US2181288A - Grid-making machine - Google Patents

Description

Nov. 28. 1939. H. M WASHBURN GRID-MAKING MACHINE 8 Sheets-Sheet 1 Qriginal Filed Oct. 26, 1936 1 11 067750 2 HENRY M MsH'Bu/N bio 3776i? Nov. 28, 1939.

H. M. wAsHBuRN GRID-MAKING MACHINE Original Fi1 ed Oct. 26, 1936 y 8 Sheets-Sheet 2 17106 1201 .figmy llMls/aau/w Nov. 28, 1939. H. M. WASHBURN GRID-MAKING MACHINE Original Filed 0ct.- 26, 1936 8 Sheets-Shet 3 Si Hi Inventor HEN/er M MSl/BURN 2.1s1,2ss

Nov. 23, 1939.

H. M. WASHBURN GRID-MAKINGMACHINE s Sheets-Sheet 4 Original Filed Oct. 26, 1936 Nov. 28, 1939. H. M. WASHBURN Gain-MAKING MACHINE Original Filed Oct. 26, 1936 8 Sheets-Sheet'S r .@N 0% WM IN W N H Nov, 28, 1939.

H. M. WASHBURN ham-MAKING MACHINE Olfiginal Filed 001;. 26, 1936 8 Sheets-Sheet 6 Patented Nov. 28, 1939 PATENT GRID -.MAKING MACHINE Henry M. Washburn, Newtonville, Mass, assignor to Raytheon Production Corporation, Newton, Mass, a, corporation of Delaware Application October 26, 1936, Serial No. 107,647

; Renewed April 21, 1939 27 Claims.

This invention relates to a novel grid-making machine adapted for the manufacture of the wound type-of grid electrode as used in radio tubes and other types of electrical space discharge devices.

An object of this invention is to devise a machine to produce wound grids in which the side rods are perfectly straight as they come off the machine, and which are ready to be assembled in a tube without further shaping or straightening.

Another object of my invention is to devise such a machine which is fully automatic, and which has a very large rate of output.

Other objects relate to the general improvement of the organization and arrangement of mechanisms of such a grid-making machine, including, among other novel mechanisms, an improved arrangement for feeding the grids through the machine and for severing completed grids, a novel arrangement for changing the driving speed so as to control the pitch and number of turns in the completed grids, a novel arrangement for supporting a rotating wire-carrying spool in dynamic balance, and a novel arrangement for enabling the machine to produce right and lefthand wound grids.

The foregoing and other objects of my invention will be best understood from the following description of an exemplification thereof, reference being had to the accompanying drawings,

wherein:

Fig. 1 is a front elevation of the machine; Fig. 2 is a section along line 22 of Fig. 1,

showing the drive of the back shaft;

Fig. 3 is a section taken along line 3-3 of Fig. 1, showing the cam mechanism for the cutter knives, swedges, and grid-straightening hammers;

Fig. 4 is a section taken along line 4-4 of Fig. 3, showing the clutch-actuating mechanismfor disengaging the cutter mechanism during the movement of the leg portion of the grid past the cutter position;

Fig. 5 is a plan view of the machine;

- Fig. 6 is a section taken along line 66 of Fig. 1, showing the winding head drive and part of the cutter-actuating mechanism;

Fig. 7 is a section taken along line of Fig.

1, showing the face of the winding head and the stripper timing switch;

Fig. 8 is an enlarged section taken along line 8-8 of Fig. 5, showing the construction of the winding head and-of the swedge mechanism unit;

g. 9 is a section taken along line 9-9 of Fig.

8, showing the cutter-actuating rocker arms and.

the grid arbor chuck;

Fig. 10 is a section taken along line Ill -i0 of Fig. 8, showing the face of the winding head;

Fig. 11 is a transverse section taken along line 5 llli of Fig. 8, showing the mechanism involving the cutter knives, the swedges, and the actuating hammers in relation to the grid and its associated arbor;

Fig. 12 is a back elevation of the machine; 19 i Fig. 13 is a'section taken along line l3-l3 of Fig. 1, showing the swedge mechanism unit;

Fig. 14 is a section taken along line M-M of Fig. 13, showing the adjustable swedge support;

Fig. 15 is a section taken along line I5-l5 of 15 Fig. 1, showing the lock and release mechanism for moving the swedge mechanism unit out of position for replacement of the. winding wire spool;

Fig. 16 is a section taken along line l6-'I6 of Fig. 1, showing the relationship of the various shafts mounted in the bearing plate at the front end of the pull-out feed unit;

Fig. 17 is an enlarged section taken along line l'iI|- of Fig. 1, showing one face of the front 25 pull-out feed carriage carrying the stripper mechanism;

Fig. 18 is .a section taken along line l8 -I8 of Fig. 17, showing further details of the associated mechanism; 30

Fig. 19 is an enlarged section taken along line l9-|9 of Fig. 1, showing the other face of the front pull-out feed carriage;

Fig. 20 is an enlarged section taken along line 2020 of Fig. 1, showing one face of the back 35 pull-out feed carriage;

Fig. 21 is a section taken along line 2I-2l of Fig. 20, showing further details of the associated 'mechanism;

Fig. 22 is an enlarged section taken along line 4 2222 of Fig. 1, showing the other face of the back pull-out carriage;

. Fig. 23 is an end view of the machine partly broken away, viewing the machine from the right Fig. 27 is a section taken along line 21-21 of Fig. 26;

Fig. 28 is an enlarged view of the grid arbor and the associated cutters, swedges, and gridstraightening hammers illustrating the formation of the grid;

Fig. 29 is a section along line 29-29 of Fig. 28; Fig. 30 is a completed grid substantially full size;

Fig.31 is an enlarged view of a swedged-joint between a grid turn and one of the side rods Fig. 32 is a plan section on line 32-32 of Fig. 1;

Fi 33 is a perspective view of the skip mechanism actuated during the winding of the loose turns on the grid;

Fig. 34 is an enlarged view of the winding wire lead-in plates;

Fig. 35 is a side view of the winding wire leadin plates;

Figs. 36 and 37 are two views of grids illustrating defects which tend to occur in, wound grids and which are eliminated by the present machine;

Fig. 38 is an enlarged view showing the relationship between the arbor, one of the side rods of the grid, and its associated swedge; and

Fig. 39 is a wiring diagram of the stripping mechanism.

The usual method of making wound grids at the present time is to cut a series of grooves in a pair of side wires, to wind a winding wire in these grooves, and to swedge the grooves over the winding wire. Grids made on the usual gridmaking machine inevitably are produced with distorted side rods so that a subsequent straightening process is necessary. This straightening process usually consists of hot stretching" the grids by heating the side rods to a relatively high temperature and giving them a slight stretch so as to straighten them out. This hot stretching produces an oxide coating on the grids, and tends .to bake other impurities thereon, which -oxides and impurities must be removed by hydrogen baking. This is not only expensive but unsatisfactory from various standpoints.

I have found that in machines which operate with relative rotation between the arbor on which the grid is formed and the swedging and cutting members, the side rods are given a twist or bow longitudinally which results in a curve of the side rods out of the plane of the grid, as illustrated in Fig. 36, which shows a completed grid viewed edgewise. I have found that the tendency for this type of distortion can be substantially eliminated by eliminating the relative rotation between the arbor and the cutting and swedging members, and causing the cutting and swedging members to contact with the side rods at the center thereof along the axis of the grid.

The elimination of the tendency to curve out of the plane of the grid still leaves a tendency for the side rods to curve in the plane of the grid, as illustrated in Fig. 37. This is probably due to the stretching of one side of the siderod during the cutting and swedging. I have provided mechanisms whereby this distortion of the side rods is also eliminated.

In the drawings, 3| designates the bed plate of the machine which is supported by the bed plate supports 32 and 33. On the bed plate 3| is mounted the two winding head-supporting standards 34 and 35. In these standards is mounted a support tube which is held stationary with respect to said support standards. 0n

the outer end of the support tube 36 is mounted a support block '31 which carries two brackets 38 and 39.- These brackets rotatably carry a pair of reels 40 and 4| from which are fed the side rod wires 42 and 43.

Arb r structure In the inner end of the support tube 36 is mounted the arbor 44 upon which the grid is formed. The arbor 44 has a shank 45 which fits tightly into an adapter 46, whereby the arbor is rigidly carried by said adapter. The arbor and its adapter are clamped in the support tube 36 by a split V-block 41. This split V-block is forced against" the adapter 46 by means of a set screw 49 which bears against the V-block base plate 48.

The set screw 49 is mounted in the main head 62 which is likewise carried by the support tube 36. The arbor 44 is provided with a pair of side grooves 50 in which the side rod wires 42 and 43 lie and through which they are fed into the gridforming position. As will be seen from Figs. .8 and 11, the inner ends of the arbor 44 and the arbor shank 45 are tapered so as to facilitate the threading of the side rod wires 42 and 43 into the grooves 50. The arbor 44 is slightly tapered so as to decrease in thickness toward its outer end. Since the minor diameter of the grid which is formed depends upon the thickness of the arbor in the grid-forming position, very fine adjustments in the exact diameter of the grid-can be secured by moving the arbor longitudinally in the support tube 36. The clamping arrangement-afiorded by the members 41, 48 and 49 permit this adjustment to be made. Of course it is to be understood that the substantial size of the grid is determined in each case by the size of the arbor which is readily removable from. the support tube 36 so that various sizes of arbors can readily be used.

Cutter mechanism Mounted at the sides of the arbor 44 are the two cutters 5|. The cutters are carried by hubs 52 which are received in hub blocks 53. The hubs 52 and consequently the cutters 5| are rotatably retained in the hub blocks 53 by means of a ballbearing backed by a spring and plug, as indicated at 54. The cutter hub blocks 53 are slidably mounted in the cutter slide carriage 55, whereby their position in said cutter slide carriage can be adjusted. The cutters are aflixed in their adjusted position by means of set screws 56. The cutter slide carriage is slidablysupported in the main head 62 by means of gibs 51 retained in place against the front face of the main head 62 by means of cover blocks 58.- In order to limit the motion of the cutter slide carriage 55, this carriage is provided with a pair of stops 60 between which is arranged a stop 59 which is formed as part of the lower cover block 58. The

cover blocks 58 are retained in place on the main head 62 by means of screws 6|.

Due to the above support arrangement, the two cutters 5| are adapted to slide as a unit back and forth in the plane of the grid, that is, in the plane in which the grooves 50 lie. In order to reciprocate the cutters 5|, a pair of rocker arms 64 push against two projections 63 formed on the back of the cutter slide carriage 55. The rocker arms 64 are mounted on the ends of two rocker arm shafts 65, which in turn are rotatably mounted in the main head 62. The rocker arm. shafts 65 project through the main head 62, and carry at the opposite ends thereof the two back link-actuating arm 69 in the forward position,

a takeup spring 68 is provided on each rocker arm link 61. Each link-actuating arm 69 is mounted on a cutter-actuating shaft 10. shown in Fig. 3, each cutter-actuating shaft 16 is driven by means of a cutter-actuating arm 1| mounted thereon. Each cutter actuating arm 3| drives its respective cutter-actuating shaft through an intermittent clutch mechanism, which will be described below. The cutter-actuating arms 1| are in turn driven by a cutteractuating cam 12, as shown in Fig. 3. The cutteractuating cam 12 is rigidly carried by a cambearing sleeve 13 onto which it is pressed tight. The cam-bearing sleeve 13 is rotatably mounted on the support tube 36. In order to drive the cutter-actuating cam 12, the cam-bearing sleeve has also pressed thereon a cam drive gear 14. As shown in Fig. 1, the gear 14 is in turn driven by a gear 15 which is mounted on the drive shaft 15 journaled in the support standards 34 and 35. The drive shaft 16 is driven from somesuitable source of motive power through a drive pulley 11 and drive belt 18.

Upon rotation of the drive shaft 16, the cutteractuating cam 12 is rotated through the gears 15 and 14, respectively. The cam 12 is provided at diametrically opposite points with a projection and a depression. Therefore, upon rotation of the cam 12, the cutter-actuating arms H are rocked back and forth once during each complete revolution of the cam 12. This in turn oscillates the slide carriage rocker arms 64 through the intermediary of the linkage, as shown on Fig. 6. The oscillation of the rocker arms 64 acting upon the projections 63 likewise oscillates the cutter slide carriage 55 carrying the cutters Since the rocker arm links 61 are driven by the link-actuating arms 69 through the intermediary of the takeup springs 58, any tendency of the 'cam 12 to over-drive the slide carriage is taken up by the pin-and-s'lot connection between the link-actuating arms 69 and the rocker arm links 61. This takeup is necessary since the travel of the cutter slide carriage 55 is limited by the stops 59 and 66. Upon the reciprocation of the cutters 5|, as described above, the cutters will cut notches 95 in the two side wires 42 and 43, as illustrated clearly in Fig. 28.

In order to compensate for different widths of arbors and to adjust for different depths of notches 95, the set screws 56 maybe released and the position of the cutter hub blocks 53 adjusted by means of adjusting screws 56, illustrated in Figs. and 11. The cutters are then retained in their adjusted down on the set screws 56. 7

Each grid which is formed contains a definite number of turns of wire which is rigidly connected by a swedging operation to the side wires 42 and 43. After the winding of a grid has been completed,'it is desirable that a few loose turns be wound around the side wires'42 and 43 before the succeeding grid is formed. The portion of the grid upon which these loose turns are wound is called the leg portion. During the travel of the leg portion of the grid past the cutters, it is desirable that the cutters shall be idle. In order to accomplish this I have proposition by tightening vided the cutters withv an intermittent drive mechanism, which includes the clutch arrangement between the cutter-actuating arm 1| and the cutter-actuating shaft 10, as mentioned above. This clutch arrangement is shown most clearly in Figs. 3 and 4. Each cutter-actuating arm 1| is mounted upon a hub 19, which in turn is provided with a recess 80 into which a tongue 8| of the sleeve 82 is adapted to be received. The sleeve 82 is rotatably mounted on the cutteractuating shaft 18, and is driven therefrom by means of' a sleeve 86 pinned onto the shaft 10. The sleeve 82 is provided with an elongated tongue 84 which fits into an elongated slot 85 in the sleeve 86. By shifting the sleeve 82 to the left in Fig. 4, the tongue 8| may be moved out of the recess 80, thus disconnecting the shaft 10 from the cutter-actuating arm 1|. In order to accomplish the shifting of the sleeve 82, it is provided with a circumferential groove 83 into which fit a pair of pins carried by a clutch throw-out lever arm 81 carried by the cross-shaft 88. This cross-shaft is mounted in bearings 89 carried by the base plate 3|. The cross-shaft 88 is rocked 'by means of a cam arm 96 cooperating with a clutch throw-out cam 9| driven from the main cam shaft 92. The driving mechanism for this cam shaft constitutes a special feature of this invention, and will be described below. As shown most clearly in. Fig. 5, the cam 9| is provided with a raised portion which pushes against the arm 90 once during each revolution of the main cam shaft 92, and thus disengages each cutteractuating shaft 18 from its respective cutteractuating arm 1|. During the time of this disengagement, the cutters are inactive and do not form any notches 95. The cam 9| is so disposed on the main cam shaft 92 that this disengagement occurs during the passage of the leg portion of the grid past the cutters. The cam 9|, as indicated in Fig. 3, is adjustable so that the initiation of the inactive period of the cutters and the duration of this inactive period can be varied at will. i

In order to avoid excessive wear and replacement of the cutters 5|, I provide each cutter in circular form with a continuous cutting edge around its periphery. I also provide means for continuously rotating the cutters so as to provide a new cutting edge to the side wires 42 and 43 for each successive notch 95. As shown in Fig. 7, this mechanism consists oftwo cutterrotating fingers 93 which are pivoted at one end to the upper cover block 58 and urged toward the cutters by means of a bias spring 94. Each cutter-rotating. finger 93 against the edge of a cutter 5| at a point slightly inside of the center. As the cutters are reciprocated back and forth underneath the fingers 93, a pawl-and-ratchet effect is produced which gives to each cutter 5| a series of thrusts which produces a slight rotation of each cutter between each cutting operation.

Winding mechanism I ,After the notches 95 have been cut into the side rod wires 42 and 43, a winding wire 96 is laid into these notches and wound around the side wires 42 and 43 so as to form the grid. In

.order to guide' the winding wire 96 into the frictionally bears are disposed around the arbor 44, as shown most clearly in Figs. 34 and 35. The winding. wire 96 is fed from a winding wire spool 98 over pulleys 99 carried by a pulley arm I06 mounted on the winding head I04. In order that the winding wire spool 98 be dynamically balanced, it is mounted concentrically with its axis of rotation upon three 'spool support pins I00 carried in the spool support ring IOI, as shown in. Fig. 8. The spool .support ring is rotatably mounted on three rollers I02 which are received in a pcripheral groove around the edge of the spool support ring, as shown in Figs. '7. and 8. The rollers I02 are in turn carried by the winding head I04. In order to place the proper tension upon the winding wire 96 as it is laid into the notches 95, there is provided a spool brake I03 which is likewise carried by the winding head I04. The spool brake engages the peripheral groove in the spool support ring I 0|. The pressure with which said brake bears upon the spool ring may be adjusted by the spring-and-screw adjustment I05.

In order to drive the: winding head I04, thereis formed integral therewith a gear I01. The winding head itself is rotatably mounted upon the main head 62 through the intermediary of ball bearings I08. One series of the ball bearings I08 is received in the ball race I09 formed on the main head 62. Another series of the ball bearings I08 is received in a ball race ring IIO which is adjustable along the main head 62. The ball race ring IIO may be locked in position by means of the lock nut III. The gear I0! is driven by a gear II2 mounted on the drive shaft I6.

Upon rotation of the drive shaft 16, the winding head I04 is driven through the intermediary of the gears H2 and I01. The winding head thereupon carries the pulley arm I06 around so as to wind the winding wire 96 around the side rods 42 and 43 and into the notches 95. The pull exerted by the winding wire 96 upon the winding wire spool 98 causes said winding wire spool, together with the spool support ring, to rotate in the rollers I02. As pointed out above, the proper tension is maintained -on the winding wire 96 by means of the brake I03.

Since' the winding wire spool 98 is mounted concentrically with its axis of rotation, it is at all times in dynamic balance independent of the amount of wire which it carries. Therefore, winding wire spools having large amounts of wire can be placed upon the machine without any inconvenience whatsoever, and thus decrease the idle time of the machine which arises from the necessity of replenishing the winding wire.

swedge mechanism After the winding wire 96 is placed in the notches 95, the notches are swedged around the winding wire 96 so as to rigidly fix the winding wire in the side rods 42 and 43. Thisswedging is illustrated in Figs. 28 and 31. In order to accomplish this swedging, I provide the machine with two swedges II3 on oppositesides of the arbor 44. As shown in Fig. 11, each swedge H3 is carried by a swedge hub II4 which is received in a swedge hub block II5. These swedges are rotatably retained in the swedge hub block II5 by means of an arrangement II6, consisting of a ball bearing backed by a spring and plug. The swedge hub blocks II5 areslidably mounted in the swedge slide blocks I I1. By adjusting the position of the swedge hub block H5 in the swedge slide block I I1, a coarse adjustment of the depth of the swedging operation is obtained. The swedge hub blocks II6 are retained in their adjusted position by means of set screws II8, as shown in Fig. 14. The swedge slide blocks are in turn slidably mounted in support blocks II9 which in turn are carried by the swedge assembly carriage I46 through an adjustable connection which will be described below.

Between the support blocks H9 and the slide 1 blocks III is provided an adjustable bearing I20 so that any wear in the bearing is readily compensated for, whereby the swedges are maintained accurately in their desired operating position.

In order to slide the blocks I I1 within the sup- 1 port blocks II 9 so as to bring the swedges II3 into contact with the side wires 42 and 43, and thus produce the swedging action referred to above, I provide the slide blocks II! with projections I2I, as shown in Figs. 11 and 13. Each 2 the carrier arm I23 which in turn provides for a 3 depth adjustment for each swedge and also for the hammer mechanism which will be described below. The actuating arm I25 has pivoted thereto a link I21 which connects it to an oscillating arm I28 pivoted approximately at its midpoint on' the swedge assembly support standard 282. The oscillating arm is extended at one end thereof, which end has pivoted thereto a connecting link I29 which is connected in turn to the rocker arm I30. The rocker arm I30 is carried on a 4 rocker arm shaft I33 journaled in the standards 34 and 35. Said rocker arm I30 is free to rotate around said rocker arm shaft. The rocker arm is driven through a driving arm I3I which is carried by the rocker arm shaft I33 and moves 4 therewith. The driving connection between the driving arm I3I and the rocker arm I30 is provided by means of an adjustable driving pin I32. Since the rocker arm I30 drives both impact arms I22, an adjustment of the driving pin I32 5 provides a simultaneous depth adjustment of both swedges and both hammer mechanisms. The rocker arm shaft I33 is oscillated by means of the swedge-actuating cam I35, as shown in Fig. 3. The driving connection between the cam 5 I35 and the shaft I33 is afforded by means of the swedge-actuating arm I34 rigidly connected to 'the shaft I33. The cam I35 is provided with a projection which by reacting upon the arm I34 oscillates the shaft I33 once during each revolu- 0 tion of said cam. The cam I35 is rigidly mounted upon the cam bearing sleeve 13 which, as described above, is driven by the gears I4 and I5 from the driving shaft 16, and thus is synchronized with the winding head I04. I! When the cam I35 is rotated, as described above, and the arm I33 is oscillated, each impact arm I 22 deals a blow to the respective projections I2I, which in turn slide the swedge slide blocks I I1 carrying the swedges II3 intoward 7 the side rods 42 and 43, thus causing the swedges I I3 to impart to the side rods 42 and 43 a swedging blow which swedges the side rods around the winding wire, as indicated in Fig. 28. Since both impact arms I22 are driven simultaneously by 1 Pivoted upon each 2 the same driving mechanism, the swedges likewise move simultaneously in toward the side rods and deliver their swedging blows on opposite sides of the arbor 44 at the same instant. Thus the thrusts upon the opposite sides of the arbor Ill and bearing against a plate I3I fastened tothe swedge slide support block H9.

In order to deactivate the swedges during the passage of the leg portions of the grids past the swedging position, each impact arm I22 is provided with a recess I38, and means are provided for raising each impact arm I 22 so as to bring said recess I38 opposite its respective projection l2I. Thus when the impact arms I22 are oscillated in their raised position, each projection I2I is received in a recess I38, and no impact blow is delivered thereto. Thus the swedges under these conditions are not actuated. In order to raise each impact arm I22, a link I39 is provided with an-elongated slot through which passes a pin which is rigidly connected to the lower end of the arm I22. Each carrier arm I23 is likewise provided with elongated slots through which the pins connected to the impact arm I22 pass so as to permit a sliding movement of the impact arm I 22 in said carrier arm I23. Each link I39 is pivoted at its lower end to a fulcrum block I40 carried by the bed plate 3I. Each link I 39 likewise has pivoted to it at an intermediate point an actuating link I4I, which in turn is pivoted at its lower end to an actuating lever I42. Each actuating lever is pivoted at an intermediate point thereon to a pivot block I43 carried by the lower face of the bed plate 3I.' Of course the bed Plate 3I is provided with openings, not shown, through which the actuating links I4I can project. The actuating levers I42 are driven by a swedge throw-out cam I44 which in turn is rigidly carried by the main cam shaft 92.

Upon rotation of the cam shaft 92 and the 'cam I44, the outer end of each actuating lever I42 is depressed when the raised portion of the cam I44 comes into contact therewith. Through the linkage described above, the outer end of each link I39 is raised, and thus each impact arm I 22 is likewise raised. In this manner the swedges are deactivated during the passage of the leg portion of the grid past the swedging position. As shown in Fig. 13, the cam H4 is adjustable so that the initiation of the'inactive period of the swedges and the duration of said inactive period may be varied at will. The slot-and-pin arrangements described above and shown most clearly in Fig. 13 permit the oscillation of the carrier arms I23 and the impact arms I22, in either the raised or lowered position of the links I39. After the raised portion of the cam I44 has traveled beyond the levers I42, each impact arm I22 is returned to its lower or active position by means of a spring I45.

As described above, the operating points on both the swedges and the cutters are oscillated in the plane passing through the centers of the side rods 42 and 43, and likewise strike the side rods at points lying in this plane. As described above, this arrangement substantially eliminates the tendency for the side rods to be distorted in the manner as indicated in 36. However, due

to inequalities in the arbor grooves, inequalities in the size of the side rods, wearing of the arbor grooves, and various other more or less obscure reasons, some tendency usually remains for the side rods to be bowed, as shown in Fig. 36. I have found that these slight residual tendencies can be compensatet for by adjustments of the swedges II3. In order to illustrate this action, reference may be had to Fig. 38. Theoretically the swedge I I3 is reciprocated along the line of the arrow d, and impacts one of the side rods 42 at the center thereof, indicated at the point a. If the side rod 42 asit comes from the machine is bowed in such a direction as to be concave at the left and convex at the right, I have found that if the swedge I I3 is shifted laterally in the direction toward the point D, the distortion can be eliminated and the side rod 42 will come off the machine perfectly straight Likewiseif the side rod 42 comes oif the machine with a concavity at the.

right and a convexity at the left of Fig. 38, shifting of the swedge II3 laterally to the left will eliminate this distortion. In shifting the swedge II3 laterally in either direction, its motion of travel during operation along the direction of the line dis undisturbed. The shifting merely causes the swedge to bear more heavily on one side or the other of the side rod 42, and thus compensate for the tendency to produce the distortions described.

The adjustment of the swedges H3, as described above, is accomplished in my machine by vertically adjusting the position of said swedges. As shown in Fig. 14, the swedge support blocks II9' are adjustably supported on the swedge assembly carriage I 46. The support block H9 is retained in place on said carriage I46 by means of screws I41 passing through elongated holes I49 There is provided a further adjustment so thatv the swedges may be adjusted laterally along the arbor 44 in order to bring the swedges exactly opposite the notches 95during the swedging action. In order to accomplish this lateral adjustment, each swedge assembly carriage I46 is adjustably mounted upon the swedge assembly frame I50, as shown" in Figs. 8 and 11. Each swedge assembly carriage I45 is also provided with a block I53 into which is tapped a microme-i ter adjustment screw II. Each micrometer adjustment screw is in turn rotatably carried bya yoke I52 mounted upon the swedge assembly frame I50. By rotating the micrometer adjustment screw I5I, the position of each of the swedges II3 laterally in the machine can be adjusted very gradually. The swedge assembly car-.

riage is firmly retained in this adjusted position by means of hold-down screws I54 whichpass through elongated slots in the swedge assembly carriage I46, and are tapped into the swedge assembly frame I 50.

The construction as described above, together with the adjustments therefor, eliminates the type of distortion as illustrated in Fig. 36. However, as stated above, a tendency still exists for the side rods to be bowed in the plane lying along the centers of the side rods, as illustrated in Fig. 37. I have found that if there is provided, as shown in Fig. 28, hammers I55 which strike the side rods 42 and 43 simultaneously with the swedges II3, the tendency for the distortion as illustrated in Fig. 37 is eliminated.- This effect produced by the hammers I55 is probably due to two reasons. First, the hammersmay actually bend the side rods 42 and 43 back into a straight condition after they have been bent out of this condition by-the action of the cutters 5I and the swedges II3. Second, by holding the side rods firmly in contact withthe arbor 44 during the time the swedging action. takes place, the side rods maybe held in their straight condition and be prevented from being bent out of that position by the swedges H3.

As shown in Fig. 11, the hammers I55 are adiustably mounted upon hammer hubs I56, which in turn are carried and pivoted upon the swedge assembly carriage I46. The hammers I55 are retained on thehubs I56 by means of screws I'51 which pass. through enlarged holes in the hammers I55, and are tapped into the hammer hubs I56. This permits the hammers to be adjusted both laterally and vertically for purposes to be described below. The hammers are actuated by hammer-actuating slides I581 which are retained in place on the swedge assembly carriages I46 by means of the cover plates I48. These hammeractuating slides are free to slide transversely in the swedge assembly carriages I46. The outer end of each hammer-actuating slide I58 is bent over to provide a portion which is adapted to be engaged bythe adjustable hammer-actuating pins I59. These hammer-actuating pins I59 are carried by the carrier arms I23. As described above in connection with the actuation of the swedges N3, the carrier arms I23 are constantly rocked back and forth by a linkage connected with the rocker arm shaft I33. As each carrier arm I23 is rocked back and forth, the pin I59 strikes the end of the hammer-actuating slide I58, and thus pushes the hammer I55 into enagement with the side rods 42 and 43. As the pins I59 leave the slides I58, the hammers I55 and the slides I58 are pulled away from the arbor 44 by the springs I60. Since each pin I 59-is independently adjustable, the intensity of the stroke of each hammer can be independently varied.

I have found that if all the curvature is not taken out of the side rods by means of the adjustment of the swedges II3, any slight residual curvature may be entirely eliminated by adjustmg the hammers I55 which have a convex impact surface, both laterally and vertically, along the side rods 42, which acts to eliminate said curvature in the same manner as indicated for the swedges H3 in Fig. 38. Such adjustment, as pointed out above, is provided by the screw and enlarged hole arrangement between the hammers I55 and the hammer hubs I56.

By proper adjustment of the swedges and hammers in the mechanism which I have described above, the completed grids which leave the arbor 44 are perfectly straight, and when ejected from the machine are ready to be assembled in tubes without any, further straightening action.

Pull -out feed mechanism In my machine I have provided a novel arrangement for feeding the grids through the machine so as to make the action of the machine entirely automatic. This feed mechanism comprises two pull-out feed carriages I 6I and I81 have mounted thereon a plate I82.

which alternately engage the side rods 42 and 43 with the winding wire wound thereon, and pull the grid structure through the machine in the manner as will be described below.

The front pull-out feed carriage I6I includes a carriage frame I62 which is mounted upon outer bearing sleeves I14. Each outer bearing sleeve I14 is in turn slidably mounted upon an inner bearing sleeve I15, which in turn is slidably mounted upon a bearing rod I16 carried by the front and rear-bearing plates I11 and I18. One of the outer bearing sleeves I14 carries a cam portion I19, as shown in Fig. 33. The inner bearing sleeve I15 associated therewith carries a cam portion I80. Intermediate the two cam portions 119 and I is located a spreading member I8I.. This spreading member is rotatably mounted upon the exterior of said inner bearing sleeve I15. The spreading member I8I when actuated produces a skip action which will be described below. However, the spreading member I8I in the position as indicated in Fig. 18, merely acts as an intermediate thrust member between the'inner and outer bearing sleeves I15 and I14. Thus as the inner bearing sleeve I16 is moved along to the right in Fig. 18, the outer bearing sleeve I14 is likewise pushed along to the right, and thus the front pull-out feed carriage IN is moved in the proper direction for feeding the grids .through the machine.

In order to produce the feeding mdvement of the inner bearing sleeves I15, said bearing sleeves The plate I82 carries a split nut I63 pivoted at one end thereof to the plate I82, as shown in Fig. 17. A biasing spring I64 connected to the other end of the split nut I63 biases the two halves thereof so as to clamp the lead screw I65. The drive of this lead screw also constitutes a novel feature of my invention, and will further be described below. Thus, when the lead screw I65 is rotated, the split nut I63 will be carried forward along said lead screw, and this in turn will move the front pull-out feed carriage in a forward-direction to feed the grids through the machine.

In order for the front pull-out feed carriage to engage the grids, it is provided with a pair of clamp slides I68 which are supported so as to slide vertically on the front carriage frame I62, as indicated in Fig. 19. In order to actuate the clamp slides, a clamp slide lever I61 is pivoted at one end to each of said clamp slides I66. The other endof each of the clamp slide levers I61 is pivoted on the front pull-out carriage frame I62. Each lever I61 has pivoted at an intermediate point thereon a link I66, which in turn is pivoted to a bell crank I69 carried by and adapted to rotate on the front carriage frame I62. The

bell crank I69 is provided with an arm I10 and is actuated by means of a cam rocker arm "I mounted upon a rod I83 carried by the front and rear bearing plates I11 and I18. Since the carriage I6I travels along the machine and the rocker arm IN is stationary, said rocker arm is provided with an extension face 2I0 extending along the machine, as shown in Fig. 5. The outer end of the arm I10 is provided with a roller which permits easy motion along the extension face 2I0. The extension face 2I0 is carried by -an arm which likewise is mounted upon the rod I83. In order to provide for different thicknesses of wire, for wear on the cam slides I66, and for adjustment of the clamping action, an adjustment thrust pin I12 is provided between the rockerarm HI and the arm carrying the extension face 2). The rocker arm "I is actuated by means of a riser cam I13 mounted upon the main cam shaft 92, as shown in Fig. 17. As the cam shaft 92 revolves in the direction as indicated by the arrow and the end of the rocker arm IN is pushed up by the raised portion of the cam, as shown, the arm I10 of the bell crank lever will be rotatedso as to cause the clamp slides I66 to clamp the grid between them. In this way the grids are effectively clamped by the front pullout feed carriage IBI, and are carried along by the carriage I8I as it.travels forward along the machine. Thus, during the forward travel of the front feed carriage I 6| the grids are advanced through the machine. The clamping action of the clamp slides I66 is so adjusted that the clamping takes place on a leg portion of the grid.

Thus any distortion which occurs on the winding wire 96 does not injure the grids inasmuch as this portion of the winding wire is later stripped from the grid and is discarded. As the cam shaft rotates further, the rocker arm I1I drops from the raised portion of the cam I13, and a retracting spring I91 pulls upon the arm I18 of the bell crank, and thus rotates the bell crank so as to pullthe clamp slides I68 away from the grid and thus release the grid. As will be described below, just prior to this release, theback pull-out feed carriage will have engaged the grid and will continue the feed action thereof through the machine.

As indicated in Fig. 39, between the tight or normal turns 241 of the grid there are wound a few loose turns 249 on the leg portion of the grid.

Since the loose turns 249 are subsequentlyv stripped off and thrown away, the wire of these loose turns is wasted. Therefore it is desirable to increase the pitch of the turns 249 so as to waste as little Wire as possible. In order to produce this action, the grids are advanced through the machine at a more rapid rate during the time that the loose turns 249 are wound on the side wires 42 and 43. This increased rate of feeding is produced bythe skip mechanism to which I have referred briefly above. This skip mechanism includes the spreading member I8I between the two cam portions I19 and I88 on the two bearing sleeves I14 and I15, as shown, for example, in Fig. 33. During a part of the time when the front feed carriage IGI is feeding the grids through the machine, the spreading member I8I is rotated so as to quickly separate the front carriage frame I62 from the plate I82. The spreading member I 8| is actuated during this time by means of a pull rod I84. The actuation of the pull rod I 84 is produced by means of a tension spring I85 which tends to pull upon the pull rod I84 and rotate the spreading member I8I so as to produce the skip action described. The action of the spring I85 is restrained by means of a cam I86 mounted upon the main cam shaft 92. As the cam I86 rotates in the direction as indicated by the arrow in Fig. 19, the end of the pull rod I84 drops from the raised portion of the cam to the depressed portion thereof, whereupon the spring I85 exerts its tension upon the pull rod I 84, and thus rotates the spreading member I8I so that it quickly separates the two cam portions I19 and I88, and thus rapidly advances the front carriage frame I 62 along the machine. Due to.

this action, the rate of feeding of the grid through the machine is increased, and thus the pitch of the wire 96 wound on the side rods 42 and 43 is increased.

The length of the leg portion of the grid can be adjusted by adjusting the distance which the spreading member I8I advances the frame I62. This distance can be adjusted by adjusting the amount of rotation of the spreading member I8I. As will be seen from Figs. 18 and 33, the further the member I8I is rotated the farther apart the cam surfaces I19 and I80 will be forced which in turn determines the skip travel of the frame I62.

In order to provide this adjustment, the depressed portion of the cam I86 is set sufficiently deep toprovide for the maximum travel of the pull rod I84 and consequently of the spreading member I8I. The pull rod I84 is usually stopped beforeit reaches the bottom of 'the depressed portion of the cam I86 by the stop 295 cooperating with the adjustable screw 296. The stop is mounted on the pull rod I84 and the screw is tapped into a block carried by the bed plate 3|, as shown in Fig. 19. By adjusting the screw 296, the amountwhich the pull rod I84 travels under the action of spring I85 may be adjusted. In this way the rotation of the spreading member I8I and consequentlythe length of the leg portion of the grid can be adjusted.

The cam I 86 isso arranged that the rotation of the spreading member I8I occurs during the passage of the leg portion of the grid past the wind ing po'sitionl The spreading action, as described above, occurs only duringthe time that the pull rod I84 drops from the raised to the depressed portion of the cam I88. Subsequent to this action, the plate I82 will cause the front carriage frame I62 to be moved along the machine at the normal rate. After the back feed carriage has taken control of the feeding of the grids and the clamp slides have released the grid, the cam I 86 pushes upon the rod I84 and moves it into the position as shown in Fig. 19, during which time the spring I85 is put under a tension so as to be ready for its next spreading operation. At this time the spreading member I8I is returned to its position, as shown in Fig. 18, by means of a retracting spring 288, as shown in Fig. 17. Upon return of the spreading member I8I to the position as shown in Fig. 18, the front carriage frame I62 is pulled back toward the plate I82 by means of a tension spring 294, as shown in Fig. 33. This reestablishes therelationship between the front carriage frame I62 and the plate I82, as'shown inFig. 18. The pull rod I84 is slidably retained on the base plate 3I while the front feed carriage carrying the spreading member I8I moves along the machine with respect thereto. In order to permit this relative motion and still maintain the operative relationship between the pull rod I84 and the spreading member I8I, said pull rod is provided with an extension. face 289, which extends along the machine a sufficient distance to be maintained in operative relationship to the spreader member I 8| which is provided with a roller at its outer end so as to permit easy motion along the extension face 289. The'return of the front carriage frame I62 to its original position will be described below.

The back feed carriage I81 which takes control of the feeding'of the grids through the machine clampthe lead screw I65, whereby the back feed carriage is advanced along the machine." The back feed carriage is also provided with clamp slides I9I slidably mounted upon the frame I88, as shown in Fig. 22. The edge of the lower clamp slide I9I is sharpened to produce a cutting edge. In this way the clamp slides I9I constitute not only a clamp but also a cutter which severs the grids after they have been completed and are ready to be ejected from the machine. The clamp slides are actuated by means of levers I92 which are pivoted at one end to the slides I9I and at the other end to the frame I88. Intermediate the ends of the levers I92 are pivoted connecting links I93 which in turn are pivotally connected to a bell crank I94. The bell crank I94 is supported upon and adapted to rotate in the frame I88. The bell crank I94 is provided with an arm I95. The arm I95 is actuated to cause the clamp slides I9] to engage the grid by means of a cam rocker arm I98, which drives an actuating arm 292 through an adjustable driving pin I 99, whereby adjustments may be made for different sizes of grids and .also for wear on the clamp slides I9I. The arms- I98 and 292 are also mounted upon the rod I83. The rocker arm .I98 is in turn actuated by a riser cam 299 mounted upon the cam shaft 92. As shown in Fig. 20, when the cam 299 rotates in\the direction as indicated by the arrow, the first raised portion of said cam which comes into contact with the arm I98 moves said arm so as to actuate the bell crank I94,

and thus cause the clamp slides I9I to clamp the grid, whereby the back feed carriage may feed said grid-through the machine. During this feeding operation, the clamp slides I9I engage the grid to such an extent that the cutting edges thereof extend about half way through the side wires. The cam 299 is so related to the cam I13 that the slides I99 clamp the grid just prior to the release of the grid by the clamps I66 of the front feed carriage. After the back feed carriage has substantially completed its feeding motion along the machine, the rocker arm I98 comes into contact with a cam face 29I on the cam 209. This causes an additional actuation of the rocker arm I98 which moves the-clamp slides I9I an additional amount sufficient to shear through the side rods, and thus cut off the completed grid. As shown in Fig. 1, the machine may be provided with a trough 258 into which the completed grids drop and through which they may be 7 removed from the machine. In order to prevent the back feed carriage from dropping the severed end of the incomplete grid which is being fed toward the back feed carriage, it is provided with a grid-centering guide 292, as shown in Fig. 20. Although this guide does not clamp the grid, it slidably supports the same during the period of time in which the clamp slides I9l are retracted from the sides of the grid.

When the front feed carriage has completed its feeding travel through the machine, the clamp slides I66 are released as described above. In order to permit the front feed carriage to be returned to its original position, the split nut I63 is released from the lead screw I65 by means of a spreader 293. This spreader consists of a tongue which extends between the two halves of the split nut, as shown in Fig. 17, and which when rotated spreads the two h'alves of the split nut against the action of the biasing spring I64.

The spreader 293 is pivoted in the plate I82, andis provided with a spreader arm 294. The spreader 293 is actuated by means of its arm 294 from a lever 295 which is pivoted on a shaft 296 carried by shaft brackets 2| 3 which are mounted on the lower face of the bed plate 3|. The lever 295 is provided with an actuating spring 291 which tends tov rotate the lever 295 so as to actuate the spreader 293 to release the split nut I63.- The action of the spring 291 is restrained by means of a push rod 298 which is'slidably supported on the bed plate 3|. The outer end of the push rod 298 rides upon the closing cam 299 which is likewise carried on the main cam shaft 92. As the cam 299 rotates in the direction as indicated by the arrows in Figs. 17 and 19, theend of the push rod 298 drops off the raised portion of the cam onto its depressed portion, whereupon the actuating spring 291 pulls upon the lever 295 and rotates the spreader 293 so as to separate the two halves of the split nut I63, This action releases the front feed carriage from the lead screw I65, whereupon the front carriage is ready to be returned to its initial position. The cam 299 is so shortly after the clamp slides I66 have released the grid. In order to produce relative sliding motion between the lever 295 and the spreader arm 294, the lever 295 is provided with an extension face 2 I2 extending along the machine sufficiently so that the lever 295 is maintained in active e'ngagement with the arm 294 throughout the travel of the front feed carriage I6I through the machine.

In order to return the front feed carriage to its original position, areturn thrust rod 2I4 is slidably mounted in the rear bearing plate I18, as shown, for example, in Fig. 1. The inner end of the thrust rod 2I4 engages the end of one of the outer bearing sleeves I14. The outer end of the'thrust rod 2I4 is provided with a head 2I5 against which a rocker arm 2I6 is adapted to push. 'The rocker arm 2I6 is journaled upon a stub shaft 2I1 carried by brackets 2I8 mounted upon the bed plate support 33. The rocker arm 2I6 has pivotally connected thereto a link 2I9 which in turn is pivoted to the end of a cam rocker arm 229. The cam rocker arm 229 is journaled at its lower end on a stub shaft 292. Rocker arm 229 carries a roller 22I which is adapted to cooperate with a return cam 222 carried by the return cam shaft 223. The return cam shaft is carried by brackets 293 mounted upon the bed plate support 33. As shown in Fig. 25, the return cam shaft 223 is driven by a right-angled gear 224 which engages a right-angled gear 225 mounted upon the main cam shaft 92. As the cam shaft 92 rotates and drives the return cam shaft 223, the cam 222 pushes upon the roller 6 221, thus rocking the arm 222 to the left. This causes the rocker arm 2 I6 to push in against the inner end of the thrust rod 2I4 pushes upon the end of the bearing sleeve I14 which returns the front carriage I62 to its original position. Also through the intermediary of the spreading meihher I 8|, the plate I82 carrying the split nut I63 head 2l5 of the thrust rod 2I4, whereupon the rod 209 riding up onto the raised portion of the cam 209, whereupon the lever 205 releases the spreader 203. Due to the relationship between the ends of the split nut I63 and the spreading member 203, as shown in Fig. 17, the biasing spring I64 forces the spreading member 203 to rotate back into the position shown in Fig. 17, and also causes the two halves of the split nut I63 to clamp the lead screw I65, whereupon the front carriage is then again fed along the machine. Just after this action, the clamping members I66 clamp the grid as described above.

After the back feed carriage has completed its feeding and severing action, as described above, it is released from the lead screw I and returned to its original position. In order to release the back feed carriage from the lead screws I65, the split nut I 89 is likewise provided with a spreader 226, as shown in Fig. 20. This spreader is mounted on a spreader arm 22'! provided at its end with a roller which rolls along an extension face 229 of a lever 228. The lever 228 is journaled on the bearing shaft 206 which, as described above, is carried by the shaft brackets 2I3. The lever 228 is actuated by a tension spring 230 which pulls upon the lever 228 and causes the spreader arm 22'! to actuate the spreader member 226 to separate the two halves of the split nut I89, and thus release the back carriage from the lead screw I65. The action of the actuating spring 230 is normally restrained by the push rod 23I which is slidably mounted on the bed plate3l. The outer end of the push rod 23l rides upon the closing cam 232. When the end of the push rod 23I is on the raised portion of the cam 232, the split nut is maintained in its clamping position on the lead screw I65. However, when the end of the push rod 23I drops down on the depressed portion of the cam 232, the actuating spring 230 is permitted to come into operation, whereupon the split nut I89 is released from the lead screw I65, as described above. This release occurs just after the clamping members I9I have completed their severing operation.

After the split nut I89 has been released from thelead screw I65, the back carriage is returned to its original position by a thrust rod 233 which is slidably carried by the rear bearing plate 211, as shown, for example, in Fig. 1. The inner end of the thrust rod 233 bears against one end of one of the bearing sleeves 290 while the outer end is provided with an operating head 234 against which a rocker arm 235 is adapted to push. -The rocker arm-235 is journaled at its lower end on the stub shaft 2I'I, and is connected by means of a link 236 to the cam rocker arm 231. This cam rocker arm is journaled at its lower end on the stub shaft 292. The rocker arm 231 is provided with a roller 238 which cooperates with a return cam 239 which is mounted upon the return cam shaft 223. As the return cam shaft 223 is rotated from the main cam shaft 92 through the gears 225 and 224, as described above, the cam 239 pushes against the roller 238 and thus actuates the rocker arm 235 which pushes upon the thrust rod, and thus machine, each carriage clamping the grid just prior to the release by the other carriage and thus overlapping in cycle. are fed continuously. Since each carriage need travel only a distance slightly greater than one- As a result the grids half the length of the individual grid, the overall Stripping mechanism.

Before the grids are completed, the loose turns I 249 illustrated in Fig. 39 must be removed from the grid. In accordance with present-day practice, this is usually done after the grids have been removed from' the machine. The present arrangement, however, affords a mechanism whereby this severing or stripping is accomplished automatically. In order to accomplish the stripping, the machine is provided with two electrodes 240 mounted as shown in Figs. 17 and 18. The electrodes 240 are carried by electrode arms 24I insulated therefrom. The arms 24I are pivotally mounted on the front carriage frame I62, and are provided with extensions 242 which are adapted to contact with the actuating cam 244. Each electrode arm 24I is provided with a biasing spring 243 which urges the electrodes The cam 244 is pivotally mounted upon the front carriage frame I62, and is provided with a cam arm 245, the outer end of which contacts the actuating pin 246 mounted upon the arm "0 of the bell crank I69. Thus when the arm I10 is actuated so as to clamp the grid between the clamp slides I66, the electrodes 240 are brought into contact with the grid, as will be more clearly pointed out in connection with Fig. 39. As shown in this figure, each grid consists of a series of normal turns 241 swedged at points 248 to the side wires 42 and 43. Between the normal turns 241 are wounda few loose turns 249. The electrodes 240 contact with the first and last loose turn at a point very near the respective side wire 42 or 43. The machine itself is grounded, as indicated at 250. Each electrode 240 is also provided with a conductor 25I which leads through a transformer secondary 252 to a ground 253. Each secondary 252 is also provided with a primary winding 254 connected by means of a main. switch 25I-to some suitable source of alternating current. Each primary 254 is controlled by a switch 255. After the electrodes-240 have come into contact with the loose turns of the grid, the switches 255 are closed, whereupon the primary and secondary windings 254 and 252 are energized. Upon the energization of the secondary windings, current passes from each electrode 240 through a short length of winding wire to one of the side rods. The current passing through this small portion of the winding wire burns it away, and thus it leaves it disconnected from the tight portion of the wound grid. This leaves all of the loose turns 249 free so that when the grid is severed, as pointed out above, these loose turns will fall off. I have found that the voltage of the secondary windings 252 may be between three and ten volts, five volts being a good working average for most kinds of wire. Of

course it is to be understood that during this action the switch 251 is in its closed position.

In order to actuate the switches 255 at the proper time, these switches are mounted upon the bed plate 3|, as shown in Fig. 7, and are each closed by means of a switch cam 256 mounted upon the cam shaft 92. Thus, by orienting the cam 256 upon the cam shaft 92, the closure of the switches 255 takes place at the proper time, that is, shortly after the electrodes 240 have come into contact with the loose turns of the grid.

Driving mechanism As previously pointed out, the driving mechanism for the cam shaft 92 constitutes a special feature of this invention. In order to drive the cam shaft, as shown in Fig. 2, the drive shaft 16 carries a gear 259 which engages a gear 260 mounted upon the back shaft 26I which extends throughout the length of the machine and thus is carried by the support standards 34 and 35 and the bearing plates I11. and I18. The opposite end of the back shaft extends through the stationary bearing 261, as shown in Figs. 1 and 5. As shown in Figs. '23 and 24, at the opposite end of the machine from the gear 260, the back shaft carries the epicyclic gear train pinion plate 262. This plate has mounted thereon to one side thereof, the pinion gear 263. This pinion gear meshes with a gear 264 rotatably mounted upon the stationary bearing 261, as shown in Figs. 1 and 5. N on-rotatably mounted upon the stationary bearing 261 is a stationary gear. 265 differing from gear 264 by one tooth. The gears 264 and 265 are of the same diameter. The gear 263 also meshes withthe stationary gear 265. Due to the fact that the gears 264 and 265 differ from each other by one tooth, as the back shaft 26I is rotated, the gear 264 is advanced one tooth for each rotation of said back shaft. Connected to the gear 264 and floating on the back shaft and stationary bearing 261 is the floating sleeve 266,

which at its inner end carries a gear 268 having the same number of teeth as 264. Thus the gear 268 rotates in synchronism with-the gear 264. As shown in Figs. 23 and 24, an intermediate gear 269 meshes with the gear 268, The'gear 269 is mounted -upon an arm 210 which is swiveled about the shaft 2,6I as a center. The arm 210 is provided with an adjustment link 21I which is provided with an elongated slot through which passes a lock bolt 212 carried by the support 33. Thus the gear 269 may be moved to a limited ex tent around the back shaft 26I and locked in its adjusted position by means of the lock bolt 212. Meshing with the intermediate gear 269 is the main cam shaft change gear 213 which is rigidly mounted upon the main cam shaft 92. The adjustment of the intermediate gear 269, described above, is necessary to take care of various sizes of the change gear 213.

As pointed out above, the winding head I04 is driven fromthe drive shaft 16 which also drives the back shaft 26I. The gear ratios are so adjusted that the winding head I04 makes one complete revolution for each revolution of the back shaft 26I'. However, the main cam shaft 92 determines the formation of individual grids; that is, during each complete revolution of the cam shaft 92, a complete grid is formed. The number -of turns of winding wire in a complete grid is therefore determined by the number of revolutions which the winding head I04 makes for each revolution of the cam shaft 92. The driving mechanism for the cam shaft described above affords a particularly flexible and simple control for the number of turns in each complete grid. Since, as has been pointed out above, the gear 264, and consequently the gear 268, advance one tooth for each revolution of the back shaft 26I, said gears 264 and 268 will also advance one tooth for each revolution of the winding head I04. Since the gear 268 through the intermediary of the gear 269 drives the cam shaft 92, the number of revolutions which the winding head or the back shaft 26I makes for each revolution of the cam shaft 92 will be determined by the number of teeth in the main cam shaft change gear 213. Thus, simply by selecting a change gear of a certain number of teeth, the grid will have that number of turns. Therefore, by my arrangement, the number of turns in the grid may be determined by a very rapid and simple adjustment of the machine. In order to permit adjustment of the position of various parts of the machine, when it is not being driven, the back shaft 26I is provided with a hand wheel 21I.

As pointed out above, the drive of the lead screw I also constitutes a special feature of this invention. In order to drive the lead screw I65, the back shaft 26I, as shown in Figs. 5 and 12, is provided with a gear 215. This gear, asshown in Fig. 24, meshes with an intermediate gear 216 which is carried on an arm 211 swiveled about the back shaft 26I as a center. The arm 216 is also provided with an adjustment link 218 having an elongated slot through which passes a lock-down bolt 219 received in the support 33. Therefore, the position of the intermediate gear 216 around the back shaft 26I can be adjusted and said gear can be locked in its adjusted position by means of the lock bolt 219. The lead screw I65 is provided with a lead screw change gear 280 which is engaged by the intermediate gear 216.

This results in the fact that the gear 280 advances one tooth for each tooth on the gear 215. By replacing the gear 280 with other size gears, a very fine adjustment of the speed of travel of the lead screw I65 can be secured. The adjustment of the gear 216 is necessary in orderto take care of various sizes of the gear 280.

Winding spool replacement In order to replace the. winding wire spool 98, the assembly carrying the swedges and hammers is mounted so as to rotate out of place in front of the winding head, whereupon the winding wire spool may he slipped off the pins I 00 and replaced by a full spool.

As shown most clearlyin Fig. 15, in order to accomplish this rotation, the swedge assembly frame I50 is pivoted on a pivotpin 28I mounted in the swedge assembly support standard 282, which 'in turn is carried by the bed plate 3|. The swedge assembly frame I50 is normally locked in position by means of a locking handle 284 pivoted at one end thereof on the swedge assembly frame I 50. The locking handle normally locks behind a plate 283 which is mounted upon the swedge support standard 282.

If it is desired to release the swedge assembly from in front of the winding head, it is merely necessary to raise the outer end of the locking handle 284, whereupon the swedge assembly frame may be rotated out of position. Inasmuch as all of the drive for the swedges and the hammers occurs through impact members rather than through any direct connection, this rotation can be accomplished without disturbing the driving members.

Retersal of grid winding In some instances it may be desirable to reverse the direction in whichthe winding wire iswhich drives the winding head and also with the gear H2 which. is mounted on the drive shaft 16. The gear H2 is provided with a set screw 285 so that it may be slid along the drive shaft 16 for a limited distance and set in its adjusted position. Normally the gear 281 is removed from the stub shaft 286 and the gear H2 meshes with the gear I01 to drive said gear and winding head directly as discussed above in connection with the normal drive of the winding head. To accomplish the reversal of winding, the gear 281 is mounted on the stub shaft 286 and the gear H2 is slid out along the drive shaft 16 so that it is no longer in direct engagement with the gear 101, In this position the drive shaft 16 drives the gear I01 8 through the intermediary of the gears H2 and 281, respectively. Under these conditions the gear ill! will be driven in the reverse direction from that in which it was driven directly by the gear H2.

This invention is not limited to the particular details of construction as described above, as many equivalents will suggest themselves to those skilled in the art. For example, grids of the type having but a single side rod could be made upon such a machine, in which case but a single cut-' ter, swedge and hammer need be employed. It is accordingly desired that the appended claims be given a broad interpretation commensurate with the scope. of the invention within the art.

What is claimed is: v 1. In a grid-making machine, a substantially stationary' windingarbor having a supporting surface to support a side rod upon which a winding wire is to be wound to form a grid, cutting means for cutting notches in said side rod, 'into which notches said winding wire is adapted to be laid, swedging means for swedging said rod upon said winding wire, and means for moving said cutting and swedging means into engagement with said side rod to deliver cutting and swedging strokes respectively to said rod, said cutting and swedging means being mounted to move in a direction to deliver the force of said cutting and swedging strokes along a llne'passing substantially through the center of said side rod.

2. In a grid-making machine, a substantially stationary winding arbor having a pairof supporting surfaces at opposite sides thereof, each to support a side-rod upon which awinding wire is to be wound to form a grid, cutting means for cutting notches in said side rods, into which notches said winding wire is adaptedt'o be laid, swedging means for swedging said rods upon said winding wire, and means for moving said cutting and swedging means into engagement with said side rod to deliver cutting and swedging strokes respectively to said side rods, said last-named means normally moving said cutting and swedg ing means in a direction to deliver the force of said cutting and swedging strokes along a line passing substantially through the center of the associated side rod.

3. In a grid-making machine, a substantially stationary winding arbor having a pair of supporting surfaces at opposite sides thereof, each to support a side rod upon which awinding wire is to be wound to form a grid, cutting means for cutting notches in said side rods, into which notches said winding wire is adapted to be laid, a pair of swedges for swedging said rods upon said winding wire, means for moving saidcutting means to deliver cutting strokes to said side rods, and means for moving said swedgesto deliver swedging strokes to said side rods, both of said last-named means normally moving said cutting means and swedges in a direction to deliver the force of said cutting and swedging strokes along a line passing substantially through the center of the associated side rod. r

4. In a grid-making" machine, a winding ar bor, having a supporting surface to support a side rod upon which a winding wire is to .be wound to 'form a. grid, a cutterforcutting notches in said side rod into which notches said winding wire is adapted to be laid, a swedge for swedging said rod upon said winding wire, means for causing said cutter and swedge to deliver cutting and swedging strokes respectively to said side rod, and holding means adapted to engage said side rod at a point adjacent to the point at which said swedge 'comes into contact with said siderod, said holding means holding said side rod in intimate contact with the supporting surface of ing wire around an elongated side rod wire to form a .grid, feeding means for advancing said side rod with said winding wire thereon through said machine, cutting means for cutting notches in said side rod, intowhich notches said winding, wire is adapted to be laid, swedging means for swedging said rod upon said winding wire, means for moving said cutting and swedging means into Y engagement with said side rod todeliver cut ting and swedging strokes respectively to said side. rod, said strokes tending to'bend said side,

rod out of a straight line, and means for bending said side rod in a direction reverse to that of the bend due to said cutting and swedging means an amount suflicient to cause said side rod to be straight.

6. Ina grid-making machine, a grid-forming mechanism adapted to wind and secure a winding wire around an elongatedside rod wire to form successive grids, feeding means for continuously advancing said side rod with said winding wire thereon through said machine, a cutter for cutting notches in said side rod into which notches said winding wire is adapted to be laid, a swedge for swedging said rod upon said winding wire, means for causing said I cutter and swedge to deliver cutting and swedging strokes respectively to said side rod, said strokes tend-- ing to bend said side rod out 'of a straight line, and means operating during'the continuous feeding of said side rod for bending said side rod in a direction reverse to that of the bend due to,

cause said side rod to be straight.

having a supporting surface to support a side rod upon which a winding wire is to be wound to form a grid, a cutter for cutting notches in said side rod into which notches said winding wire is adapted to be laid, a swedge for swedging said rod upon said winding wire, means for causing said cutter and swedge to deliver cutting and swedging strokes respectively to said side rod, said strokes tending to bend said side rod out of a straight line, and a straightening member for delivering straightening strokes to said side rod after the cutting and swedging thereof, wherebysa'id side rod in the completed grid is straight.

'8. In a grid-making machine, a winding arbor having a supporting surface to'supportqa side rod upon which a winding wire is to be wound to form a grid, a cutter for cutting notches in said side rod into which notches said winding wire is adapted to be laid, a swedge for swedging said for delivering straightening strokes to said side rod after the cutting and swedging thereof, said straightening member being adapted to contact said side rod and hold it in intimate contact with the supporting surface of said arbor during swedging.

9. In a grid-making machine, a winding arbor having a supporting surface to support a side rod upon which a winding wire is to be wound to form a grid, a cutter for cutting notches in said side rod into. which notches said winding wire is adapted to be laid, a swedge for swedging said rod upon said winding wire, means for causing said cutter and swedge to deliver cutting'and swedging strokes respectively to said side rod, said means normally moving said cutter and swedge in adirection to deliver the force of said' cutting and swedging strokes along a line passing substantially through the center of said side rod, said strokes tending to bend said side rod out of a straight line, a straightening member for delivering straightening strokes to said side rod after the cutting and swedging thereof, and means for moving said straightening member in a direction to deliver the force of its straightening blows along a line passing substantially through the center of said side rod.

10. In a grid-making machine, a Winding ar-' bor having a supporting surface to support a side rod upon which a winding wire is to be wound to form a grid, a cutter for cutting notches in said side rod into which notches said winding wire is adapted to be laid, a swedge for swedging said rod upon said winding wire, means for causing said cutter and swedge to deliver cutting and swedging strokes respectively to said side rod, said means normally movingsaid cutter and swedge in a direction to deliver the force of each of said cutting and swedging strokes along a line passing substantially through the center of said side rod, and means for adjusting said swedge transversely with respect to said side rod to shift the direction of the force of the swedging strokes through said'side rod to one side of the center of said side rod.

11. In a grid-making machine, a winding arbor having a supporting surface to support a side rod upon which a winding wire is to be wound to form a grid, a cutter for cutting notches in said 7. In a grid-making machine, a winding arbor side rod into which notches said winding wire is adapted to be laid, a swedge for swedging said rod upon said winding wire, means for causing' said cutter and swedge to deliver cutting and swedging strokes respectively to said side rod; said means normally moving said cutter and swedge in a direction to deliver the force of each of said cutting and swedging strokes along a line passing substantially through the center of said side rod, said strokes tending to bend said side rod out of a straight line, a straightening member for delivering straightening strokes to said side rod after the cutting and swedging thereof, means for moving said straightening member in a direction to deliver the force of its straightening strokes along a straight line passing substantially through the center of said side rod, and means for adjusting said swedge and straightening member transversely with respect to said side rod to shift the direction of the force of the swedging and straightening strokes through said side rod to one side of the center of said side rod.

12. In a grid-making machine, a winding arbor having a supporting surface to support a side rod upon which a winding wire is to be wound to form a grid, a cutter for cutting notches in said side rod into which notches said winding wire is adapted to be laid, a swedge for swedging said rod upon said winding wire, means for causing said cutter and swedge to deliver cutting and swedging strokes respectively to said side red, said means normally moving said cutter and swedge in a direction to deliver the force of each member for delivering straightening strokes to said side rod after the cutting and swedging thereof, means for moving said straightening member in a direction to deliver the force of its straightening blows along a line passing substantially through the center of said side rod, means for adjusting said swedge and straightening member transversely with respect to said side rod to shift the direction of the force of the swedging and straightening strokes through said side rod to one side of the center of said; side rod, and means for adjusting said straightening member longitudinally along said side rod with respect to said swedge.

13. In a grid-making machine, a winding arbor having a supporting surface to support a side rod upon which a winding wire is to be wound to form a grid, a cutter for cutting notches in said side rod into which notches said winding wire is adapted to be laid, a swedge for swedging said rod upon said winding wire, winding means for carrying the winding wire around said side rod and winding said wire upon said side rod, feeding means for advancing said side rod with said winding ,wire thereon through said machine. and means for deactivating said cutter and swedge during predetermined intervals to prevent said cutter and swedge from contacting said side rod during said intervals, whereby the turns of said winding wire wound on said side rod during said intervals are left loose.

14. In a grid-making machine, a grid-forming mechanism adapted to wind and secure a winding wire around an elongated side rod wire to form successive grids, two feeding members for feeding said side rod through said grid-forming mechanism, said feeding members being con-

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