201228908 六、發明說明： 【發明所屬之技術領域】 本發明係關於藉由驅動激振機構，使零件搬送構件振動 來搬送零件之振動式零件搬送裝置。 【先前技術】 振動式零件搬送裝置中，以賦予零件搬送構件最適合搬 送零件之振動為目的，具有採用可分別調整零件搬送構件 之水平方向振動與垂直方向振動之構成之複合振動式裝置 (例如，參照專利文獻1)。 作為如上所述之複合振動式零件搬送裝置，例如本發明 之實施形態之圖1及圖2所示之直進供料機，有在安裝零件 搬送構件即輸送機槽1之上部振動體2之周圍，配置矩形框 形狀之中間振動體4 ;以朝向垂直方向之第i板彈簧（水平 振動用彈性構件）5連結中間振動體4與基台3 ;以朝向水平 方向之第2板彈簧（垂直振動用彈性構件）6連結上部振動體] 與中間振動體4 ;且設置有使水平方向之振動產生之第1激 振機構7、與使垂直方向之振動產生之第2激振機構8之構 造者。 並且，上述各激振機構7、8係分別以交流電磁石9、 11、與可動鐵芯10、12構成，藉由分別控制施加於各激振 機構7、8之電磁石9、11之電壓，可分別調整輸送機槽1之 水平方向之振動與垂直方向之振動。 然而，如此之複合振動式直進供料機中，一般而言，欲 提高搬送零件速度時’為以少量電力有效率地加大水平方 158478.doc 201228908 向之振動之振幅，而以輪送機槽之水平方向之固有振動數 附近之頻率驅動各激振機構。此時，水平方向與垂直方向 之振動振幅，通常係以水平方向之振動振幅為數百μιη& 右，垂直方向之振動振幅為數十μιη左右以下即以讓垂 直方向之振動振幅成為水平方向之振動振幅之1/1〇左右以 下之方式來調整。 此時，如圖14所示，在以第丨激振機構振動輸送機槽時 之輸送機槽之水平方向與垂直方向之振動頻譜波形中輸 送機槽之水平方向之固有振動數匕時之水平方向之振動振 幅Vh與垂直方向之振動振幅1之差，只差1至2 dB左右之 情形下，即使以輸送機槽之水平方向之固有振動數即頻率 Fh附近之頻率來驅動第1激振機構，僅欲使水平方向之振 動產生，恐怕有使於輸送機槽產生具有較大振幅之垂直方 向之振動之虞。若該垂直方向之振動振幅為數十 上，則與以第2激振機構所產生之垂直方向之振動重疊， 輸送機槽之垂直方向之振動之調整變得困難，變得無法賦 予輸送機槽最適於搬送零件之振動。 關於此問題，複合振動式之盤形供料機（例如，參照專 利文獻2、3 )亦存在同樣之問題。 例如，上述專利文獻2之盤形供料機，係如圖15所示， 有在安裝零件搬送構件即盤51之上部振動體52與設置於地 上之基台53之間設置十字狀之中間振動體54 ;以朝向垂直 方向之第1板彈簧（迴轉振動用板彈簧）55連結該中間振動體 54與基台53 ;以朝向水平方向之第2板彈簧（垂直振動用板 158478.doc 201228908 彈簧）56連結上部振動體52與中間振動體54 ;於中間振動 體54與基台53之間，設置有產生水平迴轉方向之振動之第 1激振機構（未圖示）；於上部振動體52與基台53之間，設置 有產生垂直方向振動之第2激振機構（未圖示）者。 並且’上述各激振機構係以分別設置於基台53上之交流 電磁石與中間振動體54及安裝於上部振動體52之可動鐵芯 構成’藉由分別控制施加於各激振機構之電磁石之電壓， 可分別調整盤51之水平迴轉方向之振動與垂直方向之振 動0 然而’於如此之複合振動式盤形供料機，若盤之水平迴 轉方向之固有振動數Fh時之水平迴轉方向之振動振幅％與 垂直方向之振動振幅Vv之差，只差1至2 dB左右，則與上 述直進供料機之情況相同，以盤之水平迴轉方向之固有振 動數之頻率Fh附近之頻率來驅動第丨激振機構時，於盤產 生具有較大之振幅之垂直方向之振動，該垂直方向之振動 與以第2激振機構所產生之垂直方向之振動重疊，調整盤 之垂直方向之振動變得困難，變得無法賦予盤最適於振動 賦予搬送零件之盤之情形很多。 [先前技術文獻] [專利文獻] [專利文獻1]特開昭55-84707號公報 [專利文獻2]特開平i〇_2〇3623號公報 [專利文獻3]特開平1^^6027號公報 【發明内容】 158478.doc 201228908 [發明所欲解決之問題] 本發明之課題係在複合振動式之零件搬送裝置t，抑制 起因於水平方向之振動之垂直方向之振動之產生。 [解決問題之技術手段] 為解決上述課題，本發㈣㈣：形成有零件搬送路之 零件搬送構件，·安裝上述零件搬送構件之上部振動體；設 於地上之基台；設於上述上部振動體與基台之間之中間振 動體；連結上述中間振動體與基台之第i彈性構件；及連 結上述上部振動體與令間㈣體之第2彈性構#;且將上 述第W性構件與第2彈性構件中之—方作為水平振動用彈 性構件’將另-方作為垂直振動用彈性構件，以上述水平 振動用彈性構件與第丨激振機構賦予零件搬送構件水平方 向之振動，以上述垂直振動用彈性構件與第2激振機構賦 予零件搬送構件垂直方向之振動的振動式零件搬送裝置 中，採用在上述第1激振機構以其水平方向之固有振動數 振動零件搬送構件時，使於上述零件搬送構件所產生之垂 直方向之振動之振幅比水平方向之振動之振幅還小6 dB以 上之構成。藉由如此地使零件搬送構件之水平方向之固有 振動數中之水平方向之振動振幅與垂直方向之振動振幅產 生大的差異，於以零件搬送構件之水平方向之固有振動數 附近之頻率來驅動各激振機構時，亦可縮小起因於水平方 向之振動之垂直方向之振動之振幅。 此時，最好以上述第1激振機構振動零件搬送構件，使 該振動數作為零件搬送構件之垂直方向之固有振動數時所 158478.doc 201228908 產生之垂直方向之振動之振幅比該振動數作為零件搬送構 件之水平方向之固有振動數時所產生之水平方向之振動之 振幅還小3 dB以上。如此做的話，因水平方向與垂直方向 之振動振幅之峰值相差3 dB以上’故可簡單形成產生上述 6 dB以上振幅差之構成。 再者，若將上述水平振動用彈性構件，固定在與零件搬 送方向正交之同一水平線上之2處固定位置，則水平振動 用彈性構件之水平方向之變形與垂直方向之位移變得無關 聯，可抑制起因於水平方向之振動之垂直方向之振動。 另一方面，上述垂直振動用彈性構件係可固定於與零件 搬送方向正交之同一水平線上之2處固定位置，或可固定 於與零件搬送方向平行之同一水平線上之2處固定位置。 成有螺旋狀搬送路之盤，j 用於與上述第1激振機構一 又，作為本發明之-例，可將上述零件搬送構件作為形 上述盤之振動式零件搬送裝置（盤形供料機 並將上述水平振動用彈性構件適 一同將水平迴轉方向之振動賦予 之情形[Technical Field] The present invention relates to a vibrating component conveying apparatus that transports a component by vibrating a component conveying member by driving an excitation mechanism. [Prior Art] In the vibrating component conveying device, a composite vibrating device that can adjust the horizontal vibration and the vertical vibration of the component conveying member is provided for the purpose of imparting vibration to the component conveying member. Refer to Patent Document 1). As the above-described composite vibration type component conveying device, for example, the straight feeding machine shown in Figs. 1 and 2 of the embodiment of the present invention is provided around the vibrating body 2 above the conveyor groove 1 as the component transporting member. The intermediate vibrating body 4 having a rectangular frame shape is disposed; the intermediate vibrating body 4 and the base 3 are coupled by the i-th leaf spring (the horizontal vibration elastic member) 5 facing in the vertical direction; and the second leaf spring facing the horizontal direction (vertical vibration) The upper vibrating body 4 and the intermediate vibrating body 4 are connected by an elastic member 6; and the first excitation mechanism 7 for generating vibration in the horizontal direction and the second excitation mechanism 8 for generating vibration in the vertical direction are provided. . Further, each of the excitation mechanisms 7 and 8 is composed of AC electromagnets 9 and 11 and movable iron cores 10 and 12, and the voltages of the electromagnets 9 and 11 applied to the excitation mechanisms 7 and 8 are controlled by the respective excitation mechanisms 7 and 8 respectively. The vibration in the horizontal direction and the vibration in the vertical direction of the conveyor groove 1 are separately adjusted. However, in such a composite vibrating straight feed machine, in general, when it is desired to increase the speed of the transported parts, the amplitude of the vibration is increased by a small amount of electric power, and the wheel is sent to the machine. Each excitation mechanism is driven at a frequency near the number of natural vibrations in the horizontal direction of the groove. In this case, the vibration amplitude in the horizontal direction and the vertical direction is usually a vibration amplitude in the horizontal direction of several hundred μm & right, and the vibration amplitude in the vertical direction is about several tens μm or less, that is, the vibration amplitude in the vertical direction is horizontal. The vibration amplitude is adjusted by about 1/1 以下 or less. At this time, as shown in FIG. 14, the level of the natural vibration number in the horizontal direction of the conveyor groove in the vibration spectrum waveform of the horizontal direction and the vertical direction of the conveyor groove when the second excitation mechanism vibrates the conveyor groove When the difference between the vibration amplitude Vh of the direction and the vibration amplitude 1 of the vertical direction is only about 1 to 2 dB, the first excitation is driven by the frequency near the frequency Fh which is the natural vibration number in the horizontal direction of the conveyor groove. The mechanism is only intended to generate vibration in the horizontal direction, and there is a fear that the conveyor groove will generate a vibration having a large amplitude in the vertical direction. When the vibration amplitude in the vertical direction is several tens of degrees, the vibration in the vertical direction generated by the second excitation mechanism overlaps, and the adjustment of the vibration in the vertical direction of the conveyor groove becomes difficult, and the conveyor groove cannot be provided. Ideal for vibration of parts. Regarding this problem, the same problem exists in the composite vibrating disk feeder (for example, refer to Patent Documents 2 and 3). For example, as shown in Fig. 15, the disk-shaped feeder of the above-mentioned Patent Document 2 has a cross-shaped intermediate vibration between the upper vibrating body 52 of the disk 51 and the base 53 provided on the ground. The body 54 is connected to the intermediate vibrating body 54 and the base 53 by a first leaf spring (swinging vibration leaf spring) 55 facing in the vertical direction; the second leaf spring facing the horizontal direction (vertical vibration plate 158478.doc 201228908 spring) The upper vibrating body 52 and the intermediate vibrating body 54 are connected to each other; a first excitation mechanism (not shown) for generating vibration in the horizontal rotation direction is provided between the intermediate vibrating body 54 and the base 53; and the upper vibrating body 52 is provided. A second excitation mechanism (not shown) that generates vibration in the vertical direction is provided between the base 53 and the base 53. Further, each of the above-described excitation mechanisms is configured by respectively controlling the alternating electromagnet and the intermediate vibrating body 54 provided on the base 53 and the movable iron core attached to the upper vibrating body 52 by controlling the electromagnets applied to the respective vibrating mechanisms. The voltage can adjust the vibration of the horizontal rotation direction of the disk 51 and the vibration of the vertical direction respectively. However, in the case of such a composite vibration type disk feeder, if the natural vibration number Fh of the horizontal rotation direction of the disk is the horizontal rotation direction The difference between the vibration amplitude % and the vibration amplitude Vv in the vertical direction is only about 1 to 2 dB, and is driven by the frequency near the frequency Fh of the natural vibration number in the horizontal rotation direction of the disk, as in the case of the above-described linear feeder. In the case of the second excitation mechanism, a vibration having a large amplitude in the vertical direction is generated in the disk, and the vibration in the vertical direction overlaps with the vibration in the vertical direction generated by the second excitation mechanism, and the vibration in the vertical direction of the disk is adjusted. Difficult to make it difficult to give the disc the most suitable disc for vibrating the transported parts. [PATENT DOCUMENT] [Patent Document 1] JP-A-H05-84707 [Patent Document 2] JP-A No. Hei. [Problem to be Solved by the Invention] The problem of the present invention is to suppress the occurrence of vibration in the vertical direction caused by vibration in the horizontal direction in the composite vibration type component conveying device t. [Means for Solving the Problems] In order to solve the above problems, the present invention (4) (4): a component transporting member in which a component transport path is formed, an upper vibrating body in which the component transporting member is mounted, a base provided on the ground, and the upper vibrating body An intermediate vibrating body between the base and the base; the i-th elastic member connecting the intermediate vibrating body and the base; and the second elastic structure connecting the upper vibrating body and the inter-fourth body; and the W-th member In the second elastic member, the elastic member for horizontal vibration is used as the vertical vibration elastic member, and the horizontal vibration elastic member and the second excitation mechanism are given to the component conveying member in the horizontal direction. In the vibrating component conveying device in which the elastic member for the vertical vibration and the second excitation mechanism are provided to vibrate in the vertical direction of the component conveying member, when the first excitation mechanism vibrates the component conveying member with the natural vibration number in the horizontal direction, The amplitude of the vibration generated in the vertical direction generated by the component conveying member is smaller than the amplitude of the vibration in the horizontal direction by 6 dB or more. By causing a large difference between the vibration amplitude in the horizontal direction and the vibration amplitude in the vertical direction among the natural vibration numbers in the horizontal direction of the component conveying member, the frequency is driven at a frequency near the natural vibration number in the horizontal direction of the component conveying member. In each of the excitation mechanisms, the amplitude of the vibration in the vertical direction due to the vibration in the horizontal direction can be reduced. In this case, it is preferable that the first excitation mechanism vibrates the component transport member so that the vibration number is the natural vibration number of the component transport member in the vertical direction. The amplitude of the vibration generated in the vertical direction generated by the 158478.doc 201228908 is greater than the vibration number. The amplitude of the vibration in the horizontal direction generated when the number of natural vibrations in the horizontal direction of the component conveying member is smaller is 3 dB or less. In this case, since the peak of the vibration amplitude in the horizontal direction and the vertical direction differs by more than 3 dB, it is possible to easily form the above-described amplitude difference of 6 dB or more. In addition, when the horizontal vibration elastic member is fixed at two fixed positions on the same horizontal line orthogonal to the component conveying direction, the horizontal vibration deformation of the horizontal vibration elastic member is not associated with the vertical displacement. The vibration in the vertical direction caused by the vibration in the horizontal direction can be suppressed. On the other hand, the elastic member for vertical vibration can be fixed at two fixed positions on the same horizontal line orthogonal to the component conveying direction, or can be fixed at two fixed positions on the same horizontal line parallel to the component conveying direction. A disk having a spiral conveying path, j is used for the first excitation mechanism, and as the example of the present invention, the component conveying member can be used as a vibrating component conveying device for the disk (disc type feeding) And the above-mentioned horizontal vibration elastic member is used to appropriately impart vibration in the horizontal rotation direction
同—水平線上之2處固定位置。 又’可分別將表背面朝向 如上所述地將本發明適用於振動式盤形供料機 下’若將上述迴棘据勒用碟，Μ· 4致At m A . . 1 I58478.doc 201228908 水平方向之板彈簧來作為上述迴轉振動用彈性構件、將表 背面朝向垂直方向之板彈簧作為上述垂直振動用彈性構件 使用。 再者’以電磁石與可動鐵芯構成上述各激振機構，在朝 向其中一方之電磁石之施加電壓設定電路，設置產生施加 電壓之基準波形之基準波形產生機構、及調整上述基準波 形調整振幅之波形振幅調整機構；在朝向另一方之電磁石 之施加電壓設定電路，設置相對於上述基準波形產生具有 特定相位差之波形之相位差調整機構、及對以相位差調整 機構產生之波形調整振幅之波形振幅調整機構；若可自如 地控制向各電磁石施加電壓之波形、週期、相位差、及振 幅，則可使水平方向之振動與垂直方向之振動容易接近所 期望之振動。 又，於上述各激振機構之向電磁石之施加電壓設定電 路，設置將以上述波形振幅調整機構調整振幅後之各波形 轉換成PWM(Pulse Width Modulation脈波寬度調變）信號之 PWM信號產生機構，可以PWM方式驅動各激振機構。 [發明之效果] 本發明之振動式零件搬送裝置係如上所述，在以第^激 振機構以其水平方向之固有振動數振動零件搬送構件時， 因將於零件搬送構件所產生之水平方向之振動之振幅縮小 成比垂直方向之振動之振幅還小6 dB以上，故可有效抑制 起因於水平方向之振動之垂直方向之振動。因此分== 整水平方向與垂直方向之振動時，可以幾乎不影響=直= 158478.doc 201228908 向振動之方式調整水平方向之振動，容易實現適於零件搬 送之所期望之振動。 【實施方式】 以下’基於圖1至圖13，說明本發明之實施形態。圖1至 圖7係顯示第1實施形態。該零件搬送裝置係如圖1及圖2所 不’係將形成有直線狀之搬送路la之輸送機槽（零件搬送 構件）丨安裝於上部振動體2之上面；在上部振動體2之周圍 配置矩形框形狀之中間振動體4;以朝向垂直方向之第1板 彈賓(水平振動用彈性構件）5連結中間振動體4與基台3 ;以 朝向水平方向之第2板彈簧（垂直振動用彈性構件）6連結上 部振動體2與中間振動體4 ;在中間振動體4與基台3之間， 叹置產生水平方向振動之第1激振機構7;在上部振動體2 與基台3之間，設置產生垂直方向振動之第2激振機構8之 振動式直進供料機》該基台3係受固定於地面之防振橡膠 等防振構件（省略圖示）之支撐。 上述第1激振機構7係由設置於基台3上之交流電磁石9 ' 及以與該電磁石9間隔特定距離而對向之方式安裝於中間 振動體4之可動鐵芯10所構成。另，可動鐵芯1〇雖然在該 例中係安裝於中間振動體4，但亦可安裝於上部振動體2。 另一方面，上述第2激振機構8係由設置於基台3上之交流 電磁石11、及以與該電磁石丨丨間隔特定距離而對向之方式 裝於上部振動體2之可動鐵芯12所構成。 若對第1激振機構7之電磁石9通電，則斷續之電磁吸引 力作用於電磁石9與可動鐵芯1〇之間，藉由該電磁吸引力 158478.doc 201228908 與第1板彈簧5之復原力，而於中間振動體4產生水平方向 之振動，該振動經由第2板彈簧6傳遞至上部振動體2及輸 送機槽1。又，若對第2激振機構8之電磁石11通電，則斷 續之電磁吸引力作用於電磁石11與可動鐵芯12之間，藉由 該電磁吸引力與第2板彈簧6之復原力，於上部振動體2及 輸送機槽1產生垂直方向之振動。且，藉由該水平方向之 振動與垂直方向之振動，將供給至輸送機槽1之零件沿著 直線狀搬送路la搬送。 因此，藉由分別設定各激振機構7、8之向電磁石9、11 之施加電壓，可分別調整輸送機槽1之水平方向之振動與 垂直方向之振動。 圖3係顯示設定各激振機構7、8之向電磁石9、11之施加 電壓之電路。於第1激振機構7之電路中設有產生施加電壓 之基準波形之基準波形產生機構13。基準波形產生機構 13，產生與波形種類（例如正弦波）及其波形週期（頻率）之 設定值相符之基準波形。另一方面，於第2激振機構8之電 路，設有產生相對以基準波形產生機構13所產生之基準波 形’具有特定相位差之波形之相位差調整機構14。 且’在各激振機構7、8之電路中，將以基準波形產生機 構13或相位差調整機構14所產生之波形，以波形振幅調整 機構15調整成特定之振幅，以PWM信號產生機構16轉換成 PWM信號後’以電壓增幅機構17升壓，向各電磁石9、u 施加。藉此’可自如地控制施加向各電磁石9、丨丨之施加 電壓之波形、週期、相位差、及振幅，且可分別調整水平 158478.doc •10· 201228908 方向之振動與垂直方向之振動。另，不以PWM方式驅動各 激振機構之情形，係不需要PWM信號產生機構16。 此處’上述輸送機槽1係如圖4所示，以第1激振機構7振 動輸送機槽1時之輸送機槽1之水平方向與垂直方向之振動 頻譜波形中，使以該振動數作為垂直方向之固有振動數^ 時所產生之垂直方向之振動之振幅Vv，比以該振動數作為 水平方向之固有振動數Fh時所產生之水平方向之振動之振 幅Vh還小3 dB以上，其結果，調整成以水平方向之固有振 動數Fh振動時，垂直方向之振動振幅Vv比水平方向之振動 振幅Vh還小6 dB以上。藉由如此地使輸送機槽i之水平方 向之固有振動數Fh中之水平方向之振動振幅vh與垂直方向 之振動振幅Vv產生較大差異，以輸送機槽1之水平方向之 固有振動數Fh附近之頻率驅動各激振機構7、8時，亦可縮 小起因於水平方向之振動之垂直方向之振動之振幅。 如上所述，該振動式零件搬送裝置因可有效抑制起因於 水平方向之振動之垂直方向之振動之發生，故分別調整水 平方向與垂直方向之振動時，可以幾乎不影響垂直方向之 振動之方式調整水平方向之振動’並可容易將適合零件搬 送之所期望之振動賦予輸送機槽1。 圖5及圖6係顯示第1板彈簧5之配置之變形例。該變形例 中，於基台3之兩端立設柱狀之板彈簧安裝部3a，在與零 件搬送方向（圖中之左右方向）正交之同一水平線上之2處之 固定位置，將第1板彈簧5固定於中間振動體4與基台3之板 彈簧安裝部3a。如此做的話，第1板彈簧5之水平方向之變 158478.doc 201228908 形與垂直方向之位移變得無關聯’可更有效果地抑制起因 於水平方向之振動之垂直方向之振動發生。 又’圖7係以上述圖5、圖6之例為基礎，顯示在與零件 搬送方向正交之同一水平線上之2處之固定位置，將第2板 彈簧6固定於上部振動體2與中間振動體4之例。 圖8至圖12係顯示第2實施形態《該零件搬送裝置係將内 面形成有螺旋狀搬送路（省略圖示）之盤（零件搬送構件）21 安裝於圓盤狀之上部振動體22之上面；於上部振動體22與 設置在地上之基台23之間，設置圓筒狀之中間振動體24 ; 以作為第1彈性構件（水平振動用彈性構件）之板彈簧2 $連结 中間振動體24與基台23 ;以作為第2彈性構件（垂直振動用 彈性構件）之板彈簧26連結上部振動體22與中間振動體 24 ;於中間振動體24與基台23之間設置產生水平迴轉方向 之振動之第1激振機構27 ;於上部振動體22與基台23之間 設置有產生垂直方向之振動之第2激振機構28之振動式盤 形供料機。 上述基台23係將塊狀之板彈簧安裝構件3〇固定在矩形之 底板29之上面，並將圓板狀之電磁石設置板31固定在板彈 簧安裝構件30之上面，故其底板29係藉由固定於地上之防 振橡膠等防振構件（省略圖示）支撐，板彈簧安裝構件3〇及 電磁石設置板31係插入於中間振動體24之下部。 上述中間振動體24，自其下端嵌入之第〗板彈簧安裝部 24a與自上鳊犬出之第2板彈簧安裝部24b係分別以等間 隔4個4個地設置於圓周方向。且，上述基台23之板彈菁安 158478.docThe same - two fixed positions on the horizontal line. Moreover, the invention can be applied to the vibrating disc feeder as described above, respectively. If the above-mentioned back-spindle is used, the disc is used, and Atm A. 1 I58478.doc 201228908 The leaf spring in the horizontal direction is used as the above-described elastic member for the vibration and the leaf spring having the front and back faces facing the vertical direction as the elastic member for vertical vibration. Further, the electromagnet and the movable iron core constitute the above-described respective excitation mechanisms, and a voltage waveform setting circuit for applying one of the reference voltages of the applied voltage and a waveform for adjusting the amplitude of the reference waveform are set. An amplitude adjustment mechanism; a voltage difference setting means for generating a waveform having a specific phase difference with respect to the reference waveform, and a waveform amplitude for adjusting a waveform amplitude generated by the phase difference adjustment mechanism in an applied voltage setting circuit for the other electromagnetic wave The adjustment mechanism; if the waveform, period, phase difference, and amplitude of the voltage applied to each of the electromagnets are freely controllable, the vibration in the horizontal direction and the vibration in the vertical direction can be easily brought close to the desired vibration. Further, a voltage signal generating circuit that converts each of the waveforms obtained by adjusting the amplitude by the waveform amplitude adjusting mechanism into a PWM (Pulse Width Modulation pulse width modulation) signal is provided in the voltage applying circuit to the electromagnet of each of the excitation mechanisms. The excitation mechanism can be driven by PWM. [Effects of the Invention] As described above, in the vibrating component transporting apparatus of the present invention, when the component transporting member is vibrated by the first vibrating mechanism in the horizontal direction, the horizontal direction of the component transporting member is generated. The amplitude of the vibration is reduced by 6 dB or less than the amplitude of the vibration in the vertical direction, so that the vibration in the vertical direction due to the vibration in the horizontal direction can be effectively suppressed. Therefore, when the vibration is equal to the horizontal direction and the vertical direction, it can be hardly affected. = Straight = 158478.doc 201228908 The horizontal vibration is adjusted in the form of vibration, and the desired vibration suitable for the parts can be easily realized. [Embodiment] Hereinafter, embodiments of the present invention will be described based on Figs. 1 to 13 . Fig. 1 to Fig. 7 show a first embodiment. As shown in FIG. 1 and FIG. 2, the component conveying apparatus is not attached to the upper surface of the upper vibrating body 2 by a conveyor groove (part conveying member) in which the linear conveying path 1a is formed, and around the upper vibrating body 2. The intermediate vibrating body 4 having a rectangular frame shape is disposed; the intermediate vibrating body 4 and the base 3 are coupled to the first plate bullet (elastic vibration member for horizontal vibration) 5 in the vertical direction; and the second leaf spring is oriented in the horizontal direction (vertical vibration) The upper vibrating body 2 and the intermediate vibrating body 4 are connected by an elastic member 6; the first vibrating mechanism 7 that generates horizontal vibration is interspersed between the intermediate vibrating body 4 and the base 3; and the upper vibrating body 2 and the abutment Between the three, a vibrating straight feeder that generates the second excitation mechanism 8 that vibrates in the vertical direction is provided. The base 3 is supported by an anti-vibration member (not shown) such as anti-vibration rubber fixed to the floor. The first excitation mechanism 7 is composed of an alternating electromagnet 9' provided on the base 3 and a movable core 10 attached to the intermediate vibrating body 4 so as to face the electromagnetic stone 9 at a predetermined distance. Further, although the movable iron core 1 is attached to the intermediate vibrating body 4 in this example, it may be attached to the upper vibrating body 2. On the other hand, the second excitation mechanism 8 is composed of an alternating electromagnet 11 provided on the base 3, and a movable core 12 attached to the upper vibrating body 2 at a predetermined distance from the electromagnet. Composition. When the electromagnet 9 of the first excitation mechanism 7 is energized, the intermittent electromagnetic attraction force acts between the electromagnet 9 and the movable core 1 , by the electromagnetic attraction 158478.doc 201228908 and the first leaf spring 5 The restoring force generates vibration in the horizontal direction in the intermediate vibrating body 4, and the vibration is transmitted to the upper vibrating body 2 and the conveyor groove 1 via the second leaf spring 6. When the electromagnet 11 of the second excitation mechanism 8 is energized, the intermittent electromagnetic attraction force acts between the electromagnet 11 and the movable core 12, and the electromagnetic attraction force and the restoring force of the second leaf spring 6 are The upper vibrating body 2 and the conveyor groove 1 generate vibration in the vertical direction. Further, the components supplied to the conveyor tank 1 are conveyed along the linear conveyance path 1a by the vibration in the horizontal direction and the vibration in the vertical direction. Therefore, by individually setting the voltages applied to the electromagnets 9, 11 of the respective excitation mechanisms 7, 8, the vibration in the horizontal direction and the vibration in the vertical direction of the conveyor groove 1 can be adjusted. Fig. 3 is a view showing a circuit for setting the applied voltages of the respective excitation mechanisms 7, 8 to the electromagnets 9, 11. A reference waveform generating means 13 for generating a reference waveform of an applied voltage is provided in the circuit of the first excitation mechanism 7. The reference waveform generating unit 13 generates a reference waveform that matches the waveform type (e.g., sine wave) and its waveform period (frequency). On the other hand, the circuit of the second excitation mechanism 8 is provided with a phase difference adjustment mechanism 14 that generates a waveform having a specific phase difference with respect to the reference waveform generated by the reference waveform generation means 13. Further, in the circuits of the excitation mechanisms 7 and 8, the waveform generated by the reference waveform generation unit 13 or the phase difference adjustment unit 14 is adjusted to a specific amplitude by the waveform amplitude adjustment unit 15 to the PWM signal generation unit 16 . After being converted into a PWM signal, it is boosted by the voltage amplification mechanism 17 and applied to each of the electromagnets 9, u. Thereby, the waveform, period, phase difference, and amplitude of the applied voltage applied to each of the electromagnets 9 and 丨丨 can be freely controlled, and the vibrations in the direction of the horizontal 158478.doc • 10· 201228908 and the vibration in the vertical direction can be respectively adjusted. Further, the PWM signal generating mechanism 16 is not required in the case where the respective excitation mechanisms are not driven by the PWM method. Here, the conveyor groove 1 is as shown in FIG. 4, and the vibration frequency waveform of the horizontal direction and the vertical direction of the conveyor groove 1 when the first excitation mechanism 7 vibrates the conveyor groove 1 is used. The amplitude Vv of the vibration in the vertical direction generated as the natural vibration number in the vertical direction is smaller than the amplitude Vh of the vibration in the horizontal direction generated when the number of vibrations is the natural frequency Fh in the horizontal direction, and is 3 dB or less. As a result, when the vibration is adjusted to the natural frequency Fh in the horizontal direction, the vibration amplitude Vv in the vertical direction is smaller than the vibration amplitude Vh in the horizontal direction by 6 dB or more. By making the vibration amplitude vh in the horizontal direction and the vibration amplitude Vv in the vertical direction of the natural vibration number Fh in the horizontal direction of the conveyor groove i largely different, the natural vibration number Fh in the horizontal direction of the conveyor groove 1 is obtained. When the excitation mechanisms 7 and 8 are driven at a nearby frequency, the amplitude of the vibration in the vertical direction due to the vibration in the horizontal direction can be reduced. As described above, the vibrating component conveying device can effectively suppress the occurrence of vibration in the vertical direction due to the vibration in the horizontal direction. Therefore, when the vibration in the horizontal direction and the vertical direction are respectively adjusted, the vibration in the vertical direction can be hardly affected. The vibration in the horizontal direction is adjusted', and the desired vibration suitable for the conveyance of the parts can be easily imparted to the conveyor tank 1. 5 and 6 show a modification of the arrangement of the first leaf spring 5. In the modified example, the columnar leaf spring mounting portion 3a is erected on both ends of the base 3, and is fixed at two fixed positions on the same horizontal line orthogonal to the component conveying direction (the horizontal direction in the drawing). The leaf spring 5 is fixed to the intermediate vibration body 4 and the leaf spring mounting portion 3a of the base 3. In this case, the horizontal direction of the first leaf spring 5 is changed. 158478.doc 201228908 The displacement of the shape and the vertical direction becomes unrelated, and the vibration in the vertical direction due to the vibration in the horizontal direction can be more effectively suppressed. Further, Fig. 7 shows a fixed position at two positions on the same horizontal line orthogonal to the component conveying direction based on the above-described examples of Figs. 5 and 6, and the second leaf spring 6 is fixed to the upper vibrating body 2 and the middle. An example of the vibrating body 4. In the second embodiment, the component transfer device is mounted on a disk-shaped upper vibrating body 22 with a disk (part transfer member) 21 having a spiral conveyance path (not shown) formed on its inner surface. A cylindrical intermediate vibrating body 24 is provided between the upper vibrating body 22 and the base 23 provided on the ground; and the intermediate vibrating body is connected to the leaf spring 2 $ as the first elastic member (elastic member for horizontal vibration) 24 and the base 23; the upper vibrating body 22 and the intermediate vibrating body 24 are coupled by a leaf spring 26 as a second elastic member (elastic member for vertical vibration); and a horizontal rotation direction is provided between the intermediate vibrating body 24 and the base 23 The first vibration excitation mechanism 27 of the vibration is provided with a vibrating disk feeder that generates the second excitation mechanism 28 that vibrates in the vertical direction between the upper vibrating body 22 and the base 23. The base 23 is fixed to the upper surface of the rectangular bottom plate 29 by the block-shaped leaf spring mounting member 3, and the disk-shaped electromagnet setting plate 31 is fixed to the upper surface of the leaf spring mounting member 30, so that the bottom plate 29 is borrowed. The anti-vibration member (not shown) such as the anti-vibration rubber fixed to the ground is supported, and the leaf spring mounting member 3 and the electromagnet setting plate 31 are inserted into the lower portion of the intermediate vibrating body 24. The intermediate vibrating body 24 is provided in the circumferential direction at four equal intervals of four, respectively, from the first plate spring attachment portion 24a fitted from the lower end thereof and the second leaf spring attachment portion 24b from the upper jaw. And, the above-mentioned abutment 23 of the board of the bullets 158478.doc
-12. 201228908 裝構件30，於對應中間振動體24之第1板彈簧安裝部2乜之 位置上，設置有板彈簧安裝部30a;且上部振動體U ^於 插入中間振動體24之第2板彈簧安裝部24b之缺口之一侧 面，設置有板彈簧安裝部22a。 上述第1板彈簧25係將表背面朝向水平迴轉方向，且為 使兩端固定位置位於與盤21之垂直方向中心線〇正交之同 一水平線上，而分別將一端部固定於中間振動體24之第j 板彈簧安裝部24a;另一端部固定於基台23之板彈菁安裝 構件30之板彈簧安裝部30a ’成為在水平迴轉方向可振動 地支持中間振動體24之迴轉振動用板彈簣（迴轉振動用彈 性構件）^ 另一方面，上述第2板彈簧26係將表背面朝向垂直方 向’且為使兩端之固定位置位於沿上部振動體2 2之外周部 延伸之同一水平線上，而分別將一端部固定於上部振動體 22之板彈簧安裝部22a ;另一端部固定在中間振動體24之 第2板彈簧安裝部24b ’成為在垂直方向可振動地支持上部 振動體22之垂直振動用板彈簧。 又，上述第1激振機構27係包含以設置於基台23之電磁 石設置板3 1上之交流電磁石32 ;及可動鐵芯33，其係以與 該電磁石32間隔特定距離對向之方式安裝於中間振動體24 之内周面。另，可動鐵芯33在該例中雖安裝於中間振動體 24’但亦可安裝於上部振動體22。另一方面，上述第2激 振機構28係包含設置於基台23之電磁石設置板31上之交流 電磁石34;及可動鐵芯35，其係以與該電磁石34間隔特定 158478.doc 13 201228908 距離對向之方式安裝於上部振動體22之下面。 若對第1激振機構27之電磁石32通電，則斷續之電磁吸 引力作用於電磁石32與可動鐵芯33之間，藉由該電磁吸引 力與迴轉振動用板彈簧25之復原力，於中間振動體24產生 水平迴轉方向之振動，該振動經由垂直振動用板彈簧26傳 遞至上部振動體22及盤21。又，若對第2激振機構28之電 磁石34通電，則斷續之電磁吸引力作用於電磁石34與可動 鐵芯35之間，藉由該電磁吸引力與垂直振動用板彈簧26之 復原力’於上部振動體22及盤21產生垂直方向之振動。 且’藉由該水平迴轉方向之振動與垂直方向之振動，沿著 上述螺旋狀搬送路搬送供給至盤21之零件。 因此，藉由分別設定各激振機構27、28之向電磁石32、 34之施加電壓，可分別調整盤21之水平迴轉方向之振動與 垂直方向之振動。另，使用與圖3所示者相同者，來作為 設定向各電磁石32、34施加電壓之電路。 逖係與第1實施形 -I- lit吟 同（參照圖4)，在以第丨激振機構27振動盤2ι時之盤η之水 平迴轉方向與垂直方向之振動頻譜波形中，使該振動數作 為垂直方向之固有振動數匕時所產生之垂直方向之振動振 幅Vv’，比將該振動數作為水平迴轉方向之固有振動數^時 所產生之水平迴轉方向之振動之振幅^還小3犯以上 結果，調整成以水平迴轉方向之时振動數Fh振動時，垂 直方向之振動㈣Vv比水平迴轉方向之振動振幅^還小6 dB以上。藉由如此地使盤21 化干沿轉方向之固有振動數 158478.doc 201228908-12. The 201228908 mounting member 30 is provided with a leaf spring mounting portion 30a at a position corresponding to the first leaf spring mounting portion 2 of the intermediate vibrating body 24; and the upper vibrating body U^ is inserted into the second vibrating body 24 One side surface of the notch of the leaf spring mounting portion 24b is provided with a leaf spring mounting portion 22a. The first leaf spring 25 is configured such that the front and back surfaces are oriented in the horizontal rotation direction, and the both end fixing positions are located on the same horizontal line orthogonal to the center line 〇 in the vertical direction of the disk 21, and one end portion is fixed to the intermediate vibrating body 24, respectively. The j-plate spring mounting portion 24a; the leaf spring mounting portion 30a' of the plate-elastic mounting member 30 whose other end portion is fixed to the base 23 is a plate spring for vibratingly supporting the intermediate vibrating body 24 in the horizontal rotation direction篑 (elastic member for the rotary vibration). On the other hand, the second leaf spring 26 has the front and back faces facing the vertical direction and the fixed positions of the both ends are located on the same horizontal line extending along the outer peripheral portion of the upper vibrating body 2 2 . The one end portion is fixed to the leaf spring mounting portion 22a of the upper vibrating body 22, and the other end portion is fixed to the second leaf spring mounting portion 24b' of the intermediate vibrating body 24 to vibrately support the upper vibrating body 22 in the vertical direction. Leaf spring for vertical vibration. Further, the first excitation mechanism 27 includes an AC electromagnet 32 provided on the electromagnet setting plate 31 of the base 23, and a movable iron core 33 which is mounted at a predetermined distance from the electromagnet 32. The inner peripheral surface of the intermediate vibrating body 24 is formed. Further, the movable iron core 33 is attached to the intermediate vibrating body 24' in this example, but may be attached to the upper vibrating body 22. On the other hand, the second excitation mechanism 28 includes an AC electromagnet 34 provided on the electromagnet setting plate 31 of the base 23, and a movable iron core 35 spaced apart from the electromagnet 34 by a specific distance of 158478.doc 13 201228908 The opposite direction is attached to the lower surface of the upper vibrating body 22. When the electromagnet 32 of the first excitation mechanism 27 is energized, the intermittent electromagnetic attraction force acts between the electromagnet 32 and the movable iron core 33, and the restoring force of the electromagnetic attraction force and the rotary vibration leaf spring 25 is The intermediate vibrating body 24 generates vibration in the horizontal rotation direction, and the vibration is transmitted to the upper vibrating body 22 and the disk 21 via the vertical vibration plate spring 26. When the electromagnet 34 of the second excitation mechanism 28 is energized, the intermittent electromagnetic attraction force acts between the electromagnet 34 and the movable iron core 35, and the restoring force of the electromagnetic attraction force and the vertical vibration leaf spring 26 is utilized. 'The upper vibrating body 22 and the disk 21 generate vibration in the vertical direction. Further, by the vibration in the horizontal rotation direction and the vibration in the vertical direction, the components supplied to the disk 21 are conveyed along the spiral conveyance path. Therefore, by individually applying the voltages applied to the electromagnets 32, 34 of the respective excitation mechanisms 27, 28, the vibration in the horizontal rotation direction of the disk 21 and the vibration in the vertical direction can be individually adjusted. Further, the same as that shown in Fig. 3 is used as a circuit for setting a voltage applied to each of the electromagnets 32, 34. The 逖 is the same as the first embodiment-I- lit ( (see FIG. 4), and the vibration is generated in the vibration spectrum waveform of the horizontal rotation direction and the vertical direction of the disk η when the second excitation mechanism 27 vibrates the disk 2 The vibration amplitude Vv' in the vertical direction generated when the natural vibration number 匕 is the vertical direction is smaller than the amplitude of the vibration in the horizontal rotation direction when the number of vibrations is the natural vibration number in the horizontal rotation direction. When the above result is adjusted and the vibration is adjusted to the vibration number Fh in the horizontal rotation direction, the vibration in the vertical direction (4) Vv is smaller than the vibration amplitude in the horizontal rotation direction by 6 dB or less. By so that the disk 21 is dried in the direction of the natural vibration in the direction of rotation 158478.doc 201228908
Fh中之水平迴轉方向之振純幅％與垂直方向之振動振幅 Vv產生較大差異，以盤21之水平迴轉方向之固有振動數^ 附近之頻率驅動各激振機構27、28時亦可縮小起因於水 平迴轉方向之振動之垂直方向之振動之振幅。 或者，亦可採用如下所述之調整方法，來作為上述之盤 21之振動特性調整方法之應用例。 即’在以水平迴轉方向激振盤21時之盤21之水平迴轉方 向與垂直方向之振動頻譜波形中，如圖13⑷所示，盤以 水平迴轉方向之固有振動數Fh與垂直方向之固有振動數Fv 只差2至3 &之情形下，在頻率匕之水平迴轉方向之振動 振幅Vh與垂直方向之振動振幅、之差異並不大，即使以盤 21之水平迴轉方向之时振動數即頻率㈣近之頻率來驅 動第1激振機構27’僅欲產生水平迴轉方向之振動，恐怕 有使盤21產生具有較大純之垂直方向之振動。 因此’如圖13(b)所示’只要將盤21之垂直方向之固有 振動數Fv調整成比水平迴轉方向之固有振動抓還大5 Hz 以上’則其水平迴轉方向之固有振動數Fh中之水平迴轉方 向之振動振中田vh與垂直方向之振動振幅I變得產生較大差 異’與進行上述調整方法之情形相同，即使以盤η之水平 轉方向之g]有振動數!^附近之頻率驅動各激振機構η、 2 8時’亦可縮小起因於永 、&平、轉方向之振動之垂直方向之 振動之振幅。 此時’盤21之垂直方向之固有振動數Fv，雖亦可調整成 比水平迴轉方向之固有振動机還W上，但最好如 158478.doc 15 201228908 上述應用例地，比水平_ μ + ^ m ^ 十迴轉方向之固有振動數Fh大。若增The vibration pure amplitude % in the horizontal rotation direction and the vibration amplitude Vv in the vertical direction in Fh are largely different, and the vibration vibration mechanism 27, 28 can be reduced when the frequency of the natural vibration in the horizontal rotation direction of the disk 21 is driven. The amplitude of the vibration caused by the vertical direction of the vibration in the horizontal rotation direction. Alternatively, an adjustment method as described below may be employed as an application example of the above-described vibration characteristic adjustment method of the disk 21. That is, in the vibration spectrum waveform of the horizontal rotation direction and the vertical direction of the disk 21 when the disk 21 is excited in the horizontal rotation direction, as shown in Fig. 13 (4), the natural vibration number Fh of the disk in the horizontal rotation direction and the natural vibration in the vertical direction In the case where the number Fv is only 2 to 3 &, the difference between the vibration amplitude Vh in the horizontal rotation direction of the frequency 与 and the vibration amplitude in the vertical direction is not large, even when the vibration amount in the horizontal rotation direction of the disk 21 is The frequency (4) is close to the frequency to drive the first excitation mechanism 27' to generate only the vibration in the horizontal rotation direction, and there is a fear that the disk 21 will generate a vibration having a relatively large vertical direction. Therefore, 'as shown in Fig. 13(b)', the natural vibration number Fv in the vertical direction of the disk 21 is adjusted to be larger than the natural vibration in the horizontal rotation direction by 5 Hz or more, and the natural vibration number Fh in the horizontal rotation direction is In the vibration direction of the horizontal vibration direction, the vibration amplitude I in the vertical direction and the vibration amplitude I in the vertical direction become largely different from the same as in the case of performing the above-described adjustment method, even if there is a vibration number in the horizontal direction of the disk η. When the frequency is driven by each of the excitation mechanisms η and 28, the amplitude of the vibration in the vertical direction due to the vibration in the direction of the front and the back can be reduced. At this time, the natural vibration number Fv of the disk 21 in the vertical direction can be adjusted to be higher than that of the natural vibration machine in the horizontal rotation direction, but it is preferably as 158478.doc 15 201228908. The above application example, the ratio _ μ + ^ m ^ The natural vibration number Fh of the ten-turn direction is large. If increase
大垂直方向之固有振動數F 貝J因了^向盤21之垂直方向 之剛性’故容易縮小起因於 口於水千迴轉方向之振動之垂直方 向之振動之振幅β又，A -iffi φ4· 在調整垂直方向之固有振動數匕 時’雖調整成比水平迴棘太A々m + 1 丁、轉方向之固有振動數Fh還小之一方 存在界限，但因增大一古尤六+田Μ 方不存在界限，故亦容易進行調 整0 再者’盤21之水平迴轉方向之固有振動數匕與垂直方向 之固有振動數Fv，最好調整成使兩者各自之5以下之整數 倍之值變成互質關係。因固有振動數之整數倍成為具有與 該固有振動數不同之振_式之固有振動數，因此若盤Μ 之水平迴轉方向與垂直方向之固有振動數、、^之整數倍 係成為相同值或接近值’則起因於水平迴轉方向之振動之 垂直方向之振動之振幅會變大。此時，使該整數倍之值為 5以下，係因為若不限制該值’則各固有振動數匕、匕之 設定變得困難，及若變得比固有振動數匕、匕之5倍大， 則在該振動模式中振動振幅就變小，對盤2丨之影響亦變小 之緣故。 另’雖然盤21之起因於水平迴轉方向之振動之垂直方向 之振動振幅係越小越好，但若為此將盤2丨之垂直方向之固 有振動數Fv增大過多’則可能使垂直方向之剛性變高，有 不能藉由第2激振機構28產生垂直方向之振動之可能性。 因所期望之垂直方向之振動振幅為數十μιη，故垂直方向 之固有振動數Fv’係以起因於水平迴轉方向之振動之垂直 158478.docThe natural vibration number F in the large vertical direction is due to the rigidity of the vertical direction of the disk 21, so it is easy to reduce the amplitude β of the vibration caused by the vibration of the mouth in the direction of the water revolution, and A -iffi φ4· When adjusting the natural vibration number 垂直 in the vertical direction, it is adjusted to be smaller than the horizontal back-spindle A々m + 1 D, and the natural vibration number Fh in the direction of rotation is small, but due to the increase of one Gu Youliu + Tian Μ There is no limit, so it is easy to adjust 0. The natural vibration number 匕 of the horizontal rotation direction of the disk 21 and the natural vibration number Fv of the vertical direction are preferably adjusted so that the respective integers of 5 and below are integer multiples. The value becomes a mutual relationship. Since the integral multiple of the natural vibration number has a natural vibration number different from the natural vibration number, the number of natural vibrations in the horizontal rotation direction of the disk and the vertical direction is the same value or The near value 'is caused by the amplitude of the vibration in the vertical direction of the vibration in the horizontal rotation direction. In this case, if the value is not more than 5, the setting of the natural vibration numbers 匕 and 匕 is difficult, and the number of natural vibrations is 5 times larger than the natural vibration number 匕 and 匕. Then, in this vibration mode, the vibration amplitude becomes small, and the influence on the disk 2 is also reduced. In addition, although the vibration amplitude in the vertical direction of the vibration of the disk 21 due to the horizontal rotation direction is as small as possible, if the natural vibration number Fv in the vertical direction of the disk 2 is excessively increased, the vertical direction may be made. The rigidity becomes high, and there is a possibility that vibration in the vertical direction cannot be generated by the second excitation mechanism 28. Since the vibration amplitude in the vertical direction is tens of μm, the natural vibration number Fv' in the vertical direction is perpendicular to the vibration caused by the horizontal rotation direction. 158478.doc
201228908 方向之振動之振幅成為數μιη至十數μηι左右之方式來調整 即可》 又，在該第2實施形態中，因將迴轉振動用板彈簧25固 定於與盤21之垂直方向中心線0正交之同一水平線上之2處 之固定位置，故迴轉振動用板彈簣25之水平迴轉方向之變 形與垂直方向之位移變得無關聯，具有更能抑制起因於水 平迴轉方向之振動之垂直方向之振動之效果。 如上所述’該第2實施形態之振動式盤形供料機，亦與 第1實施形態之振動式直進供料機相同，因可有效抑制水 平迴轉方向之振動引起垂直方向之振動，故分別調整水平 迴轉方向與垂直方向之振動時，可在幾乎不影響垂直方向 之振動之情形下調整水平迴轉方向之振動，並可容易地賦 予盤21適合零件搬送之所期望之振動。 上述各實施形態中，雖然將連結中間振動體與基台之第 1板彈簧作為水平振動用彈性構件，將連結上部振動體與 中間振動體之第2板彈簧作為垂直振動用彈性構件，但與 之相反，即亦可將第i板彈簧作為垂直振動用彈性構件， 第2板彈簧作為水平振動用彈性構件來構成。，雖然將 板彈簧於各處各配置1片，但亦可將2片以上重疊使用。 又，雖然將板彈簧分為水平振動用與垂直振動用各配置4 處，但亦可以2處以上來構成。 再者，各實施形態令，雖然在水平振動㈣性構件及垂 直振動用彈性構件上使用板彈簧，但#_可❹板彈箸 以外之彈性構件…各激振機構雖然使用包含電磁石與 158478.doc •17- 201228908 可動鐵芯，但並不限定於此，亦可使用產生相同激振力之 促動器。 【圖式簡單說明】 圖1係第1實施形態之零件搬送裝置（直進供料機）之正面 剖面圖。 圖2係除圖1之輸送機槽之頂視圖。 圖3係圖1之零件搬送裝置之各激振機構之施加電壓設定 電路之概略圖。 圖4係顯示圖1之零件搬送裝置之振動頻譜波形之圖表。 圖5係顯示圖1之板彈簧之配置之變形例之正面剖面圖。 圖6係顯示去除了圖5之輸送機槽之頂視圖。 圖7係去除了圖1之板彈簧之配置之其他變形例之輸送機 槽之頂視圖。 圖8係第2實施形態之零件搬送裝置（盤形供料機）之正面 圖。 圖9係去除了圖8之盤形之頂視圖。 圖10係圖8之縱剖面圖。 圖11係沿圖1 〇之χΐ·χΐ線之剖面圖。 圖12係沿圖1〇之χπ·χπ線之剖面圖β 圖13(a)、（b)係說明圖10之零件搬送裝置之盤 特性之調整方法之應用例之圖表。· 振動 圖14係顯示先前之零件搬送裝置之振動頻譜波形之圖 表。 圖1 5係顯示先前之零件搬送裝置（盤形供料機）之一部分 158478.doc 201228908 缺口立體圖。 【主要元件符號說明】 1 輸送機槽（零件搬送構件） la 直線狀搬送路 2 上部振動體 3 基台 3a 板彈簧安裝部 4 中間振動體 5 第1板彈簧（水平振動用彈性構件） 6 第2板彈簧（垂直振動用彈性構件） 7 第1激振機構 8 第2激振機構 9 電磁石 10 可動鐵芯 11 電磁石 12 可動鐵芯 13 基準波形產生機構 14 相位差調整機構 15 波形振幅調整機構 16 PWM信號產生機構 17 電壓增幅機構 21 盤形（零件搬送構件） 22 上部振動體 23 基台 24 中間振動體 158478.doc 19. 201228908 24a 第1板彈簧安裝部 24b 第2板彈簧安裝部 25 第1板彈簧（盤形振動用彈性構件） 26 第2板彈簧（垂直振動用彈性構件） 27 第1激振機構 28 第2激振機構 29 底板 30 板彈簣安裝構件 30a 板彈簧安裝部 31 電磁石設置板 32 電磁石 33 可動鐵芯 34 電磁石 35 可動鐵芯 51 盤 52 上部振動體 53 基台 54 中間振動體 55 第1板彈簧 56 第2板彈簧 Fh 水平方向固有振動數 Fv 垂直方向固有振動數 Vh 水平方向振動振幅 Vv 垂直方向振動振幅 Vv， 垂直方向振動振幅 158478.doc -20-In the second embodiment, the vibration spring leaf spring 25 is fixed to the center line 0 perpendicular to the disk 21 in the second embodiment. The fixed position of the two orthogonal lines on the same horizontal line, so the deformation of the horizontal rotation direction of the slewing vibration plate magazine 25 is not related to the displacement in the vertical direction, and the vertical direction of the vibration caused by the horizontal rotation direction is more suppressed. The effect of the vibration of the direction. As described above, the vibrating disc feeder of the second embodiment is similar to the vibrating straight feeder of the first embodiment, and since vibration in the horizontal direction is effectively suppressed, vibration in the vertical direction is caused. When the vibration in the horizontal rotation direction and the vertical direction is adjusted, the vibration in the horizontal rotation direction can be adjusted without affecting the vibration in the vertical direction, and the desired vibration of the disk 21 suitable for the parts can be easily imparted. In the above-described embodiments, the first plate spring that connects the intermediate vibrating body and the base is used as the horizontal vibration elastic member, and the second plate spring that connects the upper vibrating body and the intermediate vibrating body is used as the vertical vibration elastic member. On the other hand, the i-th plate spring may be used as the elastic member for vertical vibration, and the second plate spring may be configured as an elastic member for horizontal vibration. Although the leaf springs are arranged one by one in each place, two or more sheets may be used in combination. Further, although the leaf spring is divided into four places for horizontal vibration and vertical vibration, it may be configured in two or more places. Further, in each of the embodiments, the leaf spring is used for the horizontal vibration (four) member and the vertical vibration elastic member, but the elastic member other than the #_ ❹ 箸 箸 ... 各 各 各 各 各 各 各 158 158 158 158 158 158 158 158 158 158 158 158 158 158 158 158 158 158 Doc •17- 201228908 Movable iron core, but it is not limited to this, and an actuator that generates the same exciting force can also be used. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a front sectional view showing a component conveying device (straight feed feeder) according to a first embodiment. Figure 2 is a top plan view of the conveyor slot of Figure 1. Fig. 3 is a schematic view showing an applied voltage setting circuit of each of the excitation mechanisms of the component transporting apparatus of Fig. 1. Fig. 4 is a graph showing the vibration spectrum waveform of the component transporting apparatus of Fig. 1. Fig. 5 is a front sectional view showing a modification of the arrangement of the leaf spring of Fig. 1. Figure 6 is a top plan view showing the conveyor slot of Figure 5 removed. Fig. 7 is a top plan view showing a conveyor groove in which other modifications of the arrangement of the leaf springs of Fig. 1 are removed. Fig. 8 is a front elevational view showing the component conveying device (disc feeder) of the second embodiment. Figure 9 is a top plan view showing the disk shape of Figure 8 removed. Figure 10 is a longitudinal sectional view of Figure 8. Figure 11 is a cross-sectional view taken along line 图·χΐ of Figure 1. Fig. 12 is a cross-sectional view taken along the line π·χ π of Fig. 1 . Fig. 13 (a) and (b) are diagrams showing an application example of a method of adjusting the disk characteristics of the component transporting device of Fig. 10. • Vibration Fig. 14 is a diagram showing the vibration spectrum waveform of the previous part carrier. Figure 1 5 shows a part of the previous part conveyor (disc feeder) 158478.doc 201228908 Notched perspective view. [Description of main component symbols] 1 Conveyor groove (part transfer member) la Linear transfer path 2 Upper vibrating body 3 Base 3a Leaf spring mounting part 4 Intermediate vibrating body 5 First leaf spring (elastic member for horizontal vibration) 6 2 leaf spring (elastic member for vertical vibration) 7 First excitation mechanism 8 Second excitation mechanism 9 Electromagnet 10 Movable iron core 11 Electromagnet 12 Movable iron core 13 Reference waveform generation mechanism 14 Phase difference adjustment mechanism 15 Waveform amplitude adjustment mechanism 16 PWM signal generating mechanism 17 Voltage amplifying mechanism 21 Disk shape (part conveying member) 22 Upper vibrating body 23 Base 24 Intermediate vibrating body 158478.doc 19. 201228908 24a 1st leaf spring mounting portion 24b Second plate spring mounting portion 25 1 Leaf spring (elastic member for disk vibration) 26 Second plate spring (elastic member for vertical vibration) 27 First excitation mechanism 28 Second excitation mechanism 29 Base plate 30 Plate magazine mounting member 30a Plate spring mounting portion 31 Electromagnet setting Plate 32 Electromagnet 33 Movable iron core 34 Electromagnetic stone 35 Movable iron core 51 Disk 52 Upper vibrating body 53 Base 54 Inter-vibration body 55 1st leaf spring 56 2nd leaf spring Fh Horizontal natural frequency Fv Vertical natural vibration number Vh Horizontal vibration amplitude Vv Vertical vibration amplitude Vv, Vertical vibration amplitude 158478.doc -20-