JPS641367B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vibrating bowl type feeder used for automatically feeding small parts and other articles, and particularly relates to a vibrating bowl type feeder in which a motor is used as a drive source and a bowl vibrates in an elliptical manner. be.

Conventionally, an electromagnet (solenoid) is driven to automatically align parts or other articles such as powder or granular materials or to supply them in required amounts to automatic manufacturing equipment such as automatic assembly machines, automatic processing machines, or automatic packaging machines. Vibrating bowl type feeders are widely used. This type of vibrating bowl type feeder supports a cylindrical or dish-shaped container, i.e., a bowl, into which parts and other items are placed, with several sets of leaf springs tilted at a certain angle, and a piece of iron (armature) at the bottom of the bowl is supported by a solenoid. At the same time, the bowl is vibrated vertically and angularly vibrated, that is, horizontally vibrated, around the vertical axis by a leaf spring, and the combined vibration in the diagonal direction is applied to the bowl. As a result, the parts and other items in the bowl are transported upward along the spiral track provided on the inner wall surface of the bowl, while being aligned by attachments etc. attached to the periphery of the track, and are transported upward from the outlet at the top of the track. Sent out.

However, the above-mentioned angular vibration is caused as a result of vertical vibration, and there is no phase difference between the two vibrations. Therefore, the diagonal vibration that is a combination of both vibrations becomes a linear simple vibration in the direction perpendicular to the leaf spring. For this reason, backward slippage tends to occur between the transported article and the raceway surface, and even if the vibration frequency or amplitude is increased, it is difficult to obtain a corresponding effect. Moreover, the frequency of vibration is determined by the power supply frequency, and if the amplitude is too large, parts separated from the raceway surface will not be able to maintain contact with the raceway surface after colliding with the raceway surface, resulting in unstable movement, which will reduce efficiency. decreases.

In order to eliminate these drawbacks, a method and device were developed that used two sets of support springs and solenoids, one for angular vibration and one for vertical vibration, and caused both solenoids to vibrate with a phase difference, thereby producing vibrations in an elliptical trajectory. (For example, Japanese Patent Publication No. 44-4289,
(Japanese Patent Publication No. 44-32368), it has a complicated structure, is difficult to adjust, and is expensive, so it is rarely used in general.

In other words, this type of vibration using a support spring and solenoid utilizes the natural vibration of the entire part supported by the leaf spring, such as the bowl or armature, including the article, but the frequency of the solenoid, which is the driving source, is as described above. In order to obtain a certain value determined by the power supply frequency, the strength of the support spring must be determined so that both frequencies match, taking into account the shape and weight of the bowl, and the unbalance of attachments and parts. In addition, adjusting the gap between the armature and solenoid (air gap) and the mounting angle of the support spring that controls the feed rate is a one-piece manufacturing process that requires extremely high skill. It is complicated and expensive. Therefore, it is clear that the above-mentioned device using two sets of these is extremely difficult to adjust. In addition, the natural frequency of the system supported by the leaf spring constantly changes depending on the amount of parts in the bowl, resulting in a gap with the frequency of the solenoid, resulting in fluctuations in performance. Furthermore, the entire device is supported by anti-seismic rubber and vibrates in the opposite direction to the bowl. Suppressing that vibration would reduce efficiency, so attachments installed from outside the bowl cannot be extended from the base of the device, and However, once the equipment is installed, it is difficult to move.

Therefore, as a result of extensive research, the inventor of the present invention found that instead of supporting the bowl with a leaf spring and driving it with a solenoid, which has various drawbacks, the bowl is supported on a base with a link or ball screw, etc., and the motor is used as the drive source. We have developed a vibrating bowl type feeder that operates well. (Patent Application No. 53-77683 (Japanese Patent Application No. 55-7126)
issue)).

The present invention is a further improvement of the motor-driven vibrating bowl type feeder, which uses a motor as the drive source and has an extremely simple structure, which applies vibration to the bowl in an inclined elliptical locus, enabling highly efficient and accurate transportation of articles. A vibrating bowl type feeder is provided.

Hereinafter, the present invention will be explained in detail based on embodiments shown in the drawings.

Figures 1 to 5 show an example of a vibrating bowl type feeder according to the present invention, in which a horizontal diaphragm 3 is installed at the bottom of a main shaft 2 which is rotatably inserted and supported in the center of a base 1 with a ball bearing 8 or the like. A diaphragm 5, which supports and fixes the bowl 4, is rotatably and vertically movably supported on the upper part of the main shaft, and the horizontal diaphragm 3 and the diaphragm 5 are connected by links 6, and a motor is used as a drive source. The drive device applies angular vibrations with a phase difference (the frequencies are the same) to both diaphragms 3 and 5. Incidentally, the bowl 4 may be formed integrally with the diaphragm 5.

The horizontal diaphragm 3 is fixed to the main shaft 2 so that its central axis serves as the center of rotation, and the diaphragm 5 is inserted and supported on the upper part of the main shaft 2 via an oil-free bearing 9 that is rotatable and slidable. The holder 10 is fixed to the holder 10 so that its center axis becomes the center of rotation, and a bowl 4 for arranging and transporting articles is attached and fixed to the upper surface of the holder 10. It is also possible to use a rotatable and slidable bearing in place of the oil-free bearing 9, or to support the peripheral portion or the lower surface so that it can move up and down and rotate.

Note that the bowl 4 may have a bottom, but
As shown in the figure, the bottom of the bowl may be cut out in a circular shape, and a separation bottom plate 11 may be attached to the upper end of the main shaft 2, which fits into the bottom of the bowl with a slight gap left in the cutout. In this way, the load of the articles on the separation bottom plate 11 is not applied to the holder 10 or the bowl 4, but directly to the base 1 via the main shaft 2, so even if a large amount of articles are thrown into the bowl, the motor 7 will not be affected. The result is that it does not impose a large burden. Furthermore, this separation bottom plate 11
When the auxiliary hopper 12 is installed on top of the hopper 12 as shown in FIG. 4, even if a large amount of articles are thrown into the auxiliary hopper 12, there is no load on the motor 7, and only the optimum amount of articles are always fed into the bowl 4 little by little. will be supplied to

At this time, if the separation bottom 11 is fixed to the upper end of the main shaft 2, the separation bottom 11 angularly vibrates in the horizontal direction together with the horizontal diaphragm 3 and, in turn, the main shaft 2, to easily move the article to the periphery of the bowl. Particularly when the auxiliary hopper 12 is provided, articles can be smoothly fed from the auxiliary hopper 12 to the bowl 4.
In addition, in the figure, 41 is the outlet of the bowl 4, 42 is the orbit,
Reference numeral 101 denotes a vibration-proof plate made of rubber or the like fixed to the lower surface of the base 1.

In the above embodiment, the main shaft 2 is fixed to the base 1,
The horizontal diaphragm 3 can also be modified such as being rotatably attached to the main shaft with a ball bearing 8.

Next, the link 6... is connected to the horizontal diaphragm 3 and the diaphragm 5.
It functions as a vertical vibration mechanism that moves the diaphragm 5 up and down by the relative rotation of the diaphragm 5, and several (three in the figure) are used. This link 6 has ball sockets at both ends and its length can be adjusted, and connects both ends to the diaphragms 3 and 5 with its axis tilted by θ in a vertical direction opposite to the transport direction of the article. This connects the two together and supports the diaphragm 5 at the same time.

The drive device includes a motor 7 fixed to the side of the bowl 4, an eccentric shaft 14 attached to the shaft of the motor 7 via an adapter 13, and a crank supported pivotally on the eccentric shaft 14 via bearings 15 and 16. Board 17,1
8 and tie rods 19 and 2 that connect the crank plates 17 and 18 to the horizontal diaphragm 3 and diaphragm 5.
0, consisting of rod ends 21 and 22. motor 7
The motor may be any type of motor such as an electric motor or an air motor, but a variable rotation speed motor is preferable. In this case, the distance between the shaft of the motor 7 and each center of the eccentric shaft 14, that is, the amount of eccentricity d, can be adjusted at the attachment portion between the adapter 13 and the eccentric shaft 14. The tie rod 19 has one end fixed to the crank plate 17 and the other end connected to a rod end 21, which is connected to the horizontal diaphragm 3 via a stay 23. The tie rod 20 has one end fixed to the crank plate 18 and the other end connected to a rod end 22, which is connected to the diaphragm 5 via a stay 24.

Therefore, in the above structure, the motor 7 is
When rotated in the direction (counterclockwise), the eccentric shaft 14
rotates eccentrically with respect to the axis of the motor 7, the crank plates 17 and 18 swing with a width of vibration twice the amount of eccentricity d, giving angular vibration to the horizontal diaphragm 3 and the diaphragm 5. At this time, both tie rods 19 and 20 are attached to the eccentric shaft 1.
4, and both diaphragms 3,
Since the horizontal diaphragms 5 and 5 are mounted so as to rotate in opposite directions, the angular vibration applied to the horizontal diaphragm 3 leads the angular vibration of the diaphragm 5 by π+α in phase. (Let this phase advance angle be φ.)
As a result, due to the action of the links 6, the diaphragm 5 and each portion of the bowl 4 fixed to the diaphragm 5 vibrate along an elliptical trajectory in substantially the same vertical plane.

Next, the form of vibration given to this diaphragm 5 will be explained. FIG. 6 is an explanatory diagram showing the relationship between the horizontal diaphragm 3, the diaphragm 5, and the link 6. Both the diaphragms 3 and 5 are angularly moved by the rotation of the motor 7 with vibration widths of 2d ₁ and 2d ₂ , respectively. Vibrated. However, the width of this vibration is extremely small compared to the radius of both diaphragms 3 and 5, and therefore, certain mass points A and B on both diaphragms 3 and 5 travel along short paths that can be approximately regarded as straight lines. Performs simple harmonic motion. Now, the diaphragm 5 is made only capable of vertical movement without angular vibration, and by rotating only the horizontal diaphragm 3 around the main shaft 2, the angular vibration is generated.
If v ₁ is given, the mass point B on the diaphragm 5 is the 6th
As shown in FIG. 7, vertical vibration V ₁ is generated in the vertical direction with a maximum width e ₁ =2d ₁ ·tan θ by the action of the link 6. This vertical vibration _V1 occurs in the form of a sine curve as shown in FIG. 7 as the eccentric shaft 14 rotates. Next, when the horizontal diaphragm 3 is fixed and angular vibration v ₂ is applied only to the diaphragm 5, the mass point B becomes a simple harmonic vibration V tilted by θ with respect to the horizontal direction due to the action of the link 6, as shown in Figs. 6 and 7. ₂ , and the vertical movement width e ₂ of the vertical component can be expressed as e ₂ =2d ₂ ·tanθ.
In this case, the mass point B moves in a sine curve manner as shown in FIG.

Therefore, angular vibration v ₁ ,
When v ₂ is given, mass point B performs a combined vibration of both V ₁ and V ₂ . When the phase advance angle φ is within a certain range, the resultant vibration causes a vibration V of an inclined elliptical locus in substantially the same vertical plane as shown in FIG. In addition, in Fig. 7, d ₁ = d ₂ = d, the inclination angle θ of the link 6 is 15 degrees, and the angle α between both tie rods 19 and 20 is
It vibrates in the direction of arrow N in the case of 90 degrees, so φ=π+π/2=3/2π.

Each part of the bowl 4, for example, the mass point C, is connected to the diaphragm 5.
Similarly, elliptical vibration is performed by the elliptical vibration V, but the manner of vibration is such that the longer axis direction of the elliptical locus extends outside the position of the stay 24 of the diaphragm 5, and the longer axis direction contracts inside.

The shape of the elliptical vibration V changes depending on the radial position of the bowl 4 as described above, but also depends on the vibration widths 2d ₁ and 2d ₂ of the angular vibrations v ₁ and v ₂ , the inclination angle θ and the phase of the link 6. It changes variously depending on the advance angle φ.

Therefore, the optimum shape of elliptical vibration can be determined depending on the type and shape of the article to be transported, the frictional force with the trajectory surface, the inclination of the trajectory 42, the required transportation speed, and other circumstances. First, when d ₁ is increased, e ₁ is increased, and the short axis of the elliptic vibration V becomes large, and when d ₂ is increased, the long axis becomes large. As described above, this adjustment can be made at the attachment portion between the adapter 13 and the eccentric shaft 14, but in the above embodiments (FIGS. 1 to 5), both d ₁ and d ₂ are increased or decreased integrally at d.

Next, changing the phase advance angle φ is equivalent to changing the angle α between the two tie rods 19 and 20 in the above embodiments (FIGS. 1 to 5). For this purpose, for example, as shown in FIG.
It is better to make the mounting position variable.

8 to 10 show other embodiments of the drive device, and FIG. 8 shows two tie rods 19, 2.
0 is fixed to one crank plate 17, and in this case, the tie rod 20 is fixed in order to release the force caused by minute changes in the angle α and the vertical movement of the tie rod 20.
The link ball 30 is interposed between the two, resulting in an extremely simple structure. However, α is fixed and d ₁ and d ₂ cannot be changed independently.

In FIG. 9, a drive shaft 31 is rotated by a separate belt or the like from the shaft of a motor 7, and adapters 13, 13' and eccentric shafts 14, 14' are attached to both sides _of this drive shaft 31. ₂ can be changed independently. Furthermore, various crank mechanisms other than those described above may also be used.

In Fig. 10, angular vibration is applied to both diaphragms 3 and 5 using a cam instead of a crank type. The signal is transmitted to both diaphragms 3 and 5 via the diaphragms 3 and 5.

FIG. 11 shows another embodiment in which a ball screw 36 is used instead of the link 6 as the vertical vibration mechanism for the diaphragm 5. In this vibrating bowl type feeder, a ball screw 36 is fixed at the center of a horizontal diaphragm 3, and a ball nut 37 that engages with the ball screw 36 is attached to a diaphragm 5.
It has a fixed structure.

However, if the ball screw 36 is used, the lead angle corresponding to the inclination angle θ of the link 6 will remain unchanged and cannot be adjusted. preferable than the case. In addition, the ball screw 36 is connected to the diaphragm 5.
It is also possible to have a structure in which a ball nut 37 that engages with the horizontal diaphragm 3 is fixed to the horizontal diaphragm 3, and the vertical movement of the horizontal diaphragm 3 is prevented.

Furthermore, a cam can also be used as the vertical vibration mechanism for the diaphragm 5. In this case, for example, as shown in FIG. 12, a cam 39 that comes into contact with the roller 38 fixed on the horizontal diaphragm 3 is attached to the lower part or side of the diaphragm 5, so that the two diaphragms 3 and 5 are The rotation causes the rollers 38 to vertically vibrate the cam 39 and, in turn, the diaphragm 5. The inclination angle of this cam 39 can be made variable as in the case of the link 6.

Further, the operating principle of the vibrating bowl type feeder according to the present invention can also be applied to a vibrating straight type feeder. In this case, instead of the angular vibration with a phase difference applied to the horizontal diaphragm 3 and the diaphragm 5, linear vibration with a phase difference may be applied.

As described above, the present invention provides a drive device using a motor as a drive source for a horizontal diaphragm supported horizontally rotatably and a diaphragm mechanically connected to the horizontal diaphragm and supported rotatably and vertically. The diaphragm is forced into angular vibration with a phase difference, and the resulting relative rotation of both diaphragms causes the diaphragm to vibrate vertically in the vertical direction. This makes it possible to apply inclined elliptical vibration within the same vertical plane, which is an ideal type of vibration, to each part of the bowl integrally formed with the bowl. Further, the shape of this elliptical vibration can be changed in various ways according to demand with a simple operation, and parts and other articles in the bowl can be transported quickly and reliably.

Furthermore, since the vibration is forced by a motor, the performance is not affected by the shape and dimensions of the bowl, the number and mounting position of attachments, or the amount of parts inserted into the bowl, and the vibration width and frequency can be freely adjusted. Since it can be selected and easily adjusted, it is possible to arbitrarily obtain the optimum feed speed according to the article and subsequent processes such as the assembly process. In addition, there is no need to use leaf springs or solenoids, and there is no need to electrically adjust the phase difference between horizontal and vertical vibrations, making it extremely easy to adjust the structure, assembly, and use.It is compact and lightweight, and does not require a large amount of power. Therefore, products of stable quality can be obtained in large quantities at low cost, and there is no problem of magnetization of the article due to the solenoid, which has extremely excellent effects.

[Brief explanation of drawings]

1 to 5 show an example of a vibrating bowl type feeder according to the present invention, and FIG. 1 is a plan view, and FIG.
The figure is a front view, FIG. 3 is a sectional view taken along the - line in FIG. 1, and FIG. 4 is a sectional view taken along the - line in FIG. 2.
FIG. 5 is a cross-sectional view taken along the line in FIG. 4 in FIG. 2. Fig. 6 is an explanatory diagram showing the relationship between both diaphragms and the link, Fig. 7 is an explanatory diagram showing the state of vibration of both diaphragms, and Figs. 8 to 10 are outlines of other embodiments of the drive device. The plan view, FIGS. 11 and 12 are longitudinal cross-sectional views of a vibrating bowl type feeder equipped with vertical vibration mechanisms of different diaphragms. 1... Base, 2... Main shaft, 3... Horizontal diaphragm, 4... Bowl, 42... Bowl orbit, 5...
...Diaphragm, 6...Link, 7...Motor, 14,
14'... Eccentric shaft, 17, 18... Crank plate,
19, 20... tie rod, 36... ball screw, 37... ball nut, 38... roller, 39... cam, θ... link inclination angle.

Claims (1)

[Claims] 1 Horizontal diaphragm 3 supported so as to be rotatable and vertically movable about the central axis and below the diaphragm 5 supporting and fixing the bowl 4 so as to be horizontally rotatable about the central axis. and diaphragm 5.
In order to move the diaphragm 5 up and down by the relative rotation of the horizontal diaphragm 3, a cam 39 is disposed between the diaphragm 5 and the horizontal diaphragm 3, or a cam 39 is arranged between the diaphragm 3 and the horizontal diaphragm 3, or the diaphragm 5 is connected by a link 6 or a ball screw 36 and a ball nut 37. , tie rods 19 and 2 connected to both diaphragms 3 and 5, respectively.
0 or the other ends of the rocking rods 34, 35 are connected to a crank mechanism or a cam mechanism rotationally driven by a motor 7 so that both diaphragms 3, 5 horizontally vibrate in opposite directions and with a certain phase difference. A vibrating bowl type feeding machine characterized by having the following configuration.