Vibrating conveyor

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 (X) conveys a conveying object (W) on a linear conveying surface by vibration, wherein the vibration conveying device (X) includes a first mass body (1) including a linear conveying surface, a second mass body (2) vibrating in an anti-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), and a second elastic body (5) connecting a base (4) and the first elastic body (3), and the elastic coefficient of the second elastic body (5) in the horizontal direction and the elastic coefficient of the second elastic body (5) in the vertical direction can at least independently change the elastic coefficient of the second elastic body (5) in the vertical direction.

Description

Technical Field

[0001] The present invention relates to a vibration conveying device which can convey a conveying object in a predetermined direction.

[0002] The present invention also relates to a rotary vibration machine and a vibration conveyor device that achieve a high frequency and a large amplitude as a vibration machine by optimizing the mounting state of main mechanical elements that determine resonance characteristics. Background Art

[0003] 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 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. 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 (vibration-proof spring).

[0004] In such a vibrating conveying device, if the structure supported by the second elastic body produces a rotational motion in the vibrating conveying direction (similar to the motion of shaking the head, hereinafter referred to as "bumping") during vibration, the conveying path cannot vibrate evenly, and in particular the vibration at the end of the conveying path (the downstream end in the conveying direction) increases, and the conveyed object is conveyed roughly, resulting in poor connection with the next process, poor conveying, etc., which has an adverse effect on smooth conveying processing.

[0005] If the elastic principal axis defined by the installation angle of the elastic body (drive spring), the center of gravity of the first mass body, and the center of gravity of the second mass body 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 the jolt is a difficult issue.

[0006] Therefore, the following technology has been proposed: by changing the angle of a flat spring (vibration-proof leaf spring) as an anti-vibration spring, adjusting the spring constant in the vertical direction of the anti-vibration leaf spring, and suppressing the bumping (Patent Document 1, Patent Document 2). When a flat spring (vibration-proof leaf spring) is used as the anti-vibration spring, the principle of suppressing the bumping by adjusting the spring constant in the vertical direction of the anti-vibration leaf spring is as follows.

[0007] That is, when the structure supported by the anti-vibration leaf spring is subjected to a bump (rotational motion), 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 is applied to the structure to suppress the bump. However, when the vertical direction of the anti-vibration leaf spring is strengthened (reinforced), the reaction force to the ground increases, which affects 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 exploring the optimal center of gravity design.

[0008] In addition, 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 vibration. The vibrating 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 path included in the movable portion (first mass body) can be vibrated in the horizontal direction by using an excitation source, so that the conveying object can be conveyed to the downstream side of the conveying 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 (vibration-proof spring).

[0009] As the production volume of the conveyed objects increases, the supply volume (conveying speed of the vibrating conveyor) from the vibrating conveyor is required to be increased more than this. In order to increase the conveying speed, increasing the frequency and amplitude is the first priority.

[0010] Therefore, in order to realize high-frequency and large-amplitude vibration, it has been proposed to use a plurality of thin leaf springs that are not damaged even at a target amplitude and are stacked (a stacked leaf spring method) (Patent Document 3).

[0011] 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 frequency of vibration is. In addition, a drive spring that does not damage each leaf spring even at a large amplitude can be mounted on the vibrating conveyor.

[0012] In addition, as types of rotary vibrators, for example, conventionally there are Fig.14 The rotary 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 for causing the vibration plate 101 and the base 102 to 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.

[0013] On the vibration plate 101 of such a rotary vibration machine 100 Fig.14 When the conveying path 105 is installed as shown and used as a feeder PF as an article conveying device, for example, a high frequency and a large amplitude are required for the rotary vibrator 100 in order to increase the conveying speed.

[0014] The first elastic body 104 is the main factor determining the resonance characteristics of the rotary vibrator 100. 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 is possible to meet the recent demands for higher frequencies and larger amplitudes.

[0015] Patent document 4 shows an improved overlapping leaf spring structure for connecting the leaf spring of 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 achieved by multiple leaf springs, and each leaf spring is easy to bend, so as a whole, the problem of leaf spring breaking is eliminated.

[0016] Prior art literature:

[0017] Patent Document 1: Japanese Patent Application Publication No. 2012-66931 (Japanese Patent No. 5741993).

[0018] Patent Document 2: Japanese Patent Application Publication No. 2007-276963 (Japanese Patent No. 5332080).

[0019] Patent document 3: Japanese Patent Application Laid-Open No. 09-123126 (Japanese Patent No. 3509397).

[0020] Patent Document 4: Japanese Patent Application Publication No. 2012-96853. Summary of the invention

[0021] In addition, if the structure is such that both the anti-vibration function (anti-vibration in the horizontal direction) and the bump suppression function (anti-vibration in the vertical direction) are realized by one anti-vibration spring, when the spring constant in the vertical direction is adjusted by adjusting 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 bump can be changed simply by slightly changing the inclination angle of the anti-vibration leaf spring, which requires strict angle adjustment.

[0022] In addition, since the vibration-proof leaf spring is provided between the base and the second mass body, the second mass body vibrates greatly in the horizontal direction, and the horizontal spring constant of the vibration-proof leaf spring needs to be reduced. As a result, the vibration-proof leaf spring is weakened in the horizontal direction, and when an impact is applied, it is displaced.

[0023] Therefore, in the existing vibration conveying device in which the vibration-proof spring is composed of a flat spring, only the angle of the vibration-proof 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.

[0024] The present invention focuses on such aspects, and a main object of the present invention is to provide a vibrating conveying device including a vibration-proof structure that can easily adjust the bumps.

[0025] In addition, regardless of how the overlapping leaf spring method is adopted, the existing leaf spring is generally fixed by bolts at positions where both ends of the first mass body and the second mass body are connected to each other.

[0026] 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 value) 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 smaller excitation force, which helps to increase the conveying speed.

[0027] However, in the existing structure in which bolts are required to be fixed to each other when the first mass body and the second mass body are connected by a leaf spring, the friction between the leaf spring and the bolt washer increases the viscosity attenuation, and there is a problem of lowering the resonance peak. In addition, due to the large elastic deformation (bending) of the leaf spring and the change in the fixed shape of the flat 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 in reducing the resonance peak, and is also considered to be a factor causing the drive frequency (resonance frequency) to decrease.

[0028] Moreover, 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 fixed ends) of the first mass body and the second mass body. Thus, the first mass body and the second mass body, which are expected to be rigid bodies, 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 components, and the viscosity attenuation increases, thereby reducing the resonance peak and the driving frequency.

[0029] The present invention focuses on such a point, and its main purpose is to provide a vibrating conveying device that can exert large-amplitude vibration performance even with limited exciting force restricted by design, thereby increasing the conveying speed of the conveyed object.

[0030] In addition, in order to achieve high frequency and large amplitude, it is required to minimize the excitation loss. The excitation loss is the loss of excitation energy caused by internal friction between the spring and the fixing part.

[0031] Fig.14The 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.

[0032] like Fig.15 As shown, 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.

[0033] exist Fig.14 In the feeder PF shown in the figure, when the vibration plate 101 and the base 102 rotate in different directions from each other, the leaf spring 104 arranged on the periphery in the longitudinal direction, as shown in FIG. Fig.16 As shown, the two fixed ends of the spring on the side and the opposite side of the origin O generate bending in the long side direction caused by the x-direction force Fx, F'x and the fixed moment My, M'y around the y-axis, i.e., deflection in mode A. 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.

[0034] Conventionally, as a method for fixing the leaf spring at the origin O and the opposite side, for example, there are methods such as Fig.17 (a) The fixing method along the y-axis direction and Fig.17 (b) The fixing method along the x-axis direction is shown.

[0035] exist Fig.17 In case (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, resulting in a large amplitude that cannot be achieved with a small exciting force.

[0036] On the other hand, in Fig.17 In the case of (b), due to the bolt fixing in the x-axis direction, Fig.16 The force Fx in the x-axis direction shown here is not a problem because the bolts are fixed in the orthogonal direction. Fig.17 As shown in (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, the original Fig.17 (c) The spring shown by the dotted line is bent in a cantilever beam manner, but since it is held by 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, in the case where the connected vibration disk 101 is a thin disk-shaped one for lightness, the rotating disk side fixing portion α is subjected to a bending moment, such as Fig.17As shown in (d), the vibration disk 101 is undulating and deflected. Therefore, the spring does not bend in an S-shape, the frequency cannot be increased, and therefore, a high frequency cannot be achieved. In addition, due to the ups and downs of the vibration disk 101, contact interference and friction occur with the conveying body B arranged on the vibration disk 101, and excitation losses still occur, and a large amplitude cannot be achieved. In the case where 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 deflection of the vibration disk 101, etc., forming a more complicated calculation formula.

[0037] However, if the vibration plate 101 as the first mass body is thickened, the inertia moment increases, and if the outer circumference is thickened, it becomes difficult to rotate. Therefore, it is also difficult to achieve high frequency and large amplitude.

[0038] Such a problem is exactly the same even in the single leaf spring structure before overlapping leaf springs. In the case of overlapping leaf spring structures, there is also the problem of sliding between the leaf springs.

[0039] The object of the present invention is to realize a rotary vibrator and a vibrating conveyor. By appropriately installing a first elastic body, which is a main mechanical element determining resonance characteristics, on a mass body, excitation losses caused by sliding between parts and bending of a spring fixing part are eliminated, thereby realizing a high frequency and a large amplitude as a vibrator.

[0040] That is, the first embodiment of the present invention relates to a vibrating conveyor device for conveying an object on a vibrating conveying linear conveying surface. Here, as the conveying object, for example, micro-sized electronic components (workpieces), medical components, etc. can be listed, but the components that can be conveyed by the vibrating conveyor device of this embodiment are not limited to these.

[0041] 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 anti-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 regarding the elastic coefficient of the second elastic body in the horizontal direction and the elastic coefficient of the second elastic body in the vertical direction, at least the elastic coefficient of the second elastomer in the vertical direction can be changed independently.

[0042] Here, the "elastic coefficient of the second elastic body in the horizontal direction" in this embodiment has the same meaning as the "elastic coefficient of the horizontal component in the second elastic body", and the "elastic coefficient of the second elastic body in the vertical direction" has the same meaning as the "elastic coefficient of the vertical component in the second elastic body". In addition, the "horizontal direction" in this embodiment refers to the direction along the elastic principal axis specified by the mounting angle of the first elastic body (the direction parallel or substantially parallel to the elastic principal axis), and the "vertical direction" in this embodiment refers to the direction orthogonal or substantially orthogonal to the elastic principal axis (the normal direction to the elastic principal axis). That is, in this embodiment, the horizontal direction and the vertical direction of the second elastic body are determined based on the elastic principal axis of the first elastic body. The horizontal direction in the "elastic coefficient of the second elastic body in the horizontal direction" is sometimes consistent with the direction intersecting the earth's gravity direction at right angles (the horizontal direction defined in physics), and sometimes is a direction not intersecting the earth's gravity direction at right angles. Similarly, the vertical direction in the "elastic coefficient of the second elastic body in the vertical direction" is sometimes consistent with the earth's gravity direction (the vertical direction defined in physics), and sometimes is inconsistent with the earth's gravity direction. The vibration conveying device of this embodiment may have any structure as long as the elastic coefficient of the second elastic body in the horizontal direction and the elastic coefficient of the second elastic body in the vertical direction can at least independently change the elastic coefficient of the second elastic body in the vertical direction, and the appearance shape of the second elastic body is not particularly limited.

[0043] According to the vibration 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 isolator, so that the first mass body vibrates, and the conveying object on the linear conveying surface can be conveyed along a predetermined conveying direction. Further, according to the vibration conveying device of this embodiment, the elastic coefficient of the horizontal direction of the second elastic body and the elastic coefficient of the vertical direction of the second elastic body are configured to be able to independently change the elastic coefficient of the vertical direction of the second elastic body, so that the elastic coefficient of the vertical direction of the second elastic body can be set to an elastic coefficient that can suppress bumps without affecting the elastic coefficient of the horizontal direction of the second elastic body, and a device that can easily adjust bumps can be realized. Therefore, in a state where the elastic coefficient of the horizontal direction of the second elastic body is set to be large in advance and set to a device that is difficult to be displaced even when an impact is applied from the outside (strong impact resistant device), the elastic coefficient of the vertical direction of the second elastic body can be set to an elastic coefficient that can suppress bumps without affecting the elastic coefficient of the horizontal direction of the second elastic body.

[0044] In particular, if the vibration conveying device of the present embodiment is constructed so as to be able to independently change the elastic coefficients of the second elastic body in the horizontal direction and the vertical direction, it is possible to easily perform bump adjustment by adjusting only the elastic coefficient of the second elastic body in the vertical direction without changing the elastic coefficient of the second elastic body in the horizontal direction, and by adjusting only the elastic coefficient of the second elastic body in the horizontal direction without changing the elastic coefficient of the second elastic body in the vertical direction (for example, maintaining the elastic coefficient in a state that can suppress bumps), the elastic coefficient of the second elastic body in the horizontal direction can be set larger, thereby realizing a device that is less likely to be displaced even when an impact is applied from the outside (a strong impact-resistant device).

[0045] In particular, in the vibration conveying device of the present embodiment, if one end of the second elastic body is mounted on a vibration node of the first elastic body, since the node is a portion that does not displace (does not vibrate) in the horizontal and vertical directions, by mounting one end of the second elastic body on the node, a vibration-proof effect is achieved, thereby enabling the horizontal elastic coefficient of the second elastic body to be set larger. In addition, a node can be specified as a point, but the "node of the first elastic body" in the present 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.

[0046] In addition, Japanese Patent Publication No. 11-91928 discloses i) a structure in which an inertial mass body is fixed on the upper surface of a transversely arranged exciter and an exciter mounting member is fixed on the lower surface thereof, ii) a structure in which the exciter mounting member and the conveyor are connected and fixed via a first connecting member arranged vertically at an angle, 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 support piece and the base are connected and fixed via a second connecting member, and in particular discloses iv) a structure in which one end of the second connecting member is fixed to the side surfaces of both ends of the base by a mechanism such as screw 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, so that the vibration from the base supporting the piezoelectric driven conveyor to the installation surface thereof can be greatly reduced. Here, the member "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, with the structure described in the publication, the elastic coefficient in the vertical direction which is involved in suppressing pitching cannot be fully adjusted.

[0047] In the vibration conveying device of the present embodiment, when an elastic body including at least one of a horizontal arm portion capable of adjusting the elastic coefficient with respect to the vibration component in the vertical direction and a vertical arm portion capable of adjusting the elastic coefficient with respect to the vibration component in the horizontal direction is used as the second elastic body, the shape is simple and the structure for achieving the purpose of the present embodiment can be achieved. It may also include both the horizontal arm portion and the vertical arm portion, or only include the arm portion of either side. In addition, the horizontal arm portion and the vertical arm portion 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 portion and the vertical arm portion intersect at an angle other than 90 degrees).

[0048] In the case where an elastomer including a horizontal arm and a vertical arm is used as the second elastomer, if it is constructed to include an elastic adjustment component that presses at least either one of the horizontal arm and the 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 to be adjusted can be simply adjusted while maintaining the relative positional relationship between the arm and the component to which the arm is connected (the base and the second mass body or the first elastomer) at an appropriate positional relationship. As a result, the elastic coefficient of at least either one of the elastic coefficient of the vibration component in the vertical direction and the elastic coefficient of the vibration component in the horizontal direction can be simply adjusted.

[0049] In particular, if the second elastic body is an L-shaped leaf spring (a flat leaf spring is bent into an L-shape) that integrally includes a horizontal arm and a vertical arm, the elastic coefficient (spring constant) in the vertical direction and the elastic coefficient (spring constant) in the horizontal direction of the second elastic body can be set to appropriate values ​​individually by appropriately adjusting or changing the effective length of either the horizontal arm or the 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 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.

[0050] In addition, a second embodiment of the present invention relates to a vibrating conveyor 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 components, etc. can be listed, but the components that can be conveyed by the vibrating conveyor device of this embodiment are not particularly limited.

[0051] Moreover, the vibration conveying device of this 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 integrally constructed.

[0052] 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 as an integral 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 integrally constructed, ii) a form in which a part of the first mass body, the entire second mass body and the first elastic body are integrally constructed, iii) a form in which the entire first mass body, a part of the second mass body and the first elastic body are integrally constructed, 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 integrally constructed, and all of these forms. In the following, the block that will become an integral structure is set as an integral structure. The linear conveying surface constitutes the first mass body, but in the case of adopting the form ii) and the form iv), the first mass body includes a component constituting an integral structure and a component separate from the integral structure, and it can be appropriately selected whether the component constituting the integral structure in the first mass body forms the linear conveying surface, or the component separate from the integral structure forms the linear conveying surface.

[0053] According to the vibration conveying device of this 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 constructed, so that no friction is generated at the connection part between the first mass body and the first elastic body, and at the connection part 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 part) 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 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 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 spring constant relative to 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 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 exciting force.

[0054] In the vibrating conveying device of the present embodiment, the position at which the first mass body and the second mass body are connected by the first elastic body is not particularly limited. However, in order to ensure a stable supporting state, it is preferably a structure based on an existing connection position based on a driving spring, that is, a structure in which the first elastic body is arranged at the positions of the ends on the upstream side of the conveying direction of the conveying object connecting the first mass body and the second mass body and the ends on the downstream side of the conveying direction.

[0055] If the existing structure of the leaf spring is to connect the two ends of the first mass body and the second mass body to each other by bolt fixing, when the leaf spring is bent, a bending moment is applied to the two ends (spring fixed ends) of the first mass body and the second mass body, thereby the first mass body and the second mass body, which are expected to be rigid bodies as the fixed part of the spring, are bent in an S-shape. At this time, the first mass body and the second mass body, which are the fixed part 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, the viscosity attenuation increases, and the resonance peak is reduced. Therefore, if a vibrating conveying device is provided with a first elastic body at a position in the middle part between the upstream end of the connecting conveying direction and the downstream end of 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 middle part in the conveying direction (front and back direction). Therefore, the first elastic body arranged in the middle part realizes the function of a rib, which can improve the bending rigidity of the first mass body and the second mass body. As a result, the flexural change of the first mass body and the second mass body is further reduced, the deformation of the linear conveying path can be suppressed, and the spring constant is improved, which becomes a structure that satisfies the good conditions of high driving frequency and reduced friction between components to improve the resonance peak.

[0056] As mentioned above, the first mass body may also include components constituting an integral structure and components separate from the integral structure, but in the latter case, if the first mass body includes a first mass body main body constituting a main frame (integral structure) forming an integral structure and a conveying path separate from the first mass body main body and including a linear conveying surface, the linear conveying path requiring high design specifications can be prepared as a special product separate from the main frame, which can reduce the processing burden during the manufacture of the main frame as an integral structure.

[0057] Furthermore, if it is a vibrating conveying device in which a plurality of first elastic bodies are separately arranged between a first mass body and a 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). If the space is a larger space, the space can also be used as an access space, for example, for installing a piezoelectric element on the first elastic body.

[0058] In addition, the third embodiment of the present invention conceives the following mechanism to achieve the above-mentioned object.

[0059] That is, the rotary vibration machine 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 an opposing axis, an excitation source that causes 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, and the first elastic body is set to include a leaf spring, a first continuously set portion continuously set on one end side of the leaf spring and forming a part of the first mass body, and a second continuously set portion continuously set on the other end side of the leaf spring and forming a part of the second mass body, wherein at least the first continuously set portion is connected to the main body of the first mass body by a connecting member along a direction parallel to the opposing axis.

[0060] 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 via the first continuous setting part, so that the fixing torque can be borne by the rigidity of the component, the occurrence of deflection 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 deflection 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.

[0061] In this case, it is preferable that the second continuous portion and the main body 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.

[0062] Therefore, strong fixation can be achieved between the second mass body and the second continuously provided portion with respect to the torsional stress of the first elastic body.

[0063] Alternatively, it is preferable that the second continuously provided portion and the main body portion of the second mass body are also connected along the opposing axis direction.

[0064] Therefore, between the second continuous portion and the second mass body, similarly to between the first continuous portion and the first mass body, it is possible to eliminate the excitation loss due to the sliding between the components and the deflection of the spring fixing member.

[0065] In the above, it is preferred that the second mass body is a fixed side and the first mass body is a movable side. Here, the movable side refers to a side including a vibrating object such as a conveyor, and the fixed side refers to a side that realizes the function of a balancing weight of the movable side.

[0066] In this way, by providing the first mass body on the movable side, it is possible to preferentially eliminate the sliding of the movable portion and the bending of the spring fixing member.

[0067] It is particularly preferable that the first continuous portion and the main body portion of the first mass body are connected at least at two locations along the opposing axis direction.

[0068] In this way, the leaf spring is firmly held at a plurality of locations on the main body of the first mass body via the first continuously provided portion, so that the first mass body can move in parallel with respect to the second mass body without bending or tilting.

[0069] Furthermore, if a vibration conveying device is constituted by any of the above-described rotary vibrators and a conveying body fixed to the first mass body and including a spiral conveying path, the conveying speed of the articles on the conveying body can be effectively increased.

[0070] The effects of the present invention are as follows.

[0071] 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 constructed to be able 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 a vibration-proof structure that can easily adjust the bumps.

[0072] 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 multiplier and obtain a large amplitude.

[0073] In addition, according to the third embodiment of the present invention, by appropriately installing the first elastic body, 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 part, thereby realizing a new rotary vibrator and vibration conveying device with high frequency and large amplitude. BRIEF DESCRIPTION OF THE DRAWINGS

[0074] Figure 1 It is a plan view schematically showing the entirety of the vibration conveyor device (linear feeder) according to the first embodiment and the second embodiment of the present invention.

[0075] Figure 2 It is an exploded perspective view of the vibration conveyor according to the first embodiment and the second embodiment.

[0076] Figure 3 yes Figure 2 Enlarged view of the main part.

[0077] Figure 4 It is a partial omission to indicate Figure 1 Side view of the vibrating conveyor device observed in the direction of arrow A.

[0078] Figure 5 It is a perspective view showing a rotary vibrator and a vibration conveyor according to a third embodiment of the present invention.

[0079] Figure 6 yes Figure 5 Exploded diagram of .

[0080] Figure 7 (a)-(b) Yes Figure 6 Illustration of the main parts.

[0081] Figure 8 It is a perspective view showing a first elastic body constituting the third embodiment.

[0082] Fig. 9 (a)-(c) are diagrams illustrating the structure and installation of the first elastic body.

[0083] Fig.10 (a)-(c) are diagrams for explaining the function of the first elastic body.

[0084] Fig.11 It is a diagram showing a modification example of the third embodiment.

[0085] Fig.12 (a)-(b) are diagrams showing another modified example of the third embodiment.

[0086] Fig.13 (a)-(b) are diagrams of still another modified example of the third embodiment.

[0087] Fig.14 It is a perspective view showing a conventional rotary vibrator and a vibrating conveyor.

[0088] Fig.15 (a) to (d) are explanatory diagrams of the first elastic body according to the conventional example.

[0089] Fig.16 It is an explanatory diagram of the vibration mode of the first elastic body.

[0090] Fig.17 (a) to (d) are diagrams for explaining the problems of this conventional example.

[0091] In the figure: 1—first mass body, 1L—linear conveying surface, 2—second mass body, 3—first elastic body, 4—base, 5—second elastic body, 7—first mass body (rotating disk), 8—second mass body (base), 9—excitation source, 20—main body of the second mass body (base body), 40—leaf spring, 42—second continuous setting part, 44—first continuous setting part, 51—vertical arm part, 52—horizontal arm part, 5A—L-shaped leaf spring (L-shaped spring), 400—first elastic body, A—rotating vibrator, B—conveyor body, K—conveyor object, m—opposing axis, PF—vibration conveyor device (feeder), s—first direction, u—second direction, v3—connector (bolt), X—vibration conveyor device (linear feeder). DETAILED DESCRIPTION

[0092] <First embodiment>

[0093] Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.

[0094] like Figure 1 As shown, the vibrating 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 vibrating conveying device X of the present embodiment is a device that conveys the workpiece K along a linear 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 of the linear conveying path 14 by vibration, and supply it to a predetermined conveying destination. The linear feeder X includes a return portion (return conveying path), which returns the workpiece K (overflowing workpiece K, workpiece K judged not to be in the predetermined conveying posture) as the object to be conveyed to the hopper conveying path when overflow occurs or the workpiece K is judged not to be in the predetermined conveying posture.

[0095] like Figures 1 to 4 As shown, the linear feeder X includes a first mass body 1 including a linear conveying surface, a second mass body 2 vibrating in an anti-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.

[0096] 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 long 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 slide slot 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 Figure 2 As shown, the movable counterweight 11 and the slideway platform 13 are connected to each other via a pair of side connecting plates 12. Figure 4 In the figure, the side connecting plate 12 on the front side of the paper is omitted among the paired side connecting plates 12.

[0097] A conveying path 14 is detachably provided on the upper surface of the chute table 13 via fixing parts such as bolts, and by applying vibration to the conveying path 14, the workpiece K moves in a linear conveying surface (conveyance 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 unit that transmits the vibration of the movable counterweight 11 to the conveying path 14.

[0098] In the following description, the conveying direction T of the workpiece K along the conveying path 14 is referred to as the front-rear direction T, the upstream side of the conveying direction T is referred to as the rear side, and the downstream side of the conveying direction T is referred to as the front side. In addition, the direction perpendicular to the conveying direction T in the horizontal plane is referred to as the width direction W (transverse direction) (see Figure 1 wait).

[0099] like Figure 2 and Figure 4 As shown, the front end and rear end of the chute platform 13 are overhanging 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 overhanging 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.

[0100] In this embodiment, the dimensions (front-to-back dimensions) of the movable counterweight 11 serving as the main component of the first mass body 1 and the balancing counterweight 21 serving 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 counterweight 11 are arranged in a posture opposing each other in the height direction.

[0101] In the line feeder X of the present embodiment, the first elastic body 3 is disposed at a position connecting the front ends and the rear ends of the movable weight 11 and the balance weight 21 .

[0102] The first elastic body 3 includes a flat spring (leaf spring) in which the 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 giving an electric 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 vertical direction. The spring constant composed of the first elastic body 3 and the piezoelectric element 31 is appropriately selected according to the conditions of an arbitrary resonant frequency determined by the weight and size of the conveyed component and the weight of the conveying path 14 (groove). In this embodiment, the first mass body 1 and the second mass body 2 are connected by multiple first elastic bodies 3.

[0103] In addition, in the present embodiment, the first elastic body 3 is also arranged at the predetermined midway portion connecting the front and rear ends of the movable weight 11 and the balance weight 21. The first elastic body 3 is arranged in pairs at respective arrangement locations (locations connecting the movable weight 11 and the balance weight 21) with a slight gap in the front-rear direction T. In the present embodiment, two first elastic bodies 3 are arranged in a manner arranged in the front-rear direction T at the location connecting the front ends of the movable weight 11 and the balance weight 21, at the location connecting the rear ends of the movable weight 11 and the balance weight 21, at the location deviated from the center in the front-rear direction T to the front end side by a predetermined distance in the midway portion between the front and rear ends of the movable weight 11 and the balance weight 21, and at the location deviated from the center in the front-rear direction T to the rear end side by a predetermined distance in the midway portion between the front and rear ends of the movable weight 11 and the balance weight 21, respectively, in the form of eight first elastic bodies 3 in total.

[0104] The linear feeder 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 balancing counterweight 21, and the first elastic body 3 as an integral structure (hereinafter, the integral 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.

[0105] In addition, the movable counterweight 11 and the balance counterweight 21 are supported at both ends and the middle part of the front-back direction T by the first elastic body 3, so 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. Further, 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 a fixing member such as a bolt, it is necessary to ensure the configuration space of the fixing member, but according to this embodiment, it is not necessary to ensure the configuration space of the fixing member, so 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 improved. 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.

[0106] In the linear feeder X of this embodiment, the first elastic body 3 arranged in the middle part 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.

[0107] In this embodiment, a main frame M including the movable weight 11, the balance weight 21 and the first elastic body 3 is integrally formed by wire cutting a piece of metal material. Alternatively, the main frame M may be formed by a processing other than wire cutting.

[0108] In the linear feeder X of the present embodiment, for example, a balancing weight (sub-balancing weight) which is separate from the main frame M may be integrally mounted on the balancing weight 21. As the location where the sub-balancing weight is to be installed, the internal space MS of the main frame M, that is, the larger space MS formed between the first elastic bodies 3 adjacent to each other in the conveying direction T (except for the space between two first elastic bodies 3 arranged closely together) 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 components other than the balancing weight 21 (the first elastic body 3, the piezoelectric element 31, the movable weight 11, the side connecting plate 12). The sub-balancing weight is a component constituting the second mass body 2 in the same manner as 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 bodies 3 adjacent to each other in the conveying direction T) may also be as shown in FIG. Figure 3 and 4 The sizes shown in the figure are equal (equally divided), but they can also be unequal (unequally divided). Figure 3 yes Figure 2In addition, the internal space MS of the main frame M can also be used as an access space for mounting the piezoelectric element 31 on the first elastic body 3.

[0109] Here, the vibration conveying device X of the present embodiment includes a structure (main frame M), which integrally includes a main component of the first mass body 1 of the movable part, namely the movable counterweight 11, a main component of the second mass body 2 functioning as a fixed part relative to the movable counterweight 11, namely the balance counterweight 21, and a first elastic body 3, and is constructed 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 the present embodiment) so that the second elastic body 5 functions as a vibration-proof spring.

[0110] like Figures 2 to 4 As shown, the linear feeder X of this embodiment has second elastic bodies 5 disposed in front and rear of the main frame M, respectively, and the base 4 and the main frame M are connected via the second elastic bodies 5 .

[0111] In the present embodiment, the second elastic body 5 is formed by a flat L-shaped elastic member (L-shaped spring 5A) integrally including a vertical arm portion 51 extending in the vertical direction and a horizontal arm portion 52 extending in the horizontal direction. Figure 2 The second elastic body 5 shown in the figure 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 does not stand up) of the horizontal arm 52 to the base 4.

[0112] 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 its two ends (upper end and lower end) respectively fixed to the movable counterweight 11 and the balance counterweight 21 (fixed and suspended at both ends), so that the node is the central portion in the long side direction. Here, the node of the first elastic body 3 can be a point, but the area where the protrusion 32 is provided on 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 separated along the width direction W of the protrusion 32 (refer to Figure 3 The vertical arm portion 51 is formed with a bolt insertion hole connected to each internal thread hole 33, and the vertical arm portion 51 of the second elastic body 5 can be fixed to the first elastic body 3 by inserting the bolt B1 through the bolt insertion hole and screwing it into the internal thread hole 33. A pressing plate is interposed between the head of the bolt B1 and the vertical arm portion 51 of the second elastic body 5.

[0113] Internal thread holes 41 are provided at two locations spaced apart in the width direction W at the front end and the rear end of the base 4 (see Figure 3The horizontal arm portion 52 is formed with an internal bolt insertion hole connected to each internal thread hole 41 . By inserting the bolt B2 through the internal bolt insertion hole and screwing it into the internal thread hole 41 , the horizontal arm portion 52 of the second elastic member 5 can be fixed to the base 4 .

[0114] In the linear feeder X of the present embodiment, in the conveying direction T, the second elastomer 5 is arranged at a position that does not overlap with the first elastomer 3, and the upper end of the second elastomer 5 is installed on a node in the first elastomer 3 which is approximately the center part in the height direction H. Therefore, when the first mass body 1 vibrates, the vibration of the conveying path 14 is stable, and further stable component conveying processing can be achieved accordingly.

[0115] Furthermore, in order to implement a more stable workpiece conveying process, it is necessary to prevent the conveying path 14 from causing bumping.

[0116] 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 vertical direction without changing the inclination angle of the front-to-back 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 substantially no bumping phenomenon. 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 vertical direction of the second elastic body" has the same meaning as the "elastic coefficient of the vertical component in the second elastic body". In addition, the "horizontal direction" in the present embodiment refers to the direction along the elastic principal axis (the direction parallel to or substantially parallel to the elastic principal axis) determined by the installation angle of the first elastic body 3, and the "vertical direction" in the present embodiment refers to the direction orthogonal or substantially orthogonal to the elastic principal axis (the normal direction relative to the elastic principal axis). In the linear feeder X of the present embodiment, a flat L-shaped second elastomer 5 is used, which includes a horizontal arm portion 52 that can adjust the elastic coefficient of the vibration component in the vertical direction and a vertical arm portion 51 that can adjust the elastic coefficient of the vibration component in the horizontal direction, thereby realizing a structure in which the elastic systems of the second elastomer 5 in the horizontal and vertical directions can be independently adjusted without affecting each other.

[0117] In this embodiment, if Figure 3 and Figure 4As shown, 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 screwed into the internal threaded hole 41 of the base 4 to be tightened. Then, while slightly loosening the tightening state of the bolt B2, the bolt B2 is guided into the long hole 61 to change the fixed position of the elastic adjustment component 6 relative to the horizontal arm portion 52. 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 portion 52 of the second elastic body 5 can be changed. As a result, the effective length of the horizontal arm portion 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.

[0118] Whether to perform such an adjustment operation on each second elastic body 5 sequentially or simultaneously can be selected according to the occurrence state of the bumping phenomenon.

[0119] The elastic adjustment member 6 is not limited to being arranged at a position sandwiching the horizontal arm 52 in the thickness direction, that is, two elastic adjustment members are arranged for one horizontal arm 52, and one elastic adjustment member may be arranged for one horizontal arm 52. In this case, the following structure is sufficient: an elastic adjustment member is used to press the horizontal arm 52 in the thickness direction, and the area pressed so as not to be elastically deformed is adjusted by the elastic adjustment member, thereby changing the effective length of the horizontal arm 52. The elastic adjustment member 6 may also function as a spacer or a gasket.

[0120] In addition, in the present embodiment, a structure in which the free area (effective length) cannot be adjusted is adopted for the vertical arm 51 of the second elastic body 5, i.e., the vertical arm 51 of the L-shaped leaf spring 5A. In such a structure, the adjustment of the elastic coefficient (spring constant) of the horizontal direction of the second elastic body 5 can be performed by replacing (changing) the vertical arm 51 with another second elastic body (omitted from the figure) having different dimensions (vertical length, spring thickness, width, number of overlaps). In addition, for the vertical arm 51 of the second elastic body 5, a structure based on the horizontal arm 52 can also be applied, that is, a flat elastic adjustment component is arranged at a position sandwiching the front end portion of the vertical arm 51 along the conveying direction T (front-back direction T), and a long hole extending in the height direction H is formed in the elastic adjustment component, and the long hole is used to change the fixed position of the elastic adjustment component relative to the vertical arm 51, thereby changing the size of the free area (area not fastened or pressed by the bolt B2 and the elastic adjustment component 6) in the vertical arm 51 of the second elastic body 5. Of course, similar to the modification example of the elastic adjustment member for the horizontal arm 52, it is also possible to adopt a configuration in which one elastic adjustment member is arranged for one vertical arm 51. In this case, as long as the elastic adjustment member is configured to press the vertical arm 51 in the thickness direction, the effective length of the vertical arm 51 can be changed by adjusting the area pressed so as to be unable to elastically deform by the elastic adjustment member.

[0121] In this embodiment, the elastic coefficients of the second elastic bodies 5 provided at two locations in the front and rear along the conveying direction T can be adjusted individually. That is, the elastic coefficients of the second elastic bodies 5 at the two locations in the front and rear can be set to different values.

[0122] In this way, 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 isolator, thereby enabling the first mass body 1 to vibrate and transport the conveying object K on the linear conveying path 14 along the predetermined conveying direction T. Moreover, according to the linear feeder X of the present embodiment, it is constructed to be able to independently change the elastic coefficients of the second elastic body 5 in the horizontal direction and the vertical direction. Therefore, by not changing the elastic coefficient of the second elastic body 5 in the horizontal direction, but only adjusting the elastic coefficient of the second elastic body 5 in the vertical direction, it is easy to adjust the bumps. Moreover, by not changing the elastic coefficient of the second elastic body 5 in the vertical direction (for example, while maintaining the elastic coefficient that can suppress bumps), only adjusting the elastic coefficient of the second elastic body 5 in the horizontal direction, the elastic coefficient of the second elastic body 5 in the horizontal direction can be set larger, and a device that is difficult to be displaced even when an impact is applied from the outside (a strong impact-resistant device) can be realized.

[0123] In particular, in the linear feeder X of the present embodiment, one end of the second elastic body 5 is installed at a node in the first elastic body 3 that does not displace (does not vibrate) in the horizontal and vertical directions even when vibrated, thereby playing a good vibration-proofing role. As a result, the elastic coefficient of the second elastic body 5 in the horizontal direction can be set larger.

[0124] In addition, with respect to the vibration conveying device X of the present embodiment, an elastomer including a horizontal arm portion 52 having an adjustable elastic coefficient for a vibration component in a vertical direction and a vertical arm portion 51 having an adjustable elastic coefficient for a vibration component in a horizontal direction is used as the second elastomer 5. Therefore, the shape is simple and the structure can achieve the purpose of the present embodiment.

[0125] Furthermore, the structure is such that an elastomer including a flat horizontal arm portion 52 and a flat vertical arm portion 51 is applied as a second elastomer, and an elastic adjustment component 6 is included for pressing the horizontal arm portion 52 in the thickness direction. The area pressed so as to be unable to elastically deform is adjusted by the elastic adjustment component 6, so that the effective length of the arm portion (horizontal arm portion 52) to be adjusted can be changed. Therefore, the effective length of the arm portion (horizontal arm portion 52) can be simply adjusted while maintaining the relative positional relationship between the arm portion (horizontal arm portion 52) and the base 4 and the first elastomer 3 which are the connection object components of the arm portion (horizontal arm portion 52) in an appropriate positional relationship. As a result, the elastic coefficient of the vibration component in the vertical direction can be easily and smoothly adjusted.

[0126] In particular, the second elastic body 5 is an L-shaped leaf spring 5A which includes a horizontal arm portion 52 and a vertical arm portion 51 as an integral unit. Therefore, by appropriately adjusting the effective length of either the horizontal arm portion 52 or the vertical arm portion 51, or the effective length of both, the elastic coefficient (spring constant) in the 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.

[0127] 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, an example is given of a structure for adjusting the effective length (the size of the free area) of the arm of the L-shaped spring using an elastic adjustment component that clamps the arm of the L-shaped spring in the thickness direction, but it is not limited thereto, and a structure for adjusting the elastic coefficient of the L-shaped spring without using an elastic adjustment component 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-mentioned embodiment), so that the L-shaped spring as a whole moves along the long side direction of the long hole, and the internal thread hole of the fixing bolt is selected and changed, thereby adjusting the effective length (the size of the free area) of the arm. If it is this structure, sometimes the entire structure (main frame) supported by the L-shaped spring also moves according to the movement amount of the L-shaped spring.

[0128] In addition, as described above, it is also possible to prepare in advance a plurality of L-shaped springs having different lengths, areas, thicknesses, etc. of the vertical arm and the horizontal arm, select a suitable L-shaped spring from them, or change the structure of the elastic coefficients of the second elastic body in the horizontal and vertical directions by replacement.

[0129] The number of the second elastic bodies and the fixing positions relative to the base can be changed appropriately. In addition, the second elastic body can also connect the base and the second mass body.

[0130] The second elastic body of this embodiment may be formed 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.).

[0131] The number and shape of the first elastomer, and the connection position of the first elastomer relative to the first mass body and the second mass body can also be appropriately changed. For example, the first elastomer can also be configured in a posture tilted at a predetermined angle in the conveying direction. In addition, the first elastomer of the above-mentioned embodiment is also configured in a posture tilted at a predetermined angle (about 2 degrees) in the conveying direction. As mentioned above, the "elastic coefficient of the horizontal direction of the second elastomer" in this embodiment has the same meaning as the "elastic coefficient of the horizontal component in the second elastomer", and the "elastic coefficient of the vertical direction of the second elastomer" has the same meaning as the "elastic coefficient of the vertical component in the second elastomer". In addition, the "horizontal direction" in this embodiment refers to the direction along the elastic principal axis specified by the installation angle of the first elastomer (the direction parallel to or approximately parallel to the elastic principal axis), and the "vertical direction" in this embodiment refers to the direction orthogonal or approximately orthogonal to the elastic principal axis (the normal direction relative to the elastic principal axis). That is, in this embodiment, the horizontal direction and the vertical direction of the second elastic body are determined based on the elastic principal axis of the first elastic body. As for the elastic coefficient of the second elastic body in the horizontal direction and the elastic coefficient of the second elastic body in the vertical direction, as long as the structure can at least independently change the elastic coefficient of the second elastic body in the vertical direction, the appearance shape 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 is consistent with the vertical direction of the second elastic body is also included in this embodiment.

[0132] In the above-mentioned embodiment, an example is given of a form in which the movable counterweight 11 (a part of the first mass body 1), the balancing counterweight 21 (a part of the second mass body 2), and the first elastic body 3 are integrally formed, but a form in which all or only a part of them are monomers may 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 it is 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 it is indirectly connected via other components.

[0133] The first mass body only needs to include a linear conveying surface. It may also not include the above-mentioned conveying path (groove) and form a linear conveying surface on the upper surface of the slide table, or form a linear conveying surface on the upper surface of the movable counterweight without including the slide table, or form a linear conveying surface on a component (not limited to the slide table) that vibrates synchronously with the movable counterweight.

[0134] In addition, the second mass body may be composed of only a single balance weight or may include a plurality of balance weights. It is also possible to adopt a structure in which the first mass body is arranged above the second mass body.

[0135] The excitation source may be a component other than the piezoelectric element.

[0136] Furthermore, the object to be conveyed may be various LEDs such as LEDs, electronic devices other than LEDs, or parts other than electronic components such as food.

[0137] 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 vertical direction, the elastic coefficient of the second elastic body in the vertical direction can be independently changed, and the elastic coefficient of the second elastic body in the horizontal direction can be independently changed.

[0138] In addition, the specific structure of each part is not limited to the above-mentioned embodiment, and various modifications can be made within the scope that does not depart from the spirit of the present invention.

[0139] <Second embodiment>

[0140] Hereinafter, a second embodiment of the present invention will be described with reference to the drawings. In the second embodiment, substantially the same components as those of the first embodiment are described with the same reference numerals.

[0141] like Figure 1 As shown, the vibration conveying device X of this embodiment is also a device that moves the workpiece K such as electronic components on the 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 the 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 of the linear conveying path 14 by vibration, and can supply it to the predetermined conveying destination. The linear feeder X includes a return part (return conveying path), and the return part (return conveying path) returns the workpiece K (overflowing workpiece K, workpiece K judged not to be in the predetermined conveying posture) as its object to the hopper conveying path when overflowing or when it is judged that the workpiece K is not in the predetermined conveying posture.

[0142] like Figures 1 to 4 As shown, the linear feeder X includes a first mass body 1 including a linear conveying surface, a second mass body 2 vibrating in an anti-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.

[0143] 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 long 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 slide slot 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 Figure 2 As shown, the movable counterweight 11 and the slideway platform 13 are connected to each other via a pair of side connecting plates 12. Figure 4 In the figure, the side connecting plate 12 on the front side of the paper is omitted among the paired side connecting plates 12.

[0144] A conveying path 14 is detachably provided on the upper surface of the chute table 13 via fixing parts such as bolts, and by applying vibration to the conveying path 14, the workpiece K moves in a linear conveying surface (conveyance 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 unit that transmits the vibration of the movable counterweight 11 to the conveying path 14.

[0145] In the following description, the conveying direction T of the workpiece K along the conveying path 14 is referred to as the front-rear direction T, the upstream side of the conveying direction T is referred to as the rear side, and the downstream side of the conveying direction T is referred to as the front side. In addition, the direction perpendicular to the conveying direction T in the horizontal plane is referred to as the width direction W (transverse direction) (see Figure 1 wait).

[0146] like Figure 2 and Figure 4 As shown, the front end and rear end of the chute platform 13 are overhanging 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 overhanging 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.

[0147] In this embodiment, the dimensions (front-to-back dimensions) of the movable counterweight 11 serving as the main component of the first mass body 1 and the balancing counterweight 21 serving 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 counterweight 11 are arranged in a posture opposing each other in the height direction.

[0148] In the line feeder X of the present embodiment, the first elastic body 3 is disposed at a position connecting the front ends and the rear ends of the movable weight 11 and the balance weight 21 .

[0149] The first elastic body 3 includes a flat spring (leaf spring) in which the 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 giving an electric charge to the piezoelectric element 31, the first elastic body 3 is elastically deformed to generate vibration, causing the first mass body 1 and the second mass body 2 to vibrate. 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 that is not elastically deformed, which is a posture standing up in the vertical direction. The spring constant composed of the first elastic body 3 and the piezoelectric element 31 is appropriately selected according to the conditions of any resonant frequency determined by the conveying speed of the conveyed component, the weight of the conveying path 14 (groove), etc. In this embodiment, the first mass body 1 and the second mass body 2 are connected by multiple first elastic bodies 3.

[0150] In addition, in the present embodiment, the first elastic body 3 is also arranged at the predetermined midway portion connecting the front and rear ends of the movable weight 11 and the balance weight 21. The first elastic body 3 is arranged in pairs at respective arrangement locations (locations connecting the movable weight 11 and the balance weight 21) with a slight gap in the front-rear direction T. In the present embodiment, two first elastic bodies 3 are arranged in a manner arranged in the front-rear direction T at the location connecting the front ends of the movable weight 11 and the balance weight 21, at the location connecting the rear ends of the movable weight 11 and the balance weight 21, at the location deviated from the center in the front-rear direction T to the front end side by a predetermined distance in the midway portion between the front and rear ends of the movable weight 11 and the balance weight 21, and at the location deviated from the center in the front-rear direction T to the rear end side by a predetermined distance in the midway portion between the front and rear ends of the movable weight 11 and the balance weight 21, respectively, in the form of eight first elastic bodies 3 in total.

[0151] Moreover, the linear feeder X of the present embodiment sets the movable counterweight 11, which is the main component of the first mass body 1, the balancing counterweight 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 the "main frame M"). The vibrating conveyor X of the present embodiment includes a structure (main frame M), which integrally includes the movable counterweight 11, which is the main component of the first mass body 1 as a movable part, the balancing counterweight 21, which is the main component of the second mass body 2 that functions as a fixed part relative to the movable counterweight 11, and the first elastic body 3, and is configured to support the integrated structure (main frame M) from the ground (the base 4 that can be regarded as the ground in the present embodiment) by the second elastic body 5, so that the second elastic body 5 functions as a vibration-proof spring.

[0152] like Figures 2 to 4As shown, the linear feeder X of this embodiment has second elastic bodies 5 disposed in front and rear of the main frame M, respectively, and the base 4 and the main frame M are connected via the second elastic bodies 5 .

[0153] In the present embodiment, the second elastic body 5 is formed by a flat L-shaped elastic member (L-shaped spring 5A) integrally including a vertical arm portion 51 extending in the vertical direction and a horizontal arm portion 52 extending in the horizontal direction. Figure 2 The second elastic body 5 shown in the figure 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 does not stand up) of the horizontal arm 52 to the base 4.

[0154] 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 its two ends (upper end and lower end) respectively fixed to the movable counterweight 11 and the balance counterweight 21 (fixed and suspended at both ends), so that the node is the central portion in the long side direction. Here, the node of the first elastic body 3 can be a point, but the area where the protrusion 32 is provided on 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 portions of the protrusion 32 separated along the width direction W (refer to Figure 3 The vertical arm portion 51 is formed with a bolt insertion hole connected to each internal thread hole 33, and the vertical arm portion 51 of the second elastic body 5 can be fixed to the first elastic body 3 by inserting the bolt B1 through the bolt insertion hole and screwing it into the internal thread hole 33. A pressing plate is interposed between the head of the bolt B1 and the vertical arm portion 51 of the second elastic body 5.

[0155] Internal thread holes 41 are provided at two locations spaced apart in the width direction W at the front end and the rear end of the base 4 (see Figure 3 The horizontal arm portion 52 is formed with an internal bolt insertion hole connected to each internal thread hole 41 . By inserting the bolt B2 through the internal bolt insertion hole and screwing it into the internal thread hole 41 , the horizontal arm portion 52 of the second elastic member 5 can be fixed to the base 4 .

[0156] In the linear feeder X of this embodiment, the second elastomer 5 is arranged at a position that does not overlap with the first elastomer 3 in the conveying direction T, and the upper end of the second elastomer 5 is installed on a node in the first elastomer 3 that is roughly the center of the height direction H, thereby improving the vibration resistance and achieving low reaction force.

[0157] 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 vertical direction without changing the inclination angle of the front-to-back 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 bumping phenomenon. 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 vertical direction of the second elastic body" has the same meaning as the "elastic coefficient of the vertical component in the second elastic body". In addition, the "horizontal direction" in the present embodiment refers to the direction along the elastic principal axis specified by the installation angle of the first elastic body 3 (the direction parallel to or approximately parallel to the elastic principal axis), and the "vertical direction" in the present embodiment refers to the direction orthogonal or approximately orthogonal to the elastic principal axis (the direction in which the elastic principal axis is found). In the linear feeder X of the present embodiment, a flat L-shaped second elastic body 5 is used, which includes a horizontal arm portion 52 capable of adjusting the elastic coefficient of the vibration component in the vertical direction and a vertical arm portion 51 capable of adjusting the elastic coefficient of the vibration component in the horizontal direction, thereby realizing a structure in which the elastic coefficients of the second elastic body 5 in the horizontal and vertical directions can be adjusted in opposition to each other without adversely affecting each other.

[0158] In this embodiment, if Figure 3 and Figure 4 As shown, 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 screwed into the internal threaded hole 41 of the base 4 to be tightened. Then, while slightly loosening the tightening state of the bolt B2, the bolt B2 is guided into the long hole 61 to change the fixed position of the elastic adjustment component 6 relative to the horizontal arm portion 52. 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 portion 52 of the second elastic body 5 can be changed. As a result, the effective length of the horizontal arm portion 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.

[0159] Whether to perform such an adjustment operation on each second elastic body 5 sequentially or simultaneously can be selected according to the occurrence state of the bumping phenomenon.

[0160] The elastic adjustment member 6 is not limited to being arranged at a position sandwiching the horizontal arm 52 in the thickness direction, that is, two elastic adjustment members are arranged for one horizontal arm 52, and one elastic adjustment member may be arranged for one horizontal arm 52. In this case, the following structure is sufficient: an elastic adjustment member is used to press the horizontal arm 52 in the thickness direction, and the area pressed so as not to be elastically deformed is adjusted by the elastic adjustment member, thereby changing the effective length of the horizontal arm 52. The elastic adjustment member 6 may also function as a spacer or a gasket.

[0161] In addition, in the present embodiment, a structure in which the free area (effective length) cannot be adjusted is adopted for the vertical arm 51 of the second elastic body 5, i.e., the vertical arm 51 of the L-shaped leaf spring 5A. In such a structure, the adjustment of the elastic coefficient (spring constant) of the horizontal direction of the second elastic body 5 can be performed by replacing (changing) the vertical arm 51 with another second elastic body (omitted from the figure) having different dimensions (vertical length, spring thickness, width, number of overlaps). In addition, for the vertical arm 51 of the second elastic body 5, a structure based on the horizontal arm 52 can also be applied, that is, a flat elastic adjustment component is arranged at a position sandwiching the front end portion of the vertical arm 51 along the conveying direction T (front-back direction T), and a long hole extending in the height direction H is formed in the elastic adjustment component, and the long hole is used to change the fixed position of the elastic adjustment component relative to the vertical arm 51, thereby changing the size of the free area (area not fastened or pressed by the bolt B2 and the elastic adjustment component 6) in the vertical arm 51 of the second elastic body 5. Of course, similar to the modification example of the elastic adjustment member for the horizontal arm 52, it is also possible to adopt a configuration in which one elastic adjustment member is arranged for one vertical arm 51. In this case, as long as the elastic adjustment member is configured to press the vertical arm 51 in the thickness direction, the effective length of the vertical arm 51 can be changed by adjusting the area pressed so as to be unable to elastically deform by the elastic adjustment member.

[0162] Moreover, as described above, the vibration conveying device X of the present embodiment sets the movable counterweight 11, which is the main component of the first mass body 1, the balance counterweight 21, which is the main component of the second mass body 2, and the first elastic body 3 as an integral 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 at 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.

[0163] In addition, according to the vibrating conveying device X of the present embodiment, the movable counterweight 11 and the balancing counterweight 21 are supported at both ends and in the middle of the front-to-back direction T by the first elastic body 3. Therefore, the flexural 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.

[0164] 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 a fixing member such as a bolt, it is necessary to ensure the configuration space of the fixing member. However, according to the present embodiment, it is not necessary to ensure the configuration space of the fixing member, 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 to be 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.

[0165] In the linear feeder X of this embodiment, the first elastic body 3 arranged in the middle part between the front end and the rear end of the first mass body 1 (movable counterweight 11) and the second mass body 2 (balancing 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.

[0166] In this embodiment, the main frame M including the movable weight 11, the balance weight 21 and the first elastic body 3 is formed by wire cutting on a single metal material. Alternatively, the main frame M may be formed by a process other than wire cutting.

[0167] In the linear feeder X of the present embodiment, for example, a balancing weight (secondary balancing weight) which is separate from the main frame M can be integrally mounted on the balancing weight 21. As the location where the secondary balancing weight is set, the internal space MS of the main frame M, that is, the larger space MS formed between the first elastic bodies 3 adjacent to each other in the conveying direction T (except for the space between the first elastic bodies 3 arranged closely in a group of two) can be cited. In this case, as long as the secondary balancing weight is set in the internal space MS of the main frame M, the condition that the secondary 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, the side connecting plate 12) is satisfied. The secondary balancing weight is a component constituting the second mass body 2 in the same manner as 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 bodies 3 adjacent to each other in the conveying direction T) can be as follows. Figure 3 and 4The sizes shown in the figure are equal (equally divided), but they can also be unequal (unequally divided). Figure 3 yes Figure 2 In addition, the internal space MS of the main frame M can also be used as an access space for mounting the piezoelectric element 31 on the first elastic body 3.

[0168] Thus, according to the linear feeder X of the present 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 portion (balance weight), and the second elastic body 5 functions as a vibration isolator, so that the first mass body 1 vibrates, and the conveying object K on the linear conveying path 14 can be conveyed along the predetermined conveying direction T. Moreover, according to the linear feeder X of the present embodiment, the movable weight 11 as a part of the first mass body 1, the balance weight 21 as a part of the second mass body 2, and the first elastic body 3 are integrally constructed, so that no friction occurs at the connection portion between the first mass body 1 and the first elastic body 3, and at the connection portion between the second mass body 2 and the first elastic body 3, and compared with a 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 conditions (connection conditions of the connection parts) do 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 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 exciting force.

[0169] 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 arranged at the positions of 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, similarly to the existing connection portion based on the driving spring, thereby ensuring a stable supporting state based on the first elastic body 3.

[0170] In particular, in the vibrating conveying device X of the present embodiment, the first elastic body 3 is also arranged at the position of the midway portion between the upstream end portion (rear end portion) of the movable counterweight 11 (the main component of the first mass body 1) and the downstream end portion (front end portion) of the conveying direction T, so that the first elastic body 3 arranged in the midway portion functions as a rib, which can further improve the bending rigidity of the movable counterweight 11 and the balancing weight 21. As a result, the flexural changes of the movable counterweight 11 and the balancing weight 21 are further reduced, and the deformation of the linear conveying path 14 can be suppressed. In addition, the spring constant is improved, which becomes a structure that satisfies the good conditions of high driving frequency and reduced friction between components to increase the resonance peak.

[0171] 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 into one structure, the driving frequency and amplitude of the vibration of the integrated structure (main frame M) can be increased, a high resonance multiplier can be achieved, a large amplitude can be obtained, and a vibrating conveying device X that can increase the conveying speed of the conveyed object K can be realized.

[0172] In addition, in the vibrating 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 a 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 used. Therefore, the linear conveying path 14 requiring high design specifications can be prepared as a special part separately from the main frame M, which can reduce the processing burden during the manufacture of the main frame M as an integral structure.

[0173] In addition, the present 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 arranged in a posture inclined at a predetermined angle in the conveying direction.

[0174] In the above-mentioned embodiment, a form in which the movable counterweight 11 (a part of the first mass body 1), the balancing weight 21 (a part of the second mass body 2) and the first elastic body 3 are integrally constructed is shown, but a form in which the entire first mass body, a part of the second mass body and the first elastic body are integrally constructed, a form in which a part of the first mass body, the entire second mass body and the first elastic body are integrally constructed, or a form in which the entire first mass body, the entire second mass body and the first elastic body are integrally constructed may also be adopted.

[0175] That is, the first mass body of the present embodiment may be composed only of a member (movable weight) constituting the integral structure (main frame), or may include a main member constituting the integral structure (main frame) and a member separate from the integral structure.

[0176] Likewise, the second mass body of this embodiment may be composed only of the main member (balance weight) constituting the integral structure (main frame), or may include the main member constituting the integral structure (main frame) and a member separate from the integral structure.

[0177] The first mass body only needs to include a linear conveying surface, and may also include the above-mentioned conveying path (groove) but form a linear conveying surface on the upper surface of the chute table, or include the chute table but form a linear conveying surface on the upper surface of the movable counterweight, or form a linear conveying surface on a component that vibrates synchronously with the movable counterweight (not limited to the chute table). In particular, when the first mass body is composed only of a component equivalent to the above-mentioned movable counterweight, it is preferred that the first mass body is arranged above the second mass body, and the linear conveying surface is formed on the upper surface of the first mass body.

[0178] The vibration conveying device of this embodiment includes a form in which the second elastic body that plays a vibration-proof role 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 their fixed positions relative to the base or the integral structure (main frame) can be appropriately changed. In addition, the second elastic body can also connect the base and the second mass body.

[0179] The second elastic body may 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.

[0180] The excitation source may be a component other than the piezoelectric element.

[0181] Furthermore, the object to be conveyed may be various LEDs such as LEDs, electronic components other than LEDs, or parts other than electronic components such as food.

[0182] In addition, the specific structure of each part is not limited to the above-mentioned embodiment, and various modifications can be made within the scope that does not depart from the spirit of the present invention.

[0183] <Third Embodiment>

[0184] Below, refer to Figures 5 to 10 A third embodiment of the present invention will be described.

[0185] The rotary vibration machine 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 causing the vibration plate 7 and the base 8 to 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 vibration machine A is equipped with a conveying body B, which includes a conveying path erected in a spiral shape, thereby forming a feeder PF as a vibrating conveying device. The conveying body B of this embodiment is configured to arrange and supply tiny items such as IC chips.

[0186] The vibration disk 7 includes a disc-shaped vibration disk body 10 that forms the main body of the first mass body and a first continuous setting portion 44, which is installed on the vibration disk body 10 and forms a part of the first mass body. On the outer periphery of the vibration disk body 10, first connection portions 16 on the vibration disk side connected to the first elastic body are provided at multiple equiangular locations, in this embodiment, at three locations, and second connection portions 17 on the vibration disk side connected to the excitation source 9 are provided at multiple equiangular locations that are phase-shifted from these first connection portions 16 on the vibration disk side, in this embodiment, at three locations. The first connection portion 16 on the vibration disk side is a shape that is hollowed out downward and radially outward, specifically, it is a downward U-shaped recess with a bottom when viewed from the side. The second connection portion 17 on the vibration disk side is a protrusion that protrudes downward from the vibration disk body 10.

[0187] The base 8 includes a truncated cone-shaped base body 20 that forms the main body of the second mass body and a second connection portion 42 to be described later that is installed 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 connection portion 26 that is located at a position corresponding to the first connection portion 16 on the vibration disk side and connected to the first elastic body 400 and a second base-side connection portion 22 that is located at a position corresponding to the first connection portion 17 on the vibration disk side and connected to the excitation source 9 are provided on the periphery of the base 8. Figure 6 and Figure 7 As shown in (a), the first connection portion 26 on the base side is hollowed out upward and radially outward, specifically, a U-shaped groove-shaped concave portion with a bottom when viewed from the side. Figure 6 and Figure 7 As shown in (b), the base-side second connection portion 22 is located inside the space where the vibration plate-side second connection portion 17 is movably arranged, and includes a second leaf spring accommodation portion 23 and a connection member contact portion 24 to be described later.

[0188] The excitation source 9 includes a connecting member 36 constituting a part of the base 8 as a second mass body, a second leaf spring 37 as a second elastic body which is arranged in a horizontal shape and has a base end connected to the connecting member 36 and a front end side extending in the radial direction, and a bimorph or unimorph type piezoelectric element driving unit 38 which is attached to both surfaces or one surface of the second leaf spring 37 and causes the second leaf spring 37 to bend by vibration. Figure 7 As shown in (b), the base 8 is provided with the above-mentioned second leaf spring accommodating portion 23 which extends in a star shape from the center to three directions when viewed from above and is open upward and radially outward, and the above-mentioned L-shaped connecting component abutment portion 24 located between adjacent second leaf spring accommodating portions 23, and the connecting component 36 on which the base end of the second leaf spring 37 is installed is fastened to the bottom surface of the base 8 from the opposite axis z direction, i.e., the upward direction, by the bolt v1 serving as a fixing member in a state in which the two surfaces abut against the connecting component abutment portion 24.

[0189] The base end of the second leaf spring 37 is horizontally connected to the connecting member 36 by a bolt v21 serving 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 disk side protruding downward from the vibration disk body 10 by a bolt v22 serving as a fixing member.

[0190] The first elastic body 400 connects the vibration plate 7 and the base 8, thereby mainly functioning as a resonance spring. Figure 8 As shown, an integrated leaf spring structure (further, an integrated overlapping leaf spring structure) is formed, which includes a plurality of (two in this embodiment) leaf springs 40, the above-mentioned first continuously set portion 44 which is continuously arranged on one end side of each leaf spring 40 and forms a part of the vibration disk 7, and the above-mentioned second continuously set portion 42 which is continuously arranged on the other end side of each leaf spring 40 and forms a part of the base 8.

[0191] The leaf springs 40 are arranged parallel to each other. Fig.15 Similarly, 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, Figure 5 and Figure 8 The leaf spring 40 shown in FIG. 1 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 with respect to the opposing axis m of the rotary vibrator A. When observing each leaf spring 40, as shown in FIG. Fig. 9As shown in (c), the width dimension D in the y direction is not a rectangular shape from one end 40e1 to the other end 40e2 as shown by the imaginary line, but is a smoothly necked shape that gradually narrows from the upper and lower ends 40e1 and 40e2 toward the central part 40m as shown by the solid line. This shape is given by necking spring steel, carbon steel, etc., which is a spring material.

[0192] Figure 8 The first continuous arrangement portion 44 shown in FIG. 1 is a rectangular parallelepiped formed integrally with the upper end of each leaf spring 40. Figure 5 and Figure 6 As shown, it is tightly arranged in the recessed portion 16 which is the first connecting portion on the vibration plate side. Figure 8 The second connecting portion 42 shown in FIG. 1 is a U-shaped structure formed by a bottom portion 42a integrally formed with the lower end portion of each leaf spring 40, and a right side portion 42b and a left side portion 42c disposed on both sides of the bottom portion 42a in a manner of surrounding each leaf spring 40. Figure 5 to Figure 7 As shown, it is tightly arranged in the recessed portion 26 serving as the first connection portion on the base side.

[0193] That is, the first elastic body 400 is disposed in a positional relationship such that the first elastic body 400 can be detachably fitted from the outside into the rotating disk 7 as the first mass body and the base 8 as the second mass body.

[0194] like Figure 5 , Figure 6 as well as Figure 8 As shown, the first continuous portion 44 and the vibration plate body 10 are connected at two locations along a direction parallel to the opposing axis m by connecting members v3. Figure 6 and Figure 8 The portion denoted by the symbol h3 is a connection hole used therefor.

[0195] 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. Figure 8 In the figure, the parts indicated by the symbols h4 and h5 are holes for connection therewith. In the case of this embodiment, the first direction s is a tangential 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 substantially consistent with the first direction s, and the width direction y of the leaf spring is consistent with the second direction u.

[0196] In this embodiment, in order to reduce the moment of inertia, the vibration plate body 10 is made of aluminum. However, if the spring is directly connected to the vibration plate 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. Fig. 9 As shown in (b), the first continuous portion 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 bending rigidity of the joint between the leaf spring 40 constituting the first elastic body 400 and the rotating disk body 10 is improved. Similarly, the second continuous portion 42 formed integrally with the leaf spring 40 is made of spring materials such as spring steel and carbon steel at the joint between the leaf spring 40 constituting the first elastic body and the base body 20 as the main body of the second mass body, which has the effect of improving the bending rigidity of the joint between the leaf spring 40 and the base body 20. In addition, for the convenience of explanation Fig. 9 (b) is represented by a leaf spring 40, but the leaf spring 40 of this embodiment is as follows Fig. 9 (a) There are two leaf springs, so each leaf spring 40 has the above-mentioned structure and has the same effect.

[0197] Then, by repeatedly applying a voltage of a desired frequency to the piezoelectric element driving unit 38, the vibration disk 7 is vibrated in the forward and reverse directions via the second leaf spring 37. Accordingly, the leaf spring 40 as the first elastic body is flexurally vibrated.

[0198] In this flexural vibration, Fig.10 (a) shows the bending in the long side direction. This bending is the decisive factor in determining the resonance characteristics. With this bending, the two fixed ends of the spring on the origin O side and the opposite side generate forces Fx and F'x in the x direction and fixed moments My and M'y around the y axis. This is called the deflection of mode A.

[0199] In addition, the resulting Fig.10 (b) shows a torsion about the z-axis. With this torsion, a moment Mz is generated around the origin O as viewed from the z-axis direction. This is referred to as deflection in the B mode.

[0200] Further, it follows Fig.10 (c) shows bending in the width direction. With this bending, a force Fy in the y direction and a fixed moment Mx around the x-axis are generated on the opposite side of the origin. That is, when the vibration disk 102 rotates relative to the base 101, the phase of the vibration disk 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 disk side fixing portion α moves in the width direction (radial direction). This is referred to as C-mode deflection.

[0201] Among them, mainly by the deflection in the A mode, it is possible to amplify the vibration to the necessary frequency and amplitude at or near the resonance point, thereby efficiently driving the vibration plate 7 .

[0202] At this time, the first leaf spring 40 as the first elastic body is arranged in the z-axis direction which is inclined relative to the opposing axis m, so that the vibration plate 7 performs simultaneous vertical motion (vibration) and circumferential rotational motion (vibration). As a result, the feeder PF as 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 upper part along the spiral conveying path.

[0203] 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 causing the rotating disk 7 and the base 8 to 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.

[0204] Moreover, the first elastic body 400 is set to an integrated leaf spring structure, which includes a leaf spring 40, a first continuously set portion 44 continuously set on one end side of the above-mentioned 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 above-mentioned 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 body 10 along a direction parallel to the opposing axis m using a bolt v3 as a connecting member.

[0205] When the so-called opposite axis direction fixing is adopted, Fig.10 As shown in (a), 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, even if a bending moment My about the y-axis is applied, Fig. 9 The axial force of the bolt v3 as a connecting member shown in (b) is orthogonal to the opposite direction, that is, the bending moment My around the axis, so it is difficult to cause sliding around the fixed part. In addition, the end of the leaf spring 40 is integrated with the first continuous setting part 10 as a part of the rotating disk 7, so that the fixing moment My can be rigidly borne by this component, and the occurrence of deflection of the vibration disk 7 can be suppressed, and appropriate parallel movement in the x and y directions can be achieved. In this way, the excitation loss caused by sliding between the first continuous setting part 44 and the leaf spring 40 and the deflection 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.

[0206] In addition, the second continuous setting portion 42 is connected to the base main body 20 serving as the main body of the second mass body along a first direction s intersecting the direction of the opposing axis m and a second direction u intersecting the direction of the opposing axis m and the first direction s. Therefore, the torsional stress on the side of the base 8 serving as the second mass body relative to the first elastic body 400 can be more strongly fixed between the base 8 and the second continuous setting portion 42.

[0207] In particular, the second mass body is the fixed side base 8, and the first mass body is the movable side rotating disk 7. At least on the rotating disk 7 side, the above-mentioned opposite axial direction fixation is adopted, so that sliding on the movable side and bending of the spring fixing parts are preferentially eliminated.

[0208] In addition, the first continuous setting portion 44 is connected to the rotating disk body 10 which is 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 body 10 at multiple locations via the first continuous setting portion 44. Therefore, the rotating disk 10 will not bend or tilt and can move parallel to the base 8.

[0209] The feeder PF as a vibration conveying device is composed of such a rotary vibrator A and a conveying body B fixed to the rotating disk 7 as the first mass body and including a spiral conveying path. Therefore, the conveying speed of the articles on the conveying body B can be effectively increased.

[0210] The third embodiment of the present invention has been described above, but the specific structure of each part is not limited to the above-described embodiment.

[0211] For example, the first mass body of the above embodiment can be used as a base and the second mass body can be used as a vibration plate inverted upside down. In this case, the second continuous setting part with an upward U-shape located below the first elastic body is located at the top and configured to be a downward U-shape, and conversely, the first continuous setting part located at the top is located at the bottom, and the connection between the base and the first elastic body in the direction of the opposing axis is preferentially performed. The shapes of the first mass body and the second mass body can be appropriately changed.

[0212] In the above embodiment, the leaf spring 40 is formed into a necked shape that narrows from the end toward the center, but it may also be formed into a necked shape. Fig.11 The other basic structures are the same as those in the above-mentioned embodiment, and the same reference numerals are given to corresponding parts. Thus, the rigidity of the leaf spring 40' itself is improved, so that a design focusing on high frequency can be performed.

[0213] In the above embodiment, the first continuous portion 44 and the rotating disk body 10 are connected at two locations in a direction parallel to the opposing axis m by bolts v3 as connecting members. However, Fig.12(a) is connected at one position with a bolt v3. In this case, it is more preferable that the connection position of the bolt v3 is located at the middle point of the two leaf springs 40' (or 40), which has the same effect in that the moment My around the y-axis is roughly orthogonal to the axial force and can prevent sliding, and the moment My is rigidly supported by the first continuous setting part 44 to prevent the vibration disk from bending.

[0214] In addition, if Fig.12 As shown in (b), when the first continuous portion 44 and the rotating disk body 10 are connected at two locations in a direction parallel to the opposing axis m using bolts v3 as connecting members, it is also effective to stagger the connecting holes h3 in the tightening direction u of the bolts v5 for tightening. In this way, the bending strength of the leaf spring 40' (or 40) can be improved.

[0215] In addition, in the above embodiment, two leaf springs 40 are used, but it is of course also possible to use Fig.13 The structure shown in (a) uses only one leaf spring 40' (or 40), but although not shown in the figure, it is implemented using a structure of three or more leaf springs.

[0216] In the above embodiment, the rotating disk 7 as the first mass body and the first continuous installation 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 installation part 42 are fastened in the s-axis direction orthogonal thereto and in the u-axis direction orthogonal to the m-axis and the s-axis. However, the above embodiment may be used as follows: Fig.13 As shown in (b), the base 8 as the second mass body and the second continuous installation part 42 are also connected along the direction of the opposing axis m. In this way, even between the base 8 and the second continuous installation part 42, as between the rotating disk 7 and the first continuous installation part 44, the excitation loss caused by the sliding between the parts and the deflection of the spring fixing part can be eliminated.

[0217] In addition, various modifications may be made without departing from the gist of the present invention, such as configuring the leaf spring not to be inclined with respect to the opposing axis direction.

Claims

1. A vibrating conveying device that conveys an object to be conveyed on a linear conveying surface by vibration, wherein the vibrating conveying device is characterized in that: Include: A first mass body, which includes the above-mentioned linear conveying surface; a second mass body that vibrates in an anti-phase relative to the first mass body; A first elastic body connecting the first mass body and the second mass body; A second elastic body, comprising a horizontal arm portion capable of adjusting an elastic coefficient with respect to a vibration component in a vertical direction and a vertical arm portion capable of adjusting an elastic coefficient with respect to a vibration component in a horizontal direction, and connecting the base and the second mass body or the first elastic body; and an elastic adjustment member, which is arranged in the thickness direction of the horizontal arm portion of the second elastic body and is fixed to the base together with the second elastic body, 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 vertical direction, at least the elastic coefficient of the second elastic body in the vertical direction can be changed independently. The elastic coefficient of the horizontal arm in the vertical direction can be changed by pressing the horizontal arm in the thickness direction with the elastic adjustment component and adjusting the area of ​​the horizontal arm that is pressed to be unable to be elastically deformed with the elastic adjustment component. By adjusting the region of the vertical arm portion that is pressed so as to be unable to elastically deform using the elasticity adjusting member, it is possible to change the elastic modulus of the vertical arm portion in the horizontal direction.

2. The vibrating conveyor according to claim 1, It is characterized in that The elastic coefficients of the second elastic body in the horizontal direction and the vertical direction can be changed independently.

3. The vibrating conveying device according to claim 1 or 2, It is characterized in that When the second elastic body connects the base and the first elastic body, one end of the second elastic body is mounted on the vibration node of the first elastic body.

4. The vibrating conveying device according to claim 3, It is characterized in that The elasticity adjusting member presses the vertical arm portion in the thickness direction, thereby changing the effective length of the vertical arm portion, thereby changing the elastic modulus of the vertical arm portion in the horizontal direction.

5. The vibrating conveyor according to claim 1, It is characterized in that The second elastic body is an L-shaped leaf spring integrally including the horizontal arm portion and the vertical arm portion.

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