US3548625A - Collapsible feed mechanism - Google Patents

Collapsible feed mechanism Download PDF

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Publication number
US3548625A
US3548625A US651292A US3548625DA US3548625A US 3548625 A US3548625 A US 3548625A US 651292 A US651292 A US 651292A US 3548625D A US3548625D A US 3548625DA US 3548625 A US3548625 A US 3548625A
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US
United States
Prior art keywords
aligning
drive plate
plate
feed mechanism
die
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
US651292A
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English (en)
Inventor
Francis Joseph Fuchs Jr
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.)
AT&T Corp
Original Assignee
Western Electric Co Inc
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Publication date
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Publication of US3548625A publication Critical patent/US3548625A/en
Assigned to AT & T TECHNOLOGIES, INC., reassignment AT & T TECHNOLOGIES, INC., CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). EFFECTIVE JAN. 3,1984 Assignors: WESTERN ELECTRIC COMPANY, INCORPORATED
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C23/00—Extruding metal; Impact extrusion
    • B21C23/007—Hydrostatic extrusion
    • B21C23/008—Continuous extrusion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C23/00—Extruding metal; Impact extrusion
    • B21C23/02—Making uncoated products
    • B21C23/20—Making uncoated products by backward extrusion
    • B21C23/205—Making products of generally elongated shape
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C23/00—Extruding metal; Impact extrusion
    • B21C23/21—Presses specially adapted for extruding metal
    • B21C23/218—Indirect extrusion presses

Definitions

  • This disclosure is directed to a collapsible feed mechanism for advancing and retracting a rod or rod-like member, and in particular a slender column, which may be subjected to large compressive axial loads.
  • the collapsible feed mechanism disclosed herein comprises a plurality of aligning plates and a drive plate all slidably mounted within a support cage.
  • Power cylinders connected to the drive plate by piston rods, advance and retract the rod, or slender column, which is also connected to the drive plate.
  • the aligning plates and drive plate cooperate to centrally position, advance and retract the rod or slender column, e.'g. an extrusion die ram, without bending or buckling the column, even when subjected to large compressive axial loads, e.g. the force of extrusion necessary to advance the die ram upwardly of a billet conned in a high pressure vessel, to extrude the billet into wire.
  • long, slender rods having a length to least radius of gyration ratio in excess of 80 to 1, are particularly susceptible to bending and buckling when subjected to large axially directed, compressive loads. These rods are known as long and slender columns.
  • the concept of long and slender columns is treated in Engineering Design, Joseph H. Faupel, published by John Wiley & Sons Inc. in 1964. Accordingly, it will be understood that the shortened expression slender column, as will be used in this specir cation and the appended claims, is used in this context.
  • the susceptibility of rods in general, and slender co1- umns in particular, to bending and buckling not only limits the capability of the rod or column to support axially directed compressive loads, but also causes misalignment and bending difficulties when it is necessary to pass a rod or slender column axially through one or more aligned orifices.
  • the extrusion of wire from a billet being subjected to high hydrostatic pressure in a uid tight pressure vessel wherein the extrusion is accomplished by advancing a ram-mounted die upwardly of the billet into a bore in the vessel, ordinarily requires the use of a hollow die ram which is a rod, or rod-like member, categorizable as a slender colu-mn.
  • the forces of extrusion are relatively high, thus increasing the likelihood of bending or buckling.
  • the alignment of the die ram with the pressure vessel bore is very important in order to preclude binding which might interfere with advancement of the die at a constant or controlled rate.
  • apparatus for advancing a rod-like member which apparatus includes driving means for transmitting advancement forces to the rod-like member to advance the member, support means for supporting and positioning the driving means co-axially with respect to the rod-like member during advancement thereof, alignment means supported and positioned co-axially of the rod-like member by the support means and for radially supporting the rod-like member during the advancement thereof, and the alignment means comprising at least one plate member axially displaceable in response to the advancement of the driving means.
  • FIG. 1 is a longitudinal view, partly in cross-section, of a collapsible feed mechanism according to the present invention
  • FIG. 2 is a longitudinal view of the collapsible feed mechanism similar to that of FIG. 1, but showing the mechanism partially advanced;
  • FIG. 3 is a fragmentary view of the collapsible feed mechanism, similar to those of FIGS. 1 and 2, and showing the rod or slender column in the fully advanced position;
  • FIG. 4 is a cross-sectional view through the plane 4-4 of FIG. l;
  • FIG. 5 is a cross-sectional view of FIG. 1;
  • FIG. 6 is a cross-sectional view through the plane 6-6 of FIG. 5, showing a locking mechanism suitable for use with the collapsible feed mechanism of the present invention.
  • a collapsible feed mechanism according to the present invention is designated generally by the reference numeral 10.
  • the collapsible feed mechanism 10 is shown being utilized with an extrusion apparatus to advance a die ram 12 to extrude a billet 14 into wire; the die ram being definable as a slender column since its ratio of length to least radius of gyration is well in excess of to 1.
  • the billet 14 is contained in a high pressure vessel 16 and may be subjected therein to a high hydrostatic pressure sufficiently great to cause the billet to increase in ductility so as to be deformable without fracture.
  • collapsible feed mechanism 10 comprises a stationary cage 11 having a series of reciprocably movable elements mounted therein.
  • the feed mechanism may be supported in any suitable manner, such as by mounting on a base or by insertion in a cylindrical support.
  • the mode of support of the feed mechanism 10 is not critical to a complete understanding of the present invention, and in the interest of drawing clarity, no support structure has been shown. It is to be understood, however, that in typical use, the feed mechanism 10 is suitably supported.
  • the collapsible feed mechanism 10 includes a plurality of spaced Co-axial rings 26 mounted in slots 27 formed in longitudinally extending rails 28.
  • the inner portions 29 of the rails cooperate to define tracks along which a plurality of aligning plates 30, 31 and 32, and a drive plate 33, slidably reciprocate.
  • the tracks defined by rails 28 position the plates 30 through 33 along a common central axis, which axis corresponds to the longitudinal axis of the die ram 12.
  • the aligning plates 30, 31 and 32, and drive plate 33 are each a circular plate having a plurality of symmetrically disposed, radially extending, generally rectangular notches 35 formed around the periphery thereof for slidably reeciving the inner portions 29 of rails 28.
  • Each aligning plate 30, 31, 32 (as shown in FIG.
  • aligning plate 31 is provided with a centrally formed aperture 34 for slidably receiving the die ram 12 therethrough.
  • Drive plate 33 is also provided with a centrally formed aperture 38, however aperture 38 is smaller in diameter than apertures 34, being only large enough to allow the free passage of the extruded product 20 therethrough.
  • the drive plate 33, as well as aligning plates 30, 31, 32, are all provided with a plurality of radially disposed axially extending holes, the purpose of which will be set forth fully hereinafter.
  • driving rods 40 one from each power cylinder 22, extend slidably through apertures 41 provided in aligning plates 30, 31, 32.
  • the free ends of rods 40 are threadedly secured to the drive plate 33 for positioning plate 33 generally perpendicularly to the longitudinal axis of die ram 12 and for transmitting driving motion directly, and solely, to the drive plate 33 for both the advancement and retraction thereof; the rods 40 transmitting no motion directly to the aligning plates.
  • the drive plate 33 is secured, such as by bolts, 37, to a shoulder 39 formed on the butt end of die rarn 12 and the drive plate transmits advancement and retraction motion directly to the die ram 12.
  • the aforementioned centrally disposed aperture 38 formed in drive plate 33 is in axial alignment with a central passageway 42 (FIG. 1) provided longitudinally through die ram 12 to accommodate the discharge of extrusion product 20.
  • Three longitudinally disposed headed bolts 51 (only two shown in FIGS. l and 2 for clarity) are slidably received within apertures 61 (FIG. 4) provided in the drive plate 33, and are threadedly secured to the aligning plate 32.
  • the heads 71 of the bolts 51 are larger than the apertures 61, and accordingly, when the feed mechanism is in its fully extended position as shown in FIG. 1, the bolt heads 71 are in engagement with the outer surface of the drive plate 33 in the manner shown in FIG. l.
  • three longitudinally disposed headed bolts 52 are slidably received within apertures 62 (FIG. l) provided in the aligning plate 32, and are threadedly secured to the aligning plate 31.
  • the heads 72 of the bolts 52 are larger than the apertures 62, and engage the outer surface of the aligning plate 32 when the collapsible feed mechanism 24 is extended to at least the position shown in FIG. 2.
  • three longitudinally disposed headed bolts 53 having heads 73 shown in broken line in FIG. 1) structurally interrelate aligning plates 30 and 31 in the same manner as described above with respect to bolts 51, 52, and plates 33, 32 and 31, respectively.
  • Drive plate 33 as shown in FIG. 4, is provided with a plurality of radially disposed apertures 55 of a diameter suiciently large to accommodate the unobstructed passage therethrough of bolt heads 72 and 73 when the drive plate has been advanced to the position shown in FIG. 3.
  • aligning plate 32 is provided with oversized apertures (not shown) for accommodating the passage therethrough of bolt heads 73 as the feed mechanism 24 is collapsed.
  • a counterbore 36 is provided in aligning plate 32 for receiving die ram shoulder 39 therein when the mechanism is collapsed as shown in FIG. 3.
  • aligning plates 30, 31 and 32 The function of aligning plates 30, 31 and 32 is twofold, to maintain the die ram 12 in close centerline alignment with the central bore of high pressure vessel 16, and to provide radial support to the die ram 12 during extrusion when it is subjected to particularly heavy compressive axial loads, so as to preclude bending or buckling which would render the mechanism effectively inoperable.
  • aligning plates 30, 31 and 32 a-re uniformly spaced longitudinally of the die ram 12 in the initial positions as shown in FIG. 1, and are maintained in this uniform spacing during advancement of the die ram 12 until they are successively positively displaced by the forward movement of the advancing drive plate 33.
  • each aligning plate 30, 31, 32 is provided with a cam latch assembly designated generally by the reference numeral 80, and shown in FIGS. 5 and 6, particularly FIG. 6.
  • the cam latch assemblies are mounted peripherally of the aligning plates 30, 31, 32, each latch being angularly displaced with respect to the others, around the longitudinal center line of die ram 12.
  • Each cam latch assembly cooperates individually with a single notch 84 formed in the surface 29 of a separate rail 28, no one rail being provided with more than one notch.
  • a representative cam latch assembly is mounted in a suitable recess 81 formed in one of the respective aligning plates.
  • a plunger 82 is biased upwardly by a coil spring 90, and extends upwardly through an aperture 83 beyond the periphery of the aligning plate so as to be engageable with a notch 84 formed in the surface 29 of a rail 28.
  • Plunger 82 is provided with beveled surfaces 85 which dene cam surfaces for cooperative engagement with the complementarily shaped cam surfaces 86 of the notch 84.
  • a generally V-shaped rocker arm 87 pivotally mounted on a pin 93 within the recess 81, is biased for clockwise rotation around pin 93 by bias spring 91.
  • a plunger engaging portion 89 maintains plunger 82 in its upwardly extended, notch engaging position. Further, when the plunger engaging portion 89 is so positioned, plate engaging portion 88 extends outwardly past the surface plane of the associated alignment plate, so that when the drive mechanism is being collapsed by the advancement of drive plate 33, the plate engaging portion 88 will be engaged by the next preceding aligning or drive plate, as appropriate, and such engagement will cause the rocker arm to pivot counterclockwise, as shown in FIG. 6, and into the position shown by the broken lines. Plunger engaging portion 89, therefore, will be pivoted out of engagement with plunger 82 thus allowing the plunger to be cammed inwardly, out of engagement with notch 84.
  • the rail cam surface 86 as best seen in FIG. 6, and the plunger cam surface 85, will, cooperatively, cam the plunger 82 downwardly against the action of the compression spring 90, thus allowing unobstructed axial displacement of aligning plate 32 with drive plate 33.
  • aligning plate 32 As aligning plate 32 is advanced continuously to the left with drive plate 33 and the die ram 12, it engages the rocker arm 87 of the *cam latch assembly 80 mounted in aligning plate 31, and unlocks aligning plate 31 in the same manner as discussed above with respect to aligning plate 32. Thereafter, aligning plate 31 advances to the left lwith drive plate 33, aligning plate 32 and die ram 12, and in the same manner as described before with respect to the other plates, unlatches and engages aligning plate 30 for advancement toward billet containing vessel 16. lUpon completion of the full advance of the die ram 12, the feed mechanism is fully collapsed, and the aligning plates, drive plate, and die ram occupy the positions shown in FIG. 3.
  • the drive plate 33 transmits solely axially directed force to the die ram ⁇ 12, of sufficient magnitude to advance the die 18 upwardly of the billet 14 to cause extrusion and production of wire 20. Further, it can be seen that spaced lateral or radial support for the die ram 12 is provided at all times by the aligning plates 30, 31 and 32. It will also be understood that the die ram is maintained in close center line alignment with the bore of pressure vessel 16 and billet 14, so as to preclude the ram from ram bending or buckling.
  • pressurized uid is suitably admitted to power cylinders 12 to force rods 40, and therewith drive plate 33, to the right as viewed in FIGS. 1-3, thus retracting the feed mechanism for a subsequent extrusion cycle.
  • Retraction of drive plate 33 causes the retraction and positioning of alignment plates 30, 31 and 32 by lost motion linkage comprised of the headed bolts
  • aligning plate 32 and, in turn, aligning plate 31 in cooperation with bolts 53 will pick up aligning plate 30.
  • the drive plate is retracted by the driving rods 40 and the lost motion linkage between drive plate 33 and aligning plates 31, 32, 33, Which linkage is defined by the headed bolts 51, 52 and 53 and the apertures ⁇ 62, transmits the retractive force successively to said aligning plates.
  • the present invention provides a collapsible feed mechanism wherein a rod or slender column, in the disclosed apparatus a die ram, can be advanced and retracted under virtually any load condition without bowing the column and with complete control of center line alignment at all times. It will also be appreciated that there is substantially no limit to the length of column to be accommodated since longer columns will require only the addition of more aligning plates and a substitution of longer cage rails.
  • collapsible feed mechanism is primarily useful with rods, and in particular slender columns, it is fully appropriate for use in any situation wherein it is desired to advance a rod or rod-like member of any type.
  • an extruding apparatus including a die ram adapted for extruding billets, a collapsible feed mechanism for advancing said die ram, said feed mechanism comprising:
  • said alignment means comprising at least one plate member axially dispaceable in response to the advancement of said driving means.
  • a billet container and a die ram adapted for advancement into and retraction from the billet container and for extruding billets, a collapsible feed mechanism for advancing, retracting and guiding said die ram, said feed mechanism comprising:
  • a drive plate for advancing and retracting said die ram, said ram drive plate being secured to driving rods extending from said power cylinders;
  • said means for axially positioning said alignment means comprises lost motion linkage and a plurality of cam latch assemblies.
  • said alignment means comprises a plurality of alignment plates slidably mounted 0n said rail elements.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Extrusion Of Metal (AREA)
  • Press-Shaping Or Shaping Using Conveyers (AREA)
US651292A 1967-07-05 1967-07-05 Collapsible feed mechanism Expired - Lifetime US3548625A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US65129267A 1967-07-05 1967-07-05

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US3548625A true US3548625A (en) 1970-12-22

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US651292A Expired - Lifetime US3548625A (en) 1967-07-05 1967-07-05 Collapsible feed mechanism

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US (1) US3548625A (xx)
BE (1) BE717658A (xx)
DE (1) DE1752698C3 (xx)
FR (1) FR1582164A (xx)
GB (1) GB1226986A (xx)
SE (1) SE354426B (xx)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3735623A (en) * 1970-11-16 1973-05-29 Texas Aluminum Co Indirect extrusion die assembly and method of extruding
US3852986A (en) * 1973-03-08 1974-12-10 Western Electric Co High pressure billet extruder
US4319476A (en) * 1978-07-19 1982-03-16 Western Electric Company, Incorporated Methods and apparatus for extrusion

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1227837B (it) * 1988-11-21 1991-05-08 Cucchi Giovanni & C Srl Alimentatore per barre.

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3181328A (en) * 1962-11-09 1965-05-04 Barogenics Inc Shock aided extrusion
FR1440859A (fr) * 1964-04-23 1966-06-03 Metal Flo Corp Presse pour l'étirage profond des métaux
US3431825A (en) * 1965-10-13 1969-03-11 Vickers Ltd High pressure device

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3181328A (en) * 1962-11-09 1965-05-04 Barogenics Inc Shock aided extrusion
FR1440859A (fr) * 1964-04-23 1966-06-03 Metal Flo Corp Presse pour l'étirage profond des métaux
US3431825A (en) * 1965-10-13 1969-03-11 Vickers Ltd High pressure device

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3735623A (en) * 1970-11-16 1973-05-29 Texas Aluminum Co Indirect extrusion die assembly and method of extruding
US3852986A (en) * 1973-03-08 1974-12-10 Western Electric Co High pressure billet extruder
US4319476A (en) * 1978-07-19 1982-03-16 Western Electric Company, Incorporated Methods and apparatus for extrusion

Also Published As

Publication number Publication date
DE1752698A1 (de) 1971-09-09
DE1752698B2 (de) 1976-10-28
GB1226986A (xx) 1971-03-31
FR1582164A (xx) 1969-09-26
SE354426B (xx) 1973-03-12
BE717658A (xx) 1968-12-16
DE1752698C3 (de) 1978-06-01

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Owner name: AT & T TECHNOLOGIES, INC.,

Free format text: CHANGE OF NAME;ASSIGNOR:WESTERN ELECTRIC COMPANY, INCORPORATED;REEL/FRAME:004251/0868

Effective date: 19831229