TWI353300B - Pressing machine - Google Patents

Pressing machine Download PDF

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Publication number
TWI353300B
TWI353300B TW097108455A TW97108455A TWI353300B TW I353300 B TWI353300 B TW I353300B TW 097108455 A TW097108455 A TW 097108455A TW 97108455 A TW97108455 A TW 97108455A TW I353300 B TWI353300 B TW I353300B
Authority
TW
Taiwan
Prior art keywords
gear
main
group
meshing
gear group
Prior art date
Application number
TW097108455A
Other languages
Chinese (zh)
Other versions
TW200920591A (en
Inventor
Tetsuyuki Terauchi
Shusaku Yamasaki
Original Assignee
Ihi Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ihi Corp filed Critical Ihi Corp
Publication of TW200920591A publication Critical patent/TW200920591A/en
Application granted granted Critical
Publication of TWI353300B publication Critical patent/TWI353300B/en

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Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B1/00Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B1/00Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • B30B1/266Drive systems for the cam, eccentric or crank axis
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B1/00Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • B30B1/268Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks using a toggle connection between driveshaft and press ram
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B1/00Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • B30B1/28Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks the cam, crank, or eccentric being disposed below the lower platen or table and operating to pull down the upper platen or slide
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B30PRESSES
    • B30BPRESSES IN GENERAL
    • B30B15/00Details of, or accessories for, presses; Auxiliary measures in connection with pressing

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Transmission Devices (AREA)
  • Gear Transmission (AREA)

Description

Γ353300 九、發明說明: 【發明所屬之技術領域】 ·„ 本發明係關於衝壓機械。 ,【先前技術】 - ㈣機械係使滑塊做昇降運動’並使被加工物夾在固 定於該滑塊的下面之上模具與配置於滑塊下方之下模具之 間而進行衝壓。Γ353300 IX. Description of the invention: [Technical field to which the invention pertains] · „ The present invention relates to a stamping machine. [Prior Art] - (4) The mechanical system causes the slider to move up and down and the workpiece is clamped to the slider. The upper mold is punched between the lower mold and the lower mold disposed below the slider.

此種衝壓機械之一例記载於下述專利文獻〗中。第i 圖顯示專利文獻i之衝壓機械。如第丨圖所示1服馬達 51的驅動力經由小齒輪53、主齒輪55、曲軸57、連接桿 (connecting r〇d)59而傳遞至滑塊61。連接桿%的大徑部 連接至曲車由57的偏心部,連接桿59的下端部連接至滑塊 6卜藉此構成,將舰馬達51之旋轉運動變換為滑塊61 之昇降運動。 (專利文獻υ日本特開2004_17089號公報「衝壓機械之 鲁滑塊驅動裝置」 然而,對於上述的衝壓機械仍有以下之期望: 第一、期望使衝麼機械整體更加小型化’,而且使飼服 馬達及齒輪等動力傳遞構件之配置的自由度提高。 •帛二、、在飼服馬達故障的情況,由於要進行飼服馬達 .之修理Ht伺服馬達之更換,因此必射斷㈣運轉。 —關於此點’期望即划服馬達故障,㈣運轉也能繼續進 行0 第二、專利文獻1巾記载使由兩㈣服馬達分別驅動 320031 ^53300 之兩個主齒輪相嚙合之技術,然而 之齒面間存在有間隙,因此衝壓中:輪相唾合部 有變動該間隙的量之傾向。運轉中,主齒輪的位置會 頻繁例如’如第2圖所示’滑塊61會在衝壓運轉中 Γ之=。此係因為滑塊61的姿勢會隨著該等主齒輪 。相對的%轉位置的變動而變化之故。 過去’如第2圖的箭號&胼-‘ balance) _ ^ ^ °所不,有平衡器—咖 器並不呈供 上頂推滑塊以進行重力消除,惟平衡 止滑塊:滑塊61的傾斜之機能。因此,期望能夠防 止π塊61之傾斜。 々 【發明内容】 本發明係為了解決上述課題而提出者。 言驅動:去本發明之第一目的在提供一種可小型化且可提 间動馬達等的配置自由度之衝Μ機械。 •也能在提供一種在驅動馬達故障的情況 屋機械立可自由變更衝壓機械的成型力之衝 的運三目的在提供一種可防止滑塊在衝壓機械 中頻繁地傾斜之衝壓機械。 ‘機片,本發明’為了達成上述第一目的,提供一種衝厘 係具備有用來進行·之驅動馬達、接受該驅動 動變換動力而旋轉之主齒輪、將該主齒輪的旋轉運 ^為在復運動之變換機構、以及連結至該變換機構而 ^動之滑塊,且藉由固定至該滑塊之模具來進行衝壓 320031 6 Γ353300 者,其特徵在於:具備:*支持前述主錢之轴支持住, 且内藏有前述變換機構之機架(frame);以及設在前述 、的外侧’將前述驅動馬達的驅動力傳遞到前述主齒輪:傳 •.動齒輪’且前述主齒輪的至少—部份係位在前述機架的外 、侧以便命述主齒輪與前述傳動齒輪嚙合。 .、上述構成中,主齒輪的至少一部份位在機架的外側, 以便主齒輪與傳動齒輪嗜合。亦即,由於主齒輪並非 鲁收納在機架的内部,因此可使機架小型化。 而且,由於將驅動馬達配置在機架的外侧而非 内部,因此驅動馬達、傳動齒輪等部件的配置自由度提言。 一、根據本發明之較佳實施形態,則在上述衝壓“二。 剷述主齒輪係配置在前述機架的外側。An example of such a press machine is described in the following patent documents. Figure i shows the stamping machine of Patent Document i. The driving force of the motor 51 is transmitted to the slider 61 via the pinion 53, the main gear 55, the crankshaft 57, and the connecting rod 59 as shown in the figure. The large diameter portion of the connecting rod % is connected to the eccentric portion of the curved car 57, and the lower end portion of the connecting rod 59 is connected to the slider 6 to thereby convert the rotational motion of the ship motor 51 into the lifting motion of the slider 61. In the above-mentioned press machine, there are still the following expectations: First, it is desirable to make the whole machine more compact, and to feed The degree of freedom in the arrangement of the power transmission members such as the motor and the gear is increased. • In the case of a failure of the feeding motor, the replacement of the Ht servo motor by the feeding motor is required to be interrupted (four). - In this regard, 'the expectation is to slap the motor failure, and (4) the operation can continue. 0. Patent Document 1 describes the technique of meshing the two main gears of the two (four) service motors to drive 320031 ^ 53300 respectively. There is a gap between the tooth faces, so during the press: the wheel phase salvage portion tends to vary the amount of the gap. During operation, the position of the main gear will be frequent, for example, as shown in Fig. 2, the slider 61 will be stamped. In operation, the position of the slider 61 changes with the change of the relative %-turn position of the main gear. In the past, the arrow & 胼-'balance of Figure 2 _ ^ ^ ° No, there is a balancer - the coffee machine is not provided with a top push slider for gravity elimination, but the balance slider: the tilting function of the slider 61. Therefore, it is desirable to be able to prevent the tilt of the π block 61. 々 SUMMARY OF THE INVENTION The present invention has been made to solve the above problems. Word Driven: The first object of the present invention is to provide a punching machine which can be miniaturized and which can provide a degree of freedom in the arrangement of the motor or the like. • It is also possible to provide a punching machine that can prevent the slider from being frequently tilted in the press machine by providing a punching machine that can freely change the forming force of the press machine in the case of a failure of the drive motor. In order to achieve the above-described first object, the present invention provides a drive motor including a drive motor for performing the drive, and a main gear that rotates by receiving the drive power, and the rotation of the main gear is performed. The conversion mechanism of the complex motion, and the slider connected to the conversion mechanism, and stamping 320031 6 Γ 353300 by the mold fixed to the slider, is characterized by: * supporting the axis of the main money Supporting a frame having the aforementioned conversion mechanism; and providing the driving force of the driving motor to the main gear: the transmission gear and the at least the foregoing main gear - Part of the tie is on the outside and side of the aforementioned frame to indicate that the main gear meshes with the aforementioned transmission gear. In the above configuration, at least a portion of the main gear is located outside the frame so that the main gear is in harmony with the transmission gear. That is, since the main gear is not housed inside the rack, the rack can be miniaturized. Moreover, since the drive motor is disposed outside the frame rather than inside, the degree of freedom in the arrangement of the drive motor, the transmission gear, and the like is emphasized. 1. According to a preferred embodiment of the present invention, the stamping "2" is described above. The main gear train is disposed outside the frame.

如此,由於主齒輪配置在前述機架的外侧,因此 輪的更換變得容易,主齒輪的維護性因而提高。 I 根據本發明,為了達成上述第二目的,提供 =其係具備有將用來進行衝屢之驅動馬: =往復運動之變換機構、以及連結至該變換機構而, 滑塊’且藉由固定至該濟塊之模具來進蝴 ,、、徵在於.具備具有驅料達可 安裝部的料,絲於馬達安W動馬料 力係傳遞至變換機構。 動 上述構成中,由於馬達安裝部係設有複數個,且 ^各馬達安裝部之驅動馬達的旋轉㈣力可機 構,因此可依據被加工物的種類而變更安裝於衝壓 320031 7 奶3300 驅動馬達的個數。藉此,可自由變更衝壓機械的成型力。 料’可在獲得必要的衝壓成型力所需之驅動馬達數 v之外—#刀別在馬達安裝部安裝一個或數個多冑的驅動馬 、達f此即使一個或數個驅動馬達故障,也能在該狀態 、下繼續進行衝壓。 /另外,根據本發明,為了達成上述第二目的,提供一 種衝壓機械,其係具備有將用來進行衝歷之驅動馬達的旋 _轉運動變換為往復運動之變換機構、以及連結至該變換機 構而往復運動之滑塊,且藉由固定至該滑塊之模具來進行 衝尾者’其特徵在於:具備具有驅動能力不同的驅動馬達 =卸之-個或複數個馬達安裝部的構件,㈣於前述馬 達女裝部之驅動馬達的旋轉驅動力係傳遞至變換機構。 上述構成中’由於設置具有驅動能力不同的驅動馬達 可襄卸之-個或複數個馬達安裝部之構件’因此可藉由變 ^驅動馬達來變更驅動能力,可自由變更衝麈機械的成型 力。 另外,根據本發明,為了達成上述第二目的,提供一 ^衝屢機械’其係具備有將用來進行㈣之驅動馬達的旋 轉運動變換為往復運動之變換機構、以及連結至該變換 2往復運動之滑塊,且藉由固定至該滑塊之模具來進行 τίΐ,其特徵在於:具備具有連結有驅動馬達之減速機 :裝卸之-個或複數個減速機安裝部的構件,前述驅動馬 轉驅動力係經由安襄於前述減速機安褒部之減速機 傳遞至别述變換機構,並且可增減連結至前述減速機之 320031 8 驅動馬達的數目。 上述構成t,由於設置驅動馬達可與之 •機,且使連結至減速機之驅動馬達的數目可增減,因此= ‘自由變更衝㈣械的成型力。而且,由於減逮機可° 因此即使減速機故障也可簡單地更換減速機。 、 另外,根據本發明,為了達成上述第二目的,提供一 種衝塵機械’其係具備有將用來進行衝愿之驅動馬達 轉運動變換為往復運動之變換機構、以及連結至 =主復運動之滑塊’且藉由固定至該滑塊之模具來進: 者’其特徵在於··具備具有連結有驅動馬達之減速機 :裝卸之-個或複數個減速機安裝部的構件,前述驅動馬 達的旋轉驅動力係經由安裝於前述減速機安裝部之減 而傳遞至前述變換機構,在前述減速機安裝部可供減速比 不同的減速機裝上拆下’而且可增減連結至前述減速機之 驅動馬達的數目。 上述構成中,由於設置具有減速機可裝卸之複數個減 =機安裝部的構件’且.使該構件可供減速比不同的減速機 裝上拆下’因此可藉由變更減速機來變更減速比,可自由 錢衝壓機械的成型力。而且,由於可增減連結於減速機 =驅動馬達的數目,因此可更細微地變更、調整衝壓機械 的成型力。 根據本發明’為了達成上述第三目的,提供一種衝壓 t,其係具備有用來進行衝壓之驅動馬達、接受該驅動 、、、的旋轉驅動力之第—窗輪群及第二齒輪群、將該第— 320031 9 K53300 ^群及第二錄群的絲旋轉運動變換 =構、以:連結至該變換機構而往復運動之滑塊 齒輪群#|有由第j仃錢者,其特徵在於:第— 之一對主齒輪,第二齒輪群在目@ 珉為相冋 抑^ 輪群係具有由第二連結部加以連姓 疋轉中心成為相同之—對主齒輪,第。 方的主齒輪係與第二齒輪 ::之,、中- 一 , 吁·^具Τ方的主齒輪嚙合,第 W輪群之另一方的主齒輪與第二齒 輪嚙合,第一齒輪群之Α& 两群另一方的主齒 置相I: 方的主齒輪係以旋轉方向位 置相對於第一齒輪群之另一方的主 式’藉由第一連結部而連結至 、疋X之方 ^ , ϋ 弟齒輪群之另一方的主齒 4=!輪群之其卜方的主齒輪的齒與第 齒於群之真茴輪的齒在%轉方向择觸’第-2群之另一方的主齒輪的齒與第二齒輪群之另一方的主 w輪的齒在旋轉方向接觸之狀態。 π之:二工於主齒輪與主齒輪相嘀合時,主齒輪相嚙合 旋轉方向會有間隙’因此主齒輪之位置不固 月塊會在_機械的運轉中頻繁地傾斜。 相對於此,上述的構成中 輪群之其中一方的主齒輪二:广連結部將第-齒 •齒輪群之另—方的主心轉方向位置相對於第一 .-齒輪群之另—方的度之方式連結至第 中一方的主告鉍 曲M•错此維持第一齒輪群之其 窗在旋轉方二Γ的齒與第二齒輪群之其中-方的主齒輪的 窗在疋轉方向接觸,第一齒輪群之另一方的主齒輪的廬與 320031 30 B53300 第二齒輪群之另一方的主齒輪的齒在旋轉方向接觸之狀 態。 - 因此,儘管主齒輪與主齒輪相嚙合部之齒面間存在有 % ' 間隙,也可維持主齒輪齒面間穩定接觸之狀態。從而,主 k 齒輪之旋轉方向位置經常保持固定。換言之,主齒輪之旋 轉方向位置不會有變動間隙的量之情形。所以,可防止滑 塊在衝壓機械的運轉中頻繁地傾斜。 上述預定的角度係大於〇度,且希望為與第一齒輪群 鲁所屬之主齒輪和第二齒輪群所屬之主齒輪之嚙合部的間隙 量相當之角度。如此,因為第一齒輪群之主齒輪的齒面不 會在旋轉方向對第二齒輪群之主齒輪的齒面施加預加負 荷,所以即'使雒持上述接觸狀態,也可避免第一連結部與 第二連結部發生扭轉。 此外,根據本發明,為了達成上述第三目的,提供一 種衝壓機械,其係具備有用來進行衝壓之驅動馬達、接受 I該驅動馬達的旋轉驅動力之第一齒輪群及第二齒輪群、將 該第一齒輪群及第二齒輪群的齒輪旋轉運動變換為往復運 動之變換機構、以及連結至該變換機構而往復運動之滑 塊,且藉由固定至該滑塊之模具來進行衝壓者,其特徵在 於:第一齒輪群及第二齒輪群係分別具有一對主齒輪,且 •第一齒輪群之其中一方的主齒輪與第二齒輪群之其中一方 '的主齒輪响合,第一齒輪群之另一方的主齒輪與第二齒輪 群之另一方的主齒輪嚙合,此外還具備有第一嚙合齒輪群 及第二喃合齒輪群,第一喃合齒輪群係具有由第一喷合齒 11 320031 P353300 輪連結部加以連結使旋轉中心成為相同之一對嚙合齒輪, 第二嚙合齒輪群係具有由第二嚙合齒輪連結部加以連結使 •、旋轉中心成為相同之一對嚙合齒輪,第一喃合齒輪群之其 ' 中一方的嚙合齒輪直接或間接地與第一齒輪群之其中一方 的主齒輪嚙合,第一嚙合齒輪群之另一方的嚙合齒輪直接 或間接地與第一齒輪群之另一方的主齒輪喃合,第二唾合 齒輪群之其中一方的嚙合齒輪直接或間接地與第二齒輪群 之其中一方的主齒輪嚙合,第二嚙合齒輪群之另一方的嚙 •合齒輪直接或間接地與第二齒輪群之另一方的主齒輪响 合,第一嚙合齒輪群之其中一方的嚙合齒輪係以旋轉方向 位置相對於第一嚙合齒輪群之另一方的嚙合齒輪偏移預定 的角度之方式,藉由第一嚙合齒輪連結部而連結至第一嚙 合齒輪群之另一方的嚙合齒輪,藉此,維持第一齒輪群之 其中一方的主齒輪的齒與第二齒輪群之其中一方的主齒輪. 的齒在旋轉方向接觸,第一齒輪群之另一方的主齒輪的齒 Φ與第二齒輪群之另一方的主齒輪的齒在旋轉方向接觸之狀 態。 上述的構成中,藉由第一嚙合齒輪連結部將第一嚙合 齒輪群之其中一方的嚙合齒輪以使旋轉方向位置相對於第 一嚙合齒輪群之另一方的嚙合齒輪偏移預定的角度之方式 連結至第一0iS合齒輪群之另一方的喊合齒輪,以藉此維持 /第一齒輪群之其中一方的主齒輪的齒與第二齒輪群之其中 一方的主齒輪的齒在旋轉方向接觸,第一齒輪群之另一方 的主齒輪的齒與第二齒輪群之另一方的主齒輪的齒在旋轉 12 320031 方向接觸之狀態。 、 儘言主齒輪與主齒輪相唾合部之齒面間存在有 、1隙也可維持主齒輪齒面間穩定接觸之狀態。從而,主 .、齒輪之旋轉方向位置經常保持固定。換言之,主齒輪之旋 .轉方向位置不會有變動間隙的量之情形。所以,可防止滑 塊在衝壓機械的運轉中頻繁地傾斜。 、上述預疋的角度係在0度以上,且希望為與第一齒輪 群所屬之主齒輪和第二齒輪群所屬之主齒輪之响合部的間 隙量相田之角度。如此,因為第一齒輪群之主齒輪的齒面 不會在旋轉方向對第二齒輪群之主齒輪的齒面施加預加負 ^所以即使維持上述接觸狀態,也可避免第—喃合齒輪 連結部與第一喃合齒輪連結部發生扭轉。 依照上収本制,第―、可小型化且可提高驅動馬 達專的配置的自由度,篦-y* 笫一在驅動馬達故障的..情況也能 繼續進行衝壓且可自由變更衝壓機械的成型力,第三、可 籲防止滑塊在衝壓機械的運轉中頻繁地傾斜。 【實施方式】 以下’根據圖式來說明本發 [第一實施形態] 第3A及3B圖顯示依據本發明第一 Λ 1罘只施形態之衝| 械的構成。第3Α圖為衝壓機械的正面斷面圖,第 第3Α圖之Β-Β線箭號方向視圖。 如第3Α及3Β圖所示’衝虔機械具備有用來進射 之驅動馬達2、接受驅動馬達2的旋轉驅動力而她 320031 13 1 齒輪3的旋轉運動變換為往復運動之變換機 構5、以及連結至變換機構5而往復運 變換機 衝屋機械還具備有:可旋轉地支持住旋轉轴。 輪3結合而作為主齒輪3的斿趟鉍 (〃、主諸 機架9、以另二: 轉轴)且内藏有變換機構5之 傳遞到主齒輪3之傳動齒輪u。而且,主歯動力 部份係位在機架9的外側,以便 的至夕一 嚙合。 便主齒輪3與傳動齒輪Π 在苐3A及3B圖的例子尹,驅動 動馬達2的輸出轴之傳動齒輪u係配置在固定於驅 (例如機架9的上面),且主齒輪3的卜=機架9的上方 突出。此主## 3 Μ ρ 、。卩從機架9向上方Thus, since the main gear is disposed outside the aforementioned frame, the replacement of the wheel becomes easy, and the maintainability of the main gear is improved. According to the present invention, in order to achieve the above second object, it is provided that the drive mechanism is provided with a drive mechanism for performing a reciprocating motion: a reciprocating motion, and a slider is coupled to the conversion mechanism, and is fixed by The mold to the die block is brought into the butterfly, and the mark is provided with the material having the driveable portion to be mounted, and the wire is transferred to the conversion mechanism by the motor. In the above configuration, since the motor mounting portion is provided with a plurality of rotations (four) force mechanisms of the drive motors of the motor mounting portions, the motor mounting portion can be changed to be attached to the stamping 320031 7 milk 3300 drive motor depending on the type of the workpiece. The number. Thereby, the molding force of the press machine can be freely changed. The material 'can be obtained in addition to the number of drive motors required for the necessary stamping forming force—#the knife does not install one or more multi-turn drive horses in the motor mounting portion, even if one or several drive motors fail, It is also possible to continue the pressing in this state. Further, according to the present invention, in order to achieve the above second object, there is provided a press machine including a conversion mechanism for converting a rotary-rotation motion of a drive motor for performing a stroke into a reciprocating motion, and coupling to the transformation a slider that reciprocates by a mechanism, and performs a punching by a mold fixed to the slider, and is characterized by: a member having a driving motor having different driving capabilities = one or a plurality of motor mounting portions, (4) The rotational driving force of the drive motor of the motor wear department is transmitted to the shifting mechanism. In the above configuration, 'the components of the motor mounting portion that can be detached by the drive motor having different driving capacities are provided'. Therefore, the driving ability can be changed by changing the driving motor, and the forming force of the punching machine can be freely changed. . Further, according to the present invention, in order to achieve the above second object, there is provided a conversion mechanism that converts a rotational motion of a drive motor for performing (four) into a reciprocating motion, and a reciprocating motion coupled to the shift 2 The slider of the movement is τίΐ by a mold fixed to the slider, and is characterized in that it includes a member having a speed reducer to which a drive motor is coupled: one or a plurality of reducer mounting portions, and the drive horse The driving force is transmitted to a different conversion mechanism via a speed reducer mounted on the aforementioned damper of the reduction gear, and the number of the 320031 8 drive motors coupled to the aforementioned reduction gear can be increased or decreased. In the above configuration t, since the number of the drive motors connected to the speed reducer can be increased or decreased by providing the drive motor, it is possible to "change the forming force of the punch (four) machine freely. Moreover, since the reducer can be used, the reducer can be easily replaced even if the reducer fails. Further, according to the present invention, in order to achieve the above second object, there is provided a dust-cleaning machine having a conversion mechanism for converting a drive motor for reciprocating motion into a reciprocating motion, and coupling to a main-reaction movement The slider is provided by a mold fixed to the slider: a member having a speed reducer to which a drive motor is coupled: a detachable one or a plurality of reducer mounting portions, the drive The rotational driving force of the motor is transmitted to the above-described conversion mechanism by being attached to the reduction gear mounting portion, and the reduction gear mounting portion can be attached and detached to a speed reducer having a different reduction ratio, and can be connected to the aforementioned deceleration. The number of drive motors for the machine. In the above configuration, since a plurality of members that are detachable from the reducer are attached and detached, and the member can be attached and detached to a speed reducer having a different reduction ratio, the speed reduction can be changed by changing the speed reducer. Compared to the forming force of the free money stamping machine. Further, since the number of the speed reducer = drive motor can be increased or decreased, the molding force of the press machine can be changed and adjusted finer. According to the present invention, in order to achieve the above third object, there is provided a press t including a first window wheel group and a second gear group for driving a motor for pressing, a driving force for receiving the driving, and The first 320031 9 K53300 ^ group and the second recorded group of the rotary motion of the wire = structure, the slider gear group that is coupled to the conversion mechanism and reciprocated #| has the money from the j, which is characterized by: The first one is the pair of main gears, and the second gear group is in the direction of the @ 冋 ^ ^ 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 轮 对 对 对 对 对 对The main gear train of the square and the second gear::,, the middle one, the main gear of the yoke, and the main gear of the other wheel of the W-wheel group mesh with the second gear, the first gear group Α& The main tooth of the two groups is placed in phase I: The main gear of the square is connected to the other side of the first gear group in the direction of rotation with respect to the other main body of the first gear group. , the main tooth of the other side of the 齿轮 齿轮 gear group 4 =! The teeth of the main gear of the wheel group and the teeth of the dent of the dent of the group are in the % direction of the other side of the 'group-2' The teeth of the main gear are in contact with the teeth of the other main w wheel of the second gear group in the rotational direction. π: When the main gear is engaged with the main gear, the main gear meshes with a gap in the direction of rotation. Therefore, the position of the main gear is not solid. The moon block is frequently tilted during the operation of the machine. On the other hand, the main gear 2 that constitutes one of the middle wheel groups described above: the wide connection portion positions the other main center of the first tooth-gear group in the direction of the first--the gear group. The way of the degree is linked to the main party of the first party. The M. error maintains the window of the first gear group. The window of the rotating gear is in the middle of the tooth and the second gear group. In the directional contact, the 主 of the other main gear of the first gear group and the teeth of the other main gear of the second gear group of 320031 30 B53300 are in contact with each other in the rotational direction. - Therefore, although there is a % ' gap between the tooth faces of the meshing portion of the main gear and the main gear, the state of stable contact between the tooth surfaces of the main gear can be maintained. Thus, the rotational direction position of the main k gear is often kept fixed. In other words, the position of the main gear in the direction of rotation does not change the amount of the gap. Therefore, it is possible to prevent the slider from being frequently tilted during the operation of the press machine. The predetermined angle is greater than the twist, and is desirably an angle corresponding to the amount of clearance of the meshing portion of the main gear to which the first gear group belongs and the main gear to which the second gear group belongs. In this way, since the tooth surface of the main gear of the first gear group does not apply a preload to the tooth surface of the main gear of the second gear group in the rotational direction, the first connection can be avoided by holding the contact state. The portion and the second joint portion are twisted. Further, according to the present invention, in order to achieve the above third object, there is provided a press machine including a drive motor for performing press, a first gear group and a second gear group that receive a rotational driving force of the drive motor, and The gear rotation motion of the first gear group and the second gear group is converted into a reciprocating conversion mechanism, and a slider that is coupled to the conversion mechanism to reciprocate, and is punched by a mold fixed to the slider. The first gear group and the second gear group respectively have a pair of main gears, and the main gear of one of the first gear groups and the main gear of one of the second gear groups are coupled, first The other main gear of the gear group meshes with the other main gear of the second gear group, and further includes a first meshing gear group and a second ring gear group, the first ring gear group having the first spray Joint teeth 11 320031 P353300 The wheel coupling portions are coupled such that the center of rotation becomes the same pair of meshing gears, and the second meshing gear group is coupled by the second meshing gear coupling portion • The center of rotation becomes the same pair of meshing gears, and the meshing gear of one of the first ring gear groups directly or indirectly meshes with the main gear of one of the first gear groups, and the first meshing gear group is another One of the meshing gears is directly or indirectly coupled with the other main gear of the first gear group, and the meshing gear of one of the second spitting gear groups directly or indirectly meshes with the main gear of one of the second gear groups The other gear of the second meshing gear group directly or indirectly engages with the other main gear of the second gear group, and the meshing gear of one of the first meshing gear sets is in a rotational direction relative to The other meshing gear of the first meshing gear group is offset by a predetermined angle, and is coupled to the other meshing gear of the first meshing gear group by the first meshing gear coupling portion, thereby maintaining the first gear group The teeth of one of the main gears and the teeth of one of the second gear sets are in contact with each other in the rotational direction, and the teeth of the other main gear of the first gear group A second group of gear teeth of the other gear of the main contact in the rotational direction of the state. In the above configuration, the meshing gear of one of the first meshing gear sets is shifted by a predetermined angle with respect to the other meshing gear of the first meshing gear group by the first meshing gear coupling portion. Connecting the shunt gear to the other of the first 0iS gear group, whereby the teeth of the main gear of one of the first gear groups and the teeth of the main gear of one of the second gear groups are in contact with each other in the rotational direction The teeth of the other main gear of the first gear group and the teeth of the other main gear of the second gear group are in contact with each other in the direction of rotation 12 320031. It is said that there is a gap between the tooth surface of the salient portion of the main gear and the main gear, and the gap between the main gear tooth surfaces can be maintained. Therefore, the position of the main shaft and the direction of rotation of the gear is often kept constant. In other words, the rotation of the main gear does not change the amount of the gap in the direction of the rotation. Therefore, it is possible to prevent the slider from being frequently tilted during the operation of the press machine. The angle of the pre-twist is above 0 degrees, and it is desirable to be at an angle to the amount of the gap between the main gear to which the first gear group belongs and the main gear to which the second gear group belongs. In this way, since the tooth surface of the main gear of the first gear group does not apply a pre-charge to the tooth surface of the main gear of the second gear group in the rotational direction, the first ring gear can be avoided even if the contact state is maintained. The portion and the first spur gear coupling portion are twisted. According to the above-mentioned system, the ―- can be miniaturized and the degree of freedom of the drive motor can be increased. 篦-y* 在 In the case of the drive motor failure, the stamping can be continued and the press machine can be freely changed. The forming force, third, can be prevented from frequently tilting the slider during operation of the stamping machine. [Embodiment] Hereinafter, the present invention will be described with reference to the drawings. [First Embodiment] Figs. 3A and 3B show the configuration of a mechanical device according to the first embodiment of the present invention. The third drawing is the front section of the stamping machine, and the third section is the Β-Β arrow direction view. As shown in Figures 3 and 3, the "crushing machine" is provided with a drive motor 2 for feeding, a rotational driving force for receiving the drive motor 2, and a conversion mechanism 5 for converting the rotational motion of the gear 3 to the reciprocating motion of the 320031 13 1 The reciprocating converter punching machine is coupled to the shifting mechanism 5 and further includes a rotatable support for the rotating shaft. The wheel 3 is combined to function as the main gear 3 (〃, the main frame 9, and the other two: the rotating shaft) and incorporates the transmission gear u of the shifting mechanism 5 which is transmitted to the main gear 3. Moreover, the main power portion is tied to the outside of the frame 9 so as to be engaged at the same time. The main gear 3 and the transmission gear Π In the example of FIGS. 3A and 3B, the transmission gear u of the output shaft of the driving motor 2 is disposed on the drive (for example, the upper surface of the frame 9), and the main gear 3 is = The top of the rack 9 protrudes. This main ## 3 Μ ρ ,.向From the rack 9 upwards

唾合。輪3的上部在機架9的上方與傳動齒輪U 因此= = =:全部收納在機"的内部,Spit. The upper part of the wheel 3 is above the frame 9 and the transmission gear U is therefore = = =: all are housed inside the machine "

的外側而非機架9的内部,因此二動:達2配置在機架9 等的配置的自由度提高。口此驅動馬達2及傳動齒輪U 驅動馬達2 A /s.i 1 達。傳動齒輪U為例如===可為其他適合的馬 輪(Pinion),但亦可為固定‘達2的輸出軸之小齒 動之減速機的輸出軸之小齒輪來:f驅動馬達2的旋轉運 架即可,惟亦可尨i 機木9為依:TIS規範之機 節連桿機構,但亦可^ °的機架。變換機構5為例如四 另外,亦;他適合的機構。 叫艮旋轉軸6配置—個主齒輪3之 320031 構成。 亦可形成為在第 9a之構成。 貝 施形態中設置後述的中間板部 化或使兩卜者:::::齒輪3與變換機構5的-部份-體 為例如偏心連;:構==變換機構5的-部份可 為使主齒輪3旋轉自如地支持於旋轉軸6之 相對於::鲶形成為將旋轉軸6固定於機架9之構成。可 鲈人而尤处:3而旋轉之前述旋轉軸6、以及與主齒輪3 多拉本ill目對於主齒輪3旋轉之上述旋轉轴6,都構成 支持主齒輪3之軸。 [第二實施形態] 第、及4Β圖顯不依據本發明第二實施形態之衝壓機 械的構成例。第4Α圖為衝壓機械的正面斷面圖,第4Β圖 為第4Α圖之Β-Β線箭號方向視圖。 —乂下針對與第—實施形態不同的構成進行說明。第 二實施形,其他構成可與第一實施形態相同。 第二實施形態中,主齒輪3係配置在機架9的外側。 例如如第4Α及4Β圖所示,主齒輪3在機架9的兩側, 配置在機架9的外側。 藉由此構成,主齒輪3的更換變得容易,主齒輪3的 維護性提高。亦即,在要將主齒輪3拆下的情況,不須將 由機架9支持住兩端之旋轉軸6從機架9拔出,也不須同 時將具有複雜構成之變換機構5從機架9拆下。因此,主 320031 1-353300 會輪3的更換變得容易,主齒輪3的維護性提高很多。 較佳者為’將主齒輪3與旋轉軸6構成為可互相分離。 如此,主齒輪3的更換變得更加容易。 此外,第二實施形態中雖設有中間板部,但亦可為 沒有中間板部9a之構成。關於中間板部%之詳細說明, 將在以後參照第12圖加以說明。 [第三實施形態] =5A及则顯核據本發明第三實施形態之衝壓機 =構成例。第5A圖為誠機械的正面斷面圖,第5B圖 為第5A圖之B-B線箭號方向視圖。 二實二:離,與第二實施形態不同的構成進行說明。第 -實㈣態之其他構成可與第二實施形態相同。 第三實施形態中,設有驅動气 達安穿邱19 P壯为動馬達2可裝卸的複數個馬 旋::動二:馬達”部12之驅動馬達2的 灰轉驅動力可傳遞至變換機構5。 為了使驅動馬達2可相對 採用例如以下之構成。在衝拆下’可 置馬達安裝構件15,並在該:固定設 馬達安裝部12。 逆文裒構件15設置複數個 然後’為了以可裝上拆下的方 馬達安裝部12,而例如:在:、駆動馬達2固定至 螺牙之安裝孔12以作為馬達·安:装構件15設置攻有内 之軸方向-端形成凸緣部17,並':12,另外在驅動馬達2 孔1 8。 W在此凸緣部1 7設置貫通 320031 16 然後’將螺絲〗9穿普 如此,就可以使驅動馬達2二:】8而鎖緊於安裝孔 ,下。另外,此時可使—個…及從該 .女裝孔】2,並對應於該等安 、 為複數個上述 成複數個貫通孔18。 、 而在各驅動馬達2形 上述之馬達安裝部〗2的構成僅 他適合的手段來構成馬達安 :個例子,亦可用其 傳動窗輪η的輸入轴來作為馬達安拿’ ζ可形成為設置 由聯結(⑽ΡΗ猶件來使傳動構件;;卩之構1 ’此時可藉 達2的輸出軸可互相連結。 的輸入軸與驅動馬 的數=構械之驅動馬達2 力。例如,可追加第二種類等而變化衝愿成型 而提高衝壓成型力。 丁之四個驅動馬達2 此外’可在獲得必要的纏成 的個數之外"“之動馬達2 動3達2 ’、、、女裝邛12安裝-個或數個多餘的驅 ^二 如第5B圖中虛線所示,預先追加四個 、、驅馬達2。如此’即使一個或數個驅動馬達2故 早,也能在該狀態下繼續進行衝壓。 尸圖係顯示第三實施形態的另一構成例之圖 將第5B圖之構成加以變更後之構成。 、、 此構成例可使驅動能力不同之複數個驅動馬達2a、2b 可相對於衝壓機械而裝上拆下。例如,使用尺寸及形狀之 至少一項不同之複數個驅動馬達’另外,尺寸及形狀相同 320031 17 1*353300 亦可。 _由、例如不只使第5β圖所示尺寸之驅動馬達2(第6圖 j 2a表不),也如第6圖所示,使比第把圖的驅動馬達 、^大型之驅動馬達2b可安裝至馬達安裝部及從該處 • ·拆下’使小型的驅動馬達2a與大型的驅動馬達几可以交 換。 /為此例如’使上述驅動馬達2a、之凸緣部17的 形狀及外位’在小型的驅動馬達2a與大型的驅動馬達㉛ 之間都㈣,而且使形成於凸緣部〗7之上述複數個貫通孔 的位置也在小型的驅動馬達2a與大型的驅動馬達2匕之 間都相同。藉此,使小型的驅動馬達h與大型的驅動馬達 2b都可安裝至同一個上述安裝孔12。 藉由此構成,即可將驅動能力不同的伺服馬達以可更 換的方式安裝至衝廢機械。因而,可依據被加工物的種類 等而變更衝壓成型力。 、 • 此外,亦可將驅動馬達連同傳動齒輪11 一起更換,或 者’亦可形成使傳動齒輪11的輸入軸可旋轉地支持於機架 9之構成’再藉由聯結n(coupling)等使更換用的驅動馬達 的輸出軸與該輸入軸結合。 第7A及7B圖係顯示本發明第三實施形態之又另一構 —成例之圖。第7A圖為衝壓機械的側面斷面圖,第7B圖為 第7A圖之B-B線箭號方向視圖。 此例係將複數個減速機21固定在機架9的上面。而 且,為了簡化,第7A圖中僅繪示一個減速機21。減速機 320031 18 21的輪出軸固定有盥主 速機2 it M輪3嚙合之小齒輪11。另外,減 之Π 輪入轴,此等輸入轴分別供驅動馬達2 出軸以可拆去的方式與之結合。 動馬、籌成即可變更結合至減速機21的輸入軸之驅 動馬達2^目,^如’可追加第7B圖令虛線所示之驅 型力。 而,可依據被加工物的種類等而變更衝壓成 ^ 21 而穿上抽_/、 )之同—位置的減速機安裝部(未圖示) 減迷ϋ詩此情況也一樣’可使安裳在機架9的上面之 合,並將驅叙’出軸上所固定的小齒輪11與主齒輪3嚙 另外,此二::達2的輸出轴結合至該減速機的輸入軸。 讓此等\樣’可在各減速機設置複數個輸入軸, 與之分别供驅動馬達2之輸出抽以可拆去的方式 減二:Π1:障亦可簡單地更換。如上述之 減速機”二…且’上述之 例如’可在機架9側設置述安=2:二者。亦即’ 15 一樣的構m、Φ拖 、孔12及馬達安裝構件 通孔18—/ 減速機21側設置與上述凸緣部17及貫 杈的構成。不過,本_ % # 乙 其他適合的手段來設置減速亦可用 ^ 21 5位置的減速機安裝部(未圖示) 19 320031 而裝上拆下。減速比 … 之任-者不同者 5之減速機21可為例如尺寸及形狀 亦可為相同者。 * 此情況也一樣,可使安奘/嫌如η ·.的輪出軸上所固定的,裝在機架9的上面之減速機21 馬達2的輪出轴結合機與主齒輪3嗔合,並將驅動 也-樣,可在各減逮機設置入轴。另外,此情況 分別供驅動馬達2之^ 輸入軸,讓此等輸入軸 外,如上述之減迷以可拆去的方式與之結合。另 此外,如設置—個村設置複數個。 部12相同者。^之=機=部^為與=述之馬達安裝 孔12及馬達安㈣件二設置與上述安裝 與上述凸緣部l7p、s f 成’在減速機21側設置 並不限定於此,允貝18 一樣的構成。不過,本發明 部。、’/、可用其他適合的手段來設置減速機安裝 年9 ’使尺寸或形狀不同之減速機21可相對於機 = = 之情況,依照所安裝之減速機21的尺寸或 變化。疋接至該減逮機21之驅動馬達2的安裝位置會 讀裝位置之變化可用一般的方法來因應,在此簡單 ^用來因應安裝位置的變化之一個例子。第7b圖之箭 琥C顯示局部擴大的部份。- 、等用來女裝在機架9的上面之板51固定在驅動馬達2 的底面,並在機架9的上面設置螺絲孔(未圖示),且對應 於-個該螺絲孔在板51設置一個貫通長孔53。然後,^ 320031 20 ^53300 具:不能通過貫通長孔53之大小的 該貫通長孔53,並使該螺絲螺合於機架 ^系^ .驅動馬達2安裝至機架9。 螺,,,糸孔,而將 ·. 此時,由於貫通長孔53在第7B圖之+ 因此能以在左右方向右方向較長, ·#右方向調整位置的方式固定驅動 -方面,對於上下方向之安裝 另 等而可農拆地將厚度不同之板51固定至;要^由螺絲 可因應。 U疋至驅動馬達2底面即 另外,在第三實施形態中,馬達安 裝部亦可設置在衝塵機械的其他部位。 /機安 =外,第三實施形態中雖設有中間板部%,但亦 -有中間板部9a之構成。關於中 … 將在以後參照第12圖加以說明。 I田說明’ [第四實施形態] “以下針對本發明之第四實施形§進行朗。第 形態之衝壓機械除了以下說明之點以外 態相同。 弟一κ知形 第:圖係顯示如第二實施形態之構成之主齒輪相 。的狀態之斜視圖。此圖中’第—齒輪群具有 部(圖中的例子為旋料6_1}加以連結使其旋轉 相同之一對主齒,. 此 „ ^ ^ 丁王茴輪3-1、3_2。第二齒輪群具有 部(圖中的例子為旋轉軸6_2)加以連結使其旋轉二= 相同之一對主齒輪3_3、3_4。 為 如第8圖所示’第一齒輪群之其中一方的主齒輪h 320031 21The outside of the rack is not the inside of the rack 9, so the degree of freedom in the configuration of the rack 2 and the like is increased. The drive motor 2 and the drive gear U drive motor 2 A /s.i 1 reach. The transmission gear U is, for example, === can be other suitable pinion, but can also be a pinion of the output shaft of the reducer that fixes the output shaft of the output shaft of 2: f drives the motor 2 Rotating the carrier can be used, but it can also be used according to the TIS standard machine node linkage mechanism, but it can also be used as a rack. The shifting mechanism 5 is, for example, four, and also a suitable mechanism. The 艮 rotating shaft 6 is configured as a 320031 of the main gear 3. It can also be formed as a structure in the 9th. In the Besch form, the intermediate plate portion to be described later is provided or the two-part:::::the gear 3 and the -partial body of the shifting mechanism 5 are, for example, eccentrically connected; the structure == the portion of the shifting mechanism 5 can be In order to allow the main gear 3 to be rotatably supported by the rotating shaft 6, the : is formed to fix the rotating shaft 6 to the frame 9. The above-mentioned rotating shaft 6 which is rotated by 3, and the above-mentioned rotating shaft 6 which rotates with respect to the main gear 3 and the main gear 3, constitute the shaft supporting the main gear 3. [Second Embodiment] Figs. 4 and 4 show a configuration example of a press machine according to a second embodiment of the present invention. The fourth drawing is the front sectional view of the stamping machine, and the fourth drawing is the 方向-Β line arrow direction view of the fourth drawing. - The configuration that is different from the first embodiment will be described. In the second embodiment, the other configuration can be the same as in the first embodiment. In the second embodiment, the main gear 3 is disposed outside the frame 9. For example, as shown in Figs. 4 and 4, the main gear 3 is disposed on the outer side of the frame 9 on both sides of the frame 9. With this configuration, the replacement of the main gear 3 is facilitated, and the maintainability of the main gear 3 is improved. That is, in the case where the main gear 3 is to be detached, it is not necessary to pull out the rotary shaft 6 supported by the frame 9 from the frame 9, and it is not necessary to simultaneously change the mechanism 5 having a complicated configuration from the frame. 9 removed. Therefore, the replacement of the main wheel 320031 1-353300 becomes easy, and the maintainability of the main gear 3 is much improved. Preferably, the main gear 3 and the rotating shaft 6 are configured to be separable from each other. Thus, the replacement of the main gear 3 becomes easier. Further, in the second embodiment, the intermediate plate portion is provided, but the intermediate plate portion 9a may be omitted. A detailed description of the intermediate plate portion % will be described later with reference to Fig. 12. [Third Embodiment] = 5A and a press machine according to a third embodiment of the present invention = a configuration example. Fig. 5A is a front sectional view of the machine, and Fig. 5B is a B-B line arrow direction view of Fig. 5A. Two real two: The configuration different from the second embodiment will be described. The other configuration of the first-solid (fourth) state can be the same as that of the second embodiment. In the third embodiment, a plurality of horse-spinnings are provided for driving the motor to pass through the Qiu 19 P-strong motor 2: the second driving force of the driving motor 2 of the motor portion 12 can be transmitted to the shift In order to make the drive motor 2, for example, the following configuration can be used. The motor mounting member 15 can be placed under the detachment, and the motor mounting portion 12 can be fixed. The counter member 15 is provided in plural and then The detachable square motor mounting portion 12 can be attached, for example, the swaying motor 2 is fixed to the mounting hole 12 of the screw to serve as a motor. The mounting member 15 is provided with an inner shaft direction-end forming a convex portion. The edge portion 17, and ':12, additionally drives the motor 2 hole 18. W is placed at the flange portion 17 through the 320031 16 and then the 'screw〗 9 is so that the drive motor 2 can be made: 8 And locking the mounting hole and the lower part. In addition, at this time, the ... can be made into a plurality of through holes 18 corresponding to the plurality of holes. The drive motor 2 has the above-described configuration of the motor mounting portion 2, and only the suitable means to constitute the motor For example, the input shaft of the transmission window wheel η can also be used as the motor's '' ζ can be formed as a connection ((10) ΡΗ 件 来 使 传动 传动 卩 卩 卩 卩 ' ' ' ' ' ' ' ' ' ' ' ' The shafts can be connected to each other. The number of input shafts and the number of driving horses = the driving motor 2 force of the mechanism. For example, a second type or the like can be added to change the punching force to increase the press forming force. In addition to obtaining the necessary number of entanglements, ""Moving motor 2 moves 3 up to 2',, women's clothing 安装12 installation - or a few extra drives ^ 2 as shown in the dotted line in Figure 5B Four motors are added in advance, and the motor 2 is driven in advance. Thus, even if one or a plurality of drive motors 2 are used earlier, the press can be continued in this state. The cadaver diagram shows another configuration example of the third embodiment. The configuration of Fig. 5B is changed. In this configuration, a plurality of drive motors 2a and 2b having different drive capacities can be attached and detached with respect to the press machine. For example, at least one of size and shape is used. Different number of drive motors 'in addition, ruler The size and shape are the same as 320031 17 1*353300. _ By, for example, not only the drive motor 2 of the size shown in the 5th figure (not shown in Fig. 6 2a), but also as shown in Fig. 6, The drive motor of the figure, the large drive motor 2b can be mounted to and from the motor mounting portion. • The small drive motor 2a can be exchanged with a large drive motor. For example, the drive motor can be used. 2a, the shape and the outer position of the flange portion 17 are both (4) between the small drive motor 2a and the large drive motor 31, and the positions of the plurality of through holes formed in the flange portion 7 are also small. The drive motor 2a is the same as the large drive motor 2匕. Thereby, both the small drive motor h and the large drive motor 2b can be attached to the same mounting hole 12 as above. With this configuration, the servo motors having different driving capacities can be mounted to the scrapping machine in a replaceable manner. Therefore, the press forming force can be changed depending on the type of the workpiece or the like. In addition, the drive motor can be replaced together with the transmission gear 11, or 'the formation of the input shaft of the transmission gear 11 can be rotatably supported by the frame 9' and replaced by coupling (coupling) or the like The output shaft of the drive motor used is combined with the input shaft. 7A and 7B are views showing still another embodiment of the third embodiment of the present invention. Fig. 7A is a side sectional view of the press machine, and Fig. 7B is a view of the arrow direction of the B-B line in Fig. 7A. In this example, a plurality of speed reducers 21 are fixed to the upper surface of the frame 9. Moreover, for the sake of simplicity, only one speed reducer 21 is shown in Fig. 7A. The pinion shaft of the reducer 320031 18 21 is fixed with a pinion 11 of the 盥 main engine 2 it M wheel 3 meshing. In addition, minus the input shaft, the input shafts are respectively detachably coupled to the drive motor 2 shaft. The driving force of the input shaft coupled to the input shaft of the reduction gear 21 can be changed by moving the horse, and the driving force indicated by the broken line of the seventh embodiment BB can be added. In addition, depending on the type of the workpiece, etc., the reduction gear mounting portion (not shown) that is pressed into the same position as the pumping _/, can be changed. The skirt is on the top of the frame 9, and the pinion 11 fixed on the shaft is meshed with the main gear 3, and the output shaft of the second: 2 is coupled to the input shaft of the reducer. Let these samples be able to set a plurality of input shafts in each speed reducer, and separately output the output of the drive motor 2 in a detachable manner. Second: Π1: The obstacle can also be easily replaced. As described above, the speed reducer "two...and the above-mentioned, for example, can be arranged on the side of the frame 9 to say that both = 2: both. That is, the same structure of the '15, the Φ drag, the hole 12 and the motor mounting member through hole 18 —/ The reduction gear 21 side is provided with the above-described flange portion 17 and the structure of the flange. However, this _% # B other suitable means for setting the deceleration can also be used with the gear unit mounting portion (not shown). 320031 and the removal and reduction ratio. The speed reducer 21 of the different ones can be, for example, the same size and shape. * The same is true for the case, which can make the ampoule/negative The reducer 21 fixed on the wheel shaft and mounted on the upper surface of the frame 9 is coupled to the main gear 3 of the motor 2, and the drive is also similar, and can be set into the shaft at each of the reducers. In addition, this case is respectively used for the input shaft of the drive motor 2, so that the input shafts are combined with the fascia in the detachable manner as described above. In addition, if a set is set, a plurality of villages are set. 12 identical. ^ = machine = part ^ for the motor mounting hole 12 and the motor (four) two set and the above installation and above The flange portions l7p and sf are provided on the side of the speed reducer 21, and are not limited thereto, and the configuration of the outer casing 18 is the same. However, the present invention section, '/, can be installed by other suitable means for the gear unit installation year 9' The speed reducer 21 having a different size or shape may be in accordance with the size or change of the mounted reducer 21 with respect to the machine ==. The mounting position of the drive motor 2 spliced to the reducer 21 will be read. The change can be responded to by a general method, and is simply used as an example of the change in the mounting position. The arrow C of Fig. 7b shows a partially enlarged portion. -, etc. is used for women's clothing on the top of the rack 9. The plate 51 is fixed to the bottom surface of the drive motor 2, and a screw hole (not shown) is provided on the upper surface of the frame 9, and a through hole 53 is provided in the plate 51 corresponding to the screw holes. Then, ^ 320031 20 ^53300: It is not possible to pass through the through hole 53 which penetrates the length of the long hole 53, and screw the screw to the frame. The drive motor 2 is attached to the frame 9. The screw, the, the hole, and the · At this time, since the through hole 53 is in the 7th figure, it can be left. The right direction and the right direction are long, and the direction of the right direction adjustment is fixed. In terms of the installation in the up and down direction, the plate 51 having a different thickness can be fixed to the soil; the screw can be used. In addition, in the third embodiment, the motor mounting portion may be provided at another portion of the dust-washing machine. In addition, in the third embodiment, the middle plate portion is provided, but - The structure of the intermediate plate portion 9a. The middle portion will be described later with reference to Fig. 12. I Field Description '[Fourth embodiment] "The fourth embodiment of the present invention is hereinafter described. The press machine of the first embodiment is the same except for the points described below.弟一κ形形: The figure shows the main gear phase as constructed in the second embodiment. An oblique view of the state. In this figure, the 'the first gear group has a portion (the example in the figure is the screw 6_1} is connected to rotate the same pair of main teeth, this „ ^ ^ Ding Wang IF wheel 3-1, 3_2. The second gear group has The part (the example in the figure is the rotating shaft 6_2) is coupled to rotate two = the same pair of main gears 3_3, 3_4. It is the main gear h 320031 21 of one of the first gear groups as shown in Fig. 8.

JUU 與第二齒輪群之其中-方的主齒輪—入 之另一方的主齒輪3_2盥第齒D,苐—齒輪群 孓4嚙合。藉由此箄主音払叫一回輪群之另一方的主齒輪 . 嗝。 等主齒輪間之嚙合,方蚀田益叙 .輪的情況,可防止滑塊或1他 複數個主齒 • •匹配或相位偏差。 構件會破損之程度的左右不 3·"=:= 態广齒輪群之其中-方的主齒輪 系以』轉方向位置相對於第一齒輪 丨Π3:偏移預定的角度之方式,藉由旋轉轴…= 輪群之一方的主齒輪Μ。藉此,維持第-齒 '、 方的主齒輪3-1的齒與第二齒輪群之其中一 沾主齒輪3·3的齒在旋轉方向接觸,第—齒輪群^另一 =裔輪^的齒與第二齒輪群之另一方的主齒輪Η 在方疋轉方向接觸之狀態。 方向因此儘管主齒輪與主齒輪相嚙合部之齒面間在旋轉 D存在有間隙,也可在衝壓機械之運轉中維持主齒輪齒 面間穩定接觸之狀態。 a本案中’旋轉方向不僅僅表示驅動馬達2所實際驅動 疋轉方向’亦包含該旋轉方向的相反方向之概念。 以下根據第9圖更詳細說明如上述第四實施形態之原 理〇 (1)第9圖中,假設第二齒輪群之主齒輪3·3、3·4以及 灰轉車由6 9 + 位 ^在旋轉方向固定不動。以此固定位置作為基準 > °此時’主齒輪3_3、3_4與旋轉軸6-2係結合成相互 疋轉方向的相位不變。其中,可使主齒輪3-3、3-4具有 22 320031 B53300 相同的形狀及尺寸,且旋 至旋轉軸6士 疋轉方向的相位相同之形態連結 :·群之=T固定在基準位置之主齒輪3+使第-齒輪 ·.:= 箭號…示的方向旋轉,形成兩齒輪的 • 之狀態,然後使主齒輪“相對於基 +位置而固定。 61 ^時1由於主齒輪3'2以於旋熟仏因此旋轉軸 定=號b所示的方向旋轉然後相對於基準位置而固 主齒輪3_卜3_2可具有相同的形狀及尺寸。 6 i 使第一齒輪群之主齒輪Μ固定於旋轉轴 〜使主=Γ整主齒輪Μ的旋轉相位而進行。具體而 ”所對於固定在基準位置之旋轉軸W朝 斤不的方向旋轉’形成兩齒輪的齒在⑻所示之處接 狀態。在此狀態,將主齒輪3·1固^至旋轉軸6-1,藉 :成主齒輪3_i、3_2、3_3、3_4全部在旋轉方向都“ :二= 立關係已經決定之狀態。在此狀態,主齒 輪丄?疋轉方向位置相對於主齒輪W偏移預定的角度。 在上述(3)中,第一齒輪群 月又 方向的相位,可藉由相位調整機構^^^ • —之相㈣整 再取弟ϋβ圖係第〗〇A圖中虛線邱々、从4丄 •斜視圖。第H)A*1GB圖中箭Ea、b、e之方心別 9圖之箭號a、b、c之方向對應,第1〇A 與第9圖之(B)所示之處對應。 )斤不之處 320031 23 1353300 相位調整機構27係如第i〇b圖所示 第-切槽部”之旋轉轴6-1、 :: 29、具有 齒輪3]所構成。 及八有第一切槽部33之主 =29係形成為其與轴方向垂直之斷面積從 一编漸增之形狀。在第1〇β 為向另 點方内子古 ,'子中’楔29具有虚f 軸方向垂直之矩形斷面,邊29a、鳥的長度 …、 度之角度範圍内從一端側向另一端侧 角、: 1度以外之角度。 角度亦可為 第一切槽部3i係在旋轉軸6-1之與主齒 部份貫通旋轉軸6_;1而形成。由 I口合 旋轉軸6]的#方於第一切槽部31而形成在 _ “方向内側之凹陷空間,係向著主齒幹3〗 !:口。此空間在旋轉轴Μ之周向延伸預定的長:。此 二間之凹陷量,亦即此空間之與 又此 行之^ 轉軸6-1的半輕方向平 仃之斷面積,係在旋轉軸6_r之周向都大致相同。千 第一切槽部33係在主齒於3 Λ 部份貫通主齒輪Ρ而形成。二第^轉車由Μ的結合 主齒輪、第一切槽部33而形成在 =輪3d的切方向外側之凹陷空間,係 侧開口。此空时主齒輪3_丨之周 =Η 空間之凹陷量,亦即此空間之鱼主二:預疋的長度。此 行之斷面積,得在主好3 的半徑方向平 .積糸在主Α Μ之周向都大致相同。 由於第-切槽部31而形成之空間以及 :”而形成之空間,係在旋轉輪“的半徑方向;= =在此重複的㈣***楔29。將楔29朝第咖 戒d之方向壓入,則由於旋轉轴固定於基準位置,= 320031 24 1353300 Ϊ = ί齒輪3“朝第1〇B圖之箭號。之方向旋轉。此時, 主齒輪3-1之旋轉量係依楔29之壓入量而定。 如此實施,即可在衝壓機械之運轉中維 _ 、 +甘rk 、乐 齒輪群 八一方之主齒輪3-1的齒與第二齒輪群之其中一方之 主齒輪3-3的齒在旋轉方向接觸,第一齒輪群之另一 主齒輪3-2的齒與第二齒輪群之另一方 在旋轉方向接觸之狀態。 的齒 為了維持嫌態’可以使第—絲.群之主齒輪3_卜 3_2的齒面在旋轉方向對第二齒輪群之主齒輪w、3 齒面施加預加負荷(推塵力)。此時,從如第9圖所 一齒輪群之盆中一方夕士在认 '、第 之I令一方Γ 士 4 齒輪3-1的齒僅僅與第二齒輪群 ^9更加μ _3的齒在旋轉方向接觸之狀態,將 輪及旋轉軸各部發生彈性變形,而在第9圖之⑷、吏: 不之各接觸部以緊壓對方的 荷。 幻w輪齒面的方式施加預加負 9 為二:第11圖所示,成為扭轉樑之旋轉軸^會因 ΐ方轉1由6^/_方向彈性變形,產生扭轉角~。此 疋轉軸6_2也同樣彈性變形。 齒面二:二 加預加負荷而維持上述狀態。此時齒:…-4的齒面施 —方之主齒輪1 ψ為第一齒輪群之其中 齒幹3 3的音少、齒僅僅與第二齒輪 齒輪3-3的齒在旋轉方向接 畔U万之主 碉之狀感。亦即,可避免旋轉 320031 25 1.353300 轴6-1、6_2發生扭轉。 換&之’利用相位調整機構27,可調整主齒輪3_ι相 •對於主齒輪3-2在旋轉方向偏移之上述預定的角度。 • 上述預定的角度係比0度大,且希望為與第一齒輪群 所屬之主齒輪3-1、3-2和第二齒輪群所屬之主盘輪 3〜部的間隙量相當之角度。如此,可避齒免輪旋= 6·1、6-2發生扭轉。 如上所述,根據第四實施形態,則儘管主齒輪盥主齒 2相喝合部之齒面間存在有間隙,也可在衝屢機械^運轉 維持主齒輪齒面間穩定接觸之狀態。從而,主齒輪之旋 轉方向位置經常保持固定。換言之,主齒輪之旋轉方向位 ,不會有變動間隙的量之情形。所以,可防止滑塊7在衝 塵機械的運轉中頻繁地傾斜。 例如’即使在例如滑塊7之下死點,也可防止滑塊7 傾斜,結果可提高衝壓成型品之品質。 另外在如第4圖使用複數個驅動馬達2之情況 ^ j駆動馬達2故障導致從驅動馬達2傳遞至第一齒輪 =弟一齒輪群之旋轉驅動力變得不同,亦接 觸的狀“維㈣塊7的姿勢為水平。 攻接 接著’說明依據第四實施形g之另外的構成例。 第12圖 ' 第13圖、第14八圖及第ι4Β圖分別顯 3四ft”之另外的構成例…。以下,在主齒輪“、 記載為主齒:ΓγΓ有必要加以區別之情況’將各主齒輪 口己戰馮王齒輪3。同樣,左妒絲+ λ ^在疑轉軸、6-2之間沒有必 320031 26 Γ3533〇〇 =以區別之情;兄,將各旋轉轴記載為旋轉轴6 成例1至3之構成,除了以下說明的以外和上’各 .第!2圖之構成例丨中,機架9的内部 目:。 .9的-部份之中間板部9a。此中間板部%以可旋:::架 =Γ6。此構成在上述施加有預加負荷的情況2 中雖會產生扭轉轉矩,但由於主齒輪3 ”a:,配Λ在其兩側,故產生扭轉轉矩之旋編的= I 主齒輪3的旋轉運動會很穩定。 另外,由於使中間板部9a與機架9一 架9整體的剛性提高。 " ,因此機 轉拇由於設置中間板部%可使得作為旋轉勒6之彎 轉轺的樑長度變短’因此剛性提 一 撓曲減少。 U成形負何荨所致之 機構在構成例1中,亦可形成為使主齒輪3 1變換 機】二:份一體化或使兩者結合之構成。此時,、變換 =二zt例如偏心連桿機構或四節連桿機構之 :輪和攻個時候,可形成為使主齒輪3旋轉自如地支 持於旋轉軸6之構成,亦可再來“ μ 捉轉自如地支 架9之構成。 再形成為將旋轉軸6固定於機 弟13圖之構成例2中,今右脸+ i 7 < ° :主ω輪與主齒輪相結合 之、,Ό合構件35。此結合構件35 延伸,且其兩端分別固定至主齒輪3之^=軸6千灯而 構成中,由於主齒輪3相互之 ^各相向側面。在此 因此可防止旋轉軸6中產生;矩、°::件35而結合, 租轉轉矩。尤其,在上述施加 320031 27 矩。、7之匱/兄’可防止或抑制旋轉軸6中產生扭轉轉 軸6=:: 2中,亦可設置中間板部%。此時,旋轉 35 . 結合第一齒輪群之主齒輪3-1、3-2之#人## 35,係與旋輕ϋ . 之結合構件 第一連接1。或取代旋轉軸6-1而構成上述之 樣。結合第二齒輪群之主齒輪 件35,係與旋轉軸6 9 . ^ 心…。稱 之第二連^ 或取代旋㈣6_2而構成上述 構5的a在構成例2巾,可形成為使主齒輪3與變換機 :冓的-部份一體化或使兩者結合之構成。此時,= 、 偏^^連知機構或四節連桿機構之偏 輪:。运個時候,可形成為使主齒輪3旋轉自如地支持 、疋轉轴6.之構成’亦可再形成為將旋轉軸6固定於機架 9之構成。 _ 第4Α及14Β圖係顯示構成例3。第丨4Α圖係衝壓機 械的側面斷面圖,第14B圖係第14A圖之B_B線箭號方向 視圖。第14B圖中為簡化而省略機架9等。 第14A及14B圖之構成例3中’在機架9的内部形成 作為機架9的-部份之中間板部%。而且,上述之各旋轉 •軸6在中間板部9a分割而成為兩個個別的旋轉軸6a、6b。 在此構成中’由於旋轉軸6a及旋轉轴6b在中間板部% 分離,因此主齒輪3及變換機構5之更換變得容易,而且 由於以連結軸14·1、14·2使兩驅動馬達2的輸出轴相結 28 320031 P353300 合,因此可穩定地驅動主齒輪3。 再者,在構成例3中,設有第一 .合齒輪群。第一嚙合齒輪群具有由一一喷合齒輪群及第二嚙 .第14B圖的例子中為連結軸Ι4·η 嚙合齒輪連結部(在 相同之一對嚙合齒輪nq、η_2。χ連結使其旋轉中心 第二喃合齒輪連結部(在第14Β圖^^嚙合齒輪群具有由 加以連結使其旋轉中心相同之一 為連結軸14·2) 第-嚙合齒輪群之其中一方的口回輪U·3、。 齒輪群之苴由 的喝合齒輪1M鱼笙 A群之其令一方的主齒輪3-1嗔人,笛— 與第一 另-方_合齒輪n_2與第—齒:群之::::輪群之 3-2嗤合。 方的主齒輪 第二唾合齒輪群之其中一方的喃合齒輪 齒輪群之其中一方的主齒輪 -、第二 另-方㈣合齒…與第二:二.之第^ 3-4嚙合。 輪群之另一方的主齒輪 另外,在第UA及14B圖的例 固定至驅動馬達2的輪, π 谷喵口齒輪雖為 叫、叫、丨丨'’惟各心齿輪 力傳遞到主齒之I兹、I * : &動馬達2的旋轉越動 :题j主齒輪3之齒輪。此時,可在該等嚙合齒 夕设置別的小齒輪,並經由該小齒輪將旋, 動馬達2傳遞到主齒輪3。 動力從驅 ㈣此構成例3’第—唾合齒輪群之—其中 :輪11-1係以其旋轉方向位置相對於第一嚙合齒於 另一方的喷合齒輪n_2偏移預定的角度之=之 符田連結 320031 29 P353300 轴14-1而連結至第一嚙合齒輪群之另一方的嚙合齒輪 11-2。 藉此,維持第一齒輪群之其中一方的主齒輪3d的齒 與第二齒輪群之其中一方的主齒輪3·3的齒在旋轉方向接 觸、第一齒輪群之另一方的主齒輪3-2的齒與第二齒輪群 之另一方的主齒輪3-4的齒在旋轉方向接觸之狀態。 如此之構成例3的原理與根據第9圖而說明過之上述 原理一樣,惟在此仍根據第15Α及15Β圖進行詳細說明。 第15Α圖係第14Β圖之a_a線箭號方向視圖,第15Β圖係 第14Β圖之b-b線箭號方向視圖。 〇)第一嚙合齒輪群之嚙合齒輪Π-2與連結軸14_1相 互連結,且假設在旋轉方向固定不動。以此固定位置作為 基準位置。 (2) 相對於固定在基準位罟 成 +位置之嚙合齒輪11-2,使第一齒 輪群之主齒輪3-2朝箭號a所示的方— / 納告私-方向碇轉’形成兩齒輪 2齒在(H)所不之處接觸之狀態’然後使主齒輪 於 基準位置而固定。 了、 (3) 接著,相對於以在基準位置之主齒輪」 二齒輪群之主齒輪3_4朝箭號W示的方向旋轉,兩 齒輪的齒在⑴料之處接觸之狀態, 對於基準位置而固定。 .更主w輪3-4相 二 ⑷然後,相對於固定在基準位置之主齒輪% 嚙合齒輪群之嚙合齒輪u、4 使第 形成兩齒輪的齒在(;)所示1 =㈣的方向旋轉, 之處接觸之狀態,然後使唾合齒 320031 30The JUU meshes with the other main gear 3_2, the third gear D, and the 苐-gear group 孓4 of the second gear group. By this, the main voice of the squad is called the main gear of the other side of the wheel group. When the main gear is meshed, the case of the wheel eclipse can prevent the slider or 1 of its main teeth • Match or phase deviation. The degree to which the member will be broken is not the same as the degree of the square gear of the wide-gear group. The main gear train is offset by a predetermined angle with respect to the first gear 丨Π3: Rotary axis...= The main gear 之一 on one side of the wheel group. Thereby, the teeth of the main gear 3-1 that maintains the first tooth ', and the teeth of one of the second gear groups are in contact with each other in the rotational direction, the first gear group ^ another = idiot wheel ^ The tooth of the other gear and the other main gear of the second gear group are in contact with each other in the direction of rotation. Therefore, although there is a gap between the tooth faces of the meshing portion of the main gear and the main gear at the rotation D, it is possible to maintain a state of stable contact between the tooth surfaces of the main gear during the operation of the press machine. In the present case, the 'direction of rotation not only indicates that the drive motor 2 is actually driven in the direction of rotation' but also includes the concept of the opposite direction of the direction of rotation. Hereinafter, the principle of the fourth embodiment described above will be described in more detail with reference to Fig. 9. In Fig. 9, it is assumed that the main gears 3·3, 3·4 of the second gear group and the gray transfer car are 6 9 + The direction of rotation is fixed. With this fixed position as a reference > ° at this time, the main gears 3_3, 3_4 and the rotating shaft 6-2 are combined so that the phases in the mutually twisting directions are not changed. In this case, the main gears 3-3 and 3-4 can have the same shape and size of 22 320031 B53300, and can be connected to the same phase in which the rotation axis 6 has the same phase in the direction of rotation: the group = T is fixed at the reference position. The main gear 3+ rotates in the direction indicated by the first gear ·.:= arrow... to form the state of the two gears, and then the main gear is fixed relative to the base + position. 61 ^ 1 due to the main gear 3 ' 2 The main gear 3_b 3_2 may have the same shape and size with respect to the reference position so as to rotate in the direction indicated by the rotation axis = the number b. 6 i The main gear of the first gear group Μ Fixed to the rotation axis - to make the rotation phase of the main = 主 main gear 。. Specifically, "the rotation axis W fixed to the reference position rotates in the direction of the jin", the teeth forming the two gears are shown in (8) Connected state. In this state, the main gear 3·1 is fixed to the rotating shaft 6-1, and the main gears 3_i, 3_2, 3_3, and 3_4 are all in the rotation direction: the state in which the two relations have been determined. The main gear 丄? 疋 direction position is offset by a predetermined angle with respect to the main gear W. In the above (3), the phase of the first gear group in the direction of the moon can be phased by the phase adjustment mechanism ^^^ (4) Take the second ϋ 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图 图b, c corresponds to the direction, the first 〇A corresponds to the position shown in Figure 9 (B).) 斤不320013 23 1353300 phase adjustment mechanism 27 is the first grooving as shown in Figure i The rotation axis 6-1, :: 29 of the "part" has a gear 3]. And the main = 29 of the first grooving portion 33 is formed such that its sectional area perpendicular to the axial direction is gradually increased from the other. In the first 〇β is a sub-guest to the other point, the 'sub-middle' wedge 29 has a rectangular cross section perpendicular to the virtual f-axis direction, and the side 29a, the length of the bird, and the angle range from one end side to the other end side Angle, angle other than 1 degree. The angle may be such that the first groove portion 3i is formed by the rotation shaft 6-1 and the main tooth portion passing through the rotation shaft 6_; The # square of the I-port rotating shaft 6] is formed in the first grooving portion 31 in the _ "the inner side of the recessed space, facing the main tooth dry 3": the port. This space extends in the circumferential direction of the rotating shaft Μ The predetermined length: the amount of the depression of the two spaces, that is, the area of the space and the half-light direction of the rotating shaft 6-1, is substantially the same in the circumferential direction of the rotating shaft 6_r. The first groove portion 33 is formed by penetrating the main gear 在 at a portion of the main tooth at 3 Λ. The second transfer car is formed on the outer side of the tangential direction of the wheel 3d by the combined main gear of the cymbal and the first grooving portion 33. The recessed space is open on the side. The space of the main gear 3_丨== the amount of recession of the space, that is, the length of the fisherman in this space: the length of the pre-turn. The broken area of this line is in the main 3 The radial direction is flat. The accumulation is substantially the same in the circumferential direction of the main Α. The space formed by the first grooving portion 31 and the space formed by the "" is in the radial direction of the rotating wheel; = = repeated here (4) Inserting the wedge 29. Pressing the wedge 29 in the direction of the first coffee ring d, since the rotating shaft is fixed at the reference position, = 320031 24 1353300 Ϊ = ί teeth 3 "of the arrow towards the Fig 1〇B. The direction of rotation. At this time, the amount of rotation of the main gear 3-1 is determined by the amount of pressing of the wedge 29. In this way, in the operation of the press machine, the teeth of the main gear 3-1 of the VIII, the ganrk, the main gear 3-1 of the music gear group and the main gear 3-3 of one of the second gear groups can be rotated. In the directional contact, the teeth of the other main gear 3-2 of the first gear group are in contact with the other of the second gear group in the rotational direction. In order to maintain the suspicion state, the tooth surface of the main gear 3_b 3_2 of the first-wire group can be applied with a preload (pushing force) on the tooth surfaces of the main gears w and 3 of the second gear group in the rotational direction. At this time, from the one in the basin of the gear group as shown in Fig. 9, one of the teeth of the priest 4, the gear of the third gear 3-1 is only more than the teeth of the second gear group ^9. When the rotation direction is in contact, the wheel and the rotating shaft are elastically deformed, and in the (Fig. 9 (4), 吏: not the contact portions are pressed against each other. In the way of the phantom w tooth surface, the pre-addition negative is applied as 9: As shown in Fig. 11, the rotation axis of the torsion beam is elastically deformed by the 6^/_ direction due to the twisting of the square, and the twist angle is generated. This cymbal shaft 6_2 is also elastically deformed. Tooth surface two: two plus preloading to maintain the above state. At this time, the tooth surface of the tooth: ...-4 is the main gear 1 of the square gear, wherein the tooth of the first gear group is small, and the tooth is only connected with the tooth of the second gear gear 3-3. The feeling of the master of U Wan. That is, it can be avoided to rotate 320031 25 1.353300 The shaft 6-1, 6_2 is twisted. By using the phase adjustment mechanism 27, the main gear 3_ι phase can be adjusted to the predetermined angle at which the main gear 3-2 is displaced in the rotational direction. • The predetermined angle is greater than 0 degrees and is desirably equal to the amount of clearance between the main gears 3-1 and 3-2 to which the first gear group belongs and the main wheel 3 to the second gear group. In this way, it is possible to avoid the rotation of the teeth without rotation = 6.1, 6-2. As described above, according to the fourth embodiment, even if there is a gap between the tooth surfaces of the main gear 盥 main tooth 2 and the nip portion, the state in which the main gear tooth surface is stably contacted can be maintained in the rushing operation. Thereby, the rotational direction position of the main gear is often kept fixed. In other words, the direction of rotation of the main gear does not change the amount of the gap. Therefore, it is possible to prevent the slider 7 from being frequently tilted during the operation of the dust washing machine. For example, even if, for example, the bottom of the slider 7 is dead, the slider 7 can be prevented from tilting, and as a result, the quality of the press-formed product can be improved. In addition, in the case where a plurality of drive motors 2 are used as shown in Fig. 4, the failure of the motor 2 causes the rotational driving force to be transmitted from the drive motor 2 to the first gear = the same gear group becomes different, and the contact is also "dimensional" (four) The posture of the block 7 is horizontal. The attack is followed by a description of another configuration example according to the fourth embodiment. The 12th figure 'the 13th, 14th, and 11th views respectively show another composition of 3 ft" example…. In the following, in the main gear ", it is described that the main tooth: Γ γ Γ is necessary to distinguish between the two main gears have been von King Gear 3. Similarly, left 妒 + λ ^ between the suspect axis, 6-2 It is necessary to distinguish the rotation axis from the rotation axis 6 into the first to third embodiments, and the configuration of the above-mentioned The inner portion of the frame 9 is: the intermediate plate portion 9a of the portion of the .9. The intermediate plate portion % is rotatable::: frame = Γ6. This configuration is the case in the case where the preloading is applied. Torsional torque is generated, but since the main gear 3"a: is fitted on both sides, the twisting torque is generated = I The rotational motion of the main gear 3 is stable. Further, the rigidity of the entire intermediate plate portion 9a and the frame 9 is improved as a whole. ", therefore, the machine's thumb can be made shorter by the length of the intermediate plate portion, so that the length of the beam as the rotation of the rotary yoke is shortened', so that the rigidity is reduced. In the configuration example 1, the mechanism for forming the U-shaped negative may be formed such that the main gear 3 1 is integrated or the two are combined. At this time, the conversion=two zt, for example, the eccentric link mechanism or the four-node link mechanism: when the wheel and the tapping are engaged, the main gear 3 can be rotatably supported by the rotating shaft 6 and can be further " μ is configured to capture the freely rotatable bracket 9. It is formed to fix the rotating shaft 6 to the configuration example 2 of the figure 13 of the machine, and the right face + i 7 < °: the main ω wheel is combined with the main gear, The coupling member 35 extends. The two ends of the coupling member 35 are respectively fixed to the main shaft 3 of the main gear 3, and the main gears 3 are opposite to each other. Therefore, the rotating shaft can be prevented. 6 is generated; moment, °:: 35 combined, renting torque. In particular, applying 320031 27 moments above, 7/匮's brother can prevent or suppress the generation of torsion axis in the rotating shaft 6=:: In the case of 2, the intermediate plate portion % can also be set. At this time, the rotation 35 is combined with the #人##35 of the main gears 3-1, 3-2 of the first gear group, and the coupling member of the first and second rotation gears. Connected to 1. Or replace the rotating shaft 6-1 to form the above-mentioned. The main gear member 35 combined with the second gear group is coupled with the rotating shaft 6 9 . The second configuration or the substitution of the rotation (four) 6_2 to form the a configuration 5 may be formed by integrating the main gear 3 with the transducer portion or the combination of the two. At this time, , the partial rotation mechanism or the four-node linkage mechanism: When transported, the main gear 3 can be rotatably supported, and the rotation shaft 6. The configuration can also be formed into a rotation shaft. 6 is fixed to the frame 9. _ 4th and 14th drawings show the configuration example 3. The fourth drawing is a side sectional view of the pressing machine, and the 14th drawing is the B_B line arrow direction view of the 14th A picture. 14B, the frame 9 and the like are omitted for simplification. In the configuration example 3 of FIGS. 14A and 14B, 'the intermediate plate portion % which is the portion of the frame 9 is formed inside the frame 9. Moreover, each of the above rotations The shaft 6 is divided into two individual rotating shafts 6a and 6b in the intermediate plate portion 9a. In this configuration, since the rotating shaft 6a and the rotating shaft 6b are separated by the intermediate plate portion %, the main gear 3 and the shifting mechanism 5 are The replacement becomes easy, and since the output shafts of the two drive motors 2 are connected by the connecting shafts 14·1, 14·2, 28 320031 P353300 Therefore, the main gear 3 can be stably driven. Further, in the configuration example 3, the first combined gear group is provided. The first meshing gear group has an example of a one-to-one jet gear group and a second mesh. The middle is a coupling shaft ·4·η meshing gear coupling portion (the same pair of meshing gears nq and η_2. χ is connected to the center of rotation of the second spur gear coupling portion (in the 14th image, the meshing gear group has a connection) One of the centers of rotation is the same as the port return wheel U·3 of one of the first meshing gear groups. The gear group is composed of the gears of the 1M fishing rod group A, which makes one of the main gears 3-1 ,, flute - and the first other - square _ gears n_2 and the first tooth: group of :::: 3-2 combination of the wheel group. The main gear of the square gear of one of the second spitting gear sets, the main gear of one of the gear sets, and the second other side (four) of the combined gears ... mesh with the second: two. In addition, the main gear of the other group of the wheel group is fixed to the wheel of the drive motor 2 in the example of the UA and 14B, and the π-valley gear is called, called, 丨丨'', but the gear force is transmitted to the main tooth. I, I * : & The rotation of the moving motor 2 is more: the gear of the main gear 3 of the j. At this time, another pinion gear can be provided on the meshing teeth, and the rotary motor 2 can be transmitted to the main gear 3 via the pinion gear. The power slave drive (4) is configured as an example 3' of the first spit gear group - wherein: the wheel 11-1 is offset by a predetermined angle with respect to the first meshing tooth to the other split gear n_2 in the direction of its rotation direction The Futian link 320031 29 P353300 shaft 14-1 is coupled to the other meshing gear 11-2 of the first meshing gear group. Thereby, the teeth of the main gear 3d of one of the first gear groups and the teeth of the main gear 3·3 of one of the second gear groups are held in contact with each other in the rotational direction, and the other main gear of the first gear group is 3- The teeth of 2 are in contact with the teeth of the other main gear 3-4 of the second gear group in the rotational direction. The principle of the configuration example 3 is the same as that described above with reference to Fig. 9, but it will be described in detail based on Figs. 15 and 15 . The 15th chart is the arrow direction of the a_a line in the 14th picture, and the 15th picture is the arrow direction view of the b-b line in the 14th picture. 〇) The meshing gear Π-2 of the first meshing gear group is interconnected with the connecting shaft 14_1, and is assumed to be stationary in the rotational direction. Use this fixed position as the reference position. (2) The main gear 3-2 of the first gear group is turned toward the direction indicated by the arrow a with respect to the meshing gear 11-2 fixed at the reference position to the + position. The two gears 2 teeth are in a state of contact with (H) and then the main gear is fixed at the reference position. (3) Next, with respect to the main gear 3_4 of the second gear group at the reference position, the main gear 3_4 is rotated in the direction indicated by the arrow W, the teeth of the two gears are in contact with each other at the (1) material, and the reference position is fixed. More main w wheel 3-4 phase two (4) Then, with respect to the main gear % fixed at the reference position, the meshing gears u, 4 of the meshing gear group make the teeth forming the two gears in the direction of 1 = (four) shown by (;) Rotate, where the state of contact, and then make the spit teeth 320031 30

UJJJUO 輪w士相對於基準位置而固定。 此4,由於嚙合齒輪11 -4係連处周^ 及喷合齒輪11_3,因此連 疋至連結軸!4_2 箭號e所示的方ή ° 及嚙合齒輪11-3亦朝 中,第二喃合齒輪群之喷合齒輪u 3、=置而固疋。其 形狀及尺寸,且可U-4可具有相同的 結麵⑹。方向的相位相同之形態連結至連 (5)接著’相對於固定在基準位置之續合齒輪旧,使 弟一齒輪群之主齒輪3_3 兩齒輪的齒在(K)所*之虚油时㈣轉,形成 相對於基準位置而固定。 I然後使主齒輪3-3 -音後’相對於以在基準位置之主齒輪3·3,使第 告I:去之主齒輪3-1朝箭號e所示的方向旋轉,形成兩 的"在(1°所示之處接觸之狀態,然後使主齒輪3]相 對於基準位置而固定。 • (7)最後,使第一嚙合齒輪群之嚙合齒輪11-1固定於 連結抽…1:此固定係調整唾合齒輪11-1的旋轉相位而進 仃。具體而言,使嚙合齒輪相對於固定在基準位置之 連結軸14-1朝箭號f所示的方向旋轉,形成兩齒輪的齒在 (M)所示之處接觸之狀態。 在該狀態,將嚙合齒輪固定於連結軸14_丨,藉此 fb成主齒輪3-1、3-2、3-3、3-4全部在旋轉方向都沒有間 隙且相互的相位關係已經決定之狀態。在此狀態,嚙合齒 輪11-1之旋轉方向相位係相對於嚙合齒輪偏移預定 31 320031 1*353300 的角度。 ‘ 11-4可具有相同 可具有相同的 之嗜合齒輪Uq之相 述的相位調整機構27 其中,嚙合齒輪11-1、11-2、 的形狀及尺寸,主齒輪3_丨、3_2、 形狀及尺寸。 在上述(7)令,第一嚙合齒輪群 對的旋轉方向的相位,可藉由與上 一樣之相位調整機構來調整。 之盆ft施’即可在衝壓機械之運轉中維持第-齒輪群 八中方之主齒輪3·1的齒與第二齒輪群之i中一方之 主齒輪3-3的齒在旋轉方向接觸,第一齒輪群^另 主齒輪3-2的齒與第二齒輪群之另一方 在旋轉方向接觸之狀態。 w輪3-4的齒 3 2的H持該狀態,^使第—齒輪群之主齒輪3-卜 =的齒面在旋轉'方向對.第二齒輪群之主齒輪 齒面施加預加負荷(推屡力),但不施加預加負荷亦可。、 換吕之,利用相位調整機構,可調整嗤合I輪 對於#齒輪H_2在旋射向偏移之上述^目 上述預定的角度係在〇度以上,且希望為鱼第角一度 群所屬之主#輪3和第二.輪群所屬之主㈣3 ; 當之角度。而且,該間隙量包 二。 與主齒輪3之唾合部的間隙量。如此,在主齒輪 合部以及嚙合齒輪η與主齒輪3之 之嚙 齒面間施加預加負荷口。 β在齒面與 結抽一-2發生扭:持齒面間之接觸’因此可避免連 32003] 32 ^亩;&卜日第嗜合盘輪群之其中一方的唾合齒輪11-1可 =接而疋透過其他齒輪而間接地與第—齒輪群之其中一 的主齒:3]唾合,第一喃合齒輪群之另一方的唾合齒 .· ί之另接而是透過其他齒輪而間接地與第一齒輪 .::ΓΓ主齒輪Μ嗜合。同樣的,第二嗜合窗輪群 ⑽㈣合錄11_3可不直接而是透過其他齒輪 而=地與第二齒輪群之其中一方的主齒輪3-3唾合,第 ==群之另一方的唾合*輪…可不直接而是透 =他齒輪㈣接地與第二齒輪群之另— =:此情況也-樣,使其他的構成與先前所述的一樣, Ρ可避免連結轴14·1、14·2發生扭轉。 :外,在構成例3中’可形成為使主齒輪3與變換機 份—體化或使兩者結合之構成(此時,變換機構 輪 j可為例如偏心連桿機構或四節連桿機構之偏心 f棘固時候’可形成為使主齒輪3旋轉自如地支持於 之2 成’亦可再形成為將旋轉轴6固^於機架9 I構成。 第16至18圖係顯示本發明的實施例之圖。其中,第 圖,上橫樑(crown)的正面斷面圖,第η圖係第Μ圖之 線斷面圖,第18圖係第17圖之B_B線斷面圖。 部份G =就與本發明有關聯之上橫樑驅動(⑽㈣把Ve) 向且’在以下的說明中,以輸送線進給方 向為「^」。、以輸运線的正交方向為「左右」、以船直方 320031 33 1-353300 一、-又換機構(四節連桿機構4〇) 採用四節連桿機構40作為變換機構。 二係由偏心圓板4〇a、搖動板儀、限制連桿•連=The UJJJUO wheel is fixed relative to the reference position. In this case, since the meshing gears 11 - 4 are connected to the circumference ^ and the split gear 11_3, they are connected to the connecting shaft! 4_2 The arrow 所示 ° shown by the arrow e and the meshing gear 11-3 are also facing inward, and the spray gear u 3 of the second spur gear group is fixed. Its shape and size, and U-4 can have the same junction (6). The direction of the same phase is connected to the connection (5) and then to the old gear that is fixed at the reference position, so that the teeth of the two gears of the main gear 3_3 of the gear group are in the virtual oil of (K)* (4) The rotation is fixed relative to the reference position. I then rotates the main gear 3-3 - after the 'with respect to the main gear 3·3 at the reference position, causes the first I: the main gear 3-1 to rotate in the direction indicated by the arrow e, forming two "In the state of contact (1°, then the main gear 3] is fixed relative to the reference position. • (7) Finally, the meshing gear 11-1 of the first meshing gear group is fixed to the connection pumping... 1: This fixing system adjusts the rotational phase of the spitting gear 11-1. Specifically, the meshing gear is rotated in the direction indicated by the arrow f with respect to the connecting shaft 14-1 fixed at the reference position to form two The teeth of the gear are in contact with each other at the position indicated by (M). In this state, the meshing gear is fixed to the connecting shaft 14_丨, whereby fb becomes the main gear 3-1, 3-2, 3-3, 3- 4 All of the states in which there is no gap in the direction of rotation and the mutual phase relationship has been determined. In this state, the phase of the rotational direction of the meshing gear 11-1 is offset from the meshing gear by an angle of a predetermined 31 320031 1*353300. 4 may have the same phase adjustment mechanism 27 which may have the same phase of the coincident gear Uq, wherein the meshing gears 11-1, 1 1-2, shape and size, main gear 3_丨, 3_2, shape and size. In the above (7), the phase of the first meshing gear group in the direction of rotation can be the same as the phase adjustment mechanism To adjust, the ft can be used to maintain the teeth of the main gear 3·1 of the first gear group and the main gear 3-3 of the second gear group i in the operation of the press machine. In the directional contact, the teeth of the first gear group and the other main gear 3-2 are in contact with each other in the rotational direction of the second gear group. The H of the teeth 3 2 of the w wheel 3-4 holds the state, and the first The tooth surface of the main gear of the gear group 3-b = in the direction of rotation, the pre-loading (pushing force) is applied to the main gear tooth surface of the second gear group, but the preloading is not applied. The phase adjustment mechanism can be used to adjust the twisting I wheel to the # gear H_2 in the above-mentioned predetermined angle of the rotation direction offset, which is above the twist, and it is desirable to be the main #轮3 of the fish first angle group. And the second. The group to which the wheel group belongs (4) 3; as the angle. Moreover, the amount of the gap is two. The amount of clearance from the salivation portion of the main gear 3 Thus, a preloading port is applied between the main gear engaging portion and the meshing gear η and the tooth surface of the main gear 3. β is twisted at the tooth surface and the knot is -2: the contact between the tooth surfaces is made ' 32003] 32 ^ mu; &pp; the day of the discuzy wheel group one of the salvage gear 11-1 can be connected through other gears indirectly with the first gear of the first gear group: 3 Squeeze, the other side of the first spur gear group is the spit teeth. · ί is connected to the first gear through the other gears indirectly.:: ΓΓ main gear Μ 。. Similarly, the second The coincident window wheel group (10) (4) The joint record 11_3 may not be directly but through other gears = ground and the main gear 3-3 of one of the second gear groups, the === the other party's salivation * wheel... Directly through: other gears (four) grounding and the second gear group - =: This situation is also the same, so that the other components are the same as previously described, Ρ can avoid the twisting of the connecting shafts 14·1, 14·2 . In addition, in the configuration example 3, 'the main gear 3 and the converter may be formed as a body or a combination of the two (in this case, the change mechanism wheel j may be, for example, an eccentric link mechanism or a four-node link) When the eccentricity f of the mechanism is rigid, it can be formed so that the main gear 3 can be rotatably supported at 2', and can be formed to fix the rotating shaft 6 to the frame 9 I. The figures 16 to 18 show the present. BRIEF DESCRIPTION OF THE DRAWINGS In the drawings, the front cross-sectional view of the upper cross member, the n-th image is a cross-sectional view of the second figure, and the 18th is a cross-sectional view taken along line B_B of the 17th drawing. Part G = is associated with the present invention. The beam drive ((10) (4) vs.) and in the following description, the feed line feed direction is "^". The orthogonal direction of the transport line is " Left and right", with boat straight 320031 33 1-353300 I, - change mechanism (four-bar linkage mechanism 4〇) Four-bar linkage 40 is used as the transformation mechanism. The second system is made up of eccentric disc 4〇a, rocking plate , limit the link • even =

Ud所構成。相關的四節連桿機構4〇揭示於例如 特願 2006-293555 ?卢 +。M + _l、 本 入'U 9 冓成,可在調整成形領域 王體發揮南加塵能力,且可抑制成形速度。 ▲在本例中,每一台衝屢機具有對稱配置在前後左右此 計四台之連桿機構(此情況為四節連桿機構4〇卜 /、 藉此,由於四組連桿機構4〇在前後方向及左右方向以Ud is composed. The related four-section linkage mechanism 4〇 is disclosed, for example, in the wish of 2006-293555? M + _l, the original 'U 9 冓, can be used in the field of adjustment and shaping. The king body exerts the south dust-removing ability and can suppress the forming speed. ▲In this example, each punching machine has a four-bar linkage mechanism symmetrically arranged in front, back, left and right (in this case, four-bar linkage mechanism 4〇/, thereby, due to the four sets of linkage mechanisms 4 〇 in the front and rear direction and the left and right direction

兩點以上支持滑塊,因此提高成形負荷偏心之際的滑塊的 安定性。 J 再者,四組連桿機構40係分別在前後方向及左 對稱地動作。 藉此,可防止左右不對稱的慣性力之發生,·使衝壓機 之橫向搖晃減到最小限度。 鲁一、主齒輪42 主齒輪42係在前後方向配置在衝壓機的中央位置。而 且,每一台衝壓機具有左右對稱地各有一個之共計兩個的 主齒輪42。 . 各主齒輪42係與前述偏心圓板40a —體化。 而且,每一個主齒輪具有在前後兩側各有一個之共計 兩個的偏心圓板40a。 藉由此構成,每一台衝壓機可用共計兩個之少個數的 主is/輪42來驅動四組連桿機構4〇,可降低成本。 320031 34 1-353300 三、旋轉轴(主銷44) 相對於左右共兩牧之主齒輪42,支持主齒輪42之主 銷44同樣有左右共兩根。 主銷44的兩端係由設在上橫襟41的前後兩側之主腹 板(main web)41a加以支持而橫架於兩主腹板❺間。 主銷44的前後端部之一係與主腹板❺結合而不能旋 轉。 四、傳動齒輪(小齒輪46) 小齒輪46係設成與部份露出於上橫標41白勺上方之主 齒輪42嗔合。 而且,小齒輪46係藉由安裝在上橫樑上部之罩蓋43 旋轉自如地支持住其兩個部位。罩蓋43_置在上橫襟上 部之框架,具有支持小絲46及覆蓋上㈣上部之機能。 小齒輪46因與齒數多之主齒輪42嗜合,因此 也承擔減速機構之機能。 藉由此構成’可使從馬達45值揀忠μ ‘ ^ . 埂5傳遞來的驅動力有效地減 遠後才傳遞到主齒輪42。 五、馬達安裝部(露出於罩蓋卜 以及馬達設置用的托架48)卜权小齒輪的軸端49、 小齒輪46的軸端49從罩蓋43突出到外側。 ,遠可藉由聯結器47而與馬達轴相結合,承擔 馬達安裝部之機能。 - 上橫樑41安裝有馬逵芎罟 作為要配罟/辟雜!°用的托杀48,此托架48係 作馬要配置在距離上橫拇夕浩, 梁之月"臭方向外側較遠的位置之驅 320031 35 ^53300 動馬達的安裝場所。 ^ 本發明並不限於上述之實施形態,可不脫離本發明的 .範圍而進行變更。 【圖式簡單說明】 -· 第1圖係顯示專利文獻1之衝壓機械的構成之示意圖。 、 第2圖係顯示先前技術中滑塊傾斜之示意圖。 第3A圖係依據本發明第一實施形態之衝壓機械的正 面斷面圖。 _ 第3B圖係第3A圖之B_B線箭號方向視圖。 第4A圖係依據本發明第二實施形態之衝壓機械的正 面斷面圖。 第4B圖係第4A圖之β_Β線箭號方向視圖。 第5A圖係依據本發明第三實施形態之衝壓機械的側 面斷面圖。 第5B圖係第5A圖之B_B線箭號方向視圖。 • 第6圖係顯示本發明第三實施形態的另一構成例之示 意圖。 f 7A圖係顯示本發明第三實施形態之再另—構成例 的側面斷面圖。 帛7B圖係第7A圖之B-B線箭號方向視圖。 第8圖係顯示互相嚙合的主齒輪之斜視圖。 第9圖係用以說明第四實施形態的原理之示意圖。 第1〇A圖係顯示相位調整機構的構成之正面圖。 第10B圖係第10A圖中之虛線部份的放大斜視圖。 320032 36 1353300 第11圖係用以說明發生於旋轉軸的扭轉之示意圖。 第12圖係顯不依據第四實施形態之另外的構成例】 之示意圖。 第13圖係顯示依據第四實施形態之另外的構成例2 之不意圖。 第14A圖係顯示依據第四實施形態之另外的構成例3 之衝壓機械的侧面斷面圖。 第14B圖係第14A圖之B-B線箭號方向視圖。 第15A圖係第14B圖之a-a線箭號方向視圖。 第15B圖係第14B圖之b-b線箭號方向視圖。 第16圖係本發明實施例之上橫樑的正面斷面圖。 第17圖係第16圖之A-A線斷面圖。 ,第18圖係第17圖之B-B線斷面圖。 2、2a、2b 3-1 至 3-4 6、6a、6b 7 滑塊 9a 中間板部 1M至11-4嚙合齒輪 14-1 連結軸 15 馬達安裝構件 18 貫通孔 21 減速機 •主姜元件符號說明】 駆動馬達 主齒輪 旋轉軸 3 主齒輪 5 變換機構 6-1、6-2旋轉軸 9 機架 11 傳動齒輪(小齒輪) 12 馬達安裝部(安裝孔) 14-2 連結軸 17 凸緣部 19 螺絲 27 相位調整機構 320031 37 B53300 29 楔 29a 29b 邊 31 33 第二切槽部 35 40 四節連桿機構 40a 40b 搖動板 40c 40d 驅動連桿 41 41a 主腹板 42 43 罩蓋 44 • 45 馬達 46 47 聯結器 48 49 。轴端 51 53 貫通長孔 55 57 曲轴 59 61 滑塊 θ · 邊 第一切槽部 結合構件 偏心圓板 限制連桿 上橫樑 主齒輪 主鎖 小齒輪 托架 板 螺絲頭 連接桿 扭轉角The slider is supported at two or more points, so the stability of the slider at the time of eccentricity of the forming load is improved. Further, the four sets of link mechanisms 40 are symmetrically operated in the front-rear direction and the left side, respectively. Thereby, the occurrence of the inertial force of the left and right asymmetry can be prevented, and the lateral shaking of the press can be minimized. Luyi, main gear 42 The main gear 42 is disposed at the center of the press in the front-rear direction. Further, each of the press machines has a total of two main gears 42 each having a left-right symmetry. Each of the main gears 42 is integrally formed with the aforementioned eccentric disk 40a. Further, each of the main gears has an eccentric disk 40a having a total of two on each of the front and rear sides. With this configuration, each of the presses can drive the four sets of link mechanisms 4 with a total of two fewer main iss/wheels 42 to reduce the cost. 320031 34 1-353300 III. Rotary shaft (main pin 44) The main pin 44 supporting the main gear 42 has two or so of the main pin 44 of the main gear 42 with respect to the left and right main gears 42. Both ends of the king pin 44 are supported by a main web 41a provided on the front and rear sides of the upper cross 41 and are transversely framed between the main webs. One of the front and rear ends of the king pin 44 is coupled to the main web 而 and cannot be rotated. 4. Transmission Gear (Pinlet 46) The pinion 46 is coupled to the main gear 42 partially exposed above the upper cross-section 41. Further, the pinion gear 46 rotatably supports the two portions thereof by the cover 43 attached to the upper portion of the upper beam. The cover 43_ is placed on the upper frame of the upper cross-body and has functions of supporting the wire 46 and covering the upper portion of the upper portion. Since the pinion 46 is in contact with the main gear 42 having a large number of teeth, it also assumes the function of the speed reduction mechanism. By this configuration, the driving force transmitted from the motor 45 value loyalty μ ^ ^ 埂 5 can be effectively reduced and then transmitted to the main gear 42. 5. The motor mounting portion (exposed to the cover 48 and the bracket 48 for motor setting), the shaft end 49 of the weight pinion, and the shaft end 49 of the pinion 46 protrude from the cover 43 to the outside. It can be combined with the motor shaft by the coupling 47 to assume the function of the motor mounting portion. - The upper beam 41 is fitted with a stirrup. ° Use the killing 48, this bracket 48 is the horse to be placed in the distance of the distance to the end of the night, the beam of the moon " the direction of the outside of the stinky drive 320031 35 ^ 53300 motor installation site. The present invention is not limited to the embodiments described above, and may be modified without departing from the scope of the invention. BRIEF DESCRIPTION OF THE DRAWINGS - Fig. 1 is a schematic view showing the configuration of a press machine of Patent Document 1. Fig. 2 is a schematic view showing the tilt of the slider in the prior art. Fig. 3A is a front sectional view showing a press machine according to a first embodiment of the present invention. _ Figure 3B is a view of the arrow direction of the B_B line in Figure 3A. Fig. 4A is a front sectional view showing a press machine according to a second embodiment of the present invention. Fig. 4B is a view of the arrow direction of the β_Β line in Fig. 4A. Fig. 5A is a side sectional view showing a press machine according to a third embodiment of the present invention. Fig. 5B is a view of the arrow direction of the B_B line in Fig. 5A. Fig. 6 is a view showing another configuration example of the third embodiment of the present invention. Fig. 7 is a side sectional view showing still another configuration example of the third embodiment of the present invention.帛7B is a view of the arrow direction of the B-B line in Figure 7A. Figure 8 is a perspective view showing the intermeshing main gears. Figure 9 is a schematic view for explaining the principle of the fourth embodiment. Fig. 1A is a front view showing the configuration of the phase adjustment mechanism. Fig. 10B is an enlarged perspective view of a broken line portion in Fig. 10A. 320032 36 1353300 Figure 11 is a schematic diagram illustrating the torsion occurring on the rotating shaft. Fig. 12 is a schematic view showing another configuration example not according to the fourth embodiment. Fig. 13 is a view showing another configuration example 2 according to the fourth embodiment. Fig. 14A is a side sectional view showing a press machine according to another configuration example 3 of the fourth embodiment. Figure 14B is a view of the direction of the arrow B-B of Figure 14A. Fig. 15A is a view of the arrow direction of the a-a line of Fig. 14B. Figure 15B is a view of the arrow direction of the b-b line of Fig. 14B. Figure 16 is a front cross-sectional view of a beam above the embodiment of the present invention. Figure 17 is a cross-sectional view taken along line A-A of Figure 16. Figure 18 is a cross-sectional view taken along line B-B of Figure 17. 2, 2a, 2b 3-1 to 3-4 6, 6a, 6b 7 Slider 9a Intermediate plate portion 1M to 11-4 meshing gear 14-1 Connecting shaft 15 Motor mounting member 18 Through hole 21 Reducer • Main ginger element Explanation of Symbols] Tilting motor main gear rotating shaft 3 Main gear 5 Conversion mechanism 6-1, 6-2 Rotary shaft 9 Rack 11 Transmission gear (pinion) 12 Motor mounting part (mounting hole) 14-2 Connecting shaft 17 Flange Part 19 Screw 27 Phase adjustment mechanism 320031 37 B53300 29 Wedge 29a 29b Edge 31 33 Second slotted section 35 40 Four-bar linkage 40a 40b Shake plate 40c 40d Drive link 41 41a Main web 42 43 Cover 44 • 45 Motor 46 47 coupler 48 49 . Shaft end 51 53 Through hole 55 57 Crankshaft 59 61 Slider θ · Edge All groove joints Eccentric discs Limiting link Upper beam Main gear Main lock Pinion Bracket Plate Screw head Connecting rod Torsion angle

38 32003138 320031

Claims (1)

J353300 _ 第97108455號專利申請案 . 100年6月27日修正替換頁 十、申請專利範圍: 1. 一種衝壓機械,其係具備有用來進行衝壓之驅動馬達、 接受該驅動馬達的旋轉驅動力之第一齒輪群及第二齒 輪群、將該第一齒輪群及第二齒輪群的齒輪旋轉運動變 ' 換為往復運動之變換機構、以及連結至該變換機構而往 復運動之滑塊,且藉由固定至該滑塊之模具來進行衝壓 者,其特徵在於. 第一齒輪群係具有由第一連結部加以連結使旋轉 # 中心成為相同之一對主齒輪,第二齒輪群係具有由第二 連結部加以連結使旋轉中心成為相同之一對主齒輪, 第一齒輪群之其中一方的主齒輪係與第二齒輪群 之其中一方的主齒輪嚙合,第一齒輪群之另一方的主齒 輪係與第二齒輪群之另一方的主齒輪嚙合, 第一齒輪群之其中一方的主齒輪係以旋轉方向位 置相對於第一齒輪群之另一方的主齒輪偏移預定角度 β 之方式,藉由第一連結部而連結至第一齒輪群之另一方 的主齒輪,藉此,維持第一齒輪群之其中一方的主齒輪 的齒與第二齒輪群之其中一方的主齒輪的齒在旋轉方 向接觸,第一齒輪群之另一方的主齒輪的齒與第二齒輪 群之另一方的主齒輪的齒在旋轉方向接觸之狀態。 -2. —種衝壓機械,其係具備有用來進行衝壓之驅動馬達、 • 接受該驅動馬達的旋轉驅動力之第一齒輪群及第二齒 輪群、將該第一齒輪群及第二齒輪群的齒輪旋轉運動變 換為往復運動之變換機構、以及連結至該變換機構而往 39 320031修正版 •1353300 - 第97108455號專利申諳案 - 100年6月27日修正替換頁 . 復運動之滑塊,且藉由固定至該滑塊之模具來進行衝壓 者,其特徵在於: . 第一齒輪群及第二齒輪群係分別具有一對主齒 . 輪,且第一齒輪群之其令一方的主齒輪係與第二齒輪群 之其中一方的主齒輪嚙合,第一齒輪群之另一方的主齒 輪與第二齒輪群之另一方的主齒輪嚙合, 此外還具備有第一嚙合齒輪群及第二嚙合齒輪群, 第一嚙合齒輪群係具有由第一嚙合齒輪連結部加 _ 以連結使旋轉中心成為相同之一對嚙合齒輪,第二嚙合 齒輪群係具有由第二嚙合齒輪連結部加以連結使旋轉 中心成為相同之一對喃合齒輪, 且第一嚙合齒輪群之其中一方的嚙合齒輪係直接 或間接地與第一齒輪群之其中一方的主齒輪嚙合,第一 喻合齒輪群之另一方的嚙合齒輪係直接或間接地與第 一齒輪群之另一方的主齒輪0i合, φ 第二嚙合齒輪群之其中一方的嚙合齒輪係直接或 間接地與第二齒輪群之其中一方的主齒輪嚙合,第二嚙 合齒輪群之另一方的嚙合齒輪係直接或間接地與第二 齒輪群之另一方的主齒輪0i合, 且第一嚙合齒輪群之其中一方的嚙合齒輪係以旋 • 轉方向位置相對於第一嚙合齒輪群之另一方的嚙合齒 輪偏移預定角度之方式,藉由第一嚙合齒輪連結部而連 結至第一嚙合齒輪群之另一方的嚙合齒輪,藉此,維持 第一齒輪群之其中一方的主齒輪的齒與第二齒輪群之 40 320031修正版 .1353300 - 第97108455號專利申請案 100年6月27曰修正替換頁 . 一方的主齒輪的齒在旋轉方向接觸,第一齒輪群之另一 方的主齒輪的齒與第二齒輪群之另一方的主齒輪的齒 在旋轉方向接觸之狀態。J353300 _ Patent No. 97108455 Patent No. 97108455 Revision No. 10, Patent Application Range: 1. A stamping machine having a driving motor for punching and receiving a rotational driving force of the driving motor a first gear group and a second gear group, a gear changer that converts a gear rotation motion of the first gear group and the second gear group into a reciprocating motion, and a slider that reciprocates by being coupled to the conversion mechanism, and borrows A stamper is formed by a mold fixed to the slider, wherein the first gear group has a first coupling portion coupled such that a center of rotation # is the same as a pair of main gears, and a second gear group has a The two connecting portions are coupled such that the center of rotation becomes one of the same pair of main gears, and one of the main gear trains of the first gear group meshes with the main gear of one of the second gear groups, and the other main gear of the first gear group And meshing with the other main gear of the second gear group, wherein the main gear train of one of the first gear groups is in a rotational direction position relative to the first gear group The main gear of one of the first gear sets is coupled to the other main gear of the first gear group so that the main gear of one of the first gears is shifted by a predetermined angle β, thereby maintaining the teeth of the main gear of the first gear group. The teeth of the main gear of one of the two gear groups are in contact with each other in the rotational direction, and the teeth of the other main gear of the first gear group and the teeth of the other main gear of the second gear group are in contact with each other in the rotational direction. -2. A press machine comprising: a drive motor for performing press, a first gear group and a second gear group that receive a rotational driving force of the drive motor; and the first gear group and the second gear group The gear rotation motion is converted into a reciprocating motion conversion mechanism, and is coupled to the conversion mechanism to 39 320031 revision version. • 1353300 - Patent No. 97108455 - Amendment page of June 27, 100. And the puncher is fixed by the mold fixed to the slider, wherein: the first gear group and the second gear group respectively have a pair of main teeth. The wheel and the first gear group have one side The main gear train meshes with the main gear of one of the second gear groups, and the other main gear of the first gear group meshes with the other main gear of the second gear group, and further includes a first meshing gear group and a second meshing gear group, the first meshing gear train has a first meshing gear coupling portion coupled to connect the rotating center to be the same pair of meshing gears, and the second meshing gear group has The two meshing gear connecting portions are coupled such that the center of rotation becomes the same pair of pinch gears, and the meshing gear of one of the first meshing gear groups directly or indirectly meshes with the main gear of one of the first gear groups, The other meshing gear of the first gear group is directly or indirectly combined with the other main gear 0i of the first gear group, and the meshing gear of one of the second meshing gear sets is directly or indirectly connected to the second The main gear of one of the gear sets meshes, and the other meshing gear of the second meshing gear group is directly or indirectly coupled with the other main gear 0i of the second gear group, and one of the first meshing gear sets The meshing gear is coupled to the other of the first meshing gear sets by the first meshing gear coupling portion in such a manner that the rotational/rotational direction position is offset by a predetermined angle with respect to the other meshing gear of the first meshing gear group a gear, whereby the teeth of the main gear of one of the first gear groups are maintained and the second gear group is 40 320031 modified version. 1353300 - No. 97108455 Application No. June 27, pp. 27, revised replacement page. The teeth of one of the main gears are in contact in the direction of rotation, the teeth of the other main gear of the first gear group and the teeth of the other main gear of the second gear group are The state of contact in the direction of rotation. 41 320031修正版41 320031 revision
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BRPI0807916A2 (en) 2014-06-24
DE112008000462T5 (en) 2010-02-11

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