US3509747A - Precision forming press - Google Patents

Description

May 5, 1970 F. R. oGlLvlE PRECISION FORMIG PRESS 4 Sheets-Sheet 1 Filed Oct. 24, 1965 HI. .nM-Hilml INVENTOR FPA/VK A. 06M v/E 4 Train/5y May 5, 1970 F. R. oGlLvu-z PRECISIQN FORMING PRESS 4 Sheets-Sheet 2 Filed 0G11. 24, 1965 INVENTOR FeAA/K P06/L we "WIWI rro/eA/ey l 4 Sheets- Sheet y:5

Trae A/ Y May 5, 1970 F. R. oGxLvlE 4 PRECISION FORMING PRESS Filed Oct. 24, 1965 May 5, 1970 F. R. OGILVIE PRECISION FORMING PRESS 4 Sheets-Sheet 4.

Filed Oct. 24, 1965 INVENTOR FRA/V KKOc-/L V/E T Tom/Ey United States Patent O 3,509,747 PRECISION FORMING PRESS Frank R. Ogilvie, 645 Claraday,

Glendora, Calif. 91740 Filed Oct. 24, 1965, Ser. No. 504,599 Int. Cl. B21d 13/02 U.S. Cl. 72-429 5 Claims ABSTRACT F THE DISCLOSURE A precision forming press which provides precision movement by an arrangement of eccentric cams cooperating with frame members to move one die relative to another die with precise motion; fluid piston means assist in providing accurate guidance and cushion relative movement between die members; adjustment means are provided for precision vertical positioning of die members relative to each other.

The present invention relates generally to a precision forming press for press-forming metal articles by hydraulic or similar pressures or forces; more particulaly, the invention relates to such a press wherein die members are brought together with considerable force to perform the forming operation.

The invention provides improved means for moving die members relative to each other whereby their movement is accomplished precisely and in a simple but effective manner. In a preferred embodiment of the invention, the dies are moved relative to each other by means of an arrangement of eccentric cams cooperating with frame members whereby one die is moved relative to the other with a precise parallel motion which is positive and eX- tremely effective, despite the simplicity of the arrangement. Additionally, fluid piston means are provided to further guide and control the parallel movement of the die members with respect to one another and to provide means to cushion the relative movement between the die members.

It is therefore a primary object of the present invention to provide a precision forming press of simplified construction.

An object of the invention is the provision of an improved press forming machine having simplified and more effective means for moving one die relative to the other with precision.

An object of this invention is to provide a forming machine according to the foregoing objects, which includes a frame assembly carrying a first die member movable with respect to a second die member, and means comprising eccentric rotor cams cooperable with follower members operative in precise regulated parallel motion upon rotation of the cams.

Another object of the invention is the provision of a press according to the foregoing object, wherein hydraulic means rotate the eccentric cam to produce the desired relative movement.

Other objects, features and advantages of the present invention will become apparent to those versed in the art from a consideration of the following description, the appended claims and the accompanying drawings, wherein:

PIG. l is a front elevational View, partially in section, of a preferred embodiment of the precision forming press according to the present invention;

FIG. 2 is a view similar to that of FIG. l, showing the parts in a different position of operation;

FIG. 3 is a top view taken at line 3-3 of FIG. 2;

FIG. 4 is a sectional view taken at line 4 4 of FIG. 3;

3,509,747 Patented May 5, 1970 Referring to the drawings, a preferred embodiment of' the precision press of the invention is shown as comprising a frame structure having lower parallel side plate members 10 and 12 (FIGURE 6). These plate members 10 and 12 are extended outwardly at the ends as indicated at 14 and 16 in FIGURE 1. At the lower corners of plates 10 and 12 legs 18 and 20 are provided and welded to plate 10 and having cylindrical supporting feet 22 and 24. As shown in FIGURE 6, the frame plate 12 has a leg 18' and a supporting foot 22.

The construction at both ends of the machine is alike so that the construction is described in detail for only one end. FIGURE 1 shows a part of the structure broken away at the right end. FIG. 6, which is a sectional view taken along line 6-6 of FIG. 2, shows the detailed construction. Frame members 10 and 12 support a longitudinal die holding platform 28 as detailed in FIG. 6. The frame members 10 and 12 carry the upper parts 30 and 32 of journal bearings having lower parts 34 and 36. Thus two journal bearings are formed having bushings 38 and 40 therein, in which is journaled a transverse shaft 42 having centrally mounted thereon the semi-circular sector gear 46. The upper and lower parts of the journal bearing, 30 and 34, are held together by bolts 48 and 50, the construction being the same on both sides of the machine and also at the opposite end.

Mounted on opposite ends of the shaft 42 are eccentrics 54 and 56. Eccentrics 54 and 56 are journaled in openings 62 and 64 in upright members or links 66 and 68, having a configuration as shown at 66 in FIG. 1. The openings 62 and 64 have bushings 70 and 72 in them in which the eccentrics 54 and 56 are journaled. Each of the eccentrics 54, 56 have an annular outer shoulder on which is fitted a holding ring 76, 78.

Platform 28 supports a lower die member 80 which is suitably held thereon, and which is further discussed bebelow.

At the upper part of the machine are similarly shaped side fra-me members 10 and 12. Supported by these frame members are journal bearings 30', 34', 32', and 36. These bearings correspond to those identified by the same unprimed numbers described above. The construction is similar at opposite ends of the machine so that both ends need not be described in detail. Journaled in the bearings Sty-36 is a shaft 86 on which is mounted a semi-circular sector gear 46. On the ends of shaft 86 are eccentrics 54 and 56 which are similar to those identified by the same numbers unprimed and described hereinabove. These eccentrics are journaled in the upper ends of link members 66 and 68. The frame members 10 and 12 support a horizontal platform 92 at their lower edges. Platform 92 carries an upper die member 96 further discussed below.

In operation, the upper die member 96 is moved downwardly towards the lower die member in order to form a piece of material 100, positioned between the dies. The operation is described in detail hereinafter.

The assembly 92 carrying the upper die 96 is movable vertically by means of a hydraulic actuating `mechanism 105. This mechanism includes a double ended hydraulic cylinder generally designated at 102 in the figures. The cylinder has in it piston 104, including sealing members 106 and 108, the assembly being held together on a piston rod 110 by nuts 112 and 114. The cylinder 102 has 3 pipe connections 120 and 122 for admitting and releasing hydraulic fluid from the cylinder. When fluid is admitted at one end, it is released from the other and vice versa, the piston 104 and piston rod 110 moving accordingly.

Connected to the right end of the piston rod 110 is a rack 126 which meshes with sector gear 46. Rack 26 is held in engagement with sector gear 46 by a roller 130 on a shaft 132. The ends of shaft 132 are journaled in bearings 134 and 136 mounted in support members 140 and 142 depending from the platform 28. The structure just described is the same at the opposite end of the machine and therefore is not described again in detail.

The means provided for adjusting manually and precisely the position of the platform 92 carrying the upper die 96 with respect to the lower die 80 comprises a longitudinal shaft 142 mounted over the platform member 92. The right end of shaft 142 is journaled in bushings in upright support members 144 and 146 upstanding from platform 92. The end part of shaft 142 is threaded as shown at 150. Mounted on threaded part 150 of shaft 142 is a worm gear 152 held in a set position by a nut 154. Worm gear 152 meshes with a semi-circular sector gear 46. The structure at the opposite end of the machine is like that just described and is not described in detail.

At the center 155 of machine shaft 142 a bushing 156 is mounted. Bushing 156 has a square annular shoulder 158. A pinion gear 160 is carried adjacent to shoulder 158. Pinion gear 160 meshes with worm gear 162 on a shaft 164. A crank 166 is on the end of shaft 164. The ends of the shaft 164 are journaled in fittings 170 and 172 supported on the inside surfaces of the frame members 10", 12.

Bushing 156 has end parts 176 and 178 of smaller diameter which carry flanged bushings 180 and 182 journaled in openings in the web parts 186 and 188 of support members having leg parts shown at 190, 192, 194 and 196. The respective web parts 186 and 188 extend between the respective leg parts 190, 192, 194, 196 of the support members. These support members are supported upon platform 92 and are attached thereto by screws 200 and 202 (FIG. 4).

From the description thus far, it will be understood that the upper assembly 92 carrying upper die 96 is adjustable manually with precision in respect to lower die 80 and may be moved downwardly with respect to the lower die 80 by the hydraulic mechanism 105 to peiform a forming operation as described below.

To further guide and regulate the vertical parallel movement between the upper frame structure and the lower, there are provided guide and cushioning cylinder and piston assemblies such as shown in FIG. 5. This assembly at the right end of the machine is designated generally at 210 in FIG. l. It comprises a cylinder 212 shown in FIG. which extends through an opening in the end of platform 92 and is welded to a plate 214 which is in turn welded to the platform 92. Within the cylinder 212 is a piston 220 which extends through an opening in the platform 28. It is welded to a plate 222 which is in turn welded to the platform 28.

The cylinder 212 has an opening 226 in its upper end and there is an annular groove 228 therein to receive a sealing O-ring 230. Piston 220 additionally has a plurality of V-shaped annular grooves 232 as shown.

The machine has a similarly constructed piston and cylinder assembly at the opposite end.

The details of operation of the machine are as follows. It is necessary to be able to set precisely the upper die 96 in a position relative to the lower die 80 before a machine forming operation is initiated. As best seen in FIG. 4 this is done by the crank 166 which rotates the worm gear 162 and in turn the pinion gear 160 in shaft 142. This rotates the worm gears 152 at the end of shaft 142 which revolves the sector gear 46', and its corresponding sector gear at the other end of shaft 142.

Rotation of gears 152, 46 and their corresponding gears, rotate the eccentric cams 54 and 56' on their corresponding eccentrics at the other end of the machine. Thus, the vertical position of shaft 86- and its corresponding shaft is adjusted so that the position of platform 92 and the upper die 96 is adjusted with respect to the lower die.

FIG. 1 shows the hydraulic mechanism 105 with the piston 104 near the left end of cylinder 102 and FIG. 2 shows the piston 104 moved to the right end. This is accomplished by applying hydraulic fluid to the left end of cylinder 102 and releasing it from the right end. As this occurs rack 126 drives sector gear 46 from the position of FIGURE 1 to that of FIGURE 2. The sector gear at the opposite end being similarly operated. Racks 126 are held firmly in engagement with sector gear by roller 130. When sector gear 46 and its corresponding gear at the opposite end is rotated, their respective eccentrics, including the eccentrics 54 and S6 and their corresponding eccentrics at the opposite end are rotated. In this manner, the uprights or link members 66 and 68 and 66 and 68 are adjusted or moved vertically with accurate parallel motion controlled by the cylinder and piston assemblies 210. The hydraulic fluid is admitted at the desired pressure and volume rate so that the hydraulic action occurs with the speed required for the particular forming action being conducted. The upper frame assembly is looped down for forming operation as illustrated in the figures and the piece of material 100 is quickly formed to a shape corresponding to that of the upper and lower dies. In this operation, the cylinders 212 as detailed in FIG` 5 move downwardly with respect to the pistons 220 compressing the air therein which is forced outwardly through the top opening 226. Thus, a regulated cushioning effect is provided so that there is no danger of injury to the machine or part being formed. The V-shaped annular grooves 232 inthe piston 220 provide for pressure differential transfer as piston 220 is moved in cylinder 212.

In the FIGURES 7 and 8, an alternative eccentric design is shown to operate in place of eccentricsV 54 and 56. The purpose of the alternative design is to provide a longer stroke capability for the press action. FIG. 7 shows one position thereof with the tension arm up. FIG. 8 shows the position with tension arm 66 down.

The extended stroke is achieved through the incorporation on shaft 42, and rotatable therewith, of a crank pin plate 300 with a pin 301 inserted therein and rotatably anchored in tension arm 66' in a bearing 303 provided therein, so that as tension arm 66 rides downward on piston and cylinder 220, 212 and shaft 42 rotates through tension arm 66 is guided on camming aperture 305 in tension arm 66.

The identical arrangement to that described above is incorporated in all four tension ' arms 66, 66', 68, 68 and operates identically lso that further description of each is not given here. Clearly all four tension arms are operlted in unison as described in the preceding paragrap The effect of operation of crank pin 301 in its plate assembly 303 is as though the diameters of eccentrics 54, 56 hand been increased so that a greater radial difference is possible in the rotation thereof during the downward stroke, and so tension arms 66, 68 and their parallel counterparts 66 and 68' move over a greater vertical distance.

From the foregoing, those versed in the art will observe that the invention achieves the objects and realizes the advantages hereinbefore mentioned, and that additional advantages are apparent from the detailed description. The precision forming press is of a relatively simple but extremely rugged construction and is capable of performing forming operations requiring very considerable force. In the press operation one die can be very precisely set relative to the other and moved with great precision relative to the other in the forming operation. The accuracy of setting is achieved by the crank operated shaft and worm gears meshing with the upper sector gears. Parallel motion is regulated and controlled very precisely and effectively by way of the eccentric cams cooperating with the four links which move up and down when the cams are rotated. The racks and sector gears operated by the hydraulic mechanism provide a very rugged but effective and accurate means for realizing the desired movement, in combination with the links which are operated by the eccentric cams.

Those versed in the art will appreciate that the present invention achieves the objects and realizes the advantages hereinbefore mentioned.

Although specific embodiments of the present invention have been illustrated and described herein, it will be understood that the same are merely exemplary of presently preferred embodiments capable of attaining the objects and advantages hereinbefore mentioned, and that the invention is not limited thereto; variations will be readily apparent to those versed in the art, and the invention is entitled to the broadest interpretation within the terms of the appended claims.

The inventor claims:

1. In a precision press forming machine, the combination comprising a rst platform, a second platform, respective matching die members carried by the first and second platforms, means comprising four spaced eccentric rotors rotatably carried by said rst platform, respective means engaging said respective eccentric rotors and movable by rotation of the rotors, said last respective means being connected with the second platform, interconnected gearing means connected with each of the eccentric rotors for rotation thereof in unison, and means to drive said interconnected gearing means, whereby upon rotation of the eccentric rotors said platforms are moved toward each other in precision parallel relation for precision engagement of said matching die members.

2. A press forming machine according to claim 1 wherein said respective means engaging respective rotors comprise four links having respective portions engageable with said respective eccentric rotors and having other respective portions connected to said second platform, whereby the relative movement of said second platform is through movement of said link.

3. A press forming machine according to claim 1 wherein said respective means engaging respective rotors includes four links having respective portions engageable with said respective eccentric rotors, and further including at least two additional rotors rotatably carried by said second platform, certain of said links having other portions having said additional rotors joumaled therein, whereby said second platform is adjustable relative to the other platform by rotation of said last mentioned rotors.

4. A press forming machine according to claim 1, wherein said respective means engaging respective rotors comprises a plurality of corresponding links and' a plurality of additional rotors corresponding to said eccentic rotors, wherein said additional rotors are rotatably carried by said second platform, and wherein said respective corresponding links are engageable with said additional rotors and are journaled thereon, and further including means for rotating said additional rotors to adjust said second platform relative to the other platform.

5. A precision sheet metal forming press comprising: an upper and a lower platform; means engageable with said platforms for moving one of said platforms relative to the other of said platforms in precise vertical align` ment with one another; and guide assemblies cushioned by iluid pressure coupled between said upper and said lower platforms and adapted to guide one of said platforms vertically with respect to the other along said precisely aligned vertical path and to provide cushioning.

References Cited UNITED STATES PATENTS 264,859 9/ 1882 Butterfield 188-94 499,075 `6/1893 Winn 188-94 676,378 6/ 1901 Wolfe 188--94 1,295,189 2/1919 Morgan 72-429 1,422,779 7 1922 Perony 72-453 2,136,856 11/1938 Long 72-429 2,656,744 10/ 1953 Saxer 72--441 3,102,575 9/ 1963 Engel 72-415 3,191,412 6/ 1965 Duvall 72-26 RICHARD J. HERBST, Primary Examiner G. P. CROSBY, Assistant Examiner U.S. Cl. X.R.

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