US1626256A - Automatic embroidering machine - Google Patents

Description

il 26 1927. Apr L. SCHWARZMANN AUTOMATIC EMBROIDERING MACHINE l3 Sheets-Sheet 1 Filed NOV. 2. 1921 April 26 1927.

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il 26 1927. Apr L. SCHWARZMANN AUTOMATIC EMBROIDERI NG MACHINE Filed Nov. 2. 1921 13 Sheets-Sheet 10 I JNVENTOR. w %4WMQMH I figm I 1921 15 Sheets-Sheet 11 NW6 m f 2 Z m 6 a Z ,,m 0%? g M u Em m L. SCHWARZMANN AUTOMATIC EMBROIDERING MACHINE Filed Nov. 2.

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L. SCHWARZMANN AUTOMATIC EMBRCSIDERING MACHINE Filed Nov. 2 1921 13 Sheets-Sheet 13 JN VEN TOR.

Patented Apr. 26, 1927.

UNITED STATES PATENT o-Farce.

LEON SCHWARZMANN, OF NEW YORK, N. Y.

I .euromarro annnomnnme MACHINE.

Application filed November 1921. Serial No. 512,184. h

The present invention relates broadly 'to sewing machines, and more particularly to sewing embroidering machines which are entirely automatic in operation and capable of producing embroidery designs of a most' result is almost impossible with machines guided by hand, as even an experienced operator is apt to produce slight variations and even mistakes.

An important object of the present invention is to provide an entirely automatic feed I for the tambour which holds the material being embroidered, so it can be moved in any direction. and to any extent within predetermined limits, radially from the needle,

to produce a stitch of any desired length within such limits and in any direction.

Another object of the inventionis to provide an embroidering machine having pattern controlled feed predetermining mechanism and feeding mechanism, which mepha- I nisms are intermittently in operative enga ement to relieve the pattern from the strains of moving the feeding mechanism.

, Still another object is to provide means for adjusting at willcthe length of the stitches irrespective of the direction of feed of the material being embroidered, so that variations in the size of a givendesign can be produced from the same pattern.

A further object of the invention is .to obtain a larger number of stitches from every inch of pattern than has heretofore been possible, whereby the cost of the pattern may be materially reduced.

A still further object of the invention is" to provide a continuously driven pattern in intermittent operative engagement with the working noiseless and insure a greater accuracy in the feeding of the pattern than feed predetermining mechanism to render its 1 inate all back lash 6f the gears arid insure accurate feeding of the cloth being embroidered. 1

An additional object of. the invention is to provide a pattern control which-"may be in tape, ring or type-like form.

Still another object of the invention is to provide convenient means whereby the clothcarryingdevice may be operatively' disconnected from the feeding mechanism to permit manual shifting thereof.

I Still a further object of the invention is to provide convenient means to put in figures, or, in other words, to make legible a I design which it is desired to automatically and correctly reproduce in embroidery by the machine. i

The foregoing and other objects of the present invention, together with their attendant advantages, will be apparent as the invention becomes better understood by reference to the accompanying specification and drawings, forming a part thereof, it being premised that changes may bemade in the various details and the manner of operation within the sco e of the appended claims, without departing from the spirit of the invention.

In the drawings- Figure 1 is a side elevation, partly broken away, of a machine embodying the present invention; a Figure 2 is a to plan view of the tambour and its operatmg arms, the arm standard being shown in section;

Figure 3 is a top plan view of the mechanism below the bed plate, the bed plate in this figure bein partlybroken away and parts of the mec anism being shown 1n section' r Figure 4 is a transverse vertical sectional view on the line IV-IV of. Figure 3;

Figure 5 is a longitudinal vertical sec- 'tional.view on theline VV of Figure 3;

Figure 6 is a horizontal sectional view on the line VI-VI of Figure 5; I I

Figure 7 is a transverse vertical sectional view through the arm standard illustrating thefeeding lever; I I

Figure, 8 is a detailsectional view through the' feeding lever andits pivotal mounting;

Figure 9 is a top plan view of the pivotal levers and their associated mechanism, certain .of the'pivots being shown in section;

Figure 10 is a perspective view of one of the pivotal levers constituting part of the feeding mechanism;

Figure 11 is a perspective view of one of the sliding levers constituting part of the feeding mechanism; a

Figure 12 is a top plan view, partly broken away, illustrating the spiral springs for preventing back lash of the gears;

Figure 13 is a side elevation of a machine embodying the. present invention;

Figures 14, 15, and 16 are perspective views of different forms of pattern engaging tongues;

Figure 17 is a vertical sectional view through the arm standard, illustrating a portion of the pattern controlled feed preetermining mechanism;

Figure 18 is a perspective view of one of the pattern wheel brackets;

Figure 19 is an end elevation, on an enlarged scale, of the pattern wheel and a portion of its operating mechanism;

Figure 20 is an end elevation of the needle, presser foot, and operating mechanism therefor;

Figures 21 to 26 are detail views of different forms of pattern wheels;

Figure 27 is a plan view of the apparatus for putting in figures or making designs;

Figure 28 isa sectional view on the line XXVIII-XXVIII of Figure 27;

Figure 29 is adiagrammatic view illustrating the periods of rest and movement of different parts of the machine;

Figure 30 is a diagrammatic view illustrating the movement of the feedin lever;

Figure 31 is a developed view 0 a portion of the pattern; r

Figure 32 is a developed view of the cam for operating the feeding lever;

Figures 33 to 38 are detail views of por-- tions of the braking mechanism, illustrating modified forms thereof;

Figure 39 is a perspective view of a portion of the feeding mechanism; and

Figures 40 and 41 are detail views illus trating the correction device for the feeding lever.

In all of the upper or foot feed, and also the under feed machines, certain kinds of material being embroidered, such as canvas or fine silk, do not lie sufliciently fiat over the bed plate during the feeding process and often become wrinkled to such an extent as to impair the operation of the machine. To overcome this, and for other obvious reasons; the present machine employs a tambour or hoop in which the material is conveniently stretched and held in position by an inner ring. The feeding movement is then imparted to the stretched cloth by means of suitable connections with the tambour, as will be explained later.

The present invention is not limited in its application to the specific construction of stitch forming mechanism in connection with which it is represented by the several views, as the drawings are illustrative only and for the purpose of giving a clear understanding of the operation of the invention.

Referring to the drawings, the bed plate 1 of the improved machine supports the usual arm standard 2, in the up er part of which is journaled'the main sha 3 in suitable bearings 4. One end of the main shaft is provided with the usual driving :pulley 5 and flywheel 6, while the other end 'is connected with any usual needle reciprocating mechanism. On the main shaft .3 is a bevel gear 7 meshing with a bevel gear 8 on the upper end of a verticalshaft- 9 'journaled in suitable bearings 10 carried by lugs 12 projecting inwardly from the arm standard 2. At the opposite end of the shaft 9 is secured a bevel gear 14 meshing with a similar ar 15 on the horizontally extendin shutt e shaft 16. The gears 7 and 8 pre erably have a gear ratio of two to one, while the gears 14 and 15 have a gearratio of one to one, so that the shuttle shaft 16 revolves twice for every revolution of the main shaft 3. The shuttle shaft 16 is journaled in suitable bearings 17 carried by the bed plate, and has secured to one end thereof a shuttle 18 which may be of any construction adaptable for machines of this type.- The needle cooperates with the shuttle to form the stitch in the well known manner, and will not be part of the present invention. The tension and take-up devices may also be of any usual or well known construction. 7

The mechanism for feeding the material to be embroidered is conveniently divided into two parts, namely. the feeding'mechanism properand .the pattern controlled described in detail herein, as it forms no l mechanism which predetermines the'variable. V

movement of the feeding mechanism bypositioning' its component parts just before each feeding period in accordance with the pattern. Both of said mechanisms are operative and inoperative alternately, as will be more fully pointed out hereinafter.

The cloth plate 19 of circular disk-like form, as clearly shown in Figure 2 preferably provided with a nickel-plated upper surface to facilitate movement of the cloth thereon, has a hole 20'formed'therein for the passage of. the needle, and is secured to the bedplate in the recessed portion 21 thereof by pins or screws22 projecting downwardly therefrom and'secured in position by locking means 23, as clearly shown in Figure 3.

The tambour 25 in which the fabric is g mbour arc to receive a knurled nut 28. ooperating with the pin and knurled amt are side pins 29 projecting inwardly from the tambour arc and engaging opemngs in the tambour.

The tambour are 27 has two lugs 30, at

substantially 90 from the other, to which plate 19 if thepivots 37 were held stationary.

On the other hand, if both arms 31 were pivotally connected to the lugs 30, instead of only one arm, as described, the tambour would be* capable of a limited swinging movement even with the pivots 37 held stati onary. There would, however, be no means of definitely controlling the movement of the tambour with such a construction. In order, therefore, to provide a controllable movement, either of the arms 31 is secured to the tambour with'a pivotal connection and the other of the arms is rigidly secured, and the pivots '37 are both movable, as will be hereinafter more fully pointed out.

A swinging movement of the arms 34 inwardly, or toward one another, an equal amount, will'cause the fabric to pass under the needlein a straightline away from the arm standard 2; while a movement of the arms 34 an equal .amount in the opposite direction will cause the fabric to move in a straight line toward the arm 'standard2. By correspondingly and simultaneously increasing or decreasing the movement of both arms by the same amount, the feeding of the fabric under'the needle will be vproportionately increased or decreased but will still be moved in a straight line in one direction or the other. However,if the .amount of movement of one of the arms 34 is made greater than the amount of movement of the other arm, either in the same or in the opposite direction; or if one arm is held stationary while the other is moving, the feeding of the fabric will deviate from. such a straight line in direct proportion to the difference of movement of said arms. By simultaneously increasing or decreasing themovement of both of said arms 34 by the same amount, irrespective of their relative direction and their relative extent of movement, the feeding of the fabric, and hence the length of the stitches, will be proportionately len thened or shortened, as the case may be, ut the direction of the feedwill not be changed.

bushings in position in the bed plate.

. predetermined limits and in any desired direction may be produced. The mechanical connections of the tambour with the pattern controlling mechanism forproducing such movements will now be pointed out.

The pivots 37 each have on their lower ends disks 39, preferably made in one piece with their shank portions, as shown in Figures 4 and 5. These pivots are journaled at their upper portions in flat bearings 40 and at their lower ends in a plate 41 secured to the ribs 42 projecting downwardly from the bed plate. The bearings 40 preferably each have a threaded engagement with relatively large bushings 45, passing through suitable openings in the bed plate, and have their portions 46 overlapping the edges of said openings to maintainthe bearings and At an intermediate portion of each of the pivots 37, and secured by means of a suitable key 47, is a gear 48 meshing with a pinion 49, as shown in Figures 3 and 5. The pinions 49 are pivotally mounted on studs 50, Figures 3, 9, and 10, projectingfrom the widened portions 51 of the pivotal members 52' loosely mounted on the pivots 37.

Mounted concentrically with the pivots 37, and lying in the same horizontal plane with the gears 48, are internal ring gears 53 which also mesh with the pinions 49. The internal ring gears are secured by suitable fastening means 54 to disks 55 pivotally mounted on the pivots 37 and rotatablyengaging the bushings 45. The disks 55 loosely overlie the gears 48 and pinions 49 and are loosely enclosed by the annular flange portions 56 of the bushings 45.

The pivotal members 52 are each in slidable connection with the comparatively short ribu58' on each of the sliding members 57.

To permit the desired reciprocating move mentof the sliding members 57 with relation to the pivotal members 52, in addition to the pivotal movement simultaneously with the members 52 about the pivots 37, the sliding members 57 are provided with slots 59 through which the pivots 37 freely pass. The pivotal members 52. in their pivotal movement, bear at one side on the face of flange 56 of the bushing 45, as shown in Figure 5, and at their other side are in engagement with the sliding members 57, as set forth. The sliding members 57 in turn have a sliding contact with the plate 41'. In order to permit ribs'42 to be of the desired strength, the bushings 45 each have a fiat portion 45 on one side-thereof foren'gag ment with the ribs and asimilar flat portion 45 on theoppos'ite side thereof to provide clearance for the shuttle shaft 16.

" In thesame transverse verticalplane with the pivots. 37 are two pivots 60, similar to the lower ends the pivots 60 are journaled in the plate 41, as clearly shown in Figure 4. On the pivots are mounted pinions 64, Figure 4, having hubs provided with set screws 66. The pinions 64 are of such diameter, and are so placed, as to be in mesh with'the internal gear 53, but out of mesh with the gears 48. The large bushings 45 are provided with. suitable openings 67 to receive the hubs 65, and the disks 55 have arcuate slots 68 for receiving the pivots 60 and permitting the necessary pivotal movement of the arts, as shown in Figure 3.

e pivots 37 are each bushings 69 secured by transverse pins to the pivots, which pins each engage one end of a volute spring 71 and the other ends of which springs pass through slots 72 in the upper part of the bushings 45. The ivots 60' are each similarly provided 'with ushings 73, volute springs 75 secured at their inner ends to thepins 74 and at their outer ends to studs 76 projecting upwardly from the plate 41.

The sliding members 57 each have i'ack teeth 77 on one side thereof, Figures 3, 9, and 11, adapted to engage intermediate inions 78 carried by pivots 79 exten ing through the late 41 and secured by nuts 80, as illustrated in Figure 4.' An operatin slide 81, Figures 4, 9, and 39, having rack teeth 82 on each side thereof, meshes with the intermediate gears 78 to transmit motion to the slide members 57. To guide said power slide during its reciprocal movements, brackets 83 are provided on both sides thereof and secured by fastening means 84 to the plate 41to abut against the upward projections 85 of the power slide. These brackets preferably have cut-away portions 86 in their central portions toaccommodate the intermediate gears 78. The slide 81 is connected with the lower forked end of a feeding lever 87. as shown in Figures 1, 7, and 9, by two links 88 having suitable ivotal connections 89 therewith and with t e slide 81. The feeding lever-87 in turn derives its motion from a cylindricalcam 90 suitably keyed to the power shaft 3'in the arm standard and secured in any desired manner against movement longitudinally thereof. The cam 90 is formed with a peripheral groove 92 to impart to the lever 87 at each revolution of the provided with main shaft 3, two periods of movement and two periods of rest, with the periods of movement and rest successively alternating and each period corresponding to 90 of rotation of the cam. A development of the cam 90 is illustrated in detail m Figure 32. The feeding lever 87 at its upper end is provided with a laterally extending stud 93 projecting from both sides thereof and provided on its inner end with a roller 94 working in the cam groove 92.

Intermediate its ends, the lever 87 is pivotally carried on the arm standard 2 bymeans of a channel shaped member 95, Figures 7 .and 8, secured to a filler block 96 by suitable fastening means 97 to form a rectangular opening adapted to slidably .receive an intermediate portion of the lever 87. The filler block 96 is pivotally secured to a slide 99 by a pivot screw 98 passing therethrough, and the slide 99 is in turn carried by a grooved plate100 fixedly securedto the inner. wall of the arm standard 2 by screws 101.

The slide 99 has rojecting therefrom an arm pivotal point up or down to vary the length of the stroke of its lower forked end, for purposes which will hereinafterbe more fully explained. It is evident that by loosening the knob 106, the slide 99 may be shifted to any desired position in the grooved plate 100 and secured in adjusted position by reclamping the knob 106.

In order to insure a construction in which the forked end of the lever 87 reaches identically the same position at the termination of each of its forward movements, which position is diagrammatically illustrated by the reference letter B in Figure 30, irrespective of the adi'ustment of its pivotal, point, the grooved p ate 100 is angularly secured to the inside of the arm standard2 atthe angle indicated by the line AB, Figure 30, and as shown in'Figure 1 along whichline the slide 99 is adapted to be adjusted, so that the axis of pivot screw 98 is in the plane of AB, regardless of its adjusted. position. p

A cylindrical cam, such .as. the cam 90, having a cam groove. in its periphery, in connection with a roller and lever both theoretically and practically, as the lateral walls of the cam groove areformed having a pivotal point as set. forth, Works incorrectly at all points at a straight angleto the longitudinal axis of the cam, while the lever moves in the arc of a circle and resents the roller '94 at an angle gradually c anging relatively to the lateral wallsof the cam.

groove. In order to obviate this objection, the roller 94 is made to travel in a true horizontal plane parallel to the longitudinal axis pf the cam 90 or shaft 3. In order to obtain this result. there are provided two levers 107 of equal length between their pivotal points, Figures 1, 7, 40, and 41, bent as required, and pivotally secured to lu s 108 on the arm 2. The opposite ends of the evers 107 have laterally projecting studs 110 secured thereto and entering suitable apertures in a horizontally floating compensating beam 111 having a central opening to receive the outer end of the stud 93.

Referring to Figures 1, 7, 8, 40, and 41, the working of the device will be clearly understood. The cam 90, during its rotation, will cause the lever 87 to move in one direction during 90 of rotation of. the cam, then rest for an equal number of degrees of rotation, then again move in the opposite direction for 90 of rotation, and thereafter again rest for a similarperiod. The compensating lever 111, being secured to the stud 93 at its intermediate portion, will necessarily follow the back and forth movements of the lever 87. This compensating lever 111, however, having pivotal connections with the levers 107, will cause these levers to swing in the arcs of circles, pulling with them in opposite directions the ends of the compensating lever 111, causin one end to move up while the other moves (Town with relation to the longitudinal axis of the cam 90, but maintaining the central portion of the compensating lever together with the upper end of lever 87 in the same horizontal plane. This is necessarily true, as the levers 107 are of the same length and the deviation of the one end of the-compensating lever 111 from the longitudinal axis of the cam 90 will be compensated for by an equal deviation in the opposite direction at its opposite end. The lever 87, to adapt itself to this movement, is permitted to slide up and down in the bearing provided therefor between the members 95 and 96.

During each rotation of the shaft 3, the upper end of lever 87 is moved in a fixed distance by cam 90, irrespective of the position of its fulcrum screw98, while the movement of the lower end and the movement of the rack slide 81 is determined by the position of the screw 98 along the longitudinal axis of lever 87 to which it is adjusted by the arm 102. It will be therefor appreciated that the throw of rack slide 81 can be varied by the up and down adjustment of fulcrum screw 98, whereby the size of the design. embroidered by the machine can be varied. This enables me to produceva-rious sized designs from the same pattern hereinafter described.

.The sole purpose of the pattern mechanism hereinafter described is to control the angular positions of slides 57 relative to the longitudinal axis of the machine or the lon' gitudinal center of the slide 81. This angularity of slides 57 determines the extent and direction of rotation of pivots or shafts 37 through their various connections, by the reciprocation of slide 81, which shafts or The gear 115 is preferably hubbed, as illustrated in Figure 6, and mounted on a'transversely extending shaft 116 journaled at its opposite ends in split bearings 117 secured to the ribs 42 of the bed plate by suitable fastening devices 118. The shaft 116 is provided with a keyway extending from one bearing 117 to the other.- and by means of a suitable key 119, the helical gear 115, a set of Six eccentrics or cams 120, and two collars or rings 121, are secured thereto. The shaft 116 is maintained against longitudinal movement by two collars 122, Figures 3 and 6, secured thereto by set screws or the like 123. As the helical gears are mounted on the shafts l6 and 116 at one to the other, they have a tendency to move the shafts in an endwise direction. To take up this end thrust, the shaft 16 is provided with a thrust ball bearing 124 and the shaft 116 is provided witha similar bearing 125.

Extending parallel to the shaft 116, and journaled in half bearings 126, also secured to the ribs 42, is a second transverse shaft 128 on which a set of six levers 129 are pivotally mounted for movement independently thereof. The levers 129 are formed with spacing hubs and are provided with vertically extending grooves 130, Figures 5.

and 6, in their longer ends to receive rollers 131 rotatably journaled therein to cooperate with the cams or eccentrics 120. The opposite or shorter ends of the levers 129 are narrowed to enter grooves 132, Figure 4, in the bell shaped brake shoes 133 loosely connected thereto by suitable pins 134. These brake shoes have on their upper faces cavities for the reception of fiber, leather, or

similar disks 135 adapted to produce a braking action on the disks 39, 61 and 183 (hereinafter described). The cams 120 and the levers 129 cooperating therewith are so positioned on their-respective shafts as to be in the same vertical planes with the axes of the ivots 37 and 60 and the gears 181 (hereina-1 ter described), as shown in Figures 4 an -6.

The distance between the shaft 116 and the shaft 128 is referably twice that which exists between t e shaft 128 and the axes of the pivots 37 and 60, whereby the leverage on the brake shoes is increased. These brake shoes are operated in such manner that they are intermittently in braking engagement with the disks 39 and 61 and the isks 183 (hereinafter described) secured to the gears 181; so that the pivots 37 and and said gears will be held stationary under the action of said brakes at different periods determined by the cams 120. These cams 1 20 are continuously rotating, and when a high portion orprojection thereon comes in contact with the rollers 131 of the levers 129, the opposite ends of the levers cause the brake shoes to press against the disks and prevent rotation thereof. When the 'low portions of the cams are effective on the rollers 131, the brake shoes are withdrawn by the action of light springs 136, and rotational movement of the pivots, the disks, and the parts to which they are connected, is permitted. The springs 136 each have one end thereof secured in the groove 130 of the levers 129, and their opposite ends engaged b a rod 138 maintained at the edge of the p ate'41 by means of suitable clamps 139 and screws 140, as shown in Figures 5 and 6. Between the levers 129 on the shaft 128 are mounted collars 141 to separate the levers and prevent displacement thereof.

For supporting the shaft 116, a roller 143- is loosely mounted thereon and journaled in a bracket 144 centrally secured to the under side of the bed plate 1. The shaft. 128 is likewise supported at its central portion by a split bearing 145 held on the plate 41- by fastening means 146.

In order that the pressure of the brake shoes on the disks may be conveniently regulated and adjusted to enable the same to be thrown out of contactwith the disks when a new fabric is placed in the tambour and manual shifting theerof is required or desired, the following means is provided: The shaft 128 has its. central and end portions eccentricallv reduced in diameter, as illustrated in Figure 6, and has one of the ec-, centrically reduced portions thereof extending beyond its bearing 126 and into enga ement with a crank lever 147. A suita le key'148 may be provided between the shaft and the crank 147, and the crank may be held inosition by a locking device 149-. The cran lever has a spring pressed device comprising a sleeve 150 secured thereto for rece ving a shouldered pin 151 detachably carrying a knurled knob 152 at one end, and.

having its opposite end projecting through an opening in the crank lever. The pin 151 is normal y maintained in projecting position by a suitable compression spring 153 engaging the shouldered portion thereof.

Between the crank lever 147 and the bearing 126 is provided a segmental plate 154, Figures 3, 6, and 13, having at one end an opening for the passage of the shaft 128 and atthe other end an elongated opening 155 to receive the protruding portion of the gin 151. The segmental plate is also prefera 1y provided with an arcuate opening 156 for adjustment purposes, the plate being held in adjusted position by a set screw 157. It will be evident that by slightly rotatin the shaft '128 it will be raised or lowere due to its eccentric portions, in proportion to the eecentricit and theamount of turning movement. T 1is enables the braking device to be lowered sufficiently to make it inopera- 'tive and release the tambour for manual shifting at will. When the shaft 128 is turned back and the pin 151 again put in engagement with the opening 155 in the adjustable segment plate .154, the braking device will again be operative. The adjustment just described, in combination with the releasing means is sufficient to give satisfactory results,;but it is preferred to combine therewith other means for regulating the pressure of the brakes, giving them a certain amount of resiliency or elasticity, and increasing their efficiency. This is accomplished by forming the end bearings- 126 and the middle bearings 145, as shown in Figure 6, with slightly elongated o e'nings tting'theshaft 128, as illustrate more particularlin Fi res 33, 35,- and I 37; Such elongate openings permit 100. a limited vertical movement of the shaft 128 independently of'the crank 147, the segmental plate 154 also being slotted to permit thismovement. The collars 141 which are adjacent the bearings 126 are formed with annular grooves 158. Dis osed in these grooves are the ends of sti springs 159 pivotally secured to the ribs 42 by screws 160. The opposite ends of the springs 159 engage short tension levers 162, pivotally mounted 1m formed on its base with grooves 164, Figure Il 34, to clamp the free ends of a spring 165. The bottom of the bearing is provided with a groove 166, to permit the opposite 'end of the'spring to bear against the shaft 128. The action of the springs 159 and 165 on the shaft 128 will cause the levers 129 to-resiliently press, with the rollers 131', against the cams 120, at one end, and with the brake shoes 133 on the disks, at their 0 posite 'ends. As the braking. action is timed by the cams 120, as illustrated diagrammaticall in Figure '29, to be effective alternately, e pressure of the springs will be evenly divided between the brakes which are in operative position only or, in other 130 words, those whose levers are in contact with the high portions of the cams 120. The levers 129 during inoperative periods will not be affected by the springs 159 and 165 as the rollers 131 thereof will be held in contact with the low portions of the cams 120 by the springs 136, with their brake shoes in lowered position. Due to the mounting of the levers 129; the pressure of the springs 159 and 165 with respect to the disks will be twice that exerted with respect to the cams 120. In order to render this supplemental means entirely independent of the adjustment and release effected by the crank 147 and its associated parts, the eccentrically reduced end portions of the shaft 128 are made sufficiently long to receive the collars 141, whereby the turning movement of the shaft 128 will have no effect on the collars.

The spring pressed device as applied to the brakes ma'y be varied at will, giving more or less the same result, and one modification thereof is illustrated in Figures 35 and 36. In this form of the invention, there are provided leaf springs 167, comprising any desired number of leaves, in place of the coiled springs 159. The springs 167 are pivotally secured to the ribs 42 by slotted pivots 168 through which the springs pass, and are adjustable by means of screws 169 passing through threaded bushings in the ends of the springs and abutting the plate 41.

The foregoing mechanism comprises that portion which for the sake of convenience has hereinbefore been termed the feeding mechanism. The portion of the mechanism comprising the pattern controlled feed predetermining' mechanism will now be described in detail.

The sliding members 57 are provided at their rear ends with studs 170 projecting downwardly therefrom and carrying rollers 171, Figures 5 and 7. These rollers 171 are in operative engagement with guide slots 172 of segments 173 Figure 6, having hubs 174, Figures 5 and 7, pivotally mounted in the plate 17 5 secared to the ribs 42 and lying in a plane below the plate 41. The seg ments 173 are maintained in such pivotal position by washers 177 and screws 17 8 threaded into the hubs 174. The sliding members 57 in their reciprocal movement cause the rollers 171 carried thereby to travel in the guide slots 172. The rear ends of the guide slots 172 are so positioned as to bring the axes of the studs 170 in line with the axes of the hubs 174 and screws 178 when the sliding members 57 reach their rearmost position and at which time the lower end of lever 87 is at point B of Figure 30, or at the other end of its throw from that shown in Figure 1. This permits the segments 173 during this time to be'swung without affecting the sliding members 57. .The segments '17 3 have downwardly projecting toothed portions 179, working in the cutaway portions 180 of the plate 41, and meshmg with gears 181 before briefly referred to. The gears 181 are preferably pivotally mounted on screws 182 threaded in the plate 41. The heads of the screws 182 enter suitable depressions in the gears so that they do not project therebeyond, as shown in Figure 5. To the gears 181 are secured disks 183,

slightly larger than the gears, on Which the central brake shoes 133 are intermittently pressed to brake said gears and consequently the segments 173 against any swinging movement. The opposite ends of the segments 17 3 are provided with elongated openings 185 in which work the upwardly projecting pin portions of the screws 186 secured to transverse slides 187. These slides 187 are in sliding engagement with a groove 188 formed in the rear ed e of the plate 17 5, at one side thereof, and 1n sliding engagement with a groove 189 formed in the front edge of a bar 190, at the other side thereof." The bar 190 is secured to the plate 175 by means of a supporting plate 191 secured to and overlying the plate 17 5 and projecting therefrom to support on its lower surface the bar 190. This supporting plate 191 is preferably cutaway in such manner as not to interfere with the pivotalmovement of the segments 173, as shown in Figures 3 and 6. Below each of the slides 187, and rotatably mounted on the screws186, is a roller 193, Figures 5 and 17, which rollers are in intermittent engagement with the ends of segmental curved levers 194 each having a pivotal mounting 195 on the plate 175. The levers 194 have intergeared portions 197 so that their free ends bothhave a simultaneously converging or diverging movement. One end of said curved levers has a projecting portion 198, Figure 3, ivotally connected with abifurcated block connection 201 with a second bifurcated block 202. Between the bifurcations of the block 202 is connected the lower end of a lever 203 having a pivotal connection 206 with a lug 205 projecting inwardly from the arm standard and formmg a part thereof.

The lever 203 derives movement from a cam 207 rigidly secured to the main shaft 3. The upper end of the lever 203 is provided with a cam roller 208 bearing on thecam 207. A tension spring 209 holds the cam roller normally in contact with the low portion of the cam 207, causing the segmental curved levers 194 to be normally in closed position, as shown in Figure 3. The function of the levers 194 is to move the segments 17 3 apart against the action of the tens on springs 210, Figures 3 and6, by bearing at their ends against the rollers 193, and then, during their converging or closing movement, to permit the segments 17 3 to gradually close under the 199. This block has a pivotal

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