JP2501996Y2 - Supply feeder for combination scales - Google Patents

Description

[Detailed description of the device]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a feed feeder for a combination scale which feeds out and feeds articles by vibration based on a magnet and a leaf spring.

[0002]

2. Description of the Related Art Conventionally, in this type of feed feeder for combination weighers, articles having particularly poor feed characteristics, such as broiler meat, pickles, umeboshi, raw sashimi, gummy candy, cut vegetables, and porridge. . The reasons why the feeding characteristics of these articles are poor are as follows:
As shown in Table 1.

[0003]

[Table 1]

In the conventional feeder, the tray 1 is supported by the upper frame 2 as shown in FIG. 7, and the lower end of the upper frame 2 is supported by the bed 4.
It is connected and supported by a plurality of leaf springs 3 fixed to. The magnet coil 6 is provided on the bed 4, and the movable core 5 is attached to the upper frame 2 with a gap t ₁ .

In the vibrating surface shown in FIG. 7 including the feeding direction for feeding and feeding the article in the vibration based on the leaf spring 3 and the magnet coil 6, the leaf spring 3 is The magnet coil 6 is arranged on the side opposite to the feeding direction with an inclination of 20 °, and the magnet coil 6 is arranged so that its attracting direction is horizontal to the vibrating surface.

[0006]

In the case of the feed feeder 1A having such a structure, it is desirable that the tray ₁ has a large amplitude (one-sided amplitude) γ ₁ for an article having a poor feed characteristic. As a component for separating from the one surface, it is desirable that the vertical vibration component h ₁ is large. In the conventional feed feeder 1A, the tray amplitude γ ₁ = t ₁ cos 20 ° = 0.9397t ₁ vertical vibration component h ₁ = γ ₁ sin 20 ° = 0.321t with respect to the gap t ₁ between the movable core 5 and the magnet coil 6. ₁ is smaller than the method of the present invention described later.

In the present invention, for the purpose of solving such a problem, a combination scale capable of increasing the amplitude of the tray and increasing the vertical component of its vibration component for articles having poor supply characteristics. It is to provide the supply feeder.

[0008]

In order to achieve the above-mentioned object, the supply feeder for combination weigher according to the present invention is the same as the supply feeder for combination weigher which feeds out and supplies articles by vibration based on a magnet and a leaf spring. In a vibrating surface including a feeding direction for feeding and feeding the article in the vibration based on the magnet and the leaf spring, the attraction direction of the magnet is inclined by a required angle on the side opposite to the feeding direction with respect to the perpendicular line on the vibrating surface. And arrange the magnet like
Further, the leaf spring is provided so as to be inclined to the side opposite to the feeding direction with respect to the perpendicular line on the vibrating surface beyond the required angle.

[0009]

According to the present invention having such a structure, the amplitude of the tray can be amplified and the vibration component in the vertical direction becomes large, so that even an article having poor supply characteristics can be smoothly supplied at a desired speed. become.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A concrete embodiment of the feed feeder for combination weigher according to the present invention will now be described with reference to the drawings.

FIG. 1 is a front view of a feed feeder for a combination weigher according to the present invention, and FIG. 2 is an AA line in FIG.
It is a perspective view. In these figures, the tray 10 is a leaf spring 14, 14 whose bottom end is attached to the upper frame 13 by attaching the lower end of the attachment piece 12 fixed to the center of the lower surface thereof to the bed 15. The upper end of the upper frame 13
Is supported by the required height. Further, the movable core 16 is attached to the lower surface of the upper frame 13, and the magnet coil 17 is mounted on the bed 15 by the movable core.
They are fixed to each other at 16 and a required gap t ₂ via a support piece 18. In the figure, reference numeral 19 is a buffer coil spring,
As shown in FIG. 2, two beds are provided on the front side of the bed 15 (the direction in which the articles are sent out by the tray 10 is taken as the front) and one on the back side.

As for the magnet coil 17 and the movable core 16, the direction of attraction of the magnet coil 17, as shown in FIG. 1, is a feeding direction a for feeding and feeding articles in vibration based on the leaf springs 14 and 14 and the magnet coil 17. In the vibrating surface including the above, it is attached so as to be inclined at a required angle, for example, 15 ° with respect to the perpendicular to the vibrating surface, on the side opposite to the feeding direction a. Also, the leaf springs 14 and 1
Similar to the magnet coil 17, 4 is assembled by inclining it at a required angle, for example, 45 ° with respect to the perpendicular. By doing this, the direction of attraction of the magnet coil 17 and the tray
The vibration direction of 10 is an intersection angle of 60 °.

With such a structure, with respect to the gap t ₂ between the magnet coil 17 and the movable core 16, the tray amplitude γ ₂ = t ₂ 1 / cos60 ° = 2t ₂ vertical vibration component h ₂ = γ ₂ cos 45 ° = 1.414t ₂ . Thus, in comparison with the conventional method described above, when the gap t ₂ between the magnet coil 17 and the movable core 16 is the same, the possible amplitude of the tray 10 is γ ₂ / γ ₁ = 2t / 0.9397t. = 2.13 times, the amplitude component of the vertical direction is _{h 2 / h 1 = 1.414t /} 0.321t = 4.4 times. However, when the gap t is the same, the component of the force in the vibration direction of the tray becomes as weak as 1 / 2.13. Therefore, when the same force component is required, a 2.13 times stronger magnet coil is required. However, this 2.13
In order to realize the double amplitude condition by the conventional method, it is necessary to increase the gap by 2.13 times, but the attractive force of the magnet coil 17 becomes weaker in proportion to the square of the gap. 17 requires 2.13 times the strength of the square. As described above, in order to increase the amplitude by 2.13 times, the method of the present invention can increase the strength by 2.13 / 2.13 ² = 1 / 2.13 compared with the conventional method.

Further, a large vertical vibration component is particularly effective for handling articles such as being soft and absorbing vibration, having a low bulk density absorbing vibration, and being attached to a tray. Therefore, the gap between the movable core 16 and the magnet coil 17 is larger than that of the conventional method.
When t is the same, it is effective as 4.4 times.

Further, when the article is cast away from the distance, the vibration direction thereof is theoretically the maximum inclination angle of 45 ° with respect to the horizontal direction, which is a conveyance efficiency as compared with 20 ° in the conventional method. More effective. This also has an advantageous effect on articles that are moist and slip on the surface of the tray 10.

Next, as shown in FIG. 3, a leaf spring is used instead of the coil spring 19 as a supporting means in the supply feeder.
This is a configuration using 25, 25 '. The tray 10, the upper frame 13, the magnet coil 17 and the movable core 16,
The leaf springs 14 and 14 have the same structure as that of the specific example. As shown in FIGS. 3 to 5, the support means for supporting the base 20 of the bed 15 includes a support fitting 22 and a support leg piece 15 ′ fixed on the base 20, and a support fitting 23 and a mounting fitting 24. Using the leaf springs 14 and 14 with the same inclination as the supporting leaf springs 25 and 25 'as the center of gravity position G ₁ ′ of the sprung weight and the center of gravity position G ₂ ′ of the unsprung weight, the both center of gravity positions G ₁ ′, The center of gravity G ₃ 'is integrated and supported on the line of action C in the vibration direction passing through G ₂ '. Incidentally, it is supported in relation to the distance J ₁ = J ₂ from the line of action C until a perpendicular direction to the supporting plate springs 25, 25 'support points (the point) b, b' in this state.

As shown in FIGS. 5 (a) and 5 (b), the front side supporting leaf spring 25 is bolted to a supporting metal member 22 having one end fixed to the base 20 side and the mounting surface inclined at a required angle. Presser foot 2 with 27
7'and the bed 15 side is attached to the mounting seat 15a of the support arm 15 'which is protruded outward by bolts 27 with a presser foot 27'.
Is fixed through. In addition, this supporting leaf spring 25
Are attached without contact with other members except for the attachment seat portion 15a of the support arm 15 'and the attachment portion of the support fitting 22. Further, the inclination angle of the supporting leaf spring 25 is set to the same inclination angle as that of the leaf spring 14, specifically 45 °.

The rear supporting leaf spring 25 'is fixed at its lower end to a supporting metal fitting 23 fixed to a base 20 having a wide inclined surface similar to that of the front supporting metal fitting 22 and its upper end to the base 15. It is fastened with a bolt 27 to a mounting bracket 24 attached to the rear end.

The reason why the supporting leaf springs 25, 25 'are used for supporting is as follows.

As shown in the above specific example (FIG. 1), in the supply feeder having a structure in which the upper side of the bed 15 is supported and buffered by the coil spring 19 on the base, the spring constant of the coil spring 19 (vibration direction The rigidity) is much smaller than the leaf springs 14, 14 supporting the tray 10. The smaller the spring constant is, the less the vibration force is transmitted to the base.

As shown in FIG. 6, the tray 10 which is the spring weight of the leaf springs 14 and 14 is used in the normal vibrating feed feeder.
And the center of gravity G ₂ between the center of gravity G ₁ and bed 15 and the magnet coil 17 of the upper frame 13, the vibration direction of the tray 10 is on a straight line (this example 45 ° from the horizontal direction). If the position of the center of gravity between the tray 10 and the upper frame 13 is at the point D and is separated by E from the straight line, the vibration force F ₁ and the distance E are applied to the tray 10 and the upper frame 13. The pitching moment M ₁ = EF is generated, and the tray 10 becomes a vibration that is a combination of the vibration in the vibration direction of the leaf spring 14 and the pitching vibration, which is the original purpose. This component of pitching vibration is harmful to the original purpose of supply and conveyance. in short,
The center of the pitching movement is at point D, and the effect of the pitching movement is small in the vicinity of that point, so the goods are transported close to normal, but at the front and rear edges of tray 10, vertical movement occurs in proportion to the distance from point D. It becomes large and the transport efficiency is significantly reduced.

Further, the coil spring a comprehensive center of gravity position of the weight and unsprung weight spring from When G _3, the gravity center position G ₃ points
The horizontal distances H ₁ and H _{2 in} the transfer direction up to 19 are almost matched in the figure, but they are arranged in a circular direction in the feed feeder used for the combination weigher, so the coil spring 19 is normally transferred due to the space. 2 in the front of the direction, 1 in the rear
Individually arranged. Further, the same coil spring 19 is usually used in terms of cost. Therefore, since there is only one rear coil spring 19, the subsidence amount of the spring is double that of the front coil spring 19, and the front portion of the tray 10 is lifted in a static natural state.

Although it is desirable for the coil spring to be soft from the viewpoint of vibration absorption, if the coil spring is too soft, the sinking amount becomes large due to the self-weight of the supply feeder, and in order to prevent the pitching movement as described above, a certain spring constant is required. You need strength. Also, due to manufacturing cost and other factors, the same coil spring is often used even if there is a slight difference in the feeder capacity, and due to the mounting space, the coil spring wire rod diameter selection conditions, etc. It is difficult to arbitrarily design the spring constants in the vertical direction and the horizontal direction. Generally, a spring constant having a weaker horizontal direction than a vertical direction is used.

It is desirable that the vibration direction of the feeding feeder for handling articles having bad feeding characteristics is 45 ° with respect to the conveying direction, that is, the amplitude between the vertical direction and the horizontal direction is 1: 1. In such a case, the amplitude of the unsprung side is larger than that of a normal article, so the difference in the spring constant between the vertical direction and the horizontal direction of the coil spring is the vibration of the unsprung weight side. The direction becomes the difference between the vertical direction and the horizontal direction, and the difference becomes the direction difference on the sprung weight side (tray) relatively,
It will not be 1: 1. In other words, the vertical direction, which is the hard direction of the coil spring, becomes larger than the horizontal direction, which defeats the intended purpose.

When the action points b and b'of the coil springs 19 and 19 of the bed 15 are defined with respect to the action line C of the vibration force of the center of gravity positions G ₁ and G ₂ of the sprung mass portion and the unsprung mass portion, Distances J ₁ and J ₂ are perpendicular to line C. Now, temporarily, coil spring 19,1
Assuming that 9 has the same spring constant before and after, and the reaction force from the coil springs 19 and 19 at the points of action b and b ′ due to the vibration of the bed 15 is equal to F ₂ before and after, K = J from the action line C. ₁ -J _2/2
The same as the force of 2F ₂ worked at the position of
15 has coil springs 19,19 and M ₂ = 2F ₂ · K = F ₂ (J ₁ -J ₂ )
Will be transmitted to the bed 15 (unsprung weight side). As described above, this pitching motion phenomenon is not preferable.

On the other hand, it is theoretically possible to change the distribution ratio of the spring constants of the coil springs 19 and 19 in the front-rear direction and bring the center of the reaction force from the coil springs 19 and 19 onto the action line C. Even so, it is important to bring the center of the reaction force on the line of action C like this, because of the vertical direction, the horizontal direction and the space.
It is difficult to realize the design by changing the mounting position.

In the above description, the explanation has been made on the assumption that the line of action C of the center of gravity of the sprung mass and the center of gravity of the sprung mass are in agreement with the vibration direction, but there is some deviation E of the working point, and the tray E There is always an unnecessary factor that causes pitching due to changes in the plate thickness of 10, changes in the shape of the tray 10 due to other factors such as the flow of goods, etc., and as long as a coil spring is used for the vibration buffering support, tray pitching movement is prevented. Is difficult to do.

In the present invention, as described above, the coil spring 1
By using the supporting leaf springs 25, 25 'instead of 9,19, the supporting leaf springs 25, 25' constitute the principle of the Robaval mechanism, so all movements are parallel movements. The subduction amount is constant irrespective of the total center of gravity position G ₃ 'of the feed feeder and the respective positions of the tray, and the tray 10
The front-down and front-up phenomenon, that is, the pitching motion does not occur. In particular, the front and rear supporting leaf springs 25, 25 'are easier to balance design of the spring constants as compared with the coil spring.

Supporting leaf springs 25, 25 'and vibrating leaf springs 14, 1
4 and 4 and the front and rear support leaf springs 2
By arranging the action points b and b'of the supporting part of 5,25 'symmetrically with the action line C of vibration, the action line C of the center of gravity of the vibrating body and the reaction force of the supporting leaf springs 25, 25' It is possible to easily match the center position of the point in terms of design calculation and design placement, and to prevent the occurrence of unnecessary pitching motion due to the deviation between this line of action and the center position of the point of reaction of the reaction force. You can

Further, since the supporting leaf springs 25, 25 'constitute a Roberval mechanism, the difference between the spring constants in the vertical direction and the horizontal direction, which is a drawback of the conventional type, is that the leaf springs 14, 14 are inclined. The angle is 1: 1 as long as the angle is 45 °, and it is easy to deal with the design without worrying about the imbalance between them as in the case of the coil spring.

Further, even if the lines of action of the centers of gravity of the sprung part and the unsprung part are not coincident with each other, or the pitching factor is generated by changing the shape or weight of the tray, the supporting leaf springs move in the pitching direction. Since it has a spring constant close to infinity, it does not cause unnecessary pitching motion in the tray.

[0032]

As described above, according to the present invention, the amplitude of the tray can be increased and the vibration component in the vertical direction can also be increased to improve the movement performance.
It has been used successfully to deliver articles with poor delivery characteristics.

[Brief description of drawings]

FIG. 1 is a front view of a first embodiment of a feed feeder for a combination scale according to the present invention.

FIG. 2 is an AA view of FIG.

FIG. 3 is a front view of a second embodiment of the feed feeder for the combination scale according to the present invention.

4 is a BB view of FIG. 3. FIG.

5A and 5B are detailed views showing a mounting portion of the supporting leaf spring of the second embodiment shown in FIG. 3, where FIG. 5A is a front view and FIG. 5B is a side view.

FIG. 6 is a diagram illustrating a problem in the case of a buffer support structure using a coil spring.

FIG. 7 is a front view showing a specific example of a conventional supply feeder.

[Explanation of reference numerals] 10 tray 12 mounting piece 13 upper frame 14 leaf spring 15 bed 15 'support arm 16 movable core 17 magnet coil 18 supporting piece 19 buffer coil spring 20 base 22, 23 supporting metal fitting 24, mounting metal fitting 25, 25 'Support leaf spring 27 bolt 27' Presser foot

Claims (1)

(57) [Scope of utility model registration request] 1. A feed feeder for a combination scale for feeding and feeding an article by vibration based on a magnet and a leaf spring, wherein the vibration in a vibration plane including a feeding direction for feeding and feeding the article in the vibration based on the magnet and the leaf spring. The magnet is arranged on the side opposite to the sending direction with respect to the vertical line on the surface so that the attraction direction of the magnet is inclined by a required angle, and further exceeds the required angle with respect to the vertical line on the vibrating surface. The feed feeder for the combination scale, wherein the leaf spring is provided so as to be inclined on the side opposite to the feeding direction.