US3830607A - Apparatus for compacting material - Google Patents

Apparatus for compacting material Download PDF

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Publication number
US3830607A
US3830607A US00321438A US32143873A US3830607A US 3830607 A US3830607 A US 3830607A US 00321438 A US00321438 A US 00321438A US 32143873 A US32143873 A US 32143873A US 3830607 A US3830607 A US 3830607A
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Prior art keywords
pressure vessel
pressure
chamber
closing
piston
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US00321438A
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English (en)
Inventor
K Baxendale
R Waasdorp
J Evershed
M Howlett
W Bergemann
D Camp
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Gleason Works
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Gleason Works
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Priority to US00321438A priority Critical patent/US3830607A/en
Priority to CA183,478A priority patent/CA997618A/en
Priority to ZA00738133A priority patent/ZA738133B/xx
Priority to GB5124373A priority patent/GB1426938A/en
Priority to JP48137249A priority patent/JPS4997970A/ja
Priority to AU63762/73A priority patent/AU474431B2/en
Priority to DE2363652A priority patent/DE2363652A1/de
Priority to BR10300/73A priority patent/BR7310300D0/pt
Priority to FR7400352A priority patent/FR2322729A3/fr
Application granted granted Critical
Publication of US3830607A publication Critical patent/US3830607A/en
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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
    • B30B11/001—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses using a flexible element, e.g. diaphragm, urged by fluid pressure; Isostatic presses

Definitions

  • the apparatus includes an essentially selfcontained isostatic system within a pressure vessel, and there is no requirement for injection of a high pressure fluid into the pressure vessel from an external source.
  • a deformable mold means is suspended within the pressure vessel by a support means arranged to be free to move for a limited distance within the pressure vessel during a pressurization of the chamber within the vessel.
  • the apparatus includes means for filling the deformable mold means with the compactible material together with means for closing the chamber of the pressure vessel in which the deformable mold means is inserted so as to allow a relatively high compacting pressure to be applied to the material without producing unwanted stresses or design variation in the final product to be produced.
  • isostatic compaction involves the loading of a powder material into an elastomeric bag or other deformable mold at a point outside of a pressure vessel, followed by an immersion of the loaded bag into a liquid system supplied to a chamber within the pressure vessel.
  • This type of isostatic compacting is more generally referred to as wet bag compacting, and its provision for complete immersion of the compactible mterial in a liquid bath which is pressurized results in a true isostatic compaction of the material.
  • a modified form of isostatic copaction involves the loading of a bag, or deformable mold, with a powder material while the bag is positioned within a chamber of a pressure vessel. After loading, the bag is plugged, the pressure vessel is closed, and a fluid pressure force is applied to certain of the external surfaces of the bag so as to compact the powder material contained therein.
  • This technique is referred to as dry bag compacting and is usually described as a form of isostatic compacting even though a part of the external surface area of the deformable mold is not subjected to direct pressure from the fluid system operating in the pressure vessel.
  • substantially theoretical isostatic compacting is achieved because indirect forces are applied to all unexposed surfaces of the mold so 'as to provide for a substantially simultaneous and equal pressure from every direction.
  • the just described dry bag technique offers an advantage of increased production capability by the fact that the deformable mold is filled with powder material and later unloaded without any required movement of the mold itself from the confines of the pressure vessel.
  • a further form of modified isostatic compaction involves a simulation of a fluid system through the use of relatively soft or flowable substances, such as certain elastomeric materials, which are placed around the quantity of material to be compacted (or a deformable mold in which the material is contained), and the relatively soft substances impart substantially uniform pressure to all sides of the material being compacted when mechanical forces are applied to the soft substances.
  • this technique is described as a dry bag technique when a deformable mold is filled in place in a pressure vessel.
  • the present invention is mainly concerned with improvements in dry bag techniques for isostatic compaction, although the principles of the invention can be applied equally well to situations where the deformable mold is initally filled while positioned externally of a pressure vessel.
  • One of the problems of prior art compacting techniques is the problem of obtaining uniform characteristics in a final product being produced by a rapid production technique. This is especially true in the case of ferrous metal powder compaction which requires relatively high compacting pressures on the order of 40,000 to 50,000 psig, or even higher pressures, to obtain coherencey and requisite density of the compacted part. It is very difficult to control the placement of a deformable mold in a pressure vessel and to avoid unwanted applications of stresses to a quantity of material contained therein during rapid pressurization and depressurization of the chamber to and from such relatively high pressures.
  • the present invention offers improvements in this relatively highly developed art by providing for an apparatus which can be used on a sustained basis for relatively rapid production of compacted parts.
  • a particular use of the apparatus of this invention permits rapid production of ferrous metal preforms which can be subjected to subsequent heating and forming treatments which produce high strength, precision parts having nearly per cent theoretical density in their final form. It has been found that the successful productionof such precision parts requires a careful control of characteristics of the intermediate compacted part which is produced by the apparatus to be discussed herein.
  • an improved compacting apparatus is provided with an essentially self-contained isostatic system within a pressure vessel so that there is no requirement there is no requirement for injecting a high pressure fluid into the pressure vessel from an external source.
  • an essentially self-contained isostatic system certain unusual fluids and semi-liquid materials can be used which are not usable in systemsrequiring a pumping and delivery of the isostatic fluid from an external source.
  • certain high viscosity silicone fluids and other polymer type fluids may be used with the apparatus of this invention.
  • the self-contained isostatic system is pressurized by an intensifier means operating through a closing means for the pressure vessel, and pressurization of the isostatic system within the pressure vessel causes the closing means to move outwardly from the pressure vessel to engage a pressure plate means while maintaining a sealed relationship between the closing means and the pressure vessel.
  • a pressure vessel is provided with closing means at opposite ends of a bore formed therethrough, and the closing means are arranged so that the pressure vessel can be loaded, pressurized, depressurized, and unloaded without disengaging high pressure seals for either end of the bore.
  • the closing means are designed to expand outwardly in opposite directions away from the pressurized inner chamber of the pressure vessel during a compacting operation so a to engage a pair of spaced pressure plates which are designed to resist the relatively high pressure developed in the pressure vessel.
  • One or more pressure vessels can be carried in a support structure for rapid, successive movement between the spaced pressure plates to provide for a pressurization of each vessel after being loaded with a quantity of compactible material. After pressurization and subsequent depressurization, each pressure vessel is moved, in turn, away from the spaced pressure plates so that the compacted material can be removed and a new quantity of material introduced into each pressure vessel.
  • the improved compacting apparatus is provided with a support means for suspending a deformable mold means in a chamber of a pressure vessel so that a quantity of material to be compacted can be subjected to substantially equal forces from all directions during a complete pressurizing and depressurizing cycle.
  • the support means is mounted within the chamber so as to be free to move for a limited distance, along an axis passing through the chamber, in response to changing pressure conditions within the chamber. This movement allows the suspended deformable mold means to follow distortions of a closing means associated with the pressure vessel without applying unwanted stresses to the material being compacted within the deformable mold means.
  • This arrangement permits a controlled pressurization of the deformable mold means without the chamber response to such pressurization being imparted to the material being contacted.
  • the specific arrangements of the invention provide for a better balancing and more uniform application of forces to a quantity of material in an isostatic technique which lends itself to very high production rates.
  • a further feature of the invention is a provision'for application of a force to a deformable mold means contained within the pressure vessel with a system which permits full control of rapid pressurizing and depressurizing cycles which do not impart unwanted loads or shocks to the material being compacted.
  • the overall arrangement of the present invention is one which includes on or more pressure vessels which can be sequentially moved into position for carrying out rapid compacting operations and which include relatively simple and reliable driving arrangements for such movements.
  • a pair of pressure vessels can be mounted to pivot about a common axis, and
  • a full cycle of closing, compacting, and depressurizing can be carried out without further movement or adjustment of position of the relatively large and heavy pressure vessel from its compacting position.
  • the pressure vessel can be rapidly rotated to a loading/unloading position while the second vessel of the pair is advanced to the compacting position.
  • compactible materials any material which can be pressed to a new shape or to an increased density by an application of force thereto.
  • this term includes material which has been previously compacted and which can be further compacted to an increased density and new size or shape.
  • deformable mold means and this is meant to include eleastomeric bag or diaphragm structures designed to contain a material during compaction.
  • Such structures can be made from various forms of polyurethane, and other elastomeric materials which offer characteristics of resilience, deformability, and recoverability of shape and size after being deformed.
  • isostatic herein is intended to include the various types of true and modified isostatic compaction discussed at the beginning portion of this specification.
  • FIG. 1 is an elevational view of the overall apparatus of the present invention together with certain collateral equipment used for dispensing powder into the apparatus and for removing compacted parts therefrom;
  • FIG. 2 is a top plan view of the apparatus shown in FIG. 1 and illustrating a driving means for controlling movement of a pair of pressure vessels associated with the apparatus;
  • FIG. 3 is a diagrammatic elevational view, in cross section, showing essential details of the pressure vessel and its contained structures in accordance with the present invention
  • FIG. 4 is an exploded isometric view showing an isostatic tooling assembly which may be used with the apparatus of this invention
  • FIG. 5 is an elevational view, partly in section, of a pressurizing means which applies a force to a selfcontained isostatic system contained within the pressure vessel of the present invention
  • FIG. 6 is a circuit diagram illustrating hydraulic control functions for pressurizing and depressurizing a pressure vessel in accordance with the present invention.
  • FIG. 7 is a circuit diagram showing hydraulic control functions for a driving means associated with movement of a pair of pressure vessels into and out of a compacting station.
  • FIGS. 1 and 2 illustrate a specific embodiment of the present invention which includes two separate pressure vessels l0 and 12 carried at opposite ends of a support structure 14 so that the two pressure vessels can be rotated about a common axis 16 to provide for altemating placement of each pressure vessel in a compacting station defined between a pair of pressure plate means comprising two relatively thick metal plates 18 and 20 mounted on a base structure 21.
  • the pair of pressure plate means 18 and 20 are rigidly secured in a parallel, spaced relationship to each other by securing devices associated with three support posts 22 which pass through openings formed in each of the pressure plates. As shown in FIG. 2, the three posts 22 are arranged in a triangular configuration so as to minimize stresses which will be applied to the two pressure plate means 18 and 20 supported thereby.
  • each of the pressure vessels and 12 is alternately loaded and unloaded at the postion shown for the pressure vessel 12 exteriorly of the compacting frame.
  • Loading of a compactible material, such equipment 24 which provides for a dispensing of measured quantities of powder into a mold cavity provide in each pressure vessel.
  • Unloading is carried out with an extractor means 26 which functions to engage a compacted part and to withdraw the compacted part from the mold cavity of the pressure vessel.
  • the loading and unloading devices may be arranged as shown in FIG. 2 so as to be alternately pivoted into position over the mold cavity of a given pressure vessel in accordance with whatever operation is to be performed.
  • a two way hydraulic ram means 28 may be controlled to advance and retract the loading and unloading devices 24 and 26 about a pivot axis 30 which is arranged to bring one or the other of the devices into alignment with the mold cavity of the pressure vessel being loaded or unloaded.
  • the pair of pressure vessels 10 and 12 are rapidly rotated to bring the loaded pressure vessel within the confines of the compacting frame and to simultaneously remove the opposing pressure vessel from the compacting frame so that a compacted part can be removed therefrom.
  • the vessels are then locked into position with a locking wedge 25 controlled by a ram 27. Rapid rotating of the two pressure vessels 10 and 12 about the common aix 16 is accomplished with a Geneva type gear mechanism which imparts a 180 reciprocating rotation to a drive gear 32 associated with the support frame 14 carrying the two pressure vessels l0 and 12.
  • the drive gear 32 is driven by gear 34 which receives its driving moments from a gear 36 via gear 35.
  • the gear 36- includes a slotted portion 38 for receiving a follower 40 carried by a driving arm 42.
  • the driving arm 42 is reciprocated back and forth by known means which includes a hydraulic motor (see FIG. 7 and discussion relating thereto) for reciprocating the arm back and forth about an axis 44 for an angular rotation of 90.
  • This 90 rotation imparts at 180 rotation to the main drive gear 32 through a selection of appropriate gear ratios between the gears 36, 35, 34, and 32.
  • FIG. 3 illustrates basic components making up the pressure vessel and compacting assemblies of the present invention.
  • Each pressure vessel 10 and 12 comprises a generally cylindrical structure having a bore 50 formed through its center axis so as to define a compacting chamber therein.
  • Separate closing means 52 and 54 are provided for closing top and bottom openings, respectively, of the bore 50 so as to provide a closed and sealed compacting chamber during a compacting operation.
  • a dry bag system is shown wherein a deformable mold means, consisting of an inner elastomeric bag 56 and an outer elastomeric bag 58, is suspended within the compacting chamber for receiving a quantity of powder material 60 to be compacted into a self-supporting form.
  • the illustrated arrangement also includes a self-contained isostatic system, comprising, for example, a quantity of hydraulic fluid 62, sealed within the compacting chamber for applying a compacting force to the quantity of material 60 when the pressure vessel is closed and pressurized.
  • a pressurizing means 64 in the form of a piston member fitted within a bore formed through the bottom closing means 54, operates through the bottom closing means 54 for pressurizing the self-contained isostatic system during a compacting operation. This is accomplished without the introduction of high pressure fluid into the pressure vessel from an external source during such pressurizing, and this arrangement eliminates any requirement for penetration of the walls of the pressure vessel or for a use of high pressure fittings through the pressure vessel or through its closing means 52 and 54.
  • the piston member 64 is driven upwardly to apply a pressurizing force to the isostatic system within the chamber of the pressure vessel by a separate piston member 70 fitted within a chamber positioned within the base 21 of the compacting frame and carried by the lower plate means 20.
  • the second piston member 70 is driven upwardly by hydraulic force applied to its bottom face, and the second piston member 70 is of a larger'diameter than the piston member 64 so as to provide for a multiplication of force which will be applied to the fluid system contained within the compacting chamber.
  • the combination of the larger piston member 70 with the small piston member 64 is known as an intensifier means and has been known in the art prior to the present invention. In, the FIG.
  • the larger diameter piston member 70 is shown with an extended portion 71 in its withdrawn position below the upper surface level of a support platform 72 provided on the pressure plate 20 of the compacting frame, and the extended portion 71 is moved upwardly in engagement with the smaller piston member 64 when the-pressure vessel is to be pressurized.
  • the smaller piston member 64 is limited in its range of downward movement by an annular retainer ring 74. Downward movement of the piston member 64, to depressurize the compacting chamber, is encouraged by an application of fluid pressure through a conduit 76 which communicates with an annular pressure reactive surface 78 of the smaller diameter piston member 64.
  • the deformable mold means can be filled with a compactible material 60, after which the pressure vessel 10 is advanced into a compacting position between the parallel pressure plate means 18 and 20. This movement places the smaller diameter piston member 64 in direct alignment with an extended portion 71 of the larger diameter piston member 70 contained within the base of the compacting frame.
  • the top of the pressure vessel is closed by a movement of the closing means 52 downwardly so as to advance a deformable plug means 80 into the open top of the deformable mold means and to close the upper end of the compacting chamber of the pressure vessel.
  • Downward and upward movements of the closing'means 52 are provided with a relatively small hydraulic ram (not shown in FIG.
  • a connecting rod 84 extends between the ram and the closing means 52 through a bore provided through the pressure plate means 18.
  • the plug means 80 is secured to the closing means 52 with an adhesive or by any other suitable means.
  • a separate spacer plate means 86 is provided for insertion between the top surface of the closing means 52 and the bottom surface of the upper pressure plate means 18 after the pressure vessel is closed.
  • the lower closing means 54 is secured to the base of the pressure vessel with a number of spring-loaded fasteners 55 which permit the lower closing means 54 to move downwardly against the support platform 72 without releasing high pressure sealing means 57 provided between the lower closing means 54 and the bore 50 of the pressure vessel. Upwardly directed forces are received by the upper pressure plate means 18, as discussed above, and downward forces are received by the lower pressure plate means 20 through the support platform 72.
  • a supporting means 90 which functions to suspend the deformable mold means within the compacting chamber of the pressure vessel so that the deformable mold means can follow the slight movement of the upper closing means 52 discussed above.
  • the arrangement of the present invention allows the deformable mold means to follow any slight movement of its deformable plug 80 (upwardly in the FIG. 3 orientation) during a pressurizing operation so as to maintain predetermined relationships between the plug means and the deformable mold means.
  • This is accomplished with the supporting means which includes an annular groove 92 about its upper end for permitting limited axial movement of the supporting means 90 relative to the upper end of the pressure vessel 10.
  • the supporting means 90 is suspended within the bore 50 by two semicircular retaining ring elements 94, and each of these elements has a projecting portion which is received within the annular groove 92 of the supporting means 90.
  • the supporting means 90 includes a small diameter bore for receiving the deformable mold means and its manifold sleeve 66, together with a larger diameter bore portion for receiving a locating ring means 96 from which the inner elastomeric bag 56 is suspended.
  • the supporting means 90 is illustrated in FIG. 3 in a slightly upwardly displaced position, but the supporting means would normally be pressed downwardly by the closing means 52 at the time of closing the pressure vessel 10 for a compacting operation. During compacting, a slight deflection of the closing means 52 upwardly would be followed by the supporting means 90, thereby maintaining the deformable mold in a predetermined and precise relative position with its plug means 80.
  • the supporting means 90 illustrated in FIG. 3 serves an additional function of reducing the diameter of the compacting chamber to receive a given diameter of isostatic tooling. Large or smaller diameters for tooling can be provided by interchanging the supporting means 90 with one having a different sized main bore therethrough. If this additional function is not desired, the following characteristic discussed above can be provided by a supporting means which consists of the loeating ring means 96, or other supporting structure for the deformable mold means, arranged to follow slight movements of the closing means 52 and the plug 80 during a compacting operation.
  • FIG. 4 taken in conjunction with illustrations of FIG. 3, further explains the various components which are assembled together to form isostatic tooling used with the apparatus of the present invention.
  • the quantity of compactible material is illustrated in the form of a finished compact 100 having a convex surface configuration 102 at one end thereof and a bore 104 formed through its center axis so as to pass completely through the compact and through the one end on which the convex surface configuration is formed.
  • the finished compact 100 is a selfsupporting product which can be subjected to further handling and treating to produce a final product.
  • the final product may be of the identical form and size as the illustrated compact 100 or it may constitute a new shape and size resulting from a subsequent forming operation applied to the intermediate compact form which is illustrated.
  • the illustrated compact is symmetrical about its center axis, and the bore 104 is precisely positioned on the center axis.
  • a base member 106 of the illustrated tooling functions to support and position a core rod means 108 for defining the bore to be formed in the compact.
  • the base member 106 constitutes a rigid, non-deformable structure which can be closely fitted within the internal diameter of the supporting means 90 (see FIG. 3) within which the isostatic tooling is to be placed.
  • the entire isostatic tooling package is precisely centered within the chamber bore 50 by a centering sleeve 110 (FIG. 3) which is fitted around an external diameter of the supporting means 90, and which provides the further function of locking the sealing ring 91 in place to precompress the sealing ring and to prevent dislodgment during depressurization of the pressure vessel.
  • the core rod means 108 may constitute an integral structure with the base member 106, formed from the same rigid material (such as steel), or may constitute a separate component which is secured to the base member 106.
  • the base member 106 supports a deformable mold means which is illustrated as including an inner elastomeric bag 56 and an outer elastomeric bag 58 to define an open-ended cavity for holding a quantity of powder material while the powder material is being formed into the illustrated self-supporting compact 100.
  • the inner and outer elastomeric bags are assembled together so as to be in substantial face-to-face contact with one another, and this provides for a frictional engagement between the two bags which is sufficient to hold them together in the assembly.
  • Each of the elastomeric bags includes an opening through its bottom wall portion for receiving the core rod means 108 therethrough. The assembled relationship is illustrated in FIG.
  • a reduced diameter portion 112 may be provided at a base level of the core rod means for receiving the base of the elastomeric bag 58 in a tight sealing engagement.
  • the base member 106 supports a manifold means 66 for distributing fluid to all external surfaces of the deformable mold means.
  • manifold means 66 is of a significantly smaller external diameter than the diameter of the bore within which the isostatic tooling is positioned so as to provide for sufficient clearance for a free flow of a pressurizing medium all around the manifold means.
  • the inside diameter and shape of the manifold means is designed to define the unpressurized condition of the deformable mold means.
  • the locating ring means 96 comprises a relatively rigid structure, formed from metal or other nondeformable material, for carrying the full weight of the isostatic tooling and its contents when the isostatic tooling is secured thereto and lowered into the chamber of the pressure vessel. Also, the locating ring means carries the load on the tooling resulting from an air differential established by the downward movement of piston 64 which draws a partial vacuum on the deformable mold means to cause it to expand to the shape of the manifold after compacting is completed.
  • the isostatic tooling which is illustrated in FIG. 4 is merely representative of one form of tooling which may be utilized with the pressure vessel apparatus of the present invention. This tooling does not form a separate part of the present invention and is described in greater detail in a commonly owned application entitled Tooling For Receiving And Supporting A Quantity Of Powder Material To Be Pressed Into A Selfsupporting Compact, filed on even date herewith in the name of Kenneth Baxendale.
  • FIG. 5 illustrates details of construction of the small diameter piston member 64 discussed above with reference to FIG. 3.
  • the small diameter piston member 64 functions to apply a compression force to an isostatic medium, such as a liquid 62, contained within the compacting chamber.
  • an isostatic medium such as a liquid 62
  • FIG. 5 illustrates details of construction of the small diameter piston member 64 discussed above with reference to FIG. 3.
  • the small diameter piston member 64 functions to apply a compression force to an isostatic medium, such as a liquid 62, contained within the compacting chamber.
  • an isostatic medium such as a liquid 62
  • a supply of replenishing oil, or other liquid is carried within the support structure 14 so that the replenishing liquid can be delivered to either of the pressure vessels 10 or 12 carried by the support structure.
  • the supply reservoir 111 includes a quantity of liquid which is pressurized by a quantity of gas contained within the reservoir. Adjustment of pressure of the gas can be used to regulate the pressure at which the reservoir liquid flows through the conduit 76. This adjustment permits an adjustment of a pressure differential that can be established between inside and outside surfaces of the deformable mold during depressurization of the system. Such depressurization causes the mold to be drawn outwardly to conform to the interior shape of the manifold means 66 dis cussed above.
  • a central chamber 121 is defined within the piston member 64 for receiving such a supply of liquid.
  • the central chamber is closed at its bottom end by an end cap structure 122 and at its top end by an assembly that includes a cylindrical block 124 which functions as a valve.
  • the cylindrical block 124 is secured to a center rod 126 which supports a spring means 128 for normally urging the cylindrical block to a downwardly directed position which seals the chamber within the piston member 64.
  • Compression on the spring means 128 is adjusted by turning an adjustment nut 129 on the threaded end of the center rod 126 (access being available through removal of end cap 122).
  • the spring means 128 is overcome by the higher pressure within the piston member 64, and this displaces the cylindrical block 124 from its sealed position on the top surface of the piston member 64. This allows a replenishing of liquid from the interior of the piston member 64 into the compacting chamber as the piston member 64 iswithdrawn to a starting position for a subsequent pressurizing operation.
  • the cylindrical block 124 may be provided with a pin 130 to prevent rotation thereof during adjustment of compression on the spring means 128 with the adjustment nut 129.
  • FIG. 6 illustrates a hydraulic control circuit for controlling pressurization and depressurization of the apparatus of the present invention.
  • a motor 200 (which may comprise a 50 horsepower motor operating at 1,200 rpm) drives two separate pumps 202 and 204.
  • the pump 202 is a fixed displacement vane type of pump (capable of delivering about 21 gallons per minute, for example) and the pump 204 is a fixed volume piston pump (capable of delivering up to 24 gallons per minute).
  • both pumps function to supply hydraulic fluid to the cylinder in which the larger piston member 70 is carried so as to drive the larger piston. This movement (upwardly in the FIG. 6 view) is transmitted to the smaller piston member 64 which applies a force to the isostatic system, as discussed above.
  • Delivery of hydraulic fluid from pump 202 is carried out through a conduit 206, through a solenoid operated valve 208, through conduit 210, past a check valve 212, and into a conduit 214 which is also receiving fluid delivery from the pump 204.
  • the conduit 214 delivers fluid through a solenoid operated valve 216 (when the valve is moved to the left from the position shown in FIG. 6) and into a delivery conduit 218 which drives the piston members 70 and 64 into the pressure vessel (in the direction of the arrow).
  • a relief valve 220 is opened (in response to a detection of 2,000 psig in pilot line 221) so that all fluid delivery from the pump 202 will be carried back to the reservoir 222.
  • This dumping action reduces the volume of fluid delivery to the piston 70 during the final portion of its pressurizing stroke, and the pump 204 continues in its delivery of fluid until a preferred peak level (for example, about 2,800 psig) is reached.
  • a relief valve 224 provides for sufficient recirculation of fluid back to tank to maintain the preferred peak level.
  • the relief valve 224 is adjusted by one of three vent controls 226, 228, or 230, as selected by operation of a solenoid valve 232.
  • vent control 228 functions to control relief valve 224 to operate at the preferred peak pressure level.
  • a pressure switch 234 senses the peak pressure level and actuates a circuit to initiate a dwell period after which a solenoid associated with valve 232 is energized to shift the valve 232 and to place the vent control 230 in circuit. This initiates a decompression cycle which includes an initial phase during which fluid from the main delivery conduit 214 is throttled back to tank until a reduced pressure (for example, about 1,000 psig) level is reached. At that point, the solenoid valve 216 is shifted (with a timing mechanism which calculates the approximate time for arriving at the reduced pressure level) to a position (as shown in FIG.
  • a limit switch (not shown) is actuated to shift the valve 232 to place vent control 226 in circuit, thereby permitting a full flow of fluid from the relief valve 224 back to tank. This reduces the operating level of the relief valve 224 down to a minimal amount of about 50 psig. This provides for a reduction of pressure within the entire system to prevent unnecessary restriction of flow and overheating of the fluid within the system, and conserves power, during idling of the system between compacting operations.
  • the solenoid valve 208 is energized to direct the flow of fluid from pump 202 to a conduit 240 leading to a hydraulic motor associated with the driving means for the pressure vessels discussed with reference to FIGS. 1 and 2 above.
  • the control circuit for this driving means is shown in FIG. 7 where the conduit 240 is continued from the circuit illustrated in FIG. 6.
  • rotation of the two pressure vessels is carried out with a known type of hydraulic motor 300 which provides for a rotary actuation of a pair of opposed vanes 302 within separate chambers 304.
  • the chambers 304 are defined by fixed structures 306 contained within the hydraulic motor.
  • Control of rotation of the hydraulic motor 300 in either a clockwise or counterclockwise direction is effected with a solenoid operated valve 310. Movement of the valve towards the right in the FIG. 7 view delivers high pressure fluid from the conduit 240 through a conduit 312 which pressurizes the chambers 304 in the areas in which have been stippled in the FIG. 7 view. This results in a clockwise rotation of the vanes 302. Movement of the solenoid control valve 310 towards the left in the FIG. 7 view results in a delivery of pressurized fluid (about l,200 psig) through a separate conduit 314 which delivers fluid to the portions of the chambers 304 which are not stippled in the FIG. 7 view, and this results in a counterclockwise rotation of the vanes 302. In either direction of movement, high pressure fluid enters the motor by way of one of the circuits in which check valves 315 are included.
  • the hydraulic motor 300 is capable of rotating the two pressure vessels illustrated in FIGS. 1 and 2 for 180 in a time period of about 1 second. This rapid rotation is achieved by initially delivering high pressure fluid at about 1,200 psig to the hydraulic motor 300 to rapidly accelerate the motor in one direction or the other. About halfway through such rotation, it is necessary to start braking the movement of the motor since the rapid movement of the pressure vessels will tend to rotate the motor if a braking force is not applied. Braking is controlled with a relief valve 316 having high and low pressure levels of operation. At the halfway point of rotation, a limit switch is contacted and the relief valve 316 is shifted to a lower pressure condition by an operation of a solenoid operated valve 318. When the solenoid operated valve 318 is in the position shown in FIG.
  • a low pressure condition is established in the main delivery line 240, thereby reducing the pressure at fluid flow to the chamber portion 304 being pressurized.
  • fluid is being exhausted from the portions of the chambers 304 which are unpressurized, and during this final half of rotation this exhausting takes place through one of the restrictor valves 320 which tends to decelerate the rotational movement of the vanes 302.
  • the high pressure delivery of fluid establishes a mode of operation for one of the relief valves 322 to allow rapid dumping of fluid from the unpressurized parts of the motor back to tank.
  • the solenoid valve 318 is shifted to lower pressure in the main delivery line 240, the valves 322 shift to a mode which prevents fluid delivery therethrough and which forces the fluid through one of the restrictor valves 320.
  • a high production rate apparatus for applying a relatively uniformly distributed pressure to a quantity of compactible material placed in a chamber defined within a pressure vessel comprising a pressure vessel having a chamber defined therein,
  • deformable mold means which can be suspended within the chamber of said pressure vessel a self-contained isostatic system carried within said pressure vessel for applying a compacting force to a quantity of material placed within said deformable mold means
  • closing means for closing said chamber during a compacting operation
  • pressurizing means operating through said closing means for pressurizing and depressurizing said isostatic system during a compacting operation without the introduction of high pressure fluid into the pressure vessel from an external source during such pressurizing, said pressurizing means comprising (a) a first piston means which can be advanced into said chamber to apply a pressurizing force to said fluid carried within the chamber, and (b) a second piston means for multiplying the force applied to said fluid by the first piston means, and
  • a hydraulic control system operated externally of said pressure vessel for controlling the movements of said first and second piston means.
  • said isostatic system includes a quantity of fluid carried within said chamber so as to contact outside surfaces of said deformable mold means during a pressurizing of the deformable mold means.
  • said chamber of said pressure vessel is defined by a bore extending completely through the pressure vessel to thereby provide oppositely directed openings extending along the axis of said bore, and wherein said closing means comprises separate closing means for each end of said bore.
  • An apparatus for containing a quantity of material to be compacted by the force of a pressurized fluid said apparatus being of a type which includes a cylindrical pressure vessel having a bore extending therethrough with the center axis of the bore being coincident with the center axis of the pressure vessel, a deformable mold carried within said bore for receiving a quantity of material to be compacted, a first closing means for closing one end of said bore of said pressure vessel, a second closing means for closing a second end of said bore of said pressure vessel, a pair of spaced apart pressure plates for receiving said pressure vessel therebetween during a compacting operation, and moving means for advancing the pressurevessel to a position between said pair of spaced apart pressure plates, the improvement comprising an essentially self-contained isostatic system carried within the bore of said pressure vessel, and pressurizing means operating through one of said closing means for imparting a pressure to said isostatic system contained within said pressure vessel so as to (a) expand said first and second closing means outwardly in opposite directions against respective pressure plate
  • said pressurizing means includes an intensifier means for multiplying the pressure on said isostatic system in said chamber, and including replenisher means in combination with said intensifier means for automatically supplying additional fluid to said chamber in response to a loss of fluid from the chamber through leakage.
  • said hydraulic control circuit includes control means for depressurizing said chamber through a reverse operation of said intensifier means.
  • unloading means for removing the material from said chamber after being compacted.
  • pressurizing means operating through a closing means for pressurizing the isostatic system carried within said pressure vessel, said pressurizing means being in the form of a piston means which can be advanced through a bore formed through said pressure vessel so as to apply a compression force to said isostatic system without the introduction of high pressure fluid into the pressure vessel from an external source.
  • said supporting means comprises an annular sleeve structure which can be suspended within a bore defined in said pressure vessel for receiving and supporting said deformable mold means, said annular sleeve structure being open at one end to allow passage of a plug means therethrough.
  • said piston means includes a replenishing means for automatically supplying a metered volume of fluid into said pressure vessel upon withdrawal of the piston means from the pressure vessel.
  • said first piston means includes a replenishing means for automatically supplying a metered volume of fluid into said pressure vessel upon withdrawal of said first piston from the pressure vessel.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Press-Shaping Or Shaping Using Conveyers (AREA)
  • Moulds For Moulding Plastics Or The Like (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)
  • Powder Metallurgy (AREA)
US00321438A 1973-01-05 1973-01-05 Apparatus for compacting material Expired - Lifetime US3830607A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
US00321438A US3830607A (en) 1973-01-05 1973-01-05 Apparatus for compacting material
CA183,478A CA997618A (en) 1973-01-05 1973-10-16 Apparatus for compacting material
ZA00738133A ZA738133B (en) 1973-01-05 1973-10-19 Improved apparatus for compacting material
GB5124373A GB1426938A (en) 1973-01-05 1973-11-05 Apparatus for compacting material
JP48137249A JPS4997970A (enrdf_load_stackoverflow) 1973-01-05 1973-12-07
AU63762/73A AU474431B2 (en) 1973-01-05 1973-12-18 Improved apparatus for compacting material
DE2363652A DE2363652A1 (de) 1973-01-05 1973-12-20 Isostatische presse
BR10300/73A BR7310300D0 (pt) 1973-01-05 1973-12-28 Aparelho aperfeicoado para compactar materiais
FR7400352A FR2322729A3 (fr) 1973-01-05 1974-01-04 Machine d'agglomeration par compression de doses de matiere compressible

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00321438A US3830607A (en) 1973-01-05 1973-01-05 Apparatus for compacting material

Publications (1)

Publication Number Publication Date
US3830607A true US3830607A (en) 1974-08-20

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00321438A Expired - Lifetime US3830607A (en) 1973-01-05 1973-01-05 Apparatus for compacting material

Country Status (9)

Country Link
US (1) US3830607A (enrdf_load_stackoverflow)
JP (1) JPS4997970A (enrdf_load_stackoverflow)
AU (1) AU474431B2 (enrdf_load_stackoverflow)
BR (1) BR7310300D0 (enrdf_load_stackoverflow)
CA (1) CA997618A (enrdf_load_stackoverflow)
DE (1) DE2363652A1 (enrdf_load_stackoverflow)
FR (1) FR2322729A3 (enrdf_load_stackoverflow)
GB (1) GB1426938A (enrdf_load_stackoverflow)
ZA (1) ZA738133B (enrdf_load_stackoverflow)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3869241A (en) * 1973-01-11 1975-03-04 Commissariat Energie Atomique Device for rapid closure and pressurization of a compression chamber
US4009977A (en) * 1976-04-29 1977-03-01 United States Steel Corporation Apparatus for the triaxial compression of particulate material
US4046499A (en) * 1973-08-16 1977-09-06 Shinagawa Firebrick Co., Ltd. Dry rubber compression molding apparatus
US4060359A (en) * 1976-06-10 1977-11-29 Ab Carbox Isostatic press
US4118161A (en) * 1975-06-12 1978-10-03 Kennametal Inc. High temperature, high pressure apparatus having a ductile driver element
US4374787A (en) * 1979-08-10 1983-02-22 British Nuclear Fuels Limited Pressing ceramic powders
US5160677A (en) * 1989-12-15 1992-11-03 United States Surgical Corporation Pressurized powder support for treating processes
US5160678A (en) * 1989-12-15 1992-11-03 United States Surgical Corporation Pressurized powder support for treating processes
US5606231A (en) * 1993-12-04 1997-02-25 Netter Gmbh Vibrating table for masses to be compacted and a vibratory method of compaction for the compaction of concrete
US5678166A (en) * 1990-06-08 1997-10-14 Henry R. Piehler Hot triaxial compaction
US20030091676A1 (en) * 2001-04-23 2003-05-15 Warren Dwight F. Sample mounting press
US20050142023A1 (en) * 2003-12-24 2005-06-30 Voice Wayne E. Apparatus and a method of manufacturing an article by consolidating powder material
WO2021236507A1 (en) * 2020-05-18 2021-11-25 The Regents Of The University Of California Structural composite materials, processes, and systems
US11782416B2 (en) 2020-05-11 2023-10-10 General Electric Company Compensation for additive manufacturing
CN120307542A (zh) * 2025-06-12 2025-07-15 醴陵市浦口电瓷制造有限公司 协同加压结构、自修复热压装置及高压绝缘子成型工艺

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2544743B1 (fr) * 1983-04-21 1985-07-12 Vauciennes Ste Sucriere Agrico Procede et dispositif de fabrication de sucres agglomeres
JPS61150798A (ja) * 1984-12-26 1986-07-09 Japan Steel Works Ltd:The 冷間静水圧減圧装置
DE102005045976A1 (de) * 2005-09-27 2007-03-29 Dorst Technologies Gmbh & Co. Kg Pressenvorrichtung bzw. Pressverfahren zum isostatischen Pressen eines Körpers
JP2016097607A (ja) * 2014-11-25 2016-05-30 株式会社日本製鋼所 樹脂成形体の成形方法
CN117920999B (zh) * 2024-03-25 2024-05-24 烟台东一粉末冶金制造有限公司 一种粉末冶金转向助力油泵定子的制备装置及其使用方法

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US2648125A (en) * 1947-08-06 1953-08-11 Kennametal Inc Process for the explosive pressing of powdered compositions
US3044113A (en) * 1959-01-08 1962-07-17 Engineering Supervision Compan Super-high pressure apparatus
US3093862A (en) * 1961-05-24 1963-06-18 Barogenics Inc Compact hydrostatic pressure apparatus
US3118177A (en) * 1960-06-20 1964-01-21 Asea Ab Autoclave
US3123862A (en) * 1964-03-10 Ultra-fflgh pressure device
US3193900A (en) * 1963-09-30 1965-07-13 Pacific Clay Products Apparatus for manufacturing clay pipe
US3593373A (en) * 1968-09-26 1971-07-20 David G Loomis Molding apparatus
US3613157A (en) * 1968-03-11 1971-10-19 Asea Ab Pressure chamber for treating material with high pressure,such as isostatic compression of powder bodies
US3664801A (en) * 1969-05-23 1972-05-23 France Etat Apparatus for developing high fluid pressure
US3761574A (en) * 1972-03-24 1973-09-25 Autoclane Engineers Inc Isostatic clamp press

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3123862A (en) * 1964-03-10 Ultra-fflgh pressure device
US2648125A (en) * 1947-08-06 1953-08-11 Kennametal Inc Process for the explosive pressing of powdered compositions
US3044113A (en) * 1959-01-08 1962-07-17 Engineering Supervision Compan Super-high pressure apparatus
US3118177A (en) * 1960-06-20 1964-01-21 Asea Ab Autoclave
US3093862A (en) * 1961-05-24 1963-06-18 Barogenics Inc Compact hydrostatic pressure apparatus
US3193900A (en) * 1963-09-30 1965-07-13 Pacific Clay Products Apparatus for manufacturing clay pipe
US3613157A (en) * 1968-03-11 1971-10-19 Asea Ab Pressure chamber for treating material with high pressure,such as isostatic compression of powder bodies
US3593373A (en) * 1968-09-26 1971-07-20 David G Loomis Molding apparatus
US3664801A (en) * 1969-05-23 1972-05-23 France Etat Apparatus for developing high fluid pressure
US3761574A (en) * 1972-03-24 1973-09-25 Autoclane Engineers Inc Isostatic clamp press

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3869241A (en) * 1973-01-11 1975-03-04 Commissariat Energie Atomique Device for rapid closure and pressurization of a compression chamber
US4046499A (en) * 1973-08-16 1977-09-06 Shinagawa Firebrick Co., Ltd. Dry rubber compression molding apparatus
US4118161A (en) * 1975-06-12 1978-10-03 Kennametal Inc. High temperature, high pressure apparatus having a ductile driver element
US4009977A (en) * 1976-04-29 1977-03-01 United States Steel Corporation Apparatus for the triaxial compression of particulate material
US4060359A (en) * 1976-06-10 1977-11-29 Ab Carbox Isostatic press
US4374787A (en) * 1979-08-10 1983-02-22 British Nuclear Fuels Limited Pressing ceramic powders
US5160677A (en) * 1989-12-15 1992-11-03 United States Surgical Corporation Pressurized powder support for treating processes
US5160678A (en) * 1989-12-15 1992-11-03 United States Surgical Corporation Pressurized powder support for treating processes
US5678166A (en) * 1990-06-08 1997-10-14 Henry R. Piehler Hot triaxial compaction
US5606231A (en) * 1993-12-04 1997-02-25 Netter Gmbh Vibrating table for masses to be compacted and a vibratory method of compaction for the compaction of concrete
US20030091676A1 (en) * 2001-04-23 2003-05-15 Warren Dwight F. Sample mounting press
US7404707B2 (en) * 2001-04-23 2008-07-29 Leco Corporation Sample mounting press
US20050142023A1 (en) * 2003-12-24 2005-06-30 Voice Wayne E. Apparatus and a method of manufacturing an article by consolidating powder material
US11782416B2 (en) 2020-05-11 2023-10-10 General Electric Company Compensation for additive manufacturing
WO2021236507A1 (en) * 2020-05-18 2021-11-25 The Regents Of The University Of California Structural composite materials, processes, and systems
US20230278263A1 (en) * 2020-05-18 2023-09-07 The Regents Of The University Of California Structural composite materials, processes, and systems
CN120307542A (zh) * 2025-06-12 2025-07-15 醴陵市浦口电瓷制造有限公司 协同加压结构、自修复热压装置及高压绝缘子成型工艺

Also Published As

Publication number Publication date
JPS4997970A (enrdf_load_stackoverflow) 1974-09-17
ZA738133B (en) 1975-05-28
FR2322729A3 (fr) 1977-04-01
GB1426938A (en) 1976-03-03
AU6376273A (en) 1975-06-19
DE2363652A1 (de) 1974-07-25
BR7310300D0 (pt) 1974-08-29
AU474431B2 (en) 1976-07-22
CA997618A (en) 1976-09-28

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