KR20210089584A - Rotating vibrator and vibration transfer device - Google Patents

Abstract

The present invention provides a vibration transfer device having a vibration isolation structure capable of easily adjusting pitching without causing significant increase in cost and complication of a structure. The vibration transfer device (X) for conveying a conveyance object (W) on a linear conveyance surface by vibration includes a first mass body (1) having a linear conveyance surface, a second mass body (2) vibrating in an opposite phase with respect 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). With respect to the elastic coefficient in the horizontal direction of a second elastic body (5) and the elastic coefficient in the vertical direction of the second elastic body (5), at least the elastic coefficient in the vertical direction of the second elastic body (5) is independently changed.

Description

Rotary vibrator and vibrating conveying device {ROTATING VIBRATOR AND VIBRATION TRANSFER DEVICE}

The present invention relates to a vibration conveying apparatus capable of conveying an object to be conveyed in a predetermined direction.

Further, the present invention relates to a rotary vibrator and a vibration conveying device in which a high frequency and large amplitude as a vibrator can be achieved by optimizing the installation state of a periodic system element that determines resonance characteristics.

DESCRIPTION OF RELATED ART Conventionally, the vibration conveying apparatus which can convey conveyance objects, such as a workpiece|work, to a predetermined conveyance destination along a conveyance path by vibration is known. The vibration transport device includes a movable part (first mass) having a transport path, a second mass functioning as a fixed part, and a plate-shaped first elastic body (drive spring) connecting the first mass and the second mass, and the movable part By vibrating the conveyance path of (1st mass body) in a horizontal direction, it is comprised so that a conveyance object can be conveyed downstream in a conveyance direction. Further, the vibration conveying device is configured to support the first mass body, the second mass body, and the structure including the first elastic body from the ground by the second elastic body (vibration-proof spring).

In such a vibration conveying device, if a movement (movement such as shaking a neck, hereinafter referred to as "pitching") occurs in the vibration conveying direction of the structure supported by the second elastic body during vibration, the conveying path does not vibrate uniformly, In particular, the vibration at the tip of the conveying path (downstream end in the conveying direction) becomes large, and the conveyed object is conveyed by shaking greatly, or poor connection with the next step or conveying failure occurs, etc., adversely affecting the smooth conveyance process.

When the elastic main shaft defined by the installation angle of the elastic body (driving spring), the center of gravity of the first mass, and the center of gravity of the second mass completely coincide, pitching can be prevented or effectively suppressed. However, since it is difficult to apply a center of gravity design that completely satisfies the above conditions to an actual machine, suppressing pitching is a difficult subject.

Then, by changing the angle of the flat-plate spring (vibration-proof plate spring) which is a vibration-proof spring, the technique of adjusting the spring constant in the vertical direction of a vibration-proof plate spring and suppressing pitching has been devised (patent document 1, patent document 2). When a flat spring (vibration-proof plate spring) is applied as the vibration-proof spring, the principle of suppressing pitching by adjusting the spring constant in the vertical direction of the vibration-proof plate spring is as follows.

That is, when the structure supported by the vibration-proof plate spring is pitching (rotational motion), in order to suppress this pitching, the vertical direction of the vibration-proof plate spring is made firm (strong) to reduce the reaction force from the ground (stable base, etc.) When transmitted to the structure, a force opposite to the rotational direction acts on the structure, and pitching is suppressed. However, if the vertical direction of the anti-vibration plate spring is strengthened (strengthened), the reaction force to the ground increases, which affects the mounting equipment, and the horizontal direction of the anti-vibration plate spring becomes weak. As a design guideline, the optimal center of gravity is After examining the design, it is desirable to suppress pitching by the vibration-proof leaf spring.

Moreover, conventionally, the vibration conveying apparatus which can convey conveyance objects, such as a workpiece|work, to a predetermined conveyance destination along a conveyance path by vibration is known. The vibration transport device includes a movable part (first mass) having a transport path, a second mass functioning as a fixed part, and a plate-shaped first elastic body (drive spring) connecting the first mass and the second mass, and the movable part It is configured such that the object to be transported can be transported downstream in the transport direction by vibrating in the horizontal direction by an excitation source having a transport path included in the (first mass). Further, the vibration conveying device is configured to support the first mass body, the second mass body, and the structure including the first elastic body from the ground by the second elastic body (vibration-proof spring).

The improvement of the amount of supply from a vibration conveying apparatus (conveyance speed by a vibration conveying apparatus) is calculated|required more than ever with the increase in the production volume of a conveyance object. Increasing the driving frequency and amplitude is the first priority to improve the conveying speed.

Therefore, in order to realize vibration of high-frequency amplitude, a mode in which a single thin plate spring that is not damaged even at the time of a target amplitude is stacked and used (superposed plate spring system) has been devised (Patent Document 3).

By adopting such a superposed leaf spring method, the more the leaf springs are overlapped, the larger the spring constant as the first elastic body becomes, enabling high-frequency vibration, and a drive spring that does not break individual leaf springs even at large amplitudes is mounted in the vibration transport device. can do.

Moreover, as a type of a rotary vibrator, the structure as shown in FIG. 14, for example is more common than the prior art. The rotary vibrator 100 includes a vibrating disc 101 as a first mass, a base 102 as a second mass as opposed to the vibrating disc 101 in the opposite axis m direction, and the vibrator. An excitation source 103 for relatively oscillating the half 101 and the base 102 around the opposing axis m, and a third disposed at a position connecting the vibration plate 101 and the base 102 1 is provided with the elastic body 104, and is comprised.

When the conveying path 105 is provided on the vibrating table 101 of the rotary vibrator 100 as shown in FIG. 14 and used as, for example, a component feeder PF which is an article conveying device, in order to increase the conveying speed, such rotation High frequency and large amplitude are required for the vibrator 100 .

In the rotary vibrator 100, mainly the first elastic body 104 is a factor determining the resonance characteristics. For example, when the first elastic body 104 is a leaf spring as shown, if the leaf spring 104 is made thick and long, it is possible to meet the recent demand for high frequency and large amplitude.

Patent Document 4 shows a superimposed plate spring structure in which a plate spring connecting a vibration plate and a base is improved. Conventionally, since it was comprised with the leaf|plate spring of a single-piece|unit, there existed a problem that it became easy to bend by thickening it. On the other hand, in the same document, the function of a single leaf spring is realized by a plurality of leaf springs, and since each leaf spring is easily bent, bending of the leaf spring as a whole is eliminated.

Japanese Patent Laid-Open No. 2012-66931 (Japanese Patent No. 5741993) Japanese Patent Laid-Open No. 2007-276963 (Japanese Patent No. 5332080) Japanese Patent Laid-Open No. 09-123126 (Japanese Patent No. 3509397) Japanese Patent Laid-Open No. 2012-96853

By the way, if two functions of the vibration-proof function (vibration resistance in the horizontal direction) and the pitch suppression function (vibration resistance in the vertical direction) are realized with one vibration-proof leaf spring, the vertical spring constant is adjusted by the angle of the vibration-proof leaf spring. In this case, the spring constant in the horizontal direction of the vibration-proof leaf spring is also necessarily changed, and the degree of pitching is changed only by slightly changing the inclination angle of the vibration-proof leaf spring, and strict angle adjustment is required.

In addition, since the vibration-proof plate spring is provided between the base and the second mass, the second mass vibrates horizontally, and it is necessary to reduce the horizontal spring constant of the vibration-proof plate spring. As a result, the anti-vibration leaf spring is weakened in the horizontal direction, and misalignment occurs when an impact is applied.

As described above, in the conventional vibration conveying apparatus in which the vibration-proof spring is constituted by a flat spring, since only the angle adjustment of the vibration-proof plate spring can be performed, the vertical and horizontal adjustments are in a trade-off relationship, and the vertical and horizontal directions It was not possible to individually adjust the spring constant of

The present invention has paid attention to this point, and its main object is to provide a vibration conveying apparatus having a vibration-proof structure in which pitching can be easily adjusted.

In addition, regardless of whether the overlapping leaf spring method is employed, the conventional leaf spring is generally fixed with bolts at positions connecting both ends of the first mass body and the second mass body, respectively.

Here, as a point for improving a conveyance speed, the point of improving the peak of a resonance characteristic (it may be abbreviated hereafter as a resonance peak) is mentioned. That is, even with the same excitation force, a larger amplitude can be obtained as the resonance magnification is higher, and it becomes possible to realize a large amplitude with a small excitation force, which contributes to the improvement of the conveying speed.

However, in a conventional configuration in which bolts are essential when connecting both ends of the first and second masses with a leaf spring, viscous damping increases due to friction between the leaf spring and the bolt flat washer, and the resonance peak is lowered. A problem arises. Also, due to the large elastic deformation (bending) of the leaf spring, the fixed shape with the flat washer changes and the effective length of the leaf spring changes, whereby the leaf spring, which was originally a linear property spring, becomes a non-linear property spring, which also resonates. It is considered to be a factor that lowers the peak and also a factor that leads to a lowering of the driving frequency (resonant frequency).

Further, in the conventional configuration in which a leaf spring connecting both ends of the first mass and the second mass is fixed with a bolt, when the leaf spring is bent, it is bent at both ends (the spring fixing end) of the first mass and the second mass. The moment acts, whereby the first and second masses, preferably 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 occurs between the parts, and viscous damping increases, so that the resonance peak and the driving frequency are lowered.

The present invention has been focused on this point, and its main object is to provide a vibrating conveying apparatus capable of exhibiting large-amplitude vibration performance even with a limited excitation force with design restrictions, thereby improving the conveying speed of an object to be conveyed. .

Moreover, in order to implement|achieve a high frequency and large amplitude, it is calculated|required to reduce the excitation loss as much as possible. The excitation loss refers to a loss of excitation energy due to, for example, internal friction between the spring and the fixing member.

In Fig. 14, the first elastic body 104 is constituted by a rectangular leaf spring. The leaf spring 104 has a rectangular shape, and is arranged to extend around an opposing axis m between the vibrating disc 101 and the base 102 in a direction inclined to the opposing axis m.

15, the origin O is taken at the center of the thickness direction and width direction of the base fixing side β of the leaf spring 104, the longitudinal direction is the z-axis, the thickness direction is the x-axis, the width direction is the y-axis, Let the opposing axis (m) be the axis of rotation.

Now, in the component feeder PF shown in FIG. 14, when the vibrating disc 101 and the base 102 rotate in different directions, the leaf spring 104 installed in the longitudinal orientation on the outer periphery is shown in FIG. As shown below, A is a bending in the longitudinal direction consisting of the x-direction force (Fx, F'x) and the fixed moment (My, M'y) around the y-axis at both fixed ends of the spring on the opposite side and on the origin (O) side. Mode warping occurs. That is, Fx, F'x, and My, M'y also act on the vibrating disc 101 and the base 102 which are fixedly connected to the leaf spring 104 at both ends.

In the prior art, for example, as a fixing method of a leaf spring on the opposite side to the origin O, a fixing method in the y-axis direction as shown in Fig. 17(a) and a fixing method in the y-axis direction as shown in Fig. 17(b) are used. Similarly, there is a fixing method in the x-axis direction.

In the case of FIG. 17A , since the bolt is fixed in the y-axis direction, when a bending moment My around the y-axis occurs, the leaf spring 104 rotates and slides around the bolt v. When this slippage occurs, it leads to energy loss due to friction, and as a result of a decrease in the resonance magnification, a large amplitude cannot be achieved with a small excitation force.

On the other hand, in the case of FIG. 17(b), since the bolt is fixed in the x-axis direction, the force Fx in the x-axis direction shown in FIG. 16 is bolted in the orthogonal direction, so there is no problem. However, as shown in FIG. 17C , the bending moment My around the y-axis is transmitted to, for example, the rotating half-side fixing part α. That is, when the leaf spring 104 is deformed, the spring is bent in a cantilever manner as shown by a broken line in FIG. The moment My around the y-axis as indicated by is transmitted to the rotating half-side fixing part α. At this time, in the case where the connected diaphragm 101 is made into a thin disc shape for weight reduction, etc., the rotating diaphragm side fixing part α loses a bending moment, and the diaphragm 101 waves as shown in Fig. 17(d). bend like a slap Then, since the spring does not bend into an S-shape and the frequency does not rise, high frequency cannot be realized. Moreover, when the vibration disk 101 undulates, contact interference or friction arises with the conveyance body B arrange|positioned on the vibration disk 101, again, an excitation loss arises, and large-amplification becomes impossible to implement|achieve. When the spring does not bend into an S-shape, it is necessary to add a spring fixed end condition due to bending of the diaphragm 101 or the like to the calculation of the elastic modulus of the first elastic body, resulting in a more complicated calculation formula.

However, if the vibration disc 101, which is the first mass, is thickened, the moment of inertia increases, and if the outer periphery is thickened, it becomes difficult to rotate. Therefore, it is difficult to realize high frequency and large amplitude even by this.

This problem is completely the same even with the single leaf spring structure, which is the predecessor of the overlapping leaf spring. In the case of the overlapping leaf spring structure, there is also a problem of sliding between the leaf springs.

According to the present invention, by properly installing the first elastic body, which is a periodic system element that determines the resonance characteristics, in the mass body, the excitation loss due to sliding between parts or bending of the spring fixing member is eliminated, and high frequency and large amplitude as a vibrator are realized. It aims at realizing the rotary vibrator and a vibration conveyance apparatus which made possible.

That is, the 1st Embodiment of this invention relates to the vibration conveyance apparatus which conveys the conveyance object on a linear conveyance surface by vibration. Here, although a micro-sized electronic component (workpiece), a medical component, etc. are mentioned as a conveyance object, for example, If it can convey by the vibration conveyance apparatus of this embodiment, it will not specifically limit.

In addition, the vibration conveying apparatus according to the present embodiment includes a first mass having a linear conveying surface, a second mass vibrating out of phase with respect to the first mass, and a first elastic body connecting the first mass and the second mass and a second elastic body connecting the base and the second mass or the first elastic body, wherein at least the second elastic body in the vertical direction with respect to the horizontal elastic modulus of the second elastic body and the vertical elastic modulus of the second elastic body It is characterized in that the elastic modulus of is configured to be independently changeable.

Here, the "modulus of elasticity in the horizontal direction of the second elastic body" in the present embodiment is synonymous with "the elastic modulus of the horizontal component in the second elastic body", and the "modulus of elasticity in the vertical direction of the second elastic body" is "the second elastic modulus" 2 It is synonymous with the elastic modulus of a vertical component among an elastic body". In addition, the "horizontal direction" in the present embodiment means a direction along the elastic main axis (a direction parallel or substantially parallel to the elastic main axis) defined by the installation angle of the first elastic body, and " "Perpendicular direction" means a direction perpendicular to or substantially perpendicular to the main axis of elasticity (the direction normal to the main axis of elasticity). That is, in the present embodiment, the horizontal direction and the vertical direction of the second elastic body are determined on the basis of the elastic main axis of the first elastic body, and the horizontal direction in the "horizontal elastic modulus of the second elastic body" is the gravitational force of the earth. In some cases it coincides with the direction (horizontal direction defined in physics) intersecting the direction at right angles to the direction, there are cases in which the direction does not intersect at right angles to the direction of gravity of the earth. In some cases, the vertical direction in ' coincides with the direction of the earth's gravity (vertical direction defined in physics), and sometimes it does not coincide with the direction of the earth's gravity. The vibration conveying device according to the present embodiment has a configuration in which at least the elastic modulus in the vertical direction of the second elastic body can be independently changed with respect to the horizontal elastic modulus of the second elastic body and the vertical elastic modulus of the second elastic body. and the external shape of the second elastic body is not particularly limited.

In the vibration transport apparatus according to the present embodiment, when the first elastic body connecting the first mass body and the second mass body is driven by an appropriate vibrating means to vibrate, the second mass body functions as a fixing part (counter weight), and the second mass body functions as a fixed part (counter weight), and the second mass body functions as a fixed part (counter weight). When the elastic body functions as a vibration isolator, the first mass vibrates and the object to be transported on the linear transport surface can be transported in a predetermined transport direction. Further, in the case of the vibration conveying device according to the present embodiment, the elastic modulus in the vertical direction of at least the second elastic body can be independently changed with respect to the horizontal elastic modulus of the second elastic body and the vertical elastic modulus of the second elastic body. Because of this configuration, the elastic modulus in the vertical direction of the second elastic body can be set to an elastic modulus capable of suppressing pitching without affecting the horizontal elastic modulus of the second elastic body, and a device with easy pitch adjustment can be realized. have. Therefore, in a state in which the horizontal elastic modulus of the second elastic body is set to be large in advance, and it is set as a device (a device resistant to impact) that is unlikely to cause displacement even when an impact is applied from the outside, the horizontal elasticity of the second elastic body is set. Without affecting the modulus, it is also possible to set the modulus of elasticity in the vertical direction of the second elastic body to the modulus of elasticity in which pitching can be suppressed.

In particular, if the vibration conveying device according to the present embodiment is configured such that the respective elastic modulus in the horizontal direction and the vertical direction of the second elastic body can be changed independently, the second elastic body does not change the horizontal elastic modulus of the second elastic body. By adjusting only the elastic modulus in the vertical direction of , the pitch adjustment becomes easy, and the second elastic body does not change the elastic modulus in the vertical direction (for example, while keeping the pitching at an elastic modulus that can be suppressed) of the second elastic body. By adjusting only the elastic modulus in the horizontal direction, the horizontal elastic modulus of the second elastic body can be set large, and even when an external shock is applied, it is possible to realize a device (a device resistant to impact) in which positional displacement is less likely to occur.

In particular, if the vibration conveying device according to the present embodiment has one end of the second elastic body provided in the vibration node of the first elastic body, since the node is a part that does not displace (does not vibrate) in the horizontal and vertical directions, By providing one end of the second elastic body in this section, an anti-vibration action is exhibited, whereby it becomes possible to set large the elastic modulus in the horizontal direction of the second elastic body. In addition, although a clause is a thing which can be specified as a point, "the clause of a 1st elastic body" in this embodiment is a concept including the predetermined area|region which contains the clause which can be specified as a point among 1st elastic bodies.

Further, in Japanese Patent Laid-Open No. 11-91928, regarding a piezoelectric drive type conveying device, i) an inertial mass is fixed to the upper surface of the vibrating body arranged in the transverse direction, and the vibrating body mounting member is fixed to the lower surface thereof A configuration, ii) a configuration for connecting and fixing the vibrating body installation member and a first connection member installed in an inclined manner to the transport body, and iii) fixing the connection member support piece to the longitudinal middle portion of the first connection member, Disclosed is a configuration in which a connecting member support piece and a base are connected and fixed via a second connecting member, and in particular, iv) one end of the second connecting member is fixed to the side surfaces of both ends of the base by means such as screwing, and the second The configuration in which the other end of the connecting member is fixed to the connecting member support piece and the connecting member support piece is fixed to a portion that becomes a section of the first connecting member greatly reduces vibration from the base supporting the piezoelectric drive type conveying device to its mounting surface. It is disclosed that it is possible to reduce. Here, the part "fixed to the part used as the part of the 1st connection member" in the same publication is a connecting member support piece rather than an elastic body, and there exists a clear difference from this embodiment in this point. In addition, if it is the structure described in the same publication, it can be easily understood that adjustment of the elastic modulus of the perpendicular direction which contributes to suppression of pitching is not possible at all.

In the vibration conveying apparatus according to the present embodiment, at least one of a horizontal arm part capable of adjusting an elastic modulus with respect to a vibration component in a vertical direction and a vertical arm part capable of adjusting an elastic modulus with respect to a vibration component in a horizontal direction as a second elastic body; When the provided one is applied, although it is a simple shape, the structure made into the objective of this embodiment can be implement|achieved. What was provided with both a horizontal arm part and a vertical arm part, or the thing provided with only one arm part may be sufficient. In addition, the horizontal arm part and the vertical arm part of a 2nd elastic body do not necessarily need to have an orthogonal relationship, and it may be a non-orthogonal relationship (a relationship where a horizontal arm part and a vertical arm intersect angle other than 90 degrees).

When a second elastic body having a horizontal arm portion and a vertical arm portion is applied, an elastic adjustment member for pressing at least one of the horizontal arm portion and the vertical arm portion in the thickness direction is provided, and the elastic adjustment member presses the elastically non-deformable region If the effective length in the arm part to be adjusted can be changed by adjusting , the relative positional relationship between the arm part and the part to be connected to the arm part (the base and the second mass or the first elastic body) is maintained in an appropriate positional relationship, The effective length of the arm portion can be easily adjusted, and as a result, it is possible to easily adjust the elastic modulus of at least either one of the elastic modulus with respect to the vibration component in the vertical direction and the elastic modulus with respect to the vibration component in the horizontal direction.

In particular, if the second elastic body is an L-shaped leaf spring (a flat plate spring bent in an L-shape) having a horizontal arm and a vertical arm integrally, the effective length of either the horizontal arm or the vertical arm, or By appropriately adjusting or changing the effective lengths of both sides, the elastic modulus in the vertical direction (spring constant) and the elastic modulus in the horizontal direction (spring constant) of the second elastic body can be individually set to appropriate values. Here, by adjusting the effective length of the L-shaped leaf spring in the longitudinal direction (effective length of the vertical arm), the spring constant in the horizontal direction can be adjusted, and the effective length of the L-shaped leaf spring in the transverse direction (effective length of the horizontal arm) can be adjusted. By adjusting, the spring constant in the vertical direction can be adjusted.

Moreover, the 2nd embodiment of this invention relates to the vibration conveyance apparatus which conveys the conveyance object on a linear conveyance surface by vibration. Here, although a micro-sized electronic component (workpiece), a medical component, etc. are mentioned as a conveyance object, for example, If it can convey by the vibration conveyance apparatus of this embodiment, it will not specifically limit.

In addition, the vibration conveying apparatus according to the present embodiment includes a first mass having a linear conveying surface, and a second mass disposed at a position opposite to the first mass in the height direction and vibrating out of phase with respect to the first mass. and a first elastic body connecting the first mass body and the second mass body, wherein 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 formed.

Here, in the aspect "in which at least a part of the first mass, at least a part of the second mass, and the first elastic body are integrally formed" in the present embodiment, i) all of the first mass and the second mass an aspect in which the entirety and the first elastic body are integrally formed, ii) a part of the first mass, all of the second mass, and the first elastic body are integrally formed, iii) the whole of the first mass; Aspects in which a part of the second mass and the first elastic body are integrally formed; iv) an embodiment in which a part of the first mass, a part of the second mass, and the first elastic body are integrally formed, all of these aspects are included. do. Hereinafter, a lump made into an integral structure is made into an integral structure. The linear conveying surface constitutes the first mass, but when the aspect ii) and the aspect iv) are adopted, the first mass includes a component constituting an integral structure and a component separate from the integral structure. , among the first mass body, whether the linear conveying surface is formed on a component constituting the integrated structure or whether the linear conveying surface is formed on a component separate from the integrated structure can be appropriately selected.

In the vibration conveying apparatus according to the present embodiment, since at least a part of the first mass, at least a part of the second mass, and the first elastic body are integrally structured, the connection point between the first mass and the first elastic body and the second Since friction does not occur at the connection point between the mass body and the first elastic body, the viscous coefficient is reduced and the resonance peak is lowered compared to a configuration in which the first elastic body is fixed to the first mass body or the second mass body with a fixing member such as a bolt. doesn't happen Moreover, even at the time of a large amplitude, the fixing condition (connection condition at a connection location) does not change, and the fall of the drive frequency (resonant frequency) by the spring constant nonlinearity of a 1st elastic body can be reduced. Here, if the first elastic body is fixed to the first mass body or the second mass body with a fixing member such as a bolt, as the amplitude of the first elastic body increases, the cross section of the first elastic body plate spring and the bolt contacting the plate spring among the bolts A gap is generated between the blade and the leaf spring and the contact surface of the first mass body or the second mass that comes into contact with the leaf spring, and the effective length of the leaf spring increases, so that the spring constant decreases. This change of the spring constant with respect to the amplitude displacement is referred to as the spring constant nonlinearity of the first elastic body, and in the conventional vibration conveying apparatus, when the amplitude becomes large, the spring constant decreases and the driving frequency tends to decrease. Therefore, in the conventional configuration in which the first elastic body is fixed to the first mass body or the second mass body with a fixing member such as a bolt, the cause of the reduction of the resonance peak, which is unavoidable, can be completely eliminated by the vibration conveying device according to the present embodiment. Therefore, a large amplitude can be realized with a small excitation force.

In the vibration conveying apparatus according to the present embodiment, the position at which the first mass and the second mass are connected by the first elastic body is not particularly limited, but in order to ensure a stable support state, the connection point by the conventional drive spring is not particularly limited. A similar configuration, that is, a configuration in which the first elastic body is disposed at a position where the ends of the object to be transported in the first mass body and the second mass are connected upstream in the transport direction and ends on the downstream side in the transport direction are connected.

In the conventional configuration in which a leaf spring connecting both ends of the first mass and the second mass is fixed with a bolt, when the leaf spring is bent, a bending moment is provided at both ends of the first and second masses (spring fixed ends). acts, whereby the first mass and the second mass, preferably rigid as the fixing part of the spring, are bent in an S shape. At this time, since the first mass and the second mass, which are the fixing parts of the spring, are bent, the spring cannot be fixed, so that the spring constant is lowered, resulting in a decrease in frequency. Also, friction occurs between the parts, which increases the viscous damping, thereby lowering the resonance peak. Therefore, in the case of a vibration conveying device in which the first elastic body is also disposed at a position where intermediate portions between the upstream end in the conveying direction and the downstream end in the conveying direction in the first mass and the second mass are connected, the first elastic body can Since the mass body and the second mass are supported at both ends and the middle part in the transport direction (front-back direction), the first elastic body disposed in the middle part serves as a rib, and the bending rigidity of the first mass and the second mass is improved. As a result, the warpage change of the first mass body and the second mass body is further reduced, the deformation of the linear conveying path can be suppressed, the spring constant is increased, the driving frequency is high, and the friction between the parts is reduced. It becomes a structure which satisfies the favorable condition for raising a resonance peak.

As described above, the first mass body may include a component constituting the integrated structure and a component separate from the integrated structure. In the latter case, the first mass is a main frame (integrated structure) formed as an integrated structure. ) and a transport path that is separate from the first mass body and has a linear transport surface, a linear transport path requiring advanced design specifications is a separate product from the main frame It can be prepared as an integral structure, and the processing burden at the time of manufacturing the main frame, which is an integral structure, can be reduced.

Further, in the case of a vibration conveying apparatus in which a plurality of first elastic bodies are disposed between the first mass and the second mass to be spaced apart along the conveying direction of the object to be conveyed, the space partitioned by the adjacent first elastic members in the conveying direction is an integral structure ( It is formed in the internal space of a main frame), and if the space is a comparatively large space, the said space can be used also as an access space for providing, for example, a piezoelectric element in a 1st elastic body.

In addition, in the third embodiment of the present invention, in order to achieve the above-described object, the following means are taken.

That is, the rotary vibrator according to the present embodiment includes a first mass, a second mass disposed to face the first mass in an axial direction opposite to the first mass, and the first mass and the second mass around the opposing axis. An excitation source for relatively vibrating, and a first elastic body disposed at a position connecting the first mass and the second mass, wherein the first elastic body is attached to a leaf spring and one end of the leaf spring An integrated leaf spring structure including a first continuous installation part that is continuously installed and forms a part of the first mass, and a second continuous installation part that is continuously installed on the other end side of the leaf spring and forms a part of the second mass, Among these, at least the first continuous installation part and the main body of the first mass are connected by a connecting member in a direction parallel to the opposite axis.

If the thickness direction of the leaf spring is the x-direction, the width direction is the y-direction, and the longitudinal direction is the z-direction, the bending moment around the y-axis when both ends of the leaf spring are fixed to the first and second masses and deformed into an S shape. takes However, when configured as described above, since the axial force of the connecting member is orthogonal to the bending moment around the axis in the opposite direction, sliding around the fixed portion is unlikely to occur. In addition, since at least the first elastic body is integrated with a part of the first mass via the first continuous mounting portion, a fixed moment can be received as a member rigidity, and the occurrence of deflection of the first mass is suppressed, so that the first mass is properly formed. Parallel movement can be realized. This eliminates the loss of excitation due to sliding between the first continuous installation part and the first mass or bending of the first mass, so that the resonance magnification is increased, and high frequency and large amplitude can be appropriately realized even with a small excitation force. .

In this case, the second continuous installation part and the main body of the second mass are connected in a first direction intersecting the opposing axial direction, and in the opposing axial direction and in a second direction intersecting the first direction. It is appropriate to do

In this way, it becomes possible to realize a fixing method strong against the torsional stress of the first elastic body on the second mass body side with the second continuous mounting portion.

Alternatively, it is also preferable that the second continuous mounting portion and the main body portion of the second mass are also connected along the opposite axial direction.

In this way, even between the second continuous installation part and the second mass, as between the first continuous installation part and the first mass, it is possible to eliminate vibration loss due to sliding between parts or bending of the spring fixing member.

In the above, it is preferable that the second mass is the fixed side and the first mass is the movable side. Here, the movable side is a side on which an excitation target such as a transport body is provided, and the stationary side is a side that acts as a counterweight on the movable side.

In this way, by setting the first mass to the movable side, sliding on the movable part side and bending of the spring fixing member are preferentially eliminated.

In particular, it is preferable that at least two locations between the first continuous installation part and the main body part of the first mass are connected along the opposite axial direction.

In this way, since the leaf spring is reliably held at a plurality of locations by the main body of the first mass via the first continuous mounting portion, the first mass can move in parallel with respect to the second mass without bending or inclining.

In addition, when the vibrating conveying apparatus is constituted by the rotary vibrator according to any one of the above and a conveying body fixed on the first mass and having a spiral conveying path, the conveyance speed of the article on the conveying body can be effectively improved. thing becomes possible

According to the first embodiment of the present invention, focusing on the second elastic body connecting the base and the second mass or the first elastic body, the elastic modulus in the vertical direction of the second elastic body affects the elastic modulus in the horizontal direction of the second elastic body By setting it as a structure which can be changed independently without giving, it is possible to provide the vibration conveyance apparatus which has a vibration-proof structure in which pitching can be adjusted easily.

Further, according to the second embodiment of the present invention, by adopting a novel configuration that has never been conceived so far, in which at least a part of the first mass, at least a part of the second mass, and the first elastic body are integrally formed, It is possible to provide a vibration transport device capable of achieving a high resonance magnification and obtaining a large amplitude while being able to increase the driving frequency at which the integral structure (main frame) vibrates.

In addition, according to the third embodiment of the present invention, by properly installing the first elastic body, which is a periodic mechanical element that determines the resonance characteristics, in the mass body, the loss of excitation due to sliding between parts or bending of the spring fixing member is eliminated, so that high frequency, It is possible to provide a novel useful rotary vibrator and a vibration conveying device that can realize a large amplitude.

BRIEF DESCRIPTION OF THE DRAWINGS It is a top view which shows typically the whole of the vibration conveying apparatus (linear feeder) which concerns on 1st Embodiment and 2nd Embodiment of this invention.
It is an exploded perspective view of the vibration conveying apparatus which concerns on 1st Embodiment and 2nd Embodiment.
Fig. 3 is an enlarged view of the main part of Fig. 2;
It is a side view which abbreviate|omits a part of the vibration conveyance apparatus seen from the arrow A direction in FIG.
5 is a perspective view showing a rotary vibrator and a vibration conveying device according to a third embodiment of the present invention.
6 is an exploded view of FIG. 5 .
Fig. 7 is an explanatory view of the main part of Fig. 6;
It is a perspective view which shows the 1st elastic body which comprises 3rd Embodiment.
9 is an explanatory diagram of the configuration and installation of the first elastic body.
Fig. 10 is an explanatory diagram of the action of the first elastic body.
11 is a diagram showing a modified example of the third embodiment.
12 is a diagram showing another modified example of the third embodiment.
13 is a diagram showing still another modified example of the third embodiment.
14 is a perspective view showing a rotary vibrator and a vibration conveying device according to a prior art.
Fig. 15 is an explanatory view of the first elastic body of the prior art example.
It is explanatory drawing of the vibration mode of the same 1st elastic body.
Fig. 17 is a diagram for explaining the problem of the prior art example.

<First embodiment>

EMBODIMENT OF THE INVENTION Hereinafter, 1st Embodiment of this invention is described with reference to drawings.

As shown in FIG. 1, the vibration conveyance apparatus X which concerns on this embodiment vibrates the workpiece|work K, such as an electronic component, on the conveyance path 14 (linear conveyance path 14 mentioned later), for example. It is a device that transports to a predetermined transport destination (supply destination) while being moved by the . The vibration conveyance apparatus X of this embodiment is an apparatus which conveys the workpiece|work K to a conveyance destination along the linear conveyance path 14 (henceforth "linear conveyance path 14"). Moreover, the downstream end of the conveyance path (ball conveyance path) of the ball feeder conveyed while aligning is connected to the upstream end of the linear conveyance path 14 (not shown). Therefore, the linear feeder X conveys the workpiece K conveyed via the conveyance path (ball conveyance path) formed in the ball feeder to the end of the linear conveyance path 14 by vibration to a predetermined conveyance destination. it is possible to supply. In this linear feeder X, when it overflows or when it is determined that the workpiece|work K is not a predetermined conveyance attitude|position, it is determined that it is not the workpiece|work K (work K which overflows) or the predetermined conveyance attitude|position which becomes the target workpiece|work K. A return unit (return conveying path) for returning one work K) to the ball conveying path is provided.

As shown in FIGS. 1 to 4 , the linear feeder X includes a first mass body 1 having a linear conveying surface and a second mass body 2 vibrating out of phase with respect to the first mass body 1 . and 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 second connecting the base 4 and the first elastic body 3 to each other It is provided with the elastic body (5).

In the present embodiment, a movable weight 11 (movable part), which is a main component of the first mass 1 , is disposed above the base 4 having an elongated shape along the conveying direction T, and the movable weight 11 is disposed. ), a counterweight 21 (fixed part), which is the main part of the second mass 2 , is disposed above the first elastic body 3 , and the side connecting plate 12 is above the counterweight 21 . ), the chute stand 13 connected to the movable weight 11 is disposed. In this embodiment, as shown in FIG. 2, the movable weight 11 and the chute stand 13 are mutually connected via the side connecting plate 12 which forms a pair. In addition, in FIG. 4, the side connection plate 12 of the front side of the paper surface is abbreviate|omitted among the side connection plates 12 which form a pair.

A conveyance path 14 is provided detachably on the upper surface of the chute stand 13 via a fixing member, such as a bolt, and vibration is applied to the conveyance path 14, so that the workpiece|work K is moved to the conveyance path 14. It moves in the linear conveyance surface (conveyance groove|channel) provided in the. The chute stand 13 shows a movement synchronized with the vibration of the movable weight 11 , and functions as a vibration transmission unit that transmits the vibration of the movable weight 11 to the conveyance path 14 .

In the following description, the conveyance direction T of the workpiece|work K along the conveyance path 14 is made into the front-back direction T, let the conveyance direction T upstream be the rear side, and let the conveyance direction T downstream. to the front side. Moreover, let the direction orthogonal to the conveyance direction T within a horizontal plane be the width direction W (transverse direction) (refer FIG. 1 etc.).

2 and 4, the front end portion and the rear end portion of the chute stand 13 are overhang portions protruding forward and rearward from the movable weight 11, respectively. A sub movable weight (not shown) may be provided, for example, on the downward surface of the front overhang portion of the chute stand 13 . The side connecting plate 12 , the chute stand 13 , and the conveying path 14 are components constituting the first mass 1 , similarly to the movable weight 11 .

In the present embodiment, the dimensions along the transport direction T (front and rear dimensions) of the movable weight 11 as the main component of the first mass body 1 and the counterweight 21 as the main component of the second mass body 2 . is set to be substantially the same, and these counterweights 21 and movable weights 11 are arranged in the postures facing each other in the height direction.

In the linear feeder X of this embodiment, the 1st elastic body 3 is arrange|positioned at the position which connects the front-ends and rear-ends of these movable weight 11 and the counterweight 21.

The 1st elastic body 3 has the form of the flat-plate-shaped spring (plate spring) which made the thickness direction substantially coincide with the conveyance direction T. As shown in FIG. A piezoelectric element 31 functioning as an excitation source is attached to the first elastic body 3, and by applying 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 2 vibrate. Accordingly, the first elastic body 3 functions as a drive spring. The 1st elastic body 3 of this embodiment is set so that the normal attitude|position which is not elastically deformed may become the attitude|position which stood up in the vertical direction. The spring constant including the first elastic body 3 and the piezoelectric element 31 is appropriately adjusted according to the condition of an arbitrary resonance frequency determined by the weight and size of the components to be conveyed, the weight of the conveyance path 14 (trough), and the like. is chosen In the present embodiment, the first mass body 1 and the second mass body 2 are connected by a plurality of first elastic bodies 3 .

Moreover, in this embodiment, the 1st elastic body 3 is also arrange|positioned also at the position which connects predetermined intermediate|middle parts between the front and rear ends of the movable weight 11 and the counterweight 21. As shown in FIG. The 1st elastic body 3 is arrange|positioned in pairs in each arrangement|positioning location (the location which connects the movable weight 11 and the counterweight 21) in the front-back direction T with a slight clearance gap. In this embodiment, a location connecting the front ends of the movable weight 11 and the counterweight 21, a location connecting the rear ends of the movable weight 11 and the counterweight 21, and the movable weight 11 and a portion in the middle between the front and rear ends of the counterweight 21 that is biased by a predetermined distance toward the front end rather than the center in the front-rear direction T, and the intermediate portion between the front and rear ends of the movable weight 11 and the counterweight 21 . The mode in which two first elastic bodies 3 are arranged in the front-rear direction (T) in four places, each of which are skewed by a predetermined distance to the rear end side of the part, by a predetermined distance from the center in the front-rear direction (T), that is, all eight pieces The aspect provided with the 1st elastic body 3 is employ|adopted.

The linear feeder X according to the present embodiment includes a movable weight 11 that is a main part of the first mass body 1 , a counterweight 21 that is a main part of the second mass body 2 , and a first elastic body 3 . ) is an integrated structure (hereinafter, this integrated structure is referred to as a “main frame M”). Thereby, friction does not occur at the connection point between the first mass body 1 and the first elastic body 3 and at the connection point between the second mass body 2 and the first elastic body 3, so that the viscous coefficient is reduced. At the same time, the fixing condition (connection condition at the connection point) does not change even at the time of a large amplitude, and the nonlinearity of the spring is reduced.

Further, since the movable weight 11 and the counterweight 21 are supported by the first elastic body 3 at both ends and the middle portion in the front-back direction T, the movable weight 11 and the counterweight 21 are The warpage change is reduced, and in particular, the friction between the movable weight 11 of the main frame M and the side connecting plate 12 is reduced, so that the viscous coefficient is reduced. In addition, if the first elastic body 3 is fixed to the first mass body 1 (movable weight 11) or the second mass body 2 (counter weight 21) with a fixing member such as a bolt, the fixing member Although it was necessary to secure an arrangement space for the , according to the present embodiment, since there is no need to secure an arrangement space for the fixing member, the height dimension of the first mass 1 can be set large, and the bending rigidity can be improved. As a result, the first mass 1 (movable weight 11) is less likely to bend in an S-shape, and the driving frequency is increased. As described above, according to the linear feeder X according to the present embodiment, the driving frequency and amplitude at which the structure (main frame M) vibrates can be increased, and a high resonance magnification can be achieved to obtain a large amplitude.

In the linear feeder X of the present embodiment, the first mass body 1 (movable weight 11) and the second mass body 2 (counter weight 21) are disposed at an intermediate portion between the front end and the rear end. The first elastic body 3 serves as a rib, and this makes it difficult for the first mass body 1 and the second mass body 2 to bend in an S-shape.

In this embodiment, the main frame M having the movable weight 11, the counterweight 21, and the first elastic body 3 integrally formed by wire-cutting a single piece of metal material is formed. . Moreover, it is also possible to shape|mold the main frame M by processing processes other than a wire cutting process.

In the linear feeder X which concerns on this embodiment, it is also possible to provide the counterweight (sub counterweight) separate from the main frame M integrally to the counterweight 21, for example. As the installation location of the sub counterweight, the internal space MS of the main frame M, that is, a relatively large space MS formed between the adjacent first elastic bodies 3 along the transport direction T ( The space between the 1st elastic bodies 3 comrades adjacently arrange|positioned by two sheets is excluded) is mentioned. In this case, in a state in which the sub-counterweight is provided in the internal space MS of the main frame M, the sub-counterweight includes components other than the counterweight 21 (the first elastic body 3, the piezoelectric element 31, It is essential to satisfy the condition of not contacting the movable weight 11 and the side connecting plate 12). The sub counterweight is a component constituting the second mass 2 similarly to the counterweight 21 . The size of the internal space MS of the main frame M (relatively large space MS partitioned by the first elastic body 3 adjacent in the transport direction T) is as shown in Figs. 3 and 4 and the like. The sizes may be equal to each other (equal parts), or they may be non-uniform sizes (unbalanced). 3 is an enlarged view of the main part of FIG. 2 . In addition, the internal space MS of the main frame M can be used also as an access space for providing the piezoelectric element 31 in the 1st elastic body 3 .

Here, the vibration conveying apparatus X of the present embodiment includes a movable weight 11 that is a main component of the first mass 1 as a movable part, and a second mass 2 that functions as a fixed part with respect to the movable weight 11 . ) and a structure (main frame M) integrally including a counterweight 21, which is a main part, and a first elastic body 3, and this structure (main frame M) is attached to a second elastic body 5 It is comprised so that it may be supported by the low mount (base 4 which can be regarded as a mount in this embodiment), and the 2nd elastic body 5 is made to function as a vibration-proof spring.

As shown in FIGS. 2 to 4, the linear feeder X according to this embodiment arranges the second elastic body 5 in front and rear of the main frame M, respectively, and each second elastic body 5 ), the base 4 and the main frame M are connected.

In the present embodiment, a second flat plate L-shaped elastic member (L-shaped spring 5A) having a vertical arm portion 51 extending in the vertical direction and a horizontal arm portion 52 extending in the horizontal direction integrally is used. The elastic body 5 is comprised. As for the 2nd elastic body 5 shown in FIG. 2 etc., the front-end|tip (upper end) of the vertical arm part 51 is fixed to the 1st elastic body 3, The front-end|tip (vertical arm part 51) of the horizontal arm part 52 is upright. The unfinished side) part is fixed to the base (4).

In the present embodiment, a protrusion 32 protruding forward or backward is provided in a section of the first elastic body 3 that is not displaced in the horizontal and vertical directions, and a vertical arm portion 51 is provided on the protrusion 32 . fixed the tip of the In addition, since the 1st elastic body 3 is what fixed both ends (upper end, lower end) to the movable weight 11 and the counterweight 21, respectively (both ends fixed support), a cleavage is a longitudinal center part. Here, the section of the first elastic body 3 can be grasped as a point, but in the first elastic body 3, the region in which the protrusion 32 is provided is a predetermined region including the section of the first elastic body 3 ( clause and the area near the clause). The protrusion part 32 is provided with the female screw hole 33 in two places spaced apart in the width direction W (refer FIG. 3). A first elastic body is formed in the vertical arm portion 51 with a bolt insertion hole communicating with each female screw hole 33 , and a bolt B1 inserted through the bolt insertion hole is screwed into the female screw hole 33 . The vertical arm portion 51 of the second elastic body 5 can be fixed to (3). A pressing plate is interposed between the head of the bolt B1 and the vertical arm 51 of the second elastic body 5 .

Female threaded 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 FIG. 3 ). In the horizontal female part 52, a female bolt insertion hole communicating with each female screw hole 41 is formed, and a bolt B2 inserted through the female bolt insertion hole is screwed into the female screw hole 41, whereby the base The horizontal arm 52 of the second elastic body 5 can be fixed to (4).

In the linear feeder X concerning this embodiment, in the conveyance direction T, the 2nd elastic body 5 is arrange|positioned at the position which does not overlap with the 1st elastic body 3, The upper end part of the 2nd elastic body 5 is arrange|positioned. Since the first elastic body 3 is provided in a section that is approximately the central portion in the height direction H, the vibration of the conveyance path 14 is stabilized when the first mass 1 vibrates, and thus the component conveyance is much more stable. processing can be realized.

By the way, in order to implement a more stable workpiece|work conveyance process, it is necessary to prevent the pitching phenomenon from generating in the conveyance path 14. As shown in FIG.

In the linear feeder X which concerns on this embodiment, each elastic modulus of the horizontal direction and the vertical direction of the 2nd elastic body 5 is independent, without changing the inclination angle of the front-back direction T of the 1st elastic body 3 By adjusting to , the vibration of the first elastic body 3 can be adjusted to be a desired vibration that makes the pitching phenomenon zero or approximately zero. Here, the "modulus of elasticity in the horizontal direction of the second elastic body" in the present embodiment is synonymous with "the elastic modulus of the horizontal component in the second elastic body", and the "modulus of elasticity in the vertical direction of the second elastic body" is "the second elastic modulus" 2 It is synonymous with the elastic modulus of a vertical component among an elastic body". In addition, the "horizontal direction" in this embodiment means the direction along the elastic main axis (parallel or substantially parallel with respect to an elastic main axis) defined by the installation angle of the 1st elastic body 3, and this embodiment The "vertical direction" in , means a direction perpendicular to or substantially perpendicular to the elastic main axis (normal to the elastic main axis). In the linear feeder X according to this embodiment, the horizontal arm part 52 capable of adjusting the elastic modulus with respect to the vibration component in the vertical direction, and the vertical arm part 51 capable of adjusting the elastic modulus with respect to the horizontal direction vibration component It has By using the flat L-shaped second elastic body 5, the respective elastic modulus in the horizontal direction and the vertical direction of the second elastic body 5 can be independently adjusted without adversely affecting each other.

In the present embodiment, as shown in Figs. 3 and 4, the position where the distal end of the horizontal arm portion 52 of the L-shaped leaf spring 5A, which is the horizontal portion of the second elastic body 5, is sandwiched in the height direction (H). The flat elastic adjustment member 6 is arrange|positioned to the pole, and these elastic adjustment member 6 and the horizontal arm part 52 are being fixed with the common bolt B2. In the elastic adjustment member 6, an elongated hole 61 extending in the conveying direction T (front-rear direction T) is formed, and a bolt B2 inserted into the elongated hole 61 is inserted into the horizontal arm portion 52 . ) is also inserted into the female bolt insertion hole of ), and is fastened by screwing into the female screw hole 41 of the base 4 . Then, the fixing position of the elastic adjustment member 6 with respect to the horizontal arm 52 is changed by guiding the bolt B2 in the long hole 61 in a state in which the fastening state by the bolt B2 is slightly loosened, By re-tightening the bolt B2 at the position, the size of the free area (the area that is not fastened or pressed with the bolt B2 and the elastic adjustment member 6 ) among the horizontal arm portions 52 of the second elastic body 5 ). can be changed, and as a result, the effective length in the horizontal arm portion 52 of the second elastic body 5 is changed, so that the elastic modulus (spring constant) in the vertical direction of the second elastic body 5 can be adjusted.

Whether these adjustment operations are performed sequentially or simultaneously for each second elastic body 5 can be selected according to the occurrence state of the pitching phenomenon.

The elastic adjustment member 6 is not limited to the one arranged at a position where the horizontal arm part 52 is sandwiched in the thickness direction, that is, to be arranged in two with respect to one horizontal arm part 52 , and one horizontal arm part 52 . Only one may be arranged with respect to . In this case, the effective length of the horizontal arm part 52 can be changed by applying an elastic adjustment member for urging the horizontal arm part 52 in the thickness direction and adjusting the area to be elastically deformed by the elastic adjustment member. Do it. It is also possible to make the elastic adjustment member 6 function as a spacer or washer.

In addition, in this embodiment, as for the vertical arm part 51 of the L-shaped leaf spring 5A which is the vertical arm part 51 of the 2nd elastic body 5, the structure in which a free area|region (effective length) cannot be adjusted is adopted, have. In such a configuration, in the adjustment of the elastic modulus (spring constant) in the horizontal direction of the second elastic body 5, the size of the vertical arm portion 51 (length in the vertical direction, thickness and width of the spring, number of overlapping numbers) is different. This can be performed by replacing (exchanging) with another second elastic body (not shown). Moreover, also about the vertical arm part 51 of the 2nd elastic body 5, the structure according to the horizontal arm part 52, ie, the front-end|tip part of the vertical arm part 51, is carried out in the conveyance direction T (front-back direction T). A flat elastic adjustment member is disposed at the fitting position, an elongated hole extending in the height direction H is formed in the elastic adjustment member, and the fixing position of the elastic adjustment member with respect to the vertical arm portion 51 is changed using the long hole. By doing so, it is possible to apply a configuration for changing the size of the free region (the region that is not fastened or pressed with the bolt B2 and the elastic adjustment member 6) among the vertical arm portions 51 of the second elastic body 5 . Do. Of course, similarly to the modified example of the elastic adjustment member related to the horizontal arm part 52, the aspect which arrange|positions one elastic adjustment member with respect to the one vertical arm part 51 is also employable. In this case, the effective length in the vertical arm part 51 can be changed by applying an elastic adjustment member for urging the vertical arm part 51 in the thickness direction and adjusting the area to be elastically deformed by the elastic adjustment member. Do it.

In this embodiment, the elastic modulus of the 2nd elastic body 5 provided in the front and back two places along the conveyance direction T can be adjusted individually. That is, it is possible to set the elastic modulus of the second elastic body 5 at the front and rear two places to different values.

In this way, according to the linear feeder X according to the present embodiment, the first mass body 1 and the second mass body 2 are connected by an excitation source (piezoelectric element 31) having the first elastic body 3 to each other. When driven and vibrated, the second mass 2 functions as a fixed part (counter weight), and the second elastic body 5 functions as a vibration isolator, so that the first mass 1 vibrates and the linear conveyance path 14 ) can be conveyed in a predetermined conveying direction T. Moreover, according to the linear feeder X which concerns on this embodiment, since each elastic modulus of the horizontal direction and a vertical direction of the 2nd elastic body 5 is comprised independently changeable, the horizontal direction of the 2nd elastic body 5 is comprised. By adjusting only the modulus of elasticity in the vertical direction of the second elastic body 5 without changing the modulus of elasticity in the direction, the pitching adjustment becomes easy and without changing the modulus of elasticity in the vertical direction of the second elastic body 5 (eg For example, by adjusting only the horizontal elastic modulus of the second elastic body 5 (while maintaining pitching at an elastic modulus that can be suppressed), the horizontal elastic modulus of the second elastic body 5 can be set large, and the impact from the outside Even when this is applied, it is possible to realize a device (a device resistant to impact) in which positional displacement is unlikely to occur.

In particular, in the linear feeder X according to the present embodiment, one end of the second elastic body 5 is installed in a section of the first elastic body 3 that does not displace (do not vibrate) in the horizontal and vertical directions even when it vibrates. Since it is doing, it becomes possible to exhibit a favorable vibration-proof action, and to set the elastic modulus of the horizontal direction of the 2nd elastic body 5 large by this.

Moreover, the vibration conveying apparatus X which concerns on this embodiment is the 2nd elastic body 5, The horizontal arm part 52 which can adjust the elastic modulus with respect to a vibration component in a vertical direction, and elasticity with respect to a vibration component in a horizontal direction. Since the thing provided with the vertical arm part 51 which can adjust a coefficient is applied, although it is a simple shape, the structure made into the objective of this embodiment can be implement|achieved.

In addition to this, a second elastic body having a flat horizontal arm portion 52 and a flat flat vertical arm portion 51 is applied, and an elastic adjusting member 6 for pressing the horizontal arm portion 52 in the thickness direction is provided, thereby providing elasticity Since the effective length in the arm part (horizontal arm part 52) to be adjusted can be changed by adjusting the area pressed by the adjustment member 6 to be elastically deformable, the arm part (horizontal arm part 52) and , while maintaining the relative positional relationship of the arm part (horizontal arm part 52) with the base 4 and the first elastic body 3, which are parts to be connected, in an appropriate positional relationship, the effective length of the arm part (horizontal arm part 52) It can be easily adjusted, and as a result, it is possible to easily and smoothly adjust the elastic modulus with respect to the vibration component in the vertical direction.

In particular, since the second elastic body 5 is an L-shaped leaf spring 5A having the horizontal arm part 52 and the vertical arm part 51 integrally, either the horizontal arm part 52 or the vertical arm part 51 is effective. By appropriately adjusting or changing the length or both effective lengths, the elastic modulus in the vertical direction (spring constant) and the elastic modulus in the horizontal direction (spring constant) of the second elastic body 5 can be individually set to appropriate values. .

In addition, this embodiment is not limited to embodiment mentioned above. For example, in the above-described embodiment, as a configuration for adjusting the modulus of elasticity of the L-shaped spring as the second elastic body, an elastic adjusting member for sandwiching the arm of the L-shaped spring in the thickness direction is used, and the effective arm portion of the L-shaped spring is used. Although the configuration for adjusting the length (size of the free region) has been exemplified, it is not limited to this, and a configuration for adjusting the elastic modulus of the L-shaped spring without using an elastic adjusting member that sandwiches the arm of the L-shaped spring in the thickness direction may be adopted. can As an example, a long hole is formed in the arm part of the L-shaped spring, and female threads are set at a predetermined pitch along the longitudinal direction of the long hole in the part (base 4 in the embodiment described above) for fixing the arm part, so that the L-shaped A configuration in which the effective length (size of the free area) of the arm is adjusted is exemplified by selecting and changing the female threaded hole for fixing the bolt while moving the entire spring along the longitudinal direction of the long hole. With this configuration, the entire structure (main frame) supported by the L-shaped spring may also move in accordance with the movement amount of the L-shaped spring.

In addition, as described above, a plurality of types of L-shaped springs having different lengths, areas, thicknesses, etc., of the vertical and horizontal arm portions are prepared in advance, and an appropriate L-shaped spring is selected or replaced from among them. A configuration in which each elastic modulus of a direction and a perpendicular direction is changed may be sufficient.

The number of 2nd elastic bodies and the fixing position with respect to a base can be changed suitably. Moreover, the 2nd elastic body may connect the base and the 2nd mass body.

It is also possible to configure the second elastic body in the present embodiment by a spring other than the L-shaped spring (for example, a spring or T-shaped spring in which the base ends of the I-shaped spring are connected) or an elastic body (rubber, etc.) other than the spring. It is possible.

The number and shape of the first elastic body and the connection position of the first elastic body to the first and second masses can also be appropriately changed. For example, it is also possible to arrange|position the 1st elastic body in the attitude|position inclined at a predetermined angle in a conveyance direction. Moreover, the 1st elastic body in the above-mentioned embodiment is also arrange|positioned in the attitude|position inclined at a predetermined angle (about 2 degrees) in a conveyance direction. As described above, the "modulus of elasticity in the horizontal direction of the second elastic body" in this embodiment is synonymous with "the elastic modulus of the horizontal component of the second elastic body", and the "modulus of elasticity in the vertical direction of the second elastic body" is , is synonymous with "the elastic modulus of the vertical component in the second elastic body.” In addition, the "horizontal direction" in the present embodiment means a direction along the elastic main axis (a direction parallel or substantially parallel to the elastic main axis) defined by the installation angle of the first elastic body, and " "Perpendicular direction" means a direction perpendicular to or substantially perpendicular to the main axis of elasticity (the direction normal to the main axis of elasticity). That is, in the present embodiment, the horizontal direction and the vertical direction of the second elastic body are determined on the basis of the elastic main axis of the first elastic body, and the horizontal elastic modulus of the second elastic body and the elastic modulus of the second elastic body in the vertical direction are determined. Regarding this, what is necessary is just a structure which can change independently the elastic modulus of the perpendicular direction of at least 2nd elastic body, and the external shape of a 2nd elastic body is not specifically limited. Therefore, the horizontal arm part and the vertical arm part of a 2nd elastic body do not necessarily need to have orthogonal relationship, for example, the relationship which is not orthogonal to each other may be sufficient. Moreover, the structure in which the height direction of a base coincides with the perpendicular direction of a 2nd elastic body is also included in this embodiment.

In the above-described embodiment, an aspect having the movable weight 11 (a part of the first mass 1), the counterweight 21 (a part of the second mass 2), and the first elastic body 3 integrally is provided. Although illustrated, you may employ|adopt the aspect in which all or part of these are separate. The vibration conveying apparatus of the present embodiment includes an aspect in which the first elastic body is directly connected to the first mass body and the second mass body, respectively, and an aspect in which the first elastic body is connected indirectly through a separate member, and similarly, the second elastic body is connected to the second elastic body. is directly connected to the base and the second mass or the first elastic body, respectively, and indirectly connected through a separate member.

The first mass may be one having a linear conveying surface, without the above-mentioned conveying path (trough), and having a linear conveying surface on the upward surface of the chute stand, or without a chute stand, on the upward surface of the movable weight A thing in which a linear conveyance surface is formed, or a thing in which the linear conveyance surface is formed in the component (not limited to a chute stand) which vibrates in synchronization with a movable weight may be sufficient.

Further, the second mass may consist of only a single counterweight or may include a plurality of counterweights. A configuration in which the first mass is disposed above the second mass may be employed.

The excitation source may be anything other than a piezoelectric element.

In addition, things other than electronic components, such as various LEDs, such as LED, electronic components other than LED, or food, may be sufficient as a conveyance object.

Moreover, in this embodiment, regarding the elastic modulus of the horizontal direction of a 2nd elastic body, and the elastic modulus of the vertical direction of a 2nd elastic body, the elastic modulus of the perpendicular direction of a 2nd elastic body is comprised so that change is possible independently, and a 2nd elastic body is comprised. Also included is a vibration conveying device in which the modulus of elasticity in the horizontal direction cannot be changed independently.

In addition, the specific structure of each part is not limited to the said embodiment also, It is the range which does not deviate from the meaning of this invention, and various deformation|transformation is possible.

<Second embodiment>

EMBODIMENT OF THE INVENTION Hereinafter, 2nd Embodiment of this invention is described with reference to drawings. In the second embodiment, components substantially the same as in the first embodiment described above are described with the same reference numerals.

As also shown in FIG. 1, the vibration conveying apparatus X which concerns on this embodiment also vibrates the workpiece|work K, such as an electronic component, on the conveyance path 14 (linear conveyance path 14 mentioned later), for example. It is a device that transports to a predetermined transport destination (supply destination) while being moved by the . Moreover, the downstream end of the conveyance path (ball conveyance path) of the ball feeder conveyed while aligning is connected to the upstream end of the linear conveyance path 14 (not shown). Therefore, the linear feeder X conveys the workpiece K conveyed via the conveyance path (ball conveyance path) formed in the ball feeder to the end of the linear conveyance path 14 by vibration to a predetermined conveyance destination. it is possible to supply. In this linear feeder X, when it overflows or when it is determined that the workpiece|work K is not in a predetermined conveyance attitude|position, it is determined that it is not the workpiece|work K (work K which overflows) or the predetermined conveyance attitude|position which becomes the target. A return unit (return conveying path) for returning one workpiece K) to the ball conveying path is provided.

As shown in FIGS. 1 to 4 , the linear feeder X includes a first mass body 1 having a linear conveying surface and a second mass body 2 vibrating out of phase with respect to the first mass body 1 . and 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 second connecting the base 4 and the first elastic body 3 to each other It is provided with the elastic body (5).

In the present embodiment, a movable weight 11 (movable part), which is a main component of the first mass 1 , is disposed above the base 4 having an elongated shape along the conveying direction T, and the movable weight 11 is disposed. ), a counterweight 21 (fixed part), which is the main part of the second mass 2 , is disposed above the first elastic body 3 , and the side connecting plate 12 is above the counterweight 21 . ), the chute stand 13 connected to the movable weight 11 is disposed. In this embodiment, as shown in FIG. 2, the movable weight 11 and the chute stand 13 are mutually connected via the side connecting plate 12 which forms a pair. In addition, in FIG. 4, the side connection plate 12 of the front side of the paper surface is abbreviate|omitted among the side connection plates 12 which form a pair.

A conveyance path 14 is provided detachably on the upper surface of the chute stand 13 via a fixing member, such as a bolt, and vibration is applied to the conveyance path 14, so that the workpiece|work K is moved to the conveyance path 14. It moves in the linear conveyance surface (conveyance groove|channel) provided in the. The chute stand 13 shows a movement synchronized with the vibration of the movable weight 11 , and functions as a vibration transmission unit that transmits the vibration of the movable weight 11 to the conveyance path 14 .

In the following description, the conveyance direction T of the workpiece|work K along the conveyance path 14 is made into the front-back direction T, let the conveyance direction T upstream be the rear side, and let the conveyance direction T downstream. to the front side. Moreover, let the direction orthogonal to the conveyance direction T within a horizontal plane be the width direction W (transverse direction) (refer FIG. 1 etc.).

2 and 4, the front end portion and the rear end portion of the chute stand 13 are overhang portions protruding forward and rearward from the movable weight 11, respectively. A sub movable weight (not shown) may be provided, for example, on the downward surface of the front overhang portion of the chute stand 13 . The side connecting plate 12 , the chute stand 13 , and the conveying path 14 are components constituting the first mass 1 , similarly to the movable weight 11 .

In the present embodiment, the dimensions along the transport direction T (front and rear dimensions) of the movable weight 11 as the main component of the first mass body 1 and the counterweight 21 as the main component of the second mass body 2 . is set to be substantially the same, and these counterweights 21 and movable weights 11 are arranged in the postures facing each other in the height direction.

In the linear feeder X of this embodiment, the 1st elastic body 3 is arrange|positioned at the position which connects the front-ends and rear-ends of these movable weight 11 and the counterweight 21.

The 1st elastic body 3 has the form of the flat-plate-shaped spring (plate spring) which made the thickness direction substantially coincide with the conveyance direction T. As shown in FIG. A piezoelectric element 31 functioning as an excitation source is attached to the first elastic body 3, and by applying 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 2 vibrate. Accordingly, the first elastic body 3 functions as a drive spring. The 1st elastic body 3 of this embodiment is set so that the normal attitude|position which is not elastically deformed may become the attitude|position which stood up in the vertical direction. The spring constant including the first elastic body 3 and the piezoelectric element 31 is appropriately selected according to the condition of an arbitrary resonance frequency determined by the conveying speed of the components to be conveyed, the weight of the conveying path 14 (trough), and the like. do. In the present embodiment, the first mass body 1 and the second mass body 2 are connected by a plurality of first elastic bodies 3 .

In addition, in this embodiment, the 1st elastic body 3 is arrange|positioned also at the position which connects predetermined intermediate|middle parts between the front and rear ends of the movable weight 11 and the counterweight 21. As shown in FIG. The 1st elastic body 3 is arrange|positioned in pairs in each arrangement|positioning location (the location which connects the movable weight 11 and the counterweight 21) in the front-back direction T with a slight clearance gap. In this embodiment, a location connecting the front ends of the movable weight 11 and the counterweight 21, a location connecting the rear ends of the movable weight 11 and the counterweight 21, and the movable weight 11 and a portion in the middle between the front and rear ends of the counterweight 21 that is biased by a predetermined distance toward the front end rather than the center in the front-rear direction T, and the intermediate portion between the front and rear ends of the movable weight 11 and the counterweight 21 . The mode in which two first elastic bodies 3 are arranged in the front-rear direction (T) in four places, each of which are skewed by a predetermined distance to the rear end side of the part, by a predetermined distance from the center in the front-rear direction (T), that is, all eight pieces The aspect provided with the 1st elastic body 3 is employ|adopted.

The linear feeder X according to the present embodiment includes a movable weight 11 that is a main part of the first mass body 1 , a counterweight 21 that is a main part of the second mass body 2 , and a first elastic body. (3) is an integral structure (Hereinafter, this integral structure is called "main frame M"). The vibration conveying apparatus X of the present embodiment includes a movable weight 11 which is a main component of a first mass 1 which is a movable part, and a second mass 2 that functions as a fixed part with respect to the movable weight 11 . A structure (main frame M) including a counterweight 21 as a main component and a first elastic body 3 integrally is provided, and this integrated structure (main frame M) is used as a second elastic body 5 It is comprised so that it may be supported from the base 4 (base 4 which can be regarded as a base in this embodiment), and the 2nd elastic body 5 is made to function as a vibration-proof spring.

As shown in FIGS. 2 to 4, the linear feeder X according to this embodiment arranges the second elastic body 5 in front and rear of the main frame M, respectively, and each second elastic body 5 ), the base 4 and the main frame M are connected.

In the present embodiment, a second flat plate L-shaped elastic member (L-shaped spring 5A) having a vertical arm portion 51 extending in the vertical direction and a horizontal arm portion 52 extending in the horizontal direction integrally is used. The elastic body 5 is comprised. As for the 2nd elastic body 5 shown in FIG. 2 etc., the front-end|tip (upper end) of the vertical arm part 51 is fixed to the 1st elastic body 3, The front-end|tip (vertical arm part 51) of the horizontal arm part 52 is upright. The unfinished side) part is fixed to the base (4).

In the present embodiment, a protrusion 32 protruding forward or backward is provided in a section of the first elastic body 3 that is not displaced in the horizontal and vertical directions, and a vertical arm portion 51 is provided on the protrusion 32 . fixed the tip of the In addition, since the 1st elastic body 3 is what fixed both ends (upper end, lower end) to the movable weight 11 and the counterweight 21, respectively (both ends fixed support), a cleavage is a longitudinal center part. Here, the section of the first elastic body 3 can be grasped as a point, but in the first elastic body 3, the region in which the protrusion 32 is provided is a predetermined region including the section of the first elastic body 3 ( clause and the area near the clause). The protrusion part 32 is provided with the female screw hole 33 in two places spaced apart in the width direction W (refer FIG. 3). A first elastic body is formed in the vertical arm portion 51 with a bolt insertion hole communicating with each female screw hole 33 , and a bolt B1 inserted through the bolt insertion hole is screwed into the female screw hole 33 . The vertical arm portion 51 of the second elastic body 5 can be fixed to (3). A pressing plate is interposed between the head of the bolt B1 and the vertical arm 51 of the second elastic body 5 .

Female threaded 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 FIG. 3 ). In the horizontal female part 52, a female bolt insertion hole communicating with each female screw hole 41 is formed, and a bolt B2 inserted through the female bolt insertion hole is screwed into the female screw hole 41, whereby the base The horizontal arm 52 of the second elastic body 5 can be fixed to (4).

In the linear feeder X concerning this embodiment, in the conveyance direction T, the 2nd elastic body 5 is arrange|positioned at the position which does not overlap with the 1st elastic body 3, The upper end part of the 2nd elastic body 5 is arrange|positioned. Since it is provided in the node which is a substantially central part of the height direction H among the 1st elastic bodies 3, vibration-proof property improves and low reaction force can be implement|achieved.

Moreover, in the linear feeder X which concerns on this embodiment, each elastic modulus of the horizontal direction and the perpendicular direction of the 2nd elastic body 5 without changing the inclination angle of the front-back direction T of the 1st elastic body 3 By independently adjusting , the vibration of the first elastic body 3 can be adjusted to be a desired vibration that makes the pitching phenomenon zero or approximately zero. Here, the "modulus of elasticity in the horizontal direction of the second elastic body" in the present embodiment is synonymous with "the elastic modulus of the horizontal component in the second elastic body", and the "modulus of elasticity in the vertical direction of the second elastic body" is "the second elastic modulus" 2 It is synonymous with the elastic modulus of a vertical component among an elastic body". In addition, the "horizontal direction" in this embodiment means the direction along the elastic main axis (parallel or substantially parallel with respect to an elastic main axis) defined by the installation angle of the 1st elastic body 3, and this embodiment The "vertical direction" in , means a direction perpendicular to or substantially perpendicular to the elastic main axis (normal to the elastic main axis). In the linear feeder X according to this embodiment, the horizontal arm part 52 capable of adjusting the elastic modulus with respect to the vibration component in the vertical direction, and the vertical arm part 51 capable of adjusting the elastic modulus with respect to the horizontal direction vibration component It has By using the flat L-shaped second elastic body 5, the respective elastic modulus in the horizontal direction and the vertical direction of the second elastic body 5 can be independently adjusted without adversely affecting each other.

In the present embodiment, as shown in Figs. 3 and 4, the position where the distal end of the horizontal arm portion 52 of the L-shaped leaf spring 5A, which is the horizontal portion of the second elastic body 5, is sandwiched in the height direction (H). The flat elastic adjustment member 6 is arrange|positioned to the pole, and these elastic adjustment member 6 and the horizontal arm part 52 are being fixed with the common bolt B2. In the elastic adjustment member 6, an elongated hole 61 extending in the conveying direction T (front-rear direction T) is formed, and a bolt B2 inserted into the elongated hole 61 is inserted into the horizontal arm portion 52 . ) is also inserted into the female bolt insertion hole of ), and is fastened by screwing into the female screw hole 41 of the base 4 . Then, the fixing position of the elastic adjustment member 6 with respect to the horizontal arm 52 is changed by guiding the bolt B2 in the long hole 61 in a state in which the fastening state by the bolt B2 is slightly loosened, By re-tightening the bolt B2 at the position, the size of the free area (the area that is not fastened or pressed with the bolt B2 and the elastic adjustment member 6 ) among the horizontal arm portions 52 of the second elastic body 5 ). can be changed, and as a result, the effective length in the horizontal arm portion 52 of the second elastic body 5 is changed, so that the elastic modulus (spring constant) in the vertical direction of the second elastic body 5 can be adjusted.

Whether these adjustment operations are performed sequentially or simultaneously for each second elastic body 5 can be selected according to the occurrence state of the pitching phenomenon.

The elastic adjustment member 6 is not limited to the one arranged at a position where the horizontal arm part 52 is sandwiched in the thickness direction, that is, to be arranged in two with respect to one horizontal arm part 52 , and one horizontal arm part 52 . Only one may be arranged with respect to . In this case, the effective length of the horizontal arm part 52 can be changed by applying an elastic adjustment member for urging the horizontal arm part 52 in the thickness direction and adjusting the area to be elastically deformed by the elastic adjustment member. Do it. It is also possible to make the elastic adjustment member 6 function as a spacer or washer.

In addition, in this embodiment, as for the vertical arm part 51 of the L-shaped leaf spring 5A which is the vertical arm part 51 of the 2nd elastic body 5, the structure in which a free area|region (effective length) cannot be adjusted is adopted, have. In such a configuration, in the adjustment of the elastic modulus (spring constant) in the horizontal direction of the second elastic body 5, the size of the vertical arm portion 51 (length in the vertical direction, thickness and width of the spring, number of overlapping numbers) is different. This can be performed by replacing (exchanging) with another second elastic body (not shown). Moreover, also about the vertical arm part 51 of the 2nd elastic body 5, the structure according to the horizontal arm part 52, ie, the front-end|tip part of the vertical arm part 51, is carried out in the conveyance direction T (front-back direction T). A flat elastic adjustment member is disposed at the fitting position, an elongated hole extending in the height direction H is formed in the elastic adjustment member, and the fixing position of the elastic adjustment member with respect to the vertical arm portion 51 is changed using the long hole. By doing so, it is possible to apply a configuration for changing the size of the free region (the region that is not fastened or pressed with the bolt B2 and the elastic adjustment member 6) among the vertical arm portions 51 of the second elastic body 5 . Do. Of course, similarly to the modified example of the elastic adjustment member related to the horizontal arm part 52, the aspect which arrange|positions one elastic adjustment member with respect to the one vertical arm part 51 is also employable. In this case, the effective length in the vertical arm part 51 can be changed by applying an elastic adjustment member for urging the vertical arm part 51 in the thickness direction and adjusting the area to be elastically deformed by the elastic adjustment member. Do it.

And, as described above, the vibration conveying device X according to the present embodiment includes a movable weight 11 that is a main part of the first mass 1 and a counterweight 11 that is a main part of the second mass 2 . 21) and the 1st elastic body 3 are made into the integral structure (main frame M). As a result, friction does not occur at the connection point between the first mass body 1 and the first elastic body 3 and at the connection point between the second mass body 2 and the first elastic body 3 , and the viscous coefficient decreases. , the fixed condition (connection condition at the connection point) does not change even at the time of large amplitude, and the nonlinearity of the spring is reduced.

Further, according to the vibration conveying device X according to the present embodiment, the movable weight 11 and the counterweight 21 are supported by the first elastic body 3 at both ends and the middle portion in the front-back direction T. Therefore, the change in bending of the movable weight 11 and the counterweight 21 is reduced, and in particular, the friction between the movable weight 11 of the main frame M and the side connecting plate 12 is reduced, so that the viscous coefficient is reduced. decreases.

In addition, if the first elastic body 3 is fixed to the first mass body 1 (movable weight 11) or the second mass body 2 (counter weight 21) with a fixing member such as a bolt, the fixing member Although it was necessary to secure an arrangement space for , according to the present embodiment, there is no need to secure an arrangement space for the fixing member, and the degree of freedom in designing the shape of the first mass 1 is increased, for example, the first mass ( By setting the height dimension of 1) large, bending rigidity can be improved, As a result, the 1st mass 1 (movable weight 11) becomes difficult to bend in an S-shape, and a drive frequency becomes high. As described above, according to the linear feeder X according to the present embodiment, the driving frequency and amplitude at which the structure (main frame M) vibrates can be increased, and a high resonance magnification can be achieved to obtain a large amplitude.

In the linear feeder X of the present embodiment, the first mass body 1 (movable weight 11) and the second mass body 2 (counter weight 21) are disposed at an intermediate portion between the front end and the rear end. The first elastic body 3 serves as a rib, and this makes it difficult for the first mass body 1 and the second mass body 2 to bend in an S-shape.

In this embodiment, the main frame M having the movable weight 11, the counterweight 21, and the first elastic body 3 integrally formed by wire-cutting a single piece of metal material is formed. . Moreover, it is also possible to shape|mold the main frame M by processing processes other than a wire cutting process.

In the linear feeder X which concerns on this embodiment, it is also possible to provide the counterweight (sub counterweight) separate from the main frame M integrally to the counterweight 21, for example. As the installation location of the sub counterweight, the internal space MS of the main frame M, that is, a relatively large space MS formed between the adjacent first elastic bodies 3 along the transport direction T ( The space between the 1st elastic bodies 3 comrades adjacently arrange|positioned by two sheets is excluded) is mentioned. In this case, in a state in which the sub-counterweight is provided in the internal space MS of the main frame M, the sub-counterweight includes components other than the counterweight 21 (the first elastic body 3, the piezoelectric element 31, It is essential to satisfy the condition of not contacting the movable weight 11 and the side connecting plate 12). The sub counterweight is a component constituting the second mass 2 similarly to the counterweight 21 . The size of the internal space MS of the main frame M (relatively large space MS partitioned by the first elastic body 3 adjacent in the transport direction T) is as shown in Figs. 3 and 4 and the like. The sizes may be equal to each other (equal parts), or they may be non-uniform sizes (unbalanced). 3 is an enlarged view of the main part of FIG. 2 . In addition, the internal space MS of the main frame M can be used also as an access space for providing the piezoelectric element 31 in the 1st elastic body 3 .

In this way, according to the linear feeder X according to the present embodiment, the first mass body 1 and the second mass body 2 are connected by an excitation source (piezoelectric element 31) having the first elastic body 3 to each other. When driven and vibrated, the second mass 2 functions as a fixed part (counter weight), and the second elastic body 5 functions as a vibration isolator, so that the first mass 1 vibrates and the linear conveyance path 14 ) can be conveyed in a predetermined conveying direction T. Further, according to the linear feeder X according to the present embodiment, the movable weight 11 which is a part of the first mass 1 , the counterweight 21 which is a part of the second mass 2 , and the first elastic body 3 . ) as an integral structure, friction does not occur at the connection point between the first mass body 1 and the first elastic body 3 and at the connection point between the second mass body 2 and the first elastic body 3, so that the bolt Compared with a configuration in which the first elastic body is fixed to the first mass body or the second mass body by a fixing member such as a back, the viscous coefficient is reduced and the resonance peak is not lowered. Moreover, even at the time of a large amplitude, the fixed condition (connection condition at a connection location) does not change, but the fall of the drive frequency (resonance frequency) by the nonlinearity of the 1st elastic body 3 can be reduced. Therefore, according to the vibration conveying device X according to the present embodiment, the cause of the reduction of the resonance peak, which is unavoidable in a configuration in which the first elastic body is fixed to the first mass or the second mass with a fixing member such as a conventional bolt, is All of them can be eliminated, and a large amplitude can be realized with a small excitation force.

In addition, in the vibration conveying device X according to the present embodiment, the location where the first mass body 1 and the second mass body 2 are connected with the first elastic body 3 is connected to a connection point by a conventional drive spring. Similarly, in the first mass body 1 and the second mass body 2, the upstream end (rear end) in the conveying direction T and the downstream end (front end) in the conveying direction T are set at a connecting position, Therefore, the stable support state by the 1st elastic body 3 can be ensured.

In particular, in the vibration conveying apparatus X according to the present embodiment, the movable weight 11 (the main part of the first mass 1 ) and the counterweight 21 (the main part of the second mass 2 ) are used. Since the 1st elastic body 3 is also arrange|positioned at the position which connects intermediate parts between the upstream end (rear end) in the conveying direction T and the downstream end (front end) in the conveying direction T, the intermediate part The arranged first elastic body 3 serves as a rib, so that the bending rigidity of the movable weight 11 and the counterweight 21 can be further improved, and thereby the movable weight 11 and the counterweight 21 can be further improved. A configuration that satisfies the good conditions of increasing the resonance peak by increasing the driving frequency and reducing friction between parts by increasing the spring constant while reducing the deformation of the linear conveying path 14 becomes

As described above, according to the present embodiment, at least a part of the first mass 1 (movable weight 11), at least a part of the second mass 2 (counter weight 21), and the first elastic body ( 3) as an integral structure, by adopting a novel configuration that has never been conceived before, the driving frequency and amplitude at which the integral structure (main frame M) vibrates can be increased, and a high resonance magnification is achieved, resulting in a large amplitude It becomes possible to obtain, and the vibration conveyance apparatus X which can improve the conveyance speed of the conveyance object K can be implement|achieved.

In addition, in the vibration conveying apparatus X according to the present embodiment, as the first mass 1 , the movable weight 11 (the "first body structure" of the present embodiment) constituting the main frame M (integral structure) which is an integral structure. 1 mass body”) and the movable weight 11 and a transport path 14 having a linear transport surface, which is separate from the linear transport path 14, which requires high design specifications. can be prepared as an exclusive product separately from the main frame M, thereby reducing the processing burden at the time of manufacturing the main frame M, which is an integral structure.

In addition, this embodiment is not limited to embodiment mentioned above. For example, the number and shape of the first elastic body, and the connection position of the first elastic body to the first mass body and the second mass body can also be appropriately changed. It is also possible to arrange|position the 1st elastic body in the attitude|position inclined at a predetermined angle in the conveyance direction.

In the above-described embodiment, the movable weight 11 (a part of the first mass 1), the counterweight 21 (a part of the second mass 2), and the first elastic body 3 are integrally structured. is exemplified, an aspect in which all of the first mass, a part of the second mass, and the first elastic body are integrally formed, an aspect in which a part of the first mass, all of the second mass, and the first elastic body are integrally formed, or An aspect in which all of the first mass body, all of the second mass body, and the first elastic body are integrally formed may be employed.

That is, the first mass in the present embodiment may consist of only the components (moving weight) constituting the integrated structure (main frame), and may be formed from the main components constituting the integrated structure (main frame) and the integrated structure. It may be equipped with a separate part.

Similarly, the second mass in the present embodiment may consist of only the main parts (counter weight) constituting the integrated structure (main frame), or the main components constituting the integrated structure (main frame) and the integrated structure. The product may be provided with a separate component.

The first mass may be one having a linear conveying surface, without the above-mentioned conveying path (trough), and having a linear conveying surface on the upward surface of the chute stand, or without a chute stand, on the upward surface of the movable weight A thing in which a linear conveyance surface is formed, or a thing in which the linear conveyance surface is formed in the component (not limited to a chute stand) which vibrates in synchronization with a movable weight may be sufficient. In particular, when the first mass is composed only of parts corresponding to the above-described movable weight, it is preferable that the first mass is disposed above the second mass, and the linear conveyance surface is formed on the upward surface of the first mass.

The vibration conveying apparatus of the present embodiment includes an aspect in which the second elastic body exhibiting a vibration-proof action is directly connected to an integral structure (main frame), and an aspect in which the second elastic body is connected indirectly through another member. The number of the second elastic body and the fixing position to the base or the integral structure (main frame) can be appropriately changed. Moreover, the 2nd elastic body may connect the base and the 2nd mass body.

The second elastic body is constituted by a spring other than the L-shaped spring (for example, a spring or T-shaped spring in which the base ends of the I-shaped spring are connected) or an elastic body other than the spring (rubber, etc.), or at a predetermined angle in the conveying direction. It is also possible to constitute the second elastic body by a leaf spring arranged in an inclined posture. Moreover, the vibration conveyance apparatus which is not provided with a 2nd elastic body is also included in this embodiment.

The excitation source may be anything other than a piezoelectric element.

In addition, things other than electronic components, such as various LEDs, such as LED, electronic components other than LED, or food, may be sufficient as a conveyance object.

In addition, the specific structure of each part is not limited to the said embodiment also, It is the range which does not deviate from the meaning of this invention, and various deformation|transformation is possible.

<Third embodiment>

Hereinafter, a third embodiment of the present invention will be described with reference to FIGS. 5 to 10 .

The rotary vibrator A of this embodiment includes a vibration disc 7 which is a first mass, and a base 8 which is a second mass which is disposed to face the vibrating disc 7 in the opposite axis m direction; , a first disposed at a position connecting between the vibrating disc 7 and the base 8 and the excitation source 9 for relatively oscillating around the opposing axis m, and the vibrating disc 7 and the base 8 An elastic body 400 is provided. The rotary vibrator A is provided with a conveying body B having a spirally upright conveying path, and a component feeder PF which is a vibration conveying device is constituted. The transport body B of this embodiment is configured to align and supply micro articles such as IC chips, for example.

The vibrating disc 7 includes a disk-shaped vibrating disc main body 10 constituting the main body of the first mass, and a first continuous installation part 44 to be described later that is installed in the vibrating disc main body 10 and forms a part of the first mass body. ) is composed of In the outer periphery of the vibrating half main body 10, there are a plurality of equal angle places, that is, in this embodiment, the first connecting portion 16 on the vibration half side connected to the first elastic body at three places, and these vibration half side first connecting portions 16 are out of phase with each other. The vibration half side 2nd connection part 17 connected with the excitation source 9 is provided in the deviated isometric multiple places, ie, three places in this embodiment. The vibration half side 1st connection part 16 is the shape which became thin in the downward and radial outward direction, specifically, it is a downward U-shape as seen from the side, and is a bottomed recessed part. The diaphragm side 2nd connection part 17 is a protrusion which protrudes downward from the diaphragm main body 10. As shown in FIG.

The base 8 is a truncated cone-shaped base body 20 constituting the main body of the second mass, and a second connecting portion 42 to be described later that is installed on the base body 20 and forms a part of the second mass. is composed The base body 20 is disposed on the mounting surface with the vibration-proof member 2a interposed therebetween. In the outer periphery of the base (8), the base side first connecting portion (26) at a position corresponding to the first connecting portion on the vibration half side (16) and connected to the first elastic body (400), and the vibration half side first connecting portion (17) A position corresponding to and a base-side second connection portion 22 connected to the excitation source 9 is provided. The base-side first connecting portion 26 is, as shown in Figs. 6 and 7 (a), a shape that is thinned in the upward and diametrically outward directions, specifically, a U-groove-shaped bottomed concave when viewed from the side. is wealth The base side 2nd connection part 22 is located inside the inside of the space in which the vibration half side 2nd connection part 17 is arrange|positioned movably, as shown to FIG.6 and FIG.7(b), The 2nd mentioned later It is composed of a leaf spring receiving portion 23 and a connecting member abutting portion 24 .

The excitation source 9 is a product of a horizontal arrangement in which a connecting member 36 constituting a part of a base 8, which is a second mass, and a base end are connected to the connecting member 36 and a front end thereof extends in a radial direction. 2 A second leaf spring 37, which is an elastic body, and a bimorph or unimorph type piezoelectric element driving unit attached to both or one side of the second leaf spring 37 to bend the second leaf spring 37 by vibration (38) is provided. In the base 8, as shown in Fig. 7(b), the second leaf spring receiving portion 23 extending in the shape of a star in three directions from the center and opening upward and radially outward when viewed from above; The L-shaped connecting member abutting portion 24 positioned between adjacent second leaf spring accommodating portions 23 is provided, and the connecting member 36 provided with the base end of the second leaf spring 37 is provided. is fastened to the bottom surface of the base 8 by a bolt v1 serving as a fixing tool from the opposite axis z-direction, that is, from the upper direction in a state in which the two surfaces are brought into contact with the connecting member abutting portion 24 .

Then, the base end of the second leaf spring 37 is connected to the connecting member 36 in the horizontal direction by a bolt v21 as a fixing tool, and the front end of the second leaf spring 37 is connected to the vibrating disc body 10 . It is connected in the horizontal direction by the bolt v22 which is a fixing tool to the vibration half side 2nd connection part 17 provided by protruding downward from it.

The first elastic body 400 functions as a main resonance spring by connecting the diaphragm 7 and the base 8, and as shown in Fig. 8, a plurality of (two in this embodiment) leaf springs 40 ), the first continuous installation part 44 which is continuously installed on one end side of each leaf spring 40 and forms a part of the diaphragm 7, and the other end side of each leaf spring 40 is continuously installed on the base An integral leaf spring structure including the second continuous installation portion 42 forming a part of (8) (in more detail, an integral overlapping leaf spring structure) is formed.

The leaf springs 40 are arranged parallel to each other. As shown in Fig. 15, when the origin O is taken at the center of the thickness direction and width direction of the leaf spring 40, the longitudinal direction is z, the thickness direction is x, and the width direction is y, Fig. 5 and Fig. The leaf spring 40 shown in 8 and the like has a thickness direction x in the circumferential direction of the rotary vibrator A, a width direction y in the radial direction of the rotary vibrator A, and a longitudinal direction ( z) is arranged to extend in a direction inclined with the opposite axis m of the rotary vibrator A. Looking at the individual leaf springs 40, as shown in Fig. 9(c), the y-direction width dimension D is from one end 40e1 to the other end 40e2 as indicated by an imaginary line along the longitudinal direction. ) is not a uniform rectangle, but a shape that is smoothly constricted so as to gradually narrow from the upper and lower ends 40e1 and 40e2 toward the central portion 40m as indicated by solid lines. This shape is provided by necking the spring steel, carbon steel, etc. which are a spring raw material.

The first continuous mounting portion 44 shown in FIG. 8 is a rectangular parallelepiped integral with the upper end of each leaf spring 40, and as shown in FIGS. 5 and 6, a concave portion ( 16) are closely placed within the The second connecting portion 42 shown in Fig. 8 is disposed so as to surround the bottom portion 42a integral with the lower end of each leaf spring 40 and the leaf springs 40 on both sides of the bottom portion 42a. The right side part 42b and the left side part 42c used together are U-shaped, and are closely arranged in the recessed part 26 which is a base side 1st connection part as shown in FIGS.

That is, the first elastic body 400 is disposed in a positional relationship that can be detachably fitted from the outside with respect to the rotating disc 7 which is the first mass and the base 8 which is the second mass.

As shown in Figs. 5, 6 and 8, between the first continuous installation portion 44 and the vibrating diaphragm body 10, the connecting member v3 in two places along the direction parallel to the opposing axis m. ) is connected with In Figs. 6 and 8, reference numeral h3 denotes a connection hole therefor.

Further, between the right side portion 42b of the second continuous installation portion 42 and the base body 20, bolts along the first direction s intersecting (orthogonal) with the opposite axis m direction at two places (v4), and between the left side portion 42c of the second connection portion 42 and the base body 20, intersect (orthogonal) with the opposite axis (m) direction and the first direction (s) at two places ) are connected by bolts v5 along the second direction u. In Fig. 8, reference numerals h4 and h5 denote connecting holes therefor. 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 longitudinal direction z of the leaf spring is slightly inclined with respect to the opposing axis m, the thickness direction x of the leaf spring 30 substantially coincides with the first direction s, and the width direction of the leaf spring 30 (y) substantially coincides with the second direction (u).

In this embodiment, in order to aim at the moment of inertia reduction, the diaphragm main body 10 is produced from aluminum. However, when the spring is directly coupled to the vibrating body 10 , the Young's modulus of the aluminum material is lower than that of iron, and thus the bending rigidity of the coupling portion is lowered. Therefore, as shown in FIG. 9B , the first continuous installation part 44 , which is a part of the first mass body, is made of a spring material such as spring steel or carbon steel together with the leaf spring 40 . For this reason, there is an effect of increasing the bending rigidity of the coupling portion of the plate spring 40 constituting the first elastic body 400 and the rotating disc main body 10 . In the same way in the coupling portion between the plate spring 40 constituting the first elastic body and the base body 20 as the main body of the second mass, the second continuous mounting portion 42 integral with the leaf spring 40 is a spring Since it is made of a spring material such as steel or carbon steel, there is an effect of increasing the bending rigidity of the coupling portion between the leaf spring 40 and the base body 20 . In addition, although FIG.9(b) is shown with the single leaf|plate spring 40 for convenience of description, since the leaf spring 40 of this embodiment is two pieces like FIG.9(a), it is Each of the leaf springs 40 has the above-described configuration and has the same effect.

Then, by repeatedly applying a voltage of a required frequency to the piezoelectric element driving unit 38 , the vibrating disc 7 is excited in the forward/reverse direction through the second leaf spring 37 . Accordingly, the leaf spring 40, which is the first elastic body, bends and vibrates.

Among the bending vibrations, bending in the longitudinal direction shown in Fig. 10A occurs. This bending becomes the dominant factor determining the resonance characteristics. With this bending, the x-direction forces (Fx, F'x) and the fixed moments (My, M'y) around the y-axis are generated at both fixed ends of the spring on the side opposite to the origin (O) side. Let this be the bending of A mode.

Also, along with this, distortion around the z-axis as shown in Fig. 10(b) occurs. With this twist, a moment Mz is generated around the origin O as viewed in the z-axis direction. Let this be the bending of the B mode.

Moreover, the bending in the width direction shown in FIG.10(c) generate|occur|produces by this. With this bending, a force Fy in the y direction and a fixed moment Mx around the x-axis are generated on the side opposite to the origin. That is, when the vibrating disc 102 rotates with respect to the base 101, the phase of the vibrating half-side fixed portion α of the leaf spring 104 changes with respect to the phase of the base-side fixed unit β. For example, when this is projected on the yz plane, the vibration half side fixed part (alpha) is carried out in the width direction (diameter outer direction). Let this be the bending of the C mode.

Among them, mainly by the A-mode bending, it is amplified to the required frequency and amplitude at the resonance point or in the vicinity of the resonance point, and the oscillator 7 can be efficiently driven.

At that time, the first leaf spring 40, which is the first elastic body, is disposed in the z-axis direction, which is a direction inclined with respect to the opposing axis m, so that the vibrating disc 7 moves vertically in translation (vibration). and rotational motion (vibration) in the circumferential direction. As a result, the components feeder PF, which is a vibration conveying device in which a conveying body B having a spiral conveying path is provided on the vibrating disc 7, causes the article on the conveying path to travel along the spiral conveying path to the conveying body ( It is conveyed from the bottom of B) toward the top.

As described above, in the rotary vibrator A of the present embodiment, the first mass body, the rotary disk 7 , and the second mass, the base, which are disposed to face the rotary disk 7 in the direction of the opposite axis m, are provided. (8), and an excitation circle (9) for relatively oscillating the rotary disk (7) and the base (8) around the opposing axis (m), and the rotary disk (7) and the base (8) arranged at a connecting position and a first elastic body 400 to be

And the first elastic body 400, the leaf spring 40, the first continuous installation portion 44 which is continuously installed on one end side of the leaf spring 40 to form a part of the rotating disc 7; It has an integrated leaf spring structure including a second continuous installation part 42 that is continuously installed on the other end side of the leaf spring 40 and forms a part of the base 8, and of which at least the first continuous installation part 44 and It is connected by a bolt (v3), which is a connecting member, along a direction parallel to the opposite axis (m) between the rotating disc main body (10).

If such a so-called opposing axial fixation is adopted, as shown in Fig. 10(a), when the both ends of the leaf spring 40 are fixed to the rotating disc 7 and the base 8 and deformed into an S shape, y Even if the bending moment My around the axis is applied, the axial force of the bolt v3 as the connecting member shown in Fig. 9B is orthogonal to the opposite direction, that is, the bending moment My around the axis. Slipping is difficult to occur. In addition, since the end of the leaf spring 40 is integrated with the first continuous mounting portion 10 that is a part of the rotary disk 7 , the fixed moment My can be received by the member rigidity, and the vibration disk 7 is The occurrence of warpage is suppressed, and appropriate parallel movement in the x and y directions can be realized. This eliminates the loss of excitation due to sliding between the first continuous mounting portion 44 and the leaf spring 40 or bending of the rotating disc 7, and the resonance magnification is increased, resulting in high frequency and large amplitude even with a small excitation force. can be properly realized.

In addition, between the second continuous installation part 42 and the base body 20, which is the main body part of the second mass, a first direction (s) intersecting the opposing axis (m) direction, and the opposing axis (m) direction and Since they are connected along the second direction u intersecting the first direction s, a strong fixing method against the torsional stress of the first elastic body 400 from the side of the base 8, which is the second mass, is applied to the base ( It becomes possible to realize between 8) and the second continuous installation portion 42 .

In particular, since the second mass is the base 8 on the fixed side, the first mass is the rotating disc 7 on the movable side, and at least the opposite axial fixation is adopted on the rotating disc 7 side, sliding on the moving part side However, the bending of the spring fixing member is preferentially eliminated.

In addition, the first continuous mounting portion 44 and the rotating disc main body 10 that is a part of the first mass are connected in at least two places along the opposite axis (m) direction, and the first continuous mounting unit 44 is interposed therebetween. Thus, since the leaf spring 40 is reliably held at a plurality of locations by the rotating disc main body 10 , the rotating disc 10 is able to move in parallel with respect to the base 8 without bending or inclining.

And, since this rotating vibrator A and the conveying body B fixed on the rotating disc 7 which is a 1st mass body and provided with the spiral conveying path, the component feeder PF which is a vibration conveying apparatus is comprised. , it becomes possible to effectively improve the transport speed of the article on the transport body B.

As mentioned above, although 3rd Embodiment of this invention was described, the specific structure of each part is not limited only to embodiment mentioned above.

For example, you may use the 1st mass body of the said embodiment by turning it upside down so that it may become a base and the 2nd mass body may become a vibrating half. In this case, the second continuous installation portion of the upward U-shape positioned under the first elastic body is positioned above and arranged as a downward U-shape, and the first continuous installation portion positioned above is located below, so that the connection in the opposite axial direction is It is preferentially performed between the base and the first elastic body. The shape of the first mass body or the second mass body may be appropriately changed.

In the above embodiment, the leaf spring 40 has a shape that becomes narrower from the end toward the center, but may have a rectangular shape like the leaf spring 40' shown in FIG. 11 . The other basic configuration is the same as that of the above embodiment, and the same reference numerals are assigned to corresponding parts. In this way, since the rigidity of the leaf spring 40' itself is increased, it becomes possible to design with emphasis on high frequency.

In addition, in the said embodiment, although the 1st continuous installation part 44 and the rotating board main body 10 were connected by the bolt v3 which is a connection member along the direction parallel to the opposing axis|shaft m at two places, FIG. As shown in (a) of 12, you may connect with the bolt v3 at one place. In this case, it is more preferable that the connection point by the bolt v3 is at the midpoint of the two leaf springs 40' (or 40), and the moment My around the y-axis is substantially orthogonal to the axial force to prevent sliding. The same effect is exhibited from the point which can prevent and the point which can prevent the curvature of a vibrating disc by receiving the said moment My with the member rigidity of the 1st continuous installation part 44. As shown in FIG.

In addition, as shown in Fig. 12 (b), between the first continuous installation portion 44 and the rotating disc main body 10, in two places along the direction parallel to the opposing axis m, the bolt ( When connecting by v3), it is also effective to tighten the connection hole h3 while shifting the fastening direction u of the bolt v5. By doing in this way, the bending strength of the leaf spring 40' (or 40) can be increased.

Note that, although two leaf springs 40 are used in the above embodiment, as shown in Fig. 13A, only one leaf spring 40' (or 40) is used, although not shown. Of course, it is also possible to implement in a configuration using three or more leaf springs.

In addition, in the above embodiment, the first mass body, the rotating disc 7 and the first continuous mounting part 44, are fastened in the opposite axis (m) direction, and the second mass body base 8 and the second continuous mounting part 44 are fastened. (42) was fastened in the s-axis direction orthogonal to this, and in the m-axis and u-axis directions orthogonal to the s-axis, as shown in FIG. You may connect between the two continuous installation parts 42 along the direction of the opposing axis m. In this way, even between the base 8 and the second continuous installation portion 42, as between the rotary disk 7 and the first continuous installation portion 44, the sliding between parts or the excitation caused by the bending of the spring fixing member losses can be eliminated.

In addition, various modifications are possible without departing from the spirit of the present invention, such as a configuration in which the leaf spring is not inclined with respect to the opposite axial direction.

1: first mass
1L: Linear conveying surface
2: second mass
3: first elastic body
4: Bass
5: second elastic body
7: First mass (rotating platen)
8: second mass (base)
9: Gainwon
20: body portion of the second mass (base body)
40: leaf spring
42: second continuous installation part
44: first continuous installation part
51: vertical arm
52: horizontal arm
5A: L-shaped leaf spring (L-shaped spring)
400: first elastic body
A: rotary vibrator
B: carrier
K: object to be conveyed
m: opposite axis
PF: Vibration conveying device (part feeder)
s: first direction
u: second direction
v3: Connecting member (bolt)
X: Vibration conveying device (linear feeder)

Claims (6)

It is a vibration conveying device which conveys a conveyance object on a linear conveyance surface by vibration,
a first mass having the linear transport surface;
a second mass vibrating out of phase with respect to the first mass;
a first elastic body connecting the first mass body and the second mass body;
a second elastic body connecting the base and the second mass or the first elastic body;
Vibration conveyance characterized in that at least the elastic modulus in the vertical direction of at least the second elastic body is configured to be independently changeable with respect to the horizontal elastic modulus of the second elastic body and the vertical elastic modulus of the second elastic body. Device. The vibration conveying apparatus according to claim 1, wherein each elastic modulus in a horizontal direction and a vertical direction of the second elastic body is configured to be independently changeable. The vibration conveying apparatus according to claim 1 or 2, wherein one end of the second elastic body is provided in a vibration section of the first elastic body. The second elastic body according to any one of claims 1 to 3, wherein the second elastic body comprises: a horizontal arm part capable of adjusting an elastic modulus with respect to a vibration component in a vertical direction; and a vertical arm part capable of adjusting an elastic modulus with respect to a vibration component in a horizontal direction. A vibration conveying device comprising at least one of. 5. The arm according to claim 4, further comprising an elastic adjustment member for pressing at least one of the horizontal arm portion and the vertical arm portion in the thickness direction, and by adjusting the region to be elastically deformed by the elastic adjustment member, in the arm portion A vibration conveying device having a changeable effective length. The vibration conveying apparatus according to claim 4 or 5, wherein the second elastic body is an L-shaped leaf spring having the horizontal arm part and the vertical arm part integrally.

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