US2362480A - Shoe tacking machine - Google Patents

Description

6v Sheets-Sheet l W. GLEISSNER SHOE TACKING MACHINE Filed Sept. 23, 1940 Nov. 14, 1944.

Nov. 14, 1944.

W. GLEISSNER SHOE TACKING MACHINE 4 Filed s'ept. 25, 1940 6 Sheets-Sheet 3 NOV' 14, 1944- w. GLElssNER SHOE TACKING MACHINE Filed Sept. 25, 1940 6 Sheets-Sheet 4 Nov. 14, 1944. w. GLEISSNER SHOE TACKING MACHINE Filed sept. 2s. 1940 1g. 5a M Eig. 6

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NOV. 14, 1944. w GLEISSNER 2,362,480

' sHoE 'TACKING MACHINE Filed sept. 25, 1940 e 4sheets-sheet ev GMS/argv' fected at equal distances from the ed Patented Nov. 14, 1944 UNITED STAT ES .PATE-N astri- T OFFICE SHOE TACKING MACHINE Walter Gleiss'ner, Weissenfels-Saale, Germany;

vested in the Alien Property Custodian Application September 23, 1940, Serial No.

. In Germany July 7, 1939 4,23 Claims Machines .are known for making shoes, particularly tacking machines. VWith these known.

applicable in the case of' tacking machinesequipped with a punching device.

f- This invention relates to'a shoe tacking machine and more particularly to means to mechanically and automatically. oscillate the lshoe support or work holder of such a machine relatively to the tacking and punching tools.

The invention resides in the provision ofan" oscillatory shaft connected with the shoe support or work holder, which oscillatory shaft is power rotated .alternately in one direction and then in the other direction from land to its normal position, to present the work, as a shoe tip, to the tools in such manner that the tacking and punching operations,A commencing at the tip of the toe of the shoe, are first eiected from said tip along one side of the toe of the shoe, the operation of the tools being arrested after the ed upon, and the power disconnected from the oscillatory shaft. Other power means rendered effective incident to the preceding operation, restores the oscillatory shaft to its starting posimeans is rendered effective to rock the oscillatory shaft in the opposite direction to present the opposite side of the toe of the shoe to the tools, after which this power means is automatically vdisconnected from the oscillatoryshaftfto enable said other power means to restore the oscillatory shaft and work to their Vstarting positions.

The invention renders possible the tacking of the front of the shoe, commencing at the tip by a single series of automatically effected operations with simultaneous punching.

As a result, damage to the goods usuallyoccurring when the work is manually presented t'o the tools, is avoided, the work of the operator is relieved, and apart from proper stretching ofthe leather or other medium, the punching is efge` of the shoe. Furthermore, the spacing between the punched holes is approximately equal depending upon the particular adjustment o f .the controls for the work support, the working of the leather onto the'edge of the last, the punching, and the `work shifting being more readily an desired extent of the shoe tip has been operat- .g5-v

, 30 tion, incident to which the rst-named power d accurately performed than heretofore. e

The invention comprises a work holder oscillating mechanism, with control means 'to intermittently connect the oscillating mechanism with a power drive, to enable the power drive to advance'the work holder relatively to theworking tools, first in one direction from an intermediate starting position and then in the other direction, means vas auxiliary'motors being provided to restore the workv holder to its startingA position after each advance. The control means is intermittently.operatedwto set means to contro1 the direction `and extent of advance imparted by the power drive to the vwork holder;- to control the engagement and disengagement oi the power 'and ythe work holder, and to determine the time of operation of the work holder restoring means. y The connection of the control means with the power drive mechanism, after-starting the machine for operation, is, in turn,l rendered effective under control of the ywork holder oscillating means. 1 i

The control mechanism isv rendered by the power drive mechanism at the conclusion ofA each advance of the work holder from its starting position, and by the auxiliary -1 motor during the rst returnv stroke of the work holder.

Means to vary the extent of each advance stroke and rto temporarily detain thework holder in its advanced position also forms part of the invention, as doesthe means to yieldingly maintain the work in contact with the during the oscillations of the work.

`Geueral description y The machine of my invention is intended t0 function as follows:

The work, as a shoe, is securd'in a suitable,l rotatable holder' or shoe support which, in turn, is pivotally connected to the frame of the machine for movement towards and from an edge rest, vtheposition of which rest determines the distance from the outer edge of the shoe sole at which the punching and tacking line shall be located.

The shoe is applied to the work holder or support when the latter is in its idle position. 5,0y remote from the ed ge rest, after which the op- ,erator manually rocks the work support to bring the lshoe into contact with the-edge rest. I n' After the shoe support is properly positioned, and means is adjusted to select the sequence of directions in which the shoe is to be presented to effective Y edge rest the tools, the operator actuates a pedal to connect the power with the operation-controlling parts of the machine.

One of the first functions performed by the operated mechanism is to render effective av means to yieldingly retain the work support in position to press the work against the edge rest, thereby relieving the operator of this labor and placing the entire control of the work on the machine.

coincidentally, means is rendered effective for partially rotating the work support in the selected direction through bevel gearing to traverse the shoe from the point of the toe, part way along the side, during which traverse the punching and tacking operations are eifected.

Provision is made to vary the extent of this traverse, to adapt the machine for shoes of varying sizes.

Upon the completion of the predetermined traverse of the shoe inthe rst direction selected relatively to the punching and tacking mechanism, the poweris automatically disconnected from the machine, and later, a spring which has been tensioned by the machine incidentto the traverse of the work in the rst direction, operates *to ,return the work support and work to its initial working or starting position.

Means operableincident tov the return of the Work support to its starting position reconnects the power with the operation-controlling means, whereupon the work support is rocked in the opposite direction from its initial working or starting position to which it was automatically returned by spring action, and at the conclusion of the traverse of the shoe in said opposite direction, the power is again automatically disconnected, after which a second spring tensioned by the machine in traversing the shoe in said last-named direction. again returns the work support and work tov initial working position.

Incidental to such second return to initial working position. the means for holding the work supportv to yieldingly press the shoe againstl the edge rest is released. so that the work support may rock away from the edge rest to enable the shoe to be removed and another substituted.

It will be understood that the punching and tacking mechanisms operate on the shoe during the traverse of the shoe from its point or toe in either direction, and are idle during each return of the shoe to its initial workingor starting position. Y

In addition to the inventive features embodied in the means for automatically effecting the traverse of the work from and back to its initial working or starting position. in opposite directions, the invention includes novel means to automatically eifect the reversal oi traverse of the work, as a shoe. novel means to prevent overthrow of the work holder and work in either direction of movement. novel means to insure the proper oscillation of the work holder in either direction. and novel means to effect and control the yielding contact of the work against the edge rest.

[n order to eifect the traverse of the work in one direction from the point of the toe for a predetermined distance relatively to the punching and tacking mechanisms, and the returnA of the work to initial working position, followed by a traverse of the work relatively to the punching and tacking mechanisms in the opposite di rection and return, there is provided a coupling or gear driven from the same shaft which imparts oscillating motion to the work support.

Power for oscillating the shaft for communieating oscillatory motion to the work support is supplied from the counter-shaft of the machine, through a reversible link drive, the sequence of the alternating oscillations being controlled by a cam on the control shaft.

The connection of the power to the countershaft is controlled by linkage operable by hand or foot power, which enables the operator to arrest the machine at will, whereby to interrupt the' punching and tasking operations at any time.

One embodiment of the invention is illustrated in the accompanying drawings, in which Fig. l is a side elevation, partly in section, of a shoe tip punching and tacking machine of conventional type, to which the invention is vapplied,

Fig. 2 is a diagrammatic view in vertical section through Fig. l, on line 2'Z looking towards the right illustrating the drive and the controls for imparting oscillating movements alternately in opposite directions, each oscillating movement traversing the work from and returning it to its initial working position.

Fig. 2a is a similar view showing the parts in their normal idle positions,

Fig. 3 is a diagrammatic view in vertical section through Fig. 1, on line 3-3, looking towards the right, illustrating the pedal mechanism and the automatic controls for connecting the power with the control shaft,

Fig. 4 is a diagrammatic illustration of the link motion for imparting movement to the work support,

Fig. 5 is a fragmentary view in side elevation showing the link motion and its connection with the work traversing disk, and the centering mechanism to return the disk-driving pawl carrier to .its normal positiom Fig. 5a, is an edge View, partly in section, of

,the reversible, intermittent feed, and centering section, showing the idle position of the means for retaining the link motion and the oscillatory shaft, at one limit of their movement,

Figure 7a is a .fragmentary sectional view through the brake member and friction disc of Figure 7, l

Fig. 8 is a view similar to Figure '7 but showing the parts in their `effective positions,

Fig. 9a is a graph showing an alternating oscillatory path illustrating the movement of the shoe from the point of the toe, first to the left, then back to initial position, and thence to the right and backv to initial position, the return paths being indicated by broken lines in each instance, and

The shoe or work |is applied to, and held f' in place on the work support by suitable clamping means, and after the work is clamped to the work support, the latter is manually rocked until the tip or toe of the shoe contacts the' edge rest 31, as shown in Fig. 1.

Contact of the shoe with-the edge rest is automatically maintained during the operation of the punching and tacking mechanisms, not shown, on the work, in a manner hereinafter explained.

A suitably supported, normally idle counterqualified by (2) an adjustable means fon. determining the direction of such rocking either to rightl or to left of the initial position of the work support and work relatively to the edge rest, and (3) means to determine the extent of 4 such rocking.

shaft 33 supports a continuously-operated drive.

pulley 39 journaled thereon.

A second pulley 40 (Figs. 1 and 3) rigidly connected with the drive pulley 39 loose on the 1j counter-shaft 33 of the tool head, is connected by a belt 3| with a driven pulley 4| journaled on a pintle 42 projecting from the machine frame, thedriven pulley 4| being attached to one member 43 of a normally idle one- revolution coupling 43, 44 likewise journaled on the pintle 42.

The pulleys 40 and 4|, and the driving memvber 43 of the coupling continuously rotate in one direction even when the machine and its a.

counter-shaft 33 are not in operation.

The driven member 44 of the coupling has fastened thereto a drive pinion 45 in constant mesh with a driven gear 46 fast on a control shaft 41, the diameter of the gear 46 being, in

this instance, four times greater than the diameter of the driving pinion 45.

The horizontal control shaft 41 is suitably journaled in the machine head frame |3, the driven gear 46 being fast on one end of the shaft. Near its opposite end, the shaft also supports a peripherally grooved cam wheel 48 for controlling the means which automatically `presses the work against the edge rest 31 as hereinafter explained.V K i A sleeve 32 splined on the control shaft 41 l for axial adjustment along the shaft but rotating therewith, supports a pair of complementary control cam members 49, 50 spaced apart from one another.

Cam grooves 49' and 50' in the apposed faces of the respective cams 49 and 50 have the dual purposes of controlling the direction of oscillation of the work support 3 relatively to the edge rest 31, and of controlling the application of power to rock the work support 3 and the work on the advance stroke in either directionfrom. the

-neutral intermediate or initial position of, the

`work support relatively to the edge rest, and

after thek work holder and work have completed their advance in either direction, the control ,cams permit a supplementary motive power to restore the work holder and work to their said initial positions.

' A better understanding of this :part of the invention will be had if it is borne in mind that there is provided (l) an intermittently driven power -means to rock or advance the work support and work relatively to the edge rest, the

operation of which power means is modied or 7 l cessive areas to the tools.

'stroke without affecting the adjustment of the meansffor determining the extent or the direction of such stroke, and upon the disconnection,

of the poWer, other means returns thework support and work to its initial position relatively to the edge-rest.

Work support traversing mechanism The shaft 4 (Figi 1) of the rocking work support '3 is connected by bevel gears 5 with an oscillatory drive shaft 2| n suitably journaled in bearings in the head frame I3.

A friction disk 12 (Figs. 1, 2 and 4 to 6 inclusive) fast on the oscillatory shaft 2|, which disk maybe peripherally grooved, as shown, is advanced or partially rotated in one direction or the other by power applied thereto by a pawlcarrier'13 anddouble-acting friction pawl 15, to rotate the shaft 2|, the work support 3 `and the work'relatively to the edge rest to present suc- A gear |05 fast on the oscillatory shaft`2| is in constant mesh with a second gear |06 fast on a restoringshaft |01 journaled in the head frame I3 parallel with the oscillatory shaft. Depending upon the direction of the advance imparted to the oscillatory shaft 2|, one or another of two opposed-spring motorsv ||0, isl

tensioned by the rotation transmitted to the restoring shaft |01 by the oscillatory shaft 2|.

At the conclusion of the effective stroke of the pawl carrier 13 and its double-acting pawl 15, and consequently at the end of the advance rotation imparted thereby to the oscillatory shaft 2|, the supply of power to the pawl carrier and pawl is automatically interrupted.

To avoid interference with other mechanisms, as Well as'to maintain a systematic cycle of operations, each depending upon the preceding operation, means is provided to retain the tensioned work support restoring spring I0 or potentially effective until other Amechanisms have operated, after which thetensioned spring motor ||0 or as the case may be, becomes effective to reversely rotate the .restoring shaft |01 and throughgears |06, |05, the oscillatory shaft 2|, back to .their starting or initial positions to return the work support and work back to their initial positions.

Means 10 (Figs. 5 and) tensioned by the pawl carrier 13 on its power o r advancing stroke, acts 'to center the pawl carrier and pawl in their starting positions upon the return ofthe pawl carrier to its normalposition tively shiftable manually into and out of oper-jy ative position.

vThese conditioning cams'also control the operativity of the driving cam member 69, and preprior to the dis-v vent premature operation. of the spring motors H0, which return the oscillatory shaft 2|, work support 3 and the work to their initial positions.

' It will be recalled that there is a normally idle one-revolution clutch mechanism 43, 44 between the constantly rotating driven pulley 4| and the driving pinion 45 inmesh with the driven gear which is four times the size of the driving pinion.

A clutch control lever |32 (Figs. l and 3) normally holds' the clutch coupling 43, 44 disconnected.

After the work support 3 has been manually rocked to bring the top or toe of the shoe against the edge rest 31, the operator steps on the end |28w (Fig. 3) of the pedal lever |28 pivoted at |2821 to depress the pedal clockwise against the tension of its return spring |28c. The free rear end of the pedal lever normally engages beneath a yielding by-pass pawl |29 pivotedY at the forward end of an intermediate lever |30 rocking about the pin |30a, the rear end of which lever is connected by a rod |31 with one arm of the'gear clutch controllever |32 pivoted at |32a.

A spring |3017 conveniently connected'to the intermediate lever |30, tends to rock the intermediate lever clockwise and through the ro'd |3|, normally restores the gear clutch control lever |32 to position to effect the disengagement of the one revolution clutch members 43, 44 and to hold them disengaged.

Therefore, when the pedal lever |28 is rocked clockwise, its rear end rocks the intermediate lever |30 clockwise against the tension of its restoring spring |3017, to shift the gear clutch control lever |32 to its ineffective position, after which the rear end of the pedal lever |28 escapes past the by-pass pawl |29, thereby releasing the gear clutch control lever |32 and the intermediate lever |30 to the action of the restoring spring |3017 which returns both levers to their normal positions, irrespective of the position of the pedal lever |28.

Return of the gear clutch control lever |32 is without effect on the instant rotation of the pinion 45 because the clutch members 43, 44 have been rotated past the end of the clutch control lever |32, which remains in position to automatically disconnect the clutch members 43, 44 at the end of a single rotation of the pinion 45, the pinion in its rotation advancing the vdriven gear `48 a quarter of a revolution.

1 Upon release of the pedal lever |28, its spring |280 restores the pedal counter-clockwise to its normal position, the rear free end of the pedal lever wiping idly past the Aicy-pass pawl l|29 to position its` rear end beneath the by-pass pawl.

The large driven gear 46 being fast on the control shaft 41'turns the' latter one quarter of a revolution, and the complementary control cams 49, 50 axially but not rotatably shiftable on the control shaft are likewise rotated one quarter of a revolution.

Control mechanism jecting from the head frame I3, the arm 54 eX- tending upwardly to a, point between the apposed cam-grooved faces of the cam disks 49, 50 approximately in horizontal alinement -with the control shaft 41.

Fig. 2A shows the normal positions of the parts disclosed in Fig. 2, and from Fig. 2A, it will be noted that, prior to the operation of the machine, the relation of the median courses of the two complementary cam grooves 49 and 50 to the ends 52 and 53 of the stud at the upper end of the intervening crank lever arm 54 is such that the cam disks 49, 50 may be slid in either direction to t oneor the other of the cam grooves 49', 50' over the adjacent protruding end 52 or 53 of the stud at thel upper end ofsaid intervening crank arm 54. In their normal positions, the median sections between the high or low points of the complementary cam grooves lie in exact alignment or register. y

These complementary cams 49 and 50 enable the operator to select which cam shall control the movement of the work throughout both oscillations thereof in opposite directions from the initial position 0f the work With its toe in contact with the edge rest 31, and the only difference between ythe cams is that if the groove 49 of cam disk 49 is tted over the projecting end 52 of the stud at theupper end of the intervening crank arm 54, the movement of the shoe will be first to the left, `then returning to its initial position, thence to the right followed by a return to to starting the machine, the operator has rocked the manual lever 5l to the right to fit the groove 49' of the cam disk 49 over the protruding end 52 of the stud at the upper end of the crank arm 54.

A pair of angularly related divergent arms 54h, 54o, extend downwardly from the hub of the crank lever 54, 54a.

VThe upper ends of links 51, 58 are pivoted to the respective free ends of the angular arms said links being slotted at their lower ends to mutually embrace a stud 59 located intermediate'the ends of, and projecting laterally from, a floating clutch control lever 60, 60a.

Under emergency conditions the stud 59 forms a pivot for the floating clutch control lever 60, 60a., as will be explained, but in the usual operations of the machine, the oating lever rocks on the pivotal connection 6| at its left hand end with the forwardly extending arm 62 of a manually operable emergency lever 62a, 62 pivoted at 63 on the head frame I3.

The emergency lever arm 62 and the floating lever 60, Bform, in eiect a toggle lever which,

at certain times during the operation ofthe inathe slide way and are tail or the pawi earner lever 66, 66a, which serves the same purpose as the hand emergency lever 62a.

The free end 60a of the floating lever 6I) extends beneath a tappet 61 fast on a clutch control rod 68 extending upwardly to control a clutch 34 on the countershaft 33, for connecting the main drive pulley39 with the driving Counter-shaft 33 to rotate said countershaft. y

A spring 68a, one end of which abuts against a guide lug 68D- on the head viranie I3, through which lug the clutch control rod 68 passes, and the other end of which spring presses against a collar 68e on the clutch rod 68, holds the clutch normally disconnected.

It will be noted that in the normal idle position of the machine, the crank arms 54, 54a have been brought by Whichever cam 49 o-r 50 Was last engaged therewith, into a substantially vertical position coinciding with the line M (Fig. 2) passing through the pivotal center 55 of' the crank lever 54, 54', which has resulted in positioning the divergent arms 54h, 54C with their outer ends in the same horizontal plane.

The cam 49 or 50, by bringing the crank lever 54, 54a to its vertical position and the divergent arms 54h, 54e to their intermediate position, Operated to relax the support afforded the floating lever 60, BDa'by the connection of the bridle links 51, 58 with the floating lever stud 59, Whereupon the clutch disabling spring 68a forced the clutch control rod 68 downwardly to disengage e the clutch members 34 and disconnect the constant drivepulley 39'and counter-shaft33.

Oscillating shaft drive and in addition, has fixed thereto a face cam 66 (Figs. lnand 2) having a cam grooveI 69' formed on one side face, which groove is engaged by a roll mounted on one arm of a bell crank lever- 10 pivoted at 10' on the head frame |3.

A link 1| pivotally connects theremainingarm of the bell crank lever 10 with a slide block 85 (Figs. 2a, 5 and 6) fitting and shiftable and upand down in a slide Way 86' pivoted near its upper end at 81 to the head irame"|3 Y The link 1I is pivotally connected at 84 to the slide block, and a connecting link83`securedat" one end to the same pivot 84, extendsto and' is pivotally connected at 82 with the tail of theA pawl carrier 13journaled on the extension of one of the bearing sleeves 18 in which the oscillator shaft 2| is journaled.

Obviously, the angular relationv of the connecting link 83 and the pawl carrier 13" varieswith the position of the slide way 86 in vrelation.

to the vertical indicated bythe dash line M. 'on Fig. 2. l

To enable the slideway to be rocked first to one side of the vertical and then to the opposite' side thereof, a radius link 56 pivotally connects the lower arm 54a ofv the cam-controlled crank lever 54, 54a, with the slide way 86 atk 91.

In the normal positions of the parts as shown in Fig. 2A, the crank lever arms 54, 54a bei-ng: in their vertical positions, wherein: they have enabled the spring-pressed clutch control rod 68 to disengage the clutch 34 between the normally idle countereshaft 33 andthe power pulley 39`,'it,-will be noted that the radius bar' 56 normally holds the oscillating slide way 86 in its vertical posi-jv tion and that the slide Way, in turn, through the connecting link. 83 between' the slide block: 85 ink 13, holdsthe pawl carrier 13 in verticalposition to which it has been returned by the pinions sequence of operations.

Spring-pressed centering arms 19 (Figs. 5 and 6), independently journaled at theirinner ends on the bearing 18 of the oscillatory shaft 2| adjacent the pawl. carrier assist in such return, the outer ends of'a the centering arms terminating in radially projecting' `aws 19'," which, when the pawl'carrier isin its normal vertical position, embrace a fixed stud 11 (see also Fig. 5a) projecting from the head frame I3, and also a stud 16 projecting laterally from the inner face of the double acting pawl 15.

In this position of the double-acting pawl,

The idle position of the machine, the clutch lever |32 (Figs. 1 and 3) maintains the clutch membersf43, 44 disengaged and the studv |24- (hereinafter referred to) Figs. 1 and 3, projecting from the large gear 46 will occupy substane tialIy the position shown. in Fig. l about 180 degrees distant from the shift lever |23 to operate the latter near the end of the second "l advance of the control shaft 41. f

Work retaining means At' the very beginningk of the first quarter revolution the peripheral cam groove 48' (Fig. l) of the cam disk 48 fast near the inner end of the control shaft 41, acts on a roll |34" projecting from an oiset finger onthe upper free end of a retaining lever |34 into the cam groove.

The Work retaining lever is of suitable thick-v ness and is pivotally secured at |33 to the head frame I3 at a point beneath the cam disk 48, the upper end of the retaining lever" being grooved transversely of its upper wider end at |43, which groove is laterally recessed, as at |42 to form a'pocket having alower wall formed on `divergent angles'.' Friction locking rollsv |31 are located within the pocket, onel on each side of the central high point towards' which the rolls are respectively spring-pressed', to normally engage and frictionally gripf a brake strip |38 seatedy in the groove and extending over the' rolls; whereby the brake strip |38 is snuglyl held against longitudinal movement between said rolls and the opposite wall of the groove- |43 in the retaining lever |34. y

One end of the brake stripv |38 is pivotally connected to the adjacent end of a pilot and spring terminal2 |381 the opposite end of the pilot and terminal being telescopically entered in the open end of a socket |41'. theV closed end of which is pivotally connected at |44 to the' rocking work support 3. A spring |48 anchored at' the inner' closed end of the socket, isl connected at its outer f centralV point between the friction gripping rollsV |31Il from which the tooth is normally held withdrawnby a spring |45 to free the' rolls for gripping action.

When the work-retaining cam 48 is in its normal idle position, the roll |34a of the retaining lever |34 has been shifted by the cam groove 48 at the end of its preceding operation, to the left to engage the laterally extending tail of the trip member |35 with a stationary stud |35 mounted in the head frame I3. Such engagement rocked the trip member counterclockwise (Fig. 1) to project its wedge-shaped tooth between the friction locking rolls |31, separating them so as to deprive them of their locking action on the brake strip |38 by forcing the rolls towards the wider ends of the recess |42.

Release of the friction clutching action of the rolls |31 on the brake strip |38 enabled the operator to rock the work holder.3 and work away from the edge rest, assisted, it may be, by gravity. A

The spring |40 serves as a flexible link between the work holder and the edge rest to enable yielding movement of the work support relatively to the edge rest during oscillation of the work to compensate for the irregular contour of the shoes, and for various sizes of shoes while maintaining snug contact between the shoe and the edge rest.

It will be recalled that-after rocking the work holder 3 and the shoe in operative relation to the edge rest, during which rocking the brake strip |38 slides idly along the groove |43 in the retaining arm, the operator, having engaged control cam 49, say, with the upwardly extending arm 54 of the crank lever 54,l 54a, depresses the pedal |28 (Fig. 3) to free the gear clutch 43,- 44 for operation.

Thereupon the pinion 45 is given a single complete rotation and drives the large gear 46 with its control shaft 41 and the cams 48, 49 and 50 through a quarter revolution.

The cam groove 48 of the work-retaining cam 48 operates early in the beginning of therst quarter revolution to rock the retaining lever |34 to the right (in Fig. l), thereby withdrawing the tail of the trip member |35 from the stud |36. The spring |45 thereupon retracts the wedge-shaped tooth of the `trip member from between the spring-pressed locking rolls |31 which immediately ride up their respectiveinclines to tightly grip the brake strip |38 and hold the latter and the work holder in position with the work in contact with the edge rest 31. The came groove 48 maintains the retaining lever |34 against rocking movement to the left until the close of the final quarter revolution of the cam 48, but'l the contour of the work as it is rotated relatively to the edge rest may force the pivoted work support outwardly against the tension of the spring |40. i

Meanwhile the control cam 49 (Figs. 1 and 2) associated `with the power control crank lever arm 54 has been gradually shifting the crank lever 54, 54a counter-clockwise from its normal vertical position, the divergent arms 54h, 54o moving with the crank lever in counter-clockwise direction.

,The depending arm 54a of the crank lever 54, 54a, on said counter-clockwise travel, thrusts the radius link 56 to the right to rock the slide wayv 86 to the right to the position indicated by the line I Fig. 2.

Because of the approximate concentricity of the pivotal connection 04 of the pawl carrier link 83 and slide block B5 with the pivot 81 of the slide way 86, the rightward adjustment of the slide way by the control lever armur54a only slightly shifts the lower end of the link 1| also connected with the slide block at 84, and the pawl carrier 13.

Such slight shifting of the pawl carrier may be sufficient to displace the pivot 14 (Figs. 5 and 6) necting the power pulley 39 with the counter shaft 33 is still disengaged, no movement is imparted to the power transmitting bell crank 10.

However, the divergent power clutch controlling arms 54b,54c, on their counterclockwise travel with the control crank lever 54, 54a, about the stud 55 as a center, operate, the arm 5419v to lower its slotted link 51 relatively to the stud 59 on the floating clutch control lever 60, 60a and the arm 54e to raise its slotted link 58, so

' that the lower wall of the slot in contact with the stud 59 will rock the floating clutch control leverl counterclockwise on its pivot 6| and press the free end 60a of such lever against the tappet 61 on the clutch control rod 68.

The slotted link 58, in its continued upward movement causes the clutch control lever arm 60a to lift the clutch control rod 6B against the tension of its restoring spring 68a and as the rst quarter revolution of the gear 46 and contiol shaft is completed, the clutch 34 connects the power drive pulley 39 with the counter-shaft 33 to rotate the power cam 69 and the remaining cams (not shown) controlling the actuation of the punching and tacking mechanisms operating on the shoe.

Just prior to the end of the first quarter of a revolution, the high point of the control cam 49, as shown in Fig. 2, has rocked the control lever 54, 54a to the position indicated by the line I corresponding to the position I of the slide way, where it is held during the following operation to maintain the slide wayA 86 in its inclined adjustment during the reciprocation down and up 0f theslide block 85.

The operator having removed his foot from the pedal starting lever |28, the springs |28c and |30() (Fig. 3) have restored the pedal lever and the intermediate lever |30 to their normal positions, the spring l30b in addition returning the starting clutch control lever |32 to position to disengage the clutch members 43, 44 at the end of one complete rotation of the pinion 45, as the large gear 46 completes ,its advance of a quarter revolution.

Therefore, the control shaft 41 and control cams 49 and 50 cease rotation together with vthe retaining cam disk 48.

The high point of cam 49 acting upon the control crank lever 54, 54a, maintains the slide way 86 at the extreme right hand limit of travel1 First quarter rotation .It Will be recalled that the active control cam 49 or 50 (Fig. 2) on the first quarter rotation of control shaft 41, operated the floating clutch control lever 60, 60a, to connect the power drive pulley 39 with the counter shaft 33 through the clutch 34, this connection being timed to occur substantially as the active cam is completing its rst quarter revolution, and as its power connection is disengaged.

Thereupon, the drive pulley 39 starts rotation of the counter shaft 33 and the drive cam 69 (Fig. 2) together with the cams (not shown) controlling the punching and tacking mechanisms. Because of the four to one ratio between the large gear 46 and the pinion 45, the pulley 4I of which is about the size of the drive pulley 40 fast with maindrive pulley 39, it is obviousfthat the shaft 33, when driven by the pulley' 39, will make a complete rotation in approximately the same time that the controll shaft 41 makes. av quarter -of a revolution.

' Normally, the roll on the shorter arm of the bell crank (Fig. 2) lies at the loW point ofthe drive cam 59, as shown in Fig. 2a, and the slide block 85 lies at the upper end of the slide way 86 adjacent to or partially over-lapping the pivotal center 81 of the slide way (Fig. 5). ,Also the pawl carrier 13 is in its substantially vertical position. Due to the previous shift of the slide way to its inclined position during the rst quarter. revolution of the controlshaft 41, a slight movement may be imparted to the pawl carrier through its link connection with the slide block 85, sufcient to engage the proper tooth ofthe double acting pawl 15 with the friction disk 12.

Therefore, the drive cam 69 as it makes a come plete rotation, imparts a quick oscillation to the bell crank 10 which movementis transmitted through the connecting rod 1 I, slide block 85 and link 83 to the pawl carrier 13. The block 85 sliding smoothly down theinclined slide way 8B, first draws the link 83 to the right (Fig. 6), to impart a clockwise rotation to the, pawl carrier 13, and on its return, forces the pawl carrier back to a substantially vertical position.

If the pawl is not already in frictional engagement with the friction disk 12 at the outset of the clockwise advance of the pawl carrier, the stud 16 of the do-uble acting friction pawl 15will contact with the jaw 19 ofthe left hand centering arm 19 which causes the pawl to rock until its left hand tooth grips the friction disk 12 to impart a partial'rotation to the `friction disk and the oscillatory shaft 2 I, which movement is transy mitted through the bevel gears 5 (Fig. l) to the block 85 as it is forced downwardly inthe slide way 86, and hence pressure is communicated to the slide way tending to restore it to a'vertical position, but such pressure is opposed by the radius link 5B between the slide way 86 andthe crank lever 54, 54a. i Rotation of the oscillatory shaft 2|, which rotates the work support,' is also transmitted through the gear |05 (Fig. 1) fast on the opposite end of the oscillatory shaft, to the gear |06 fast on the corresponding. end of the return shaft |01 journaled inthe head frame parallel with and beneath the oscillatory shaft.

The return shaft |01-supports a pair of opposed collars |08ffast on the shaft. Oppositely coiled springs |I0, II| on the respective collars are held in tension by contact of the outer end of each spring with a traveling pin |09 project ing laterally from a radial arm on each of `said collars |08, the opposite endv Illia, IIIa of each spring |I0, `|II contacting the respectively op posite sides of an anchory pin' II3 supported intermediate its ends on a post |I2 projectingupwardly between the two opposed springs I I0, I I I.

Rotation of the oscillatory shaft v2| inv either directionby the pawl carrier 13, pawl 15 and friction .disk 12 will'operate through the gears |05, |06 to rotatel the return shaft |01 and further tension one or lthe other of the already tensioned return springs |I0, III by movement of its traveling pin |00 in a direction to wind the corresponding spring more tightly; Obviously, one spring or the other will be coiled more tightly depending upon the direction in which the return shaftl |01 is rotated by the pawl carrier 13 and pawl 15, that spring not being wound being slightly relaxed or uncoiled due to movement of its traveling pin |09 towards the anchoredy end of the spring.

As the driving cam 69 (Figs. 1 and 2) through the bell crank 10 and link 1| retracts vthe slide block 85 upwardly along the inclined slide Way work holder or support 3 to shift the toe portion of the shoe to the right While still pressed against the edge rest 31, so as to feed the shoe relatively to the working tools for a limited distance along l the left hand side of the toe (Fig. 9a), during the operation of the punching and tacking mech-l anisms, simultaneously operated by the counter shaft 33.

The stud 1B of the pawl 15, as the pawl carrier proceeds on its advance stroke, forces the left hand centering arm 19 leftward (Fig. 6) tensioning the spring 80 connectingthe two centering armsthe right hand centering arm being held in normal .position by contact of its jaw 19', with the stationary stud 11. y

Obviously, .the resistance opposed to the advanceoscillation of the shoe orworkand inertia of ltheparts is overcome by the power/driven ,slide carrier.

86, the pawl carrier 13 is rocked counter-clockwise back to its normal vertical position, at the beginning of which movement the left hand tooth of the double-acting pawl 15 disengages from the friction disk 12. L. l

Such return movement of the vpawl carrier is assisted by the centering arm 19`unde1 the ten# sion of the spring 80, which acts to insure an accurate-centering of the pawl carrierand its pawl in their normal verticall positions.

Upon release of thegripping action of the pawl 15 on the friction disk 12, the oscillatory shaft 2| controlling the rotation of the work support would ordinarily be free to be returned with the work to its normal position Aunder the stored tension of the spring II0 or III, at the Very beginning of the return movement Aof However, the main drive shaft 33 is still operating to restore thev slide block 86 andfthe pawl carrier to'their .starting positions, andthe return-of the work before the tools Vhave ceased to operate should be prevented.

Tothis end, that side of the friction disk 12 facing the. adjacent side wall of the head frame I3, is circularly chambered (see Fig. 7a) to ace. commodate a circular brake .member 90 (Figs. '7-8) j ournaled on the projecting shouldered end of the bushing 18 fast in'the head frameand extending into the chambered portion of the friction disk 12.

l Opposed arcuate grooves formed near thejpe-r riphery of the circular brake memberl90' extend from the respective opposite ends of ajperipherally formed recess |49 inthe brake member.

Springs 96 seated in the respective opposed arcuate grooves press against the adjacent ends of arcuate followers 95 to maintain the opposed ends of such followers in contact with friction rolls 92, 93 located on respectively opposite sides of a stationary separator 94 projecting from the head frame |3 centrally -into the peripheral recess |49, opposite a pair of divergently inclined braking faces' 92a, 93a, locatedcentrally, and forming a part of the inner wall, of the'recess |49, the rolls 92, 93 adapted to bind between lone or the other braking face and the periphery of the chamber in the friction disk 12, depending upon the direction in which the brake member 99 is rocked, to lock the friction disk, its oscillating shaft 2|, 'the work holder 3 andthe work against return at this time to their normal starting positions.

A link 89 pivoted at 90 to the braking member 90, connects the member with the adjustable slide way 86 at 88.

In the normal vertical position of the slide way 86 (Fig. '1), the link connection with the brake member 90 maintains the braking faces 92a, 93a centered beneath the separator 94 and the spring-pressed followers 95 maintain their respective rolls 92, 93 against the respective opposite edges of the separator 94, the rolls resting on the lower ends of the braking faces 92a, 93a, so that no braking action can occur, and the friction disk 12 can freely rotate in either direction.

During the first quarter rotation of the active control cam 49 or 50 which rocks the control crank lever 54, 54a, to swing the slide way 86 to one side or the other from the vertical position, the slide way, through its link connection 89,

rocks the brake member 90 to the position shown i in Fig. 8, or to the exact reverse of such position, depending upon which control cam is effectively connected with the slide way.

Rotation of the brake member 90 clockwise,

as in Fig. 8, for instance, shifts the divergent braking faces 92a, 93a, awayfrom the left hand roll 92 which is held against movement in the same direction by the separator 94, and its spring 96 is merely compressed. Therefore, the left hand roll 92 resting in the deeper or Wider portion of the recess, can exercise no braking function.

But as the brake member 90 rocked clockwise, it shifted its right hand inclined braking face 93a farther beneath the co-acting friction roll 93, and the tendency of the roll to accompany the brake member 90 being retarded or resisted by its associated spring-pressed follower 95, the friction roll 93 is brought to a position where it can bind between the braking face 93a and the inner periphery of the friction disk 12 as soon as a reverse motion of the friction disk is attempted.

The rotation of the friction disk 12 by the pawl `carrier 13 and pawl 15 to turn the work rotating shaft 2| in a direction to advancethe work from its normal starting position, turns the friction disk in the same direction in which the braking member 90 was turned so that no binding action of the friction rolls 92, 93 can occur at this time.

But when, upon the release of the friction disk 12 by the double-acting pawl 15 at the very beginning of the return of the pawl carrier 13 towards its starting position, tensioned return spring or starts to rotate its return shaft |01 and, through gears |09,l |05, the oscillatory shaft 2| and friction disk 12 in the opposite direction, the friction roll 93 (in the present instance) Fig. 8, will immediately grip the frictiondisk 12 locking it, together with the oscillatory shaft 2| and the work against restoration to their starting positions.

This locking action is rendered possible because the high point of the control cam 49 (say) Fig. 2, is still maintaining the slide way 86 and hence the braking member 9|) stationary in their rightward adjusted positions.

This restraining action of the friction' rolls 92 or 93 binding between the friction disk 12 and braking member 90 will be maintained until the end of the second quarter rotation of the control shaft 41.

Second quarter rotation Clutch tripping studs ||4, ||5 (Figs. l and 3) adjustably mounted in spaced relation on the outer face of the gear |06 project laterally into the vertical plane of the upright arm ||8a of a multiple-armed lever |18 journaled on an axleA ||1 projecting from the head frame |3 in vertical alinement with and beneath the work-return shaft |01.

Divergent arms H81), ||8c depend at substantial right angles to each other from the hub of the multiple-armed lever ||8 of which they constitute a part. Links |25, |26 individual to the respective depending arms |1811, |8c are pivoted to the outer ends of said arms, the respective links being slotted at their lower ends to embrace the opposite ends of a pin |21 passing through the rear arm of the pedal lever |28. The lpedal restoring spring |28c acting through the pedal lever |28 and pin |21 normally centers the multiple armed lever ||8.

Consideration of Figs. l and 3 will indicate thata rocking of the upwardly extending arm ||8a in either direction is effective to rock the depending arms HBD, ||8c to thrust one slotted link downwardly and pull the remaining link upwardly, thereby rocking the pedal lever |28 clockwise to cause the clutch control lever |32 to release the clutch members 43, 44 for operation, resulting in another complete rotation of the pinion d5 and another quarter of a rotation of the control shaft 41.

It will be recalled that immediately subsequent to the completion of the first quarter rotation of the control shaft 41 and as a result thereof, the clutch 34 connected the counter shaft 33 with the main power pulley 39 which imparted a partial rotation to the work oscillating shaft 2|, and that said work oscillating shaft, in turn rotated the l restoring shaft |01 through the gears |05, |06, after which, continued rotation of the cam 69 in making one complete revolution returned the slide block and pawl carrier 13 to their normal positions.

The pawl carrier 13 at the end of its advance stroke has imparted a rotation of such extent to the oscillatory shaft 2| and the gears |05, |06 as to cause the stud H4 on the gear |06 to collide with and rock the arm |8a of the multiple armed lever ||8 in clockwise direction. The multiplearmed lever through link |25 rocks the pedal lever |23 clockwise, tripping the control shaft clutch 43, 44 for operation.

Therefore, as the drive cam 69 is completing 'its single cycle of rotation, and restoring the slide block 85 and pawl carrier 13 to their idle positions, which occurs with great rapidity, the pinion 45 is starting the rotation of the large gear 4B to impart the second,quar-terrevolution to the control shaft 41.

The cam groove 48 of the v vork-restrainingk cam 48 continues to hold the work against the edge rest throughout such second quarter rotation, but the groove 4;!3` of the control cam 49, shifts the control crank lever 54, 54a to the vertical or median position indicated in Fig. 2 by the i line M and 'through the radius llink 56,A swings the slide way 86 back to its vertical median posi tion also indicated by theline M in Fig. 2.

The slide way, in turn,through link 489 (Fig. .8) returns the braking drum 90 counterclockwise (in Fig. 8) to its normal position, and as ksoon as the lower surface of the inclined braking face 93a has released .the friction roll 93, the #tensioned return spring reversely rotates the return shaft v|l1 and through gears |06, |05 restores the oscillatory shaft 2|, the work support and the .work

to normal starting position.

' The projecting stud I|.4 (Fig. 3) on 'the gear wheel |06 has been .holding the multiple-armed lever IIB in its counter-clockwise position, and' hence the pedal lever |28 is held in actuated position, notwithstanding the return of the intermediateclutch lever |30 and clutch .control lever |32 to their normal positions. But upon the reverse rotation of the restoring shaft |01 by the tensioned spring I|0, the gear stud I4 releases the multiple armed lever v||8 and pedal lever |28 At the end of this second quarter rotation the shoe I is again in contact with the edge ple-armed lever ||8 in a direction transverse to its pivotal motioni The lever arm ||9 projects lupwardly behind '.(to the left in Fig. 1) the gear .wheel |06 fast on the return shaft |01, where it is shiftable into `and out of the path of a stud I|.6\proJ` ecting from the rear face ofthe gear |06.

Aspring 1| 2.0.normally holds the upperfree'end of the lever arm IIS out of the path of the stud ||6 and in contact with the broadened depending arm of vthe .bell crank lever |2I.

' The mamme-armed lever Ila, it will be re-" called, is connected with the starting pedal lever |28 in, such manner `that rotation of themultiplearmed lever .H3 .in either direction will operate the pedal lever '|28 to release the control shaft clutchmembers 43, 44 fo i,ac'tioi1.y It Awill vbe recalled also that the first quarter rotation of the control shaft 41 resulted in tripping the vcountershaft driving clutch 34, to impart the rst advance of the oscillatory Work traversing shaft 2| which, inturn, resulted in Vautomatically 'tripping the clutch 43, 44 to ven- Vable a second quarterrotation of the control shaft 41 which, in turn, resulted in disconnecting the counter-.Shaft clutch 34. Meanwhile during apart of the second quarter rotation of the'control vs ljlaft .41, the oscillatory work traversing shaft rest 31, the- clutches 34 and 43, 44 are' disengaged and the slide way 86 andthe pawl carrier 13 4are in their vertical positions. Clutch 43, 44 was disengaged becauseof the presence of the,

clutch control lever |32 in the path of the clutch as the latter completes its single revolution.

Third quarter rotation I The large gear 46. (Figsrl and 3) which i's advanced always in one direction by quarter revolutions, carries on its inner face a projecting stud |24 which, in the normalhome position of the gear, lies vertically above the shaft 41` of the gear. At the endrof the rst quarter revolution of the shaft 41 and gear 46, the stud ,has advanced to the position shown in Fig.' 3,-where it projects above but isstill nearly7 one step apart 'l from a lever |23 pivoted at |46 to the head frame I3. This lever |23 'is connected by a rod |22 with theV rearwardly extending arm of a bell crank'lever |2I pivoted at |41 to the head frame.`

The depending arm` of the bell crank |2| is Widened to afford a surface of suilcient area for engagement by thefree end of a forked lever ||9 transversely embracing the hub of the multiple-armed starting clutch tripping lever ||8 to which it is pivoted at |48. AIt will be noted that the lever'arm 9 is rockablegon itspivot v|48in one direction and also can turn with the multi-.

of the control shaft 41, the tip of the toe of 45.

onthe Vgear, |06 has advanced from .shown in Fig.. l. to .that shown in Fig. 3.

2| and its connected gears |65,l |06 remained in the positions to which they wereadvanced, due

tothe restraining action of the brake'mechanism 0.10, 9 3 on the friction disk 12.

Then, Vneartlie vend of the second quarter rota- .tionof the controlshaft 41, thev brake vis released to'enable `the tensioned spring Il 0 to restore theoscillatory work traversing Shaft .2| and work holder 3 .to their starting positions, by reversely rotating the gears |06,v I 05.

fWhen the machine is at rest in its normal position, the ,projecting stud 'I I6 on the inner `faceof the gear |06 lies opposite the free end of .the pivotedlever `arrn |.I9 .which', at that time,

is held by its spring I20` in contact with thefbroadeneddepending arm ofthe idlebell crank 2 and outfof thepathororbitof the'stud |6, as'sliown. Ain-Eig. 1.

However, `asa result of .advancing the oscil- -latory .work traversing shaft 2| and thegears |05, ,|06`,. on the r'stadvance stroke of the pavvl carrier .1 3,.immediately,followingthe rst quar-y ter .rotation of lthe control shaft 41, the stud .I I6 its position This .advance, as heretofore explained,occurs prior .to .thefsecond .quarter or .rotation ofthe `,controlshaft4,1, and .thebrakemechanism 90, v|l3-retains the gear |06 and its stud .I |16- inl such advanced `position-duringa part of the ensuing secondduarter 4rotation of the control shaft 41. vl'-rio rto thecompleterelease of the brake mech- - vanism 80, 93 .and the .operation of the tensioned `spring motor |I0to restore the oscillatory shaft 2 I ,which occurs lat .the end. off such second. quar- .ter-rotation` ofthe control shaft41, thestud |24 onthe large gear 46y which advanced: to-ft'heposition shown in Figr 3 on the precedingfrstlquare .ter rotation of said,shaftfadvanceswith thelarge gear 46 during such. second ,quarterloperatmn to shift the leverarmllf into V,the'return path Tlie,control.,shaft.4f1 with-itslgeard comes to restatf the endof thelsecondduarter rotation of the con-trolshaft (-due .to the completion ofi rotaing and punching mechanisms,

rocks the pedal lever clockwise and trips the control shaft drive clutch 43, 44 for operation in the same manner as heretofore explained, the stud l I6, as it returns to its normal position, holding the multiple-armed lever ||8` in its rocked position, although the pedal lever |28 as usual, after tripping the clutch 43, 44, escapes past the intermediatelever |30, which immediately restores to *normal with the clutch'trippinglever |32.

The pinion 45 makes its third complete revolution upon the tripping of theclutch 43, 44 to advance the control shaft 41 through its third quarter of a revolution.

One of the first results is that the stud |24 which initiated the clutch tripping operation, escapes past the lever |23, which'together with the .pedal lever |28 return tonormal under the influence of pedal lever spring |28c, thus freeing the lever arm ||9 for return to its normal idle position by the spring |20.

The control cam 49 turns a quarter revolution to present its low point to the roll 52 at the upper end of the crank lever 54, 54a which results in swinging the crank lever from the vertical Y position last occupied to the inclined position indicated by the line II (Fig. 2) and similarly swinging the slide way 86 from its vertical posi- ,tion to the position indicated by the line II adjacent the slide way in Fig. 2.

These inclined positions of the crank lever and slide Way are just ,the reverse of those occupied by these elements as a result of the first quarter rotation of the control shaft 41.

The crank lever 54, 54a, as it is rocked clockwise by the control cam 49, rocks the divergent levers 54h, 54o, in like direction, to cause the link 51 to swing the floating clutch control lever 60, 50a counter-clockwise, lifting the clutch rod 68 to render clutch 34 effective as the third quarter rotation of the control shaft 41 is completed.

The vdrive cam 69 upon its connection with the power pulley 39 through clutch 34 and countershaft 33, actuates the bell crank 10 and link I1| to impart a rapid -reciprocation down and back to the slide block 85 traversing the slide way, and through link 83, rocks the pawl carrier 13 and its pawl 15 counter-clockwise and then back to their normal vertical or substantially vertical positions.

Because this movement of the pawl carrier due to the reversed position of the slide -way 86 is just the opposite of the movement of the pawl carrier during the iirst quarter rotation, the friction disk 12 imparts a movement to the oscillatory shaft 2| and the Work support 3 in a direction to present the right side of the toe of the shoe to the tack- Also the oscillatory shaft through gears and Hl'a` transmits a reverse rotation to the return 'shaft |01 to tension motor spring Adjustment of the slide way 86 clockwise to its II position during the third quarter rotation of the control shaft 41, conditioned the restraining brake mechanism 90, 92 for operation, the brake 'member 90 having been rockedl counter-clockwise through its rod connection 89 with the slide way so that the formerly effective friction roll 93 is rendered ineffective and the opposite friction roll 92 rendered effective.

Therefore, the' motor spring is prevented from restoring the work support and work to their initial positions at this time.

Fourth, quarter rotation At the end of the third quarter rotation of the control shaft 41., the stud |24 (Figs. 1 and 3) on the inner face of the large gear 46 was brought to its nine oclock position and near the end of the subsequent advance throw of the pawl carrier 13, in counter-clockwise direction, a stud l5 adjustable on and projecting from the outer face of the gear |06 fast on the return shaft |01,.col lides with the arm ||8a of the multiple-armed lever H8 to operate the pedal lever |28 and release the control shaft clutch 43, 44 for operation.

Thereupon, and while the oscillatory shaft 2|, its work support 3 and the work is still maintained by the braking mechanism in their advanced positions, the control shaft clutch 43, 44 starts to drive the control shaft 41 through the final or fourth quarter. of a complete revolution.

As a result, the control cam 49, the low point of which has been holding the crank lever 54, 54a and the slide way 8G in their clockwise positions' as indicated by the lines II in Fig. 2, starts to return these elements to their vertical positions M, the angular arms 54h, 54e, turning counterclockwise with the crank lever, to enable the slotted link 51 at this time maintaining the floating clutch control lever 60, 60a in its effective position, to descend.

Thereupon, the spring 68a, of the clutch control rod |58 forces the rod downward together with the oating lever 00, 60a, to disable the counter-shaft driving clutch 34 and discontinue the operation of the power cam 69, slide block 85, pawl carrier 13, friction disk 12 and oscillatory shaft 2| with its connections.

As the control shaft clutch 43, 44 is timed to start to operate prior to the disengagement of the countershaft clutch 34, the drive cam 69 is enabled to complete its revolution, the slide block 85 is brought up to its normal position, and the pawl carrier 13 returned to a substantially vertical position as the countershaft clutch comes to rest. I

Following these operations, the continued movement of^the crank lever 54, 54a and slide way 86 clockwise towards the vertical turns the brake drum 90 clockwise a suicient distance to relieve the braking action of the roll 02 on the friction disk '52,' ywhereupon the tensioned spring |l| restores the return shaft |01 and through gears |00, |05, restores the oscillatory shaft 2|, the work holder 3 and the work to their initial startingpositions. At this time the appropriate spring-pressed centering arm 19 acts to correctly yposition the pawl carrier 13 and paWl 15.

At about the same time, the work support restraining cam 48 (Fig. l) will shift the restraining lever |34 counter-clockwise, relaxing the tenrest 31, to remove the nished work andsubywork to present the right hand side of the rtoe of the shoe to the tools, rotated the gear |06 with its studs I I4, II and H 6 in counter-clockwise direction when tensioning the motor spring I I I.

This movement of the gear |06 was without consequence so far as the tripping studs I I4, II5

were concerned, but the stud I I6 was brought to the left of the pivote-d clutch-tripping lever arm II9 (Fi-gs. 1 and 3).` However, the condi'- -tioning stud |24 which was left `in a position to the left of the control shaft 41 at the end vof the third quarter rotation of said shaft, is brought Ito its normal `position vertically above the shaft 41 at the end of the fourth quarter rotation and hence does not operate the lever 423 to vshift the pivoted lever arm I I9 into the returnA path of the tripping stud IE6. f

'Consequently,as the motor spring YI I I returns the gear IDB to its normal' position, the stud I I6 merely returns to its normal position directly in front of the pivoted lever arm without colliding therewith.

Hence, as neither of the'clutches 34 01143, 144 is tripped, the machine comes to rest. 1

From the foregoing description,'it is yclear that the work is intermittently'presented to the tools at regular intervals and "for regular'periods of time.v i f During the operation of the machine, if any reason should develop justifying an immediate stoppage of operation, as failureLof the toolsv through breakage or lack of material, the operator may manually rock theV emergency lever 62a (Fig. 2) or depress the treadle 66a, either of which will ileX the levers 62, Ell, ayattheir pivotal connection 6I in the manner of, a toggle lever to immediately free the clutch control rod 68 to the action of its spring 68a, which at once disengages the counter vshaft driving 'clutch 34,

Idepriving the drive cam '69 of power to yactuate' the pawl carrier 13, and the machine Comes to rest, with its parts in their partially, operated positions. l

In' this operation, they floating lever (il), ,60a pivots on the stud 59 as a fulcrum, as shownin dotted lines in Fig. 2.-

' After repairing the fault, return of the manual lever l62a. to its normal position willre-engage the clutch'34 and the machine will complete the interrupted operation.

support '3 and'work by the oscillating. shaft; 2l

may be varied or adjusted to a limited extentacrcording to the size of the shoe loperated upon; or

to the stretch of shoe desired tobe tacked. v

To this end the pivotal connection 91 `(Fig, 2)

, of the radius link 56 tothe swinging slide way 86 may be arranged for `adjustment lengthwise of the rear face ofthe sliderway, by meansof an adjusting lever IUII pivoted at IDI, a suspension link 98 being pivotally connected at S9 -to the free end of the adjusting lever andsupporting the pivotal connection 91 at its lower vend. By swinging the adjusting Alever I in oney direction or .the other, from the position shown in Fig. 2, to one or another of the recesses I'5Il while the machine .is at lrest with the slide way in its vertical position', the connection `91 is moved relatively to the pivotal support 81 of the slide way to enable the radius rod under control of the cam 49 or 50, to position the slide Way 86 to one side or the other of the vertical at a greater or lesser angle, it being remembered that the cam groove contours 49', lEll are'xed'and i always impart the same` degree of Athrow to the l slide Way. f The adjustment of the extent of inclination which may be assumed by the slide way 805v also results in varying the distances or spaces between the fasteningsapplied vto the shoe, as indicated inFigsQa to 9c. O

What is claimed is:

1. vIn a shoe tacking machine, the combina'- tion with a work support; an edge rest against which the work is held; and a constant power drive; of an oscillatory'shaft connected with the work support; a countershaft; a normally disconnected clutch between the power drive and v thecountershaft; means operable by the counnormal intermediate position subsequent to each advance of the oscillatory shaft.

2. A shoe tacking machine, including a work support for the Work; an edge rest against which the work is pressed; a power drive; an oscillatory shaft connected With'the work support'to rotate the latter; normally idle means operable by 'the power drive to positively rook the work support and work first in one direction and later along one side of the toe of the shoe can be performed intermittently instead of by a continuous succession of operations, if desired.

Or by holding the emergency lever effective and manipulating thevpedal lever I23,the shoe may be returned to itsy initial starting position Vand the work holder 3 released to permit rea partial operation ofl `at any other time vthan when the countershaft 33 is beingpower driven. I

The vcam 69 operates the means for properly presenting the work to the tools, and the cams 449, 5D condition such `means for operation in one direction 'or the other. i

rllhe extent'o'f oscillationlimparted to 4thework in the opposite direction from a normal inter` mediate or starting position; means to detain the work support and work in either of itsv advanced positions; means to release said detaining means;

and means to restore the work support and work k to its normal intermediate or starting position after each said advance, upon the release ofsaid detaining means. i y y 3. A shoe tacking machine, including a rotatable work support; an edge rest against which the work on the work support is'pressed during rotation of the supporta power drive; normally idle means operable by the power drive to positively rotate the work support and work, first, in one direction and llater in the opposite direction from a normal intermediate or starting position in each instance; a" normally disconnected clutch between the power drive and -the work-support rotating means; means advancing through a complete revolution by successive steps, to control the alternate connection and disconnection of the clutch according to the step to which the means has been advanced; an automatically disengaged coupling between the power drive and said clutch control means; means controlled by said work support rotating means to render the coupling effective; and means to restore the work support and work to their normal intermediate or starting positions subsequent to each advance of the support.

4. A shoe tacking machine, including a rotat able work support; an edge rest against which the work on the work support is pressed during rotation of the support; a power drive; normally idle means operable by the power drive to positively rotate the work support and work, iirst, in one direction and later in the opposite direction from a normal intermediate or startingposition in each instance; a normally disconnected clutch between the power drive and the worksupport rotating means; means advancing through a complete revolution by successive steps, to control the alternate connection and disconnection of the clutch according to the step to which the means has been advanced; an automatically disengaged coupling between the power drive and said clutch control means-means controlled by said work support rotating means to render the coupling effective; and opposed motor spring mechanism operable by said work support rocking means when advancing the work support, to restore the work support and work to their normal intermediate or starting positions subsequent to each advance of the support.

5. A shoe tacking machine including a rotatable work support; an edge rest against which the work on the work support is pressed during rotation of the support; a power drive; normally idle means operable by the power drive to positively rock the work support and work, rst, in one direction and later in the opposite direction from a normal idle intermediate or starting position in each instance; a normally disconnected clutch between the power drive and the work support rocking means; means rotated by successive steps to complete a revolution to control the alternate connection and disconnection of the power drive andy the work support rocking means; a drive pinion; an automatically disengageable one-revolutioncoupling between the power drive and the drive pinion; a driven gear connected with the intermittently rotated control means, the gear having a ratio lto the pinion equalvto the number of steps required to complete a revolution of the control means; means controlled by said work-support rocking means to render the one revolution coupling effective; and means to restore the work support and work to their normal intermediate or starting position's subsequent to each advance of the support,

6. A shoe tacking machine, including a rotatable work support; an edge rest against which the work on the work support is pressed during rotation of the support; a power drive; normally idle means operable by the power drive to positively rotate the work support and work, firstl in one direction and later in the opposite direction from a normal intermediate or starting position in each instance; a normally disconnected clutch between the power drive and the worksupport rotating means; means advancing through a complete revolution by successive steps, to control the alternate connection and disconnection of the clutch according to the step to which the means has been advanced; an automatically disengaged coupling between the power drive and said clutch control means; a tripping member rockable with said work support by said power drive; coupling tripping means connected with said coupling; means on the tripping member operable upon the coupling tripping means in either direction of travel of the work-support; and means to restore the work-support and work to their normal intermediate or starting positions subsequent to each advance of the support.

7. A shoe tacking machine, including a rotatable work support; an edge rest against which the Work on the work support is pressed during rotation of the support; a power drive; normally idle means operable by the power drive to positively rotate the work support and work, rst; ine one direction and later in the opposite direction from a normal intermediate or starting position in each instance; a normally disconnected clutch between the `power drive andthe worksupport rotating means; means advancing through a complete revolution by successive steps, to control the alternate connection and disconnection of the clutch according to the step to which the means has been advanced; an automatically disengaged coupling between the power drive and said clutch control means; means to automatically connect theV coupling, including a clutch closing lever; a double acting trip lever linked to the clutch closing lever to operate the latter upon movement of the trip lever in either direction; means operable with said work support in both directions of rotation of the latter to actuate the double acting lever and render the coupling operative; and means to restore the work support and work to their normal intermediate or starting positions subsequent to each advance of the support.

8. A shoe tacking machine, including a rotatable work support; an edge rest against which the work on the work support is pressed during rotation of the support; a power drive; normally idle means operable by the power drive to positively rotate the Work support and work, rst, in one direction and later in the opposite direction from a normal intermediate or starting position in each instance; a normally disconnected clutch between the power drive and the work-support rotating means; means advancing through a complete revolution by successive steps, to control the alternate connection and disconnection of the clutch according to the step to which the means has been advanced; an automatically disengaged coupling between the power drive and said clutch control means; means to automat-y ically connect the coupling, including a clutch control lever; a double-acting trip lever linked to the clutch control lever to operate the latter upon movement of the trip lever in either direction; means operable with said work support in both directions of rotation of the latter to actuate the double acting trip lever and render the coupling operative; a normally idle lever arm shiftably connected with the trip lever; means actuated by the step-advanced means to shift said lever arm into effective position relatively to the actuating means for the double-acting trip lever for operation by said trip lever; and means to restore the work support and work to their normal intermediate or starting positions subsequent to each advance of the support, said last-named means Voperating the actuating means for the double acting trip lever toeiect an operation of. thetrip lever through the shiftable lever arm.

9. A shoe tacking machine, including a rotatby successive steps in completing a revolution, to

control the alternate connection and disconnection of the clutch according to the position to which the means has been advanced, including a pair of complementary cams and a clutch control lever operable by either cam; means to select the particular cam which shall control thev clutch control lever; means controlled by either cam to reverse the direction of` rotation of the work support; an automatically disengaged coupling between the power drive and the complementary cams; means controlled by the work support rotating means to render the coupling eifective; and means to restore the Work support and work to their normal intermediate or start.

ing positions subsequent to each advance ofthe support. 1

10. A shoe tacking machine including a rotatable worksupport; an edge rest against which the work on the work `support is pressed during rotation of the work support; a power drive; means operable by the power drive to positively rotate the work support and work, rst, in one j direction and later in the opposite direction from a normal intermediate or starting position in each instance, including a counter-shaft; a cam on the counter-shaft; a normally disconnected clutch between the power drive and #counter-shaft; areciprocatory member driven by the cam; means to intermittently connect the reciprocatory member and the work support; means to adjust the path of travel of the reciprocatory member to one side or the other of the vertical position to reverse the direction of rotation of the work support; `means to control the connection and disconnection oi said clutch; and means to restore the work support and work to their normal intermediate or starting positionsr subsequent to each `advance of the support and at such times as the connection between the reciprocatorymember and the work support is intermittedjy 11. A shoe tacking machine including a rotatable work support; an edge rest against which the work on the work support 'is pressed during rotation of the support; a'power drive; means operable by the powerdrive to positively rotate the work support and work, rst, -in one direction and later in the opposite direction from a normal intermediate or starting position in each instance, including a reciprocatory member; an adjustable guide means for said reciprocating member; means to variously adjust the angular position of the guide member relatively to the vertical position, including a cam; a lever controlled thereby; a radius link connecting the lever with the adjustable guide means; means'to vary the point of connection of the link and the guide means;means to' impart a step by step rotation in one direction to the cam to variously rock the lever, including a normally disconnected coupling between the power drive and the cam;

means also controlled by said cam to engage and ldisengage the clutch; and `means to restore the work support and work-to their normal intervwork on the support is pressed diring rotation of the support; a power drive; means operableA by the power drive to positivelyl rotate the work support and work, first, in one direction and later in the opposite direction from. anormal intermediate or starting position in each instance, including a reciprocatory member; an oscillatory shaft connected with the work support; a disk fast on said shaft; a normally'vertical rocking pawl carrier rotatable about said s haft,v a doubleacting pawl mounted on the carrier and effective to turn said disk, the shaft and the work support in either direction; means to transmit power from the rcciprocatory member to, the pawl carrier; means to rcontrol the path of reciprocation ofthe reciprocatory member to rock the pawlA carrier in either direction from its normal position offrest to reverse the direction of rotation of the Work support; a normally idle clutch between the power drive and the` work support rotating means;

means to engageand disengage said clutch to effect intermittent advances of the work support from said normal or starting position; and means to restore the work support and work to` their normalv intermediate positions at sometime during the periods of disconnection-of the clutch.

13. A shoe tacking machineincluding a rotatable vvork support; an edge rest against which the work on the support is pressed during rotation of the support; a power drive; means operable byv the power drive to positively rotate the work support and work, first in one direction and later in the opposite direction from. a normal intermediate or starting position in each instance; means to restore the work support and work after their advance in either of said directions by the power drive; a clutch betweenthe power drive and the work support rotating mechanism; control means to intermittently open and close the clutch; and i normally idle'means operable byr said control means to prevent restoration of the worktsupport and work to their normal positions. j

l14. A shoe tacking machine including arotatable work support; an edge rest against which the work on the work support is. held during rotation of the support; a power drive; means operable by the power drive -to positively and intermittently rotate the Work support and work in one direction and then in the opposite direction .from the normal intermediate orstarting position of the Work support;,means to control the direction in which the lWork support shall rst rotate ;l a clutch between the power drive and the work l support rotating means; clutch engaging and disltion .until the means controlling the direction of rotation is restored to its normal idle position.

l5. A shoe tacking machine including a rotatable work support; an edge rest against which the Work on the work support is held during rotation of the support; apower drive; means operable by the power drive to positively rotate the work support and work, rst in one direction and later in the opposite direction from the normal intermediate or starting position of the work support; a clutch between the power drive and the work support rotating means; intermittently operated means to render the clutch effective or ineffective alternately; means to control the direction of rotation of the work support from its normal intermediate or starting position; and spring motormeans tensioned by the work support rotating means when rotating the support in either direction, to restore the work support and work to their normal starting positions after every advance of said work support and work from its normal starting position and during the time said clutch is ineiective.

16. A shoe tacking machine, including a rotatable work support; an edge rest against which the work on the work support is held during rotation of the support; a power drive; means operable by the power drive to rotate the work support and work, first in one direction, and then after an l interval, in the opposite direction from the normal intermediate or starting position of the work support in each instance; a clutch between the power drive and the work support rotating means; means, the operation of which is co-ordinated with the operation of the work support rotating means, to engage and disengage said clutch and to control the direction of rotation of the work support; means to restore the work support and work to the normal intermediate or starting position after each advance rotation of the work support and during the periods of disengagement of the clutch; and automaticallyoperable means to restrain the work support against return to normal starting position after each advance until after the clutch is disengaged.

1'7. A shoe tacking machine, including a rotatable work support; an edge rest against which the work on the work support is held during rotation of the support; a power drive; means operable by the power drive to rotate the work support and work. rst in one direction, and then after an interval. in the opposite direction from the normal intermediate or starting position of the work support in each instance; a clutch between the power drive and the work support rotating means; a transmitting lever normally lying intermediate its limits of travel; a cam to rock said lever first in one direction and then in theother from and to its normal intermediate position; a clutch control member; a bellcrank rockingwith said transmitting lever; and slotted links to connect the opposite arms of the bellcrank with the clutch control member to actuate the clutch control member in one and the same direction irrespective of the direction of movement of the bellcrank.

18. A shoe tacking machine, including a rotatable work support; an edge rest against which the work on the work support is held during rotation of the support; a power drive; means operable by the power drive to rotate the work support and work, first in one direction,- and then after an interval, in the opposite direction from the normal intermediate or starting position of the work support in each instance; a clutch between the power drive and the work support rotating means; a transmitting lever normally lying intermediate its limits of travel; a cam to rock said lever first in one direction and then in the other from and to its normal intermediate psition; a clutch control member; a pivotally supported manually operable emergency lever to which one end of the clutch control member is pivotally connected; a bellcrank rocking with said transmitting lever; and slotted links connecting the respective arms of the bellcrank with the clutch control member intermediate its ends, to actuate the clutch control member on its connection with the emergency lever as a fulcrum whenever the transmitting lever is rocked to either limit or its movement, to engage the clutch, said connection of the slotted links with the clutch control member constituting the fulcrum about which said clutch control member rocks, upon actuation of the emergency lever to shift said clutch control member in the opposite direction and disengage the clutch.

19. A shoe tacking machine including a rotatable work support; an edge rest against which the work on the work support is held during rotation of the work support; a power drive; normally idle means operable by the power drive to rotate the work support and work, first in one direction and later in the opposite direction from the normal intermediate or starting position of the work support in each instance; selective means to determine the direction in which the work support shall first rotate from its normal starting position and to automatically condition the work support rotating means to rotate the work support successively in opposite directions from its normal starting position; means under control of the selective means to retain the Work support at each limit of its advance travel; and means to restore the work support and work to its normal starting position upon the release oj the retaining means.

20. In a shoe tacking machine, the combination with a continuously operating driving member; an edge rest; and a work holder shiftable towards and from the edge rest, and rotatable while the work is in contact with the edge rest; of means operable by the driving member to rotate the work holder from an intermediate or normal starting position, rst in one direction with a smooth uninterrupted movement, and later in the opposite direction; control means to determine the direction in which the work holder shall rotate; clutch means controlled by the control means to connect and disconnect the drive member and the work holder rotating means; coupling means controlled by the means which rotates the work holder, to alternately connect and disconnect the control means and the driving member; and means connected with the means which rotates the work holder, for restoring the work holder and work to starting position during each disconnection of the driving member and work holder rotating means.

21. In a shoe tacking machine, the combination with a continuously operable drive member; an edge rest; and an axially rotatable work holder shiftable towards and from the edge rest; of means to automatically oscillate the work holder, when in contact with the edge rest, rst in one direction from and to its normal intermediate or starting position, and then in the opposite direction from and to its normal intermediate or starting position by successive movements, effected by mechanisms, the successive and repeated and alternating operations of which are dependent upon each other, comprising a control mechanism, a Work rotating mechanism for positively advancing the work in one direction and in the other from its normal intermediate4

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