US2020657A

US2020657A - Bolt machine

Info

Publication number: US2020657A
Application number: US615368A
Authority: US
Inventors: Michael J Riley
Original assignee: National Machinery Co
Current assignee: National Machinery Co
Priority date: 1932-06-04
Filing date: 1932-06-04
Publication date: 1935-11-12
Anticipated expiration: 1952-11-12

Description

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M. J. RILEY BOLT MACHINE Filed June 4. 1932 10 Sheets-Sheet 5 F'IGJI M. J. RILEY BOLT MACHINE Nov. 12, 1935.

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Filed June 4, 1932 10 Sheets-Sheet 9 amt/whim s hza/ a a Nov. 12, 1935. M. J. RILEY BOLT MACHINE Filed June 4, 1952 10 Sheets-Sheet l0 Patented Nov. 12, 1935 UNITED STATES PATENT OFFICE National Machinery Company,

corporation 01' Chi Timn, Ohio, a

Application June 4, 1932. Serial No. 615,368

43 Claims.

This invention pertains to bolt machines, and the general object thereof is the provision of an automatic machine for effecting a plurality of metal working operations simultaneously on several work blanks.

A further object of my invention is the provision of such a machine and which is adapted to effect extruding, trimming, cutting, and thread forming operations on screw products.

A still further object is the provision of a bolt working machine having mechanisms incorporated therein adapted to automatically feed bolt blanks to the machine and to move the blanks from station to station in said machine, whereby successive operations may be performed upon the bolt blank by other mechanisms comprising part of the machine and all operations are performed substantially simultaneously in a single machine. A still further object of my invention is to employ mechanisms for effecting the foregoing referred to operations, which mechanisms shall be coordinated and controlled in such-manner that high speed accurate production of finished work pieces may be eifected.

A further object of my invention is to provide an automatic machine for extruding the thread receiving portions of the shanks of a series of bolt blanks, pointing the ends of the shanks and rolling threads upon the extruded portions, while positively maintaining the bolt blanks in the same consecutive order through each of these operations. In this way the lapse of time between any two operations on each blank of the series remains constant so as to avoid any possibility of age hardening aifecting the uniformity of the product. At the same time the wear of the extrusion die during service cannot interfere with the accuracy of the threads rolled upon the shank, since as the extrusion die wears and as a consequence the portion of the shank extruded thereby becomes larger, the roll threading dies'may be adjusted to maintain at all times a spacing of the roll threading dies giving the most desirable thread and avoiding any danger of making the threaded portions oval or in any way injuring the metal of the blank.

A further object of my invention is the provision of a novel thread rolling machine having features for automatically pointing and feeding a bolt to the thread rolling dies.

A further object of my invention is the provision of a novel device for accurately and efficiently bodily transferring a plurality of work pieces in successive manner to each of a plurality of mechanisms, adapted to perform different operations on the work pieces. The transfer mechanism is claimed in my co-pendlng application Serial No. 6,934, filed February 5, 1935.

Other objects of my inventions will hereinafter become apparent from the description thereof and which description refers to the accompanying drawings, the drawings disclosing preferred embodiments of the inventions.

In the drawings, Fig. 1 is a side elevation of an automatic machine embodying the features of my invention. Fig. 2 is a transverse cross-sectional vertical elevation taken through the machine, substantially along the plane defined by the line 2-2 of Fig. 1. Fig. 3 is a cross sectional elevation as viewed along the line 33 in Fig. 1 and illustrates the transfer mechanism claimed in said co-pending application. Fig. 4 is a longitudinal elevation of the machine with parts in section. Fig. 5 is a plan view of part of the mechanism shown in Fig. 3 and is indicated by the line 5-5 of Fig. 3. Fig. 6 is a cross-sectional plan view taken substantially along the line 6-6 in Fig. 1. Fig. 7 is a longitudinal cross-sectional fragmentary view of part of the mechanism shown in Fig. 6 and taken substantially along the line l! of Fig. 6. Fig. 7A is a cross-sectional side elevation through a work holding hopper, work raceway and work segregating device, and the plane of this section corresponds substantially to the line 1A--'|A of Fig. 6. Fig. 8 is a similar cross-sectional view taken along the line 88 of Fig. 6. Fig. 9 is a fragmentary crosssectional-view taken substantially along the line 99 of Fig. 6. Fig. 10 is a cross-sectional detail view taken substantially along the line Ill-l0 of as Fig. 9. Fig. 11 is a cross sectioral plan detail of part of the mechanism shown in Fig. 6, but showing the operating elements thereof in a position different than that of the same elements as viewed in Fig. 6. Fig. 12 is a fragmentary detail in side elevation of part of the mechanism shown in Fig. 7A. Fig. 13 is an enlarged side elevation of the work segregating mechanism shown in Fig. 7A. Figs. 14 and 15 are transverse crosssectional views of part of the segregating mechanism shown in Fig. 13, as viewed along the planes defined by the lines |4-|4 and I5-l5, respectively, of Fig. 7.

My invention contemplates a combination of mechanisms incorporated in a single machine to to effect the performance of various operations on a work piece in a completely automatic manner, whereby the work pieces may be deposited in a hopper and be selected therefrom and subsequently segregated one at a time while positioned in a meway, whereby a-single work blank is automatiodiy'horisontally positioned to be engaged by a gripper mechanism, which will transfer the work from one group of mechanisms to an adjacent group of mechanisms, and still further to a third group of mechanisms, whereby the distinctive operations of each group of mechanisms, may function to perform anoperation on The mechanisms disclosed in the drawingscomprise primarily a hopper mechanism to which the bolt blanks may be indiscriminately dumped; mechanism to cause the hopper mechanism to upend and select the bolt blanks from the hopper, whereby the bolt blanks escape from the hopper to a raceway in head-up position; a work piece segregating mechanism associated with the raceway, whereby a single work blank may first be segregated from a plurality of bolt blanks present in the raceway, and which segregated piece may thereafter be permitted to escape from the raceway to a positioning means, which holds the bolt blank in a substantially vertical position from where it is swung to a horizontal position.

I also provide a work transferring mechanism in the form of a series of equidistantly spaced, simultaneously operated work gripper fingers, which, when operated progressively and intermittently, advance the bolt blank from the horizontal positioning means to a chuck associated with the extruding mechanism, which mechanism serves to reduce a portion of the bolt shank.

The gripper fingers thereafter engage the bolt blank and shift it sideways to a trimming mechanism and thereafter through two successive intermittent, transverse movements of the bolt blank the bolt blank is presented to a thread rolling mechanism in an accurately positioned manner, whereupon the threads are formed on the extruded portion of the bolt blank, and the completed article is then permitted to fall into a suitable receptacle. All of the foregoing referred to mechanisms have associated therewith suitable operating gears, cams, levers, and shafts, arranged in such manner that all movements of the various elements of the mechanisms comprising the machine can be coordinated in timed relation, whereby accurate high speed reduction may be effected; and further, the supporting elements for all such mechanisms are arranged in such manner that the machine may be set up and tooled for effecting operations upon work of different lengths and cross-sectional size.

The machine generally may comprise a base 30 of suitable weight and design to support, in a precision manner, the various mechanisms comprising the machine. The upright portion 3| of the machine frame, (see Fig. 1), is adapted to support a crank shaft 34, and this crank shaft is suitably powered from any source, such as belt 35 and fly-wheel 36. From the crank shaft power is imparted to a horizontally acting slide 31 (see Figs. 1 and 2) by a toggle mechanism, comprisaoaosm ing a connecting-rod 38 attached at the upper end to the crank of the shaft 34 and at its lower end to toggle

arms

39 and 40, the latter arm having its lower end suitably pivotally connected to the machine frame at 4|, while the forward 5 arm 39 has the lower end thereof suitably connected to the slideway 31 at 42. The siidewny 31 is of substantial design and suitably supported in the longitudinally extending slideway 43, formed in the upright portion 3| of the machine 10 frame 30; the slideway and slide operating longitudinally of the machine to carry pointing tools and an extruding die to and from the work, as for example, extruding mechanism 43 and pointing mechanism 48, which last two named mech- 1g anisms will be hereinafter described in detail.

For the purpose of operating a thread rolling mechanism, the crank shaft 34 has mounted on the right-hand end thereof, as viewed in Fig. 2, an arm 50, comprising part of a Scotch yoke 29 mechanism for operating a vertical slide 5|, which vertical slide 5| carries the reciprocating member of a pair of thread rolling dies. The Scotch yoke mechanism comprises in addition to the slide arm 50, the slide block 53. which is 25 operated by a crank and pin 53, the crank and pin 53 being carried by a stud shaft 54, upon which iskeyed gear member 55 (see Figs. 1 and 2). The gear 55 is driven by a gear 53, mounted on the end of the crank shaft 34. The upper reciprocation of the thread rolling die slide II in a manner obvious to those skilled in the art.

A further description of the thread rolling mechanism will be hereinafter set forth.

In order to transfer power to the forward end of the machine, whereby the hopper mechanism, 0 work segregator mechanism, chucks and transferring mechanism, may be driven from the crank shaft 34, I provide a longitudinally extending shaft 10 at the lower left of the machine. as viewed in Fig. 2. This shaft III has mounted on 45 the rear end thereof a bevelled gear 1| (see Figs. 1 and 7A) the shaft 10 being supported in any suitable manner in the machine frame 30 by brackets 59, 60 and iii! (see Fig. 7A), whereby the bevel gear 1| may be driven by a companion bevel gear 50 12, which is mounted upon transversely disposed shaft 13, extending through the lower part of the rear of the machine frame. Upon the outside of the upright portion 3| of the machine frame, I provide a spur gear 15, which may be by the crank shaft gear 58 (see Fig. 1) through the medium of an intermediate idler gear 35, the idler gear being suitably supported on a stud 8|, the stud being secured to the side of the upright portion of the machine frame 3|. The 60 shaft 10 has mounted thereon at the forward end thereof and within a frame member comprising a chuck head frame 84, a series of cams which operate the work transferring mechanism, work holding chucks, the hopper and the work segthe sides slope-to alongitudinal bottom opening. 75

driven 55 I swung upwardly to the position shown in Fig. 7A,

the top surfaces 05 of the plates 34 will lie in a common plane with the top surfaces of two spaced apart parallel bars 00, which form the raceway onto which the bolts are permitted to slide when once engaged between the plates 04 and raised to the position shown in Fig. 7A. The plates are rigidly supported by arms 00 which arms are pivotally mounted on a pin 03 to permit the plates and arms to be oscillated as a unit from the extreme upward position shown in Fig. 7A to the lowermost position, as indicated by the dot and dash lines shown in Fig. 7A, whereby the top surface of the plates are brought down to the inner bottom surface of the hopper. Oscillating action of the plates 94 is effected through the medium of a crank arm I00, shown dotted in Fig. 7A, and this crank arm is provided with a slot III at its outer end for the reception of a roller and pin indicated at I02; the roller and pin are mounted upon a vertically reciprocal bar I03,

the bar I03 being suitably supported in a boss bearing I04, formed on the outer side wall of the hopper body 30. The lower end of the pin I03 is pivotally connected to a crank rod I05, as indicated at I05, and the crank rod I05 effects vertical reciprocation of the pin I03. The bar I05 is actuated by an adjustable crank pin I06 and which crank pin is carried by a crank arm I0'I. The crank arm I0! is mounted upon the forward extremity of the shaft 10 which is suitably supported by the bearing member I09, connected to the chuck head frame.

I provide an ejector mechanism in association with the hopper, which serves to elect any bolt blanks which may become disposed lengthwise of the plates 34 on the top faces 95 thereof. This mechanism may take the form of spur wheels I00 and H0, and which wheels may be mounted in any suitable manner, as, for example, upon a small shaft II2, suitably rotatably supported by the hopper body 90 at a position immediately above the top surfaces of the raceway plates 95. The wheel H0 is spaced above the top surface 95 of the raceway plates a sufilcient distance to permit a bolt head to pass downwardly under the influence of gravity between the raceway bars 96, but should a bolt be mispositioned the wheels I08 and I I0 will serve to kick the same back into the hopper.

I provide a work piece segregating mechanism in immediate association with the raceway leading from the hopper, which serves to segregate one bolt blank from the remaining bolt blanks te ng to slide down the raceway, and this segrega ng mechanism functions to permit the escape of single segregated work piece along the raceway and drop therefrom, whereupon the bolt blank is presented in a vertical position with head up to a blank positioning means that is adapted to swing the blank to a horizontal position, at which position the blank may be engaged by gripper fingers, to be described. This segregating mechanism is illustrated in detail in Figs. 13 to 18 inclusive. In Fig. 13 the continuation of the raceway plates or rails 36 comprises the lower part of the raceway. Diagrammatically illustrated in Figs. 17 and 18, I show a pair of stop members comprising swingable fingers H2 and H3, disposed immediately below the top surfaces of the raceway bars 06. The fingers are of such shape and size as to extend from opposite sides of the raceway'plates 00 to substantially the center of the runway thereof, whereby these 1111- s gers, when in the position shown in 18. serve to intercept the lowermost of a series of horizontally positioned bolt blanks, which are tending to slide downwardly out of the raceway under the influence of gravity. 10 A second set of oscillating fingers Ill and III are similarly arranged a short distance below the operating position of the fingers I I2 and I I3 and mechanism is provided to alternately oscillate these two pairs of fingers, whereby an escapement 15 action is obtained on the lower one of the row of bolt blanks in the raceway. In Fig. 17 fingers I I2 and H3 are shown as having been swung out-- wardly from the center of the runway of' the raceway, thus permitting the bolt K to slide 20 downwardly and contact with the lower pair of fingers II and I I5. The actuating mechanism is such that when the upper fingers H2 and 3 are swung outwardly, the lower fingers Ill and H5 are disposed inwardly. Further operation of the mechanism will cause the fingers H2 and II! to assume the position. shown in Fig. 18, while the fingers I It and I I5 are shown as having been swung outwardly, thus permitting the bolt blank K to individually escape down the raceway while the remaining bolts are retained by fingers H2 and H3.

The mechanism for actuating these two pairs of fingers may comprise a pair of vertical shafts H6 and I" to which the fingers H2 and H3 are respectively rigidly attached, and a pair of shaft members H8 and II! to which the lower set of fingers I I4 and I I5 are rigidly attached. These shaft members are respectively supported by a vertically extending bracket I20 that is of a 0 shape to straddle the raceway bars 93 and which bracket is secured to the raceway plates 30 in any suitable manner such as machine screws I2I. As shown in Fig. 13, the raceway plates 30 are provided with side openings I22, which openings are formed in the raceway plates 00 adjacent the bolt head sliding surfaces of the raceway plates 96, whereby the respective pairs of fingers engage the bolt blank slightly beneath the head of the blank. The two pairs of bolt engaging fingers and vertically extending shafts which support them are actuated as follows:

Suitably positioned on the top of the bracket I20 is a slide member I25, which is reciprocated by a bifurcated arm I 26 which arm is suitably attached to the upper end of a vertically extending rocker shaft I21. The slide I25 is provided with a vertically extending pin I28, which, when the slide is reciprocated, acts upon cam arms I30 and I3| respectively, amxed to the upper ends of the vertical shafts H6 and I". When the pin I28 is moved downwardly the cam arms I30 and I3I are rocked in a downward, outward direction, thus causing swinging of the shafts H6 and Ill and the fingers I I2 and H3 are. thus swung to the position shown in Fig. 17. The position shown in Fig. 16 of the pin I20 and cam arms I30 and I3I is the position of these members when the fingers I I 2 and I I3 are located as shown in Fig. 18. A second pin I35 is provided, 79 on the slide I 25 and similarly acts upon a pair of cam arms I36 and I31, and which cam arms are respectively afiixed to the top ends of the vertical shaft members H8 and H9. However, the action of the pin I35 is reverse to that of the pin I20 and which bracket I42 suitably supports the vertical shaft I21. The bracket I42 is suitably attached to one of the raceway plates 88. Oscilla tion of the bevel gear I48 is effected by a reciprocating rack bar I48 (see Figs. 13 and 16). The rack end of the-bar I48 is supported'by a loose bearing member I41, which bearing member is supported by a shaft I48, and the shape of the bearing member I41 is such as to conveniently span a spur gear pinion I58, suitably mounted on the inner end of the shaft I48. The rack bar I48 has the lower end thereof supported by a bracket member I52, .comprising part of the bracket I58 and which latter bracket supports the lower end of the raceway plates 86. Reciprocation of the rack bar I48 is eflfected in a downward direction by a spring member I58 in an obvious manner and the upward, positive movement of the rack bar is effected by a cam I88 and which cam is mounted upon the longitudinally extending general cam shaft 18.

As the bolt blank K is permitted to escape downwardly along the raceway plates 88 by the lower pair of fingers H4, H5 of the segregator mechanism, the bolt is dropped onto a pair of spaced apart, curved rails which may comprise extensions I18 of the lower ends of the raceway bars 88, and I provide a suitable mechanism which may be positioned first behind the bolt blank as it rests head-up on the extensions I18, and which will thereafter swing the bolt through a 90 degree movement into a horizontal position shown by the dot and dash lines at H in Figs.

7A and 13. This mechanism is such as to sup-' port the bolt in the horizontal position shown until the bolt blank shank can be engaged by a pair of transfer fingers, which are adapted to remove the bolt in a lateral arcuate swing to the center line of the first chuck and the extruding mechanism. This mechanism may comprise a specially formed sleeved arm I 88, which is caused to shift in a transverse direction inwardly behind the bolt blank, and thereafter swing the blank through a 90 degree arc. This arm is shown in Figs. 3, 6 and 13, as a sleeve slidably mounted upon a rigid supporting pin I15. The mounting is such that the member I88 may also be swung 90 degrees with the center of the pin I15 as an axis. In the positions shown in these figures the arm is in inoperative position and is actuated from right to left in Fig. 3 by a lever I8I, having the upper end thereof bifurcated to engage in the spool formation I88a, formed on the arm I88. That portion of the arm I88, which engages the bolt is bevelled, whereby the bolt nests between the plate extension I18 and the bevelled surface when the bolt blank is being swung and when horizontally at rest. A notch I88c formed in the arm I88 affords clearance for the ends of the gripper fingers. The lever I8I is piv tally mounted at I18 on a stud which is fixed o a frame member I11 carried by the chuck bead frame 84. The frame member I11 also supports the pin I15. The lever I8I has 9.

roller I82 provided on the lower end thereoftc suitablyengage an actuating cam I88, which is mounted upon the shaft 18. The lever III Is actuated outwardly to the inoperative posititm bolt horizontally is effected by the longitudinal 15- movement of a bar I88 (see Figs. 3, 6 and 7A) in the following manner. The bar I88 is slidably supported in a bracket I14, supported by the chuck head frame 84. Thesliding movement of the bar is transverse to the axis of the supporting pin 20 I15 and the bar isprovlded with a pin I88 at its inner end, which is engaged by the upper bifurcated end of a lever member I88. The levermemher is pivotally supported on stud I18, which is fixed to the frame member I11. The lever I88 25.

may be actuated in one direction by a barrel cam I8I, suitably attached to the shaft 18.v Actuation of the lever in the opposite direction may be effected by a spring I82. The bar I88 isprovided with a second pin I84, which engages in a slot formed in a branch arm I88b, comprising an integral part of the arm I88.

Thus a movement of the bar I88 from left to right, see Fig. 7A, will cause the pin I84 to act on the portion I 8811 of the arm I88 and effect a swinging movement thereof in its bearing, and the bolt is thus swung to the position shown in dot and dash lines (see Figs. 7A and 13). The camming relation between the cam I88 which actuates the segregator mechanism and the cams I83 and I9I which actuate the bolt swinging mechanism, is such that the arm I88 will not be positioned inwardly behind the bolt vertical rest-- ing position until a bolt has been permitted to escape downwardly by the segregator mechanism 5 and the arm I88 is then swung about pinions I15 through 90 degrees and is held in horizontal bolt supporting position a sufficient time to permit the gripper fingers to engage the bolt and remove it from the pedestal of the arm I88. It will be noted that the pedestal portion of the arm I88 is shaped to nest the bolt blank shank and the members I18 have arcuate surfaces to guide the head of the blank, and as shown in Fig. 13, a notch I18a in the member I18 gives clearance for the ends of gripper fingers to engage the horizontally supported bolt blank.

To present the bolt blank to the respective chucks which are associated with the extruding and trimming mechanisms, I provide four sets of depending gripper fingers, which are mounted upon a common bar 288, extending transversely of the machine above the chuck centers, whereby the sets of fingers are moved in unison. The

fingers are actuated also in timed relation to the 65,

with the center line of the bolt blank when the bolt blank is being horizontally supported on the pedestal of the swinging arm I80.

In Figs. 3, 4, 5, 6 and 7, the transversely dis-. posed bar 200 is illustrated in various ways. The bar 200 (see Figs. 3 and is mounted upon a. pair of links 2M and 202, which are suitably supported .by

stud pins

203 and 204, respectively. The

pins

203 and 204 are revolvably supported by bearing

brackets

205 and 206, respectively, the bearing brackets being suitably attached to the top of the chuck head frame 84, adjacent the inner edge thereof, whereby a plurality of gripper fingers H0, H2, 214 and 2l6 may depend from the bar 200 and overhang the upper, inner face of the chuck head frame. The fingers 2|0, H2 and 2|4 are in transverse aligmnent with the slot I a formed in the extensions I10 of the raceway plate 98. The links l and 202 are swung through a movement of 180 degrees by actuation of

pinions

223 and 224, suitably mounted upon the link stud pins 203 and 204, and the pinions are actuated by a rack 225, which rack is supported in a suitably formed slideway in the top of the chuck head frame 84, and by a guide plate 2 l8 extending outwardly from the top of the chuck head frame 84 over the cam shaft 10. The rack is reciprocated by a fan gear 226, see Fig. 5, formed on the upper end of a lever 227, supported on a stud 2 l9 carried by the frame member H1. The lower end of the lever is provided with a roller 228, which is disposed within the groove 229 of the cam member 230, the shape of the camming surface of the cam member 230 being such as to cause the fan gear 225 to impart sufficient motion to the rack 225 to cause the

pinions

223 and 224 to be revolved onehalf revolution, thus causing the bar 200 to be swung by the links 20!, 202, as indicated by the dot and dash arcs 200a (see Fig. 3) and to cause the bolt blanks carried by the fingers 2 l 0, 2l2, 2 l4 and 2l8 to be swung through the arcs, indicated by the dot and dash lines 208. The fingers may be of the shape shown in Fig. 3 and may be supported on pins 230, which pins are suitably supported by bracket members 23 I, the bracket members being afiixed to the bar 200 in any convenient manner. Leaf spring members 232 are attached to the bracket members 23! in such manner that the lower free ends thereof may tend to keep the fingers in a closed or blank gripping position. The lower ends of the fingers are shaped to permit the spreading thereof when brought into engagement with the bolt blank shank, whereby they may be caused to slip into and out of engagement with the shank of the bolt blank by the forceful actuation of the bar 200 in opposition to the tendency of the leaf springs 232 to maintain the fingers closed.

I have provided chucks at stations A, B and C, which are adapted to firmly engage the shank of the bolt blank immediately adjacent the head of the blank, and the chuck at station A cooperates with the extruding mechanism, while the chuck at station B cooperates with the pointing mechanism to hold the bolt blanks while operations are being performed thereon. The chuck provided at station C is merely intermediate in its function and serves to hold a bolt blank while the pair of fingers 214 are being swung to the right to assume the position of the fingers 212 and to firmly hold the bolt while the fingers 2|6 are caused to engage the bolt blank. The position of the fingers 2|8 shown in Fig. 3 is the position at which the bolt blank is shifted in a transverse direction to present the blank to the thread rolling mechanism. This operation and the elements for the effecting thereof will be hereinafter described in detail, but it is here desired to point out that the fingers 2I6 are not in transverse alignmentwith the other pairs of fingers but are posi- 5 tioned somewhat forwardly, as indicated in Fig. 5, to grip the bolt blank a substantial distance away from the head of the bolt blank, and thus serve to more accurately function to guide the end of the bolt blank shank into the thread rolling dies. 10 A description of the chuck and the actuating mechanism therefor shown at station A will sufficefor the description of the chucks shown at B and C, where the mechanisms may be identical. In Figs. 3, 4, 7 and 8 and Fig. 7A and 12, the 15 various elements comprising the chuck and the operating elements therefor are shown. The chucks comprise pairs of opposed rockable arms 240 of substantial design and which are mounted upon horizontally disposed pins 2 supported by 0 the chuck frame head 84 on the inner or forward vertical transverse face thereof. The forward ends of the pins 2 (see Fig. 3) are supported by plate members 242, which are suitably bolted to the chuck frame head 84 in any convenient manner. The upper ends of the chuck arms 240 carry adjustable chuck blocks 243, the jaws of which are suitably shaped to conform to the shape of the work and in this instance, as stated, a bolt blank shank. The lower ends of the chuck arms 240 are provided with friction rollers 244, which are engaged by rockable cam plates 245. The cam plates are mounted on stud shafts 248, suitably supported by bracket members 241, the bracket members being bolted to the chuck head frame 84. Mounted upon the studs 246 are pinions 248, which are actuated by a rack bar 249, the rack bar being suitably slidably supported in operative relation to the pinions 248 by the chuck head frame 84 and by brackets 241, whereby reciprocation of the rack bar 249 will cause slight oscillating movement of the pinions 24B and accordingly, the camming plates 245, thus causing the chuck arms to be swung open and closed. It will be-noted in Figs. 7 and 8 that the camming plates245 are disposed at the inner end of the stud shafts 246, while the pinions 240 and rack bar 249 are supported at the rear or outer end of the chuck head frame 84. In order to effect the operation of the chucks in timed relation to the movements of the work transferring fingers, the rack bar 249 is actuated by a closed face cam 250 (see Figs. 7A and 12) the cam being mounted upon the shaft 10, the outer end of the rack bar 249 being provided with a rectangular slot 25l, which engages a bearing block 252, loosely mounted on the shaft 10, whereby other than a. transverse horizontal movement of the rack bar 249 will be prevented.

A roller 253, mounted upon the rack bar 249 and engaging in the slot 250a of the cam 250, is actuated by rotation of the cam, and thus the rack bar movements are positively controlled in both directions.

From the foregoing description of the chuck actuating mechanism, it will be apparent that 6 the shape of the cam 259 and the angular disposition thereof upon the shaft 10, relative to the cams I60 and I83 and 239, predetermines the transverse blank transferring movements of the sets of fingers 2|0, 2|2, 2M, and H6, in timed relation to the movement of the blank from the segregator mechanism to the horizontal positioning thereof.

In order that the bolt blanks will have one end thereof definitely positioned relative to the extruding and pointing mechanism, I provide means associated with the chucks at stations A and B for shifting the bolt blank longitudinally of its axis after it has been placed in the chuck jaws and before the chuck jaws have been finally looked upon the work, whereby the underside of the head of eaclibolt blank is forced against the inner vertical end surface of the chuck Jaws. I incorporate this means in the chuck head frame 84 in such manner that this means may also serve to transfer any undue longitudinal strains exerted upon the bolt blanks when being operated upon by the extruding mechanism directly to the bed of the machine frame, thus protecting the various operating elements of the chuck head. In Figs. 1 and 6 I show a solid block of metal 300., extending upwardly from the bed 36 of the machine frame in the rear of the chuck head frame 84. This portion 30a of the machine frame serves to support in a suitable manner an adjusting screw 260, which screw may be manually turned by a wheel 26i to efiect longitudinal adjustment of the chuck head frame 84 for different lengths of work. It will be noted in the drawings that the chuck head frame has the bottom thereof shaped to comprise a slide which fits in a slideway formed in the base of the machine frame 30, whereby it may be firmly clamped to the base in adjusted position by the guideway clamping plates 85. The shaft 10 is provided with a splined coupling 86 (see Fig. 7A) whereby such adjustment is permitted without disturbing the driving action of the rear and forward parts of the shaft 10.

In the upper part of the machine frame portion 38a, I provide adjustable threaded back-up

sleeves

264 and 265, which are in threaded engagenient with the bushing members 266 and 261, respectively. These sleeves also serve as fixed cam members and are retained in place on the fixed frame portion 30a by the bushings 266 and 261, which bushings are retained by small pins 268 and which pins are adapted to shear, should any undue strains be exerted upon the chuck operating elements, as will be described.

To position the bolt blanks longitudinally while in the chucks, I provide a slight longitudinal shifting movement of back-up rods 218, the inner ends of which rods engage the top faces of the bolt blank heads. The rods 216 are in threaded engagement with the sleeve members 2H for adjusting purposes and extend rearwardly and freely through the back-up

sleeves

264 and 265. The sleeve members 2" .are adapted to shift longitudinally of the bolt blank and to be axially turned through a small part of one revolution by pinions 212. The pinions are longitudinally fixed by the chuck head frame 84 and are actuated by vertically extending rack bar members 213. The rack bar members are suitably supported in vertical operating position by slideways, formed in the chuck head frame 84, and the pinions 212 are so positioned on the sleeves 21! that the vertically extending rack bars 213 may extend downwardly and engage with and be operated by the chuck arm operating pinions 248, (see Figs. 6 and 8). The outer ends of the sleeves 2" are provided with camming heads 280, the camming surfaces of which are complementary to the camming surfaces formed on the inner ends of the

sleeves

264 and 265.

Hence a slight turning or revolving movement of the sleeve 21! will cause the cam heads. 28!] thereof to ride up upon the camming surfaces of the heads 264a and 265a of the fixed backp sleeves. 264 and 286, thus causing the sleeves to shift the back-up pins 210 into engagement with the heads of the bolt blanks held by the chuck jaws. Thi longitudinal shifting or positioning of the bolt blanks in the chuck laws is effected 5 just prior to the final cinching or looking action of the camming plates 24', and accordingly,'I control this'timing movement by a predetermined relationship in the amount of movement required'of the vertically disposed rack bars v218 10 actuated of! of the chuck actuating pinions 246 and the contour of the camming surfaces of the camming plates 245. a

In Fig. 11 I show the relationship of the various elements just described when the back-up pin is 15* away from the head of the bolt, while in Fig. 6

the rack bar 213 and pinions 212 have caused a slight revolving movement of the sleeves 21f, thus causing the back-up pins 218 to wedge the 20 bolt heads against the inner end faces of. the chuck jaws. When the sleeves are revolved in a reverse direction, the springs 28l cause the sleeve to assume the position shown in Fig. 11- in an obvious manner. exerted upon the back-up pin 216, such strain will be transmitted to the sleeve 21l by reason of the threaded engagement thereof with the thrust pin 210 and by the cam head 288 of the sleeve 21I to the head 264a and the

thrust member

264, 30 thus causing the pins 268 to shear and permit the bushings 266 to be forced backwardly and outwardly.

After a bolt blank has been positioned at station A, and the chuck has firmly closed there- 35 upon, actuation of the slide 31, which carries the extruding die 48, if effected by reason of the timed relation of the angular disposition of the crank arms 34a, crank shaft 34, train of gears, compris ing 58, 80, 15, transverse shafts 18, bevelled gears 40 1|, 12, shaft 10 and the series of cams hereinbefore described as being mounted on the shaft 10, and which cams actuate the work segregator mechanism, the work positioning means, the

swinging bar carrying the gripper fingers, the 5'.

locking of the chucks and the longitulflnal positioning of the work in the chucks.

As the slide 81 is shifted outwardly toward the shanks of the bolt blanks held by the chuck at station A and station B, the work blank at sta- 50 tion A has the shank thereof reduced in diameter by an extruding die 290, supported by an adjustabledie holder 29L The slide 81 is moved away from the work stations A and B to free the Should any unusual strain be as blanks from the tools carried by the slide and 5 in this connection it will be observed that since the extruded blanks are rigidly held by their heads as the slide moves away from the blank, it is unnecessary to. provide any knockouts or analogous mechanism. This outward movement of 5 the slide 31 also causes a second work blank, the shank of which had previously been extrud-. ed at station A and thereafter transferred to station B, to be pointed by a cutting mechanism which may be in the form of a box tool 282, which tool 292 has the shank 294 thereof suitably se- 7 cured in the end of a spindle 205 (see Fig. 8) which spindle is rotatably mounted in the slide. Rotation of the spindle. may be effected by a bevelled pinion 290, which has a 'splined con- 5 nection with a rearward extension 295a of the spindle 295, and the pinion 29B is supported in a convenient manner by a bearing bracket 293, secured to the'ffame 30 of the machine. A driving connection between the bevelled gear pinion 10 296 and the crank shaft 34 may comprise a spur gear 299, mounted upon the crank shaft 34 at the right side of the machine, as viewed in Fig. 2,

.\which gear drives a spur gear 300, shown in dotted position in Fig. 2. The spur gear 300 is 5 mounted upon a stud shaft 30!, which extends through the side wall of the machine frame portion 3i, and mounted upon the inner end of the shaft 30| is a sprocket 302, which is drivingly connected to a pinion sprocket 303. The sprock- 2 et 303 is supported by a small stud shaftv 304,

which supports the bevelled gear 305, the bevelled gear 305 serving to drive the bevelled gear pinion 306. Thus it .will be apparent that regardless of the longitudinal motion of the slide 25 31, the box tool and its supporting spindle will be rotated at all times at the desired metal cutting speed. It will also be apparent that while the extruding action is being eifected upon one bolt blank at station A, the pointing action is 30 being effected upon a previously extruded bolt blank simultaneously at station B. Suitable adjusting means may be associated with both the extruding and pointing mechanisms to adapt the machine to different sizes of work.

The extruding die 290 reduces the original diameter of the blanks to the pitch diameter of the threads to be formed thereon. In this way the blanks are prepared for a roll threading operation, during which the metal of the extruded 40 portion is pressed inwardly and caused to fiow outwardly by the die impressions so that the resulting overall diameter of the threads equals the diameter of the unextruded portion of the shank. In this way I am able to obtain the advantages of the greater strength and accuracy of roll threads as compared to cut threads, while retaining a uniform overall diameter of the shank portion and thread portion of the resulting bolt.

50 The roll threading dies are incorporated into the machine and driven in timed relation to the other elements of the machine. The blanks after being extruded and pointed are transferred preferably by a positive gripping transfer to position ,5 in front of the roll threading dies and are then fed into these dies in the same consecutive order in which the extruding and pointing operations are carried out. The extrusion die is subject to wear at its throat so that the extruded portions 0 of the shanks of the blanks gradually become larger as the operation of the machine proceeds. By positively maintaining the blanks presented to the roll threading dies in the same consecutive order in which they are acted upon by the 55 extrusion die any increase in size of the extruded portions of the shanks can be accommodated as it occurs by adjustment of the roll threading dies.

It will be understood that a narrow tolerance 70 is allowed for wear of the extrusion die and that when this wear has exceeded the tolerance after the making of a large number of blanks the die is replaced. If the roll threading dies are ini-- tially adjusted to receive blanks having the larg- 75 est diameter with the tolerance range the Cit threads produced on the blanks of the smallest diameter within this range will not be completely filled up and sharp. Such threads are extremely objectionable in appearance, being ragged on the edges and are also apt to catch or cut any-. 5 thing a "th which they may come in contact. 0,11, the other hand, if the threading dies are adjusted to completely fill out the threads on blanks of the smallest diameter within the tolerance range, a larger diameter blank will be rolled oval because of the excess metal. The 7 threads on these blanks will then not fit the threaded part with which they are to co-operate since the overall diameter of the threads across the major axis of the oval will be excessively large. However, by combining the extrusion die and the threading dies in the same machine the operator may initially adjust the threading dies to receive the smallest diameter blanks within the tolerance range and as soon as a blank is discharged which will not fit the gauge, the roll threading dies may be separated sufliciently, within the tolerance limits, to avoid any oval formation of the threads.

The mechanism for imparting reciprocating movement to the thread forming die slide 5| has been hereinbefore described, and I will now set forth the cooperation of the stationary and moving die blocks, which roll the thread upon the blank as wellas the mechanism for effecting the transferring of the bolt blank from station B to station C, and from station C to the thread rolling dies. As hereinbefore stated, no operation is performed upon the bolt blank at station C but the particular place where the gripper fingers engage the bolt blank is changed at station C.

It will be noted in Figs. 5 and 6, and particularly in Fig. 6 that the pairs of fingers H0, H2 and 214 at stations A, B and C, respectively, are all arranged in a common vertical transverse plane so as to be disposed immediately adjacent the outer faces of the chuck jaws, while the tingers 2l6 are spaced forwardly (note also Fig. 5), whereby the fingers 2l6 willv grip the bolt blank adjacent the outer extruded end of the blank, 5 and when the fingers 2l6 swing from-station C to station D with a bolt blank, the fingers 2| 6 v are disposed close to the thread rolling dies 3| 0 and 3|2. The die 3l2 is fixed to the slide in any convenient manner and the stationary die is provided with a wedge mounting, as shown in Fig. 2, whereby it may be firmly held in place. upon a supporting block 380 by clamp plate 3". Bolts 382 serve to hold the block 380 firmly to the frame 3|. Adjusting screws 383, threaded in the machine frame 3|, provide means for refinement of adjustment of the die 3I0 relative to the die 3|2.

When the fingers 2I6 are holding the bolt blank in the position shown in Fig. 6, the die block slide 5| is at the uppermost part of its stroke and the bolt is shifted longitudinally to be disposed between the thread rolling dies by an injecting plunger 3I5. The action of the plunger 3l5 on the bolt causes the fingers to be spread slightly to remain in engagement with the larger diameter portion of the bolt blank.

I also provide a second'means for acting upon the shank of the bolt blank, whereby the bolt blank will be trued up relative to the rolling threads of the die blocks H0 and M2. I accomplish this by a vertically movable member 320, which is operatively supported in a suitable slideway, whereby the member 320 may be disposed to move at a position between the stationary die the bolt levelling member 323. The lever member 32I is secured to a small transversely extending shaft 323, which extends alongside of the slide member and is supported at its inner end by a bracket member 326. A bell crank 321 is attached to the inner end of the shaft 325 and to a vertically extending connecting rod 323, which rod is reciprocated by a lever 323, supported at the top of the machine, whereby the lever 329 may carry a roller 333, which is actuated by a cam 33I, the cam 33I being mounted upon the shaft 54 and which shaft carries the gear 33. The shape of the cam 33I is such that the bolt engaging member 323 is actuated through the described mechanism only after the plunger member 3I5 has injected the bolt to the thread rolling position. Thereafter the Scotch yoke mechanism functions to cause a downward movement of the slide 5I to a lowermost position, in-

dicated by the dot and dash lines 3I2 in Fig. 2.

It will be apparent that when the die block 3I2 is in the position shown by the dot and dash lines, the bolt is permitted to escape into a chute 343, which will guide the finished bolt to a receptacle 34I.

The plunger 3I5 is spring actuated in a forward direction and to a retractive, inoperative position positively by a cam. The plunger 3I5 is actuated by a lever 344, suitably mounted upon a. pin 345, the pin being attached to the chuck head frame 34 (see Figs. 6 and 9). The lower end of the lever 344 is provided with a roller 343 and the location of the lever 344 is such that the roller 346 will ride against the side of the cam'extension 243a of the rack bar 249. This extension 243a of the rack bar is provided with a camming notch, as indicated at 353, whereby the movement of the bar from right to left of Fig. 3 will permit the lever to be actuated by the spring 343, thus causing the plunger rod 3I5 to act upon the bolt blank to position the bolt blank between the thread rolling die blocks.

The crank shaft 34 is continuously rota-ting. The longitudinal cam shaft I3 is also continuously rotating by reason of the train gear connection comprising gears 53, 33, I5, transverse shaft I3, and bevel gears II and 12. The crank arm I31 on the forward end of the shaft I3, constantly oscillates a pair of hopper members 95 to cause the bolt blanks to be lifted from the hopper 93, head end up, from which the bolts slide downwardly to the raceway members 96. There is no timed relation between the actuation of the hopper and the other mechanisms of the machine, other than that there are sufficient reciprocations or oscillations of the hopper agitator members 34 to always eifect the positioning of a greater number of bolt blanks per minute in the raceway 33, than the operating demand of the machine would require.

The work segregator mechanism, shown in Figs. 13 to 18 inclusive, serves 'to permit the escape of one bolt blank at a time from the raceways and this escapement is effected in timed relation to the other cooperating parts of the machine, by reason of the cam I33 and the separator elements operated thereby. The bolt then drops by gravity to the vertical position shown in Fig. 7A, and Fig. 13, whereupon the bolt positioning arm I33 is shifted to a. position behind the bolt and thereafter swings the bolt to the dot and dash position shown in Figs. 7A and 13.

The four sets of fingers 2I3, 2I2, 2I4, and 5 2I6 are then swung simultaneously through an arc, as indicated on Fig. 5, by the actuation of the bar 233, which timed movement'is controlled by the relationship of the cam 233 to the cams I33, I33, and I3I. Toward the latter part of the arcuate movement of the fingers 2"! from left to right of Fig. 5, the lower part of the fingers 2I3 are brought downwardly into the slot "Ia and are forced to spread over the bolt blank as it is held in position by the bolt positioning mem- 13 her I33. There is a slight dwell at this point in the movement of the bar 233 and consequently in the four sets of fingers carried thereby, while the extruding, pointing and thread rolling mechanism are completing the intended operations 20 thereof, whereupon the bar 233 is then swung from right to left, the bolt blank is then presented to the first set of chuck jaws at station A; a repetition of the foregoing movements then causes the bolt blank to remain at station A, while the fingers 2I3 swing from left to right to pick up another bolt. In the meantime, the fingers 2I2 will have engaged the bolt blank remaining at station A and will transfer this bolt blank to station B. The chucks are synchronized in their movements with the movements of the fingers whereby the chuck jaws will never be completely open when the fingers are swinging.

A second repetition of the foregoing operations will cause the fingers 2I4 to then transfer the first bolt blank to station C and, as will be obvious, in the meantime the following bolt blanks will be positioned in the chuck jaws at stations A and B. No operation is performed upon the bolt blank at station C. It is there held 49 by the chuck jaws until the forwardly positioned fingers 2I6 come into engagement with the bolt blank toward the outer extruded end of the bolt blank. A still further cycle of operations will then position the first bolt blank at station D, whereupon the plunger 3I3 will position the bolt blank forwardly, as shown in Fig. 4. The slide Si is then operated and when the bolt blank is engaged by the thread rolling die blocks III and 3I2, the bolt blank is snapped downwardly, out of engagement with the fingers 2I3 but just before the blank is engaged'by the thread rolling die blocks, the vertically reciprocating bolt engaging member 323 is caused to come down- 55 wardly in timed relation to the movement of the fingers on the bar 233, and the slide II to level the bolt should it not be in proper position longitudinally.

From the foregoing description of my inven- 00 tion it will be apparent to those skilled in the art that I provide in a composite machine, groups of coordinated mechanisms, which are adapted to effect the simultaneous performance of operations on work pieces, that the arrangement is adaptable to a variety of operations, which it may be desired to perform upon a piece of work, and that the machine is adaptable to various sizes of work. It will be also apparent to those skilled in the art that the advantages of pre- 73 senting work, gauging the same relative to thread rolling die blocks which are disposed to operate vertically likewise the work segregator mechanism associated with the hopper adapted to a variety of uses, not necessarily confined to bolt 73 making, and that the mechanism for transferring a piece of work from one mechanism to another is also adaptable to various mechanical'uses i the metal working arts.

I claim:

1. In a bolt forming machine, the combination of means to extrude the shank end of a bolt blank, means to point the extruded portion of the bolt blank, adjustable roll threading dies to form a thread on the extruded portion of the bolt blank, and means for successively transferring a series of bolt blanks in the same consecutive order to each of said means, whereby the extrudin pointing and threading operations may be automatically consecutively performed upon each of the series of bolt blanks.

2. In a bolt forming machine, the combination of means to extrude the shank end of a bolt blank, means to point the extruded portion of the bolt blank, adjustable roll threading dies to form a thread on the extruded portion of the bolt blank, means for successively transferring a series of bolt blanks in the same consecutive order to each of said means, and driving mechanisms for actuating all of said means in timed relation.

3. In a bolt forming machine, the combination of means for reducing the diameter of a portion of the shank of a bolt blank by working to flow the metal therein, means to form a convex point upon the bolt blank, adjustable roll threading dies to form a thread on the bolt blank, and means for successively transferring a series of bolt blanks in the same consecutive order to each of said means whereby the reducing, pointing and threading operations may be automatically consecutively performed upon the bolt blanks.

4. In a machine of the character described, the combination of a plurality of reciprocating mechanisms each of which effects a diiferent operation on a piece of work, said mechanisms including a thread rolling mechanism, non-rotating Work holding chucks co-acting with a plurality of said mechanisms for holding the work rigid while said mechanisms act thereon, and work transferring means coacting with said mechanisms and chucks for transferring a plurality of work pieces from chuck to chuck, means coordinating the operation of said mechanisms, chucks, and transferring means and means for injecting a work piece into the thread rolling mechanism from the transferring means.

\ 5. In a machine of the character described, the combination of a plurality of reciprocating mechanisms each of which effects a different op-- eration on a piece of work and including an extruding mechanism, a turning out mechanism and a thread rolling mechanism, a work holding chuck co-operating with said turning mechanism for holding the work rigid while said mechanism acts thereon, a work transferring means cooperating with said mechanisms for simultaneously transferring a plurality of work pieces from station to station, means coordinating the operation of said mechanisms, and transferring means, and a second work transferring mechanism for finally presenting the extruded and turned piece of work to the thread rolling mechanism.

6. In a machine of the character described, the

combination of an extruding mechanism adapted to eifect a diameter reducing operation on a round piece of work, a chuck cooperating with said extruding mechanism for holding the work piece stationary while the work piece is being extruded, means for opening and closing said chuck, a sec ond mechanism for pointing the extruded part of the work including a second chuck, a plurality of work gripper means positioned to grip the work in front of said chucks and operated in unison to transfer work pieces fromchuck to chuck, a third chuck at an idle position and arranged to receive work transferred from the second-named chuck, a thread rolling mecha- 10f nism, a work gripper for transferring the work from said last-named chuck to a position in alignment with said thread rolling means, means to move said work longitudinally in said last-named work gripper into the path of the thread rolling means, and means for actuating said chuck operating means, said mechanisms and said gripper means in timed relation, whereby said operations may be effected upon the work pieces automatically in sequence. '7. In a machine of the character described, the combination of means for reducing the diameter of a piece of work, means for pointing said reduced portion of the work, means for positioning the work in a longitudinally adjusted manner relative to each of said means, means for holding the work after being thus positioned, a common support on which said reducing means and said trimming means are mounted for movement towards and from said workholding means, means to move said reducing means and said trimming means, said trimming means being also rotatably mounted in said support, means to rotate said trimming means, a work transferring device for shifting the work from one to the other of said 85 reducing and trimming means, and a plurality of motion transmitting mechanisms for operating all of said means and said device in timed relation, whereby said operations on the work may be successively performed. 8. In a machine of the character described the combination of a series of chucks adapted tohold a bolt blank while the same is being worked upon, said chucks being equidistantly mounted upon an adjustable head, a means cooperating with each chuck for performing an operation on the bolt blank, means on said head for adjusting the position of the bolt blank while in the chucks, and means for transferring the bolt blank from chuck to chuck sequentially. 9. In a metal working machine, a plurality of fabricating mechanisms, a work holding head provided with a separate chuck for each of said mechanisms, said head being adjustable to and. from said mechanisms for adaptation to the holding of work blanks of different lengths, a work transferring mechanism adapted to transfer a piece of work from chuck to chuck, whereby sequential operations may be performed upon the work by said mechanisms, said head including means for positioning a work piece longitudinally after the work piece is placed in the chuck, and a longitudinal thrust absorbing means for backing up the work pieces held in the chucks in longitudinal direction, whereby longitudinal strains created by the operation of said mechanisms upon the work pieces will be transmitted through the head to the machine frame and thereby protect the operating members of the work head from excessive strain. 10. In a metal working machine, a plurality of mechanisms, a work holding head provided with a separate chuck for each of said mechanisms, a work transferring mechanism adapted to transfer a piece of work from chuck to chuck, where- .work transferring mechanism adapted to transfer a piece of work from chuck to chuck, means for positioning work pieces longitudinally after the work pieces are placed in' the chucks and a longitudinal thrust absorbing means for'gauging the work pieces and for backing up the work pieces in the chucks in longitudinal direction.

12. In a metal cutting machine, a frame, a pair of slides each mounted in said frame for reciprocation movement toward and away from each other, a plurality of workholders carried by one slide, means to manually position said workholder slide, means to transfer workpieces from one workholder to another, a series of mechanisms carried by the other slide and arranged to operate on work carried by opposing workholders, means to reciprocate said last-named slide to cause said mechanism to coact with work carried by said workholders, and means to operate said work transferring mechanism in timed relationship with said last-named slide.

13. In a metal cutting machine, a frame, a pair of slides each mounted in said frame for reciprocation movement toward and away from each other, a plurality of workholders carried by oneslide, transfer means carried by said lastnamed slide to transfer work from one workholder to another sequentially, means to manually position said workholder slide, a series of mechanisms carried by the other slide and arranged to operate simultaneously on work carried by opposing workholders, one of said mechanisms including a member rotatable in said slide, means to reciprocate said last-named slide a predetermined distance to cause said mechanism to coact with work carried by said workholders, and means to rotate said rotatable mechanism.

14. In a metal working machine, a main frame, a series of chucks adapted to hold bolt blanks, a common support for said chucks, a guideway in which said support is mounted for movement in a direction parallel with the axis of the blanks, means to secure the support in an adjusted position in said guideway whereby all of said chucks may be simultaneously moved to position them for holding work blanks of different length, means movably carried by the frame and coacting with respective chucks for performing operations on the blank, means to move said lastnamed means intermittently toward and away from said chucks, and means to transfer the blanks from chuck to chuck sequentially when the operating means is away from their respective chucks.

15. In a metal working machine, a main frame, a series of chucks adapted to hold bolt blanks, a common support for said chucks, a guideway :in which said support is mounted for movement in a direction parallel with the axis of the blanks, means to clamp the support in adjusted position in said guideway whereby all of said chucks may be simultaneously moved to position them for holding work blanks of different length, means carried by and movable with saidsupport to transfer the blanks from chuck to chuck sequentially, means movably carried by the frame and coacting with respectivechucks for performing operations on the blank, means to move said lastnamed means intermittently toward and away from said chucks in timed relationship with said transfer means 16. In a metalworking machine a main frame, a series of chucks adapted to hold bolt blanks, a common support for said chucks mounted for sliding movement in said frame in a direction parallel with the axis of the blanks, manually operable means to move said support to adjust the chucks for bolt blanks of different lengths, independent means coacting with the blanks in each chuck to position the blanks relative to their respective chucks, a second support mounted in said frame for reciprocatory movement-toward and away from said chucks, a blank extruding g mechanism carried by said last-named support, a blank pointing mechanism rotatably mounted in said support, means to rotate said-pointing mechanism, means to reciprocate said last-named support, and a work transferring mechanism acting in timed relationship with said last-named means to transfer blanks from chuck to chuck in sequence.

17. In a metal working machine, a main frame, a series of chucks adapted to hold headed bolt 6 blanks, a common support for said chucks, a guideway in which said support is mounted for movement in a direction parallel with the axis of 'the blanks, means to clamp the support in adjusted position in said guideway whereby all of said chucks may be simultaneously moved to position them for holding work blanks of different length, positioning means carried by the frame to force the head of the blanks against a face of their respective chucks, means movably carried by the frame and coacting with respective chucks for performing operations on the blank while said last-named means is in contact with the blank, operating means to move said positioning and said operating means intermittently toward and away from said chucks, and means to transfer the blanks from chuck to chuck sequentially when both of said last-named means are away from their respective chucks.

18. In a bolt machine, an extrusion die, means for presenting bolt blanks in sequence into alignment with said die, means for producing relative reciprocation of a blank and said die to extrude a portion of the length of each blank to a smaller diameter, a pair of reciprocating roll threading dies adjustable toward and away from each other to roll threads on shanks of different diameter, and means for transferring the extruded blanks to said threading dies in the same consecutive order in which the blanks are acted on by said 0 extrusion die and in position to have threads rolled on the extruded portions.

19. In a bolt machine, an extrusion die, means for presenting bolt blanks in sequence into alignment with said die, means for producing relative 5 reciprocation of a blank and said die to extrude a portion of the length of each blank to a smaller diameter, a pair of reciprocating roll threading dies adjustable toward and away from each other to roll threads on shanks of different diameter, 7 means for transferring the extruded blanks to said threading dies in the same consecutive order in which the blanks are acted on by said extrusion die and in position to have threads rolled on the extruded portions, andmeans for operating