US3877285A - Machine for treating workpieces at elevated pressures, especially a high-pressure press - Google Patents

Machine for treating workpieces at elevated pressures, especially a high-pressure press Download PDF

Info

Publication number
US3877285A
US3877285A US390173A US39017373A US3877285A US 3877285 A US3877285 A US 3877285A US 390173 A US390173 A US 390173A US 39017373 A US39017373 A US 39017373A US 3877285 A US3877285 A US 3877285A
Authority
US
United States
Prior art keywords
fly
wheel
cam
machine
treating
Prior art date
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
Application number
US390173A
Other languages
English (en)
Inventor
Sten Trolle
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.)
Carbox AB
Original Assignee
Carbox AB
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Carbox AB filed Critical Carbox AB
Application granted granted Critical
Publication of US3877285A publication Critical patent/US3877285A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/12—Drives for forging presses operated by hydraulic or liquid pressure
    • 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
    • B30B1/26—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 cams, eccentrics, or cranks
    • B30B1/261—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 cams, eccentrics, or cranks by cams
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B7/00—Presses characterised by a particular arrangement of the pressing members
    • B30B7/04—Presses characterised by a particular arrangement of the pressing members wherein pressing is effected in different directions simultaneously or in turn

Definitions

  • ABSTRACT A machine for treating workpieces at elevated pressures, especially a press, includes a large mass flywheel without spokes, crank-shaft or central bearing means. Instead, the fly-wheel is supported at its periphery only and the inner wall of its annular body has excenter or cam curves driving the plungers of control cylinders. These communicate with a working cylinder the piston of which actuates a movable tool. The flywheel surrounds the workpiece treating mechanism.
  • the present invention relates to such machines, particularly forging machines and presses but also bending machines, in which a metallic workpiece is subjected to one or more impacts by a tool for the purpose of causing a plastic deformation of the workpiece.
  • a tool for the purpose of causing a plastic deformation of the workpiece.
  • the tool is also called upon to operate at a high repetition rate.
  • the first one of the above two requirements stems from the necessity of on the one hand protecting the tool against a considerable temperature rise and, on the other, preventing such a great heat loss from the workpiece that its capacity to be subjected to the deformation in question is reduced to an unacceptable level.
  • the prevailing circumstances call for a great number of strokes during a short time period.
  • the result may be a destroyed workpiece.
  • the object of this invention is to provide a machine for the deformation of workpieces under the influence of extremely high forces, of the order of magnitude of 10 Meganewton. More particularly, the invention aims at providing a press featuring the combined advantages of the various prior art types but not suffering from their most outstanding disadvantages.
  • the machine according to the present invention comprises at least one stationary tool and one tool movable relatively thereto.
  • the machine comprises a power-driven, high mass flywheel without either spokes or crank-shaft. Instead, the internal wall of the annular fly-wheel is provided with excenters, cam curves or similar control means which drive the movable tool via force-multiplying means.
  • FIG. 1 is a part-sectional vertical view of a machine according to the illustrated embodiment.
  • FIG. 2 is a section taken along line IIII in FIG. 1.
  • the machine is intended by a pressing operation to deform a workpiece (not shown on the drawing) positioned between a stationary and a mobile tool.
  • the stationary tool can be constituted either by the bottom surface of yoke 5 or, which is generally the case, by a die or the like secured thereto.
  • the mobile tool does in this case comprises a press piston 8 cooperating with a hydraulic cylinder resting on the top of yoke 2.
  • the wall of the hydraulic cylinder consists of a heavy ring 9 secured to a thick bottom plate 10.
  • the cylinder chamber communicates via vertical bores 12 with four horizontally and radially extending cylinders 13, 14, 15 16.
  • These cylinders respectively house plungers 17-20 journalled for a reciprocatory motion therein.
  • the plungers are actuated upon by an annular fly-wheel 21 the inner wall of which has guide rails 22, 23 for four slide shoes 24-27, one for each of plungers 17-20.
  • the guide rails are circular but excentrically located relatively to each other and in relation to the rotational axis of fly-wheel 21.
  • FIG. 2 illustrates that the four control cylinders 13-16 are arranged pairwise, each pair comprising two diametrically opposed cylinders. It is also apparent from the drawing that the cylinders are symmetrically located in relation to a vertical central plane perpendicular to the plane of the drawing in FIGS. 1 and 2.
  • the plungers have been shown in their innermost extreme positions, i.e. the positions corresponding to a positive pressure acting on the hydraulic fluid in the press cylinder 11 for the purpose of raising piston 8. While all the four radial cylinders are active simultaneously and due to their symmetrical arrangement, which involves that two of the plungers engage the one guide rail and the remaining two the other guide rail, the result will be a self-contained system as far as the forces are concerned, i.e. actional as well as reactional forces are absorbed by the fly-wheel.
  • the mass of the fly-wheel is typically about 50-100 tons and that very large amount of material will exert two functions.
  • the first function is the classical role of a fly-wheel, the large mass and the corresponding large inertia provide a possibility to store very high dynamic energy levels.
  • the second function is that the material of the flywheel is relied upon also to absorb the just-mentioned forces. It is accordingly a characteristic of the fly-wheel that surrounds the press and that it has neither a central wheel disc nor spokes or a crank-shaft. The absence of a crank-shaft mounted in bearings eliminates the corre sponding disadvantages above discussed.
  • the fly-wheel is surrounded by a number of supporting rollers 28 and is vertically carried by heavy rollers or wheels 29. On top of the fly-wheel there is a gear ring 30 for cooperation with drive means including pinions or tooth-wheels.
  • Those components can be conventional and have not been shown on the drawing.
  • Reference numeral 31 indicates clutch pieces which are ovale in a horizontal plane and located between the slide shoes 24-27 and the piston 17-20. By means of a control mechanism (not shown) these clutch means can be brought into and out of their active positions in which latter case the cylinders 13-16 are disengaged also when the fly-wheel 21 rotates. This arrangement has two advantages.
  • the first one is that one can stop piston 8-for example in order to remove the workpiece and replace it by a fresh onewithout having to stop the fly-wheel.
  • the second advantage is that the hydraulic system can be disconnected from the mechanical system during two or more consecutive revolutions of the fly-wheel or, stated otherwise, impulses for driving the control plungers do not have to be derived during each revolution of the fly-wheel. In this way dynamic energy can be stored during two or more consecutive revolutions, thereby increasing the le'vel of the power instantaneously derived during a portion of the active revolution of the fly-wheel.
  • the changed ratio normally means a reduction, i.e. the sum of the active areas of plungers 17-20 should be substantially lower than the area of press piston 8.
  • fly-wheel In the practical application of the invention one may, of course, utilize several embodiments deviating from the one here described and shown for illustration purposes.
  • the main characteristic of the fly-wheel is its annular shape, the location thereof surrounding the press, the absence of any centrally located members, such as a shaft, cranks, spokes or a disk etc., and the presence of the internal guide rails resulting in a self-contained force-transmitting system.
  • the supporting or bearing means for the fly-wheel can be chosen freely.
  • One alternative solution of the bearing problem is to utilize air cushions.
  • control cylinders can vary from two and upwards. It is, however, preferred to locate the cylinders symmetrically and to have them uniformly spaced.
  • the force transmission to plungers 17-20 can be attained by the use of any suitable means and it should especially be emphasized necessarily have to be circular and excentric but may also consist of cam curves or the like.
  • clutch means 31 are preferably provided with a mechanism allowing disengagement.
  • the release movement can take place at right angles to the rotational plane of the fly-wheel but also in that plane in which latter case the clutch means are rotated around vertical shafts. lane of the fly-wheel but also in that plane Another way of providing engage ment and disengagement is to axially displace the flywheel.
  • the press cylinder 8, 9 can be shaped in other ways than illustrated in the drawings and one can use more than one press piston.
  • the machine can be used for pressing, forging, bending, powder-compaction and the like.
  • a machine for treating workpieces at elevated pressures comprising:
  • movable workpiece treating means mounted to a frame
  • said supporting means supporting said fly-wheel at a low level relative to said frame so that reactional forces generated each time the workpiece treating means is operated via said cam means are transmitted to said frame at or near its center of gravity, thereby reducing tilting effects on the frame during operation of the machine.
  • said movable workpiece treating means includes workpiece treating surfaces, and wherein said supporting means supports said fly-wheel at a level below the lowermost treating surfaces of said movable workpiece treating means.
  • a machine according to claim 1 wherein said movable workpiece treating means comprises a press.
  • said means operatively coupling said cam means with said movable workpiece treating means comprises at least one hydraulic cylinder having a plunger operatively coupled with said cam means, said cam means reciprocating said plunger for controlling movement of said movable work-piece treating means.
  • a machine as claimed in claim 5 comprising a slide shoe interconnected between said cam means and each plunger.
  • said means operatively coupling said cam means with said movable workpiece treating means comprises at least one hydraulic cylinder having a plunger operatively coupled with said cam means, said cam means reciprocating said plunger for controlling movement of said movable workpiece treating means.
  • a machine as claimed in claim 7 comprising a slide shoe interconnected between said cam means and each plunger.
  • a machine according to claim 7 comprising a plurality of said hydraulic cylinders arranged in pairs, each pair comprising two diametrically opposed cylinders.
  • said cam means includes at least two circular cam curves, each of which is eccentrically located in relation to the other cam curves and in relation to the rotational axis of the fly-wheel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
US390173A 1972-08-28 1973-08-20 Machine for treating workpieces at elevated pressures, especially a high-pressure press Expired - Lifetime US3877285A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE11124/72A SE366233B (fr) 1972-08-28 1972-08-28

Publications (1)

Publication Number Publication Date
US3877285A true US3877285A (en) 1975-04-15

Family

ID=20293399

Family Applications (1)

Application Number Title Priority Date Filing Date
US390173A Expired - Lifetime US3877285A (en) 1972-08-28 1973-08-20 Machine for treating workpieces at elevated pressures, especially a high-pressure press

Country Status (5)

Country Link
US (1) US3877285A (fr)
JP (1) JPS5041181A (fr)
DE (1) DE2343189A1 (fr)
FR (1) FR2197723A1 (fr)
SE (1) SE366233B (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1981000528A1 (fr) * 1979-08-27 1981-03-05 P Poulsen Procede et machine de formage de haute energie
US5243893A (en) * 1992-04-21 1993-09-14 Pitt-Des Moines, Inc. Mechanism for positioning a material working machine
US20040250714A1 (en) * 2001-07-04 2004-12-16 Lennart Svensson High-pressure press

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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3024676A (en) * 1958-11-28 1962-03-13 Sack Gmbh Maschf Hydraulic presses
US3508429A (en) * 1968-05-13 1970-04-28 Charles F Staples Frame for large press
US3589278A (en) * 1968-12-03 1971-06-29 Kieserling & Albrecht Percussion power press
US3724311A (en) * 1970-03-14 1973-04-03 F Streich Construction of mechanical presses

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3024676A (en) * 1958-11-28 1962-03-13 Sack Gmbh Maschf Hydraulic presses
US3508429A (en) * 1968-05-13 1970-04-28 Charles F Staples Frame for large press
US3589278A (en) * 1968-12-03 1971-06-29 Kieserling & Albrecht Percussion power press
US3724311A (en) * 1970-03-14 1973-04-03 F Streich Construction of mechanical presses

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1981000528A1 (fr) * 1979-08-27 1981-03-05 P Poulsen Procede et machine de formage de haute energie
US5243893A (en) * 1992-04-21 1993-09-14 Pitt-Des Moines, Inc. Mechanism for positioning a material working machine
US20040250714A1 (en) * 2001-07-04 2004-12-16 Lennart Svensson High-pressure press
US7310990B2 (en) * 2001-07-04 2007-12-25 Avure Technologies Ab High-pressure press
US7650771B2 (en) 2001-07-04 2010-01-26 Avure Technologies Ab High-pressure press

Also Published As

Publication number Publication date
SE366233B (fr) 1974-04-22
DE2343189A1 (de) 1974-03-14
JPS5041181A (fr) 1975-04-15
FR2197723A1 (fr) 1974-03-29

Similar Documents

Publication Publication Date Title
US3635074A (en) Compensating system for presses
US3507143A (en) Forming machine
US7165437B2 (en) Mechanical press device
CN103459134A (zh) 用于压制工件的压力机和方法
US3108503A (en) High energy rate forming machine
US4291571A (en) Forging press
US3877285A (en) Machine for treating workpieces at elevated pressures, especially a high-pressure press
GB2301546A (en) Bodymaker tool pack
EP1252943A1 (fr) Presse radiale pour la fixation des embouts
US3589278A (en) Percussion power press
US3422658A (en) High velocity forming machine
JP3251135B2 (ja) 順送り加工装置
US3991681A (en) Disc type press with hydrostatic bearings
US3916700A (en) Machine for treating workpieces at elevated pressures, especially a high-pressure press
US3783672A (en) High-speed machines for shaping metals which employ the energy of high-pressure gas
CN1141845A (zh) 压力机
US3296853A (en) Fluid-operated press
JP2540450B2 (ja) Ｃ形フレ―ム構造のプレス装置
US2236154A (en) Press combination having means for avoiding jamming
JPH0349653B2 (fr)
JPS6220527Y2 (fr)
DE4042189C2 (de) Steuerung des energetischen und dynamischen Verhaltens von Antrieben in Umformmaschinen
RU2080996C1 (ru) Гидравлический ковочный пресс
US4064733A (en) Press
RU2204455C2 (ru) Пресс для штамповки обкатыванием