US3890413A - Apparatus and method for compacting particulate materials - Google Patents

Apparatus and method for compacting particulate materials Download PDF

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Publication number
US3890413A
US3890413A US497573A US49757374A US3890413A US 3890413 A US3890413 A US 3890413A US 497573 A US497573 A US 497573A US 49757374 A US49757374 A US 49757374A US 3890413 A US3890413 A US 3890413A
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punches
head
powder
die
cylinders
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Expired - Lifetime
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US497573A
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English (en)
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William M Peterson
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Hydramet American Inc
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Hydramet American Inc
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Priority to US497573A priority Critical patent/US3890413A/en
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Priority to CA232,661A priority patent/CA1056573A/fr
Priority to JP50097241A priority patent/JPS5145681A/ja
Anticipated expiration legal-status Critical
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B11/00—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses
    • B30B11/02—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses using a ram exerting pressure on the material in a moulding space
    • B30B11/04—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses using a ram exerting pressure on the material in a moulding space co-operating with a fixed mould
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/06—Platens or press rams
    • B30B15/065—Press rams
    • B30B15/067—Press rams with means for equalizing the pressure exerted by a plurality of press rams
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0005—Details of, or accessories for, presses; Auxiliary measures in connection with pressing for briquetting presses
    • B30B15/0017—Deairing means

Definitions

  • Some powders have peculiar characteristics which compound the difficulties in obtaining an acceptable product. Notable among these is uranium-dioxide powder which is compacted to cylindrical pellets for use as fuel in nuclear reactors. This material has unusually poor flowability and frequently has an unusual amount of entrapped air. It is made in relatively small batches which vary in physical characteristics from one to another. The material is extremely expensive so that any appreciable percentage of defective pellets is unacceptable. Finally, these pellets are made in vast numbers and at very high production rates.
  • Uranium-dioxide is selected for illustration of the invention because it involves not only problems common to the compacting powders in general, but additional problems as well.
  • the object of the present invention is to provide a relatively simple, inexpensive press structure which is improved to overcome the problems arising from the above-discussed factors.
  • FIGS. 1 through 6 are diagrammatic sectional views illustrating successive steps in a cycle of operation of a press embodying the present invention
  • FIG. 7 is an enlarged scale diagrammatic sectional view illustrating a compensator and accumulator feature of the invention.
  • a conventional hydraulic press 10 of the opposed ram type on which is mounted a stationary die plate 12 which defines a plurality of die cavities 14, each having an open upper end 16. Each die cavity has a bottom wall 18 which is formed by the upper surface of a punch 20.
  • Punches 29 are mounted on a lower platen 22 which is driven by a powered ram 24 for moving punches vertically in die cavities 14. The speed of the ram and the pressure exerted by the ram at various portions of the compacting cycle are regulated by conventional hydraulic controls on the control circuit of the press.
  • Press 10 has a head 26 which is supported on an upper platen above die plate 12 by a ram 28 which is power driven in a manner similar to ram 24 to move the head downwardly in closing movement relative to plate 12 and upwardly in reacting movement relative thereto.
  • the control circuit of the press is adapted to adjustably regulate the speed of and force on each ram independently by such means as pressure and flow control valves.
  • Head 26 carries a plurality of compacting punches 30 each aligned with a die cavity 14. Each punch 30 passes slidably through an opening 32 in head 26 and terminates at its upper end in an enlarged head 34 forming a piston in a hydraulic cylinder 36 in the head. In the upward retracted position of head 26 (FIGS. 1 and 6) each piston 34 is supported by the bottom end wall 38 of its respective cylinder 36.
  • Cylinders 36 communicate with each other hydraulically through ports 40 and a passageway 42 in head 26.
  • a body 44 which defines an internal hydraulic accumulator cylinder 46 having a piston 48 therein.
  • Cylinder 46 has an end wall 50 and an opposite end wall 52, a central portion of which is reparked to receive a compressed spring 54 and to provide a seat 56 therefor.
  • Spring 54 engages piston 48 and urges the piston toward end wall 50.
  • Passageway 42 communicates hydraulically with cylinder 46 through a conduit 58 and a port 60 in body 44.
  • cylinders 36 are in hydraulic communication with cylinder 46 as well as with each other.
  • a valve 62 is hydraulically connected with cylinder 46 at the side of piston 48, opposite from port 60 by means of a port 64 connected with valve 62 by conduits 66, 68.
  • Valve 62 has an inlet connected with a source of hydraulic fluid under relatively low pressure (not shown) and has an outlet 72 connected to a drain 74.
  • Valve 62 is actuated by a solenoid 76 for interconnecting conduit 68 and inlet 70 and is returnable by a spring 78 to disconnect conduit 68 from inlet 70 and connect it with outlet 72.
  • Conduits 58, 68 are intercon nected through a check valve 80 which permits a flow of fluid from conduit 68 into conduit 58 but prevents the flow of fluid in the opposite direction.
  • Passageway 42 is hydraulically connecteed with a pressure gauge 82 and a pressure relief valve 84 through conduits 86, 88.
  • valves 80, 84 are closed, a closed fluid circuit is established between cylinders 36 and accumulator cylinder 46, the pressure being the same throughout the circuit.
  • head 26 comprises body to which a retainer plate 92 is secured by such means as bolting (not shown).
  • O-rings 94 are interposed between the body and retainer plate.
  • Body 90 defines cylinders 36, ports 40 and passageway 42.
  • Body 90 forms part of a platen 96 to which ram 28 is secured.
  • Retainer plate 92 defines the openings through which enlarged portions 98 of punches 30 slidably extend. 0- rings 100 are interposed between enlargements 98 and openings 32. Plate 92 forms the bottom walls 38 of cylinders 36 and is also bored to form a system of passageways 102, 104, 106, 108 which communicate with the lower ends of cylinders 36 and with an outlet H0 into a drain 112. Each piston 34 is provided with a high pressure seal 114 secured thereto as by a retaining washer I16 and a screw 118. Seals I14 slidably engage the walls of cylinders 36.
  • Accumulator body 44 may be mounted on platen 96 or may be machined as part of head 26 and/or platen 96.
  • Accumulator piston 48 has a high pressure seal 120 secured thereto by a retaining washer I22 and a screw I24.
  • Accumulator body 44 comprises two sections 126, 128 secured together by such means as bolting (not shown). Section 126 defines cylinder 46, end walls 50 and 52 thereof and port 60. Section 128 forms the recess for spring 54, spring seat 56 and port 64. An ring 130 is provided between sections 126, 128.
  • a rod 132 is threaded to piston 48 at 134. This rod extends through the interior of spring 54, projects slid ably through an opening 136 in body section 128 and has an end portion 138 disposed outside of the accumulator body. An O-ring 140 is provided between the rod 132 and body section 128.
  • Valve 62 has a body 142 forming an internal cylinder 144 within which a spool 146 is slidable.
  • Spool 146 has an annular groove I48 which interconnects conduit 68 with outlet 72 in one position and interconnects conduit 68 with inlet 70 in another position.
  • outlet 72 is connected with conduit 68, inlet 70 is cut off from communication therewith and vice versa.
  • the valve spool is moved in one direction by plunger 150 of solenoid 76 and is returned in the other direction by spring 78.
  • Pressure relief valve 84 has a body 152 which defines an internal cylinder 154 having a side port 156 connected with conduit 88 and a shunt passageway 158 which opens into an end 160 of the cylinder.
  • the cylinder has a side outlet port 162 aligned with port 156.
  • a piston 164 in the cylinder is urged against cylinder end 160 by a spring I66 to close shunt passageway 158. In this position piston 164 isolates port 156 from port I62 to contain fluid under pressure in the system comprised of cylinders 36, 46 and the various interconnecting ports and passageways.
  • the stress of spring 166 is adjustable to maintain piston 164 in this position until hydraulic pressure in such system exceeds a predetermined selected pressure, whereupon that pressure forces piston 164 to the left as FIG. 7 is viewed to align a port 168 therein with ports 156, 162 which permits fluid to pass out of the system through outlet 162 into drain 170 until the pressure lowers again to the predetermined maximum. At that time spring 166 returns piston 164 to the right, removing port 168 from registry between ports 156 and 162 to again close the system.
  • the maximum pressures to which rams 24, 28 are subjected are controlled by relief valves in the press control circuit.
  • Relief valve 84 is provided as a precaution in the event of a malfunction of the press controls. Valve 84 is set to open at a pressure slightly in excess of the relief valves in the press circuit.
  • FIG. 1 In use, at the beginning of a cycle of operation press is in the condition illustrated in FIG. 1. Lower punches are in a downward position so that their upper end surfaces 18 are positioned in lower portions of die cavities 14. Each cavity 14 has been filled or partially so with a quantity of powder P to be compacted. As a practical matter the quantity of powder frequently varies from cavity to cavity, as shown in exaggerated form in FIG. 1 for purposes of illustration.
  • Valve solenoid 76 is in de-energized condition and valve 62 is in the position of FIGS. 1 and 7 wherein the portion of accumulator cylinder 46 to the left of piston 48 is in communication with drain outlet 72 and inlet is cut off from communication with the hydraulic compensator system.
  • Suitable conventional controls on the press are now actuated to cause the various components of press 10 to function in the manner and sequence described below.
  • Ram 28 is actuated to lower head 26 so that punches 30 enter the upper ends 16 of die cavities l4 and begin to compact powder P.
  • the individual punches encounter different degrees of initial resistance when there are varying amounts of powder in the individual die cavities. Since the powder levels in the cavities are assumed to be different, each punch moves upwardly with respect to head 26 a distance which is commensurate to the resistance which it has encountered and thereby forces its respective piston 34 upwardly a like distance in cylinder 36. This retrograde movement is represented by arrows on punches 30 in FIG. 2.
  • pistons 34 Upward movement of pistons 34 displaces hydraulic fluid from cylinders 36 through ports 40, passageway 42, conduit 58, port 60 and into accumulator cylinder 46.
  • the pressures generated or applied at each of the pistons are identical.
  • Accumulator piston 48 is forced to the left as the drawings are viewed until it bottoms against end wall 52 of cylinder 46. This movement of piston 48 displaces hydraulic fluid from the left portion of cylinder 46 and through port 64, conduits 66, 68 and outlet 72 into drain 74.
  • By the time that piston 48 has bottomed against end wall 52 the relative movement of pistons 34 to compensate for the different amounts of powders in cavities 14 has been completed and identical low pressures are applied to all pistons.
  • the various distances through which punches 30 and their pistons 34 have shifted are represented at a, b and c in FIGS. 2 through 4.
  • This decompression and expansion of the hydraulic fluid serves a very useful purpose in that it facilitates an initial relatively gradual reduction of the force applied by punches 20, 30 on the opposite ends of the compacted material, which in turn facilitates a relatively gradual decompression of the compacted material itself.
  • This initial decompression prevents sudden recovery expansion of the powder itself and sudden expansion of air entrapped within the compacted powder and, thus, tends to prevent the formation of internal faults in the compacted material such as cracks, laminations and end caps.
  • pellets gradually emerge through the open upper ends 16 of die cavities 14 and entrapped air in the pellets escapes progressively and gradually as the pellets emerge.
  • This step is illustrated in FIG. 5.
  • Head 26 continues upwardly thereby disengaging upper punches 30 from the pellets and removing the forcible contact of the upper and lower punches against the pellets. Head 26 continues upwardly to its initial position of FIGS. 1 and 6 at which time upper ram 28 halts movement of head 26.
  • ram 24 and punches are retracted downwardly to the starting position of FIG. 1.
  • solenoid 76 is energized to shift valve spool 146 leftward as FIG. 7 is viewed to connect hydraulic inlet 70 with conduit 68 and disconnect conduit 68 from outlet 72.
  • Accumulator cylinder 46 is thereby pressurized to move piston 48 to the right as the drawings are viewed (under the assistance of spring 55 and- /or rod 132), thereby emptying the accumulator and returning pistons 34 and punches 30 to their downward bottoming position.
  • pressure in cylinder 46 and conduit 68 builds to that of the supply pressure at inlet 70. If there has been any loss of fluid from the system downstream of the accumulator (through the seals, for example), check valve 80 opens under this pressure differential to replenish the supply of fluid to the closed circuit. Thereafter the check valve closes.
  • Solenoid 76 is now de-energized and spring 78 returns valve spool 146 to the right, cutting off inlet from conduit 68 and, through conduit 68, connecting the left end of accumulator cylinder 46 with drain outlet 72.
  • Spring 54 in accumulator cylinder 46 holds piston 48 against the right end wall 50 of the accumulator cylinder and the press is now in its initial condition of FIG. 1 ready for operation in a subsequent cycle in the manner described above.
  • Portion 138 of piston rod 132 which projects exteriorly of accumulator body 44 provides a visual indication of the position of accumulator piston 48 and, in some circumstances, may be used as a manual plunger for returning piston 48 to its initial position against end wall 50.
  • Check valve and high pressure seals 114 serve to isolate the circuitry between compensator cylinders 36 and accumulator piston 48 during the compaction cycle.
  • Check valve 80 opens only to permit replenishment of fluid into the circuitry between compacting cycles.
  • Gauge 82 shows the pressure in the compensator/accumulator system at various stages in cycle of operation of the press.
  • the pressure in the compensator/accumulator circuit is nominally zero, being only that which is created by the force of spring 54 on piston 48, and typically this force is about l0 pounds.
  • Accumulator 46, 48 is mounted as close as is practical to compensator cylinders 36 to minimize pressure losses in the system and, for this purpose, it is preferable to mount the accumulator on head 26 as shown or to form it as part of head 26 and/or platen 96.
  • the accumulator is shown as comprising a cylinder 46 and piston 48 therein, but broadly this accumulator is an expansible chamber having a predetermined maximum volume and other types of expansible chambers could be used.
  • cylinders 36, 46 have a diameter of about one inch and punches 20, 30 have a diameter of about onequarter inch.
  • the compacting stroke of punches 30 is about one-half inch.
  • the travel of accumulator piston 48 is correlated to permit a retrograde compensating stroke of pistons 34 which is about one-quarter of the compacting stroke of punches 30.
  • the press rams can be controlled to produce maximum pressure on the top sides of pistons 34 (FIG. 3) of from about 3,000 p.s.i. to about 10,000 p.s.i. and a back pressure during decompression and ejection (FIGS. 4 and 5) of from about 500 p.s.i. to about 3,000 p.s.i.
  • the pressure developed by the hydraulic source which supplies oil to the system through valve 62 can be in the range of about 250 p.s.i. to 500 p.s.i.
  • Press is illustrated as having three die cavities l4 and as being of the opposed ram type with the compensator system (pistons 34, cylinders 36 and accumulator body 44) mounted on the upper platen.
  • the invention is not limited to this specific arrangement; for example, the compensator system could be mounted on both platens or the lower platen.
  • the lower platen could be stationary and die plate 12 could be ram operated to apply compaction force to the lower ends of the pellets being formed.
  • the number and shape of the cavities can also be varied. Such modifications would require corresponding, readily apparent modifications in the compensator system and the press control circuit.
  • the cavities may be other than cylindrical.
  • a typical press in accordance with the invention is capable of satisfactory operation at rates up to about 75 cycles per minute and at such rates produces pellets of uranium-dioxide which are of acceptable quality and at acceptably low percentages of defective pellets.
  • an apparatus for forming powder material into pellets which are uniformly compacted to substantially the same density which comprises, a die having a plurality of through cavities therein in which powder is adapted to be compacted to form said pellets, a head having a plurality of punches thereon aligned one with each of said cavities, the leading end of each punch being adapted to be advanced into one end of its respective cavity to compact the powder therein, said head having a plurality of hydraulic cylinders therein, a piston axially slidable in each cylinder and operatively connected to the opposite end of a respective punch, means defining an accumulator chamber having a pressure responsive member therein movable to expand the chamber to a predetermined maximum size, means forming a closed hydraulic fluid circuit between said accumulator chamber and said cylinders so that the fluid pressures in said cylinders are substantially identical, a second plurality of punches for closing the other ends of said cavities, said last-mentioned punches being mounted on a common support which is
  • the apparatus called for in claim 1 including means for moving said support relative to said die upon said further relative movement of said head for causing the second set of punches to positively displace powder at said opposite ends of said powder columns in a compacting direction relative to the cavities.
  • the apparatus called for in claim 3 including a source of hydraulic fluid connected with said closed circuit for replenishing the same.
  • said accumulating chamber comprises a cylinder having a piston movable axially therein, said accumulator cylinder having one end thereof in said closed fluid circuit, the opposite end of the accumulator cylinder having a stop therein for limiting the extent of axial movement of the piston therein in one direction to thereby define said maximum size of the accumulator chamber.
  • the apparatus called for in claim 7 including means biasing said accumulator piston toward said one end of the accumulator cylinder to thereby permit the flow of fluid from said punch cylinders into said accumulator cylinder upon retraction movement of the punch pistons.
  • the method called for in claim 11 including the step of relatively moving the second set of punches and the die when said force is increased to positively displace the powder at said opposite ends of the columns in a compacting direction relative to the cavities.
  • said low pressure is in the range between 250 and 500 p.s.i..
  • said high pressure is in the range between 1,000 and 10,000 psi.
  • said intermediate pressure is in the range between 500 and 3,000 psi.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Moulds For Moulding Plastics Or The Like (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)
  • Powder Metallurgy (AREA)
US497573A 1974-08-15 1974-08-15 Apparatus and method for compacting particulate materials Expired - Lifetime US3890413A (en)

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US497573A US3890413A (en) 1974-08-15 1974-08-15 Apparatus and method for compacting particulate materials
CA232,661A CA1056573A (fr) 1974-08-15 1975-07-31 Dispositif et methode de compactage de materiaux en particules
JP50097241A JPS5145681A (fr) 1974-08-15 1975-08-13

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Cited By (37)

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US4017235A (en) * 1974-10-30 1977-04-12 Edward Kusters Apparatus for avoiding an excess of pressure in a continuous press
US4029456A (en) * 1974-10-31 1977-06-14 Eduard Kusters Maschinenfabrik Rapid load-relieve device for continuous press
US4053276A (en) * 1975-03-18 1977-10-11 Eduard Kusters Press for exerting a pressure over an area
US4145174A (en) * 1978-02-15 1979-03-20 Leningradskoe Spelsialnoe Konstruktorskoe Bjuro Polimernogo Masinostroenia Rotary tabletting machine
US4240778A (en) * 1979-08-27 1980-12-23 Efco, Inc. System for providing for parallelism in fluid powered press or the like
FR2462996A1 (fr) * 1979-08-10 1981-02-20 Gulf & Western Mfg Co Dispositif d'equilibrage de charge pour outillage de presse
FR2464131A1 (fr) * 1979-08-31 1981-03-06 Laeis Werke Ag Machine a mouler sous pression, en particulier pour elements moules en ceramique
US4302412A (en) * 1977-05-20 1981-11-24 Ptx-Pentronix, Inc. Method for compacting an article of powder material and for ejecting the article from a compacting die
US4379684A (en) * 1980-06-13 1983-04-12 Yoshizuka Seiki Co., Ltd. Press for powder metallurgy
US4570229A (en) * 1983-09-19 1986-02-11 Pennwalt Corporation Tablet press controller and method
US4588539A (en) * 1985-02-04 1986-05-13 James River Corporation Of Virginia Process and press with a controlled pressure system
EP0136695A3 (en) * 1983-10-05 1986-07-02 Maschinenfabrik Lauffer Gmbh & Co. Kg Press with several injection plungers
US4802836A (en) * 1987-07-13 1989-02-07 Gilles Whissell Compaction device for concrete block molding machine
US4880373A (en) * 1988-04-28 1989-11-14 The Upjohn Company Tablet press
US4959003A (en) * 1987-02-23 1990-09-25 Kvm Industrimaskiner A/S Device for die-casting of concrete goods such as block stones in a cellular mould
EP0445106A3 (en) * 1990-03-02 1991-12-04 Leinweber Maschinen Gesellschaft M.B.H. & Co. Kg Press for making articles from particulate material
WO1994005487A1 (fr) * 1992-08-28 1994-03-17 John T. Hepburn, Limited Repartition des forces de compression d'une presse sur plusieurs pieces
US5474726A (en) * 1992-06-12 1995-12-12 North American Refractories Company Method of making interlocking checker bricks
US5756017A (en) * 1995-09-08 1998-05-26 Sumitomo Chemical Company, Limited Method of simulating resin behavior in press molding
US5838571A (en) * 1996-01-29 1998-11-17 Alza Corporation Tablet press monitoring and controlling method and apparatus
EP0931644A1 (fr) * 1998-01-21 1999-07-28 Longinotti Meccanica S.r.l. Presse pour presser des carreaux fabriqués en ciment et un aggrégat quelconque tel que de la pierre concassée ou similaire
EP0911129A3 (fr) * 1997-08-27 2000-08-16 KOBRA FORMEN-UND ANLAGENBAU GmbH Moule pour la fabrication d'articles pressés
ES2181514A1 (es) * 1999-07-15 2003-02-16 Rodriguez Constantino Parra Dispositivo para regular la compactacion en punzones para prensas.
US20030041749A1 (en) * 2001-08-31 2003-03-06 Jurgen Hinzpeter Hydraulic press for compressing metallic powder
US20030047089A1 (en) * 2001-08-31 2003-03-13 Jurgen Hinzpeter Method and apparatus for minimizing the spread of maximumcompression forces in a powder press
US20050186300A1 (en) * 2004-02-20 2005-08-25 Jurgen Hinzpeter Powder press
EP1403017A3 (fr) * 2002-09-29 2005-10-12 Fabio Casolari Moule pour la fabrication de carreaux en céramique
US7150617B1 (en) 2003-11-17 2006-12-19 The United States Of America As Represented By The Secretary Of The Navy Multiple position press
US20110123663A1 (en) * 1999-07-29 2011-05-26 Glenn L Beane Method, System, and Computer Program for Controlling a Hydraulic Press
WO2012126930A1 (fr) * 2011-03-23 2012-09-27 Areva Nc Presse a maintenance amelioree
US20130140740A1 (en) * 2011-12-02 2013-06-06 Wildcat Discovery Technologies Hot pressing apparatus and method for same
CN103418789A (zh) * 2013-08-08 2013-12-04 中国地质大学（武汉） 一种用于热压pdc钻头胎体粉末成型的多孔模具
CN103434171A (zh) * 2013-07-19 2013-12-11 合肥海德数控液压设备有限公司 一种可同时压制双发射孔弹的液压机
US20140124985A1 (en) * 2012-11-07 2014-05-08 Oci Company Ltd. Method for molding core of vacuum insulation panel
CN107599253A (zh) * 2017-08-18 2018-01-19 厦门艾斯霖橡塑科技有限公司 花洒喷嘴的生产加工工艺
CN110481086A (zh) * 2019-09-17 2019-11-22 中国工程物理研究院化工材料研究所 一种多通道变阻尼粉末成型压制工装及其控制方法
US20220373000A1 (en) * 2021-04-19 2022-11-24 Walvoil S.P.A. Hydraulic distributor with pressure compensator for directional valves

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JPS60168617A (ja) * 1984-02-13 1985-09-02 Idemitsu Petrochem Co Ltd プレス成形装置
JPS63230313A (ja) * 1987-03-19 1988-09-26 Nippon Sheet Glass Co Ltd プレス成形装置
JP2012245562A (ja) * 2011-05-31 2012-12-13 Mitsubishi Materials Techno Corp 粉末成形装置
JP2022165770A (ja) * 2021-04-20 2022-11-01 久慈琥珀株式会社 成形装置

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US2675581A (en) * 1951-08-13 1954-04-20 Speer Carbon Company Apparatus for producing insulated resistor shells
US2926412A (en) * 1953-12-31 1960-03-01 French Oil Mill Machinery Press
US2825092A (en) * 1954-11-17 1958-03-04 Bliss E W Co Briquetting press
US3060506A (en) * 1957-06-24 1962-10-30 Uschmann Curt Molding press
US3052918A (en) * 1958-08-04 1962-09-11 Stanley H Holmes Hydraulic molding apparatus
US3279021A (en) * 1963-09-26 1966-10-18 Pratt Concrete products machine
US3524220A (en) * 1967-11-15 1970-08-18 Western Electric Co Die set for compacting powder
US3545045A (en) * 1968-09-04 1970-12-08 Paul Vinson Powder compacting subpress
US3664784A (en) * 1970-01-19 1972-05-23 Pennwalt Corp Compacting press

Cited By (54)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4017235A (en) * 1974-10-30 1977-04-12 Edward Kusters Apparatus for avoiding an excess of pressure in a continuous press
US4029456A (en) * 1974-10-31 1977-06-14 Eduard Kusters Maschinenfabrik Rapid load-relieve device for continuous press
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JPS5145681A (fr) 1976-04-19
CA1056573A (fr) 1979-06-19

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