US3707866A - Machines for forming a workpiece between two ram heads - Google Patents

Machines for forming a workpiece between two ram heads Download PDF

Info

Publication number
US3707866A
US3707866A US00118528A US3707866DA US3707866A US 3707866 A US3707866 A US 3707866A US 00118528 A US00118528 A US 00118528A US 3707866D A US3707866D A US 3707866DA US 3707866 A US3707866 A US 3707866A
Authority
US
United States
Prior art keywords
cylinder space
ram
ram head
press
valve
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
US00118528A
Other languages
English (en)
Inventor
W Brauer
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.)
Langenstein and Schemann GmbH
Original Assignee
Langenstein and Schemann GmbH
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 Langenstein and Schemann GmbH filed Critical Langenstein and Schemann GmbH
Application granted granted Critical
Publication of US3707866A publication Critical patent/US3707866A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • B21J9/18—Drives for forging presses operated by making use of gearing mechanisms, e.g. levers, spindles, crankshafts, eccentrics, toggle-levers, rack bars
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J11/00—Forging hammers combined with forging presses; Forging machines with provision for hammering and pressing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/22—Drives for hammers; Transmission means therefor for power hammers
    • B21J7/24—Drives for hammers; Transmission means therefor for power hammers operated by steam, air, or other gaseous pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/22—Drives for hammers; Transmission means therefor for power hammers
    • B21J7/34—Drives for hammers; Transmission means therefor for power hammers operating both the hammer and the anvil, so-called counter-tup
    • 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
    • B21J9/16—Drives for forging presses operated by hydraulic or liquid pressure in conjunction with steam or gas power
    • 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
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06M—TREATMENT, NOT PROVIDED FOR ELSEWHERE IN CLASS D06, OF FIBRES, THREADS, YARNS, FABRICS, FEATHERS OR FIBROUS GOODS MADE FROM SUCH MATERIALS
    • D06M23/00—Treatment of fibres, threads, yarns, fabrics or fibrous goods made from such materials, characterised by the process
    • D06M23/04—Processes in which the treating agent is applied in the form of a foam

Definitions

  • ABSTRACT Improved hydraulic forming and forging presses for g combined operation, in which there are valving facili ties and piston and cylinder arrangements enabling [58] Field of Search 100/269 R various combinations of relative movement and rates of movement of the rams to be adjusted, in ac- [56] References cued cordance with the kind of metal-forming operations UNITED STATES PATENTS which are to be effected.
  • a workpiece When forming a workpiece between two ram heads, the two heads press against the workpiece.
  • One method is forging and the other is press-forming.
  • a ram head or hammer transfers impact energy to the workpiece and the degree of deformation of the workpiece is dependent upon the amount of impact energy involved.
  • the deformation or shaping in this kind of operation is carried out in a relatively short time.
  • press-forming a ram exerts a pressure on the workpiece and the degree of deformation or shaping thereof as a consequence of the ram travel, is dependent upon the press force exerted.
  • the deformation of the workpiece is thus a factor which can be influenced not simply by whether or not a press-forming or a forging operation is used, but also by the application of varying degrees of press-forming force or varying degrees of impact energy.
  • Each of these possible controls on the operation of forming is a factor which may be included in a machine for forming a workpiece between two ram heads.
  • Amachine of this kind which will be referred to in the following as a forming machine, and which has many possible applications, is particularly useful in situations where none of the forming facilities is used frequently and many different forming facilities are required.
  • One quite generally known forming machine is what will be referred to subsequently as a single press.
  • one of the two rams is fixed and the other movable in relation to the workpiece, for the purpose of pressing the latter.
  • the maximum press load in a single press is unlimited as far as practical requirements are concerned.
  • the disadvantage of this kind of press is that it is not very versatile in application since it cannot perform any forging-type operations.
  • the present invention has as its object a machine of the kind referred to above, which is characterized in that provision is made for a mutual opposing movement of each of the rams in extension and retraction directions as well as for engagement of pistons delimiting the return cylinder space and an impact cylinder space, with the rams, at least one of the two rams additionally being associated with a press cylinder space delimited by a piston engaging said ram and associated with supply facilities for the introduction of pressurized fluid.
  • one cylinder space to which a pressurized medium is supplied which produces a hammer blow, is designated the impact cylinder space.
  • the press cylinder space is supplied with the pressurized medium which produces a pressure stroke of the ram
  • the return cylinder space is supplied with the pressurized fluid which causes the rams to retract.
  • the object of the present invention is a forming machine which not only is more versatile in application than the known forming machines, but which enables the additional applications to be achieved in an economical way.
  • the forming machine in accordance with the invention is a twin hammer press which can be operated arbitrarily as a twin hammer (forging) machine and as a press. It is designed to produce either a high impact energy or a high press force, and the essentials of its design for high press force can also be exploited in a forging context.
  • the two rams are moved in opposition to one another in forging operations, but not in pressing operations.
  • An embodiment of this kind operating as a single press, is obtained when the hammer blow cylinder space is provided in association with one of the rams and the piston delimiting this space arranged to engage with the other ram.
  • the piston delimiting the press cylinder space to which pressurized fluid is'supplied engages with the ram associated with the hammer blow cylinder space.
  • a piston delimiting the return cylinder space is supplied with pressurized fluid medium and likewise engages the ram associated with the hammer blow cylinder space. Pressing is carried out against the force of the pressurized medium in the return cylinder space.
  • a machine in accordance with the invention is preferably equipped with a control facility in which the return cylinder space is connected with an extension valve device.
  • the extension valve device will include an impact valve and a travel valve for slowly moving the two rams towards each other.
  • the supply to the return cylinder space will be via a check valve and that to the press cylinder space via a press valve.
  • the impact valve has a large flow cross-section and is designed, for example, in the manner disclosed in German specification No. 974,854 in relation to a drop-hammer.
  • the travel valve will have a variable, small flow cross-section and serves to slowly move the two rams together, and is open during pressing operations.
  • the extension movement of the rams displaces fluid out of one of the return cylinder spaces through the open impact valve and the open travel valve.
  • the extension valve device In order to return the rams, the extension valve device is closed, the press valve closed and the return valve opened.
  • the opening of the latter valve causes pressurized fluid to be supplied to one of the return cylinder spaces.
  • the travel valve is opened, the press valve opened and the return valve shut.
  • pressurized fluid is fed into the press cylinder space and fluid escapes from the return cylinder space through the open travel valve.
  • the impact valve For hammer blow movement of the ram, the impact valve is opened and the return valve closed. Fluid leaves the return cylinder space through the open impact valve.
  • facility for supplying pressurized fluid or gas to the impact cylinder space.
  • a preferred embodiment is one in which with the rams retracted, a closed-off pressure chamber surrounding the impact cylinder space is filled with compressed, high-pressure gas.
  • impact is produced not by the supply of pressurized fluid or gas to an impact cylinder space, but by the pressure of the gas compressed (preferably by the return motion of the rams) in the closed-off pressure or compression chamber.
  • the rams are moved in opposition during press-forming operations as well, so that a means used only during press-forming operations in order to hold one ram stationary, is no longer needed and the installed height of the machine is reduced as a consequence.
  • a means used only during press-forming operations in order to hold one ram stationary is no longer needed and the installed height of the machine is reduced as a consequence.
  • This preferred embodiment may conveniently be further developed to the point where there is a positive hydraulic coupling between the two rams.
  • the two rams can be made to move synchronously in opposition to one another not only during retraction, but also in forging operations and when executing a press stroke.
  • FIG. 1 illustrates a section through a machine according to the invention operating as a single press
  • FIG. 2 illustrates a section through a machine according to the invention operating as a twin press.
  • the two machines illustrated operate in a vertical position and in each case incorporate two rams 1, 2 arranged in line one above the other.
  • the two rams l, 2 are movable in relation to one another, in a frame 3.
  • the bottom ram 2 is preferably several times heavier than the upper ram 1 and accordingly travels a shorter distance than said upper ram. This is a convenient feature especially in the embodiment of FIG. 1, in which the bottom ram 2 is stationary during press-forming operations.
  • Above the upper ram 1 there is an upper press cylinder space 4a defined by cylinder walls 5 rigidly fixed to the frame 3.
  • the press cylinder space 4a is defined by a vertically reciprocating piston 6a, which, in executing upward and downward movements, reduces or increases the volume of the press cylinder space, with the piston bearing against the upper ram 1 when moved downwards.
  • a return cylinder space 7 is provided which is likewise defined by the cylinder walls 5 rigidly attached to the frame 3.
  • a piston 8 defining the return cylinder space 7, enlarges the volume of this space with any upward movement and reduces it with any downward movement.
  • the piston 8 is rigidly attached to the ram 1.
  • a hammer blow cylinder space 9 which in the example of FIG.
  • piston 8 rigidly fixed to the upper ram 1, and the movement of which piston 8 can be coupled, through the medium of a hydraulic link 10, with a piston 11 rigidly fixed to the bottom ram 2.
  • the piston 11 can move upwards and downwards and in so doing changes the volume of an additional, lower return cylinder space 12.
  • the hammer blow cylinder space 9 is located above the ram 1, and the gas, e.g., nitrogen, which it contains applies its pressure to the piston 8 rigidly attached to ram I. Said piston 8 is acted upon on its underside by a pressurized fluid medium, e.g., oil, located in the return cylinder space 7 above the ram 1.
  • a pressurized fluid medium e.g., oil
  • An upper stern 20a which projects into the hammer blow cylinder space 9, tenninates at its free end on top of the piston 8 fixed to the ram 1 and is rigidly attached at its other end to the piston 6a defining the press cylinder space 4a above the ram 1.
  • the return cylinder space 7 above the ram 1 connected via a transfer line 31 belonging to the link 10, to a coupling cylinder space 21 in which a plunger or piston, rigidly connected with the bottom ram 2, can slide.
  • This plunger or piston in the embodiment of FIG. 1, is identical with the piston 11 rigidly fixed to the bottom ram 2 and defining the bottom return cylinder space 12.
  • the hammer blow cylinder space 9 is-rigidly fixed to the frame 3 and the means 10 linking the rams l, 2, is a positive one.
  • An extension valve device is provided, which includes an impact valve 18 and a travel valve 19.
  • the travel valve 19 and the impact valve 18 are, in each case, connected with cylinder spaces which are delimited by the pistons 8, 11 rigidly fixed to the two rams l, 2 and are in fact return cylinder spaces 7, 12. Both the impact valve 18 and the travel valve 19 are connected to one of the two return cylinder spaces 7, 12.
  • the press valve 15 In order to retractthe two rarns l, 2, the press valve 15 is closed so that no pressurized fluid can pass into the press cylinder space 4a.
  • the valve 17, on the other hand, is open and the pump 14 supplies pressurized fluid to the return cylinder space 12 associated with the bottom ram 2 and retracts this ram downwards.
  • the piston 11 rigidly fixed to the bottom ram 2, in so doing displaces fluid via the coupling cylinder space 21 and the link 10, into the return cylinder space 7 associated with the upper ram.
  • the piston 8 rigidly attached to the ram 2, retracts upwards and in so doing compresses the gas in the hammer blow cylinder space 9.
  • the impact valve 18 is opened, with this valve having a large flow area.
  • the gas compressed in the hammer blow cylinder space or compression chamber 9 forces the piston 8 rigidly attached to the upper ram 1, downwards, and, via the link 10, forces the piston 11 rigidly attached to the bottom ram 2, upwards, fluid being displaced through the impact valve 18 from the corresponding return cylinder space 12.
  • additional fluid is continuously supplied to the return cylinder space 12 and the gas holds the (twice) piston 6a, which delimits the top press cylinder space 411, in its topmost position against the stem a, by pressure.
  • the press valve 15 and the travel valve 19 are operated, with the press valve 15 being open so that pressurized fluid has access via the line 13 to the press cylinder space.
  • the travel valve 19 is opened as well so that liquids can discharge from the return cylinder space 12.
  • the pressurized fluid entering the press cylinder space 40 forces the piston 6a delimiting this space, downwards and likewise, via the stem 20a, the piston 8 rigidly fixed to the upper ram 1 and hence the ram 1 itself.
  • the gas in the hammer blow cylinder space 9 is at the pressure required for a hammer blow stroke. During the hammer blow, it is subject only to the pressure fluctuations which stem from change in volume.
  • the travel valve 19 is arranged in the link 10 and during a pressforming stroke fluid flows from the return cylinder space 7 associated with the ram 1, to the travel valve.
  • the bottom ram 2 does not move during a press-forming operation but rests upon a fluid cushion in the coupling cylinder space 21 which is shut off by a cock 22. Accordingly,'the press cylinder space 40 is provided only in respect of the upper ram 1.
  • a press cylinder space 4b is provided in respect of the bottom ram 2 as well, with this space 4b being located centrally below the bottom ram 2.
  • a piston 6b delimiting the bottom press cylinder space 4b acts via a bottom stem 20b on the piston 11 which is rigidly fixed to thebottom ram 2.
  • the pressurized areas of the two pistons 6a, 6b delimiting the two press cylinder spaces 4a, 4b, are identical.
  • the piston and cylinder spaces 6b, 4b are larger in the ratio of the masses involved, in order to achieve complete compensation.
  • the bottom coupling pistons 21 are made larger than the annular areas 7 of the upper piston.
  • the travel valve 19 is connected to the return cylinder space 12 which is supplied with pressurized fluid from the main pump 14.
  • both rams l, 2 have the same weight whereas in the machine of FIG. 1, the bottom ram 2 is heavier than the upper ram 1.
  • the machines in the drawing also include a cylinder 23a of compressed gas, from which, through a pressure-reducing valve 23b and a stop-cock 23c, and also via a gas manometer 23d and a pressure-relief valve '23e, gas can be introduced into the hammer blow cylinder space 9 in a controlled fashion.
  • a transfer pump 24a pumps pressurized fluid into the coupling line 10 and the return cylinder space 7 of the ram 1, via a check valve 24b and via a controlling transfer valve 24c.
  • two additional pressure-relief valves 25c, 25c" are so arranged in the line 16 to the retraction cylinder space 12, that they are disposed between the travel valve 19 and the retraction cylinder space 12.
  • the main pump 14, the transfer pump 24a and a control pump 26a pump fluid from a reservoir 27, to which it ultimately returns from the press cylinder spaces 4 or the retraction cylinder speces 12.
  • the control pump 26a delivers across a check valve 26b and its delivery is controlled by a hydraulic accumulator 260 with a pressure switch and bleed valve. It feeds a selec-' tion stage control system 28 for the press valve 15 and the retraction valve 17, and also serves a hammer blow safety valve 29 and a hammer blow tripping valve 30.
  • the safety valve 29 provides the system with an excesspressure blow-off facility, and the valve 30 operates the hammer blow valve 18.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Forging (AREA)
US00118528A 1967-10-09 1971-02-24 Machines for forming a workpiece between two ram heads Expired - Lifetime US3707866A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT913467A AT271143B (de) 1967-10-09 1967-10-09 Maschine zur Unformung eines Werkstückes zwischen zwei Bären

Publications (1)

Publication Number Publication Date
US3707866A true US3707866A (en) 1973-01-02

Family

ID=3611483

Family Applications (1)

Application Number Title Priority Date Filing Date
US00118528A Expired - Lifetime US3707866A (en) 1967-10-09 1971-02-24 Machines for forming a workpiece between two ram heads

Country Status (4)

Country Link
US (1) US3707866A (de)
AT (1) AT271143B (de)
DE (1) DE1777033C3 (de)
GB (1) GB1230218A (de)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3822579A (en) * 1972-10-24 1974-07-09 V Kononenko High-speed counterstroke hammer
US3847008A (en) * 1972-05-02 1974-11-12 Schloemann Ag Hydraulic forging press
US3979174A (en) * 1975-10-24 1976-09-07 Corning Glass Works Article trimming apparatus
FR2338133A1 (fr) * 1976-01-13 1977-08-12 Knaebel Horst Dispositif utilisable pour produire brusquement une charge sur un corps destine a etre usine, transforme ou charge
US4142397A (en) * 1976-10-14 1979-03-06 "Wefoba" Werkzeug-und Formenbau Gesellschaft m.b.H. Co. KG Counterblowing machine hammer
US5038598A (en) * 1990-09-07 1991-08-13 Gene Pitzer Method and apparatus for performing secondary operations in a press
EP0447839A1 (de) * 1990-03-19 1991-09-25 DANIELI & C. OFFICINE MECCANICHE S.p.A. Schmiedeverfahren und Schmiedemaschine zur Durchführung des Verfahrens
US5092151A (en) * 1988-12-29 1992-03-03 Amada Company, Limited Sheet workpiece bending machine
US5199293A (en) * 1988-12-29 1993-04-06 Amada Company, Limited Sheet workpiece bending machine
US6212929B1 (en) * 1997-08-16 2001-04-10 Fritz Binhack Device and method for forming, in particular cold-forming, workpieces
US20020090880A1 (en) * 2000-09-07 2002-07-11 Lee James S.W. Jointed support system and method of constructing same
US20090188292A1 (en) * 2006-08-07 2009-07-30 Felss Gmbh Device and method for forming a workpiece
US20100040485A1 (en) * 2008-08-12 2010-02-18 Gm Global Technology Operations, Inc. High Pressure Dual-Action Hydraulic Pump
CN101462147B (zh) * 2009-01-12 2011-04-13 张国庆 高速气动锻锤装置
CN102688971A (zh) * 2012-06-08 2012-09-26 镇江市锻压机床厂 双缸液压锤
CN102794379A (zh) * 2012-07-16 2012-11-28 胡大勇 全液压对击锤
US20150013423A1 (en) * 2013-07-12 2015-01-15 The Boeing Company Apparatus and Method for Momentum-balanced Forging

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108097857B (zh) * 2018-01-25 2024-05-28 温岭立骅机械有限公司 压力机
RU2764620C2 (ru) * 2018-07-10 2022-01-18 Общество С Ограниченной Ответственностью "Бетарут" Способ и устройство жидкой ковки двойного действия
CN110918853B (zh) * 2019-12-07 2021-09-03 南京宏擎精密材料科技有限公司 一种节能模锻液压机及其使用方法

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US352314A (en) * 1886-11-09 Forging plant
US962705A (en) * 1909-08-18 1910-06-28 John Fielding Machine for forging metals.
US2409254A (en) * 1944-06-02 1946-10-15 Solar Aircraft Co Apparatus for die-forming sheet material
US3105414A (en) * 1961-12-26 1963-10-01 Gen Dynamics Corp High energy impactor apparatus
US3173286A (en) * 1961-01-19 1965-03-16 Hasenclever Ag Maschf Method of operating a pressure fluidoperated press as a hammer and pressure fluid-operated press serving for carrying out the method
US3180129A (en) * 1961-10-19 1965-04-27 Eumuco Ag Fur Maschb Top-pressure forging hammer
US3209578A (en) * 1960-02-11 1965-10-05 Hydraulik G M B H Fa Apparatus for forging ingots into a base material
US3336788A (en) * 1964-04-01 1967-08-22 Us Industries Inc High energy impact machines
US3353396A (en) * 1962-10-31 1967-11-21 Langenstein & Schemann Ag Swaging hammers
US3429174A (en) * 1965-02-10 1969-02-25 Langestein & Schemann Ag Presses

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US352314A (en) * 1886-11-09 Forging plant
US962705A (en) * 1909-08-18 1910-06-28 John Fielding Machine for forging metals.
US2409254A (en) * 1944-06-02 1946-10-15 Solar Aircraft Co Apparatus for die-forming sheet material
US3209578A (en) * 1960-02-11 1965-10-05 Hydraulik G M B H Fa Apparatus for forging ingots into a base material
US3173286A (en) * 1961-01-19 1965-03-16 Hasenclever Ag Maschf Method of operating a pressure fluidoperated press as a hammer and pressure fluid-operated press serving for carrying out the method
US3180129A (en) * 1961-10-19 1965-04-27 Eumuco Ag Fur Maschb Top-pressure forging hammer
US3105414A (en) * 1961-12-26 1963-10-01 Gen Dynamics Corp High energy impactor apparatus
US3353396A (en) * 1962-10-31 1967-11-21 Langenstein & Schemann Ag Swaging hammers
US3336788A (en) * 1964-04-01 1967-08-22 Us Industries Inc High energy impact machines
US3429174A (en) * 1965-02-10 1969-02-25 Langestein & Schemann Ag Presses

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3847008A (en) * 1972-05-02 1974-11-12 Schloemann Ag Hydraulic forging press
US3822579A (en) * 1972-10-24 1974-07-09 V Kononenko High-speed counterstroke hammer
US3979174A (en) * 1975-10-24 1976-09-07 Corning Glass Works Article trimming apparatus
FR2338133A1 (fr) * 1976-01-13 1977-08-12 Knaebel Horst Dispositif utilisable pour produire brusquement une charge sur un corps destine a etre usine, transforme ou charge
US4048840A (en) * 1976-01-13 1977-09-20 Korst Knabel Apparatus for producing an instantaneous pressure on a workpiece
US4142397A (en) * 1976-10-14 1979-03-06 "Wefoba" Werkzeug-und Formenbau Gesellschaft m.b.H. Co. KG Counterblowing machine hammer
US5092151A (en) * 1988-12-29 1992-03-03 Amada Company, Limited Sheet workpiece bending machine
US5199293A (en) * 1988-12-29 1993-04-06 Amada Company, Limited Sheet workpiece bending machine
EP0447839A1 (de) * 1990-03-19 1991-09-25 DANIELI & C. OFFICINE MECCANICHE S.p.A. Schmiedeverfahren und Schmiedemaschine zur Durchführung des Verfahrens
US5038598A (en) * 1990-09-07 1991-08-13 Gene Pitzer Method and apparatus for performing secondary operations in a press
US6212929B1 (en) * 1997-08-16 2001-04-10 Fritz Binhack Device and method for forming, in particular cold-forming, workpieces
US20020090880A1 (en) * 2000-09-07 2002-07-11 Lee James S.W. Jointed support system and method of constructing same
US6681472B2 (en) * 2000-09-07 2004-01-27 C.J. Associates, Ltd. Method of assembling jointed support system
US20090188292A1 (en) * 2006-08-07 2009-07-30 Felss Gmbh Device and method for forming a workpiece
US8091400B2 (en) * 2006-08-07 2012-01-10 Felss Gmbh Device and method for forming a workpiece
US20100040485A1 (en) * 2008-08-12 2010-02-18 Gm Global Technology Operations, Inc. High Pressure Dual-Action Hydraulic Pump
US8061179B2 (en) * 2008-08-12 2011-11-22 GM Global Technology Operations LLC High pressure dual-action hydraulic pump
CN101462147B (zh) * 2009-01-12 2011-04-13 张国庆 高速气动锻锤装置
CN102688971A (zh) * 2012-06-08 2012-09-26 镇江市锻压机床厂 双缸液压锤
CN102794379A (zh) * 2012-07-16 2012-11-28 胡大勇 全液压对击锤
US20150013423A1 (en) * 2013-07-12 2015-01-15 The Boeing Company Apparatus and Method for Momentum-balanced Forging
US9573185B2 (en) * 2013-07-12 2017-02-21 The Boeing Company Apparatus and method for momentum-balanced forging

Also Published As

Publication number Publication date
AT271143B (de) 1969-05-27
DE1777033A1 (de) 1970-12-17
GB1230218A (de) 1971-04-28
DE1777033C3 (de) 1974-01-24
DE1777033B2 (de) 1973-06-28

Similar Documents

Publication Publication Date Title
US3707866A (en) Machines for forming a workpiece between two ram heads
US3470725A (en) Hydraulic spindle press for drawing metal
US3158048A (en) Impact machine
US3352143A (en) Impact apparatus
RU2382241C2 (ru) Блок поршень-цилиндр и гидравлический пресс
US3412554A (en) Device for building up high pulse liquid pressures
US3766830A (en) Percussion apparatus
US3518869A (en) Hydraulic press,more particularly for treating metals by shaping
US4291571A (en) Forging press
US3456478A (en) Hydraulic locking cylinders
US3464315A (en) Mechanical pneumatic servo control system for high-speed impact devices
US4370878A (en) Workpiece ejector system for presses
US3596499A (en) Machine for pressure forming and impact forming workpieces
US3898834A (en) High energy forging press
US3271991A (en) High energy impact machine
US3103136A (en) High energy impact machine
US2438951A (en) Hydraulic overload-release device or cushion for presses
US3173286A (en) Method of operating a pressure fluidoperated press as a hammer and pressure fluid-operated press serving for carrying out the method
EP0080964A2 (de) Steuereinrichtung für hydraulisches Schlagwerkzeug
US4212185A (en) Hydraulic press system
US897048A (en) Drawback mechanism for presses.
US4206628A (en) Press with hydraulic load transferring mechanism
US3296853A (en) Fluid-operated press
US4191045A (en) Power hammer with opposed movement of ram and bolster
US3525220A (en) Hammer with hydraulic coupling