US1248784A - Sewing-machine. - Google Patents

Description

F. ASHWORTH.

SEWING MACHINE.

. APPLICATION FILED JAN. 27. 1913.

Patented Dec. 4, 191?.

7 SHEETS-SHEET I.

F. ASHWORTH.

SEWING MACHINE.

APPLICATION FILED JAN-2771913.

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F. ASHWORTH. SEWING MACHINE.

APPLICATION FILED JAN. 27. I913.

Patented Dec. 4, 1917,

ISHEETS-SHEET 3.

F- ASHWORTH.

SEWING MACHINE.

APPLICATION FILED IAN. 27. I913.

Patented Dec. 4, 1917.

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F. ASHWORTH.

SEWING MACHINE.

APPLICATION FILED JAN. 27, 1913.

Patented Dec. 4, 1917.

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SEWING MACHINE.

APPLICATION man JAN.27. 191a.

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FRED ASHWORTH, 0F BEVERLY, MASSACHUSETTS, ASSIGNOJR, TO UNITED SHOE MACHINERY COMPANY, OF PATERSUN, NEJV JERSEY, A CORPOEA'I'ION NEW JERSEY.

SEWING-MACHINE.

To all whom it may concern:

lBe it known that I, FRED AsHwoRTH, a citizen of the United States, residing at Beverly, in the county of Essex and State of Massachusetts, have invented certain new and useful Improvements in Sewing-Machihes; and I do hereby declare the following to be a full, clear, and exact description of the invention, such as will enable others skilled in the art to which it appertains to make and use the same.

This invention relates to sole sewing machines, and more particularly to sole sewing machines of the so-called McKay type.

Machines of this type comprise a rotatable horn which extends within and supports the shoe at the sewing point durmg the stitch forming operation, and a straight hook needle which during each cycle of operations of the machine is projected through the sole of the shoe into position to receive the thread from a looping device located in the tip of the horn. The work is engaged at the sewing point by the horn, and by a presser foot located on the opposite side of the work, one of which is movable relatively to the other to accommodate work of varying thicknesses between them. The movements imparted to the needle during each cycle of operations comprise a work penetrating movement during which the needle is projectedthrough the work in position to receive the thread from the looper, followed by a period of substantial dwell to give time for the looper to lay the thread in the barb of the needle, and a retracting move ment during which the loop of thread is drawn by the needle through the materials 71s therefore essential, in order that the and through the preceding loop. It is essential that the relative positions of the needle and horn which supports the looping device be unvaried at the time the needle is looped in successive cycles of operations. In this type of machine the needle, during its retracting stroke, by its backward pull on the loop of thread which it carries, acts to draw the slack out of the thread leading to the preceding loop and thereby tighten the preceding stitch, and to draw off from the supply sufficient thread to form the stitch. lt

stitches may be formed and tightened in a Specification of Letters JPatent.

Patented Dec 4, T91??? Application filed January 27, 1913. Serial No. 744,465.

uniform and reliable manner, that the length of the loop drawn out by the needle, measured from the lower or inner end of the needle hole, be increased or decreased upon a change in the thickness of the work, an amount substantially the same as the increase or, decrease in the thickness of the work between successive stitches, or in other words, that the length of the loop of thread drawn out by the needle above the work in forming successive stitches be unvaried, and therefore that the needle retract substantially the same distance from the work in successive cycles of operations, regardless of the thickness of the work. In the most common commercial forms of the McKay type of sewing machine, the machine is provided with a verticall immovable work supporting horn and wlth a presser foot, the position of which when the work is engaged between the presser foot and the horn, varies in accordance with the variations in the thickness of the work. The needle actuating mechanism has a provision for lost motion between two limiting stops, and during the lost motion periods, which occur respectively when the needle is at the limit of its stroke in each direction, the needle is held stationary by frictional devices. During the dwell thus produced in the needle movement at the end of the work penetrating stroke of the needle the thread is laid in the hook of the needle by the looper. The retracting stroke of the needle is varied in accordance with the changes in the thickness of the work by varying the position of one of the stops, the position of said stop being controlled by the position of the presser foot as determined by the thickness of the work.

Machines of this type are usually provided with a cast-cit to prevent the fouling of the thread of the previously formed loop in the barb of the needle as the needle is retracted out of engagement with the work. The cast-oil" in the commercial machines has usually been actuated in timed relation to the needle from the needle actuating mecha nism by the engagement of abutments on the needle actuating mechanism with abutments carried by the cast-ofi' mechanism, and frictional devices have'been employed to hold the cast-oft from movement until it is positively actuated. Certain mechanisms of the commercial machines, particularly the mechanisms for actuating and controlling the needle and the cast-off, above briefly described, are open to serious objections, on account of the lost power due to the employment of frictional devices, and on account of the excessive pounding vibration and wear on the parts of the machine, especially when the machine is run at high speed.

One object of the present invent1on is to produce an improved sole sewing machine of the McKay type which will operate without undue loss of power, and without excessive vibration and wear on the parts, even when the machine is run at high speed.

Another object of the invention is to improve the' construction, arrangement and mode of operation of various parts of the machine, particularly with a view to rendering these parts more certain and reliable in operation.

With these objects in view, certain features of the invention relate to novel and improved mechanism for actuating the needle. This mechanism is constructed to produce the required var ations in the needle stroke in a certain and reliable manner while maintaining the needle under positive control throughout its movements, and comprises various novel and advantaeous constructions and combinations set forth in the following description and pointed out in the claims.

A further featur'eof the invention contemplates the provision of mechanism for actuating the cast-off in timed relation to the needle constructed and arranged to control the cast-ofi positively throughout substantially its entire movements. The mechanism' for actuating the cast-oif is preferably independent of the needle actuating mechanism, and the path of the cast-off is varied in accordance with the changes in the needle stroke through a connection which acts upon a change in the relative position of the presser foot and work support,

as determined by the thickness of the work,

to vary the path of the cast-off.

Other features of the invention consist of novel and improved constructions and combinations hereinafter described and claimed, the advantages of which will be apparent to those skilled in the art. I

In the accompanying drawings illustrating the preferred form of the invention, Figure 1 is a side elevation of the head of a machine embodying the invention; Fig. 2 is a front elevation of the head of the machine; Fig. 3 is a plan of the head of the machine; Fig. 4 is a sectional elevation taken substantially on the line 4-4 of Fig. 1; Fig. 5 is a detail sectional view illustrating particularly a portion of the mechanism. for lifting the presser foot; Fig. 6 is a section taken on the line 66 of Fig. 5; Fig. 7 is a section taken on the line 77 of Fig. 5; Fig. 8 is an enlarged front elevation of the head of the machine, showing the positions of the parts when the machine is operating upon thin work, and illustrating the needle in its lowermost position; Fig. 9 is a view similar to Fig. 8, illustrating the needle in raised position; Fig. 10 is an enlarged front elevation of the head of the machine, showing the positions of the parts when the machine is operating upon thick work, and illustrating the needle in its lowermost position; and Fig. 11 is a view similar to Fig. 10 showing the needle in raised position.

Referring to the drawings, the work supporting horn is indicated at 1, and the presser foot cooperating therewith at 2. In the present embodiment of the invention the horn is vertically immovable, and the presser foot is arranged for movement with relation to the horn to accommodate work of varying thicknesses. The presser foot is secured to the lower end of a presser bar 8 which is arranged to slide vertically in a suitable guide formed in the lower plate of the head of the machine. A cap or sleeve 4, arranged to slide in a guide in the upper plate of the head of the machine, is secured to the upper end of the presser bar, and the upper end of the cap is engaged by a coiled spring 5 which acts yieldingly to hold the presser foot in engagement with the work. The downward movement of the presser foot when no Work is in the machine is limited by the engagement of the lower end of the sleeve 4 with a bracket 6 provided with a perforation through which the presser bar passes, and adjustably secured by screws 7 to the side of the machine frame. The mechanism for lifting the presser foot during each cycle of operations, to permit the work to be fed, comprises a clamping or locking device to enable the presser foot to be lifted a uniform distance, regardless of its vertical position. This locking device is illustrated particularly in Figs. 5, 6 and 7, and comprises a nut 8 engaging screw threads 9 of steep pitch out on the presser bar, and a split clamping block 10 surrounding the nut. The nut, when not engaged by the clamping block, is free to turn so that it offers no resistance to the rising and falling movements of the presser foot. The nut 8 and the clamping block 10 are supported by a sleeve 11 surrounding the presser bar, which sleeve is provided with a recess to receive both the nut and the block. The upper end of the sleeve is engaged by a coiled spring 11 surrounding the presser bar, and confined between the upper end of the sleeve and the lower face of the bracket 6. This spring acts to hold the sleeve 11 in its lowermost position with relation to the presser bar, the downward meagre i movement of the sleeve being limited by the engagement of its lower end with a portion of the machine frame. In lifting the presser foot the clamping block is first actuated to engage the arms thereof with the nut 8'to clamp the nut and lock the same from turning movement on the presser bar, and the clamping block and nut are then lifted to lift the presser foot from the work. To enable the arms of the clamping block to be relatively actuated to clamp the nut 8,

the ends of these arms projecting rearwardly beyond the nut are constructed with oppositely inclined outer faces, shown in Fig. 6, and an actuating lever 12 is pivoted on the sleeve -11, said lever being constructed in the form of a yoke, the arms of which embrace the clamping block. the lever 12 are provided with inclined surfaces 13 for engagement with the opposite inclined surfaces on the arms of the clamping block. lFhe lever 12 is connected by an adjustable link 14 with the forwardly eX- tending arm of a bell crank 15 pivoted at 16 on the machine frame, the other arm of which is provided with a cam roll 17 which engages a cam groove 18 in a cam disk 19 .mounted on the main shaft 20 of the mafreely upon the presser bar, and the presser foot to be engaged with the Work by the action of the coiled spring 5; As the pivotal connection between the link 14 and the lever 12 is moved upwardly, the lever 12 first swings about its pivotal connection with= the sleeve ll, until the inclined surfaces 13 of the lever are engaged with the opposite inclined surfaces on the arms of the clamping block and the arms of the clamping block are thereby relatively actuated to en- .gage the nut 8 and lock the same from turning on the presser bar. After the nut has been locked in this manner upon the resser bar, the swinging movement of the ever 12 upon its pivot is limited by the engagement of the lever with the clamping block, and the clamping block, the nut 8,

engages the frame of the machine. this occurs, the lever 12 is swung down- The arms of shaft 29.

When

wardly about its pivotal connection with the sleeve 11, thereby disengaging the 1nclined surfaces 13 on the lever from the inclined surfaces on the arms of the clamping block and allowing the clamping block toexpand by itsown resiliency and release the-nut 8. The nut is then free to rotate on the presser bar, and the presser bar and nut are free to move relatively under the influence of the springs 5 and 11- to accommodate themselves to any variation in the thickness of the work. The same operation occurs during each cycle of operations of the machine, the presser foot lifting mechanism acting to lift the presser foot substantially the same distance during each cycle.

In order that the presser foot may be lifted by the operator to permit the removal andinsertion of the work, a pin 21 is secured to the presser bar, and arranged to project laterally therefrom through a slot in the frame of the machine, and a lever 22 is pivoted on the side of the machine frame .and arranged so that its forwardly projecting end engages beneath the pin 21. The lever 22 is connectedwith a treadle rod 23 b which the lever 22 is actuated to lift the presser bar. j

The presser-foot mechanism above de scribed is covered in'an application -;Serial No. 69,983, filed January 3, 1916, constituting a division of the present application.

The work is fed by means of an awl or feed point 24: mounted in the lower end of an awl or feed bar 25 pivoted at 26 on an extension on the sleeve 1, so that the vertical position-of the awl bar is varied as the position of the presser foot is varied in accordance with changes in the thickness of the work. The work is fed by the lateral swinging movements of the aw]. bar on its pivot while the awl is projected into engagement with the work. The mechanism for imparting the'lateral or feed movements to the awl barcomprises a link 27 pivotally connected to the awl bar at one extremity, and at the other to an arm 28 mounted on a rock A second arm 30 is secured to the rock shaft, and is connected by means of a link 31 to a. lever 33 pivoted at 34 on the machine frame, and provided with a roll 35 which engages a cam groove36in the cam disk 19'. A bolt and slot connection is provided between the arm 30 and the link 31, so that the length of feed may be varied, the slot being made in the form of an are which is struck from the center of the connection tween the link 31 and the lever 33 when is parts of the feed'mechanisin are in the position which they occupy at the beginning of the work feeding stroke. With this construction, the adjustment of the bolt in the slot in the lever will produce variations in the length of feed, while the feeding devices will always be retracted t6 the same position of the feed.

The feed point or awl is mounted in the feed bar so that it can be projected into engagement with the work and heldin engagement therewith while the work is fed, and so that it can be retracted out of engagement with the Work during the retracting movement of the feeding devices. In the construction illustrated the feed point is provided with a shankwhich is arranged to slide in a suitable guide in the lower end of the feed bar, and rack teeth 37 are formed on the shank of the feed point, which are engaged by the teeth of a pinion 38 journaled on a shaft 39 mounted in the feed bar. A rack bar 40 is mounted to slide vertically in the lower end of the feed bar, the teeth of which rack bar are also in mesh with the teeth of the pinion 38, the width of the teeth of the pinion being suflie'ient to engage both the teeth on the shank of the feed point and those on the rack bar. A block 41 is mounted on a pin secured in the upper end of the rack bar, and is received in a recess or slot in the forward end of a lever 42 pivoted at 43 on the link 27, and connected by a link 44 with an arm 45 mounted on a rock shaft 46. In order to actuate the rock shaft 46, an arm 47 is secured thereto and provided with a roll 48 which engages a cam groove 49 also formed in the cam disk 19. Through the connections described the oscillation of the arm 47 causes the reciprocation of the rack bar 40 in the feed bar, thereby rotating the pinion 38 and causing the feed point to be projected from the feed bar into engagement with the work and withdrawn from engagement with the work. The mechanism for projecting and withdrawing the feed point with relation to the feed bar is actuated in timed relation to the mechanism for imparting the lateral movements'to the feed bar, so that the feed point is projected into engagement with the work while the feed bar is moved laterally to feed the work, and so that the feed point is withdrawn from engagement with the work when the feed bar is brought back to its initial position, ready to begin a work feeding stroke.

The connection between the link 44 and the arm 45 is arranged so that it is substantially in alinement with the axis of the rock shaft 29 when the feed point is projected into engagement with the work, with the result that the movement of the feeding mechanism does not affect the position of the lever 42 with relation tothe link 27 during the work feeding movement of the feeding devices, and the position of thefeed point with relation to the feed bar is substantially unchanged while the work is being fed.

The work feeding mechanism described above is covered in an application Serial No. 69,984, filed January 3, 1916, constituting a division of the present application.

The stitch forming devices of the machine comprise a straight hook needle 46 which during each cycle of operations is projected through the work into position to receive the thread from the whirl or looping device located in the tip of the horn, and which is then retracted to draw the loop of thread through the materials and through the previously formed loop, and to draw the slack out of the thread leading to the preceding loop to tighten the preceding stitch. The needle is mounted upon the lower end of a needle bar 47 mounted to reci rocate in guideways in the upper and lower plates of the head of the machine. The mechanism for actuating the needle comprises a. link 48 pivotally connected at 49 with the needle bar, and a second link 50 pivotally. con-' nected at 51 with the outer end of the link 48*. The link 50 is mounted to swing about a supporting pivot 52 carried by a member 53 which in turn is mounted to swing about a fixed center or axis 54. In the construction illustrated, the member 53 is constructed in the form of ayoke, the arms of which embrace links 48 and 50, and the yoke is pivoted upon studs, one of which is carried by a bracket 55 secured to the frame of the machine, and the other is mounted in the body of the frame. The pivotal connection 51 between the link 50 and the link 48 is actuated to reciprocate the needle by means of an oscillatory lever 56 which is connected with the pivotal connection 51 byv means of a link 57 The amplitude of oscillation of the lever 56 is substantially uniform during successive cycles of operations of the machine, and the movements of said lever swing the connection 51 in are shaped paths about the pivot 52. The parts above described are constructed and arranged so that the shifting of the position of the member 53 about the axis 54 will cause variations in the reciprocatory movements of the needle bar in a manner hereinafter explained. In order that the stroke of the needle may be varied in accordance with changes in the thickness of the work, the machine is provided with a connection between the member 53 and the presser bar which acts to swing said member about its axis 54 as the position of the presser bar is varied by reason of changes in the thickness of the work, said connection consisting of a link 58 pivoted at one extremity to an arm 59 on the member 53, and at the other extremity pivotally connected with the sleeve 4 by the pin upon which the. feed bar is pivoted. When operating upon thin Work the memnaaegrea ber 53, through its connection with the presser foot, is caused to assume the position illustrated in Figs. 2, 8 and 9. When the member 53 occupiesthis position the connection 51 is swung by the oscillation of the lever 56 in a path extending generally in the same direction as the direction of reciprocation of the needle bar. When the Work-increases in thickness, the presser foot assumes a higher work engaging position, and the member 53, by reason of its connection with the presser foot, is swung downwardly about the axis 54. The parts of the needle actuating mechanism are constructed and arranged so that the pivotal connection 51 is brought into alinement with the axis 54 at the limit of the downward stroke of the needle bar. The changes in the position of the member 53 caused by changes in the thickness of the work therefore will not affect the lower limit of the needle stroke. For the sake of clearness in theexplanation of the efiect of the shifting of the position of the member 53 about the axis 54 caused by variations in the position of the presser foot, due to changes in the thickness of the work upon the upper limit of the needle stroke, let it be assumed that the lever 56 is at the limit of its needle bar lifting stroke and is fixed, while the member 53 swings downwardly from the position illustrated in Figs. 2, 8 and 9 which it occupies when the machine is operating upon thin work. The downward swinging movement of the member 53 about the axis 54 will act to swing the pivotal connection 51 about the pivotal connection of the link 57 with the lever 56. The link 57 and the lever 56 are constructed and arranged so that this swinging movement of the connection 51 abput the pivotal connection of the link with the lever will move the con nection 51 away from the axis 54, and will also lift the connection 51 vertically. When the member 53 shifts its position downwardlyfrom the position illustrated in Figs. 2, 8 and 9, the oscillation of the lever 56 will reciprocate the connection 51 in a path which is angular to the direction of reciprocation of the needle bar. It will be evident, therefore,-that the downwardshift in the position ofthe member 53 about the axis 54, caused by an increase in the thickness of the work, will cause an increase in the amplitude of movement of the connection 51, will raise the vertical position of the upper limit of the path of said connection, and will cause the connection to swing outwardly in an angular direction away from the needle bar during its upward stroke, and that these changes in'the path of the connection 51 will produce an increase in the upward stroke of the needle bar. The lever 56 is mounted upon a rock shaft 60 extending rearwardly from the front of the machine, and a second arm 61 by a link 62 with an arm 63 carried by a sleeve 64 loosely mounted on a shaft 65 which forms part of the cast-ofl' actuating mechanism. The sleeve 64 is provided with a second arm 66 which is connected by means of a pitman 67 with a crank 68 carried by the main shaft 20 of the machine. The rotation of the crank 68 causes the oscillation of the sleeve 64 on the shaft 65, and the oscillation of the lever 56 which actuates the pivotal connection between the link 48 and the link 50.

The parts of the mechanism above described are soconstructed and arranged that the connection 51 is brought into alinement with the center 54 at the limit of the work penetrating stroke of the needle. Referring to Figs. 8 and 9, in which the various parts of the needle actuating mechanism are illustrated in the positions which they assume when operating upon thin work, it will be noted that the movement of the oscillatory lever 56 from the position of Fig. 8, with the needle at the end of its work penetrating movement, to the position of Fig. 9 to retract the needle, acts to swing the pivotal connection 51 about the pivot 52, thereby lifting the outer end of the link 48 to raise the needle bar. The position of'the member 53 as determined by the connection 58 between the said member and the presser foot is such when operating upon thin work that the pivotal connection 51 swings in a path which has the same general direction as the direction of reciprocation of the needle.

Referring now to Figs. 10 and 11, in which the parts of the needle actuating mechanism are shown in the positions which they occupy when operating upon thick work, it will be noted that the position of the member 53 is changed from the position which it assumed when operating upon thin work, on account of the raised position of the presser foot, due to the presence of thick work between the presser foot and the horn. This change in the position of the presser foot has caused the member 53 to swing downwardly about the fixed center 54, thereby lowering the position of the pivot 52 on which the link 50 swings. Onaccount of the arrangement of the parts, so that the connection 51 is brought into alinement with the center 54 at the limit of the work penetrating stroke of the needle, the swinging of the member 53 about the center 54 causes no variation in the lower limit of the needle stroke. During the movement, however, of

is attached to said rock shaft and connected the oscillatory lever 56 from the position member 53, the connection 51, instead of moving in a path substantially parallel with the direction of reciprocation of the needle bar, is swung in an angular direction with relation to the direction of reciprocation of the needle bar, so that said connection swings away from the needle bar during its needle bar lifting stroke, the amplitude of movement of the connection 51 is increased, and the connection is lifted to a higher position at the end of its needle bar lifting stroke.

The upward stroke of the needle bar will therefore be increased to correspond with the increase in the thickness of the work.

It will be understood without further explanation that in the needle actuating mechanism described a decrease in the thickness of the work will produce a corresponding decrease in the upward stroke of the needle bar, and that the extent of the variations in the upward stroke of the needle bar will de pend upon the extent of the variations in the thickness of the work.

The dwell in the movement of the needle when the needle has penetrated the work and has arrived in position to receive the thread from the looper is produced by arranging the parts so that the crank 68 is substantially at dead center with relation to the point of connection of the pitman 67 with the arm 66, and so that the point of connection of the link 62v with the arm 63 is approximately at dead center with relation to the point of connection of saidlink with the arm 61 when the needle approaches the end of its work penetrating movement. It is to be noted that the needle actuating mechanism described is constructed to, produce the required variations in the stroke of the needle in a certain and reliable manner while the needle is maintained under positive control throughout its movements, and that the connections between the relatively movable parts of said mechanism are pivotal connections. The needle actuating mechanism therefore operates without undue vibration, friction or wear on the parts of the machine, even when the machine is run at high speed. r

The cast-off for preventing the fouling of the thread of the previously formed loop in the barb of the needle as the needle retracts out of engagement with the work, is indicated at 69. The cast-ofi' is secured to the end of a cast-ofi' bar 69. which is dove-tailed in cross-section, and is arranged to slide in a suitably formed dove-tailed groove in the lower plate of the head of the machine. The cast-ofi' actuating mechanism comprises a toggle consisting of pivotally connected links 70 and 71, of which the link 70 is connected with the u per end of the cast-off bar, and the link 1 is pivotally connected with an extension 72 formed on the sleeve 4 attached to the presser bar. The central joint of the toggle is recipro'cated to actuate the cast-off in timed relation to the needle through a link 73 pivotally connected at 7% with the toggle, and at 75 with an arm 7 6 attached to the rock shaft 65. A second 'arm 78 is attached to the rock shaft 65,

and is connected by an eccentric strap and pitman 79 with an eccentric 80 mounted on the main shaft 20 of the machine. The pin or screw 81, which connects the member 70 of the toggle with the cast-off bar, is provided with a portion considerably smaller than the aperture in the link 70 through which the pin passes, and a leaf spring 82 is mounted on the link 70 and arranged to engage the upper end of the cast-oif bar, thereby allowing the cast-off to yield slightly when brought into engagement with the work. The cast-ofi' actuating mechanism is timed with relation to the mechanism for actuating the needle to actuate the cast-off in timed relation to the needle in substantially the same manner in which it is actuated in the present commercial machines.

The connection between the cast-off mechanisin and the presser foot bar causes a variation in the path of the cast-off to correspond with variations in the needle stroke produced by variations in the position of the presser foot. The cast-off mechanism above described is constructed to control the castoff positively through substantially its entire movements, thereby avoiding many disadvantages inherent in the cast-off mechanisms heretofore employed. The connection between the link 70 and the cast-off bar permits the cast-off to yield slightly when brought into engagement with the work, preventing the cast-off from being forced into the work, and from enlarging the mouth of the hole in the work punctured by the needle.

It is to be understood that except as defined in the claims the invention is not limited to any particular machine or type of machine, or to any particular construction and arrangement of parts of the illustrated embodiment, but that the invention may be embodied in any form within the scope of the claims.

Having explained the nature and object of the invention, and having specifically described a machine embodying the same in its preferred form, what is claimed is 2- 1. A sewing machine, having, in combination, a needle, a needle bar, mechanism for actuating the needle comprising a link pivotally connected to the needle bar, means to swing the outer end of the link in the arc of a circle to reciprocate the needle, a work support, a presser foot, and means to vary the path of the outer end of said link angularly with relation to the direction of reciprocation of the needle bar upon a change in the relative positions of the work support and presser foot due to a change in the thickness of the work to vary one of the limits of the needle stroke.

2. A sewing machine, having, in combination, a needle, mechanism for actuating the needle. comprising pivotally connected links, one of which is pivotally connected directly to the needle bar, asupporting pivot for the other of said links, means to swing the pivotal connection of the links about said supporting pivot to reciprocate the needle, a work'support, a presser foot, and means to vary the position of said supporting pivot upon a change in the relative positions of the work support and presser foot due to a change in the thickness of the work to vary the path of the pivotal connection between the links and thereby vary one of the limits of the needle stroke.

3. A sewing machine, having, in combination, a needle, a needle bar, mechanism for actuating the needle comprising pivotally connected links, one of which is pivotally connected directly to the needle bar, a supporting pivot for the other of said links, means to swing the pivotal connection of the links about the supporting pivot to reciprocate the needle, a work support, a presser foot, and means to swing the supporting pivot about a fiXed axis upon a change in the relative positions of the work support and presser foot due to a change in the thickness of the work to vary one of the limits of the needle stroke.

-l. A sewing machine, having, in combination, a needle, a needle bar, mechanism for actuating the needle comprising pivotally connected links, a connection between one of the links and the needle bar, a supporting pivot for the other of the links,

. means to swing the pivotal connection of the links about the supporting pivot to reciprocate the needle, a work support, a presser foot, and means to swing the supporting pivot about a fixed axis substantially coincident with the pivotal connection of the links at one of the limits of the needle stroke upon a change in the relative positions of the'work support and presser toot due to a change in the thickness of the work to vary the other limit of the needle stroke.

5. A sewing machine, having, in combination, a needle, a needle bar, mechanism for actuating the needle comprising pivotally connected links, one of which is pivotally connected directly to the needle bar, an oscillatory lever, a pivotal connection between the other link and the oscillatory lever, a work support, a presser foot, and a connection for controlling the path of the pivotal connection between said links acting upon a change in the relative position of the work support and presser foot due to a change in the thickness of the work to vary the path of said connection to vary one of the limits of the needle stroke.

6. A sewing machine, having, in combination, a needle, a needle bar, mechanism for actuating the needle comprising pivotally connected links, one of which is pivotally connected directly to the needle bar, an oscillatory lever, a pivotal connection between the other link and the oscillatory lever, a work support, a presser foot, and a connection for controlling the path of the pivotal. connection between said links acting. upon a change in the relative positions of the work support and presser foot due to a change in the thickness of the work to swing the pivotal connection between the links about the pivotal connection with the oscillatory lever to vary one. of the limits of the needle stroke.

7. A sewing machine, having, in combination, a needle, a needle bar, mechanism for actuating the needle coniprising a link pivotally connected with the needle bar, a second link pivotally connected with the first link, a supporting pivot for the second link, a member on which the supporting pivot is carried mounted to swing about a fixed axis, means to swing the pivotal connection between the links about the supporting pivot of the second link to reciprocate the needle bar, and a connect-ion between said member and the presser foot for swinging said member about its axis upon a change in the relative positions of the work support and the presser foot due to a change in the thickness of the work to vary the position of the supporting pivot and thereby vary one of the limits of the needle stroke. a

8. A shoe sewing machine, having, in combination, a needle, mechanism for actuating the needle,,,a cast-off for the needle, mechanism for actuating the cast-oi" in timed relation to the needle acting to maintain the cast-ofi' under positive control throughout substantially its entire movements and a connection for varying the path of the cast-oft in accordance with changes in tne stroke. of the needle.

9. A shoe sewing machine, having, in combination, a needle, mechanism for actuating the needle, a cast-off for the needle, and mechanism for actuating the cast-off in timed relation to the needle comprising a toggle, a pivotal connection between one member of the toggle and the cast-oft, and means to reciprocate the central joint of the toggle.

10. A shoe sewing machine, having, in combination, a needle, mechanism for actuating the needle arranged to vary the stroke of the needle in accordance with changes in the thickness of the work, and means independent of the needle for actuating the cast-oft" in timed relation to the needle, comprising a connection for varying the path of the cast-off in accordance with changes in the stroke of the needle.

11. A shoe sewing machine, having, in combination, a needle, mechanism for actuating the needle arranged to vary the stroke of the needle in accordance with changes in the thickness of the work, a cast-off for the needle, and means for actuating the cast-ofii in timed relation to the needle acting to maintain the cast-off under positive control throughout substantially its entire movements, and comprising a connection for varying the path of the cast-ofi' in accordance with changes in the stroke of the needle.

12. A shoe sewing machine, having, in combination, a needle, mechanism for actuating the needle arranged to vary the retracting stroke of the needle in accordance with changes in the thickness of the work, a work support, a presser foot, a cast-off for the needle, and means for actuating the cast-off in timed relation to the needle comprising a connection between the presser foot and the cast-off mechanism acting upon a change in th position of the presser foot due to a change in the thickness of the work to vary the path of the cast-off.

13. A shoe sewing machine, having, in combination, a needle, mechanism for act-uating the needle arranged to vary the retracting stroke of the needle in accordance with changes in the thickness of the work, a work support, a presser foot, a cast-ofi' for the needle, means for actuating the cast-ofi' comprising a toggle, a connection between one member of the toggle and the cast-ofi', a connection between the other member of the toggle and the presser foot for varying the position of the toggle and thereby varying the position of the cast-ofi' in accordance with changes in the position of the presser foot due to variations in the thickness of the work, and means to reciprocate the central joint of the toggle to actuate the castoii in timed relation to the needle.

FRED ASHVVORTH. \Vitnesses CHESTER E. Romans, RUTH E. \VARD.

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