US3336788A

US3336788A - High energy impact machines

Info

Publication number: US3336788A
Application number: US356544A
Authority: US
Inventors: Jack B Ottestad; Gerald J Farrell
Original assignee: US Industries Inc
Current assignee: US Industries Inc
Priority date: 1964-04-01
Filing date: 1964-04-01
Publication date: 1967-08-22
Anticipated expiration: 1984-08-22
Also published as: GB1072747A; CH441945A

Description

Aug. 22, 1967 J. B. OTTESTAD ETAL 3,336,788

HIGH ENERGY IMPACT MACHINES 6 Sheets-Sheet 1 Filed April 1, 1964 w T N E /V m w W 5 m u r/Q fi u F JACK B. OTTESTAD QERALD J. FARRELL Aug. 22, 1967 J. B. OTTESTAD ETAL 3, 36,788

HIGH ENERGY IMPACT MACHINES Filed April 1, 1964 6 Sheets-$heet 2 f TZ Y Cwl w "i Wu, q]

AI-IgQZZ, 1967 J. B. OTTESTAD ETAL 3,336,788

I HIGH ENERGY IMPACT MACHINES Filed April 1, 1964 6 Sheets-Sheet 5 INVENTORS JACK B. OTTESTAD GERALD .J. FARRELL Aug. 22, 1957 J. B. OTTESTAD ETAL 3,336,788

' HIGH ENERGY I MPACT MACHINES Filed April 1, 1964 e Sheets-Sheet 4 mumg u III JIHEHHI JACK B. OTTESTAD GERALD B. FARRELL li w MvQA United States Patent 3,336,788 HIGH ENERGY IMPACT MACHINES Jack B. Ottestad, La Jolla, Calif., and Gerald J. Farrell, Park Forest, 111., assignors to US. Industries, Inc., New York, N.Y., a corporation of Delaware Filed Apr. 1, 1964, Ser. No. 356,544 15 Claims. (Cl. 72-453) ABSTRACT OF THE DISCLOSURE High energy impact machine wherein driver piston is isolated from the source of working fluid used in driving it, when the machine is cocked and ready to fire, and firing is triggered by the feeding of working fluid from said source to the portion of said piston acted upon by said working fluid during driving thereof.

machines have proven to be highly practical and successful in operation. It is an important object of the present invention to afford improvements over such high-energy rate mchines as have been heretofore known in the art.

In high-energy impact machines of the type to which the present invention relates, two plates are moved together by a suitable pressurized elastic medium such as a compressed gas, forcing a driver piston and a cylinder to move in opposite directions. In such machines the pressure exerted on the pistons and cylinders is relatively high, such as, for example, 1,500 pounds per square inch, or more, with the plates delivering 145,000 foot pounds of energy, or more, at impact. Also, in such machines it is not uncommon for the plates thereof to accelerate from a stationary condition to a closure rate of 50 feet per second, or more, in a total stroke distance between the two plates of twelve inches.

High-energy impact machines of the preferred type of construction shown herein, and in the aforementioned copending application, Ser. No. 190,524, now Patent No. 3,135,140, embody two driver assemblies, each including a driver piston and a cylinder. In the operation thereof, when the machine is cocked and ready to be fired, the pistons are disposed in such position in the respective cylinders that they are effective to prevent the flow of the high pressure gas, by which the driver assemblies are to be actuated, from the source thereof into the cylinders; and, thereafter, in firing the machines, the pistons are moved out of such cocked position into a firing position effective to permit the gas to flow into position in the cylinders effective to drive the pistons and cylinders apart, the flow of gas into the cylinders being so rapid, when the pistons are moved into the firing positino, that the driver assemblies are substantially instantaneously subjected to the full pressure of the source of gas. Under such conditions, the acceleration of the driver assemblies is very fast. Therefore, if in the movement of the pistons from cocked position to firing position, one piston leads the other into firing position by even a minute fraction of a second, the tendency to tilt the platesice plates places an excessive strain on the machine, tending to force the guides for the plates outwardly away from each other, among other things. It is an important object of the present invention to insure that the driver pistons of such high-energy impact machines all move simultaneously into firing position without any time lag between them.

An object ancillary to the foregoing is to effect the movement of all such pistons in such a machine into firing position in a novel expeditious manner.

Another object of the present invention is to afford a novel machine of the aforementioned type wherein such movement of all of the pistons thereof into firing position may be simultaneously effected in a novel and expeditious manner by gas pressure.

Another object is to afford a novel machine of the aforementioned type wherein the pressurized gas from the source used to fire the machine may be used to move the pistons into such firing positions.

A further object is to afford a novel machine of the aforementioned type embodying a novel chamber, constituted and arranged in a novel and expeditious manner therein for storing the pressurized gas used in firing the machine.

In high-energy impact machines heretofore known in the art of the type to which the present invention appertains, the driver pistons thereof have commonly embodied bleed passageways therethrough, the bleed passageways opening at both ends thereof into a respective end portion of the cylinders in which the pistons are disposed. With such construction, when the high pressure gas flows into the cylinders on one side of the pistons during a firing operation, it flows through such bleed passageways into the portion of the cylinders, disposed on the side of the respetcive pistons remote from the aforementioned one side at a high velocity. The velocity of such flow through the bleed passageways is sufiiciently high that the heat caused by the friction of the gas passing therethrough is suflicient to create a serious problem, tending to distort the pistons, and tending to cause the pistons to seize in the cylinders. The pistons being in the interior of such machines, cooling thereof is difficult to achieve, and, therefore, such heating of the pistons necessitates a slower rate of repeat firing of the machine than would be possible without the problem of overheating. It is a further object of the present invention to afford a novel machine of the aforementioned type wherein the parts thereof are so constituted and arranged that no heating, sufiicient to cause such a problem, occurs.

Another object is to enable the equalizing of the pressures on the opposite sides of the driver pistons thereof to be accomplished in a novel and expeditious manner.

Another object is to afford a novel high-energy impact machine of the aforementioned type which is relatively small and compact in size, while having a relatively high impact force capacity.

A further object is to afford a novel high-energy impact machine of the aforementioned type which is practical and efiicient in operation, and which may be readily and economically produced commercially.

Other and further objects of the present invention will be apparent from the following description and claims and are illustrated in the accompanying drawings which, by way of illustration, show a preferred embodiment of the present invention and the principles thereof and what we now consider to be the best mode in which we have contemplated applying these principles. Other embodiments of the invention embodying the same or equivalent principles may be used and structural changes may be made as desired by those skilled in the art without departing from the present invention and the purview of the appended claims. 9

In the drawings:

FIG. 1 is a front view, partly in cut-away section and partly schematic, illustrating a high-energy impact machine embodying the principles of the present invention;

FIG. 2 is a detail sectional view of the upper plate in the machine shown in FIG. 1 taken substantially along the line 2-2 in FIG. 1;

FIG. 3 is an enlarged detail sectional view taken substantially along the line 3-3 in FIG. 2;

FIG. 4 is an enlarged, fragmentary detail sectional view taken substantially along the line 4-4 in FIG. 1;

FIG. 5 is a schematic view of the machine shown in FIG. 1 illustrating the position of various parts thereof before charging;

FIG. 6 is a view similar to FIG. 5 illustrating the machine in charged condition;

FIG. 7 s a view similar to FIG. 5 illustrating the machine in cocked position, wherein it is ready to be triggered for firing;

FIG. 8 is a view similar to FIG. 5 illustrating the machine in fired position;

FIG. 9 is a schematic diagram of the hydraulic and gas circuits of the machine shown in FIG. 1; and

FIG. 10 is a schematic diagram of the electrical circuits of the machine shown in FIG. 1.

A machine 1, embodying the principles of the present invention is shown in the drawings to illustrate the presently preferred embodiment of the present invention. The machine 1 embodies, in general, an upright frame 2 having two plates 3 and 4 slidably mounted in gibs 5 and 6 therein for movement toward and away from each other, two driver mechanisms 7 and 8 being connected to the plates 3 and 4, respectively, for driving the plates 3 and 4 vertically along the gibs 5 and 6 toward each other, as will be discussed in greater detail presently.

Only the one driver mechanism 8 will be discussed in detail, it being understood that the driver mechanism 7 is identical thereto. Each of the driver mechanisms 7 and 8 includes a cylinder 9 mounted on the projecting upwardly from a respective end portion of the upper plate 3. The lower ends of the cylinders 9 extend downwardly into the upper plate 3. A main chamber or high pressure chamber 10 extends between the lower end portions of the cylinders 9 in the upper plate 3. The main chamber 10 embodies four elongated, substantially cylindricalshaped compartments 11, 12, 13, and 14 disposed in substantially parallel spaced relation to each other, FIGS. 2 and 3, and each of the compartments 11-14 is connected by a respective opening 15 into the lower end portion of each of the cylinders 9. The outer ends of the compartments 1114 in the upper plate 3 are plugged to prevent the escape of gas therefrom.

Each of the driver mechanisms 7 and 8 also includes a driver piston 16 reciprocably mounted in the cylinder 9 thereof. The driver pistons 16 are sealingly and slidingly engaged with the side walls of the respective cylinders 9, and have respective mounting posts 17 connected thereto and extending downwardly therefrom through the upper plate 3. The pistons 16 are adapted to seat on respective annular valve seats 18 mounted in the lower end portions of the respective cylinders 9, when the pistons 16 are disposed in lowermost position in the cylinders 9. When the pistons 16 are disposed in such owermost position in the cylinders 9, an auxiliary chamber or triggering chamber 19 is defined within each valve seat 18 by the lower end of the respective cylinder 9 and the lower face of the respective piston 16, FIG. 6. When the pistons 16 are disposed in raised position in the cylinders 9, the chamber 10, the interior of the cylinders 9, and the triggering chambers 19 are in direct communication with each other. However, when the pistons 16 are disposed in the aforementioned lowermost position in the cylinders 9, they are disposed in position to cover and close off the openings 15 and thereby said off communication of the main chamber 10 with the cylinders 9 and the triggering chambers 19 through the openings 15.

The lower end of each of the posts 17 is connected to the lower plate 4 by suitable connecting members 21 and 22, so that the lower plate 4 is movable in the gibs 5 and 6 upwardly and downwardly relative to the upper plate 3 upon movement of the pistons 16 upwardly and downwardly, respectively, relative to the cylinders 9. Each of the posts 17 has an elongated passageway 23 extending longitudinally therethrough, the upper end of the passageway opening upwardly through the piston 16 into the respective cylinder 9. The lower end portions of the passageways 23 are connected by respective trombone tubes 24, a passageway 25, a suitable control valve 26, and a passageway 27 to a suitable source of pressurized gas or pressurized elastic medium, such as, for example, pressurized nitrogen. The lower end portions of the passageways 23 are slidingly connected to the respective trombone tubes 24 by suitable seals 28 to thereby seal the connections between the posts 17 and the trombone tubes 24 against leakage of gas therepast.

The main chamber 10 is disposed longitudinally in the upper plate 3 in downwardly spaced relation to the top face 29 of the plate 3, with the compartments 11-14 disposed in horizontally spaced relation to each other, FIGS. 2 and 3. The compartments 11 and 12, 12 and 13, and 13 and 14 are spaced from each other by webs 30, 31, and 32, respectively. Another passageway 33 extends downwardly through the upper plate 3 from the upper face 29 thereof, FIGS. 2 and 4, the passageway 33 extending downwardly through the web 30 and terminating at its lower end in a passageway 34 extending longitudinally through the upper plate 3 in downwardly spaced relation to the chambers 10 and 19. Each of the ends of the passageway 34 is connected by a respective passageway 35 extending upwardly therefrom and opening into the lower end of a respective cylinder 9 within the confines of the annular sea-t 18 therein, to thereby interconnect each end of the passageway 34 with a respective one of the triggering chambers 19.

Another passageway 36 extends horizontally across the passageway 33 from one side wall 37 of the top plate -3 and terminates at its inner end substantially vertically above the compartment 12 of the main chamber 10, FIG. 4. The inner end of the passageway 36 interconnects with the upper end portion of a passageway 38 which extends downwardly through the plate 3 from the upper face 29 thereof, and terminates at its lower end in direct communication with the compartment 12, FIG. 4.

A valve seat 39 is mounted in the passageway 38 between the interconnection of the latter with the passageway 36 and the compartment 12, and a poppet valve 40 is slida-bly mounted in the valve seat 39 for vertical movement between seating engagement with the valve seat 39 and spaced relation thereto, as shown in solid and broken lines, respectively, in FIG. 4, to thereby close and open the passageway 38. The valve 40 is effective to control the triggering of the machine 1 for firing, as will be discussed in greater detail presently.

A hydraulically operated actuator 41 is mounted on the frame 2 above the valve 40 in position to actuate the latter, FIGS. 1 and 4. The actuator 41 includes a housing 42 having an upright cylinder 43 disposed above the valve 40 in vertical alignment therewith, and a piston 44 reciprocably mounted in the cylinder 43 for movement upwardly and downwardly therein, into and out of the housing 42. Two hydraulic lines 45 and 46 are connected into the upper and lower end portions of the cylinder 43, and are connected through suitable valving to a suitable source of hydraulic fluid, as will be discussed in greater detail presently, for feeding hydraulic fluid under pressure into the upper end lower end portions of the cylinder 43 and thereby force the piston 44 downwardly and upwardly, respectively. Downward movement of the piston 44 is effective to push the poppet valve 40 into open position, and upward movement of the piston 44 is effective to permit the poppet valve 40 to move upwardly into closed position.

The upper end portion of the passageway 33 is connected to a trombone tube 47 which is mounted on and projects downwardly from the upper portion of the frame 2, FIG. 4. The passageway 33 is slidingly connected to the trombine tube 47 by a suitable seal 51 to prevent the leakage of gas therebetween, and the upper end portion of the trombone tube 47 is connected by a passageway 48, a valve 49, and a passageway 50 to the passageway 25 and, therefore, the valve 26, FIG. 1. It will be remembered that the valve 26 is connected to a suitable source of pressurized gas, and, therefore, it will be seen that when the valves 26, 49, and 40 are open, passageways 23, 25, 50, 48, 33, 36 and 38 afford passageways for simultaneously feeding gas from said source into the cylinders 9 and the chambers 10 and 19 irrespective of the position of the pistons 16 in the cylinders 9. Thus, with the valves 26, 49, and 40 open, the entire gas circuit for firing the machine 1 may be filled with pressurized gas from the gas source connected to the valve 26 as illustrated diagrammatically in FIG. 9.

In the preferred form of the machine shown in the drawings, the outer end of the passageway 36 extends through the side wall 37 of the upper plate 3 to facilitate the formation of the passageway 36 in the plate 3, and is plugged by a suitable plug 52, the connection between the valve 49 and the passageway 33 being made through the trombone tube 47 and the passageway 48. However, as will be appreciated by those skilled in the art, if desired, the connection between the valve 49 and the passageway 33 may be made through the outer end of the passageway 36, the plug 52 being removed for such purposes, and, in that event, the upper end of the portion of the passageway 33 above the passageway 36 would be suitably closed such as, for example, by a suitable plug, not shown.

The valve 49 is preferably of the same construction as the trigger valve mechanism 39-41, embodying a poppet valve 53 which is movable into and out of engagement with a valve seat 54, and embodying a hydraulically operated actuator 55 which is identical in construction to the actuator 41, as illustrated diagrammatically in FIG. 9. In the operation of the machine 1 the opening and closing of the valves 40 and 49 is controlled by the actuators 41 and 55, as will be discussed in greater detail presently.

Two compensating or counter balancing units 56 are mounted at respective ends of the upper plate 3 for supporting the latter against the force of gravity, FIGS. 1 and 9. Each of the counter balancing units includes a cylinder 57 connected to the frame 2 in depending relation thereto above the upper plate 3, and has a piston 58 sealingly and slidably mounted in the cylinder 57 and connected to the upper plate 3 by a piston rod 59 extending downwardly through the cylinder 57. The cylinder 57 of each of the counter-balancing units '56 is filled with compressed gas below the proton 58 therein so that the force of the compressed gas is such as to overcome the force of gravity on the plate 3. The counter-balancing units 56 are also effective to return the upper plate 3 to raised position after a firing of the machine 1, as will be discussed in greater detail presently.

Each of the driver mechanisms 7 and 8 also includes a floating piston 60 sealingly and slidably engaged in the cylinder 9 thereof above the piston 16 in that cylinder. The floating piston 60 is preferably cup-shaped both upwardly and downwardly, having an upwardly opening concavity 61 and a downwardly opening concavity 62 therein FIG. 1. The floating pistons 60 in the driver mechanisms 7 and 8 are reciprocable longitudinally of the cylinders 9 between a fully raised position, as shown in FIGS. 1 and 5, and a fully lowered position as shown in FIG. 6.

Two tubes 63 are threaded into the upper ends of respective ones of the cylinders 9, and project upwardly through the upper end of the frame 2 into vertically extending cylinders 64 mounted thereon. Each of the tubes 63 includes a guide piston 65 sealingly and slidingly engaged with the side walls of a guide cylinder 66 mounted in the respective cylinder 64. The guide cylinders 66 are sealed at their lower ends to the respective cylinders 64 in which they are mounted, and above the lower ends are spaced radially inwardly therefrom, terminating at their upper ends in downwardly spaced relation to the upper ends of the respective cylinders 64. Suitable conduits, such as pipes 68 are connected to the lower end portions of the cylinders 64 above the seals 67 for feeding hydraulic fluid into the guide cylinders 64, the fluid thus fedinto the cylinders 64 flowing upwardly through the passageways 69 defined by the radially spaced portions of the cylinders 64 and 66, and then downwardly through the tubes 63 into the cylinders 9 above the floating pistons 60. The conduits 68 are connected through suitable controls to a suitable source of pressurized hydraulic fluid for feeding hydraulic fluid into and out of the cylinders 9 above the floating pistons 60, as will be discussed in greater detail presently.

In FIGS. 58 of the drawings various steps in the operation of the machine 1 are diagrammatically illustrated. Thus, for example, in initially preparing the machine 1 for operation, the valves 26, 40, and 49 may all be opened and a suitable pressurized elastic medium, such as, for example, compressed nitrogen may be fed from a suitable gas source through the valves 26, 40, 49 into the cylinders 9 and the chambers 10 and 19 to thereby completely fill the gas circuit of the machine 1 with the pressurized gas, as illustrated in FIG. 5, and the valve 26 may then be closed.

After the gas circuit of the machine 1 has thus been filled with gas to the desired proper pressure, the pistons 60 may be moved downwardly in the cylinders 9 by hydraulic fluid pressure applied to the upper faces of the pistons 60. This downward movement of the floating pistons 60 is effective to move the pistons 16 downwardly into seating engagement with the annular seats 18 and to compress all of the gas in the machine 1 to a high pressure, as illustrated in FIG. 6.

Thereafter, the triggering valve 40 is closed by means which will be described in greater detail presently, to thereby close off communication between the main chamber 10 and the triggering chambers 19. With the valve 49 remaining open the hydraulic fluid above the floating piston 60 is then released to sump, permitting the floating pistons 60 to move upwardly in the cylinders 9. During this movement of the pistons 60, the pressurized gas in the passageways 36, 33, 34, 35, 48, 5t), 25 and 23, the triggering chambers 19, and the valve 49 expand into the cylinders 9 above the driver pistons 16, and the pressure thereof equalizes throughout this portion of the gas circuit at a relatively low pressure as compared to the pressure in chamber 10, as illustrated in FIG. 7.

In this connection it will be noted that during both charging and venting of the machine 1, FIGS. 6 and 7, gas is trapped between the pistons 60 and the pistons 16, which is substantially at the same pressure as the gas in the triggering chambers 19. Because of the greater area of the pistons 16 subjected to the pressure of gas between the pistons 16 and the floating pistons 60, as compared to the area of the pistons 16, subjected to the pressure of gas in the triggering chambers 19, the gas pressure above the pistons 16 retains the pistons 16 in seated relation to the annular seats 18 during the aforementioned upward movement of the floating pistons 60. When, during the aforementioned upward movement of the pistons 60, they reach their fully raised positions, as shown in FIG. 7, the valve 49 is closed, and, therefore, at this stage of the operation of the machine 1, the main chamber 10 is pressurized to a high pressure, the valve 40 remaining closed, and the remainder of the gas circuit of the machine 1 is at the low pressure, so that the machine 1 is in cocked condition ready to be triggered for firing.

In the firing of the machine 1, the valve 40 is moved into open position. The opening of the valve 40 permits high pressure gas to flow from the main chamber through the passageways 38, 36, 33, 34, and 35 into the triggering chambers 19 to substantially instantaneously subject the lower faces of the driver pistons 16 and the lower ends of the cylinders 9 to the full pressure of the main chamber 10, and thereby quickly unseat the driver pistons 16 and uncover the openings connecting the cylinders 9 to the main chamber 10. The uncovering of the openings 15 permits high pressure gas to flow therethrough from the main chamber 10 into the cylinders 9 below the pistons 16, and thereby continues to subject the lower faces of the driver pistons 16 and the lower ends of the cylinders 9 to the full pressure of the main chamber 10, as the pistons 16 and lower ends of the cylinders 9 are accelerated away from each other. The force of the gas thus released into the cylinders 9 from the main chamber 10 causes the driver pistons 16 to be accelerated upwardly at a high rate, and causes the cylinders 9 to be accelerated downwardly at a high rate. The acceleration of the driver piston 16 and the cylinders 9 causes the lower plate 4 and the upper plate 3, respectively, to be likewise accelerated, and brings the plates 3 and 4 together at a relatively high impact speed. The movement of the plates 3 and 4 toward each other is effective to cause die parts 63 and 64 carried thereby to be brought together in the same manner, to thereby perform a forming action on a piece of metal, not shown, placed therebetween.

A machine constructed according to the construction shown herein may operate on less than ten-second cycles and may deliver as much as 145,000 foot pounds of energy where the weight of the plates 3 and 4 are approximately 4800 pounds each and where normal operating gas pressure is 1500 pounds per square inch, with the plates having a combined stroke of twelve inches.

Referring now primarily to FIGS. 9 and 10', in the operation of the machine 1 the selector switch SS-l, FIG. 10, may first be closed to thereby operatively connect the power lines 70 and 71 to a suitable source of electric power 72. Thereafter, the two push button switches PB1 and PB-2 may be closed to thereby energize the two motors 73 and 74, respectively. The motors 73 and 74 may be connected to suitable hydraulic pumps, not shown, affording the high pressure oil source 75, FIG. 9, for feeding hydraulic fluid under pressure through the lines 79 and 81, respectively, of the machine 1. The closing of the push button switches PB-l and PB-2 are also effective to energize the holding relay coils HR-l and HR-2 to thereby close the normally open relay contacts HR-l' and HR2, respectively, and thus afford holding circuits effective to maintain energization of the motors 73 and 74 until the push botton switches PB-3 and PB-4 are moved into open position to thereby open the circuits to the motors 73 and 74 and the holding relays HR-l and HR2. When the motors 73 and 74 are thus energized, the incandescent lamps 76 and 77 are illuminated to thereby indicate that the motors 73 and 74 are running and hydraulic pressure is available for the hydraulic circuit of the machine.

The actuators 41 and 55 for the valves 40 and 49, respectively, are operatively connected to solenoid valves SV2 and SV4, respectively, FIG. 9, for controlling the operation thereof. The solenoid valve SV2 is connected by a hydraulic line 80 to a high pressure hydraulic line 81 connected to the high pressure oil source 75. The solenoid valve SV2 is also connected by the two hydraulic lines 45 and 46 to the upper and lower ends of the cylinder 42 of the actuator 41. The solenoid valve SV2 is so constructed that when it is not energized, hydraulic fluid is fed under pressure through the line 45 into the actuator 41 to thereby force the piston 44 thereof downwardly and move the valve 40 into open position, the hydraulic fluid below the piston 44 being fed through the line 46 and the valve SV2 to sump 82. Energization of the solenoid valve SV2 is effective to reverse the connections of the lines 45 and 46, the line 46 then being connected to the high pressure hydraulic line 81, and the line 45 then being connected to sump 82, to thereby move the piston 44 upwardly in the actuator 41 and permit the valve 40 to move upwardly into closed position.

The solenoid valve SV4 is connected between the high pressure hydraulic line 81 and the actuator 55 for the valve 49 in a reverse manner from that in which the solenoid valve SV2 is connected between the hydraulic line 81 and the actuator 41, FIG. 9. The valve SV-4 is connected by a line 84 to the hydraulic line 81, and by two lines and 86 to the bottom and top, respectively, of the actuator 55. Energization of the solenoid valve SV4 is effective to cause hydraulic fluid to flow from the line 81 through the line 86 to the upper portion of the actuator 55, and permit hydraulic fluid to flow from the bottom portion of the actuator 55 through the line 85 to sump 82. Thus, energization of the solenoid valve SV4 is effective to so actuate the actuator 55 that the valve 49 is opened thereby. When the solenoid valve SV-4 is not energized it is effective to reverse the connections of the lines 85 and 86, the line 85 then being connected to the high pressure line 81, and the line 86 then being connected to sump 82 to thereby move the piston of the actuator 55 upwardly therein and permit the valve 49 to move into closed position.

Thus, it will be seen that after operation of the motors 73 and 74 has been initiated in the aforementioned manner, so that hydraulic fluid under pressure is present in the hydraulic line 81, and with both of the solenoid valves SV2 and SV-4 deenergized, the actuator 41 is effective to open the triggering valve 40, and the actuator 55 is effective to permit the vent valve 49 to close. If, at this time, the gas circuit of the machine 1 has not been initially charged with low pressure gas, or it is desired to feed additional gas into the gas circuit of the machine 1, these things may now be accomplished by opening the valve 49 and the valve 26. Opening of the valve 49 may be accomplished by closing the selector switch SS-3, FIG. 9, to thereby energize the valve SV4 and thus cause the actuator 55 to move the valve 49 into open position. The valve 26 may then be opened to permit the flow of gas through the valves 40 and 49 into the gas circuit of the machine 1, the pressure equalizing throughout the gas circuit, as illustrated in FIG. 5, as previously described. When the gas circuit has been pressurized to the desired pressure, the valve 26 may be closed to stop the flow of gas thereinto. Thereafter, the selector switch SS-3 may again be moved into open position, to thereby deenergize the solenoid valve SV-4 and permit the piston in the actuator 55 to move upwardly and thus permit the valve 49 to be closed by the pressure of the gas in the passageway 48.

The machine 1 is then in condition to be charged with high pressure gas. This may be accomplished by moving the selector switch SS-2, FIG. 10, from stop to run position and then closing the charge push button switch PB-S. The closing of the push button switch PB-5 energizes the control relay CR-l to thereby close the normally open relay contacts CR1' to afford a holding circuit around the push button switch PB-5, which may then be permitted to move to open position. The energization of the holding relay CR-l also closes the normally open relay contacts CR1", which energizes the solenoid valve SV-l, FIG. 10. The solenoid valve SV-l may be embodied in the control panel 78, and the energization thereof is effective to connect the hydraulic line 79 to the high pressure oil source 75, FIG. 9. The hydraulic line '79 is connected to the lines 68, which are connected to the cylinders 64, FIGS. 1 and 9, and, therefore, when the solenoid valve SV-l is energized,

9 hydraulic fluid is fed under pressure through the lines 69, the cylinders 64, and the tubes 63 into the cylinders 9 above the floating piston 60 to thereby move the pistons 60 downwardly from the position shown in FIG. into the position shown in FIG. 6.

During this movement of the floating pistons 60 downwardly, the valve 40 remains open, the solenoid valve SV-2 not being energized. Also, during the initial movement of the pistons 60 downwardly the valve 49 remains closed, the solenoid valve SV-4 not being energized.

However, a pressure switch PS-2 is connected to the hydraulic line 79, and is effective to cause the solenoid SV-4 to be energized, to thereby open the valve 49 so that the passageways between the triggering chambers 19 and the cylinders 9 above the pistons 16 are open to permit charging of the entire gas circuit with high pressure gas, illustrated in FIG. 6. The pressure switch PS-2 is such that when the pressure in the hydraulic line 79 is below a relatively high pressure, such as, for example, 1800 pounds per square inch, the pressure switch contacts PS-Z thereof, FIG. 10, are disposed in open position, and when the pressure in the line 79 exceeds the aforementioned 1800 pounds per square inch the pressure switch PS2 is effective to close the contacts PS2. Thus, during a charging operation, as the pressure in the hydraulic line 79' rises to thereby force the floating pistons 16 downwardly, the pressure switch PS-Z is actuated when the pressure in the line 79 exceeds 1800 pounds per square inch, and the pressure switch contacts PS-Z' are thereby closed. The closing of the contacts PS2' energizes the control relay CR-2, the circuit for the relay CR-2 extending through the normally closed relay contacts CR-3". The energization of the relay CR-2 closes the normally open relay contacts CR-2' to thereby afford a holding circuit for the relay CR-2 around the pressure switch contacts PS-Z'. The energization of the control relay CR2 also closes the normally open relay contacts CR-Z", which energizes the solenoid valve SV-4 and opens the valve 49 to thus permit the charging pressure to equalize throughout the gas circuit as illustrated in FIG. 6.

At the completion of the downward movement of the floating pistons 60, the driver pistons 16 are disposed in seating engagement with the annular seats 18, and the entire gas circuit of the machine 1 is charged with high pressure gas, as shown in FIG. 6.

Thereafter, a stroke push button switch PB-6 may be actuated, which energizes solenoid valve SV-2, the circuit for solenoid valve SV-Z extending through the normally closed relay contacts CR-3'. The energization of the solenoid valve SV-2 is effective to permit the valve 40 to be closed by the gas pressure in the passageway 38, as previously described, to thereby close communication between the main chamber 10 and the triggering chambers 19.

The actuation of the stroke push button switch PB-6 is also effective to energize the timer relay TR1 and the warning lamp 83, the circuit for doing so extending through the aforementioned normally closed relay contacts CR-3'. The energization of the timer relay TR-l closes the normally open relay contacts TR-l' to thereby afford a holding circuit for the timer relay TR-l, the solenoid valve SV-2 and the warning lamp 83, around the push button switch PB-6.

The energization of the timer relay TR-l also closes the normally open relay contacts TR-l". However, the contacts TR-l" are delayed closing contacts, the timing of which is such that they do not close until after the trigger valve 40 has seated. The closing of the contacts TR-l" energizes valve windings SV-S, FIG. 10. The valve windings SV-3 are on the same valve as the valve windings SV-l, and the actuation of the stroke push button switch PB-6 opened the circuit to the valve windings SV-l and thereby deenergized the latter. Therefore, the energization of the windings SV-3 actuates the solenoid valve SV-l to a position wherein the cylinders 64 are connected through the hydraulic lines 68 and 79 and the solenoid valve SV-1 to sump to thereby permit the hydraulic fluid above the floating pistons 60 to flow to sump, the gas pressure beneath the floating pistons 60 moving the latter upwardly into fully raised position in the cylinders 9.

It will be remembered that energization of the solenoid valve SV-l caused by closing of the charge push button PB-S, and the consequent energization of the control relay CR-l, caused the hydraulic line 79 to be pressurized. A pressure switch PS-l is connected to the hydraulic line 79 and is operable upon the pressure in the line 79 exceeding a suitable predetermined pressure, such as, for example, 35 pounds per square inch, to open pressure switch contacts PS-l'. Therefore, while the pressure in the line 79 exceeds 35 pounds per square inch a circuit through the timer relay contacts TR-l' to the control relay CR-3 remains open. The exhausting of the hydraulic fluid from the hydraulic line 79 and from the cylinders 9 above the pistons 60, and the consequent relieving of the pressure in the hydraulic line 79 by the aforementioned deenergization of the solenoid valve SV- 1 and the energization of the valve windings SV-3 causes the pressure in the line 79 to drop below the aforementioned 35 pounds per square inch so that the contacts PS-l' of the pressure switch PS-l again move the closed position.

The closing of the pressure switch contacts PS-l, caused'by the drop of pressure in the line 79, energizes the control relay CR3, which opens the normally closed relay contact CR-3', and thereby deenergizes the solenoid valve SV-2, the warning lamp 83, and the timer relay TR1. The energization of the control relay CR-3 also opens the normally closed relay contacts CR-3" and thereby opens the holding circuit for the control relay CR2 and thereby deenergizes the latter.

The deenergization of the control relay CR-Z opens the normally open relay contacts CR-Z" and -deenergizes the solenoid valve SV-4. The deenergization of the solenoid valve SV-4 causes the lower end of the actuator 55 to be connected through the hydraulic line to the pressurized hydraulic line 81, and causes the upper end portion of the actuator 55 to be connected to the hydraulic line 85 to sump 82, to thereby cause the valve 49 to close, so that the machine 1 is now ready to be fired in the preferred manner.

The aforementioned deenergization of the solenoid valve SV-2 caused by the drop in pressure in the hydraulic line 79 below 35 pounds per square inch, and the consequent opening .of the relay contact CR-3 causes the valve SV-2 to connect the hydraulic line 45 to the high pressure hydraulic line 81 to thereby force the piston 44 of the actuator 41 downwardly and thus move the trigger valve 40 to open position. The opening of the trigger valve 40 triggers the firing of the machine 1, the high pressure gas in the main chamber 10 flowing from the main chamber 10 past the valve 40 and through the passageways 36, 33, 34, and 35 into the triggering chambers 19 to thereby substantially instantaneously subject the lower faces of the driver pistons 16 and the lower ends of the cylinders 9 to the full pressure of the gas in the main chamber 10. This causes the driver pistons 16 and the lower ends of the respective cylinders 9 to be rapidly accelerated away from each other, and the consequent uncovering of the openings 15 permits the high pressure gas in the main chamber 10 to continue to rush into the cylinders 9 below the lower faces of the driver pistons 16 and continue to subject the spaces between the lower faces of the driver pistons 16 and the lower ends of the cylinders 9 to the full pressure of the main chamber 10, as the pistons 16 and lower ends of the cylinders 9 are accelerated away from each other. The force created by the flow of gas from the main chamber 10 into the cylinders 9 causes the driver pistons 16 to be rapidly accelerated upwardly, and likewise causes the cylinders 9 to be rapidly accelerated downwardly. Such movement of the pistons 16 and the cylinders 9 causes corresponding movement of the lower plate 4 and the upper plate 3, respectively, to thereby bring the plates 3 and 4, and the die parts 63 and 64 carried thereby, respectively, into contact with each other with a high impact force.

The deenergization of the timer relay TR1, caused by the opening of the pressure switch contacts PS-1' upon the drop in pressure in the line 79 below 35 pounds per square inch, and the consequent opening of the relay contact CR-3' caused the timer relay contacts TR-l to again open, thus opening another portion of the circuit to the control relay CR3. The deenergization of the timer relay TR1 also caused the timer relay contacts TR1 to open and thereby deenergize the windings SV3 on the solenoid valve SV1. Therefore, if the stroke push button PB6 is then released to thereby close the circuit to the solenoid valve SV-l, a new cycle of operation of the machine 1 is commenced, the charging circuit through the control relay CR-l remaining closed because of the holding circuit through the relay contacts CR-l'.

In such a new cycle of operation the release of the stroke push button switch PB6 commences a new charging operation, and after charging of the machine with high pressure gas is completed, as illustrated in FIG. 6, the stroke button switch PB-6 may again be actuated to again cause the venting operation, as illustrated in FIG. 7, and the firing operation, as illustrated in FIG. 8, to again be performed as previously described. Thus, it will be seen that in the machine 1 the gas used for actuation of the driver mechanism thereof is embodied in a closed circuit, and no new gas need be fed into the machine between cycles of operation thereof.

The machine 1 also includes a shut-down push button switch 87, FIG. 10, which may be actuated by the operator when it is desired to shut down operation of the machine 1. Actuation of the push button switch 87 from its normal position shown in FIG. 10 restores the machine 1 to the condition in which it was prior to the initial actuation of the charge push button switch PBS, even if the machine 1 has been charged. Such actuation of the shut-down switch 81 opens the circuit through the holding relay contacts CR-l' and thereby deenergizes the relay CR-l. This makes actuation of the charge button switch PBS necessary to again initiate operation of the machine 1.

The actuation of the shut-down push button switch 87 also closes the center contacts thereof to thereby energize the solenoid valve SV3, and in addition closes the lower contacts thereof to thereby energize the control relay CR-3 and thus open the normally closed relay contacts CR-3'. The energization of the solenoid valve SV-3 causes the hydraulic fluid in the cylinder 64 to drain to sump. The opening of the normally closed contacts CR-3 insures that the solenoid valve SV2 is deenergized so that no hydraulic pressure is present in the actuator 41 below the piston 44 thereof and the trigger valve 40 is disposed in open position. The latter insures that no gas is trapped in the main pressure chamber 10 for accidentally firing the machine.

Thereafter, to complete shutting down of the machine 1, the operator may actuate push button switches PB-3 and PB4, FIG. 10, to thereby open the circuits to HR-l and HR-2, respectively, and thereby deenergize the motors 73 and 74. The deenergization of the holding relays HR1 and HR2 makes it necessary to actuate the push button switches PB-l and PBZ when it is again desired to start the machine 1 in operation.

It will be remembered that in the operation of the machine 1 shown in the drawings, the vent valve 49 is closed during firing of the machine. This closes the passageway 48-50 and thereby prevents the flow of gas from the main chamber 10 through the passageways 48, 50, 25, and 23 into the cylinders 9 above the pistons 16. The vent valve 49 remains closed after firing until the next charging operation of the machine, when the pressure in the hydraulic line 79 builds up to over 1800 pounds per square inch.

If desired, the machine 1 may be constructed without the vent valve 49 being embodied therein, the passageways 48 and 50 then being connected directly to each other. The valve 49 in the preferred embodiment of the machine 1 shown in the drawings serves the highly useful purpose of preventing high pressure gas from flowing through the driver pistons 16 during firing of the machine 1, and thereby prevents the heating which would otherwise occur from the flow of gas through the pistons 16. However, in a machine constructed in accordance with the principles of the present invention, the passageways extending from the trombone tubes 24 in the driver piston 16 to the passageway 33 in the upper plate 3 may readily be disposed outside of the machine 1 so that they are readily accessible for efficiently cooling of the gas passing therethrough. Thus, even if the valve 49 were eliminated from the machine 1, the machine 1 would afford a novel construction which eliminates a substantial portion of the disadvantages heretofore caused by the passage of gases through driver pistons during the firing of high-energy impact machines.

From the foregoing it will be seen that the present invention affords a novel high-energy impact machine which may be charged, vented, and fired in a novel and expeditious manner.

Also, it will be seen that the present invention affords a novel high-energy impact machine, the entire gas circuit of which may be filled with gas from an outside source irrespective of whether or not the driver pistons thereof are unseated from the annular seats therefor.

In addition, it will be seen that the present invention affords a novel high-energy impact machine which does not require the recharging of any portion of the gas circuit thereof between successive cycles of operation, and wherein the time between such successive cycles of operation may be extremely small.

Thus, while we have illustrated and described the preferred embodiment of our invention, it is to be understood that these are capable of variation and modification, and we therefore do not wish to be limited to the precise details set forth, but desire to avail ourselves of such changes and alterations as fall within the purview of the following claims.

We claim:

1. A high-energy impact machine comprising (a) a pair of plates movable toward and away from each other,

(b) a first of said plates having a cylinder and two chambers therein,

(c) said chambers and cylinder intersecting each other,

(d) a driver piston (1) slidably mounted in said cylinder and (2) having (a') a first end face facing toward one of said chambers and (b) an opposite second end face facing into said cylinder,

(e) a seat member extending around and defining the outer periphery of said one chamber disposed in position to engage said piston to cut off direct communication between said one chamber and both said cylinder and the second of said chambers,

(f) a post attached to said piston and to the second of said plates,

(g) means for supplying gas under pressure to said second chamber, and

(11) means for feeding said gas under pressure from said second chamber to said first chamber to thereby move said piston off said seat to expose said first face to the pressure in said second chamber and thereby 1 3 force said cylinder and piston in opposite directions and thereby move said plates toward each other.

2. A high-energy impact machine comprising (a) a pair of plates movable toward and away from each other,

(b) a first of said plates having (1) a cylinder and two chambers therein, and

(2) a passageway therein extending between said chambers,

(c) said chambers and cylinder intersecting each other,

(d) a driver piston (1) slidably mounted in said cylinder and (2) having (a) a first end face facing toward one of said chambers and (b') an opposite second end face facing into said cylinder,

(e) a seat member extending around and defining the outer periphery of said one chamber disposed in position to engage said piston to out off direct communication between said one chamber and both said cylinder and the second of said chambers.

(f) a post attached to said piston and to the second of said plates,

(g) means for supplying gas under pressure to said second chamber, and

(h) valve means for closing and opening said passage- .way to thereby, respectively,

(1) prevent the flow of gas through said passageway from said second chamber to said first chamher, and

(2) permit the flow of gas through said passageway from said second chamber to said first chamber to thereby force said piston off said seat to expose said first face to the pressure in said second chamber and thereby force said cylinder and piston in opposite directions and thereby move said plates toward each other.

5 3 A high-energy impact machine as defined in claim 2, and in which '(a) said'valve means includes a poppet valve mounted in said one plate and movable into open and closed position in said passageway.

4. A high-energy impact machine as defined in claim (a) in which said piston and post have a second passageway extending therethrough,

(b) which includes (1) a third passageway extending between said first-mentioned passageway and said second passageway, and

(2) other valve means for opening and closing said third passageway, and

'(c)-in which said first-mentioned valve means are disposed between said third passageway and said second chamber. 5. A high-energy impact machine as defined in claim 4,

and in which (a) said first-mentioned valve means includes a poppet valve mounted in first-mentioned passageway,

(b) said third passageway extends through a portion of said first plate and connects to said first-mentioned passageway therein, and

(c) said poppet valve is movable into open and closed position to thereby open and close communication through said first-mentioned passageway between said second chamber and both said first chamber and said third passageway.

6. A high-energy impact machine comprising (a) first and second movable plates adapted to be simultaneously accelerated toward each other by an acceleration force,

(b) a source of a confined pressurized elastic medium,

(0) a cylinder on said first plate having connection with said source for substantially instantaneously releasing said pressurized elastic medium from said source into said cylinder, (d) said cylinder having two ends, (e) a driver piston in sealing and slidable contact with the side walls of said cylinder, (f) said driver piston (1) having opposite end faces facing toward respective ends of said cylinder, (2) being operatively connected to said second plate, and (3) being reciprocable longitudinally of said cylinder between (a) one position adjacent one end of said cylinder effective to close said connection, and (b') another position wherein said connection is disposed between said one end and the one of said faces facing said one end to thereby open said connection, and (g) means for feeding pressurized elastic medium from said source to between said one end and said one face when said piston is disposed in said one position to thereby move said piston to said other position and thereby open said connection and substantially instantaneously release said pressurized elastic medium through said connection fromsaid source into said cylinder to act on said one end and said one face to provide an acceleration force to simultaneously accelerate said piston and cylinder in opposite directions and said plates toward each other. 7. A high-energy impact machine comprising (a) first and second movable plates adaptedto be simultaneously accelerated toward each other by an acceleration force, (b) a source of a confined pressurized elastic medium in said first plate, (c) a cylinder on said first plate having connection with said source for substantially instantaneously Y releasing said pressurized elastic medium from said source into said cylinder, (d) said cylinder having two ends, (e) one of said ends facing toward said second plate, (f) a driver piston in sealing and slidable contact with the side walls of said cylinder, (g) said driver piston (1) having opposite 'end faces facing toward respective ends of said cylinder, (2) being operatively connected to saidv second plate, and (3) being reciprocable longitudinally of said cylinder between (a) one position adjacent said one end of said cylinder effective to close said connection, and t (b') another position wherein said connection is disposed between said one end and the one face facing said one end to thereby open said connection, and (h) means in said first plate for feeding pressurized elastic medium from said source to between said one end and said one face when said piston is disposed in said one position to thereby move said piston to said other position and thereby open said connection and substantially instantaneously release said pressurized elastic medium through said connection from said source into said cylinder to act on said one end and said one face to provide an acceleration force to simultaneously accelerate said piston and cylinder in opposite directions and said plates toward each other. a 8. A high-energy impact machine comprising (a) first and second movable plates adapted to be simultaneously accelerated toward each other by an acceleration force, (b) a chamber in said first plate for holding a supply of a pressurized elastic medium,

15 (c) a cylinder in said first plate having two oppositely disposed ends, (d) one of said ends facing toward said second plate, (e) said cylinder having an opening through the side wall thereof adjacent said one end and in communication with said chamber for substantially instantaneously releasing said pressurized elastic medium from said chamber into said cylinder, (f) a driver piston in sealing and slidable contact with the side walls of said cylinder, (g) said driver piston (1) having opposite end faces facing toward respective ends of said cylinder, (2) being operatively connected to said second plate, and (3) being reciprocable longitudinally of said cylinder between (a') one position adjacent said one end of said cylinder effective to cover and close said opening, and (b') another position wherein said opening is disposed between said one end and the one face facing said one end, (h) a passageway in said first plate connected into said chamber and said one end of said cylinder for feeding said pressurized elastic medium from said chamber into said cylinder between said one end and said one end face when said piston is disposed in said one position to thereby move said piston to said other position and thereby substantially instantaneously release said pressurized elastic medium though said opening from said source into said cylinder to act on said one end and said one face to provide an acceleration force to simultaneously accelerate said piston and cylinder in opposite directions and said plates toward each other, and (i) valve means in said passageway for opening and closing the latter. 9. A high-energy impact machine as defined in claim 8, and which includes (a) another passageway (1) connected at one end to said first-mentioned passageway on the side of said valve means remote from said chamber, and (2) connected at the other end to the interior of said cylinder disposed between the other end thereof and the other end of said piston. 10. A high-energy impact machine as defined in claim 9, and which includes (a) valve means in said other passageway for opening and closing the latter. 11. A high-energy impact machine as defined in claim 10, and in which (a) said other passageway includes trombone tubes mounted in said first and second plates. 12. A high-energy impact machine comprising (a) first and second movable plates adapted to be simultaneously accelerated toward each other by an acceleration force, (b) a chamber in said first plate for holding a supply of a pressurized elastic medium, (c) two cylinders mounted in said first plate in substantially parallel spaced relation to each other, (d) each of said cylinders (1) having two oppositely disposed ends with one of said ends facing toward said second plate, and (2) having passage means through the side wall thereof adjacent said one end and in communication with said chamber for substantially instantaneously releasing said pressurized elastic medium from said chamber into said cylinder, (e) two driver pistons, (f) each of said driver pistons,

(1) being in sealing and slidable contact with the side walls of a respective one of said cylinders, (2) being operatively connected to said second plate, (3) having opposite end faces facing toward respective ends of said respective cylinder, and (4) being reciprocable longitudinally of said respective cylinder between (a') one position adjacent said one end of said respective cylinder effective to close said passage means, and (b') another position wherein said passage means are disposed between said one end and the one face of said respective piston facing said one end to thereby open said passage means in said respective cylinder, and (g) means for simultaneously feeding pressurized elastic medium from said chamber into both of said cylinders between said one ends and said respective one faces when said pistons are disposed in said one position to thereby simultaneously move both of said pistons to said other position and thereby open said passage means in both cylinders and substantailly instantaneously release said pressurized elastic medium from said chamber simultaneously into both of said cylinders to simultaneously act on said one end of both of said cylinders and said one face of both of said pistons to provide an acceleration force to simultaneously accelerate said pistons and said cylinders in opposite directions and said plates toward each other. 13. A high-energy impact machine as defined in claim 12 and in which (a) said chamber comprises a plurality of elongated compartments extending through said one plate between said cylinders and connected to both of said cylinders by said passage means. 14. A high-energy impact machine as defined in claim 13, and in which (a) said means includes (1) an elongated passageway extending through a portion of said first plate and connected between one of said compartments and said one end of both of said cylinders, and (2) valve means in said passageway for opening and closing said passageway to thereby control the flow of said medium therethrough from said one compartment to said cylinders. 15. A high-energy impact machine as defined in claim 14, and which includes (a) a second passageway (1) extending through said pistons and a portion of said one plate, and (2) operatively connected to said elongated passageway on the side of said valve means remote from said one compartment for interconnecting said elongated passageway and the interior of said cylinders on the side of said pistons remote from said second plate, and (b) valve means in said second passageway for opening and closing the latter.

for feeding pressurized elastic medium References Cited UNITED STATES PATENTS 8/1961 Ottestad 73-12 6/1964 Ottestad 72-453

Claims

1. A HIGH-ENERGY IMPACT MACHINE COMPRISING (A) A PAIR OF PLATES MOVABLE TOWARD AND AWAY FROM EACH OTHER, (B) A FIRST OF SAID PLATES HAVING A CYLINDER AND TWO CHAMBERS THEREIN, (C) SAID CHAMBERS AND CYLINDER INTERSECTING EACH OTHER, (D) A DRIVER PISTON (1) SLIDABLY MOUNTED IN SAID CYLINDER AND (2) HAVING (A'') A FIRST END FACE FACING TOWARD ONE OF SAID CHAMBERS AND (B'') AN OPPOSITE SECOND END FACE FACING INTO SAID CYLINDER, (E) A SEAT MEMBER EXTENDING AROUND AND DEFINING THE OUTER PERIPHERY OF SAID ONE CHAMBER DISPOSED IN POSITION TO ENGAGE SAID PISTON TO CUT OFF DIRECT COMMUNICATION BETWEEN SAID ONE CHAMBER AND BOTH SAID CYLINER AND THE SECOND OF SAID CHAMBERS,