US1177827A - Screw-machine. - Google Patents

Description

C. M. SPENCER.

SCREW MACHINE.

APPLICATION FILED SEPT-28.1914.

10 SHEETS-SHEET l- Patented Apr. 4,1916.

@Znegses C. M. SPENCER. SCREW MACHINE.

'APPLICATION min SEPT-28.1914. 1, 17 7,827.

Patented Apr. 4,1916.

10 SHEETS-SHEET 2.

C. M. SPENCER.

SCREW MACHINE.

APPLiCATION FILED SEPT- 28. 1914.

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I SCREW MACHINE.

APPLICATION man SEPT. 28. 1914.

Patented Apr. 4, 1916.

I0 SHEETS-SHEET 5- C. M. SPENCER.

SCREW MACHINE.

APPL|CATION man SEPT- 28, 1914.

Patented Apr. 4,1916.

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Patented Apr. 4,1916.

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SCREW MACHINE.

APPLICATION FILED SEPT- 28, 1914.

1,177,827. I Patented Apr. 4, 1916.

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WQQA C. M. SPENCER.

scnsw MACHINE.

APPLICATION FILED SEPT- 28, I 9I4- Patented Apr. 4, 1916.

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7 7 I i I I 7 UNIT D STATES PATENT OFFICE.

CHRISTOPHER M. SPENCER, OF I-IARTFORD, CONNECTICUT, ASSIGNOR TO THE NEW- BRITAIN MACHINE COMPANY, OF NEW BRITAIN, CONNECTICUT, A CORPORA- TION OE CONNECTICUT.

Specification of Letters Patent.

SCREW-MACHINE.

- Patented Apr. 4; 1916.

To all whom it may concern Be it known that I, CHRISTOPHER M. SPENCER, a citizen of the United States, residing at-Hartford, in the county of Hartford and State of Connecticut, have invented certain new and useful Improvements in Screw-Machines, of which the following'is a specification.

This invention relates to what I shall for convenience term a screw-machine. Some or the improvements, however, can be incorporated in machines of other kinds, for

-which reason I have as indicated, selected the scope of the invention defined by the claims following 'said description.

One of the objects of the invention is the provision of a work carrier having compact and readily accessible means for eflecting adjustments of bearing and other elements. Another feature is the facility with .which f the spindles and spindle operating shaft'on the work carrier can be lubricated.

Another point is the provision of effective indexing mechanism and operating means therefor. Another is the substantial mounting of the tool slide. Still, another is the provision of a cam having cam members or strips thereon of maximum strength yet susceptible of easy and ready adjustment.-

The invention comprises numerous other. features of novelty and utility which with the foregoing willbe stated at length in' said description.

Referring to said drawings: Figure 1 is a front elevation of a metal-working machine involving my invention. Fig. 2 is a rear elevation of saidmachine.

Fig. 3 is atop plan view of the same. Fig. 4 is a vertical, longitudinal sectional elevation of the work-carrier, spindles and certain -adjunctive elements. Fig. 5 is a transverse sectional view on the line 5-5 of Fig. 4 showing a lever and a gear element, omitted for sake of clearness, in Fig. 4. Fig. 6 is a transverse section on the line 66 of Fig. 1. Fig. 6 is a sectional detail of a part of the work-carrier, locking-bolt and certain cooperating devices hereinafter more fully described. F ig'. 7 is avertical sectional view on the line 77 of Fig. 3. Fig. 8 is a ver tical sectional view of parts of the driving mechanism, the section being taken through the change-gear box. Fig. 9 is a horizontal sectional view on the line 99 of Fig. 1. Fig. 10 is a section on the line 1010 of -Fig. 2. Fig. 11 is a face view of a portion of the cam-drum. Fig. 12 is a section on the line 12-12 of Fig. 11. Fig. 13 is a detail view in elevation of the work carrier. Fig.

14 is a detail view of portion of a frictionaldrive hereinafter more particularly described; Fig. 15 is a vertical sectional view of the work carrier and parts associated therewith. Fig. 16 is a detail view in elevation partly in section, of change gearing hereinafterdescribed. Fig. 17 is a side elevation partly in section of gearing'also hereinafter more particularly described. Fig.

18 is a top plan view of the gearing shown in Fig. 17. Fig. 19 is a horizontal section on the line 1919 of Fig. 10. Fig. 20 is a side elevation, and Fig. 21 a rear elevation of a clutch member. Fig. 22 is a side elevation of a companion clutch member. .Fig. 23 is a front elevation of the clutch member shown in Fig. 22. Fig. 24 is a transversev The machine as shown is of multiplespindle type and preferably involves in its make-up two carriers, one for the work and the other for atool or tools, In the present,

common in the case of so-called screw machines. This work-carrier as shown is given an intermittent rotary movement, suitable indexing mechanism being provided to attain this particular function, the work-carrier after each movement being locked for example by a bolt or equivalent element.

A work-carrier such as meets my requirements is shown in Figs. 1, 2 and in detail in Figs. 4, 5, 13 and 15. This work-carrier or head 5 as illustrated is cylindrical and is mounted for turning movement in a suitable casing such as that denoted in a general way by 6. This casing 6 as illustrated consists of a lower section 7 and an upper section 8 bolted or otherwise suitably connected together, the lower section 7 in turn being similarly fastened to the top of the framemember 3. The mating sections 7 and 8 of said casing or housing 6 receive within them the work-carrier 5 which as shown is practically cylindrical. Said casing 6 has an opening in its top, closed normally by the removable cover 9, by taking off which access may be had to the carrier 5 but more especially to certain adjusting mechanism therein. Said casing 6 interiorly thereof has at longitudinally-separated points the abutments 10 and 11 of practically similar construction to be engaged by the annular bear-- ing-surfaces 12 and 13 respectively, of the rotary carrier 5, which present a simple and convenient .means for preventing endwise movement of said carrier.. As I have virtually intimated when this carrier 5 is employed for sustaining the work, the latter may be associated with the former in any desirable manner, one or more spindles as 14 (Fig. 15,) being generally provided for this purpose, these spindles being rotary and as somewhat common in the so-called screw I machine art, being hollow. The spindles 14 are continuously rotated and by con-- tinuous I mean aslong as the machine is in action. The carrier itself as will herein after appear, through the intervention of suitable means is' given a step-by-step rotary or indexing. motion, being positively locked for examplethrough the medium of a bolt as will hereinafter appear, at the conclusion of each intermittent movement. The spindles 14 extend entirely through the carrier 5, and there may be any desired number of them, and in like manner they may be also rotated in any convenient manner, although the complete length'of the machine and is rotated in some convenient way. Fastened suitably to the rear end of said shaft 15 is the pinion 16, the teeth of which are in mesh with an annular series of pinions 17 carried by the respective spindles 14, said pinions 17 being loose with respect to said spindles and not directly supported thereby. Said pinions receive the friction-collars '18 which as shown are externally tapered or conical to fit correspondingly shaped openings in said pinions), said cone-collars 18 surrounding and being rigidly fastened to the elongated hubs 19 of-the pinions 20 keyed or otherwise suitably fastened to the respective spindles 14 (Fig. 15), the hubs 19 extending into the several pinions 17. Normally the respective pairs of pinions 17 and 20 are clutched together through the intervention of suitable means hereinafter described, and it will be clear that when they are thus clutched together and thatwhen the pinion 16 rotates on the turning of the shaft 15, the pinions 17 will be simultaneously rotated, and owing to their clutched connection with the pinions 20, the latter in turn will be rotated to effect the simultaneous rotation of the spindles 14. Rotatively connected with the several spindles are finger blocks as 21, each finger block being provided with a plurality of fingers 22 pivoted between their endsto the respective blocks and the operative ends of which are caused to press against the pinions 20 to fprcethe same into the cooperating pinions 17 to thus maintain a clutched relation between the respective 'pairs of pinions 17 and 20, thus making the same practically rigid or integral with each other. For thus operating the pivoted fingers 22, the spools 23 slidablel on the respective spindles 14 may be utilized, these spools being furnished with cone or wedge portions 24. When the spools 23 are slid toward the right in Fig. 15, the wedge or cone portions 24 'by acting against the free outer ends of the fingers 22 force said free ends outward and the tips inward on which'motion the pinions 20 are forced inward and into solid clutched relationwith the respective pinions 17. By sliding the spools 23 to the left along the respective spindles,the fingers 22 will be freed and in turn will free the pinions 20 from engagement with the respective pinions 17 so that at this time should the pin-ions 17 be rotated they will not turn the pinions 20 owing to the fact that they are unclutched from each other. r a

Any type of tool may be utilized vfor opcrating the work held in the spindles 14, but

it is frequently necessary. to use a threading-tool. It is a recognized fact that a threading-operation must of necesslty be a comparatively slow one, and this is the purpose of clutching together the several pairs of pinions. It is not essential that any specific mechanism be provided for obtaining this office, my aim being to provide effective means by'which at least one spindle can when desired be rotated at adifferent speed from another spindle or spindles, and as I have intimated in the threading operation this is a lower speed. The means for automatically operating the spindles 14 will be hereinafter more particularly described as will be a suitable threading mechanism. Said spindles while supported by the rotary :arrier 5 are not, strictly speaking directly connected therewith but extend through bearings as 25 which as illustrated, are set into openings in the ends of the carrier 5, these hearings being preferably of such nature as to compensate for wear therein and in .the spindles, and this result I can obtain for example by externally tapering said bearings, the taper as illustrated being inward. It will be clear, therefore, that these tapered or conical bearing sleeves 25 fit correspondingly tapered openings in the ends of the cylindrical carrier 5. By moving the bearings 25 inward I can take up wear. Usually these bearings 25'a1'e split or divided so as to provide for their contraction. Conical, split or resilient bearing sleeves for taking up wear, are not uncommon in a number of arts, and I lay no claim to them, theinvention residing in the manner in which they are adjusted, in the accessibility to the adjusting means and the extreme compactness of the organization. The carrier 5 as represented has between its ends openings into which the respective bearings 25 project, these openings as shown consisting of annular channels or grooves 26, the inner threaded approximately cylindrical ends of the two sets of bearlng sleeves 25 projecting into said openings 26 (Fig. 15). Fitted onto said threaded ends are adjusting nuts 27 and check-nuts 28. By slightly backing off the check-nuts 28 the adjusting-nuts 27 can be rotated to draw the bearing sleeves 25 inward to thus take-up wear, and when the necessary adjustment or adjustments are obtained, the .check-nut or nuts 28 are set up to eifectually maintain the same. It will be clear that the several pairs of nuts are located within the respective annular channels 26. By lifting from place the cap 9, the hand can be reached into the channels 26 to secure the adjustment to which allusion has been made. It will be evident that the adjusting nuts 27 fit substantially against the outer walls of the channels 26.

In connection with each spindle there is provided a suitable end-thrust bearing and -justing-collars 31 which as shown are threaded to the respective spindles and also disposed in the forward channel 26, thus insuring compactness in the case of the ballbearings and their adjusting means whether they be in the form of collars 31 or otherwise. By turning these collars 31 the respective bearings 29 can be shifted on their cooperating spindles to adjust to a nicety the contact between the forward flanges 32 of the spindles and the front end of the cylindrical carrier5; as a matter of fact owing t0 the described construction engagement between the flanges 32 or equivalent projections and the carrier or head 5 can be made practically nothing, just suflicient practically to prevent chips or other material working between the flanges 32 and the carrier or head 5. The wear-take-up mechanism and the adjusting means therefor and the anti-friction thrust means and adjust ing mechanism therefor are as observed, housed or incased within the carrier 5, thus securing compactness; at the same time they are readily accessible.

Thespindles 14 are provided at their for- .ward ends with the chucks 33 closable by the nose pieces 34 rotativewith said spindlesl ward cause the closing of the chucks 33 on the work. Connected with the outer end of the spindles are the finger blocks 36 to which are pivoted the fingers 37 operated by, the conical members 38slidable on the respective spindles and actuated by a slide operated in turn by a cam-drum 39 (Fig. 1, for example) on the shaft 40. The feed sleeves 41 inclosed by the respective spindles are provided at their outer ends with spools 42 actuated by a slide operated in turn by a cam 43 on said shaft 40 as shown in Figs. 1 and 4 for example. The stock-feeding and chucking-means are very common in the art. and therefore, has been but briefly described. In the present case the chucks are opened after which the stock or work is advanced following which the chucks are 7 Inclosed bythe spindles 14 are the push sleeves 35 which on being thrust forclosed all as very common in automatic screw-machines.

It will be remembered that I have referred tothe fact that normally the spindles 14 are constantly rotated. and that also norstant operativeconnection with the shaft 15 or something of an equivalent character. Mounted for swinglng movement on the frame member 3 such for example by being pivoted thereto between its ends,-isthe lever 44 presenting asuitable means for governing the spools 23; this lever 44 in fact constituting a suitable clutch actuating or governing means. The upper branch of said lever 44 (Figs. 2 and 15) is provided with an inwardly extending stud or projection 45 adapted to successively enter the peripheral channels of the spools 23 as the carrier or head 5 rotates, the stud 45 being caused to enter such a channel as the carrier is indexed. This lever 44 is normally at rest. It will be assumed that the carrier 5 has been indexed and that on the turning of the carrier the stud 45 has been projected into the channel of a spool 23. This spool is on the spindle l4 which carries the work which should be threaded. When the stud' is positioned in the requisite channel the lever 44 is operated as will hereinafter appear to cause its upper arm to swing outward, thereby carrying the spool 23 which the stud engages therewith and causing the unclutching of the pinions 20 and 17 cotiperative with said spool. At the conclusion of the threading operation the shaft 44 is oppositely swung so as to return the spool which it engages to its initial position, thereby again clutching the two pinions 20 and 17 associated with said spool, by virtue of which the spindle carrying such particular pinions can be driven at its high speed. On a second motion of the carrier 5, the operation is repeated. The cam-drum 39 (Fig. 2) is provided on its peripherywith a camstnip 46 adapted to engage a projection as the anti-friction roller-47 on the lower end of the lever 44. As the cam-drum" rotates and just about the time the stud 45 enters the channel of a spool 23, the wedge or active face of this cam 46 engages the stud or projection 47 of the lever 44, swings the lower branch of said lever 44 to the left in Fig.

2, and the upper branch to the right, thereby moving to the right in said Fig. 2 the upper arm of the lever and correspondingly moving the spool which said lever engages so as to unclutch the two pinlons 20 and 17 associated with the spool 23 thus shifted. At a subsequent point in the rotation of the cam drum 39 the active portion of the cam element 48 thereon engages the stud or projection 47 and as the drum continues to rotate the lever 44 and there fore the spool which for the time being it controls,. are returned to their initial positions to again clutch together the two pinions mentioned.

Between the points at which the cam- elements 46 and 48 operate, the lever 44, the pinion 20 which for the time beingis unclutched from the coact-ing pinion' 17 is driven at a low speed, and the means shown rier 5 is indexed and looked as will hereinafter appear a pinion 20 is brought oppo site the pinion 53 and as will be inferred this particular pinion is unclutched from the coiiperating pinion 17 and when thus unclutched the pinion 53 is moved by the shifting of the lever 50 to cause its teeth to mesh with the adjacent pinion 20 to thereby drive the latter and'the spindle 14 connected therewith at a low speed. Normally this lever 50 and therefore the pinion 53 supported thereby, is. maintained out of the path of movement of the pinions 20, for instance by the spring 54 acting thereagainst as shown best in Fig. 5. The end-of the shaft 51 opposite that provided with the spur gear or pinion 53 is supported by the boxing or housing 55 fastened to and risingfrom the frame member 3, said shaft 51 being connected by speed-reducing change-gearing shaft 15 as shown in Fig. 16. It, therefore, follows that the shaft 51 is constantly driven at a low speed. ,Anydesirable means may be provided for operating the lever 50 to put the pinion 53 into mesh with the pinion 20 between times at which said leveris operated by the cam elements 46 and 48 as already described. For this purpose I have shown the cam element 56 fastened'to the disk 57 (Fig.5), the disk in turn being rigid with the shaft 40. Between the point at which the; cam members '46 and 48 oscillate the lever 44 the cam 56 engages the free end of the lever 50 swinging said free end outward and-thereby causing the pinion 53 to engage the pinion 20 which for the time being is exactly opposite it. 'When the active portion of the cam 56 passes from oft the free end-of the lever 50, the-spring 54 acts against said lever 50 to move the upper arm thereof outward and cause the pinion 53 to be disengaged'from a pinion 20 and when the unmeshed relation is accomplished, the

carrier '5 is indexed.

denoted in a general Way by 55 with the I provide means for checking the motion of each spindle just before the pinion or spur gear 53 is thrown into mesh with the pinion 20 on said spindle, and for this means a suitable brake as the lever 58 (Figs. 2 and .latter is freed. the brake lever exercising its function in the short interval between the point at which the quick feed mechanism.

and the slow speed mechanism for a spindle are successivelv operated.

Any desirable means may be provided for indexing the rotary carrier or head 5,,

although that shown and now to be described has been found eminently satisfactory and highly advantageous. In conjunction with the carrier 5 or its equivalent, there is provided a suitable locking bolt as 61 which is supported for sliding movement in a seat or opening formed radially in the casing 6. From this casing there extend outward the rods 62 tapped into or otherwise suitably rigidly connected with the casing, these rods forming a suitable guide support for the yoke 63 held in place on the rods by the nuts 64 fitted to said rods 62. This yoke 63 constitutes a suitable bearing for the duplicate springs 65 which enter holes in the bolt 61 and by acting against the abutments of said holes to exert a constant tendency to thrust the bolt inward where it can engage in the appropriate one of keepers or channels as 66 connecting the apertures 26 to which I have already referred. The bolt 61 is slotted to receive the operating lever 67 (Fig. 2) fulcrumed between its ends to a bracket on the frame member 3. The lever 67 is provided at its lower end with a stud 68 operable by the cam-disk 69 rotative with the shaft 40. The operative part f the cam-disk 6%) strikes this stud 68 inst prior to the point at which the carrier 5 is to be indexed. wherebv the bolt 61 through the lever 67 is retracted or drawn outward to release the carrier 5 and permit its being indexed. The operative portion of the cam disk 69 acts onlv momentarily against the lever 67 releasing said lever just about the time the carrier 5 commences to turn bv virtue of which when the cam-disk 69 releases the lever. the springs 65, can thrust the bolt 61 inward. so that when a ch .nnel or locking seat 66 comes opposite the bolt, the inner end of the bolt can be instantly shot into said channel or lockingseat by the power of the two springs 65.

The indexing mechanism is shown best in Figs. 6 and 7. Rigid and concentric with the carrier 5 is a spur-gear 70 in mesh with the spur gear 71 which with the star-Wheel 72 is loose on the shaft 10, the star-wheel being rotative with the spur-gear 7-1 which condition is best secured by making the two in one piece. As shown the carrier 5 supports six spindles 14, and it, therefore, follows that the said carrier on each intermittent or indexing motion is given a onesixth turn, the star wheel 72 as a consequence having six teeth or spokes. As shown each of the teeth Or spokes of the star wheel 72 has a channel or slot 73 dis- ,posed radially of said star wheel and open .rotation by said brackets 76 and 77. The

spur gear is provided with a lateral stud 80 which is adapted to operate against the teeth or spokes of the star or Geneva wheel 72. This stud may as shown consist of an anti-friction roller. The spur gear 75 is intermittently operated, being given a complete turn on each intermittent movementbut the full turn, however, is not utilized for operating through the stud 80 the star-or Geneva wheel 72 for a reason that will be hereinafter explained. When the intermittent motion of the spur-gear 75 is completed, the stud or anti-friction roller 80 will be exactly opposite the outer open end of a channel or slot 73, so that when the spur gear 75 is turned, this stud 80 will ride up into and then out of said groove or channel 73 which it may be opposite to thereby turn the star or Geneva wheel 72 one-sixth of a rotation, the stud 80 during this action following an are defined by the distance between the outer ends of two adjacent channels 73. The shaft 79 may be driven in any desirable manner. for example by the spurgear 82 driven in turn by the pinion 83. the means for rotating which latter will be hereinafter described. One end of the shaft 79 extends into the bushing 81 supported by the bracket 77 and projecting into the elongated hub 85 of the boxing 86 provided on its inner side with an annular flange 87. Surrounding the hub 85 is the member 89 provided with a flange 90 opposite and practically complemental to the flange 87. The spur-gear 82 surrounds the hub or member 89 and between said spur-gear and the flanges 87 and 90 are disks of leather or equivalent friction material 91 to thereby provide for slippage in case any obstruction is met by the carrier 5 during indexing operation. This boxing 86 constitutes one member of a clutch being chambered on its outer side as at 92 and in which chamber is disposed the companion clutch member 93. The clutchmember 93 is rigid with the shaft 79. It

follows that if the tooth 95 be out of the notch 94 the shaft 79 will not be rotated, notwithstanding the fact that the spur gear 82 be turning. If, however, the shaft 79 be moved endwise toward the left in Fig. 7 in the present case, the tooth 95 will be projected into the notch 94 relatively to effect the rotation of said shaft 79 on the rotation of the spur gear 82. When the members 93 and 86 of the clutch are disengaged, the rotation of the shaft 79 will be stopped.

Around the body of the clutch member 93 which it will be remembered is rigid with the shaft 79 is the friction-ring 96 (Figs. 7 and 14) which in turn is surrounded by the split clamping-ring 97 constituting itself one member of a clutch. This divided clamping ring 97 is provided with a radial outwardly-extending dog or lug 98. Said ring 97 is inclosed by the chamber 92 and the dog 98 enters a notch 99 in the wall of said chamber 92. so that the clutch-member 86 is constantly frictionally clutched to the clutchmember 93, the friction between the elements 93 and 97, however, being much lighter than that between the gear 82 and the flanges 87 and 90. On the shaft 79 (Fig. 7) is a slidable collar 100, there being a second collar 101 fastened to said shaftsurrounding which between the two collars and bearing against said collars, is the coiled spring 102 the purpose of which Wlll be hereinafter explained. On the shaft 40 is the drum 103, Fig. 2 for example, and on the side of this drum is a cam member or tappet 104 (Fig. 7) coiiperative with the lever 105 pivoted on the framing of the machine and cooperative in turn with the flange 106 of the collar 100.

The stud 80 is normally opposite the outer open end of one of the channels 73 and the tooth 95 is normally out of the notch 9 1. At the appropriate point in the operation of the machine or just prior to indexing, thetappet or cam member 104 on the rotation of the drum 103, will engage the lever 105 and swing the same toward the left in Fig. 7, thereby moving the collar 100 in a corresponding direction and through the spring 102, the collar 101 and shaft 79 in a similar direction, the shaft owing to the presence of the spring 102 being yieldingly operated which is advantageous inthat if initially the tooth 95 should strike the uncut part of the clutch member 93, no damage can ensue. If this condition should occur the spring will be tensioned so that when the notch 94: comes opposite the tooth 95 on the rotation of the clutch-member 93, the tooth will be relatively forced into said notch, thereby causing the rotation of the shaft 79 and through the described parts, the indexing of the work-carrier 5. As I have noted the work-carrier 5 is not indexed through the complete rotation of the spur gear but only on a partial rotation thereof. The indexing should be accomplished, however, while the tooth 95 is in 'the notch 94 at which point as will be understood the shaft 79 is clutched to the gear 82 through the leather disks 91, the friction at this time being pow-. erful. WVhen the carrier 5 has been given a one-sixth turn as previousl set forth, the tooth 95 relatively is withdrawn from the notch 941 by the motion toward the right in the present case, of the shaft 79, and this result can be obtained through the button 107 on the spur gear 75, the conical portion of which button is adapted to engage the correspondingly conical portion of the disk 107 rigid with the shaft 79, the parts being so organized that after the work-carrier 5 has been indexed and locked by the bolt 61 in the manner already described the button 107 will be carried against the disk 108 to move the shaft 79 longitudinally to the right in Fig. 7, whereby the tooth 95 will be relatively withdrawn from the notch 91. At this time, however, there is friction between the clutchmember 86 and shaft 79 through the friction-ring 96 and other parts already set forth, suflicient to impart to the shaft 79 and therefore the spur-gear 75 through the intermediate parts, the complete rotation or sufficient to carry the stud opposite the outer end of a channel 73 at this time at rest.

- WVhen the button 107 passes free of the disk 108, the spring 102 by acting against thecollar 101 will move the shaft 79 toward the left in Fig. 7 so as to cause the tooth 95 to enter the notch 91 which in fact is the normal relation of the parts.

The pinion 83 is fastened to the shaft 109 which in turn has rigid with it the spur gear 110 (Figs. 17 and 18) in mesh with the pinion 111 fastened in some desirable way to the shaft 112 which as shown extends into the -/change-gear-box 113 rigid with and extend ing from the frame member 1. This shaft 112 is the main or primary one of the machine and may be driven in any desirable manner, for example by the pulley 111 fastened to the outer projecting end thereof as shown best in Fig. 8.

The tool-carrier as stated is reciprocatory and a tool-carrier such as meets the desired conditions is that denoted by 115 (see Fig, 10 for example and also Figs. 1, 2 and 3). This tool-carrier or slide 115 is provided at its inner end with an approximately cylindrical rigid head 116 to the inner face of which are connected in some desirable manner the necessary tools by which the work is reduced or otherwise acted upon. Each piece of work as will be clear is presented to a tool. The part 117 shown, for instance, in Figs. 2 and 19 is a die-holder used in threading and with its actuating mechanism will be hereinafter more particularly set forth. It will be clear that when the work is presented to the threading-die, the spindle coaxial with the die-holder is driven at a low speed. The frame member 4 has a table or top 118 presenting a suitable support for the slide 115. It will be noted that the shaft 15 extends through the tool-carrying head 116 and thus aids in guiding and supporting the slide 115. The table 118 is rabbeted out at opposite sides on the top thereof as at 119 to receive the lateral portions of the slide 115, the gib pieces 120 fastened by screws or otherwise to the table 118 overlying said lateral portions to aid in guiding the slide 115, the planes of support of the slide being coincident and practically intersecting the axis of the head 116 so as to provide for an easy and balanced movement of said slide. One and probably the principal function of the drum 103 is to reciprocate the tool carrying slide 115. This camdrum 103 has on its periphery two cam members 121 and 122 (see Figs. 1, 10, 11 and 12) which successively act against a suitable projection on the slide 115 for reciprocating the latter. This projection as shown consists of a shoe 123 pivoted as .by the pin 124 to the under side of the slide 115 between the ends thereof, the shoe as will be clear having a surface contact with the edge portions of the cam members 121 and 122. The cam member 121 encircles the drum 103 for the major part of the circumference thereof, being disposed spirally thereof and its forward or inner edge portion by wiping against the shoe 123 moves the slide or carriage 115 inwardly to carry the tools thereon against and then onto the work in the carrier 5 at this time at rest. When the tail portion of the cam 121 (the upper part of said cam in Fig. 1) passes free of the shoe 123 there is an interval between the time at which the cam 122 comes against the shoe. The pitch of the cam 121 is a very low onebut extends over a considerable part of the circumference of the drum 103, by reason of which the full inward stroke of the slide 115 is secured slowly. The pitch of the cam member 122 is, however, very steep so that when the cam 122 acts against the shoe 123 after the cam 121 and after the cutting or other operations have been concluded said cam 122 will rapidly retract or return said slide 115 to its extreme backward position. There is a very small interval between the leading end of the cam 122 and the entering end of the cam 121, so that the slide 115 is in its back position but a comparatively short interval. The slide advancing cam 121 is laminated or in layers. It is imperative that this cam should be of a certain thickness in order to possess the requisite strength or resisting ability, and if it were in a single thick piece'it would be practically impossible to wrap it tightly about the drum 103 on different spirals, but by laminating the cam I find that I can easily bend or flex the same to the precise shape of the cam drum at any place in the lateral extent of said drum and thus cause said cam to closely hug the drum. The cam 121 is of course laterally adjustable and the bolts 125 are utilized in the present instance for maintaining the adjustment. By this lateral adjustment the stroke of the slide 115 can be regulated. At the same time the bolts 125 can be utilized for holding the sections or strips of said cam 121 in rigid relation with each other. As shown these bolts 125 project into T-openings 126 extending crosswise of the periphery of the drum '103, the inner ends of the bolts carrying T-nuts 127, the bodies or cross portions of which fit in the transverse portions of said T-openings 126 which openings as shown are in the form of grooves. 'By backing out the several bolts 125 the cam 121 can be loosened sufficiently to permit lateral adjustment thereof, and when this is secured the bolts will be set to clamp the laminated cam member substantially in place.

The framework of the machine may as shown be provided with a depending stud 123 in the form for example of an antifriction roller adapted to receive backthrust of the cam drum 103. Said roller 123 is adjacent the shoe 123, the latter being located at one side of the cam members 121 and 122 and the stud or roller 123' at the other. In the organization shown said stud or roller 123' is supported by the table 118.

The cam drum 103 can be driven in any desirable manner. The mechanism shown for this purpose will now be described and is satisfactory. Said cam drum has within it the internal gear 129 fastened in place by screws or otherwise andin mesh with the pinion 130 (Figs. 8 and 10 for example). This pinion 130 is loose on the shaft 131 and rigid with it is the friction clutch member 132 (Figs. 8 and 9) which receives within it the clutch member 133. This shaft 131 may be supported in any desirable manner. As

shown its inner end extends into the camdrum 103, (Fig. 8) there being provided a bearing within the cam drum for supporting the inner end of said shaft 131. The pinion 130 and clutch member 132, are loose on the shaft while the clutch member 133 is rigid with said shaft, for instance, by being keyed thereto. Rigid also with said shaft 131 is I fitting the finger block 134 having the fingers 135 the free ends of which are forced outwardby the conical portion of the sleeve 136 to cause the tips of said fingers to force the clutch member 133 into driving engagement with the clutch-member 132. Supported by the frame work is the shaft 137 having at its inner end the bifurcation 138 straddling the sleeve 136 and provided with studs 139 in the peripheral channel of said sleeve 136. At the forward end of the shaft 137 is a hand lever 140 by which said shaft 137 can be oscillated. In Figs. 8 and 9 the hand lever 140 has been swung over by the attendant of the machine to cause the conical portion of the sleeve 136 to swing the free parts of the fingers 135 outward and thereby cause the tips of said fingers to press the clutch member 133 into coupled relation with the clutch member 132 to effect the rotation of the pinion 130 and hence through the described parts the rotation of the drum 103. By swinging the bifurcation 138 to the right in Fig. 8 through the agency of the lever 140, the sleeve 136 will he slid along the shaft 131 to cause the fingers 135 to free the clutch member 133 whereby the latter can be disengaged from the companion clutch memher by the springs 142.

The shaft 15 can be driven by change gearing denoted in a general way by 143 from the primary or main shaft 112. Said shaft 15 in turn can be connected through change gearing of suitable kind such for instance as that shown and now to'be described,

with the shaft 131. 'Fastened to the shaft 15' is a pinion 15 in mesh with the spur gear 144 (Fig. 8) fastened by keying, pinning or otherwise to the pinion 144, the spur gear 144 and pinion 144' being loose on the shaft 131. This pinion 144' is in mesh with the spur gear 144 to which is keyed or otherwise suitably connected the pinion 145, the spur gear 144 and pinion 145 being loose on the shaft 40. The pinion 145 is in mesh with, the spur gear 145 keyed orotherwise suitably fixed to the shaft 131 to which it will be remembered the cam-drum-operating pinion 130 is fastened. The spindles 14 it will also be remembered are driven from the shaft 15. Through the change gearing 143 I can vary the speed of the spindles 14 and cam drum 103 in exact correspondence with each other without in any manner varying the speed of the indexing mechanism which in the organization shown is operated primarily from the shaft 112 and pulley 114, said pulley 114 being in the present case operated at a constant speed. I can also through the change gearing between the shafts 15 and 131 vary the speed of the shaft 131 without changing the speed of the shaft 15. In these changes, however, the speed of the shaft 112 and pulley 114 and the shaft 109 driven from the shaft 112 and oper- Fig. 9. The clutchmember 132 has on its inner edge teeth 146 of bevel form meshing with the bevel teeth 147 at the inner end of the shaft 148. This shaft 148 is socketed as at .149 to receive the stud 150 of the handcrank 151, the stud 150 being provided with a key 152 to enter keyways 153 in the outer end of the shaft 148 when the pin or stud 150 is introduced into the socket 149. When the hand lever 140 is thrown or shifted to cause the operation of the shaft 131 by power, said hand lever 140 will cross the socket or opening 49, so that the pin 150 cannot be introduced into said socket or opening at such time. When, however, the handlever is operated to arrest the motion of the shaft 131 by power, said hand lever will be carried from across said opening 149 so that the pin 150 can be introduced into the socket and the key 152 into the keyways or notches 153 at which point the shaft 148 can be rotated by the crank 151 to effect through the described connections the manual adjustment of the slide 115. When the crank 151 is in place, it prevents movement of the hand lever 140 sufiicient to cause engagement of the clutch- members 133 and 132, so that there isQa mutual locking action.

I have briefly alluded hereinbefore .to a die-holder as 117. This die-holder is shown in several of the principal views, among them Fig. 2 and with its associated parts is illustrated indetail in Figs. 19 to 24 inclusive to which reference may now be had. Said die-holder'117 is rigid with the spindle 160 being situated at'the forward end of said spindle, provided approximately near itsrear end with the finger or projection 161, the purpose of which will be hereinafter explained. Between the die- .holder and the tool-carrying head 116 is inthe head 116. Loose on the outer projecting end of the bushing 163 is the clutch member 164 rigid with which is the pinion 165 in mesh with the spur-gear 166 fastened to the spindle operating shaft 15. The spur-gear 166 is constantly driven and in turn constantly drives the pinion 165, which latter is normally disconnected from the spindle 160. Intermittently, however, the pinion 165 is clutched to said spindle through the agency of the clutch member 16% and a companion clutch member 167 hereinafter more particularly described, and when this clutched relation occurs said spindle will be rapidly backed off the particular piece of work which has been threaded. The finger 161 to which I have referred coiiperates with a slide 168 on the main slide or table 115, the auxiliary slide 168 being held in position and guided by'gibs as 169 fastened to the slide 115. Rising from the slide 168 is the upright 170'to which is fastened by screws or otherwise the flange or plate 171 cotiperative with the finger 161 and associated with this slide 168 is a stop as 172 which is preferably adjustable and which as shown consists of a nut threaded onto the rod or screw 173 rigid with and projecting outwardly from the slide 168, the nut 172 being maintained in its adjusted relation by a check-nut 174 backing up the same. When the slide 115 is in its retracted position the finger 161 rests on the plate or flange 171. As the slide 115 is advanced in the manner already described and shortly before said slide 115 and hence the head 116 reach their extreme inner positions the adjustable stop 172 will strike a fixed part as the arm 175 connected with the frameworkof the ma- ,chine so that on the continued movement of the slide 115 the small slide 168 will be arrested and will be pulled relatively from under the finger 161 at the time the die in the die holder 117 finishes the threading operation. Then the finger 161 passes from off the slide 168 the spindle 160 can rotate to permit it being backed ofi the work. The threaded rod or screw 173 extends through an opening in the free end of the arm or fixture 175. After the tools, except the threading tool, have performed their functions, the slide 115 is returned to its primary position, the threading tool being still on the work, and on this retractive movement of the slide 115 the clutch member 167 will be caused to engage the clutch member 161, the two being held out of clutched re lation normally by the spring 176 encircling the spindle 160 and bearing respectively against the bushing 163 and clutch member 167 which clutch member 167 is pinned or otherwise suitably fastened to said spindle 160. This clutch member 167 is provided with a spring actuated pawl 177 adapted to enter the longitudinally extending channel or notch 178 in the clutch memher 161. lVhen the slide 115 has been re tracted a certain distance or up to about the point that the threading operation is concluded the pawl 177 will be entered in the channel or groove 178, thereby connecting the clutch members 167 and 1641 and as a consequence effecting the rapid rotation of the spindle 160 and hence the backing off of the (lie or threading tool from the work. Whenthe die has been wholly freed of the work, at which time the slides 115 and 168 will have been returned to their original positions, the slide 168 will be in the path of the finger 161 to arrest the rotation thereof and also of the spindle 160.

I provide means of a highly effective character for lubricating the various spindles 14 and the spindle-operating shaft 15, and this means is shown best in Fig. 15. Extending radially of the work carrier 5 are ducts 179 the inner ends of these ducts opening into the bore or hearing opening of the carrier 5 into which the shaft 15 is fitted. These ducts 179 also intersect the openings in which the spindle bearings 25 are fitted, said spindle bearings having between their ends annular channels 180. The shaft 15 is fitted in bushings 181 disposed in the work carrier 5 and each bushing 181 has ports 182 in constant register with the inner ends of the ducts 179. F itted into the upper section 8 of the casing 6- as shown for example in Figs. 1 and 2 are oil cups 183 which discharge into the ports 181 (Fig. 15) in said casing section 8, the oil cups or equivalentsconstantly supplying these ports 184 with oil or other lubricant which in turn is supplied to the ducts 179 as the outer ends of said ducts register with said ports 184 on the rotation of the work carrier, two bores or ducts 179 registering with the ports 18& at the conclusion of each indexing operation. From these ducts the lubricant is conducted into the channels 180 of the bearings 25 and also into the ports 182. The oil passing into the ports 182 lubricates the shaft 15. Leading from the annular channels 180 are ports 185 by which the spindles 1a are lubricated.

What I claim is:

1. A carrier provided with a plurality of rotary spindles, the inner ends of which are provided with projections fitted against the carrier and the latter having an annular groove, bearings for the spindles, adjusting for use in machines of the class described,

having a series of spindle-receiving openings arranged in approximately annular order and also having an approximately central shaft receiving opening, and a series of lubricant-conveying ducts, each duct intersecting diametrically Opposite spindle-receiving openings and the shaft receiving opening, the ends of the ducts opening into the periphery of the carrier.

4. A rotary carrier provided with a, series of rotary spindles and also having lubricant-conveying ducts opening at their ends into the periphery of the carrier, said ducts intersecting diametrically-opposite spindlereceiving openings, and a casing in which the head is mounted, the casing having a port to register with the ends of the ducts. on the rotation of the carrier.

5. A carrier provided with a rotary spindle, a bearing for the spindle supported by the carrier, the bearing having an annular circumferential channel and also having a.

ery of the head.

7 A carrier provided with rotary spindles, bearings for the spindles, the carrier having openings to receive the bearings, the bearings having annular channels and also having ports leading from said channels to the respective spindles, said carrier having a duct intersecting the'b'earing openings at the-point in which said channels are located, the ends of the duct opening into the periphery of the head, and a casing in which said headis rotatively mounted, having a port adapted to register with the opposite ends of said duct on the rotation of the head.

8. A carrier provided with rotary spindles and with arotary shaft, connections between the shaft and the spindles for rotating the latter, bearings for the spindles, and a bushing for the shaft, the carrier having a duct opening at its ends into the periphery thereof and intersecting the spindle openings and the shaft opening, the bearings and bushing having means to receive lubricant from the duct and for conveying the same to the spindles and shaft respec- 'tively.

9. A rotary carrier provided with a plurality of rotary spindles. a driven element loosely connected with each spindle, a second driven element rotative with each spindle, mechanism for connecting and discons necting the driven elements of the respective spindles, means for rotating the first driven elements of the several spindles, and independent mechanism for intermittently rotating each second driven elementwhen it is disconnected from the companion driven element. i

10. A rotary carrier provided with a plu-i rality of rotary spindles, a pinion loosely connected with each spindle, a second pinion rotative with each spindle, mechanism for connecting and disconnecting the pinions of the respective spindles, a rotary pinion in mesh-with all the first pinions, and a pinion for driving each second pinion when the same is disconnected from the companion pinion. r

11. A rotary carrier provided with a plu-' rality of rotary spindles,'a pinion loosely connected with each spindle, a second pinion rotative with each spindle, a rotary shaft supported by the carrier and provided with a pinion in constant mesh with said first pinions, mechanism for connecting and disconnecting the respective pairs of pinions, a rotary pinion supported independently of the several pinions, and means for moving said independently supported pinion into mesh with each second pinion when 'the latter is disconnectedfrom its companion pinion.

12. A rotary carrier provided with a plurality of rotary spindles, mechanism for indexing said carrier, a pinion loosely con nected with each spindle, a second pinion rotative with each spindle, mechanism for connecting the sets of pinions and for disconnecting the same approximately at the conclusion of each indexing operation,

- means for simultaneously rotating the first pinions, a rotary pinion supported independently of the carrier, and mechanism for a moving the independently supported pinion into mesh with each second pinion when the same 1s disconnected from a companion PHI-*- ion and approximately at the conclusion of each indexing operation.

13. A rotary carrier provided with a plurality of rotary spindles, adriven element loosely connected with each spindle, a second driven element rotative with each spindle, a. friction coupling device between each pair of driven elements, indexing mechanism. for the carrier, means for pressing the sets of driven elements toward each other to secure through said clutch device a driving connection therebetween and for moving them away from each other at approximately the conclusion of each indexing operation, means for simultaneously rotating the first driven elements, and independent means for inter-

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