US3145648A - High energy impact forming machine - Google Patents

Description

Aug. 25, 1964 J. K. MUREK ETAL HIGH ENERGY IMPACT FORMING MACHINE 6 Sheets-Sheet 1 Filed April 26, 1962 Cfimziopizer Zezlefga,

Aug. 25, 1964 J. K. MUREK ETAL 3,145,648

HIGH ENERGY IMPACT FORMING MACHINE Filed April 26, 1962 6 Sheets-Sheet 2 INVENTORS 4 T jsefflflar ek 6km50fier 222527 940 g 04;; 75%,, was, W

Aug. 25, 1964 J. K. MUREK ETAL HIGH ENERGY IMPACT FORMING MACHINE 6 Sheets-Sheet 3 Filed April 26, 1962 Z; TM 3 Aug. 25, 1964 Filed April 26, 1962 J. K. MUREK ETAL HIGHENERGY IMPACT FORMING MACHINE 6 Sheets-Sheet 5 W INVENTORS 04W, 7% wi 25, 1964 J. K. MUREK ETAL 3,145,648

HIGH ENERGY IMPACT FORMING MACHINE Filed April 26, 1962 6 Sheets-Sheet 6 8 INVENTOR-S ikmmk 110 535 Cmi'z gver Zeale ga/ 0km, 7W

United States Patent 3,145,648 HIGH ENERGY IMPACT FORMING MACHINE Josef Karl Mun-eh, San Diego, Calif, and Christopher Zeilenga, Chicago, Ill., assignors to Trans Energy Corp., New York, N.Y., a corporation of Delaware Filed Apr. 26, 1962, Ser. No. 190,359 17 Claims. ((11. 100-264) The present invention relates to a novel high energy rate Or high velocity impact forming or workpiece processing machine.

It is contemplated that a machine incorporating features of the present invention will include substantially sealed high fluid pressure chamber means providing fluid under pressure for driving a ram or the like through a working stroke at a high velocity. The high velocities and energies encountered in such a machine impose great stresses on the machine so that substantial problems of reliability and machine life are encountered.

After each working stroke of the ram it is necessary to return or recock the ram against the force of the fluid under pressure which bears against the ram. Additional substantial problems have been encountered in providing a structure capable of accommodating the forces and stresses involved during recocking and subsequent retention of the ram while, at the same time, capable of functioning rapidly and reliably.

An important object of the present invention is to provide a novel machine of the above described type having improved strength, ruggedness and reliability.

A further object of the present invention is to provide a novel apparatus of the above described type which incorporates means for resetting or recocking the ram of the apparatus, which means is capable of functioning rapidly and reliably and has an improved working life.

Still another important object of the present invention is to provide a novel high energy impact forming machine of the above described type having means for resetting or recocking the ram constructed and supported with respect to a main frame of the apparatus in a. manner which enables the recocking means to be effectively and substantially isolated from the remainder of the apparatus at the instant of impact of the ram against a work structure so as to minimize or substantially elimimate a transfer of impact and inertia stresses and loads between the recocking means and the remainder of the apparatus whereby to reduce any possibility of injury to the apparatus.

Other objects and advantages of the present invention will become apparent from the following description and the accompanying drawings, wherein:

FIG. 1 is a front elevational view showing an apparatus incorporating features of the present invention;

FIG. 2 is a side elevational view of the apparatus shown in FIG. 1;

FIG. 3 is an enlarged sectional view of a main frame member of the apparatus taken generally along line 3-3 in FIG. 2;

FIG. 4 is an enlarged fragmentary partial sectional view taken generally along line 44 in FIG. 2;

FIG. 4a is an enlarged fragmentary partial sectional View taken generally along line ta-4a in FIG. 2 and provides an extension of FIG. 4;

FIG. 5 is a sectional view taken along line 5-5 in FIG. 4;

FIG. 6 is an enlarged fragmentary sectional view similar to a portion of FIG. 5 and shows the structure for I guiding a corner of the ram in greater detail; and

FIG. 7 is a schematic diagram showing hydraulic and electrical actuating and control means for the apparatus.

Referring now more specifically to the drawings Wherein like parts are designated by the same numerals throughout the various figures, an apparatus 10 incorporating features of the present invention is shown in FIGS. 1 and 2. The apparatus comprises a main frame structure or casting 12 which is preferably formed substantially in one piece, as will be described more in detail below. The main frame structure or casting is provided with a substantially spherical head portion 14 which is sealed and adapted to contain air or other suitable gas under high pressure. A ram 16 is telescopically associated with the spherical head portion 14 and is adapted to be actuated by the fluid or gas under pressure through a downward or Work stroke. The rain is provided with an elongated shank portion 18 slidably extending through an opening at the lower end of the spherical head portion. The trailing shank portion 18 of the ram merges with an enlarged head portion 20, which is adapted to carry a suitable workpiece processing die 22.

The main frame structure or casting 12 is provided with a relatively heavy base portion 24 which is suitably supported above a fixed floor 26. The frame head and base portions 14 and 24 are integrally connected by pairs of upstanding side or corner portions 28-30 and 32-34 as shown in FIGS. 1-3 and 5. These upstanding corner or side portions respectively gradually increase in transverse cross-section and weight from their upper ends toward integral junctions with the base portion 24.

In accordance with a feature of the present invention, the junctions between the side or corner portions and the base portion 24 are formed so as to minimize any concentration of stresses at such junctions during working of the machine whereby to reduce any possibility of injury to the machine. In this connection, it is to be noted that the base portion 24 is formed with a substantially semicylindrical seat 36 which extends between the opposite pairs of side or corner portions 28-30 and 32-34. As shown best in FIGS. 1 and 3, the semicylindrical surface or seat 36 is formed so that it merges with the lower ends of the opposite side or corner portions so as to eliminate sharp corners between the corner portions and the base portion of the frame structure. It is also to be noted that the surface of the base portion 24 which extends directly between the lower ends of the corner portions 32 and 34 is in the form of an arcuate surface 40 as shown in FIGS. 2 and 3. It is to be understood that the upper surface of the base portion is similarly curved between the lower ends of the corner portions 28 and 30, as shown at 41 in FIG. 3.

As shown in FIGS. 1 and 4a, a substantially semicylindrical solid pad 42 is disposed on the seat 36. The pad presents a horizontal upper surface 44 on which a work structure or die 46 to be processed may be disposed. A bolt 48 extends through an aperture provided in the base portion 24 and is connected with the pad 42 for drawing the pad firmly against the seat 36. The semicylindrical pad 42 and the seat 36 are formed with accurately finished complementary surfaces. Thus, when an impact load is imposed on the pad 42 during a working stroke of the ram, the pad 42 will tend to distribute the load and the resulting stresses radially and generally uniformly over the seat 36. As a result, stress concentrations in the main frame of the machine are minimized and injury to the machine is avoided and its working life is increased.

As shown best in FIG. 5, the head portion 2d of the ram 16 is generally rectangular. Corners of the ram head portion are retained and supported by vertical guide elements 50, 52, 54 and 56 which are respectively secured to the upstanding corner or side portions 28, 30, 32 and 34 of the frame structure. These elements extend for guiding the lower end of the ram as the ram moves be tween the upper or cocked position, shown in FIG. 1,

and a lower or work engaging position. As previously indicated, the ram is adapted to be driven downwardly at a high velocity by means of air or gas under pressure within the chamber portion 14 of the frame structure so as to accomplish processing or forming of a workpiece with a high velocity, high energy impact force.

In order to rccock and releasably retain the ram, the machine is provided with means 58 which is adapted to be moved between raised and lowered positions and to be releasably interconnected with the head portion 20 of the ram. The recocking and control means 58 comprises a yoke or casting 60 which encircles the main frame or casting 12, as shown best in FIG. 5. Rollers 62, 64, 66 and 68 are bounded on the yoke or casting 61 respectively, for engagement with vertical side or guide surfaces presented by the upstanding corner portions 28, 3t), 32 and 34 of the main frame structure. The casting 60 is thus supported and guided for vertical movement relative to the main frame structure.

The recocking means 58 includes latch means carried by the casting 60, as shown best in FIGS. 4 and 5, and releasably engageable with the head portion 20 of the ram. This latch means comprises a first pair of links 7% and 72 pivotally mounted on the casting 61 by a pin 74 at one side of the ram, and a pair of essentially identical links 76 and 78 pivotally carried by a pin 86 at the opposite side of the ram. Rods 82 and 84 respectively extend between the pairs of links 7072 and 76-78, which rods rotatably carry elongated star wheels 86 and 88. These star wheels are formed with circumferentially spaced elongated grooves which are arcuately formed for accommodating rounded bosses 90 and 92 formed integrally with the opposite margins of the ram head portion 20. It will be observed that when the star wheels are supported by their respective link structures in the positions shown in FIG. 4, they engage beneath the rounded bosses 90 and 9 2 of the ram structure, which bosses conform to and are fully seated within a pair of grooves of the star wheels whereby the star wheels are effectively locked against rotation about their own axes.

When it is desired to release the ram, the link structures supporting the star wheels are pivoted in opposite directions so that the star wheels are shifted laterally outwardly away from the bosses 9t? and 92. This immediately causes partial disengagement of the bosses from the arcuate seats on the star wheels and the star wheels are no longer locked against rotation about their own axes. Thus, as the star wheels are shifted laterally outwardly with their linkage structures, they also begin to rotate about their own axes under the pressure exerted by the ram until the movement of the star wheels has been sufficient completely to release the ram for its downward or working stroke. This rolling contact between the ram and the latch elements or star wheels greatly minimizes wear between these parts and reduces maintenance on the machine.

In order to control the latch elements of the recocking mechanism, hydraulic or fluid pressure cylinders 94 and 96 are provided in the casting 60 at opposite sides of the ram. Pistons 9S and 100 are operable in these cylinders, which pistons are secured to rods 192 and 104 having hook portions 106 and 1618. The book portion 106 engages over a bar 110 extending between and connected to upper end portions of the links 70 and 72, while the hook portion 108 engages over and is connected to a bar 112 which extends between upper end portions of the links 76 and 78. It will be appreciated that by controlling the operation of the hydraulic cylinders 94 and 96, in a manner which will be described more fully below, the latch elements may be actuated for engagement with or disengagement from the ram.

As previously indicated, the pressure chamber 14 is sealed so that the gas therein is always maintained under a high pressure which might, for example, be on the order of 2000 p.s.i. Thus, when the ram is in the raised or cocked position, there will always be a great force biasing the ram downwardly regardless of whether or not the machine is in use or being attended to by an operator. Therefore, the machine is provided with means for releasably locking the latch elements so as to preclude any possibility of the latch elements accidentally becoming disengaged from the ram as a result, for example, of a failure in the hydraulic system controlling the cylinders 94 and 96.

The safety or locking means comprises hydraulic or fluid pressure cylinders 114 and 116 formed in the casting 60 beneath the cylinders 4 and 96. A piston 118 is slidably mounted in the cylinder 114 and is adapted to be actuated by fluid or hydraulic pressure toward the left as viewed in FIG. 4. A similar piston 12% is dispose in the cylinder 116 and is adapted to be actuated by fluid or hydraulic pressure outwardly or toward the right, as viewed in FIG. 4. Outer ends of the pistons 118 and 129 are respectively connected to transverse or yoke members 122 and 124. As shown in FIGS. 4 and 5, opposite ends of the transverse member 122 are respectively secured to outer ends of rods 126 and 128. Identical rods 13% and 132 are connected with the transverse or cross member 124.

As shown best in FIG. 5, the rods 126 and 128 extend through suitable guideways formed in the casting at opposite sides of and parallel to the cylinder 114. The rods 130 and 132 slidably extend through similar guideways at opposite sides of the cylinder 116. Inner ends of the rods 126 and 128 are threadedly or otherwise suitably connected to a transverse stop or latch bar 134 which is adapted to slide along and bear against abutment surfaces 136 and 138 formed on the casting. As shown in FIGS. 4 and 5, the bar 134 is adapted to be positioned beneath laterally extending stop or abutment portions 140 and 142 of the links 70 and 72. The latch or stop bar 134 is thus adapted to prevent the links '71) and 72 from pivoting in a counterclockwise direction, as viewed in FIG. 4, so as to preclude release of the ram when the latch bar is in the position shown. A substantially identical transverse member or latch bar 144 is connected to inner ends of the rods 130 and 132 and is slidable on surfaces 146 and 148 between the extended position shown in FIGS. 4 and 5 and a retracted position. The bar 144 is also adapted to engage beneath abutment portions 159 and 152 of the links 76 and 78 for locking the links against clockwise pivotal movement, as viewed in FIG. 4.

The stop or latch bars 134 and 144 are normally biased toward their extended or link locking positions by compression springs 154, 156, 153 and 160, respectively disposed around the rods 126, 128, 130 and 132. The arrangement of the pistons in the cylinders 114 and 116 is such that, when fluid under pressure is directed into the cylinders, the pistons are shifted outwardly for moving the bars 134 and 144 from their extended or locking positions shown outwardly in opposite directions sufiiciently to preclude engagement with the projecting abutment portions of the links. Preferably the locking or latch bars are operated so that they will be withdrawn one at a time, in the manner described more fully below, for providing a further safety factor precluding accidental discharge of the ram.

The recocking and locking casting or frame member 60 is supported and adapted to be actuated for enabling it to be lowered from the position shown in FIGS. 1, 2 and 4 after the ram has been released for movement downwardly through a working stroke. The arrangement is such that the member 61} may be moved to a lowered position at which the latch elements 86 and 83 may be reengaged with the ram, whereupon the member 60 may be raised for lifting the ram to its elevated or recocked position.

In order to support and actuate the member 60, vertically disposed hydraulic or fluid pressure cylinders 162 and 164 are formed integrally with the casting 60. Hollow piston structures 166 and 168 are respectively associated with the cylinders 162 and 164. As shown best in FIG. 4a, the piston structure 166 comprises a first tubular member 170 having an upper end portion slidably disposed within the cylinder 162 and having a lower end portion telescopically receiving and welded or otherwise fixed to an upper end portion of a second tubular member 172. A lower end of the piston member 170 is adapted to engage and rest on an annular abutment surface 174.provided on the base portion of the main frame while the piston member 172 slidably extends through a vertical bore 176 provided in the base portion of the main casting. A sleeve bearing 173 is disposed on the portion of the tubular member 172 extending through the bore 176 for facilitating sliding movement of the tubular piston member 172 relative to the base portion of the main frame member. The bearing sleeve is retained between an annular shoulder 180 formed on the tubular member 172 and a collar 182 fixed on the tubular member beneath and spaced from the bottom surface of the main frame member.

A lower end portion of the tubular piston member 172 extends into and is slidable relative to a tubular fitting 184 which is suitably secured to the floor 26 or other support surface. The tubular fitting 184- is provided with openings or" ports 186 and 187 adapted to be connected with conduits ofa hydraulic system described in detail below. The ports 186 and 187 communicate with an annular chamber 188 within the fittting 184, which chamber in turn communicates with a port 1% formed in the wall of the tubular piston 172. The lower end of the piston 172 is, of course, closed and sealed by a plug 192, and annular packing and seal means 194 and 196 are provided above and below the annular chamber 188 for sealing the chamber while permitting the piston mem her 172 to slide relative to the fitting 184. With this structure, hydraulic fluid may be delivered under pressure to or discharged from the cylinder 162 by flowing through the ports 186, 187 and 190 and the hollow or turbular piston members 170 and 1.72.

The hollow piston structure 168 is identical to the piston structure 166 and, therefore, need not be described in detail. It suflices to state that the piston structure 168 comprises tubular members 198 and 200 corresponding to the previously described tubular piston memof a hydraulic control system.

In FIG. 7 a hydraulic and electrical control system included in the apparatus is shown in simplified anddiagrammatic form. This control system comprises a hydraulic pump 21% which is constantly driven by a suitable electric motor or any other prime mover. The pump 210 has its inlet side connected by conduit means 212 with a reservoir 214 through a cooler 216 of known construction. An outlet port of the pump is connected with a pressure conduit 218. Preferably a pressure relief valve 220 is connected between the pressure line and the reservoir for returning any excess fluid to the reservoir.

In the embodiment shown the pressure line 218 is connected with a port 222 of a spring offset single solenoid four-way valve 224. The valve 224 has a second port 226 connected with a conduit 228 and another port 230 connected with a conduit 232. The valve is spring biased so as normally to interrupt communication between the port 222 and the port 226 while connecting the port 226 to the port 230. The solenoid 232 is provided for actuating the valve so as to connect the port 222 with the port 226 and direct fluid under pressure to the conduit 228.

The conduit 228 is connected by suitable branch conduits 234 and 236 with the lock cylinder 114. In addition the conduit 228 is connected through a check valve 238, permitting flow in one direction, with a first port 240 of a mechanically operated four-way valve 242 associated with the cylinder 114. As indicated in FIG. 7, the valve 240 is mechanically interconnected with the piston 113 so as to be operated in response to movement of the piston 113.

The valve 242 includes another port 244 connected with the conduit 228 through a check valve 246 permitting flow in a direction opposite to the flow through check valve 238. Still another port 248 of the valve 242 is connected by a conduit 250 with the lock cylinder 116. The piston in the cylinder 116 is also mechanically interconnected with another valve 252 which serves to control the operation of the latch cylinders 94 and 96 in a manner to be described.

The valve 252 is adapted to be actuated in one direction by the mechanical linkage with the piston 120, and to be operated in the opposite direction by a pilot 254. The valve 252 is provided with a pressure inlet port 256 connected with the pressure conduit 218 by suitable branch conduits 258 and 260. Preferably a check valve 262 is connected in the conduit 260 so as to minimize any possibility of reverse flow of fluid from the latched cylinders in the event of a failure of the pump.

The valve 252 includes a second port 264 connected with first ends of the latch cylinders 94 and 96 by a'conduit 266 and suitable branch conduit means 268. Opposite ends of the cylinders 94 and 96 are connected with another port 270 of the valve 252 by a conduit 272 and suitable branch conduit means 274. An outlet port 276 of the valve 252 is connected by conduit means 278 with the reservoir 214 through a spring biased pressure relief valve 280.

The apparatus includes an electrical control and relay panel 281 electrically connected by Wires 283 and 285 with suitable power lines L-l and L2. This panel is also connected by wires 287 and 289 with the solenoid 232. The control panel includes a relay for controlling the solenoid 232, which relay is adapted to be manually actu. ated upon the depression of a start button 291.

The portion of the hydraulic and electrical control means thus far described serves to control the operation of the latch cylinders 94 and 96 and the locking cylinders 114 and 116 in the following manner. It is assumed that the apparatus is in an idle condition with the ram 26 latched and locked in its elevated position. When the machine is in this condition, the solenoid 232 is deenergized so that the pressure port 222 of the valve 224 is disconnected from the port 226. At the same time the valve 242 is conditioned so that the port 240 is disconnected from the port 243, and the valve 252 is positioned so that the port 256 is connected to the port 264, while the port 270 is connected with the port 276. In other words, the valves are conditioned so that hydraulic fluid under pressure is blocked from the latching cylinders 114 and 116, while the fluid under pressure is directed to the outer ends of the latch cylinders 94 and $6.

In order to actuate the apparatus, the start button 292 is manually depressed so that the solenoid 232 is energized for shifting the valve 224 to connect the port 222 with the port 226. Hydraulic fluidunder pressure is then directed to the locking cylinder 114 for shifting the piston 118 to disengage the locking element associated therewith from the links of the latching means. Upon substantial completion of the movement of the piston 11%, the valve 242, which is mechanically linked with the piston, is actuated for connecting the port 240 with the port 248 so that hydraulic fluid under pressure is directed to the locking cylinder 116 The locking element associated with the piston 120 is then retracted from the latch means as the piston is shifted by the fluid under pressure. It is to be noted that with this arrangement the piston 120 is actuated only after the piston 118' has been actuated whereby a double safety is provided. When the piston 12% has withdrawn its associated locking element from the latch means, the mechanical interlock between the piston 120 and the valve 252 causes the valve to be actuated for connecting the port 256 with the port 275 and the port 264 with the port 276. When this occurs, fluid under pressure is directed to the cylinders 94 and 96 for causing the latch means to be retracted, whereby to release the ram. At the same time fluid is forced from the outer ends of the cylinders 94 and 96 and down through the conduits 265 and 278.

In addition to the previously described means for controlling and actuating the latching cylinders and the look ing cylinders, the system comprises means for controlling and actuating the cylinders 162 and 164 in the recocking slide or frame member 69. This means includes a spring centered four-way valve 282 adapted to be actuated in opposite directions by solenoids 284 and 286 and having a pressure inlet port 288 connected with the pressure conduit 258 by a branch conduit 290. The valve 282 has another port 292 connected by conduits 294 and 296 with the main ports 186 and 2% of the fittings 184 and 2% through main check valves 298 and 300, respectively. These check valves are of known construction and normally permit flow only into the ports 1% and 208. However, these check valves are of a type including pressure actuated devices 362 and 304 which are adapted to be operated for unseating or opening the check valves 2% and 300 for permitting reverse flow of the hydraulic fluid.

The valve 282 includes a third port 3% connected by conduits 3G8 and 310 with the pilot or actuating devices 362 and 394 of the check valves 29? and 306. The structure of the valve 282 is such that the port 306 is normally in communication with the port 292 and with a drain port 312 when the valve 282 is centered, while at the same time the pressure inlet port 238 is blocked. The drain port312 is connected by a suitable conduit 314 with the reservoir.

The additional ports 187 and 189 of the fittings 184 and 2%, respectively, are connected with check valves 32d and 322 having outlets connected with the reservoir through conduits 324 and 326. These check valves are of known construction and are normally closed to prevent the flow of hydraulic fluid therethrough. These valves are similar to the previously described check valves in that they include pressure operated actuating or pilot devices 328 and 33% which are adapted to be operative for opening the check valves 32% and 322 for permitting fluid to drain from the cylinders 162 and 164. Fluid under pressure is provided for operating the devices 328 and 338 through conduit 332 which is connected with the previously described conduit 278 by a branch conduit 334. With this arrangement it is to be noted that, when the latch cylinders 94 and 96 are actuated for releasing the ram and for forcing fluid under pressure from their outer ends and down through the conduit 278, a portion of the fluid under pressure will be delivered to the devices 323 and 33a? for opening the check valves 32% and 322, whereby fluid starts to drain from the cylinders 162 and 164 while permitting the recocking casting or frame member 6%) to move from its fully raised position toward a lowered position. It will be appreciated that the spring biased pressure relief valve 280 is such as to maintain the desired pressure for enabling the check valves to be opened, and, if desired, a suitable time delay device 336 may be interconnected with the pressure relief valve for preventing the valve from opening prematurely.

It is important to note that, when the ram 16 is released and starts accelerating rapidly downwardly, a reaction force is provided which causes the main frame 12 of the machine and all of the pants fixed thereto, or supported thereby, to start to move upwardly. Since the mass of the main frame and its related components is much larger than that of the ram, the length of travel of the main frame and the components supported thereby is quite small as compared with that of the ram at the instant of impact of the ram against the Work structure supported on the base of the main frame.

The masses of the ram and the main frame with its connected components are related to each other so that the inertia of the upwardly moving main frame will be suflicient to offset the inertia and impact forces provided by the downwardly moving ram at the moment of impact. With this arrangement the machine needs no heavy supporting floors or other structure since substantially all of the stresses and shock loads are absorbed within the machine itself.

As previously indicated, everything fixed to or supported by the main frame begins to move upwardly immediately upon downward movement of the ram. This includes the recocking frame or slide member 60 and its associated mechanism, which initially is supported on the main frame through the piston structures 166 and 168 and the columns of hydraulic fluid under pressure within these piston structures and the associated cylinders 162 and 164. However, it is to be noted that upward acceleration of the recoclcing frame 60 is minimized by the previously described control circuit means which causes the check valves 32% and 32.2 to open for permitting fluid to drain from the cylinders 162 and 164 substantially immediately after the release of the ram. The arrangement is such that, at the instant of ram impact, the recocking frame tl is no longer mechanically or hydraulically supported on the main frame. Furthermore, since the piston structures 166 and 168 are slidable relative to the main frame, in the manner previously described, the recocking frame 60 is free to float in space substantially independently of the main frame at the moment of ram impact. Thus, the ram does not serve to stop any upward movement of the recocking frame 60 as it does serve to stop the upward movement of the main frame, and any inertia forces which may be provided by the recocking frame are not imposed on the main frame of the machine or the ram, whereby to minimize any possibility of injury to the main frame as a result of impact and inertia forces which must be absorbed thereby.

In order to decelerate the recocking frame 60 and its associated mechanism, which, as indicated above, is effectively disconnected from the main frame at the moment of ram impact, dashpot devices 338 and 340 are connected with opposite sides of the frame member 60 as shown in FIGS. 1, 2 and 4d. Each of these devices comprises a cylinder 342 having a piston slidable therein and connected by means of a rod 344 with the frame 60. The devices may utilize known constructions for providing resistance to the movement of the piston within the cylinder 342 for providing the desired braking eflect. Since the acceleration of the recocking frame 60 is minimized by releasing the fluid within the cylinders 162 and 164 in the manner described above, the deceleration of this frame member may be readily controlled by the devices 3 33 and 340 which have their lower ends fixed to the floor or any other suitable support structure separate from the main frame of the machine.

Referring again to FIG. 7, it is seen that the control system includes a limit switch 346 adapted to be engaged and closed by a dog 348 carried by the recocking frame when the recocking frame has moved from its raised position to a lowered position at which the latch means may again be engaged with the ram. The limit switch is suitably connected with the power lines L-l and L-2 and with a solenoid 356 by wires 352 and 354. The solenoid is associated with and adapted to control a spring biased valve 356 having a first port 358 connected with 9 the hydraulic pressure line 258 by a branch conduit 360.

The valve 356 includes another port 362 connected with the conduit 278 by a branch conduit 364, a third port 366 connected with the pilot device 254 of the valve 252 by a conduit 368, and still another port 370 connected with the reservoir by a conduit 372.

The valve 356 is spring biased so that, when the solenoid 350 is deenergized, the ports 358 and 362 are blocked and the port 366 is connected with the drain port 37 0. When the recocking mechanism has reached its lowermost position and the limit switch 346 is closed, the solenoid 350 is deenergized and the valve 356 is shifted for connecting the port 358 with the port 366, and the port 362 with the drain port 370. Hydraulic fluid under pressure is then directed to the pilot device 254 for shifting the valve 252 in a manner which causes the cylinders 94 and 96 to be operated for reengaging the latch means with the ram. At the same time, fluid forced from the inner ends of the cylinders 94 and 96 is directed through the conduits 270 and 278 to the reservoir through the valve 356. Since the conduit 278 is connected directly with the reservoir through the valve 356, the pressure on the check -valve control devices 328 and 330 is relieved so that the check valves 320 and 322 are closed. The limit switch 346 is also connected by wires 374 and 376 between the power supply and a relay in the con- .trol panel 281 which is connected by wires 391 and 393 with a solenoid 378 associated with a spring biased valve 380. The valve has a normally blocked inlet port 382 connected by conduit 384 with a conduit 386 that is in turn connected to the port 230 of the valve 224. The -valve'380 also has a drain port 388 connected with the reservoir by suitable conduit 390. The control panel 281 is wired so that the starting relay therein is also operatively connected with the limit switch 346. The arrangement is such that when the limit switch 346 is closed, the starting relay is actuated so that the solenoid 232 is deenthe limit switch 394 is closed whereupon relay means in the control panel 281 is operated for deenergizing the solenoid 378.

The limit switch 394 is suitably connected to an associated relay in the control panel by wires 395 and. 397, which relay is connected by means of wires 396 and 398 with the solenoid 284 associated with the valve 282.

When the switch 394 is closed, the solenoid 284 is energized for shifting the valve 282 to connect the inlet port 238 with the port 292 for directing fluid under pressure through the check valves 298 and 300 and into the cylinders 162 and 164 for raising the recocking mechanism which, as explained above, has already been reengaged with the ram.

When the recocking mechanism reaches its uppermost position, the dog 348 engages and actuates a limit switch 400 which is suitably connected by wires 402 and 404 with 'the relay and'control panel 381 for deenergizing the solenoid 284 so that the valve 282 is shifted for blocking the inlet port 288.

It is contemplated that under certain circumstances it may be desirable manually to control raising of the recocking mechanism. This may be accomplished by providing the relay or control panel 281 with a switch suitably electrically connected with the solenoid 284 and manually operable by a push button 406. In order to preclude any possibility of any injury to the apparatus during manual raising of the recocking mechanism, a mechanically operable, normally closed valve 408 is positioned to be actuated by a finger 410 carried by the recocking mechanism. The arrangement is such that the finger 410 is adapted to actuate and open the normally closed valve 408 when the recocking mechanism has reached its uppermost position. The valve 408 has one port connected by a conduit 412 with the pressure line 296, and another port connected by a drain line 414 with the reservoir.

It is contemplated that there are many instances in which it may be desirable to release the ram from a position beneath its normal fully raised or uppermost position. Thus, the control circuit is provided withmeans whereby the ram may be manually lowered to the desired intermediate position or even to its lowermost position. This means includes a switch in the control panel 281 manually operable by a push button 416 and suitably connected by wires 418 and 420 with the solenoid 286. When the button 416 is depressed, the solenoid 286 is energized for shifting the valve 282 in a manner which causes the pressure inlet port 288 to be connected with the port 306 while the port 292 is connected with the drain port 312. This causes fiuid under pressure to be directed to the check valve actuating devices 302 and 304 for opening the check valves 298 and 300 and permitting fluid to flow from the cylinders 162 and 164 through the check valves 298 and 300 and back to the reservoir in order to lower the recocking mechanism and thus the ram.

While the preferred embodiment of the present invention has been shown and described herein, it is obvious that many details may be changed without departing from the spirit and scope of the appended claims.

The invention is claimed as follows:

1. A machine of the type described, comprising a onepiece completely metal frame including a head portion, a

relatively heavy base portion spaced from said head portion and side elements extending from said head portion and having integral junctions with said base portion, a ram disposed for reciprocal movement between said head I and base portions, sealed high pressure pneumatic means on said head portion for actuating said ram through a working stroke at a high Velocity and directing the ram against a workpiece with a high impact force, means for recocking and releasably retaining said ram including a latch structure mounted for movement along said frame between said head and base portions, means for actuating said latch structure between said head and base portions, said base portion including a rounded seat oppositely from said ram and substantially merging with said junctions, and a metal pad member separate from and substantially complementary to and fitting within said seat for supporting a workpiece to be processed and for distributing impact loads across said base portion in a manner which minimizes stress concentrations at said junctions.

2. A machine, as defined in claim 1, wherein said means for actuating said ram comprises a spherical pressure chamber, said ram including an elongated portion siidably extending into said chamber.

3. A machine, as defined in claim 1, wherein said seat and said pad member have a semicylindrical configuration.

4. A machine of the type described, comprising a metal main frame comprising a hollow head portion providing a high pressure pneumatic chamber, a relatively heavy base portion spaced from said head portion, and a plurality of side elements extending from said head portion and having junctions with said base portion, a ram telescopically associated with and extending into said pressure chamber for actuation by fluid pressure therein at a high velocity through a working stroke between a cooked position and an extended position, said base portion including a generally semicylindrical seat oppositely from said ram and substantially merging with said junctions, a substantially semicylindrical metal pad member separate from and complementary to and removably fitting within said seat for supporting a workpiece to be processed and for distributing impact loads across said base portion, and means for recocking and releasably retaining said ram at the cocked position including latch means releasably engageable with the ram and extended positions, and means for actuating said latch means between said cocked and extended positions and connected with and supporting said latch means from said main frame while the latch means is engaged with the ram and is moving toward or retained at said cocked position and for effectively disconnecting said latch means from said main frame while said ram is moving through its work stroke.

5. A machine of the type described, comprising a one piece main frame including a hollow head portion providing a pressure chamber, a relatively heavy base portion spaced from said head portion, and a plurality of side elements extending from said head portion and having integral junctions with said base portion, a ram telescopically associated with and extending into said pressure chamber for actuation by fluid pressure therein at a high velocity through a working stroke, said base portion including a generally semi-cylindrical seat oppositely from said ram and substantially merging of said junctions, and a substantially semi-cylindrical pad member complementary to and fitting within said seat for supporting a workpiece to be processed and for distributing impact loads across said base portion, said ram being movable between a retracted and cocked position and an extended position, said machine including means for returning said ram to and releasably retaining the ram in said cocked position, said cocking and retaining means comprising a cocking frame shiftable along said first mentioned frame between said extended and cocked positions, means on said cocking frame for releasably engaging the ram, means on said cocking frame for releasably locking said ram engaging means, and means for actuating said cocking frame between the extended and cocked positions and for supporting said cocking frame on said first mentioned frame while the ram is being moved toward and retained in said cocked position and for effectively disconnecting said cocking frame from said first mentioned frame while said ram is moving during a working stroke toward said extended position.

6. A machine of the type discribed, comprising a main frame including spaced apart head and base portions and connecting elements extending between said portions, pressure actuating means on said head portion, a ram assembled with and operable by said actuating means through a work stroke between extended and cocked positions, and means for recocking and releasably retaining said ram including a cocking frame mounted for movement along said main frame between said cooked and extended positions, latch means on said cocking frame for releasably engaging and retaining said ram, releasable locking means for preventing accidental release of said latching means, and means for actuating said cocking frame between said cocked and extended positions.

7. A machine, as defined in claim 6, which includes a plurality of said latch means spaced around said ram and a plurality of said locking means respectively associated with said latch means, and means for sequentially actuating and releasing said locking means and then simultaneously actuating all of said latch means for releasing the ram.

8. A machine, as defined in claim 6, wherein said latch means comprising a pivotally supported member, a roller element on said pivotally supported member engageable beneath a portion of said ram, and means for shifting the pivotally supported member for selectively engaging said roller element with and disengaging the roller element from said ram.

9. A machine as defined in claim 8, wherein said latch means includes fluid pressure actuated means connected with said pivotally mounted member for operating the pivotally supported member for engaging the roller element with the ram,

10. A machine, as defined in claim 6, wherein said means for actuating said cocking frame between said cocked and extended positions includes complementary fluid cylinder and piston means acting between said cocking frame and said main frame for shifting the cocking frame toward and releasably retaining the cocking frame at said cocked position, one of said last named means being connected to one of said frames and the other of said last named means being axially shiftably connected to the other of said frames, means limiting axial movement in one direction between said other of said last named means and said other frame while permitting such relative movement in an opposite direction for supporting said cocking frame while the ram is being shifted toward or retained in said cocked position and for effectively disconnecting said cocking frame from said main frame during movement of the ram through its Working stroke.

11. A machine of the type described, comprising a main frame including spaced apart head and base portions and connecting elements extending between said portions, a ram movable through a working stroke between said portions and to and from extended and cocked positions, pressure means on said head portion for actuating said ram through said working stroke, and means for recocking and releasably retaining said ram including a latch structure mounted for movement along said main frame between said cocked and extended positions, means for actuating said latch structure between said cocked and extended positions, said latch structure comprising a pivotally mounted member, a roller element on said pivotally mounted member and engageable beneath a portion of said ram, and means for shifting said pivotally mounted member for engaging said roller element and disengaging the roller element from said ram.

12. A machine, as defined in claim 11, wherein said roller element comprises a plurality of circumferentially spaced recesses substantially complementary to and adapted to receive a marginal portion of the ram.

13. A machine of the type described, comprising a main frame including spaced apart head and base portions and connecting elements extending between said portions, a ram movable through a work stroke toward said base portion and between extended and cocked positions, fluid pressure means on said head portion for actuating said ram through said work stroke, and means for recocking and releasably retaining said ram at the cocked position including latch means releasably engageable with the ram and mounted for movement along said main frame between said cocked and extended positions, and means for actuating said latch means between said cocked and extended position and connected with and supporting said latch means from said main frame while the latch means is engaged with the ram and is moving toward or retained at said cocked position and for effectively disconnecting said latch means from said main frame while said ram is moving through its work stroke.

14. A machine, as defined in claim 13, which includes motion arresting means connected between said latch means and anchored separately from said main frame for arresting motion which may be imparted to the latch means as a result of reaction forces created upon movement of the ram through its working stroke.

15. A machine, as defined in claim 13, wherein said means for recocking and releasably retaining the ram comprises a cocking frame supporting said latch means and mounted for movement along said main frame between said cocked and extended positions, and said means for actuating and supporting said latch means from and disconnecting the latch means with respect to the main frame comprises complementary fluid cylinder and piston means acting between said cocking frame and said main frame.

16. A machine, as defined in claim 15, which includes means for introducing hydraulic fluid under pressure into said cylinder means for actuating the cylinder means for moving said cocking frame toward and retaining the cocking frame in said cocked position, and means for relieving the pressure of said hydraulic fluid substantially immediately upon the start of downward movement of the ram.

17. A machine, as defined in claim 15, wherein said cylinder means is fixed with respect to said cocking frame, said piston means includes a passageway therethrough for accommodating How of hydraulic fluid into and out of said cylinder means, and said machine including coupling 10 means having a sliding connection with said piston means and supported separately from both of said frames for connecting the piston means with a source of hydraulic fluid.

References Cited in the file of this patent UNITED STATES PATENTS Shipway Jan. 26, 1904 Irvine Feb. 11, 1913 Schneider May 1, 1934 Myercord et a1 Apr. 30, 1935 Oeckl et al. June 20, 1939 Chapman Oct. 3, 1939 Fitzgerald et a1. Oct. 29, 1940 Steinfort et al Dec. 9, 1958 Kandall et al. Dec. 1, 1959 Smith Nov. 28, 1961 Ottestad et a1. May 29, 1962

Claims (1)

1. A MACHINE OF THE TYPE DESCRIBED, COMPRISING A ONEPIECE COMPLETELY METAL FRAME INCLUDING A HEAD PORTION, A RELATIVELY HEAVY BASE PORTION SPACED FROM SAID HEAD PORTION AND SIDE ELEMENTS EXTENDING FROM SAID HEAD PORTION AND HAVING INTEGRAL JUNCTIONS WITH SAID BASE PORTION, A RAM DISPOSED FOR RECIPROCAL MOVEMENT BETWEEN SAID HEAD AND BASE PORTIONS, SEALED HIGH PRESSURE PNEUMATIC MEANS ON SAID HEAD PORTION FOR ACTUATING SAID RAM THROUGH A WORKING STROKE AT A HIGH VELOCITY AND DIRECTING THE RAM AGAINST A WORKPIECE WITH A HIGH IMPACT FORCE, MEANS FOR RECOCKING AND RELEASABLY RETAINING SAID RAM INCLUDING A LATCH STRUCTURE MOUNTED FOR MOVEMENT ALONG SAID FRAME BETWEEN SAID HEAD AND BASE PORTIONS, MEANS FOR ACTUATING SAID LATCH STRUCTURE BETWEEN SAID HEAD AND BASE PORTIONS, SAID BASE PORTION INCLUDING A ROUNDED SEAT OPPOSITELY FROM SAID RAM AND SUBSTANTIALLY MERGING WITH SAID JUNCTIONS, AND A METAL PAD MEMBER SEPARATE FROM AND SUBSTANTIALLY COMPLEMENTARY TO AND FITTING WITHIN SAID SEAT FOR SUPPORTING A WORKPIECE TO BE PROCESSED AND FOR DISTRIBUTING IMPACT LOADS ACROSS SAID BASE PORTION IN A MANNER WHICH MINIMIZES STRESS CONCENTRATIONS AT SAID JUNCTIONS.

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