 2, and the vibration mechanism 6 is supported on the base 3 by the coil spring 36. The same effect as described in the above embodiment can be obtained by suspending the vibration mechanism 6 from a stationary body fixed to a part of the building by means of a leaf spring 2 and suspending it by means of a coil spring. It will be done.

In the vibration mechanism 6 of the above-described embodiment, the vibration part 6at
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 configured as described above, the structure is simple, and although the trough moves slowly in the conveying direction,
Since the return is rapid, unlike the conventional method in which the conveyed object jumps while colliding with the trough, the conveyed object slips (see Figure 6B), and there is no noise from the conveyed material and the material "breaks". It does not cause any "chip" or "chip" and does not generate dust like conventional methods.

For example, when the present invention is applied to a so-called picking table used by an operator to manually remove defective items such as materials and workpieces flowing on a conveyor, it is possible to remove the materials, workpieces, etc. Since there are no jumps, operator eye fatigue is drastically reduced.

Since the vibrating conveyor according to the present invention is not a resonant type, there is no need for troublesome design or adjustment, vibration isolation is easy, and furthermore, the conveyance speed of materials can be maximized with the same component, and various other advantages are possible. It is effective.

[Brief explanation of the drawing]

1 to 6 show a first embodiment of the vibrating conveyor of the present invention. FIG. 1 is a side view of the vibrating conveyor, FIG. 2 is an enlarged plan view of the same part, and FIG. m-1n in the figure
Linear sectional views, FIGS. 4A to 4D, and 5 are side views of each unbalanced weight for explaining the operation of the first embodiment of the present invention, and FIGS. 6A and 6B are similar views. It is a graph explaining the effect. 7 to 21 are side views or graphs of an unbalanced weight for explaining the present invention in detail, and FIGS.
Figures 13, 16 and 19 are side views showing each side of the mounting position of the unbalanced weight on the rotating shaft, Figures 8, 11, 14, 17 and 20. The figure is a side view to explain the resultant force of the centrifugal force of the unbalanced weight at time t on each side, and Figure 9 is a side view of the above-mentioned It is a graph showing the state of the combined excitation force and trough displacement on the side. FIG. 22 shows a second embodiment of the vibrating conveyor of the present invention,
A side view of the same essential parts, FIGS. 23 and 24 show a third embodiment of the vibrating conveyor of the present invention, and a side view and a partially sectional plan view of the same main parts, FIGS. 25 and 26. The figure shows a fourth embodiment of the vibrating conveyor of the present invention, and is a side view and a partially sectional plan view of the same essential parts. In the figure, 7a, 7b...first unbalanced weight, 8
a, 8b...second unbalanced weight, 30a, 30b...
Synchronization leaf spring, 40a, 40b, 42a, 42b-Support shaft, 44a, 44b... Connection bar, 48... Connection bracket, 52a, 52b--Outer cylinder, 54a, 54b
-Rubber, 58-...Connecting rod, 70a, 70b=Plate rubber, 72a, 72b...Plate rubber. 39

Claims (1)

[Claims] 1. A vibrating mechanism including a vibrating part extending in a predetermined direction, an elastic member that supports the vibrating part so as to be able to vibrate in the predetermined direction, and a vibrating mechanism that supports the vibrating part in the predetermined direction. a connecting member that connects the vibrating mechanism to the vibrated part so as to vibrate integrally with the vibrating part and vibrate relative to the vibrated part in a direction perpendicular to the predetermined direction; The vibration mechanism includes first and second unbalanced weights having different degrees of eccentricity, rotating shafts for fixing these unbalanced weights, and rotating shafts of rotation in mutually opposite directions.
: consisting of a pair of vibrating parts each having a gear mechanism and a driving source coupled to rotate at a speed ratio of 2, each of the driving sources being connected to a first and a second unbalanced part 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. After that, the first and second unbalanced weights of one of the vibrating parts are synchronized so as to rotate at the same speed in opposite directions to the unbalanced weight of the other vibrating part, and in this case, , the first and second unbalanced weights are attached to the rotating shaft at angular positions such that centrifugal force components of the vibrating part in a direction perpendicular to the predetermined direction cancel each other out in the pair of vibrating parts. The centrifugal force component in the predetermined direction of the first unbalanced weight, which is fixed respectively and of the both jaw swinging parts, is expressed as A
sinωt, and the centrifugal force component of the second unbalanced weight in the predetermined direction is ±B 5in(2ωt−α
) (where ω is the angular velocity t is time), A,
B represents a constant determined by the angular velocity and the eccentricity of the unbalanced weight, α represents a constant determined by the relative mounting angular position of the first unbalanced weight with respect to the second unbalanced weight, and (the sign is determined by the direction of rotation of the first and second unbalanced masses), and the first and second unbalanced masses are located at angular positions such that α is approximately 0° or 180°, respectively. A vibrating conveyor characterized by being fixed to a rotating shaft.