JPH03106711A - Straight type vibration feeder - Google Patents

Abstract

PURPOSE:To make the vibration mode uniform over the overall length of a trough and to facilitate the adjustment of a feed speed by selecting spring constants of a pair of front and rear vibration suppressing leaf springs so that one of the leaf spring has a lager spring constant in a direction parallel to the rectilinear vibration and a smaller spring constant in a direction orthogonal thereto, and the other one of the leaf spring small spring constants in both directions, and by making the attaching angle of the one of leaf springs able to be changed. CONSTITUTION:In a front side vibration suppressing leaf spring assembly 12, a leaf spring 18 is attached to a counter-weight 3 and a base block 14 by means of bolts 19, 20 so that its attaching angle is adjustable. Further, a rear side vibration suppressing leaf spring 13 is formed in an L-like shape, having a vertical plate part 13a and a horizontal plate part 13b. With this arrangement, the leaf spring 13 has a sufficiently low spring constant in a direction parallel to the direction of the rectilinear vibration but has a large spring constant in a direction orthogonal thereto. With this arrangement, the attaching angle of the vibration suppressing leaf spring is changed to make vibration modes in different parts of the trough, and it is possible to surely adjust the feed speed.

Description

[Detailed description of the invention]

[Industrial Field of Application] The present invention relates to a linear vibratory feeder. [Prior art and its problems 1 Figure 14 shows a conventional example of this type of linear vibration feeder. In the figure, the trough (l) extends linearly from side to side, and Its width is usually sufficiently small compared to its length. A leaf spring mounting block (2)' is integrally fixed below the trough (l)', and this blocks the lower counterway 1-(3)' and a pair of front and rear inclined leaf springs (41'(51)'). An electromagnet mounting member (6) is fixed on the counterweight (3), and a yoke (7) made of a magnetic material is integrally fixed to this. A coil (8)' is wound around this.A movable core mounting member (9)' is fixed to the above-mentioned leaf spring mounting block (2)' by hanging from this, and the above-mentioned yoke is attached to this. A movable core (101') is integrally fixed so as to face (7)° with a gap g in between.The counterweight (3)° is a base block (ill'') and a pair of front and rear vibration isolating leaf springs ( 12) ' (13) ' Connected by vibration isolation leaf spring (12) ' (13) '
As is well known, the spring constant is sufficiently small to prevent vibration reaction force from being transmitted onto the base block (11)', that is, the floor (17)' which supports the entire linear vibratory feeder. On the other hand, the above-mentioned inclined leaf spring (4)゜(5)
゛ is for driving, and as is well known, this spring constant is sufficiently large, and the weight of the work body mass side (consisting of trough (1)', leaf spring mounting block (2)゜, etc.) and these spring constants. The resonant frequency determined by is selected so as to almost match the frequency of the alternating current applied to the coil (8), so it is sufficiently large. The excitation mechanism consists of the coil (8) and the yoke (7) as described above.
゜, Movable core (101'. Drive leaf spring (4)'
(5)', etc., but the entire vibrating mechanism is covered by a cylindrical cover (14)'. This is the bolt (15)'(16)' on the counterweight (3)°.
(The shaft portion is shown in cross section in FIG. 14). In addition, on the right side of the figure of the counterweight (3)°, there is a block part (3) for adjusting the center of gravity in order to make the vibration mode of the trough (l)° as appropriate as possible.
It is formed as al'. When alternating current is applied to the coil (8), an alternating magnetic attraction force is generated between the yoke (7) and the movable core fIO), and the pair of front and rear driving leaf springs (4)'(S)' A linear vibration force that is regulated in the direction of inclination is also applied to the counterweight (3) through the lower end of the trough (1) and the leaf spring (4) (5V).Usually, the trough (1) and The total mass of the members integrally fixed to this is sufficiently smaller than the total mass of the counterweight (3)° and each member fixed to it, so the trough (l)° The swing width is sufficiently larger than that of the counterweight (3)°.The driving leaf spring (4)'(5)' It would be fine if the whole vibrated in a direction almost perpendicular to the longitudinal direction of the trough (desired vibration direction α), but in reality, uneven vibration occurs in the front-rear direction of the trough (l)°, for example, at the right end. The vibration angle is α
. In some cases, it may be much smaller and almost horizontal. On the other hand, at the left end, the vibration angle is α. It's bigger than that. Therefore, the parts on the trough (l)° are transferred to the right as a whole by direct vibration, but the transfer speed is uneven, and therefore they are transferred to the right as a group, but the layer thickness is uneven. occurs. For example, if some kind of sorting means is used, this sorting effect will be reduced, and if there is a plurality of sorting means, the parts sorted by the upstream sorting means may be returned to their original disordered posture. be. Although not shown, the tip is connected to the next process, such as a belt conveyor or a robot hand, which must be supplied with the desired tact, but the next process is not possible. The process may be run idle. In order to avoid the above-mentioned inconveniences, conventionally the spring constant of the vibration isolating leaf springs (12)'(13)' was made sufficiently large to make the entire vibration of the trough (1)° uniform. is approaching. In other words, the center of gravity G of the entire linear vibratory feeder is Anti-vibration leaf spring (12) ' (13
)" makes a circular rotation around the fixed point to the base block (11)', and this is added to the linear vibration in the α direction mentioned above, resulting in the vibration of the trough (l)° as described above. This causes unevenness in the longitudinal direction.In order to further reduce this vibration unevenness, conventionally, as mentioned above, a block part (3a)' for adjusting the center of gravity is formed in a part of the counterweight (3)°. or adjust the mounting position of the trough (l) back and forth.On the other hand, if the spring constant of the vibration isolating leaf springs (12)'(13)' is increased, the rotation around the center of gravity G of the whole is increased. The magnitude of the movement becomes smaller, and the vibration unevenness in the front-rear direction of the trough (l)° also becomes smaller.
When the spring constant of ' increases, the vibration reaction force transmitted to the base block (11) increases, making it impossible to perform the original vibration isolation effect. Also, vibration-proof leaf spring (12)
'(13)' has a spring constant of almost f infinity in its long plane direction, and is sufficiently large in its width direction. Therefore, as mentioned above, the width of the trough (l) of a linear vibratory feeder is sufficiently smaller than that in the longitudinal direction, so the width of the trough (l) in the longitudinal direction is much smaller than when rubber is used as the vibration isolation spring. This has some merit as it can almost eliminate the oscillating motion around the base block, but considering the characteristics of the vibration isolating leaf spring (121'(13)', its spring constant is sufficiently small, (The rotational movement around the fixed point to 111' cannot be avoided. In Fig. 14, G is the trough (l), the leaf spring mounting block (21'. movable core mounting member f9)', Represents the center of gravity of the working side mass consisting of a movable core (such as 101', and G is the counterway)
f31', represents the center of gravity of the mass on the counterweight side consisting of the electromagnet mounting member (6), the yoke (7), the coil {8}, etc. And the above-mentioned arrows X,,,X. direction is the desired vibration direction, but in this direction there is a trough (l)
゛It is sufficient if the whole body vibrates, but as mentioned above, G
, and 01 rotate around the center of gravity G, so the trough (l)° causes uneven vibrations in its longitudinal direction. On the other hand, depending on the equipment conditions for the next process, it may be necessary to increase the transport speed of parts in the front (right) part of the trough (l)°.
Alternatively, there may be a request to increase the transfer speed at the rear part of the trough (l)°, or to make the transfer speed constant over the entire length of the trough (l)° as described above. Some kind of adjustment mechanism is required for this, and for example, in the conventional configuration, the above-mentioned request is met by changing the mounting angle of the driving leaf springs (4)'(5)'. However, if this mounting angle is adjusted and the side of the vibrator is driven again, the resonance frequency may change significantly. This is because the drive leaf spring is the one whose mounting angle position has been adjusted, but it is sufficiently larger than the spring constant of the anti-vibration spring. (due to differences in direction, etc.) greatly affects the overall resonant frequency. In addition, once the driving leaf springs (4)'(5)' are removed, the movable core (10)' is used to adjust the mounting angle.
The size of the gap g between the
(Since the mounting angle with respect to the leaf spring mounting block (2) of 51', that is, the position and direction of the point of action changes, not only the resonant frequency changes as described above, but also the amplitude changes significantly compared to the desired size. Therefore, as mentioned above, it is very difficult to make adjustments to match the equipment conditions of the next process. [Problem to be solved by the invention 1] The present invention was made in view of the above problems, To provide a linear vibration feeder that can make the vibration mode uniform over the entire length and can easily adjust the transfer speed at the front, rear, or other parts of the trough depending on the equipment conditions of the next process. 1. Means for solving the problem 1. The above object is to provide a linearly extending trough, 5. a pair of front and rear driving leaf spring means for connecting the trough and a counterweight, A pair of front and rear vibration isolating leaf spring means for supporting the counterweight on a base, and an excitation mechanism for linearly vibrating the trough in a direction substantially perpendicular to the extending direction of the driving leaf spring means. In the linear vibration feeder, one of the pair of vibration isolating leaf spring means has a sufficiently small spring constant in a first direction parallel to the direction of the linear vibration, but It has an extremely large spring constant in the second vertical direction, and the other of the pair of vibration isolating leaf spring means has a sufficiently small spring constant in both the first direction and the second direction, and This is achieved by a linear vibration feeder characterized in that one of the pair of vibration-isolating plate spring means is attached to the counterweight and/or the base so that the attachment angle can be changed.

[For production]

One of the pair of front and rear vibration isolating leaf spring means has a sufficiently small spring constant in the first direction parallel to the direction of linear motion of the trough, but has a sufficiently small spring constant in the second direction perpendicular to the first direction. The other of the pair of vibration isolating leaf spring means has a sufficiently small spring constant both in the first direction and in the second direction, so that the overall center of gravity is centered on the pair of vibration isolators. The rotational movement of one of the leaf spring means around the attachment point to the counterweight can be made uniform over the entire length of the trough. In the above-mentioned action, one of the pair of front and rear vibration isolating plate spring means is attached to the counterweight and/or the base so that the attachment angle can be changed, so that the trough can be adjusted by simply changing the attachment. The overall vibration mode can be changed, and since the mounting angle of the pair of front and rear driving leaf springs connecting the trough and counterweight is not adjusted as in the conventional method, the resonance frequency is hardly affected. Therefore, its amplitude can be adjusted with almost no change. [Embodiment] A linear vibratory feeder according to an embodiment of the present invention will be described below with reference to the drawings. 1 to 5 show a linear vibratory feeder according to the first embodiment of the present invention. In the figures, the trough m has a sufficiently elongated linear shape as in the conventional case, and a trough m is integrally formed on the bottom surface of the feeder. Both end faces of the leaf spring mounting block (2) fixed to the counterweight (3) are connected to the counterweight (3) by a pair of front and rear driving leaf springs (5) +6). A weight (4) for adjusting the position of the entire center of gravity is movably fixed to the rear part of the counterweight (3) by a mechanism not shown. A movable core mounting member (7) is suspended and fixed to the leaf spring mounting block (2), and a movable core (8) is integrally fixed to this. Further, a yoke mounting member (9) is fixed on the counterweight (3), and a yoke (11) made of a magnetic material is attached to the yoke mounting member (9) so as to face the above-mentioned movable core (8) with a gap g therebetween. A coil (lO) is wound around the yoke (11). Also, the counterweight (3) is the base block (14)
and a pair of front and rear anti-vibration leaf spring devices (12). +(1 3
) are connected by. Front anti-vibration leaf spring system i!
! (12) is for changing the mounting angle according to the present invention and will be described later, but the rear vibration isolating leaf spring device {l3} is L
It forms a vertical plate part (13a) and a horizontal plate part (13b).
and one end of the vertical plate part (13a) is a bolt (l).
5) is fixed to the counterweight (3), and one end of the horizontal plate part (13b) is fixed to the base block (l4) with a bolt (l6) via a spacer (l7).For front vibration isolation. The leaf spring device (12) mainly consists of leaf springs (l
8), whose upper and lower ends are bolted (19
) As shown in FIGS. 3 to 5 by (20), the mounting angle is fixed to the counterweight (3) and the base block or pedestal (l4) so that the mounting angle can be adjusted. In other words, one mounting angle is shown in Fig. 3, which is the case where the drive leaf spring (S) (6) is mounted parallel to it. In this case, horizontal adjustment blocks (21) and (22) are interposed at the upper and lower ends of the leaf spring (l8) as shown in the figure, and bolts (1
9) Hole (21a) through which the shaft of (20) is inserted (22
A) is formed, but the bolts (19) and (20) are inserted into the holes of the leaf spring (l8) and the holes (21a and 22a) of the blocks (21 and 22), and the counterweight (3) screw hole (3a) and base block (l
4) is fixed at the angle shown in Figure 3 by screwing it into the screw hole (14a). Furthermore, the block (2
l) The installation angle of the leaf spring (l8) is adjusted by interposing (22), but at the same time, the screw holes (3a) (14a) formed in the counterweight (3) and base block (l4) Bolt (19) (2G
) are aligned so that they can be screwed together. Also, the mounting angle shown in Fig. 4 is the same as that of the driving leaf spring (51 (61
In this case, the angle adjustment blocks (23) (24) (25) prepared in advance are attached to the bolts (19) and the plate springs as shown in the figure. {l8) and bolt (20)
and the plate spring (l8) and the plate spring (l8) and the base block (l4), respectively, and the bolts (
19) Insert (2G) into the screw hole (3) as shown in Figure 3.
a) By screwing and tightening bolts (19) and (20) to (14a), the mounting angle as shown in FIG. 4 can be obtained. Also, Fig. 5 is different from Fig. 4 and shows driving leaf springs (5) and (6).
), the case is fixed with an inclination in the opposite direction with respect to
In this case, the angle adjustment block (26) f27)
(28) are interposed between the leaf spring (18) and the counterweight (3), and between the bolt (20) and the leaf spring (l8), and the holes (26a) and (27a) formed in these
By inserting the bolt (19) (201) into the screw hole (3a) (1.4a) and tightening it, the mounting angle β shown in Fig. 5 is obtained. According to the above, the structure is configured so that three mounting angles can be taken (α and β are 10° or less).The first embodiment of the present invention is configured as described above, As is well known, when alternating current is applied to the coil (lO), an alternating magnetic attraction force is generated between the yoke (l1) and the movable core (8), which causes the driving leaf spring (5) (6 ) through the trough (11) receives a linear vibration force in a direction almost perpendicular to the longitudinal direction of the leaf spring (51 (6)).In this case, the mounting angle of the front vibration-proof spring W (12) is As shown in Figure 3, it is assumed that the driving leaf spring (51 (6)) is fixed in parallel.In the case of this installation, the trough side consists of the trough (11, leaf spring mounting block (2), etc.). The composite center of gravity of the center of gravity of the mass and the center of gravity of the counterweight side mass consisting of the adjustment weight (4), etc. ), shown as point O in Fig. 1, performs a rotational movement around this point 0, which adds to the linear vibration relative to the trough (1). Conventionally, the anti-vibration spring device (12) (13) Instead, for example, vibration isolating rubber was used, but in this case, the spring constant of the vibration isolating rubber as a whole is sufficiently small in all directions, so that the entire vibrating feeder rotates around its center of gravity. The moment of inertia is smaller than in the example, and therefore the rotational movement is large.For this reason, the vibration of the trough (1) is largely uneven over the entire length as described in the prior art, but in this example, the moment of inertia is Since the rotational movement around the center of gravity of the whole becomes large, the rotational movement around the center of gravity of the whole becomes small, and therefore it is possible to perform almost only linear vibration and uniform vibration over the entire length. The parts can be transferred at a uniform transfer speed over the entire length of the trough (1).Next, in the next process, the transfer state is desired such that the transfer speed is low at the front of the trough (1) and high at the rear. In this case, as shown in Fig. 4, instead of blocks (21) (22), blocks (23) (24) (251) are interposed as shown, and leaf springs (l8) are used. , and thereby the driving leaf spring (5) (61) is attached at an inclination angle of α. In this state, when an alternating current is applied to the coil (lO) and the trough (1) is vibrated by an alternating attraction force, the vibration angle is small in the front part F of the trough m and large in the rear part H, as shown in Fig. 13. . Also, in the center of this tenon, the driving leaf spring (5) (61
It vibrates at an angle of vibration almost perpendicular to the longitudinal direction of . Due to such vibrations, it is possible to obtain a high transfer speed in the front part of the trough (1) and a small transfer speed in the rear part, and it is possible to meet the demands of the next process. Next, a case will be described in which the next step requires a low transfer speed in the front part F of the trough (1) and a large transfer rate in the rear part R. In this case, as shown in FIG. 5, the blocks (23) (24) (
Instead of 251, the leaf spring (18) is fixed with a block (26) (2g+) interposed.In other words, in this case, the leaf spring (18) is fixed at an angle opposite to that shown in Fig. 4 with respect to the driving leaf spring (5) (6). It is installed at an angle of β.In this state, when alternating current is applied to the coil (lO) to generate an alternating attraction force, the trough (1) vibrates with the vibration angle distribution shown in Figure 13.In other words, the trough The vibration angle is large in the front part F of (1) and small in the rear part R, and the vibration angle is small in the rear part R.
．． At the center of No. 1, there are drive leaf springs (5) (6)
It vibrates in a mode in which it vibrates at an angle of vibration approximately f perpendicular to the longitudinal direction of . In this case, the parts are transferred at a lower transfer speed at the front part of the trough 111 and at a higher transfer speed at the rear part, thereby making it possible to meet the demands of the next process. In addition, “0” in Figure 13
” is the case of the mounting angle shown in Figs. 1 and 3. The structure and operation of the first embodiment of the present invention have been explained above, but as is clear from the above explanation, it is difficult to meet the requirements of the next process. This can be easily and accurately responded to by adjusting the mounting angle of the front vibration isolator (l2). In order to adjust the drive leaf spring (5
) After loosening the mounting bolts (6), the block is interposed and fixed again, but at this time, as mentioned above, the gap g between the movable core (8) and the yoke (11) changes. Or, due to a change in the overall resonant frequency, the amplitude was significantly different from that required for the next process, and it was necessary to readjust it again. However, according to this embodiment, this is not necessary and can be done once. 6 and 7 show a linear vibration feeder according to the second embodiment of the present invention, and parts corresponding to the first embodiment are designated by the same reference numerals. , and the detailed explanation thereof will be omitted. That is, in this embodiment as well, the counterweight (30
The corner member disposed above 1 is the same as in the first embodiment, but this counterweight (30) and base plate (33
) is different from the first embodiment in the structure of the vibration isolating leaf spring devices (3l) (34) that connect them. In other words, the front vibration isolating leaf spring device (3l) is attached to a mounting block (31) that is integrated with the base plate (33) via a counterweight (30) and a structure to be described later.
32) with bolts (40) and (41), and the rear vibration isolating leaf spring device (34) has a V-shape unlike the first embodiment, and its diagonal plate portion (34a) is A counterweight (30 mm) is attached to one end by a bolt (35).
), and one end of the horizontal plate part (34b) is fixed to the bolt (
36) is fixed to the base plate {33} via a spacer (l7) and a column (37). At the upper end of the front vibration isolating leaf spring device (31),
The leaf spring (50) is fixed to the counterweight (30) by screwing and tightening ports (40) into a pair of screw holes formed in the U-shaped leaf spring mounting block (38). In other words, the leaf spring mounting block {38}
Both arm portions (38a) (38b) of the counterweight {30} have cutouts (37) formed on both sides of the front portion of the counterweight {30}.
a) (37b) as shown in Figures 6 and 7, and bolts (39a) (39b) with notches (37b).
a) By screwing and tightening the leaf spring (50) into the screw hole formed in (37b), the mounting block (3
8) is fixed to the counterweight (30). In addition, the lower end of the leaf spring (50) is fixed with a bolt (4l) to the mounting block (42), which is arranged almost vertically in the illustrated state, and for this purpose a pair of screws are attached to the horizontal arm. A hole is formed, and the leaf spring (50) is fixed to the block (42) by screwing and tightening the bolt (4l) into the hole. Also, both arm parts (42a) of the block (42)
(42b) are applied to both sides of the mounting block (32) as shown in Fig. 7, and screw holes (44a) and (44b) formed in pairs in this mounting block {32}
(45a) (45b) and screw holes (46a) (46b) (to which they are currently screwed)
) By screwing and tightening (43b), the leaf spring (50) can be made to take the mounting angle shown in the figure, for example. For example, when fixing the leaf spring (50) to the driving leaf spring (5) [6] at an angle of β as in the first embodiment, loosen the bolts (39a) and (39b), and The bolt (
43a) Loosen (43b) and remove them from the block (CHI). Secure the entire plate spring (50) with bolts (3
9a) While rotating the leaf spring (50) around the axis of the screw holes formed in the notches (37a) and (37b) of the counterweight (30) into which the counterweight (39b) is screwed, The block (42
) are aligned with the screw holes (45a) (45b) formed in the mounting block {32}, and then removed. By inserting the bolts (43a) (43b) into the loose holes of the mounting block (42) and tightening them into the screw holes (45a) (45b) of the mounting block (32), the same procedure as in the first embodiment is carried out. Drive leaf spring (
5) It is possible to take the angle of inclination β with respect to (6). Similarly to the first embodiment, when the mounting angle is α relative to the driving leaf spring, the operation is performed in the same manner as described above.
In this case, the screw hole (44a) of the mounting block (32)
Arm part (42a) of block (42) in (44b)
Align the matching holes formed in (42b) and bolt (
43a) This mounting angle can be achieved by screwing and tightening (43b). The adjustment work for this mounting angle is shown in Fig. 8, where the solid line indicates the mounting angle of the leaf spring device (3l) as shown in Fig. 6, and the dashed line indicates the mounting angle with respect to the driving leaf spring (51 (6)). This is the case of β, and the case shown by the two-dot chain line shows the case where the driving leaf springs (5) and (6) are attached at the mounting angle β. Although this shows a linear vibratory feeder according to an embodiment, parts corresponding to those in the above embodiment are given the same reference numerals and detailed explanation thereof will be omitted. That is, in this embodiment as well, the counterweight +90
1 is different in shape, but it is fixed to the base plate (53) by a pair of front and rear vibration-proof leaf spring devices (51) (54). In other words, the rear vibration isolating leaf spring device (54) has an L-shape as a whole, but the leaf springs (561 (57)) are applied to both side plates of the angle member (55), and these are attached to the bolts (581 (59)). It is fixed to the angle member (55), the counterweight (90), and the column (60).The front anti-vibration plate spring device (5l) is connected to a pair of plate springs (61).
a) (slb), the upper end of which has a nearly cylindrical block shape, and this part [62a) (62b)
A loose hole for inserting a bolt is formed in the hole, and a bolt (
64a) (64b) to the cylindrical block part (62a) f
The upper end of the leaf spring (61al (61b) is fixed to the counterweight (90) by inserting it through the plate spring (62b) and fixing it by screwing. Also, the lower end of the leaf spring (61al (61b) is fixed to the counterweight (90). f63b),
this. A bolt (65al) is attached to a pair of play cards formed in
(65b) and screw it into the screw hole formed in the block (52) to secure the leaf spring (61a).
) (6lb) is attached to the mounting block (52). That is, it is fixed to the base plate (53). The mounting block (52) also has pairs of screw holes [71a] (7) for adjusting the mounting angle, as shown in Figure 9.
lb) and [72a) (72b) are formed, and the screw hole currently attached is formed between these. By screwing and tightening bolts (65al, f65b) on either of these, the plate springs (61a) (6lb) are fixed to the base plate (53), for example, at the mounting angle shown. Although the third embodiment of the present invention is constructed as described above, its operation is essentially the same as that of the first and second embodiments, so a detailed explanation thereof will be omitted. To adjust the mounting angle, loosen the bolts (64al (64b) and remove the pair of bolts (65a) J6Sb) in the same way as in the second embodiment, and then adjust the block part to the desired mounting angle. Align the mating holes (63a) (63b) with the paired screw holes (71a) (7lb) or f72a) (f72b) formed in the block (52), and then tighten the bolts (65a) (65b). After inserting it and tightening it, remove the upper bolt (64a)
(64b) and plate it to obtain the desired mounting angle. Fig. it and Fig. 12 show a linear vibratory feeder according to a fourth embodiment of the present invention. In the figures, parts corresponding to the I to third embodiments are denoted by the same reference numerals, and their details are shown. Further explanation will be omitted. In this embodiment as well, the shape of the counterweight (70) is different from that in the above embodiment, and its front end and rear end are attached to the base plate (73) and the anti-vibration leaf spring device (71) according to the present invention.
(74). The rear vibration-proof leaf spring device (74) has an L-shape as a whole, but the leaf spring (76)
(77) is attached to the counterweight (70) and base plate (73) by bolts (78) and (79).
80). Also, the front vibration-proof leaf spring device (71) consists of a pair of leaf springs (81a) (8lb) as in the third embodiment, and a cylindrical block part (82) integrally formed at the upper end thereof.
a) A loose hole for inserting a bolt is formed in (82b), and a through bolt (85) is inserted into this, and a through hole (83) formed in the counterweight (70) is also inserted to insert a nut. By screwing and tightening the bolt (84) onto the bolt (85), the leaf spring (81a) (8lb) is fixed to the counterweight (70). Also leaf spring (81
a) Holes for bolt insertion are formed in the similarly cylindrical block portions (86a) and (86b) at the lower end of (8lb), and the mounting block C72) also has an insertion hole (1).
00) is formed, and a through bolt (88) is formed on this.
The shaft (87) of the is inserted through the shaft, and a nut (89
) by screwing and tightening the leaf spring (81a) (8
lb) is fixed to the base plate (73). According to this embodiment, the leaf spring mounting block (72) has a first
As shown in Figure 1, an elongated hole (100) for bolt insertion and angle adjustment is formed, and the mounting angle of the leaf spring (81a) (8lb) can be continuously adjusted within this range. Can be done. That is, in the above embodiment, three angular positions were selected, but according to this embodiment, the mounting angle can be adjusted continuously within the elongated hole (100). Other functions and effects are the same as those in the above embodiment, so their explanation will be omitted. Although each embodiment of the present invention has been described above, the present invention is of course not limited to these, and various modifications can be made based on the technical idea of the present invention. For example, in the above embodiment, the movable core (8
) and attach the yoke (11) to the counterweight side.
Although the coil (lO) wound around this is fixed, this attachment relationship may be reversed. Furthermore, in the above embodiments, an electromagnetic drive unit has been described as the linear vibration excitation mechanism, but the present invention is not limited to this, and other drive units, such as two vibrating motors, may be used. Further, although the detailed structure of the trough (1) has not been explained in the above embodiments, it may be provided with some kind of parts feeding means to feed the parts to the next process in a predetermined posture. Furthermore, in the above embodiments, the mounting angle of the front vibration-proofing leaf spring device was made variable, but instead, the mounting angle of the rear vibration-proofing leaf spring device may be changed using a similar configuration.

【Effect of the invention】

As described above, according to the linear vibration feeder of the present invention, by changing the mounting angle of the front or rear vibration isolating plate spring device, the vibration mode in each part of the trough can be easily and reliably adjusted according to the requirements of the next process. You can respond to the following.

[Brief explanation of drawings]

FIG. 1 is a side view of a linear vibration feeder according to a first embodiment of the present invention, FIG. 2 is a front view of the same, and FIGS. 3 to 5 are partially enlarged cross-sectional views showing how the main parts are installed. FIG. 6 is a side view of a linear vibratory feeder according to a second embodiment of the present invention, and FIG.
The figure is a front view of the same, FIG. 8 is a partially enlarged side view showing the adjustment effect of the mounting angle of the main parts in the same embodiment, and FIG. 9 is a side view of a linear vibratory feeder according to a third embodiment of the present invention. lO
11 is a side view of the linear vibration feeder according to the fourth embodiment of the present invention, FIG. 12 is a front view of the same, and FIG.
FIG. 3 is a graph showing the operation of the first embodiment, and FIG. 14 is a partially cutaway side view of a conventional linear vibratory feeder. In the figure, (1)...
Rough (3) (30) (70)
(90)...Counterweight (12) (31)
(51) (71)・Front vibration isolation plate spring device (131 (
34) (54) (74)・Rear anti-vibration plate spring device fee
Science Human food Hanyasu Yu Figure 8 Betlough fL setting

Claims (1)

[Claims] A linearly extending trough, a pair of front and rear drive leaf spring means that connect the trough and a counterweight, a pair of front and rear vibration isolation leaf spring means that support the counterweight on a base, and the drive and an excitation mechanism for linearly vibrating the trough in a direction substantially perpendicular to the extending direction of the vibration-isolating leaf spring means, one of the pair of vibration-isolating leaf spring means The pair of vibration-isolating leaf spring means has a sufficiently small spring constant in a first direction parallel to the direction of vibration, but has an extremely large spring constant in a second direction perpendicular to the first direction. The other one has a sufficiently small spring constant in both the first direction and the second direction, and one of the pair of vibration isolating leaf spring means is attached to the counterweight and/or the base. A linear vibratory feeder characterized in that it is installed so that its angle can be changed.