US3583191A - Compressive straightener - Google Patents

Compressive straightener Download PDF

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Publication number
US3583191A
US3583191A US798908A US3583191DA US3583191A US 3583191 A US3583191 A US 3583191A US 798908 A US798908 A US 798908A US 3583191D A US3583191D A US 3583191DA US 3583191 A US3583191 A US 3583191A
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Prior art keywords
set forth
compressive
straightening machine
load
straightening
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US798908A
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English (en)
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Raymond E Colonius
George L Andersen
John E Nohren Jr
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Cargill Detroit Corp
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Cargill Detroit Corp
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D3/00—Straightening or restoring form of metal rods, metal tubes, metal profiles, or specific articles made therefrom, whether or not in combination with sheet metal parts
    • B21D3/02—Straightening or restoring form of metal rods, metal tubes, metal profiles, or specific articles made therefrom, whether or not in combination with sheet metal parts by rollers
    • B21D3/04—Straightening or restoring form of metal rods, metal tubes, metal profiles, or specific articles made therefrom, whether or not in combination with sheet metal parts by rollers arranged on axes skew to the path of the work
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D3/00—Straightening or restoring form of metal rods, metal tubes, metal profiles, or specific articles made therefrom, whether or not in combination with sheet metal parts
    • B21D3/10—Straightening or restoring form of metal rods, metal tubes, metal profiles, or specific articles made therefrom, whether or not in combination with sheet metal parts between rams and anvils or abutments
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S72/00—Metal deforming
    • Y10S72/70—Deforming specified alloys or uncommon metal or bimetallic work

Definitions

  • the invention pertains to the cold straightening of long slender parts made of brittle and hard materials such as grey cast iron camshafts. Beam loading in a straightening machine will ordinarily cause tensile failure of such a part if straightening is attempted.
  • the invention provides for compressive column loading of the part so that the neutral axis of the part is moved towards the opposite outermost fibers as the beam loading is applied.
  • the tensile stress may be minimized or eliminated while the compressive stress in the outermost fibers of the side towards the beam loading increases beyond the compressive yield strength and plastic strain occurs.
  • the part will be plastically deformed and possess a statistically balanced internal residual stress distribution when the loading is released.
  • the invention provides for rotation of the part as the beam loading is released resulting in cyclic plastic deformation and relaxation for all the outermost fibers about the desired axis.
  • a brittle material such as grey cast iron that has a significantly larger plastic range in compression than in tension may be successfully straightened in this manner.
  • the beam loading will result in a cyclic plastic deformation in tension and in compression as the shaft turns.
  • the shaft will be straightened if sufficient beam loading is applied to stress the outermost fibers into the plastic strain region and gradually released as the shaft continues to turn.
  • sufficient beam loading to cause plastic strain in the outermost fibers will often result in tensile failure of the shaft.
  • Some brittle materials may be hot straightened to a greater extent than cold straightening allows.
  • parts that require more extensive straightening than the above methods will allow usually must be scrapped.
  • the invention is an improvement that may be incorporated into a basic straightening machine for straightening ductile parts by rotating them and applying a beam loading that is gradually released as the part rotates.
  • the part rests on rollers near each end and the part is driven by a chuck at one end that is free to accommodate changes in the deflection angle of the longitudinal axis of the part at that end.
  • a ram with rollers applies a bending load to the part as the part revolves.
  • the load initially is sufficient to cause plastic deformation in the outer fibers of the part cyclically as the part revolves.
  • the ram is then gradually retracted resulting in a relaxation of the cyclic loading.
  • the initial loading preferably is sufficient to cause a deflection in the part from its nominal neutral axis equal or greater than the plastic yield point of a straight part.
  • the invention replaces the supporting rollers near each end with compression thrust bearings at each end of the part.
  • the bearings are free to accommodate changes in the deflection angle of the longitudinal axis of the part at each end.
  • the bearings will accommodate both transverse loads and longitudinal loads.
  • a framework connects the stationary portions of the bearings and incorporates an hydraulic cylinder to apply a force to one of the bearings such that the part can be compressively loaded as a column between the bearings.
  • the other end bearing incorporates a through shaft in the moving part of the bearing to rotate the part.
  • a universal joint connects the through shaft to an hydraulic motor.
  • the part is loaded to an amount just below theoretical column failure.
  • pairs of rollers are provided along the part and resiliently supported by an amount sufficient to prevent buckling of the part.
  • the ram is also positioned close to the shaft to prevent buckling. With the column loading applied and the shaft rotating the ram now moves and applies a load sufficient to cause a deflection in the shaft from its nominal neutral axis equal or slightly greater than the plastic yield point of a straight shaft. The ram then retracts gradually as above.
  • a combination of column and bending loading shifts the neutral axis of the stress distribution in the same direction as the deflection. Therefore, the proper chosen values of bending and compressive column loading will eliminate or minimize tensile stress in the shaft.
  • a shaft such as a camshaft made of grey cast iron may be plastically strained in compression without subjecting the shaft to tensile stresses.
  • the outermost fibers will cycle through a maximum compressive stress resulting in plastic strain and as the ram retracts this maximum compressive stress will reduce, the cycling strain will tend to reduce and the part will tend to relax into a straightened position with an internal statistically balanced stress distribution.
  • the stiffness of the resiliently loaded rollers along the shaft must be sufficient to prevent buckling but flexible enough to allow the necessary deflection caused by the ram.
  • the part to be straightened need only be cylindrical in cross section at the locations where the rollers touch the part. Therefore, in the case of a camshaft, the camshaft bearing locations may be used and in the case of a part that does not have any cylindrical cross sections, cylindrical collars may be fitted over the part such that they are concentric with the axis of rotation desired.
  • the invention may also be usefully employed for straightening notched parts where a tensile stress at the base of the notch would result in failure.
  • FIG. 1 is a side view of a straightening machine fitted and adapted for compressive column loading of a part
  • FIG. 2 is a fragment cross section taken along the lines 2-2 of FIG. 1;
  • FIG. 3 shows the bearing assemblies at each end of the part loaded in the machine
  • FIG. 4 shows the centering and driving means applied to the driven end of the rotating part
  • FIG. 5 is a schematic of the hydraulic and pneumatic circuits for the machine
  • FIG. 6 is a schematic of the electrical control circuit for the machine
  • FIG. 7 shows a modification utilizing a cylindrical collar around a noncylindrical part
  • FIG. 8 is taken along the line 8-8 of FIG. 7;
  • FIG. 9 is a representation of a typical tensile stress-strain diagram for three engineering materials.
  • FIG. 10 is a representation of a tensile and compressive stress-strain diagram for two engineering materials that may utilize the present invention to advantage;
  • FIG. I! is a schematic of a part showing the cross-sectional orientation of the stress distributions shown in FIGS. 12-14;
  • FIGS. 12a-12j are idealized stress distributions under a combination of specified loading for a material with a definite yield strength.
  • FIGS. l3a-l3j are idealized stress distributions under a different combination of specified loading for a material with a definite yield strength
  • FIGS. 14d14j are idealized stress distributions under a combination of specified loading for a material with virtually no elastic range.
  • FIGS. l4d-Mj are idealized stress distributions under a combination of specified loading for a material with virtually no elastic range.
  • a machine frame 11 supports an overhead member 12 which in turn supports the ram assembly 13.
  • the ram assembly 13 is actuated by the ram 14 of an hydraulic cylinder 15.
  • the ram assembly 13 is kept in proper alignment by the guide cylinders 16 sliding in guides 17.
  • Attached to the ram assembly are one or more roller assemblies 18 and rollers 19.
  • the rollers 19 contact the cylindrical portions 20 of the part to be straightened 21.
  • rollers 22 that are mounted on one or more air cylinders 24.
  • the part 21 is held between bearing and spindle assemblies 26 and 27 and rotated by a motor and gear box 25 through a flexible coupling at 28.
  • Each bearing and spindle assembly 26 and 27 is mounted on the bed of the machine 29 and kept in proper alignment by tie rods 30.
  • An hydraulic cylinder 31 for applying an axial load to the part 21 is fastened to the rods 30 and the rods 30 are fastened to the bearing and spindle assembly 26 so as to provide the proper reaction force at the other end of the part 21.
  • FIG. 2 a roller assembly 18 mounted on the ram is shown with paired rollers 19 in contact with a cylindrical portion 20 of a part 21.
  • Below the part 21 is another pair of rollers 22 mounted on an air cylinder 24.
  • the rollers 22 are also in contact with a cylindrical portion 20 of the part 21.
  • Alignment guides and stops 32 are also provided for the rollers 22.
  • FIG. 3 the left-hand bearing and spindle assembly 26 and the right-hand bearing and spindle assembly 27 are shown in cutaway detail.
  • the left-hand spindle 35 is driven by a coupling at 28 and revolves in the roller bearing 36.
  • the spindle 37 rotates in a similar bearing 38. Since the part 21 is squeezed between the spindles 35 and 37 and loaded by the ram through the rollers 19, the bearings 36 and 37 and loaded by the ram through the rollers 19, the bearings 36 and 38 are specially made to accept both the axial loading, the transverse loading and the slight angular deflection of each spindle 35 and 37 due to the beamwise deflection of the part 21.
  • the hydraulic cylinder 31 by means of the piston 39 and cylindrical yoke 40 acting against the bearing holder 41 provides for the axial loading to the part 21.
  • the spindle 37 is fastened to a retainer 42 by means of a bolt 43.
  • the retainer 42 is guided by the spherically shaped back surface 48 of the bearing holder 41.
  • the left-hand spindle 35 is held in place by a retainer 44 and collar 45.
  • the collar 45 is held in place by means of a setscrew 46 and the retainer 44 slides on a spherical back surface 49 of the bearing holder 47.
  • the configuration of the spindles 35 and 37 depends upon the means used to attach the part 21 and the means used depends upon the configuration of the part 21.
  • the part 21 is a camshaft.
  • the cylindrical right-hand end 50 of the camshaft fits into a socket 51 of the spindle 37.
  • the spindle 35 transmits rotational torque to the left end 52 of the part 21.
  • a live center 53 actuated by a spring 54 is incorporated into the spindle 35.
  • a hardened disc 55 Surrounding the live center 53 and attached to the spindle 35 is a hardened disc 55 having a toothed edge 56 attached. Upon application of the axial force to the part 21 the toothed edge 56 will be driven into the left-hand end of the part 52 sufficient to transmit the necessary rotational torque to the part 21.
  • a constant speed electric motor 60 drives two pressure-controlled variable flow hydraulic pumps 61 and 62.
  • the hydraulic pump 61 provides hydraulic power for the spindle drive 25 by means of a fluid motor control circuit 63 and three-position solenoid control valve 64.
  • the hydraulic pump 62 supplies hydraulic power for the axial compression cylinder 31 and ram cylinder 15.
  • the movement and location of the piston 39 in the axial compression cylinder 31 is determined by the solenoid operated three-position valve 65 in a low-pressure circuit controlled by the pressure valve 66.
  • the high pressure circuit 67 supplies hydraulic power to the ram cylinder and ram 14.
  • the three-position solenoid-operated valve 68 controls the rapid up and rapid down motion of the ram assembly when the ram assembly is not in contact with the part.
  • the motion of the ram assembly when the ram assembly is in contact with and applying a load to a part is controlled by the three-position solenoid-operated valve 69.
  • the flow rate of hydraulic fluid is controlled by the reversible, variable restrictions 70.
  • Limit switches 71 actuated by the ram 14 control the operation, through the electric circuitry shown in FIG. 6, of the various control valves in the hydraulic circuit.
  • the control 72 releases pressure in the high-pressure circuit 67 when the ram 14 is in its uppermost position.
  • the air cylinder 24 is supplied with compressed air through the circuit 73 including a pressure control 74.
  • the pressure setting in the pressure control 74 is sufficient to apply a load to the part 21 to prevent buckling when the part is under compressive loading and provides a resilient air spring action when the ram assembly 13 is applied to the part 21 as shown in FIG. 1.
  • the power circuit provides electrical power for the hydraulic pump motor 60 and the transformer 81.
  • the transformer 81 provides electrical power for the secondary control circuit 82.
  • Closure of the starting switch 83 completes the subcircuit 84 thus energizing the relays l-M and CRM.
  • Relay 1-M completes the circuit through the hydraulic pump motor 60 and relay CRM completes the control circuit to the rest of the subcircuits.
  • Closure of the switch 85 completes the subcircuit 86 energizing the relay 1 CR.
  • the relay 1 CR completes the subcircuit through the solenoid valve 64 thus turning on the spindle drive.
  • the pressure switch 1 PS When the hydraulic pressure in the compression circuit reaches a predetermined amount, the pressure switch 1 PS will close thus completing the subcircuit 91 and energizing the relay 5 CR.
  • the relay 5 CR thereupon completes the subcircuit 103 through the solenoid valve 69 and the ram feeds downward a predetermined amount to apply the proper beam load to the part.
  • the limit switch 3 LS will close at this full depth point and complete the subcircuit 92 energizing the relay 6 CR.
  • Subcircuit 91 will thus be opened and subcircuit 93 will be closed energizing relay 7 CR.
  • Relay 7 CR will energize the subcircuit 104 and reverse the solenoid valve 69 thus allowing the ram to raise slowly at a predetermined rate.
  • the feed rate as the ram withdraws will be such that all portions of the part undergo cyclic stress several times as the part revolves.
  • Limit switch 4 LS which is open during ram feed closes as the ram just clearsthe part and completes subcircuit 94 energizing timed relay 1 TR which thereupon breaks circuit 93 stopping the ram.
  • the timed relay 1 TR also completes the subcircuit 105 through the solenoid valve 65 which allows the column loading to be released. Upon release of the column loading, the timed relay 1 TR completes the subcircuit 95 energizing relay 8 CR. Relay 8 CR then energizes the subcircuit 106 thus energizing the solenoid valve 68 and the ram raises rapidly back up to its beginning position.
  • the limit switch 1 LS is reopened and the subcircuit 88 is broken.
  • the relay 2 CR is deenergized and the subcircuits 89 through 95 are opened again.
  • subcircuit 92 is now opened relay 6 CR is deenergized and subcircuit 88 is now in its initial condition such that a closure of switch 87 will again start the cycle all over for the next part.
  • the switch 87 may be automatically closed when the next part is placed in the machine. In such an installation the spindle drive may continue during the load and unload cycles by utilizing spindles conventional in the art that will completely release the part when the compression is released.
  • FIGS. 7 and 8 illustrate a modification for a long slender part that is noncylindrical in cross section. Shown here is an 1- section 21a. Modified spindles 35a and 37a are provided for gripping the ends of the l-section. One or more collars 110 having a cylindrical outer surface 200 and a suitable configuration 20b for gripping the surface of the l-section 21a may be provided and locked into place by the setscrew 111 prior to loading in the compressive straightening machine. Thus, an irregular shape may be rotated in the compressive straightening machine with the air cylinder rollers 22 and ram rollers 19 utilized.
  • FIG. 9 three typical tensile test results for metals are illustrated.
  • Curve 1211 is a typical result for a low-carbon steel with definite elastic and plastic regions.
  • Curve 1121 illustrates a smooth blending of the elastic and plastic regions for a ductile iron.
  • curve 123 for grey cast iron indicates a smooth blending of plastic and elastic regions.
  • the elastic region is only very limited and the ultimate strength in tension for grey cast iron is relatively much less than in the case of steel or ductile iron. Therefore, plastic deformation of grey cast iron in tension is greatly limited and the straightening of a grey iron bar with a simple bending load is usually impracticable.
  • Most ductile materials exhibit curves similar to 120 or 121 both in tension and in compression.
  • the present invention takes advantage of the fact that some engineering materials such as grey cast iron exhibit a much higher strength in compression than they do in tension. Such materials may be deformed to a greater extent under compression loading with a higher compression stress.
  • Curves 125, 1126 and 127 illustrate a material that has an ultimate strength in compression significantly greater than the ultimate strength in tension and a significantly large elastic region 127. Most important, however, to the usefulness of the present invention as applied to this material is the fact that the plastic region in compression given by 125 is much larger than the plastic region in tension shown by 126. Thus, a bar under compressive stress only, may be deformed or straightened to a much greater extent than if a portion of the bar is under a severe tensile stress. Simple beam loading would provide essentially the same compressive stress in the outer fibers of the bar as tensile stress.
  • the present invention overcomes this problem by allowing an increase in the compressive stress and at the same time providing a decrease or elimination of the tensile stress in the bar.
  • the bar may be deformed to an extent that would be impossible without tensile failure if simple beam loading were used.
  • Curves 128, I29 and 130 illustrate a material having a very limited elastic range 130 but again an ultimate strength in compression significantly greater than the ultimate strength in tension and a plastic region in compression 128 significantly greater than the plastic region in tension 129.
  • the selection of compressive load and bending load to straighten a bar will depend upon the material and the configuration of the bar.
  • the compressive load applied to the ends of the bar will subject the bar to column loading; therefore, the possibility of elastic buckling due to the column loading must be considered.
  • the present invention provides for lateral support along the column.
  • the air cylinders 24 provide lateral support through rollers 22 to the part 21 and the positioning of the ram assembly 13 with the rollers 19 just contacting the part 21 also provides lateral support when the compression load is applied.
  • the material and the slendemess ratio of the part 21! will determine how many of the roller assemblies l8 and air cylinders 2 will be necessary to prevent column buckling of the part 21. With column buckling thus prevented sufficient compressive load can be applied to the part such that the compressive yield strength may be as closely approached as desired.
  • FIGS. 12, 13 and 14 pertain to the cross section shown in FIG. 11.
  • the bending load 139 is shown imposed at this cross section.
  • the compression load is distributed evenly over the cross-sectional area.
  • FIG. 12a depicts the stress distribution due to column loading alone that may be found along the line 145. In this case the stress due to compression is assumed to be about three-fourths of the yield strength in compression.
  • FIG. 12b depicts the normal stress distribution along the line 145 due to the bending load 139 alone. The maximum is assumed here to be approximately one-half of the yield strength in compression.
  • the resultant normal stress for a perfectly elastic material is depicted in FIG. 120. However, for a material, such as that shown in curves -127 of FIG.
  • the bar may be rotated so that the initial curvature of the bar does not need to be determined prior to straightening.
  • the bar continues to rotate in the direction 144 and as it rotates 90 such that the line 145 coincides with the line 146, the stress distribution shown in FIG. 12f will occur along this line. Since this distribution is now along the neutral axis of the bar, it is under compression loading only, but the normal stress distribution shows the effect of the plastic deformation previously. A further rotation of 90 in the direction 144 will result in a normal stress distribution as shown in FIG. 123 along the line 145.
  • the plastic deformation in the fibers of the bar having the greatest radius of curvature will be more extensive than the plastic deformation in the outer fibers of the bar having the least radius of curvature. Therefore, the bar will be straightened by this method.
  • the rotation of the bar continues as the bending load is gradually removed, thus the cyclic plastic deformation will diminish with each cycle and when the bending load is finally removed the bar will be substantially straight and will have an internal stress distribution approximately that shown in FIG. l2j when the compression loading is released.
  • the residual stress distribution will be skewed toward the portion of the bar whose fibers initially have the largest radius of curvature prior to the straightening of the bar.
  • FIG. 13f indicates the normal stress distribution with release of the bending load
  • FIG. 13c shows the residual stress distribution with the release of the compression load.
  • FIG. Mf indicates the stress distribution inside the bar after the bending load is released and FIG.
  • FIG. 14f indicates the normal stress distribution along the line 145 which now coincides with the line 146 in FIG. II.
  • a further rotation of 90 in the direction 1144 will result in the stress distribution as shown in FIG. Mg for the line 145.
  • the plastic deformation again takes place along the full length of the line 145 because of the almost totally nonlinear character of the stress-strain curve for cast iron in compression.
  • FIG. 14h the stress distribution after 270 of rotation is shown and finally the stress distribution after 360 of rotation is shown in FIG. Mi.
  • a part-straightening machine comprising means for applying a longitudinal compressive load on a part and means for simultaneously applying a transverse bending load on said part.
  • A. part-straightening machine as set forth in claim 1 including means for changing the effective plane of bending while said part remains under said compressive load and said transverse load.
  • a part-straightening machine as set forth in claim 1 including support means substantially at each end of a part.
  • a part-straightening machine as set forth in claim 3 including end support means adapted to accommodate part axis deflection.
  • a part-straightening machine as set forth in claim 4 including intermediate support means adapted to resist buckling from the compressive loading.
  • a part-straightening machine as set forth in claim I incorporating means to rotate a part simultaneously with the application of said transverse and said compressive loads.
  • transverse load means incorporates a ram as sembly and one or more rollers mounted on said ram assembly arranged to contact cylindrical portions of a part upon extension of the ram assembly.
  • a part-straightening machine as set forth in claim 11 including and support means, spindle bearings in said end support means. spindles rotatably mounted in said spindle bearings and concentrically contacting each end of a part.
  • each spindle bearing is adapted to accommodate a changeable deflection angle in the axis of a part.
  • a part-straightening machine as set forth in claim 1 wherein said means to apply a compressive load includes a fluid pressure actuated cylinder.
  • a part-straightening machine as set forth in claim 1 incorporating control means to establish a predetermined transverse and compressive load application and release sequence such that the neutral axis of the stress distribution will shift in substantially the same direction as the deflection and the maximum compressivestress will cause plastic deformation in a part.
  • a method for bending parts composed of material with a greater range of compressive than tensile plastic deformation and comprising the steps of: applying a longitudinal compressive load which per se produces a compressive stress which does not exceed the elastic limit of the material; applying a transverse bending load, said bending load in combination with said compressive load providing a maximum compressive stress exceeding the elastic limit of the material while restricting the maximum tensile stress to a relatively lower value than said maximum compressive stress; and releasing said compressive and bending loads.
  • a method for straightening parts comprising the steps of: applying a longitudinal compressive load which per se produces a compressivestress which does not exceed the elastic limit of the material; applying a transverse bending load, said bending load in combination with said compressive load providing a maximum compressive stress exceeding the elastic limit of the material; and releasing said compressive and bending loads.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Forging (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Wire Processing (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Straightening Metal Sheet-Like Bodies (AREA)
US798908A 1969-02-13 1969-02-13 Compressive straightener Expired - Lifetime US3583191A (en)

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US79890869A 1969-02-13 1969-02-13

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DE (1) DE2006728C3 (de)
FR (1) FR2031400B1 (de)
GB (1) GB1270883A (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3823588A (en) * 1972-10-19 1974-07-16 Newport News Shipbuilding Method and system for straightening large diameter shafts by selective cold rolling
US4076136A (en) * 1974-11-21 1978-02-28 English Clays Lovering Pochin & Co. Ltd. Pipe straightening and spinning method and apparatus
US4624123A (en) * 1985-05-07 1986-11-25 Bertolette Machines, Inc. Straightening machine for motor armature assemblies and the like
US6651474B2 (en) * 2000-10-25 2003-11-25 Hegenscheidt-Mfd Gmbh & Co. Kg Device for the fixed-rolling of crankshafts
US20040231381A1 (en) * 2001-08-20 2004-11-25 Juranitch James C Shaft truing system
US20070178808A1 (en) * 2004-03-17 2007-08-02 Georg Himmelsbach Method and device for grinding assembled camshafts with a high concentricity accuracy
US20150068008A1 (en) * 2013-09-06 2015-03-12 The Boeing Company Automated tube straightening apparatus
CN106441180A (zh) * 2016-12-07 2017-02-22 怀宁县鑫泰钢结构有限公司 铸铁管校直检测装置
CN107570559A (zh) * 2017-09-06 2018-01-12 肇庆宏旺金属实业有限公司 一种五辊矫直机
US11072010B2 (en) 2016-04-13 2021-07-27 Most Technik Gmbh Method and device for straightening a workpiece

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5342587Y2 (de) * 1973-05-04 1978-10-13

Citations (3)

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Publication number Priority date Publication date Assignee Title
US624019A (en) * 1899-05-02 Apparatus for making crank-shafts
US3113608A (en) * 1962-03-29 1963-12-10 Puyear Wallace Ray Method and apparatus for roll straightening forged, cast and machined round parts
US3213659A (en) * 1963-01-28 1965-10-26 Ohio Crankshaft Co Apparatus and method for straightening metal shafts

Family Cites Families (1)

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Publication number Priority date Publication date Assignee Title
GB1074747A (en) * 1963-11-08 1967-07-05 American Brake Shoe Co Apparatus for straightening shafts

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US624019A (en) * 1899-05-02 Apparatus for making crank-shafts
US3113608A (en) * 1962-03-29 1963-12-10 Puyear Wallace Ray Method and apparatus for roll straightening forged, cast and machined round parts
US3213659A (en) * 1963-01-28 1965-10-26 Ohio Crankshaft Co Apparatus and method for straightening metal shafts

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3823588A (en) * 1972-10-19 1974-07-16 Newport News Shipbuilding Method and system for straightening large diameter shafts by selective cold rolling
US4076136A (en) * 1974-11-21 1978-02-28 English Clays Lovering Pochin & Co. Ltd. Pipe straightening and spinning method and apparatus
US4624123A (en) * 1985-05-07 1986-11-25 Bertolette Machines, Inc. Straightening machine for motor armature assemblies and the like
US6651474B2 (en) * 2000-10-25 2003-11-25 Hegenscheidt-Mfd Gmbh & Co. Kg Device for the fixed-rolling of crankshafts
US20040231381A1 (en) * 2001-08-20 2004-11-25 Juranitch James C Shaft truing system
US7162903B2 (en) * 2001-08-20 2007-01-16 Veri-Tek International Corporation Shaft truing system
US20070178808A1 (en) * 2004-03-17 2007-08-02 Georg Himmelsbach Method and device for grinding assembled camshafts with a high concentricity accuracy
US20150068008A1 (en) * 2013-09-06 2015-03-12 The Boeing Company Automated tube straightening apparatus
US9138792B2 (en) * 2013-09-06 2015-09-22 The Boeing Company Automated tube straightening apparatus
US11072010B2 (en) 2016-04-13 2021-07-27 Most Technik Gmbh Method and device for straightening a workpiece
CN106441180A (zh) * 2016-12-07 2017-02-22 怀宁县鑫泰钢结构有限公司 铸铁管校直检测装置
CN107570559A (zh) * 2017-09-06 2018-01-12 肇庆宏旺金属实业有限公司 一种五辊矫直机

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GB1270883A (en) 1972-04-19
DE2006728A1 (de) 1970-09-03
FR2031400B1 (de) 1973-07-13
DE2006728B2 (de) 1974-02-21
DE2006728C3 (de) 1974-09-12
FR2031400A1 (de) 1970-11-20

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