JP7436802B2 - Rotary vibrator and vibrating conveyance device - Google Patents

Description

The present invention relates to a rotary vibrator and a vibrating conveyance device that achieve high frequency and large amplitude as a vibrator by optimizing the mounting state of main mechanical elements that determine resonance characteristics.

As this type of rotary vibrator, a structure as shown in FIG. 10, for example, is conventionally common. This rotary vibrator 100 includes a diaphragm 101 that is a first mass body, a base 102 that is a second mass body that is arranged opposite to the diaphragm 101 in the direction of the opposing axis m, and and an excitation source 103 that causes the base 102 to vibrate relatively around the opposing axis m, and a first elastic body 104 disposed at a position connecting the vibration plate 101 and the base 102. It is configured.

When a conveying path 105 is attached to the vibrating plate 101 of such a rotary vibrator 100 as shown in FIG. 10 and used as a parts feeder PF, which is an article conveying device, for example, the rotary vibrator 100 is used in order to increase the conveying speed. High frequency and large amplitude are required.

In the rotary vibrator 100, the first elastic body 104 is the main factor that determines the resonance characteristics. For example, when the first elastic body 104 is a leaf spring as shown in the figure, by making the leaf spring 104 thicker and longer, it is possible to meet the recent demands for higher frequencies and larger amplitudes.

Patent Document 1 shows a stacked leaf spring structure in which a leaf spring connecting a diaphragm and a base is improved. Conventionally, they were constructed from a single leaf spring, which had the problem of being made thicker and more likely to break. On the other hand, in the same document, multiple leaf springs perform the function of a single leaf spring, and each individual leaf spring bends easily, eliminating the problem of the leaf spring breaking as a whole. ing.

Japanese Patent Application Publication No. 2012-96853

By the way, in order to achieve high frequency and large amplitude, it is required to reduce excitation loss as much as possible. Vibration loss refers to the loss of vibration energy due to internal friction between the spring and the fixed member.

In FIG. 10, the first elastic body 104 is constituted by a rectangular leaf spring. The leaf spring 104 has a rectangular shape and is disposed around the opposing axis m of the diaphragm 101 and the base 102 so as to extend in a direction inclined to the opposing axis m.

As shown in Fig. 11, the origin O is set at the center of the thickness direction and width direction of the base fixed 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, and the opposing axis m is Let it be the axis of rotation.

Now, when the vibrating plate 101 and the base 102 rotate in different directions from each other in the parts feeder PF shown in FIG. A-mode deflection, which is longitudinal bending, is generated at both fixed ends of the opposite spring, consisting of forces Fx, F'x in the x direction and fixing moments My, M'y about the y-axis. That is, Fx, F'x and My, M'y also act on the diaphragm 101 and the base 102 to which the plate spring 104 is fixedly connected at both ends.

Conventionally, for example, there are two ways to fasten a leaf spring on the side opposite to the origin O: in the y-axis direction, as shown in FIG. 13(a), and in the x-axis direction, as shown in FIG. 13(b). There is.

In the case of FIG. 13A, since the bolts are fastened in the y-axis direction, when a bending moment My about the y-axis occurs, the leaf spring 104 rotates and slips around the bolt v. When this slippage occurs, it leads to energy loss due to friction, and as a result, the resonance magnification decreases, making it impossible to achieve a large amplitude with a small excitation force.

On the other hand, in the case of FIG. 13(b), since the bolts are fastened in the x-axis direction, there is no problem because the bolts are fastened in a direction perpendicular to the force Fx in the x-axis direction shown in FIG. However, as shown in FIG. 13(c), the bending moment My around the y-axis is transmitted to, for example, the rotary disk side fixed part α. That is, when the leaf spring 104 is deformed, the spring would normally bend in a cantilevered manner as shown by the broken line in FIG. A moment My around the y-axis as shown in is transmitted to the rotating disk side fixed part α. At this time, if the diaphragm 101 to be connected has a thin disk shape to reduce weight, the fixed part α on the rotary disk side will succumb to the bending moment, causing vibration as shown in FIG. 13(d). The board 101 bends in a wavy manner. If this happens, the spring will not bend into an S-shape, and the frequency will not increase, making it impossible to achieve high frequencies. Further, the undulation of the vibration plate 101 causes contact interference and friction with the carrier B placed on the vibration plate 101, which also causes vibration loss and makes it impossible to achieve a large amplitude. If the spring does not bend in an S-shape, it is necessary to add the spring fixed end condition due to the deflection of the diaphragm 101 etc. to the calculation of the elastic coefficient of the first elastic body, resulting in a more complicated calculation formula.

In other words, if the diaphragm 101, which is the first mass body, is made thicker, the moment of inertia will increase, and if the outer periphery becomes thicker, it will become difficult to rotate. Therefore, even with this, it is difficult to achieve high frequency and large amplitude.

Such problems are exactly the same even in the single leaf spring structure, which is the predecessor of the stacked leaf spring. In the case of a stacked leaf spring structure, there is also the problem of slippage between the leaf springs.

By properly attaching the first elastic body, which is the main mechanical element that determines the resonance characteristics, to the mass body, the present invention eliminates vibration loss caused by slipping between parts and deflection of the spring fixing member. The objective is to realize a rotary vibrator and a vibration transfer device that can achieve high frequency and large amplitude.

In order to achieve this object, the present invention takes the following measures.

That is, the rotary vibrator according to the present invention includes a first mass body, a second mass body disposed opposite to the first mass body in the opposite axial direction, and the first mass body and the second mass body. An excitation source that causes a body to vibrate relatively around the opposing axis; and a first elastic body disposed at a position connecting between the first mass body and the second mass body, the first elastic body comprising: 1 elastic body, a leaf spring, a first connecting part that is connected to one end of the leaf spring and forms a part of the first mass body, and a first connecting part that is connected to the other end of the leaf spring and forms a part of the first mass body. an integral leaf spring structure including a second continuous portion forming a part of the second mass body; The leaf springs are connected by connecting devices along parallel directions , the leaf springs extend along the opposing axes, and are arranged within a projected cross section of the first connecting portion along the direction of the opposing axes. It is characterized by the presence of

Assuming that 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, when both ends of the leaf spring are fixed to the first mass body and the second mass body and deformed into an S shape, A bending moment around the y-axis is applied. However, with the above configuration, the axial force of the connector is perpendicular to the opposing direction, that is, the bending moment around the axis, so slippage around the fixed portion is less likely to occur. Further, since at least the first elastic body is integrated with a part of the first mass body via the first continuous portion, the fixing moment can be received by the member rigidity, and the occurrence of deflection of the first mass body is prevented. Therefore, appropriate parallel movement of the first mass body can be realized. This eliminates excitation loss due to slipping between the first connecting part and the first mass body and deflection of the first mass body, increasing the resonance magnification, and appropriately increasing the frequency and amplitude even with a small excitation force. It will be possible to realize this.

Further, the rotary vibrator according to the present invention includes a first mass body, a second mass body disposed opposite to the first mass body in an opposing axial direction, the first mass body and the second mass body. An excitation source that causes a body to vibrate relatively around the opposing axis; and a first elastic body disposed at a position connecting between the first mass body and the second mass body, the first elastic body comprising: 1 elastic body, a leaf spring, a first connecting part that is connected to one end of the leaf spring and forms a part of the first mass body, and a first connecting part that is connected to the other end of the leaf spring and forms a part of the first mass body. an integral leaf spring structure including a second continuous portion forming a part of the second mass body; The second connecting portion and the main body portion of the second mass body are connected by a connecting tool along parallel directions, and the second connecting portion and the main body portion of the second mass body are connected in a first direction intersecting the opposing axial direction, and in the opposing axial direction and It is preferable that they are connected along a second direction intersecting the first direction.

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

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

In this way, between the second continuous part and the second mass body, as well as between the first continuous part and the first mass body, slippage between parts and deflection of the spring fixing member can be prevented. Vibration loss can be eliminated.

In the above, it is preferable that the second mass body is on the fixed side and the first mass body is on the movable side. Here, the movable side is a side on which a vibrating object such as a carrier is provided, and the fixed side is a side that functions as a counterweight for the movable side.

In this way, by setting the first mass body on the movable side, slippage on the movable part side and deflection of the spring fixing member are preferentially eliminated.

In particular, it is preferable that the first continuous portion and the main body portion of the first mass body are connected at at least two locations along the opposing axis direction.

In this way, the leaf spring is firmly held on the main body of the first mass body at a plurality of locations via the first continuous portion, so that the first mass body does not bend or tilt, and the second mass body You will be able to move parallel to your body.

If a vibration conveyance device is constituted by the rotary vibrator according to any one of the above and a conveyance body fixed on the first mass body and provided with a spiral conveyance path, the article can be conveyed on the conveyance body. It becomes possible to effectively improve speed.

According to the present invention described above, by appropriately attaching the first elastic body, which is the main mechanical element that determines the resonance characteristics, to the mass body, vibration loss due to slippage between parts and deflection of the spring fixing member can be eliminated. It is possible to provide a new and useful rotary vibrator and vibration conveyance device that can achieve high frequency and large amplitude.

FIG. 1 is a perspective view showing a rotary vibrator and a vibration conveyance device according to an embodiment of the present invention. Exploded view of FIG. 1. FIG. 3 is an explanatory diagram of the main parts of FIG. 2. FIG. 3 is a perspective view showing a first elastic body constituting the same embodiment. FIG. 4 is an explanatory diagram of the configuration and attachment of the first elastic body. An explanatory diagram of the action of the first elastic body. The figure which shows the modification of this invention. The figure which shows the other modification of this invention. The figure which shows the other modification of this invention. FIG. 2 is a perspective view showing a rotary vibrator and a vibration conveyance device according to a conventional example. FIG. 4 is an explanatory diagram regarding the first elastic body of the conventional example. FIG. 4 is an explanatory diagram of vibration modes of the first elastic body. FIG. 3 is a diagram illustrating a problem in the conventional example.

An embodiment of the present invention will be described below with reference to FIGS. 1 to 6.

The rotary vibrator A of this embodiment includes a diaphragm 1 as a first mass body, a base 2 as a second mass body disposed opposite to the diaphragm 1 in the direction of the opposing axis m, and It includes an excitation source 3 that causes the diaphragm 1 and the base 2 to vibrate relative to each other around an opposing axis m, and a first elastic body 4 arranged at a position connecting the diaphragm 1 and the base 2. A conveyor B having a spiral conveyance path is attached to the rotary vibrator A, thereby configuring a parts feeder PF as a vibration conveyance device. The carrier B of this embodiment is configured to align and supply minute articles such as IC chips, for example.

The diaphragm 1 consists of a disc-shaped diaphragm main body 10 that is the main body of the first mass body, and a first connecting portion 41 (described later) that is attached to the diaphragm main body 10 and forms a part of the first mass body. configured. On the outer periphery of the diaphragm main body 10, there are diaphragm-side first connection parts 11 connected to the first elastic body at multiple equiangular locations, that is, three locations in this embodiment, and these diaphragm-side first connection parts 11. The second connecting portions 12 on the diaphragm side, which are connected to the vibration source 3, are provided at a plurality of equiangular locations with phase shifts, that is, three locations in this embodiment. The first connecting portion 11 on the diaphragm side has a shape that is hollowed out in the downward and radial direction, specifically, it is a concave portion that is downwardly U-shaped and has a bottom when viewed from the side. The second diaphragm-side connecting portion 12 is a protrusion that projects downward from the diaphragm main body 10 .

The base 2 includes a truncated conical base main body 20 that forms the main body of the second mass body, and a second connecting portion 42 (described later) that is attached to the base main body 20 and forms a part of the second mass body. It consists of The base body 20 is placed on the installation surface via the vibration isolating member 2a. On the outer periphery of the base 2, there is a base-side first connection part 21 located at a position corresponding to the diaphragm-side first connection part 11 and connected to the first elastic body 4, and a diaphragm-side first connection part 21. A base-side second connection portion 22 is provided at a position corresponding to the connection portion 12 and connected to the vibration source 3 . As shown in FIGS. 2 and 3(a), the base-side first connection portion 21 has a shape that is cut upward and radially outward, specifically, a U-shaped groove with a bottom when viewed from the side. It is a concave part that forms a As shown in FIGS. 2 and 3(b), the base-side second connection part 22 is located deep inside the space in which the diaphragm-side second connection part 12 is movably arranged, and It is composed of a leaf spring accommodating part 23 and a connecting member abutting part 24.

The vibration source 3 includes a connecting member 31 constituting a part of the base 2 which is a second mass body, and a second elastic body which is arranged horizontally and whose base end is connected to the connecting member 31 and whose distal end side extends in the radial direction. It includes a second plate spring 32 and a bimorph or unimorph type piezoelectric element drive unit 33 that is attached to both surfaces or one side of the second plate spring 32 and deflects the second plate spring 32 by vibration. As shown in FIG. 3(b), the base 2 includes the second leaf spring accommodating part 23 which extends in a star shape in three directions from the center when viewed from above and opens upward and radially outward, and an adjacent second leaf spring accommodating part 23. The L-shaped connecting member abutting part 24 is located between the two leaf spring accommodating parts 23, and the connecting member 31 to which the base end of the second leaf spring 32 is attached has two sides abutting the connecting member. While in contact with the contact portion 24, it is fastened to the bottom surface of the base 2 from the direction of the opposing axis z, that is, from above, with a bolt v1, which is a fastener.

Then, the base end of the second leaf spring 32 is horizontally connected to the connecting member 31 by the bolt 21, which is a fastener, and the tip of the second leaf spring 32 is made to protrude downward from the diaphragm body 10. It is horizontally connected to the provided second connection part 12 on the vibration plate side by a bolt v22 which is a fastener.

The first elastic body 4 functions as a main resonance spring by connecting the diaphragm 1 and the base 2, and as shown in FIG. The first connecting part 41 is connected to one end of each leaf spring 40 and forms a part of the diaphragm 1, and the first connected part 41 is connected to the other end of each leaf spring 40 and forms a part of the base 2. An integrated leaf spring structure (more specifically, an integrated stacked leaf spring structure) including the second continuous portion 42 is formed.

The leaf springs 40 are arranged parallel to each other. As shown in FIG. 11, if the origin O is set at the center of the thickness direction and width direction of the leaf spring 40, and the longitudinal direction is z, the thickness direction is x, and the width direction is y, the plate shown in FIGS. 1, 4, etc. The spring 40 has a thickness direction x directed toward the circumferential direction of the rotary vibrator A, a width direction y directed toward the radial direction of the rotary vibrator A, and a longitudinal direction z directed in a direction inclined to the opposing axis m of the rotary vibrator A. placed in an extended manner. Looking at the individual leaf springs 40, as shown in FIG. 5(c), the width W in the y direction does not have a uniform rectangular shape from one end 40e1 to the other end 40e2 as shown by an imaginary line along the longitudinal direction. Rather, as shown by solid lines, it has a smoothly constricted shape that gradually becomes narrower from the upper and lower ends 40e1 and 40e2 toward the center portion 40m. This shape is given by constricting the spring material, such as spring steel or carbon steel.

The first connecting portion 41 shown in FIG. 4 is a rectangular parallelepiped that is integral with the upper end of each leaf spring 40, and is inserted into the recess 11, which is the first connecting portion on the diaphragm side, as shown in FIGS. 1 and 2. Closely placed. The second connecting portion 42 shown in FIG. 4 includes a bottom portion 42a that is integral with the lower end of each leaf spring 40, and a right side portion 42b and a left side portion 42c that are arranged on both sides of this bottom portion 42a so as to surround each leaf spring 40. It is U-shaped and is integrally constructed with a U-shape and is tightly arranged in the recess 21 which is the first connection part on the base side, as shown in FIGS. 1 to 3.

That is, the first elastic body 4 is arranged in a positional relationship that allows it to be removably fitted into the rotary disk 1, which is the first mass body, and the base 2, which is the second mass body, from the outside.

As shown in FIGS. 1, 2, and 4, the first connecting portion 41 and the diaphragm main body 10 are connected at two locations along a direction parallel to the opposing axis m by a connector v3. . In FIGS. 2 and 4, the reference numeral h3 indicates a connecting hole for this purpose.

Further, the right side portion 42b of the second continuous portion 42 and the base main body 20 are connected at two places by bolts v4 along the first direction s that intersects (orthogonally) with the direction of the opposing axis m. The left side part 32c of the two-part connecting part 32 and the base body 20 are connected at two places by bolts v5 along the direction of the opposing axis m and the second direction u that intersects (orthogonally) with the first direction s. ing. In FIG. 4, reference symbols h4 and h5 are connection holes for this purpose. In 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. Further, 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 almost coincides with the first direction s, and the width direction y of the leaf spring coincides with the second direction u. They almost match.

In this embodiment, the diaphragm body 10 is made of aluminum in order to reduce the moment of inertia. However, when a spring is directly connected to the diaphragm body 10, the bending rigidity of the joint decreases because the Young's modulus of aluminum material is lower than that of iron. Therefore, as shown in FIG. 5(b), the first continuous portion 41, 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. Therefore, there is an effect of increasing the bending rigidity of the joint between the leaf spring 40 constituting the first elastic body 4 and the rotary disk main body 10. Similarly, at the joint portion between the leaf spring 40 constituting the first elastic body and the base body 20 that is the main body of the second mass body, the second connecting portion 42 that is integral with the leaf spring 40 is made of spring steel. It is made of a spring material such as carbon steel or carbon steel, and has the effect of increasing the bending rigidity of the joint between the leaf spring 40 and the base body 20. Although FIG. 5B shows one leaf spring 40 for convenience of explanation, since there are two leaf springs 40 in this embodiment as shown in FIG. The spring 40 has the above configuration and has similar effects.

Then, by repeatedly applying a voltage of a required frequency to the piezoelectric element driving section 33, the vibration plate 1 is vibrated in the forward and reverse directions through the second plate spring 32. Along with this, the plate spring 40, which is the first elastic body, bends and vibrates.

Among the bending vibrations, bending in the longitudinal direction shown in FIG. 6(a) occurs. This bending becomes a dominant factor that determines the resonance characteristics. With this bending, forces Fx, F'x in the x direction and fixing moments My, M'y about the y axis are generated at both fixed ends of the spring on the side of the origin O and on the opposite side. This is called the A-mode deflection.

Additionally, along with this, twisting around the z-axis as shown in FIG. 6(b) occurs. Along with this twisting, a moment Mz is generated around the origin O when viewed from the z-axis direction. This is called B-mode deflection.

Furthermore, along with this, bending in the width direction as shown in FIG. 6(c) occurs. With this bending, a force Fy in the y direction and a fixing moment Mx around the x axis are generated on the side opposite to the origin. In other words, when the diaphragm 102 rotates with respect to the base 101, the phase of the diaphragm-side fixed part α of the leaf spring 104 changes with respect to the phase of the base-side fixed part β, so for example, this is When projected onto the z-plane, the diaphragm-side fixing portion α is brought out in the width direction (radially outward direction). This is called C-mode deflection.

Of these, the A-mode deflection is amplified to the required frequency and amplitude at or near the resonance point, and the diaphragm 1 can be driven efficiently.

At this time, the first leaf spring 40, which is the first elastic body, is disposed in the z-axis direction, which is diagonal to the opposing axis m, so that the diaphragm 1 can perform translational movement (vibration) in the vertical direction. Performs rotational movement (vibration) in the circumferential direction. As a result, in the parts feeder PF, which is a vibrating conveyance device in which a conveyor B having a spiral conveyance path is mounted on a vibrating plate 1, the articles on the conveyance path are moved to the bottom of the conveyor B along the spiral conveyance path. It will be transported from the top to the top.

As described above, the rotary vibrator A of the present embodiment includes a rotary disk 1 as a first mass body and a base as a second mass body disposed opposite to the rotary disk 1 in the direction of the opposing axis m. a table 2, an excitation source 3 that causes the rotary disk 1 and the base 2 to vibrate relative to each other around the opposing axis m, and a first elastic body 4 disposed at a position connecting the rotary disk 1 and the base 2; Equipped with.

The first elastic body 4 is connected to a leaf spring 40, a first connecting portion 41 that is connected to one end of the leaf spring 40 and forms a part of the rotary disk 1, and a first connecting portion 41 that is connected to the other end of the leaf spring 40. It has an integrated leaf spring structure including a second connecting part 42 which is connected to the base 2 and forms a part of the base 2, and an opposing axis m is formed between at least the first connecting part 41 and the rotary disk main body 10. They are connected by a bolt v3, which is a connecting member, along a direction parallel to .

If such a so-called opposing axis direction fastening is adopted, when both ends of the leaf spring 40 are fixed to the rotary disk 1 and the base 2 and deformed into an S-shape, as shown in FIG. 6(a), the y-axis Even if a bending moment My is applied around the fixed part, slipping around the fixed part is unlikely to occur because the axial force of the bolt v3, which is a connector shown in Fig. 5(b), is in the opposite direction, that is, perpendicular to the bending moment My around the axis. . In addition, since the end of the leaf spring 40 is integrated with the first continuous portion 10 that is a part of the rotary disk 1, the fixing moment My can be received by the rigidity of the member, and the diaphragm 1 is deflected. is suppressed, and appropriate parallel movement in the x and y directions can be realized. This eliminates excitation loss due to slippage between the first connecting portion 41 and the leaf spring 40 and deflection of the rotary disk 1, increasing the resonance magnification, and appropriately increasing the frequency and amplitude even with a small excitation force. It becomes possible to realize it.

In addition, a first direction s intersecting the direction of the opposing axis m, and a direction of the opposing axis m and the first direction s exist between the second continuous portion 42 and the base body 20 which is the main body of the second mass body. Since the connection is made along the second direction u that intersects with the base 2, a method of fastening that is strong against the torsional stress of the first elastic body 3 on the side of the base 2, which is the second mass body, is made to connect the base 2 and the second connection. This can be realized between the installation section 42 and the installation section 42.

In particular, the second mass body is the base 2 on the fixed side, the first mass body is the rotary disk 1 on the movable side, and the above-mentioned opposing axial fastening is adopted at least on the rotary disk 1 side, so that the movable This means that slipping on the side and deflection of the spring fixing member are preferentially eliminated.

Further, the first continuous portion 41 and the rotary disk main body 10, which is a part of the first mass body, are connected at least at two locations along the direction of the opposing axis m. Since the plate springs 40 are firmly held at a plurality of locations on the rotary disk main body 10, the rotary disk 10 can be moved parallel to the base 2 without being bent or tilted.

The parts feeder PF, which is a vibration conveyance device, is constituted by such a rotary vibrator A and a conveyor B, which is fixed on the rotary disk 1, which is the first mass body, and has a spiral conveyance path. , it becomes possible to effectively improve the conveyance speed of articles on the conveyor B.

Although one embodiment of the present invention has been described above, the specific configuration of each part is not limited to the above-described embodiment.

For example, the first mass body of the above embodiment may be used as a base, and the second mass body may be used as a diaphragm, upside down. In this case, the second continuous part located under the first elastic body in the shape of an upward U-shape is located above and arranged in a downward U-shape, and conversely, the first continuous part located above is arranged downward. Thus, the connection in the opposing axial direction is preferentially performed between the base and the first elastic body. The shapes of the first mass body and the second mass body may be changed as appropriate.

Further, in the above embodiment, the leaf spring 40 has a constricted shape that becomes narrower from the end to the center, but it may also have a rectangular shape like the leaf spring 40' shown in FIG. . Other basic configurations are the same as those of the above embodiment, and corresponding parts are given the same reference numerals. In this way, the rigidity of the leaf spring 40' itself becomes high, so that it is possible to design the leaf spring 40' with emphasis on increasing the frequency.

Furthermore, in the above embodiment, the first connecting portion 41 and the rotary disk main body 10 are connected at two locations along a direction parallel to the opposing axis m by bolts v3, which are connectors. They may be connected by a bolt v3 at one location as shown in FIG. In this case, it is more preferable that the connection point by the bolt v3 is located at the midpoint between the two leaf springs 40' (or 40), since the moment My around the y-axis is approximately perpendicular to the axial force, so that slipping can be prevented; A similar effect can be achieved in that deflection of the diaphragm can be prevented by receiving the moment My by the rigidity of the member of the first continuous portion 41.

Further, as shown in FIG. 8(b), when connecting the first connecting portion 41 and the rotary disk main body 10 at two locations along a direction parallel to the opposing axis m using bolts v3, which are connectors, It is also effective to shift the connection hole h3 in the fastening direction u of the bolt v5 when fastening. By doing so, the bending strength of the leaf spring 40' (or 40) can be increased.

In addition, although two leaf springs 40 are used in the above embodiment, a configuration using only one leaf spring 40' (or 40) as shown in FIG. Of course, it is also possible to implement a configuration using a leaf spring.

Further, in the above embodiment, the rotary disk 1, which is the first mass body, and the first connecting portion 41 are fastened in the direction of the opposing axis m, and the base 2, which is the second mass body, and the second connecting portion 42 are fastened together. As shown in FIG. 9(b), the second continuous connection with the base 2, which is the second mass body, is performed. The portion 42 may also be connected along the direction of the opposing axis m. In this way, between the base 2 and the second connecting part 42, as well as between the rotary disk 1 and the first connecting part 41, slippage between parts and deflection of the spring fixing member can be prevented. Vibration loss can be eliminated.

In addition, various modifications can be made without departing from the spirit of the present invention, such as configuring the leaf spring without inclining it with respect to the opposing axis direction.

1...First mass body (rotary disk)
2...Second mass body (base)
3... Vibration source 4... First elastic body 20... Main body of second mass body (base main body)
40...Plate spring 41...First connecting part 42...Second connecting part A...Rotating vibrator B...Transporting body m...Opposing shaft PF...Vibration conveying device (parts feeder)
s...First direction u...Second direction v3...Connector (bolt)

Claims (6)

a first mass body, a second mass body disposed opposite to the first mass body in a direction of an opposing axis; A vibration source, and a first elastic body disposed at a position connecting between the first mass body and the second mass body,
The first elastic body is connected to a leaf spring, a first connecting part that is connected to one end of the leaf spring and forms a part of the first mass body, and a first connecting part that is connected to the other end of the leaf spring. and a second continuous portion forming a part of the second mass body, and at least the first continuous portion and the main body portion of the first mass body are connected to each other. connected by a connector along a direction parallel to the axis, the leaf spring extends along the opposing axis, and is disposed within a projected cross section of the first connecting part along the direction of the opposing axis. A rotating vibrator characterized by: a first mass body, a second mass body disposed opposite to the first mass body in a direction of an opposing axis; A vibration source, and a first elastic body disposed at a position connecting between the first mass body and the second mass body,
The first elastic body is connected to a leaf spring, a first connecting part that is connected to one end of the leaf spring and forms a part of the first mass body, and a first connecting part that is connected to the other end of the leaf spring. and a second continuous portion forming a part of the second mass body, and at least the first continuous portion and the main body portion of the first mass body are connected to each other. Connected by a connector along the direction parallel to the axis,
between the second continuous portion and the main body of the second mass body along a first direction intersecting the opposing axis direction and a second direction intersecting the opposing axis direction and the first direction; A rotary vibrator characterized by being connected. The rotary vibrating body according to claim 1, wherein the second connecting portion and the main body portion of the second mass body are also connected along the direction of the opposing axis . The rotary vibrator according to claim 1, wherein the second mass body is on the fixed side and the first mass body is on the movable side. The rotary vibrator according to any one of claims 1 to 4, wherein the first connecting portion and the main body portion of the first mass body are connected at at least two locations along the direction of the opposing axis . A vibration conveyance device comprising: the rotary vibrator according to any one of claims 1 to 5; and a conveyance body fixed on the first mass body and provided with a spiral conveyance path.

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