HK1106205B - A components feeder - Google Patents

Description

Parts supply device

Technical Field

The present invention relates to a component supply device capable of conveying a component by vibration.

Technical Field

A component supply unit is known as one of component supply apparatuses that supply components while arranging the components by giving vibrations to the components. The component supplying section can adjust the posture of the component by giving vibration to the component, and supply the component to a subsequent step.

Patent document 1 describes a piezoelectric driven component supply unit that can suppress stress acting on a vibration generating mechanism while ensuring a sufficient amplitude even during high-frequency driving, and that facilitates replacement of the vibration generating mechanism and change and adjustment of the resonance frequency.

Further, patent document 2 describes a piezoelectric-driven conveyor device capable of reducing a load acting on a piezoelectric element, and expecting an amplification of vibration amplitude, thereby obtaining a sufficiently practical conveying speed.

In the piezoelectric driving type transport apparatus described in patent document 2, an oscillator and a transport body, each of which is configured by mounting a piezoelectric element on an elastic plate, are connected to each other by a lower end portion and an upper end portion of an elastic plate-shaped connecting member, and the bending rigidity of the connecting member is set to be lower than the bending rigidity of the elastic plate by changing the plate width or the plate thickness of the connecting member.

Therefore, the change in the angle between the vibration-imparting body and the conveying body is allowed by the elastic deformation of the portion where the bending rigidity is low during vibration, and the load acting on the vibration-imparting body is reduced, so that the vibration amplitude of the vibration-imparting body and the conveying body can be expected to be increased.

Further, patent document 3 describes a piezoelectric driving type transport apparatus capable of carrying a transport component at a high speed by increasing a ratio of flexural rigidity of a portion of a coupling member.

In the piezoelectric driving type transport apparatus described in patent document 3, a connecting member which is one of the components of the piezoelectric driving type transport apparatus is laminated with two or more connecting members to form a laminated connecting member.

Therefore, the ratio of the bending rigidity of the part of the connecting component can be further improved than the prior art, and the parts can be conveyed at high speed.

Patent document 1: international publication No. 2004/067413 catalog;

patent document 2: japanese examined patent publication No. 6-13369;

patent document 3: japanese patent laid-open No. Hei 7-257724.

However, there are 2 problems with the existing parts supply unit. The following are described separately. First, the problem of the 1 st is that since the conventional component feeder is configured such that the base portion, the counter weight, the vibrating portion, and the conveyance path are stacked in this order from bottom to top, the swinging direction of the support spring is opposite to the swinging direction of the plate spring for vibration prevention, and uniform vibration cannot be imparted to the conveyance path. As described in detail below.

Fig. 18 is a schematic diagram for explaining the swing direction of the support spring and the swing direction of the vibration-proof plate spring in the conventional component supply unit 900.

As shown in fig. 18, the support spring 980 connecting the vibration applying section 902 and the counter weight 903 is in a state of swinging in the direction of the arrow R1 in the figure, but the plate spring 990 connecting the counter weight 903 and the base section 901 is in a state of swinging in the direction of the arrow R11 in the figure, and the bending modes are in opposite phases and swing in opposite directions. As a result, there is a problem that the swing on the conveying path 905 is unstable, and the conveying of the parts is stopped or reversed.

In the component supplying apparatus using the support spring 980 and the anti-vibration plate spring 990, the support spring 980 and the anti-vibration plate spring 990 are linearly arranged, and therefore the size of the component supplying apparatus (H in the drawing) is large₁₀) Is large.

Further, in the component supplying apparatus using not only the component supplying apparatus described in patent document 1 but also a general supporting spring and a plate spring for vibration damping, since 2 kinds of springs are used, a distance between a position of a center of gravity of a mass on the spring and a fulcrum of the plate spring for vibration damping is large, and there is a problem that a conveyed component is unstable, oblique transmission, retention, or driving of the component supplying apparatus is unstable or yaw occurs.

The 2 nd problem is explained below. The 2 nd problem is that in the piezoelectric-driven transport device described in patent document 2, since the piezoelectric spring that excites vibration is directly attached with the coupling spring, and the piezoelectric spring resonates to drive the piezoelectric-driven transport device, a load of the groove or the spiral transport path as the transport body directly acts on the piezoelectric spring. Further, since the load is supported and vibration is excited, there is a problem that appropriate vibration cannot be excited in the piezoelectric spring. Further, even when the vibration is excited, the load of the carrier acts on the piezoelectric element as a load in a shearing direction different from the original driving direction of the piezoelectric element, and therefore there is a problem in that the piezoelectric element may have a long life.

In the piezoelectric driving type transport apparatus described in patent document 3, since the coupling springs are mounted in series on the piezoelectric elements and the coupling springs are laminated to increase the bending rigidity, the load of the transport body directly acts on the piezoelectric springs, as in the piezoelectric driving type transport apparatus described in patent document 2. As a result, there is a problem that appropriate vibration cannot be excited and a problem of long-term life.

Disclosure of Invention

The invention aims to provide a component supply device which improves vibration-proof efficiency, reduces the height of the gravity center position of a sprung mass and realizes stable component conveying and component supply device self-shortening.

Another object of the present invention is to provide a component supply apparatus having a vibration plate capable of enhancing durability and exciting appropriate vibration by freely selecting rigidity.

Another object of the present invention is to provide a parts feeder having the following vibration plate: durability can be improved, and rigidity can be freely selected; the mounting precision is improved, the manufacturing time and the maintenance time can be reduced, and the proper vibration can be excited; the vibration-proof efficiency is improved, and the height of the gravity center position of the sprung mass can be reduced to realize stable component conveyance and reduction in the height of the component supply apparatus itself.

(1) The component supply device of the present invention is a component supply device for conveying a component by giving vibration thereto, and includes: a conveying part having a conveying passage for conveying the parts; a vibration applying part for supporting the conveying part; a fixing portion provided as a member different from the vibration applying portion; one end of the driving component is arranged on the vibration adding part, and the other end of the driving component is arranged on the hammer part and can elastically deform; a vibrator generating stress in response to the electric signal; a vibrating plate having a horizontally disposed horizontal plate portion and a vertically disposed vertical plate portion, the vibrating plate exciting vibration by attaching a vibrator to at least one of front and back surfaces of the vertical plate portion; in the vibrating plate, one of the horizontal plate portion and the vertical plate portion is attached to the weight portion, the other of the horizontal plate portion and the vertical plate portion is attached to the vibrating portion, and the thickness of the joint portion between the horizontal plate portion and the vertical plate portion is larger than the thickness of the other of the horizontal plate portion and the vertical plate portion.

In the component supplying apparatus of the present invention, the vibrator is attached to the vibrating plate. When an electric signal is applied to the vibrator, the vibration plate to which the vibrator is attached is driven to excite vibration, and the fixed portion attached to one of the vertical plate portion and the horizontal plate portion of the vibration plate and the vibrating portion attached to the other surface of the vibration plate vibrate in opposite phases. The vibration is transmitted to the conveying section supported by the vibration applying section, and the component is conveyed from the upstream side to the downstream side of the conveying section.

In this case, since the horizontal plate portion and the vertical plate portion of the diaphragm have different thicknesses, the horizontal plate portion and the vertical plate portion of the diaphragm can have different rigidities. Further, the thickness of at least the joint portion between the horizontal plate portion and the vertical plate portion of the diaphragm can be increased. Thus, the thickness of the portion requiring rigidity is increased, and the thickness of the portion requiring less rigidity is reduced, thereby realizing a component supply device including a vibration plate having the optimum rigidity and the optimum vibration frequency.

Further, since the load of the vibration applying section and the load of the conveying section can be supported by the driving member, it is expected that the durability of the vibration plate and the vibrator can be improved, and that appropriate vibration can be excited from the vibration plate to which the vibrator is attached.

(2) The vibrating plate may include: 1 st flat plate-like elastic member forming a horizontal plate portion; a 2 nd flat plate-like elastic member forming a vertical plate portion, different from the 1 st flat plate-like elastic member; and a connecting member for connecting the horizontal plate portion formed by the 1 st plate-shaped elastic member and the vertical plate portion formed by the 2 nd plate-shaped elastic member.

At this time, the vibration plate is formed by bonding the 1 st flat plate-like elastic member and the 2 nd flat plate-like elastic member by the bonding member. Further, the 1 st flat plate-like elastic member forming the horizontal plate portion is formed of a member different from the 2 nd flat plate-like elastic member forming the vertical plate portion. Therefore, the thickness of the 1 st flat plate-like elastic member and the thickness of the 2 nd flat plate-like elastic member can be freely adjusted. By using the joining member, the rigidity can be improved also for the present bent portion. This makes it possible to design the rigidity of the horizontal plane and the vertical plane of the vibration plate to different values. Thus, the thickness of the surface requiring rigidity is increased, and the thickness of the portion requiring less rigidity is reduced, whereby a component supply apparatus including a vibration plate having the optimum rigidity and the optimum vibration frequency can be realized.

Further, since the 1 st flat plate-like elastic member and the 2 nd flat plate-like elastic member are joined by the joining member, the right angle accuracy can be greatly improved as compared with the case where a horizontal plate portion and a vertical plate portion are formed by bending a single flat plate-like elastic member. As a result, mounting displacement when the diaphragm is mounted on the fixing portion and the vibration applying portion can be prevented, and the number of manufacturing steps can be reduced.

Further, the load of the vibration applying portion and the load of the conveying portion can be supported by the driving member provided together with the vibration plate. Therefore, it is expected that the durability of the diaphragm and the vibrator can be improved and appropriate vibration can be excited from the diaphragm and the vibrator.

(3) The vibration plate may be constituted by a flat plate-like elastic member having a longitudinal direction and having a thick portion in a region along a part of the longitudinal direction; the vertical plate portion and the horizontal plate portion are formed by bending the thick portion of the flat plate-like elastic member.

In this case, since the thickness of one of the horizontal plate portion and the vertical plate portion is reduced by machining, the thickness of the horizontal plate portion and the thickness of the vertical plate portion can be freely adjusted. As a result, the rigidity of the horizontal plate portion and the vertical plate portion of the diaphragm can be designed to be different. Thus, the thickness of the surface requiring rigidity is increased, and the thickness of the portion requiring less rigidity is reduced, thereby realizing a component supply device including a vibration plate having the optimum rigidity and the optimum vibration frequency.

(4) The transport path may also be a linear transport path.

At this time, since the conveyance path may be a linear conveyance path, the component can be conveyed by giving vibration to the linear conveyance path.

(5) The component supplying apparatus of the present invention further includes a base portion and a vibration-proof member, the vibration-proof member being attached to the vibration-applying portion and the base portion to reduce vibration transmitted from the vibration-applying portion to the base portion; the driving member is attached to the vibration applying section and a fixing section disposed below the vibration applying section and above the base section disposed at the lowermost portion, and elastically deforms to generate vibrations in mutually opposite phases in the fixing section and the vibration applying section.

In this case, the base portion, the fixing portion, and the vibration applying portion are provided in this order from the lower portion, the vibration isolating member is attached to the vibration applying portion and the base portion, and the driving member is attached to the vibration applying portion and the fixing portion. As a result, since the driving member and the vibration isolation member are disposed to overlap each other between the vibration applying portion and the fixing portion, the bending modes of the driving member and the vibration isolation member are in opposite phases, and vibration isolation efficiency can be improved. Further, since the driving member and the vibration isolating member are disposed so as to overlap each other in the longitudinal direction of the driving member and in a part of the longitudinal direction of the vibration isolating member, the component supply apparatus can be made shorter, and the distance between the center of gravity of the mass on the member and the fulcrum of the vibration isolating member can be shortened. As a result, the parts can be prevented from being unstable, skewed, retained, or unstable or yawing in driving of the parts feeder.

(6) The driving member and the vibration isolating member may be disposed to have a height overlapping each other in a height direction in the vertical direction.

In this case, since the driving member and the vibration-proof member have portions whose heights overlap each other in the height direction in the vertical direction, the component supply device can be made shorter, and the distance between the center of gravity of the mass on the member and the fulcrum of the vibration-proof member can be shortened. As a result, the parts can be prevented from being unstable, skewed, retained, or unstable or yawing in driving of the parts feeder.

(7) The driving member and the vibration isolating member may be disposed in a stacked state.

In this case, since the vibration isolation member and the driving member, which are formed of plate-like elastic plates, are disposed in a state of being stacked on each other, the bending modes of the driving member and the vibration isolation member are in opposite phases, and vibration isolation efficiency can be improved.

(8) The driving member and the vibration isolating member are each formed of a flat plate-like elastic plate having a hole, and the vibration isolating member and the driving member may be fixed to the vibration applying portion by the same shaft member penetrating the hole of the vibration isolating member and the hole of the driving member.

In this case, the driving member and the vibration isolating member are fixed to the vibrator through a through hole such as a bolt or the like, which is a coaxial member. Therefore, in a state where the driving member and the vibration isolating member are arranged linearly with respect to each other, the longitudinal length of the driving member and a part of the longitudinal length of the vibration isolating member are overlapped with each other, so that the component supply device itself can be made low, and the distance between the center of gravity of the mass on the member and the fulcrum of the vibration isolating member can be shortened. Further, since the number of parts of the fixing member such as a bolt can be reduced, the cost of the parts themselves and the cost at the time of manufacturing can be reduced.

Drawings

Fig. 1 is a schematic diagram showing an example of a micro component supply apparatus according to an embodiment of the present invention.

Fig. 2 is a schematic diagram showing an example of a micro component supply apparatus according to an embodiment of the present invention.

Fig. 3 is a schematic perspective view showing an example of the shape of the micro component to be transported in the present embodiment.

Fig. 4 is a schematic side view of the linear feeder according to embodiment 1 with a part cut away.

Fig. 5 is a schematic assembly view showing an example of the diaphragm of fig. 4.

Fig. 6 is a schematic side view of the vibration plate of fig. 5.

Fig. 7 is a schematic side view for explaining an example of the lowering of the linear feeder of the present embodiment shown in fig. 4.

Fig. 8 is a schematic view showing an example of the structure of the support spring and the anti-vibration plate spring.

Fig. 9 is a schematic sectional view for explaining the structure of the support spring and the plate spring for vibration damping in fig. 8.

Fig. 10 is a diagram for explaining the effect of the linear feeder.

Fig. 11 is a diagram for explaining the effect of the linear feeder.

Fig. 12 is a side view showing another example of the diaphragm of fig. 5 and 6.

Fig. 13 is a side view showing another example of the diaphragm of fig. 5 and the diaphragm of fig. 12.

Fig. 14 is a schematic side view showing another example of the linear feeder of fig. 7.

Fig. 15 is a schematic view showing an example of the structure of the support spring and the plate spring for vibration damping in fig. 14.

Fig. 16 is a schematic view showing an example of the structure of the support spring and the plate spring for vibration damping in fig. 14.

Fig. 17 is a schematic side view showing another example of the linear feeder.

Fig. 18 is a schematic diagram for explaining the swing direction of the support spring and the swing direction of the vibration-proof plate spring in the conventional component supply unit.

Detailed Description

An embodiment of the present invention will be described below with reference to the drawings. A case of a micro component supply device suitable for conveying micro components will be described as an example of the component supply device of the present invention.

(one embodiment)

Fig. 1 and 2 are schematic views showing an example of a micro component supply apparatus 100 according to an embodiment of the present invention. Fig. 1 shows an upper surface of the micro parts feeder 100, and fig. 2 shows a side surface of the parts feeder 100.

As shown in fig. 1 and 2, the micro-component supply apparatus 100 includes a component supply unit 200, a linear feeder 300, and a stage 900.

As shown in fig. 2, the component supply unit 200 includes a bowl-shaped feed unit 210 and a piezoelectric vibration unit 220.

In the micro-parts feeder 100 according to the present embodiment, the parts feeder 200 and the linear feeder 300 are provided on the stage 900. The micro-component feeding unit 311 of the linear feeder 300 is connected to the micro-component discharging unit 211 of the component supplying unit 200. And the receiving channel 217 of the parts supply part 200 is connected to the circulation type conveying part 317 of the linear feeder 300.

The vibration oscillated by the vibrator 400 (not shown) provided in the piezoelectric vibration unit 220 of the component supply unit 200 is applied to the bowl-shaped transport unit 210 placed on the piezoelectric vibration unit 220. In the bowl-shaped conveying part 210, a spiral micro component conveying passage is provided along the inner periphery of the bowl-shaped conveying part 210. The micro component 800 is supplied to the center bottom of the bowl-shaped conveying unit 210, conveyed on a spiral conveying path by the vibration of the micro component 800 from the piezoelectric vibrating unit 220, and conveyed from the micro component discharging unit 211 to the micro component feeding unit 311 of the linear feeder 300.

Further, 1 vibrator mainly including a piezoelectric vibration portion 303, a vibration plate 400, and a weight portion (balance weight) 302 is provided in the linear feeder 300, and vibration oscillated by the vibrator is applied to each transport path of the linear feeder 300. So that the micro-component supply apparatus 100 can supply the micro-components 800 to a later process of the micro-component supply apparatus 100.

When the micro-components 800 that are not arranged in the predetermined posture exist on the transfer path of the linear feeder 300 or when the micro-components 800 are not transferred to the subsequent process side due to a failure in the subsequent process, the micro-components 800 are returned from the circulating type transfer unit 317 to the central bottom portion of the bowl-shaped transfer unit 210 through the receiving path 217 of the component supply unit 200.

Next, fig. 3 is a schematic perspective view showing an example of the shape of the micro component 800 conveyed in the present embodiment.

As shown in fig. 3, the micro component 800 is formed of a rectangular parallelepiped having a length L, a height H, and a width B. The relationship among the length L, the height H and the width B is H < B < L. Thus, the micro component 800 is constituted by a flat plate-like micro component.

In addition, the micro component supply apparatus 100 often forms an electrode on one surface of the micro component 800, and generally the size of the micro component 800 is about 3.2mm to 8mm in length L, about 2.5mm to 5.0mm in width B, and about 0.8mm to 1.7mm in length H.

Next, fig. 4 is a schematic side view of the linear feeder 300 according to embodiment 1, with a part removed.

The linear feeder 300 mainly includes a vibration-proof table 301 (base), a weight (counter weight) 302, a piezoelectric vibration portion 303, a 1 st conveying member (linear conveying passage member) 320, a 2 nd conveying member (linear conveying passage member) 330, a connecting member 340, a 3 rd conveying member (circulating conveying member) 350, a coupling plate 370, a support spring 380, a vibration-proof plate spring 390, and a vibrator 400.

As shown in fig. 4, a weight (counter weight) 302 is provided above the vibration isolation table 301, and a piezoelectric vibration unit 303 is provided above the weight (counter weight) 302. The weight portion (counter weight) 302 is constituted by a weight formed in accordance with the weight of the piezoelectric vibrating portion 303, the 1 st conveying member 320, and the like.

As shown in fig. 4, the piezoelectric vibrating portion 303 is held by a plurality of support springs 380 from the side surface of the vibration prevention table 301. The piezoelectric vibrating portion 303 is held by a plurality of support springs 380 from the side surface of the weight portion (counter weight) 302. In the linear feeder 300 of the present embodiment, the support spring 380 and the plate spring 390 for vibration prevention are disposed to overlap each other in the vertical direction. The support spring 380 and the plate spring 390 for vibration isolation are disposed in a state of being inclined at substantially the same angle from the vertical direction.

Further, a vibration plate 400 is provided inside the weight portion (balance weight) 302 and the piezoelectric vibration portion 303 in fig. 4. The diaphragm 400 includes a flat plate-like elastic member 420 forming a vertical plate portion, a flat plate-like elastic member 421 forming a horizontal plate portion, a connecting member 422 connecting the flat plate-like elastic member 420 and the flat plate-like elastic member 421, and a piezoelectric element 411. The flat plate-like elastic member 420 is attached to the piezoelectric vibrating portion 303, and the flat plate-like elastic member 421 is attached to the weight portion (counter weight) 302. The detailed structure of the diaphragm 400 will be described later.

The 1 st transport member 320 is fixed to the upper portion of the piezoelectric vibrating portion 303, the 2 nd transport member 330 is connected to one end side of the 1 st transport member 320, and the connecting member 340 is provided on the side surface of the 1 st transport member 320. The 1 st conveying member 320 is provided with a 3 rd conveying member 350 via a plurality of elastic plate members 360. That is, one end of the plurality of elastic plate-like members 360 having a flat plate shape is fixed to the 1 st conveying member 320 by bolts, and the other end is fixed to the back surface of the 3 rd conveying member 350 by bolts. In this state, the plurality of elastic plate-like members 360 are inclined at an angle closer to the horizontal plane than the vertical plane.

As described above, in the linear feeder 300 of the present embodiment, the vibration is excited by the vibration plate 400 to which the piezoelectric element 411 described later is bonded, the piezoelectric vibration portion 303 and the weight portion (balance weight) 302 held by the support spring 380 vibrate in opposite phases, the vibration of the piezoelectric vibration portion 303 is applied to the 1 st transport member 320, and the micro component 800 is transported along the transport path on the 1 st transport member 320.

Next, fig. 5 is a schematic assembly view showing an example of the diaphragm 400 of fig. 4, and fig. 6 is a schematic side view of the diaphragm 400 of fig. 5.

First, as shown in fig. 5, a piezoelectric element 411 is disposed in the center portion of the front and back surfaces of a flat plate-like elastic member 420. The spring constant of the flat plate-like elastic member 420 and the piezoelectric element 411 is appropriately selected according to the condition of an arbitrary resonance frequency determined by the weight and size of the micro component 800 to be conveyed, the weight of the 1 st conveying member 320, and the like.

Specifically, in transducer 400, piezoelectric ceramic is polarized, piezoelectric element 411 having a polarization potential of an anode is attached to one surface (front surface) of flat plate-shaped elastic member 420, and piezoelectric element 411 having a polarization potential of a cathode is attached to the other surface (back surface) of flat plate-shaped elastic member 420. Thus, a bimorph piezoelectric element structure including the plurality of piezoelectric elements 411 is formed on the front and back surfaces of the flat plate-shaped elastic member 420.

Then, the vibration is excited in the diaphragm 400 by applying (adding) an electric charge to the plurality of piezoelectric elements 411, and the piezoelectric vibration portion 303 and the weight portion (balance weight) 302 held by the support spring 380 vibrate in opposite directions to each other.

Next, as shown in fig. 5, a flat plate-like elastic member 420 to which the piezoelectric element 411 is bonded is provided as a vertical plate portion and a flat plate-like elastic member 421 is provided as a horizontal plate portion in the diaphragm 400. The coupling member 422 of the diaphragm 400 included in the vertical plate portion has a substantially quadrangular prism shape having a longitudinal direction. The coupling member 422 has 2 surfaces 423 and 424 adjacent to each other with the longitudinal side being one side, and the angle formed by the 2 surfaces 423 and 424 is 90 degrees. Further, a screw-fastenable hole (not shown) is provided in the surface 423 and the surface 424.

The flat plate-like elastic member 420 has the piezoelectric element 411 attached to a substantially central portion of the front and back surfaces thereof, and the through-holes 430 and 440 are provided in portions where the piezoelectric element 411 is not attached. On the other hand, the flat plate-like elastic member 421 is provided with through holes 431 and 450.

The bolt a is fastened to a hole provided in the surface 423 of the coupling member 422 through a through hole 430 provided in a lower surface portion of the flat plate-shaped elastic member 420, and the bolt B is fastened to a hole provided in the surface 424 of the coupling member 422 through a through hole 431 of the flat plate-shaped elastic member 421.

The flat plate-like elastic member 420 and the flat plate-like elastic member 421 are fixed to the coupling member 422 by the bolts A, B at an angle of about 90 degrees, thereby forming the substantially L-shaped diaphragm 400 shown in fig. 6.

As shown in fig. 4 and 6, the plate-shaped elastic member 421 of the diaphragm 400 is fastened to the weight portion (counter weight) 302 by a bolt C, and the plate-shaped elastic member 420 of the diaphragm 400 is attached to the piezoelectric vibration portion 302. So that the vibration plate 400 is built in the linear feeder 300. In the present embodiment, the flat plate-like elastic member 420 has a thickness L1 and a rigidity value Nm 1; the flat plate-like elastic member 421 has a thickness L2 and a rigidity value Nm 2. Since the flat plate-like elastic members 420 and 421 can be formed of different members, the thickness and the rigidity can be freely selected without depending on the members.

As described above, in the component supplying apparatus according to the present embodiment, since the thickness of the flat plate-shaped elastic member 421 of the horizontal plate portion of the vibration plate 400 is different from that of the flat plate-shaped elastic member 421 of the vertical plate portion, the rigidity values Nm1 and Nm2 of the flat plate-shaped elastic member 421 of the horizontal plate portion of the vibration plate 400 and the flat plate-shaped elastic member 420 of the vertical plate portion can be set to different values. Further, at least the joint between the horizontal plate portion and the vertical plate portion of the diaphragm 400 may be increased in thickness. Accordingly, the thickness of the portion requiring less rigidity can be reduced by increasing the thickness of the portion such as the joint portion requiring rigidity, and the component supply apparatus 100 including the diaphragm 400 having the optimum rigidity and the optimum vibration frequency can be realized. In particular, since the 1 st flat plate-like elastic member 420 and the 2 nd flat plate-like elastic member 421 are coupled by the coupling member 422, the right angle accuracy can be greatly improved as compared with the case where a horizontal plate portion and a vertical plate portion are formed by bending a single flat plate-like elastic member. As a result, mounting displacement when the diaphragm 400 is mounted on the weight portion (balance weight) 302 and the piezoelectric vibration portion 303 can be prevented, and the number of manufacturing steps and the number of maintenance steps can be reduced.

Further, since the load of the 1 st transport member 320 and the piezoelectric vibration portion 303 can be supported by the support spring 380, it is expected that the durability of the vibration plate 400 and the piezoelectric element 411 can be improved, and appropriate vibration can be excited from the vibration plate 400 to which the piezoelectric element 411 is attached.

Further, the thickness of the 1 st plate-like elastic member 420 and the thickness of the 2 nd plate-like elastic member 421 can be freely adjusted. As a result, the rigidity of the horizontal plane and the vertical plane of the diaphragm can be designed to have different values. Further, since the rigidity of the joint 422 interposed between these members is increased, the thickness of the portion requiring less rigidity can be reduced by increasing the thickness of the surface requiring rigidity, and a component supply apparatus including a diaphragm having the optimum rigidity and the optimum vibration frequency can be realized.

Next, fig. 7 is a schematic side view for explaining an example of the reduction of the height of the linear feeder 300 of the present embodiment shown in fig. 4. The linear feeder 300 shown in fig. 7 is the same as the linear feeder 300 of fig. 4. The structures of the support spring 380 and the plate spring 390 for vibration damping will be described below.

As shown in fig. 7, in the linear feeder 300 of the present embodiment, a support spring 380 and a plate spring 390 for vibration prevention are arranged to overlap each other.

Next, fig. 8 is a schematic diagram showing an example of the structure of the support spring 380 and the anti-vibration plate spring 390.

As shown in fig. 8, the support spring 380 and the plate spring 390 for vibration damping are each formed of a flat plate-like elastic member. Between the support spring 380 and the plate spring 390 for vibration damping, 2 flat plate-like spacers 391 and 2 annular spacers 392 are provided.

As shown in fig. 8, 2 through holes 380a are provided on one end side of the support spring 380, and 2 through holes 380b are provided on the other end side. Further, 2 through holes 390a are provided on one end side of the plate spring 390 for vibration isolation, 2 through holes 390b are provided near the center portion, and 2 through holes 390c are provided on the other end side.

The bolt 385 has a spring washer and a flat washer, and is fixed to the piezoelectric vibrating portion 303 through a through hole 380a penetrating the support spring 380, a through hole 391a penetrating the plate spacer 391, and a through hole 390a penetrating the plate spring 390.

The bolt 386 has a spring washer and a flat washer, and is fixed to the weight portion (balance weight) 302 through a through hole 380b of the support spring 380, the annular pad 392, and a through hole 390b of the plate spring 390 for vibration damping.

The bolt 395 includes a spring washer and a flat washer, and is fixed to the base 301 through the through hole 390 c.

Fig. 9 is a schematic sectional view for explaining the structures of the supporting spring 380 and the plate spring 390 for vibration damping shown in fig. 8.

As shown in fig. 8 and 9, the through-hole 390b of the plate spring 390 for vibration isolation has a larger diameter than the other through-holes 380a, 380b, 390a, and 390 c. That is, the diameter of the through hole 390b of the plate spring 390 for vibration damping is formed to be larger than the diameter of the head of the bolt 386. Therefore, the support spring 380 can transmit the vibration of the piezoelectric vibrating portion 303 to the weight portion (counter weight) 302 side without interfering with the movement of the anti-vibration plate spring 390.

The following describes the effects of the linear feeder 300 according to the present embodiment.

Fig. 10 and 11 are diagrams for explaining the effect of the linear feeder 300. Fig. 10(a) is a diagram showing the structures of the support spring 380 and the plate spring 390 for vibration prevention of the linear feeder 300, and fig. 10(b) is a diagram showing the structures of the support spring 980 and the plate spring 990 for vibration prevention of the conventional linear feeder (see fig. 18). Fig. 11 a is a diagram showing an initial state (denoted by reference numeral Z) and a maximum amplitude state (denoted by no reference numeral) of the support spring 380 and the plate spring 390 for vibration damping according to the present invention, and fig. 11 b is a diagram showing an initial state (denoted by reference numeral Z) and a maximum amplitude state (denoted by no reference numeral) of the support spring 980 and the plate spring 990 for vibration damping at present.

The support spring 380 and the plate spring 390 for vibration prevention shown in fig. 10(a) are deformed in the same manner when the linear feeder 300 is driven. On the other hand, the support spring 980 and the plate spring 990 for vibration prevention shown in fig. 10(b) deform in different patterns (X1 and X2 in the drawing) when the linear feeder 300 is driven. The following explains the modes.

Here, as shown in fig. 11(a), the support spring 380Z and the anti-vibration plate spring 390Z in the initial state are disposed in a state of being overlapped with each other, and the distance between the end of the support spring 380Z and the end of the anti-vibration plate spring 390Z is a distance L1. In the state of maximum amplitude, the support spring 380 and the anti-vibration plate spring 390 move (mode) in unison, and the distance L2 between the end of the support spring 380 and the end of the anti-vibration plate spring 390 is substantially equal to the distance L1, and the rate of change of the distance L2/L1 is a value very close to 1.

On the other hand, as shown in fig. 10(b) and 11(b), the support spring 980Z and the vibration damping leaf spring 990Z in the initial state are arranged on a straight line, and the distance therebetween is L3. In a state of maximum amplitude, the support spring 980 and the vibration damping leaf spring 990 are moved (in a mode) opposite to each other, and are spaced apart by a distance L4. The distance L3 and the distance L4 are in the relationship of distance L3 < distance L4, and the rate of change of distance L4/L3 is greater than 1, for example, the rate of change is close to 6 in fig. 11 (b).

As described above, in the conventional support spring 980 and leaf spring 990 for vibration damping shown in fig. 10(b) and 11(b), the distance between them during vibration is increased from the state of distance L3 to the state of distance L4, and therefore, they are pulled to each other, and vibration is disturbed. As a result, the support spring 980 and the vibration-proof plate spring 990 move (or move) differently from each other, and it is difficult to achieve the vibration-proof effect of the vibration-proof plate spring 990.

On the other hand, since the support spring 380 and the plate spring 390 for vibration isolation shown in fig. 10(a) and 11(a) vibrate in the same motion (mode), and the distance therebetween during vibration is shifted from the state of the distance L1 to the distance L2 substantially equal to the distance L1, the vibration of the support spring 380 and the plate spring 390 does not become disturbed. As a result, the movement (mode) of the support spring 380 and the vibration-proof plate spring 390 are matched, and the vibration-proof effect of the vibration-proof plate spring 390 is easily exhibited.

As can be seen from the above, the linear feeder 300 of the present embodiment has improved vibration-proof efficiency as compared with the linear feeder having the structure of fig. 10 (b).

Further, as shown in fig. 10(a), the support spring 380 is disposed to overlap a part of the plate spring 390 for vibration damping in the longitudinal direction, and therefore the length in the vertical direction can be shortened. Thereby achieving the full height H of the linear feeder shown in FIG. 18₁₀In comparison, the full height H of the linear feeder 300 of fig. 7₁Becomes low. Further, the fulcrum height H of the plate spring 990 for vibration isolation shown in fig. 18 is equal to₂₀In comparison, the fulcrum height H of the plate spring 390 for vibration prevention of fig. 7₂Becomes low. And a distance L from the height of the fulcrum of the vibration-proof plate spring 990 to the center of gravity W of the mass on the vibration-proof plate spring 990₃₀+H₂₀Is also compared withDistance L from the fulcrum height of the vibration-proof plate spring 390 to the center of gravity W of the mass on the vibration-proof plate spring 990 shown in fig. 7₃+H₂Short.

As described above, in the linear feeder 300 according to the present invention, the instability, skew transfer, and stagnation of the conveyed parts, or instability and yaw of the driving of the linear feeder 300 can be prevented, and stable parts conveyance can be performed.

(Another example)

Next, fig. 12 is a side view showing another example of the diaphragm 400 of fig. 5 and 6. The diaphragm 400a shown in fig. 12 is different from the diaphragm 400 shown in fig. 5 and 6 in the following point.

Unlike the vibrating plate 400 shown in fig. 5 and 6, the vibrating plate 400a shown in fig. 12 is configured by a flat plate-like elastic member 420a and a piezoelectric element 411. The flat plate-like elastic member 420a shown in fig. 12 is formed by cutting a partial region from a thickness L1 to a thickness L2, and is formed of flat plate-like elastic members having different thicknesses. The flat plate-shaped elastic member 420a having different thicknesses is formed by being bent at a position of the thickness L1 by about 90 degrees. In the flat plate-like elastic member 420a shown in fig. 12, the region having a thickness L1 is a vertical plate portion, and the region having a thickness L2 is a horizontal plate portion.

The piezoelectric element 411 is attached to the front and back surfaces of the vertical surface of the flat plate-like elastic member 420 a. Further, by applying an electric signal to the piezoelectric element 411, stress is generated in the flat plate-like elastic member 420 a. Here, in the present embodiment, since the flat plate-like elastic member 420a is bent by 90 degrees in the region of the thickness L1 where the rigidity is high, the rigidity of the bent portion can be increased, and stable vibration can be excited in the diaphragm 400 a.

In this case, the rigidity and thickness of the horizontal plate portion and the vertical plate portion of the vibration plate 400a can be designed to be different by processing or laminating components. Thus, the thickness of the surface requiring rigidity is increased, and the thickness of the portion requiring less rigidity is reduced, whereby the microdevice supplying apparatus 100 including the vibrating plate 400a having the optimum rigidity and the optimum vibration frequency can be realized.

(Another example)

Next, fig. 13 is a side view showing another example of the diaphragm 400 of fig. 5 and the diaphragm 400a of fig. 12.

The diaphragm 400b shown in fig. 13 differs from the diaphragms 400 and 400a shown in fig. 5, 6, and 12 in the following manner.

The vibrating plate 400b shown in fig. 13 is composed of a flat plate-like elastic member 420b, a flat plate-like elastic member 421b, a piezoelectric element 411, and a bolt D.

The flat plate-like elastic member 420b has a thickness L1, and the flat plate-like elastic member 421b has a thickness L2. In the present embodiment, the flat plate-like elastic members 420b and 421b are designed to have different thicknesses, but the present invention is not limited thereto, and may be formed of the same thickness.

The flat plate-like elastic member 420b is formed by bending the member front end by about 90 degrees. The flat plate-like elastic member 421b extends in a direction opposite to the direction in which the flat plate-like elastic member 420b is bent by 180 degrees and is provided along the front end surface of the bent flat plate-like elastic member 420 b. As shown in fig. 13, the front end surface of the curved flat plate-like elastic member 420b and the end surface of the flat plate-like elastic member 421b are fastened by a bolt D.

In this way, in the diaphragm 400b of fig. 13, a vertical plate portion having a thickness of L1, a horizontal plate portion having a thickness of L2, and a joint portion between the vertical plate portion and the horizontal plate portion having a thickness of L1+ L2 are formed. As a result, the diaphragm 400b having high rigidity can be formed at the joint portion. In addition, the joint portion includes a horizontal plate portion.

The piezoelectric element 411 is attached to the front and back surfaces of the vertical surface of the flat plate-like elastic member 420 b. Further, by applying an electric signal to the piezoelectric element 411, stress is generated in the flat plate-like elastic member 420 b. Here, in the present embodiment, since the flat plate-like elastic members 420b and 421b having the high rigidity and the thickness L1+ L2 are bent by 90 degrees, the rigidity of the bent portion can be increased, and stable vibration can be excited in the diaphragm 400 b.

In this case, the rigidity and thickness of the horizontal plate portion and the vertical plate portion of the vibration plate 400b can be designed to be different by stacking the components. Thus, the thickness of the surface requiring rigidity is increased, and the thickness of the portion requiring less rigidity is reduced, thereby realizing the microdevice supplying apparatus 100 including the vibrating plate 400b having the optimal rigidity and the optimal vibration frequency.

(Another example)

Next, fig. 14 is a schematic side view showing another example of the linear feeder 300 of fig. 7.

The linear feeder 300a shown in fig. 14 is different from the linear feeder 300 shown in fig. 7 in the following point.

As shown in fig. 14, in the linear feeder 300a, a plate spring 390 for vibration isolation is provided at a place where the support spring 380 of fig. 7 is disposed, and the support spring 380 is provided at a place where the plate spring 390 for vibration isolation of fig. 7 is disposed. That is, the plate spring 390 for vibration prevention is provided between the support spring 380 and the weight 302, and the support spring 380 is provided outside the plate spring 390 for vibration prevention and the linear feeder 300. The configuration thereof is explained in detail below.

Fig. 15 is a schematic diagram showing an example of the structure of the supporting spring 380 and the plate spring 390 for vibration damping in fig. 14.

As shown in fig. 15, the support spring 380 and the plate spring 390 for vibration damping are each formed of a flat plate-like elastic member. A flat plate-like spacer 391 is provided between the support spring 380 and the vibration isolating plate spring 390.

As shown in fig. 15, 2 through holes 380a are provided on one end side of the support spring 380, and 2 through holes 380b are provided on the other end side. Further, 2 through holes 390a are provided on one end side of the plate spring 390 for vibration isolation, 2 through holes 390d are provided near the center portion, and 2 through holes 390c are provided on the other end side. Here, the through hole 390d has a larger diameter than the head of the bolt 386 a.

The bolt 385 has a spring washer and a flat washer, and is fixed to the piezoelectric vibrating portion 303 through a through hole 390a penetrating through the vibration damping plate spring 390, a through hole 391a penetrating through the flat plate spacer 391, and a through hole 380a penetrating through the support spring 380.

The bolt 386a has a spring washer and a flat washer, and is fixed to the weight portion (balance weight) 302 through a through hole 380a of the support spring 380.

The bolt 395a has a spring washer and a flat washer, and is fixed to the base 301 through the through hole 390 c.

Fig. 16 is a schematic diagram showing an example of the structure of the supporting spring 380 and the plate spring 390 for vibration damping in fig. 14.

As shown in fig. 15 and 16, the through hole 390d of the plate spring 390 for vibration isolation has a larger diameter than the other through holes 380a, 380b, 390a, and 390 c. Therefore, the support spring 380 can transmit the vibration of the weight (counter weight) 302 to the piezoelectric vibration unit 303 side without interfering with the movement of the anti-vibration plate spring 390.

As described above, in the linear feeder 300a of the present invention, the instability, the skew transfer, the stagnation of the conveyed parts, or the instability and the yaw of the driving of the linear feeder 300a can be prevented, and the stable parts conveyance can be performed.

Next, fig. 17 is a schematic side view showing another example of the linear feeders 300, 300 a.

In the linear feeder 300b shown in fig. 17, the plate spring 390 for vibration prevention is provided on a surface different from the surface on which the support spring 380 is provided. That is, a convex portion is formed on each of the base portion 301 and the piezoelectric vibration portion 303, and the vibration isolating plate spring 390 is fixed to the convex portions formed on the piezoelectric vibration portion 303 and the base portion 301 by bolts.

At this time, since the vibration modes of the support spring 380 and the plate spring 390 for vibration isolation can be matched, the parts to be conveyed can be prevented from being unstable, transferred obliquely, or staying, or the linear feeder 300b can be prevented from being unstable or swinging, and stable parts conveyance can be performed.

In the parts feeding apparatus of the present invention, the linear feeders 300, 300a, 300b correspond to the parts feeding apparatus, the base 301 corresponds to the base, the weight (counter weight) 302 corresponds to the weight, the piezoelectric vibrating portion 303 corresponds to the vibrating portion, the plate spring 390 for vibration prevention corresponds to the vibration preventing member, the support spring 380 corresponds to the driving member, the bolt 385 corresponds to the same shaft member, the piezoelectric element 411 corresponds to the vibrator, the vibrating plates 400, 400a, and 400b correspond to the vibrating plate, the coupling member 422 corresponds to the coupling member, the flat plate elastic members 420, 420a, 420b correspond to the 1 st flat plate elastic member, the flat plate elastic member 421, 421b corresponds to the 2 nd plate-like elastic member, the thicknesses L1, L2, and (L1+ L2) correspond to the thicknesses, the 1 st conveying member 320, the 2 nd conveying member 330, and the 3 rd conveying member 350 correspond to the conveying portions, and the micro component 800 corresponds to the component.

The present invention is described in the above preferred embodiment, but the present invention is not limited thereto. It will be understood that various embodiments may be additionally implemented without departing from the spirit and scope of the invention. In the present embodiment, the operation and effect of the configuration of the present invention are described, but these operation and effect are an example, and the present invention is not limited thereto.

Claims (8)

1. A component supply device for conveying a component by applying vibration thereto, comprising:

a conveying part having a conveying passage for conveying the parts;

a vibration applying unit for supporting the conveying unit;

a weight portion provided as a member different from the vibration applying portion;

a driving member having one end mounted on the vibration applying portion and the other end mounted on the hammer portion and elastically deformable;

a vibrator generating stress in response to the electric signal;

a vibrating plate having a horizontal plate portion disposed horizontally and a vertical plate portion disposed vertically, the vibrator being attached to at least one of front and back surfaces of the vertical plate portion to excite vibration;

one of the horizontal plate portion and the vertical plate portion of the diaphragm is attached to the weight portion, the other of the horizontal plate portion and the vertical plate portion is attached to the vibration applying portion, the horizontal plate portion and the vertical plate portion are joined to each other by a joining portion, and one of the horizontal plate portion and the vertical plate portion is thicker than the other of the horizontal plate portion and the vertical plate portion.

2. The parts supplying apparatus according to claim 1, wherein the vibration plate comprises:

a 1 st flat plate-like elastic member forming the horizontal plate portion;

a 2 nd flat plate-like elastic member which is formed with the vertical plate portion and has a thickness different from that of the 1 st flat plate-like elastic member;

and a coupling member that couples the horizontal plate portion formed by the 1 st plate-like elastic member and the vertical plate portion formed by the 2 nd plate-like elastic member.

3. The parts supplying apparatus according to claim 1,

the diaphragm is formed of a flat plate-like elastic member having a longitudinal direction and a thick portion in a region along a part of the longitudinal direction;

the vertical plate portion and the horizontal plate portion are formed by bending the thick portion of the flat plate-like elastic member.

4. The parts supplying apparatus according to any one of claims 1 to 3, wherein the conveying passage is a linear conveying passage.

5. The parts supplying apparatus according to claim 1,

a vibration damping member attached to the vibration applying portion and the foundation portion to damp vibration transmitted from the vibration applying portion to the foundation portion;

the driving member is attached to the vibration applying portion and the weight portion provided below the vibration applying portion and above the base portion disposed at the lowermost portion, and elastically deforms to generate vibrations in opposite phases with respect to the weight portion and the vibration applying portion.

6. The parts supplying apparatus according to claim 5,

the driving member and the vibration isolating member are disposed to have portions overlapping in height in the vertical direction.

7. The parts supplying apparatus according to claim 6,

the driving member and the vibration isolating member are disposed in a stacked state.

8. The parts supplying apparatus according to any one of claims 5 to 7,

the driving member and the vibration isolating member are each formed of a flat plate-like elastic plate having a hole,

the vibration isolation member and the driving member are fixed to the vibration applying section by the same shaft member penetrating through a hole of the vibration isolation member and a hole of the driving member.