US3625263A

US3625263A - Roll bending machine and method

Info

Publication number: US3625263A
Application number: US812534A
Authority: US
Inventors: John F Kopczynski
Original assignee: Individual
Current assignee: Individual
Priority date: 1969-03-07
Filing date: 1969-03-07
Publication date: 1971-12-07
Anticipated expiration: 1988-12-07

Abstract

A method and machine for straightening an elongated wirelike workpiece wherein the machine includes a plurality of substantially parallel shafts each mounting a series of spaced coaxial rolls with at least one of said series being radially movable into overlapping relationship with the other series to define a central opening, and cam means for sequentially varying the orientation of the series of rolls relative to each other to provide a first opening between the rolls which is sufficiently large to receive the wire in a radial direction, a second opening which is relatively small for providing an overbending action in which axial portions of the wire are bent back and forth while the wire is rotated about its longitudinal axis while in engagement with the rolls, a third opening which is larger than the second opening to provide straightening action wherein the wire is continued to be rotated about its own axis in an opening which is substantially the same diameter as the wire while in contact with the rolls so as to straighten it, and a fourth opening wherein one of the series of rolls is moved away from the others to permit the workpiece to drop out of the opening in a radial direction. The cam means may be of a contour so as not to include the overbending action when this is not required. All of the rolls of adjacent series may be axially staggered relative to each other and oriented in radially overlapping relationship. The rolls also may be of different hardnesses in certain roll orientations. Certain of the rolls of each series may alternately be of larger and smaller diameter. A machine for rotating a spindle having first, second, and third series of rolls mounted on parallel shafts with the rolls of each series being axially offset and radially overlapping the rolls of the other series and defining a space therebetween to receive the spindle.

Description

United States Patent [72] Inventor John F. Kopczynski 1671 Sweeney St., North Tonawanda, N .Y. 14120 [21] Appl. No. 812,534

[22] Filed [45] Patented Mar. 7, 1969 Dec. 7, 1971 [54] ROLL BENDING MACHINE AND METHOD 32 Claims, 28 Drawing Figs.

[52] US. Cl 140/147,

72/110, 72/DlG. 10 [51] lnt.Cl B2" 1/02 [50] Field of Search 140/ 147;

72/94, 107, 108, 110, 224, DIG. l0

Primary Examiner- Lowell A. Larson Attorney-Sommer, Weber and Gastal ABSTRACT: A method and machine for straightening an elongated wirelike workpiece wherein the machine includes a plurality of substantially parallel shafts each mounting a series of spaced coaxial rolls with at least one of said series being radially movable into overlapping relationship with the other series to define a central opening, and cam means for sequentially varying the orientation of the series of rolls relative to each other to provide a first opening between the rolls which is sufficiently large to receive the wire in a radial direction, a second opening which is relatively small for providing an over bending action in which axial portions of the wire are bent back and forth while the wire is rotated about its longitudinal axis while in engagement with the rolls, a third opening which is larger than the second opening to provide straightening action wherein the wire is continued to be rotated about its own axis in an opening which is substantially the same diameter as the wire while in contact with the rolls so as to straighten it, and a fourth opening wherein one of the series of rolls is moved away from the others to permit the workpiece to drop out of the opening in a radial direction. The cam means may be of a contour so as not to include the overbending action when this is not required. All of the rolls of adjacent series may be axially staggered relative to each other and oriented in radially overlapping relationship. The rolls also may be of different hardnesses in certain roll orientations. Certain of the rolls of each series may alternately be of larger and smaller diameter.

A machine for rotating a spindle having first, second, and third series of rolls mounted on parallel shafts with the rolls of each series being axially offset and radially overlapping the rolls of the other series and defining a space therebetween to receive the spindle.

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ATTORNEY.

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ItOlLlL IBIENDING MAtCI-IINE AND METHOD BACKGROUND OF THE INVENTION The present invention relates to an improved machine and method for straightening elongated wirelike workpieces. The present invention also relates to an improved machine for rotating a spindle at high speeds.

SUMMARY OF THE INVENTION It is accordingly the object of the present invention to provide an improved straightening machine and method by which elongated wirelike workpieces can be straightened in a rapid and efficient manner to remove all the bends therein.

Another object of the present invention is to provide an im proved machine for rotating a spindle at ultrahigh speeds and minimizing vibration and chatter which may accompany such operation. Other objects and attendant advantages of the present invention will readily be perceived hereafter.

The improved method of the present invention comprises the steps of inserting a wire workpiece between a plurality of parallel series of spaced rolls which are positioned about a central opening in which the elongated wire workpiece is deposited, effecting rotation of the rolls to cause the wire workpiece to be rotated about its longitudinal axis while in engagement with said rolls and initially causing the opening to be of a relatively small size so that the rolls will cause an overbending action on axially spaced portions of the rotating workpiece to remove any severe bends therein, and thereafter increasing the size of the opening between the rolls to approximately the size of the wire so that a straightening action will be exerted on the rotating wire so that the wire will be worked back and forth as it rotates with the rolls until such time as it is straight.

The improved machine of the present invention comprises a plurality of substantially parallel series of coaxial rollers mounted on a base with at least one Series movable toward and away from the others and the rolls of at least one of the series being axially offset from the others and in radially overlapping relationship therewith, and an opening between said series for receiving a wirelike workpiece, and means for varying the size of the opening which includes opening of the rolls to a sufficient degree to receive a wire therebetween, moving the rolls sufficiently close to each other to define a relatively small opening therebetween to effect an overbending of axially spaced portions of the wire while rotated on its own axis as a result of being in engagement with the rolls, moving the rolls radially outwardly relative to each other so as to enlarge the opening so that it is essentially of the same diameter as the wire thereby to provide a straightening action on the wire as it continues to be rotated about its longitudinal axis, and moving the rolls apart in a radial direction so as to provide an opening for discharging the workpiece. The overbending is employed for relatively resilient materials. For less resilient materials the overbending may be eliminated. The rolls of each series may consist of alternating smaller and larger rolls; or certain of the rolls may be of different hardnesses in any predetermined orientation; or all of the rolls may be in radially overlapping and staggered relationship relative to each other.

The present invention also relates to an improved machine for rotating a spindle at ultrahigh speeds and minimizing vibration on chatter due to unbalancing forces on said spindle by mounting the spindle between three series of rolls mounted on parallel shafts with the rolls of each series being axially offset relative to the rolls of the other series. Therefore, the rolls will not grip the spindle at diametrically opposed locations and thus permit it to flex as required to absorb unbalancing forces. In addition, the rolls of each series preferably radially overlap the rolls of each of the other two series to provide a firm mounting for the spindle with contact on the spindle periphery at approximately 120 increments to provide a balanced holding force.

The various aspects of the present invention will be more fully understood when the following portions of the specification are read in conjunction with the accompanying drawings wherein:

BRIEF DESCRIPTION OF THE DRAWINGS FIG. I is a side elevational view of a bending machine embodying principles of the present invention;

FIG. 2 is a fragmentary side elevational view taken in the direction of arrows 2--2 of FIG. 1 and showing the bending rolls in the position which they occupy during a bending operation;

FIG. 3 is a fragmentary side elevational view taken substantially along line 33 of FIG. 1 and showing the relative positions of the rolls and the cam during the loading of the workpiece;

FIG. 4 is a view similar to FIG. 3 and showing relative positions of the rolls and the cam when the workpiece is being straightened;

FIG. 5 is a view similar to FIG. 4 showing the relative positions of the cam and the roll during unloading of the workpiece;

FIG. 6 is a side elevational view of a workpiece such as a transistor with its leads in a bent condition;

FIG. 7 is a side elevational view of the same transistor of FIG. 6 with its leads straightened;

FIG. 8 is a fragmentary view taken substantially along line 8-8 of FIG. 4 and showing the axial relationship between the series of upper rolls and the series of rocking rolls;

FIG. 9 is a fragmentary schematic view taken substantially along line 99 of FIG. 4, but showing a modified relationship wherein the top and bottom rolls are of different sizes, with the rocking rolls being shown in phantom to indicate their axial relationship relative to the other two sets of rolls;

FIG. I0 is a schematic view of a further modified roll arrangement which is taken in the same direction as line 9-9 of FIG. 3 with the movable rolls in phantom and showing the rolls axially staggered and all of the rolls being of the same hardness;

FIG. II is a view similar to FIG. 10 but showing an arrangement wherein the rolls may be of different hardness;

FIG. 12 is a view similar to FIG. 9 but showing staggered rolls of different hardness;

FIG. 13 is a fragmentary view of a modified wire straightening device and showing spring guide fingers for guiding the article to be straightened between the rollers;

FIG. M is a view of a modified device wherein the fixed rolls are spaced apart approximately the thickness of the wire to be rolled with the rolls in the wire-straightening position;

FIG. 15 is a view similar to FIG. 14 but showing the movement of the movable roll to a position for kicking out the straightened wire workpiece;

FIG. 16 is a side elevational view of a modified form of the invention having a combined clutch and brake for selectively starting and stopping one of the rolls to permit the rotation of the other roll to eject the workpiece from the machine;

FIG. 17 is a schematic view of the cam of the machine and showing the different portions for performing the various functions;

FIG. 18 is a fragmentary side elevational view of the bending rolls in a further modified orientation;

FIG. 19 is a view taken in the direction of arrows 19I9 of FIG. 18;

FIG. 20 is a schematic side elevational view of a further embodiment of the present invention in which all series of the rolls are driven by a linkage which permits one of the series of rolls to be moved away from the other two series to provide a loading position analogous to that shown in FIG. 3 but while maintaining a drive to all three series of rolls;

FIG. 21 is a view similar to FIG. 20 but showing the rolls in a bending position;

FIG. 22 is a view similar to 21 but showing one series of the rolls moved to an unloading position;

FIG. 23 shows a modified linkage which may be used in the embodiment of FIGS. 20 to 22;

FIG. 24 is an end elevational view of a further modified embodiment of the present invention;

FIG. 25 is a plan view of the embodiment of FIG. 24;

FIG. 26 is a side elevational view of a machine for rotating a spindle at high speed with greatly reduced vibration;

FIG. 27 is an end elevational view taken from the right of FIG. 26; and

FIG. 28 is a fragmentary side elevational schematic view showing the workpiece supported by the rolls and showing the manner in which the spindle flexes radially to compensate for irregularities which give rise to vibration.

DESCRIPTION OF THE PREFERRED EMBODIMENTS In FIGS. 1 and 2 a bending machine is shown for carrying out the principles of the present invention. This machine includes a base 11 from which a pair of spaced standards 12 and 12' extend. An upper shaft 13 which is driven from a suitable motor or source (not shown) has spaced end portions journaled in bearings 14 and 15 in spaced

standards

12 and 12, respectively. A lower shaft 16 is joumaled in spaced bearings 17 and 18 which are mounted in spaced standards 12 and 12', respectively. A drive gear 19 has a collar 20 attached thereto which in turn is secured to shaft 13 by setscrew 21 to cause gear 19 to rotate with shaft 13. An idler gear 22 is mounted for rotation on stub shaft 23 extending from standard 12' and is in mesh with gear 19 for the purpose of driving lower gear 24 which is attached to lower shaft 16 by setscrew 25 which extends through collar 26 attached to gear 24. As can be seen from FIG. 2,

shafts

13 and 16 will be driven in the same direction, namely, counterclockwise as indicated by the arrows.

Extending upwardly from base 11 is a bearing block 27 in which a rockshaft 28 is mounted and onto which spaced

arms

29 and 30 are pinned by pins 31 and 32', respectively, for movement in unison as shaft 28 pivots.

Arms

29 and 30 have

bearings

32 and 33 suitably mounted thereon for supporting the spaced ends of shaft 34. In order to cause carrier 35, which consists of

arms

29 and 30, to move back and forth and thus cause shaft 34 to move toward any away from

shafts

13 and 16, a cam 36 is keyed to shaft 13. A cam follower roller 37 is mounted on stub shaft 38 which extends outwardly from the upper end of carrier arm 29. The movement of carrier in a counterclockwise direction in FIG. 2 is against the bias of springs 39 and 39'. Spring 39 has one end anchored on pin 40 attached to standard 12 and the other end attached to pin 41 attached to arm 29 of carrier 35. Spring 39 which is identical to spring 39 extends between arm 30 and standard 12' in an analogous manner. Carrier 35 pivots back and forth about the axis of shaft 28 as it follows the surface 42 of cam 36, as will become more apparent hereafter. Other types of arrangements may be used to pivot carrier 35, such as hydraulic or pneumatic motors, positive cams, or the like.

The straightening of the wire is effected by working the wire while it is located in the opening 43 (FIG. 4) between

rolls

44, and 46. As can be seen from FIG. 1, a series of rolls 44 are mounted in spaced relationship on shaft 13. These rolls are generally in the nature of cylindrical discs and are spaced by portions 47 between adjacent rollers. The unit 44-47 may be machined as an integral piece, or the rolls 44 and spacers 47 may be separately mounted on shaft 13. There is a driving relationship between rolls 44 and shaft 13. Rolls 45 are mounted on shaft 16 and are spaced by spacers 48. The construction may be similar to rolls 44 and spacers 47 discussed above. As can be seen from FIG. 1 in this particular embodiment rolls 45 and 44 are in exact axial alignment with their

peripheries

49 and 50 in contact, as can be seen from FIG. 4. Rolls 46 are mounted on shaft 34, rolls 46 being spaced by spacers 51 in a manner analogous to the other rolls. As can be seen from FIG. 1, rolls 46 are interspersed between axially aligned rolls 44 and 45 so as to define the small space 43 in which the workpiece is located during wire straightening. In the embodiment of FIGS. l-5 rolls 44 are all of equal size, as are

rolls

45 and 46. If desired, each series of

rolls

44, 45 and 46 may differ in diameter from the other series.

The workpiece (FIGS. 6 and 7) which is to be straightened by roll bending machine 10 is transistor or diode 52 having a body portion 53 and wire leads 54 and 55. FIG. 6 shows leads 54 and 55 in a bent condition which exists immediately after manufacturing is completed but before straightening, and FIG. 7 shows leads 54 and 55 after they have been straightened by the present roll bending machine. While the present discussion will be directed to the straightening of transistor lead wires such as 54 and 55, it will be appreciated that the present machine and its underlying principles are applicable to the straightening of any type of wires or rods, whether they are lengths of plain wire or whether they are incorporated into a device such as the transistor 52 shown in the present instance.

In order to load the workpiece 52 into the machine, carrier 35 is swung in a counterclockwise direction about the axis of shaft 28 from the position shown in FIG. 2 to the position shown in FIG. 3. This is efi'ected by causing cam follower 37 to move from point A to point B on cam 36 (FIG. 17). During this movement rolls 46 will move away from both

rolls

44 and 45 to the position shown in FIG. 3 wherein there is a space 56 between

rolls

44 and 46 but there is still a radial overlap between

rolls

45 and 46 to prevent the workpiece from dropping downwardly between them. The workpiece 52 is dropped into space 56 from a suitable automatic hopper or chute, not shown, and it is guided into position by passing between the

arms

57 and 58 of

guides

59 and 60, respectively.

After the cam follower 37 has reached point B on the cam, it will travel along the surface between points B and C to provide an overbending type of action which flexes the leads or

wires

54 and 55 back and forth. This is shown in FIG. 8. It will be appreciated that the diameter of

wires

54 and 55 is extremely small as compared to the diameter of the bending rolls. Therefore, these wires, when driven by the bending rolls, will make an extremely great number of revolutions for every fraction of a revolution of the bending rolls, and therefore notwithstanding that the distance between points B and C on the cam reflects only such a fraction of a revolution of the bending rolls, there will be numerous revolutions of the wires which are to be straightened. This overbending which occurs for a great number of revolutions of the wire, flexes the wires back and forth to insure that all of the extreme bends are removed from

wires

54 and 55 and to also insure that the memory" of the wires, that is, their tendency to return to their original bent condition, cannot cause the wires to return to their bent condition. The overbending is employed for wires which are relatively resilient. However, if the wires are less resilient, the overbending portion of the cam may be eliminated.

At point C on the cam (FIG. 17) the overbending has been completed and cam follower 37 is caused to travel along the surface 42 of the cam between points C and D, which is the straightening portion. In this portion, which extends for a much longer number of degrees than the overbending portion, the opening 43 between all of the rolls is approximately the diameter of the wires to be straightened. It can readily be seen that if the wire to be straightened has reached a perfectly straight condition, it will merely rotate between the rolls without being subjected to a bending action. However, if for any reason the

wires

54 and 55 are not yet straight, they will be flexed back and forth as they are driven with the rolls until such time as they assume a straight condition.

After point D on the cam has been reached by follower 37, the rolls will start to open, that is, rolls 46 will be moved away from

rolls

44 and 45 because follower roll 37 will travel from point D to point A on the surface 42 of cam 36. The limit of counterclockwise movement of carrier 35 in FIG. 2 is shown in FIG. 5. Rolls 46 are now spaced from rolls 45 and do not have the overlapping relationship therewith shown in FIG. 3 during loading. This will cause roll 45, which is rotating in a counterclockwise direction, to move the workpiece to the left and cause it to pass through the space 62 between spaced

arms

63 and 64 of

guides

59 and 60 and fall downwardly in the direction of arrow 61. In the embodiment of FIGS. 1-5 and 8, all of the

rolls

44, 45 and 46 are of equal hardness.

It is to be noted from FIGS. 1 and 2 that a roll 66 is mounted centrally on shaft 34 and is spaced from adjacent rolls 46 by spacers 67. As can best be seen from FIG. 8, roll 66 is located in contiguous relationship to body 53 of the transistor and acts to prevent it from shipping about excessively during the roll straightening operation. Roll 66 is mounted on a bearing 66' so that it can rotate freely as required when it is in engagement with body 53. If required, any of the other rollers may be mounted on separate bearings if additional spaced bodies, such as 53, are on the workpiece.

As noted above relative to the embodiment of FIGS. I through 5 and 8, the peripheries 49 and 50 (FIG. 4) of

rolls

44 and 45, respectively, are substantially in engagement and roll against each other. FIG. 9 is taken along line 9-9 of FIG. 4 but shows a modification from FIGS. 1 and 2 only in the respect that alternating rolls of different sizes are mounted on shafts I3 and I6 to contribute a slight overbending action for the purpose of flexing the wires back and forth for a number of revolutions to remove the bends and erase any memory" in the wire, as defined above. More specifically, rolls 44 and 44" are mounted in alternating relationship on shaft 13. Rolls 44' are of slightly greater diameter than rolls 44". Rolls 45' and 45 are mounted in alternating relationship on shaft 16. Rolls 45' are of slightly greater diameter than rolls 45". While the larger and smaller rolls were. shown as being substantially in contact in FIG. 9, if desired the smaller rolls on one or both shafts may be made of still smaller diameter so that they are not in contact with the larger rolls. If desired, the overbending portion may be omitted from the cam, as the difference in roll size can produce the overbending. The difference in the size between the larger and smaller rolls on both of the shafts is relatively small, possibly on the magnitude of a few thousandths of an inch, depending on the size of the wire. Rolls 46 are shown in phantom in FIG. 9. In an actual model rolls 44' and 45' were 2.010 inches and rolls 44" and 45" were 2.000 inches and the wire was 0.020 inches in diameter.

It can readily be visualized that during the overbending portion of the cycle, that is, while the cam follower 37 is moving between points D and C on cam 36, alternate lengths of the

wires

54 and 55 will be worked back and forth to remove any excessive bends in the wire and also provide overbending of an amount which will prevent the memory of the wire from causing the wire to return or tend to return to its original bent state. However, as the cam follower moves between points C and D on cam 36, rolls 46 will be moved away from the other two sets of rolls so that the space or opening 43 between the rolls will be larger. During this portion of the cycle the overbending effect will not be present and the wire will be straightened because the exaggerated condition depicted in FIG. 9 no longer exists because rolls 46 no longer force the wires tightly between the other two sets of rolls, but permit the wire to move to the left in space 43 in FIG. 4 where the staggered relationship between the

rolls

44, 45, 44", 45" cannot affect the wire.

In FIG. 10 another embodiment of the present invention is disclosed which is taken generally along line 9--9 of FIG. 4 but shows an orientation of rolls which is different from that shown in FIGS. 8 and 9. Rolls 46, that is, those mounted on the carrier 35, are identical to the previous embodiments but rolls 46, I44 and 145 are axially staggered relative to each other.

Rolls

144 and 145 are of larger diameter than

rolls

44 and 45, respectively, of the preceding figures so that they overlap radially with each other slightly and with rolls 46. The orientation of rolls shown in FIG. 10 is intended to be used on the machine of FIGS. I and 2.

FIG. II shows the same orientation of rolls as is shown in FIG. I0, except in this embodiment, which differs from the preceding embodiments. Various of the rolls are of different hardness. In this embodiment, rolls I45 may be harder than rolls 144 or vice versa, with the softer rolls providing a better traction on the workpiece. Alternatively, alternate rolls 145' on one shaft and alternate rolls 144' on the other may be of different hardness, with the softer rolls providing good traction.

In FIG. 12 a still further embodiment of the present invention is disclosed. In this embodiment the rolls are oriented in the same manner as those of FIG. 9. However, the top rolls 244 and 244', which are mounted on shaft I3, are of the same diameter, respectively, as are bottom rolls 245 and 245', respectively, which are mounted on shaft 16. However, the rolls 244 and 245' which are mounted on shaft 13 are relatively soft whereas the

rolls

245 and 244 which are mounted on shaft I6 are relatively hard. This difference in hardness gives a relatively good straightening effect because it permits overbending of the wires, as required to provide straightening because the soft rolls may yield somewhat too during the process of straightening, as can be seen from the drawing. In other words, in addition to the overbending provided by rolls 46 overlapping radially with the other rolls, there is an overbending due to the fact that the relatively soft rolls can yield when the opposed relatively hard rolls press the wire against them.

In FIG. I3 a modification which may be applied to FIGS. 1 and 2 is shown. This modification utilizes a pair of spaced

wire fingers

70 and 71 which extend downwardly from a suitable support, not shown, into the opening between the three sets of coacting rolls at their central location where the body of the device to be straightened is received. In this instance there is shown a resistor 72 having a body 73 and wires 74 and 75 extending from opposite ends thereof. The

wires

70 and 71 support the wires on opposite sides of body 73 so as to guide the resistor 72 into position where the wires 74 and 75 are straightened. In FIG. 13 rolls 44' and 45 are analogous to the identically numbered rolls shown in FIG. 9.

In FIGS. 14 and 25 a still further modification of the present invention is disclosed. In this modification three shafts l3, l6 and 34 are provided which are identical to like-numbered shafts in FIGS. [-5. In this embodiment top rolls 76 and bottom rolls 77 rotate in a stationary position and they are analogous to

rolls

44 and 45 of FIGS. l-5. All of the series of rolls 76 are of the same size and all of the rolls 77 are of the same size and both series of rolls are of the same diameter. However, it is to be noted that the

peripheries

78 and 79 of

rolls

76 and 77, respectively, are spaced apart at 80 whereas the peripheries of

rolls

44 and 45 of FIGS. 1-5 were substantially in contact. Rolls 46 which are identical to rolls 46 of FIGS. 1-5 are mounted on shaft 34. In this embodiment the workpiece or wire 81 which is to be straightened is deposited between the rolls in the same manner as described in detail above relative to FIGS. l-5. In FIG. 14 rolls 46 are shown in the straightening position. When the wire initially drops between the rolls, it will be in a bent condition and therefore it will stay in position in the opening 80 because it is in engagement with the peripheries of the three rolls. The space 80 at its narrowest dimension is equal to the diameter of the wire. The cam associated with FIGS. 14 and I5, which is not shown in the drawings, is generally similar to cam 36 of FIG. ll, except that it includes a portion at the end of the straightening portion which causes rolls 46 to move to the right. Therefore after the wire has become straightened, rolls 46 will be moved in the direction of the arrow to force the wires through space 80 to eject the wires from their work position shown in FIG. 14 and move them to the position shown in FIG. 15 preparatory to their discharge from the machine. If desired either of

rolls

76 or 77 may be softer than the rolls axially aligned with them. In this case space 80 can be smaller than the diameter of the wire because the soft roll will yield when the wire 81 is forced through this space.

In FIG. I6 a still further modification of the present invention is shown. In this modification standard 12' is identical to standard 12' of FIG. I as are

gears

19, 24 and 22 on the shafts on which they are mounted. In this embodiment shaft 16 is driven. A combined clutch brake mechanism 82' has a housing 82 which includes

collars

83 and 84 which are fixed relative to each other and collar 84 is fixedly mounted relative to standard 13. Gear 19 is joumaled between

collars

83 and 84 and is in driving engagement with a combined clutch-brake mechanism within housing 82 which is energized from an extemal source, not shown. In the operation of this embodiment the workpiece is loaded into the machine as described in detail above relative to FIGS. 1 and 2.

Except for the structure shown in FIG. 16 the remainder of the machine of FIG. 16 is identical to that shown in FIGS 1 and 2. When the unloading portion of the cam 36 is reached by the cam follower 37, the drive from gear 19 through the clutch within housing 82 will be terminated so that shaft 13 is no longer driven but instead a brake within housing 82 will lock shaft 13 to stop it. The direction of rotation of shaft 16 is the same as shown in FIGS. 2 and 5 and therefore the continued rotation of shaft 16 will cause the workpiece which is between series of

rolls

44 and 45 to be ejected to the left after rolls 46 have swung outwardly to the position shown in FIG. 5.

In FIGS. 18 and 19 a further modified orientation of the rolls are shown. In this modification, rolls 344, 345 and 346, which are analogous to

rolls

44, 45 and 46, respectively, of FIGS. 1-5, overlap radially a substantial amount as is best shown in FIG. 19, that is, the arcs or surfaces of each of the rolls intersect the arcs or surfaces of each of two of the other rolls incidental to providing the opening 90 in which the workpiece is located during the bending operation. It is to be noted that rolls 344, 345 and 346 are intended to be mounted on shafts such as l3, l6 and 34, respectively, of the machine of FIG. 1. Because of the overlapping relationship shown in FIG. 19, an equal pressure is exerted on the workpiece at 120 intervals on its periphery, thereby insuring a precise straightening. It is also to be noted relative to FIGS. 18 and 19 that the four-stage cycle is maintained, namely, the loading, overbending, bending and discharging of the workpiece, as described in detail above, relative to FIG. 1. However, the overbending portion of the cycle can be omitted, if desired, where less resilient workpieces permit this.

In FIGS. 20, 21 and 22 a further modification of the present invention is shown in which series of

rolls

444, 445 and 446 are analogous to series of

rolls

44, 45 and 46 of FIGS. 1 and 2 and are oriented in the same manner as shown in these Figures on shafts I3, 16' and 34, which are analogous to

shafts

13, 16 and 34 of FIG. 1. The frame on which the shafts and the rolls are mounted is generally similar to that shown in FIGS. 1 and 2. However, there are modifications which will become apparent hereafter because of the manner in which this embodiment operates. The loading position is shown in FIG. wherein rolls 446 have been moved away from rolls 444 and 445 in the direction of arrow 91. This moving away is effected by the use of a suitable cam follower or the like which is journaled onto shaft 34' or otherwise connected to link 92. It will be appreciated that shaft 34 has one end journaled in link 92 and the other end journaled in a counterpart link (not shown) which is identical to link 92 and which is mounted in a similar manner and which is rigidly connected relative to link 92. When rolls 444 and 446 are separated, the workpiece is dropped into space 93, as described in detail above relative to FIGS. 1, 2 and 3. While this is occurring shaft 13', which is driven, drives shaft 34' because of the

gear train

19', 94, 95, 96 and 24". Gears 19 and 24' are analogous to

gears

19 and 24 of FIG. 2.

Gears

94, 95 and 96 are idler gears mounted on

stub shafts

97, 98 and 99, respectively, which in turn are mounted on frame 100 affixed to the machine, preferably to a standard such as 12' of FIG. 1.

In FIGS. 20, 21 and 22 shaft 13' is fixed in position between frame portion 100 and a standard such as 12 shown in FIG. 2, that is, shaft 13' rotates but does not move or change its position in any other respect. In moving rolls 446 from the position shown in FIG. 21 to the position shown in FIG. 20, link 92 and its counterpart (not shown) are pivoted in a clockwise direction about the axis of shaft 99, and to return them to the position shown in FIG. 21, they are pivoted in a counterclockwise direction about the axis of shaft 99. As explained above relative to FIGS. 1 through 5, when rolls 446 are returned to a position such as shown in FIG. 21, the cam or other linkage which moves link 92 causes it to move to such a position where it effects overbending, as described in detail above, and thereafter it is backed off to provide a straightening action wherein the workpiece is straightened. It is to be noted that since

rolls

444, 445, and 446 are positively driven, there can be no slippage between the workpiece and any of the rolls, thereby to obviate the possibility of scoring or marring of the workpiece. As noted above relative to the other embodiments, the overbending can be eliminated, by suitable modification of the cam, for certain less resilient workpieces.

In order to facilitate ejection of the workpiece, rolls 445 are swung to the position shown in FIG. 22 from the position shown in FIG. 21. This is possible because shaft 16 is mounted on link 101 which also mounts stub shaft 102 on which idler gear 103 is journaled, and which is in mesh with both drive gear 19 and driven gear 24'. In order to cause rolls 445 to move to the position shown in FIG. 22 from the position shown in FIG. 21, a suitable linkage is attached to link 101 and this linkage is driven from a cam or the like, not shown, which is synchronized with the operation of the remainder of the machine. It will be appreciated that one end of shaft 16' is mounted on link 101 and the other end is mounted on a counterpart link which is similar to link 101 and which pivots about the axis ofshaft 13', and which is rigidly affixed relative to link 101.

After the workpiece has been ejected in the direction of the arrow 105 in FIG. 22, the rolls 445 will be returned to the position shown in FIG. 21 and rolls 446 will be moved to the position shown in FIG. 20 to effect a subsequent loading cycle.

In FIG. 23 a modification of the embodiment of FIGS. 20 to 22 is shown. In this embodiment rolls 446, gear 24" and link 92 are identical to the preceding figures, as are gear 97 and gear 19'. The drive between rolls 446 and 444 is identical to that discussed above relative to FIGS. 20 to 22. In this embodiment however rolls 445 can be swung independently relative to rolls 444 so that the space between them can be varied, whereas this is not possible in the embodiment of FIGS. 20-22. More specifically, a link is pivotally mounted by pin III on extension 112 of frame 100. Rolls 445 are mounted on shaft 113 which extends between link I10 and a spaced counterpart link (not shown) mounted on a spaced counterpart of extension 112. Link 110 and its counterpart are secured for movement in unison by a suitable link not shown. Link 110, as noted above, pivots about the axis of shaft 11 1 in response to a suitable motivating arrangement, such as a cam or motor. Rolls 445 are driven through gears 19', 103' and 114, the latter being keyed to shaft 113.

Since the embodiment of FIG. 23 is identical in all respects to the embodiment in FIGS. 20-22 except for the structure described immediately above, it can readily be seen that the space between rolls 444 and 446 may be varied by the movement of link 92 and its counterpart link so that a workpiece may be deposited between the rolls. At this time roll 445 will occupy a position such as shown in FIG. 20. Thereafter rolls 446 are moved the shown in FIG. 21 to effect the straightening of the workpiece, and thereafter links 110 are moved in the direction of the arrow in FIG. 23 in order to provide a space between the rolls for discharge of the workpiece. Thus, in FIG. 23 there is an arrangement wherein both

rolls

446 and 445 can be moved toward and away from each other and from stationary rolls 444, whereas in FIGS. 20-22 while

rolls

445 and 446 can be moved away from each other, and rolls 446 can be moved away from rolls 444, rolls 445 could not be moved away from rolls 444. In other words, in FIG. 23 rolls 446 can move toward and away from rolls 444 and 445 and rolls 445 can move toward and away from rolls 446 and rolls 444. In FIGS. 20-23 all of the rolls are driven through the gear arrangement.

In FIGS. 24 and 25 a still further embodiment of the present invention is shown. This embodiment is similar to that discussed above relative to FIG. 23 in the sense that one of the series of rolls is fixed against radial movement on the frame and each of the other two series is radially movable toward and away from the fixed series. The straightening machine includes a base having a pair of spaced

upstanding standards

121 and 122 thereon connected by cross member 120. Located to the side of standard 122 is a motor 123 which is coupled to gear reducer 124 having an output gear 125 which rotates about the axis of shaft 126. Gear 125 is in mesh with gear 127 mounted on shaft 128 which extends between

standards

121 and 122. A plurality of spaced rolls 130 (omitted in the interest of clarity from 1116. 25) are also mounted on shaft 1211. lltolls 13 0, while rotatable, are not radially movable on

standards

121 and 122. Gear 125 is also in mesh with gear 131 which is mounted on shaft 132 having its opposite ends mounted in

bearings

133 and 134 which are located in spaced

arms

136 and 137, respectively, of carrier 13%. Spaced

arms

136 and 137 are connected by frame portion 138'. A plurality of rolls 135 are spacedly mounted on shaft 132. Ht can thus be seen that motor 123 drives both series of rolls 13111 and 135. Arm 136 terminates in extension 1216 which is pivotally mounted on pin or stub shaft 126 secured to ear 121 of standard 121. A counterpart (not shown) of extension 136' extends downwardly from arm 137. A counterpart of pin 126 extends between standard 122 and the counterpart of extension 136. Because of the connection of the extensions, namely, 136 and its counterpart to pin 126 and its counterpart, the carrier frame 138 can pivot about the axis of pin 126 so that rolls 135 can be moved toward and away from rolls 130. To achieve this a fluid motor 139 has one end M11 pivotally secured between arm portions 1 11 of base 1211 and piston rod 142 pivotally secured to spaced arms 1113 forming an extension of carrier 1311. Suitable connections and conduits (not shown) are supplied to fluid motor 139 to cause the piston and rod 1 12 attached thereto to move in and out of the cylinder with which it is associated and thus pivot carrier 13% in a clockwise and counterclockwise direction, respectively.

Also pivotally mounted on base 120 is a second carrier 144 having spaced arms M and 146, connected by portion 145', and mounting bearings 14 7 and 1418, respectively, which support the opposite ends of shaft 149, which in turn supports spaced rolls 150. Spaced arms 1 and 1416 of carrier 1% are mounted on shaft 151 which extends through crossmember 120' of base 1211. Carrier 1% is caused to pivot about shaft 151 whenever fluid motor 152 is actuated. This motor is pivotally mounted by means of a trunnion 153 to base 120. This piston rod 154 is connected to carrier 1414 by means of pin 155 which extends between spaced ears 155. The connections to fluid motor 152 are not shown but it will be appreciated that when piston rod 154 is driven upwardly in FIG. 24, carrier 1 14 will pivot in a counterclockwise direction and when piston 1541 is driven downwardly carrier 1441 will pivot in a clockwise direction. The use of

fluid motors

139 and 152 permits varying the pressure applied to the workpiece. This permits an overbending action to be obtained by supplying a relatively high pressure to motor 152, followed by a lower pressure for the straightening portion of the cycle. If desired the overbending may be eliminated for less resilient workpieces. In fact any desired sequence of pressures may be applied to the workpiece by varying the pressure to fluid motor 152 accordingly.

As can be visualized from FlG. 2 1, there is a large rectangular opening 161 in carrier 13%. This opening extends between

arms

136 and 137. An elongated opening 162 is in communication therewith and also extends between

arms

136 and 137. it is through these two openings that workpieces are deposited between the rolls. More specifically, during the loading cycle, carrier 1 1 1 is in the position shown in F161. 24! with rolls 150 away from rolls 135. The workpiece is deposited through the above openings 161 and 162 into space 163. At this time rolls 135 and 1311 occupy the positions shown in MG. 241. Thereafter, motor 152 is actuated to cause carrier 1441 to pivot in a counterclockwise direction so as to cause the workpiece to be acted on by the three series of rolls. After rolling is complete, fluid motor 125 is actuated to pivot carrier 138 in a counterclockwise direction. This will cause rolls 135 to move away from rolls 1311 and thus provide a discharge opening therebetween through which the workpiece can be dropped into discharge chute 16 1 between

standards

121 and 122.

While rolls are not shown in plan, because they were omitted from 116. 25 in the interest of clarity, it will be appreciated that they occupy the same relationship to rolls as do rolls 14 to rolls 45 in HQ 1. It will be appreciated however that any roll combination discussed above relative to any of the preceding figures of the present invention can be incorporated in the embodiments of FIGS. 24 and 25. it is to be noted that a roll is mounted on shaft 149 and this roll is analogous both by way of mounting and function to roll 66 of FIG. 1.

it will also be appreciated that any of the roll arrangements shown in the drawings and discussed above can be mounted on any of the bases shown in FIGS. 1 and 2 and 20-25.

While the preceding portions of the description have been directed primarily to straightening of wire, it will be appreciated that the principles of the present invention can be applied to any elongated workpieces including rods, tubes and the like.

Furthermore, it was specifically noted above relative to certain embodiments that the overbending portion of the cycle could be eliminated for workpieces where this was not required. it will be appreciated that any of the embodiments of the invention may be practiced with or without the overbending which is provided by the cam action or the like. In other words, the cam may be modified so as not to provide overbending.

lln FIGS. 26, 27 and 211 a high-speed spindle driving machine is shown for driving a spindle at ultrahigh speeds without overheating of bearings while minimizing the vibration and chatter of the spindle which may normally accompany such high-speed operation. This machine includes a base 176 having spaced upstanding standards 177 and 178 mounting shafts 179 and 181) therein in suitable bearings (not numbered). Shaft 17% mounts a plurality of spaced rolls 181 of equal diameter and shaft 180 mounts a plurality of spaced rolls 182 of equal diameter which are axially offset from rolls 181 and are radially overlapping relationship therewith. A pulley 182' is fixedly secured to shaft 179 and a pulley 183 is fixedly secured to shaft 11111. A belt 184, which is driven from a suitable source, encircles pulleys 182' and 183 to drive them in the same direction.

A carrier 185 is provided which includes spaced

arms

186 and 187 connected by cross-portion 188 which receives shaft 189 mounted in arms 1911 and 191 extending from standards 178 and 177, respectively. Cross-portion 188 also threadably receives a jackscrew 192 in tapped portion 193. Screw 192 abuts base 176 (FlG. 27) to pivot carrier 185 about the axis of shaft 189 and thus move the carrier 185 toward and away from rolls 151 and 1321.

A shaft 195 has its opposite ends rotatably mounted in suitable bearings (not numbered) in

carrier arms

186 and 187. Spacedly mounted on shaft 195 are rolls 196 of equal diameter which are axially offset (FIG. 26) from

rolls

181 and 182 and are placed in radially overlapping relationship therewith (FlG. 27) when a spindle is clamped between the rolls. Preferably the diameter of the workpiece has such a relationship to the diameter of the

rolls

181, 182 and 196 so that radially overlapping relationship between the rolls exists.

it will readily be appreciated that the linear speed of the surface of spindle 197 will be the same as the linear speed of the surfaces of

rolls

181, 182 and 196 in contact therewith, but because of the relatively large diameters of the rolls as compared to the spindle, the spindle will have a much greater angular speed. This means the spindle 197 can be rotated at relatively high speeds, as is well known. Normally, when a spindle, which may be a tool, such as a punch or the like which is to be ground, or a shaft for mounting a tool, is rotated at extremely high speeds which may be in excess of 100,000 r.p.m. any small irregularities or eccentricities of the spindle or in the mounting of the rolls which drive the spindle will be greatly magnified to produce undesirable chatter, vibration, or the like. The orientation of the

rolls

181, 182 and 196 tends to obviate the foregoing objectionable characteristics. More specifically, first of all because of the radial overlap of each of the series of rolls with two of each of the other series, a good centering action is obtained wherein the round workpiece is supported by the supporting rolls at 120 increments about its periphery. This will provide a balanced supporting force on the spindle. This 120 relationship will vary somewhat with the size of the spindle. Furthermore, because the rolls radially overlap with each other, there will be a size relationship between the spindle and the rolls which provides a good degree of contact therebetween.

As noted above, each of the rolls of each series is axially off set from each of the rolls of the other series, as can best be seen from FIG. 26. This produces an action on spindle 197 which permits its axis 198 to deflect, as required, away from the force causing the deflections. This is shown in a greatly magnified and exaggerated manner in the schematic of FIG. 28, wherein the axis 198 is shown deflected merely because of the pressure applied by the rolls. The foregoing deflection of the shaft is less than a few ten thousandths of an inch for a shaft of less than 1 inch diameter. Stated another way, because

rolls

181, 182 and 196 are not in direct opposition to each other on diametrically opposed portions of the spindle, the spindle can flex so as to absorb any unbalancing forces applied thereto without producing attendant vibration and chatter. Thus, regardless of whether the forces are due to eccentricities in the shaft itself or in the mounting of the driving rolls of other factors, these forces will be taken up or absorbed by the deflection of the spindle 197, which is possible because of the fact that it is not supported at diametrically opposed portions along its length. Furthermore, because there are a great number of rolls mounted on each of the shafts, the spindle 197 is supported for a substantial portion of its length so as to provide a firm mounting. in addition, because of the contact of a plurality of rolls on each shaft with the spindle, the driving pressure need not be excessive because there are a large number of rolls in contact with the spindle. In essence, therefore, spindle 197 will float, and its axis will remain relatively true during rotation because its axis is actually determined by averaging all of the individual deflections which occur. If desired a suitable provision may be made to lock the spindle against endwise travel.

lclaim:

l. A machine for straightening an elongated workpiece comprising a base, a first shaft, a series of first rolls spacedly and coaxially mounted on said first shaft, a second shaft laterally ofiset from said first shaft and extending in substantially the same direction as said first shaft, a series of second rolls spacedly and coaxially mounted on said second shaft with their peripheries in contiguous relationship to said first rolls, a third shaft laterally offset from said first and second shafts and extending in substantially the same direction, a series of third rolls spacedly and coaxially mounted on said third shaft with their peripheries in contiguous relationship to said first and second rolls to define an opening between said first and second and third rolls for receiving a workpiece to be straightened, and said series of third rolls extending between said first and second rolls in radially overlapping relationship therewith, said first and second rolls being substantially in axial alignment with each other, both said first and second rolls comprising alternating relatively hard and relatively soft rolls, and said rolls which are in axial alignment comprising one of said relatively hard rolls and one of said relatively soft rolls.

2. A machine for straightening an elongated workpiece comprising a base, a first shaft, a series of first rolls spacedly and coaxially mounted on said first shaft, a second shaft laterally offset from said first shaft and extending in substantially the same direction as said first shaft, a series of second rolls spacedly and coaxially mounted on said second shaft with their peripheries in contiguous relationship to said first rolls, a third shaft laterally offset from said first and second shafts and extending in substantially the same direction, a series of third rolls spacedly and coaxially mounted on said third shaft with their peripheries in contiguous relationship to said first and second rolls to define an opening between said first and second and third rolls for receiving a workpiece to be straightened, and said series of third rolls extending between said first and second rolls in radially overlapping relationship therewith, said first and second rolls being substantially in axial alignment with each other, both said first and second rolls comprising alternating rolls of first and second diameters with said rolls of said first diameter being slightly larger than said rolls of said second diameter, and said first and second rolls which are in axial alignment comprising one of said rolls of said first diameter and one of said rolls of said second diameter.

3. A machine for straightening an elongated workpiece comprising a base, a first shaft, a series of first rolls spacedly and coaxially mounted on said first shaft, a second shaft laterally offset from said first shaft and extending in substantially the same direction as said first shaft, a series of second rolls spacedly and coaxially mounted on said second shaft with their peripheries in contiguous relationship to said first rolls, a third shaft laterally offset from said first and second shafts and extending in substantially the same direction, a series of third rolls spacedly and coaxially mounted on said third shaft with their peripheries in contiguous relationship to said first and second rolls to define an opening between said first and second and third rolls for receiving a workpiece to be straightened, and said series of third rolls extending between said first and second rolls in radially overlapping relationship therewith, said first, second and third rolls being axially offset from each other, and said first and second rolls including rolls of different hardness.

4. A machine for straightening an elongated workpiece comprising a base, a first shaft, a series of first rolls spacedly and coaxially mounted on said first shaft, a second shaft laterally offset from said first shaft and extending in substantially the same direction as said first shaft, a series of second rolls spacedly and coaxially mounted on said second shaft with their peripheries in contiguous relationship to said first rolls, a third shaft laterally offset from said first and second shafts and extending in substantially the same direction, a series of third rolls spacedly and coaxially mounted on said third shaft with their peripheries in contiguous relationship to said first and second rolls to define an opening between said first and second and third rolls for receiving a workpiece to be straightened, and said series of third rolls extending between said first and second rolls in radially overlapping relationship therewith, said first, second and third rolls being axially offset from each other, said first and second rolls overlapping in a radial direction.

5. A machine for straightening an elongated workpiece comprising a base, a first shaft, a series of first rolls spacedly and coaxially mounted on said first shaft, a second shaft laterally offset from said first shaft and extending in substantially the same direction as said first shaft, a series of second rolls spacedly and coaxially mounted on said second shaft with their peripheries in contiguous relationship to said first rolls, a third shaft laterally offset from said first and second shafts and extending in substantially the same direction, a series of third rolls spacedly and coaxially mounted on said third shaft with their peripheries in contiguous relationship to said first and second rolls to define an opening between said first and second and third rolls for receiving a workpiece to be straightened, said series of third rolls extending between said first and second rolls in radially overlapping relationship therewith, and means for positioning said first and second and third rolls relative to each other to cause said opening to be of a first dimension to initially overbend said workpiece as said workpiece is being rotated while in contact with said rolls, and for subsequently causing said opening to be of a second dimension which is larger than said first dimension to straighten said workpiece.

6. A machine for straightening an elongated workpiece comprising a base, a first shaft, a series of first rolls spacedly and coaxially mounted on said first shaft, a second shaft laterally offset from said first shaft and extending in substantially the same direction as said first shaft, a series of second rolls spacedly and coaxially mounted on said second shaft with their peripheries in contiguous relationship to said first rolls, a third shaft laterally offset from said first and second shafts and extending in substantially the same direction, a series of third rolls spacedly and coaxially mounted on said third shaft with their peripheries in contiguous relationship to said first and second rolls to define an opening between said first and second and third rolls for receiving a workpiece to be straightened, said series of third rolls extending between said first and second rolls in radially overlapping relationship therewith, and means for opening the space between said rolls to radially admit said workpiece into said opening for straightening and for opening the space between the rolls to permit a workpiece to be discharged from said opening.

7. A machine for straightening an elongated workpiece comprising a base, a first shaft, a series of first rolls spacedly and coaxially mounted on said first shaft, a second shaft laterally offset from said first shaft and extending in substantially the same direction as said first shaft, a series of second rolls spacedly and coaxially mounted on said second shaft with their peripheries in contiguous relationship to said first rolls, a third shaft laterally offset from said first and second shafts and extending in substantially the same direction, a series of third rolls spacedly and coaxially mounted on said third shaft with their peripheries in contiguous relationship to said first and second rolls to define an opening between said first and second and third rolls for receiving a workpiece to be straightened, said series of third rolls extending between said first and second rolls in radially overlapping relationship therewith, and first means for moving said third rolls toward and away from said first rolls for providing a space between said first rolls and said third rolls for loading said workpiece into said opening in a direction radially of said first and third rolls, and second means for moving said second rolls toward and away from said first rolls for unloading said workpiece from said opening in a direction radially of said second and first rolls.

8. A machine for straightening an elongated workpiece comprising a base, a first shaft, a series of first rolls spacedly and coaxially mounted on said first shaft, a second shaft laterally offset from said first shaft and extending in substantially the same direction as said first shaft, a series of second rolls spacedly and coaxially mounted on said second shaft with their peripheries in contiguous relationship to said first rolls, a third shaft laterally offset from said first and second shafts and extending in substantially the same direction, a series of third rolls spacedly and coaxially mounted on said third shaft with their peripheries in contiguous relationship to said first and second rolls to define an opening between said first and second and third rolls for receiving a workpiece to be straightened, said series of third rolls extending between said first and second rolls in radially overlapping relationship therewith, and fourth roll means on one of said shafts, said fourth roll means being of lesser diameter than the remainder of said rolls on said shaft, and means journaling said fourth roll means on said shaft for rotation independently of the remainder of said rolls on said shaft.

9. A machine for rotating an elongated spindle comprising a base, a first shaft, a series of first rolls spacedly and coaxially mounted on said first shaft, a second shaft extending substantially parallel to said first shaft, a series of second rolls spacedly and coaxially mounted on said second shaft and being axially offset from said first rolls, a third shaft extending substantially parallel to said first and second shafts, a series of third rolls spacedly and coaxially mounted on said third shaft and being axially offset from said first and second rolls and being positioned relative thereto to define an opening between said first and second and third rolls for receiving said spindle so as to support said spindle along a substantial portion of its length at axially and circumferentially spaced locations while permitting axial portions thereof to flex radially in various directions during rotation because of said axial and circumferential spacing of said first, second, and third rolls, each of said first, second, and third series of rolls being in radially overlapping relationship with each of the other two series.

10. A machine for straightening an elongated workpiece as set forth in claim 4 wherein said first and second rolls include rolls of different hardness.

1 l. A machine for straightening an elongated workpiece as set forth in claim 5 wherein said means for positioning said first and second and third rolls relative to each other comprises a carrier mounted on said base, said third shaft being mounted on said carrier, and means for moving said carrier toward and away from said first and second shafts.

12. A machine for straightening an elongated workpiece as set forth in claim 111 wherein said means for moving said carrier comprises a fluid motor.

13. A machine for straightening an elongated workpiece as set forth in claim 11 wherein said means for moving said carrier includes a pivot mounting said carrier on said base, and means operatively connected between said carrier and said base for moving said third shaft toward said first and second shafts.

14. A machine for straightening an elongated workpiece as set forth in claim 13 wherein said last-mentioned means comprises a cam mounted on said first shaft.

15. A machine for straightening an elongated workpiece as set forth in claim 5 including gear means on said first and second shafts for causing said first and second series of rolls on said first and second shafts to rotate at the same peripheral speed and in the same direction.

16. A machine for straightening an elongated workpiece as set forth in claim 6 wherein said means for opening the space between said rollers comprises a carrier, said third shaft being mounted on said carrier, means mounting said carrier for movement on said base, and means for moving said carrier for movement on said base, and means for moving said carrier toward and away from said first and second rolls.

17. A machine for straightening an elongated workpiece as set forth in claim 16 including means for driving said first and second rolls.

18. A machine for straightening an elongated workpiece as set forth in claim 17 including means for driving said third shaft.

19. A machine for straightening an elongated workpiece as set forth in claim 7 including third means for moving said second rolls away from said first rolls.

20. A machine for straightening an elongated workpiece as set forth in claim 7 including means for driving said first and second rolls.

21. A machine for straightening an elongated workpiece as set forth in claim 20 including means for driving said third rolls.

22. A machine for straightening an elongated workpiece as set forth in claim 7 wherein said means for moving said third and second rolls comprise'first and second carriers, respectively, and fluid motors for moving said carriers.

23. A machine for straightening an elongated workpiece as set forth in claim 22 including means for pivotally mounting said first and second carriers on said base.

24. A machine for straightening an elongated workpiece as set forth in claim 5 wherein said first and second rolls are substantially in axial alignment with each other.

25. A machine for straightening an elongated workpiece as set forth in claim 24 wherein both said first and second rolls comprise alternating relatively hard and relatively soft rolls, and wherein said rolls which are in axial alignment comprise one of said relatively hard rolls and one of said relatively soft rolls.

26. A machine for straightening an elongated workpiece as set forth in claim 24 wherein both said first and second rolls comprise alternating rolls of first and second diameters wherein said rolls of said first diameter are slightly larger than said rolls of said second diameter, and wherein said first and in a radial direction.

30. A machine for straightening an elongated workpiece as set forth in claim 29 wherein said first and second rolls include rolls of different hardness.

31. A machine for rotating an elongated spindle as set forth in claim 9 including means for driving said rolls.

32. A machine for rotating an elongated spindle as set forth in claim 31 including means for moving said third rolls toward and away from said first and second rolls.

l i t i l $3? UNITED STATES PATENT CERTIFICATE OF CGllRECTlQh Patent N 3I625!263 Dated December 7,

Inventor) John F. Kopczynski It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

Column 3, line 40, change "any" to and-; line 47, change "39" to 39'.

Column 5, line 5, change "shipping" to -whipping. Column 6, line 32, change "25" to --l5-.

Column 8, line 55, after "moved" insert -into, and before "shown" insert -position.

Column 9, line 43, change "This" to --The-; line 71, change 129" to -l39.

Column 1G, line 38, before "radially" insert in--; line 58, after "that" insert the-.

5 gnarl and sealed 23rd day of v o g

Claims

1. A machine for straightening an elongated workpiece comprising a base, a first shaft, a series of first rolls spacedly and coaxially mounted on said first shaft, a second shaft laterally offset from said first shaft and extending in substantially the same direction as said first shaft, a series of second rolls spacedly and coaxially mounted on said second shaft with their peripheries in contiguous relationship to said first rolls, a third shaft laterally offset from said first and second shafts and extending in substantially the same direction, a series of third rolls spacedly and coaxially mounted on said third shaft with their peripheries in contiguous relationship to said first and second rolls to define an opening between said first and second and third rolls for receiving a workpiece to be straightened, and said series of third rolls extending between said first and second rolls in radially overlapping relationship therewith, said first and second rolls being substantially in axial alignment with each other, both said first and second rolls comprising alternating relatively hard and relatively soft rolls, and said rolls which are in axial alignment comprising one of said relatively hard rolls and one of said relatively soft rolls.

11. A machine for straightening an elongated workpiece as set forth in claim 5 wherein said means for positioning said first and second and third rolls relative to each other comprises a carrier mounted on said base, said third shaft being mounted on said carrier, and means for moving said carrier toward and away from said first and second shafts.

12. A machine for straightening an elongated workpiece as set forth in claim 11 wherein said means for moving said carrier comprises a fluid motor.

22. A machine for straightening an elongated workpiece as set forth in claim 7 wherein said means for moving said third and second rolls comprise first and second carriers, respectively, and fluid motors for moving said carriers.

26. A machine for straightening an elongated workpiece as set forth in claim 24 wherein both said first and second rolls comprise alternating rolls of first and second diameters wherein said rolls of said first diameter are slightly larger than said rolls of said second diameter, and wherein said first and second rolls which are in axial alignment comprise one of said rolls of said first diameter and one of said rolls of said second diameter.

27. A machine for straightening an elongated workpiece as set forth in claim 5 wherein said first, second, and third rolls are axially offset from each other.

28. A machine for straightening an elongated workpiece as set forth in claim 27 wherein said first and second rolls include rolls of different hardness.

29. A machine for straightening an elongated workpiece as set forth in claim 27 wherein said first and second rolls overlap in a radial direction.