JP2021075383A - Oscillating conveyor - Google Patents

Abstract

To provide an oscillating conveyor that can restrict the increase in cost and installation space by eliminating the necessity of a driver controller that controls the motor rotation.SOLUTION: The oscillating conveyor includes: a trough 3 that can be reciprocated and conveys a workpiece: a rotational member 42 as a circulating member that makes a circulating movement by the driving force from a driving source 41, the rotational member 42 making a rotational movement at a constant speed on the oscillating conveyor provided between the rotational member 42 and the trough 3; and a conversion mechanism 43 that converts the rotational movement of the rotational member 42 into a linear reciprocating movement of the trough 3. The conversion mechanism 43 has one end 431A connected to the rotational member 42, and includes: an oscillating member 431 designed to oscillate around a shaft 8 that is approximately parallel to a rotational shaft 41A of the rotational member 42 at a middle part 431C between the end 431A and the other end 431B; and a connection member 432 having one end connected to the other end 431B of the oscillating member 431, and the other end 431B connected to the trough 3.SELECTED DRAWING: Figure 2

Description

The present invention relates to a vibrating conveyor that conveys a work by reciprocating a trough.

As a conventional vibration conveyor, for example, there is one described in Patent Document 1. In this vibration conveyor, the power from the rotary motor is transmitted to the trough via a parallel link, so that the trough is reciprocated to convey the work on the trough. When the rotary motor moves the trough in the transport direction of the work, the rotation speed is controlled so as to move the trough at a speed slower than the speed at which the trough is moved in the direction opposite to the transport direction of the work.

By reciprocating the trough as described above, the work can be moved so as to slide on the trough while giving acceleration in the transport direction to the work placed on the trough.

In Patent Document 1, in the configuration for controlling the rotation speed of the motor, a dedicated driver controller is required separately from the motor, which not only leads to an increase in cost and installation space, but also causes a control load.

Japanese Unexamined Patent Publication No. 2005-272132

Therefore, it is an object of the present invention to provide a vibration conveyor capable of suppressing an increase in cost and installation space by eliminating the need for a driver controller that controls rotation of a motor.

The present invention is provided between a reciprocating trough that conveys a work, an orbiting member that orbits at a constant speed by a driving force from a drive source, and the orbiting member and the trough, and orbits the orbiting member. In a vibration conveyor provided with a conversion mechanism for converting motion into a linear reciprocating motion of the trough, the orbiting member orbits at a constant speed, and one end of the conversion mechanism is connected to the orbiting member and one end thereof. An oscillating member configured to swing around an axis substantially parallel to the axis passing through the orbiting center of the circling member in the intermediate portion between the oscillating member and the other end, and one end at the other end of the oscillating member. The rocking member includes a connecting member which is connected and the other end is connected to the trough, and the rocking member includes a distance between one end of the rocking member and the shaft and the other end of the rocking member. The vibration conveyor is characterized in that the ratio of the distance between the portion and the shaft is movable so as to change momentarily with the rotation of the reciprocating member.

As described above, the ratio of the distance between one end of the swinging member and the shaft and the distance between the other end of the swinging member and the shaft moves so as to change momentarily as the orbiting member orbits. By doing so, the acceleration of the phase in which the trough reverses from forward to backward can be made larger than the acceleration of the phase in which the trough reverses from backward to forward. Further, the connecting member is pushed and pulled in conjunction with the movement of the swing member swinging around the axis while moving with respect to the shaft, thereby converting the orbital motion of the orbiting member into a linear reciprocating motion of the trough. The trough can be reciprocated. That is, the present invention is a conversion mechanism that converts the orbital motion of the orbiting member into the linear reciprocating motion of the trough as described above, without performing the orbital control of the orbiting member by using a drive source such as a servomotor as in the prior art. By mechanically realizing the above, it is possible to configure the orbiting member to orbit at a constant speed. This not only eliminates the need for an expensive servomotor as a drive source, but also eliminates the need for a driver controller for orbit control, and also eliminates the need for a drive circuit and a control circuit. In addition, since it has a mechanical configuration, when a failure occurs, it is easy to investigate the cause of the failure and repair it on site.

Further, the swing member may include a slide portion that can swing while holding the shaft and slides in the longitudinal direction while holding the shaft.

As described above, by sliding the swing member by the slide portion, the ratio change between the distance between one end of the swing member and the shaft and the distance between the other end of the swing member and the shaft. Is done smoothly.

Further, the slide portion may be composed of elongated holes formed in the swing member.

As described above, since the slide portion can be formed only by forming a long hole in the swing member, the swing member can be easily manufactured.

Further, in the swing member, when the driving force transmitted to the trough via the connecting member is reversed in one direction from the other direction as compared with the case where the driving force transmitted to the trough is reversed from one direction to the other direction related to the linear reciprocating motion. The configuration may be such that the movement is larger than the size of the above.

According to the above configuration, the acceleration acting on the trough when reversing from one direction to one direction can be made larger than the acceleration acting on the trough when reversing from one direction to the other direction. This can be achieved with a mechanical configuration.

According to the present invention, it is possible to provide a vibration conveyor capable of suppressing an increase in cost and installation space by eliminating the need for a driver controller that controls rotation of a motor.

It is a top view which shows by extracting the conversion mechanism of the vibration conveyor which concerns on 1st Embodiment of this invention. It is a side view of the vibration conveyor. (A) and (b) are explanatory views which simplify the conversion mechanism of the vibration conveyor and show the movement. (A) and (b) are explanatory views which simplify the conversion mechanism of the vibration conveyor and show the movement. It is a side view of the vibration conveyor which concerns on 2nd Embodiment of this invention. It is a side view of the vibration conveyor which concerns on 3rd Embodiment of this invention. It is a side view of the vibration conveyor which concerns on 4th Embodiment of this invention. It is a top view which shows by extracting the conversion mechanism of the vibration conveyor which concerns on 5th Embodiment of this invention.

The vibration conveyor of the present invention will be described with reference to the drawings.
<First Embodiment>

FIG. 2 shows the vibration conveyor 1 of the first embodiment according to the present embodiment. In FIG. 2, the left-right direction (longitudinal direction) of the figure is the front-back direction, and the direction penetrating the paper surface is the left-right direction, which will be described below. The vibration conveyor 1 includes a trough 3 that is reciprocally supported on the ground G via a support portion 2 in the front-rear direction, and a drive unit 4 for reciprocating the trough 3.

In FIG. 2, the support portion 2 supports the front and rear ends of the trough 3, but the support portions 2 are also provided at both left and right ends, and the trough 3 is supported at a total of four locations. Each support portion 2 is rotatably attached to a fixed block 21 fixed to the ground G and a support member 22 extending above the fixed block 21 around the horizontal axis X, and a wheel that abuts and supports the lower surface of the trough 3. 23 and.

The trough 3 is long in the front-rear direction, and includes a bottom wall 31 and left and right wall portions 32, 32 extending upward from both left and right ends of the bottom wall 31 (in FIG. 2, only one wall portion is shown). It is an upward open type equipped with a, and is configured in a substantially U-shape when viewed in the front-rear direction.

The drive unit 4 is attached to a fixed unit 5 fixed to the ground G. The fixing portion 5 is a rectangular plate-shaped plate member 51 that is long in the front-rear direction that supports the drive portion 4, and four block-shaped leg portions 52, 52, 52, 52 that support the four corners of the plate member 51 (FIG. In 2, only one side in the left-right direction is shown).

Specifically, the drive unit 4 orbits the drive shaft 41A at a constant speed by receiving rotational force from the electric motor 41 as a drive source driven by the power supply 6 and the drive shaft 41A of the electric motor 41. As described above, the rotating member 42 as an oval and plate-shaped rotating member pivotally supported by the drive shaft 41A is provided between the rotating member 42 and the trough 3, and the rotational movement of the rotating member 42 (moves on a perfect circle). It is provided with a conversion mechanism 43 that converts the orbital motion) into a linear reciprocating motion of the trough 3. As the electric motor 41, for example, an inexpensive general-purpose motor such as an induction motor, or a motor in which a speed reducer such as a gear mechanism is combined with these can be used. When a speed reducer is combined, it is possible to obtain an appropriate rotation speed according to the specifications of the vibration conveyor and easily obtain the torque required to drive the vibration conveyor.

The electric motor 41 includes a motor body 41B and a drive shaft 41A protruding upward from the motor body 41B. The motor body 41B is fixed with its upper end surface in contact with the lower surface of the plate member 51, and the drive shaft 41A penetrates the plate member 51 and projects upward from the upper end surface of the plate member 51. A rotating member 42 is integrally rotatably attached to the upper end of the protruding drive shaft 41A.

The conversion mechanism 43 is arranged between the upper surface of the plate member 51 and the lower surface of the bottom wall 31 of the trough 3. Specifically, in the conversion mechanism 43, one end portion 431A is pivotally connected to the rotating member 42 via a pin P1, and the circumferential center of the rotating member 42 is centered at the intermediate portion 431C between the one end portion 431A and the other end portion 431B. A swing member 431 configured to swing around a shaft 8 (see FIG. 1) substantially parallel to the drive shaft 41A, which is a passing shaft, and a pin P2 at one end 432A on the other end 431B of the swing member 431. A connecting member 432 which is pivotally connected via a pin P3 to a rectangular plate-shaped fixing plate 7 whose other end 432B is fixed to the bottom wall 31 of the trough 3 is provided. There is. The rotating member 42 and the conversion mechanism 43 form a link mechanism for connecting the electric motor (drive source) 41 and the trough 3. The trough 3 is reciprocated by converting the rotational force from the rotating member 42 that orbits at a constant speed into a linear reciprocating motion by the conversion mechanism 43. This not only eliminates the need for an expensive servomotor as a drive source, but also eliminates the need for a driver controller for orbit control, and also eliminates the need for a drive circuit and a control circuit. In addition, since it has a mechanical configuration, when a failure occurs, it is easy to investigate the cause of the failure and repair it on site.

The shaft 8 is composed of a shaft main body 82 that protrudes upward from the upper end of a rectangular base member 81 in a plan view fixed to the upper surface of the plate member 51, and a roller 83 that is rotatably fitted onto the shaft main body 82. Has been done.

The swinging member 431 is formed of a plate-shaped member having a substantially rectangular shape and having rounded corners at both ends, and can swing by holding the roller 83 constituting the shaft 8, and holds the roller 83. It is provided with a slide portion 431G that slides in the longitudinal direction while being maintained. The slide portion 431G is an elongated hole formed in the swing member 431, and by allowing the swing member 431 to move with respect to the shaft 8, the swing member 431 has one end portion 431A and the shaft 8 in the longitudinal direction. The distance between them and the ratio between the other end portion 431B of the swing member 431 in the longitudinal direction and the shaft 8 change every moment as the rotating member 42 rotates. By sliding the swing member 431 by the slide portion 431G in this way, the distance between the longitudinal end portion 431A of the swing member 431 and the shaft 8 and the other end portion 431B and the shaft 8 of the swing member 431 are obtained. The ratio change with the distance between and is smoothly performed. Further, since the slide portion 431G can be formed only by forming the elongated hole in the swing member 431, the swing member 431 can be easily manufactured.

Further, in the swing member 431, the driving force transmitted to the trough 3 via the connecting member 432 is reversed from one direction related to the linear reciprocating motion of the trough 3 to the other direction (direction opposite to the transport direction). , It is configured to move so as to be larger when it is reversed from the other direction to one direction (transportation direction). Therefore, the acceleration acting on the trough when reversing from one direction to one direction is larger than the acceleration acting on the trough when reversing from one direction to the other direction. Moreover, this movement can be realized by a mechanical configuration.

The connecting member 432 is composed of a plate-shaped member that is substantially rectangular and has rounded corners at both ends, is slightly smaller than the width of the swing member 431, and is slightly longer than the length of the swing member 431. However, it is not limited to this.

A pair of left and right rotating rollers 9 and 9 are arranged in the front-rear direction at the left and right ends of the fixing plate 7 so that the fixing plate 7 moves linearly in the front-rear direction. Each rotating roller 9 is rotatably fitted onto a shaft 10 fixed to the ground G.

Next, the movement of the conversion mechanism 43 when the work is conveyed by the vibration conveyor 1 will be described with reference to the schematic views shown in FIGS. 3 (a) and 3 (b) and FIGS. 4 (a) and 4 (b).

First, with reference to FIGS. 3 (a) and 3 (b) and FIGS. 4 (a) and 4 (b), the first section (reference section) 11 is the portion where the electric motor 41 is installed (attached). Corresponds to the plate member 51 of 2. Section 2 12 is a member that rotates and pairs with the drive shaft 41A of the electric motor 41, and corresponds to a rotating member 42 connected to the drive shaft 41A of FIG. The third section 13 is a member that rotates around the second section 12 and forms a kinematic pair, and corresponds to a swing member 431 connected to the rotating member 42 of FIG. 1 by a pin P1. Section 4 14 is a member forming a sliding (slide) kinematic pair with Section 3 13 and is a member (for example, a tubular member) that allows the swinging member 431 to swing and slide. It is installed in a state where it can only swing. Therefore, the fourth section 14 has the same function as the elongated hole (slide portion 431G) formed in the swing member 431 of FIG. Section 5 15 is a member that forms a kinematic pair with Section 3 13 and corresponds to a connecting member 432 in FIG. Section 6 16 is a member that forms a kinematic pair with Section 5 15 and corresponds to the fixing plate 7 of FIG. The third section 13 and the fifth section 15 are connected by the pin P2, and the sixth section 16 and the fifth section 15 are connected by the pin P3. Further, a drive shaft 41A of the electric motor 41, a swing fulcrum 17 described later, and a pin P3 which is a connecting portion between the sixth section 16 and the fifth section 15 are arranged on the first section 11. ..

When the electric motor 41 is driven, the second section 12 rotates counterclockwise as indicated by an arrow in a plan view as shown in FIG. 3A. Due to the rotation of the second section 12, the third section 13 swings and moves to the second section 12 side (left side). The movement of the third section 13 pulls the fifth section 15 and pulls the sixth section 16 linearly along the first section 11. As a result, the trough 3 moves to the left (see FIGS. 3 (a) to 3 (b)). Further, when the second section 12 rotates, as shown in FIG. 4A, the second section 12 pushes and moves the third section 13 while swinging in the direction opposite to the above. As a result, the trough 3 moves from the left side to the right side (see FIGS. 4 (a) to 4 (b)).

In the vibration conveyor 1 having the above configuration, the conversion rate of the amount of motion between the input and the output (the operation of the output with respect to the input) in the phase in which the trough 3 reverses from forward to backward and the phase in which the trough 3 reverses from backward to forward. Amount ratio) changes. Explaining this point, FIG. 3B shows a phase of reversing from backward to forward, and the trough side end portion of the third section 13 with respect to the input in which the second section 12 is rotated by driving the electric motor 41. (Output) operation is small. This is because the distance L2 from the swing fulcrum (corresponding to the shaft body 82 in FIG. 1) 17 of the third section 13 to the pin P2 which is the connecting portion between the third section 13 and the fifth section 15 is the second section. This is because the distance from the pin P1 which is the connecting portion between the 12 and the third section 13 to the swing fulcrum 17 of the third section 13 is shorter than the distance L1 (due to the principle of leverage).

On the other hand, FIG. 4B shows a phase of reversing from forward to backward, and the trough side end portion (output) of the third section 13 with respect to the input in which the second section 12 rotates by driving the electric motor 41. ) Is large. This is because the distance L2 from the swing fulcrum 17 of the third section 13 to the pin P2, which is the connecting portion between the third section 13 and the fifth section 15, is the connecting portion between the second section 12 and the third section 13. This is because the distance from the pin P1 to the swing fulcrum 17 of the third section 13 is longer than the distance L1 (due to the principle of leverage). As described above, the conversion rate of the amount of movement between the input and the output is caused by the change in the lever ratio due to the change in the position of the swing fulcrum 17 with respect to the third section 13.

Therefore, in the phase where the trough 3 reverses from forward to backward, the operation of the output with respect to the input is large, so that the reverse from forward to backward is quickly performed. That is, the acceleration (deceleration) at the time of reversal is large. On the other hand, in the phase where the trough 3 reverses from backward to forward, the reverse from backward to forward is slowly performed because the output operation with respect to the input is small. That is, the acceleration (deceleration) at the time of reversal is small. Then, the maximum value of the acceleration (deceleration) of the trough 3 at the time of reversal from forward to backward is larger than the value of the static friction coefficient x gravitational acceleration between the work and the trough 3, so that the work and the trough 3 Slip occurs between them. The work moves forward relative to the trough 3 because it is a slip that occurs when reversing from forward to backward. As described above, the work in which the slip occurs in the reversal phase from forward to backward continues to advance relative to the trough 3 while decelerating due to the dynamic friction force. On the other hand, the trough 3 enters a reversal phase from backward to forward after performing a backward movement, and performs an acceleration movement in the forward direction. Eventually, the speed of the trough 3 and the speed of the work match, and a static frictional force acts. In the phase where the trough 3 reverses from backward to forward, the acceleration is smaller than in the phase where it reverses from forward to backward, so that slip does not occur between the trough 3 and the work, and the trough 3 is united while receiving static frictional force. Exercise. By repeating such movements by the trough, the work is conveyed forward.

The distance between the drive shaft 41A of the electric motor 41 and the swing fulcrum (corresponding to the shaft main body 82 in FIG. 1) 17 of the third section 13 may be adjustable. As a result, the movement pattern (magnitude of acceleration) of the trough 3 can be changed, and the movement of the trough can be optimally adjusted according to the characteristics of the work.
<Second Embodiment>

In the first embodiment, the plate member 51 that supports the drive unit 4 is fixed to the leg portion 52 installed on the ground G, so that the reaction force when the vibration conveyor 1 is driven is transmitted to the ground. However, it can be a simpler configuration. On the other hand, in the second embodiment, the reaction force when the vibration conveyor 1 is driven is not easily transmitted to the ground. Specifically, as shown in FIG. 5, it may be composed of a plurality of supports 18 (specifically, four arranged at the four corners of the plate member 51) that abut and support the plate member 51 from below. .. Each support 18 is rotatably attached to a fixed block 181 fixed to the ground G and a support member 182 extending above the fixed block 181 around the horizontal axis X1 to abut and support the lower surface of the trough 3. It is equipped with 183. A counterweight 19 is attached to the lower surface of the plate member 51.

By supporting the plate member 51 in this way, the plate member 51 can freely move linearly with respect to the ground, and receives a reaction force to move in the direction opposite to the movement of the trough 3. However, the reaction force transmitted from the plate member 51 to the ground is reduced. Since the amount of movement of the plate member 51 depends on the ratio of the weight to the trough 3, a counterweight 19 may be installed to balance the weight of the trough 3. The parts having the same configuration as that of the first embodiment are designated by the same reference numerals, and the description thereof is omitted.
<Third Embodiment>

As shown in FIG. 6, the vibration conveyor 1 shown in the second embodiment may be provided with a spring as an elastic body (here, a coil spring, but a spiral spring, a leaf spring, or the like) 20 may be provided. Good. Specifically, the rear end of the fixing block 21 fixed to the ground G on the front side and the front end of the plate member 51 are connected by a spring (coil spring) 20 along the front-rear direction (horizontal direction), and are connected to the ground G. The front end of the fixed block 21 located on the fixed rear side and the rear end of the plate member 51 are connected by a spring (coil spring) 20 along the front-rear direction (horizontal direction). By arranging the spring 20 in this way, the plate member 51 has a restoring force to a predetermined center position, and when the vibration conveyor 1 is driven, the plate member 51 and the trough 3 are centered on the predetermined position. You will be able to perform the reciprocating motion. The parts having the same configuration as that of the second embodiment are designated by the same reference numerals, and the description thereof will be omitted.
<Fourth Embodiment>

In the third embodiment, the case where the spring 20 is arranged in the horizontal direction is shown, but the spring 20 is omitted, and the plate member 51 has an R shape (circle) in which the portion of the lower surface of the plate member 51 with which the wheel 183 abuts projects upward. It may be composed of a member formed in the concave portion 51A (arc-shaped). In this case, as in the second embodiment, the plate member 51 has a restoring force to a predetermined center position, and when the vibration conveyor 1 is driven, the plate member 51 and the trough 3 are centered on the predetermined position. You will be able to perform the reciprocating motion. The parts having the same configuration as that of the third embodiment are designated by the same reference numerals, and the description thereof will be omitted.
<Fifth Embodiment>

In the first embodiment, the swing member 431 is rocked by the shaft 8, and the swing member 431 is slid by the elongated hole 431G of the swing member 431 through which the shaft 8 penetrates. Then, the swinging member 431 may be rocked and slid by the holding body 24 rotatably attached to the base member 81 fixed to the plate member 51. The holding body 24 is arranged so as to sandwich the swing member 431 from both sides in the lateral direction orthogonal to the longitudinal direction of the swing member 431 at the intermediate portion 431 between one end portion 431A and the other end portion 432B of the swing member 431. The two rollers 241,241 and the shafts 241A and 241A that rotatably support the rollers 241,241 are supported at both ends and the holding member 242 rotatably attached to the shaft 82 fixed to the base member 81. And have. Therefore, when the holding member 242 rotates around the shaft 82, the swinging member 431 swings, and the swinging member 431 is guided by the rotation of the rollers 241,241 on the holding member 242 in the linear direction of the arrow. By sliding, the rotational motion of the rotating member 42 can be converted into a linear reciprocating motion of the trough 3. By sliding the swing member 431 on the holding member 242 in this way, the distance between the longitudinal end portion 431A of the swing member 431 and the shaft 82, and the other end portion 431B and the shaft of the swing member 431 are obtained. The ratio change with the distance to 82 is smoothly performed. The parts having the same configuration as that of the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

The vibration conveyor according to the present invention is not limited to the above embodiment, and various modifications can be made without departing from the gist of the present invention.

For example, the rotating member 42 may be formed into a polygonal shape such as a triangular shape or a square shape, or a disk shape.

In the above embodiment, the connecting member 432 is connected to the trough 3 via the fixing plate 7, but the connecting member 432 may be directly connected to the trough 3.

Further, in the above-described embodiment, a tubular body is formed by forming a long hole 431A in the swinging member 431 and a fourth section 14 which is a sliding pair in the third section 13 corresponding to the swinging member 431. A long groove recessed upward may be formed in the swing member 431, and a roller 83 (a shaft may be used instead of the roller) may be engaged with the long groove.

Further, in the above-described embodiment, the drive shaft 41A is arranged in a vertical direction, but the drive shaft 41A may be arranged in a horizontal (horizontal) direction.

Further, in the above embodiment, the rotating member 42 is provided so that one end of the swinging member 431 moves on a perfect circle, but an elliptical member is provided so that one end of the swinging member 431 moves on an ellipse. May be good. The rotating member 42 and the elliptical member correspond to the rotating member.

1 ... Vibration conveyor, 2 ... Support part, 3 ... Trough, 4 ... Drive part, 5 ... Fixed part, 6 ... Power supply, 7 ... Fixed plate, 8 ... Shaft, 9 ... Rotating roller, 10 ... Shaft, 11 ... First Section (reference section), 12 ... second section, 13 ... third section, 14 ... fourth section, 15 ... fifth section, 16 ... sixth section, 17 ... rocking fulcrum, 18 ... support, 19 ... counter Weight, 20 ... Spring, 21 ... Fixed block, 22 ... Support member, 23 ... Wheel, 24 ... Holder, 31 ... Bottom wall, 32 ... Left and right wall, 41 ... Electric motor (drive source), 41A ... Drive shaft ( Rotating shaft), 41B ... Motor body, 42 ... Rotating member (circling member), 43 ... Conversion mechanism, 51 ... Plate member, 51A ... Recessed, 52 ... Leg, 81 ... Base member, 82 ... Shaft body, 83 ... Roller , 84 ... shaft, 181 ... fixed block, 182 ... support member, 183 ... wheel, 241 ... roller, 242 ... holding member, 431 ... swinging member, 431A ... one end, 431B ... other end, 431C ... intermediate part, 431G ... Slide portion (long hole), 432 ... Connecting member, 432A ... One end, 432B ... Other end, G ... Ground, L1, L2 ... Distance, P1, P2, P3 ... Pin, X, X1 ... Horizontal axis

Claims (4)

A reciprocating trough that conveys a work, an orbiting member that orbits by a driving force from a drive source, and a orbiting member provided between the orbiting member and the trough, and the orbiting movement of the orbiting member is linearly reciprocated by the trough. In a vibration conveyor equipped with a conversion mechanism for converting into motion,
The orbiting member orbits at a constant speed and
One end of the conversion mechanism is connected to the circumferential member, and the conversion mechanism is configured to swing around an axis substantially parallel to an axis passing through the orbital center of the orbital member at an intermediate portion between one end and the other end. A swing member and a connecting member having one end connected to the other end of the swing member and the other end connected to the trough are provided.
In the rocking member, the ratio of the distance between one end of the rocking member and the shaft and the distance between the other end of the rocking member and the shaft increases with the rotation of the rotating member. A vibrating conveyor characterized in that it is configured to be movable so as to change from moment to moment. The vibration conveyor according to claim 1, wherein the swing member includes a slide portion that can swing while holding the shaft and slides in the longitudinal direction while holding the shaft. The vibration conveyor according to claim 2, wherein the slide portion is composed of an elongated hole formed in the rocking member. The rocking member is used when the driving force transmitted to the trough via the connecting member is reversed in one direction from the other direction as compared with the case where the driving force transmitted to the trough is reversed from one direction to the other direction related to the linear reciprocating motion. The vibration conveyor according to any one of claims 1 to 3, wherein the vibration conveyor moves so as to increase the size.

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