US3518869A - Hydraulic press,more particularly for treating metals by shaping - Google Patents

Hydraulic press,more particularly for treating metals by shaping Download PDF

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Publication number
US3518869A
US3518869A US643903A US3518869DA US3518869A US 3518869 A US3518869 A US 3518869A US 643903 A US643903 A US 643903A US 3518869D A US3518869D A US 3518869DA US 3518869 A US3518869 A US 3518869A
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Prior art keywords
press
piston
approach
work
fluid
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Expired - Lifetime
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US643903A
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English (en)
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Gaston Sebastien Forichon
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/10—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by toggle mechanism
    • B30B1/16—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by toggle mechanism operated by fluid-pressure means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure

Definitions

  • the pressure of a work fluid is used, both for the approach stage of the press plate as for the work stage itself.
  • FIG. 1 illustrates by means of diagrams the various stages of the operating cycle of known hydraulic presses. To the left of the diagram the press punch 1 is diagrammatized, as well as the billet 2, before treatment.
  • the press piston, and hence the punch are in the top position, i.e., the pressure chamber, delimited between said piston and its cylinder, is reduced to a minimum volume.
  • the billet 2 for treatment is placed on the lower female die plate and the press is ready for operating.
  • the slowing-down stage is also detrimental to the speed of operating the press, owing to braking the punch which, before all things, is necessary if we wish to avoid an abrupt impact of said punch on the billet, which may lead to the damaging of the tools.
  • This Work stage is again also determined by an increase of the pressure of the fluid, so that the punch deforms the billet for modelling it into the required shape.
  • the piston now returns to its initial position.
  • the press is once more ready to operate.
  • the times required for each working stage of the press are given, by way of example, in seconds, and this, so as subsequently to be able to compare these times with those obtained by the press according to the invention.
  • the invention has the object of obviating these disadvantages and relates, to this end, to an hydraulic press for treating metals by shaping comprising an upper punch holder plate and a lower female die holder plate, one of these two plates being mobile in relation to each other by a hydraulic unit, adjustable mechanical means ensuring the movement of the press piston in the corresponding stroke at its approach stage, i.e., until it abuts on the face of the rough part, these same mechanical means also acting for returning the press piston to its initial position.
  • the mechanical means determining the approach of the press piston, act in relation with a direct reading device.
  • the reading device consists of a sliding-gauge in front of which a pointer moves integral with an intermediate plate, itself in relation with the adjustable mechanical means, which enables instantaneously the ascertaining of the approach stroke of the press piston.
  • FIG. 1 is a diagram corresponding to the work cycle of known presses.
  • FIG. 2 is a diagram, showing the possibility of comparing the results obtained with a press according to 3 the invention in relation to the diagram shown in FIG. 1, and corresponding to the work cycle of known presses.
  • FIG. 3 is a diagrammatical view showing a method of making the press according to the invention, in which the punch is in the top position.
  • FIG. 4 is a diagrammatical view corresponding to FIG. 3, in which the punch is in the bottom position.
  • FIGS. 5 and 6 are diagrammatical views showing an alternative embodiment.
  • FIG. 7 is a diagrammatical view of a third method of embodiment.
  • One of the objects of the invention is to make the maximum reduction of the work cycle time of a hydraulic press, so as to increase the rhythm of output of said press, in order to reduce the cost price of treated arts.
  • the fundamental idea of the invention essentially lies in the temporary substitution of mechanical means for hydraulic means, more particularly in the approach stage of the punch or press piston, which thus leads to the suppressing of the slowing-down stage F and a considerable reduction of the compression and decompression stages of the fluid.
  • the hydraulic press itself consists of a hydraulic unit comprising a tank 3, from which two pumps P and P draw (P being a reduced pressure pump), said pumps being actuated by a Motor It is from these pumps P and P that the dispatching of the work fluid takes place, and this by means of a series of electro-valves EVa, EVb, EVc, EVd, which direct the fluid in a direction pertinent to the stage that it must fulfill at a precise moment, of the work cycle.
  • P being a reduced pressure pump
  • the press is made of a partially hollowed out frame 9, so as to form a cavity in which the press piston 10 can move in a vertical plane, which delimits, in relation to the cavity 11 forming the cylinder, a chamber 12, called the pressure chamber.
  • the piston 10 is also hollowed out so as to accommodate the body of a displaceable screw 13, whose base is provided with a pinion 15 actuated by an auxiliary electric motor 16.
  • This screw 13 is connected to an intermediate plate 17, which comprises a pointer 18, able to move in front of a graduated scale 19.
  • the mechanical means causing the movement of the work piston 10, and hence that of the intermediate plate, are made, in this example of embodiment, from two jointed links 26 and the first one 26 being connected to the intermediate plate 17, whereas the second 20 is connected to the upper punch holder plate 21.
  • the angle of opening or closing, formed by the two jointed links 20 and 20 is ensured by an auxiliary piston 22, connected to the latter by a third link 23, said intermediate piston being movable crosswise in a cylinder 24 filled with fluid.
  • a first adjustment of the position of the jointed links 20 and 20 is ensured by a screw stop 25, maneuvered by a second auxiliary motor 26, whose driving pinion 27 constantly meshes with a lock-nut 28 connected to the screw stop 25.
  • the guiding and recoil of the upper punch-holder plate 21 is ensured by two small jacks, formed by the pistons 29 and 29 which move in the cylinders 30 and 30
  • the lower female die holder plate of the press 31 is, more- 4 over, provided with an ejecter 32 for withdrawing the finished parts.
  • the pump P delivers at low pressure (adjusted by the valve 6 in the rising cylinders 30 and 30 so that the pistons 29 and 29 hold the upper punch-holder plate 21 in its top position, in like manner as the auxiliary piston 22 is kept in a retracted position, i.e., pressed against the screw stop 25, owing to the electrovalve EVd being positioned for affording free passage for the fluid delivered by the pump P to the chamber 24 situated in front of the piston 22, the chamber 24 situated behind the piston, being, on the contrary, connected by the electro-valve EVd, to the tank 3, so that the pressure proportionally lowers in this chamber.
  • FIG. 4 is a view corresponding to FIG. 3, the upper punch holder press plate being nevertheless in its end of stroke position.
  • the auxiliary piston 22 is moved in the direction of the arrow F, this movement being the more favorized in that the pressure initially prevailing in the cylinders 30 and 30 diminishes and that, hence, the upper punch-holder plate 21 is free to move downwards (in a vertical plane), the displacement of the auxiliary piston 22 (in the direction of the arrow F) progressively determining the alignment of the links 20 and 20 and hence, the downward movement of the upper punch-holder plate 21, until it abuts against the billet 2 to be treated.
  • This stroke forming the approach stage, is pre-regulated by means of the stop screw 25, whereas the possible displacement of the intermediate plate 17, whose stroke can be ensured by the auxiliary motor 16, enables the upper face of the piston 10 to be correctly pressed against the bottom of the cylinder 11, for preserving, before the piston is displaced, a minimum volume in the pressure chamber 12.
  • the approach travel corresponds to the distance h checked, by direct reading on the graduated scale 19, by means of the pointer 18 integral with the intermediate plate, wheras the distance H (FIG. 3) between the plates is checked by the pointer 18 on the graduated scale 19
  • the swiveljoint 43 comes into contact with the electric switch 8 which inverts the electro-valve EVa; it then suflices to invert it, from the position it occupies in FIG. 3, to bring it to the position that it occupies in FIG. 4.
  • the electro-valve EVa directly connects the pump P to the work chamber 12; situated behind the upper face of the press piston 10, and this by means of ducts 41 and 42 put into relation.
  • the hydraulic pressure ensured in the chamber 12, causes the crushing, i.e., the deforming of the billet, until the latter is modeled to the required shape, by the cooperation of the die integral with the lower plate 31 and the punch integral with the upper plate 21.
  • the pressuregauge contact 7 When the shaping operation itself is terminated, the pressure having reached the required value, the pressuregauge contact 7 immediately operates the inversion of the electro-valves to bring them back to the position that they originally occupied, i.e., that shown in FIG. 3.
  • the auxiliary jack 22 recoils, to become pressed against the screw stop 25.
  • the articulation points of the links come close to each other, corresponding to the rise of the upper punch-holder plate, this action being moreover favorized by the electro-valve EVd which enables the fluid to enter, delivered by the pump P into the cylinders 30, and 30 where the lifting pistons 29 and 29 of the plate are found.
  • the pump P ensures, by means of the duct 44, the working of the ejector 32 which enables the shaped part to be withdrawn.
  • FIGS. 5 and 6 show an alternative embodiment, in which it is not the upper punch-holder plate 21 that is displaced by mechanical means, but on the contrary, the lower female die-holder plate 31.
  • the links which, here again, determine the approach stage of the plate, are no longer two in number, but four, symmetrically distributed so as to enable a regular ascensional displacement in a horizontal plane, of the press plate 31.
  • screw stop 25 is, according to this embodiment, no longer driven as in FIGS. 3 and 4 by means of an intermediate motor 26, but by hand by means of a winch 45.
  • the punch-holder plate 21 is moreover returned to the top position by recoil pistons 48 and 48 which move in cylinders 49 and 49 made in the frame of the machine.
  • the auxiliary piston 22 ensures, by moving in the direction of the arrow F, the alignment of the links 20 20 and 20 which determines the displacement of the female die-holder lower plate 31, whose travel corresponds to the approach stage h, checked by direct reading on the graduated scale 19, by means of the pointer 12 integral with the lower female-die-holder plate 31.
  • the distance H between the plates is always checked by a pointer 18, moving in front of the slidinggauge 19,.
  • the ejector 32 need not be driven, and in this case it is the return of the lower female dieholder plate 31 which ensures the ejecting of the finished part.
  • FIG. 7 shows another alternative embodiment, in which the links of the knuckle-joint type are replaced by a high-speed screw 50, this screw being maneuvered by an auxiliary motor 51 (electric or hydraulic) whose driving pinion 52 continually meshes with a toothed crown wheel 53, integral with the screw 50 of the punch-holder upper press piston 21.
  • auxiliary motor 51 electric or hydraulic
  • This switch 8 must be positioned so as to start up the work operation at the end of the approach travel.
  • a hydraulic press comprising,
  • first and second holder plates adapted for relative movement from an open position to an approach position of reduced separation, and from said approach position to a closed position of yet further reduced separation
  • approach-recoil drive means for effecting approach movement between said open position and said approach position and for effecting recoil movement between said approach position and said open posiion
  • workk-stroke drive means for effecting work-stroke movement between said approach position and said closed position
  • adjustable control means for determining the amplitude of movement between said open position and said approach position and for determining the separation of said holder plates at said approach position, and indicator means to provide a visual indication of the setting of said control means.
  • said work-stroke drive means comprises a hydraulic cylinder and a cooperating piston
  • said piston is connected to said first holder plate through a first adjustable linkage and having a second linkage capable of variable positioning,
  • said first linkage serving to determine the separation of said holder plates at said approach position, said secnd linkage being controlled by said approach-recoil drive means,
  • control means comprising means to determine amplitude of variation in positioning of said second linkage produced by operation of said approach-recoil drive means, said indicator means comprising a first visual indicator for indicating the amplitude of said approach movement and a second visual indicator for indicating the amplitude of said work-stroke movement.
  • said indicator means comprises a first pointer integral with said first holder plate and adapted to indicate the absolute position of said plate with respect to said press, and a second pointer integral with said piston and adapted to indicate the relative separation of said piston and said first holder plate.
  • said approach-recoil drive means comprises an auxiliary hydraulic cylinder, a cooperating auxiliary piston, and an adjustment screw to regulate the initial position of said auxiliary piston and to thereby determine the amplitude of said approach movement.
  • said work-stroke drive means comprises a hydraulic cylinder and a cooperating piston
  • said piston is connected to said first holder plate through an adjustable linkage
  • said second holder plate is driven by said approach-recoil drive means
  • said indicator means comprises a first pointer integral 3 with said first holder plate, and a second pointer integral with said second holder plate.
  • said approach recoil drive means comprise a plurality of articulated links connecting said second holder plate to the frame of said press and actuated by a hydraulic jack having a piston adapted to have its initial position manually pre-regulated.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Press Drives And Press Lines (AREA)
US643903A 1967-03-30 1967-06-06 Hydraulic press,more particularly for treating metals by shaping Expired - Lifetime US3518869A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR100829A FR1517290A (fr) 1967-03-30 1967-03-30 Presse hydraulique notamment pour le traitement de métaux par formage

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US3518869A true US3518869A (en) 1970-07-07

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US (1) US3518869A (fr)
DE (2) DE1972393U (fr)
FR (2) FR1517290A (fr)
GB (1) GB1186369A (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3763689A (en) * 1970-08-20 1973-10-09 B & R Products Proprietary Ltd Multi-purpose sheet metal folding press, punch, and nibbling machine
JPS5074267A (fr) * 1973-11-05 1975-06-18
US3926033A (en) * 1974-01-28 1975-12-16 Renault Toggle-joint press
JPS5264983U (fr) * 1976-09-30 1977-05-13
US4393684A (en) * 1981-02-12 1983-07-19 Penn Engineering & Manufacturing Corp. Press having a linkage mechanism connectable and disconnectable from a ram
US4944221A (en) * 1986-06-20 1990-07-31 E. Bruderer Maschinenfabrik Ag Articulated lever cutting and forming press
US5253572A (en) * 1991-09-24 1993-10-19 Aida Engineering, Ltd. Press with independent controls for reciprocation of and pressure application by RAM
US5845528A (en) * 1997-10-07 1998-12-08 Artos Engineering Company Apparatus for crimping terminals on an electrical conductor

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4646555A (en) * 1985-02-26 1987-03-03 Andrew Postupack Dual stage press
DE4018493C2 (de) * 1990-06-09 2000-07-27 Bernd Hoerner Presse, insbesondere Verformungspresse
DE4106639A1 (de) * 1991-02-28 1992-09-10 Mannesmann Ag Hydraulische presse fuer pulverfoermige massen
JP2917615B2 (ja) * 1991-06-20 1999-07-12 富士電機株式会社 圧電アクチュエータ応用のプレス装置
DE4216210A1 (de) * 1992-05-15 1993-11-18 Multivac Haggenmueller Kg Arbeitsstation mit einem Oberteil und einem relativ dazu bewegbaren Unterteil
DE4322318A1 (de) * 1993-07-05 1995-01-12 I Vom Heu Rationalisierungstec Pressvorrichtung
DE4410004C2 (de) * 1994-01-31 1996-09-19 Baumueller Nuernberg Gmbh Vorrichtung zum Pressen oder hydraulische Hubeinrichtung
CN104626631A (zh) * 2015-03-13 2015-05-20 康凤明 一种助力伺服压力机

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1007792A (en) * 1910-10-17 1911-11-07 Bliss E W Co Press.
US1696849A (en) * 1928-12-25 Bending machine
US1956658A (en) * 1930-10-11 1934-05-01 Schmidt Wilhelm Engaging and disengaging device for presses, stamping machines, and similar machine tools
US2087811A (en) * 1934-06-15 1937-07-20 Hydraulic Press Corp Inc Press
US2339855A (en) * 1942-05-05 1944-01-25 Ralph W Hodil Machine for testing adherence of sheet coatings
US2353895A (en) * 1941-11-06 1944-07-18 Folmer Graflex Corp Film pack holder or adapter
GB782948A (en) * 1954-08-10 1957-09-18 Schloemann Ag Control for a forging press
US2962960A (en) * 1956-09-29 1960-12-06 Loewy Eng Co Ltd Remote positional control for hydraulic presses
US3162232A (en) * 1963-01-14 1964-12-22 Niagara Machine & Tool Works Multiple depth control for power press brakes
US3373596A (en) * 1965-06-18 1968-03-19 Gerd M. Moeller Hydraulic press

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1696849A (en) * 1928-12-25 Bending machine
US1007792A (en) * 1910-10-17 1911-11-07 Bliss E W Co Press.
US1956658A (en) * 1930-10-11 1934-05-01 Schmidt Wilhelm Engaging and disengaging device for presses, stamping machines, and similar machine tools
US2087811A (en) * 1934-06-15 1937-07-20 Hydraulic Press Corp Inc Press
US2353895A (en) * 1941-11-06 1944-07-18 Folmer Graflex Corp Film pack holder or adapter
US2339855A (en) * 1942-05-05 1944-01-25 Ralph W Hodil Machine for testing adherence of sheet coatings
GB782948A (en) * 1954-08-10 1957-09-18 Schloemann Ag Control for a forging press
US2962960A (en) * 1956-09-29 1960-12-06 Loewy Eng Co Ltd Remote positional control for hydraulic presses
US3162232A (en) * 1963-01-14 1964-12-22 Niagara Machine & Tool Works Multiple depth control for power press brakes
US3373596A (en) * 1965-06-18 1968-03-19 Gerd M. Moeller Hydraulic press

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3763689A (en) * 1970-08-20 1973-10-09 B & R Products Proprietary Ltd Multi-purpose sheet metal folding press, punch, and nibbling machine
JPS5074267A (fr) * 1973-11-05 1975-06-18
US3926033A (en) * 1974-01-28 1975-12-16 Renault Toggle-joint press
JPS5264983U (fr) * 1976-09-30 1977-05-13
US4393684A (en) * 1981-02-12 1983-07-19 Penn Engineering & Manufacturing Corp. Press having a linkage mechanism connectable and disconnectable from a ram
US4944221A (en) * 1986-06-20 1990-07-31 E. Bruderer Maschinenfabrik Ag Articulated lever cutting and forming press
US5253572A (en) * 1991-09-24 1993-10-19 Aida Engineering, Ltd. Press with independent controls for reciprocation of and pressure application by RAM
US5845528A (en) * 1997-10-07 1998-12-08 Artos Engineering Company Apparatus for crimping terminals on an electrical conductor

Also Published As

Publication number Publication date
FR94434E (fr) 1969-08-14
GB1186369A (en) 1970-04-02
DE1972393U (de) 1967-11-09
DE1627818A1 (de) 1971-01-21
FR1517290A (fr) 1968-03-15

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