次、發明說明： 技術領域】 【發明所屬 發明背景 1. 發明的領域 5 本發明係與機械壓機有關。 C先前技術2 2. 相關技藝的描述 在習知技藝的典型機械壓機中，一曲柄軸之偏心 部件8a和一滑動件3係如第1〇圖所示與一連桿23 1〇連接。一調整螺釘桿24係被提供在連桿23與滑動 件3之間以調整該滑動件。在習知技藝的這個具體例 中’連和· 23與存在可以避免曲柄轴和滑動件3之間 的距離縮短’而使得機械壓機因為距離較高而變的較 1¾的。 15 一沒有連桿的機械壓機係被揭示於尚未審查的 專利公開案第S55-48500號中。既然在該具體例申沒 有連桿’該機器的兩度可以降低，但是其無法提供一 用於滑動調整之螺釘桿，而使得機械壓機在衝壓操作 中非常不方便。 *° 習知技藝的另一具體例係被揭示在未審查的專 利公開案第H06-269996號中。如該公開案的第5圖 所示’其包含有：裝設在曲柄軸之偏心部件上之一襯 套和一滑動件塊；可滑動地包含有滑動塊的連桿；與 '提供在一頂點中之導轴襯以在向上與向下的方向上 5 1328506 導引一連桿，雖然連桿和一滑動件係藉著一鑄模高度 調整機構來連接》 依據該習知技藝，因為連桿係如前述的於該頂點 中被導引，所以滑動件無法提昇比該導引部件更高 5處。換句話說’該機器的高度無法更進一步縮短。 習知技藝的另一具體例係被揭示於未審查之專 利公開案第S57-14499號中。如該公開案的第圖所 示’ 一導引板係被導引件所導引。因此，一個滑動件 無法尚於邊導引件’所以曲柄轴和滑動件之間的距離 10 無法被縮短。因此’縮短機器的高度是困難的。 如上述所提，在所有的這些習知技藝中，如果其 使用了連桿或類似的東西要縮短機器高度是困難的。 另一方面，可以被製成較短高度之機器在衝壓作業中 係不方便的。 15 本發明係要提供不需犧牲壓機作業的便利性，就 可以架構之在向度上較短的機械壓機，同時提供穩定 性和長使用壽命的功效。 t發明内容；3 本發明係具有提供在一調整構件之上的一導引 20機構’其係用於將曲柄軸的偏心部件之迴轉運動轉換 成一往復式直線運動的機構、一被提供在下面的位置 調整機構與一用於導引並避免該調整構件相對於該滑 動件轉動之裝置。 6 XJ^^〇6 更明碟地說，如申請專利範圍第χ項的發明提 供：一調整構件’其上具有導引機構，其係用於將曲 柄軸的偏心部件之迴轉運動轉換成一與該機械壓機的 滑動件相對之往復式直線運動的機構；一被提供在該 5調整構件之下的位置調整機構，其係用於將調整構件 則推或縮回；與一用於導引並避免該調整構件相對於 該滑動件轉動之裝置。 10 15 除了如申請專利範圍第i項的特徵之外，在申 請專利範圍第2項的發明中，該用於導引與避免該調 整構件相對於該滑動件轉動之裝置使用了 _球形構 件，該球形構件係由一球形部件與一平面部件所組 成。除了如申請專利範圍第2項的特徵之外，在如申 :專利範圍第3項的發明中，提供了一對球形構件與 一導引平面，每個球形構件的該平面部件係與該導引 平面接觸並彼此形成一角度。 除了申請專利範圍第3項的特徵之外，在申& 專利範圍第4項的發明中包含有該導引平面之滑塊， 該導引平面具有在曲柄抽的偏心部件之 p I 乃问中的 調整之位置。除了如申請專利範圍 20竹今从 一飞4項的特 徵之外，在申請專利範圍第5項的發 忑球形部 件係與調整構件所提之凹入球形表面嚙合，且其之·， 面部分係以可滑動地的方式架構在引導平面之内。 除了申請專利範圍第3或4項的特徵之外，在 申請專利範圍第6項的發明中’該球形構件係與一接 7 收構件的凹入球形表 V表面嚙合，且该平面部分係以可滑 動地的方式架構在彳丨導平 宜' . 守卞卸乙円除了申睛專利範圍 5 或4項的特徵之外，在申請專利範圍第7項的 發明中’該球形構件係被附接至該調整構件並且係 以一帽蓋架構在該球形部件上。 至7項之外，在本案申 ’該滑塊的位置係可藉由 除了申請專利範圍第4 °月專利範圍第8項的發明中 。亥偏心銷的方式來調整。 圖式簡要說明 第1圖係為本發明的機械壓機之一正視圖和部 分剖面圖； 第 圖係為第1圖的機械壓機的左視圖與部分 剖面圖； 第3圖是本發明的連接構件之透視圖； 第4圖是該連接構件的放大圖； 第5圖是另一個具體例的頂視圖和部分剖面圖； 第6圖是該連接構件之另一具體例的頂視圖和 部分剖面圖； 第7圖是球形構件的第二具體例； 第8圖是球形構件的第三具體例； 第9圖是該偏心銷的概略圖；和 第10圖是具有一連桿的習知技藝之機械壓機的 正視圖》 C實施冷式j 1328506 具體的詳細說明 在第1圖中，一提供在機械壓機1的框架2上 之滑動件3係可上下自由地移動，且一承樑4係面 對滑動件3地固定在一框架2上。一振動預防裝置5 係被固疋在框架2的下端，以將機械壓機的振動與機 器的基座相隔離。 滑動件3係被導引以藉由滑動導引件is的方 式上下地相對於框架2運動*滑動件3係由一平衡 器25懸垂。平衡器25係由一汽缸所組成，並且平 10衡滑動件3的重量以及固定至滑動件3的底部之一 上鑄模的重量。 在第2圖中’曲柄轴8係由框架2支持。曲 柄軸8係可旋轉地由框架2所提供之軸承所支持，並 且係被架構成在相對於框架2之前後方向中。 15 一主要傳動機構9係被固定至曲柄軸8。另一 方面，飛輪11係可旋轉地提供在框架2 _。飛輪u 包含有一離合器-煞車且其係被一馬.達（未顯示）所旋 轉驅動。一小齒輪傳動機構10係被形成在一軸上， 在該軸上具有該離合器_煞車β小齒輪傳動機構⑺係 20 與該主要傳動機構9嚙合。 曲柄軸8係由一驅動機構所驅動，其包含有一 馬達、飛輪11、該離合器-煞車、小齒輪傳動機構1〇與 主要傳動機構9。因為飛輪η具有一相對較大的直 徑’其係被架構成與曲柄轴8大約相同的高度中因 9 1328506 而框架2的高度（也就是機械壓機i的高度）可以 被縮短。 參照第3圖和第4圖’-調整構件12和其之 鄰近區域係被更詳細地描述。降楚 除了第3圖是一個透視 圖以外，其係與第4圖類似。滑動件3僅部份地顯 不在第3圖中，這兩個圖式都顯示曲柄角度為⑽。， 滑動件3位在下死點之系統。 10 一滑動導引機構6與-位置調整機冑7係一體 化地提供。滑動機構6係被提供在調整構件12、之上 面而位置調整機構7係被提供在下面。調整構件12 :被一經過間隔器15以螺拾固定之帽蓋13所覆 蓋0調整構件12、間隔琴 &益15，15的與帽蓋13成為一 甲央具有一空間的框架。 15 該空間收納曲柄# 8的偏心部# “、一上 塊16和一下滑動塊17。上 ’月 俾八& 呢16和下滑動塊17 =別與偏心部件8&上下連結，同時上_塊16可 dl 13自由地滑動，且下滑動塊17可相對 滑動塊 由地滑動。滑動導引機構6係由上 2〇 動塊U、下滑動塊17、調整構件 間隔器15等等所組成。 帽盖& C16和下滑動塊17係橫向於框架移 開型二塊16和下滑動· 17會構成-所謂的分 塊。該分開型滑動塊具有不需螺拾空間的功 10 ^28506 2 l累拾係用於將上和下滑動塊結合，因此每個滑 塊可以變窄，而滑動塊進出之間隙可以減半等等。 5 -螺紋桿12a係在調整構件12下端形成 ^21係被安裝至㈣桿係以可以自由 旋轉i_疋會在垂直的方向中收縮的方式裝設在滑動 3内。螺帽21係以-…2固持至滑動件3β 蜗輪20係被形成在螺帽21的外側上。蜗輪 2〇係與—在滑動# 3中可旋轉地提供的螞桿轴19 10 嚙合。蝸桿19係被—馬達（未顯示）驅動而旋轉。螺 紋桿 12a、螺帽 、 磲帽盖21、蝸輪2〇、蝸桿軸19等會構 成—位置調整機構7,其係對應於傳統的滑動件調整 機構。 15 這個具體例的位置調整機冑7使用一螺紋機 構’但是其也可以由液壓構件所構成。換句話說，盆 可以被架構成在調整構# 12的下方提供一液壓缸:、 以藉由調整油量方式相對於滑動# 3移動調整構件 12。或者，—逐漸尖細的滑塊可被提供在調整構件η 之下，以相對於滑動件3移動調整構件U。 20 在第4圖中，在旋轉蝎桿軸19時，蝸輪和 螺帽21會旋轉以藉著螺紋機構上下地舉昇調整的構 件12。因此，調整構件12能相對於滑動彳3向前 和向後移動。 調整構件12係藉由一導引裝置來避免意外轉 動。換句話說，該導”裝置係具有在壓機操作期間避 11 免由調整構件12的旋轉所引起的滑動件調整量 變的功能。 勒件調整！之改 在第4圖和第5圖中，一滑堍9 滑動件3的導引孔"“ 係被建構在 與螺检29 内。滑塊27係藉由偏心销28 在滑塊=定至滑動件3。_球形構件％係位 和調整構件12之間。球形構件26係由 Γ::件與-平面部件所組成，並且形成一球形： :二球形構件26的高度是大約球體直徑的30%。 10 孔”件26係被容納在調整料12所具有的球形 八且该平面部分係與滑塊27接觸。滑塊27且 有一導引平面。 /、 15 在這-個具體例中，由在滑塊27與—對球形構 典6的平面之間的接觸所形成的角度“是η。。。由 作7彻1丨來看角度α I凸出的。這個角度係以 立在調整構件12上之偏心負載來選擇。其係依據 上 1和右側方向的偏心負載會比前側與後側方向 大如果^疋120。，依據三角函數的關係其之投 ’面積比是/ 3: 1 ’換句話說大約為i 7: i。 20 ’月塊27的位置可藉由在前進和後退方向上（曲 柄輛^的偏心部分8a的轴向方向）調整偏心銷Μ 來調即。滑塊27係在相對於上和下滑動塊16和η ㈣別是滑動塊η)的前進和後退方向上調整，以調節 調正構件12料引平面之頓斜度。換句話說，其係 1確定曲柄轴3的偏心部件8a之外部周圍與該下 12 1328506 滑動塊17之内部周圍以及該下滑動塊17之底部表 面與調整構件12的水平面（頂部表面）係分別接觸。 因為調整構件12係藉由螺紋桿12a而固定至 該滑動件3，滑塊27的向前方和向後調整會使得調 整構件12的水平表面（頂部表面）對應地向前和向 後傾斜。 10 在第9圖中，在偏心銷28左端上之圓筒形部 分，係在中心上相對於該圓筒形部分以一值"e”偏離 中心。藉由些微地鬆開螺拴29，將特殊工具與扭轉孔 35嚙合並以箭號B的方向旋轉偏心器銷28，滑塊 27會以方向A移動。在調整滑塊27之後，螺栓μ 係被鎖緊以使滑塊27固定至滑動件3。 第6圖顯示另一個具體例且係對照於上述第$ 圖。在第5圖的情況中’一對球形的構件％的導引 15面會形成角度"，其由滑塊—側來看是凸出的。 另一方面，在第6圖的情況下—角《0董十應於由滑 塊3〇和31 一側來看係為凸出的角度α。結果，調 整構件12，㈣面係朝向滑塊％ _ μ ^ 20 滑塊27的情況下，滑塊3〇和3ι 銷28來調整。 ’、。糟由一偏心 第7圖和第8圖顯示球形構件％BACKGROUND OF THE INVENTION 1. Field of the Invention 1. Field of the Invention 5 The present invention relates to a mechanical press. C Prior Art 2 2. Description of Related Art In a typical mechanical press of the prior art, a eccentric member 8a of a crankshaft and a slider 3 are coupled to a link 23 1〇 as shown in Fig. 1 . An adjustment screw lever 24 is provided between the link 23 and the slider 3 to adjust the slider. In this specific example of the prior art, the "and the 23 can be prevented from shortening the distance between the crankshaft and the slider 3" causes the mechanical press to be relatively larger due to the higher distance. A mechanical press without a connecting rod is disclosed in the unexamined patent publication No. S55-48500. Since there is no link in this specific example, the machine can be lowered twice, but it cannot provide a screw rod for sliding adjustment, which makes the mechanical press very inconvenient in the punching operation. Another specific example of the prior art is disclosed in Unexamined Patent Publication No. H06-269996. As shown in Fig. 5 of the publication, 'they include: a bushing and a slider piece mounted on the eccentric member of the crankshaft; a link slidably including the sliding block; The guide bushing in the apex guides a link in the upward and downward directions 5 1328506, although the connecting rod and a sliding member are connected by a mold height adjusting mechanism according to the prior art, because the connecting rod The guide is guided in the apex as described above, so the slider cannot be lifted five places higher than the guide member. In other words, the height of the machine cannot be further shortened. Another specific example of the prior art is disclosed in Unexamined Patent Publication No. S57-14499. As shown in the figure of the publication, a guide plate is guided by the guide. Therefore, one slider cannot be attached to the side guides' so that the distance 10 between the crankshaft and the slider cannot be shortened. Therefore, it is difficult to shorten the height of the machine. As mentioned above, in all of these conventional techniques, it is difficult to shorten the height of the machine if it uses a connecting rod or the like. On the other hand, machines that can be made into shorter heights are inconvenient in the stamping operation. 15 The present invention provides a mechanical press that is shorter in orientation than the convenience of the press operation, while providing stability and long service life. SUMMARY OF THE INVENTION The present invention has a guide 20 mechanism provided on an adjustment member for converting a rotary motion of an eccentric member of a crankshaft into a reciprocating linear motion, one of which is provided below The position adjustment mechanism and a means for guiding and avoiding rotation of the adjustment member relative to the slider. 6 XJ^^〇6 More specifically, the invention according to the scope of the patent application provides: an adjusting member having a guiding mechanism for converting the rotary motion of the eccentric member of the crankshaft into a a mechanism for the linear movement of the slider of the mechanical press relative to the reciprocating linear motion; a position adjustment mechanism provided below the 5 adjustment member for pushing or retracting the adjustment member; And the means for rotating the adjustment member relative to the slider is avoided. 10 15 In addition to the features of the item i of the patent application, in the invention of claim 2, the means for guiding and avoiding the rotation of the adjustment member relative to the slider uses a spherical member, The spherical member is composed of a spherical member and a planar member. In addition to the features of claim 2, in the invention of claim 3, a pair of spherical members and a guiding plane are provided, the planar member of each spherical member being associated with the guiding member The lead planes are in contact and form an angle with each other. In addition to the features of claim 3, the invention of claim 4 includes the slider of the guiding plane having the eccentric component of the crank pumping. The position of the adjustment in the middle. In addition to the features of the patent application scope 20, the hairpin spherical member of the fifth application of the patent application scope is engaged with the concave spherical surface of the adjustment member, and the surface portion thereof It is slidably embedded within the guiding plane. In addition to the features of claim 3 or 4, in the invention of claim 6 'the spherical member is engaged with the concave spherical surface V surface of the receiving member, and the planar portion is The structure of the slidable method is suitable for the guidance of the ' ' .. In addition to the features of the patent scope 5 or 4, the spherical member is attached to the invention of claim 7 Attached to the adjustment member and attached to the spherical member with a cap. In addition to the item 7, the position of the slider in the present application can be obtained by the invention of the eighth item of the patent range 4th. Hai eccentric pin way to adjust. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a front view and a partial cross-sectional view of a mechanical press of the present invention; FIG. 3 is a left side view and a partial cross-sectional view of the mechanical press of FIG. 1; Fig. 4 is an enlarged view of the connecting member; Fig. 5 is a top view and a partial cross-sectional view of another specific example; Fig. 6 is a top view and a portion of another specific example of the connecting member Fig. 7 is a second specific example of the spherical member; Fig. 8 is a third specific example of the spherical member; Fig. 9 is a schematic view of the eccentric pin; and Fig. 10 is a conventional example having a connecting rod Front view of the mechanical press of the art" C implementation of the cold type j 1328506 Detailed detailed description In the first figure, a slider 3 provided on the frame 2 of the mechanical press 1 is freely movable up and down, and a bearing The beam 4 is fixed to a frame 2 facing the slider 3. A vibration prevention device 5 is fixed to the lower end of the frame 2 to isolate the vibration of the mechanical press from the base of the machine. The slider 3 is guided to move up and down relative to the frame 2 by means of the slide guides i. The slider 3 is suspended by a balancer 25. The balancer 25 is composed of a cylinder and weighs the weight of the slider 3 and the weight of the mold fixed to one of the bottoms of the slider 3. In Fig. 2, the crankshaft 8 is supported by the frame 2. The crank shaft 8 is rotatably supported by bearings provided by the frame 2, and is framed in a front-rear direction with respect to the frame 2. A primary transmission mechanism 9 is fixed to the crankshaft 8. On the other hand, the flywheel 11 is rotatably provided in the frame 2_. The flywheel u contains a clutch-brake and its drive is rotated by a horse (not shown). A pinion gear mechanism 10 is formed on a shaft having the clutch _ brake β pinion gear mechanism (7) 20 engaged with the main transmission mechanism 9. The crankshaft 8 is driven by a drive mechanism comprising a motor, a flywheel 11, a clutch-brake, a pinion drive mechanism 1 and a main transmission mechanism 9. Since the flywheel η has a relatively large diameter 'the frame is constructed to be approximately the same height as the crankshaft 8 by 9 1328506 and the height of the frame 2 (i.e., the height of the mechanical press i) can be shortened. Referring to Figures 3 and 4', the adjustment member 12 and its adjacent regions are described in more detail. In addition to Figure 3, which is a perspective view, it is similar to Figure 4. The slider 3 is only partially shown in Fig. 3, both of which show a crank angle of (10). , the slider 3 position in the bottom dead center system. A slide guide mechanism 6 is provided integrally with the position adjuster 胄7. The slide mechanism 6 is provided on the upper surface of the adjustment member 12, and the position adjustment mechanism 7 is provided below. The adjusting member 12 is covered by a cap 13 which is screwed and fixed by a spacer 15 to cover the adjusting member 12, the spacers 15, and the caps 13 and the cap 13 have a frame having a space. 15 This space accommodates the eccentric portion of the crank #8 #", one upper block 16 and the lower sliding block 17. Upper 'Monthly eight' & 16 and lower sliding block 17 = not connected with the eccentric part 8 & The block 16 is slidably slidable 13 and the lower sliding block 17 is slidable relative to the sliding block. The sliding guide mechanism 6 is composed of an upper 2 turbulent block U, a lower sliding block 17, an adjustment member spacer 15, and the like. The cap & C16 and the lower sliding block 17 are transverse to the frame-moving type two blocks 16 and the lower sliding plate 17 will constitute a so-called block. The split type sliding block has the work of not requiring a screwing space 10 ^ 28506 2 l is used to join the upper and lower sliding blocks, so each slider can be narrowed, and the gap between the sliding blocks can be halved, etc. 5 - The threaded rod 12a is formed at the lower end of the adjusting member 12 It is mounted to the (4) rod system so that it can be freely rotated and the i_疋 will be contracted in the vertical direction. The nut 21 is held by -...2 to the slider 3β. The worm gear 20 is formed in the snail. On the outer side of the cap 21. The worm gear 2 is tied with the lance shaft 19 10 rotatably provided in the slide #3 The worm 19 is driven to rotate by a motor (not shown). The threaded rod 12a, the nut, the cymbal cap 21, the worm wheel 2, the worm shaft 19, etc., constitute a position adjustment mechanism 7, which corresponds to the conventional sliding. The adjustment mechanism of the piece. 15 The position adjustment mechanism 7 of this specific example uses a threaded mechanism 'but it may also be constituted by a hydraulic member. In other words, the basin may be constituted by a frame to provide a hydraulic cylinder below the adjustment structure #12: The adjustment member 12 is moved relative to the slide #3 by adjusting the amount of oil. Alternatively, a gradually tapered slider may be provided under the adjustment member η to move the adjustment member U relative to the slider 3. In Fig. 4, when the mast shaft 19 is rotated, the worm wheel and the nut 21 are rotated to lift the adjusted member 12 up and down by the screw mechanism. Therefore, the adjusting member 12 can move forward and backward with respect to the sliding jaw 3. The adjusting member 12 is prevented from accidentally rotating by a guiding device. In other words, the guiding device has a function of avoiding the amount of adjustment of the slider caused by the rotation of the adjusting member 12 during the operation of the pressing machine. Thrill adjustment! In the 4th and 5th drawings, the guide hole of a slider 9 slider 3 is constructed in the thread check 29. The slider 27 is fixed by the eccentric pin 28 in the slider = To the slider 3. Between the spherical member % ties and the adjustment member 12. The spherical member 26 is composed of a Γ::-and-planar member and forms a spherical shape: the height of the two spherical members 26 is approximately the diameter of the sphere 30% of the 10 hole" member 26 is housed in the spherical shape eight of the adjustment material 12 and the planar portion is in contact with the slider 27. The slider 27 has a guiding plane. /, In this specific example, the angle formed by the contact between the slider 27 and the plane of the spherical structure 6 is "n....the angle α I is seen by 7 丨1丨This angle is selected by the eccentric load standing on the adjusting member 12. The eccentric load according to the upper 1 and the right direction is larger than the front side and the rear side if it is 120. According to the trigonometric function Its investment 'area ratio is / 3: 1 'in other words, i 7: i. 20 ' position of the month block 27 can be in the forward and backward directions (the axial direction of the eccentric portion 8a of the crank handle ^) Adjusting the eccentric pin Μ to adjust. The slider 27 is adjusted in the forward and backward directions with respect to the upper and lower sliding blocks 16 and η (four) and not the sliding block η) to adjust the material of the alignment member 12 In other words, the system 1 determines the outer circumference of the eccentric part 8a of the crankshaft 3 and the inner circumference of the lower 12 1328506 sliding block 17 and the bottom surface of the lower sliding block 17 and the horizontal plane of the adjustment member 12 (top surface) ) are respectively in contact. Because the adjustment member 12 is fixed by the threaded rod 12a To the slider 3, the forward and backward adjustment of the slider 27 causes the horizontal surface (top surface) of the adjustment member 12 to be inclined forward and backward correspondingly. 10 In Fig. 9, the circle on the left end of the eccentric pin 28 The cylindrical portion is centered on the center with respect to the cylindrical portion at a value "e". By slightly loosening the thread 29, the special tool is engaged with the torsion hole 35 and the eccentric pin 28 is rotated in the direction of the arrow B, and the slider 27 is moved in the direction A. After the slider 27 is adjusted, the bolts μ are locked to fix the slider 27 to the slider 3. Figure 6 shows another specific example and is based on the above Figure #. In the case of Fig. 5, the guide faces 15 of the pair of spherical members % form an angle " which is convex from the side of the slider. On the other hand, in the case of Fig. 6, the angle "0" is assumed to be a convex angle α as seen from the side of the sliders 3A and 31. As a result, the adjustment member 12, (4) face is oriented toward the slider % _ μ ^ 20 slider 27, and the slider 3 〇 and the 3 ι pin 28 are adjusted. ',. The eccentricity is shown in Figures 7 and 8 showing the spherical member %
模式之其他具體例。在第 门·，且D 32係被提供在調整構：二圖的情況中，-接收構件 接受該球形構件26。換句节 接收構件32係 句話說’接收構件32係存在 13 5 於調整構件12與 藉由螺拾33而间 26之間。接收構件32係 3而固定至調整 > 其必須在調整構件12上/件2°在⑨種結構中’ 其更容易機械加工製造，成一凹入球形表面’而使 形構件在I/圖的情況中’-帽蓋34係被設置在球 彼此滑動。W允許帽蓋34的平面表面與滑塊27 形構;：26帽|,34具有一凸面球形表面，其係與球 的球形表面嚙合。球形構件261係藉由螺 10 的方式固定至調整構件12。球形體26，係被容 納在調整構件12中。 本發明的功效 15 本發明使得一對應於_連桿的構件變的不必 要，所以其可以在-較高的位置上提供該滑動件。這 使得機械壓機的高度可以縮短。因為這樣在垂直方 向上的剛性會增加，而在水平方向上的剛性也會增加。 这也使得我們可以降低收容機械壓機的建築物 之天花板高度，並同時形成該壓機作業的改善。除此 之外，在調整構件12以一更合理的導引件來導引下， 本發明提供機械壓機更穩定的效能且與更長的使用壽 20 命。 【圖式簡單說明】 第1圖係為本發明的機械壓機之一正視圖和部 分剖面圖； 14 1328506 第2圖係為第1圖的機械壓機的左視圖與部分 剖面圖； 第3圖是本發明的連接構件之透視圖； 第4圖是該連接構件的放大圖； 5 第5圖是另一個具體例的頂視圖和部分剖面圖； 第6圖是該連接構件之另一具體例的頂視圖和 部分剖面圖； 第7圖是球形構件的第二具體例； 第8圖是球形構件的第三具體例； 10 第9圖是該偏心銷的概略圖；和 第10圖是具有一連桿的習知技藝之機械壓機的 正視圖。 【圖式之主要元件代表符號表】 1 機械壓機 10 小齒輪傳動機構 2 框架 11 飛輪 3 滑動件 12 調整構件 3a 導引孔 12a 螺紋桿 4 承樑 13 帽蓋 5 振動預防裝置 15 間隔器 6 滑動導引機構 16 上滑動塊 7 位置調整機構 17 下滑動塊 8 曲柄軸 18 滑動導引件 8a 偏心部件 19 蝸桿軸 9 主要傳動機構 20 蜗輪 1328506 21 螺帽 28 偏心銷 23 連桿 29 螺栓 22 扣件 30和31滑塊 24 調整螺釘桿 32 接收構件 25 平衡器 33 螺拴 26 球形構件 34 帽蓋 27 滑塊 35 扭轉孔Other specific examples of the pattern. In the case of the door, and the D 32 is provided in the adjustment configuration: the second figure, the receiving member receives the spherical member 26. In other words, the receiving member 32 is said to say that the receiving member 32 is present between the adjusting member 12 and the screw 26 therebetween. The receiving member 32 is 3 and fixed to the adjustment> it must be on the adjusting member 12/piece 2° in 9 structures 'it is easier to machine and manufacture, into a concave spherical surface' and the shaped member is in the I/picture In the case of the '-cap 34 is arranged to slide the balls against each other. W allows the planar surface of the cap 34 to be shaped with the slider 27; 26 cap|, 34 has a convex spherical surface that engages the spherical surface of the ball. The spherical member 261 is fixed to the adjustment member 12 by means of a screw 10. The spherical body 26 is received in the adjustment member 12. EFFECT OF THE INVENTION 15 The present invention makes it unnecessary to change a member corresponding to the _ link, so that it can be provided at a higher position. This allows the height of the mechanical press to be shortened. Because of this, the rigidity in the vertical direction increases, and the rigidity in the horizontal direction also increases. This also allows us to reduce the ceiling height of the building that houses the mechanical press and at the same time to improve the press operation. In addition to this, the present invention provides a more stable performance of the mechanical press and a longer life span with the adjustment member 12 being guided by a more reasonable guide. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a front view and a partial cross-sectional view of a mechanical press of the present invention; 14 1328506 Fig. 2 is a left side view and a partial cross-sectional view of the mechanical press of Fig. 1; Figure 4 is a perspective view of the connecting member of the present invention; Figure 4 is an enlarged view of the connecting member; 5 Figure 5 is a top view and a partial cross-sectional view of another specific example; Figure 6 is another specific of the connecting member A top view and a partial cross-sectional view of the example; Fig. 7 is a second specific example of the spherical member; Fig. 8 is a third specific example of the spherical member; 10 Fig. 9 is a schematic view of the eccentric pin; and Fig. 10 is A front view of a mechanical press of the prior art having a link. [Main component representative symbol table of the drawing] 1 Mechanical press 10 Pinion gear mechanism 2 Frame 11 Flywheel 3 Slide 12 Adjustment member 3a Guide hole 12a Threaded rod 4 Bearing beam 13 Cap 5 Vibration prevention device 15 Spacer 6 Sliding guide mechanism 16 Upper slide block 7 Position adjustment mechanism 17 Lower slide block 8 Crank shaft 18 Sliding guide 8a Eccentric member 19 Worm shaft 9 Main transmission mechanism 20 Worm gear 1328506 21 Nut 28 Eccentric pin 23 Connecting rod 29 Bolt 22 Buckle 30 and 31 sliders 24 adjustment screw lever 32 receiving member 25 balancer 33 thread 26 spherical member 34 cap 27 slider 35 torsion hole
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