WO1981000687A1 - Procede et appareil de cisaillement de barres billettes et autres lopins de forme allongees - Google Patents

Procede et appareil de cisaillement de barres billettes et autres lopins de forme allongees Download PDF

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Publication number
WO1981000687A1
WO1981000687A1 PCT/US1980/001177 US8001177W WO8100687A1 WO 1981000687 A1 WO1981000687 A1 WO 1981000687A1 US 8001177 W US8001177 W US 8001177W WO 8100687 A1 WO8100687 A1 WO 8100687A1
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WO
WIPO (PCT)
Prior art keywords
bar
clamp
force
infeed
relative
Prior art date
Application number
PCT/US1980/001177
Other languages
English (en)
Inventor
J Lazar
B Shvartsman
Original Assignee
Slugger Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Slugger Corp filed Critical Slugger Corp
Publication of WO1981000687A1 publication Critical patent/WO1981000687A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D23/00—Machines or devices for shearing or cutting profiled stock
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D33/00—Accessories for shearing machines or shearing devices
    • B23D33/08—Press-pads; Counter-bases; Hold-down devices

Definitions

  • Machines have been developed for hydraulically shearing bar stock and examples of such machines are described in the U.S. Patent No. 3,908,496 to Moelbert and the U.S. Patent No. 3,972,257 to Lazar, Jr. These machines are of the hydraulically operated type which include at least one main hydraulic ram for moving one portion of the bar relative to a clamped portion of the bar to effect a shearing of the bar.
  • a bar shearing machine a first portion is clamped and restrained against movement while a moving member is forced against a second portion of the bar adjacent the first clamped portion to cause the bar to rupture and be sheared.
  • relatively large diameter bars With relatively large diameter bars
  • the shearing force is considerable.
  • Reduction of bending in the portion of the bar to be sheared off would also reduce the crushing effect at the shear plane. This can reduce the production scrappage rate.
  • a reduction in the crush of the bar at the shear plane can also reduce the number of stress riser concentration points. This would be desirable because such stress riser concentration points can serve as propagations points for cracking or failure in the bar when the bar is subsequently treated (e.g., heated or forged) or used.
  • the shearing mechanisms are retained within a housing.
  • the reaction forces from the bar and from the shearing dies or blades are transferred to the housing.
  • stresses on the housing connections and bolts can be considerable. Therefore, it would be desirable to provide a housing which would eliminate or reduce such resulting stresses on the bolts employed in the structure and which would transfer the large reaction forces of the bar bending load to substantial structural members capable of withstanding such forces.
  • bars to be sheared are not completely regular in cross section along their length. Consequently, difficulty can be encountered in firmly clamping a bar on the infeed side of the machine and in restraining the bar against movement while a portion is sheared off. Also, in bar stock shearing machines, the bars are typically fed in end-to-end fashion with the end of one bar abutting the end of the next upstream bar. If a first bar is of one size and the second bar is of another size, difficulty in clamping the bars where they abut can be encountered.
  • a novel housing construction is provided for reducing or eliminating the shearing load-induced stresses on welded and bolted connections.
  • the machine has first and second end bolsters, a center bolster, and a main hydraulic cylinder positioned between the first end bolster and the center bolster.
  • a retainer plate housing is positioned between the center bolster and second end bolster.
  • Four tie rods securely join all three bolsters and maintain the hydraulic cylinder, bolsters, and retainer plate housing in a fixed position. The tie rods are stressed after assembly thus holding the entire assembly under a relatively high compressive load.
  • a fixed or infeed die assembly and a movable die assembly adapted to receive a bar are disposed in the housing between the center bolster and the second end bolster.
  • the movable die assembly is adapted to be moved relative to the fixed die assembly by the main hydraulic cylinder between the center and second end bolsters to shear the bar.
  • the fixed and movable die assemblies are generally retained within the housing formed by a plurality of retainer plates extending between the center bolster and the second end bolster.
  • the housing defines the die receiving cavity and restrains the die assemblies against movement that would result from the reaction forces generated during the shearing of the bar.
  • Each retainer plate has two ends with one end being adjacent the center bolster and with the other end being adjacent the second end bolster.
  • each retainer plate defines therein at least one key cavity.
  • the center bolster and second end bolster each define therein key cavities in alignment with and facing the key cavities of the retainer plates.
  • a plurality of key members are provided with each key member being inserted and interfitted partially in a retainer plate key cavity and partially in an aligned bolster key cavity thereby providing an interlocking construction retained by the stressed tie rods. This eliminates bolts and welds that are necessary to join the confining members in conventional machines.
  • the interfitted keys and key cavities thus form the only joints within the retainer plate and bolster assembly defining the die housing and serve to bear the component forces normal to the direction of movement of the movable die assembly which result from the shearing of the bar.
  • the fixed or infeed die assembly is provided with a novel construction to accommodate the variation in cross section along the length of a bar.
  • a guideway is provided through the bar stock shear machine for receiving bars in end-to-end alignment.
  • the infeed die assembly includes a stationary die or clamp which defines a part of the guideway and is adapted to engage a first surface region of at least one bar.
  • the infeed die assembly also includes a movable infeed clamp assembly on the other side of the guideway opposite the stationary die.
  • the infeed clamp assembly is adapted to move between a retracted position providing clearance for the bar in the guideway opposite the stationary die and an extended position to engage a second surface region of the bar generally opposite the first surface region.
  • the movable infeed clamp assembly includes a support block and an infeed clamp.
  • the support block has a partially cylindrical concave bearing surface and the infeed clamp has a partially cylindrical convex bearing surface received on the support block concave bearing surface.
  • the infeed clamp is thus freely pivotable relative to the support block.
  • the infeed clamp has an engaging face adapted to be oriented at an angle relative to the longitudinal axes of the bars when the infeed clamp is pivoted on the support block.
  • a hydraulic cylinder actuated wedge i ⁇ provided to be moved relative to and against the support block to cause the infeed clamp assembly to move from the retracted position towards and against at least one of the bars.
  • the infeed clamp engaging face can thus be forced against the second surface region of the bar to force the first surface region of the bar against the stationary die.
  • the infeed clamp can pivot on the support block, in response to the reaction forces transmitted to the infeed clamp from the regions of contact with the bar, to orient the infeed clamp at an angle relative to the longitudinal axis of the bar and in contact with the bar in at least two longitudinally spaced-apart regions along the bar.
  • a bar having a variation in cross section along its length can be more easily clamped.
  • the infeed clamp is forced against the bar, the larger cross-sectional area portion of the bar will be contacted first by the infeed clamp.
  • the clamp will swivel or pivot on the support block until another portion of the clamp engages a smaller cross-sectional area region of the bar.
  • at least two points of contact can be obtained.
  • the clamp would similarly pivot as necessary to provide at least a two point contact orientation.
  • a novel method for shearing a bar with a reduction in the bending of the portion of the bar to be sheared off. Specifically, a first portion of the bar is initially clamped and restrained against movement by the above-described infeed die assembly.
  • a movable force transmitting means or load bearing cage is provided for engaging at least first and second generally opposite surface regions of a second portion of the bar adjacent the clamped first portion.
  • the bar is engaged on the first surface region of the second portion with the force-transmitting means and a first force is applied against the first surface region generally normal to the longitudinal axis of the bar while simultaneously the resulting reaction force is transmitted through the force-transmitting means to the bar on the second surface region of the second portion of the bar.
  • the first force and the reaction force are thus exerted in opposing directions on the first and second surface regions, respectively, along the second portion of the bar generally perpendicular to the longitudinal axis of the bar to prevent bending of the second portion of the bar about the longitudinal axis of the bar relative to the first portion of the bar .
  • a second force is then applied to the load bearing cage in a direction normal to the longitudinal axis of the bar sufficient to move the cage engaged with the second portion of the bar relative to the clamped first portion of the bar thereby shearing the bar without substantially bending the second portion of the bar relative to the first portion of the bar.
  • the force-transmitting means or cage is a rectangular frame defining an interior guideway.
  • a backing clamp is carried by, and slidably movable relative to, the cage frame.
  • a hydraulic cylinder-actuated wedge is provided to slide against the backing clamp and move the clamp initially against the first surface region of the second portion of the bar.
  • the cage necessarily moves relative to the bar and to the clamp until the other end of the cage contacts the second surface region of the second portion of the bar. In this manner, the second portion of the bar is securely clamped and restrained against bending.
  • a main ram is provided for moving the entire cage relative to the clamped first portion of the bar to cause the second portion of the bar to be sheared from the first portion of the bar.
  • the quality of the shear is improved because the bending of the sheared-off portion of the bar is substantially reduced or eliminated during the shearing process.
  • the mechanical wedge engaging system that is employed to grip the portion of the bar to be sheared off and to prevent bending thereof provides a more positive restraint againstbending than in those types of bar shear machines wherein a main shearing member or clamp is moved against the bar and wherein an independently supported clamp or member is provided behind the bar to reduce the bending.
  • Figure 1A and 1B are diagrams illustrating a prior art method of shearing a bar in a bar stock shearing machine
  • Figure 1C is a diagram of a novel method of shearing a bar
  • Figure 2 is a fragmentary side view of the novel bar stock shear machine described herein;
  • Figure 3 is a fragmentary plan view of the top of the machine illustrated in Figure 2;
  • Figure 4 is an enlarged end view taken generally along the plane 4-4 in Figure 2;
  • Figure 5 is a fragmentary, cross-sectional view taken generally along the plane 5-5 in Figure 4;
  • Figure 6 is a fragmentary, cross-sectional view taken generally along the plane 6-6 in Figure 4;
  • Figure 7 is a perspective, exploded view of the retainer plate and die housing assembly with external and internal components, such as tie rods, wear plates and shear clamps, omitted for purposes of clarity;
  • Figure 8 is an enlarged, cross-sectional view taken generally along the plane 8-8 in Figure 2;
  • Figure 9 is an enlarged, fragmentary cross-sectional view taken generally along the plane 9-9 in Figure 2;
  • Figures 10A, 10B, and 10C are diagrams illustrating the novel method for clamping a bar or bars on the infeed side of a bar shearing machine
  • Figure 11 is a greatly enlarged, fragmentary, partial cross-sectional view taken generally along the plane 11-11 in Figure 2;
  • Figure 12 is a view similar to Figure 11 but showing the range of pivotal movement of the infeed clamping block in dashed lines;
  • Figure 13 is an enlarged, fragmentary, partial cross-sectional view similar to Figure 11;
  • Figure 14 is a fragmentary cross-sectional view taken generally along the plane 14-14 in Figure 13 showing the stationary infeed backing die insert and holder;
  • Figure 15 is a fragmentary cross-sectional view taken generally along the plane 15-15 in Figure 13 showing the movable shear die assembly insert and cage;
  • Figure 16 is an enlarged cross-sectional view taken generally along the plane 16-16 in Figure 15;
  • Figure 17 is an enlarged fragmentary, cross-sectional view taken generally along the plane 17-17 in Figure 15;
  • Figure 18 is a fragmentary cross-sectional view taken generally along the plane 18-18 in Figure 13;
  • Figure 19 located on the sheet with Figures 16 and 17, is an enlarged cross-sectional view taken generally along the plane 19-19 in Figure 18;
  • Figure 20 is a greatly enlarged, fragmentary side view similar to Figure 2, showing the infeed clamp assembly actuator mechanism located on the central portion of the machine;
  • Figure 21 is a fragmentary cross-sectional view taken generally along the plane 21-21 in Figure 20;
  • Figure 22 is an enlarged, fragmentary cross-sectional view taken generally along the plane 22-22 in Figure 20;
  • Figure 23 is a fragmentary cross-sectional view taken generally along the plane 23-23 in Figure 20;
  • Figure 24 is a fragmentary, cross-sectional view taken generally along the plane 24-24 in Figure 23;
  • Figure 25 located on the sheet with Figure 21, is a fragmentary, cross-sectional view taken generally along the plane 25-25 in Figure 23.
  • Description of the Preferred Embodiment This invention may be used in many different forms.
  • This specification and the accompanying drawings disclose only one specific form of novel methods and apparatus. The invention is not intended to be limited to the embodiments of the features illustrated and described, and the scope of the invention will be pointed out in the appended claims.
  • the bar shear apparatus has certain conventional mechanisms, the details of which, though not fully illustrated or described, will be apparent to those having skill in the art and an understanding of the necessary functions of such mechanisms.
  • FIGS. 1A and 1B diagrammatically illustrate a method of shearing bar stock as taught by the prior art.
  • a bar 50 is fed into the infeed side of a bar stock shearing machine and clamped or fixed against movement by means of clamps 52 and 54.
  • the clamps 52 and 54 are engaged with a first portion 56 of the bar from which a second portion 58 extends and which second portion 58 is to be sheared off.
  • a shear blade or die 60 is moved to engage one side of the second portion 58 of the bar 50.
  • the shear blade 60 may be moved against the bar by means of a conventional hydraulic cylinder-piston actuator 62.
  • a backing member or die clamp 64 is moved against the side of the bar opposite the shear blade 60.
  • Die 64 may be moved against the bar by means of a conventional hydraulic cylinder-piston actuator 66. It is to be noted that backing die 64 is operated independently of shearing die or blade 60. The force exerted by actuator 62 thus has to be great enough to overcome both the strength of the bar and the backing force of actuator 66 in order to rupture and shear the bar at the shear plane P between the two clamped bar portions 56 and 58.
  • the clamps 52 and 54 On the restrained portion 56 of the bar 50, the clamps 52 and 54, being restrained against all movement during the shearing operation, do not permit bending of the first portion of the bar 56. However, to the extent that there may be some "looseness" in the clamps 52 and 54, the reaction load on clamp 54 would be greatest at the outer end of clamp 54 as indicated by the load acting at arrow 80 and the reaction load on clamp 52 would be greatest on the end of the clamp 52 adjacent the shearing plane P as indicated by the arrow 82.
  • the concentration of loads at points 74 and 78 on the clamps 60 and 64, respectively, can cause rapid die wear.
  • the bending of the bar decreases the quality of the shear. The bending occurs until the ultimate shear strength of the bar is exceeded and until there is an actual displacement along the shear plane P.
  • the above described bending of a bar stock and the disadvantages associated with that bending can be substantially reduced, if not eliminated, with a novel method as illustrated in Figure 1C.
  • the bar 50 is restrained against movement on its first portion 56 by clamps 52 and 54. Adjacent these clamps 52 and 54, the second portion 58 of the bar is received in a movable force transmitting means, such as a cage or holder 90.
  • the cage 90 may be moved from a loading position (for receiving the bar 50) in a direction to shear the bar by a suitable actuator 62.
  • the cage 90 is adapted for engaging at least first and second generally opposite surface regions of the second portion 58 of the bar.
  • the cage 90 carries a clamp 92 and a means 94 for moving the clamp 92 against a first surface region of the second portion 58 of the bar.
  • the clamp moving means 94 may include a wedge 96 reciprocated by a hydraulic cylinder actuator 98 against an inclined surface 100 of the clamp 92.
  • a novel method is provided wherein the bar 50 is initially positioned with the first portion 56 clamped and restrained against movement and with its second portion received in the cage 90 which is initially aligned in a position for receiving the bar with clearance around the bar.
  • the clamp 92 is forced by wedge 96 against the first surface region of the second portion 58 of the bar.
  • the cage 90 moves relative to both the bar 50 and to the clamp 92 engaged with the bar 50 until the cage 90 becomes engaged with a second surface region of the second portion 58 of the bar opposite the clamp 92.
  • the second portion 58 of the bar is tightly and mechanically clamped so as to prevent or substantially reduce bending.
  • the actuator 62 is operated to move the entire cage assembly 90 as indicated by arrow 102 to move the bar second portion 58 perpendicular to the longitudinal axis of the bar to thereby shear the bar along the shear plane P. Since the second portion 58 of the bar is securely clamped, and since bending is thereby eliminated or substantially reduced, reaction forces are more uniformly distributed along the second portion 58 within the cage 90. Thus, concentrated loads, such as those illustrated in Figure 1B by arrows 74 and 78 for the prior art, are much reduced. Thus, the wear of the shearing mechanism is substantially reduced.
  • a preferred embodiment of a bar stock shearing machine for effecting the method described above is designated generally by numeral 103 in
  • the bar stock shear includes a pair of end bolsters, first end bolster 110 and second end bolster 112, and a center bolster 114 forming major structural elements of the unit. Interposed between the first end bolster 110 and the center bolster 114 is a hydraulic cylinder 116. Similarly, interposed between center bolster 114 and second end bolster 112 is a die housing assembly generally indicated at 118. Each bolster is apertured at its four corners and tie rods 121-124 are inserted through the respective apertures. The entire assembly is joined together by means such as nuts 126-133. The tie rods are preferably pre-stressed by heating them and tightening the nuts while the rods are hot. This procedure places the apparatus under a relatively high compressive load. The assembly may be supported on a continuous bed plate 136 and maintained at a convenient height by support legs 138.
  • An opening or guideway 140 is defined on the infeed side of the machine 108 as illustrated in Figure 2. Bar stock is inserted through the guideway as best illustrated in Figure 3 where a bar 50 is shown with a first portion 56 entering the infeed side of the machine and with a second portion 58 extending from the outfeed side of the machine.
  • the bars are automatically fed by suitable conventional mechanisms (not illustrated) in end-to-end relationship into the bar shear machine. Further, such mechanisms typically automatically feed a predetermined length of bar into the machine for shearing off predetermined lengths or slugs of the bar.
  • the particular feeding mechanism forms no part of the present invention and will not be described in detail.
  • mechanisms may be provided at the outfeed side of the bar shear for stacking, weighing, or conveying the sheared bar stock slugs to subsequent stations. Such outfeed mechanisms form no part of the present invention and will not be described.
  • the bar 50 is clamped or restrained against movement on the infeed side of the machine by mechanisms to be described in detail hereinafter.
  • the clamped bar is sheared by operation of the cylinder actuator 116 and a moving shear blade assembly in a manner to be described in more detail hereinafter.
  • the loads or reaction forces must be accommodated by the machine.
  • a novel die housing or retainer structure is incorporated in the machine as will next be described.
  • the die housing assembly 118 between bolsters 114 and 112 is configured so that the resulting loads and forces are transmitted directly to the bolsters without reliance upon bolted or welded joints.
  • the novel interlocking system of the die housing 118 can be seen in an exploded view.
  • the internal parts, such as the tie rods, shearing and retaining clamps, pistons, and wear plates, have all been omitted for purposes of clarity.
  • a plurality of retainer plates Disposed between the center bolster 114 and the second end bolster 112 are a plurality of retainer plates, namely a generally U-shaped retainer plate 144, an upper infeed side retainer plate 146 and an upper outfeed side retainer plate 148.
  • the bottom U-shaped retainer plate 144 is provided with bores 150 and 152 adapted to align with bores 154 and 156, respectively, in the second end bolster 112 and adapted to align also with bores 158 and 160, respectively, in the center bolster 114.
  • Bottom retainer plate bore 150 and the aligned bolster bores 158 and 154 accommodate tie rod 123 ( Figures 2 and 4).
  • Bottom retainer plate bore 152 and the aligned bolster bores 160 and 156 receive the tie rod 124 ( Figures 2 and 4).
  • the plate 144, as well as the other plates, may, if desired, comprise a plurality of suitably interlocked members.
  • Upper infeed side retainer plate 146 defines a bore 162 adapted to align with a bore 164 in second end bolster 112 and a bore 166 in center bolster 114 for receiving tie rod 122 (see Figures 2 and 4).
  • upper outfeed side retainer plate 148 defines a bore 168 adapted to be aligned with a bore 170 in second end bolster 112 and a bore 172 in center bolster 114 for receiving tie rod 121 (see Figures 2 and 4).
  • bottom retainer plate 144 defines three key cavities 174 on each end. That is, three key cavities 174 face the second end bolster 112 and three key cavities (not visible in Figure 7) face center bolster 114.
  • the center bolster 114 has similar key cavities 176 aligned with the facing key cavities of the bottom retainer plate 144.
  • second end bolster 112 is provided with key cavities (not visible in Figure 7) which are aligned with the facing key cavities 174 in the bottom retainer plate.
  • Key members 178 are provided to interfit in the key cavities with substantially one half of the thickness of each key member 178 extending into the bottom retainer plate 144 and one half of each key member extending into the respective center or end bolster. In this manner, the transverse loads which result from the shearing operation and are imposed by the shearing blades onto the bottom retainer plate can be transferred to the center and second end bolsters.
  • the upper infeed side retainer plate 146 is provided with a key cavity 180 at each end and the upper outfeed side retainer plate 148 is provided with a key cavity 182 at each end.
  • the center bolster 114 is provided with a pair of key cavities 184 aligned with and facing the key cavities in the upper retainer plates.
  • the second end bolster 112 is provided with key cavities (not visible in Figure 7) which are aligned with and face the key cavities 180 and 182 in the upper retainer plates.
  • Key members 186 are provided for joining the upper retainer plates 146 and 148 to the center bolster 114 and second end bolster 112 in the same manner in which the bottom retainer plate 144 is joined to the center bolster 114 and second end bolster 112.
  • the assembly With the key members properly interfitted in the retainer plates and bolsters, the assembly provides a secure housing for the internal clamps and dies with the interfitted key members and key cavities serving to bear the component forces normal to the direction of movement of the movable shear dies and blades operating within the housing as will be explained in detail hereinafter.
  • the assembled die housing is seen to have an opening accessible from the top of the machine between the upper retainer plates 146 and 148. This opening permits removal and installation of internal parts, including replaceable shear blades and die inserts to be described in detail hereinafter.
  • a novel method for clamping the bar from which a slug is to be sheared and for restraining it against movement as it is sheared.
  • An infeed clamping assembly for effecting this method is mounted partially within the above-described retaining plate housing on the infeed side of the machine 108.
  • the novel clamping assembly includes a backing or bar support clamp or die 196 and a movable infeed clamp 198, both being disposed within the opening defined between the bottom retaining plate 144 and the upper infeed side retaining plate 146 and defining therebetween them the aperture or guideway 140 into which the bars are fed.
  • the backing bar support die or clamp 196 is best illustrated in Figure 6 which shows the bar support clamp 196 slidibly supported on a support surface 200 of the bottom retainer plate 144.
  • the clamp 196 has a V-shaped notch defining a bar-engaging surface 197 and the clamp 196 can be moved on the support surface 200 towards or away from a bar within the guideway.
  • the position of clamp 196 is initially set and the clamp 196 is prevented from being moved by a bar by properly adjusting a ram 202 carried within channel 204 of the bottom retainer plate 144 ( Figure 7) .
  • the ram 202 is threadingly engaged with a rod 206 which projects through a bore 208 in the second end bolster 112 and which may be rotated from the back of the machine as necessary to move the ram 202 to the desired position.
  • the movable infeed clamp 198 which is omitted for clarity from Figure 6, is disposed between the upper infeed side retainer plate 146 and the bottom retainer plate 144 as best illustrated in Figure 23.
  • the bottom retainer plate 144 defines a channel 310 and the upper infeed side retainer plate 146 defines a channel 312 for receiving, respectively, guide keys 314 and 316 respectively.
  • Key 314 projects within a channel 318 in the bottom of the clamp 198 and key 316 projects within a channel 320 in the top of clamp 198.
  • a pair of plates, 322 and 324 are secured to the top of the infeed side of bottom bracket 144 to provide suitable sliding bearing surfaces.
  • Clamp 198 can thus be moved towards or away from the backing clamp 196 on the plates 322 and 324 to engage a bar disposed therebetween in the guideway. The mechanisms by which clamp 198 is thus moved will be described in detail hereinafter.
  • clamp 198 In order to accomodate cross section variation along the length of a bar, clamp 198 is supported so that it can pivot with respect to a vertical plane passing through the machine. Specifically, with reference to Figures 11, 12 and 13, the clamp 198 has a generally V-shaped clamping or engaging face 326 on one side and a partially cylindrical convex bearing surface 328 on the other side which is received in a partially cylindrical concave bearing surface 330 defined within a support block 332.
  • a spring 334 is disposed within aligned bores 336, 338, and 340 of center bolster 114, support block 332, and clamp 198, respectively, for holding the clamp 198 and support block 332 together and for biasing the assembly towards the center bolster 114.
  • spring 334 is secured to rod 342 at one end on center bolster 114 and to pin 344 at the other end in clamp 198.
  • Rod 342 is threadingly engaged with a collar 346 mounted to center bolster 114 so that the tension on the spring 334 may be varied by appropriate rotation of the collar 346 relative to rod 342.
  • the channel 320 in the top of clamp 198 is wider than the interfitted key 316 and that the channel 318 in the bottom of clamp 198 is wider than the interfitted key 314.
  • the clamp 198 can be rotated, relative to a vertical plane passing through the longitudinal axis of a bar to be clamped, as indicated in dashed lines in Figure 12. This rotation is accomodated by the partially cylindrical mating bearing surfaces 328 and 330 of the clamp 198 and support block 332, respectively.
  • the infeed clamp 198 extends towards the middle of the machine as illustrated in Figures 11, 13, 14, and 23. As best shown in Figures 14 and 23, the top and bottom of the clamp 198 is notched inside the machine at its upper and lower corners at 350 and 352, respectively.
  • the notches are slanted at 354 and 356 so that the clamp 198 fits within an aperture 360 of a stationary backing die holder assembly 366.
  • a second backing die or support clamp 370 Opposite the notched end of the movable clamp 198 is a second backing die or support clamp 370 which is supported within the die holder assembly 366 as best illustrated in Figure 14.
  • the die 370 has a partially circular configuration with a generally V-shaped cut out for providing an engaging face 372 opposite the engaging face 326 of movable infeed die 198.
  • the die 370 is retained within the holder 366 by locking pins 377 and 378 which pass through notches or channels in the top and bottom, respectively, of the die 370.
  • the pins 377 and 378 are retained within holder 366 by plugs 377a and 378a, respectively.
  • the entire holder 366 is secured within the machine with bolts 373-376 connecting the holder to the retainer plates 144 and 146.
  • the bolts are not subjected to any significant transverse shear stress since the portion of the force on the bar during shearing that is transmitted back to the holder 366 is transferred to the second end bolster 112.
  • the holder 366 can be easily removed from the machine by removing the bolts and then pulling it upwardly through the space between the upper infeed side retainer plate 146 and the upper outfeed side retainer plate 143. When the holder 366 is thus removed, the pins 377 and 378 may be removed to allow replacement of the backing clamp 370.
  • Figure 10A shows a bar 50' with a generally uniform cross section along its length.
  • the clamp 198 can float or pivot on the support block 330 to align its engaging face 326 in generally continuous contact with the bar 50'.
  • Figure 10B illustrates two bars of different sizes being clamped.
  • bar 50' has a larger cross section than bar 50''.
  • the bars are fed into the clamping assembly in end-to-end relationship.
  • the clamp 198 pivots on the support block 332 in response to the reaction forces transmitted to the clamp 198 from the regions of contact with the two bars.
  • This orients the infeed clamp 198 at an angle relative to the longitudinal axis of the bars and in contact with the bars in at least two longitudinally spaced-apart regions. In this manner, two points or lines of contact are created with a point of contact being made on each of the two bars.
  • this novel method of clamping two bars of different cross sectional area it is possible to shear each bar to relatively short lengths while still providing adequate infeed clamping capability.
  • Figure 10C illustrates the novel clamping assembly in operation with a bar 50''' which has a bump or bulge B.
  • the clamp 198 When the clamp 198 is brought against the bar 50''' in the region of the bulge, the clamp pivots on the block 332 to establish at least 2 point contact with the bar 50'''.
  • One region of contact is at the high point of the bulge B and the other region of contact is on the surface of the bar at a location spaced from the bulge B. This provides a better clamping action than prior art non-pivoting clamping assemblies.
  • the infeed clamping assembly is moved toward and forced against a bar to effect clamping thereof by a novel wedge drive system best illustrated in Figures 11 and 20-25.
  • the support block 332 is provided with two slanted surfaces 380 and 382 which are engaged by vertically reciprocable wedges 384 and 386, respectively.
  • wedges 384 and 386 are secured to rods 388 and 390' respectively.
  • the rods 388 and 390 are received in a mounting assembly 392 which is connected through piston rod 394 to a hydraulic cylinder actuator 396 supported from a frame structure 393.
  • assembly 392 is guided for its reciprocating movement by guide members 397 and 398 engaging either side of assembly 392.
  • the entire assembly 392 may thus be reciprocated by the actuator 396 to move the wedges 386 and 384 up and down relative to the support block 332.
  • the wedges 384 and 386 are restrained against lateral movement by exterior cover plate 387 and by internal guides 389.
  • the vertically reciprocable assembly 392 also carries a cross shaft 404 having a worm gear 406 engaged with gear 400 and a worm gear 408 engaged with gear 402.
  • Hand wheels 410 and 412 are mounted on opposite ends of the shaft 404 by which the shaft may be rotated to turn the gears 400 and 402. Since the gears 400 and 402 are threadingly engaged with the rods 388 and 390, respectively, the vertical position of the wedges 384 and 386 may be varied by operation of either of the hand wheels 410 or 412.
  • the initial elevation position of the wedges 384 and 386 is set by one of the hand wheels 410 or 412 to provide a maximum clearance for the size of the bar to be sheared.
  • operation of the machine includes the automatic actuation of cylinder actuator 396 to move the wedges downwardly to force the clamp 198 tightly against the bar.
  • a limit switch 416 ( Figure 24) with the control system for terminating the actuation of cylinder 396 before it has retracted the wedges to the full stroke height.
  • the limit switch 416 is preferably actuated by a finger element 418 carried by the assembly 392 as best illustrated in Figure 24.
  • a suitable sensing mechanism on the infeed conveyor can be provided to override the limit switch 416 so that the cylinder actuator 396 is permitted to operate through its full retraction stroke and thereby provide the maximum set clearance for admission of the new bar.
  • a movable force-transmitting means or load bearing holder or cage 430 is disposed adjacent the stationary backing die holder assembly 366 and within the housing defined by the retainer plates.
  • the cage 430 is a substantially right rectangular prism-shaped frame defining a central opening in which are disposed a bar backing clamp or die 436 and a shear blade 438.
  • the backing die 436 is adapted for sliding movement relative to the cage 430 toward and away from a bar to be sheared while shear blade 438 is retained so that it is prevented from moving relative to the cage 430.
  • Shear blade 438 has a substantially circular cross section with a V-shaped notch cut out defining a bar engaging face 440 and is retained within the cage 430 by bolts 442 and 444 which pass through notches in the top and bottom, respectively, of the shear blade 438.
  • the backing clamp or die 436 defines a V-shaped notch or bar engaging surface 446 on one side and a channel with a slanted bearing surface 448 on the other side.
  • the slanted bearing surface 448 is adapted to be engaged by a wedge 450 as best illustrated in Figures 17 and 18.
  • the wedge 450 is secured to a rod 454 connected to a cylinder actuator 456 mounted to the top of the cage 430.
  • the rod 454 and the upper portion of the wedge 450 are received between a pair of guide members 458 and 460 which project downwardly from the cylinder actuator 456 into a cavity 462 within the cage 430.
  • actuation of the cylinder 456 to move the wedge 450 downwardly forces the backing clamp 436 against the bar 50.
  • An appropriate cavity 464 is provided in the cage 430 below the wedge 450 to receive the projecting bottom portion of the wedge 450 as it is moved downwardly by the cylinder 456.
  • the backing clamp 436 is positioned sufficiently away from the shear blade 438 (to the right as viewed in Figure 18) to provide adequate clearance for an incoming bar.
  • the backing clamp 436 moves against the bar (to the left as viewed in Figure 18) and engages the bar.
  • backing clamp 436 is slidibly disposed within the cage 430 and the cage 430 is slidibly disposed within the die housing (on wear plate 466 on the bottom retainer plate 144 as illustrated in Figure 8).
  • cage 430 will move and carry the shear blade 438 against the bar (to the right as viewed in Figure 13). In this manner, the portion of the bar to be sheared is securely clamped between the backing clamp 436 and the shear blade 438.
  • the positioning of the holder 366 and the movement of the cage 430 therealong are accommodated by various side and end shim and wear plates positioned within the retainer plate cavity.
  • the bar is then sheared by actuation of the hydraulic cylinder 116 ( Figures 2 and 3).
  • the cylinder 116 acts on a main ram 468 extending through a bore 469 in center bolster 114 ( Figure 18) to move the entire cage 430 (to the right as viewed in Figure 18) to shear the bar.
  • the cage 430 is returned to the initial loading position and the backing clamp 436 is moved to a clearance position relative to the shear blade 438 by mechanisms as will next be described.
  • the entire cage 430 is returned to the initial position by a small return ram 474 operated by a hydraulic cylinder actuator 476.
  • the distal end of ram 478 is received in a suitable cavity 478 defined in the end of cage 430.
  • operation of the actuator 476 to move the ram 474 to the left will return the cage 430 to the initial bar loading position.
  • a novel return mechanism is provided. Specifically, and as best illustrated in Figures 15-17, a pair of side links 484 and 486 are pivotally mounted about pin 488 at their upper ends on either side of cage 430. To this end, cage 430 is provided with a channel 490 for receiving link 484 and with a channel 492 for receiving link 486. The links 484 and 486 are thus recessed in the channels in the cage 430 and may pivot within the channels about the pin 488.
  • a pin 494 is mounted through backing clamp 436 and is received on each end within elongated apertures 496 and 498 in the links 484 and 488, respectively.
  • a pin 500 joins the bottom ends of the links 484 and 486.
  • the bottom portion of cage 430 defines a cavity 502 to allow movement of the pin 500 and to receive a pin engaging block 504.
  • the cavity 502 communicates at the sides of cage 430 with the link channels 490 and 492.
  • Block 504 defines a channel 506, the vertical walls of which are adapted to engage the pin 500.
  • Block 504 is slidibly disposed within cavity 502 on plate 466 and is connected to rods 508 and 509 passing through bore 510 in a second end bolster 112.
  • Rod 509 is connected to a hydraulic cylinder actuator 512 mounted to bolster 112.
  • the actuator 512 is operated to move the block 504 to the right, as viewed in Figures 15 and 18 to move pin 500 to the right.
  • This movement of the links forces pin 494, and hence the backing clamp 436, to the right, as viewed in phantom lines in Figure 15, to provide an initial clearance for the incoming bar.
  • the second end bolster 112 is provided with a bore 514 for receiving a travel indicating rod 516 extending therethrough.
  • the rod 516 is connected to ram 474 by a bracket 517 engaging a circumferential channel 519 in the ram 474.
  • the rod 516 has oppositely facing flat surfaces 518 and 520 extending beyond bolster 112.
  • Mounted to the end of the rod 516 projecting on the exterior side of the second end bolster 112 are adjustable clamps 522 and 524. The clamps may be adjusted to any position on the flattened portion of the rod 516 extending exterior of the second end bolster 112.
  • limit switches 526 and 528 may be provided to be actuated by downwardly extending portions of the clamps.
  • limit switches 526 and 528 are shown supported from a bracket 530 secured to the exterior surface of the second end bolster 112.
  • movement of the ram 474 causes the clamps 522 and 524, carried on rod 516, to actuate their associated limit switches.
  • the interaction of the limit switches with the control system in the operation of shearing the bar will next be explained.
  • the infeed side clamp assembly comprising clamps 196 and 198
  • the shearing clamps, clamps 436 and 438 are also open to provide the initial loading clearance.
  • an appropriate signal from the bar feeding mechanism initiates the clamping of the bar on the infeed side by actuating the cylinder 396 to move the infeed clamp 198 against the bar and force the bar against the backing clamp 196.
  • the cylinder 456 is actuated to move the backing clamp 436 against the bar.
  • continued force applied to the clamp 436 by the cylinder 456 causes the cage 430 to move relative to both the bar and clamp 436 to engage the shear blade 438 securely against the bar.
  • the cylinder 476 may be continuously pressurized so as to provide a suitable nominal return force (e.g., 20 tons) against the cage 430. This force will be overcome by the movement of the cage 430 under the actuation of the wedge cylinder 456 and main ram cylinder 116. The force exerted by these cylinders is relatively great and of course easily overcomes the continuously applied return force of cylinder 476.
  • a pressure switch (not illustrated) in the hydraulic circuit of the wedge actuator 456 can be provided to actuate the main ram cylinder 116 to move the main ram 468 against the cage 430.
  • a signal generated at the completion of the shear step is used to reverse the operation of the main ram cylinder 116 and to reverse the operation of the wedging cylinder 456. Since the cylinder 476 is continuously pressurized, reversal of the main ram cylinder 116 permits the low pressure cylinder 476 to force the cage 430 back to the initial bar loading position. As this is occurring, the wedge 450 is being retracted by cylinder 456.
  • the second limit switch 526 associated with travel clamp 522 senses the return of the cage 430 to the initial bar loading position and actuates the cylinder 512 to move the backing clamp 436 away from the shear blade 438 to thus "open up" the assembly and provide clearance for the next portion of the bar to be inserted therein.
  • the moving shear assembly including the cage 430, shear blade
  • the entire machine may be operated in either vertical or horizontal orientations.
  • the clamping of the portion of the bar to be sheared between the backing clamp 436 and shear blade 438 is effected by means of a positive metal-to-metal transference of load through the drive wedge 450. Any tendency of this portion of the bar to bend is countered by the direct mechanical restraint which does not oppose (and hence does not substract from) the shearing force applied by the main shearing ram cylinder 116. Bending of the bar is substantially reduced with this apparatus so that the deformation of the bar occurs primarily across the shear plane.
  • the center bolster 114 is interlocked with the housing retainer plates 144, 146, and 148 and receives the main ram 468 so that the piston rod bearing of cylinder 116 is relatively close to the moving shear assembly. This reduces the moment arm length through which the transverse bending-induced shear loads act. The transverse loads on the bearing structure are thus reduced.
  • center bolster provides a direct transfer of clamping load on the infeed side of the apparatus. This elimiates the tendency of the apparatus acting as a "knuckle press" which characterizes some prior art machines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shearing Machines (AREA)

Abstract

Procede et appareil de fixation d'une barre a couper, de cisaillement de la barre, et de transmission des forces de cisaillement. Un assemblage de fixation d'alimentation (196, 198) et un ensemble a lames de cisaillement mobile (430, 436, 438) sont retenus dans une enceinte formee d'une pluralite de plaques de retenue (144, 146, 148) qui sont disposees entre et reliees a une paire de porte-matrices (112, 114) ayant des cles (178, 186) s'inserant et s'adaptant dans des cavites de cles alignees (174, 176, 180, 182) dans les plaques de retenue (144, 146, 148) et les porte-matrices (12, 114). L'ensemble de fixation d'alimentation (196, 198) est pourvu d'une bride d'approvisionnement (198) adaptee pour pivoter sur un bloc support (332) lorsque ce bloc support (332) et cette bride d'alimentation (198) sont deplaces contre une barre pour rattraper les variations de section de la barre sur sa longueur. Une cage rectangulaire (430) ayant un chemin de guidage interieur est prevue pour recevoir une portion de la barre a couper. Une contre-bride (436) est portee par la cage (430) et coulisse dans celle-ci. La contre-bride (436) est coincee contre un cote de la portion de la barre a couper jusqu'a ce que l'autre cote de la barre soit engagee par une partie de la cage (430). La cage (430) et la contre-bride (436) sont forcees par un mouton (468) pour couper la barre. Cette conception elimine ou reduit sensiblement le probleme de flexion de la barre pendant le cisaillement.
PCT/US1980/001177 1979-09-04 1980-09-04 Procede et appareil de cisaillement de barres billettes et autres lopins de forme allongees WO1981000687A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US7222379A 1979-09-04 1979-09-04
US7222479A 1979-09-04 1979-09-04
US7222579A 1979-09-04 1979-09-04
US72223 1979-09-04

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WO1981000687A1 true WO1981000687A1 (fr) 1981-03-19

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Application Number Title Priority Date Filing Date
PCT/US1980/001177 WO1981000687A1 (fr) 1979-09-04 1980-09-04 Procede et appareil de cisaillement de barres billettes et autres lopins de forme allongees

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EP (1) EP0035557A1 (fr)
WO (1) WO1981000687A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2636872A1 (fr) * 1988-09-28 1990-03-30 Peddinghaus Rolf Installation pour tronconner des sections de barres d'acier a partir d'une barre d'acier
EP0372528A2 (fr) * 1988-12-09 1990-06-13 Elhaus Industrieanlagen Gmbh Cisaille à lingots chauds
US6012369A (en) * 1997-11-21 2000-01-11 Abbey Etna Machine Company Tube cut-off device having a die set removal apparatus

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2132136A (en) * 1937-08-04 1938-10-04 Buffalo Forge Co Holding or stripping mechanism for shearing machines
US3039344A (en) * 1956-08-24 1962-06-19 Lad L Hercik Stock shear having stock stop and clamping means
US3908496A (en) * 1973-01-18 1975-09-30 Advanced Machine Design Co Hydraulic shearing machine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2132136A (en) * 1937-08-04 1938-10-04 Buffalo Forge Co Holding or stripping mechanism for shearing machines
US3039344A (en) * 1956-08-24 1962-06-19 Lad L Hercik Stock shear having stock stop and clamping means
US3908496A (en) * 1973-01-18 1975-09-30 Advanced Machine Design Co Hydraulic shearing machine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2636872A1 (fr) * 1988-09-28 1990-03-30 Peddinghaus Rolf Installation pour tronconner des sections de barres d'acier a partir d'une barre d'acier
EP0372528A2 (fr) * 1988-12-09 1990-06-13 Elhaus Industrieanlagen Gmbh Cisaille à lingots chauds
EP0372528A3 (en) * 1988-12-09 1990-11-22 Elhaus Industrieanlagen Gmbh Warm ingots shear
US6012369A (en) * 1997-11-21 2000-01-11 Abbey Etna Machine Company Tube cut-off device having a die set removal apparatus

Also Published As

Publication number Publication date
EP0035557A1 (fr) 1981-09-16

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