US2893195A - Coil winding machine - Google Patents

Description

July 7, 1959 A. GREINER 2,893,195

COIL WINDING MACHINE Filed June 17 1958 5 Sheets-Sheet 1 TURNS PER mgu TURNS PER. mcH

SELECTOR 23 INVENTOR. 60mm @IZEWVEB.

BY FW A. GREINER COIL WINDING MACHINE 5 Sheets-Sheet 2 INVENTOR. flE/VO TeE/A ER July 7, 1959 Filed June 17, 1958 y 7, 1959 A. GREINER I 2,893,195

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/777UE/VEY- July 7, 1959 A. GREINER COIL WINDING MACHINE 5 Sheets-Sheet 4 Filed June 17, 1958 J a m 1 4% K k 0 1 6 w O Q 2/11 0 1 o 3 5 m 0 5 4 4 4 a A a INVENTOR. flz,v0 aka/v52 y 7, 1959 A. GREINER 2,893,195

COIL WINDING MACHINE Filed June 17, 1958 5 Sheets-Sheet 5 States Patent 2,893,195 com WINDING MACHINE I Arno Greiner, 'Irvington, N.J., assignor to Uwimco, Inc., Springfield, N.J., a corporation of New Jersey Application June 17, 1958, Serial No. 742,675 12 Claims. (Cl. 57-3) This invention relates to coil winding machines and more particularly to machines which wind a coil on a continuously fed mandrel. i

The coils made by the present invention are predominatingly' used as filaments for lamps, and it is consequently of great importance that the winding shall be uniform and made precisely witha predetermined number of convolutions or turns of filament per unit length of the mandrel. Heretofore attempts have been made to attain the specified number of turns by calculation of gear ratios determinative of the advancement of the mandrel in its relationto the number of revolutions of the winding head. Even with the most careful calculations and construction, theprior art machines often fail to produce the intended and. desired accuracy. Furthermore, in the prior art machines it is necessary to laboriously change the gears or, t.p.i. drums (abbreviation used in the trade meaning turns per inch) in order to obtain any change from a fixed number of convolutions of filament produced by the machine to any. other number of convolutions.

Basically, the present invention proposes a machine wherein extremely accurate precision of number of convolutions per unit length of the mandrel can be readily accomplished.

Of similar nature, the .invention proposesa construction permitting both adjustment and large change of the numbertof convolutionsby a readily manipulated means underoperator control, and. without requiring present-day elaborate calculations, or in fact, without requiring any calculations by the. operator or any mechanical replacement of gears or drums.

More specifically, the invention provides a machine wherein minute or other adjustment as 'well as large change of the convolutions per unit length of mandrel by direct reference thereto and by implication from the context.

Referring to the accompanying drawings, in which like numerals of reference indicate similar parts throughout the several views; 1

Figures 1 and 2 are side elevations of a machine, looking at opposite sides thereof, incorporating the present invention;

Figure 3 is a front elevation of the machine;

. Figure 4 is an enlarged fragmentary portion of the dial control for setting the turns per unit length on the mandrel;

Figure 5 is a sectional view on line V--V of Fig. 7;

Figure 6 is a sectional view on line VI-V1 of Fig. 5;

Figure 7 is a sectional view on line VII-VII of Fig. 5;

Figure 8 is a sectional view on line VIII-VIII of Fig. 5;

Figure 9 is a sectional view on line IX -IX of Fig. 5;

Figures 10 and 11 are corresponding sectional views on lines X-X and XI-XI respectively of Fig. 9;

Figures 12, 12a and 12!) are diagrammatic Views showing three different possible settings for the actuating on line XIV-XIV of in said drawings, the general organization-of the ma-- chine provides a hollow casting or housing 20 which contains essential portions of the mechanism, and on the outside of which a spool 21 containing a supply of mandrel wire 22 may be mounted upon a shaft 23 that extends from side to side of the housing and projects at one side to receive said spool 21, and projects at the other side to receive a reel 24 on which the finished prodnot is wound. At the top of said housing 20 is provided a Winding head 25 which is carried by and rotates with a tubular shaft identified in the trade as the winding spindle 26, parallel to the spool and reel shaft 23. The

justment or change just referred to above, to .be made i with the machine in motion or not in motion, and re-" quires no materialdelay in productivetoperation of the.

machine.

improved means obtaining forward motion only thereof and completely eliminating detrimental occurrences of hesitation thereof heretofore caused by gear back-lash and similar mechanical deficiencies.

In conjunction with the foregoing last-recited object, the invention also provides for applying desired tension in the mandrel wire-both in feeding the same to the coil winding head and in subsequent travel thereof to the reel on which the coil, with its mandrel, is wound.

A further important consideration of the invention is provision of one that is usable for winding a selected one of various sizes of coil wire on a selected one of various sizes of mandrel wires, thereby providing a machine of universal character. I a

The invention also in'corpora'tes an improved spreader appropriate sheaves and another t.p.i. drum and thence to the reel 24 under guidance of tracking mechanism 27 so as to be evenly wound in sequentially close convolutions and in successive layers on said reel.

For descriptive purposes, the winding head 25 includes a winding frame 28 which revolves with the spindle 26 around the axis thereof and may be considered at this stage of the description as operating at a constant rate and therefore the number of turns or convolutions of the coil upon the mandrel will be varied only by varying the forward rate of travel of the mandrel wire. An essen- 'tial feature of the present invention is provision of a An electric motor 29 mounted at the top of the hous- 4 ing 2!) proximate to what is herein termed the rear end of the machine, provides the actuating motive power, through a belt 30 and appropriate pulleys 31, 32 to a drive shaft 33 located'near the top; of: the; honslinrapproximately midway from front to. rear thereofand parallel to aforementioned shaft 23 and spindle 26; Said;

drive shaft 33 rotates at the selected ratingof the motor at. a constant speed and continuously-while themachine; is, in operation, but; to accommodate operation withdifferent sizes of wire, I prefer to'use a two-speed motor so as to use the machine either with one or the other;

of the selected speeds. Drive shaft 33 is-shown projecting at one side, here termed the; left side, of the housing, and there carries the belt pulley 32 in fixed position,

thereon so as to be driven thereby, Next to that pulley,

and meunted in the proximate wall of the housing vis. av

bearing 34 for the shaft 33 and within the-housingtis a fixed frame '35 providing, interalia, two other and spaced apart bearings-36, 36.; Fixed on said-drive shaft, between housing bearing 34-and; the most proximate of. frame:

bearings 36 are two adjacent drive gears which maybe distinguished by calling them respectively small drive gear: 37 and large drive gear 38 and constitute selective drive for speed; ofdrive. for the above-mentioned winding head 25 which will be hereinafter more fully described; Between the; pair of spaced apart bearings 36,

36 a worm 39 is fixed on said drive shaft 33. The small andlargedrive. gears 37, 38 and the worm- 39 accordingly will be subject to the selected speed'of themotor, and any change of-speed -of the motor reflects a corre-. sponding change of;speed of both of said drive gears and of the worm.

Worm 39 meshes with a worm wheel 40 therebelow.

(seefigs. 6" and7) whichis mounted: upon what will be termed an intermedi te -shaft41 that extends from the worm Wheel in a direction toward the rear of the housing and suitahlywjournaled in saidframe 35; At

the rear end of said intermediate shaft 41 is a bevelz.

gear 42 which is in, mesh with. a. driven bevel gear 43 on yetanother shaft 44 which for convenience in distinguish ing by terminology, willbe referred, to as 'theccam shaft since there, are two earns 45 thereon toward. oppositesides of thehousing from, driven bevel gear 43 as may.

beclearly seeninFig. 6. It will be understood that the camsha t; 44;and the intermediate shaft 41. are axially in a common: horizontal plane and are entirely within. the .housingand with the cam. shaft parallel to drive shaft 33 andv in constant rotation. from said drive shaft.

General mention hasrbeen made hereinbefore that the mandrel wire passes around appropriate t.p.i. drums.

More specifically, it may now. be stated that at the leftorfeeding side of the machine there is a multiple-groove jacent thereto with. the. wirefrorn one groove-- of thedrurn-going around the idler-and then back to another groove'of .the t.p.i. drum, making at least partial convolutions. in selected grooves of the drums so as to be positively driven and controlledin speed by said drums. T.p .i. drurns 46and 47 areboth ofthe same diameter and are-mounted on opposite ends of a drum shaft 49- that. extends through the housing 20 and projects at the sides thereof-near the front end. Said'drum shaft 49 is at about the same-levelas and parallel to afore-mentioned'cam-shaft 44 which is near the rear end of the housing so that said shafts have considerable distance between them.

The outstanding feature of the present invention comprises. means for effecting-continuous steady drive for said t.p.i. drum shaft 49 from the cam shaft 44, but with capability of adjusting or altering the speed of the drum 1 therefrom at thec-sidepofv the-.lever:

dewnriina-zthehousihgthan.'theclevel'ofiithe cam shaft 44: andrdru'rrr shaft .49 :andihas. a general directio'mfrom front shaft.v while the cam shaft continucsatits previousspeed. It has been stated that there are two cams 45 on the cam shaft, and now it maybe said that there are two gears 50 rotatably journaled on the drum shaft 49, and for reasons that will presently appear, these may be termed oscillating gears. Each of said oscillating gears has a one-way clutch 51 (see Figs. 6, and 9 to 11) connecting it to the drum shaft-49so thatwhenan oscillating gear 50 rotates in one direction it will actuate the drum shaft, but ,when the: gear, oscillates; inathe: other direction the clutch therefor releasesso' the. gear merely" rotates on said drum shaft without thenv actuatingit. One of said oscillating gears is driven by one of the earns 45 and the other of said.oscill'ati'ng v gears. is driven by the other one of the cams.

The driving connections for the oscillating gears is the same construction for each, so description of one Will-orifice fonbotll: Generally speaking, thetsaid driving connection is ilrthe nature ofsafwalking-beam. andaccords ingly comprises a lever 52 whiclrxisz'carriedibya-pivotrocl 53:1 transverse toi both; levers; and: located; medially between; thei'oppositezendsgofrthex levers="(see-'Figs .r..5. and 9'- 7 tall); Beyondrthe pivotal mouutingrofthe; lever, longitudina'lly' toward both ends, said lever-issbifurcateitthere byx-providingn;oppositely extending pairssof rails 54 conveniently kept fromnspreadingvby' end.:caps:.55. A slide, block. 5.6::is carriedeibetween each: pair; ofi-rails; so there. will -be one block at. onezlever. portion: beyon'dtthet pivot 53, toward; the front ofthe;.housing and: another. block at the-oppositesiderof'the-pivotinnthe:other end portiongof -the lever toward the rearzofthe; housing; Each slide block-s56 has a;. pivot-pin SCI-projecting.- laterally. Said-:lever islowen to. -re'ar; of; said; housing, so; the; CHdS':LOfi= said lever are located more. .or. less beneath: said's shafts.

Associatedrwith. each cam-45, is .a rocker 58 pivoted 3.13159 to frame35: and-.jhavingJan. arm 62 :at the side of the. cam with ascam-follower 670:. riding in thecam groove 61. That groove has a contour such that for partof. the :rotation of the cam, here ashown asone quadrant and designated-the inactiveportion ofithe complete ro-- tative cycle,=. ityactuates therrocker on areturn swing,

whereasanother andimuchi longer portion ofthecamgroove 61,, here shown, asthree quadrants and designated theu active portion. Ofith'. complete. rotation; hasia con-- tour which applies anadvancing: orrrdrivingr actuation to swing the rocker in a'direction opposite-tosaid return swing. By this construction,theactuationofone rockerin. the; return portion of its swinging. cycle-Willi prevail during-pa. part only .of the activerordriving portion of the cycleof. swing ofth'e other rocker,- and vieeversar Each:rocker. 58has an arm 63' projecting from: the pivot 5-9h-away from. both-said :pivot. and cam, and: according tothe present showing that: arm 63, whichis'-more or less: horizontal, has adownward 'driving -stroke"or swing due'=to;its cam (see Fig. 10) during-and in excess of the interval that the corresponding arm 63 of the-otherrocker '58 is on upwardlinactiveor returnportion of its swing-under actuation from-ifsrcam: Thus at all times,

one or. the other of 'said horizontal-1y proje'cting arms 63 isuoperating ina downwardor driving direction, and each with-said gear-segment 64st): that-as the gearsegment" oscillates up and'down under influence of the cam rocking the rocker, said rack'will have" a correspondingup and downbut guided straight-line.longitudinal motion. Said rack depends at the side of the afore-mentioned bifuirted lever 52 proxi'ma te to block 56and is trunnioned connection. therewith by pivot pin 57 projecting from said .blojck into said rack. Thus swing of the rocker imparts swinging actuation for said walking-beam lever 52.

- The other block 56 in the other. end portion of said lever 52 makes trunnioned connection by its pivot pin 57 with another rack 66 which also is vertically and slidably mounted to have straight-line longitudinal movement in the frame. There is, of course, a different rack 66 for eaohlever, and each is in mesh with a respective one of aforementioned oscillating gears 50. Cylinder 67 of the respective clutch 51 is fixed with respect to its oscillating gear, whereas the internal rotor 68 ,of both of the clutches are fixed on the drum shaft 49. The rotors have tapered pockets 69 next to the cylinders, and therein are rollers 70 which ,frictional ly wedge betweenthe rotor and cylinder when the cylinder rotates in one direction and release when the cylinder rotates in the other direction. This or any suitable type of oneway clutch may be employed, and by use thereof the clutches will each function to rotate the drum shaft upon upward movement of the rack 66 in mesh with and oscillating the respective oscillating gear 50. Downward movement of the rack 66 consequently applies no driving impetus to the drum shaft, and this inactivity occurs during the functioning of the above-described inactive or return portion of the swing of the corresponding rocker 58. The overlap of driving strokes of said rockers also applies to the oscillating gears, so said drum shaft is driven without intermission. It may now be said, furthermore, that the cam groove contours are such that theimparted rotation of the oscil- Zlating gears during the active or driving direction of oscillation applies a constant or even rate of movement :thereto so that the drum shaft has a smooth constant rate of rotation for any given setting of the speed-regulating mechanisms as well as for the selected speed of the motor.

One speed changing mechanism is a selective drive at either one or two speeds for the winding head obtained by utilization of large drive gear 38 meshing with a small gear 71 on tubular shaft or spindle 26, or by utilization of small drive gear 37 in mesh with a large drive gear 72 on said spindle 26. These two gears 71 and 72 on the spindle are on a common hub 73 slid-ably splined on said spindle and will be referred to as the small and large shift gears respectively. The hub 73 spaces the shift gears laterally far enough apart so that only one at a time can mesh with its respective drive gear, the spacing also being sufiicient to accommodate both of the driving gears between and free from the shift gears for a neutral or non-driven location. A suitable gear-shift mechanism is provided, and as here shown, a yoke 74 rides in a circumferential groove in hub 73 and projects upwardly to and secured on a slide rod 75 that extends parallel to the spindle to one side of the machine where it has a run 76 fixed thereon and to another rod, here called lockrod 77, parallel to and above slide rod 75. The rung 76 has a knob 78 at its outside for ease of manipulation. The lock-rod has three notches 79 at its upper side for receiving a latch 80 to hold said lock-rod in any one of three positions. The spacing of the notches is made to correspond to the proper movement of the shift gears to cause either one to register with its driving gear or to straddle both in neutral or non-driven position. There is thus a choice afforded of different rates of speed for rotating spindle 26, and as the winding head 25 is on that spindle, the choice of speed will determine the number of coils produced per rotation of the drive shaft.

It may here be noted that the winding head 25 provides a face-plate 81 fast on the spindle 26 so as to be rotated at the selected speed. Outwardly beyond the face plate 81 the hollow shaft projects far enough to rotatably carry thereon the bobbin of filament or wire to be wound onto the mandrel wire. Said bobbin is designated by numeral 82 and the wire therefrom by numeral 83. Projecting from, the face-plate 31 is winding frame 28 having guiding pulleys 8 4, 85 thereon for guiding passage of the wire 83 off of the reel and back down to the mandrel. As the frame revolves around the mandrel, coiling of wire 83 around the mandrel will be effected. This or any suitable winding head may be employed.

The important speed-changing mechanism featured in the present invention is one affecting the speed of travel of the mandrel wire at the selected speed of winding the filament coils therearound. In other words, the faster the mandrel wire feeds, the less number of filament coils will be wrapped around it per unit length of the mandrel wire, and vice versa the slower the mandrel wire moves, the greater will be the number of filament coils wrapped around it, on the premise of course that the coiling continues at the same selected speed. This speed changing mechanism is for the purpose of effecting change of speed of the mandrel wire only, and the range of change is such that the number of filament coils per unit'of length of the mandrel may be greatly. increased or diminished if desired, or may be changed only slightly for precise adjustment of coils per unit length. This change and/or adjustment of speed of the mandrel is obtained by varying the length of lever-arms of the walking-beam lever 52 between pivot 53 thereof to the respective pivots 57 of slide blocks 56 for racks 65 and 66. For this purpose, pivot rod 53 has both of its ends, as shown in Fig. 7, protruding from the sides of a carriage 86 riding in a trackway 87 that extends in the same general direction as the lever toward the front and rear of the housing, said trackways being formed as part of said frame 35 in the housing.

It may now be observed that whereas the total distance along lever 52 from one rack 65 to the other rack 66 always remains constant, the leverage length from the fulcrum of the lever to the respective racks may be varied by shifting the lever pivot 52. It is also a fact that the cam 45 always produces the same stroke S to its associated rack 65 as diagrammatically indicated in Figures 12, 12a and 12b. With the lever pivot 53 midway between the racks, both of said racks will have equal stroke, so that the stroke S of the second rack will then be an amount equal to S of the first rack, this condition being illustrated in Fig. 12. By moving pivot 53 closer to the second rack 66, as in Figure 12 the stroke S produced in that rack will be less than the constant length of stroke S of the first rack 65. Likewise when the lever pivot is moved from its midway position toward the first rack 65 as in Fig. 12b, the constant stroke of that rack will produce a greater stroke S in the second rack. The variable distances of the lever pivot 53 to the pivot pins 57 that connect the lever to the first and second racks are indicated in Figure 10 as variables r and r respectively. When r is shortened, the second rack not only has greater stroke, but has to accomplish that stroke in the same fixed time of the constant stroke of the first rack, and as a result the second rack has to move faster and thus will rotate the t.p.i. drum shaft 49 faster. When r is shortened, the second rack 66 has a shortened stroke and the rack moves slower and drives the drum shaft correspondingly slower. As adjustment of r and r may cover a wide range, the speed of the drum shaft may thus be changed minutely or greatly as desired and thereby obtain the corresponding change in movement of the mandrel.

Adjustment for lengths r and r is placed conveniently under the immediate control of the operator, so that should the count of number of coils per unit length of mandrel show a discrepancy from the desired number, the operator may make the change to the desired number in a quick and convenient manner without stopping the machine. In carrying out this feature of the invention, a horizontally disposed rack 88 is provided atone side of carriage 86 next to the top thereof and has a pinion 89 in mesh therewith which will be rotated by,

thexrack whenthe: carriage is niovedback andforth.

The pinion is ona vertical shaft 90 shown protruding" through'the: top of the housingandth'erehas abevelgear 91meshing with asimi'laribevelgear92'on a'hori- Zontal' shaft" 93 that: extends tothe. front'of'th'e machine' and on which is a dial 94-rotatable'. in a casing 951 The casing hasan. opening.96 for viewing the dial and has" -a setline. 97 for reading. thesetting shownon'the dial.

The dial is shown as having severahscales'thereon,'.one of which would apply, for instance, atone speed of the two-speedmotorandanother scale for the other speed of "the motor, and another scale would. apply for one location of the .gear shift and another scale for a differ ent location of gear-shift.

Adjiisted movement of'the carriage .is effected by a worm v98 that. rotates .in a nut 99 fixed on the bottom offthe carriage- The worm projects at the front of the housing, and appropriately retained from longitudinal taut to. the t.p.i. drumatthat side of the machine, and' for keeping the woundmandrel' taut inits approach to and winding upon its reel. Said shaft 23 isrotated in a direction to wind the wound mandrel on its. reel. and

therefore also in a direction which will tend. to wind;

the mandrel wire onto the spool, but the spool is adapted to rotate on said shaft permitting the wire to unwind therefrom. However, a.frictional engagement is maintained upon said spool so: as totake up any slack in the wire: as itfeeds to the t.p.i. drumt Morespecifically, the construction hereshown. comprises an arbor 1 rotatable: on said spooland reel shaft.23 and having an outside -diameter appropriate to receive the spool 21 thereon with. sufficient frictional contact so that the spool and arbor function as a unit. The inner end of the arbor has: aperipheral flange102 directedtoward an annular seat 103 fixed on: and rotatable with said shaft 23. A friction washer 104is interposed between saidseat and flange and frictional engagement is maintainedv by a spring 105 at. theou-ter end of the arbor held under compression by nutsv 106-v on the end of the shaft. the unwinding, of the mandrel wire from the spool rotates the spool counter to: the direction of rotation of the shaft, any slack in'the wire is immediately taken up by counter rotation transmitted to the spool from the shaft.

Similarly, at. the other end of the spool and reel shaft 23, is an arbor 107. rotatable thereon and receiving the. reel. 24 frictionally thereon. A friction washer 103- is interposed between the inner end of thearbor and an annular seat 109 fixed on and rotatable with said shaft 23. Frictional. contact of said Washer with the arbor and seat is maintained by a spring 110 at the outer end of .the arbor heldunder. compression by nuts 111 on theend .of the shaft. The diameter of the reel is madealarger than the t.p.i. drum 47 from which the. woundmandrel is-received, so the greater surface speed of the reel will keep the wound. mandrel under tension, slippage of the arbor on shaft 23 accommodating the difference. It. mayherebe noted that the spool and reel shaft 23 is driven by a gear 112 on the cam shaft 44 in mesh with an idler gear. 113 in turn meshing with a driven gear 114 fixed on-thespool and reel. shaft 23.

Tracking mechanism for guiding the filament-wound mandrel onto-the reel with the convolutions juxtaposed insequentialorder and successive-layers, acquires itsmotivation, from 'therreel arbor'107 vsothe: tracking will As here confornrto thexspeed tof-rotation of the reel. showngmthe reel arbor has amintegral'ring 115'at the 8.5. endthereof toward the housing and of: greater diameterthan the-reel,-themuter periphery of thering 'having wornr threads 116 thereon."- A worm wheel"117"(see Fi'g-. 3') meshes with sai worm threads-and through the agency- 11 of a -vertical axle 118 at the upper end ofwhich is a gear 119 (-see -Fig, 6-) drives an idler 1211 ('Figs. 6; l3 and l'4-)-' ingtur-n-im mesh with a gear 121 on a" vertical cam shaft" 122, on which b'oth 'said gear andaa cam 1 23' are rotat able. Afri'ction engagement 1-24 is1 interposed between" said 'gear- 1'2Iand'cam"1'23"by which the carn is-normally driven by rotation'of"thegear; The frictional engage---- ment 1-2'4= permits setting the cam to proper position for starting the tracking at the proper part of the reel. The cam rides against an arm 1'25"pivoted next to its rear end and swung toward 'the cam by a spring126.. A guide throat constituted byi-two parallel and proxi m'aterollers 127 depending from abracket 128 "at"the-- forwardly projecting end portionof said arm, is providedand as the wound mandr'ehpasses through said throat in' its approach to the reel, the gradual backand forth swing'of thearm will feed the wound mandrel 1 with successive convolutions close to each other. Pref erably the arm has a longitudinal slot 129 adjustably receivingga screw'130 which holds thebracket '1'28" on the arm, whereby the amplitude of swing of the throat maybe made more or lessagreeable to the requirements of the reel.

I claim: I

l. A coil winding machine comprising a tubular spin die, a revolvable: frame havinga path of rotation coaxial to said spindle, means for continuously advancing a man= drel through'said'spindle and out of a forward end thereof, a walking-beamactuatingsaid means, said frame .coiling a filament around saidmandrel where advancing from said spindle, andmeans 'forshifting'the fulcrum of said walking-beam and "thereby varying the rate of advancement of said mandrel from saidspindle for there? by varyingthe number of coils of filament applied'to said" mandrelper'unit length of advancement of said mandrel.

2. A coil. winding machine comprising a tubular spin dle, arevolvable-framehaving a path of rotation coaxial" to said'spind'le', means for continuously advancing amandrel through said spindle and outof a forward end thereof,v a pair of walking-beams with overlapping strokes applying continuous and constant rate ofactuation' to said means, saidframe coiling afilament around said mandrel where 'a'dvancing from said spindle;and means for shift.- ing the fulcrums of saidwalking-beams and thereby vary ing the'rate of advancement of said mandrel from said" spindle for thereby varying the number of coils of filament" applied to said mandrel perunit length of advancement of said mandrel;

3. A coil winding machine comprising a tubular spin-' die, a revolva'bl'e frame having a path of rotation coaxial to said'spindle,rotatingmeans for continuously advancing a mandrel through said spindle and out of a forward end thereof, said frame coiling a filament around said i mandrel where advancingfromsaid spindle, a Walking beam, a first reciprocating member at one end portion of the walking-beam always applying the same length of stroke thereto, a second" reciprocating member at the other endportion of. said'walking-beam actuating said rotating means, said walking-beamhaving a fulclum betweensaid first'and second members, and means for shifting the fulcrum of saidwalking-beamv with respect to said" first and .second'members and thereby varying the rate of advancementof said mandrel from said spindle for there-' by varying the number of coils of filament applied to said mandrel per unit length of advancement of said mandrel;

4. A coil winding machinecomprising a'tubular spindle, a revolvable frame having'a path of rotation coaxial to-said spindleg rotating meansfor continuously'advancinga mandrel through'sai'd spindle and out of a forward end thereof, said frame coiling a filament around said" mandrel where advancing from said 'spindle; az pair of walking-beams, a first reciprocating member at one end portion of one of the pair of walking-beams and another first reciprocating member a; a corresponding end portion of the other walking beam, both of said first members always applying the same length of stroke to its respective walking-beam, a second reciprocating member at the other end portion of one of said walking-beams and another second reciprocating member at the corresponding end portion of the other walking-beam, said second reciprocating members successively actuating said rotating means, said walking-beams having a fulcrum between said first and second members, and means for shifting the fulcrum of said walking-beams with respect to said first and second members and thereby varying the rate of advancement of said mandrel from said spindle for thereby varying the number of coils of filament applied to said mandrel per unit length of advancement of said mandrel.

5. A coil winding machine in accordance with claim 4, wherein each of said first reciprocating members is a slidable rack, and wherein there are two cams and two oscillating gear segments respectively actuated by said cams, said gear segments each in mesh'with a respective one of said racks for reciprocating the same.

6. A coil winding machine in accordance with claim 4, wherein each of said second reciprocating members is a slidable rack, and wherein there are two oscillating gears respectively in mesh with and actuated by said racks, said gears each having a one-way clutch on a common shaft and said shaft having the afore-mentioned rotating means for continuously advancing the mandrel mounted thereon.

7. A coil winding machine in accordance with claim 4, wherein each of said first reciprocating members is a slidable rack, and wherein there are two cams and two oscillating gear segments respectively actuated by said cams, said gear segments each in mesh with a respective one of said racks for reciprocating the same, and wherein each of said second reciprocating members is a slidable rack, and wherein there are two oscillating gears respectively in mesh with and actuated by said last-mentioned racks, said gears each having a one-way clutch on a common shaft and said shaft having the afore-mentioned rotating means for continuously advancing the mandrel mounted thereon.

8. A coil winding machine in accordance with claim 7, wherein a slidable carriage is provided carrying the fulcrum for said walking-beam, and wherein slide blocks are slidably mounted in said walking-beam and each pivoted to a respective one of said racks whereby sliding said carriage varies the length of lever arm of the walking-beam from the fulcrum to each rack.

9. A coil winding machine in accordance with claim 7, wherein a slidable carriage is provided carrying the fulcrum for said walking-beam, said carriage having a worm control for manually sliding the same, and wherein slide blocks are slidably mounted in said Walking-beam and each pivoted to a respective one of said racks whereby sliding said carriage by operation of said worm varies the length of lever arm of the walking-beam from the fulcrum to each rack.

10. A coil winding machine in accordance with claim 7, wherein a slidable carriage is provided carrying the fulcrum for said walking-beam, said carriage having a worm control for manually sliding the same, and a dial connected with and responsive to sliding motion imparted by said worm control to said carriage.

11. A coil winding machine comprising a tubular spindle, variable speed actuating means for advancing a continuous mandrel through said spindle out of a forward end thereof, a gear-driven winding head proximate to said forward end of said spindle adapted to coil a filament around said mandrel upon passage of the mandrel from said forward end of the spindle, a shaft adapted to mount a spool for feeding supply of mandrel and to mount a reel for the wound mandrel, said shaft rotating in a direction tending to wind the mandrel back onto the spool and to wind the wound mandrel onto the reel, and means permitting slippage of the spool on the shaft for withdrawal of the mandrel from the spool.

12. A coil winding machine comprising a tubular spindle, variable speed actuating means for advancing a continuous mandrel through said spindle out of a forward end thereof, a gear-driven winding head proximate to said forward end of said spindle adapted to coil a filament around said mandrel upon passage of the mandrel from said forward end of the spindle, a shaft adapted to mount a spool for feeding supply of mandrel and to mount a reel for the wound mandrel, means permitting slippage of the reel with respect to the shaft, and tracking means for feeding the wound mandrel to said reel, said tracking means having a drive coordinated to the rotation of the reel and its slippage.

References Cited in the file of this patent UNITED STATES PATENTS 1,094,047 Ames Apr. 21, 1914 2,706,376 Kerr Apr. 19, 1955 2,815,638 Curtiss et al. Dec. 10, 1957

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