JP6745684B2 - Vibratory parts carrier - Google Patents

Description

The present invention relates to a vibration type component transfer device that drives a vibrating mechanism to vibrate a component transfer member to transfer a component.

The vibration type component transfer device has a structure in which a linear component transfer path is formed on the upper vibrating body to which the component transfer member is attached and on the floor for the purpose of imparting optimum vibration to the component transfer member. An intermediate vibrating body is placed between the installed base and the horizontal vibrating leaf spring connects the upper vibrating body and the intermediate vibrating body with the horizontal vibrating leaf spring. There is a compound vibration type in which the intermediate vibration body and the base are connected to each other so that the horizontal vibration and the vertical vibration of the component conveying member can be adjusted respectively (for example, refer to Patent Documents 1 and 2). ..

JP-A-55-84707 JP, 11-180525, A

FIG. 6 shows a model of an example of the composite vibration type component transfer device as described above (the vibrating mechanism serving as a vibration source is not shown). The component transfer device includes, as a vibration system, roughly three parts, that is, a part in which a trough (component transfer member) A and an upper vibrating body B are integrated, an intermediate vibrating body C and a base D. The upper vibrating body B and the intermediate vibrating body C are connected by a vertical vibration leaf spring Kb, the intermediate vibrating body C and a base D are connected by a horizontal vibration leaf spring Kc, respectively, and the base D is a vibration-proof spring ( Anti-vibration member) Kd is connected to the floor. Here, for the following description, the component transport direction is defined as the X-axis direction, the horizontal direction orthogonal to the component transport direction is defined as the Y-axis direction, and the vertical direction orthogonal to the component transport direction is defined as the Z-axis direction.

This vibration system can be regarded as a vibration system having two degrees of freedom in vibration engineering. That is, as shown in FIG. 7, two objects m1 and m2 are placed on a friction-free roller on a horizontal table, and one of the objects m1 is connected to a fixed body by an elastic body K1. This is the same as the model in which m2 is connected by the elastic body K2. In the model of FIG. 7, with respect to the free vibration when the displacement of D1 or D2 in the figure is given, the equation of motion can be created by the balance force between Newton's second law and the spring stress by the elastic body, Can explain various situations. If the spring constant of the elastic body K1 that connects the object m1 and the fixed body is so small that it can be ignored, only the elastic body K2 needs to be considered. Further, when the mass of the object m1 coupled to the fixed body is very large, the object m1 hardly moves, so that it can be regarded as a one-degree-of-freedom vibration system in which one object m2 is displaced on one axis.

Based on this, referring to FIG. 6, the vibration-proof spring Kd that connects the base D to the floor is normally set to be sufficiently soft for the vibration system above it, so that its spring action is almost ignored. be able to. Therefore, in the vibration system of FIG. 6, only the above-described three components and the vertical vibration leaf spring Kb and the horizontal vibration leaf spring Kc that connect them need to be considered.

Here, in general, the leaf spring deforms with a constant spring constant in the thickness direction, but has large rigidity in the plane direction orthogonal to the thickness direction and hardly deforms. Therefore, in the component transfer device of FIG. 6, since the horizontal vibration leaf spring Kc and the vertical vibration leaf spring Kb act as elastic bodies in their respective thickness directions, the intermediate vibration body C and the base D vibrate horizontally. Although the plate spring Kc can move in the thickness direction relatively, it moves integrally in the plane direction orthogonal to the thickness direction, and the upper vibrating body B and the intermediate vibrating body C vibrate vertically. Although the leaf spring Kb can move in the thickness direction, it moves integrally in the plane direction orthogonal to the thickness direction.

For example, when only the horizontal vibration exciting mechanism (not shown) is operated in this component transfer device, the trough A, the upper vibrating body B, and the intermediate vibrating body C vibrate integrally, so that these three components (Hereinafter, collectively referred to as "upper member ABC"), the natural frequency (circular frequency) ω _h of the horizontal vibration system formed by the base D and the horizontal vibration leaf spring Kc is expressed by equation (1).

ここで、ｋ_ｃ：水平振動用板ばねＫｃのばね定数、
Ｍ_abc：トラフＡ、上部振動体Ｂおよび中間振動体Ｃの質量の総和、
Ｍ_ｄ：基台Ｄの質量
である。

Here, k _c : the spring constant of the horizontal vibration leaf spring Kc,
_Mabc : Sum of masses of trough A, upper vibrating body B and intermediate vibrating body C,
M _d : Mass of the base D.

Therefore, when the driving frequency of the horizontal vibration exciting mechanism is brought close to the natural frequency ω _{h of the} equation (1), the horizontal vibration leaf spring Kc is greatly deformed, and the amplitude of the vibration of the upper member ABC in the component conveyance direction is increased. growing. At this time, as shown in FIG. 8A, if the distances between the center of gravity G _abc of the upper member ABC and the center of gravity G _{d of the} base D and the center of gravity G _{abcd of the} entire transport apparatus are r1 and r2, then the center of gravity G _abc and Since the vibration forces F1 and F2 act on the center of gravity G _d , moments F1×r1 and F2×r2 are generated around the center of gravity G _abcd . As a result, the entire transporting device performs a rotational movement about the Y axis around the center of gravity G _abcd (hereinafter, referred to as “pitching movement”). The vibration displacements (amplitudes) X1 and X2 of the centers of gravity G _abc and G _d at this time are, as shown in FIG. 8B, magnitudes of a straight line e connecting the entire center of gravity G _abcd and the centers of gravity G _abc and G _d. Is represented. Therefore, it can be seen that the amplitudes X1 and X2 are inversely proportional to the ratio of the two masses.

Next, a vertical vibrating system including a vertical vibrating leaf spring Kb connecting the intermediate vibrating body C, the upper vibrating body B and the trough A will be described. During actual operation, the vertical vibration generated by the vertical vibration system and the horizontal vibration generated by the horizontal vibration system are combined to generate vibration having a required angle and waveform (for example, elliptical vibration). Since the vertical vibration leaf spring Kb differs from the horizontal vibration leaf spring Kc in the coupling direction by 90°, it is naturally displaced only in the vertical direction. Since the vertical vibrating vibration mechanism is not operated here, there is no forced vibration force in the vertical direction. Therefore, as long as there is no mechanical external force, there is no vertical vibration of the upper vibrating body B and the trough A, and only the above-mentioned horizontal displacement should occur. However, since the horizontal vibration system is accompanied by the pitching motion due to the difference in the center of gravity positions of the upper member ABC and the base D, the trough A and the upper vibrating body B are excited with rotational vibration around their center of gravity G _ab. R. The natural frequency (circular frequency) ω _v of this rotational vibration is as shown in equation (2).

ここで、ｋ_ｂ：鉛直振動用板ばねＫｂのばね定数（１ラジアンあたりのモーメント）、
Ｊ_ab：トラフＡと上部振動体Ｂの慣性モーメントの和、
Ｊ_cd：中間振動体Ｃと基台Ｄの慣性モーメントの和
である。

Where k _{b is} the spring constant of the vertical vibration leaf spring Kb (moment per radian),
J _ab : Sum of inertia moments of trough A and upper vibrator B,
J _cd : Sum of inertia moments of the intermediate vibrating body C and the base D.

By approaching the natural frequency ω _v , the trough A and the upper vibrating body B generate large rotational vibration with respect to the intermediate vibrating body C. This vibration force is mechanical due to the pitching motion of the horizontal vibration system. As shown in FIG. 9, if the rotation angle β of the trough A and the upper vibrating body B with respect to the horizontal vibration system at the maximum rotation is equal to the rotation angle α of the horizontal vibration system with respect to the floor surface (the rotation direction is opposite to that of the vertical vibration system). ), the trough A apparently loses the pitching motion on the floor surface, and only horizontal vibration is observed.

By the way, as described above, in order to eliminate the apparent pitching motion of the trough A and realize stable component transportation, the base D can smoothly perform a combined motion of horizontal vibration and pitching motion in the X-axis direction. Therefore, in the conventional component transfer device, the vibration-proof spring Kd that connects the base D to the floor is set sufficiently soft as described above.

However, in the component transfer device using the soft vibration-proof spring Kd, the base D rotates and moves in the Y-axis direction around the X-axis, and the front end of the trough A and the component supply port at the upstream end. The positional relationship between the parts discharge port of the process equipment and the positional relationship between the parts discharge port at the downstream end of the trough A and the parts supply port of the next process device are not within the allowable range, and the previous process and the next process are performed. There is a risk that the parts will not be transferred smoothly between the two and the parts will be clogged.

Therefore, an object of the present invention is to suppress the rotational movement around the X axis and the displacement in the Y axis direction of the base connected to the floor by the vibration isolating member in the complex vibration type component transfer device.

In order to solve the above problems, the present invention provides a component conveying member having a linear component conveying path, an upper vibrating body to which the component conveying member is attached, a base installed on the floor, and the base. A vibration damping member that connects both ends of the platform in the component transport direction to a floor member, an intermediate vibration body provided between the upper vibration body and the base, and a first coupling the intermediate vibration body and the base. Elastic member and a second elastic member connecting the upper vibrating body and the intermediate vibrating body, one of the first elastic member and the second elastic member being a horizontal vibrating elastic member, and the other being the horizontal vibrating elastic member. Is a vertical vibration elastic member, and the horizontal vibration elastic member and the first vibrating mechanism apply horizontal vibration to the component conveying member, and the vertical vibration elastic member and the second vibrating mechanism In a vibration type component transfer device configured to apply vertical vibration to a component transfer member, the vibration isolating member is a stabilizer disposed between the base and the floor member, and the front and back surfaces in the component transfer direction. A first anti-vibration connecting plate that connects the stabilizer and the floor member in a facing position, and a second anti-vibrating connecting plate that connects the stabilizer and the base in a position in which the front and back surfaces are oriented in the component transport direction. Adopted a configuration that consists of.

That is, a vibration isolating member that connects the base to the floor member, a stabilizer disposed between the base and the floor member, and a stabilizer and the base and floor member with the front and back surfaces oriented in the component transport direction, respectively. By configuring with the first and second vibration-proof connecting plates to be connected, the vibration-proof member has a large compliance in the vertical plane (XZ plane including the X axis and Z axis) parallel to the component conveying direction. In addition, it has a large rigidity with respect to the rotational movement (about the X-axis) about the component conveyance direction and the movement displacement in the horizontal direction (Y-axis direction) orthogonal to the conveyance direction. ..

Here, if a configuration is adopted in which a weight that can swivel in a vertical plane (XZ plane) parallel to the component conveying direction is attached to the base, it is possible to easily adjust the swivel position of the weight. It is possible to suppress the apparent pitching movement of the transport member and stabilize the component transport. The operation of this weight will be described below with reference to FIG.

First, in this type of component transfer device, it is necessary to make the trough A of various lengths, materials, and forms according to the parts to be transferred. Differently, the natural frequency of the equation (2) cannot be maintained. On the other hand, as can be seen from the equations (1) and (2), a desired natural frequency can be obtained by changing one or both of the mass (inertia moment) and the spring constant. However, since the spring constant of the leaf spring is usually changed by changing the number of leaf springs, continuous adjustment is difficult. In addition, the operating frequencies of horizontal vibration and vertical vibration are mechanically the same (actually, they are driven by two vibration mechanisms, but the frequencies are also the same) from the above-mentioned mechanism, so efficient operation is possible. In order to perform, the natural frequencies ω _h and ω _v must be set to values as close as possible. Therefore, if ω _{h of the} equation (1) and ω _v of the equation (2) are set equal, the equation (3) is obtained, and if this is modified, the equation (4) is obtained.

From the above equation (4), even if the spring constants k _c and kb of the leaf spring Kc for horizontal vibration and the leaf spring Kb for vertical vibration cannot be adjusted, the relationship between the mass of each member and the moment of inertia can be _expressed by equation (4). It can be seen that efficient operation can be performed if adjustment is made so as to ensure it.

Therefore, if a weight that can swivel in the XZ plane is attached to the base D, even if the specifications such as the length of the trough A change according to the usage conditions, the swiveling position of the weight is adjusted and the base is adjusted. By changing the moment of inertia while keeping the mass of D as a whole constant, the relation of equation (4) is ensured and efficient operation can be performed. In addition, the moment of inertia is changed by adjusting the turning position of the weight because the figure skating player moves his/her open arms toward the trunk side to speed up the rotation (reduce the moment of inertia to save the stored energy). Add to rotation) is the same reason.

Further, if the weight has a horizontally movable portion that can move in the horizontal direction (Y-axis direction) orthogonal to the component transport direction, the component transport member passes through the center of the apparatus in the width direction XZ. If not designed symmetrically with respect to the plane, adjust the Y-axis position of the horizontal movable part to suppress rotational movement around the Z-axis (yawing movement) and the resulting meandering of components on the component conveyance path. You can

Further, the base has a pair of center-of-gravity adjusting portions facing the upper vibrating body and the intermediate vibrating body on both sides in the horizontal direction (Y-axis direction) orthogonal to the component conveying direction, and the center of gravity of the base is adjusted. It is desirable that the position is set in the vicinity of the center of gravity of the vibration system including the component conveying member, the upper vibrating body, and the intermediate vibrating body.

That is, in the above-described configuration, as shown in FIG. 10 corresponding to FIG. 6 (only the side plate Da serving as the center-of-gravity adjusting portion on the front side of the base D is shown by a chain double-dashed line), the center of gravity G _d ′ of the base D is 6 is higher than the position of the center of gravity G _{d in} the case of FIG. 6, and as shown in FIG. 8C corresponding to FIG. 8A, the arm length r1′ of the moment around the center of gravity G _abcd ′. , R2′ is shorter than the arm lengths r1 and r2 in the case of FIG. 8A, the moment is also smaller than that of the case of FIG. 8A. As a result, the pitching motion generated by each moment becomes small, and the rotation angle α of the horizontal vibration system described in FIG. 9 becomes small. Therefore, when trying to eliminate the apparent pitching motion of the trough A, The rotation angle β of the pitching motion with respect to the horizontal vibration system is also small. Therefore, the deformation of the vertical vibration leaf spring Kb is reduced, and the vertical vibration required for the composite vibration type component transfer device can be more stably realized.

Also, in order to match the natural frequency ω _h of the horizontal vibration system with the natural frequency ω _v of the rotational vibration around the center of gravity G _ab of the trough A and the upper vibrating body B, the absolute amount of pitching motion is preferably smaller. This is convenient because the effect is small.

If the mass of the base D is increased without increasing the size of the entire apparatus, the amplitude X1 on the base D side described in FIG. 8B decreases and the amplitude X2 on the trough A side increases. , If the amplitude X2 is kept constant, the total amount of the amplitudes X1 and X2 becomes small, so that the load on the horizontal vibration leaf spring Kc can be reduced and the component carrying capacity can be improved.

As described above, the vibration-type component conveying device of the present invention has a large compliance in the vertical plane (XZ plane) parallel to the component conveying direction, as a vibration isolating member that connects the base to the floor member. XZ of the base is adopted, which has great rigidity with respect to rotational movement (about the X-axis) about the transport direction and movement displacement in the horizontal direction (Y-axis direction) orthogonal to the component transport direction. Since there is little resistance to movement in the plane and rotational movement around the X axis and displacement in the Y axis direction are suppressed, it is possible to smoothly move between the parts conveying member and the device of the previous process or the next process. Parts can be delivered.

Partial cross-sectional front view of the component transfer device of the embodiment (excluding the side plate on the front side of the base) Partial cross-section right side view of FIG. The front view which expands and shows the one vibration-proof member vicinity of FIG. FIG. 3 is an external perspective view of the stabilizer of the anti-vibration member of FIG. FIG. 1 is a partially sectional front view showing the vicinity of one weight in FIG. 1 in an enlarged manner. Front view of a simplified model of a general compound vibration type component transfer device Explanatory diagram of general two-vibration system model 6A and 6B are explanatory views of a pitching motion generation mechanism and an amplitude ratio in the component transfer apparatus of FIG. 6, respectively, and c is an explanatory view showing a case where the position of the center of gravity of a is changed. The front view explaining the pitching movement of the component conveyance apparatus of FIG. The front view which shows the example which changed the gravity center position of the base of FIG.

Embodiments of the present invention will be described below with reference to the drawings. As shown in FIG. 1 and FIG. 2, this vibrating-type component conveying apparatus attaches a trough (component conveying member) 1 in which a linear component conveying path 1a is formed on an upper surface of an upper vibrating body 2 to form an upper vibrating body 2. And the base 3 installed on the floor, an intermediate vibrating body 4 is provided, the intermediate vibrating body 4 and the base 3 are connected by a leaf spring 5 as a first elastic member, and the intermediate body 4 and the upper vibrating body 2 are intermediate. The first vibrating body 4 is connected to the vibrating body 4 by a leaf spring 6 as a second elastic member, and the first vibrating body 4 generates vibration between the intermediate vibrating body 4 and the base 3 in the horizontal direction (component conveying direction, X axis direction). The vibrating mechanism 7 is provided, and the second vibrating mechanism 8 that generates vibration in the vertical direction (Z-axis direction) is provided between the upper vibrating body 2 and the base 3.

The trough 1 has a component discharge port of the apparatus in the previous process, whose component supply port at the upstream end (one end in the X-axis direction) is not shown, and a component discharge port at the downstream end (the other end in the X-axis direction). The parts are opposed to the parts supply ports of the apparatus of the process with predetermined gaps, and the parts are delivered between the previous process and the next process.

The first leaf spring 5 has its front and back surfaces oriented in the X-axis direction and has one end fixed to the base 3 and the other end fixed to the intermediate vibrating body 4 in a posture extending in the Z-axis direction for horizontal vibration. It is a leaf spring (elastic member for horizontal vibration).

On the other hand, the second leaf spring 6 has its front and back surfaces oriented in the Z-axis direction and has one end fixed to the upper vibrating body 2 and the other end fixed to the intermediate vibrating body 4 in a posture extending in the X-axis direction. It is a leaf spring for vertical vibration (elastic member for vertical vibration).

The first vibrating mechanism 7 and the second vibrating mechanism 8 are composed of an AC electromagnet and a movable iron core that faces the AC electromagnet at a predetermined interval, but the present invention is not limited to this, and the same vibrating mechanism is used. Any actuator that can generate a force may be used.

Both ends of the base 3 in the X-axis direction are connected to the floor member F by the vibration isolating members 9, and the central portion and both ends in the X-axis direction are fixed to the floor member F on the floor surface, respectively. It is supported by the first and second anti-vibration rubbers 10 and 11.

As shown in FIG. 3, the anti-vibration member 9 includes a stabilizer 12 arranged between the base 3 and the floor member F, and a stabilizer 12 and the floor member F with the front and back surfaces thereof oriented in the X-axis direction. And a pair of second anti-vibration connection plates 14 that connect the stabilizer 12 and the base 3 in a posture in which the front and back surfaces are oriented in the X-axis direction.

The stabilizer 12 of the anti-vibration member 9 is a tough component that is formed of cast steel or the like and is hard to deform, and as shown in FIG. 4, it extends in the horizontal direction (Y-axis direction) orthogonal to the X-axis direction. A long arm portion 12b extending in the X-axis direction and a short arm portion 12c extending upward from a root portion of the long arm portion 12b are provided at both ends of the main body portion 12a arranged. The short arm portions 12c are held by the first and second anti-vibration connecting plates 13 and 14 without being brought into contact with the concave portions 3a on the lower surface of the base 3.

The first vibration-proof connecting plate 13 has a substantially rectangular shape with a long Y-axis direction, and is bolted to the short arm portion 12c of the stabilizer 12 and the floor member F by mounting portions 13a protruding from the four corners. Further, a reinforcing portion 13b bent in the X-axis direction is formed at the edge of the short side. On the other hand, the second anti-vibration connecting plate 14 is a rectangle having a long Z-axis direction, and is bolted to the base 3 and the tip of the long arm 12b of the stabilizer 12 at the upper and lower ends thereof. Each of these vibration-proof connecting plates 13 and 14 is made of spring steel or the like and serves as a plate spring.

Then, the first and second anti-vibration connecting plates 13 and 14 are deformed by a constant spring constant in the thickness direction (X-axis direction), but are deformed in the plane (YZ plane) direction orthogonal to the thickness direction. Since the stabilizer 12 which is a tough component is hardly deformed against the torsional force, the vibration-proof member 9 as a whole is within a vertical plane (XZ plane) parallel to the component transport direction. It has a large compliance and has a large rigidity with respect to rotational movement (about the X-axis) around the component conveyance direction and movement displacement in the Y-axis direction.

The first and second anti-vibration rubbers 10 and 11 that support the base 3 have a large degree of freedom of deformation in each direction, and appropriately dampen the vibration within a range that does not hinder the operation of the base 3. It is a thing.

Further, as shown in FIGS. 1 and 2, the base 3 is provided with a pair of side plates (center of gravity adjusting portions) 3b facing the upper vibrating body 2 and the intermediate vibrating body 4 on both sides in the Y-axis direction. Weights 15 are attached to both ends of the pair of side plates 3b in the X-axis direction, and the center of gravity of the base 3 including the side plates 3b and the weight 15 is such that the trough 1, the upper vibrating body 2, and the intermediate vibrating body 4 are aligned. It is set near the center of gravity of the vibration system.

As shown in FIG. 5, the weight 15 passes through a body portion 15a extending in the Y-axis direction, a pair of arm portions 15b formed at both ends of the body portion 15a in the Y-axis direction, and both arm portions 15b. A pivot 15c fixed to both arms 15b of the lever and a horizontally movable part 15d attached to the body 15a on the side opposite to the arms 15b. Then, both ends of the turning shaft 15c are knurled, and both ends of the turning shaft 15c are formed into saddle-shaped pressing fittings 16 on the end surface of the side plate 3b of the base 3 to form a semicircular recess. By attaching the pressing metal fitting 16 to the side plate 3b with the bolts 17a and 17b in a state of being pressed against 3c, the weight 15 can be swung in the XZ plane (fixed at an arbitrary swivel position).

Further, the horizontal movable portion 15d of the weight 15 has a slot 15e extending in the Y-axis direction formed in the central portion thereof, and a groove 15f having a convex cross-section extending in the Y-axis direction substantially continuous with the slot 15e is formed. The projection 15g of the main body 15a having the same shape is fitted. Then, by tightening the bolt 18 screwed so as to be orthogonal to the slot 15e, the slot 15e and the groove 15f are elastically deformed in a direction in which the width of the slot 15e and the groove 15f are narrowed, and the protrusion 15g of the main body 15a is sandwiched. That is, the horizontal movable portion 15d can be moved in the Y-axis direction by loosening the bolt 18, and can be fixed at any Y-axis direction position.

On the other hand, the upper vibrating body 2 is provided with auxiliary weights 19 on the lower surface sides of both ends in the X-axis direction. As shown in FIG. 2, the auxiliary weight 19 has a groove 19a having a convex cross-section extending in the X-axis direction fitted to the protrusion 2a of the upper vibrating body 2 having substantially the same shape, and a bolt screwed from the lower surface side. It is fixed to the protrusion 2 a of the upper vibrating body 2 by tightening 20. That is, the auxiliary weight 19 can be moved in the X-axis direction by loosening the bolt 20.

This vibrating-type component conveying device has the above-mentioned configuration, and the vibrating force of the first vibrating mechanism 7 and the restoring force of the horizontal vibrating leaf spring 5 cause horizontal vibration in the intermediate vibrating body 4. The vibration is transmitted to the upper vibrating body 2 and the trough 1 via the leaf spring 6 for vertical vibration. Further, the vibration force of the second vibration mechanism 8 and the restoring force of the vertical vibration leaf spring 6 cause vertical vibration in the upper vibrating body 2 and the trough 1. Then, due to the horizontal vibration and the vertical vibration, the components supplied to the trough 1 are transported on the component transport path 1a.

Here, the vibration damping member 9 that connects both ends of the base 3 in the X-axis direction to the floor member F has a large compliance in the XZ plane, and has a rotational movement about the X-axis and a movement in the Y-axis direction. Since it has a large rigidity against displacement, the base 3 can be displaced with almost no resistance in the XZ plane, while rotational movement around the X axis and displacement in the Y axis direction can be suppressed. Therefore, the positional relationship between the component supply port of the trough 1 and the component discharge port of the apparatus in the previous process, and the positional relationship between the component discharge port of the trough 1 and the component supply port of the device in the next process are within the allowable range, 1, the parts can be smoothly delivered to and from the devices of the previous process and the next process.

Further, since the weight 15 that can be swung in the XZ plane is attached to the base 3, even if the specifications such as the length of the trough 1 are changed, the turning position of the weight 15 is adjusted and the weight of the base 3 is adjusted. By changing the moment of inertia, it is possible to easily suppress the apparent pitching movement of the trough 1 and stabilize the component transportation. If the pitching movement is not sufficiently suppressed by adjusting the weight 15 of the base 3, the pitching movement can be suppressed by adjusting the position of the auxiliary weight 19 attached to the upper vibrating body 2 in the X-axis direction. However, since the auxiliary weight 19 makes the trough 1 heavier and reduces the carrying capacity, it is preferable not to attach the auxiliary weight 19 when the weight 15 of the base 3 can suppress the pitching movement.

Since the weight 15 of the base 3 has the horizontal movable portion 15d movable in the Y-axis direction, the trough 1 is not designed symmetrically with respect to the XZ plane passing through the center of the device in the width direction. In this case, the position of the horizontally movable portion 15d in the Y-axis direction can be adjusted to suppress rotational movement (yaw movement) about the Z-axis and the resulting meandering of the components on the component transport path 1a.

Further, the base 3 is provided with a pair of side plates 3b which face the upper vibrating body 2 and the intermediate vibrating body 4 on both sides in the Y-axis direction and to which the weights 15 are attached, and the base including the side plates 3b and the weights 15 is provided. The center of gravity of 3 is set in the vicinity of the center of gravity of the vibrating system including the trough 1, the upper vibrating body 2 and the intermediate vibrating body 4, so that in FIG. As described, the pitching motion and the deformation of the vertical vibration leaf spring 6 are small, and stable vertical vibration can be obtained.

In the above-described embodiment, the first leaf spring that connects the intermediate vibrating body and the base is the horizontal vibrating leaf spring, and the second leaf spring that connects the upper vibrating body and the intermediate vibrating body is the vertical vibrating plate. Although a spring is used, conversely, the first leaf spring may be a vertical vibration leaf spring and the second leaf spring may be a horizontal vibration leaf spring.

1 Trough (Parts conveying member)
1a Component Conveying Path 2 Upper Vibrating Body 3 Base 3b Side Plate (Center of Gravity Adjustment)
4 Intermediate Vibrator 5 First Leaf Spring (Horizontal Vibration Leaf Spring)
6 Second leaf spring (vertical vibration leaf spring)
7 First Vibration Mechanism 8 Second Vibration Mechanism 9 Vibration Isolation Member 12 Stabilizer 13 First Vibration Isolation Connection Plate 14 Second Vibration Isolation Connection Plate 15 Weight 15d Horizontal Movable Part 19 Auxiliary Weight F Floor Member

Claims (4)

A component conveying member having a linear component conveying path, an upper vibrating body to which the component conveying member is attached, a base installed on the floor, and both end portions of the base in the component conveying direction as floor members. A vibration damping member to be connected, an intermediate vibrating body provided between the upper vibrating body and the base, a first elastic member connecting the intermediate vibrating body and the base, and the upper vibrating body and the intermediate vibration. A second elastic member for connecting to the body, wherein one of the first elastic member and the second elastic member is an elastic member for horizontal vibration and the other is an elastic member for vertical vibration, The elastic member and the first vibrating mechanism apply horizontal vibration to the component conveying member, and the elastic member for vertical vibration and the second vibrating mechanism apply vertical vibration to the component conveying member. In the vibration type component transfer device
The anti-vibration member includes a stabilizer disposed between the base and the floor member, and a first anti-vibration connection plate that connects the stabilizer and the floor member with the front and back surfaces thereof oriented in the component transport direction. A vibration-type component transfer device comprising: a second vibration-proof connecting plate that connects the stabilizer and the base with the front and back surfaces thereof oriented in the component transfer direction. The vibration type component transfer device according to claim 1, wherein a weight that can be swung within a vertical plane parallel to the component transfer direction is attached to the base. The vibration type component transfer device according to claim 2, wherein the weight has a horizontal movable portion that is movable in a horizontal direction orthogonal to the component transfer direction. The base has a pair of center-of-gravity adjusting portions facing the upper vibrating body and the intermediate vibrating body on both sides in the horizontal direction orthogonal to the component conveying direction, and the center of gravity of the base is the component conveying member. The vibration type component transfer device according to any one of claims 1 to 3, wherein the vibration type component transfer device is set in the vicinity of a center of gravity of a vibration system including an upper vibration body and an intermediate vibration body.

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