JPS5953310A - Vibrative conveyor - Google Patents

Abstract

PURPOSE:To reduce noise and prevent damage to material or the like and further increase speed by forming the captioned vibrative conveyor, for conveying massive material or the like, in such a manner as a trough capable of reciprocating motion is put in said motion through a reciprocating motion driving part equipped with a driving rod and two sets of crank mechanisms. CONSTITUTION:Rotation of a motor 28 causes a driver link 42 to rotate at a speed decelerated by means of gears 36, 37. Rotation of said link 42 causes displacement of links 43, 44 and the follower link 44 is rotated repeating increase and decrease in angle of rotation. Thus, the follower link 44 is rotated circulatively at a speed higher than that of the driver link 42 and also lower than the same, and puts a driving rod 21 in a reciprocating motion through a rotary shaft 47 and a driving link 52. This reciprocating motion is transmitted to a trough 11 through a rubber bush 19 and binding members 17a, 17b to vibrate the trough 11. Since vibration parallel to the conveyance surface can be given due to this structure, reduction of noise and prevention of damage to material or the like and also increase of conveyance speed can be realized.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vibrating conveyor for transporting various lumps, grains, powder particles or particulates by vibration.

In the conventionally widely known 4-axis conveyor,
A vibration force in an oblique direction is applied to the transfer surface on which various materials are placed, and as a result, the materials on the transfer surface are transferred in one direction while repeating a jumping motion. In this case, the vibration force changes sinusoidally with time, and the side slope periodically undergoes a jumping motion (repeat and impinge on the transport surface).

However, when transporting metal materials, such as bolts and nuts, using the above-mentioned vibrating conveyor, the material repeatedly jumps, causing noise eruptions when it collides with the transport surface (which is often made of metal). In some cases, it can also become a pollution problem.

In addition, when transporting fragile materials such as biscuits or Senbei using a fully vibrating conveyor, periodic collisions with the transport surface may cause problems such as "breaks" and "overs". Troublesome restrictions were placed on surface quality and vibration conditions.

Furthermore, when conveying particles that easily form lumps, such as fine particles on the side, using a vibrating conveyor, it is difficult to prevent the particles from forming.
Instead, it required a lot of troublesome design and tuning to achieve synchronization. Furthermore, in the resonant type, the loss width tends to be fast, and therefore it is difficult to obtain the full specified material transfer speed because of the constant vibration of 1p.
In order to obtain the best results, a fixed width adjustment circuit is especially required, which leads to high costs.

Furthermore, in a vibrating conveyor that applies a vibration force in an oblique direction to the transfer surface, if the trough that constitutes the transfer surface is long, secondary vibration or high-order uplift is likely to occur in the trough, and the old quality (4) A swing width that is too thick is not allowed considering the full strength of the blade.

The present invention has been made in view of the above-mentioned problems, and has the key to eliminating the drawbacks of the conventional vibrating conveyor that applies a vibration force in an oblique direction to the conveying surface. 4) The overall purpose is to provide a vibrating conveyor. To this end, according to the first aspect of the present invention, there is provided a trough which is supported in a reciprocating manner and extends linearly; a drive rod which extends parallel to the trough and is connected to the trough; a joint link, a fixed link; , a reciprocating unit jlj17 equipped with two sets of crank mechanisms formed by a follower link and an intermediate link.
This can be achieved by a vibrating conveyor consisting of parts and; characterized in that the rotation of the follower link obtained by rotating the single link at a constant speed is converted into a straight line and transmitted to the first drive rod. According to the second aspect of the present invention, a trough that is supported in a reciprocating manner and extends linearly; a six-movement rod that extends parallel to the trough and is connected to the trough; a reciprocating drive unit including two sets of crank mechanisms formed by a link, a fixed link, a follower link, and an intermediate link; a drive link fixed to the follower link in the same way; This is achieved by rotating the links at a constant speed, and by means of a vibrating conveyor, which converts the rotation of the drive link into a straight line and transmits it to the drive rod.

Furthermore, the above object is achieved according to a third aspect of the present invention; 4) a trough that is reciprocably supported and extends linearly; a first drive rod that extends parallel to the trough and is coupled to the trough;
a swinging lever supported swingably in the direction of the first drive rod and having the first drive rod pivoted at its upper end; and a reciprocating drive unit comprising two sets of crank mechanisms formed by an extending link, a fixed link, a follower link, and an intermediate link, and causing all of the partial links to rotate at a constant speed. The rotation of the follower link obtained by converting the entire rotation into a straight line and transmitting it to the first driving rod via the second driving rod and the swinging lever is achieved by a vibrating conveyor. Before explaining the vibrating conveyor according to the embodiment of the present invention, the mechanical principle applied to the vibrating conveyor will be explained with reference to FIG.
A mechanism in which a rotating couple is combined with a bottle, or a mechanism in which a part is made to be a rotating couple is called a link bond, of which 4
A mechanism in which all wooden links are connected is called a full four-joint rotation mechanism, but in addition, the shortest link of this four-joint rotation mechanism is fixed,
When the unequal relationship described below does not exist between the lengths of these links, the ζ- mechanism is called a two-set crank mechanism. The principle of this two-set crank mechanism is applied to the first invention, and FIG. 1 is an illustration of this principle. In Figure 1, four links (11 (2) (3) (4)) are connected to bins (
5) (6) (7) (combined at 81, 4 links (
], IJ2) (a) The length δ of (4) is to, respectively.
Assuming t2, t8, and L4, between these lengths, t, + t, (t, + /, , t, + to>
There is a relationship of 4 + to, and the shortest link t4 is fixed.

That is, four links (IJ (2) (3) (4
) consists of two crank mechanisms, and according to this example, 4=9cmn1, ts=7.5cm, t,=9
cm, t=4.5 cm.

+ In this specification, in FIG. 1, the link (IJ (2)
(3) (4) respectively for thick link, intermediate link,
They are called follower links and fixed links, but in this embodiment, the thick link (1) rotates at a constant speed around the entire bottle (5), and the follower link is obtained at this time. J sink 3) bin (6
) is converted into linear motion, which is transmitted to the trough via the drive rod 00. In addition, in this embodiment, the subordinate link (3) katana r) is directly connected to the 161 sect, so there is no illusion, but the fifth link (3') identified coaxially with the subordinate link (3). JC (referred to as the driving link in this specification 1). That is, the drive link (3) rotates around the pin (6) together with the follower link (3) as shown in FIG. It does not have to be in the same phase relationship as link (3). In Figure 1, the drive rod (1 (1 +
The pivot point between the drive link (3) and the drive link (3) is shown by (9). In this embodiment, the length of the drive link (3) is 6α.

The mechanical principle applied to the vibrating conveyor VC according to the embodiment of the present invention is as described above. In Fig. 2, the trough σV extends in the left-right direction, and the bottom surface thereof has multiple pairs of rail portions IM (as shown in Fig. 3).
12aX12b) are fixed. The trough fly 1 is supported by a plurality of pairs of columns (13a and 13b), and on the tops of these columns (13a and 13b) there are roller supports (13a and 13b).
L4a) (14b) are fixed, and these roller supports have rollers (15a) (15b) supported by members (14a) (14b). The rollers (15aX15b) are close to each other on the outside of the rail members (12a) (12), so that the trough 0υ is Jf
j trilled so that it can reciprocate 19 (13a) (
13b).

At the center of the bottom of the trough Ov, a reinforcing member QC9 is fixed to receive the driving force from the reciprocating wind movement section, which will be described later.
a) (17b) is fixed. Connecting member (Eflova 17
b) A rubber bush (19) is connected via a bottle a→, and a trough tt11 is attached to the outer periphery of this rubber bush 01.
1 connecting ring (4) is fixed. The connecting ring (4) is fixed by a nut (24) to the tip of a drive rod (2]l extending in parallel with the trough aη, and a ringing rod (24).
The other end of 21J is (naso) (231
The drive unit side connection ring (241) is fixed by the drive unit side connection ring (241), and the drive shaft (26) is fixed to the inner ring of the bear link (25) that is tightly fitted to this connection ring (24I).

As will be described later, a reciprocating drive unit (2) is attached to this drive shaft (26).
The rotational force from 7) is transmitted.

The reciprocating drive unit (2η drive valve is an electric motor (20),
This rotational force is transmitted to the thick pulley (7) via the boot 9431) and belt tray 9). A pair of bearings (33) (40) are supported on the foundation by the support block 0 (0). A small diameter gear i: 3G) is fixed at the center of the frame, and this meshes with a large diameter gear 0゛θ. Bearing 0
1 (4)) is fitted onto the rotating shaft 3~. Pulley (30:1131), gear (36) G
7) The rotational speed of the electric motor (28) is reduced to a predetermined rotational speed, for example, 100r, pom. One end of the rotating shaft (to) of the large diameter gear 07) is
As shown in Figure A, a plate-shaped original link member (4) is fixed on one end side. That is, one end between the rotating shafts is fitted between the fork portions (42a and 42b) formed on the one end side, Pol) (42C) k It is fixed by tightening. One part of the fork part is removed (a similar fork part is formed on the other end of the 4, and the - mark on this part is between the shafts)
(42d) K is fixed. The shaft is connected to one end of a track-shaped plate-shaped intermediate link member (43) via a bear link (43b), and the other end of this intermediate link member (431 is connected to a bearing (43a) via a bearing (43a)). This shaft (46) is connected to the shaft (4G).This shaft (46) is further connected to one end of the follower link member (441) with the fork part (44a (4, 4d).A fork portion is similarly formed on the other end side of the follower link member (goods).
It is fixed to this by a rotating shaft (44C) with one end of 4η being a pole. The rotating shaft (47) is mounted on a bearing (49) 51 fixed to the top surface of a pair of support blocks (4851).
) is supported by the sink part side (4 corresponds in principle to the link (1) in FIG. 7)
corresponds to Similarly, the intermediate link member 143) is the link (
2), the shaft +45) (46+) is connected to this via a bearing (43bX43a), respectively.
7) Corresponding to (8), the follower link part 1' (441 is attached to the link (3), and the shaft (461 (47)
) corresponds to bin (8) (6).

As shown in FIG. 7A, the distance t0 between the axes 138H4'5,
The distance m between the axes (4G) and the distance t between the axes (4fi) and (47) are respectively the straight line connecting the axes with the present implementation (47) and the angle α0 with respect to the horizontal line. In the example, this is G0-30°, and the distance t in the horizontal direction between the axes
−cos3Q°×4.5m. That is, the length δ of the fixed link (4) shown virtually at 16 in FIG.
．． 5 cm.

At the end of the rotating shaft (4η) on the trough Qη side, a plate-shaped drive link member (52) is further fixed as shown in FIG. One end (2) of the drive shaft (26) coupled to the drive rod (21)
6a) is fixed. Fork portions (52a) (52b) are also formed at both ends of this link member (52), and the shaft (26a) t4η is fitted into these.
2d) By tightening the shaft (26a) (4
I am fixed. Axis (26a) (The distance between the four shafts is 6 cm in this example.

The vibrating conveyor according to the embodiment of the present invention is constructed as described above, and its operation will be explained next.

When power is applied to the electric motor (C), the electric motor (2) rotates, and this rotation is caused by the pulley (3010I) and gear (3G) G
37) and is transmitted to the rotating shaft G. For example, the deceleration σ is reduced to 100 r, p, m. That is, a one-piece link member (Ishi is clockwise in FIG. 7A), O
It rotates at speeds of Or, p, and m.

Now, to explain the movement of each link member (4" 1431 (441) in the rotation phase shown in FIG. Then, each link member (431 (4
4) U m 7 L (the position indicated by the solid line in the figure fur ?r
and 6° This position is indicated by a dashed line in Figure 7A. On the other hand, if this is shown with respect to the principle diagram in Fig. 1, Section 8A
As shown in Figure and Figure 8B. That is, thick links (
The original 145 link part corresponding to IJ (when the 4 parts rotate 90a, the follower link member (3) corresponds to follower link (3)
44) t, J: Angle β0 rotation larger than 90°, one after the other: l', 7 [From the rotation phase in Figure 3, one part of the sink part Io (471 further rotates 90°, then each link The member (44J) takes the position shown by the solid line in FIG. 7C.

This position is indicated by a dash-dotted line in FIG. 7B. On the other hand, if this is illustrated with respect to the principle diagram of FIG. 1, it will become as shown in FIGS. 8B and 8C. That is, the one-piece link member (6)
When rotates by 90 degrees between these rotational phases, the follower link part side (4 degrees rotates by an angle smaller than 90 degrees!).

Similarly, when the one-part link member (4) rotates another 90a from the rotational phase in Fig. 7C, each link member (431t4()
is the position shown by the solid line in Figure 7D! Take it. This position is the 7th C
In the figure, it is indicated by a dashed line. On the other hand, if this is illustrated with respect to the principle diagram of FIG. 1, it will be as shown in FIGS. 8C and 8D. When the lj jaw piece and sink part side (4) rotate by 90a between these rotational phases, the follower link member (44) rotates by an angle β0 smaller than 90°.

Furthermore, in the same way, from the rotational phase in FIG. 7D, the one-piece link member (4
2) is further rotated 90 degrees (B), and each link part (43
(Baku takes the position shown by the solid line in Figure 7A. This position is shown by the dashed-dotted line in Figure 7D.
The principle diagrams shown in the figure are as shown in Fig. 81) and Fig. 8A. That is, the one-part link member (421) rotates 90a between these rotational phases, and the follower link member (421 rotates with an angular history β greater than 90°).

From the above explanation, it will be understood that the follower link part side (44) periodically rotates faster than the thick link member (44) in a certain phase, and rotates more slowly in other phases. The drive link part Paulownia (52) which is fixed to the shaft (52) also rotates in the same way as the follower link member (44), and this rotational force is transmitted to the shaft (
26) and the bear link (25) K that fixes this shaft 2G+'. The drive unit side connecting ring 4 rotates around the rotation axis (4η) and rotates relative to the axis (26).Thereby, the drive rod (2υ is the sixth
It performs reciprocating motion as shown by the arrow in the figure. That is, the rotational motion is converted into linear reciprocating motion by the connecting ring (24) and the bearing (25) (However, the drive rod (211) is sufficiently long compared to the rotation radius of the drive link control (52). ) The reciprocating motion of the drive rod (211) is transmitted to the trough aU through the rubber pushpiece (17aX17b), and the trough Qυ vibrates in the horizontal direction as shown in FIG. 9A. When the section control member (4) rotates at a constant speed at an angular velocity ω, the follower link member (44) rotates at an inconstant speed as described above, and as a result, the trough 0υ moves in the horizontal direction as shown in Figure 9A. Although it vibrates, its displacement is not sinusoidal, and if differentiated, it changes as shown in Figure 9B, and if further differentiated, it changes as shown in Figure 9C.In other words, the velocity and acceleration of the trough 0υ [t + Figures 9B and 9C] This changes as shown in Figure 9C, but this causes a relative movement as shown in Figure 9B between the side slope on the transfer surface of the trough Q and the transfer surface of the 0 trough. , the transfer speed of the fine particles changes as shown by the dotted line.Here, assuming that the friction coefficient μ between the transfer surface of the trough Ov and the U material is 0.3, 6°, such a graph can be calculated theoretically. can also be obtained experimentally. (1
In the rotational phase of ), the side slope slides in the positive direction with respect to the trough 01), and in the rotational phase of ([), it slides in the negative direction with respect to the trough Qυ. In addition, in the rotational phase of 1), the trough moves by 1υ with the trough aυ, and in the rotational phase of transport, the trough Ov
Move the vector in the negative direction with respect to K. In steady state, then (
V) (b) Similar "normal slip" at the rotational phase of cvii
"Negative slip""Adhesion" [Negative slip pJ all the way, repeat this phenomenon, and since the vector to be corrected in the cycle is larger than the negative slip, in the end, the material is 12 crn
The reciprocating movement of the trough (11) moves in the forward direction of the stopper with the stroke of .
As is clear from the figures and Figures 8A to 8D, the side slope advances to the left in Figure 2. In other words, in this embodiment, the left direction in FIG. 2 is the positive direction.In this embodiment, the reciprocating motion is obtained from the movable link member 2 on the bar.・In order to change the stroke of the trough 01, it is preferable to obtain a reciprocating motion from the drive link part 521 as in this embodiment. .That is,
Various lengths of the dynamic link are prepared, and the drive link for the desired stroke is selected each time, and the rotation axis (4'0 and shaft (26) are connected) (52c) (52d)
) so that the displacement can be changed by changing the stroke without changing the mode of motion of the trough 0υ.

Therefore, it becomes easy to adjust the transfer speed of the side slope. In addition, when changing the drive link part phase 62, the length of the movement rod circle can be changed by adjusting the nut (2).In addition, in the above embodiment, the rotation of the electric motor (2) is changed. Since the large pulley (301) is used for deceleration, when the reciprocating drive unit +27 is to be fully started or stopped, the large pulley (30) can move smoothly as the flywheel plow. reactor.

10 to 12 show a vibrating conveyor according to another embodiment of the present invention. In the figures, parts corresponding to those in the above-described embodiment are denoted by the same reference numerals, and detailed explanation thereof will be omitted.

That is, this embodiment differs from the above-mentioned embodiments in that the reciprocating drive unit (2
7) and the trough Qη, but otherwise are completely the same. As shown in Figures 1O and 11, the driving force of the drive link member 7 is connected to the second drive rod (721,
It is transmitted to the trough (I〃) via the swinging lever (6G) which is swingably supported and the first driving rod (G3'i). Similarly, the coupling ring (2 pieces), the bearing (25) and the shaft C1
It is connected to the drive link members 2 through 61ffi, and the other end is connected to the swing lever ((:0) via the coupling ring member f'10. The swinging lever 6) is fixed to a rotating shaft (Ufl) supported by a pair of bearings (67) +619 fixed to the pillars (71a and 71b).Thereby, the swinging lever (66) It is said to be able to swing freely around the axis of t8B. One end of the first drive ring (65) is pivoted to the upper end of the swing lever Q; G) via the coupling ring part 14. , the long end is the same as in the above-mentioned embodiment, with a connecting link (Ii row, rubber push, tG2), a bin j61), a pair of connecting parts tJ (
GOa%60b) and reinforcing member (trough u through 8υ
According to this embodiment, as shown in FIG. Part 1'
The distance L', tS to the center of (61fto) is 1:2. Therefore, in order to provide the same stroke of 12 crnk as in the first embodiment, the rough 0υ, the second drive rod (7 strokes) must be driven with a stroke of 24 crnk, which is twice that of the first embodiment.
The radius of rotation of the drive link side 62 that drives the drive rod (7), that is, the axis (4n), must be twice as long as that in the first embodiment, but in order to make the diagram easier to understand, the drive link in Fig. 11 is The member Q'i2+e is shown in the same size as in FIG.

When the electric motor (2e) is fully rotated, the reciprocating drive unit (27) operates in exactly the same manner as in the first embodiment, and the second drive rod (7) reciprocates, thereby causing the swinging lever (6G) to move around the rotation axis. It swings around the circumference as shown by the arrow in Fig. 12. 1st ff
The i-driving rod is thus the driving rod G of the first embodiment.
It reciprocates with the same stroke as 11l, and the trough Qv vibrates as shown in the graph of FIG. Therefore, the action on the material on the trough Qυ is exactly the same as in the first embodiment.

According to this embodiment, the stroke of the trough 0υ can be changed by changing the swing lever (6e) in addition to the drive link member @, and the following effects are also achieved.

That is, if the length of the swing lever (6(i)) is long enough, the movement of its upper end can be made very linear.

This allows the first drive rod to be brought closer to the bottom side of the entire trough Ov. On the other hand, in the first embodiment, since the connection point between the drive link member 521 and the drive rod 0υ rotates around the axis (4η) with a radius of half the predetermined stroke, the drive rod (211) must be far apart.

Therefore, the first (/J drive 1υ rod 165) is
Bin (1; υ sword 1 etc. trough Qv J
Distance 1 at +M t to l', ff1l Example 1
1) Lough (distance to the bottom of IU) 'flA'L can be made smaller 4). In each embodiment, a vibration force is applied to the trough 1.lυ through the reinforcing member 0(ν(81)'), and the coupling part f
The moment of force related to 91 can be made smaller in this embodiment. This has the effect that the mechanical strength of the trough Ov at this connection point may therefore be smaller.

On the other hand, when the trough (lvke!vII6) is supplied with a side tilt, a large reaction force is applied to the ground side pivot point with the rocking lever ([i61] via the connection part with the first drive rod Qi5). 11, but since t::t't-t:2, this reaction force is halved and applied to the pivot point on the to side.From this, the second drive rod (/7)' is applied. The reaction force applied to the reciprocating drive unit (27) through the blade is reduced by half in the sword of this embodiment compared to the first embodiment.In other words, a more stable driving action can be guaranteed. Although each embodiment of the present invention has been described, 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, each link constituting the two-crank mechanism has a length of 1. ．． 11, tl, t4 9crn each
, 7.5 crn, 9 side, and 4.50, but of course, the lengths are not limited to these, and various lengths can be used as long as the conditions for the two-crank mechanism are met.

Furthermore, in the above embodiment, the rail members (12a) (12b) and rollers (15a) (15b) were used to support the trough (+υ) in a reciprocating manner, but instead of these, the trough (11)'e It may also be supported on the foundation with leaf springs or coil springs.

Furthermore, in the above embodiments, the drive rods are connected at the bottom of the trough Ov, but instead, they may be connected at one end or side of the trough Ov.

As described above, according to the structure of the vibrating conveyor of the present invention, it is possible to transfer parts or products by vibrating the trough parallel to its transfer surface, so that Compared to the J daytime conveyor that transfers monthly parts or parts, the noise can be reduced, there is no problem with the noise caused by cracks or cracks of materials or parts, and the transfer speed is even higher. This is what FIJ is capable of.

[Brief explanation of drawings]

Fig. 1 is a principle diagram of a 62 crank mechanism applicable to an embodiment of the present invention, Fig. 2 is a circular view of a photographing conveyor according to an embodiment of the present invention, and Fig. 3 is a diagram of the second diagram of the same conveyor. B-key I-1
#, i+% cross-sectional view, Figure 4 is the second section of the same conveyor.
5th enlarged cross-sectional view in the direction of arrow 61V-IV in the figure.
The figure is an enlarged partially broken side view of the main part of the conveyor, Figure 6 is an enlarged cross-sectional view taken along the line Vl-Vl in Figure 4, and Figure 7A is an enlarged side view taken along the line vITA-X'nA in Figure 4. 7B to 7D are enlarged sectional views similar to FIG. 7A for explaining the operation of this embodiment together with FIG. 7A, and FIGS. 8A to 8D are enlarged sectional views in the same direction as FIGS. 7th D
Principle diagram for explaining the operation of this embodiment with figures, No. 9
10 is a side view of a vibrating conveyor according to another embodiment of the present invention, and FIG. 11 is a graph showing the action of the present embodiment, and FIG. The enlarged sectional view and FIG. 12 are enlarged side views of the main parts of the conveyor. In the figure, (tυ・・・・・・・・・・・・・・・・・・・
・ Tora )(,12a)(
12h)・・・・・・・・・ V-ru member (138Xi
3b)......... Support pillar (15a) (15b)
) ・・・・・・・・・ B −
La (17a) (17b) (60a) (60b) ・-
==,,-coupling member Qllil (6υ・・・・・・・
... Song/Bin (1113...
・・・・・・Song・・・・ Rubber Pussy (4) (24
) (fi3)・・・・・・・・・・・・・・・ Connecting ring (2 totes・・・・・・・・・・・・・・・・ Song Drive rod C25)・・・・・・・・・・・・・・・・・・・・・
・・Song Hair Ring (26)・・・・・・・・・・・・・
・・・・・・・・・・Drive shaft C force・・・・・・・・・・
・・・・・・・・・・Song Reciprocating drive part (blade...
···················Electric motor(
4 moats・・・・・・・・・・・・・River・・Song Origin link members (4 moats・・・・・・・・・・・・・・・・・・
・・・・・・ Intermediate link parts (published・・・・・・・・・・・・
・・・・・・・・・・・・ Subordinate link moderation (47)・
··················· rotate
Axis G2・・・・・・・・・・・・・・・・・・
・ Drive link side 65)
・・・・・・・・・ 1st drive Rondo 1Gtj...
・・・・・・・・・・・・・・・・・・・ Rock M V Bar (Scream (70)
Combined link moderation (7″4・・・・・・・・・・・・・
・・・・・・・・・・・・ 2nd driving rod representative Yasuo Iisaka Figure 1 Figure 6 Figure 7A Figure 7D Figure 8A Figure 8B

Claims (1)

[Claims] (17) A trough supported in a reciprocating manner and extending linearly; a driving rod extending parallel to the trough and coupled to the trough; a one-part link, a fixed link, a follower link, and an intermediate link; a reciprocating drive unit equipped with two sets of crank mechanisms formed by links; and a rotational sound angle tI of the follower link obtained by rotating the one-piece link at a constant speed.
(2) a trough that is supported in a reciprocating manner and extends linearly;
six drive rods extending parallel to the trough and coupled to the trough; a reciprocating drive unit comprising two sets of crank mechanisms formed by a one-piece link, a fixed link, a follower link and an intermediate link; the follower; It is characterized by comprising a drive link coaxially fixed to the link, and the rotation of the drive link obtained by rotating the one part at a constant speed is converted into a straight line and transmitted to the drive rod. vibrating conveyor. (3) a trough supported so as to be reciprocally movable and extending linearly; a first drive rod extending parallel to the trough and coupled to the trough; supported so as to be swingable in the direction of the first drive rod; a swinging lever having the first ffiiIJI rod pivotally attached to its upper end; a second drive rod pivotally mounted to the lower end of the swinging lever and extending parallel to the trough; a one-piece link, a fixed link, a follower; a reciprocating drive unit including a two-set crank mechanism formed by a link and an intermediate link;
The rotation of the follower link obtained by rotating the one-part link at a constant speed is converted into a straight line and transmitted to the first drive rod via the second drive rod and the swing lever. A vibrating conveyor with all the features.