US3910087A - Hydraulic-forming machine - Google Patents

Hydraulic-forming machine Download PDF

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Publication number
US3910087A
US3910087A US533992A US53399274A US3910087A US 3910087 A US3910087 A US 3910087A US 533992 A US533992 A US 533992A US 53399274 A US53399274 A US 53399274A US 3910087 A US3910087 A US 3910087A
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Prior art keywords
pressure
chamber
fluid
piston
valve
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US533992A
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Everett E Jones
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Boeing Co
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Boeing Co
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Priority to US533992A priority Critical patent/US3910087A/en
Priority to AU82500/75A priority patent/AU489019B2/en
Priority to JP50081373A priority patent/JPS5171574A/ja
Priority to FR7521521A priority patent/FR2294779A1/fr
Priority to GB29309/75A priority patent/GB1505669A/en
Priority to DE19752534226 priority patent/DE2534226A1/de
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
    • B21D22/10—Stamping using yieldable or resilient pads
    • B21D22/12—Stamping using yieldable or resilient pads using enclosed flexible chambers

Definitions

  • ABSTRACT Hydraulic-forming apparatus for compressively con forming a workpiece to the contour of a die by applying uniform forming effort from pressurized hydraulic pressure fluid in a pressure cell chamber surrounding both the part and die. Pressure is transmitted to the part and die through a pressure deformable plastic mandrel, the pressure supporting the part and die in their natural attitudes and causing the part to conform to the shape of the die without distorting the adjacent areas of the workpiece.
  • the fluid pressure system includes means for pressurize the pressure cell chamber to pump output pressure, a lower pressure amplifier for intermediate pressurization of the system and a high pressure amplifier to apply maximum forming pressures to the workpiece.
  • Each amplifier includes a pressure multiplying apparatus such as a reciprocative piston assembly in which a larger diameter master piston drives a smaller diameter slave piston to develop higher hydraulic pressures for use in the forming apparatus.
  • the fluid pressure amplifiers communicate with the pressure cell chamber so that reciprocation of each piston assembly incrementally increases the fluid pressure therein.
  • the lower pressure amplifier output has a designed maximum pressure at which the lower pressure amplifier is isolated from the pressure cell chamber and the higher pressure amplifier operates to further increase the fluid pressure applied to the pressure cell chamber.
  • the hydraulic fluid activating the higher pressure amplifier Upon completion of pressurization of the pressure cell chamber to the desired pressure for forming the workpiece, the hydraulic fluid activating the higher pressure amplifier is released and is caused to flow back into a reservoir through a velocity control means in the conduit.
  • the velocity control means provides a tortuous path for the hydraulic fluid to prevent damage to the equipment from sonic or near sonic flow rates.
  • This invention relates to hydraulic-forming apparatus of the type in which forming effort for conforming a metal blank to the contour of a die is exerted compressively through a pressure deformable mandrel surrounding the workpiece and die, and more particularly to multiple stage pressurization systems for controlling the forming effort exerted and to depressurize the unit after forming is completed.
  • Presently-known hydraulic-forming systems typically achieve maximum forming pressures of from 5,000 pounds per square inch (psi) up to 25,000 psi.
  • psi pounds per square inch
  • it is desirable to increase the versatility of the apparatus to accommodate a wider variety of shapes and sizes of parts and to achieve a wider range of formed shapes.
  • a related object is to provide such apparatus capable of achieving the pressures achieved by forming pressures substantially higher than the prior art devices.
  • An additional object is to provide hydraulic-forming apparatus which is compact, structurally simple, and economical to operate.
  • a further related object is to provide such apparatus useful to locally form one sec tion of elongated workpieces.
  • a still further related object is to provide hydraulic-forming apparatus with multiple access ports to the pressure chamber which enable rapid and easy removal or advancement of workpieces and dies through the apparatus.
  • Another object is to provide hydraulic-forming apparatus including surge suppression or control equipment for suppressing or eliminating catastrophic failures and shock waves in the hydraulic system and for preventing damage and injury to operating personnel as a result of rapid depressurization of the apparatus at the termination of a forming cycle.
  • Another object is to provide hydraulic-forming apparatus of increased pressure chamber volume with the capability of accommodating larger parts
  • the equipment for controlling and operating the hydraulic system includes a multiple stage hydraulic fluid supply to first accommodate, by means of a lower pressure, higher volume hydraulic source, the compressibility of the hydraulic-forming system; and secondly, apply a substantially higher hydraulic pressure from a lowervolume, higher-pressure hydraulic source, thereby achieving a substantially higher hydraulic-forming pressure in a hydraulic-forming system of reasonable size and of convenient operability.
  • the fluid pressure in the pressure chamber is first brought up to the maximum output pressure of a hydraulic fluid source, then incrementally increased by a low pressure amplifier up to an intermediate fluid pressure, and then is increased by a high pressure amplifier.
  • the amount of forming pressure exerted by the pressure amplifiers is controlled by a pressure selector switch, which is selectively responsive to the fluid pressure applied to the pressure amplifiers for deactuating the pressure amplifiers when the fluid pressure reaches the maximum desired forming pressure.
  • a transition pressure switch responsive to fluid pressure applied to the lower pressure amplifier actuates the high pressure amplifier, as needed, for selected forming pressures greater than the intermediate fluid pressure developed by the lower pressure amplifier.
  • a preferred embodiment of the invention includes three electromagnetically actuated control valves, two of which are selectively responsive to the pressure selector and alternatively responsive to the transition pressure switch elements for actuating and deactuating the low and high pressure amplifiers.
  • the third control valve actuates an unload valve for depressurizing the pressure chamber after the forming cycle is completed.
  • the pressure amplifiers may include a double-acting master piston, at least one face of which has a large surface area relative to the surface area of a slave piston which is movable conjointly with the master piston.
  • An input pressure chamber and a second pressure chamber, respectively associated with the large face and an opposite face of each master piston, are alternately pressurized with hydraulic pressure fluid in order to produce reciprocative motion of each piston assembly which thus incrementally increase the pressure in output chambers respectively associated with each slave piston.
  • Both output chambers communicate with the pressure chamber surrounding the mandrel.
  • a check valve means in the hydraulic conduit from the low pressure amplifier permits repeated cycling of the low pressure amplifier and isolates the low pressure amplifier from the pressure vessel pressure chamber during operation of the high pressure amplifier.
  • a surge control valve positioned in the exhaust line from the high pressure amplifier controls fluid velocity and flow regime to eliminate or minimize shock waves during depressurization.
  • the cylindrical pressure vessel is provided with two end breach screws for clamping the tubular mandrel therebetween.
  • FIG. 1 is a combined partial side elevation and schematic outline of hydraulic-forming apparatus and control systems according to the present invention.
  • FIG. 2 is a cross-sectional view taken along lines 22 of FIG. 1 showing the interior of the hydraulic-forming machine pressure cell.
  • FIG. 3 is a cross-sectional view taken along lines 33 of FIG. 1.
  • FIG. 4 is a cross-sectional view of the velocity control means utilized in this invention.
  • FIG. 5 is a schematic circuit diagram of one portion of the l volt segment of the control means used in the preferred embodiment of this invention.
  • FIG. 6 is a schematic representation of the lower voltage portion of the control system of this invention.
  • FIG. 7 is a schematic representation of another part of the l 10 volt portion of the control system utilized in the preferred embodiment of this invention.
  • FIG. 8 is a schematic representation of one portion of the hydraulic circuitry of this invention showing the preloading of the apparatus with pump pressure.
  • FIG. 9 is a schematic similar to FIG. 8 showing the mid-range pressure operation.
  • FIG. 10 is a schematic similar to FIGS. 8 and 9 showing high pressure operation of the system.
  • FIG. 11 is a schematic similar to FIGS. 8, 9 and 10 showing completion of the forming cycle and release of the pressure from the forming chamber.
  • FIG. 1 an overall schematic and partial side elevational view of the apparatus of this invention in the nonpressurized mode such at completion of a forming cycle or prior to initiation of a forming cycle.
  • Hydraulic pump 10 is situated to withdraw hydraulic fluid from reservoir 11 and force the fluid into conduit 62 thus providing the primary source of hydraulic pressure fluid for the system.
  • Valve 140 permits depressurization of conduit 62 by flow of hydraulic fluid into return conduit 63.
  • the pressure in conduit 62 may be noted at pressure gauge 85.
  • a circumferential pressure cell shown generally at 40 includes a pressure container 27 surrounding a chamber block 123 which in turn encloses a hydraulicforming chamber 12.
  • a pair of breach screws 107 and 107a are shown threaded into the chamber block 123 to hold the elements of the hydraulic forming cell in place.
  • the hydraulic duct 28 communicates with fluic chamber 12 which comprises a substantially cylindrica chamber means bounded on its exterior by the inner surface of chamber block 123 and on its interior b1 bladder 14.
  • Bladder 14 in turn engages the forming core mandrel 105 which comprises a pressure deform able material such as polyurethane or the like. Posi tioned inside the mandrel are workpiece 25 and die 2t which are supported by end plates 106 and 106a.
  • the deformable mandrel 105 surrounds the workpiece 25 and the die 26 so that pressure imposed upon the mandrel 105 through bladder 14 is equally distributed circumferentially about the workpiece and die.
  • FIGS. 2 and 3 cross-sectional views of the pressure cell 40 are shown at two locations along the axis of the cell.
  • workpiece 25 is shown in engagement with the contoured surface of die 26.
  • a job 26a in die 26 is shown. Imposition of pressure from the surrounding deformable mandrel 105 will force workpiece 25 into engagement with the surface of die 26.
  • Pressure is supplied to hydraulic duct 28 and thereby to fluid chamber 12 serially from three sources according to the ultimate pressure desired.
  • the first source of pressure is via conduit with the hydraulic control system in the preload circuit mode as is shown in FIG. 8.
  • Valve 101 has been repositioned so that pressure from pump 10 may flow through valve 101 into conduit 70 and thence through check valve 15 into the bottom of lower range pressure intensifier 37, through check valves l8, l9 and 60 and then into flow chamber 12.
  • hydraulic fluid at pump output pressure acts upon the bladder 14 and the mandrel I05 and thereby upon the workpiece 25 to urge the workpiece 25 into conformance with the die 26.
  • Double-acting piston 32 is adapted to travel up and down in cylinder 29 due to hydraulic pressure imposed either in upper chamber 30 or in lower chamber 31.
  • a slave piston 33 having a substantially smaller diameter than master pis ton 32 is solidly connected to master piston 32 by piston rod 36. Downward travel of master piston 32 causes fluid within chamber 39 to become pressurized and forced into fluid chamber 12. The travel of master piston 32 and slave piston 33 is controlled by the flow of hydraulic fluid through valve 102. To cause downward travel of the piston assembly, valve 102 is switched to the position shown in FIG. 9 for mid-range pressure. In this position hydraulic fluid from pump 10 is forced into upper chamber 30 forcing the piston assembly downward.
  • valve 102 is returned to the position shown in FIG. 1, thereby pressurizing the fluid contained in lower chamber 31 and permitting the hydraulic fluid in upper chamber 30 to exhaust to reservoir 1 1. Valve 102 may then be returned to the position shown in FIG. 9 so as to cause downward travel of the piston assembly and consequential pressurization of the fluid contained in chamber 39.
  • the higher range pressure intensifier 57 is utilized. Similar in structure to the lower range pressure intensifier 37, the higher range pressure intensifier 57 includes a piston assembly comprising master piston 52, piston rod 56, and slave piston 53. Substantial pressure intensification is achieved by the ratio of the areas of piston 52 and piston 53. Pressure imposed within upper chamber 50 when the hydraulic circuit is in the position shown in FIG. causes downward motion of the piston assembly with consequential pressurization of the fluid contained in chamber 59, the pressure being transmitted into fluid chamber 12 through hydraulic duct 28.
  • the pressure in fluid chamber 12 may be relieved by activating the chamber pressure release system. That system includes the valve actuator piston 17, unload check valve 16, and conduit 78. By imposing pump hydraulic fluid under pressure from pump 10 through valves 101 and 138 into valve actuator 17, the ball valve 16 is unseated and pressurized fluid permit ted to flow through conduits 78 back into reservoir 11.
  • Both pressure intensifiers have an emergency depres surization system which permits pressurized fluid to be dumped from both sides of the upper pistons 52 and 32.
  • This safety system includes valve 130 and conduit 75 connected into higher pressure intensifier 57 through check valves 131 and 132, and into lower pressure intensifier 37 through check valves 133 and 134. The presence of these check valves permits pressurization desired on either side of the piston; however, upon opening valve 130, the pressure on each side of the piston will be equalized.
  • Valve 101 is positioned so that check valve 16 is unseated and any pressure in fluid chamber 12 is dumped into conduit 63 via conduit 78.
  • the workpiece and die 26 are placed within the pressure fluid chamber 12 surrounded by deformable mandrel 105.
  • Pump 10 is then actuated forcing hydraulic fluid into conduit 62 which acts as a manifold to distribute the hydraulic fluid to the various fluid pressure users in the system. As shown in FIG.
  • the hydraulic circuitry would be switched to that shown in the partial hydraulic diagram (FIG. 9) in which valve 102 is reversed so that pressure from pump 10 enters conduit 73 and pressure previously imposed upon conduit 74 is exhausted and returned to reservoir 11 (not shown).
  • the piston assembly comprising piston 32, piston rod 36 and slave piston 33, is caused to move downwardly against the pressure already imposed upon chamber 39 due to the relief of pressure in chamber 31 and the imposition of pump pressure in chamber 30 above the piston 32. Since the upper face of piston 32 is of substantially greater area than the lower surface of slave piston 33, a substantial intensification of fluid pressure is achieved in chamber 39.
  • Chamber 39 is in fluid communication with fluid chamber 12 and therefore the pressure in fluid chamber 12 is raised to the same level as that in compression chamber 39.
  • Piston assembly 32 and slave piston 33 travel downwardly under the influence of pressure in chamber 30 until either the desired pressure is achieved, as indicated by pressure responsive means 22, or the piston assembly makes the full travel along its length to the position shown in dotted lines.
  • valve 102 is switched so that pressure in chamber 30 is exhausted to reservoir 11 and pressure from pump 10 is imposed upon the lower side of piston 32,
  • lower range pressure intensifier 37 may be repeated in order to bring the fluid pressure in fluid chamber 12 up to the maximum pressure attain able in intensifier 37 by repeated cycling thereof. This would be the case, for example, when workpiece 25 must be deformed a large distance to conform to the die 26, thus requiring a substantial volume of hydraulic fluid.
  • unload check valve 16 may be activated by valve actuator piston 17 and the system depressurized.
  • the higher range pressure intensifier 57 may be activated by switching valve 103 to the position shown in FIG. 10.
  • the hydraulic circuitry shown therein causes fluid at pump pressure to enter conduit 76 and pass into the upper chamber 50 of higher range pressure intensifier 57.
  • the hydraulic fluid in chamber 59 would already be at the maximum output pressure of intensifier 37.
  • FIG. 4 When exhausting hydraulic fluid from cylinder 50, extremely high flow rates are occasionally encountered. To prevent damage to the equipment and danger to operating personnel, the flow control device shown in FIG. 4 is utilized to suppress excessive flow rates.
  • a plug 42 is placed within the body 43 of the surge control valve 41.
  • the structure provides a circuitous path for the hydraulic fluid through ducts 44 to induce turbulence and prevent unduly high oil velocity.
  • the chamber 45 being of a larger diameter than fluid conduit 76 further acts to prevent damage to the apparatus from high oil velocity, frequently approaching sonic speeds.
  • the pressure achieved in fluid chamber I2 may be readily ascertained by reading the pressure of the fluid in chamber 30 or chamber 50 depending upon which intensifier is being utilized.
  • pressure switches 22 and 20 may be utilized to determine the pressure level and then to activate other functions of the hydraulic system as discussed above.
  • the momentary closing of normally open switch S1, FIG. 5, provides a circuit to relay coil R9.
  • the energized relay coil closes contacts R9-1 and R9-3 and opens contacts R9-2.
  • the closed contacts R9-l provide a holding circuit to the R9 relay coil through normally closed switch SI-A.
  • the closed contacts R9-3 provide a closed circuit for the machine operating circuit.
  • the open R9-2 contacts turn the L2 indicator light off, and closed contacts R9-I turn the L1 indicator light on.
  • the machine power circuit may be turned OFF" by momentarily opening switch Sl-A, breaking the holding circuit to power relay coil R-9 thereby returning the circuit to its normal position, as shown in FIG. 5.
  • the machine control circuit is energized by momentarily closing switch S2, FIG. 5, which energizes relay coil R closing contacts RS-l and R5-2 and opening contacts R5-3.
  • the closed contacts RS-I, FIG. 5, provide a holding circuit through normally closed switch S3 to relay coil R5.
  • the open R5-3 contacts turn the L5 light off, and the closed contacts RS-l turn the L3 light on.
  • the closed contacts R5-2 provide a circuit to the transformer T1 and rectifier RF-l to provide a 28V DC current to terminals TBS-l and TB3-l in the machine sequencing circuit.
  • This DC circuit energizes relay coil R4, FIG. 6, and closes contacts R4-l, FIG. 5, setting up a potential circuit for the hydraulic directional control valves.
  • the hydraulic pump motor 10, FIG. 5, is started by momentarily closing switch S5, FIG. 5, which provides an energizing circuit to relay coil R7, FIG. 5, which closes relay contacts R7-l and R7-2 and opens R7-3 contacts.
  • the closed R7-l and R7-2 contacts and normally closed switch S4, FIG. 5, provide a holding circuit to relay coil R7 and a sustained circuit to the pump motor and indicator L6.
  • the opened contacts R7-3 turn the L4 indicator light off.
  • the pump motor is turned off by momentarily opening the normally closed switch S4, returning the circuit to its normal position as shown in FIG. 5.
  • the machine has two integrated automatic circuits; one for forming pressures up to 50 KSI known as the low pressure circuit, and a second circuit for forming pressures above 50 KSI known as the high pressure circuit. Forming pressures are selected using rotating switch S36, FIG. 6.
  • the low pressure forming circuit is as follows: When switch S8, FIG. 6 is momentarily closed, it starts an automatic pressurization of chamber 23, FIG. 3, and then a depressurization of chamber 23, FIG. 2. Its sequence is as follows: 7
  • a circuit is provided to relay coil R3 to close contacts R3-l and provide a holding circuit to relay coil R3 through the normally closed contacts R6-l.
  • This circuit also energizes time delay relay coils R8 and R6 and normally closed contacts R6-2 to energize the coil of latching relay Rl-A.
  • the time delay relay R6 is set for a longer time delay than R8, and R8 is delayed until the preload pressure cycle is completed, FIG. 8.
  • the energized latching relay coil Rl-A closes contacts RlA-2 to provide a circuit to light indicator light L8, FIG. 6, and RlA-l, FIG. 5, provides a circuit through previously closed contacts R4-l to one of the solenoids of hydraulic directional control valve I01. Fluid under pressure is now directed through preload check valve 15, and transition check valves 18 and 19 and into chamber 23. Naturally this also pressurizes cylinders 39 and 59, with pump pressure.
  • time delay relay contacts R8-1 are closed providing a circuit to energize solenoid 112 of hydraulic directional control valve 102 and shift valve 102 to direct fluid under pressure to the top side of piston 32.
  • the time delay relay R6 opens contacts R6-I and R6-2, FIG. 6, breaking the holding circuit to the coils of relays R3, Rl-A, R6 and R8.
  • Relays R3, R6 and R8 return to their normal position as shown in FIG. 6.
  • Relay Rl-A being a latching relay, will retain the contacts RlA-l in a closed position even though the coil is de-energized.
  • the energized R2-A relay coil closes contacts R2A-1 and R2A-2.
  • the closed R2A-I contacts provide a circuit to light unload indicator light L7.
  • the closed R2A-2 contacts provide a circuit through previously closed contacts R4-l to energize relay coil R11, which closes contacts R1 l-l, R1 1-2 and Rll-3.
  • These closed circuits energize solenoids 113 and 115 in hydraulic directional control valves 102 and 103, respectively, and solenoid in hydraulic directional control valve 101,
  • Valve 103 was not moved because it was in its normal position for low pressure forming and is only used in high pressure forming which is described later.
  • valve 102 now directs fluid under pressure to the bottom of piston 32, returning it to its normal position.
  • Valve now directs fluid under pressure to piston 17 to force check valves 16 from its seat, FIG. 1, and release the fluid pressure in chamber 12 and cylinder 59.
  • the manual cycle completion switch S9 is now momentarily closed, energizing latching relay coil R2-B, opening contacts R2A-2 and R2A-1 and lighting cycle completion light L9.
  • the opened R2A-1 turns off the unload indicator light L7, FIG. 6.
  • the opened R2A-2 contacts break the circuit to relay coil R11, causing relay contacts R11-1, R11-2 and R11-3 to open, deenergizing one solenoid in directional control valves 102 and 103 and one solenoid in directional control valve 101.
  • the low pressure forming cycle is now complete.
  • the high pressure forming cycle is as follows:
  • the pressure selector switch S36 is set to a pressure in the higher operating range and in contact with switch S20.
  • form switch S8 FIG. 6 When form switch S8, FIG. 6, is momentarily closed, the coils of relays R3 and R6 are energized, closing contacts R3-1, providing a holding circuit through normally closed timed delayed relay contacts R6-1 and R6-2 to relay coils Rl-A, R3, and R8.
  • R6 and R8 are time delay relays, and their function is the same as described in the low pressure circuit.
  • R6 is timed to open and break the holding circuit after R8 has been delayed long enough to preload pressure chamber 12, chamber 39 and chamber 59 with pump pressure.
  • RlA-l closed contacts provide a circuit to solenoid 111 of valve 101, which directs pump pressure fluid through preload check valve 15, and transition check valves 18 and 19 into chamber 12. Naturally this also provides pump pressure fluid in cylinders 39 and 59, FIG. 1.
  • time delay relay contacts R8-l FIG. 5, are closed providing a circuit to one solenoid of directional control valve 102.
  • time delay relay R6 opens the holding circuit contacts R6-1 and R6-2, FIG. 6, breaking the holding circuit to relay coil R3, RlA, R6 and R8, FIG. 6.
  • Solenoid 112 in directional control valve 102 directs fluid under pressure to the top side of piston 32 forcing it and piston 33 down, intensifying the pressure in cylinder 39, which in turn intensifies the pressure in cylinder 59 and chamber 12.
  • transition pressure switch 22 a 6
  • RlA-2 contacts and closed pressure switch S22 energizes the coil in relay R12, closing contacts R12-l (FIG. 6).
  • R12-2 and R12-3 (FIG. 5).
  • Closed contacts R12-l provide a holding circuit to R12 coil.
  • Closed R12-2 contacts, FIG. 5, provide a circuit to solenoid 114 of directional control hydraulic valve 103.
  • Closed R12-3 contacts provide a circuit to solenoid 1 13 of directional control hydraulic valve 102. The valve directs fluid to the bottom of piston 32 bringing it back to its normal position.
  • Valve 103 directs fluid to the top of piston 52 forcing piston 52 and piston 53 down, intensifying the pressure in cylinder 59 and chamber 12.
  • a circuit is provided to latching relay coils R2-A and Rl-B, which opens R1A-2 contacts breaking the holding circuit to R12 relay coil, FIG. 6, which opens contacts R12-1 (FIG. 6), R12-2 and R12-3 (FIG. 5) to de-energize solenoids 113 and 114 of valves 102 and 103, respectively.
  • the energized coil of relay R2-A, FIG. 6, also closes contacts R2A-2, FIG. 5, to provide a circuit to relay coil R11 which closes contacts R1 1-1, R11-2 and R11- 3, which in turn provide circuits to solenoid 113 of valve 102, solenoid 115 of valve 103 and solenoid of valve 101 (FIG. 5).
  • These valves unload the forming pressure in the chamber 12, FIG. 1.
  • Valve 103 reverses the pressure on piston 52 returning it to its normal position.
  • Valve 101 applies pressure to piston 17 to force check valve 16 from its seat and release the remaining pressure in chamber 12. Solenoid 113 in valve 102 had previously been energized to return the piston 32 to its normal position.
  • Emergency unload switch S7 can be actuated anytime during a forming cycle to duplicate this pressure unloading operation because it duplicates the circuit provided by pressure switches 20 or 21.
  • the machine can be operated manually as well as automatically.
  • switch S33 is momentarily closed energizing relay coil R-10, closing contacts RIO-1 and R10-2 establishing a holding circuit through normally closed switch S34, to solenoid 111 of valve 101 to preload cylinders 39, 59 and chamber 12, FIG. 3, with pump pressure.
  • L14 and L15 are lighted. This pressure can be unloaded through unlead check valve 16 when switch S34 is momentarily opened and combined switch S37 is momentarily closed.
  • switch S34 breaks the holding circuit to solenoid 111 of valve 101 and momentarily closed switch S37 energizes solenoid 110 of valve 101 to shift the directional control valve 101 and pressurize piston 17 to force check valve 16 from its seat and release the pressurized fluid in cylinders 39 and 59 and chamber 12.
  • the manual piston control switch S40 is actuated, setting up a start circuit as previously described.
  • the preload valve switch S33 is actuated setting up the preload circuit and preloading the hydraulic working area as previously described.
  • Forming pressures in the medium pressure range are developed by momentarily closing piston forward switch S42, FIG. 7.
  • the momentary closing of switch S42 energizes relay coil R14 closing contacts R14-1 and opening contacts Rl4-2.
  • the closed R14-1 contacts provide a holding circuit to relay coil R14, and a circuit through previously closed contacts R16-1 to energize solenoid 112 of valve 102, so that fluid pres sure is now directed to the top side of piston 32 forcing it down, intensifying the pressure in cylinders 39 and 59, and chamber 12.
  • the pressure intensification is measured by the pump pressure gauge 85. If pressures above the medium pressure range are desired, the piston forward switch S44, FIG. 7, is momentarily closed after piston 32 reaches its maximum pressure.
  • switch S44 The momentary closing of switch S44, FIG. 7, energizes relay coil R15, closing contacts R15-1 and opening contacts R15-2.
  • the intensified pressure is read on the pump pressure gauge 85.
  • switch S43 is momentarily opened breaking the holding circuit to relay coil R14 and opening contacts R14-l and closing contacts R14-2.
  • the closed contacts R14-2 provide a circuit through normally closed switch S43 and previously closed contacts Rl6-2 to solenoid 113 of valve 102, which shifts the directional control valve and direct fluid pressure to the bottom of piston 32, returning it to its retracted position.
  • Switch S45 FIG. 7, is now momentarily opened breaking the holding circuit to relay coil R15, opening contacts RlS-l and closing contacts R15-2.
  • a circuit is now provided through normally closed switch S45 through closed contacts R15-2 and previously closed contacts R17-1 to solenoid 115 of directional control valve 103 to shift the valve and direct fluid pressure to the bottom of piston 52, returning it to its retracted position, reducing the pressure in chamber 12 and cylinder 59.
  • the combined switches S34 and S37 are now actuatcd.
  • the normally closed switch S34 is opened breaking the holding circuit to relay coil R10, opening contact RIO-1, de-energizing solenoid 111 of valve 101.
  • the closing of switch 537 provides a circuit to so lenoid 1 10 of valve 101 shifting the directional control valve 101 to direct fluid pressure to the piston 17 which pushes the ball check 16 from its seat and releases the pressurized fluid in cylinder 59 and chamber 12.
  • An apparatus for compressively conforming a metal part to the contour of a die a pressure vessel defining a pressure chamber, a pressure-deformable mandrel enclosed within the chamber, the part and the die being positionable inside the mandrel, supply means for supplying pressure fluid, means for selectively connecting the supply means with the pressure vessel pressure chamber to prepressurize the pressure vessel pressure chamber;
  • low pressure amplifier means having an input chamber selectively connectable with the supply means and an output chamber in communication with the pressure vessel pressure chamber, the low pressure amplifier means being operable when the input chamber is pressurized with pressure fluid from the supply means to increase the pressure in the pressure vessel pressure chamber for exerting compressive forming effort through the mandrel upon the part, the low pressure amplifier means being operable to increase the fluid pressure in the pressure vessel pressure chamber up to a first maximum fluid pressure;
  • high pressure amplifier means having a second input chamber selectively connectable with the supply means and a second output chamber in communication with the pressure vessel pressure chamber, the high pressure amplifier means being operable when the second input chamber is pressurized with pressure fluid from the supply means to increase the fluid pressure in the pressure vessel pressure chamber for exerting compressive effort through the mandrel upon the part;
  • control valve actuator means responsive to the transition pressure means for connecting the supply means with the first-mentioned input chamber to operate the low pressure amplifier to increase the fluid pressure in the pressure vessel pressure chamber for selected forming pressures up to the first maximum pressure, and alternatively for connecting the supply means with the first-mentioned input chamber to operate the low pressure amplifier to increase the fluid pressure in the pressure vessel pressure chamber up to the first maximum pressure, and then for connecting the supply means with the second input chamber to operate the high pressure amplifier to further increase the fluid pressure in the pressure vessel pressure chamber for selected forming pressures greater than the first maximum pressure;
  • control valve means also being responsive to the pressure selector means for depressurizing the firstmentioned input chamber, and alternatively the first-mentioned and second input chambers when the fluid pressure in the pressure vessel pressure chamber reaches the selected forming pressure;
  • depressurization means responsive to the pressure selector means for depressurizing the pressure vessel pressure chamber upon depressurization of the first-mentioned input chamber and alternatively with depressurization of the first-mentioned and second input chambers.
  • the low pressure amplifier means comprises a reciprocative piston assembly including a double end face master piston, a single end face slave piston movable conjointly with the master piston, one end face of the master piston being exposed to the first-mentioned input chamber, the other face of the master piston being exposed to a second chamber, the end face of the slave piston being exposed to the first-mentioned output chamber, the surface area of the one end face of the master piston being substantially greater than the surface area of the end face of the slave piston, and wherein the control valve means includes means for connecting the supply means to the first-mentioned input chamber for pressurizing the first-mentioned input chamber to move the piston assembly in one direction to increase incrementally the pressure in the first-mentioned output chamber, and alternately for connecting the supply means to the second chamber for pressurizing the second chamber to move the piston assembly in the reverse direction, and including intermediate valve means intermediate the first-mentioned output chamber and the pressure vessel pressure chamber for preventing reduction in fluid pressure in the pressure vessel pressure chamber
  • the high pressure amplifier means comprises a reciprocative piston assembly including a double end face master piston. a single end face slave piston movable conjointly with the master piston, one end face of the master piston being exposed to the second input chamber, the other face of the master piston being exposed to a second chamber, the end face of the slave piston being exposed to the second output chamber, the surface area of the one end face of the master piston being substantially greater than the surface area of the end face of the slave piston.
  • control valve means includes means for connecting the supply means to the second input chamber for pressurizing the second input chamber to move the piston assembly in one direction to increase incrementally the pressure in the pressure vessel pressure chamber and alternately for connecting the supply means to the second chamber for pressurizing the second chamber to move the piston assembly in the reverse direction.
  • the low and high pressure amplifiers each comprise reciprocative piston assemblies including master pistons having faces respectively exposed to the firstmentioned and second input chambers, and wherein the surface area of the master piston face associated with the high pressure amplifier is greater than the surface area of the master piston face associated with the low pressure amplifier.
  • the apparatus includes means defining a primary flow passage between the second output chamber and the pressure vessel pressure chamber, and means defining a secondary flow passage between the first-mentioned output chamber and the pressure vessel pressure chamber, and wherein the check valve means includes a one-way valve in the secondary flow passage, the one-way valve adapted for allowing passage of hydraulic pressure fluid through the secondary flow conduit only in a direction of flow from the first-mentioned output chamber to the pressure vessel pressure chamber.
  • the confusing means includes a disc member extending perpendicularly to the flow of pressurized pressure fluid through the valve means, the disc member having a plurality of holes therethrough, the holes being of various diameters and being positioned at various angles relative to the flow so as to create confusion in the flow through the holes.
  • the pressure vessel comprises an open ended tubular housing, the housing having a first inner diameter, first and second end sealing means for respectively sealing either end of the housing, the mandrel being tubular with a diameter less than the first. inner diameter.
  • first and second clamping means respectively threadedly coupled with either end of the housing for axially clamping the end sealing means and the mandrel therebetween, the first and second clamping means and the end sealing means each having relatively axially alignable apertures through which the portions of the elongated part and die on either side of the part section to be conformed are extendable.
  • control valve means comprises a valve selectively operable for connecting the first-mentioned input chamber with the supply means, and valve actuator means responsive to the pressure selector means for operating the valve means.
  • the pressure selector means includes a time delay relay, the actuator means being energizable by the time delay relay, the time delay relay adapted for energizing the actuator means once the pressure chamber has been prepressured with pressure fluid from the supply means.
  • the pressure selector means includes a second time delay .relay, the actuator means also being de-energizable by the second time delay relay, the second time delay relay adapted for de-energizing the actuator means once the fluid pressure in the pressure vessel pressure chamber has been increased by the low pressure amplifier.
  • the apparatus according to claim 12 including discharge means for receiving pressurized pressure fluid from the first-mentioned input chamber, and wherein the valve is further selectively operable for connecting the first-mentioned input chamber to the discharge means, the actuator means alternatively being responsive to the transition pressure means for further operating the valve.
  • control valve means comprises a valve selectively operable for connecting the second input chamber with the supply means, and valve actuator means responsive to the transition pressure means for operating the valve means.
  • the apparatus according to claim 16 including discharge means for receiving pressurized fluid from the second input chamber, and wherein the valve is fur ther selectively operable for connecting the second input chamber with the discharge means.
  • the apparatus according to claim 1 including discharge means for receiving pressurized pressure fluid from the pressure vessel pressure chamber, and wherein the depressurization means comprises unload valve means intermediate the discharge means and the pressure vessel pressure chamber operable for selectively allowing passage of pressurized pressure fluid from the pressure vessel pressure chamber, the unload valve means being responsive to the pressure selector means for allowing flow of pressurized pressure fluid therethrough simultaneously with depressurization of the first-mentioned and second input chambers.
  • the apparatus according to claim 18, including pressure responsive actuator means for Operating the unload valve means, a control valve for selectively connecting the supply means with the pressure responsive actuator means for operating the unload valve means, the control valve being responsive to the pressure selector means.
  • control valve alternatively connects the supply means with the pressure vessel pressure chamber.
  • the pressure selector means comprises a plurality of pressure responsive switching elements, one group of the switching elements being responsive to fluid pressure in the first-mentioned input chamber and another group of the switching elements being responsive to the fluid pressure in the second input chamber, and means for selecting one of the switching elements, the control valve means being responsive to the selected one of the switching elements.
  • transition pressure means comprises a pressure responsive switch element responsive to pressure in the first-mentioned input chamber.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Control Of Presses (AREA)
US533992A 1974-12-18 1974-12-18 Hydraulic-forming machine Expired - Lifetime US3910087A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US533992A US3910087A (en) 1974-12-18 1974-12-18 Hydraulic-forming machine
AU82500/75A AU489019B2 (en) 1974-12-18 1975-06-26 Hydraulic-forming machine
JP50081373A JPS5171574A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1974-12-18 1975-06-30
FR7521521A FR2294779A1 (fr) 1974-12-18 1975-07-09 Appareil pour conformer par compression une piece metallique au contour d'une matrice
GB29309/75A GB1505669A (en) 1974-12-18 1975-07-11 Method and apparatus for compressively conforming a portion of a metal blank to the contour of a die using pressurised fluid
DE19752534226 DE2534226A1 (de) 1974-12-18 1975-07-31 Hydraulische presse

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US533992A US3910087A (en) 1974-12-18 1974-12-18 Hydraulic-forming machine

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US3910087A true US3910087A (en) 1975-10-07

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US (1) US3910087A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
JP (1) JPS5171574A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
DE (1) DE2534226A1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
FR (1) FR2294779A1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
GB (1) GB1505669A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)

Cited By (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4183124A (en) * 1977-11-21 1980-01-15 Kisco Company Method of and apparatus for fabricating spiral wrapped cartridge cases
EP0251416A1 (en) * 1986-06-27 1988-01-07 Mark Jacob Goedkoop Deep-forming press
WO1996041957A1 (de) * 1995-06-09 1996-12-27 Mannesmann Rexroth Gmbh Hydraulische druckübersetzereinheit, insbesondere für eine nach dem innenhochdruckumformverfahren arbeitende presse
KR19990057196A (ko) * 1997-12-29 1999-07-15 오상수 압력유체 공급장치
US6000271A (en) * 1998-11-06 1999-12-14 Ap Parts International, Inc. Metal forming apparatus and method of use
US20040187546A1 (en) * 2003-03-28 2004-09-30 Shigeki Kodani Die cushion apparatus of press machine and surge pressure reduction method for die cushion apparatus
CN1306171C (zh) * 2004-07-06 2007-03-21 许宏 一种无源的流体动力控制方法及其控制系统
US7658196B2 (en) 2005-02-24 2010-02-09 Ethicon Endo-Surgery, Inc. System and method for determining implanted device orientation
US7775966B2 (en) 2005-02-24 2010-08-17 Ethicon Endo-Surgery, Inc. Non-invasive pressure measurement in a fluid adjustable restrictive device
US7775215B2 (en) 2005-02-24 2010-08-17 Ethicon Endo-Surgery, Inc. System and method for determining implanted device positioning and obtaining pressure data
US7844342B2 (en) 2008-02-07 2010-11-30 Ethicon Endo-Surgery, Inc. Powering implantable restriction systems using light
US7927270B2 (en) 2005-02-24 2011-04-19 Ethicon Endo-Surgery, Inc. External mechanical pressure sensor for gastric band pressure measurements
US8016745B2 (en) 2005-02-24 2011-09-13 Ethicon Endo-Surgery, Inc. Monitoring of a food intake restriction device
US8016744B2 (en) 2005-02-24 2011-09-13 Ethicon Endo-Surgery, Inc. External pressure-based gastric band adjustment system and method
US8034065B2 (en) 2008-02-26 2011-10-11 Ethicon Endo-Surgery, Inc. Controlling pressure in adjustable restriction devices
US8057492B2 (en) 2008-02-12 2011-11-15 Ethicon Endo-Surgery, Inc. Automatically adjusting band system with MEMS pump
US8066629B2 (en) 2005-02-24 2011-11-29 Ethicon Endo-Surgery, Inc. Apparatus for adjustment and sensing of gastric band pressure
US8100870B2 (en) 2007-12-14 2012-01-24 Ethicon Endo-Surgery, Inc. Adjustable height gastric restriction devices and methods
US8114345B2 (en) 2008-02-08 2012-02-14 Ethicon Endo-Surgery, Inc. System and method of sterilizing an implantable medical device
US8142452B2 (en) 2007-12-27 2012-03-27 Ethicon Endo-Surgery, Inc. Controlling pressure in adjustable restriction devices
US8152710B2 (en) 2006-04-06 2012-04-10 Ethicon Endo-Surgery, Inc. Physiological parameter analysis for an implantable restriction device and a data logger
US8187163B2 (en) 2007-12-10 2012-05-29 Ethicon Endo-Surgery, Inc. Methods for implanting a gastric restriction device
US8187162B2 (en) 2008-03-06 2012-05-29 Ethicon Endo-Surgery, Inc. Reorientation port
US8192350B2 (en) 2008-01-28 2012-06-05 Ethicon Endo-Surgery, Inc. Methods and devices for measuring impedance in a gastric restriction system
US8221439B2 (en) 2008-02-07 2012-07-17 Ethicon Endo-Surgery, Inc. Powering implantable restriction systems using kinetic motion
US8233995B2 (en) 2008-03-06 2012-07-31 Ethicon Endo-Surgery, Inc. System and method of aligning an implantable antenna
US8337389B2 (en) 2008-01-28 2012-12-25 Ethicon Endo-Surgery, Inc. Methods and devices for diagnosing performance of a gastric restriction system
US8377079B2 (en) 2007-12-27 2013-02-19 Ethicon Endo-Surgery, Inc. Constant force mechanisms for regulating restriction devices
US8591395B2 (en) 2008-01-28 2013-11-26 Ethicon Endo-Surgery, Inc. Gastric restriction device data handling devices and methods
US8591532B2 (en) 2008-02-12 2013-11-26 Ethicon Endo-Sugery, Inc. Automatically adjusting band system
US8870742B2 (en) 2006-04-06 2014-10-28 Ethicon Endo-Surgery, Inc. GUI for an implantable restriction device and a data logger
CN105252796A (zh) * 2014-03-26 2016-01-20 株式会社三井高科技 薄板凹凸部件的制造装置和制造方法
US9821360B2 (en) 2013-07-26 2017-11-21 Mitsui High-Tec, Inc. Apparatus and method for manufacturing thin uneven member
CN111720378A (zh) * 2020-07-23 2020-09-29 南通锻压设备如皋有限公司 充液成型液压机的多级增压安全耦合液压系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0225296A (ja) * 1988-07-15 1990-01-26 Amino Tekkosho:Kk 超高圧液圧成形機

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US3290919A (en) * 1963-12-18 1966-12-13 Cincinnati Milling Machine Co High pressure hydraulic forming press
US3376723A (en) * 1965-08-16 1968-04-09 Bolt Associates Inc Methods and apparatus for forming material by sudden impulses
US3635061A (en) * 1968-12-09 1972-01-18 Saab Ab Forming apparatus for hydraulic press
US3657793A (en) * 1967-11-22 1972-04-25 Siemens Ag Method and device for reducing the spacing between the jacket tube of nuclear reactor fuel rods and the charge of fuel received therein

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3290919A (en) * 1963-12-18 1966-12-13 Cincinnati Milling Machine Co High pressure hydraulic forming press
US3376723A (en) * 1965-08-16 1968-04-09 Bolt Associates Inc Methods and apparatus for forming material by sudden impulses
US3657793A (en) * 1967-11-22 1972-04-25 Siemens Ag Method and device for reducing the spacing between the jacket tube of nuclear reactor fuel rods and the charge of fuel received therein
US3635061A (en) * 1968-12-09 1972-01-18 Saab Ab Forming apparatus for hydraulic press

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4183124A (en) * 1977-11-21 1980-01-15 Kisco Company Method of and apparatus for fabricating spiral wrapped cartridge cases
EP0251416A1 (en) * 1986-06-27 1988-01-07 Mark Jacob Goedkoop Deep-forming press
WO1996041957A1 (de) * 1995-06-09 1996-12-27 Mannesmann Rexroth Gmbh Hydraulische druckübersetzereinheit, insbesondere für eine nach dem innenhochdruckumformverfahren arbeitende presse
KR19990057196A (ko) * 1997-12-29 1999-07-15 오상수 압력유체 공급장치
US6000271A (en) * 1998-11-06 1999-12-14 Ap Parts International, Inc. Metal forming apparatus and method of use
US20040187546A1 (en) * 2003-03-28 2004-09-30 Shigeki Kodani Die cushion apparatus of press machine and surge pressure reduction method for die cushion apparatus
US7197910B2 (en) * 2003-03-28 2007-04-03 Komatsu Ltd. Die cushion apparatus of a press machine and surge pressure reduction method for a die cushion apparatus
CN1306171C (zh) * 2004-07-06 2007-03-21 许宏 一种无源的流体动力控制方法及其控制系统
US7658196B2 (en) 2005-02-24 2010-02-09 Ethicon Endo-Surgery, Inc. System and method for determining implanted device orientation
US7775966B2 (en) 2005-02-24 2010-08-17 Ethicon Endo-Surgery, Inc. Non-invasive pressure measurement in a fluid adjustable restrictive device
US7775215B2 (en) 2005-02-24 2010-08-17 Ethicon Endo-Surgery, Inc. System and method for determining implanted device positioning and obtaining pressure data
US7927270B2 (en) 2005-02-24 2011-04-19 Ethicon Endo-Surgery, Inc. External mechanical pressure sensor for gastric band pressure measurements
US8016745B2 (en) 2005-02-24 2011-09-13 Ethicon Endo-Surgery, Inc. Monitoring of a food intake restriction device
US8016744B2 (en) 2005-02-24 2011-09-13 Ethicon Endo-Surgery, Inc. External pressure-based gastric band adjustment system and method
US8066629B2 (en) 2005-02-24 2011-11-29 Ethicon Endo-Surgery, Inc. Apparatus for adjustment and sensing of gastric band pressure
US8870742B2 (en) 2006-04-06 2014-10-28 Ethicon Endo-Surgery, Inc. GUI for an implantable restriction device and a data logger
US8152710B2 (en) 2006-04-06 2012-04-10 Ethicon Endo-Surgery, Inc. Physiological parameter analysis for an implantable restriction device and a data logger
US8187163B2 (en) 2007-12-10 2012-05-29 Ethicon Endo-Surgery, Inc. Methods for implanting a gastric restriction device
US8100870B2 (en) 2007-12-14 2012-01-24 Ethicon Endo-Surgery, Inc. Adjustable height gastric restriction devices and methods
US8142452B2 (en) 2007-12-27 2012-03-27 Ethicon Endo-Surgery, Inc. Controlling pressure in adjustable restriction devices
US8377079B2 (en) 2007-12-27 2013-02-19 Ethicon Endo-Surgery, Inc. Constant force mechanisms for regulating restriction devices
US8192350B2 (en) 2008-01-28 2012-06-05 Ethicon Endo-Surgery, Inc. Methods and devices for measuring impedance in a gastric restriction system
US8591395B2 (en) 2008-01-28 2013-11-26 Ethicon Endo-Surgery, Inc. Gastric restriction device data handling devices and methods
US8337389B2 (en) 2008-01-28 2012-12-25 Ethicon Endo-Surgery, Inc. Methods and devices for diagnosing performance of a gastric restriction system
US7844342B2 (en) 2008-02-07 2010-11-30 Ethicon Endo-Surgery, Inc. Powering implantable restriction systems using light
US8221439B2 (en) 2008-02-07 2012-07-17 Ethicon Endo-Surgery, Inc. Powering implantable restriction systems using kinetic motion
US8114345B2 (en) 2008-02-08 2012-02-14 Ethicon Endo-Surgery, Inc. System and method of sterilizing an implantable medical device
US8057492B2 (en) 2008-02-12 2011-11-15 Ethicon Endo-Surgery, Inc. Automatically adjusting band system with MEMS pump
US8591532B2 (en) 2008-02-12 2013-11-26 Ethicon Endo-Sugery, Inc. Automatically adjusting band system
US8034065B2 (en) 2008-02-26 2011-10-11 Ethicon Endo-Surgery, Inc. Controlling pressure in adjustable restriction devices
US8233995B2 (en) 2008-03-06 2012-07-31 Ethicon Endo-Surgery, Inc. System and method of aligning an implantable antenna
US8187162B2 (en) 2008-03-06 2012-05-29 Ethicon Endo-Surgery, Inc. Reorientation port
US9821360B2 (en) 2013-07-26 2017-11-21 Mitsui High-Tec, Inc. Apparatus and method for manufacturing thin uneven member
CN105252796A (zh) * 2014-03-26 2016-01-20 株式会社三井高科技 薄板凹凸部件的制造装置和制造方法
CN105252796B (zh) * 2014-03-26 2017-09-22 株式会社三井高科技 薄板凹凸部件的制造装置和制造方法
CN111720378A (zh) * 2020-07-23 2020-09-29 南通锻压设备如皋有限公司 充液成型液压机的多级增压安全耦合液压系统

Also Published As

Publication number Publication date
JPS5171574A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1976-06-21
GB1505669A (en) 1978-03-30
AU8250075A (en) 1977-01-06
FR2294779A1 (fr) 1976-07-16
FR2294779B1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1979-05-18
DE2534226A1 (de) 1976-07-01

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