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Title:
Spring coiling machine
United States Patent 2119002
Abstract:
The present invention relates to spring coiling machines of the type adapted to intermittently feed predetermined lengths of wire for coiling into springs of different forms, the completed springs being severed in the intervals between successive operations of the feeding devices. Spring coiling...


Inventors:
Bergevin, Charles R.
Nigro, Arthur C.
Publication Date:
05/31/1938
Assignee:
TORRINGTON MFG COMPANY
Primary Class:
Other Classes:
72/138, 72/145
International Classes:
B21F3/02
View Patent Images:
Description:

The present invention relates to spring coiling machines of the type adapted to intermittently feed predetermined lengths of wire for coiling into springs of different forms, the completed springs being severed in the intervals between successive operations of the feeding devices.

Spring coiling machines of this general character are known in the trade as universal coilers, by reason of the ability of such machines to produce springs of different forms, that is, springs with either open or closed convolutions, of barrel or cone shape, or with portions of different diameters. In order to obtain the desired variations in spring forms, it is necessary to be able to ad-15 just the tools controlling the pitch and diameter of springs being coiled, as well as the wire feeding and cut-off mechanisms, and a machine having these general capabilities is shown in Sleeper Patent No. 1,266,070, issued May 14, 1918. The object of the present invention is to provide a universal coiling machine of the above indicated type, which is characterized by the provision of readily accessible means for adjusting the spring forming tools, as well as the cut-off and feeding devices. In a machine embodying the present invention, it is possible for the operator to stand at a point where he can readily observe the actual formation of a spring by the coiling tools, and at the same time, conveniently reach devices for adjusting the tools controlling the pitch and diameter of the spring being coiled.

It is also possible for the operator, without changing his position, to adjust the coiling arbor, as well as the cut-off tools, with reference to the line of wire feed, as determined by the grooves of the feed rolls. The above and other advantageous features of the invention will hereinafter more fully appear from the following description considered in connection with the accompanying drawings, in which:Fig. 1 is a view in front elevation of the coiling machine.

Fig. 2 is a side elevation of the machine of Fig. 1, as viewed from the left.

Fig. 3 is a vertical sectional view illustrating the drive for the feed rolls.

Fig. 4 is a fragmentary plan view, showing a detail of the cut-off tool adjustment.

Fig. 5 is a sectional view along the line 5-5 of Fig. 4.

Fig. 6 is a fragmentary view in section, illustrating the mounting of the tool holder.

Figs. 7 and 8 are fragmentary views in front elevation and plan, showing a modification in 5s the manner of mounting a rotatable coiling point, Referring to the drawings, the machine consists of spaced upright frame members I and 2 mounted on a suitable base 3, with the various wire feeding and coiling tools mounted on the front frame member I, and the several mechanisms for driving all of the tools mounted between the members I and 2. The line of feed for the wire 4 is indicated by the arrow in Fig. 1, the wire being fed through a preliminary guide 5 to cooperating pairs of feed rolls 6, 6 and 7, 7, which rolls project the wire forward for operation upon by the coiling tools. Wire guides 8 are provided between the feed rolls 6 and 7, as well as between the feed rolls and the coiling tools, and both the rolls and guides are provided with grooves of different sizes, so that a considerable range of wire sizes may be fed into the machine without necessitating any change in the associated rolls and guides.

The feed rolls 6 and 1 are carried by shafts 9, journalled in the frames I and 2 and bearings I0, for the upper feed roll shafts 9 are capable of slight vertical movement. A bowed spring II with its ends resting on the bearings 10 and a cooperating hand wheel 12 mounted on a threaded stud 13 enables pressure to be applied to the bearings 10 through the spring I , and so press the upper feed rolls upon the wire 4, as supported by the lower feed rolls. The feed roll shafts 9 are geared together for synchronous rotation, as shown in Fig. 3, and are adapted to be driven intermittently in one direction of rotation in a manner hereinafter described.

As the wire is gripped between the feed rolls 6 and 7 and is fed forward, it passes over or under an arbor 14, and against a coiling point 15, which deflects the wire down or upward, according to the adjustment of the coiling tools, to produce either a right or a left-hand spring.

The arbor 14 is carried by a tool holder 16, hereinafter more fully described, and a pitch tool 17 is also mounted on the holder 16. The function of the pitch tool 17 is to deflect the coil after it has been formed, and to give to it the necessary pitch, or space, between adjacent convolutions, to which end the pi-;h tool is movable within the holder 16. A guide 18 is mounted on the holder 16, to prevent the wire from bowing between the end of the feed roll guide 8 and the coiling point 15, and the relative positions of the pitch tool 17 and guide 18 San be reversed on the holder 16, in order to provide for the coiling of a left-hand spring instead of a right-hand spring, as shown.

In the formation of a spring, the wire is fed forward against the coiling point 15 by the feed rolls 6 and 7, and is thereby deflected around the arbor 14. The amount of this deflection and consequently the diameter of the coil, is determined by the relative positions of the coiling point 15 and arbor 14, and the invention provides means whereby the coiling point 15 may be adjusted, and its movement during the coiling operation readily controlled. After a coil has been formed, the'pitch tool 17 presses against the end of the coil in such a manner as to deflect the wire continuously into a series of spirals of the required pitch, and the adjustment of this tool 17, as well as its movement during coiling, is also 16 provided for, in accordance with the invention.

As soon as the rolls 6 and 7 stop, following the feeding of a predetermined length of wire, cutting tools I9 come into operation to effect the severing of the wire at the arbor 14. The cutting tools 19 are mounted on oscillatory heads 20 above and below the arbor 14, and when right-hand springs are being coiled, the lower tool 19 is mounted in its head 20 so as to cooperate with the arbor 14 in cutting the wire. The upper tool 19 is then held to an inactive position, and is only brought into operation when forming left-hand coils. As will hereinafter appear, the heads 20 carrying the cutting tools 19 ar adapted to be ted oscillated in unison, and means are provided for shifting the heads 20 along the axis of coiling, so as to cause the tools 19 to cooperate properly with the arbor 14, as it may be positioned to receive wire from any particular set of grooves in the feed rolls 6 and 7.

Having thus described the general function and operation of the essential tools entering into the formation of springs, as well as their desired adjustments, there will next be described, in the order named, (a) the feed roll drive, (b) the tool holder mounting, (c) diameter control, (d) pitch control, and (e) cut-off tool adjustment.

Feed roll drive The machine is driven from any suitable source 45 of power, such as a motor 21 connected by a belt 22 to a pulley 23. As best shown in Figs. 2 and S3, the pulley 23 is adapted to be connected to a shaft 24 by means of a clutch 25 operable by a fork 26 connected to a lever 27 mounted at the front of the machine. The pulley shaft 24 extends into a housing 28 containing selective change speed gearing 29 of any suitable type, through which rotation of the shaft 24 is converted into rotation of a drive shaft 30, at different speeds. A handle 31 is provided for operating the gearing 29.

The shaft 30 extends through the housing 28 and carries a pinion 32 in mesh with a gear 33 mounted on a shaft 34. The gear 33 carries a gear 35 of smaller diameter, which is in mesh with a gear 36 mounted on a cam shaft 37, see Fig. 2, to drive the shaft 37 continuously, for operating the coiling tools and cutters, in a manner hereinafter described. Rotation of the gear 33 is also adapted to be converted into intermittent rotation of the feed roll shafts 9 by an adjustable crank connection and gearing, so designed as to control the wire feed, within a wide range.

To this end, the front face of the gear 33 carries a crank block 38, adjustable'between ways 39, and providing a crank pin 40, on which is mounted an anti-friction bearing 41. As best shown in Fig. 1, the outer raceway of the bearing ,. 41 fits between the parallel-walls of a slot 42, provided in a gear segment 43 pivoted on a rock shaft 44. Therefore, circular motion of the gear 33 is transmitted through the crank pin 40 and bearing 41 to the segment 43 without appreciable friction, and causes the segment to oscillate across the face of the gear 33, the amplitude of movement of the segment 43 being proportional to the distance that the pin 40 is positioned away from the axis Of the shaft 34, on which the gear 33 is mounted. Teeth formed on the outer circumference of the segment 43, engage the teeth of a pinion 45 loosely mounted on a shaft 46 parallel to the feed roll shafts 9 that the pinion 45 is driven back and forth as the segment 43 oscillates. The pinion 45 forms part of a sleeve 47, free to turn on the shaft 46, and the sleeve carries a flange 48 surrounding a toothed ratchet wheel 49 mounted to turn with the shaft 46. As indicated in dotted lines in Fig. 1, a awl 50 is pivotally supported on a pin 51, movable with the flange 48, and is so constructed as to engage teeth 49a on the ratchet wheel 49 in one direction of movement of the pinion 45 by the segment 43. Therefore, for each complete oscillation of the segment 43, the shaft 46 is turned through a predetermined angle, as the segment is turned in one direction, after which the shaft 46 remains stationary, as the segment is turned in the opposite direction. The shaft 46 extends through the rear frame 2, and carries a gear 52 in mesh with gears 53 carried by the lower feed roll shafts 9. These shafts 9 also carry gears 54 inside the frame 2, in mesh with gears 55 mounted on the upper feed roll shafts 9. With all four feed roll shafts 9 thus driven in synchronism from the ratchet wheel shaft 46, it follows that each complete revolution of the gear 33 is adapted to turn the feed rolls 6 and 7 through a predetermined angle to feed a certain amount of wire 4 to the coiling tools, after which the rolls remain at rest for a predetermined period, during which the cutting tools operate.

As previously pointed out, the crank pin 40 is carried by a block 38, and this block is radially adjustable on the gear 33, by means of a screw 56 threaded into the block 38 and turnable in a bearing 57 provided by the gear 33, see Fig. 3.

The end of the screw 56 provides a squared head 5 58, by means of which a tool may be readily applied so as to turn the screw and shift the crank pin 40 with respect to the axis of the shaft 34. In this way, the amplitude of oscillation of the segment 43 may be adjusted in order to vary the N amount of wire fed by the rolls 6 and 7, and after such an adjustment, the block 38 may be tightly locked by means of a wedge-shaped gib 59, disposed between one side of the block 38 and one of the ways 39, having an inclined face, see Fig. 1. A threaded stud 59a carried by the gib 59, provides means whereby the block 38 may be tightly locked, it being noted that both the crank-pin block adjusting screw 58 and the locking stud 59a are readily accessible from between the frame 06 members, when the segment occupies the position of Pig. 1.

While the adjustment of the radial position of the crank pin 40 provides a wide range of wire feeds, as for example, up to 60 inches, this range of feed can be greatly increased by changing the ratio of the gears 52 and 53 mounted on the shafts 46 and 9, respectively. Since these gears are mounted on the rear face of the frame 2, they are readily accessible, and by changing the ° ratio of this gearing so as to increase the degree of turning of the shafts 9, it is possible to practically double the length of maximum wire feed, as for example, up to 120 inches. This increase in the range of wire feed is accomplished without any other changes in the machine, provided a smaller diameter of wire is used, so that the power required is still within the rating of the driving motor 21.

When changing the feed rolls 6 and 1 to provide rolls with different grooves for different wire sizes, or for replacement of worn out rolls, it is also necessary to change or replace the guides 8, which provide grooves corresponding to the grooves in the rolls. In order to provide for convenient mounting of these guides 8, each guide is secured to a plate 60 by means of bolts 8a screwed into the tapped holes in the plate, without coming into contact with the frame I. Each plate 60 is in turn secured to the frame I by screws 60a having countersunk heads, so as to be flush with the front face of the plate.

The above described construction is clearly shown in Fig. 6, in which a portion of the forward guide 8 is broken away to expose the plate 60, and it is apparent that when a guide 8 is removed, the plate 60 remains in place. If, however, repeated removals of a guide 8 should result in wearing of the tapped holes in the plate 60 for receiving the bolts 8a, it is an easy matter to replace the plate, upon removing the screws 60a. This construction, therefore, eliminates any possibility of having to retap worn holes in the frame I, which would become necessary were the bolts 8a, which hold a guide 8 in position, threaded into openings in the frame itself. In other words, the guides 8 and supporting plates 60 may be removed as often as may be necessary, without affecting the frame 1, a decided advantage over previous constructions of this character.

As previously pointed out, the feed rolls 6 and 7 provide a number of grooves for receiving different sizes of wire, and it is necessary to adjust the tool holder 16 laterally with respect to the frame I, in order to bring the tools which it carries into alinement with any selected set of feed roll grooves. In order to expedite such adjustment of the tool holder, the invention provides an improved mounting therefor, which permits the tool holder to be adjusted and locked in position, at a point readily accessible to the machine operator, as will next be described.

SMounting of tool holder 55 As best shown in Fig. 6, the frame I provides an opening 61 for receiving the cylindrical tool holder 16,which provides a longitudinally extending locating groove 62, for a key 63 forming part of the forward guide plate 60, previously described. The tool holder 16 also provides openings 64 and 65, for receiving the arbor 14 and the pitch tool I7, respectively, with a slot 66 extending across the axis of the opening 64.

The frame I provides an opening 67 extending at right angles to the axis of the tool holder opening 61, and of such diameter that a portion of the periphery of the tool holder 16 projects into the opening 61. A pair of cylindrical clamping blocks 68 and 69 are received in the opening 67, with a portion of each block cut away at 68a and 69a, with a curvature corresponding. to that of the cylindrical surface of the holder 16. A screw 10 extends freely through the upper clamping block 69, with its end threaded into the lowei TS block 68, so that turning of the screw 70 by its head 70a will move the lower block 68 either toward or away from the upper block 69. A pin 7t extending between the blocks, serves to keep the curved surfaces 68a and 69a in alinement, and both blocks may be readily turned within the opening 61 by means of a knurled portion 12 at the top of the upper block.

When it is desired to mount the tool holder 16 within the frame, the blocks 68 and 69 are positioned in the opening 67, with a considerable spacing between the blocks. This enables the holder to be readily inserted in the opening 61, with its cylindrical surface loosely engaging the curved surfaces 68a and 69a of the blocks. If necessary, the blocks can be turned by the knurled portion 12, in order to expedite the insertion of the holder 16. In order to clamp the holder 16 in position, the screw 70 is turned to draw the blocks 68 and 69 together, which causes the curved surfaces of the block to exert enough pressure on the holder 16 to prevent it from moving longitudinally of the opening 61. The arbor 14 is then inserted in the opening 64, and after it has been properly adjusted with relation to the line of wire feed, the screw 10 is turned further, to exert greater pressure on the holder. This has the effect of compressing the holder upon the arbor to firmly clamp it in position, the slot 66 imparting a considerable yieldability to that portion of the arbor which is engaged by the clamping blocks 68 and 69.

It is to be noted, in Fig. 1, that the head 70a of the screw 70 and the knurled portion 12, are readily accessible at the front of the machine to an operator making adjustments to set up the machine for coiling the desired form of spring.

In setting up the machine for coiling, it is also necessary to adjust the coiling point 15, both laterally with respect to the line of wire feed, and radially with respect to the arbor 14, and the manner of mounting and adjusting this tool for the purpose of controlling the diameter of the springs being coiled, will next be described.

Control of diameter The coiling point 15 consists of a bar having a groove at its end to receive the wire being coiled, and is carried by a holder 13 mounted on a pin 74 forming part of a slide 75 movable at right angles to the axis of coiling. The holder 73 is 50 adapted to be adjusted laterally on the pin 74, and clamped in position by means of a bolt 16, the holder 73 also being radially adjustable on the pin 14, as desired.

Reciprocatory movement is adapted to be im- 55 parted to the slide 75 by means of a link 77 connected at its ends to a pin 78 on the slide and to a crank arm 79. The arm 19 is turnable with a shaft 80 extending through the frame I and provided at its inner end with an operating arm 60 81. The arm 81 is connected by a link 82 to a lever 83 that cooperates with a pivoted arm 84 carrying a roll 85 bearing on the face of a cam 86. The cam 86 is mounted on the shaft 37 which, as previously pointed out, is continuously 65 driven from the gear 35 rotating in unison with the gear 33, which drives the feed rolls.

The several elements of the mechanism for actuating the slide 15 are maintained in operative relation by means of a spring 81, see Fig. 2, which 70 tends to turn the arm 81 in a counterclockwise direction, as viewed in Fig. 1, and urge the slide 15 to the left. With the parts arranged as shown, eacl complete revolution of the cam 86 causes the coiling point slide 15 to move back and forth, 75 with reference to the coiling axis, and thereby cause the coiling point 15 to control the diameter of the spring being coiled. It is to be noted that movement is imparted to the slide 75 without lost motion, through the crank 79 and link 77.

By varying the form of the cam 86, it is possible to produce springs of varying contour, such as cone springs, barrel springs or two-diameter springs, and the machine provides means whereby with a given cam to determine the general form of a spring, adjustments can be made to take care of small variations in diameter that are often required in springs of this description.

To this end, the link 82 passes through a socket 88 at the end of the arm 81, and extends upwardly to a point above.the top of the frame I. The upper end of the link 82 is threaded to receive a hand wheel 89, which bears on the end of a sleeve 90, loosely surrounding the link 82, with its lower end bearing on the socket 88. The hand wheel 89 is easily reached by an operator adjusting the coiling tools, and by turning of the wheel 89 it is possible to adjust the effective length of the link 82 between the end of the arm 81 and the lever 83. In this way, very close adjustment of the coiling point 15 can be obtained, in the formation of an irregular spring under the control of the cam 86. Should it be desired to form a straight spring of uniform diameter, the wheel 89 is turned until the link 82 is of such length as to lower the lever 83 and cam arm 84 so that the roll 85 remains out of contact with the cam 86. With this adjustment, a set screw 91 determines the position of the slide 75 during the coiling operation, the spring 87 serving to maintain the slide 75 in engagement with the end of the screw 91. Obviously, the set screw 91 can also be employed in cooperation with the cam 86 in determining the maximum diameter of a cylindrical portion of a spring having tapered ends whose formation is under the control of the cam 86.

In order to provide for further adjustment of the form of a spring, in addition to that provided by the link 82, the lever 83 carries an adjustable block 83a, whereby the point of application of the force exerted by the cam roll arm 84, as it turns on its pivot shaft 92, may be varied with respect to the pivot of the lever 83. The block 83a is threaded to receive a screw 93 turnable in the end of the lever 83, with a squared portion 93a of the screw extending beyond the lever providing means whereby a tool may be applied to the screw, for making the adjustment. The hand wheel 89 and the screw 93 thus provide means .5 for quickly adjusting the functioning of the coiling point 15.

As a spring is formed of constant or variable diameter under the control of the coiling point 15, as described above, the pitch of its convoluco tions is determined by the pitch tool 17. This tool bears on the wire after it leaves the coiling point, and the invention contemplates means for controlling the position of the tool 17, as will next be described.

('; Pitch tool control As best shown in Fig. 2, the pitch tool 17 provides a shank 94 extending through the opening 65 of the tool holder 16 and pivotally connected to a link 95. The other end of the link 95 is connected to one arm of a bell crank lever 96, pivotally mounted at 97. The other arm of the lever 96 is connected by an adjustable link 98 to a lever 99 mounted on the same pivot as the lever 83. The lever 99 is associated with an arm 100 mounted on the plvot shaft 92, and carrying a roll 100a, cooperating with a cam 101 on the shaft 37.

A spring 102 is connected to the bell crank lever 96, where it is joined to the link 95, and tends to retain the pitch tool 17 in a retracted position, .5 subject to outward movement, away from the end of the tool holder under the control of the cam 101.

Adjustments in the setting of the pitch tool 17 to obtain desired variations of the pitch when utilizing a given cam 101, are obtained through the link 98. The link extends through a socket 103 at the end of the bell crank lever 96, to a point above the frame I, where it is threaded to receive a hand wheel 104. A sleeve 105 loosely 13 surrounds the link 98 between the wheel 104 and the socket 103, so that turning the wheel 184 changes the effective length of the link 98 between the levers 96 and 99. It is evident from Fig. 1, that the hand wheel 104 is readily accessible to i0o an operator adjusting the coiling tools. Adjustment of the effective length of the lever 99 can be obtained by means of a screw 106, adapted to shift a block 99a, similar to the block 83a on the lever 83, with reference to the pivotal axis of the 4~ cam roll arm 100. A set screw 107 is provided to bear on one arm of the lever 96, in order to limit inward movement of the pitch tool under the pull of spring 102, and make it possible to coil a spring of uniform pitch, free of the control of the cam : 101.

After a spring has been coiled with the desired diameter and pitch, as determined by the functioning of the coiling point 15 and pitch tool I7, the feed rolls 6 and 7 come to rest and one of the cutters 19 operates to sever the completed coil in the interval between successive feeding movements of the wire 4. As previously pointed out, only one cutter is mounted so as to cooperate with the arbor 14, depending upon the formation of .either a right-hand or.left-hand coil, and provision is made for laterally adjusting one cutter or the other, with respect to the line of wire feed, as will next be described.

Adjustment of cutters As best shown in Fig. 2, the heads 20 carrying the cutters 19 are mounted on shafts 108 rotatably supported in parallel relation between the frames I and 2. The upper shaft 108 carries a 50 collar 109, from which projects an arm 110 pivotally connected to a link III extending downwardly and connected at its lower end to an arm 112 mounted on the same pivot shaft 92 which supports the cam roll arms 84 and 100. The arm 5.5 112 carries a roll 112a bearing on a cam 113 mounted on the shaft 37, the cam 113 being so designed that an oscillatory movement is im-. parted to the upper cutter shaft 108 during each complete revolution of the cam shaft 37. As best 60 shown in Fig. 5, turning movement of the upper cutter shaft 108 is imparted to the lower shaft 108 by means of arms 114 mounted on the shafts and connected by link 115, so that the cutter heads 20 are adapted for synchronous turning 65 movement, although in opposite directions with respect to the coiling arbor 14.

In order to line up the cutter heads 20, with respect to the line of wire feed, as determined by the grooves on the feed rolls, the entire cutter T0 assembly, including both the heads 20 and the shafts 108, are adapted to be moved in unison.

As best shown in Figs. 4 and 5, a bracket 116 embraces the cutter shafts 108, and is held against the arms I14, by means of collars 117 secured to .?7 the shafts 108. The bracket II6 provides a projecting lug 118, having an opening in which is screwed the threaded end of a shaft 119, extending through the front frame I and held against longitudinal movement therein by collars 120. The projecting end of the shaft 119 is squared, as indicated at 119a, to receive a tool whereby the shaft 119 may readily be turned at a point adjacent the lower head 20. .When it is desired to line up the cutting tool heads 20 with the line of wire feed, collars 121 mounted on the shafts 108 adjacent the frames I and 2, are loosened, and the entire cutter assembly may then be shifted laterally by turning the shaft 119. In this way, the machine operator may adjust the cutters for proper operation, at the same time as making the above described adjustments of the coiling tools, and without moving from his position.

In order to expedite adjustment of all of. the tools, preparatory to producing a spring of the desired form, a hand wheel 122 is provided just below the coiling todls, see Fig. 3, whereby the cam shaft 31 may be turned by hand. The hand wheel 122 is mounted on a shaft 123, slidable in a bearing in the frame I to bring a pinion 124 into mesh with a gear 125 on the cam shaft, see Fig. 2. Normally, the pinion 124 is. out of mesh with the gear 125, but when it is in mesh, turning of the hand wheel 122 causes the coiling tools, as well as the feed rolls, to operate. This permits the machine operator to closely observe the feeding of the wire and the formation of a coil, and to make such adjustments as may be necessary by turning the readily accessible hand wheels 89 and 104 for varying the diameter and pitch of the spring being coiled.

In Figs. 7 and 8, there is shown a modification in the form of the coiling point, wherein a grooved roll 126 is substituted for the coiling point 15, shown in Fig. 1. The roll 126 is rotatably mounted on a pin 127 carried between the spaced arms of a bracket 128 providing a round shank 129. This shank 129 is received in an opening 130 provided in a holder 131 adapted to be mounted on the slide pin 74, in the same manner as the holder 13. The holder 131 provides a slot 132 communicating with the opening 130, and a bolt 133 is adapted to compress the gO holder upon the shank 129, to clamp the bracket 128 in position. With this mounting of the coiling roll 126, a slight angular adjustment of the bracket 128 can be made to dispose the groove in the roll 126 at an angle best suited for the pitch of the spring being coiled.

From the foregoing, it is apparent that by the present invention there is provided a spring coiling machine of the universal type, by means of which a wide variety of spring forms may be produced. The various adjustments that may be required for varying the product of the machine, are so arranged that an operator standing in front of the machine, right over the coiling tools, can make the necessary adjustments of the arbor, coiling point and pitch tool, as well as the cutters, without having to move from a position in which he can also turn over the niachine by hand. This arrangement makes possible a delicacy of control and accuracy of adjustment not heretofore obtainable in machines of this character.

In the operation of the machine, the intermittent drive for the feed rolls functions in an extremely effective manner, owing to the fact that the shaft carrying the ratcheting device is supported at its ends between the frame members of the machine. Therefore, the thrust of the segment gear on the pinion driving the ratchet pawl is absorbed without anytendency to spring the ratchet shaft. The mounting of an antifriction bearing on the crank pin which actuates the segment gear also results in an extremely smooth action of the crank drive, so that intermittent motion is imparted to the feed rolls without strain and vibration.

Reciprocatory movement is imparted to the slide carrying the coiling point, for diameter control, by means of a crank arm and link motion, which results in actuation of the slide without shock, due to lost motion. The adjustment of the mechanisms for controlling the coiling point and the pitch tool by means of hand wheels operable from points removed from the mechanisms, insures that the operator will always have the diameter and pitch of springs being coiled under, close control, without the necessity of having to leave his position in front of the coiling tools, to make any adjustments.

We claim: 1. In a spring coiling machine, spaced frame members, cooperating feed rolls mounted on shafts supported by said frame members, with one of said shafts extending beyond a frame member, a rotating driving element, a pivotally supported toothed segment, a crank and pin connection between said driving element and segment, a shaft supported at its ends between said frame members carrying a ratcheting device for converting oscillatory movement of said segment by said driving element into intermittent rotative movement of said shaft, with one end of said shaft extending beyond a frame member adjacent to the extended end of said feed roll shaft, and gearing mounted outside of one frame member on said extended shaft ends for driving said feed roll shafts from said ratchet shaft, the ratio of said gearing being changeable to vary the degree of rotation of said feed roll shafts for a given amplitude of oscillation of said segment by said driving element.

2. In a spring coiling machine, rotatably mounted feed rolls, a continuously rotating driving element, a pivotally mounted toothed segment, a shaft carrying a ratcheting device for converting oscillatory movement of said segment into intermittent rotative movement of said feed rolls and a connection between said driving element and said segment, comprising a crank pin movable in a slot provided by said segment and mounted on a block, means for shifting said crank pin block on said driving element with respect to its axis of rotation, and a wedge shaped gib movable parallel to said block for locking the latter in position.

3. In a spring coiling machine rotatably mounted feed rolls, a continuously rotating driving element, a pivotally mounted toothed segment, a shaft carrying a ratcheting device for converting oscillatory movement of said segment into intermittent rotative movement of said feed rolls and a connection between said driving element and said segment, comprising a crank pin movable in a slot provided by said segment and mounted on a block adjustable in radial ways provided by said driving element, a screw shaft for shifting said block and a wedge shaped gib movable between said ways for locking said crank pin block in position.

4. In a spring coiling machine, a frame, wire feeding mechanism mounted on said frame, a cylindrical holder for wire coiling tools movable in an opening in said frame, with respect to the line of wire feed, and a clamping means for said tool holder receivable in an opening in said frame communicating with said tool holder opening and operable from a point at the front of said frame adjacent to said wire feeding mechanism to frictionally engage said tool holder on opposite sides of the axis of said tool holder opening.

5. In a spring coiling machine, a frame, wire feeding mechanism mounted on said frame, a holder for wire coiling tools movable in an opening in said frame, with respect to the line of wire feed, clamping means for said tool holder comprising blocks receivable in an opening communieating with said tool holder opening, and means accessible from the front of said frame for drawing said blocks together to engage and clamp said tool holder.

6. In a spring coiling machine, a frame, wire feeding mechanism mounted on said frame, a holder for wire coiling tools movable in an opening In said frame, and carrying a coiling arbor adjustable to the line of wire feed, and a clamping device for said tool holder comprising blocks receivable in an opening communicating with said tool holder opening and a member operable from a point at the front of the frame for drawing said blocks together .to frictionally engage said tool holder and also compress the body of the holder on the coiling arbor to maintain the arbor in adjusted position.

7. In a spring coiling machine, a frame, wire feeding mechanism, a tool holder carrying a coiling arbor providing a cutting edge and adjustable on said frame with respect to the line of wire feed, a pair of oscillatory cutters mounted above and below said arbor, with one cutter set to cooperate with the edge of said arbor to sever the wire after coiling, and means for laterally moving both of said cutters in unison to line up the operative cutter with said arbor.

8. In a spring coiling machine, a frame, wire feeding mechanism, a tool holder carrying a coiling arbor providing a cutting edge and adjustable on said frame with respect to the line of wire feed, a head carrying a cutter adapted to cooperate with the edge of said arbor to sever the wire after coiling, a shaft carrying the cutter head, means for imparting an oscillatory movement to said 60 shaft, and a screw shaft parallel to said cutter head shaft and operable from the front of said frame to shift said cutter head shaft longitudinally and line up its cutter with said arbor.

9. In a spring coiling machine, a frame, wire feeding mechanism, a tool holder carrying a coiling arbor providing a cutting edge- and adjustable on said frame with respect to the line of wire feed, heads mounted above and below said arbor, with one head carrying a cutter set to cooperate with the edge of said arbor to sever the wire after coiling, parallel shafts mounted in said frame for carrying said cutter heads, means for imparting an oscillatory movement to said shafts in unison, and a screw shaft parallel to said cutter 05 head shafts and operable from-the front of said frame to shift both of said shafts axially to aline the cutter on one head with the arbor.

10. In a spring coiling machine, wire feeding mechanism, a coiling arbor, a coiling point mounted on a slide movable at right angles to the axis of coiling to vary the distance between said coiling point and said arbor, and means for controlling the movement of said coiling point slide comprising a rotating cam, a lever actuated IS by said cam, a pivoted arm connected to said slide, a connecting member extending between said arm and cam actuated lever, and means operable from a point removed from said lever and slide arm for varying the effective length of said connecting member.

11. In a spring coiling machine, wire feeding mechanism, a coiling arbor, a coiling point mounted on a slide movable at right angles to the axis of coiling to vary the distance between said coiling point and said arbor, and means for controlling the movement of said coiling point slide comprising a rotating cam, a pivoted arm actuated by said cam, a lever carrying a block in contact with said cam arm, an operative connection between said lever and said coiling point 15. slide, and means operable from the free end of said lever for shifting the position of its block with respect to the pivot of said cam actuated arm.

12. In a spring coiling machine, wire feeding mechanism, a coiling arbor, a coiling point mounted on a slide movable at right angles to the axis of coiling to vary the distance between said coiling point and said arbor, and means for controlling the movement of said coiling point slide comprising a rotating cam, a pivoted arm actuated by said cam, a lever carrying a block in contact with said arm, a second pivoted arm for operating said coiling point slide, a link connecting said slide arm to said lever, means operable from the end of said lever for moving said block with respect to the pivot of said cam actuated arm, and means operable from a point removed from said lever and said slide arm to vary the effective length of said connecting link. 13. In a spring coiling machine, wire feeding mechanism, a coiling arbor, a coiling point mounted on a slide movable at right angles to the axis of coiling to vary the distance between said coiling point and said arbor, and means for controlling the movement of said coiling point slide comprising an oscillatory shaft, a crank arm carried by said shaft, a pin provided by said slide and a link pivotally connected at its ends to said crank arm and said pin. 14. In a spring coiling machine, wire feeding mechanism, a coiling arbor, a tool movable along the coiling axis to vary the pitch of the. spring being coiled and means for controlling the movement of said pitch tool comprising a rotating cam, a lever actuated by said cam, a pivoted arm connected to said pitch tool, a connecting member extending between said arm and cam actuated lever and means operable from a point removed from said lever and tool operating arm for varying the effective length of said connecting .member.

15. In a spring coiling machine, wire feeding mechanism, a coiling arbor, a tool movable along the coiling axis to vary the pitch of the spring Go being coiled and means for controlling the movement of said pitch tool comprising a rotating cam, a pivoted arm actuated by said cam, a lever carrying a block in contact with said cam arm, an operative connection between said lever and 5. said pitch tool, and, means operable from the free end of said lever for shifting the position of said block with respect to the pivot of said cam actuated arm.

16. In a spring coiling machine, wire feeding mechanism, a coiling arbor, a tool movable along the coiling axis to vary the pitch of the spring being coiled and means for controlling the movement of said pitch tool comprising a rotating cam, a pivoted arm actuated by said cam, a lever TS carrying a block in contact with said arm, a second pivoted arm for operating the pitch tool, a link connecting said tool operating arm to said lever, means operable from the end of said lever for moving said block with respect to the pivot of said cam actuated arm and means operable from a point removed from said lever and said tool arm to vary the effective length of said connecting link.

17. In a spring coiling machine, wire feeding mechanism, a coiling arbor, a slide movable at right angles to the axis of coiling, a grooved roll for receiving the wire and deflecting it around the arbor in a coil the diameter of which is determined by the position of the coiling roll slide, a holder for rotatably supporting said roll and providing a shank extending in the direction of the movement of said slide and means for clamping said shank on the slide with said roll in different angular positions.

18. In a spring coiling machine, a frame, cooperating wir i'eeding rolls mounted on said frame, a wire guide mounted adjacent to a pair of rolls, a plate disposed beneath said guide, members for removably securing said plate to the frame, and other members carried by said plate for retaining said guide in position, independently of said plate-securing members.

19. In a spring coiling machine, a frame cooperating wire feeding rolls mounted on said frame, a holder for a coiling arbor received in an opening in said frame, a wire guide located between a pair of rolls and said arbor holder, a plate positioned beneath said guide and providing a key cooperating with said holder, members removably securing said plate to the frame and other members carried by said plate for retaining said guide in position, independently of said platesecuring members. __ ____ orGEVIN