TWI862771B - Vibrating conveyor - Google Patents

Abstract

The present invention provides a vibration conveying device, which includes an anti-vibration structure that can easily adjust the bumps without causing a significant increase in cost or complication of the structure. The vibration conveying device conveys a conveying object on a linear conveying surface by vibration, wherein the vibration conveying device includes a first mass body including the linear conveying surface, a second mass body vibrating in an opposite phase relative to the first mass body, a first elastic body connecting the first mass body and the second mass body, and a second elastic body connecting a base and the first elastic body, and with respect to the elastic coefficient of the second elastic body in the horizontal direction and the elastic coefficient of the second elastic body in the lead-vertical direction, at least the elastic coefficient of the second elastic body in the lead-vertical direction can be independently changed.

Description

Vibrating conveyor

The present invention relates to a vibrating conveying device capable of conveying an object in a predetermined direction.

In addition, the present invention relates to a rotary vibrator and a vibrating conveyor device that realizes a high frequency and large amplitude as a vibrator by properly installing the main mechanical elements that determine the resonance characteristics.

It has long been known that a vibrating conveying device can convey a conveying object such as a workpiece along a conveying path to a predetermined conveying destination by vibrating. The vibrating conveying device includes a movable portion (first mass body) including the conveying path, a second mass body functioning as a fixed portion, and a plate-shaped first elastic body (driving spring) connecting the first mass body and the second mass body, and is configured so that the conveying object can be conveyed to the downstream side of the conveying direction by vibrating the conveying path included in the movable portion (first mass body) in the horizontal direction. In addition, the vibrating conveying device is configured so that a structure including the first mass body, the second mass body, and the first elastic body is supported from the ground by a second elastic body (anti-vibration spring).

In such a vibrating conveying device, if the structure supported by the second elastic body generates a rotational motion in the vibrating conveying direction (similar to the motion of a shaking head, hereinafter referred to as "jolt") during vibration, the conveying path cannot vibrate uniformly, especially the vibration at the end of the conveying path (downstream end in the conveying direction) increases, the conveying object is roughly conveyed, resulting in poor connection with the next process, poor conveying, etc., which has an adverse effect on smooth conveying processing.

If the elastic main axis, the center of gravity of the first mass body, and the center of gravity of the second mass body, which are determined by the installation angle of the elastic body (drive spring), are completely consistent, the jolt can be prevented or effectively suppressed. However, it is difficult to apply a center of gravity design that fully meets the above conditions to actual equipment, so suppressing jolts is a difficult issue.

Therefore, the following technology has been proposed: by changing the angle of a flat spring (anti-vibration leaf spring) as an anti-vibration spring, adjusting the spring constant in the vertical direction of the anti-vibration leaf spring, and suppressing the vibration (Patent Document 1, Patent Document 2). When a flat spring (anti-vibration leaf spring) is used as an anti-vibration spring, the principle of suppressing the vibration by adjusting the spring constant in the vertical direction of the anti-vibration leaf spring is as follows.

That is, when the structure supported by the anti-vibration leaf spring is bumped (rotating), in order to suppress the bump, when the vertical direction of the anti-vibration leaf spring is strengthened (reinforced) to transmit the reaction force from the ground (stable base, etc.) to the structure, a force in the direction opposite to the rotation direction acts on the structure to suppress the bump. However, when the vertical direction of the anti-vibration leaf spring is strengthened (reinforced), the reaction force on the ground increases, affecting the mounted equipment, and the horizontal direction of the anti-vibration leaf spring is weakened. Therefore, as a design guideline, it is preferred to suppress the bump caused by the anti-vibration leaf spring after considering the optimal center of gravity design.

In addition, a vibration conveying device that can convey a conveying object such as a workpiece along a conveying path to a predetermined conveying destination by vibration has long been known. The vibration conveying device includes a movable portion (first mass body) including the conveying path, a second mass body that functions as a fixed portion, and a plate-shaped first elastic body (driving spring) connecting the first mass body and the second mass body, and is configured so that the conveying object can be conveyed to the downstream side of the conveying direction by vibrating the conveying path included in the movable portion (first mass body) in the horizontal direction using an excitation source. In addition, the vibration conveying device is configured so that a structure including the first mass body, the second mass body, and the first elastic body is supported from the ground by a second elastic body (anti-vibration spring).

As the production volume of the transported objects increases, the supply volume from the vibrating conveyor (the transport speed of the vibrating conveyor) is required to be increased above this. In order to increase the transport speed, increasing the frequency and amplitude is the first priority.

Therefore, in order to achieve high-frequency and large-amplitude vibration, a scheme has been proposed to use multiple thin leaf springs that will not break even at the target amplitude (the stacked leaf spring method) (Patent Document 3).

When such a stacked leaf spring method is adopted, the more the leaf springs are stacked, the larger the spring constant of the first elastic body is, and the higher the possibility of high-frequency vibration is. In addition, the drive spring that will not damage each leaf spring even under large amplitude can be mounted on the vibrating conveyor.

In addition, as a type of rotational vibration machine, for example, it has always been generally a structure as shown in FIG. 14. The rotational vibration machine 100 is configured to include a vibration plate 101 as a first mass body, a base 102 as a second mass body arranged opposite to the vibration plate 101 in the direction of the opposing axis m, an excitation source 103 that makes the vibration plate 101 and the base 102 vibrate relative to each other around the opposing axis m, and a first elastic body 104 arranged at a position connecting the vibration plate 101 and the base 102.

When a conveying path 105 is installed on the vibration plate 101 of such a rotary vibrator 100 as shown in FIG14 and used as a feeder PF as an article conveying device, in order to increase the conveying speed, the rotary vibrator 100 is also required to have a high frequency and a large amplitude.

For the rotary vibration machine 100, the first elastic body 104 is the main factor that determines the resonance characteristics. For example, when the first elastic body 104 is a leaf spring as shown in the figure, if the leaf spring 104 is thickened and lengthened, it can cope with the recent requirements for high frequency and large amplitude.

Patent document 4 shows an improved overlapping leaf spring structure for connecting the vibration plate and the base. Currently, it is composed of a single leaf spring, so there is a problem that it is easy to break due to the thick wall. In this regard, in this document, the function of one leaf spring is realized by multiple leaf springs, and each leaf spring is easy to bend, so as a whole, the problem of leaf spring breaking is eliminated.

Existing technical literature

Patent document 1: Japanese Patent Publication No. 2012-66931 (Japanese Patent Publication No. 5741993)

Patent document 2: Japanese Patent Publication No. 2007-276963 (Japanese Patent Publication No. 5332080)

Patent document 3: Japanese Patent Publication No. 09-124126 (Japanese Patent Publication No. 3509373)

Patent document 4: Japanese Patent Publication No. 2012-96853

In addition, if the structure is such that both the anti-vibration function (horizontal anti-vibration property) and the bump suppression function (vertical anti-vibration property) are realized by one anti-vibration spring, when the spring constant in the vertical direction is adjusted by the angle of the anti-vibration leaf spring, the spring constant in the horizontal direction of the anti-vibration leaf spring will definitely change. The degree of bumping can be changed by only slightly changing the tilt angle of the anti-vibration leaf spring, which requires strict angle adjustment.

In addition, since the vibration-proof leaf spring is placed between the base and the second mass body, the second mass body vibrates greatly in the horizontal direction, and the spring constant of the vibration-proof leaf spring in the horizontal direction needs to be reduced. As a result, the vibration-proof leaf spring is weakened in the horizontal direction, and when an impact is applied, misalignment occurs.

Therefore, in the existing vibration conveying device in which the anti-vibration spring is composed of a flat spring, only the angle of the anti-vibration leaf spring can be adjusted, so the adjustment in the vertical direction and the horizontal direction is in a compromise relationship, and the spring constants in the vertical direction and the horizontal direction cannot be adjusted independently.

The present invention focuses on such aspects, and its main purpose is to provide a vibrating conveying device including an anti-vibration structure that can easily adjust the bumps.

In addition, regardless of how the overlapping leaf spring method is adopted, the existing leaf spring is generally fixed by bolts at the position where the two ends of the first mass body and the second mass body are connected to each other.

Here, as a point for increasing the conveying speed, the point of increasing the peak value of the resonance characteristic (hereinafter, sometimes referred to as the resonance peak) can be cited. That is, even if the excitation force is the same, the higher the resonance magnification, the larger the amplitude can be obtained, and the larger the amplitude can be achieved with a small excitation force, which helps to increase the conveying speed.

However, in the existing structure where the two ends of the first mass body and the second mass body must be fixed by bolts when connected by a leaf spring, the friction between the leaf spring and the bolt washer increases the viscosity attenuation, which causes the resonance peak to decrease. In addition, due to the large elastic deformation (bending) of the leaf spring and the change in the fixed shape of the washer, the effective length of the leaf spring changes, and the leaf spring originally a linear characteristic spring becomes a nonlinear characteristic spring, which also becomes a factor that reduces the resonance peak and is also considered to be a factor that causes the drive frequency (resonance frequency) to decrease.

Furthermore, if the existing structure is to fix the leaf springs connecting the two ends of the first mass body and the second mass body with bolts, when the leaf spring is bent, a bending moment acts on the two ends (spring fixing ends) of the first mass body and the second mass body. As a result, the first mass body and the second mass body, which are rigid bodies, are expected to become elastic bodies that bend in an S shape. When the first mass body and the second mass body are bent in an S shape, friction is generated between the parts, and the viscosity attenuation increases, thereby reducing the resonance peak and the driving frequency.

The present invention focuses on such a point, and its main purpose is to provide a vibration conveying device that can exert large-amplitude vibration performance even with limited excitation force restricted by design, thereby increasing the conveying speed of the conveyed object.

In addition, in order to achieve high frequency and large amplitude, it is required to minimize the excitation loss. Excitation loss is the loss of excitation energy caused by internal friction between the spring and the fixed parts.

In FIG. 14 , the first elastic body 104 is composed of a rectangular leaf spring. The leaf spring 104 is rectangular and is arranged to extend around the opposing axis m between the vibration plate 101 and the base 102 in a direction inclined to the opposing axis m.

As shown in FIG15 , the center of the thickness direction and width direction of the base fixing side β of the leaf spring 104 is set as the origin O, the long side direction is set as the z-axis, the thickness direction is set as the x-axis, the width direction is set as the y-axis, and the opposing axis m is set as the rotation axis.

In the feeder PF shown in FIG14, when the vibration plate 101 and the base 102 rotate in different directions, the leaf spring 104 disposed on the periphery in the longitudinal direction generates a bending in the long-side direction, i.e., A-mode bending, formed by the x-direction force Fx, F'x and the fixed moment My, M'y around the y-axis, at both fixed ends of the spring on the origin O side and the opposite side, as shown in FIG16. That is, Fx, F'x and My, M'y also act on the vibration plate 101 and the base 102 to which the leaf spring 104 is fixedly connected at both ends.

Conventionally, methods for fixing the leaf springs such as the origin O and the opposite side include a method for fixing along the y-axis direction as shown in FIG. 17(a) and a method for fixing along the x-axis direction as shown in FIG. 17(b).

In the case of Figure 17(a), since the bolts are fixed in the y-axis direction, when the bending moment My around the y-axis is generated, the leaf spring 104 rotates and slides around the bolt v. When this sliding occurs, energy loss due to friction occurs, and the resonance magnification decreases. As a result, a large amplitude cannot be achieved with a small excitation force.

On the other hand, in the case of FIG. 17(b), since the bolt fixing is performed in the x-axis direction, the bolt fixing is performed in the orthogonal direction with respect to the force Fx in the x-axis direction as shown in FIG. 16, so there is no problem. However, as shown in FIG. 17(c), the bending moment My around the y-axis is transmitted to the rotating disk side fixing portion α, for example. That is, when the leaf spring 104 is deformed, it is originally bent in a spring cantilever beam type as shown by the dotted line in FIG. 17(c), but since it is held at the rotating disk side fixing portion α, the moment My around the y-axis as shown by the arrow in the figure is transmitted to the rotating disk side fixing portion α. At this time, when the connected vibration disk 101 is a thin disk-shaped device for lightness, the rotating disk side fixing portion α is subjected to bending moment, and the vibration disk 101 is undulating and twisted as shown in FIG17(d). Therefore, the spring does not bend in an S-shape, and the frequency cannot be increased, so high frequency cannot be achieved. In addition, due to the fluctuation of the vibration disk 101, contact interference and friction occur with the conveying body B arranged on the vibration disk 101, and excitation loss still occurs, and large amplitude cannot be achieved. When the spring is not bent in an S shape, the calculation of the elastic coefficient of the first elastic body requires the addition of the spring fixed end condition caused by the bending of the vibration plate 101, etc., resulting in a more complicated calculation formula.

However, if the vibration plate 101 as the first mass body is thickened, the inertial moment will increase, and if the outer periphery is thickened, it will be difficult to rotate. Therefore, it is also difficult to achieve high frequency and large amplitude.

This problem is exactly the same even in a single leaf spring structure before the leaf spring is stacked. In the case of a stacked leaf spring structure, there is also a problem of sliding between the leaf springs.

The purpose of the present invention is to realize a rotary vibrator and a vibrating conveying device. By properly installing the first elastic body, which is the main mechanical element that determines the resonance characteristics, on the mass body, the excitation loss caused by the sliding between the parts and the bending of the spring fixing parts can be eliminated, so that the high frequency and large amplitude of the vibrator can be realized.

That is, the first embodiment of the present invention relates to a vibration conveying device that conveys a transport object on a linear conveying surface by vibration. Here, as the transport object, for example, micro-sized electronic components (workpieces), medical components, etc. can be listed, but the components that can be transported by the vibration conveying device of this embodiment are not limited to these.

Moreover, the vibration conveying device of the present embodiment is characterized in that it includes a first mass body including a linear conveying surface, a second mass body vibrating in an opposite phase relative to the first mass body, a first elastic body connecting the first mass body and the second mass body, and a second elastic body connecting the base and the second mass body or the first elastic body, and the elastic coefficient of the second elastic body in the horizontal direction and the elastic coefficient of the second elastic body in the lead-vertical direction can at least independently change the elastic coefficient of the second elastic body in the lead-vertical direction.

Here, the "elastic coefficient of the second elastic body in the horizontal direction" and the "elastic coefficient of the horizontal component in the second elastic body" in this embodiment have the same meaning, and the "elastic coefficient of the second elastic body in the lead-vertical direction" and the "elastic coefficient of the lead-vertical component in the second elastic body" have the same meaning. In addition, the "horizontal direction" in this embodiment refers to the direction along the elastic main axis specified by the installation angle of the first elastic body (the direction parallel or substantially parallel to the elastic main axis), and the "lead-vertical direction" in this embodiment refers to the direction orthogonal or substantially orthogonal to the elastic main axis (the normal direction relative to the elastic main axis). That is, in the present embodiment, the horizontal direction and the lead-vertical direction of the second elastic body are determined based on the elastic principal axis of the first elastic body, and the horizontal direction in the "elastic coefficient in the horizontal direction of the second elastic body" is sometimes consistent with the direction intersecting the earth's gravity direction at right angles (the horizontal direction defined physically), and sometimes is a direction not intersecting the earth's gravity direction at right angles. Similarly, the lead-vertical direction in the "elastic coefficient in the lead-vertical direction of the second elastic body" is sometimes consistent with the earth's gravity direction (the lead-vertical direction defined physically), and sometimes is inconsistent with the earth's gravity direction. The vibrating conveying device of this embodiment has no particular limitation on the appearance of the second elastic body, as long as the structure can at least independently change the elastic coefficient of the second elastic body in the vertical direction.

According to the vibrating conveying device of this embodiment, when the first elastic body connecting the first mass body and the second mass body is driven to vibrate by an appropriate excitation mechanism, the second mass body functions as a fixed part (balance weight) and the second elastic body functions as a vibration-isolating body, so that the first mass body vibrates and can transport the conveying object on the linear conveying surface along a predetermined conveying direction. Furthermore, according to the vibrating conveying device of the present embodiment, the elastic coefficient in the horizontal direction of the second elastic body and the elastic coefficient in the lead-vertical direction of the second elastic body are constructed so as to be able to at least independently change the elastic coefficient in the lead-vertical direction of the second elastic body. Therefore, the elastic coefficient in the lead-vertical direction of the second elastic body can be set to an elastic coefficient that can suppress bumps without affecting the elastic coefficient in the horizontal direction of the second elastic body, thereby realizing a device that can easily perform bump adjustment. Therefore, the elastic coefficient of the second elastic body in the horizontal direction can be set to a coefficient that can suppress bumps without affecting the elastic coefficient of the second elastic body in the horizontal direction, while setting the device to be difficult to displace even when an impact is applied from the outside (strong impact resistant device).

In particular, if the vibrating conveying device of the present embodiment is configured to independently change the elastic coefficients of the second elastic body in the horizontal direction and the lead-vertical direction, it is possible to adjust the elastic coefficient of the second elastic body in the lead-vertical direction without changing the elastic coefficient of the second elastic body in the horizontal direction, thereby facilitating the adjustment of the turbulence, and by not changing the elastic coefficient of the second elastic body in the horizontal direction, By adjusting only the elastic coefficient in the horizontal direction of the second elastic body (for example, maintaining the elastic coefficient that can suppress bumps), the elastic coefficient in the horizontal direction of the second elastic body can be set larger, and a device that is unlikely to be dislocated even when an impact is applied from the outside can be realized (strong impact resistant device).

In particular, if the vibrating conveying device of this embodiment installs one end of the second elastic body on the vibrating node of the first elastic body, since the node is a part that does not displace (does not vibrate) in the horizontal and vertical directions, by installing one end of the second elastic body on the node, a vibration-proof effect is played, thereby enabling the horizontal elastic coefficient of the second elastic body to be set larger. In addition, the node can be specified as a point, but the "node of the first elastic body" in this embodiment is a concept that includes a predetermined area in the first elastic body that includes a node that can be specified as a point.

In addition, Japanese Patent Publication No. 11-91928 discloses a piezoelectric drive type conveying device comprising i) a structure in which an inertial mass is fixed on the upper surface of a transversely arranged exciter and an exciter mounting member is fixed on the lower surface, ii) a structure in which the exciter mounting member and the conveying member are connected and fixed via a first connecting member arranged vertically and obliquely, iii) a connecting member support piece is fixed to the middle portion of the long side direction of the first connecting member, and the connecting member is fixed to the middle portion of the long side direction of the first connecting member. The structure in which the component support piece and the base are connected and fixed via the second connecting member, in particular, the structure in which one end of the second connecting member is fixed to the two end sides of the base by a mechanism such as thread fixing, the other end of the second connecting member is fixed to the connecting member support piece, and the connecting member support piece is fixed to the node portion of the first connecting member, can significantly reduce the vibration from the base supporting the piezoelectric drive type conveying device to the installation surface thereof. Here, the component "fixed to the node portion of the first connecting member" in the publication is not an elastic body but a connecting member support piece, which is clearly different from the present embodiment. Therefore, it can be easily understood that the structure described in the bulletin cannot fully adjust the spring coefficient in the vertical direction that is involved in suppressing turbulence.

In the vibration conveying device of the present embodiment, when an elastic body including at least one of a horizontal arm capable of adjusting the elastic coefficient relative to the vibration component in the lead-vertical direction and a lead-vertical arm capable of adjusting the elastic coefficient relative to the vibration component in the horizontal direction is applied as the second elastic body, the shape is simple and the structure capable of achieving the purpose of the present embodiment. It may also include both the horizontal arm and the lead-vertical arm, or only one of the arms. In addition, the horizontal arm and the lead-vertical arm of the second elastic body do not necessarily have to be in an orthogonal relationship, and may also be in a non-orthogonal relationship (a relationship in which the horizontal arm and the lead-vertical arm intersect at an angle other than 90 degrees).

In the case where an elastic body including a horizontal arm and a lead-vertical arm is applied as the second elastic body, if the structure includes an elastic adjustment component that presses at least one of the horizontal arm and the lead-vertical arm in the thickness direction, and the effective length of the arm to be adjusted can be changed by adjusting the area pressed to be unable to elastically deform by the elastic adjustment component, the effective length of the arm can be simply adjusted while maintaining the relative positional relationship between the arm and the connecting target component (the base and the second mass body or the first elastic body) of the arm in an appropriate positional relationship, and as a result, the elastic coefficient of at least one of the elastic coefficient of the vibration component relative to the lead-vertical direction and the elastic coefficient of the vibration component relative to the horizontal direction can be simply adjusted.

In particular, if the second elastic body is an L-shaped leaf spring (a flat leaf spring is bent into an L shape) that includes a horizontal arm and a lead-vertical arm, the elastic coefficient (spring constant) in the lead-vertical direction and the elastic coefficient (spring constant) in the horizontal direction of the second elastic body can be set to appropriate values by appropriately adjusting or changing the effective length of either the horizontal arm or the lead-vertical arm, or the effective length of both. Here, if the effective length in the longitudinal direction of the L-shaped leaf spring (the effective length of the lead-vertical arm) is adjusted, the spring constant in the horizontal direction can be adjusted, and if the effective length in the transverse direction of the L-shaped leaf spring (the effective length of the horizontal arm) is adjusted, the spring constant in the vertical direction can be adjusted.

In addition, the second embodiment of the present invention relates to a vibration conveying device that conveys a conveying object on a linear conveying surface by vibration. Here, as the conveying object, for example, micro-sized electronic components (workpieces), medical parts, etc. can be listed, but the parts that can be conveyed by the vibration conveying device of this embodiment are not particularly limited.

Moreover, the vibration conveying device of the present embodiment includes a first mass body including a linear conveying surface, a second mass body arranged at a position opposite to the first mass body in the height direction and vibrating in an anti-phase relative to the first mass body, and a first elastic body connecting the first mass body and the second mass body, so that at least a portion of the first mass body, at least a portion of the second mass body and the first elastic body are an integrated structure.

Here, the form of "making at least a part of the first mass body, at least a part of the second mass body, and the first elastic body into an integrated structure" in this embodiment includes i) a form in which the entire first mass body, the entire second mass body, and the first elastic body are an integrated structure, ii) a form in which a part of the first mass body, the entire second mass body, and the first elastic body are an integrated structure, iii) a form in which the entire first mass body, a part of the second mass body, and the first elastic body are an integrated structure, iv) a form in which a part of the first mass body, a part of the second mass body, and the first elastic body are an integrated structure, and all of these forms. Hereinafter, a block that becomes an integrated structure is set as an integrated structure. The linear conveying surface constitutes the first mass body, but in the case of adopting the form of ii) and the form of iv), the first mass body includes components constituting an integral structure and components separate from the integral structure, and it can be appropriately selected whether the components constituting the integral structure in the first mass body form the linear conveying surface or the components separate from the integral structure form the linear conveying surface.

According to the vibration conveying device of the present embodiment, at least a part of the first mass body, at least a part of the second mass body, and the first elastic body are integrally structured, so that no friction is generated at the connection portion between the first mass body and the first elastic body, and at the connection portion between the second mass body and the first elastic body, and compared with the structure in which the first elastic body is fixed to the first mass body and the second mass body by a fixing member such as a bolt, the viscosity coefficient is reduced and the resonance peak value does not decrease. In addition, even when the amplitude is large, the fixing condition (connection condition at the connection portion) does not change, and the reduction of the driving frequency (resonance frequency) caused by the nonlinearity of the spring constant of the first elastic body can be reduced. Here, if the first elastic body is fixed to the first mass body and the second mass body by a fixing member such as a bolt, the larger the amplitude of the first elastic body, the more gaps are generated between the leaf spring as the first elastic body and the bolt end face in contact with the leaf spring in the bolt, and between the leaf spring and the contact surface in contact with the leaf spring in the first mass body or the second mass body, and the effective length of the leaf spring increases, thereby reducing the spring constant. Such a change in the spring constant relative to the amplitude displacement is called the nonlinearity of the spring constant of the first elastic body. In the existing vibration conveying device, if the amplitude is large, the spring constant decreases, and the driving frequency tends to decrease. Therefore, according to the vibration conveying device of this embodiment, the factor of reducing the resonance peak value that is inevitable in the existing structure of fixing the first elastic body to the first mass body and the second mass body by bolts and other fixing parts can be completely eliminated, and a large amplitude can be achieved with a small excitation force.

In the vibration conveying device of the present embodiment, the position of connecting the first mass body and the second mass body through the first elastic body is not particularly limited, but in order to ensure a stable support state, it is preferred to use a structure based on the existing connection part based on the driving spring, that is, the structure of arranging the first elastic body at the position of connecting the ends of the first mass body and the second mass body on the upstream side of the conveying direction of the conveying object and the ends on the downstream side of the conveying direction.

In the conventional structure of a leaf spring in which both ends of a first mass body and a second mass body are connected to each other by bolts, when the leaf spring is bent, a bending moment acts on both ends of the first mass body and the second mass body (spring fixing ends), thereby causing the first mass body and the second mass body, which are expected to be rigid bodies as the fixing parts of the spring, to bend in an S-shape. At this time, the first mass body and the second mass body, which are the fixing parts of the spring, are bent, so that the spring cannot be fixed, the spring constant decreases, and the frequency decreases. In addition, friction is generated between the components, and the viscosity attenuation increases, thereby reducing the resonance peak. Therefore, if a vibration conveying device is provided with a first elastic body at the midway position between the upstream side end portion in the connecting conveying direction and the downstream side end portion in the conveying direction of the first mass body and the second mass body, the first elastic body is used to support the first mass body and the second mass body at both ends and the midway portion in the conveying direction (front-rear direction), so that the first elastic body arranged in the midway portion realizes the function of a rib, and the bending rigidity of the first mass body and the second mass body can be improved, thereby further reducing the bending change of the first mass body and the second mass body, and suppressing the deformation of the linear conveying path. In addition, the spring constant is improved, and it becomes a structure that satisfies the good conditions of high driving frequency and reduced friction between components to increase the resonance peak.

As described above, the first mass body may also include components constituting an integrated structure and components separate from the integrated structure. However, in the latter case, if the first mass body includes a first mass body main body constituting a main frame (integrated structure) constituting an integrated structure and a conveying path separate from the first mass body main body and including a linear conveying surface, the linear conveying path requiring a high degree of design specifications can be prepared as a dedicated component separate from the main frame, and the processing burden during the manufacture of the main frame as an integrated structure can be reduced.

Furthermore, if it is a vibration conveying device in which a plurality of first elastic bodies are separately arranged between the first mass body and the second mass body along the conveying direction of the conveyed object, the space separated by the first elastic bodies adjacent to each other in the conveying direction is formed in the internal space of the integrated structure (main frame), and if the space is a relatively large space, the space can also be used as an access space for mounting a piezoelectric element on the first elastic body, for example.

In addition, the third embodiment of the present invention contemplates the following mechanism in order to achieve the above-mentioned purpose.

That is, the rotary vibrator of the present embodiment is characterized in that it includes a first mass body, a second mass body arranged opposite to the first mass body in the direction of the opposing axis, an excitation source for causing the first mass body and the second mass body to vibrate relative to each other around the opposing axis, and a first elastic body arranged at a position connecting the first mass body and the second mass body, wherein the first elastic body is configured to include a leaf spring, a first continuously arranged portion continuously arranged on one end side of the leaf spring and forming a part of the first mass body, and a second continuously arranged portion continuously arranged on the other end side of the leaf spring and forming a part of the second mass body, wherein at least the first continuously arranged portion is connected to the main body of the first mass body in a direction parallel to the opposing axis by a connecting member.

If the thickness direction of the leaf spring is set to the x direction, the width direction is set to the y direction, and the long side direction is set to the z direction, then when the two ends of the leaf spring are fixed to the first mass body and the second mass body and deformed into an S shape, a bending moment around the y axis is applied. However, according to the above structure, the axial force of the connecting member is orthogonal to the opposite direction, that is, the bending moment around the axis, so it is difficult to produce sliding around the fixed part. In addition, at least the first elastic body is integrated with a part of the first mass body through the first continuous setting part, so that it can bear the fixed torque through the rigidity of the component, and the occurrence of bending of the first mass body can be suppressed, and the appropriate parallel movement of the first mass body can be achieved. As a result, the excitation loss caused by the sliding between the first continuous setting part and the first mass body and the bending of the first mass body is eliminated, the resonance magnification is high, and even a small excitation force can appropriately achieve high frequency and large amplitude.

In this case, it is preferred that the second continuously disposed portion and the main body portion of the second mass body are connected along a first direction intersecting the opposing axis direction and a second direction intersecting the opposing axis direction and the first direction.

Therefore, the torsional stress of the first elastic body on the second mass body side can be strongly fixed between the second continuous setting part.

Alternatively, it is preferred that the second continuously disposed portion and the main body portion of the second mass body are also connected along the direction of the opposing axis.

Therefore, between the second continuous setting part and the second mass body, as between the first continuous setting part and the first mass body, the excitation loss caused by the sliding between the parts and the bending of the spring fixing part can be eliminated.

In the above, it is preferred that the second mass body is the fixed side and the first mass body is the movable side. Here, the movable side refers to the side including the vibrating object such as the transport body, and the fixed side refers to the side that realizes the function of the balancing weight of the movable side.

In this way, by setting the first mass body on the movable side, the sliding of the movable part and the bending of the spring fixing part can be eliminated preferentially.

It is particularly preferred that the first continuously disposed portion and the main body portion of the first mass body are connected at least at two locations along the direction of the opposing axis.

In this way, the leaf spring is firmly held at multiple locations on the main body of the first mass body via the first continuous setting portion, so that the first mass body will not bend or tilt and can move parallel to the second mass body.

Furthermore, if a vibrating conveying device is formed by any of the above-described rotary vibrators and a conveying body fixed to the above-mentioned first mass body and including a spiral conveying path, the conveying speed of the items on the conveying body can be effectively increased.

The effects of the present invention are as follows.

According to the first embodiment of the present invention, the second elastic body connecting the base and the second mass body or the first elastic body is configured to independently change the elastic coefficient of the second elastic body in the vertical direction without affecting the elastic coefficient of the second elastic body in the horizontal direction, thereby providing a vibration conveying device including an anti-vibration structure that can easily adjust the bumps.

In addition, according to the second embodiment of the present invention, an unprecedented new structure is adopted in which at least a part of the first mass body, at least a part of the second mass body, and the first elastic body are integrated into one structure, which can increase the driving frequency of the vibration of the integrated structure (main frame) and provide a vibration conveying device that can achieve a high resonance magnification and obtain a large amplitude.

In addition, according to the third embodiment of the present invention, by properly installing the first elastic body, which is the main mechanical element that determines the resonance characteristics, on the mass body, it is possible to eliminate the excitation loss caused by sliding between parts and bending of the spring fixing parts, and to realize a new rotary vibrator and vibrating conveyor with high frequency and large amplitude.

1: First mass body

2: Second mass body

2a: Anti-vibration components

3: The first elastic body

4: Base

5: Second elastic body

6: Elastic adjustment parts

7: First mass body (rotating disk)

8: Second mass body (base)

9: Excitation source

10: Vibration plate main body

11: Movable counterweight

12: Side connecting plate

13: Slide table

14: Transportation Road

16: First connection part on the vibration plate side

17: Second connection part on the vibration plate side

20: Main body of the second mass body (base body)

21:Balance weight

22: Second connection part on the base side

23: Second leaf spring accommodating portion

24: Connecting part abutment part

26: First connection part on the base side

31: Piezoelectric components

32: protrusion

33: Internal thread hole

36: Connecting parts

37: Second leaf spring

38: Piezoelectric element drive unit

40: Leaf spring

40′: Leaf spring

40m: Central part

40e1, 40e2: upper and lower ends

41: Internal thread hole

42: Second connection part (second continuous setting part)

42a: Bottom

42b: Right side

42c: Left side

44: First continuous setting unit

51: Lead drop arm

52: Horizontal arm

5A: L-shaped leaf spring (L-shaped spring)

61: Long hole

100: Rotary vibrator

101: Vibrating plate

102: Base

103: Excitation source

104: First elastic body (leaf spring)

105: Install the conveyor belt

400: First elastic body

A: Rotary vibrator

B: Transporter

B1: Bolt

B2: Bolts

D: Width dimension in y direction

Fx, F′x: force in x direction

Fy: Force in y direction

K: Workpiece (transport object)

M: Main frame

m: Opposing axis

Mx: torque

My, M′y: moment (bending moment)

Mz: torque

MS: Inner space (space)

PF: Vibrating conveyor (feeder)

T: Transport direction (front and back)

W: width direction

s: first direction

u: Second direction (fastening direction)

v: bolt

v1: Bolt

v21: Bolts

v22: Bolts

v3: Connectors (bolts)

v4: Bolts

v5: Bolts

X: Vibrating conveyor (linear feeder)

α: Vibration plate side fixing part

β: Abutment side fixing part

h3:Hole for connection

h4: Connection hole

h5: Connection hole

FIG1 is a schematic top view of the entire vibrating conveying device (linear feeder) of the first embodiment and the second embodiment of the present invention.

Figure 2 is an exploded perspective view of the vibration conveying device of the first embodiment and the second embodiment.

Figure 3 is an enlarged view of the main part of Figure 2.

FIG4 is a partially omitted side view of the vibrating conveyor device viewed from the direction of arrow A in FIG1.

Figure 5 is a three-dimensional diagram showing a rotary vibrator and a vibrating conveying device according to the third embodiment of the present invention.

Figure 6 is an exploded view of Figure 5.

Figure 7 is an illustration of the main parts of Figure 6.

FIG8 is a three-dimensional diagram showing the first elastic body constituting the third embodiment.

Figure 9 is a diagram illustrating the structure and installation of the first elastic body.

Figure 10 is a diagram illustrating the function of the first elastic body.

FIG11 is a diagram showing a variation of the third embodiment.

FIG12 is a diagram showing another variation of the third embodiment.

FIG. 13 is a diagram of yet another variation of the third embodiment.

FIG. 14 is a perspective view showing a conventional rotary vibrator and a vibrating conveying device.

FIG15 is an explanatory diagram of the first elastic body of the prior art.

Figure 16 is an explanatory diagram of the vibration mode of the first elastic body.

Figure 17 is a diagram illustrating the problem of the prior art.

<First implementation method>

Below, the first embodiment of the present invention is described with reference to the drawings.

As shown in FIG. 1 , the vibration conveying device X of the present embodiment is a device that moves a workpiece K such as an electronic component on a conveying path 14 (the linear conveying path 14 described later) by vibration, and conveys it to a predetermined conveying destination (supply destination). The vibration conveying device X of the present embodiment is a device that conveys the workpiece K along a straight-line conveying path 14 (hereinafter referred to as "linear conveying path 14") to a conveying destination. In addition, the downstream end (not shown) of the conveying path (hopper conveying path) of a hopper feeder that arranges and conveys while being connected to the upstream end of the linear conveying path 14. Therefore, the linear feeder X can convey the workpiece K conveyed via the conveying path (hopper conveying path) formed in the hopper feeder to the terminal end of the linear conveying path 14 by vibration, and supply it to a predetermined conveying destination. The linear feeder X includes a return section (return conveying path). When overflow occurs or the workpiece K is judged not to be in the predetermined conveying posture, the return section (return conveying path) returns the workpiece K (overflowing workpiece K, workpiece K judged not to be in the predetermined conveying posture) to the hopper conveying path.

As shown in Figures 1 to 4, the linear feeder X includes a first mass body 1 including a linear conveying surface, a second mass body 2 vibrating in an opposite phase relative to the first mass body 1, a first elastic body 3 connecting the first mass body 1 and the second mass body 2 to each other, a base 4, and a second elastic body 5 connecting the base 4 and the first elastic body 3 to each other.

In this embodiment, a movable counterweight 11 (movable part) as a main component of the first mass body 1 is arranged above the base 4 including a strip shape along the conveying direction T, a balancing counterweight 21 (fixed part) as a main component of the second mass body 2 is arranged above the movable counterweight 11 via the first elastic body 3, and a chute table 13 connected to the movable counterweight 11 is arranged above the balancing counterweight 21 via the side connecting plate 12. In this embodiment, as shown in FIG. 2, the movable counterweight 11 and the chute table 13 are connected to each other via a pair of side connecting plates 12. In addition, in FIG. 4, the side connecting plate 12 near the front side of the paper surface is omitted in the pair of side connecting plates 12.

The conveying path 14 is detachably mounted on the upper surface of the chute table 13 by bolts and other fixing parts. By giving vibration to the conveying path 14, the workpiece K moves in the linear conveying surface (conveying trough) provided in the conveying path 14. The chute table 13 moves synchronously with the vibration of the movable counterweight 11 and functions as a vibration transmission part that transmits the vibration of the movable counterweight 11 to the conveying path 14.

In the following description, the conveying direction T of the workpiece K along the conveying path 14 is set as the front-rear direction T, the upstream side of the conveying direction T is set as the rear side, and the downstream side of the conveying direction T is set as the front side. In addition, the direction orthogonal to the conveying direction T in the horizontal plane is set as the width direction W (cross-sectional direction) (refer to Figure 1, etc.).

As shown in Figures 2 and 4, the front and rear ends of the chute platform 13 are suspended portions that protrude forward and backward respectively from the movable counterweight 11. For example, a movable counterweight (not shown) can also be installed on the downward facing surface of the front suspended portion of the chute platform 13. The side connecting plate 12, the chute platform 13, and the conveying path 14 are components that constitute the first mass body 1 in the same manner as the movable counterweight 11.

In this embodiment, the dimensions (front-rear dimensions) of the movable counterweight 11 as the main component of the first mass body 1 and the balancing counterweight 21 as the main component of the second mass body 2 along the conveying direction T are set to be approximately the same, and these balancing counterweights 21 and movable counterweights 11 are arranged in a posture facing each other in the height direction.

In the linear feeder X of this embodiment, a first elastic body 3 is arranged at the positions connecting the front ends and rear ends of the movable counterweight 11 and the balancing counterweight 21.

The first elastic body 3 is in the form of a flat spring (leaf spring) whose thickness direction is roughly consistent with the conveying direction T. A piezoelectric element 31 that functions as an excitation source is attached to the first elastic body 3. By applying a charge to the piezoelectric element 31, the first elastic body 3 is elastically deformed to generate vibration, and the first mass body 1 and the second mass body 2 vibrate. Thus, the first elastic body 3 functions as a driving spring. The first elastic body 3 of this embodiment is set to a normal posture in which no elastic deformation occurs, which is a posture standing upright in the plumb direction. The spring constant formed by the first elastic body 3 and the piezoelectric element 31 is appropriately selected according to the conditions of an arbitrary resonance frequency determined by the weight and size of the transported component and the weight of the transport path 14 (groove). In this embodiment, the first mass body 1 and the second mass body 2 are connected through a plurality of first elastic bodies 3.

In addition, in the present embodiment, the first elastic body 3 is also arranged at the predetermined midway position between the front and rear ends of the movable weight 11 and the balance weight 21. The first elastic bodies 3 are arranged in pairs at their respective arrangement positions (positions connecting the movable weight 11 and the balance weight 21) with a slight gap in between along the front-rear direction T. In the present embodiment, two first elastic bodies 3 are arranged in a manner along the front-rear direction T at the portion connecting the front ends of the movable counterweight 11 and the balancing weight 21, at the portion connecting the rear ends of the movable counterweight 11 and the balancing weight 21, at the portion between the front and rear ends of the movable counterweight 11 and the balancing weight 21, which is offset from the center of the front-rear direction T to the front end side by a predetermined distance, and at the portion between the front and rear ends of the movable counterweight 11 and the balancing weight 21, which is offset from the center of the front-rear direction T to the rear end side by a predetermined distance. That is, a total of eight first elastic bodies 3 are arranged in these four portions.

The linear feeder X of this embodiment forms an integrated structure of the main component of the first mass body 1, namely the movable counterweight 11, the main component of the second mass body 2, namely the balancing counterweight 21, and the first elastic body 3 (hereinafter, the integrated structure is referred to as the "main frame M"). As a result, no friction is generated at the connection part between the first mass body 1 and the first elastic body 3, and the connection part between the second mass body 2 and the first elastic body 3, the viscosity coefficient is reduced, and even at a large amplitude, the fixing condition (connection condition of the connection part) does not change, and the nonlinearity of the spring is reduced.

In addition, the first elastic body 3 is used to support the movable counterweight 11 and the balancing counterweight 21 at both ends and the middle part in the front-rear direction T. Therefore, the bending change of the movable counterweight 11 and the balancing counterweight 21 is reduced, especially the friction between the movable counterweight 11 of the main frame M and the side connecting plate 12 is reduced, and the viscosity coefficient is reduced. Furthermore, if the first elastic body 3 is fixed to the first mass body 1 (movable counterweight 11) and the second mass body 2 (balance counterweight 21) by bolts or other fixing parts, it is necessary to ensure the configuration space of the fixing parts. However, according to this embodiment, it is not necessary to ensure the configuration space of the fixing parts. Therefore, the height dimension of the first mass body 1 can be set larger, and the bending rigidity can be improved. As a result, the first mass body 1 (movable counterweight 11) is difficult to bend in an S shape, and the driving frequency is increased. In this way, according to the linear feeder X of this embodiment, the driving frequency and amplitude of the vibration of the structure (main frame M) can be increased, and a high resonance magnification can be achieved to obtain a large amplitude.

In the linear feeder X of this embodiment, the first elastic body 3 disposed in the middle between the front end and the rear end of the first mass body 1 (movable counterweight 11) and the second mass body 2 (balance counterweight 21) realizes the function of a rib, thereby making it difficult for the first mass body 1 and the second mass body 2 to bend in an S shape.

In this embodiment, a main frame M including a movable counterweight 11, a balancing counterweight 21 and a first elastic body 3 is formed by performing wire cutting on a piece of metal raw material. In addition, the main frame M can also be formed by processing other than wire cutting.

In the linear feeder X of the present embodiment, for example, a balancing weight (sub-balancing weight) separated from the main frame M may be integrally mounted on the balancing weight 21. As the location where the sub-balancing weight is installed, the internal space MS of the main frame M, that is, the relatively large space MS formed between the first elastic bodies 3 adjacent to each other along the conveying direction T (except for the space between two first elastic bodies 3 arranged closely in a group) can be cited. In this case, mainly when the sub-balancing weight is installed in the internal space MS of the main frame M, the sub-balancing weight satisfies the condition of not contacting the components (first elastic body 3, piezoelectric element 31, movable weight 11, side connecting plate 12) other than the balancing weight 21. The sub-balancing weight is a component constituting the second mass body 2 similarly to the balancing weight 21. The size of the internal space MS of the main frame M (the larger space MS separated by the first elastic body 3 adjacent to each other in the conveying direction T) can also be equal in size (equally divided) as shown in Figures 3 and 4, or unequal in size (unequally divided). In addition, Figure 3 is an enlarged view of the main part of Figure 2. In addition, the internal space MS of the main frame M can also be used as an access space for installing the piezoelectric element 31 on the first elastic body 3.

Here, the vibration conveying device X of this embodiment includes a structure (main frame M), which integrally includes a movable counterweight 11, which is a main component of the first mass body 1 of the movable part, a balance counterweight 21, which is a main component of the second mass body 2 that functions as a fixed part relative to the movable counterweight 11, and a first elastic body 3, and is configured so that the structure (main frame M) is supported by the second elastic body 5 from the ground (the base 4 that can be regarded as the ground in this embodiment), and the second elastic body 5 functions as an anti-vibration spring.

As shown in Figures 2 to 4, the linear feeder X of this embodiment is provided with second elastic bodies 5 in front and rear of the main frame M, respectively, and the base 4 and the main frame M are connected by each second elastic body 5.

In this embodiment, a flat L-shaped elastic member (L-shaped spring 5A) including a vertical arm 51 extending in the vertical direction and a horizontal arm 52 extending in the horizontal direction is used to constitute the second elastic body 5. The second elastic body 5 shown in FIG. 2 and the like fixes the front end (upper end) of the vertical arm 51 to the first elastic body 3, and fixes the front end (the end on the side where the vertical arm 51 is not erected) of the horizontal arm 52 to the base 4.

In the present embodiment, a protrusion 32 protruding forward or backward is provided at the portion of the node that does not displace in the horizontal and vertical directions in the first elastic body 3, and the front end portion of the vertical arm portion 51 is fixed to the protrusion 32. In addition, the first elastic body 3 has both ends (upper end and lower end) fixed to the movable counterweight 11 and the balance counterweight 21 respectively (both ends are fixed and suspended), so the node is the central portion in the long side direction. Here, the node of the first elastic body 3 is enough to be a point, but the area where the protrusion 32 is provided in the first elastic body 3 is a predetermined area including the node of the first elastic body 3 (the node and the vicinity of the node). An internal threaded hole 33 is provided at two locations of the protrusion 32 separated along the width direction W (refer to FIG. 3). The lead arm 51 is formed with a bolt insertion hole connected to each internal threaded hole 33. By inserting the bolt B1 through the bolt insertion hole and threading it into the internal threaded hole 33, the lead arm 51 of the second elastic body 5 can be fixed to the first elastic body 3. A pressing plate is interposed between the head of the bolt B1 and the lead arm 51 of the second elastic body 5.

Internal threaded holes 41 are provided at two locations separated along the width direction W at the front and rear ends of the base 4 (see FIG. 3 ). Internal bolt insertion holes connected to each internal threaded hole 41 are formed in the horizontal arm 52. By inserting the bolt B2 through the internal bolt insertion hole and threading it into the internal threaded hole 41, the horizontal arm 52 of the second elastic 5 can be fixed to the base 4.

In the linear feeder X of this embodiment, the second elastic body 5 is arranged at a position that does not overlap with the first elastic body 3 in the conveying direction T, and the upper end of the second elastic body 5 is mounted on the node of the first elastic body 3 that is approximately the center of the height direction H. Therefore, when the first mass body 1 vibrates, the vibration of the conveying path 14 is stable, and a more stable component conveying process can be achieved accordingly.

In addition, in order to implement more stable workpiece conveying processing, it is necessary to prevent the conveying path 14 from generating jolts.

In the linear feeder X of the present embodiment, the elastic coefficients of the second elastic body 5 in the horizontal direction and the lead-vertical direction are independently adjusted without changing the tilt angle of the front-rear direction T of the first elastic body 3, so that the vibration of the first elastic body 3 can be adjusted to the desired vibration with no or almost no jolt. Here, the "elastic coefficient of the horizontal direction of the second elastic body" in the present embodiment has the same meaning as the "elastic coefficient of the horizontal component in the second elastic body", and the "elastic coefficient of the lead-vertical direction of the second elastic body" has the same meaning as the "elastic coefficient of the lead-vertical component in the second elastic body". In addition, the "horizontal direction" in this embodiment refers to the direction along the elastic main axis (the direction parallel or substantially parallel to the elastic main axis) specified by the mounting angle of the first elastic body 3, and the "plumb-vertical direction" in this embodiment refers to the direction orthogonal or substantially orthogonal to the elastic main axis (the normal direction to the elastic main axis). In the linear feeder X of this embodiment, a flat L-shaped second elastic body 5 including a horizontal arm 52 that can adjust the elastic coefficient of the vibration component in the plumb-vertical direction and a plumb-vertical arm 51 that can adjust the elastic coefficient of the vibration component in the horizontal direction is used, so as to realize a structure in which the elastic systems in the horizontal and plumb-vertical directions of the second elastic body 5 can be independently adjusted without affecting each other.

In the present embodiment, as shown in Fig. 3 and Fig. 4, a flat elastic adjustment member 6 is arranged at the position of the front end portion of the horizontal arm 52 of the L-shaped leaf spring 5A sandwiching the horizontal portion of the second elastic body 5 in the height direction H, and these elastic adjustment members 6 and the horizontal arm 52 are fixed by a common bolt B2. The elastic adjustment member 6 forms a long hole 61 extending along the conveying direction T (front-rear direction T), and the bolt B2 inserted into the long hole 61 is also inserted into the female bolt insertion hole of the horizontal arm 52, and is threadedly engaged with the internal thread hole 41 of the base 4 to be tightened. Then, the bolt B2 is guided in the long hole 61 in a state in which the tightening state of the bolt B2 is slightly loosened, and the fixed position of the elastic adjustment member 6 relative to the horizontal arm 52 is changed. By tightening the bolt B2 again at this position, the size of the free area (the area not tightened or pressed by the bolt B2 and the elastic adjustment member 6) in the horizontal arm 52 of the second elastic body 5 can be changed. As a result, the effective length of the horizontal arm 52 of the second elastic body 5 can be changed, and the elastic coefficient (spring constant) of the second elastic body 5 in the vertical direction can be adjusted.

Whether to perform such adjustment operation on each second elastic body 5 sequentially or simultaneously can be selected according to the occurrence state of the turbulence phenomenon.

The elastic adjustment component 6 is not limited to being arranged at a position sandwiching the horizontal arm 52 in the thickness direction, that is, two elastic adjustment components are arranged for one horizontal arm 52, and one elastic adjustment component can also be arranged for one horizontal arm 52. In this case, the following structure is sufficient: an elastic adjustment component is applied to press the horizontal arm 52 in the thickness direction, and the area pressed to be unable to elastically deform is adjusted by the elastic adjustment component, thereby changing the effective length of the horizontal arm 52. The elastic adjustment component 6 can also function as an insulator or a gasket.

In addition, in the present embodiment, a structure in which the free area (effective length) cannot be adjusted is adopted for the lead arm 51 of the second elastic body 5, i.e., the lead arm 51 of the L-shaped leaf spring 5A. In such a structure, the adjustment of the elastic coefficient (spring constant) in the horizontal direction of the second elastic body 5 can be performed by replacing (replacing) the lead arm 51 with another second elastic body (not shown) having a different size (length in the vertical direction, thickness of the spring, width, number of overlaps). In addition, the structure based on the horizontal arm 52 can also be applied to the lead arm 51 of the second elastic body 5, that is, a flat elastic adjustment member is arranged at a position sandwiching the front end of the lead arm 51 along the conveying direction T (front-rear direction T), and a long hole extending along the height direction H is formed in the elastic adjustment member. The long hole is used to change the fixed position of the elastic adjustment member relative to the lead arm 51, thereby changing the size of the free area (area not fastened and pressed by the bolt B2 and the elastic adjustment member 6) in the lead arm 51 of the second elastic body 5. Of course, as with the modified example of the elastic adjustment member for the horizontal arm 52, a form in which one elastic adjustment member is arranged for one lead arm 51 can also be adopted. In this case, as long as an elastic adjustment component is used to press the lead vertical arm portion 51 in the thickness direction, the effective length of the lead vertical arm portion 51 can be changed by adjusting the area pressed to be unable to elastically deform by the elastic adjustment component.

In this embodiment, the elastic coefficients of the second elastic body 5 provided at the front and rear positions along the conveying direction T can be adjusted individually. That is, the elastic coefficients of the second elastic body 5 at the front and rear positions can be set to different values from each other.

Thus, according to the linear feeder X of this embodiment, when the first elastic body 3 connecting the first mass body 1 and the second mass body 2 is driven to vibrate by the excitation source (piezoelectric element 31), the second mass body 2 functions as a fixed part (balance weight) and the second elastic body 5 functions as a vibration-isolating body, thereby enabling the first mass body 1 to vibrate and transport the transport object K on the linear transport path 14 along the predetermined transport direction T. Moreover, according to the linear feeder X of this embodiment, the elastic coefficients of the second elastic body 5 in the horizontal direction and the lead-vertical direction can be independently changed. Therefore, by not changing the elastic coefficient of the second elastic body 5 in the horizontal direction, only adjusting the elastic coefficient of the second elastic body 5 in the lead-vertical direction, it is easy to perform the turbulence adjustment. By adjusting the elastic coefficient of the second elastic body 5 in the horizontal direction (for example, while maintaining an elastic coefficient that can suppress bumps), the elastic coefficient of the second elastic body 5 in the horizontal direction can be set larger, and a device that is unlikely to be dislocated even when an impact is applied from the outside can be realized (strong impact resistant device).

In particular, in the linear feeder X of this embodiment, one end of the second elastic body 5 is mounted on a node in the first elastic body 3 that does not move (does not vibrate) in the horizontal and vertical directions even when vibrating, thereby playing a good vibration-proof role, thereby enabling the horizontal elastic coefficient of the second elastic body 5 to be set larger.

In addition, in the vibration conveying device X of the present embodiment, as the second elastic body 5, an elastic body including a horizontal arm 52 that can adjust the elastic coefficient of the vibration component in the vertical direction and a vertical arm 51 that can adjust the elastic coefficient of the vibration component in the horizontal direction is applied, so that the shape is simple and the structure that can achieve the purpose of the present embodiment is achieved.

Furthermore, the structure is such that an elastic body including a flat horizontal arm 52 and a flat vertical arm 51 is applied as the second elastic body, and an elastic adjustment member 6 is included to press the horizontal arm 52 in the thickness direction. By adjusting the area pressed so as not to be elastically deformable by the elastic adjustment member 6, the effective length of the arm (horizontal arm 52) to be adjusted can be changed. Therefore, the effective length of the arm (horizontal arm 52) can be simply adjusted while maintaining the relative positional relationship between the arm (horizontal arm 52) and the base 4 and the first elastic body 3 as the connecting target components of the arm (horizontal arm 52) in an appropriate positional relationship. As a result, the elastic coefficient of the vibration component in the vertical direction can be adjusted easily and smoothly.

In particular, the second elastic body 5 is an L-shaped leaf spring 5A including a horizontal arm 52 and a lead-vertical arm 51. Therefore, by appropriately adjusting the effective length of either the horizontal arm 52 or the lead-vertical arm 51, or the effective length of both, the elastic coefficient (spring constant) in the lead-vertical direction and the elastic coefficient (spring constant) in the horizontal direction of the second elastic body 5 can be individually set to appropriate values.

In addition, the present embodiment is not limited to the above-mentioned embodiment. For example, in the above-mentioned embodiment, as a structure for adjusting the elastic coefficient of the second elastic body, i.e., the L-shaped spring, a structure is exemplified in which an elastic adjustment member that clamps the arm of the L-shaped spring in the thickness direction is used to adjust the effective length (size of the free area) of the arm of the L-shaped spring, but the present invention is not limited to this, and a structure that adjusts the elastic coefficient of the L-shaped spring without using an elastic adjustment member that clamps the arm of the L-shaped spring in the thickness direction can also be adopted. As an example, the following structure can be cited: a long hole is formed in the arm of the L-shaped spring, and an internal thread is set at a predetermined pitch along the long side direction of the long hole in the portion that fixes the arm (the base 4 in the above embodiment), so that the entire L-shaped spring moves along the long side direction of the long hole, and the internal thread hole of the fixing bolt is selected and changed to adjust the effective length of the arm (the size of the free area). If this structure is used, sometimes the entire structure (main frame) supported by the L-shaped spring also moves according to the movement amount of the L-shaped spring.

In addition, as described above, a structure can also be formed in which a plurality of L-shaped springs with different lengths, areas, thicknesses, etc. of the vertical arm and the horizontal arm are prepared in advance, and an appropriate L-shaped spring is selected from them, or the elastic coefficients of the second elastic body in the horizontal direction and the vertical direction are changed by replacement.

The number of the second elastic body and its fixed position relative to the base can be changed appropriately. In addition, the second elastic body can also connect the base and the second mass body.

The second elastic body of this embodiment may also be composed of a spring other than an L-shaped spring (for example, a spring formed by connecting the base ends of an I-shaped spring, a T-shaped spring, etc.) or an elastic body other than a spring (rubber, etc.).

The number and shape of the first elastic body, and the connection position of the first elastic body relative to the first mass body and the second mass body can also be appropriately changed. For example, the first elastic body can be arranged in a posture tilted at a predetermined angle in the conveying direction. In addition, the first elastic body of the above-mentioned embodiment is also arranged in a posture tilted at a predetermined angle (about 2 degrees) in the conveying direction. As mentioned above, in this embodiment, the "elastic coefficient of the second elastic body in the horizontal direction" and the "elastic coefficient of the horizontal component in the second elastic body" are synonymous, and the "elastic coefficient of the second elastic body in the lead-vertical direction" and the "elastic coefficient of the lead-vertical component in the second elastic body" are synonymous. In addition, the "horizontal direction" in this embodiment refers to the direction along the elastic main axis specified by the mounting angle of the first elastic body (a direction parallel or substantially parallel to the elastic main axis), and the "plumb-vertical direction" in this embodiment refers to the direction perpendicular or substantially perpendicular to the elastic main axis (a normal direction relative to the elastic main axis). That is, in this embodiment, the horizontal direction and the plumb-vertical direction of the second elastic body are determined based on the elastic main axis of the first elastic body, and the elastic coefficient of the horizontal direction of the second elastic body and the elastic coefficient of the plumb-vertical direction of the second elastic body can be any structure as long as the elastic coefficient of the plumb-vertical direction of the second elastic body can be changed independently, and the appearance of the second elastic body is not particularly limited. Therefore, the horizontal arm and the vertical arm of the second elastic body do not necessarily have to be orthogonal to each other, for example, they can also be non-orthogonal to each other. In addition, the structure in which the height direction of the base and the vertical direction of the second elastic body are consistent is also included in this embodiment.

In the above-mentioned embodiment, a form including a movable counterweight 11 (a part of the first mass body 1), a balancing counterweight 21 (a part of the second mass body 2) and a first elastic body 3 is exemplified, but a form in which all or only a part of them are a single body can also be adopted. The vibration conveying device of this embodiment includes a form in which the first elastic body is directly connected to the first mass body and the second mass body respectively, and a form in which they are indirectly connected via other components. Similarly, it includes a form in which the second elastic body is directly connected to the base and the second mass body or the first elastic body respectively, and a form in which they are indirectly connected via other components.

The first mass body only needs to include a linear conveying surface. It can also include the above-mentioned conveying path (groove) and form a linear conveying surface on the upper surface of the chute table, or include a linear conveying surface on the upper surface of the movable counterweight without including the chute table, or form a linear conveying surface on a component (not limited to the chute table) that vibrates synchronously with the movable counterweight.

In addition, the second mass body may be composed of only a single balancing weight or may include multiple balancing weights. It is also possible to adopt a structure in which the first mass body is arranged above the second mass body.

The excitation source can also be a component other than a piezoelectric element.

In addition, the transported objects can also be various LEDs such as LEDs, electronic equipment other than LEDs, or parts other than electronic components such as food.

In addition, the present embodiment includes the following vibration conveying device: regarding the elastic coefficient of the second elastic body in the horizontal direction and the elastic coefficient of the second elastic body in the lead-vertical direction, the elastic coefficient of the second elastic body in the lead-vertical direction can be changed independently, and the elastic coefficient of the second elastic body in the horizontal direction can be changed independently.

In addition, the specific structure of each part is not limited to the above-mentioned implementation method, and various modifications can be made within the scope of the purpose of the invention.

<Second implementation method>

The second embodiment of the present invention is described below with reference to the drawings. In the second embodiment, the same symbols are used to describe the structures that are substantially the same as those in the first embodiment described above.

As shown in FIG1 , the vibration conveying device X of the present embodiment is also a device that moves a workpiece K such as an electronic component on a conveying path 14 (the linear conveying path 14 described later) by vibration, and conveys it to a predetermined conveying destination (supply destination). In addition, the downstream end (not shown) of the conveying path (hopper conveying path) of a hopper feeder that is arranged and conveyed is connected to the upstream end of the linear conveying path 14. Therefore, the linear feeder X conveys the workpiece K conveyed via the conveying path (hopper conveying path) formed in the hopper feeder to the terminal end of the linear conveying path 14 by vibration, and can be supplied to the predetermined conveying destination. The linear feeder X includes a return section (return conveying path), which returns the workpiece K (overflowing workpiece K, workpiece K judged not to be in the predetermined conveying posture) to the hopper conveying path when overflow occurs or the workpiece K is judged not to be in the predetermined conveying posture.

As shown in Figures 1 to 4, the linear feeder X includes a first mass body 1 including a linear conveying surface, a second mass body 2 vibrating in an opposite phase relative to the first mass body 1, a first elastic body 3 connecting the first mass body 1 and the second mass body 2 to each other, a base 4, and a second elastic body 5 connecting the base 4 and the first elastic body 3 to each other.

In this embodiment, a movable counterweight 11 (movable part) as a main component of the first mass body 1 is arranged above the base 4 including a strip shape along the conveying direction T, a balancing counterweight 21 (fixed part) as a main component of the second mass body 2 is arranged above the movable counterweight 11 via the first elastic body 3, and a chute table 13 connected to the movable counterweight 11 is arranged above the balancing counterweight 21 via the side connecting plate 12. In this embodiment, as shown in FIG. 2, the movable counterweight 11 and the chute table 13 are connected to each other via a pair of side connecting plates 12. In addition, in FIG. 4, the side connecting plate 12 near the front side of the paper surface is omitted in the pair of side connecting plates 12.

The conveying path 14 is detachably mounted on the upper surface of the chute table 13 by bolts and other fixing parts. By giving vibration to the conveying path 14, the workpiece K moves in the linear conveying surface (conveying trough) provided in the conveying path 14. The chute table 13 moves synchronously with the vibration of the movable counterweight 11 and functions as a vibration transmission part that transmits the vibration of the movable counterweight 11 to the conveying path 14.

In the following description, the conveying direction T of the workpiece K along the conveying path 14 is set as the front-rear direction T, the upstream side of the conveying direction T is set as the rear side, and the downstream side of the conveying direction T is set as the front side. In addition, the direction orthogonal to the conveying direction T in the horizontal plane is set as the width direction W (cross-sectional direction) (refer to Figure 1, etc.).

As shown in Figures 2 and 4, the front and rear ends of the chute platform 13 are suspended portions that protrude forward and backward respectively from the movable counterweight 11. For example, a movable counterweight (not shown) can also be installed on the downward facing surface of the front suspended portion of the chute platform 13. The side connecting plate 12, the chute platform 13, and the conveying path 14 are components that constitute the first mass body 1 in the same manner as the movable counterweight 11.

In this embodiment, the dimensions (front-rear dimensions) of the movable counterweight 11 as the main component of the first mass body 1 and the balancing counterweight 21 as the main component of the second mass body 2 along the conveying direction T are set to be approximately the same, and these balancing counterweights 21 and movable counterweights 11 are arranged in a posture facing each other in the height direction.

In the linear feeder X of this embodiment, a first elastic body 3 is arranged at the positions connecting the front ends and rear ends of the movable counterweight 11 and the balancing counterweight 21.

The first elastic body 3 is in the form of a flat spring (leaf spring) whose thickness direction is roughly consistent with the conveying direction T. A piezoelectric element 31 that functions as an excitation source is attached to the first elastic body 3. By applying a charge to the piezoelectric element 31, the first elastic body 3 is elastically deformed to generate vibration, thereby vibrating the first mass body 1 and the second mass body 2. Therefore, the first elastic body 3 functions as a driving spring. The first elastic body 3 of this embodiment is set to a normal posture of standing up in the vertical direction without elastic deformation. The spring constant formed by the first elastic body 3 and the piezoelectric element 31 is appropriately selected according to the conditions of an arbitrary resonance frequency determined by the transport speed of the transported component, the weight of the transport path 14 (groove), etc. In this embodiment, the first mass body 1 and the second mass body 2 are connected through a plurality of first elastic bodies 3.

In addition, in the present embodiment, the first elastic body 3 is also arranged at the predetermined midway position between the front and rear ends of the movable weight 11 and the balance weight 21. The first elastic bodies 3 are arranged in pairs at their respective arrangement positions (positions connecting the movable weight 11 and the balance weight 21) with a slight gap in between along the front-rear direction T. In the present embodiment, at the portion connecting the front ends of the movable counterweight 11 and the balancing counterweight 21, at the portion connecting the rear ends of the movable counterweight 11 and the balancing counterweight 21, at the portion between the front and rear ends of the movable counterweight 11 and the balancing counterweight 21 offset by a predetermined distance toward the front end side from the center in the front-rear direction T, and at the portion between the front and rear ends of the movable counterweight 11 and the balancing counterweight 21 offset by a predetermined distance toward the rear end side from the center in the front-rear direction T, These four portions are respectively arranged in a manner that two first elastic bodies 3 are arranged along the front-rear direction T, that is, a form that includes a total of eight first elastic bodies 3.

Moreover, the linear feeder X of this embodiment configures the movable weight 11 which is the main component of the first mass body 1, the balance weight 21 which is the main component of the second mass body 2, and the first elastic body 3 as an integrated structure (hereinafter, the integrated structure is referred to as "main frame M"). The vibration conveying device X of this embodiment includes a structure (main frame M), which integrally includes a movable counterweight 11 as a main component of a first mass body 1 as a movable part, a balance counterweight 21 as a main component of a second mass body 2 that functions as a fixed part relative to the movable counterweight 11, and a first elastic body 3, and is configured to support the integral structure (main frame M) from the ground (a base 4 that can be regarded as the ground in this embodiment) by a second elastic body 5, so that the second elastic body 5 functions as an anti-vibration spring.

As shown in Figures 2 to 4, the linear feeder X of this embodiment is provided with second elastic bodies 5 in front and rear of the main frame M, respectively, and the base 4 and the main frame M are connected by each second elastic body 5.

In this embodiment, a flat L-shaped elastic member (L-shaped spring 5A) including a vertical arm 51 extending in the vertical direction and a horizontal arm 52 extending in the horizontal direction is used to constitute the second elastic body 5. The second elastic body 5 shown in FIG. 2 and the like fixes the front end (upper end) of the vertical arm 51 to the first elastic body 3, and fixes the front end (the end on the side where the vertical arm 51 is not erected) of the horizontal arm 52 to the base 4.

In the present embodiment, a protrusion 32 protruding forward or backward is provided at the position of the node that does not displace in the horizontal and vertical directions in the first elastic body 3, and the front end portion of the vertical arm portion 51 is fixed to the protrusion 32. In addition, the first elastic body 3 has both ends (upper end and lower end) fixed to the movable counterweight 11 and the balance counterweight 21 respectively (both ends are fixed and suspended), so the node is the central portion in the long side direction. Here, the node of the first elastic body 3 is enough to be a point, but the area where the protrusion 32 is provided in the first elastic body 3 is a predetermined area including the node of the first elastic body 3 (the node and the vicinity of the node). Internal threaded holes 33 are provided at two locations of the protrusion 32 separated along the width direction W (refer to Figure 3). The lead arm 51 is formed with a bolt insertion hole connected to each internal threaded hole 33. By inserting the bolt B1 through the bolt insertion hole and threading it into the internal threaded hole 33, the lead arm 51 of the second elastic body 5 can be fixed to the first elastic body 3. A pressing plate is interposed between the head of the bolt B1 and the lead arm 51 of the second elastic body 5.

Internal threaded holes 41 are provided at two locations separated along the width direction W at the front and rear ends of the base 4 (see FIG. 3 ). Internal bolt insertion holes connected to the internal threaded holes 41 are formed in the horizontal arm 52. By inserting the bolt B2 through the internal bolt insertion hole and threading it into the internal threaded hole 41, the horizontal arm 52 of the second elastic 5 can be fixed to the base 4.

In the linear feeder X of this embodiment, the second elastic body 5 is arranged at a position that does not overlap with the first elastic body 3 in the conveying direction T, and the upper end of the second elastic body 5 is mounted on a node in the first elastic body 3 that is approximately the center of the height direction H, thereby improving vibration resistance and achieving low reaction force.

In addition, in the linear feeder X of the present embodiment, by independently adjusting the elastic coefficients of the second elastic body 5 in the horizontal direction and the lead-vertical direction without changing the tilt angle of the front-rear direction T of the first elastic body 3, the vibration of the first elastic body 3 can be adjusted to the desired vibration with no or almost no jolt. Here, the "elastic coefficient of the horizontal direction of the second elastic body" in the present embodiment has the same meaning as the "elastic coefficient of the horizontal component in the second elastic body", and the "elastic coefficient of the lead-vertical direction of the second elastic body" has the same meaning as the "elastic coefficient of the lead-vertical component in the second elastic body". In addition, the "horizontal direction" of the present embodiment refers to the direction along the elastic main axis specified by the mounting angle of the first elastic body 3 (the direction parallel or substantially parallel to the elastic main axis), and the "plumb-vertical direction" of the present embodiment refers to the direction orthogonal or substantially orthogonal to the elastic main axis (the direction in which the elastic main axis is found). In the linear feeder X of the present embodiment, a flat L-shaped second elastic body 5 including a horizontal arm 52 capable of adjusting the elastic coefficient of the vibration component in the plumb-vertical direction and a plumb-vertical arm 51 capable of adjusting the elastic coefficient of the vibration component in the horizontal direction is used, so as to realize a structure in which the elastic coefficients of the second elastic body 5 in the horizontal direction and the plumb-vertical direction can be adjusted in opposition without adversely affecting each other.

In the present embodiment, as shown in Fig. 3 and Fig. 4, a flat elastic adjustment member 6 is arranged at the position of the front end portion of the horizontal arm 52 of the L-shaped leaf spring 5A sandwiching the horizontal portion of the second elastic body 5 in the height direction H, and these elastic adjustment members 6 and the horizontal arm 52 are fixed by a common bolt B2. The elastic adjustment member 6 forms a long hole 61 extending along the conveying direction T (front-rear direction T), and the bolt B2 inserted into the long hole 61 is also inserted into the female bolt insertion hole of the horizontal arm 52, and is threadedly engaged with the internal thread hole 41 of the base 4 to be tightened. Then, the bolt B2 is guided in the long hole 61 in a state in which the tightening state of the bolt B2 is slightly loosened, and the fixed position of the elastic adjustment component 6 relative to the horizontal arm 52 is changed. By tightening the bolt B2 again at this position, the size of the free area (the area not tightened or pressed by the bolt B2 and the elastic adjustment component 6) in the horizontal arm 52 of the second elastic body 5 can be changed. As a result, the effective length of the horizontal arm 52 of the second elastic body 5 can be changed, and the elastic coefficient (spring constant) of the second elastic body 5 in the vertical direction can be adjusted.

Whether to perform such adjustment operation on each second elastic body 5 sequentially or simultaneously can be selected according to the occurrence state of the turbulence phenomenon.

The elastic adjustment component 6 is not limited to being arranged at a position sandwiching the horizontal arm 52 in the thickness direction, that is, two elastic adjustment components are arranged for one horizontal arm 52, and one elastic adjustment component can also be arranged for one horizontal arm 52. In this case, the following structure is sufficient: an elastic adjustment component is applied to press the horizontal arm 52 in the thickness direction, and the area pressed to be unable to elastically deform is adjusted by the elastic adjustment component, thereby changing the effective length of the horizontal arm 52. The elastic adjustment component 6 can also function as an insulator or a gasket.

In addition, in the present embodiment, a structure in which the free area (effective length) cannot be adjusted is adopted for the lead arm 51 of the second elastic body 5, i.e., the lead arm 51 of the L-shaped leaf spring 5A. In such a structure, the adjustment of the elastic coefficient (spring constant) in the horizontal direction of the second elastic body 5 can be performed by replacing (replacing) the lead arm 51 with another second elastic body (not shown) having a different size (length in the vertical direction, thickness of the spring, width, number of overlaps). In addition, the structure based on the horizontal arm 52 can also be applied to the lead arm 51 of the second elastic body 5, that is, a flat elastic adjustment member is arranged at a position sandwiching the front end of the lead arm 51 along the conveying direction T (front-rear direction T), and a long hole extending along the height direction H is formed in the elastic adjustment member. The long hole is used to change the fixed position of the elastic adjustment member relative to the lead arm 51, thereby changing the size of the free area (area not fastened and pressed by the bolt B2 and the elastic adjustment member 6) in the lead arm 51 of the second elastic body 5. Of course, as with the modified example of the elastic adjustment member for the horizontal arm 52, a form in which one elastic adjustment member is arranged for one lead arm 51 can also be adopted. In this case, as long as an elastic adjustment component is used to press the lead vertical arm portion 51 in the thickness direction, the effective length of the lead vertical arm portion 51 can be changed by adjusting the area pressed to be unable to elastically deform by the elastic adjustment component.

Moreover, as described above, the vibration conveying device X of this embodiment sets the main component of the first mass body 1, namely the movable counterweight 11, the main component of the second mass body 2, namely the balance counterweight 21, and the first elastic body 3 as an integrated structure (main frame M). As a result, no friction is generated at the connection part between the first mass body 1 and the first elastic body 3, and the connection part between the second mass body 2 and the first elastic body 3, the viscosity coefficient is reduced, and the fixing condition (connection condition of the connection part) does not change even at a large amplitude, and the nonlinearity of the spring is reduced.

In addition, according to the vibration conveying device X of this embodiment, the movable counterweight 11 and the balance counterweight 21 are supported at both ends and the middle part in the front-rear direction T by the first elastic body 3, so that the bending change of the movable counterweight 11 and the balance counterweight 21 is reduced, especially the friction between the movable counterweight 11 of the main frame M and the side connecting plate 12 is reduced, and the viscosity coefficient is reduced.

Furthermore, if the first elastic body 3 is fixed to the first mass body 1 (movable counterweight 11) and the second mass body 2 (balance counterweight 21) by bolts or other fixings, it is necessary to ensure the configuration space of the fixings. However, according to the present embodiment, it is not necessary to ensure the configuration space of the fixings, and the design freedom of the shape of the first mass body 1 is improved. For example, by setting the height dimension of the first mass body 1 larger, the bending rigidity can be improved. As a result, the first mass body 1 (movable counterweight 11) is difficult to bend in an S shape, and the driving frequency is improved. In this way, according to the linear feeder X of the present embodiment, the driving frequency and amplitude of the vibration of the structure (main frame M) can be increased, and a high resonance magnification can be achieved to obtain a large amplitude.

In the linear feeder X of this embodiment, the first elastic body 3 disposed in the middle between the front end and the rear end of the first mass body 1 (movable counterweight 11) and the second mass body 2 (balance counterweight 21) realizes the function of a rib, thereby making it difficult for the first mass body 1 and the second mass body 2 to bend in an S shape.

In this embodiment, a main frame M including a movable counterweight 11, a balancing counterweight 21 and a first elastic body 3 is formed by performing wire cutting on a piece of metal raw material. In addition, the main frame M can also be formed by processing other than wire cutting.

In the linear feeder X of the present embodiment, for example, a balancing weight (sub-balancing weight) separated from the main frame M can be integrally mounted on the balancing weight 21. As the location where the sub-balancing weight is installed, the internal space MS of the main frame M, that is, the relatively large space MS formed between the first elastic bodies 3 adjacent to each other along the conveying direction T (except for the space between two first elastic bodies 3 arranged closely in a group) can be cited. In this case, as long as the sub-balancing weight is installed in the internal space MS of the main frame M, the condition that the sub-balancing weight does not contact the components other than the balancing weight 21 (the first elastic body 3, the piezoelectric element 31, the movable weight 11, and the side connecting plate 12) is satisfied. The sub-balancing weight is a component constituting the second mass body 2 similarly to the balancing weight 21. The size of the internal space MS of the main frame M (the larger space MS separated by the adjacent first elastic body 3 in the conveying direction T) can be equal in size (equally divided) as shown in Figures 3 and 4, or unequal in size (unequally divided). In addition, Figure 3 is an enlarged view of the main part of Figure 2. In addition, the internal space MS of the main frame M can also be used as an access space for installing the piezoelectric element 31 on the first elastic body 3.

Thus, according to the linear feeder X of this embodiment, when the first elastic body 3 connecting the first mass body 1 and the second mass body 2 is driven to vibrate by the excitation source (piezoelectric element 31), the second mass body 2 functions as a fixed part (balance weight) and the second elastic body 5 functions as a vibration-isolating body, so that the first mass body 1 vibrates and can transport the transport object K on the linear transport path 14 along the predetermined transport direction T. Moreover, according to the linear feeder X of this embodiment, the movable counterweight 11 as a part of the first mass body 1, the balance counterweight 21 as a part of the second mass body 2, and the first elastic body 3 are integrated, so that no friction occurs at the connection part between the first mass body 1 and the first elastic body 3, and the connection part between the second mass body 2 and the first elastic body 3. Compared with the structure in which the first elastic body is fixed to the first mass body and the second mass body by a fixing member such as a bolt, the viscosity coefficient is reduced and the resonance peak value is not reduced. In addition, the fixing condition (connection condition of the connection part) does not change even when the amplitude is large, and the reduction of the driving frequency (resonance frequency) caused by the nonlinearity of the first elastic body 3 can be reduced. Therefore, according to the vibration conveying device X of this embodiment, the cause of the reduction of the resonance peak value that cannot be avoided as long as the existing structure fixes the first elastic body to the first mass body and the second mass body by bolts and other fixing parts can be completely eliminated, and a large amplitude can be achieved with a small excitation force.

Moreover, in the vibration conveying device X of the present embodiment, the portion connecting the first mass body 1 and the second mass body 2 through the first elastic body 3 is set at the positions connecting the upstream ends (rear ends) of the first mass body 1 and the second mass body 2 in the conveying direction T and the downstream ends (front ends) in the conveying direction T in the same manner as the existing connection portion based on the driving spring, so that a stable support state based on the first elastic body 3 can be ensured.

In particular, in the vibration conveying device X of the present embodiment, the first elastic body 3 is also arranged at the midway position between the upstream side end (rear end) of the movable counterweight 11 (the main component of the first mass body 1) and the balancing counterweight 21 (the main component of the second mass body 2) in the conveying direction T and the downstream side end (front end) in the conveying direction T. Therefore, the first elastic body 3 arranged in the midway portion functions as a rib, and the bending rigidity of the movable counterweight 11 and the balancing counterweight 21 can be further improved. As a result, the bending change of the movable counterweight 11 and the balancing counterweight 21 is further reduced, and the deformation of the linear conveying path 14 can be suppressed. In addition, the spring constant is improved, and it becomes a structure that satisfies the good conditions of high driving frequency and reduced friction between components to increase the resonance peak.

As described above, according to the present embodiment, by adopting an unprecedented new structure in which at least a portion of the first mass body 1 (movable counterweight 11), at least a portion of the second mass body 2 (balance counterweight 21) and the first elastic body 3 are integrated, the driving frequency and amplitude of the vibration of the integrated structure (main frame M) can be increased, a high resonance magnification can be achieved, a large amplitude can be obtained, and a vibration conveying device X that can increase the conveying speed of the conveying object K can be realized.

In addition, in the vibration conveying device X of the present embodiment, as the first mass body 1, a mass body including a movable counterweight 11 (equivalent to the "first mass body main body" of the present embodiment) constituting the main frame M (integrated structure) as an integral structure and a conveying path 14 which is separate from the movable counterweight 11 and includes a linear conveying surface is applied, so that the linear conveying path 14 requiring a high degree of design specifications can be prepared as a dedicated part separately from the main frame M, and the processing burden during the manufacture of the main frame M as an integral structure can be reduced.

In addition, this embodiment is not limited to the above-mentioned embodiment. For example, the number and shape of the first elastic body and the connection position of the first elastic body relative to the first mass body and the second mass body can also be appropriately changed. The first elastic body can also be configured in a posture tilted at a predetermined angle in the conveying direction.

In the above-mentioned embodiment, the movable weight 11 (a part of the first mass body 1), the balance weight 21 (a part of the second mass body 2), and the first elastic body 3 are shown as an integral structure, but it is also possible to adopt a structure in which the entire first mass body, a part of the second mass body, and the first elastic body are integrally structured, a structure in which a part of the first mass body, the entire second mass body, and the first elastic body are integrally structured, or a structure in which the entire first mass body, the entire second mass body, and the first elastic body are integrally structured.

That is, the first mass body of the present embodiment may be composed only of components (movable counterweight) constituting an integrated structure (main frame), or may include main components constituting an integrated structure (main frame) and components separate from the integrated structure.

Similarly, the second mass body of the present embodiment may be composed only of the main components (balance weight) constituting the integrated structure (main frame), or may include the main components constituting the integrated structure (main frame) and components separate from the integrated structure.

The first mass body only needs to include a linear conveying surface, and may also include the above-mentioned conveying path (groove) and form a linear conveying surface on the upper surface of the chute table, or include the chute table and form a linear conveying surface on the upper surface of the movable counterweight, or form a linear conveying surface on a component (not limited to the chute table) that vibrates synchronously with the movable counterweight. In particular, when the first mass body is composed only of a component equivalent to the above-mentioned movable counterweight, it is preferred to arrange the first mass body above the second mass body and form a linear conveying surface on the upper surface of the first mass body.

The vibration conveying device of this embodiment includes a form in which the second elastic body having a vibration-proof effect is directly connected to the integral structure (main frame) and a form in which it is indirectly connected via other components. The number of second elastic bodies and the fixed position relative to the base or the integral structure (main frame) can be appropriately changed. In addition, the second elastic body can also be connected to the base and the second mass body.

The second elastic body may also be formed by a spring other than an L-shaped spring (for example, a spring formed by connecting the base ends of an I-shaped spring to each other, a T-shaped spring, etc.), an elastic body other than a spring (rubber, etc.), or a leaf spring arranged in a posture inclined at a predetermined angle in the conveying direction. In addition, a vibration conveying device that does not include a second elastic body is also included in this embodiment.

The excitation source can also be a component other than a piezoelectric element.

In addition, the transported objects may also be various LEDs such as LEDs, electronic components other than LEDs, or parts other than electronic components such as food.

In addition, the specific structure of each part is not limited to the above-mentioned implementation method, and various modifications can be made within the scope of the purpose of the invention.

<Third implementation method>

Below, the third embodiment of the present invention is described with reference to Figures 5 to 10.

The rotary vibrator A of this embodiment includes a vibration plate 7 as a first mass body, a base 8 as a second mass body arranged opposite to the vibration plate 7 in the direction of the opposing axis m, an excitation source 9 for making the vibration plate 7 and the base 8 vibrate relative to each other around the opposing axis m, and a first elastic body 400 arranged at a position connecting the vibration plate 7 and the base 8. The rotary vibrator A is equipped with a conveyor body B, which includes a conveyor path rising in a spiral shape, thereby constituting a feeder PF as a vibration conveying device. The conveyor body B of this embodiment is configured to arrange and supply tiny objects such as IC chips.

The vibration plate 7 includes a disk-shaped vibration plate main body 10 forming the main body of the first mass body and a first continuous installation portion 44 to be described later which is mounted on the vibration plate main body 10 and forms a part of the first mass body. On the outer periphery of the vibration plate main body 10, first vibration plate side connecting portions 16 connected to the first elastic body are provided at multiple equiangular locations, in this embodiment, at three locations, and second vibration plate side connecting portions 17 connected to the excitation source 9 are provided at multiple equiangular locations, in this embodiment, at three locations, which are phase-shifted with these first vibration plate side connecting portions 16. The first vibration plate side connecting portion 16 is a shape hollowed out downward and radially outward, and specifically, is a downward U-shaped concave portion with a bottom when viewed from the side. The second connecting portion 17 on the vibration plate side is a protrusion protruding downward from the vibration plate body 10.

The base 8 includes a base body 20 of a truncated cone shape forming the main body of the second mass body and a second connecting portion 42 to be described later which is mounted on the base body 20 and forms a part of the second mass body. The base body 20 is arranged on the installation surface via a vibration-proof component 2a. A first base-side connecting portion 26 which is located at a position corresponding to the first connecting portion 16 on the vibration plate side and connected to the first elastic body 400 and a second base-side connecting portion 22 which is located at a position corresponding to the first connecting portion 17 on the vibration plate side and connected to the excitation source 9 are provided on the outer periphery of the base 8. As shown in FIG. 6 and FIG. 7(a), the first base-side connecting portion 26 is a shape hollowed out upward and radially outward, specifically, a U-shaped groove-shaped concave portion with a bottom when viewed from the side. As shown in FIG. 6 and FIG. 7(b), the second connection part 22 on the base side is located inside the space where the second connection part 17 on the vibration plate side can be movably arranged, and includes the second leaf spring accommodating part 23 and the connection member abutting part 24 described later.

The excitation source 9 includes a connecting component 36 that constitutes a part of a base 8 serving as a second mass body, a second leaf spring 37 that is laterally arranged and serves as a second elastic body and has a base end connected to the connecting component 36 and a front end extending in a radial direction, and a dual piezoelectric chip or single piezoelectric chip type piezoelectric element driving portion 38 that is adhered to both sides or one side of the second leaf spring 37 and causes the second leaf spring 37 to bend by vibration. As shown in FIG. 7(b), the base 8 is provided with the second leaf spring accommodating portion 23 extending in a star shape from the center in three directions and opening upward and radially outward, and the L-shaped connecting component abutting portion 24 located between adjacent second leaf spring accommodating portions 23. The connecting component 36 on which the base end of the second leaf spring 37 is mounted is fastened to the bottom surface of the base 8 from the opposite axis z direction, i.e., the upward direction, by means of a bolt v1 serving as a fixing member in a state where both surfaces abut against the connecting component abutting portion 24.

Furthermore, the base end of the second leaf spring 37 is horizontally connected to the connecting member 36 via a bolt v21 as a fixing member, and the front end of the second leaf spring 37 is horizontally connected to the second connecting portion 17 on the vibration plate side protruding downward from the vibration plate main body 10 via a bolt v22 as a fixing member.

The first elastic body 400 connects the vibration plate 7 and the base 8, thereby mainly functioning as a resonance spring, and as shown in FIG8, forms an integrated leaf spring structure (more specifically, an integrated overlapping leaf spring structure), which includes a plurality of leaf springs 40 (two in this embodiment), the first continuously disposed portion 44 continuously disposed on one end side of each leaf spring 40 and forming a part of the vibration plate 7, and the second continuously disposed portion 42 continuously disposed on the other end side of each leaf spring 40 and forming a part of the base 8.

The leaf springs 40 are arranged parallel to each other. As shown in FIG15 , when the center of the leaf spring 40 in the thickness direction and the width direction is set as the origin O, the long side direction is set as z, the thickness direction is set as x, and the width direction is set as y, the leaf spring 40 shown in FIG5 and FIG8 is arranged so that the thickness direction x is oriented in the circumferential direction of the rotary vibrator A, the width direction y is oriented in the radial direction of the rotary vibrator A, and the long side direction z extends in a direction inclined to the opposing axis m of the rotary vibrator A. If each leaf spring 40 is observed, as shown in FIG9(c), its width dimension D in the y direction is not a rectangular shape from one end 40e1 to the other end 40e2 as indicated by the imaginary line, but is a shape that is smoothly narrowed from the upper and lower ends 40e1 and 40e2 toward the center 40m as indicated by the solid line. This shape is given by necking the spring steel, carbon steel, etc., which is the raw material of the spring.

The first continuous setting part 44 shown in FIG8 is a rectangular parallelepiped formed integrally with the upper end of each leaf spring 40, and as shown in FIG5 and FIG6, is tightly arranged in the recess 16 as the first connecting part on the vibration plate side. The second connecting part 42 shown in FIG8 is a bottom 42a formed integrally with the lower end of each leaf spring 40, and a right side part 42b and a left side part 42c arranged on both sides of the bottom 42a in a manner surrounding each leaf spring 40. It is U-shaped and is tightly arranged in the recess 26 as the first connecting part on the base side as shown in FIG5 to FIG7.

That is, the first elastic body 400 is arranged in a positional relationship so as to be removably embedded from the outside relative to the rotating disk 7 as the first mass body and the base 8 as the second mass body.

As shown in Figures 5, 6 and 8, the first continuous setting portion 44 and the vibration plate main body 10 are connected by a connecting member v3 at two locations along a direction parallel to the opposing axis m. The location indicated by the symbol h3 in Figures 6 and 8 is a connecting hole used for this purpose.

In addition, the right side portion 42b of the second continuous setting portion 42 is connected to the base body 20 by bolts v4 at two locations along the first direction s intersecting (orthogonal) with the above-mentioned direction of the opposing axis m, and the left side portion 42c of the second connecting portion 42 is connected to the base body 20 by bolts v5 at two locations along the second direction u intersecting (orthogonal) with the above-mentioned direction of the opposing axis m and the above-mentioned first direction s. In FIG8, the portions indicated by symbols h4 and h5 are connection holes used therefor. In the case of this embodiment, the first direction s is a tangent direction on the circumference of the opposing axis m, and the second direction u is a radial direction passing through the opposing axis m. In addition, the long side direction z of the leaf spring is slightly inclined relative to the opposing axis m, the thickness direction x of the leaf spring 30 is roughly consistent with the first direction s, and the width direction y of the leaf spring is consistent with the second direction u.

In this embodiment, in order to achieve the reduction of inertial moment, the vibration plate main body 10 is made of aluminum. However, if the spring is directly connected to the vibration plate main body 10, the bending rigidity of the connection part is reduced because the Young's modulus of the aluminum material is lower than that of iron. Therefore, as shown in FIG9(b), the first continuous setting part 44 and the leaf spring 40, which are part of the first mass body, are made of spring materials such as spring steel and carbon steel. Therefore, the effect of improving the bending rigidity of the connection part between the leaf spring 40 constituting the first elastic body 400 and the rotation plate main body 10 is included. This includes the effect of improving the bending rigidity of the joint between the leaf spring 40 and the base body 20, which is the main body of the second mass body, by similarly making the second continuous setting part 42 formed integrally with the leaf spring 40 from spring materials such as spring steel and carbon steel. In addition, for the convenience of explanation, FIG9(b) shows one leaf spring 40, but the leaf spring 40 of this embodiment is two as shown in FIG9(a), so each leaf spring 40 includes the above-mentioned structure and has the same effect.

Furthermore, by repeatedly applying a voltage of a desired frequency to the piezoelectric element driving part 38, the vibration plate 7 is vibrated in the forward and reverse directions through the second leaf spring 37. As a result, the leaf spring 40, which serves as the first elastic body, is bent and vibrated.

In this bending vibration, bending occurs in the long-side direction as shown in Figure 10(a). This bending is a decisive factor in determining the resonance characteristics. Along with this bending, forces Fx and F′x in the x direction and fixed moments My and M′y around the y axis are generated at the two fixed ends of the spring on the origin O side and the opposite side. This is referred to as A-mode bending.

In addition, a torsion around the z-axis as shown in Figure 10(b) is generated. With this torsion, a moment Mz is generated around the origin O when viewed from the z-axis direction. This is referred to as the B-mode deflection.

Furthermore, bending in the width direction as shown in FIG10(c) is generated. With this bending, a force Fy in the y direction and a fixed moment Mx around the x axis are generated on the side opposite to the origin. That is, when the vibration plate 102 rotates relative to the base 101, the phase of the vibration plate side fixing portion α of the leaf spring 104 changes relative to the phase of the base side fixing portion β, so that, for example, when it is projected onto the y-z plane, the vibration plate side fixing portion α moves in the width direction (outer diameter direction). This is referred to as C-mode bending.

Among them, the A-mode bending can be mainly used to amplify the necessary frequency and amplitude at or near the resonance point, and efficiently drive the vibration plate 7.

At this time, the first leaf spring 40 as the first elastic body is arranged in the z-axis direction which is tilted relative to the opposite axis m, so that the vibration plate 7 performs simultaneous vertical movement (vibration) and circumferential rotational movement (vibration). As a result, the feeder PF, which is a vibration conveying device having a conveying body B including a spiral conveying path mounted on the vibration plate 7, conveys the articles on the conveying path from the bottom of the conveying body B to the top along the spiral conveying path.

As described above, the rotary vibration machine A of the present embodiment includes a rotating disk 7 as a first mass body, a base 8 as a second mass body arranged opposite to the rotating disk 7 in the direction of the opposing axis m, an excitation source 9 for making the rotating disk 7 and the base 8 vibrate relative to each other around the opposing axis m, and a first elastic body 400 arranged at a position connecting the rotating disk 7 and the base 8.

Furthermore, the first elastic body 400 is set as a one-piece leaf spring structure, which includes a leaf spring 40, a first continuously set portion 44 continuously set on one end side of the leaf spring 40 and forming a part of the rotating disk 7, and a second continuously set portion 42 continuously set on the other end side of the leaf spring 40 and forming a part of the base 8, wherein at least the first continuously set portion 44 is connected to the rotating disk main body 10 along a direction parallel to the opposing axis m by a bolt v3 used as a connecting member.

When the so-called opposite axial fixation is adopted, when the two ends of the leaf spring 40 are fixed to the rotating disk 7 and the base 8 and deformed into an S shape as shown in FIG10(a), even if a bending moment My around the y axis is applied, since the axial force of the bolt v3 as a connecting member shown in FIG9(b) is orthogonal to the opposite direction, that is, the bending moment My around the axis, it is difficult to generate sliding around the fixing portion. In addition, the end of the leaf spring 40 is integrated with the first continuous setting portion 10 as a part of the rotating disk 7, so that the fixing moment My can be rigidly borne by the component, and the occurrence of bending of the vibration disk 7 can be suppressed, and appropriate parallel movement in the x and y directions can be achieved. Thus, the excitation loss caused by the sliding between the first continuous setting part 44 and the leaf spring 40 and the bending of the rotating disk 7 is eliminated, the resonance magnification is improved, and even a small excitation force can appropriately achieve high frequency and large amplitude.

In addition, the second continuous setting part 42 is connected to the base main body 20 as the main body of the second mass body along the first direction s intersecting the direction of the opposing axis m and the second direction u intersecting the direction of the opposing axis m and the first direction s, so that the torsional stress of the first elastic body 400 on the side of the base 8 as the second mass body can be more strongly fixed between the base 8 and the second continuous setting part 42.

In particular, the second mass body is the base 8 on the fixed side, and the first mass body is the rotating disk 7 on the movable side. At least on the rotating disk 7 side, the above-mentioned opposite axis direction fixation is adopted, so the sliding on the movable side and the bending of the spring fixing parts are eliminated first.

In addition, the first continuous setting part 44 is connected to the rotating disk main body 10 as a part of the first mass body at least at two locations along the direction of the opposing axis m, and the leaf spring 40 is firmly held on the rotating disk main body 10 at multiple locations through the first continuous setting part 44, so that the rotating disk 10 will not bend or tilt and can move parallel to the base 8.

Moreover, the feeder PF as a vibration conveying device is composed of such a rotary vibrator A and a conveying body B fixed on the rotating disk 7 as the first mass body and including a spiral conveying path, so the conveying speed of the items on the conveying body B can be effectively increased.

The third embodiment of the present invention is described above, but the specific structure of each part is not limited to the above embodiment.

For example, the first mass body of the above-mentioned embodiment can be used as a base, and the second mass body can be used as a vibration plate in an upside-down manner. In this case, the second continuous setting part located below the first elastic body and facing upward is arranged in a downward U-shape at the top, and conversely, the first continuous setting part located at the top is arranged at the bottom, and the connection between the base and the first elastic body in the direction of the opposite axis is preferentially performed. The shapes of the first mass body and the second mass body can be appropriately changed.

In addition, in the above-mentioned embodiment, the leaf spring 40 is set to a necked shape that narrows from the end toward the center, but it can also be a rectangular shape as shown in FIG. 11. The other basic structures are the same as the above-mentioned embodiment, and the corresponding parts are marked with the same symbols. In this way, the rigidity of the leaf spring 40' itself is improved, so it is possible to design with a focus on high frequency.

In addition, in the above-mentioned embodiment, the first continuous setting part 44 and the rotating disk main body 10 are connected at two locations along the direction parallel to the opposing axis m using bolts v3 as connecting members, but they can also be connected at one location using bolts v3 as shown in Figure 12 (a). In this case, it is more preferred that the connection location using bolts v3 is located at the middle point of the two leaf springs 40' (or 40), which can prevent sliding by making the moment My around the y-axis roughly orthogonal to the axial force and prevent the vibration disk from bending by using the first continuous setting part 44 to rigidly bear the moment My.

In addition, as shown in FIG12(b), when the first continuous setting portion 44 and the rotating disk main body 10 are connected at two locations in a direction parallel to the opposing axis m using bolts v3 as a connecting member, it is also effective to stagger the connecting hole h3 in the tightening direction u of the bolt v5 for tightening. In this way, the bending strength of the leaf spring 40' (or 40) can be improved.

In addition, in the above-mentioned embodiment, two leaf springs 40 are used, but of course, it is also possible to implement the structure using only one leaf spring 40' (or 40) as shown in FIG13 (a), or a structure using three or more leaf springs, although not shown.

In addition, in the above-mentioned embodiment, the rotating disk 7 as the first mass body and the first continuous setting part 44 are fastened in the direction of the opposing axis m, and the base 8 as the second mass body and the second continuous setting part 42 are fastened in the direction of the s axis orthogonal thereto and the direction of the u axis orthogonal to the m axis and the s axis. However, as shown in FIG. 13(b), the base 8 as the second mass body and the second continuous setting part 42 may also be connected along the direction of the opposing axis m. In this way, even between the base 8 and the second continuous setting part 42, the excitation loss caused by the sliding between the parts and the bending of the spring fixing part can be eliminated in the same manner as between the rotating disk 7 and the first continuous setting part 44.

In addition, various modifications can be made without departing from the scope of the present invention, such as making the leaf spring not tilted relative to the opposing axis direction.

1: First mass body

2: Second mass body

3: The first elastic body

4: Base

5: Second elastic body

6: Elastic adjustment parts

11: Movable counterweight

12: Side connecting plate

13: Slide table

14: Transportation Road

21:Balance weight

31: Piezoelectric components

32: protrusion

51: Lead drop arm

52: Horizontal arm

5A: L-shaped leaf spring (L-shaped spring)

B1: Bolt

B2: Bolts

T: Transport direction

M: Main frame

MS: Inner space (space)

X: Vibrating conveyor (linear feeder)

Claims (6)

A vibration conveying device, which conveys a conveying object on a linear conveying surface by vibration, comprises: a first mass body, which includes the linear conveying surface; a second mass body, which vibrates in an opposite phase relative to the first mass body; a first elastic body, which connects the first mass body and the second mass body; a second elastic body, which connects a base and the second mass body or the first elastic body. body; and an elastic adjustment component, which can change its fixed position relative to the second elastic body; wherein, with respect to the horizontal elastic coefficient of the second elastic body and the lead-vertical elastic coefficient of the second elastic body, by changing the fixed position of the elastic adjustment component in the horizontal region of the second elastic body, at least the lead-vertical elastic coefficient of the second elastic body can be changed independently. A vibrating conveying device as described in claim 1, wherein: the elastic coefficients of the second elastic body in the horizontal and vertical directions can be independently changed. A vibration conveying device, which conveys a conveying object on a linear conveying surface by vibration, comprises: a first mass body, which includes the linear conveying surface; a second mass body, which vibrates in an anti-phase relative to the first mass body; a first elastic body, which connects the first mass body and the second mass body; and a second elastic body, which connects a base and the second mass body or the first elastic body; wherein, with respect to the elastic coefficient of the second elastic body in the horizontal direction and the elastic coefficient of the second elastic body in the lead-vertical direction, at least the elastic coefficient of the second elastic body in the lead-vertical direction can be independently changed, and one end of the second elastic body is installed at the vibration node of the first elastic body. A vibrating conveying device as described in claim 1 or 2, wherein: the second elastic body includes at least one of a horizontal arm portion capable of adjusting the elastic coefficient relative to the vibration component in the lead-vertical direction and a lead-vertical arm portion capable of adjusting the elastic coefficient relative to the vibration component in the horizontal direction. The vibrating conveying device as described in claim 4, wherein: The elastic adjustment component is used to press at least one of the horizontal arm or the vertical arm in the thickness direction, and the effective length of the arm can be changed by adjusting the area pressed to be unable to elastically deform by the elastic adjustment component. The vibrating conveying device as described in claim 4, wherein: the second elastic body is an L-shaped leaf spring including the horizontal arm and the vertical arm.