US3550425A - Hydraulic machine for deforming sheet metal - Google Patents

Hydraulic machine for deforming sheet metal Download PDF

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Publication number
US3550425A
US3550425A US747330A US3550425DA US3550425A US 3550425 A US3550425 A US 3550425A US 747330 A US747330 A US 747330A US 3550425D A US3550425D A US 3550425DA US 3550425 A US3550425 A US 3550425A
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United States
Prior art keywords
machine
hydraulic
bolster
jacks
sheet metal
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US747330A
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English (en)
Inventor
Paul Cailloux
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Promecam Sisson Lehmann SA
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Promecam Sisson Lehmann SA
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D15/00—Shearing machines or shearing devices cutting by blades which move parallel to themselves
    • B23D15/12—Shearing machines or shearing devices cutting by blades which move parallel to themselves characterised by drives or gearings therefor
    • B23D15/14—Shearing machines or shearing devices cutting by blades which move parallel to themselves characterised by drives or gearings therefor actuated by fluid or gas pressure
    • 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
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
    • B21D5/0272—Deflection compensating means
    • 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
    • B30B15/24—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam
    • B30B15/245—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam using auxiliary cylinder and piston means as actuating members
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/28—Arrangements for preventing distortion of, or damage to, presses or parts thereof
    • B30B15/281—Arrangements for preventing distortion of, or damage to, presses or parts thereof overload limiting devices

Definitions

  • FIG.1 A first figure.
  • HYDRAULIC MACHINE FOR DEF'ORMING SHEET METAL Dec. 29, 1970 Filed July 24, 1968 3 Sheets-Sheet 5 United States Patent 3,550,425 HYDRAULIC MACHINE FOR DEFORMING SHEET METAL Paul Cailloux, Le Perreux, France, assignor to Promecan Sisson-Lehmann, Saint-Denis, France, a French body corporate Filed July 24, 1968, Ser. No. 747,330 Claims priority, application France, July 26, 1967, 115,702 Int. Cl. B21j 9/12 US. Cl.
  • the present invention relates to hydraulic machines for deforming or working sheet metal, such as shears, presses in general, and in particular folding presses comprising a fixed bolster and a moving bolster.
  • devices For maintaining the moving bolster parallel to the fixed bolster, devices are known comprising two correcting jacks located on each side of the longitudinal axis of the machine, these jacks, of the double-rod type and having two equal chambers, are interconnected by two crossed conduits so that they are self fed for movements in the same direction and of the same amplitude. Devices of this type are also known in which the two crossed conduits are also fed in such manner that a predetermined inclination of the moving bolster relative to the fixed bolster can be maintained during the stroke and that possible leakages or reduction in the volume of oil due to compression can be compensated.
  • the object of the invention is to remedy the aforementioned defects and insufficieneies.
  • the invention provides a machine for deforming sheet metal, such as shears, presses, folding presses and the like, comprising a fixed bolster and a moving bolster actuated by one or more jacks and equipped with a synchronizing system comprising two hydraulic compensating devices which are fed by the action of an indicator indicating angular deviations between the two bolsters which acts on a distributor valve which is so inserted in the hydraulic circuit that any angular deviation between the holsters results in a corresponding movement but of opposite direction of the hydraulic compensators.
  • the indicator in addition to its usual functions of maintaining the parallelism and the predetermined angles between the bolsters, receives impulses which are proportional to deviations due to the opening of the swan-neck side walls, that is, to differences in the elastic deformation of said side walls under stress, from a hydraulic corrector comprising a part fixed to the frame of the machine and a movable part connected to said distributor, whereby said impulses produce an additional correction of the position of the moving bolster relative to the fixed bolster and nullify the consequences of the deviations due to the opening of the side walls.
  • This machine also comprises a safety device which cuts off the supply of the motor of the machine as soon as the difference in the elastic deformations of the side walls reaches a predetermined limit value.
  • a safety device which cuts off the supply of the motor of the machine as soon as the difference in the elastic deformations of the side walls reaches a predetermined limit value.
  • FIG. 1 is a front elevational view of the assembly of a typical machine showing the position of the main parts
  • FIG. 2 is a side elevational view of the assembly of the machine
  • FIG. 3 is a hydraulic diagram showing the indicator indicating angular deviations and the system correcting the deviations
  • FIG. 4 is a view of another version of the hydraulic correcting device.
  • FIG. 5 is a corresponding electric circuit diagram.
  • the fixed frame 1 of the presently described machine comprises two transverse side walls 10, 1a to which is secured a fixed bolster 2, and two longitudinal walls 1a and 111 between which is movable a moving bolster 3 whose stroke or travel towards the fixed bolster 2 results from the action of thrust jacks or rams 4 which bear against the walls 1a and 1b through journals 4a, 417.
  • the moving bolster 3 is made parallel to, or placed at any other given angle relative to the fixed bolster 2, by the action of two auxiliary jacks 3 which operate in opposite directions as shown in FIG. 3 and constitute compensating devices,
  • the auxiliary jacks 5 are connected by two crossed conduits or lines 22a and 23a in such manner that the chamber of one communicates with the chamber 21 of the other and vice versa.
  • conduits 22b, 23b and 230 are connected by conduits 22b, 23b and 230 to two outlet ports of a distributor slide valve 7 whose body is integral with the fixed frame 1.
  • One of two inlet ports of this valve is connected by the conduit to the general tank of the machine and the other is connected by the conduit 24 to the common supply conduit of the thrust rams 4 so that, if the auxiliary jacks 5 must be fed, they are fed under a pressure which is proportional to that prevailing in these rams.
  • One end of the slide of the valve 7 is connected to the fixed frame 1 through a tension spring 9 and the other end is connected to a flexible element 10 which can be, for example, a wire, cable, chain or ribbon preferably of steel.
  • the valve 7 thus forms a part of the device that compensates for angular deviations of the bolsters.
  • this flexible element 10 travels round two rollers 11 and 12, the spindles of which are carried by the fixed frame 1, and, between these rollers, round a roller 13 whose spindle is carried by a yoke 14 controlled by a screwthreaded rod 15 screwthreadedly engaged in a nut 17 which is integral with the frame 1.
  • the rod is provided with a handwheel 16 for varying the position of the roller 13 on the axis of symmetry between the two rollers 11 and 12 and consequently the length of the flexible element 10 in this part of its path.
  • the flexible element 10 travels round two rollers 18 and 19 whose spindles are carried by the moving bolster 3 and located on a line which is substantially perpendicular to the direction of the movement of the moving bolster towards the fixed bolster 2.
  • the other end of the element 10 is connected to the hydraulic correcting device, described hereinafter, which modifies the action of the element 10 on the valve 7 as a function of the pressures admitted into the conduits 220 or 23c.
  • this hydraulic correcting device is a double-rod jack 26 whose cylinder 27 is integral with the fixed frame 1 and divided into two chambers 29 and 30 by a piston 28 having double rods, these chambers being fed by way of the conduits 23c and 220, respectively.
  • the piston 28 is biased to a midway position in its travel by two opposed compression springs 31 and 32 hearing against the cylinder 27.
  • the action of the spring 31 opposes those of the springs 9 and 32 and the piston 28 is therefore in static equilibrium while the flexible element 10 is under permanent tension.
  • the assembly is adjusted in such manner that, in this situation, the position of the two rollers 18 and 19 corresponds to a correct parallelism between the fixed and moving bolsters 2 and 3 and that the slide of the valve 7 is exactly in the midway position of its travel.
  • a block 33 integral with the piston 28 is adapted to actuate microswitches 34 and 35 of conventional break type integral with the frame 1 (FIG. 5). These microswitches cut off the current of the maintaining coil 36 of the main switch 44 of the motor-pump M and stop the whole of the machine as soon as a given amplitude of the travel of the piston 28 is reached.
  • this hydraulic correcting device consists of three pins 37a, 38b and 38c which are integral with the fixed frame 1 and on which are pivotable respectively a jack 38a, a straight lever 39 and a cranked lever 40.
  • the other end of the jack 38a is connected to the end of the straight lever 39 by a pin 39a and a second jack 38b is connected to the other end of the lever 39 by a pin 39b and, moreover, to the cranked lever 40 by a pin 40a.
  • Hooked onto the lever 40 4 is one end of the flexible element 10. The whole of this arrangement is put under tension by the spring 9.
  • the jack 38a is fed by way of the conduit 23c and the jack 38/) by way of the conduit 22c.
  • These two jacks comprise two cylinders 41a and 41b to which are fixed two pistons 42a and 4212, respectively, by two rods 43a and 4312 which become elastically extended as a function of the pressures prevailing in each jack and pivot the cranked lever 40 in one direction or the other on its pin 370.
  • the lever 40 actuates the microswitches 34 and 35 as soon as a predetermined amplitude of movement has been reached and these switches stop the whole of the machine as explained with reference to FIG. 3.
  • the two auxiliary jacks 5 which have opposite directions of action, then produce a couple in the clockwise direction, that is, in the direction opposed to that of the inclination of the aforementioned imaginary line, this couple being maintained so long as the disequilibrium lasts and so long as the spindles of the rollers 18 and 19 have not resumed their initial position.
  • this action is also proportional to the machine loading pressure which is defined by the pressure prevailing in the suply conduit 24 and is consequently proportional to the elastic deformations or openings of the branches of the vertical uprights 1c and 1d of the machine.
  • These openings are of extent DC and DC (FIG. 2) and have no effect on the parallelism of the two bolsters in that they are of the same value at both ends of the bolsters and are not corrected in this case, but only in this case.
  • the auxiliary jacks 5 in the suitable direction owing to the action of the jack 26. shown in FIG.
  • the machine according to the present invention consequently achieves a degree of operational precision in practice which is of particular interest for the user while affording a remarkable protection of the main parts.
  • a hydraulic machine for deforming sheet metal of the type having a fixed bolster, a moving bolster supported on a fixed frame having swan-neck lateral walls and a motor-pump unit for supplying oil under pressure from a tank to a hydraulic circuit which feeds at least one thrust ram, the movement of the moving bolster being controlled by a hydraulic synchronizing device which maintains said bolsters in a predetermined relative posi-- tion, said synchronizing device including a hydraulic distributor valve, and means for operating said valve in response to angular deviation of one of said bolsters relative to the other bolster, the improvement comprising a correcting device, said correcting device including means for modifying the effect of said operating means on said distributor valve in proportion to hydraulic pressure in said circuit, whereby the correcting device modifies the action of said synchronizing device so as to compensate dilferences in the elastic deformations of said lateral walls under load and thus maintain said relative position of said bolsters.
  • said hydraulic synchronizing device comprises two jacks having four chambers and two crossed conduits putting said chambers in communication with each other, said correcting device comprising two chambers which communicate with the respective conduits of said jacks of said synchronizing device and are defined by at least one piston,
  • said distributor valve having a slide valving element
  • said operating means including a flexible element having one end connected to said piston and another end connected to said slide of said valve, whereby the differences in the pressures in the conduits act through said valve on said synchronizing device so as to compensate the differences between the elastic deformations of said lateral walls due to differences in load.
  • a machine as claimed in claim 2 comprising a lever having two arms and pivotally mounted on a pin integral with said frame, a crank lever having two branches and pivotally mounted on a pin integral with said frame, said two chambers of said correcting device being defined in two hydraulic jacks the first jack of which has a cylinder connected to a pin integral with said fixed frame and a piston connected to one of said arms of said lever, whereas the second of said hydraulic jacks has a cylinder connected to the other arm of said lever and a piston is connected to one of said branches of said cranked lever, the other of said branches being connected to said flexible element of said operating means.
  • said actuating element includes one of the branches of said cranked lever.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Control Of Presses (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Mounting, Exchange, And Manufacturing Of Dies (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Press Drives And Press Lines (AREA)
US747330A 1967-07-26 1968-07-24 Hydraulic machine for deforming sheet metal Expired - Lifetime US3550425A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR115702A FR1539817A (fr) 1967-07-26 1967-07-26 Machine hydraulique pour la déformation de métaux en feuilles
FR154510A FR95083E (fr) 1967-07-26 1968-06-11 Machine hydraulique pour la déformation de métaux en feuilles.

Publications (1)

Publication Number Publication Date
US3550425A true US3550425A (en) 1970-12-29

Family

ID=26178403

Family Applications (1)

Application Number Title Priority Date Filing Date
US747330A Expired - Lifetime US3550425A (en) 1967-07-26 1968-07-24 Hydraulic machine for deforming sheet metal

Country Status (14)

Country Link
US (1) US3550425A (xx)
AT (1) AT286747B (xx)
BE (1) BE717792A (xx)
CH (1) CH516355A (xx)
DK (1) DK137949B (xx)
ES (1) ES356803A1 (xx)
FR (2) FR1539817A (xx)
GB (1) GB1195448A (xx)
IE (1) IE32208B1 (xx)
IL (1) IL30366A (xx)
LU (1) LU56479A1 (xx)
NL (1) NL156963B (xx)
NO (1) NO128751B (xx)
SE (1) SE355512B (xx)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3668919A (en) * 1969-09-12 1972-06-13 Toshio Hongo Combination hydraulic shearing and pressbrake machine
US3702558A (en) * 1971-09-09 1972-11-14 Niagara Machine & Tool Works Deflection compensating press brake die support
US3914975A (en) * 1970-12-25 1975-10-28 Amada Co Ltd Hydraulic press brake
US4321819A (en) * 1980-07-23 1982-03-30 Dyneer Corporation Press construction
US4580434A (en) * 1983-11-14 1986-04-08 Cincinnati Incorporated Deflection compensating assembly for a press brake
US5067340A (en) * 1988-05-05 1991-11-26 Macgregor Donald C Precision press brake
US5193452A (en) * 1989-09-11 1993-03-16 Willem Dieperink Folding press with deflection compensating means
US5243902A (en) * 1989-12-19 1993-09-14 Amada Co. Hydraulic bending press with movable lower platen
US5426966A (en) * 1992-10-26 1995-06-27 M & S Brugg Ag Hydraulically operated press brake
US5653848A (en) * 1994-10-07 1997-08-05 Shikoku Kakoki Co. Ltd. Tape joining device

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2525391C3 (de) * 1975-06-06 1986-10-23 Peddinghaus, Rolf, Dipl.-Ing., 5828 Ennepetal Druckmittelbetätigte Schere, Lochstanze o.dgl. Maschine
PT68274A (en) * 1978-07-11 1978-08-01 A A Ribeiro De Almeida Device applicable to presses and metal bending presses to syncronize the movements of the hydraulic cylinders and control slider cross member
DE2919012A1 (de) * 1979-05-11 1980-11-20 Schloemann Siemag Ag Ueberlastsicherung an hydraulischen umformpressen, insbesondere blechformziehpressen
US4366699A (en) * 1980-05-26 1983-01-04 Amada Company, Limited Hydraulic presses
FR2507507B1 (fr) * 1981-06-16 1986-07-04 Promecan Sisson Lehmann Dispositif de bombage d'un porte-outil d'une presse plieuse ou analogue
CN112808845B (zh) * 2020-12-19 2022-06-24 爱驰威汽车零部件（盐城）有限公司 一种汽车壳体类零件的侧冲平衡装置

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3668919A (en) * 1969-09-12 1972-06-13 Toshio Hongo Combination hydraulic shearing and pressbrake machine
US3914975A (en) * 1970-12-25 1975-10-28 Amada Co Ltd Hydraulic press brake
US3702558A (en) * 1971-09-09 1972-11-14 Niagara Machine & Tool Works Deflection compensating press brake die support
US4321819A (en) * 1980-07-23 1982-03-30 Dyneer Corporation Press construction
US4580434A (en) * 1983-11-14 1986-04-08 Cincinnati Incorporated Deflection compensating assembly for a press brake
US5067340A (en) * 1988-05-05 1991-11-26 Macgregor Donald C Precision press brake
US5193452A (en) * 1989-09-11 1993-03-16 Willem Dieperink Folding press with deflection compensating means
US5243902A (en) * 1989-12-19 1993-09-14 Amada Co. Hydraulic bending press with movable lower platen
US5426966A (en) * 1992-10-26 1995-06-27 M & S Brugg Ag Hydraulically operated press brake
US5653848A (en) * 1994-10-07 1997-08-05 Shikoku Kakoki Co. Ltd. Tape joining device

Also Published As

Publication number Publication date
ES356803A1 (es) 1970-06-01
DK137949B (da) 1978-06-12
IL30366A (en) 1972-07-26
LU56479A1 (xx) 1968-10-24
IE32208L (en) 1969-01-26
GB1195448A (en) 1970-06-17
SE355512B (xx) 1973-04-30
BE717792A (xx) 1968-12-16
DE1752860B2 (de) 1975-07-17
IL30366A0 (en) 1968-09-26
IE32208B1 (en) 1973-05-16
FR1539817A (fr) 1968-09-20
FR95083E (fr) 1970-06-19
NO128751B (xx) 1974-01-07
DK137949C (xx) 1978-11-06
NL156963B (nl) 1978-06-15
DE1752860A1 (de) 1971-10-07
CH516355A (fr) 1971-12-15
AT286747B (de) 1970-12-28
NL6810532A (xx) 1969-01-28

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