JP2014125339A - Vibratory conveying apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibratory conveying apparatus that can enhance adaptability to conveyance conditions by reducing a rotation moment, in addition to action effect equal to a balanced vibration system.SOLUTION: A vibratory conveying apparatus of the present invention comprises a first mass body 1 and a second mass body 2, and the first mass body 1 and the second mass body 2 include vibration units 1, 2, 3 vibratably connected in a predetermined vibration direction, respectively. The first mass body 1 has: a one mass part 1A vibratably connected in the vibration direction to the second mass body 2 respectively at two places along the vibration direction through vibration springs 3A, 3A configured to extend from the second mass body 2 to one side of the circumference of a central axis line Xo passing the center of gravity position; and the other mass part 1B vibratably connected in the vibration direction to the second mass body 2 at two places along the vibration direction through vibration springs 3B, 3B configured to extend from the second mass body 2 to the other side around the central axis line Xo.

Description

  The present invention relates to a vibration type conveying apparatus, and more particularly to a structure of an apparatus for conveying an object such as a part on a conveying path by vibrating an elastically supported conveying path.

  2. Description of the Related Art Conventionally, a vibration conveyance device including a so-called balanced vibration system that operates a working mass and a reaction mass in opposite phases to cancel harmful vibrations has been known for a long time. Examples of this type of apparatus include the following Patent Documents 1 to 5.

  On the other hand, in the conventional normal linear transfer device represented by Patent Document 6 below, the occurrence of a rotational moment is suppressed by matching the counterweight and the center of gravity of the transfer path (part) as much as possible with respect to the vibration direction. Some have done so.

Japanese Patent Publication No.49-38357 Japanese Patent Publication No.54-24198 JP-A-2-204209 JP-A-2-204210 JP-A-2-43118 JP 2009-298498 A

  However, although the method using the above balanced vibration system is possible in principle as seen in the vibration of a tuning fork, the mass and spring constant of a pair of vibration systems must be strictly matched. It is difficult to apply to the situation of use, that is, the requirement that various transport paths with different masses and forms must be mounted, and a truly practical one has not been made. In addition, even if the combination of the two masses of the action mass body and the reaction mass body and the spring constant is ideal, it is necessary to correctly match the position of the center of gravity in order to suppress the generation of moment as described later. It is difficult to prevent practical use.

  On the other hand, in a normal linear conveyance device that suppresses the generation of a rotational moment by matching the position of the center of gravity to the vibration direction as much as possible, its handling is not as difficult as that using the balanced vibration system, but the length of the conveyance path and The application range of mass is narrow and it is difficult to drive at a high frequency.

  Therefore, the present invention solves the above-mentioned problems, and its problem is to improve the adaptability to the conveyance conditions by reducing the rotational moment in addition to the same effects as the balanced vibration system. The object is to realize a vibration transfer device that can be used.

  In order to solve the above-mentioned problem, in the present invention, the reaction of vibration is canceled by operating the first mass body and the second mass body that vibrates against the first mass body in opposite phases. The first mass body is divided into two parts, and one of the mass parts and the other mass part thereof are arranged on both sides, preferably symmetrical positions, with respect to the center of gravity of the second mass body. Moreover, a conveyance path is provided in at least one of the first mass body and the second mass body. When a conveyance path is provided in the first mass body that is divided into two, the conveyance path may be provided in any of the one mass part and the other mass part. One mass part and the other mass part of the divided first mass body are coupled by the connecting means, and are driven in the same direction with the same frequency and the same phase.

  At this time, it is preferable that the center of gravity of each of the first mass body and the second mass body is configured to exist somewhere on a straight line parallel to the vibration direction. That is, a straight line connecting the center of gravity position (1g) of the entire first mass body including one mass part and the other mass part and the center of gravity position (2g) of the second mass body is substantially parallel to the vibration direction. It is desirable to be configured. Furthermore, it is preferable that one mass part and the other mass part of the first mass body are arranged above and below the second mass body. In this case, the center of gravity of the one mass part and the other mass part are further arranged. It is desirable that the center of gravity of the mass portion and the center of gravity of the second mass body are both disposed on the same plane along the vibration direction, preferably on the same vertical plane.

  The vibratory transfer device of the present invention includes a first mass body (1) and a second mass body (2), and the first mass body (1) and the second mass body (2). Is a vibration-type transfer device including vibration units (1, 2, 3) which are connected via a vibration spring (3) and are connected to each other so as to vibrate in a predetermined vibration direction. Here, the first mass body (1) has one mass part (1A) and the other mass part (1B). Then, the one mass portion (1A) has a central axis (Xo) along the vibration direction passing through the center of gravity from the second mass body (2) at two locations along the vibration direction. Each of the second mass bodies (2) is connected to the second mass body (2) so as to vibrate in the vibration direction by vibration springs (3A, 3A) configured by leaf springs orthogonal to the vibration direction. Arranged on the one side. The other mass portion (1B) extends from the second mass body (2) to the opposite side to the one side around the central axis (Xo) at two locations along the vibration direction. The vibration springs (3B, 3B) configured by leaf springs orthogonal to the vibration direction are connected to the second mass body (2) so as to vibrate in the vibration direction and arranged on the opposite side. Is done.

  In addition, the second mass body (2) is vibrated in the vibration direction at two locations along the vibration direction by support springs (4, 4) composed of leaf springs orthogonal to the vibration direction, respectively. Supported as possible. Furthermore, driving means (3Ad, 3Bd, mg1, mg2) for vibrating the first mass body (1) and the second mass body (2) in opposite phases, the one mass section (1A), A transport unit (tp) provided in at least one of the other mass unit (1B) or the second mass body (2) and having a transport path for transporting a transported object in the vibration direction; And connecting means (cb, 1s) for causing the first mass part (1A) and the second mass part (1B) to vibrate in the same phase in synchronization with the vibration direction.

  The vibratory transport apparatus according to the present invention is characterized in that the first mass body (1) and the second mass body (2) are driven in the vibration direction in opposite phases by the driving means. As a result, the reaction force in the vibration direction of both mass bodies is reduced, so that vibration leakage to the support base through the support spring is reduced. In the present invention, the one mass part (1A) and the other mass part (1B) are disposed on both sides around the central axis (Xo) passing through the center of gravity of the second mass body (2). It is characterized by that. Thereby, since it is possible to reduce the deviation between the gravity center position of the first mass body (1) and the gravity center position of the second mass body (2) that vibrate in mutually opposite phases, the moment force generated with the vibration is reduced. Can be reduced. Furthermore, in this invention, said one mass part (1A) and said other mass part (1B) vibrate in the same phase by the said connection means. As a result, moment forces associated with vibrations of the one mass part and the other mass part arranged on both sides of the center of gravity position of the second mass part are reduced in opposite directions, and thus are accompanied by vibration. The moment force can be further reduced, and the pitching operation of the entire vibration unit including the first mass body and the second mass body connected via the vibration spring can be reduced. In particular, the second mass body (2) during vibration is configured to substantially cancel the moment force received from one mass portion (1A) and the moment force received from the other mass portion (1B). preferable. The center of gravity (1ga) of one mass part (1A) and the center of gravity (1gb) of the other mass part (1B) are both arranged on a plane (Px) including the central axis (Xo). Is preferred. At this time, the plane (Px) is preferably a plane along the direction from one side of the central axis (Xo) to the opposite side. For example, if the opposite side to the one side is an upper side and a lower side, the plane (Px) is preferably a vertical plane.

  In the present invention, the connecting means (cb, 1s) realizes an in-phase vibration mode by a connecting structure that connects the one mass part (1A) and the other mass part (1B). The connection structure (cb, 1s) may simply connect and fix the one mass part (1A) and the other mass part (1B), but the one mass part (1A) and the It is preferable to synchronize the one mass part (1A) and the other mass part (1B) in the vibration direction while allowing a variation in distance between the other mass parts (1B). In the connection structure, for example, the rigidity with respect to the displacement in the vibration direction between the one mass part (1A) and the other mass part (1B) is such that the one mass part (1A) and the other mass part (1A) It is desirable that the coupling portion (cb, 1s) is configured to be higher in rigidity than the variation in the coupling distance with the mass portion (1B). According to this, since one mass part and the other mass part can be operated in the same direction in the vibration direction, and it is possible to absorb the distance variation between the two mass parts due to vibration, the vibration unit Since the load during vibration can be reduced, a smooth vibration mode can be realized and the durability of the vibration spring and the like can be enhanced.

  In the present invention, the gravity center position (1g) of the first mass body (1) and the gravity center position (2g) of the second mass body (2) are arranged on a straight line substantially parallel to the vibration direction. It is preferable. As a result, the gravity center positions of the first mass body and the second mass body at the time of vibration are arranged on the same line of action, and the pitching operation is less likely to occur, so that the transport unit can be vibrated substantially in parallel. A uniform conveying force can be given over the entire conveying path.

  In the present invention, the natural frequency determined by the vibration unit (1, 2, 3) and the support spring (4) is 1/10 or less of the operating frequency (vibration frequency) of the vibration unit (1, 2, 3). Preferably there is. According to this, the vibration frequency leaked to the base via the support spring is further reduced by significantly reducing the natural frequency of the entire vibration system including the support spring with respect to the operating frequency (vibration frequency) of the vibration unit. Can be reduced.

  In the present invention, the drive means (3Ad, 3Bd) constitutes the vibration spring (3A, 3B) by being connected in series with an amplification spring (3As, 3Bs) made of a leaf spring orthogonal to the vibration direction. It may be a piezoelectric driving body (3Ad, 3Bd). In this case, the driving means may be provided only in one of the one-side vibration spring (3A) and the opposite-side vibration spring (3B).

  In the present invention, the drive means (mg1, mg2) is an excitation force generated by a magnetic force based on an alternating magnetic field with respect to at least one of the first mass body (1) and the second mass body (2). In some cases, an AC electromagnet that affects In this case, the driving means may be provided so as to exert a vibration force only on one of the one mass part (1A) and the other mass part (1B).

  In the present invention, the side portion of the second mass body (2) between the one mass portion (1A) and the other mass portion (1B) is spaced along the central axis (Xo). It is preferable that protrusions or recesses are provided in at least two positions. According to this, since the balance around the central axis of the vibration unit can be confirmed using the protrusion as a fulcrum or the pin contacting the recess as a fulcrum, the weight balance of the vibration unit can be inspected and adjusted. You can do it.

  In the present invention, the attachment posture adjusting means for adjusting the posture of the transfer portion (tp) with respect to the central axis (Xo) and the angle of the central axis (Xo) with respect to the base can be adjusted. It is preferable that both of the vibration unit installation posture adjusting means are provided. According to this, since the mounting posture of the transport unit that defines the transport direction and the installation posture of the vibration unit that defines the vibration direction can be adjusted separately, the projection angle φ is appropriately set separately from the posture in the transport direction. Since it can be set, it is possible to flexibly cope with various transport conditions, and the transport mode can be easily optimized.

  According to the present invention, in addition to the effect of the balanced vibration system, an excellent effect is achieved in that it is possible to realize a vibration type conveying apparatus that can reduce the rotational moment and increase the adaptability to the conveying conditions. obtain.

The schematic diagram which shows the 1st vibration model of a vibration type conveying apparatus. The schematic diagram which shows a 2nd vibration model. The schematic diagram which shows a 3rd vibration model. The figure which shows the shape of a tuning fork. The schematic diagram which shows the structure which has a support spring comprised with a leaf | plate spring in a 2nd vibration model. The schematic diagram which shows the vibration model which has the basic composition of an Example. The figure which shows a mode that the vibrating bodies A and C vibrate with an antiphase. The figure which shows a mode that the vibrating bodies A and C vibrate with the same phase. The block diagram which shows the example of the vibration system which uses an electromagnet as a drive source. The block diagram which shows the example of another vibration system which uses an electromagnet as a drive source. The block diagram which shows the example of another vibration system which uses an electromagnet as a drive source. The block diagram which shows the example of the vibration system which uses a pneumatic unit as a drive source. The block diagram which shows the example of the vibration system which uses a piezoelectric element as a drive source. The block diagram which shows the example of the 1st type vibration system which uses a piezoelectric element as a drive source. The block diagram which shows the example of another vibration system of the 1st type which provided the conveyance part in the example shown in FIG. 14, and changed arrangement | positioning of a piezoelectric drive part. The front view (a) and side view (b) which show the structure in the case of providing a conveyance part in the example shown in FIG. The block diagram which shows the example of the 2nd type vibration system which uses a piezoelectric element as a drive source. The block diagram which shows the example of another vibration system of the 2nd type which uses a piezoelectric element as a drive source. The block diagram which shows a mode that the conveyance part was provided in the example shown in FIG. The front view (a) of the example shown in FIG. 19, and the front view (b) which shows the example which provided another conveyance part. Explanatory drawing which shows the equivalent structure of the whole vibration system of an Example. The schematic diagram which shows the equivalent structure of the vibration unit of an Example. The block diagram (a) and (b) which shows the example of a 1st mass body. The block diagram (a)-(c) which shows the example of a coupling body. The perspective view for explanation which shows the relation of the gravity center position of an example. Sectional drawing (a)-(c) for description which shows the example of the relationship of the gravity center position of an Example. Explanatory drawing (a) and (b) which show the relationship between a gravity center position and a moment arm. Explanatory drawing (a) and (b) which show the relationship between the gravity center position and moment arm in an Example. The side view of Example 1, and the projection view along the central axis line Xo of a vibration system. Explanatory drawing which shows the connection structure and the vibration unit fixing mechanism of Example 1 in the cross section along the center axis line Xo. The 3rd view and sectional drawing of a 1st connection member. Explanatory drawing which shows the mode at the time of gravity center adjustment. The side view of Example 2, and the projection figure along the center axis line Xo of a vibration system. 33 is a cross-sectional view along the line AA ′ shown in FIG. 33 (a), a cross-sectional view along the line BB ′ (b), and an arrow view showing a state seen along the arrow C shown in FIG. c) and a plan view and a side view (d) of the center of gravity adjustment mechanism. The side view of Example 3 (a) and the arrow view (b) seen in the arrow B direction of (a). FIG. 36 is a cross-sectional view along the line AA ′ shown in FIG. The side view (a) and back view (b) of the 1st mass body of Example 3. The side view of Example 4. FIG. The rear view of Example 4. FIG. The top view of Example 4, the side view (a) of a conveyance part, and the fragmentary sectional view (b) of a vibration system. The side view (a) and front view (b) of Example 5. FIG. 42 is a cross-sectional view along the line AA ′ in FIG. 41, a cross-sectional view along the line BB ′, and a cross-sectional view along the line CC ′. An explanatory diagram (a) of the projection angle φ, an explanatory diagram (b) when the projection angle φ is small, and an explanatory diagram (c) when the projection angle φ is large.

  Next, an embodiment of the vibratory conveyance device of the present invention will be described in detail with reference to the accompanying drawings. The following embodiments are not affected by the rigidity of the installation part (base, support column, base, other base), and there is little conveyance unevenness over the entire length of the conveyance path. It is applicable to various shapes and mass ranges of transport paths while maintaining performance such as no fluctuations), and can handle various operating frequencies, making it easy to design and adjust transport paths on-site. This is the pursuit of a structure capable of maximizing the function as a linear transport device.

  As shown in FIG. 1, the simplest vibratory conveyor such as a linear feeder is configured such that both ends of a vibrating body A positioned above a base portion B fixed to a base G are vibrated in the direction of vibration (the horizontal direction in the figure). ) Is a vibration system supported by leaf springs D and D orthogonal to each other. When the vibrating body A is displaced in either the left or right direction and is released suddenly, the elastic energy and the velocity energy due to the deformation of the leaf spring D are exchanged, and the vibration is damped at a constant frequency. In an actual vibration type conveying apparatus, steady vibration is maintained with a small amount of energy by driving at a frequency close to the natural frequency of the vibration system by driving means such as an electromagnet or a piezoelectric element.

  On the other hand, as shown in FIG. 3, there is a vibration system in which two sets of vibration bodies A and A ′ having the same mass and size are supported by leaf springs D, and the masses of vibration bodies A and A ′ are When the leaf springs D that support them have the same spring constant and the leaf springs D are attached to a common strong base G or a base B fixed to the same, the vibration body A and If A ′ is vibrated in the opposite direction, that is, in opposite phase, all the forces cancel each other as will be described later, and neither the rotational moment nor the horizontal driving force is generated in the lower base portion B or base G. . Therefore, no vibration is transmitted to the gantry where the device is installed. This is a so-called balanced vibration system model. The tuning fork used by the musician shown in FIG. 4 for tuning is also a kind of balanced vibration system, and the cantilever beams on both sides generate bending and vibration in opposite phases to each other, thereby generating a sound wave having a stable and constant frequency. When one beam (strip) is hit, the strips on both sides are drawn to the same frequency and damped and oscillated at a certain natural frequency.

  In the vibration system composed of a pair of vibration bodies A and leaf springs D shown in FIG. 1, the force due to elastic deformation of the leaf springs D due to vibrations is transmitted from the vibration body A to the base portion B and generates a periodic rotational moment. If the base part B is floating from the base G by the anti-vibration mechanism having the anti-vibration spring E as shown in FIG. 2, the base part B is periodically tilted and the whole is like a ship receiving longitudinal waves. Cause pitching. When the pitching motion occurs, the vibration direction of the transport path T attached to the vibrating body A changes over the entire length of the transport path, so the transport speed is not fixed, and the basic as a linear feeder such as stagnation or reverse travel of the transport Function is impaired. In addition, since a reaction force is generated with respect to the acting force caused by the vibration of the vibrating body A, a force that moves in the horizontal direction opposite to the vibrating body A is also generated in the base portion B. As described above, in the linear feeder type vibration system as shown in FIG. 1, the moment force Fm to rotate the whole and the horizontal force Fh based on the reaction force always work. Although the linear feeder of the basic type as shown in FIG. 1 is also used in a limited manner, it can be fixed to a gantry having high rigidity and mass that is not displaced (deformed) by the moment force and reaction force as described above. It can be put into practical use for the first time. In other words, in this case, the reaction force is confined by the strength and rigidity of the gantry, and it is preferable that the vibrating body A and the conveyance path T are light and small. In addition, as the vibration engineering teaches, this acting force increases in proportion to the square of the operating frequency and the amplitude, so that driving at a high frequency becomes difficult in terms of acceleration, and the extremely strong and heavy base B or G It is necessary to firmly fix to

  Next, based on such a basic mechanism, the “symmetric drive mechanism” according to the present invention will be described. FIG. 5 shows a general configuration of the vibration model, and shows that plate springs orthogonal to the vibration direction are used for the vibration spring D and the support spring E, respectively. FIG. 6 shows a vibration model according to the present invention. The vibration body A is connected to the base portion B by vibration springs Da at two locations in the vibration direction (left-right direction in the figure), and the base portion B is shown. A vibrating body C connected by a vibration spring Db is provided at two locations in the vibration direction, and the base portion B is supported by a support spring E at two locations in the vibration direction. In the illustrated example, the vibrating body A and the vibrating body C are arranged vertically symmetrically with respect to the base portion B. In this vibration model, when a force is applied in the horizontal direction in the drawing, the vibration model vibrates in a manner as shown in FIG. 7 or FIG. 7 and 8 show the state of the maximum amplitude in which the vibrating body A (and the vibrating body C) and the base part B are displaced to the left side, and the next moment represents the time point of shifting to the right side. .

  In this case, different operations are performed depending on the phase relationship of vibration. As shown in FIG. 7, when the upper and lower vibrating bodies A and C operate in opposite phases, both the upper vibrating body A and the lower vibrating body C generate counterclockwise moments. Overlapping, the base part B receives a large rotational moment. On the other hand, since the reaction force accompanying the vibration operation of the vibrating bodies A and C cancels out the vibration force in the horizontal direction, it hardly acts on the base portion B.

  Next, when the upper and lower vibrating bodies A and C operate in the same phase, the clockwise moment of the lower vibrating body C and the counterclockwise moment of the upper vibrating body A are shown in FIG. Is offset and no rotational moment is generated in the base portion B. However, with respect to the horizontal vibration, the base B receives a vibration force having a phase opposite to that of the vibration bodies A and C due to a reaction force accompanying the vibration operation of the vibration bodies A and C. As will be described later, the movement of the base portion B in the horizontal direction can be reduced to a level where there is no practical problem if it is held by a support spring E (leaf spring) having low rigidity in the horizontal direction. Note that driving in the same phase as shown in FIG. 8 is generally difficult in a free state as shown in the figure, and automatically enters reverse phase operation as shown in FIG. 7 under normal operating conditions.

  In the vibration model shown in FIG. 5 to FIG. 8, the two vibration bodies A and C are arranged symmetrically with respect to the base portion B, and each is coupled with vibration springs Da and Db each consisting of a leaf spring. However, in an actual vibration transfer machine, continuous vibration cannot be generated unless any drive mechanism is incorporated. FIGS. 13 to 20 are models in which a piezoelectric drive element is incorporated in a part of the vibration springs Da and Db as drive mechanisms, and FIGS. 9 to 11 are examples of driving by an AC electromagnet separately from the vibration springs Da and Db. is there. In the following description, the combination of the vibrating bodies A and C is referred to as a first mass body 1, the vibrating body A is referred to as a mass portion 1A, the vibrating body C is referred to as a mass portion 1B, and the base portion B is referred to as a first mass body 1. 2 mass body 2.

  First, the case where it operates with a piezoelectric drive body is demonstrated with reference to FIGS. Piezoelectric driving bodies are widely used as driving sources because the driving force of piezoelectric elements has been improved and reliability has been increased. As shown in FIG. 13, in this vibration model, the first mass body 1 having the mass m1 is divided into two parts, which are a mass part 1A having a mass m1a and a mass part 1B having a mass m1b, and these mass parts 1A and 1B. Are arranged on both sides of the second mass body 2 having the mass m2 (both sides in the vertical direction in the illustrated example), and the vibration direction (actually, the left-right direction shown in the figure between the mass portion 1A and the second mass body 2). The vibration springs 3A are connected at two locations in the conveying direction (the same applies hereinafter). Further, a vibration spring 3B is connected between the mass portion 1B and the second mass body 2 at two locations in the vibration direction which is the horizontal direction shown in the drawing. Further, the second mass body 2 is supported by support springs 4 at two locations in the vibration direction, and the support springs 4 are connected to the base G. At this time, the vibration spring 3A is constituted by a piezoelectric drive body 3Ad and an amplification spring 3As connected in series, and the vibration spring 3B is constituted by a piezoelectric drive body 3Bd and an amplification spring 3Bs connected in series. In the illustrated example, piezoelectric driving bodies 3Ad and 3Bd are connected to the second mass body 2 (the side), and amplification springs 3As and 3Bs are connected to the mass portions 1A and 1B (the side).

  In the piezoelectric driving bodies 3Ad and 3Bd, so-called bimorph type piezoelectric elements that contract and expand on the front and back sides are used, and the piezoelectric elements are attached to both sides of a thick steel plate (steel plate). The steel plate serving as the driving source is made thick so as not to be greatly deformed. This is to prevent the adhesion between the piezoelectric element and the steel plate from being peeled off. However, since the practical vibration amplitude cannot be obtained only with the piezoelectric driving members 3Ad and 3Bd, the amplifying springs 3As and 3Bs made of a slightly thin leaf spring are inserted into the intermediate portion, and the spring constant k3 and mass of the leaf spring are inserted. It is preferable to drive the piezoelectric element at a frequency close to the natural frequency of the vibration system constituted by the masses m1a and m1b of the part 1A or the mass part 1B to create a resonance state and efficiently obtain a large vibration amplitude.

  The basic configuration shown in FIG. 13 includes those shown in FIGS. 14 to 20 depending on the mass distribution of the mass m1 of the first mass body 1 and the mass m2 of the second mass body 2 and the arrangement of the piezoelectric drive unit. Various variations are conceivable. The first type shown in FIG. 14 is a so-called reaction mass body in which the mass m2 of the second mass body 2 is heavier than the mass m1 of the first mass body 1 (the sum of the mass parts 1A and 1B). It is said. In this case, the method of increasing the mass m2 of the second mass body 2 is not particularly limited, but in the illustrated example, the second mass body 2 is used as one method when the method of increasing the volume is employed. It is made into the shape which has the expansion parts 2A and 2B extended up and down inside two connection places of the front and back of the conveyance direction between mass parts 1A and 1B. In particular, in the illustrated example, the second mass body 2 is formed in a shape that is expanded between the connecting portions in the vibration direction of the support spring 4, so that the stability around the center of gravity of the second mass body 2 is improved.

  In the vibration model shown in FIG. 15, a transport unit tp including a transport path is provided in the mass unit 1 </ b> A of the first mass body 1. However, the transport unit tp is not limited to the mass unit 1A and may be provided in the mass unit 1B. In terms of mass balance, the first mass body 1 is preferably provided with the transport unit tp, but may be provided on the second mass body 2. In FIG. 15, contrary to that shown in FIG. 14, the piezoelectric driving bodies 3Ad and 3Bd are connected to the mass part 1A or the mass part 2B (on the side), and the amplification springs 3As and 3Bs are connected to the second mass body 2. Connected to (side). As shown in FIGS. 17 and 18, the arrangement of the piezoelectric drive unit is as shown in FIGS. 13 and 14 or as shown in FIG. It can be realized in various combinations with other structural examples. Note that any of these connection modes can be used in the other illustrated examples and examples. These combinations have some advantages and disadvantages, but experimentally, characteristics similar to those described above with reference to FIG. 8 were confirmed. However, with regard to the arrangement of the piezoelectric drive unit, the piezoelectric drive bodies 3Ad and 3Bd are mass bodies having a larger mass (in the case of FIGS. 14 and 15, the second mass body 2, in the case of FIGS. 17 and 18 described later). Is arranged on the first mass body 1, that is, on the side of the mass parts 1A and 1B), the amplitude becomes relatively small. Therefore, the connection mode shown in FIGS. 14 and 18 is slightly more advantageous.

  As explained in the previous section, in this configuration, no matter how carefully the upper and lower mass parts 1A and 1B are driven in the same phase, they are naturally shifted to the opposite phase, so the side view of FIG. 16 (a) and FIG. 16 (b) As shown in the front view, the mass part 1A and the mass part 1B must be mechanically coupled by a connecting body cb such as a side plate. In addition, this connection body cb is good also as a structure which passes the opening part provided in the 2nd mass body 2 like the 2nd type mentioned later. The connecting body cb is not limited to the side plate-shaped one in the illustrated example, but by using the side plate-like connecting body cb, this can be avoided without changing the structure of the second mass body 2 and the mass part 1A and the mass part. 1B can be connected. In the illustrated example, slits cba and cbb cut from the front and rear in the vibration direction are formed in the connection body cb, and a connection portion cbs having a shape extending in the vibration direction is formed therebetween. As will be described later, these slits cba and cbb (or connecting portion cbs) are distances that change according to the position in the front-rear direction when the mass part 1A and the mass part 1B swing back and forth in the vibration direction. The distance between the two mass parts is changed by lowering the rigidity in the direction connecting the mass parts 1A and 1B while ensuring the rigidity in the vibration direction in order to be able to follow (the vertical distance in the illustrated example). It is an elastic deformation structure that makes it possible.

  In contrast to what is shown in FIG. 14, what is shown in FIG. 17 is so called that the total mass m 1 of the mass parts 1 A and 1 B of the first mass 1 is made heavier than the mass m 2 of the second mass 2. The second type is a reaction mass. In this case, it is preferable to attach the transport path tp to the second mass body 2 by mass balance. Here, the method of configuring the first mass body 1 to be heavy is not limited in the same manner as described above, but in the illustrated example, both the mass portion 1A and the mass portion 1B are disposed on the second mass body 2 side ( It extends to the upper and lower sides.

  Similarly to the first type, if the mass part 1A and the mass part 1B are separated, the in-phase operation may be started. Therefore, the mass parts 1A and 1B are mechanically connected as shown in FIG. Is bound to. Here, in the illustrated example, the mass parts 1A and 1B extend as they are to the side of the second mass body 2, and are integrally configured through an opening 2n provided in the center of the second mass body 2. Alternatively, they are directly connected. Also in this example, slits 1a and 1b similar to those described above are formed in the portion passing through the opening 2n, and a connecting portion 1s is formed between them, so that it is possible to follow a change in the distance between the mass portions 1A and 1B. Configured as follows. Here, since the mass parts 1A and 1B are integrally formed or directly connected, the first mass body 1 has mutual rigidity in the vibration direction in the middle part of the mass parts 1A and 1B. It can be considered that the structure has an elastic deformation structure in which the rigidity in the direction in which the distance of the gap changes is lowered and the gap can be changed. In the second type as well, as in the first type, the mass part 1A and the mass part 1B are not directly connected, but may be connected via a separate connecting body cb. Good. Further, the connecting body cb may be constituted by a side plate as shown in FIG. Further, FIG. 18 shows the arrangement of the piezoelectric drive section (connection mode of the piezoelectric drive body and the amplification spring) opposite to the structure shown in FIG. 17 as described above.

  In the structure shown in FIG. 19, the transport unit tp is provided in the second mass body 2. In this structure, as shown to Fig.20 (a), the conveyance part tp is attached via the support body sb comprised from the 2nd mass body 2 by the side frame. In the illustrated example, the transport unit tp is supported by the support sb above the mass unit 1A. In this case, it is preferable to provide a counterweight cw at a position below the support sb in order to align the center of gravity. Further, if the transport part tp is directly attached to the side of the second mass body 2 as shown in FIG. 20B instead of the vertical direction as shown in FIG. 19 and FIG. , The overall height can be kept compact. In this case as well, the balance in the width direction can be achieved by providing the counterweight cw on the opposite side of the conveyance section tp in the width direction.

  15 and 19 illustrate a structure provided with a transport unit tp having a transport path for the sake of explanation. In the structures of these drawings themselves, the vibration direction is horizontal and components are placed on the transport path. Can not be transported. Actually, the entire vibration unit may be inclined at a certain angle so as to vibrate so as to push the conveyance path obliquely upward in the conveyance direction. In addition, the vibration springs 3A and 3B are attached in an inclined posture so as to be inclined obliquely upward in the transport direction, a spacer having a predetermined thickness is interposed between the piezoelectric drivers 3Ad and 3Bd and the amplification springs 3As and 3Bs, The conveying force can be similarly generated by configuring the vibration springs 3A and 3B with a plurality of springs and interposing a spacer having a predetermined thickness therebetween.

  Next, in order to explain the vibration mode of each example described above, as shown in FIG. 22, the piezoelectric drive unit and the amplification spring unit having the structure shown in FIGS. 13 to 20 are integrated link arms LAa and LAb. Consider a vibration model of a vibration unit that is connected at both ends with a spindle that moves smoothly. Since this vibration model is a parallel link mechanism, when the mass parts 1A and 1B, which are upper and lower movable parts, move from the neutral position before and after the vibration direction to the maximum shake position at both front and rear ends (see the two-dot chain line in the figure) The mutual distance between the parts 1A and 1B is reduced to P1 with respect to the distance P0 when the parts are in the neutral position. Arise. In order to absorb the difference between the distances P0 and P1, the force is transmitted in the vibration direction as in the connecting structure having the slits shown in FIGS. 16 to 19, but the vertical movement is allowed. It is desirable to couple by a rigid coupling mechanism.

  As an example of the above coupling mechanism, FIGS. 23A and 23B show shape variations in the case where the mass part 1A and the mass part 1B are coupled at the central part. In the connecting mechanism of FIG. 23A, slits 1a and 1b cut from the front and rear in the vibration direction are formed between the mass part 1A and the mass part 1B, and the shape (narrow width) is extended between the slits in the vibration direction. By forming the elastically deformable connecting portion 1 s of the shape), elastic deformation in the vertical direction is facilitated while ensuring the rigidity in the vibration direction of the first mass body 1. In the connecting mechanism of FIG. 23 (b), the mass part 1A and the mass part 1B are connected by an elastic connecting material 1s which is an extended member (elongated shape) extending in the vibration direction, and the elastic connecting member 1s is connected in the extending direction (longitudinal). (Direction) is high in rigidity and difficult to elastically deform, and in the vertical direction (orthogonal direction), the rigidity is low and easy to elastically deform, thereby ensuring the rigidity of the first mass body 1 in the vibration direction. However, the elastic deformation in the vertical direction is facilitated.

  Further, FIGS. 24A to 24C show shape variations in the case where the mass part 1A and the mass part 1B are coupled by the side plate-like coupling bodies cb on both sides (shown in FIG. 16). In the coupling mechanism of FIG. 24A, slits cba and cbb cut from the front and rear in the vibration direction are formed in the middle part of the coupling body cb in the vertical direction, and an extended shape elastically deformable extending in the vibration direction therebetween. By providing the connecting portion cbs, the structure is configured to facilitate elastic deformation in the vertical direction. In the connecting mechanism of FIG. 24B, the connecting body cb has a triangular first connecting part cbA having a vertex on the lower side fixed to the mass part 1A, and a triangle having an apex on the upper side fixed to the mass part 1B. A second connecting portion cbB having a shape, and an elastic connecting portion cbS having a shape extended in a vibration direction connecting the lower end corresponding to the apex of the first connecting portion cbA and the upper end corresponding to the apex of the second connecting portion cbB. ing. In this structure, bending deformation occurs elastically in the region between the first connection part cbA and the elastic connection part cbS that are configured to be relatively narrow, and between the second connection part cbB and the elastic connection part cbS. That is, the first connecting portion cbA and the second connecting portion cbB are configured to be movable in the vertical direction by changing the posture so that the extending direction of the elastic connecting portion cbS deviates from the vibration direction. In the connecting mechanism of FIG. 24C, a triangular first connecting part cbA ′ fixed to the mass part 1A and a second connecting part cbB ′ fixed to the mass part 1B are provided, and the first connecting part cbA ′ and The second connecting portion cbB ′ has a structure in which the vertices are connected to each other. Also in this case, since the elongated holes cbo provided beside the fixing holes at the four corners are configured to be elastically deformed on both sides of the elongated holes cbo, the portions extending in the vibration direction are configured. The structure can be easily elastically deformed in the vertical direction while ensuring the rigidity in the direction.

  In addition, although the said connection part and a connection body are each fixed to mass part 1A and 1B as what was comprised so that elastic deformation was possible in the up-down direction, instead, the connection part and connection body which consist of a rigid body are massed. It is connected to at least one of the parts 1A and 1B so as to be movable in the vertical direction using a long hole or the like, and non-rotatably connected to at least one of the mass parts 1A and 1B ( For example, a connecting link configured to be completely fixed) may be used. If it does in this way, the said connection link will act so that mass body 1A and 1B may be synchronized with a vibration direction, accept | permitting the distance fluctuation | variation of mass body 1A and 1B in the up-down direction. As long as the connection part which concerns on this invention acts in this way as a result, any of the above-mentioned elastically deformable connection part or connection body, and the said connection link may be sufficient.

As described above, comparing the mass m1 of the first mass body 1 and the mass m2 of the second mass body 2, the reason why the transport part tp is provided on the light mass body side is that This is because the amplitude is inversely proportional to the ratio of the masses m1 and m2, and therefore it is more efficient to provide the transport unit tp as a load on the lighter side. This is derived by Newton's "second law of motion" and "third law (law of action and reaction)". A second mass body 2 constrained to the base G by a spring 4 (spring constant k ₀ ) on a horizontal plane as shown in FIG. 21, a second mass body 2 (mass is M ₂ ), and a spring 3 (spring In a model in which the first mass body 1 (mass is m ₁ ) connected by the constant k1) is configured to be able to move on wheels that move without resistance, the two mass bodies 1 and 2 can move freely. Therefore, it is a two-vibration system in terms of vibration engineering, and is considered to be the same vibration system as FIGS. Here, when the spring constant k ₀ of the spring 4 is set to ₀ as much as possible, the first mass body 1 and the second mass body 2 exert the same force F by the spring 3. When the angular frequency ω is used, the equation of motion shown in Equation 2 is obtained. Note that f is the frequency, x ₁ is the amplitude (x coordinate) of the first mass body, and x ₂ is the amplitude (x coordinate) of the second mass body 2. As a result, the relationship shown in Equation 3 below is established.

  Next, a model driven by an electromagnet will be described with reference to FIGS. The drive source is changed from the above-described piezoelectric element to an electromagnet, but an equivalent configuration can be easily realized by using a combination of a piezoelectric drive body and an amplification spring as in the previous model. Here, in this model, as shown in FIG. 9, as an elastic support structure, the mass parts 1A (mass = m1a) and 1B (mass = m1b) of the first mass body 1 corresponding to the link arm of FIG. The link arms LAa and LAb that connect the second mass body 2 (mass = m2) and the link arm LA2 that connects the second mass body 2 to the base G are drawn with white circles at both ends at two locations in the vibration direction. Spring elements SRa (spring constant = ka), SRb (springs) between the mass parts 1A, 1B of the first mass body 1 and the second mass body 2 and coupled by a rotatable joint without resistance. Constant = kb), and each mass portion 1A, 1B and the second mass body 2 are elastically held in a substantially horizontal direction by the spring element SR2 (spring constant = k0) between the second mass body 2 and the base G. Has been. Although the above structure of FIG. 9 shows an equivalent structure, which differs from the actual configuration, the actual product has a leaf spring (vibration spring) orthogonal to the vibration direction and the horizontal movement of the link arm and the spring element. The work is the same just by giving them together. Note that the spring constant k0 of the spring element SR2 is a much weaker spring constant than the spring constants ka and kb of the spring elements SRa and SRb. It is preferable that the vibration frequency generated by the vibration unit composed of m2 is suppressed to 1/10 or less.

  In the model shown in FIG. 9, if mass parts 1A and 1B are made of a ferromagnetic material such as iron and an alternating voltage is applied to the electromagnets Mga and Mgb fixed to the second mass body 2, they are intermittently provided via a gap. The three masses vibrate with each other. As described with reference to FIGS. 13 to 22, the mass parts 1 </ b> A and 1 </ b> B vibrate up and down in opposite phases as indicated by arrows in FIG. 9 in a free state. Even if the electromagnets Mga and Mgb are driven in the same phase, it is difficult to move in the same phase. Similar to the contents described with reference to FIGS. 7 and 8, pitch vibration is generated in the case of oscillating in the upside down phase, and the link arms LAa and LAb are pushed and pulled in the opposite directions as shown by the arrows in the figure. The force works, and the base G (mounting part) is strongly shaken via the second mass body 2.

  On the other hand, in the model shown in FIG. 10, it passes through the outside of the second mass body 2 or passes through the opening 2n provided in the second mass body 2 as shown in FIG. The mass part 1A and the mass part 1B are mechanically coupled via the connecting part cb or the like. Thereby, mass parts 1A and 1B cannot move in a mutually different direction, and if electromagnets MMa and Mgb are driven in the same phase, the operation can be continued in the same phase. Thereby, the pitching force as described above is not generated. Although vibration due to the reaction occurs in the horizontal direction, transmission to the base G (mounting part) can be cut off almost without problems by the link arms LAa and LAb and the weak spring element SR2. In this case, although not shown in the figure, as described with reference to FIGS. 23 and 24, the force in the horizontal direction (vibration direction) is transmitted, but the mass portion 1A is connected to the mass portion 1A by a connecting structure with reduced rigidity in the vertical direction. It is desirable to bind 1B. Without this, particularly when the amplitude becomes large, a large burden is imposed on the link mechanism (actually, the leaf spring), which causes problems in terms of operating efficiency and life. In addition, of course, the structure like the above-mentioned connection link can be used also in each embodiment shown in FIGS.

  Thus, in the structure in which the upper and lower mass parts 1A and 1B are connected, when driven using only one electromagnet Mga (Mgb) as shown in FIG. 11, the mechanical symmetry is lost, If symmetry is secured by attaching, for example, a weight (not shown) having the same mass as the electromagnet Mga as an appropriate counterweight on the lower side, the symmetry of operation is not impaired. Since attraction driving with an electromagnet acts like a vibration trigger, some imbalance in driving force is not a problem. However, if only one electromagnet Mma is used, the vibration energy is halved, so it is necessary to confirm whether the necessary amplitude value can be secured.

  Various driving forces are conceivable. For example, if a piston ps that reciprocates by air pressure as shown in FIG. 12 is incorporated in a part of the second mass body 2 together with the cylinder cd, this vibration system is similar to the electromagnet. Can be driven. In this case, the required vibration can be obtained by resonance driving or forced driving by switching the air pressure supply direction at a constant frequency by the electromagnetic valve. There is also a free piston type that automatically continues reciprocating motion by simply applying air pressure, so if this is used, a control mechanism becomes unnecessary.

  Next, a description will be given of the most important position of the center of gravity and its adjustment when operating the vibratory transfer device of the symmetrical drive mechanism. When we prototyped various types of the present invention described so far, we were able to confirm that they all demonstrated superior performance compared to conventional machines, but the center of gravity is the key to performance, and adjustment is necessary. It is no exaggeration to say that it is exhausted. Then, next, consider in detail the center of gravity of the symmetrical drive mechanism described with reference to FIGS.

  For example, in the vibration model shown in FIG. 13, the mass part 1A and the mass part 1B of the first mass body 1 have the same mass (m1a = m1b), and the mass part 1A and the mass part 1B as viewed from the second mass body 2. The center of gravity position is symmetrically equidistant from each other, and also in the vibration direction (horizontal direction corresponding to the left-right direction in the figure) and in the width direction (horizontal direction corresponding to the direction orthogonal to the paper surface) This is based on the assumption that the center of gravity is at the center point. Further, the center of gravity of the second mass body 2 exists in a symmetrical position with respect to each of the vibration direction, the width direction, and the vertical direction as shown in the figure (the center of gravity is at the point-symmetrical position in the center of the vertical, horizontal, and height). ), The center-of-gravity position obtained by combining the mass part 1A and the mass part 1B comes to the center point, so that it matches the center-of-gravity position of the second mass body 2. Under such conditions, as described above, the moment arm associated with the vibration becomes zero, and the moment force is completely canceled by the vibrations of the upper and lower mass portions 1A, 1B. Only a reaction force in the horizontal direction is applied to the second mass body 2, and the second mass body 2 vibrates only by this reaction force. This movement can be easily released by the support plates at both ends (anti-vibration springs corresponding to the spring element 4 and having a small rigidity in the vibration direction), so transmission of harmful pitching vibrations to the gantry (base) Can be dramatically reduced.

  The pitching vibration is as described above. However, if the transmission of vibration is viewed from the opposite side, the vibration system of the present invention itself does not generate the rotational moment force accompanying the vibration in the system. As a result, the fixing method to the gantry is not chosen, which means that it operates completely even in a floating state where nothing is fixed extremely. This has been proved in the evaluation test, even if it is placed on a cap roll (packing material with air-filled protrusions) etc. of the packaging material, and on the contrary, even if the base part is firmly fixed directly on the hard concrete floor There is no change in the transport state.

  As described with reference to FIG. 13, for the second mass body 2, each member is arranged symmetrically with respect to the three-dimensional center point of the structure, and a thorough orthogonal shape design is performed. As a result, machining is facilitated and machining accuracy is also improved. Further, as a result, the center of gravity position is also brought to the three-dimensional center point, so that the total center of gravity adjustment and verification are facilitated. However, in view of the principle of the present invention, the position of the center of gravity does not necessarily have to be the center point. FIG. 26A shows the arrangement of each part on the cross section when the mass portions 1A, 1B and the gravity center positions 1ga, 1gb, 2g of the second mass body 2 are arranged on the cross section orthogonal to the vibration direction. It is a schematic diagram which shows. Even when the gravity center positions 1ga and 1gb of the mass part 1A and the mass part 1B of the first mass body 1 are both shifted to the right in the figure, the gravity center position 2g of the second mass body 2 is also shifted there. There is no problem. Further, the line connecting the gravity center positions 1ga and 1gb of the mass portions 1A and 1B of the first mass body 1 is not orthogonal to a horizontal plane P2 (described later) along the vibration direction, as shown in FIG. Even if it intersects diagonally, there is no problem if the center of gravity position 2g of the second mass body 2 exists on the line Lab connecting the center of gravity position 1ga of the mass part 1A and the center of gravity position 1gb of the mass part 1B. Further, there is no problem even when the line Lab is largely tilted to form a horizontal structure in which the mass portion 1A and the gravity center positions 1ga and 1gb of the mass portion 1B are arranged in the width direction (horizontal direction orthogonal to the vibration direction). .

  On the other hand, as shown in FIG. 26 (c), the gravity center positions 1ga and 1gb of the mass part 1A and the mass part 1B may not necessarily be equidistant from the gravity center position 2g of the second mass body 2. . The position of the center of gravity where the mass part 1A and the mass part 1B of different masses are combined is on the line connecting the center of gravity points 1ga and 1gb of each mass part, and at a position prorated in inverse proportion to the masses m1a and m1b of each mass part. Since there is a center of gravity position 2g of the second mass body 2 there is no problem. That is, when Sa is the distance between the centroid positions 1ga and 2g and Sb is the distance between the centroid positions 1gb and 2g, if m1a × Sa = m1b × Sb, that is, m1a / m2b = Sb / Sa, the above is equivalent. Situation.

  Furthermore, since the actual object is a three-dimensional object, it is not sufficient to consider the two-dimensional center of gravity position on the cross section perpendicular to the vibration direction shown in FIGS. . In addition to the two-dimensional arrangement shown in FIG. 26, a three-dimensional model as shown in FIG. 25 is required in consideration of the positional relationship in the direction (vibration direction) orthogonal to the drawing sheet. FIG. 25 is a perspective view showing the positional relationship of the center of gravity of each mass body with reference to a plane Px and a plane P2 that are both parallel to the vibration direction and orthogonal to each other. Here, with reference to FIG. 26, in the above-described argument describing the relationship between the gravity center positions 1ga, 1gb, and 2g on the cross section orthogonal to the vibration direction, the center point in this vibration direction (horizontal direction in FIG. 13) passes. The center of gravity position 2g of the second mass body 2 is assumed to be located on the cross section. However, since each mass part 1A, 1B and the second mass body 2 actually vibrate in the vibration direction, their center of gravity position 1ga. , 1gb, 2 also move in the vibration direction. However, as long as it oscillates horizontally with a small amplitude, it will be the same according to the laws of mechanics (the action position of the force is the same from anywhere on the action line), so each of the mass parts 1A, 1B and the second mass body The deviation of the center-of-gravity positions 1ga, 1gb, and 2g in the vibration direction due to the vibration of 2 is allowable. However, in the case of an actual object that is restrained by a leaf spring and caused to vibrate substantially horizontally, a moment force is generated although it is slight as described in the previous principle.

  However, the center of gravity positions 1ga, 1gb, and 2g of the mass portions 1A and 1B and the second mass body 2 at rest or in the neutral position are not in the vibration direction, but are not shifted in the center of gravity due to vibration as described above. Even when they are deviated from each other, a relationship in which the entire moment is canceled may be established. That is, considering the combination of the three-dimensional center of gravity position and considering the model shown in FIG. 25, first, “a plane that passes through the center of gravity position 2g of the second mass body 2 and is parallel to the vibration direction and is horizontal. When (or a plane perpendicular to the thickness direction when the second mass body 2 is plate-like) is defined as the plane P2, the second mass body 2 that is also “parallel to the vibration direction and parallel to the vibration direction” is defined on the plane P2. The line passing through the center of gravity position 2g of FIG. When considering a plane Px that includes the line L2 and intersects the plane P2 (that is, intersects the plane P2 at the line L2), the mass parts 1A and 1B of the first mass 1 are included in the plane Px. The centroid positions 1ga and 1gb and the centroid position 2g of the second mass body 2 are all included so as to satisfy the condition. At this time, as shown in FIG. 26A, the surface P1a that is parallel to the surface P2 and passes through the gravity center position 1ga of the mass part 1A and the surface P2 that is parallel to the surface P2 and the gravity center position of the mass part 1B. Considering the surface P1b passing through 1 gb, as described above, the distance Sa between the surface P2 and the surface P1a, the distance Sb between the surface P2 and the surface P1b, and the relationship in which the surface Px is orthogonal to the surface P2 are practical. Is easy to adjust and is desirable. However, considering the enlargement similarly to the case shown in FIG. 26B, in principle, the intersection angle between the plane Px and the plane P2 is not limited to 90 degrees (when orthogonal), but 180 degrees. Any angle including degrees is acceptable. Furthermore, as shown in FIG. 26 (c), the relationship between the mass ratio of the mass parts 1A and 1B and the ratio of the distance Sa and the distance Sb is maintained, and the synthesized gravity center of the mass parts 1A and 1B is maintained. This means that the point only needs to be on the line L2.

  In the scene of FIG. 25, not only when all the gravity center positions are arranged on the cross section orthogonal to the vibration direction shown in FIG. 26, the gravity center positions 1ga and 1gb of the mass parts 1A and 1B are located at different positions in the vibration direction. It doesn't matter. At this time, the center of gravity position of the entire first mass body 1 (the center of gravity position 1g obtained by combining the center of gravity positions 1ga and 1gb) and the center of gravity position 2g of the second mass body 2 during the vibration operation of the vibration unit are If it is configured to be arranged together on a straight line along the direction, the reaction force in the vibration direction generated between the first mass body 1 and the second mass body 2 is reduced, and the conveyance path Variations in the vibration direction along are also reduced. This point is only a relationship between the first mass body 1 and the second mass body 2, but the second mass body 2 is connected to the mass part 1A of the first mass body 1 as described below. The relationship in which the moment force received from 1B is canceled is established as follows even when the gravity center position 1ga of the mass part 1A and the gravity center position 1gb of the mass part 1B are arranged at different positions in the vibration direction. There is a case.

  On the other hand, as shown in FIG. 27, considering the case where the movable part A is elastically supported so as to be swingable in the vibration direction at two locations in the vibration direction with respect to the base part B, this elastic support structure is a parallel link. And a support structure having spring elements connected in the vibration direction. In this case, as shown in FIG. 27 (a), when the center of gravity position ga of the movable part A is at the center point between the two connected portions before and after the vibration direction, the moment arm MA is short and has a vertical posture. As shown in FIG. 27 (b), when the center of gravity position ga ′ of the movable part A ′ deviates from the center point in the vibration direction, the moment arm MA ′ becomes a long slanted posture. In particular, as shown in FIG. When the center of gravity position ga ′ is disposed outside, the length and inclination of the moment arm MA ′ further increase.

Applying the above points to the vibration model of the present invention, as shown in FIG. 28 (a), in the mass part 1A and the mass part 1B of the first mass body arranged above and below the second mass body 2, Consider a case where the center of gravity position 1ga of the mass part 1A and the center of gravity position 1gb of the mass part 1B are different from each other in the vibration direction. In this case, the moment arm MAa of the mass part 1A and the moment arm MAb of the mass part 1B have different lengths and inclination angles. For this reason, it seems that the moment force during vibration is not canceled by the difference between the two moment arms MAa and MAb. There is a case. That is, the lengths of the moment arms MAa and MAb shown in FIG. 28B are r (ra and rb), the inclination angles of the moment arms MAa and MAb are θ (θa and θb), the mass parts 1A, 1B and the second When the distance between the mass bodies 2 is S (Sa and Sb), the moment force is the length of the moment arm r = S / sin θ (S is the mutual mass between the mass parts 1A and 1B and the second mass body 2). Distance) and the rotational force component Fr = Fsinθ (F is the acting force F on the center of gravity position F = mxω ² ). At this time, the component force Fr in the rotation direction decreases because the inclination angle θ decreases as the center of gravity positions 1ga and 1gb move away from the rotation center, but the length r increases conversely, so the moment force S × F is the moment arm. Therefore, even when the center of gravity positions 1ga and 1gb move to different positions in the vibration direction, the relationship between the moment forces of the moment arms MAa and MAb does not change, and ra · Fsinθa = Rb · Fsinθb and the moment forces of the mass parts 1A and 1B may be offset. However, this is based on the premise that the vibration is completely in the horizontal direction and actually does not always follow the theory. Therefore, in reality, it is safer not to increase the displacement of the center of gravity in this vibration direction. .

  In the above description, the results of various considerations have been described for the case where the moment forces generated by the mass parts 1A and 1B are completely cancelled. However, the relationship between the mass of each mass part 1A and the mass of 1B, and the distance Sa Even when the relationship between Sb and the relationship between the moment arm angles θa and θb does not strictly satisfy the conditions, the rotational moment is not completely canceled out. However, in the basic configuration shown in FIG. As a result, it is clear that the pitching operation is reduced as compared with the conventional structure, which is an operational effect of the basic configuration of the vibration system or the vibration unit according to the present invention.

[Example 1]
Next, various examples whose performance has been confirmed by trial manufacture and experiment will be sequentially described. The following embodiments are all based on the above-described principle model, and the basic configuration and the operational effects are the same, so that they are omitted, and only the main part and the specific structure will be described.

  Initially, Example 1 which shows a structural example is demonstrated based on FIG. FIG. 29 shows a side view of the first embodiment and a projection view along the center axis Xo (axis along the vibration direction passing through the center of gravity of the entire vibration unit) of the vibration unit of the side view. The vibration system of the present embodiment corresponds to the first type of vibration model shown in FIG. 14, and includes the mass parts 1A and 1B of the first mass body 1, the second mass body 2, and the vibration direction. A vibration spring 3A that elastically connects the mass portion 1A and the second mass body 2 at two locations (left and right in the drawing), and a vibration spring that elastically connects the mass portion 1B and the second mass body 2 at two locations in the vibration direction. And a vibration unit having 3B. In addition to the vibration unit, the entire vibration system of the present embodiment includes support springs 4 that elastically support the second mass body 2 on the gantry 10 at two locations in the vibration direction. As explained in the section of the principle, in this embodiment, two connecting bodies cb (two-dot chain lines in the figure) composed of side plates are provided on both sides of the mass portions 1A and 1B of the first mass body arranged vertically. The upper and lower mass portions 1A and 1B are fixed by screwing or the like so that they do not move freely. However, the connecting structure has a shape with reduced rigidity so as to allow slight vertical movement. The shape of the connecting body cb includes the first connecting portion cbA and the second connecting portion cbB similar to those in FIG. 24B, but unlike FIG. 24B, the central opening cbS ′ is provided in the elastic connecting portion therebetween. This facilitates elastic deformation in the vertical direction. Of course, the one shown in FIGS. 24 (a) to 24 (c) and the above-described connecting link can also be used. This is the same in other embodiments. As a result, the upper and lower mass portions 1A and 1B are constrained in the vibration direction, so that they can be operated at the same phase and the same frequency, and the fluctuations in the vertical motion associated with the amplitude can be received.

  Since the conveyance part tp provided with the conveyance path can be mounted on the upper part of the mass part 1A of the first mass body, the mass part 1A is actually configured including the conveyance part tp. On the other hand, since the counterweight cw can be attached to the lower surface of the mass portion 1B with a screw or the like, the mass portion 1B including the counterweight is configured similarly to the above. Furthermore, since the transport part tp and the counterweight cw are coupled by the connecting part cb which is a side plate, the transport part tp vibrates as an integrated first mass body 1. It is also possible to adjust the mass and the center of gravity by adding or removing the adjustment weights cw1, cw2, etc. to the counterweight cw.

  Next, the second mass body 2 is an integrated solid lump and is made of a material such as cast steel. Although the second mass body 2 may basically be configured in a rectangular shape, in this embodiment, the second mass body 2 has a portion 2A projecting to the mass portion 1A side and a portion 2B projecting to the mass portion 1B side. . Also, at two locations in the vibration direction of the second mass body 2 (both ends before and after the vibration direction in the illustrated example), piezoelectric elements of the vibration springs 3A and 3B (piezoelectric elements are pasted on both sides of a thick steel substrate). The piezoelectric driving bodies 3Ad and 3Bd constituting the weared parts are fixed by screwing or the like. Since the piezoelectric drive unit of the present embodiment has a completely vertical symmetrical structure with respect to the central axis Xo, the piezoelectric drive bodies 3Ad and 3Bd on both sides of the second mass body 2 have a total of four piezoelectric elements. If a bimorph type element is adopted for the piezoelectric driving body, the number of elements is eight because it is attached to both sides of the substrate. Amplifying springs 3As and 3Bs are fixed to the opposite ends of the piezoelectric driving bodies 3Ad and 3Bd with two bolts or the like via a presser plate and a plate nut. Further, the other ends of the amplification springs 3As and 3Bs are fixed to the mass portions 1A and 1B of the first mass body, respectively. As described above, the four connecting portions of the mass parts 1A, 1B and the second mass body 2 are arranged at point-symmetrical positions around the center point (center of gravity) of the upper, lower, left and right sides of the second mass body 2, By connecting the first mass body 1 and the second mass body 2 at the connection point, the vibration unit of the present embodiment is configured as a whole.

  The vibration unit of the present embodiment is connected and fixed to the upper ends of the support springs 4 and 4 on both sides via a connection structure 13 having both ends in the direction along the central axis Xo of the second mass body 2 made of a connection fitting or the like. The other lower ends of the support springs 4 and 4 are installed in a state where they are connected and fixed to the gantry 10. The gantry 10 is attached to a floor surface or a separate base to constitute a base G. Here, the board | substrate G can take various structures, such as the floor surface of a factory itself, the mounting stand installed on a floor surface, and the vibration isolator installed on a floor surface. This point is the same in any embodiment. In the present embodiment, the first mass body 1 (mass portions 1A and 1B), the second mass body 2, two vibration springs 3 (3A and 3B) at the front and rear in the vibration direction, and the vibration direction The entire vibration system including the support springs 4 at the front and rear portions is installed so as to incline obliquely to the upper right side in the figure with respect to the conveyance path provided in the gantry 10 and the conveyance unit tp. Since the conveyance path vibrates so as to be pushed up diagonally to the upper right, conveyance objects such as parts (not shown) arranged on the conveyance path are conveyed to the right side in the figure.

  Next, the operation of this embodiment will be described. The piezoelectric element expands or contracts depending on the direction in which the voltage is applied. The piezoelectric elements pasted on both sides of the steel plates of the piezoelectric drive units 3Ad and 3Bd are driven by applying a voltage so that when one side expands, the other side contracts. Therefore, the polarity of the piezoelectric element needs to be attached so that it can be realized in actual driving. In this symmetric drive mechanism, for example, when the right piezoelectric element expands in the right vibration spring 3A in the figure, the right piezoelectric element of the left vibration spring 3A in the figure must be driven with the same polarity so that it also expands. Don't be. At this time, the piezoelectric drive mode must be aligned for the lower vibration spring 3B in the same manner as described above. That is, with respect to the left-right direction in FIG. 29, the right piezoelectric element must expand at the same time in the upper, lower, left and right vibration springs 3A, 3B, and at the same time the left piezoelectric element must contract at the same time.

  Since the piezoelectric driving units 3Ad and 3Bd are made of thick steel plates, the bending rigidity is very large, so that a large amount of bending cannot be expected despite the strong expansion / contraction force by the piezoelectric element. In view of this, in a vibration device using piezoelectric drive, a necessary amplitude is obtained by interposing a thin steel plate spring plate called an amplification spring. Also in this embodiment, the four amplification springs 3As and 3Bs are interposed between the first mass body 1 and the second mass body 2 to increase the amplitude.

  Next, the second mass body 2 is connected to the gantry 10 by the support springs 4 and 4 on both sides via the connection structure 13, but the support spring 4 is made of a relatively thin steel plate or the like. The rigidity is weak against displacement in the (horizontal) direction. Therefore, as described above, the transmission of the horizontal vibration to the base G due to the reaction is also effectively blocked in the principle section.

  As described above, the position of the center of gravity is important in the vibration system of the present invention, but in this embodiment, various ideas are made so that the center of gravity position can be easily adjusted and confirmed. As shown in FIG. 29, in the illustrated example, the connection structure 13 is a structure that sandwiches the central portions of the piezoelectric drive bodies 3Ad and 3Bd and is fixed to the second mass body 2 and simultaneously coupled to the support spring 4. Is shown in FIG. FIG. 30 shows the connection structure 13 on the left side of FIG. 29 together with the vibration unit fixing mechanism 15. The connection structure 13 is fixed to the second mass body 2 with a bolt or the like, and the first connection member 13a shown in FIG. 31 is fixed with the support spring 4 held between the first connection member 13a with a bolt or the like. And the second connecting member 13b shown in FIG. Here, a V-shaped groove 13a1 is formed on the side surface of the first connecting member 13a.

  The method for checking the center of gravity is as follows, for example. As shown in FIG. 32, two sharp pins PN fixed on a common support plate SB are prepared in advance at an interval substantially equal to the pitch between the groove portions 13a1 of the left and right first connection members 13a in FIG. Keep it. In FIG. 32, only the first connection member 13a and the pin PN are shown. And in the state which fixed the conveyance part tp provided with the conveyance path to the mass part 1A of the 1st mass body 1, after releasing the connection structure 13 and separating the support spring 4, the vibration unit is laid horizontally, and the pin The vibration unit is supported by the two pins PN so that the PN engages with the groove 13a1. While observing the balance in this supported state, the counterweight cw is increased or decreased so that the entire vibration unit is substantially horizontal. In the present embodiment, the second mass body 2 is a solid lump and is designed symmetrically on the central axis Xo of the vibration unit shown in FIG. 29, so that the center of gravity is the thickness direction of the first connecting member 13a. On the center line, that is, on the groove 13a1. Therefore, if the center of gravity adjustment and check are performed as described above, the center of gravity position of the mass portion 1A and the mass portion 1B of the first mass body 1 is on the same line as the center of gravity position of the second mass body 2. Thus, as described above, the condition of the center of gravity of the two mass portions 1A and 1B is satisfied, so that no pitching occurs, and as a result, no harmful vertical movement is transmitted to the gantry 10. Not limited to this embodiment, the combination of the illustrated examples is reversed, that is, the connecting member provided in the connection structure 13 on both sides is provided with a sharp protrusion, and the protrusion is placed on an appropriate flat plate so that the protrusion is a fulcrum of the balance. You can also check the center of gravity like this.

  As described above, the support spring 4 is made to have a relatively weak spring constant so that the natural frequency of the entire vibration system by the vibration unit and the two support springs 4 becomes 1/10 or less of the operation frequency of the vibration unit. For example, the vibration unit can be configured to vibrate the first mass body 1 and the second mass body 2 in the horizontal direction without resistance and to block the vibration. However, on the other hand, the support spring 4 needs to be firmly supported by the gantry 10 with a strong holding force so that the vibration unit does not wobble in the plane viewed from above. Therefore, as shown in the projection view of FIG. 29, the effective spring constant is reduced by hollowing out the central portion of the plate surface of the support spring 4 to provide the opening 4a. On the other hand, in order to prevent buckling at the center of the span due to a decrease in strength, the sides 4b on both sides are bent to increase the apparent rigidity, that is, the rigidity in the support direction (vertical direction).

  In such a configuration, even if there is no problem during normal operation, if a force is applied in the left-right direction in FIG. 29 during transportation or adjustment, the displacement becomes excessive, causing interference at the connection with peripheral devices or the like, or the support spring 4 It may be permanently deformed. Therefore, as shown in FIG. 30, during transportation, the second mass body 2 is fixed by the vibration unit fixing mechanism 15 using the bolts 15 b and 15 c attached to the column 15 a fixed to the gantry 10. That is, if the column 15a is fastened to the second connecting member 13b by the bolt 15b using a screw hole provided on the outer surface side of the second connecting member (pressing plate) 13b, the vibration unit is fixed. During operation, the bolt 15b is removed, the gap Z between the bolt 15c and the second connecting member 13b is adjusted to a value slightly plus the vibration amplitude during operation, and the bolt 15c is fixed with the illustrated set nut. In FIG. 30, the gap Z in the operating state is shown. However, when the bolt 15b is tightened and fixed as shown in the drawing, the entire vibration unit is drawn toward the support column 15a and the gap Z disappears. Configured as follows.

[Example 2]
Next, Example 2 will be described with reference to FIG. In the present embodiment, parts common to the first embodiment have the same names. The present embodiment is based on the second type of vibration model shown in FIG. 18, and portions corresponding to those in FIG. 18 are denoted by corresponding reference numerals as in the first embodiment. As described above, in this embodiment, the mass portions 1A and 1B of the first mass body 1 arranged on the upper and lower sides are so-called reaction mass bodies. Here, the mass portions 1A and 1B have an integral structure and are provided with a connecting portion 1s having a shape whose rigidity is lowered to allow a slight vertical displacement. In this embodiment, since it is necessary to form the slits 1a and 1b for forming the connecting portion 1s, it is designed on the assumption of, for example, wire cutting, but the present invention is not limited to this, and FIG. By using the connecting member 1s as shown, it is possible to assemble with normal parts. Since the mass parts 1A and 1B of the first mass body 1 are constrained in the direction of vibration by this connecting part 1s, the distance in the vertical direction between the mass parts 1A and 1B can be operated in the same phase and is associated with the amplitude. Variations can be passed.

  The main body of the second mass body 2 is an integrally molded article made of, for example, aluminum die-casting or the like having a substantially “B” -shaped frame shape as viewed from the side that makes one round in the vibration direction. Here, the left and right central ends 2c between the upper part 2a and the lower part 2b are coupled to the amplification springs 3As and 3Bs constituting the vibration springs 3A and 3B. As shown in FIG. 34 (c), the second mass body 2 is integrally formed by fixing the upper transport portion tp to the upper portion 2a of the main body and fixing the lower counterweights cw and cw 'to the lower portion 2b. It has become. Further, the second mass body 2 is also covered with a side plate 2s made of, for example, stainless steel having high strength, which also serves as a reinforcing material and a cover for improving the overall rigidity. The entirety of the second mass body 2 configured as described above and the reaction mass body obtained by combining the mass portions 1A and 1B of the first mass body 1 are complementary (in harmony with each other in opposite directions). ) Vibrate and operate as a symmetric drive linear feeder.

  The method of aligning the center of gravity is substantially the same as in the first embodiment, but in this embodiment, the center of gravity can be rotated around the mounting base ao mounted on the left side of the lower portion 2b of the second mass body 2 in the drawing. And a center of gravity adjustment mechanism 17 having a center of gravity adjusting counterweight cw ″ fixed to the right end of the rotation mounting plate am in the drawing. As shown in FIG. 34 (d), a pair of rotational mounting plates am is attached to the lower part 2b around the mounting base ao, and the center of gravity is a cylindrical weight between the tips of the pair of rotational mounting plates am. Counter weight cw "is fixed. The rotation mounting plate am is configured so as to be able to swivel up and down steplessly around the mounting base ao with respect to the lower part 2b within a predetermined range by a combination of the arc-shaped elongated hole ap and a bolt. The center of gravity can be easily adjusted.

  As shown in FIG. 34 (a), support springs 4 are respectively attached to the front and rear outer sides in the vibration direction of the central end 2c of the frame-shaped part of the second mass body 2 formed by die-casting aluminum. Similarly, the second mass body 2 is coupled to the gantry 10 by support springs 4 at two locations in the vibration direction. The vibration unit fixing mechanism 15 provided on the gantry 10 is the same as that of the first embodiment.

  This example is superior to Example 1 in that the overall height can be kept low, and the position of the center of gravity can be adjusted more accurately and easily, resulting in an ideal operation with very little vibration leakage. It has the advantage that it can be done.

[Example 3]
Next, Example 3 will be described with reference to FIGS. Parts having the same functions as those in the first and second embodiments have the same names. Since the present embodiment is based on the same principle as the second embodiment, the description of the same contents is omitted. As shown in FIGS. 35 and 36, in the second mass body 2 of the present embodiment, there is no square-shaped frame in a side view as in the second embodiment, and the two mass bodies 2 are respectively provided at two front and rear positions in the vibration direction. A side plate portion 2s (two-dot chain line in the figure) is coupled to the side surface of the plate-shaped main body portion 2a from both sides with a total of four bolts or the like, and a transport portion tp provided with a transport path by an upper mounting plate ts at the upper end of the side plate portion 2s. Is fixed. Further, the counterweight cw is attached and fixed by the lower mounting plate cs at the lower end of the side plate portion 2s. Reinforcing plates 2t (two-dot chain lines in the figure) for connecting the two main body portions 2a in the vibration direction are attached to both outer sides of the side plate portion 2s.

  Here, as shown in FIG. 36, the mounting portion 2b is fixed with bolts or the like before and after the vibration direction of the main body portion 2a, and a portion corresponding to the amplification spring 3As and 3Bs between the main body portion 2a and the mounting portion 2b. The vertically central part of the vertically symmetrical leaf spring body integrally provided with corresponding parts is fixed in a sandwiched manner. The leaf spring body is formed by integrating a portion corresponding to the amplification spring 3As and a portion corresponding to 3Bs. However, the leaf spring body is substantially the same as a separate body. However, this configuration is advantageous in that the structure can be simplified and the assembly work can be facilitated. Such a configuration can be similarly adopted in other embodiments as long as the amplifying spring is arranged on the center side of the vibration springs 3A and 3B as in this embodiment. In contrast to the present embodiment, if the piezoelectric driving body is arranged on the center side of the vibration springs 3A and 3B, the substrates of the piezoelectric driving bodies on both the upper and lower sides are integrated and the center in the vertical direction is fixed. It is possible to adopt the configuration to be similar to the above.

  Further, support springs 4 and 4 are connected to the mounting portion 2b from the front and rear outside in the vibration direction by bolts or the like. The lower ends of these support springs 4 are coupled to the gantry 10. The gantry 10 is configured in a U shape in plan view (when viewed from above), and a back plate 10a disposed behind the vibration unit in FIG. 35A and both left and right ends of the back plate 10a shown in the figure. Mounting end portions 10b and 10b protruding from the front side in the figure, and the lower ends of the support springs 4 are fixed to these mounting end portions 10b.

  In the present embodiment, the main body portion 2a, the side plate portion 2s, the mounting portion 2b, the upper mounting plate ts and the transport portion tp, the lower mounting plate cs and the counterweight cw are all integrated to form the second mass body 2. doing. The transport portion tp is mounted on the upper surface of the upper mounting plate ts. As shown in FIG. 35, the upper mounting plate ts is fastened to the mounting holes of the side plate portions 2s on both sides with three bolts. Here, except for the central mounting hole aoa of the side plate portion 2s for fixing the upper mounting plate ts, the left and right mounting holes apa are elongated holes extending in the vertical direction, so the side plate portion 2s. Since the inclination of the transport part tp relative to the central axis Xo can be adjusted within a predetermined angle (± 2 ° in the vertical direction in the embodiment), the mounting posture of the transport part tp with respect to the vibration unit can be set appropriately. Yes. Such an attachment posture adjusting means of the transport unit can be applied to other embodiments. The lower mounting plate cs is fastened to the mounting holes aob and apb of the side plate portion 2s with three bolts or the like. Here, since the mounting holes apb on both the left and right sides as well as the central mounting hole aob are elongated holes extending in the vertical direction, the mounting posture (angle) in the vertical direction with respect to the central axis Xo of the counterweight cw is adjusted. In addition, the vertical position of the entire counterweight cw can be adjusted.

  On the other hand, with respect to the first mass body 1, as shown in FIG. 37, mass portions 1A and 1B are integrally formed, and a connecting portion 1s constituted by slits 1a and 1b is formed at the upper and lower center positions. Since it is the same as that of the second embodiment, the description thereof is omitted.

  As shown in FIG. 35, in the installation structure of the present embodiment, a gantry 10 that elastically supports the vibration unit via a support spring 4 and a vertical plate-like column portion 11 to which a back surface portion 10a of the gantry 10 is attached. And a base part 12 provided with. In the case of the illustrated example, the gantry 10 is supported by the base portion 12 so as to protrude to the front side in the figure. Three mounting holes 11a arranged along the vibration direction are formed in the support column 11, and these mounting holes 11a are each formed as an elongated hole in the vertical direction, so that the gantry 10 with respect to the base 12 can be The mounting position is configured to be movable up and down, and the mounting angle with respect to the vibration direction (center axis Xo) of the gantry 10 is configured to be adjustable. Thereby, the installation posture of the vibration unit, that is, the angle of the central axis Xo with respect to the horizontal direction can be adjusted. Further, similarly to the fourth embodiment described later, the gantry 10 may be mounted on the support column 11, and the angle of the installation posture of the vibration unit may be adjusted by adjusting the mounting position of the gantry 10 and the support column 11. Such a vibration unit installation posture adjusting means can be applied to other embodiments.

  Since the vibration direction of the second mass body 2 is a direction (direction along the central axis Xo) orthogonal to the vibration springs 3A and 3B including the piezoelectric drive portions 3Ad and 3Bd and the amplification springs 3As and 3Bs, it is the transport portion tp. The vibration angle of the transport path is an original design angle (for example, 5 °) when the mounting angle of the transport portion tp is 0 °. Here, if both the mounting attitude adjusting means and the installation attitude adjusting means are provided, the vibration unit (center axis line Xo) is adjusted using the installation attitude adjusting means, and then the vibration unit is adjusted. Regardless of the installation angle, it is possible to horizontally install the conveyance path by adjusting the attachment angle of the conveyance unit tp using the above-described attachment posture adjusting means. Thereby, the vibration angle (projection angle φ described later) of the conveyance path can be changed in accordance with the adjustment angle range of both adjustment means. In the case of the present embodiment, the mounting angle can be adjusted within a range of ± 2 ° by the mounting posture adjusting means. Therefore, if the original design angle is 5 °, the vibration angle is adjusted within a range of 3 ° to 7 °. it can. These configurations can also be applied to other embodiments.

[Example 4]
Next, Example 4 will be described with reference to FIGS. The fourth embodiment is devised as another version (modification) of the third embodiment. In principle, it is the same as in the second and third embodiments, but there is no frame or side plate for attaching the conveyance path and the counterweight, and as shown in FIGS. 38 and 39, the main body of the second mass body 2 is It has a square-shaped main body block 2h arranged at the center and a pair of side blocks 2i attached to both sides in the width direction of the main body block 2h, and directly to the pair of side blocks 2i. It has a structure in which a transport part tp having a transport path and a counterweight cw are attached to opposite sides. Also in the present embodiment, the attachment angle of the transport part tp is configured to be variable with respect to the main body of the second mass body 2. As shown in FIG. 40 (a), the transport portion tp is integrated with the lower mounting portion ts, and among the three mounting holes provided in the mounting portion ts, the mounting holes sa on both sides are replaced with the central mounting holes so. Since it is constituted by a long hole extending in the up-down direction in a circular arc shape as the center, the mounting angle of the transport part tp can be adjusted with respect to the main body of the second mass body 2.

  In the present embodiment, as in the third embodiment, as shown in FIG. 39, the back surface of the gantry 10 to which the lower end of the support spring 4 connected to the second mass body 2 is attached is attached to the column portion 11. A support column 11 is provided on the base 12. Therefore, the vibration unit of the present embodiment is supported so as to project to the side of the support column 11. Similarly to the third embodiment, the gantry 10 is coupled to a column portion 11 having a long hole-like attachment hole via bolts or the like through three screw holes provided on the back surface. Thus, the angle between the gantry 10 and the column 11 can be adjusted and the height can be adjusted. As a result, the installation posture of the vibration unit, that is, the angle of the central axis Xo with respect to the horizontal direction can be adjusted. It is like that.

  On the other hand, the counterweight cw is attached to the opposite side of the transport part tp when viewed in the width direction. And it is comprised so that the center of gravity of the 2nd mass body 2 which combined the conveyance part tp and the counterweight cw may be balanced so that it may become symmetrical with respect to the vertical centerline shown in FIG. Otherwise, when looking down from above, a turning motion (yawing) occurs. However, in the case of the present embodiment, since the transport part tp (counterweight cw) is located on the side of the main body of the second mass body 2, the upper and lower sides of the vibration unit are arranged at the center of gravity in the vertical direction. The need for adjustment weights to balance the direction is low.

  In the present embodiment, the height of the entire apparatus can be suppressed because the installation position of the transport section tp is low, and a complicated support structure that connects the transport section tp and the counterweight cw as in the previous embodiments is unnecessary. Therefore, the whole structure is simple and lightweight. Furthermore, since the conveyance part tp can be installed in the vicinity of the amplification springs 3As and 3Bs, it is advantageous that the second mass body 2 can be configured to have high rigidity as a whole. Further, since the mounting angle between the transport unit tp and the counterweight cw is adjustable as in the third embodiment, the mounting angle can be applied in the opposite direction to the illustrated mounting example across the horizontal. In that case, since the moving direction of the parts is opposite to the example shown in FIG. 40, it is possible to set the conveying direction to both directions with one unit, and it is necessary to have extra stock by arbitrarily handling the conveying direction. Disappears.

  Since the vibration direction of the second mass body 2 is a direction orthogonal to the piezoelectric drive units 3Ad, 3Bd and the amplification springs 3As, 3Bs, the angle of the vibration direction of the conveyance path (projection angle) is determined by the attachment angle of the conveyance path. The angle of 0 ° is an angle (for example, 5 °) set at the time of original design. In addition, since three vertical holes are provided in the support column 11, the gantry 10 can adjust the angle and the vertical position of the entire vibration unit. Therefore, the vibration angle (projection angle) with respect to the horizontal of the conveyance path is adjusted steplessly in the range of 3 ° to 7 ° by setting the conveyance path inclined by adjusting the angle with respect to the vibration unit horizontally (returning). Can do. Note that the mounting posture adjusting means of the transport unit tp and the installation posture adjusting means of the vibration unit of the present embodiment can be similarly applied to other examples.

  Here, the projection angle (also referred to as the throw-up angle) will be briefly described. As shown in FIG. 43A, an angle indicating the direction of vibration with respect to the horizontal plane of the transport path tw of the transport unit tp is called a projection angle φ. Since the projection angle φ is a direction orthogonal to the vibration spring (amplification spring) as described above, this direction is eventually given by the mounting angle of the vibration unit. Depending on the projection angle φ, the state of conveyance of the vibration transporter varies greatly. Practically, it can range from about 5 ° to 30 °, but generally, as shown in FIGS. 43B and 43C, the smaller the projection angle φ, the smoother the object to be conveyed (parts). On the contrary, as the projection angle φ increases, the conveyance state is disturbed and the movement progresses roughly while dancing up and down. The optimum value of the projection angle φ varies depending on the combination of the surface of the transport path tw, the physical properties of the transported object (especially the elastic modulus and friction coefficient), and the vibration frequency, but the mere transport efficiency (transport distance per unit amplitude) is 10 °. The neighborhood is the most efficient. The lower the projection angle φ seems to be ideal, but if the conveyance path tw itself has an ascending gradient, the conveyance ability (propulsion force) is lost as soon as possible. In addition, when the projection angle φ at the time of design is set to a small value, in the conventional linear feeder, due to the variation of the vibration angle according to the position in the transport direction caused by the vibration mode, in practice, at the specific position in the transport direction. A portion where the projection angle φ is less than 0 ° occurs, and as a result, the conveyed object may stop or be reversely fed.

  In the symmetrical drive system of the present invention, the pitching operation of the vibration system can be reduced, so that the variation of the vibration angle over the entire length of the conveyance path tw can be minimized, and in the linear vibration type conveyance device, as in the bowl feeder Because there is almost no ascending slope, it can be put to practical use aiming at a drastic low projection angle φ. However, in the extremely low projection angle φ region around 5 °, the allowable angle range of the projection angle φ varies greatly depending on the surface condition of the conveyance path, the combination of part shape and material, the operating frequency, etc. To do. Under such severe usage conditions, a fine adjustment or selection of 1 ° or less is required to obtain the optimum setting value of the projection angle φ. Therefore, the mechanism that can finely adjust the projection angle φ steplessly as in this embodiment. Is very effective and useful.

[Example 5]
Next, Example 5 is shown in FIG.41 and FIG.42. This is the various electromagnetic examples described with reference to FIGS. 9 to 11, and corresponds to FIG. 11 in the overall configuration. However, the necessary spring constant is given at the same time that the vibration direction angle is given by a leaf spring instead of the link mechanism. The mass parts 1A and 1B constituting the first mass body 1 are coupled to each other at the center in the vertical direction by a connecting part 1s having reduced vertical rigidity in the same manner as in Examples 2 to 4. In this embodiment, although it is a piezoelectric vibration system, the structure of the vibration unit is the same except for the vibration model type and drive type shown in FIG. In the present embodiment, the movable iron core mg1 is attached to a horizontal bar sm that penetrates the leaf springs constituting the vibration springs 3A and 3B and protrudes to the side of the mass part 1B on either outer side of the vibration direction as a drive source. The electromagnet mg2 is provided on the side facing this.

  In the present embodiment, as shown in FIG. 42, a large number of leaf springs are stacked on both front and rear sides in the vibration direction of the main body 2j made of a square-shaped frame member in a plan view constituting the second mass body 2. A spring structure corresponding to the configured vibration springs 3A and 3B is fixed with two bolts. This spring structure has a vertically symmetrical shape with respect to the connecting portion between the mass portions 1A and 1B of the first mass body. Side plate portions 2s are fixed to both sides of the main body portion 2j by screwing together with the reinforcing plate 2p. The side plate portion 2s extends long to the right, and is fixed with an upper mounting plate ts and a lower mounting block mgs shown in FIG. 41 sandwiched from both sides. Further, as shown in FIG. 42, the main body block 2j has an opening 2jp in the center, and the mass parts 1A and 1B are connected through the opening 2jp through a connecting part 1s extending in the vibration direction. Yes.

  The transport part tp is mounted and fixed on the upper mounting plate ts, and the electromagnet mg2 is mounted and fixed on the lower mounting block mgs. A counterweight cw for balancing the center of gravity is attached to the lower surface of the lower attachment block mgs. As shown in FIG. 41, the upper end of the support spring 4 is connected to one side in the vibration direction of the main body 2j of the second mass body 2 via a mounting portion 2k. The main body 2j is fixed to the lower mounting block mgs via the side plate 2s, and the lower mounting block mgs is connected and fixed to the upper end of the other support spring 4 in the vibration direction. The lower ends of the support springs 4 before and after these vibration directions are connected and fixed to the gantry 10.

  The main body portion 2j, the side plate portion 2s, the reinforcing plate 2p, the upper mounting plate ts, the transport portion tp, the lower mounting block mgs, and the counterweight cw together constitute the second mass body 2, and the first mass A vibration unit of a two-degree-of-freedom vibration system is configured in combination with a reaction mass body in which the mass portions 1A, 1B and the connecting portion 1s constituting the body 1 are set. When an AC voltage having a frequency close to the natural frequency of the vibration unit composed of the first mass body 1, the second mass body 2, and the vibration springs 3A and 3B connecting them is applied to the electromagnet mg2, the movable iron core mg1 is alternated. As a result, the complementary vibrations of the two masses which are greatly amplified are continuously generated.

  The position of the center of gravity is also important in this embodiment, but the adjustment procedure is the same as in the previous embodiments. That is, in order to arrange the center of gravity of the second mass body 2 on the central axis Xo of the vibration unit, the mass of the counterweight cw is increased or decreased so as to match the mass of the transport unit tp. In addition, since the horizontal bar sm and the movable iron core mg1 are added to the mass part 1B as compared with the mass part 1A of the first mass body 1, a dotted line is drawn on the lower surface of the mass part 1B so as to reduce the mass. A recessed portion 1 bp is provided to ensure a mass balance. In this way, the center of gravity position of the mass portions 1A and 1B is arranged on the central axis Xo, so the mass of the counterweight cw is adjusted and the center of gravity of the second mass body 2 is placed on the central axis Xo. By doing so, the moment force accompanying the vibration is not generated.

  Since the vibration trajectory of the vibration unit obtained in this way is parallel to the central axis line Xo, the two support springs 4 (plate surfaces) having low rigidity are placed at two positions in the front and rear in the vibration direction as in the previous embodiment. In FIG. 2, the apparatus is installed in a posture orthogonal to the central axis Xo and is connected to the gantry 10, so that it can be installed and configured so that harmful vertical movement components hardly occur.

  In each of the above-described embodiments, the following functions and performances that could not be achieved by the conventional linear feeder can be exhibited, and it is possible to cope with various shapes of conveyance chutes and a wide frequency range. In particular, since almost no harmful vertical vibration leaks are eliminated, the conventional heavy and large fixed base is not required, and the entire apparatus can be made compact and light. Thus, since it does not depend on the rigidity or mass of the mounting portion (installation portion), it can be transported under any mounting (installation) conditions, and has little influence on the transport state.

  In addition, since the variation in the vibration angle can be minimized over the entire length of the transport path, a smooth transport such as sliding can be realized by setting a small projection angle φ that is impossible with a conventional machine. At the same time, even if the chute is long, the conveyance state at the end portion which is the entrance and exit of the conveyance path does not deteriorate.

  Furthermore, the attachment to the pedestal can be mechanically fixed without going through an elastic vibration isolation mechanism, so that the positional deviation (height deviation) between other devices at the entrance and exit of the conveyance path can be avoided. It is possible to receive and supply a stable article.

  Note that the vibratory conveyance device of the present invention is not limited to the above-described illustrated examples, and it is needless to say that various changes can be made without departing from the gist of the present invention. For example, the mechanisms and means described in the following vibration models and examples can be easily realized by appropriate combinations in other vibration models and examples as long as no contradiction arises.

DESCRIPTION OF SYMBOLS 1 ... 1st mass body, 1A, 1B ... Mass part, 2 ... 2nd mass body, 3A, 3B ... Vibration spring, 3Ad, 3Bd ... Piezoelectric drive body, 3As, 3Bs ... Amplification spring, 4 ... Support spring, DESCRIPTION OF SYMBOLS 10 ... Mount, tp ... Conveying part, cw ... Counterweight, Xo ... Center axis of (vibration unit), cb ... Connection body, cbs, 1s ... Connection part

Claims (8)

A first mass body (1) and a second mass body (2) are provided, and the first mass body (1) and the second mass body (2) are interposed via a vibration spring (3). A vibratory transfer device including vibration units (1, 2, 3) connected to each other so as to vibrate in a predetermined vibration direction,
The first mass body (1) has one mass part (1A) and the other mass part (1B),
The one mass portion (1A) is along the vibration direction passing through the center of gravity of the second mass body (2) from the second mass body (2) at two locations along the vibration direction. The vibrations (3A, 3A) made up of leaf springs that extend to one side around the central axis (Xo) and are orthogonal to the vibration direction, respectively, cause the vibration to the second mass body (2). Arranged to be vibrated in the direction and arranged on the one side,
The other mass part (1B) extends from the second mass body (2) to the opposite side to the one side around the central axis (Xo) at two locations along the vibration direction. By virtue of vibration springs (3B, 3B) composed of leaf springs orthogonal to the vibration direction, the second mass body (2) is connected to the second mass body (2) so as to vibrate in the vibration direction and arranged on the opposite side,
The second mass body (2) can be vibrated in the vibration direction at two locations along the vibration direction by support springs (4, 4) configured by leaf springs orthogonal to the vibration direction, respectively. Supported,
Driving means (3Ad, 3Bd, mg1, mg2) for vibrating the first mass body (1) and the second mass body (2) in opposite phases;
Provided in at least one of the one mass part (1A), the other mass part (1B), or the second mass body (2), and having a conveyance path for conveying a conveyed product in the vibration direction. Transport unit (tp),
Connecting means (cb, 1s) for causing the one mass part (1A) and the other mass part (1B) to vibrate in the same phase in synchronization with the vibration direction;
The vibratory conveyance device further comprising:   The connecting means (cb, 1s) allows the one mass part (1A) and the other mass to allow variation in distance between the one mass part (1A) and the other mass part (1B). The vibratory transfer device according to claim 1, wherein the vibratory conveying device is a connecting structure that synchronizes the position of the portion (1B) with the vibration direction.   The centroid position (1g) of the first mass body (1) and the centroid position (2g) of the second mass body (2) are arranged on a straight line substantially parallel to the vibration direction. The vibratory transfer device according to claim 1 or 2.   The natural frequency determined by the vibration unit (1, 2, 3) and the support spring (4) is 1/10 or less of an operating frequency of the vibration unit (1, 2, 3). The vibration type conveying apparatus according to any one of claims 1 to 3.   The drive means (3Ad, 3Bd) is connected in series with an amplifying spring (3As, 3Bs) made of a leaf spring orthogonal to the vibration direction, thereby constituting a piezoelectric drive body (3A, 3B) constituting the vibration spring (3A, 3B). 3) (3Ad, 3Bd).   The drive means (mg1, mg2) includes an AC electromagnet that exerts an excitation force by a magnetic force based on an alternating magnetic field on at least one of the first mass body (1) and the second mass body (2). The vibration type conveying apparatus according to claim 1.   At least two positions spaced along the central axis (Xo) on the side of the second mass (2) between the one mass (1A) and the other mass (1B) 7. The vibration transfer device according to claim 1, wherein the protrusion is provided with a protrusion or a recess.   An attachment posture adjusting means for adjusting the angle of the conveying portion (tp) with respect to the central axis (Xo), and a vibration unit for adjusting the angle of the central axis (Xo) with respect to the base The vibration type conveying apparatus according to any one of claims 1 to 7, further comprising an installation posture adjusting unit.

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