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Publication numberUS3328995 A
Publication typeGrant
Publication dateJul 4, 1967
Filing dateDec 21, 1964
Priority dateDec 21, 1964
Also published asDE1527437A1, DE1527437B2, DE1527437C3
Publication numberUS 3328995 A, US 3328995A, US-A-3328995, US3328995 A, US3328995A
InventorsJohn H Rohlfs
Original AssigneeTurner & Seymour Mfg Company
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Vibratory straightening machines
US 3328995 A
Abstract  available in
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Claims  available in
Description  (OCR text may contain errors)

July 4, 1967 J. H. ROHU-S 3,328,995

VI BRATORY STRA IGHTEN I NG MACHINES Filed Deo. 2l, 1964 3 Sheets-Sheet l F/G. g2

5f y y 64 62 A ATTORNEYS July 4, 1967 .1, H RoHLFs VIBRATORY STRAIGHTENING MACHINES 3 Sheets-Sheet-2 Filed Deo. 2l, 1964 July `4, 1967 J, H, RQHLFS' A 3,328,995

VIBRATORY STRAIGHTENING MACHINES Filed Dec. 2l, 1964 This invention relates to a vibratory straightening machine for straightening elongated workpieces.

4It is the general object of the present invention to provide a straightening machine which is particularly adapted to accommodate relatively small elongated workpieces, and which includes means for vibrating a workpiece in Va fixed plane relative thereto to effect substantial longitudinal alignment of the workpiece portions.

It is a further object of the invention to provide a machine adapted to accommodate and straighten a small workpiece in at least two planes relative thereto by vibrating the workpiece in planes passing through its longitudinal axis to effect straightening of the same with no substantial endwise movement thereof.

The drawings show a preferred embodiment of the invention and such embodiment will be described, but it will be understood that various changes may be made from the construction disclosed, and that the drawings and description are not to be construed as defining or limiting the scope :of the invention, the claims forming a part of this specification being relied upon for that purpose.

Of the drawings:

FIG. 1 is a fragmentary perspective view of a straightening machine constituting a presently preferred embodiment of the invention and showing the general arrangement of the Work holders.

FIG. 2 is a fragmentary transverse vertical section taken as indicated by the line 2 2 of FIG. 1, showing a iirst group work holder.

FIG. 3 is a fragmentary transverse vertical section taken as indicated by the line 3-3 in FIG. 1, showing a second group work holder.

FIG. 4 is a fragmentary plan view of the work holders of FIG. 1 showing a workpiece therein bent to an undulating shape, the position of the workpiece in an alternate portion of the operating cycle being indicated by broken lines.

FIG. 5 is a fragmentary transverse vertical section taken as indicated by the line 5 5 in FIG. l, showing means for moving the Work holders, and a 'means for adjustably ,controlling workiholder movement.

FIG. 6 is a fragmentary side view, partially broken Aaway as generally indicated by the line 6-6 in FIG. 5,

showing the mechanism of FIG. 5.

Generally speaking, the straightening machine of the present inventioncomprises at least three work holders which are positioned in series along a longitudinal axis and which are respectively adapted to vengage successive longitudinally spaced portions of an elongated workpiece 'arranged with its centerline in general alignment with the .ing of the workpiece in at least two planes. Also included United States Patent O in the machine is a power means for varying the magnitude of transverse displacement of the said workpiece portions between a position of maximum displacement and a position wherein the workpiece portions are substantially longitudinally aligned. Still further, a manual adjustable controlling means is provided for preselecting the maximum magnitude of work holder movement.

In the straightening operation, the workpiece is first held straight in one channel with the centerline of the workpiece in general alignment with the longitudinal axis of the work holders. The workpiece is then vibrated by transversely displacing the centerline portions thereof, associated with the moving work holders, to one and the opposite side of said axis while the magnitude of transverse displacement is varied between a position of maximum workpiece centerline displacement and a position wherein the workpiece portiops are substantially longitudinally aligned. Thereafter, the workpiece may be positioned in the other channel and the operation repeated to atfect substantial longitudinal alignment of the workpiece portions in a second plane thereof. The alternate bending operations cause the workpiece to assume a permanently straight set. The machine constituting the presently preferred embodiment of the invention is particularly suited for straightening small workpieces with no substantial endwise movement of the workpiece occurring during the straightening operation, however, it is not necessarily restricted to such application and may be adapted to accommodate elongated workpiece for axial passage therethrough.

Referring now to FIG. l, it will be noted that the straightening machine illustrated therein includes a plurality of work holders indicated generally at 10. The work holders 10, 10 are arranged in a longitudinal series along a longitudinal axis 12 fixed relative to a machine frame 14.

It will be noted that the plurality of work holders designated generally as 10 includes two groups of work holders alternately arranged in longitudinal series along the aforementioned axis 12. The iirst group of work holders comprises four similar work holders, each of which is designated by the reference numeral 16, whereas the second group of work holders comprises four similar work holders each respectively designated by the reference numeral 18. The total number of work holders employed in practicing the invention is optional; however, it is evident that the number employed may be somewhat dependent upon vthe length of the elongated workpiece to be straightened, particularly where the straightening operation is to be performed with no substantial endwise movement of the workpiece. It should be noted that at least three work holders will be employed in practicing the invention.

Referring to FIG. 2, wherein a iirst group work holder 16 is shown, it will be noted that the said wor-k holder comprises a pair of transversely aligned members 20, 20 having transversely spaced opposed inner radial edge surfaces 22, 22, and 24, 24 which surfaces respectively define portions of a first channel 23 and a second channel 25. Each of the two channels, is adapted to receive an associated portion of an elongated workpiece. Each of the members 20, 20l also includes abutting inner edge surfaces 26, 26 and 27, 27, a lower edge surface 28, 28 and a longitudinally disposed shoulder surface 30, 30. A generally H-shaped press plate 32 fastened to the machine frame 14 defines a shallow rectangular recess 34 with a fiat bottom surface 36 generally centrally positioned Within the upper surface thereof for receiving the Work holders in longitudinal alignment therein and also includes transversely extending end portions 38, 38 for supporting a pair of lever shafts or pins 40, 40'. A pair of press levers 42, 42, which will be hereinafter further described, are pivotally mounted on the said shafts. A pair of elongated hardened tool steel liner bars 44, 44 are positioned in longitudinal parallel alignment along the transversely spaced side surface portions of the recess 34. The shoulder surfaces 30, 30 of the members 20, abut the liner bars 44, 44 thereby serving to secure the first group work holders against transverse movement within the recess. At this point, it should be noted that the press levers 42, 42 do not engage the first group work holders.

Each of the second group work holders 18, 18, best shown in FIG. 3, comprises a pair of transversely aligned members 46, 46 having transversely spaced opposed radial inner edge surfaces 22, 22 and 24, 24 partially defining a first channel 23 and a second channel 25 respectively, each of the said channels being identical in both configuration and function to a corresponding channel defined by the lirst group work holders. Each of the members 46, 46 further includes abutting edge surfaces 48, 48 and 49, 49, a lower surface 50, 50, a longitudinally disposed outer edge surface 52, 52 which slants outwardly and downwardly from the vertical and a longitudinally disposed shoulder surface 54, 54. A pair of vertically adjustable wedges 56, 56 having inclined inner edge surfaces 58, 58 associated with and complementary to the inclined outer edge surfaces 52, 52 provide for adjustable engagement between the second group work holders 18, 18 and the press levers 42, 42 to facilitate alignment of the movable second group work holders with the stationary first group ones. It should be noted that when the members 46, 46 are positioned within the recess 34 with the lower surfaces 50, 50 slidably engaging the fiat surface 36 there is clearance 60, 60 between lthe shoulder surfaces 54, 54 and the liner bars 44, 44. Thus, it will be evident that the second group work holders 18, 18 are slidably movable upon the flat surface 36 between limits established by the hardened tool steel liner bars 44, 44 which serve to buffer work holder movement. A pair of transversely spaced longitudinally aligned hold down bars 62, 62 fastened to the press plate 32 in position immediately above the work holders secure the work holders against vertical movement. As previously mentioned, the total number of work holders employed in practicing the invention is optional, and when less than the total number that can be accommodated within the recess 34 is used a plurality of filler bars 64, 64 are employed to fill the space within the recess not occupied by work holders, thereby securing the work holders against longitudinal movement within the recess as shown in FIG. 1.

In FIG. 4, a workpiece 66 is shown positioned within the first channel 23. The movable work holders 18, 18 are shown in a position of maximum leftwardly transverse displacement relative to the stationary first group work holders 16, 16. The portions of the workpiece engaged by the second group work holders 18, 18 are transversely displaced causing the workpiece to assume an undulating shape. The resulting condition can best be seen by observing the displacement of the workpiece centerline 68 relative to the stationary axis 12. The position of the workpiece when two holders have assumed the position of maximum rightwardly transverse displacement is indicated by broken lines. Thus, it should be apparent that the reciprocal motion of the movable tool holders relative to the stationary ones impart a vibratory motion to the workpiece by moving the centerline thereof between a position of maximum transverse displacement and an intermediate position wherein the portions of the workpiece centerline are substantially longitudinally aligned. With regard to FIG. 4, it should be further noted that the contour radius of the inner edge surface 22, 22 is smaller than the maximum radial bend assumed by the associated portion of the workpiece in its maximum undulated position so that the vertically disposed edges of the work holder do not contact the workpiece surface.

This arrangement minimizes the risk of workpiece surface damage.

Simultaneous reciprocal transverse movement of the work holders 18, 18 may obviously be provided for in a variety of ways. In the presently preferred embodiment of the invention this movement is effected by a power operated lever system as best seen in FIG. 5. The lever system generally comprises a pair of first class levers 42, 42 arranged for parallel oscillation on a pair of first axes 72, 72, which parallel the work holder axis 12 and which are fixed relative thereto, for operably engaging the work holders 18, 18. A third class lever 74 is arranged for oscillation about a second axis 76 parallel to the work holder axis 12 and movable relative thereto, for transmitting power to the first class levers 42, 42. Power is transmitted from the third class lever 74 to the first class levers 42, 42 at the axes 77, 77, which are aligned in parallel with the work holder axis 12 and movable relative thereto. A power operated eccentric means 78, which cooperates with the lever 74 to translate the rotary motion of the eccentric shaft to an oscillatory motion in the lever system, is preferably employed to drive the lever system. The eccentric means 78 is arranged for rotation about a third axis 80 parallel to the work holder axis 12 and fixed relative thereto. The aforementioned power means for varying the magnitude of work holder movement is preferably a solenoid operated double acting air motor 82 having a reciprocating part 84 operably connected to the movable second axis 76, which is the primary fulcrum of the lever system, and a stationary part 86 secured to the machine frame. It should be apparent that movement of the axes 76 and 77, 77 relative to the fixed axes 80 and 72, 72 alters the mechanical advantage of the lever system thereby varying the extent or magnitude reciprocal motion of the work holders 18, 18. Also included in the machine is a manual adjustable controlling means for preselecting the maximum magnitude of work holder movement, which controlling means is preferably an adjustable microswitch 87 mounted in the path of travel of the reciprocating part on the air motor 82 for operating an electrical solenoid which, in turn, actuates an air valve to reverse the direction of travel of the reciprocating part. The aforementioned generally described operating mechanisms will be hereinafter more specifically defined.

Referring now to the FIGS. 5 and 6 it will be seen that a pair of longitudinally spaced side plates 88, 88 are fastened to the side portions of the press plate 32 and extend vertically downward therefrom. Each of the said plates has therein defined a downwardly opening inverted U-shaped channel 90. A pair of hub bearings 92, 92 for journalling the aforementioned eccentric means are fastened to the side plates 88, 88 in longitudinal coaxial alignment above the channels 90, 90. A pair of rectangular bearing blocks 94, 94 having channeled transverse side edge portions 96, 96 adapted to engage the transverse edge surfaces of the channel are positioned within the said channel for rectilinear vertical slidable movement therein. The bearing blocks 94, 94 have longitudinally coaxially aligned bores 98, 98 adapted to receive the opposite end portions of a cylindrical pusher shaft in press tit assembly therewith. A pair of set screws 99, 99 lock the pusher shaft in assembly with the drawing blocks. The shaft 100 serves as a fulcrum for the third class lever 74, and also has assembled thereon a pusher yoke 101 which operably connects the lever system with the aforementioned power means for varying the magnitude of work holders movement, which power means will hereinafter be further described. The pusher yoke 101 is a generally T-shaped member including a vertical downwardly extending portion 105 and a cross bar portion 107, and a pair of spaced apart centrally bored coaxially aligned cylindrical members 109, 109 welded to the upper surface of the cross bar 107 at the outer end portions thereof, adapted to receive the shaft 100 for assembly therewith. The previously generally described third class lever 74, is more specifically defined as a bearing yoke 74 comprising an elongated generally vertically disposed bifurcated member defining an upwardly opening U-shaped channel 102 and further including a longitudinally aligned central bore in the lower end portion thereof, said bore having therein a bushing 111 adapted to receive the shaft 100. The bearing yoke is assembled with the shaft 100 intermediate the cylindrical members 109, 109 and is thus arranged for oscillation on the shaft, said shaft also having been previously generally referred to as the axis 76 and the primary fulcrum of the lever system. A pair of transversely spaced longitudinally axially aligned knuckle joints 104, 104 are pivotally connected to the upper outer edge portions of the bearing yoke. To the knuckle joints 104, 104 are fastened a pair of bearing pads 106, 106 for transmitting the oscillatory motion of the bearing yoke to the first class levers 42, 42 to be hereinafter more fully described. The bifurcated upper ends of the bearing yoke are rigidly connected by a yoke spacer 108.

As aforementioned, the press levers 42, 42 also previously referred to as first class levers comprise a pair of transversely spaced elongated members having opposing interior edge surfaces. Radially contoured opposing inner surface portions 110, 110 are provided on the upper end portions of the press levers for operably engaging associated adjusting wedges 56, 56 on a work holder 18, 18. A longitudinally disposed recess 112 partially defined by a flat surface portion 114 is defined in the lower interior surface portion of each of the press levers for receiving an associated bearing pad 104 in slidable engagement therewith. Each of the levers 42, 42 further includes a downwardly extending pin 113 on the lower end thereof. As stated above, the levers 42, 42 are pivotally mounted on the lever shafts 40, 40 which shafts are assembled by press fit within the end portions 38, 38 of the plate 32. A tension spring 115 connecting the pins 113, 113 urges the lower end portions of the levers 42, 42 into engagement with the associated bearing pads 106, 106.

In accordance with the presently preferred practice, the operation of the straightening machines as set forth above is effected by a power operated eccentric means. The eccentric means indicated generally lby the numeral 78 generally comprises an eccentric bearing block 116 and an eccentric shaft 118. The eccentric block 116 is an elongated block of generally rectangular cross section having a longitudinal central bore 120 adapted to receive an eccentric portion of the shaft 118 and including vertically disposed channels 122, 122 defined within the longitudinally disposed side edge surfaces thereof adapted for vertical slidable lengagement within the channel 102 of the yoke 74. The eccentric shaft 118 is journalled at the end portions thereof within the hub bearings 92, 92 and includes a generally longitudinal eccentric portion 124 intermediate the ends thereof coaxially extending through the bore 120. vA plurality of needle bearings contained within the bearing hubs 92, 92 and the bore 120 provide means for journalling the end portions and the eccentric portion of the shaft 118. Power means for rotating the eccentric shaft is preferably provided by a variable speed drive motor 126 mounted on the machine frame 14 and coupled to the eccentric shaft by a universal coupling 128.

In operation, the eccentric means 78 cooperates with the yoke 74 to translate the rotary motion of the shaft 118 to an oscillatory motion of the yoke 74, said motion being transmitted to the press levers 42, 42 by the bearing pads 106, 106 to cause parallel oscillation of the press levers. The adjustable wedges 56, 56 cooperate with the radially contoured surface portions 110, 110 of the press levers 42, 42 to translate the oscillatory motion of the press levers to a reciprocal motion. The reciprocalV motion is imparted to the tool holders 18, 18 to move them -in unison.

In the presently preferred embodiment of the invention, the power means for varying the magnitude 0f work holder movement is preferably a solenoid actuated double acting air cylinder 82 having a cylinder portion 86 mounted on the frame 14 and a movable piston rod 84 arranged for vertical reciprocal movement. A link 130 threadably connected to the upper end portion of the piston rod 84 and locked in position relative thereto by a locking nut 132 provides operable connection with the pusher yoke 101, said yoke being secured at its downwardly extending portion 105 to the link by a pin 134. Thus, the vertical reciprocal movement of the piston rod 84 is transmitted to the fulcrum 76 by the pusher yoke 101 causing the bearing yoke 74 to move generally vertically upward. The U-shaped channel 102 moves vertically upward relative to the eccentric bearing block 116 in slidable engagement therewith. The bearing pads 106, 106 pivotally connected to the bearing yoke also move vertically upward in slidable engagement with the surfaces 114, 114 defined by the press levers 42, 42. It should be apparent that movement of the axis 76 results in relative movement between the movable axes 76 and 72, 72 and the fixed axes 80 and 77, 77 which varies the mechanical advantage of the lever system and which, in turn, varies the extent or magnitude of the reciprocal movement of the work holders 18, 18.

As previously noted, a manually iadjustable control means for preselecting the maximum magnitude of work holder movement is also included in the aforedescribed machine. The adjustable control means is preferably a microswitch 87 secured to a bracket 136 which is slidably mounted upon an adjustment -r-od 138, positioned in parallel alignment with the piston rod 84, and which is releasably secured thereto by a thumb screw 140. A trip lever 142 secured to the piston rod 84 in alignment with the microswitch 87 engages and thereby actuates the microswitch as the piston rod moves vertically upward. The microswitch 87 is electrically connected to a solenoid operated air valve which arrests the upward travel of the piston rod 84 and reverses its -direction of travel when the microswitch is actuated. The adjustment rod 138 has indicia 144 thereon indicating work holder movement so that the maximum magnitude of the work holder movement may be predetermined by manually positioning the microswitch bracket 136 in selected position relative to-the adjustment bracket 138.

The machine preferably idles with the drive motor 126 in continuous operation and the piston rod 84 in its maximum downwardly position, as shown in FIGS. 5 and 6. Thus, the eccentric means 78 continuously imparts a slight motion t-o the lever system; however, the adjustable wedges 56, 56 on the outer end portions of the movable work holders 18, 18 are so adjusted that this idling motion is not transmitted to the work holders. Preferably, a manually operable switching means, independent of the drive motor starting circuit, is provided to energize the air motor 82, thereby starting the -operating cycle by causing the reciprocating part or piston rod 84, and the mechanism associated therewith, to move upwardly. When the piston rod reaches the preselected position of maximum upwardly travel, as determined lby the adjustably positioned microswitch 87, the trip lever 142 contacts the microswitch, thereby reversing the direction of piston rod motion causing the piston rod to return to its maximum downwardly position completing the cycle.

The invention claimed is:

1. In a vibratory straightening machine for straightening elongated workpieces the combination comprising at least three work holders positioned in series along a longitudinal axis, said work holders being adapted to engage successive longitudinally spaced portions of Van elongated workpiece arranged with its centerline in general alignment with said axis, means for moving at least one of the said work holders relative to another of said work holders transversely of said axis to vibrate the workpiece by displacing said centerline of the workpiece to one and the opposite side of said axis, and means for varying the magnitude of said work holder movement between a position of maximum centerline displacement and a position wherein said workpiece portions are substantially longitudinally aligned while the workpiece is being vibrated.

2. In a vibratory straightening machine for straightening elongated workpieces the combination of at least three work holders comprising first and second groups of work holders arranged in alternate series along a fixed longitudinal axis, said work holders being adapted to engage successive longitudinally spaced portions of a workpiece, each of the said work holders in said first group being secured against movement, each of the said work holders in said second group being arranged for reciprocal transverse movement relative to said axis, means for transversely reciprocating said work holders in said second group to vibrate said workpiece in a plane fixed relative thereto and means for varying said transverse movement of said second group work holders to effect substantial longitudinal alignment of the workpiece portions.

3. In a vibratory straightening machine for straightening elongated workpieces the combination of at least three work holders aligned in series along a fixed longitudinal axis, said work holders defining therein first and second channels in longitudinal alignment with said axis, said channels being adapted to longitudinally receive an elongated Workpiece with the centerline thereof in general alignment with said axis, said first channel being adapted to receive the workpiece with a major dimension of the cross section thereof substantially vertically disposed, said second channel being adapted to receive the workpiece with the major dimension of the cross section thereof substantially horizontally disposed, and means for reciprocally moving at least one of the work holders relative to another transversely of said axis to vibrate said workpiece by displacing said centerline of the workpiece to one and the opposite side of said axis to effect substantial longitudinal alignment -of the workpiece in at least two planes thereof.

4. In a vibratory straightening machine for straightening elongated workpieces the combination of at least three work holders comprising first and second groups of work holders arranged in alternate series along a fixed longitudinal axis, said work holders defining therein first and second channels in longitudinal alignment with said axis, said channels `being adapted to receive an elongated workpiece with the centerline thereof in general alignment with said axis, said first channel being adapted to receive the workpiece with a major dimension of the cross section thereof substantially vertically disposed, said second channel being adapted to receive the workpiece with the major dimension of the cross section thereof substantially horizontally disposed, each of the said work holders in said first group being secured against movement, each of the said work holders in said second group being arranged for reciprocal transverse movement relative to said axis, means for transversely reciprocating said work holders in said second group to vibrate said workpiece in a plane fixed relative thereto, and means for varying said transverse movement of said second group work holders to effect substantial longitudinal alignment of the workpiece in at least two planes thereof.

5. A vibratory straightening machine for straightening elongated workpieces comprises at least three work holders positioned in series along a longitudinal axis, said work holders being 'adapted to engage successive longitudinally spaced portions of an elongated workpiece arranged with its centerline in general alignment with said axis, means for moving at least one of the said work holders relative to another -of said work holders transversely of said axis to vibrate the workpiece by displacing said centerline of the workpiece to one and the opposite side of said axis, means for varying the magnitude of said work holder movement between a position of maximum centerline displacement and a position wherein said workpiece portions are substantially longitudinally aligned while the workpiece is being vibrated, and manually adjustable controlling means for preselecting said maximum magnitude of said work holder movement.

6. The combination defined in claim 1 further characterized by said means for moving at least one of said work holders being adjustable.

7. The combination defined in claim 1 further characterized by said means for moving at least one of said work holders including eccentric means, and a lever system operated by said eccentric means, said lever system being operably connected to said one work holder.

8. The combination defined in claim 7 further characterized by said means for varying said work holder movement including power means operably connected to a fulcrum means in said lever system for moving said fulcrum means relative to said eccentric means.

9. A vibratory straightening machine as set forth in claim 5, wherein said means for moving `at least one of said work holders includes a first class lever arranged for oscillation about a first axis parallel to said longitudinal axis and fixed relative thereto, said first class lever having first and second end portions, said first end portion being operably connected to said movable work holder, a third class lever arranged for oscillation about a second axis parallel to said longitudinal axis and movable relative thereto, said third class lever including an oscillating end portion operably connected to said second end portion of said first class lever, and eccentric means rotatable about a third axis parallel to said longitudinal axis and fixed relative thereto, said eccentric means arranged to operably engage said third class lever between said second axis and said oscillating end portion.

10. A vibratory straightening machine as set forth in claim 9, wherein said means for varying said magnitude of said work holder movement includes a motor having a stationary part and a reciprocating part, said stationary part being secured in a position fixed relative to said longitudinal axis, said reciprocating part being operably secured to said second axis for moving said second axis in parallel relation to said longitudinal axis.

11. A vibratory straightening machine as set forth in claim 10, wherein said manually adjustable controlling means includes Ian adjustably positioned switching means actuated by said reciprocating part for reversing the direction of motion of said reciprocating part.

12. A vibratory straightening machine as set forth in claim 11, wherein said manually adjustable controlling means includes manually operable switching means for energizing said motor.

13. In a vibratory straightening machine for straightening elongated workpieces, the combination comprising a machine frame having a substantially fiat surface, at least three work holders supported on said fiat surface in series along a longitudinal axis fixed relative to said frame, said work holders including first and second group -of work holders each of the said first group work holders being secured on said fiat surface against movement relative thereto, each of the said second group work holders being slidably movable on said fiat surface transversely relative to said axis, each of the said work holders comprising a pair of transversely aligned members having transversely spaced opposing inner edge surfaces adapted to engage associated portions of an elongated workpiece arranged therebetween with its centerline in general alignment with said longitudinal axis, each of the said second group work holders having outer end portions transversely disposed from said axis, power means for moving said second group work holders to vibrate the workpiece by alternately displacing the centerline of the workpiece to one and the opposite side of said axis, and means for varying said movement of said second group work holders to effect substantial longitudinal alignment of the workpiece portions.

14. The combination dened in claim 13 further characterized by said inner edge surfaces defining r'st and second channels in longitudinal alignment with said axis, said rst channel being adapted to receive the workpiece with a major dimension of the cross section thereof substantially perpendicular to said at surface, said second channel -being adapted to receive the workpiece with the major dimension ofthe `cross section thereof substantially parallel to said flat surface.

10 and a lever system -operated by said eccentric means, said lever means operably engaging said outer end portions of said second group work holders for moving said work holders in unison.

16. The combination dened in claim 15 further characterized by said louter end portions being adjustable.

CHARLES W. LANHAM, Primary Examiner.

15. The combination dened in claim 13 further char- 15 R D- GREFE, ASSSHU Examineracterized by said power means including eccentric means,

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US237515 *May 19, 1880Feb 8, 1881 Crimping-machine
US3051216 *Nov 10, 1958Aug 28, 1962Nordberg Manufacturing CoElectrode bar straightener
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3426569 *Jan 31, 1967Feb 11, 1969Cyril Bath CoStretch forming machine and segmental adjustable die combination
US3518868 *Jan 11, 1968Jul 7, 1970Don A CargillStraightening machine and method
US3525247 *Jan 8, 1968Aug 25, 1970Cyril Bath CoStretch bending machine with segmental die,tolerance detector,and safety shock absorber
US4334418 *Jul 18, 1980Jun 15, 1982Siegrand CorporationPortable strip steel camber straightening machine
US4385513 *Jul 23, 1980May 31, 1983Salvagnini Transferica S.P.A.Forming presses
US4455857 *Sep 27, 1982Jun 26, 1984Salvagnini Transferica S.P.A.Forming press for bending a blank
US4488423 *May 31, 1983Dec 18, 1984Bertolette Machines, Inc.Straightening machine
EP0003356A1 *Jan 25, 1979Aug 8, 1979International Business Machines CorporationStraightening machine for elongated work-pieces
EP0053803A2 *Dec 3, 1981Jun 16, 1982Bertolette Machines, Inc.Straightening machine
EP0340495A2 *Apr 13, 1989Nov 8, 1989Krupp Widia GmbHExtrusion tool
Classifications
U.S. Classification72/297, 72/413, 72/311, 72/400, 72/383, 72/164, 72/390.5
International ClassificationB21D3/10, B21F1/02
Cooperative ClassificationB21F1/02, B21D35/008, B21D3/10
European ClassificationB21D35/00B6, B21F1/02, B21D3/10