JP2007168920A - Parts feeder - Google Patents

Parts feeder Download PDF

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Publication number
JP2007168920A
JP2007168920A JP2005364814A JP2005364814A JP2007168920A JP 2007168920 A JP2007168920 A JP 2007168920A JP 2005364814 A JP2005364814 A JP 2005364814A JP 2005364814 A JP2005364814 A JP 2005364814A JP 2007168920 A JP2007168920 A JP 2007168920A
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Prior art keywords
vibration
spring
component supply
supply device
support spring
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JP2005364814A
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JP5011720B2 (en
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Shuichi Narukawa
修一 成川
Tetsuyuki Kimura
哲行 木村
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Shinko Electric Co Ltd
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Shinko Electric Co Ltd
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Priority to JP2005364814A priority Critical patent/JP5011720B2/en
Priority to TW101135285A priority patent/TWI490153B/en
Priority to TW095142811A priority patent/TWI389831B/en
Priority to KR1020060128986A priority patent/KR101244236B1/en
Priority to CN2006101693845A priority patent/CN1986358B/en
Publication of JP2007168920A publication Critical patent/JP2007168920A/en
Priority to HK07111606.6A priority patent/HK1106205A1/en
Application granted granted Critical
Publication of JP5011720B2 publication Critical patent/JP5011720B2/en
Priority to KR1020120150439A priority patent/KR101267924B1/en
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a parts feeder capable of enhancing the vibration-isolating efficiency, consistently conveying parts by reducing the height of the position of the center of gravity of a sprung mass, and reducing the height of the parts feeder itself. <P>SOLUTION: A base part 301 is arranged under a linear type parts feeder 300, a counterweight 302 is arranged thereon via a vibration-isolating leaf spring 390, and a piezoelectric type vibration unit 303 is further arranged thereon. A supporting spring 380 connected to the counterweight 302 and the piezoelectric type vibration unit, and the vibration-isolating leaf spring 390 connected to the base part 301 and the piezoelectric type vibration unit 303 are arranged in an overlapping manner in the vertical direction. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、部品を振動により移送することが可能な部品供給装置に関する。   The present invention relates to a component supply apparatus capable of transferring components by vibration.

従来、部品に対して振動を与えることにより、部品を整列させるとともに、部品の供給を行う部品供給装置の一つとしてパーツフィーダがよく知られている。このパーツフィーダは、部品に振動を与えることにより部品の姿勢を整え、次工程に供給することができる。   2. Description of the Related Art Conventionally, a parts feeder is well known as one of parts supply apparatuses that align parts by supplying vibration to the parts and supply the parts. This parts feeder can adjust the posture of the part by applying vibration to the part and supply it to the next process.

特許文献１には、高周波数駆動時であっても十分な振幅を確保するとともに振動発生手段に作用する応力を抑制し、振動発生手段の取り替えや共振周波数の変更及び調整を容易に行うことができる圧電駆動式パーツフィーダが開示されている。
国際公開第２００４／０６７４１３号パンフレット In Patent Document 1, it is possible to ensure sufficient amplitude even during high frequency driving and to suppress stress acting on the vibration generating means, and to easily change the vibration generating means and change and adjust the resonance frequency. A piezoelectric driven parts feeder is disclosed.
International Publication No. 2004/067413 Pamphlet

しかしながら、従来のパーツフィーダにおいては、ベース部、カウンターウェイト、可動部および搬送路を順に下から積み上げる構成となっていたため、支持ばねにおける揺動方向と防振用板ばねにおける揺動方向とが相反する方向となり均一な振動を搬送路に与えることができないという課題があった。以下、詳細について説明する。   However, in the conventional parts feeder, since the base portion, the counterweight, the movable portion, and the conveyance path are sequentially stacked from the bottom, the swinging direction of the support spring and the swinging direction of the vibration-proof leaf spring are contradictory. There is a problem that uniform vibration cannot be applied to the conveyance path. Details will be described below.

図１０は従来のパーツフィーダ９００の支持ばねにおける揺動方向と防振用板ばねにおける揺動方向とを説明するための模式図である。   FIG. 10 is a schematic diagram for explaining the swing direction of the support spring of the conventional parts feeder 900 and the swing direction of the vibration-proof leaf spring.

図１０に示すように、可動部９０２とカウンターウェイト９０３とを接続する支持ばね９８０は、図中の矢印Ｒ１の方向に揺動する状態であるが、カウンターウェイト９０３とベース部９０１とを接続する防振用板ばね９９０は、図中の矢印Ｒ１１の方向に揺動する状態であり、互いに曲げモードが逆位相となり、対向する方向に揺動していた。その結果、搬送路９０５における振動が安定せず、部品の搬送が停止したり、逆送されるという課題があった。   As shown in FIG. 10, the support spring 980 that connects the movable portion 902 and the counterweight 903 is in a state of swinging in the direction of the arrow R1 in the figure, but connects the counterweight 903 and the base portion 901. The anti-vibration leaf spring 990 is in a state of swinging in the direction of the arrow R11 in the figure, and the bending modes are opposite to each other, and swings in opposite directions. As a result, the vibration in the conveyance path 905 is not stable, and there is a problem that the conveyance of components stops or is reversely fed.

さらに、支持ばね９８０および防振用板ばね９９０を用いた部品供給装置では、直線状に支持ばね９８０および防振用板ばね９９０を配置させるため、部品供給装置のサイズ（図中Ｈ１０）が大きくなっていた。 Further, in the component supply device using the support spring 980 and the vibration isolating plate spring 990, since the support spring 980 and the vibration isolating plate spring 990 are arranged linearly, the size of the component supply device (H 10 in the figure) is It was getting bigger.

また、特許文献１記載の部品供給装置に限らず、一般の支持ばねおよび防振用板ばねを用いた部品供給装置では、２種類のばねを使用するため、ばね上質量の重心位置と、防振用板ばねの支点との距離が大きくなり、搬送部品の不安定、斜め搬送、滞留、または部品供給装置の駆動不安定性、横揺れが生じる。   Further, not only the component supply device described in Patent Document 1, but also a general component supply device using a support spring and an anti-vibration leaf spring uses two types of springs. The distance from the fulcrum of the vibration plate spring becomes large, and unstable parts of the conveying parts, oblique conveying, staying, driving instability of the parts supplying device, and rolling occur.

本発明の目的は、防振効率を向上させるとともに、ばね上質量の重心位置の高さを低くして安定した部品の搬送および部品供給装置自体の低背化を実現することができる部品供給装置を提供することである。   An object of the present invention is to improve the vibration isolation efficiency and reduce the height of the center of gravity of the sprung mass to achieve stable component transportation and a low profile of the component supply device itself. Is to provide.

課題を解決するための手段及び効果Means and effects for solving the problems

（１）
本発明に係る部品供給装置は、搬送路に振動を発生させることにより搬送路内に供給される部品を直線状に移送する部品供給装置であって、下部に配設されるベース部と、搬送路が設けられているとともにベース部の上方に配設されて振動を発生する加振部と、加振部よりも下方でベース部よりも上方に設けられる固定部と、加振部とベース部とに取り付けられ、加振部からベース部へ伝達される振動を減衰させる防振部材と、加振部と固定部とに取り付けられ、弾性変形することにより、固定部と加振部とに互いに逆位相の振動を発生させる駆動部材とを備えたものである。 (1)
A component supply apparatus according to the present invention is a component supply apparatus that linearly transfers a component supplied into a conveyance path by generating vibration in the conveyance path, and includes a base portion disposed at a lower portion, and a conveyance A vibration portion that is provided above the base portion and generates vibration, a fixed portion that is provided below the vibration portion and above the base portion, and the vibration portion and the base portion. Are attached to the vibration isolating member for attenuating the vibration transmitted from the vibration exciter to the base, and are attached to the vibration exciter and the fixed member. And a drive member that generates anti-phase vibrations.

本発明に係る部品供給装置においては、下部よりベース部、固定部、加振部の順に設けられ、防振部材が加振部とベース部とに取り付けられ、駆動部材が加振部と固定部とに取り付けられる。   In the component supply apparatus according to the present invention, the base portion, the fixed portion, and the vibration portion are provided in this order from the bottom, the vibration isolation member is attached to the vibration portion and the base portion, and the drive member is the vibration portion and the fixed portion. And attached.

この場合、駆動部材と防振部材とが加振部および固定部の間において、重複して配設されるため、駆動部材および防振部材の互いの曲げモードが同位相となり、防振効率を向上させることができる。また、従来、駆動部材および防振部材が互いに直線状に配置された状態に対して、駆動部材の長手方向の長さが、防振部材の長手方向の一部と重複して設けられるため、部品供給装置自体の低背化が可能となり、部材上質量の重心位置と防振部材の支点との距離を縮めることができる。その結果、搬送部品の不安定、斜め搬送、滞留、または部品供給装置の駆動不安定性および横揺れを防止することができる。   In this case, since the driving member and the vibration isolating member are disposed in an overlapping manner between the vibrating portion and the fixed portion, the bending modes of the driving member and the vibration isolating member are in phase, and the vibration isolating efficiency is improved. Can be improved. In addition, conventionally, the length in the longitudinal direction of the driving member is overlapped with a part in the longitudinal direction of the vibration isolating member with respect to the state in which the driving member and the vibration isolating member are linearly arranged with each other. The height of the component supply device itself can be reduced, and the distance between the center of gravity of the mass on the member and the fulcrum of the vibration isolation member can be reduced. As a result, it is possible to prevent the instability of the conveying parts, the oblique conveyance, the stay, or the driving instability and the rolling of the parts supply device.

（２）
駆動部材および防振部材は、上下方向の高さ方向において高さが互いに重なっている部分を有するように配設されてもよい。 (2)
The driving member and the vibration isolating member may be disposed so as to have a portion where the heights overlap each other in the vertical height direction.

この場合、駆動部材と防振部材とが上下方向の高さ方向において高さが互いに重なっている部分を有するので、部品供給装置の低背化が可能となり、部材上質量の重心位置と防振部材の支点との距離を縮めることができる。その結果、搬送部品の不安定、斜め搬送、滞留、または部品供給装置の駆動不安定性および横揺れを防止することができる。   In this case, since the driving member and the vibration isolating member have a portion where the heights overlap each other in the vertical direction, it is possible to reduce the height of the component supply device, and the position of the center of gravity of the mass on the member and the vibration isolating The distance from the fulcrum of the member can be reduced. As a result, it is possible to prevent the instability of the conveying parts, the oblique conveyance, the stay, or the driving instability and the rolling of the parts supply device.

（３）
駆動部材および防振部材は、互いに積層状態で配設されてもよい。 (3)
The driving member and the vibration isolating member may be disposed in a stacked state.

この場合、板状の弾性板からなる防振部材および駆動部材が、互いに積層された状態で配設されるので、駆動部材および防振部材の互いの曲げモードが同位相となり、防振効率を向上させることができる。   In this case, since the vibration isolating member and the drive member made of a plate-like elastic plate are disposed in a stacked state, the bending modes of the drive member and the vibration isolating member are in phase, and the vibration isolating efficiency is improved. Can be improved.

（４）
駆動部材および防振部材は、それぞれ孔を有する平板状の弾性板から形成され、防振部材および駆動部材は、加振部に対して同一の軸部材により防振部材の孔および駆動部材の孔を貫通して固定されていてもよい。 (4)
The driving member and the vibration isolating member are each formed of a flat elastic plate having a hole, and the vibration isolating member and the driving member are formed in the vibration isolating member hole and the driving member hole by the same shaft member with respect to the excitation unit. It may be fixed through.

この場合、駆動部材および防振部材が、同軸部材、例えばボルト等により孔を貫通して加振器に固定される。したがって、従来、駆動部材および防振部材が互いに直線状に配置された状態に対して、駆動部材の長手方向の長さが、防振部材の長手方向の一部と重複して設けられるため、部品供給装置自体の低背化が可能となり、部材上質量の重心位置と防振部材の支点との距離を縮めることができる。さらに、ボルト等の固定部材の部品点数を削減することができるので、部品自体のコストおよび製造時におけるコストの低減を図ることができる。   In this case, the driving member and the vibration isolating member are fixed to the vibration exciter through the hole with a coaxial member such as a bolt. Therefore, conventionally, the length in the longitudinal direction of the drive member is overlapped with a part in the longitudinal direction of the vibration isolation member with respect to the state in which the drive member and the vibration isolation member are linearly arranged with respect to each other. The height of the component supply device itself can be reduced, and the distance between the center of gravity of the mass on the member and the fulcrum of the vibration isolation member can be reduced. Furthermore, since the number of parts of fixing members such as bolts can be reduced, it is possible to reduce the cost of the parts themselves and the cost during manufacturing.

以下、本発明に係る部品供給装置の実施の形態について説明する。なお、以下の実施の形態においては、リニア型パーツフィーダ３００を例にとって説明する。   Embodiments of a component supply apparatus according to the present invention will be described below. In the following embodiment, a linear parts feeder 300 will be described as an example.

（実施の形態）
図１は、本発明の実施の形態に係るリニア型パーツフィーダ３００の一例を示す模式的側面図である。 (Embodiment)
FIG. 1 is a schematic side view showing an example of a linear part feeder 300 according to an embodiment of the present invention.

図１に示すように、リニア型パーツフィーダ３００は、ベース部３０１、カウンターウェイト３０２、圧電式振動部３０３、振動伝達部３０４、搬送路３０５、連結板３７０、支持ばね３８０および防振用板ばね３９０を含む。   As shown in FIG. 1, a linear part feeder 300 includes a base part 301, a counterweight 302, a piezoelectric vibration part 303, a vibration transmission part 304, a conveyance path 305, a connection plate 370, a support spring 380, and a vibration-proof plate spring. 390.

図１に示すように、ベース部３０１の上方にカウンターウェイト３０２が設けられる。カウンターウェイト３０２の上方には、支持ばね３８０を介して圧電式振動部３０３が設けられる。   As shown in FIG. 1, a counterweight 302 is provided above the base portion 301. Above the counterweight 302, a piezoelectric vibrator 303 is provided via a support spring 380.

また、本実施の形態におけるリニア型パーツフィーダ３００においては、支持ばね３８０および防振用板ばね３９０が重複して配設される。この重複配設の詳細については後述する。   Further, in the linear part feeder 300 according to the present embodiment, the support spring 380 and the vibration-proof plate spring 390 are disposed in an overlapping manner. Details of the overlapping arrangement will be described later.

また、図１のカウンターウェイト３０２および圧電式振動部３０３の内部には、平板を屈曲させたＬ字状の弾性部材４１０が設けられる。弾性部材４１０の一端側が圧電式振動部３０３に固定され、他端側がカウンターウェイト３０２に固定される。   Further, an L-shaped elastic member 410 having a bent flat plate is provided inside the counterweight 302 and the piezoelectric vibrating portion 303 in FIG. One end side of the elastic member 410 is fixed to the piezoelectric vibrating portion 303, and the other end side is fixed to the counterweight 302.

さらに、弾性部材４１０の両面には、圧電素子４１１が配設される。この弾性部材４１０および圧電素子４１１からなるばね定数は、搬送する部品の重量、大きさおよび搬送路３０５の重量等によって定められる任意の共振周波数の条件に応じて適宜選択される。   Further, piezoelectric elements 411 are disposed on both surfaces of the elastic member 410. The spring constant composed of the elastic member 410 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 parts to be transported, the weight of the transport path 305, and the like.

圧電素子４１１は、具体的に、圧電セラミックスを分極処理して弾性部材４１０の一方の面にプラス極性の分極電位を持たせたものを貼り付け、弾性部材４１０の他方の面にマイナス極性の分極電位を持たせたものを貼り付ける。それにより、弾性部材４１０の表裏面に圧電素子４１１によるバイモルフ構造が形成される。圧電素子４１１に電荷を付与することにより振動が生じ、圧電式振動部３０３とカウンターウェイト３０２とが互いに逆方向に振動する。   Specifically, the piezoelectric element 411 is obtained by attaching a piezoelectric ceramic having a positive polarity polarization potential on one surface of the elastic member 410 and applying a negative polarity polarization on the other surface of the elastic member 410. Affix an electric potential. Thereby, the bimorph structure by the piezoelectric element 411 is formed on the front and back surfaces of the elastic member 410. By applying electric charges to the piezoelectric element 411, vibration is generated, and the piezoelectric vibrating portion 303 and the counterweight 302 vibrate in opposite directions.

続いて、圧電式振動部３０３の上部には、振動伝達部３０４が設けられる。この振動伝達部３０４は、カウンターウェイト３０２に固設された連結板３７０により固定される。すなわち、振動伝達部３０４は、カウンターウェイト３０２の振動と同期した動きをする。また、振動伝達部３０４の上面には、搬送路３０５が設けられる。搬送路３０５に振動が付与されることにより、部品が搬送路３０５に設けられた搬送溝内を移動する。   Subsequently, a vibration transmission unit 304 is provided above the piezoelectric vibration unit 303. The vibration transmitting unit 304 is fixed by a connecting plate 370 fixed to the counterweight 302. That is, the vibration transmission unit 304 moves in synchronization with the vibration of the counterweight 302. A conveyance path 305 is provided on the upper surface of the vibration transmission unit 304. When vibration is applied to the conveyance path 305, the component moves in a conveyance groove provided in the conveyance path 305.

図２は、支持ばね３８０および防振用板ばね３９０の構造の一例を示す模式図である。   FIG. 2 is a schematic diagram showing an example of the structure of the support spring 380 and the vibration-damping leaf spring 390.

図２に示すように、支持ばね３８０および防振用板ばね３９０はそれぞれ平板状の弾性部材からなる。支持ばね３８０および防振用板ばね３９０の間には、平板状スペーサ３９１および２個のリング状スペーサ３９２が設けられる。   As shown in FIG. 2, the support spring 380 and the vibration-damping leaf spring 390 are each made of a flat elastic member. A flat spacer 391 and two ring spacers 392 are provided between the support spring 380 and the vibration isolation leaf spring 390.

図２に示すように、支持ばね３８０の一端側に貫通穴３８０ａが２個設けられ他端側に貫通穴３８０ｂが２個設けられる。また、防振用板ばね３９０の一端側に貫通穴３９０ａが２個設けられ、中央部近傍に貫通穴３９０ｂが２個設けられ、他端側に貫通穴３９０ｃが２個設けられている。   As shown in FIG. 2, two through holes 380 a are provided on one end side of the support spring 380, and two through holes 380 b are provided on the other end side. Further, two through holes 390a are provided on one end side of the vibration-proof leaf spring 390, two through holes 390b are provided near the center, and two through holes 390c are provided on the other end side.

ボルト３８５は、スプリングワッシャおよび平座金を備え、さらに支持ばね３８０の貫通穴３８０ａ、板状スペーサ３９１の貫通穴３９１ａおよび防振用板ばね３９０の貫通穴３９０ａを貫通して、圧電式振動部３０３に固定される。   The bolt 385 includes a spring washer and a plain washer, and further penetrates the through hole 380 a of the support spring 380, the through hole 391 a of the plate-like spacer 391, and the through hole 390 a of the vibration isolating plate spring 390, so Fixed to.

また、ボルト３８６は、スプリングワッシャおよび平座金を備え、さらに支持ばね３８０の貫通穴３８０ｂ、リング状スペーサ３９２および防振用板ばね３９０の貫通穴３９０ｂを貫通して、カウンターウェイト３０２に固定される。   The bolt 386 includes a spring washer and a plain washer, and further passes through the through hole 380 b of the support spring 380, the ring spacer 392, and the through hole 390 b of the vibration isolating plate spring 390, and is fixed to the counterweight 302. .

さらに、ボルト３９５は、スプリングワッシャおよび平座金を備え、さらに貫通穴３９０ｃを貫通してベース部３０１に固定される。   Further, the bolt 395 includes a spring washer and a plain washer, and further passes through the through hole 390 c and is fixed to the base portion 301.

図３は、図２の示した支持ばね３８０および防振用板ばね３９０の構造を説明するための模式的断面図である。   FIG. 3 is a schematic cross-sectional view for explaining the structure of the support spring 380 and the vibration isolating leaf spring 390 shown in FIG.

図３に示すように、防振用板ばね３９０の貫通穴３９０ｂの直径は、他の貫通穴３８０ａ、３８０ｂ、３９０ａ、３９０ｃよりも大きい。すなわち、防振用板ばね３９０の貫通穴３９０ｂの直径は、ボルト３８６のヘッド部よりも大きな穴径から形成される。よって、支持ばね３８０が防振用板ばね３９０の動きに干渉されることなく、圧電式振動部３０３の振動をカウンターウェイト３０２側に伝達することができる。   As shown in FIG. 3, the diameter of the through-hole 390b of the vibration-proof plate spring 390 is larger than the other through-holes 380a, 380b, 390a, and 390c. That is, the diameter of the through hole 390 b of the vibration-proof plate spring 390 is formed to be larger than the diameter of the head portion of the bolt 386. Therefore, the vibration of the piezoelectric vibrating portion 303 can be transmitted to the counterweight 302 side without the support spring 380 interfering with the movement of the vibration-proof plate spring 390.

次に、本発明の実施の形態におけるリニア型パーツフィーダ３００の効果について説明する。   Next, the effect of the linear part feeder 300 in the embodiment of the present invention will be described.

図４および図５は、リニア型パーツフィーダ３００の効果について説明するための図である。図４（ａ）はリニア型パーツフィーダ３００の支持ばね３８０および防振用板ばね３９０の構造を示し、図４（ｂ）は従来のリニア型パーツフィーダ(図１０参照)の支持ばね９８０および防振用板ばね９９０の構造を示す図である。また、図５（ａ）は本発明に係る支持ばね３８０および防振用板ばね３９０の初期状態（添付符号Ｚ）および最大振幅状態を示し、図５（ｂ）は従来の支持ばね９８０および防振用板ばね９９０の初期状態（添付符号Ｚ）および最大振幅状態を示す。   4 and 5 are diagrams for explaining the effect of the linear part feeder 300. FIG. FIG. 4A shows the structure of the support spring 380 and vibration isolating plate spring 390 of the linear type part feeder 300, and FIG. 4B shows the support spring 980 and anti-vibration of the conventional linear type part feeder (see FIG. 10). It is a figure which shows the structure of the vibration plate spring 990. FIG. FIG. 5A shows an initial state (attached symbol Z) and a maximum amplitude state of the support spring 380 and the vibration isolating plate spring 390 according to the present invention, and FIG. The initial state (attached code Z) and the maximum amplitude state of the vibration leaf spring 990 are shown.

図４（ａ）に示す支持ばね３８０および防振用板ばね３９０は、リニア型パーツフィーダ３００の駆動時に、同じモードで変形する。一方、図４（ｂ）に示す支持ばね９８０および防振用板ばね９９０は、リニア型パーツフィーダの駆動時に、互いに異なるモード（図中Ｘ１およびＸ２）で変形する。以下、モードについて説明する。   The support spring 380 and the vibration isolating leaf spring 390 shown in FIG. 4A are deformed in the same mode when the linear part feeder 300 is driven. On the other hand, the support spring 980 and the vibration isolating leaf spring 990 shown in FIG. 4B are deformed in different modes (X1 and X2 in the figure) when the linear part feeder is driven. The mode will be described below.

ここで、図５（ａ）に示すように、初期状態の支持ばね３８０Ｚおよび防振用板ばね３９０Ｚは、互いに重複した状態で設けられ、支持ばね３８０Ｚの端部と防振用板ばね３９０Ｚの端部との距離は、距離Ｌ１である。また、最大振幅の状態において支持ばね３８０および防振用板ばね３９０は、互いに動き（モード）が一致しており、支持ばね３８０の端部および防振用板ばね３９０の端部の距離Ｌ２は、距離Ｌ１とほぼ等しく、距離の変化率Ｌ２／Ｌ１が限りなく１に近い値を示す。   Here, as shown in FIG. 5A, the support spring 380Z and the vibration isolating plate spring 390Z in the initial state are provided so as to overlap each other, and the end portion of the support spring 380Z and the vibration isolating plate spring 390Z are provided. The distance from the end is the distance L1. In the maximum amplitude state, the support spring 380 and the vibration isolating plate spring 390 have the same movement (mode), and the distance L2 between the end of the support spring 380 and the end of the anti-vibration leaf spring 390 is The distance change rate L2 / L1 is almost as close to 1 as the distance L1.

一方、図４（ｂ）および図５（ｂ）に示すように、初期状態の支持ばね９８０Ｚおよび防振用板ばね９９０Ｚは、一直線上に配置され、互いの間隔が距離Ｌ３である。また、最大振幅の状態において支持ばね９８０および防振用板ばね９９０は、互いに動き（モード）が逆となり、間隔が距離Ｌ４となる。この距離Ｌ３と距離Ｌ４とは、距離Ｌ３＜距離Ｌ４の関係であり、距離の変化率Ｌ４／Ｌ３が１よりも大きい、例えば図５（ｂ）においては、６に近い値を示す。   On the other hand, as shown in FIGS. 4B and 5B, the support spring 980Z and the vibration-proof plate spring 990Z in the initial state are arranged on a straight line, and the distance between them is the distance L3. Further, in the state of the maximum amplitude, the support spring 980 and the vibration isolating leaf spring 990 have opposite movements (modes), and the distance is the distance L4. The distance L3 and the distance L4 have a relationship of distance L3 <distance L4, and the distance change rate L4 / L3 is larger than 1, for example, a value close to 6 in FIG.

以上のように、図４（ｂ）および図５（ｂ）に示す従来の支持ばね９８０および防振用板ばね９９０は、振動する際に互いの間隔が、距離Ｌ３の状態から距離Ｌ４に広がるため、互いに引っ張り合う状態となり、振動の乱れが生じることとなる。その結果、支持ばね９８０と防振用板ばね９９０とは、動き（モード）が一致せず、個々多様な動きをすることとなり、防振用板ばね９９０による防振効果が発揮されにくくなる。   As described above, when the conventional support spring 980 and the vibration isolating leaf spring 990 shown in FIGS. 4B and 5B are vibrated, the distance between them increases from the distance L3 to the distance L4. For this reason, they are in a state of pulling each other, and vibration disturbance occurs. As a result, the support spring 980 and the vibration isolating plate spring 990 do not have the same movement (mode) and move in various ways, and the anti-vibration effect by the anti-vibration leaf spring 990 is hardly exhibited.

一方、図４（ａ）または図５（ａ）に示す支持ばね３８０および防振用板ばね３９０は、同じ動き（モード）で振動し、振動する際に互いの間隔が、距離Ｌ１の状態から距離Ｌ１とほぼ同じ距離Ｌ２に移行するため、支持ばね３８０および防振用板ばね３９０における振動の乱れが生じない。その結果、支持ばね３８０および防振用板ばね３９０は、動き（モード）が一致し、防振用板ばね３９０による防振効果が発揮されやすい。   On the other hand, the support spring 380 and the vibration isolating leaf spring 390 shown in FIG. 4A or FIG. 5A vibrate in the same movement (mode), and when they vibrate, the distance between them is from the state of the distance L1. Since the distance L2 is substantially the same as the distance L1, vibration disturbance does not occur in the support spring 380 and the vibration isolating leaf spring 390. As a result, the movement (mode) of the support spring 380 and the vibration isolating plate spring 390 is the same, and the anti-vibration effect by the anti-vibration leaf spring 390 is easily exhibited.

以上のことから、本願発明に係るリニア型パーツフィーダ３００においては、図４（ｂ）の構造を備えたリニア型パーツフィーダと比較して、防振効率が向上することがわかる。   From the above, it can be seen that the anti-vibration efficiency is improved in the linear part feeder 300 according to the present invention as compared with the linear part feeder having the structure of FIG.

また、図４（ａ）に示すように、支持ばね３８０が、防振用板ばね３９０の長手方向の一部と重複して配設されるため、鉛直方向の長さを縮めることができる。よって、図１０に示すリニア型パーツフィーダの全高さＨ１０と比較して、図１のリニア型パーツフィーダ３００の全高さＨ１は低くなる。また、図１０の防振用板ばね９９０の支点高さＨ２０と比較して、図１の防振用板ばね３９０の支点高さＨ２ は低くなる。さらに、防振用板ばね９９０の支点高さから防振用板ばね９９０の上質量の重心Ｗまでの距離Ｌ３０＋Ｈ２０も、図１に示す防振用板ばね３９０の支点高さから防振用板ばね３８０の上質量の重心Ｗまでの距離Ｌ３+Ｈ２まで短くなる。 Further, as shown in FIG. 4A, the support spring 380 is disposed so as to overlap with a part in the longitudinal direction of the vibration-proof plate spring 390, so that the length in the vertical direction can be reduced. Therefore, as compared with the overall height H 10 of the linear type parts feeder shown in FIG. 10, the total height H 1 of the linear parts feeder 300 in FIG. 1 becomes lower. Further, as compared with the fulcrum height H 20 of the vibration isolating plate spring 990 in FIG. 10, the fulcrum height H 2 of the vibration isolating plate spring 390 of Figure 1 is low. Further, the distance L 30 + H 20 from the height of the fulcrum of the vibration isolating leaf spring 990 to the center of gravity W of the upper mass of the vibration isolating leaf spring 990 is also prevented from the height of the fulcrum of the vibration isolating leaf spring 390 shown in FIG. The distance to the center of gravity W of the upper mass of the vibration leaf spring 380 is shortened to L 3 + H 2 .

以上のことより、本願発明に係るリニア型パーツフィーダ３００では、搬送部品の不安定、斜め搬送、滞留、またはリニア型パーツフィーダ３００の駆動不安定性、横揺れを防止することができ、安定した部品の搬送を行うことができる。   As described above, in the linear type part feeder 300 according to the present invention, it is possible to prevent the instability of the conveying parts, the oblique conveyance, the stay, or the driving instability and the rolling of the linear type parts feeder 300, and the stable parts. Can be carried.

次に、図６は、図１のリニア型パーツフィーダ３００の他の例を示す模式的側面図である。   Next, FIG. 6 is a schematic side view showing another example of the linear part feeder 300 of FIG.

図６に示すリニア型パーツフィーダ３００ａが図１に示すリニア型パーツフィーダ３００と異なるのは以下の点である。   The linear part feeder 300a shown in FIG. 6 differs from the linear part feeder 300 shown in FIG. 1 in the following points.

図６に示すように、リニア型パーツフィーダ３００ａにおいては、図１の支持ばね３８０の配置場所に防振用板ばね３９０が設けられ、図１の防振用板ばね３９０の配置場所に支持ばね３８０が設けられる。すなわち、防振用板ばね３９０が支持ばね３８０と圧電駆動部３０２との間に設けられ、支持ばね３８０が防振用板ばね３９０およびリニア型パーツフィーダ３００の外側に設けられる。以下、その配置について詳細に説明する。   As shown in FIG. 6, in the linear part feeder 300a, a vibration isolating plate spring 390 is provided at the location of the support spring 380 in FIG. 1, and the support spring is provided at the location of the vibration isolating plate spring 390 in FIG. 380 is provided. That is, the vibration-proof plate spring 390 is provided between the support spring 380 and the piezoelectric drive unit 302, and the support spring 380 is provided outside the vibration-proof plate spring 390 and the linear part feeder 300. Hereinafter, the arrangement will be described in detail.

図７は、図６の支持ばね３８０および防振用板ばね３９０の構造の一例を示す模式図である。   FIG. 7 is a schematic diagram showing an example of the structure of the support spring 380 and the vibration isolating leaf spring 390 of FIG.

図７に示すように、支持ばね３８０および防振用板ばね３９０はそれぞれ平板状の弾性部材からなる。支持ばね３８０および防振用板ばね３９０の間には、平板状スペーサ３９１が設けられる。   As shown in FIG. 7, the support spring 380 and the vibration isolating leaf spring 390 are each made of a flat elastic member. A flat spacer 391 is provided between the support spring 380 and the vibration-proof plate spring 390.

図７に示すように、支持ばね３８０の一端側に貫通穴３８０ａが２個設けられ他端側に貫通穴３８０ｂが２個設けられる。また、防振用板ばね３９０の一端側に貫通穴３９０ａが２個設けられ、中央部近傍に貫通穴３９０ｄが２個設けられ、他端側に貫通穴３９０ｃが２個設けられている。ここで、貫通穴３９０ｄは、ボルト３８６ａのヘッド部よりも大きな穴径を有する。   As shown in FIG. 7, two through holes 380 a are provided on one end side of the support spring 380, and two through holes 380 b are provided on the other end side. Further, two through holes 390a are provided on one end side of the vibration isolating leaf spring 390, two through holes 390d are provided in the vicinity of the center portion, and two through holes 390c are provided on the other end side. Here, the through hole 390d has a larger hole diameter than the head portion of the bolt 386a.

ボルト３８５は、スプリングワッシャおよび平座金を備え、さらに防振用板ばね３９０の貫通穴３９０ａ、平板状スペーサ３９１の貫通穴３９１ａおよび支持ばね３８０の貫通穴３８０ａを貫通して、圧電式振動部３０３に固定される。   The bolt 385 includes a spring washer and a flat washer, and further penetrates the through hole 390a of the vibration-proof plate spring 390, the through hole 391a of the flat spacer 391, and the through hole 380a of the support spring 380, and passes through the piezoelectric vibration portion 303. Fixed to.

また、ボルト３８６ａは、スプリングワッシャおよび平座金を備え、さらに支持ばね３８０の貫通穴３８０ｂを介してカウンターウェイト３０２に固定される。   The bolt 386 a includes a spring washer and a plain washer, and is further fixed to the counterweight 302 via the through hole 380 b of the support spring 380.

さらに、ボルト３９５ａは、スプリングワッシャおよび平座金を備え、さらに貫通穴３９０ｃを貫通してベース部３０１に固定される。   Further, the bolt 395a includes a spring washer and a plain washer, and further passes through the through hole 390c and is fixed to the base portion 301.

図８は、図６の支持ばね３８０および防振用板ばね３９０の構造の一例を示す模式図である。   FIG. 8 is a schematic diagram showing an example of the structure of the support spring 380 and the vibration isolating leaf spring 390 of FIG.

図８に示すように、防振用板ばね３９０の貫通穴３９０ｄの直径は、他の貫通穴３８０ａ、３８０ｂ、３９０ａ、３９０ｃよりも大きい。よって、支持ばね３８０が防振用板ばね３９０の動きに干渉されることなく、カウンターウェイト３０２の振動を圧電式振動部３０３側に伝達することができる。   As shown in FIG. 8, the diameter of the through hole 390d of the vibration-proof plate spring 390 is larger than the other through holes 380a, 380b, 390a, and 390c. Therefore, the vibration of the counterweight 302 can be transmitted to the piezoelectric vibrating portion 303 side without the support spring 380 interfering with the movement of the vibration-proof plate spring 390.

以上のことより、本願発明に係るリニア型パーツフィーダ３００ａでは、搬送部品の不安定、斜め搬送、滞留、またはリニア型パーツフィーダ３００ａの駆動不安定性、横揺れを防止することができ、安定した部品の搬送を行うことができる。   As described above, in the linear type part feeder 300a according to the present invention, it is possible to prevent the instability of the conveying parts, the oblique conveyance, the stay, or the driving instability and the rolling of the linear type parts feeder 300a. Can be carried.

次に、図９は、リニア型パーツフィーダ３００、３００ａの他の例を示す模式的側面図である。   Next, FIG. 9 is a schematic side view showing another example of the linear part feeders 300 and 300a.

図９に示すリニア型パーツフィーダ３００ｂは、防振用板ばね３９０を支持ばね３８０が設けられる面とは別の面に設けている。ちなわち、ベース部３０１および圧電式振動部３０３に凸部を形成し、防振用板ばね３９０をボルトにより圧電式振動部３０３とベース部３０１とに取り付けて固定させている。   In the linear parts feeder 300b shown in FIG. 9, the vibration-proof plate spring 390 is provided on a surface different from the surface on which the support spring 380 is provided. In other words, convex portions are formed on the base portion 301 and the piezoelectric vibration portion 303, and a vibration-proof plate spring 390 is attached and fixed to the piezoelectric vibration portion 303 and the base portion 301 with bolts.

この場合、支持ばね３８０および防振用板ばね３９０の振動モードを一致させることができるので、搬送部品の不安定、斜め搬送、滞留、またはリニア型パーツフィーダ３００ｂの駆動不安定性、横揺れを防止することができ、安定した部品の搬送を行うことができる。   In this case, since the vibration modes of the support spring 380 and the vibration isolating plate spring 390 can be matched, it is possible to prevent instability of conveying parts, oblique conveyance, stay, or drive instability and roll of the linear part feeder 300b. Can be carried out stably.

本発明に係る部品供給装置においては、リニア型パーツフィーダ３００，３００ａ，３００ｂが部品供給装置に相当し、ベース部３０１がベース部に相当し、カウンターウェイト３０２が固定部に相当し、圧電式振動部３０３、搬送路３０５が加振部に相当し、防振用板ばね３９０が防振部材に相当し、支持ばね３８０が駆動部材に相当し、ボルト３８５が同一の軸部材に相当し、搬送路３０５が搬送路に相当する。   In the component supply device according to the present invention, the linear part feeders 300, 300a, and 300b correspond to the component supply device, the base portion 301 corresponds to the base portion, the counterweight 302 corresponds to the fixed portion, and the piezoelectric vibration. The part 303 and the conveyance path 305 correspond to the vibration exciting part, the vibration-proof plate spring 390 corresponds to the vibration-proof member, the support spring 380 corresponds to the driving member, and the bolt 385 corresponds to the same shaft member. A path 305 corresponds to a conveyance path.

本発明は、上記の好ましい第１および第２の実施の形態に記載されているが、本発明はそれだけに制限されない。本発明の精神と範囲から逸脱することのない様々な実施形態が他になされることは理解されよう。さらに、本実施形態において、本発明の構成による作用および効果を述べているが、これら作用および効果は、一例であり、本発明を限定するものではない。   Although the present invention has been described in the above preferred first and second embodiments, the present invention is not limited thereto. It will be understood that various other embodiments may be made without departing from the spirit and scope of the invention. Furthermore, in this embodiment, although the effect | action and effect by the structure of this invention are described, these effect | actions and effects are examples and do not limit this invention.

本発明に係る実施の形態に係るリニア型パーツフィーダ３００の一例を示す模式的側面図Schematic side view showing an example of a linear part feeder 300 according to an embodiment of the present invention 支持ばねおよび防振用板ばねの構造の一例を示す模式図Schematic diagram showing an example of the structure of a support spring and a vibration-proof leaf spring 図２の示した支持ばねおよび防振用板ばねの構造を説明するための模式的断面図Typical sectional drawing for demonstrating the structure of the support spring shown in FIG. リニア型パーツフィーダの効果について説明するための図The figure for explaining the effect of the linear type parts feeder リニア型パーツフィーダの効果について説明するための図The figure for explaining the effect of the linear type parts feeder 図１のリニア型パーツフィーダの他の例を示す模式的側面図Schematic side view showing another example of the linear part feeder of FIG. 図６の支持ばねおよび防振用板ばねの構造の一例を示す模式図The schematic diagram which shows an example of the structure of the support spring of FIG. 図６の支持ばねおよび防振用板ばねの構造の一例を示す模式図The schematic diagram which shows an example of the structure of the support spring of FIG. リニア型パーツフィーダの他の例を示す模式的側面図Schematic side view showing another example of linear type parts feeder 従来のパーツフィーダの支持ばねにおける揺動方向と防振用板ばねにおける揺動方向とを説明するための模式図Schematic diagram for explaining the swing direction in the support spring of the conventional parts feeder and the swing direction in the vibration-proof leaf spring

符号の説明Explanation of symbols

３００，３００ａ，３００ｂ リニア型パーツフィーダ
３０１ ベース部
３０２ カウンターウェイト
３０３ 圧電式振動部
３０４ 振動伝達部
３０５ 搬送路
３７０ 連結板
３８０ 支持ばね
３９０ 防振用板ばね
４１０ 弾性体
４１１ 圧電素子 300, 300a, 300b Linear type part feeder 301 Base part 302 Counterweight 303 Piezoelectric vibration part 304 Vibration transmission part 305 Conveying path 370 Connecting plate 380 Supporting spring 390 Anti-vibration leaf spring 410 Elastic body 411 Piezoelectric element

Claims (4)

搬送路に振動を発生させることにより前記搬送路内に供給される部品を直線状に移送する部品供給装置であって、
下部に配設されるベース部と、
前記搬送路が設けられているとともに前記ベース部の上方に配設されて振動を発生する加振部と、
前記加振部よりも下方で前記ベース部よりも上方に設けられる固定部と、
前記加振部と前記ベース部とに取り付けられ、前記加振部から前記ベース部へ伝達される振動を減衰させる防振部材と、
前記加振部と前記固定部とに取り付けられ、弾性変形することにより、前記固定部と前記加振部とに互いに逆位相の振動を発生させる駆動部材と、を備えたことを特徴とする部品供給装置。 A component supply device that linearly transfers a component supplied into the conveyance path by generating vibration in the conveyance path,
A base portion disposed at the bottom;
A vibration unit that is provided above the base unit and generates vibration by being provided with the conveyance path;
A fixed portion provided below the excitation portion and above the base portion;
An anti-vibration member attached to the excitation unit and the base unit and dampening vibration transmitted from the excitation unit to the base unit;
A component, comprising: a drive member that is attached to the vibration part and the fixed part and elastically deforms to generate vibrations in opposite phases to the fixed part and the vibration part. Feeding device. 前記駆動部材および前記防振部材は、
上下の高さ方向において高さが互いに重なっている部分を有するように配設されていることを特徴とする請求項１に記載の部品供給装置。 The drive member and the vibration isolation member are
The component supply device according to claim 1, wherein the component supply device is disposed so as to have portions whose heights overlap each other in the vertical height direction. 前記駆動部材および前記防振部材は、
互いに積層状態で配設されたことを特徴とする請求項２に記載の部品供給装置。 The drive member and the vibration isolation member are
The component supply device according to claim 2, wherein the component supply devices are arranged in a stacked state. 前記駆動部材および前記防振部材は、
それぞれ孔を有する平板状の弾性板から形成され、
前記防振部材および前記駆動部材は、前記加振部に対して同一の軸部材により前記防振部材の孔および前記駆動部材の孔を貫通して固定されていることを特徴とする請求項１から請求項３のいずれか１項に記載の部品供給装置。 The drive member and the vibration isolation member are
Each is formed from a flat elastic plate having holes,
2. The vibration isolating member and the driving member are fixed to the vibration exciting portion through the hole of the vibration isolating member and the hole of the driving member by the same shaft member. The component supply device according to claim 3.
JP2005364814A 2005-12-19 2005-12-19 Parts supply device Active JP5011720B2 (en)

Priority Applications (7)

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JP2005364814A JP5011720B2 (en) 2005-12-19 2005-12-19 Parts supply device
TW101135285A TWI490153B (en) 2005-12-19 2006-11-20 Part supply device
TW095142811A TWI389831B (en) 2005-12-19 2006-11-20 Part supply device
KR1020060128986A KR101244236B1 (en) 2005-12-19 2006-12-15 Parts Supply Apparatus
CN2006101693845A CN1986358B (en) 2005-12-19 2006-12-19 Parts supplying device
HK07111606.6A HK1106205A1 (en) 2005-12-19 2007-10-26 A components feeder
KR1020120150439A KR101267924B1 (en) 2005-12-19 2012-12-21 Parts Supply Apparatus

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JP2009274800A (en) * 2008-05-14 2009-11-26 Yamato Scale Co Ltd Straight advancing feeder, and its fixing method and combination measure equipped therewith
WO2012147838A1 (en) * 2011-04-27 2012-11-01 シンフォニアテクノロジー株式会社 Article separation and conveyance device
JP2012229120A (en) * 2011-04-27 2012-11-22 Sinfonia Technology Co Ltd Article separation and conveyance device
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CN102700906A (en) * 2011-05-28 2012-10-03 上海天怡塑胶工业有限公司 Compatible lead end post vibration arraying device with positive and negative electrode error correcting functions
JP2013095564A (en) * 2011-11-02 2013-05-20 Daishin:Kk Vibration type conveyance device
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