JPS6115003B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a high-speed transport vibratory conveyor that transports various lumps, grains, powder materials or various parts at high speed 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, and this causes the materials on the transfer surface to repeatedly jump in one direction. being transported. In this case, the vibration force varies sinusoidally with time, and the material periodically repeats the jump motion and impinges on the transfer 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), They make noise and in some cases become a pollution problem. Furthermore, when fragile materials such as biscuits and senbei are transferred using a vibrating conveyor, periodic collisions with the transfer surface may cause problems such as cracks and cracks. had some troublesome restrictions added to it.

Furthermore, when materials that tend to generate dust, such as finely powdered materials, are transported by a vibrating conveyor, there are cases in which the dust is undesirable from a sanitary standpoint.

In addition, conventional conveyors are generally of the resonant type,
Not only was the structure complex, but it also required troublesome design and adjustment to achieve synchronization.

In addition, without giving jump motion to the material,
There is a vibrating conveyor called a reciprocating conveyor that transfers material only by sliding motion, but in this case, the drive unit uses a crank mechanism or a complicated mechanical configuration, which is not only expensive but also damages the base and ground. There was a problem with vibration isolation.

In order to eliminate the above-mentioned drawbacks of the conventional vibrating conveyor, the applicant of the present invention previously proposed the following vibrating conveyor in Japanese Patent Application No. 162,463/1983 (Japanese Unexamined Patent Publication No. 93,713/1982). That is, this vibrating conveyor includes a vibrating part extending in a predetermined direction, an elastic member that supports the vibrating part so as to vibrate in the predetermined direction, a vibrating mechanism, and a vibration part extending in the predetermined direction. The vibrating mechanism and the vibrating part are configured to vibrate the vibrating mechanism and the vibrated part integrally, and to vibrate the vibrating mechanism relatively to the vibrating part in a direction perpendicular to the predetermined direction. a connecting member that connects the vibrated part, and the vibrating mechanism includes first and second unbalanced weights having different degrees of eccentricity, and a rotating shaft that fixes the unbalanced weights, respectively; A vibrating conveyor comprising a drive source and a transmission means for coupling the two rotating shafts so that the two rotating shafts are rotated in opposite directions at a predetermined speed ratio by the drive of the drive source. .

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. 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.

An object of the present invention is to achieve the above-mentioned effects while also maximizing the material transfer speed and making it possible to reverse the transfer direction.

According to the present invention, the above objects include: a vibrated part extending in a predetermined direction; an elastic member that supports the vibrated part so as to be able to vibrate in the predetermined direction; an excitation mechanism; The excitation mechanism and the vibrated part are vibrated integrally in a direction, and the vibration mechanism is vibrated relative to the vibrated part in a direction perpendicular to the predetermined direction. A connecting member that connects a vibration mechanism and the vibrated part is provided, and the vibration mechanism fixes first and second unbalanced masses having different degrees of eccentricity, and fixes each of these unbalanced masses. A rotary shaft, a reversible rotary drive source, and a transmission means for coupling the two rotary shafts so that the two rotary shafts are rotated in opposite directions at a speed ratio of 1:2 by the drive of the rotary drive source. The centrifugal force component of the first unbalanced weight in the predetermined direction is expressed as A sin ωt, and the centrifugal force component of the second unbalanced weight in the predetermined direction is expressed as ±
When expressed as B sin(2ωt-α) (however,
ω is the angular velocity, t is the time, A and B are constants determined by the angular velocity and the eccentricity of the unbalanced mass, and α is the relative attachment of the first unbalanced mass to the second unbalanced mass. Represents a constant determined by angular position,
The ± sign is determined by the rotation direction of the first and second unbalanced weights), and the first and second unbalanced weights are such that α is approximately 0° or 180°. are fixed to the rotating shafts at respective angular positions, and by reversing the direction of rotation of the rotary drive source, the direction of transport of the object in the vibrated section is reversed at approximately the same maximum speed. This is achieved by a high-speed transfer vibratory conveyor, characterized by:

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a vibrating conveyor capable of reversing a material transfer direction according to an embodiment of the present invention will be described with reference to the drawings.

1 to 8 show a first embodiment of the present invention,
In FIGS. 1 to 3, the conveying trough 1 is made of steel, for example, has a letter-shaped cross section, extends horizontally, is open at both ends, and has its left end, right end, or center. Materials to be transported (such as billets and bolts) are supplied from above, discharged from the right end or left end, and transported 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 (i.e., in the transport direction). ) is fixed so that it is vertically positioned. The conveying trough 1 is thus supported by the leaf spring 2 so as to be able to vibrate in the direction of the arrow X.

According to the present invention, the above-mentioned transport trough 1 as the vibrated part is coupled to the vibrating mechanism 6 via the connecting part C below.

That is, in the connecting portion C, a pair of plate spring mounting angle members 30a and 30b having a U-shaped cross section are provided.
is fixed to the bottom surface of the central part of the trough 1, for example, by welding, and on the other hand, to the front part of the rectangular parallelepiped-shaped bracket 10 of the vibration mechanism 6, an angle member 32 for attaching a plate spring having an L-shaped cross section is fixed, for example, by bolts. Ru. A pair of leaf springs 34a are provided at one end of these mounting angle members 30a and 32, and at the other end of 30b and 32.
34b are fixed with their longitudinal directions parallel to the longitudinal direction of the trough 1, for example by bolts. These leaf springs 34a, 34b are made of steel or FRP, for example.
It is made of (fiber reinforced plastic) material and is easily deformed, that is, bent, in the direction perpendicular to its longitudinal direction, but exhibits rigidity against compression and tension in the longitudinal direction, and hardly deforms.

Although the connecting portion C according to the embodiment of the present invention is configured as described above, the vibration mechanism 6 coupled to the trough 1 via this connecting portion C will be described in detail below.
That is, in the vibration mechanism 6, two pairs of bearing housings 11, 12 and 13, 14 are fixed to both side walls of the mounting bracket 10. A first rotating shaft 15 is supported at both ends by bearing housings 11 and 12, and a second rotating shaft 16 is supported at both ends by bearing housings 13 and 14. As clearly shown in FIG. 3, a first unbalanced weight 7 having a substantially semicircular shape is fixed to the first rotating shaft 15 with bolts or the like. Each first unbalanced weight 7 in this embodiment consists of two identical unbalanced weights, as is clearly shown in FIG. Furthermore, as clearly shown in FIG. 3, a second unbalanced weight 8, which is smaller in diameter than the first unbalanced weight 7 but also has a semicircular shape, is fixed to the second rotating shaft 16 with bolts or the like. Ru.

An induction motor M is mounted on the rear wall of the mounting bracket 10.
is fixed. A small-diameter pulley 18 is fixed to one end of the rotating shaft of the induction motor M, and a large-diameter pulley 20 is fixed to one end of the first rotating shaft, and a V-belt 22 is wound around these pulleys 18 and 20. be done.

A large diameter gear 24 is fixed to the other end of the first rotating shaft 15, and a small diameter gear 26 is fixed to the end of the second rotating shaft 16 on the bearing housing 14 side.
In this embodiment, the ratio of the number of teeth between the large diameter gear 24 and the small diameter gear 26 is 2:1, and they mesh with each other.

According to this embodiment, the first unbalanced weight 7 and the second unbalanced weight 8 are connected to the first rotation axis 15 and the second rotation axis 16, respectively, in a phase relationship as shown in FIG. are fixed, and as is known, their rotation causes centrifugal forces F and f (see Figures 4A to 4D).
is generated, and the sum of these centrifugal forces F and f becomes the vibration force generated from the vibration mechanism 6. Centrifugal force F and f
The size of the first and second unbalanced weights 7, 8 is the center of gravity G of the first and second unbalanced weights 7, and the distance of g from the axes of the rotation axes 15, 16 is R, r. , 8 as M and m, and the angular velocities of the rotating shafts 15 and 16 as ω ₁ and ω ₂ , F=MRω ₁ ² and f=mrω ₂ ² , respectively. Further, according to this embodiment, the second rotating shaft 16 rotates at twice the speed of the first rotating shaft 15, so ω ₂ =2ω ₁ . Furthermore, according to this embodiment, the first unbalanced weight 7 consists of two unbalanced weights of the same shape as shown in FIG. 2, but instead of this, one unbalanced weight of the same shape is used. When a balanced weight (however, the mass is twice as large as in the case of two weights) is fixed to the rotating shaft 15 at the center position between the two unbalanced weights 7, 7 as shown in Figure 2. Since the centrifugal force and the centrifugal force are the same, in the explanation of the operation of this embodiment, for the sake of simplicity, it will be assumed that there is only one force. Further, in this specification, the above-mentioned MR and mr will be referred to as the eccentricity of the unbalanced weight. The vibration mechanism 6 configured as described above is supported on the base 3 by a plurality of coil springs 36 at the bottom wall of the mounting bracket 10.

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

When electric power is applied to electric motor M and it is driven,
For example, the first rotating shaft 15 is connected via the V-belt 22.
Rotates clockwise at a rotation speed of 800r.pm. On the other hand, due to the meshing of gears 24 and 26 fixed to one end of the first rotating shaft 15 and the second rotating shaft 16, the second rotating shaft 16 rotates counterclockwise at a rotational speed of 1600 rpm.

Below, each rotational phase of the unbalanced weights 7 and 8 will be explained, as shown in FIGS. 4A to 4D.
When the first unbalanced weight 7 rotates 90 degrees clockwise from the rotational phase shown in FIG. 4A, the second unbalanced weight 8 rotates 180 degrees counterclockwise and enters the state shown in FIG. 4B. When the first unbalanced weight 7 rotates 90 degrees clockwise, the second unbalanced weight 8 rotates 180 degrees counterclockwise to the state shown in Fig. 4C, and then from the state shown in Fig. 4D to the state shown in Fig. 4A. Return to state. That is, when the first unbalanced weight 7 rotates once clockwise, the second unbalanced weight 8 rotates twice counterclockwise. Below, the fourth
Periodic rotational movements shown in Figures A to 4D are performed.

To explain the direction of the centrifugal force in each of the above-mentioned rotational phases, in the rotational phase shown in FIG. This generates an excitation force F+f in the excitation mechanism 6 in the same direction as the centrifugal force f acting thereon and in a direction Y perpendicular to the longitudinal direction X of the trough 1. Next, in the rotational phase of FIG. 4B, the centrifugal force F acting on the center of gravity G of the first unbalanced weight 7
is in the X direction, but the center of gravity g of the second unbalanced weight 8
The centrifugal force f acting on the centrifugal force f is in the Y direction, and causes the excitation mechanism 66 to generate excitation forces −F and f in the X direction and Y direction, respectively.

Next, in the rotational phase of FIG. 4C, the centrifugal force F acting on the center of gravity G of the first unbalanced weight 7 is in the Y direction, but the centrifugal force f acting on the center of gravity g of the second unbalanced weight 8
is in the −Y direction, and causes the vibration mechanism 6 to generate an excitation force F−f in the Y direction. Next, in the rotational phase of FIG. 4D, the center of gravity G of the first unbalanced weight 7
The centrifugal force F acting on the center of gravity g of the second unbalanced weight 8 is in the Y direction, and the centrifugal force F acting on the center of gravity g of the second unbalanced weight 8 is in the Y direction. generates an excitation force of

It has become clear that the above-mentioned excitation force is periodically generated in the excitation mechanism 6 in each rotational phase shown in FIGS. 4A to 4D, but the general rotational phase will be explained. It is as follows. That is, after time t from the rotational phase shown in FIG. 4A, the first unbalanced weight 7 and the second unbalanced weight 8 come to the rotational positions shown in FIG. 5, respectively. In the general rotational phase shown in FIG. 5, the X-direction component of the centrifugal force F acting on the center of gravity G of the first unbalanced weight 7 is -
F sin ωt (ω; angular velocity), and the Y-direction component is −F cos ωt. On the other hand, the X-direction component of the centrifugal force f acting on the center of gravity g of the second unbalanced weight 8 is f sin 2ωt, and the Y-direction component is −f cos
2ωt. Therefore, the resultant force in the X direction of the centrifugal forces of the first and second unbalanced weights 7 and 8 is Q=-F
sin ωt+f sin 2ωt, and the resultant force in the Y direction P=-F cos ωt-f cos 2
It becomes ωt. That is, the above-mentioned excitation force P is generated from the excitation mechanism 6 in the Y direction, and the above-mentioned excitation force Q is generated in the X direction.

However, according to this embodiment, since the excitation mechanism 6 is coupled to the trough 1 via the leaf springs 34a and 34b, the above-mentioned excitation force P causes the leaf springs 34a and 34b to
34b bends vertically as shown by the broken line, and the vibration mechanism 6 itself vibrates vertically relative to the trough 1. Therefore, the Y-direction component of the force from the vibration mechanism 6 is hardly transmitted to the trough 1 side, and only the X-direction component is directly transmitted to the trough 1 via the leaf springs 34a, 34b. This is because the leaf springs 34a, 34b exhibit rigidity in this direction as described above. That is, from the vibration mechanism 6 to the trough 1, Q=-F sib ωt+f sin 2ωt
Only the resultant force is added. A graph of this resultant force is shown in FIG. 6A. In addition, in the illustration, F=2f.

That is, as shown in FIG. 6A, the X-direction component f' of the centrifugal force f due to the second unbalanced weight 8 is a sine with a period twice the X-direction component F' of the centrifugal force F due to the first unbalanced weight 7. Q is a graph that combines these changes. The vibration conveyor according to this embodiment constitutes one mass in the X direction from a vibration perspective, and the elastic constant of the entire leaf spring 2 and the mass supported by these (the trough 1, the connecting part C, the excitation The resonant frequency of this mass system is determined by the total mass of the mechanism 6), but if the elastic constant of the entire leaf spring 2 is made sufficiently small and the trough 1 is excited at a driving frequency higher than the resonant frequency, vibration theory As is clear from the above, the trough 1 vibrates with a phase difference of 180 degrees from the excitation force. Therefore, when excited with a resultant force Q as shown in FIG. 6A, the trough vibrates as shown in the graph s. This graph s is a graph
It is obtained by inverting f' and F' with respect to the horizontal axis t (time axis) and then combining them. However, for the graph s, the vertical axis represents displacement.

As understood from the graph s, trough 1 is a
Move forward at low speed to a point (the right side of trough 1 is the forward direction), then move backward at high speed from this forward position point a to point b, then at low speed from this backward position point b to forward position point a move forward. By repeating this periodic movement, trough 1
Material on the transfer bed 1a of the trough 1, e.g. billet
M' is being moved to the right in the figure. That is, in the high-speed backward motion region between () and () in FIG. 6A, only the trough 1 performs a backward movement by overcoming the static friction force between the material and the floor surface of the trough 1, and the trough 1 moves backward. Slippage occurs between the material on the floor and the floor. Then ()~
In the low-speed advance region between (), the material moves forward together with the material trough 1 on the transfer bed 1a surface of the trough 1.
That is, the trough 1 repeatedly moves forward and backward as shown in FIG. 6B. By repeating such a phenomenon, the material is transferred to the right on the floor of the trough 1 in FIG. 1. For example, if billet (ferrous material to be fed to the furnace) is used as the material to be conveyed, the rotating shaft 1
When the rotational speed of No. 5 is approximately 1000 rpm, the material is transferred at a speed of approximately 12 m/min. Moreover, unlike conventional vibrating conveyors, there is no noise caused by the jumping movement of the material, and the material is transferred smoothly.

Next, a case will be described in which the rotation direction of the induction motor M is reversed. That is, if the connection to the three-phase power supply is changed and the rotation direction of the induction motor is reversed, the first unbalanced weight 7 will rotate counterclockwise, and the second unbalanced weight 8 will rotate clockwise, as shown in FIG. Rotate in the direction. Unbalanced weights 7 and 8 at time t with reference to FIG.
The centrifugal force of is calculated as follows. That is,
X of the centrifugal force F acting on the center of gravity G of the first unbalanced weight 7
The direction component is F sin ωt (ω; angular velocity), and the Y direction component is −F cos ωt. On the other hand, the centrifugal force f acting on the center of gravity g of the second unbalanced weight 8
The X-direction component of is -f sin 2ωt, and the Y-direction component is -f cos 2ωt. Therefore, the resultant force in the X direction of the centrifugal forces of the first and second unbalanced weights 7 and 8 is Q=F sin ωt−f sin 2ωt, and the resultant force in the Y direction P=−F cos ω
t-fcos 2ωt. That is, the vibration mechanism 6
The above-mentioned excitation force P is generated in the Y direction, and the above-mentioned excitation force Q is generated in the X direction.

However, as mentioned above, since the excitation mechanism 6 vibrates vertically relative to the trough 1 due to the excitation force P, only the excitation force Q directly applies to the trough 1. conveyed through. That is, only the resultant force Q=F sin ωt−f sin 2ωt is applied to the trough 1 from the vibration mechanism 6 in the X direction. A graph of this resultant force is shown in FIG. 8A. In addition, in the illustration, F=
It is set as 2F. Further, as in FIG. 6A, for the graph s, the vertical axis represents displacement (length). As can be seen by comparing FIG. 8A and FIG. 6A, the graphs s representing the trough displacement are mutually inverted in phase. That is, in FIG. 8A, the trough 1 moves forward at a high speed to point a (the right side of the trough 1 is the front side), then moves backward at a low speed from this forward position point a to point b, and then moves backward from this forward position point a to point b. It moves forward at high speed from point b to forward position point a. By repeating such periodic movements of the trough 1, the material on the transfer bed 1a of the trough 1, for example billet M', is transferred to the left. That is, in the high-speed advance region between () and () in FIG. 8A, only the trough 1 moves forward by overcoming the static friction force between the material and the floor surface of the trough 1, and the trough 1 moves forward. Slippage occurs between the material on the floor and the floor. Next, in the low speed backward movement region between () and (), the material on the transfer bed 1a side of the trough 1 moves backward together with the trough 1. That is, the trough 1 repeatedly moves forward and backward as shown in FIG. 8B. By repeating this phenomenon, the material moves on the floor of the trough 1 as shown in Fig. 1.
It will be moved to the left. For example, as in the case of FIG. 6A, the conveyed material is a billet (iron material supplied to the furnace), and the rotational speed of the rotating shaft 15 is set to about 1000 r.p.
m, the material is transported at a speed of approximately 12 m/min. Moreover, unlike conventional vibrating conveyors, there is no noise caused by the jumping movement of the material, and the material is transferred smoothly.

According to the embodiment described above, the first and second unbalanced weights 7 and 8 are fixed so that their centers of gravity G and g are directly below the rotating shafts 15 and 16, respectively. The following explains why such a mounting position is one of the optimum mounting positions.
In the following description, only the centrifugal force component in the vertical direction, that is, the Y direction, will be explained because the component component of the centrifugal force in the vertical direction, that is, the Y direction, does not act as an excitation force of the trough 1 as described above.

Figure 9 shows the mounting angular position of the second unbalanced weight 8 relative to the first unbalanced weight 7 in the opposite direction to its rotation direction.
45°, shown when shifted from the position shown in Figure 4A. In this case, the first and second unbalanced weights 7,
8 assumes the rotational position shown in FIG. 10 after time t, and the respective X direction components F' and f' are F'=-F
sin ωt and f′=−f cos(2ωt+π/4), therefore, the total resultant force Q=F′+f′=−F sin ω
t−f cos(2ωt+π/4). If these are shown in a graph, it will look like FIG. 11. In the figure, F=2f. The trough displacement S can be obtained by inverting the excitation force Q 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 graph below).

As can be seen by comparing Figures 6A and 11,
Although the excitation force Q and the trough displacement S change in almost the same way, they differ in the details, so the material transfer speed is approximately the same or lower (because there is a partial high-speed advance region in the ~ section). ). As a result of the experiment, when the first and second unbalanced weights 7, 8 are fixed to the rotating shafts 15, 16 as shown in FIG. 9, and the other conditions are the same as in the above case, the material transfer speed is was approximately 9 m/min. That is, the transfer speed decreased from about 12 m/min to about 9 m/min.

Next, Fig. 12 shows the case where the mounting angle position of the second unbalanced weight 8 with respect to the first unbalanced weight 7 is shifted by 90 degrees in the opposite direction to the rotation direction from the position shown in Fig. 4A. . In this case, the first and second unbalanced weights 7, 8 assume the rotational positions shown in FIG. 13 after time t, and the respective X-direction components F' and f' are
F'=-F sin ωt and f'=-f cos 2ωt
Therefore, the total resultant force Q=F′+f′=−F sin
ωt−f cos 2ωt. 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. 14, 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 b and the transfer speed from the reverse position b to the forward position a are expressed in the graph with respect to the axis. changes similarly due to the symmetry of . Therefore, it is presumed that the material transfer speed is extremely low. The experimental results were also almost zero.

Furthermore, FIG. 15 shows the case where the mounting angle position of the second unbalanced weight 8 with respect to the first unbalanced weight 7 is shifted by 135 degrees in the opposite direction to the rotation direction from the position shown in FIG. 4A. . In this case, the first and second unbalanced weights 7 and 8 assume the rotational positions shown in FIG. 16 after time t, and the respective X-direction components F' and f' are
F'=-F sin ωt and f'=-f sin(2ωt
+π/4), and therefore the total resultant force Q=F'+f'=-F sin ωt-f sin(2ωt+π/4). If these and the trough displacement S are shown in a graph, it will be as shown in FIG. 17.

As can be seen from FIG. 17, in this case, the trough 1 moves from forward position a to reverse position b at a relatively low speed, and from reverse position b to forward position a at a relatively high speed. Moreover, when comparing FIG. 11 and FIG. 17, it can be seen that if the directions of the time axes are reversed, the two graphs match. Therefore, it is assumed that the material transport speed is the same in magnitude as in FIG. 11, although the direction is opposite. As a result of the experiment, the transfer speed was about 8 m/min and the direction was opposite, but it was 9 m/min in the case of Fig. 11.
The minutes were almost the same.

Further, FIG. 18 shows a case where the mounting angular position of the second unbalanced weight 8 with respect to the first unbalanced weight 7 is shifted by 180 degrees in the opposite direction to the direction of rotation from the position shown in FIG. 4A. In this case, the first and second unbalanced weights 7 and 8 assume the rotational positions shown in FIG. 19 after time t, and the respective X-direction components F' and f' are
F'=-F sin ωt and f'=-f sin 2ωt, so the total resultant force Q=F'+f'=-F sin
ωt−f sin 2ωt. 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. 20, in this case, the trough 1 moves from the forward position a to the reverse position b at a relatively low speed, and from the reverse position b to the forward position a at a relatively high speed. Moreover, when comparing FIG. 6A and FIG. 20, it can be seen that if the directions of the time axes are reversed, the two graphs match. Therefore, it is assumed that the material transport velocity is the same in magnitude as in FIG. 6A, although the direction is opposite. As a result of the experiment, the transfer speed is about 13 m/min and the direction is opposite, but it is about 12 m/min in the case of Fig. 6A.
m/min.

In addition, FIG. 21 shows the mounting angle position of the second unbalanced weight 8 relative to the first unbalanced weight 7 in the direction of rotation.
°, shows the case shifted from the position shown in FIG. 4A. In this case, the first and second unbalanced weights 7,
8 assumes the rotational position shown in FIG. 22 after time t, and the respective X direction components F' and f' are F'=-F
sin ωt and f′=f sin(2ωt+π/4), so the total resultant force Q=F′+f′=−F sin ω
t+f sin(2ωt+π/4). If these and the trough displacement S are shown in a graph, it will be as shown in FIG. 23.

As can be seen by comparing the graph in FIG. 17 and the graph in FIG. 23, the graphs of trough displacement S become the same if they are reversed with respect to the time axis t.
It can be seen that the transport speeds are the same and the directions are opposite to each other. Furthermore, in the above explanation, the rotation direction of the first unbalanced weight 7 was clockwise, and therefore the rotation direction of the second unbalanced weight 8 was counterclockwise, but these rotation directions were reversed. In this case, graphs representing the excitation force Q and the trough displacement S can be obtained by inverting each of the above graphs with respect to the time axis t. Therefore, the above figures 9, 12, and 15
When the first and second unbalanced weights 7 and 8 are fixed to the rotating shafts 15 and 16 as shown in FIG. and the transfer speed is the same.

The excitation force Q explained above can be generally expressed as follows. That is, Q=A sin ωt±B sin(2ωt−
α), where A=MRω ² and B=mr(2ω) ² ,
α represents the angle of deviation from the first unbalanced weight 7 in the direction opposite to the rotational direction of the second unbalanced weight 8, with reference to the mounting position of FIG. 4A of the second unbalanced weight 8. Further, the ± sign is determined by the rotation direction of the unbalanced weights 7 and 8.

For example, as shown in FIG. 4A, unbalanced weights 7 and 8
When fixed to the rotating shaft, the 6th A
As is clear from the figure, the excitation force Q=A sin ω
It is expressed as t+B sin(2ωt-0). 9th
When fixed as shown in the figure, Q=A sin ωt+B sin(2ω
t-45°), and when fixed as shown in Figures 12, 15, and 18, the first
As is clear from Figures 4, 17, and 20, Q
=A sin ωt+B sin(2ωt-90°), Q
=A sin ωt+B sin(2ωt-135°), Q
It is expressed as =A sin ωt+B sin (2ωt−180°). Furthermore, when the unbalanced weights 7 and 8 are fixed to the rotating shaft as shown in FIG.
As is clear from Figure 3, Q=A sin ωt+B
It is expressed as sin(2ωt+45°). That is, in the case of FIG. 21, the mounting position of the second unbalanced weight 8 is deviated from the position shown in FIG. 4 by 45 degrees in the rotation direction, unlike in other cases.
The above α is negative. In addition, when the rotation direction of the unbalanced weights 7 and 8 is reversed, in each graph, the graph representing the excitation force f' of the second unbalanced weight 8 is moved in the negative direction parallel to the time axis t. Since it will move 180 degrees, the excitation force Q = A in this case
sin ωt+B sin(ωt-α+π)=Asin ω
t-B sin(ωt-α).

As is clear from the above explanation, the maximum transfer speed can be obtained when α=0° or 180°. Note that even when α=45° or 135°, as mentioned above, a transfer speed considerably higher than the maximum transfer speed can be obtained, so the actual unbalanced weights 7 and 8 are attached to the rotating shaft at α≒0 or α≒180. ° is sufficient.

Although the first embodiment of the present invention is configured as described above, a second embodiment to which the present invention is applied will be described below.

24 and 25 are a side view of a portion of a vibrating conveyor capable of reversing the conveyance direction according to a second embodiment of the present invention, and a partially cutaway plan view as viewed from the - line direction in FIG. 24. This embodiment differs from the above-described embodiment only in the connecting portion C, and is otherwise the same, so corresponding parts are designated by the same reference numerals and description thereof will be omitted.

That is, in the connecting portion C of this embodiment, the excitation force transmission member 40 is fixed to the bottom surface of the approximately central part of the trough 1 by bolts or welding, and on the other hand, the excitation force transmission member 40 is fixed to the front wall of the mounting bracket 10 of the excitation mechanism 6. A pair of support shaft mounting plates 44a and 44b are fixed by welding in parallel to the X direction with the same spacing as the spacing between both side surfaces 42a and 42b of the excitation force transmission member 40 on the trough 1 side.

The above members 42a, 42b, 44a, 44b have vertical support shafts 46a, 46b, 48a, respectively.
48b is fixed by welding. These support shafts 46
Connecting rods 50 and 52 are pivotally attached to a and 48a and to 46b and 48b at their ends.
That is, ring portions 50a, 50b and 52a, 5 formed at both ends of the connecting rods 50 and 52
2b is rotatably fitted to the support shafts 46a, 48a and 46b, 48b.

The connecting portion C of this embodiment is configured as described above,
The above-mentioned vibration mechanism 6 and trough 1 are coupled through this, and the same vibration force Q as in the above-mentioned embodiment is applied to the trough 1, causing the trough 1 to move in the same way. Let's do it.

That is, due to the Y-direction component of the excitation force from the vibration mechanism 6, the vibration mechanism 6 itself moves the connecting rods 50 and 52 to the support shafts 46a and 4 as shown by broken lines in FIG.
6b, it vibrates relative to the trough 1 in the Y direction. As a result, the Y-direction component from the vibration mechanism 6 is not transmitted to the trough 1, and only the X-direction component is transmitted to the trough 1 via the rigid connecting rods 50, 52, and the vibration mechanism 6 and the trough 1 means Fig. 6A and Fig. 6 in the X direction.
Perform the vibration shown in Figure B. Therefore, the material M' on the floor surface 1a of the trough 1 moves to the right of the trough 1 by performing a periodic sliding motion on the floor surface 1a without making a jump motion, as described in the above embodiment. being transported.

Note that when the rotation directions of the first and second unbalanced weights 7 and 8 are reversed, the material is transferred to the left of the trough 1 at substantially the same speed as in the above embodiment.

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

For example, in the above embodiment, the first unbalanced weight 7
is made up of two unbalanced weights, but of course it may be made to consist of one unbalanced weight like the second unbalanced weight 8, and the shape is not limited to the semicircular shape. . However, if the first unbalanced weight 7 is composed of two unbalanced weights as in the above embodiment, the stress distribution due to the centrifugal force on the rotating shaft 15 will be more preferable. In this respect, the first unbalanced weight 7 may be configured to include a larger number of unbalanced weights. The same can be said of the second unbalanced weight 8.

Furthermore, in the above-described embodiment, the trough 1 is supported on the base 3 by the leaf spring 2, but it may be suspended from above via the leaf spring. In this case, the vibration mechanism 6 is also suspended from above via a coil spring.

Furthermore, although the leaf springs 2 are arranged vertically in the above-described embodiments, they may also be arranged with some inclination in the vertical direction. However, in this case, the condition that the vertical component of the vibrational acceleration of the trough 1<gravitational acceleration g is satisfied so that no jump motion of the material occurs. For example, the vibration stroke of trough 1 is 10
mm, the frequency of vibration is 700 times/min, and the inclination angle of the leaf spring 2 with respect to the vertical direction is 20 degrees, the material is transferred without jumping. In the above embodiments, the plate springs 34a and 34b or the connecting rods 50 and 52 hinged to the trough and the vibration mechanism at both ends were used as the connecting portion C, but the above-mentioned hinges are not limited to this. The same effect as described above can be obtained by replacing the section with a rubber bush or by using a rubber plate and arranging it so that its shear direction is parallel to the Y direction and its compression direction is parallel to the X direction.

Furthermore, in the embodiment, the trough 1 that simply transfers the material was explained as the vibrated part, but the invention is not limited to this, and additional structures such as protrusions and grooves on the floor of the trough 1 may be used as is known in the art. In addition, actions such as sorting and sorting of materials may be performed while being transported. In this case, for example, if the present invention is applied to a so-called picking table used for manually picking out defective items such as materials or parts transferred on a conveyor, it is possible to Since there is no jump, this has the effect of reducing the fatigue of the worker.

Since the present invention is constructed as described above, the structure is simple, and the trough as the vibrated part advances slowly in the transport direction, but returns rapidly, so the transported object is different from that of the conventional one. Unlike the method in which the material jumps while colliding with the trough, the material slips (see Figure 6B), so there is no noise from the transferred material, and the material does not crack or crack. It also doesn't create dust like traditional methods. Moreover, since it is not a resonant type, it does not require complicated design or adjustment, and has various effects such as easy vibration isolation, and the direction of material transfer can be easily reversed. Furthermore, the direction of material transport can be easily reversed if necessary.

[Brief explanation of the drawing]

1 to 8 show a high-speed transfer vibration conveyor capable of reversing the transfer direction according to a first embodiment of the present invention. FIG. 1 is a side view of the same vibration conveyor, and FIG. FIG. 3 is an enlarged plan view of the same part seen from the line direction, FIG. 3 is a sectional view in the - line direction in FIG. 2, and FIGS. 4A to 4D and FIG. The side view of the unbalanced weight, FIGS. 6A and 6B, are graphs similarly illustrating the effect. Figure 7 and Figure 8A, Figure 8
Figure B is a side view and a graph of an unbalanced weight for explaining that the vibrating conveyor according to the same embodiment can reverse the material transfer direction. 9 to 23 are side views or graphs of an unbalanced weight for explaining the effects of the present invention, and FIGS. 9, 12,
Figures 15, 18, and 21 are side views showing examples of mounting positions of the unbalanced weight on the rotating shaft;
13, 16, 19, and 22 are side views for explaining the resultant force of the centrifugal force of the unbalanced weight at time t in each of the above examples, and FIG.
FIG. 14, FIG. 17, FIG. 20, and FIG. 23 are graphs showing the state of the excitation force and trough displacement in each of the above examples. 24 and 25 show another embodiment of a high-speed transfer vibrating conveyor capable of reversing the material transfer direction according to the second embodiment of the present invention.
25 is a side view of the same essential part, and FIG. 25 is a plan view of the same essential part seen from the - line direction in FIG. 24. In the figure, 1...trough, 2...plate spring, 7...first unbalanced weight, 8...second unbalanced weight, 24, 26...gear, M...induction motor, 3
4a, 34b...plate spring, 50, 52...connection rod.

Claims (1)

[Claims] 1. A vibrated part extending in a predetermined direction, an elastic member that supports the vibrated part so as to vibrate substantially in the predetermined direction, an excitation mechanism, and an excitation mechanism and the The vibrating mechanism and the vibrated part are vibrated integrally with the vibrated part, and the vibrating mechanism is vibrated relative to the vibrated part in a direction perpendicular to the predetermined direction. The vibration mechanism includes first and second unbalanced masses having different degrees of eccentricity, a rotating shaft for fixing these unbalanced masses, and a reversible rotational drive. a first unbalanced weight; The centrifugal force component in the predetermined direction of the second unbalanced weight is expressed as A sin ωt, and the centrifugal force component of the second unbalanced weight in the predetermined direction is expressed as ±B sin (2ωt−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 angular position of the first unbalanced weight with respect to the second unbalanced weight. (the ± sign is determined by the rotation direction of the first and second unbalanced weights), and the first and second unbalanced weights have α of approximately 0° or 180°. are fixed to the rotating shafts at angular positions such that, by reversing the rotational direction of the rotary drive source, the direction of transport of the object in the vibrated section is reversed at approximately the same maximum speed. A high-speed transfer vibrating conveyor characterized by a structure in which: