US2061193A - Setter for snap fasteners - Google Patents

Description

Nov. 17, 1936. GUALTlERE' 2,061,193

SETTER FOR SNAP FASTENERS Filed May 16, 1934 10 Sheets-Sheet 1 I INVENTOR -BY 'blf W ATTORNEYS Nov. 17, 1936.

JIGUALTIERE 2,061,193

SETTER FOR SNAP FASTENERS Filed May 16, 1934 10 Sheets-Sheet 2 INVENT'OR t E Jzz/zzzw fizzali z'r'e BY 10 M M ORNEYS Nov. 17, 1936. GUALTERE 2,061,193

BETTER FORSNAP FASTENERS Filed May 16, 1.934 10 Sheets-Sheet 3 INVEENTOR JZZZZ'ZZJ' fizzalizere ATTORNEYS Nov. 17, 1936. J. GUALTIERE 2,051,193

BETTER FOR SNAP FASTENERS Filed May 16, 1954 10 Sheets-Sheet 4 i n I I MrBlf Jim TTORNEYS Nov. 17, 1936. .11 GUALTIERE 2,061,193

SETTER FOR SNAP FASTENERS Filed May 16, 1934 10 Sheets-Sheet 5 II I INVENTOR BY W #M (ATTORNEYS 1936. J.GUALTIERE SETTER FOR SNAP FASTENERS Filed May 16, 1934 10 Sheets-Sheet 6 INVENTO'R .fzzZzgzr film/here B W Woumfi J. GUALTIERE 2,061,193

- SETTER FORSNAP FASTENERS Filed May 16, 1934 10 Sheets-Sheet 7 Nov. 17, 1936.

Nov. 17, 1936. JIGUALTIERE SETTER FOR SNAP FASTENERS Filed May 16, 1934 Z/ I g !T./--1 I 10 Sheets-Sheet 9 214.47 M A ORNEYS C Wm w l v av N Patented Nov. 17, 1936 SETTER FOR SNAP FASTENERS Application May 15, 1934, Serial No. 725,888

8 Claims.

The present invention relates to rivet setting machines and more especially to a machine for setting sockets and caps for snap fasteners.

Snap fasteners usually comprise two members, namely, a snap socket which passes through the material and a cap on the other side of the material into which the socket is expanded to anchor the cap in place and to hold the socket securely riveted in place in the material. Snap fasteners of this kind are common as glove snaps and as many other articles of commerce.

Heretofore in the art, it has been customary to feed the parts by hand to a rivet setter which was adapted to apply pressure to expand the socket within the cap and hold the parts securely locked in place.

The present invention comprises an automatic machine which for each operation of the machine automatically feeds a socket member and a fastener cap and then applies pressure to expand the fastener within the cap. The cycle of operations is such that a socket is positioned at the work anvil. The goods, having an opening perforated therein to receive the stem of the fastener, is slipped over the socket and the machine is then operated. The operation of the machine feeds a cap over the portion of the socket extending through the goods, and applies pressure to expand the stem of the socket within the cap. It, therefore, will be seen that each operation of the machine results in a completed fastener comprising a socket and av cap being automatically applied to the goods.

The feed mechanism of the machine comprises a novel construction for feeding both the caps and the sockets. The sockets are small hollow stemmed tubular members shaped somewhat like a head gear known as a stove pipe hat. The feed mechanism for the sockets comprises a feed drum and a feed ring spaced slightly from the face of the drum, so that the socket members leave the feed drum with the stems passing through exit slots in the feed ring. The stems of the sockets extend inwardly toward the machine. This is the opposite position usually provided for feeding articles of this shape and the reversal of the feed position is due to the novel feed ring spaced from the face of the feed drum.

The caps comprise hollow members being rounded or oval on one side and provided with an opening on the other side. The feed passageways provided in the edge of the feed drum for the caps are constructed with conical projections located in the central part of each feed passageway. The facing adjacent the cap feed drum is provided with an annular groove opposite the path of the said projections. A capfalling into a passageway with the back of the cap toward the outer face of the feed drum will be blocked from going through the passageway by the conical projection, but any cap falling into a passageway with the back of the cap toward the facing will slide downward through the passageway and. the conical projection will pass into the opening in the cap and gravity will cause the cap to slide over the face of the conical projection and out into a feed channel. This arrangement permits the feed of the caps in such manner that all of the tops of the caps face in one direction in the cap runway so that the caps come right side up into proper place for further operations.

The runway or feed chute for the sockets is arrranged to deliver sockets adjacent a feed slide, which in the operation of the machine moves sockets one at a time from the end of the chute forward over an anvil at the Work station. As soon as the slide has moved a socket to position over the anvil, a holding pin rises through the anvil and enters the opening in the socket, thereby positioning and holding the socket in place at the work station when the feed slide retreats. The caps are fed downward one at a time into a spring armed cup located directly over the anvil on which the socket has been positioned. When the operator has placed the material over the socket, so that the socket extends over an opening in the material and the machine is set into operation, a plunger drives the cap through the spring cup with the opening in the cap downward so that it covers the end of the socket and the plunger continues its downward travel to apply pressure which expands the socket within the cap.

During the setting operation, the socket holding pin remains within the socket, but since this pin is supported by a yielding spring, the holding Din moves downward under the influence of the pressure applied through the plunger. The spring arm cup is constructed to descend with the setting plunger until the cap held in the cup has substantially reached the end of the socket, thereby obviating any danger of the cup being displaced during the setting operation. The holding pin is withdrawn when the operation is completed and the work may be removed from the machine.

Other and further objects of the present invention will in part be obvious and will in part be pointed out hereinafter in the specification following by reference to the accompanying drawings which illustrate the preferred form of the present invention.

It is realized that the invention may be practiced by constructions other than those specifically illustrated herewith, so, therefore, the specific disclosure herewith is to be understood as illustrative and not in the limiting sense.

Fig. 1 is a view showing a side elevation of the machine with certain portions broken away to illustrate interior constructions.

Fig. 2 is a View showing a side elevation of the head of the machine with a portion of the drive wheel broken away.

Fig. 3 is a top plan view showing certain parts in section.

Fig. 4 is a front elevational view showing certain parts in section.

Fig. 5 is a detail sectional view of the anvil and socket holding pin.

Fig. 6 is a detail view showing parts in section and illustrating mechanism for operating the socket feed slide.

Fig. '7 is a perspective view illustrating the operating arm for the socket feed slide.

Fig. 8 is a view similar to Fig. fi'showing the socket slide moved to position where a socket has been placed over the socket holding pin.

Fig. 9 is a detail view illustrating the position of the parts where a socket has accidentally caught and held the socket slide.

Fig. 10 is a detail view illustrating the drive mechanism for intermittently rotating the feed drums which feed the sockets and the caps.

Fig. 11 is a sectional view on' line llll of Fig. 10.

Fig. 12 is a sectional view of a portion of the rim and attached ring of the socket feeding drum.

Fig. 13 is a detail view of a portion of the face in the socket feeding drum on line i3l3 of Fig. 12.

Fig. 14 is an elevational edge view of the feed ring adapted to be attached to the feed drum illustrated in Figs. 12 and 13 and showinig a portion of the ring broken away.

Fig. 15 is a front view of the face of the ring shown in Fig. 14.

Fig. 16 is a detail view illustrating a portion of the rotating feed drum for feeding the caps.

Fig. 1'7 is a front face view of the feed drum shown in Fig. 16.

i Fig. 18 is a detail plan view of a portion of the guide way for the socket feed slide.

Fig. 19 is a detail view of the end of the socket runway adapted to cooperate with the slide guide way shown in Fig. 18.

Fig. 20 is a sectional view on line 2ll2!l of Fig. 18 showing the end of the socket runway.

Fig. 21 is a sectional view on line 2|2l of Fig. 20 indicating the path of sockets down the socket runway.

Fig. 22 is a plan view of the socket feed slide.

Fig. 23 is a sectional view of the socket feed slide on line 23-23 of Fig. 22.

Fig. 24 is a detail plan View of the socket feed dog mounted on the socket feed slide in Fig. 22.

Fig. 25 is an elevational view of the feed dog illustrated in Fig. 24.

Fig. 26 is a detail view of the socket feed dog and slide in position to receive a socket from the socket runway.

Fig. 27 illustrates the socket feed slide positioning a socket over the socket holding pin at the anvil.

Fig. 28 illustrates the socket feed slide moving backward after having positioned a socket on the socket holding pin at the anvil.

Fig. 29 illustrates a modified form of a socket holding dog and slide.

Fig. 30 is a sectional view on line sir-s0 of Fig. 29.

Fig. 31 illustrates a sectional view of a completely assembled snap fastener socket and cap and illustrates the finished product produced by the present invention.

Referring to the drawings and more especially to Fig. l, a pedestal frame I carries an electric motor 2 which is the driving unit for the device. An operating pedal 4 is pivoted in the base of the pedal frame and is normally held in raised position by a coil spring 5 anchored at one end to the pedestal frame and at the other end to the pedal. An adjustable stop 5 limits the upward movement of the pedal. A head frame 7 is securely mounted on the pedestal frame I and is the main support for the operating mechanism. The electric motor 2 is connected by a belt 8 with a weighted drive pulley 9 to rotate the pulley in the direction of the arrow A (Fig. 1). A clutch link 89 extends from the pedal i to the clutch mechanism whereby the operator upon depressingthe pedal 4 causes the clutch mechanism to engage the driving pulley 9 with the operating mechanism.

Referring now to Figs. 2, 3, and 4, the clutch link Hi is provided with an offset l I that engages a pin l3 on an arm l2 of a bell crank lever 34 which is connected by a pin l 5 to the clutch cam bolt 16. The inward travel of the cam bolt 56 is controlled by the stop plate 23 which extends into a groove in the side of the cam bolt Hi. This arrangement also prevents the cam bolt from rotating. The pin l5 operates in a slot in the bell crank M so that when the clutch link I0 is pulled downwardly by the pedal i, the bell crank M. pulls the cam bolt 5 outwardly beyond the path of movement of a clutch bar I? (Fig. 4). This clutch bar ll slides under the influence of a spring 18 until the operating end of the clutch bar comes into the path of a clutch stud 69 which is carried by the hub of the weighted drive pulley 9. This drive pulley normally rotates loosely on a bearing sleeve 20 on a main shaft The clutch bar is mounted in a collar 22 rigidly fastened to the main shaft 2!. When the head of the clutch bar ll slides inwardly into the path of the clutch stud I9, the engagement of this stud I9 with the end of the clutch bar I? drives the main shaft from the drive pulley 9, thereby causing the mechanism to operate. When the cam bolt i6 is at normal position, a cam 24 (Fig. 3) on this bolt l6 engages a cam 25 on the clutch bar ll and withdraws the clutch bar from engagement with the clutch stud l9 and the operating cycle stops. A coiled spring 26 connected with the arm l2 of the bell crank l4 causes the cam bolt l6 to return to normal position as soon as it has been withdrawn by the pedal 4. A spring 21' (Fig. 2) normally pulls the upper end of the clutch link into position over the inner end of the pin 93 which extends inwardly from the arm l2 of the bell crank (Fig. 2). The upper end of the clutch link I!) is attached to a slotted link 28 which is connected with a crank arm 29 on a slide operating shaft 3D. This shaft 39 oscillates from its normal vertical position (Fig. 2) when the machine operates. When the clutch link i B is moved downward by the depression of the pedal Q, the offset H on the arm I2 engages the inner end of the pin l3 and swings the bell crank Hi to withdraw the bolt 15 from its normal position. This permits the spring is (Fig. 4) to move the clutch bar ll inward to engage the clutch stud l9, thereby causing the ma- 1 chine to operate. When the machine operates, the upper end of the crank arm 23 swings toward the left (Fig. 2) and pulls the offset II on the link [0 from in position over the inner end of the pin 3, even if the pedal 4 is held depressed. The spring 26 then swings the bell crank M to cause the cam bolt |6 to move inward so that the cam 24 on the end thereof comes into the path of the cam 25 on the clutch bar I1 and the continued rotation of the main shaft 2| causes the engagement of these cams 24 and 25 to withdraw the clutch bar H from the clutch l9. From the foregoing, it will be noted that the machine will make but one single cycle of operations, each time the pedal is depressed regardless of whether or not the operator lifts his foot promptly after he has depressed the pedal 4. When the shaft turns to swing the crank arm 29 to the right the spring 21 returns the offset II to normal position over the inner end of the pin l3.

The main shaft 2| carries a brake drum 32 (Figs. 2 and 3). A brake shoe 34 sets solidly against this brake drum 32 but is effective on only a part of the brake drum. The brake drum 32 is provided with a slight high spot adjacent the angular position where the clutch bar I! is disengaged from the clutch stud l9. This slight high spot on the brake drum comprises a very simple expedient for applying the brake effect at the proper moment, so that as soon as the clutch is opened, the main shaft 2| stops rotating with the parts at the end of an operating cycle.

The brake drum 32 carries a heavy stud 35 (Figs. 2, 6, and 8), upon which a thrust link 36 is mounted. This thrust link 36 is connected at its upper end with a main lever 31. The connection between the thrust link and the main lever comprises an adjustable eccentric stud 38, which is held in adjusted rotative position by the clamp nut 39. The adjustable eccentric stud 38 is for the purpose of adjusting the working zone of the main lever 31 as will be explained later. The main lever 31 is pivoted on a short shaft 40 (Figs. 10 and 11) which rotates in bearing arms 4| and 42 (Figs. 3, 4, and 11) on the head frame 1. The forward end of the main lever 31 is connected by links 44 with a plunger 45 that reciprocates in bearings 46 and 41 in the front portion of the head frame 1 and carries a setting head 48 adapted to cooperate with an anvil 49 (Figs. 6 and 8) to set caps in position over fastener sockets. The anvil 49 is removably mounted in the head frame 1 by a locking screw 56 (Fig.

A socket holding pin 5| is mounted to reciprocate through the center of the anvil 49. This holding pin (Figs. 5, '7, and 9) is guided by a head sleeve 52 and is urged upwardly by a spring 54 mounted in an adjustable screw cup 55. The head sleeve 52 is adapted to reciprocate in the frame 1 and is stopped in its upward movement by a stop lever 56 mounted on a rocker arm 51 which is pivoted on a rocker shaft 58 and is provided with an anti-friction roll 59 that is held in engagement with a rocker arm cam 69 on the main shaft 2| by the operation of the spring 54. The distance the holding pin 5| extends through the anvil 49 may be adjusted by an adjustable stop 6| carried by the rocker arm 5| and operative upon the stop lever 56 to adjust its angular relation relative to the rocker arm 51. It will be noted that the rocker arm cam 68 is effective to cause the rocker arm 51 to depress the holding pin 5| for slightly more than one-half revolution of the main shaft 2|.

The upper part of the head frame 1 carries a pair of feed drums. One of these feed drums feeds the socket members in a proper unright position and the other of the feed drums feeds the cap members properly positioned. Socket feed drum 62 (Figs. 3 and 4) feeds the socket members. The socket members are fed into this feed drum from a feed hopper 64. This drum 62 is removably mounted upon a socket drum shaft 65 and is intermittently rotated by a ratchet 66 which is fixedly mounted on the shaft 65. This ratchet is intermittently operated by a thrust dog 61 (Figs. 3, 4, and This thrust dog 61 is mounted on an arm 68 fixedly secured to oscillate with a short shaft 46 to which the main lever 31 is anchored by an anchor stud 69, so that each time the main lever 31 is oscillated, the thrust dog 61 engages and pushes forward the notches of the ratchet 66. As the feed drum 62 is intermittently rotated, socket members within this fed drum are tumbled about and tend to slide toward the facev of the drum.

In order that the socket members may be properly positioned for further operations, it is necessary that the stems of the socket members shall be fed in an outward position relative to the rim of the drum 62. This desirable and necessary operation is accomplished by the utilization of an auxiliary member comprising a ring (Figs. 12, 13, 14, and mounted upon the face edge of the drum 62. The face of the drum 62 is provided with guide grooves 19. These guide grooves lead to escape exits 1| for the socket members. These escape exits are in the separate ring 12 which is mounted upon the face edge of the feed drum 62. By this construction, it will be observed that the socket members 14 can only escape from the feed drum 62 with the stems of the socket members extending toward the central axis of the machine frame. The socket members, after escaping from the drum 62, slide down a runway 15 (Figs. 1, 2, and 4). This runway leads to a socket feed slide bar 16 (Figs. 26 to 30). One side wall of the end of the runway comprises a. removable end 11, which may be easily removed in case of injury should a defective socket become caught in the mechanism. The bottom of the slide bar carrier adjacent the outlet of the socket runway is provided with a recess 18 (Figs. 18, 20, and 21) which has an inclined surface 19 leading toward the forward end of the slide-way for the slide bar. Sockets 14 coming down the runway 15 slide into the recess 18 and remain in this position until they are carried forward by the socket feed slide.

The main shaft 2| carries an eccentric 60 fixedly secured to the main shaft (Figs. 6, 8, and 9). A thrust arm 8| is mounted on the eccentric 89. This thrust arm is provided at its upper end with a guide-way for a slide block through which a stub shaft 84 extends. The slide block 82 is normally held against an adjustable stop 85 by a coil spring 86. The stub shaft 84 is connected with an arm 81 of a bell crank member mounted on the slide operating shaft 38. The other arm 88 of the bell crank member carries a tension spring 89, which is connected with a swinging link 98 that is loosely mounted to rotate about the shaft 36 at one end and is connected with a slide block 9| at the other end. The slide block 8| is vertically slideable upon a thrust pin 92 on the slide bar 16. The arm 88 of the bell crank at its outer end is provided with a thrust face 94, and the arm 81 of the bell crank being in the form of an inclosing hood is provided with an opening 95 (Fig. 3) through which the adjustable stop 85 may be accessible. The tension spring 89 normally holds the swinging link 98 against the arm 88 of the bell crank as is illustrated in Figs. 6 and 8. If a deformed or imperfect socket member jams the slide bar 75 so that it cannot move, the tension spring 89 will be stretched as indicated in Fig. 9 without injury to the parts. If on the return movement of the slide bar I8, any unusual resistance occurs, the spring 86 will be slightly compressed.

Referring now to Figs. 26 to 30 inclusive, a socket member I4 is fed into the recess I8 in the path of the slide bar it. This recess will hold only one socket so that the succeeding sockets are blocked in the end of the runway I5. The forward end of the slide bar is provided with a notch 96 in the path of which stands the stem of the socket member I4. A socket holding pawl 91 is provided with a head member 98 and a plate like body portion 99 which carries flat pin I88. This flat pin is movable in the recess IEII in the slide bar l8 and is normally urged toward the rear of this recess by a coiled spring I92. A stop pin I84, mounted stationary in the bed plate I05 for the slide bar 78, is adapted to pass through a groove I 88 in the under side of the slide bar I6 and to engage the end of the body 99 when the parts are in normal position as indicated in Fig. 26, and thereby move the holding pawl 91 away from the notch 98 to permit the stem of a socket member I I to be positioned between these two members. At the end of the movement of the slide bar I6, in moving from the front of the machine back to its normal position as illustrated in Figs. 6 and 26, the slide bar it contacts with a stop pin I83, thereby stopping the movement of this bar, and also stopping the swing of the bell crank 8'I88. The continued movement of the eccentric 89 forces thrust arm 8| upwardly. During this time, the coil spring 86 contracts and this operation provides a dwell equivalent to about 35 rotation of the main shaft, during which time a socket member It may come into position between the jaws 96 and 98. This dwell is of substantial importance where the machine is being operated rapidly wherein one cycle of operations quickly follows another.

It will be noted from Figs. 6, 8, and 25 that the head 96 of the pawl 97 is wedge shaped. It will be also noted in Fig. 8 that this wedge shaped head passes the riveting position. The purpose of the wedge shape on the head 91 is to permit this member to pass under work which is positioned at the riveting station to receive rivets. A blunt head would force the work aside and the operator would be disturbed during rapid operations of riveting. As soon as the slide bar I6 is moved toward the front of the machine, by the swing of the swinging link 98, the coil spring I82 causes the holding pawl 9? to move toward the notch 96 and thereby clamp the stem of the socket member 14 between the notch and the pawl. At the same time, a guide pin ID! on the slide bar I6 enters an opening I98 in the head 98 of the holding pawl 91 to maintain the proper relation of the parts. forward to position the socket member I4 directly over the socket holding pin 5| which has been withdrawn below the surface of the anvil 49 as the slide bar I6 is moved forward. As soon as the socket reaches this position, the rocker arm 51' operates to permit the spring 54 to raise the holding pin 5| into the opening in the socket I4 so that the socket is now securely set over the holding pin 5|. The travel of the slide bar I6 is adjustable by the adjustable stop 85 in The slide bar I6 is moved order to position the socket I4 accurately over to pin 5|. As the machine continues to operate, the eccentric through the bell crank 87, 88, and the swinging link 98 pulls the slide I6 away from the front of the machine. The holding pawl 91 drags over the socket on the pin 5| and compresses the coil spring I82 until the socket holding pawl 97 escapes from the socket on the holding pin 5|. As soon as this happens, the spring I02 snaps the holding pawl back in position on the end of the slide bar I6 with the guide pin III? in the guide opening I88.

Figs. 29 and 30 indicate a slight modification of the holding pawl in that the guide pin I81 and the opening I88 are replaced by an inclined surface I09 on the end I8 and an inclined surface I III on the head of the holding pawl. The spring I82 causes these inclined surfaces to slide one upon the other until the inner face of the holding pawl contacts with the side face on the slide bar. The operation of the modification as shown in Figs. 29 and 30 is the same as that previously described relative to the construction shown in Figs. 26, 27, and 28.

The feed mechanism for the cap comprises a cap feed drum III (Figs. 1, 2, 3, and 4) which is removably mounted on a drum shaft I I2 that rotates in a bearing II4 in the head frame I. The inner end of this shaft II2 carries a feed ratchet II5' (Fig. 10) which is engaged by a pull ratchet pawl H6. This ratchet pawl H6 is mounted on an arm II I fixedly secured to the shaft 48 for the main lever 37. As the main lever 3'! cscillates, the arm I ll swings to cause the ratchet pawl IIB to engage the ratchet H5 and rotate the drum shaft II2 step by step. The rotation of the drum shaft causes caps fed into the drum I I I by the hopper I I8 to be tumbled about in the cap feed drum I II. The feeding edge of this drum III (Figs. 16 and 17) is provided with exit pathways II9. In the center of each pathway II9 is a conical projection I20 comprising the head of a stud set in the edge of the drum. A groove I2I is provided in the facing I22 opposite the path of the conical heads I28. Baffie plates I24 are also provided within the body of the drum II I to loosen up the mass of caps within the drum as the drum rotates. These caps I25 are oval on the top and are provided with an opening on the opposite side. The studs I20 present obstacles to the escape of caps having the tops thereof in contact with the studs, but permit caps having the open sides toward the studs to slide over the studs into the groove I20 and then slide off the studs into the feed groove I26. Caps in the feed groove I28 slide down the cap runway I2'I to the cut-off feed bar I28, which feeds caps one at a time from the runway I2'I into the terminal guides I29, at each operation of the machine.

This cut-off feed I28 is reciprocated by a spring member (Fig. 2) I30 which is carried upon a lever I3I pivoted in the main frame. The upper end of this lever I3I is provided with a stud I32, which stud extends between bifurcated arms I34 comprising a continuation of the arm In (Fig. 10) which operates the ratchet pawl for the cap drum shaft. During each cycle of operations of the machine, the bifurcated arms I39 swing the lever |3I to operate the cut-off I28 to release one cap I25 from the runway I2'I into the terminal guides I29. The terminal guides I29 are normally in contact with a spring arm cup I35 (Fig. 4) which comprises a pair of spring arms i 36 and [31. each of which carries a half portion of the cup member I35. This spring arm cup, which is adapted to hold a single cap, is positioned directly over the socket holding pin SI and holds a cap directly beneath the setting. head 48 carried by the plunger 45. The spring arms I36 and I3! are carried by a vertical slideable cup bar I38 mounted to slide in bearings in the head frame I. This cup bar I38 is normally held up by a coiled spring I39 to bring the cup I30 into contact with the terminal guides I29. The coiled spring I39 has one end anchored to the head frame I and the other end anchored to the cup bar I38. An adjustable stop I40 limits the downward movement of the cup bar I38.

As the machine operates, a cap resting in the cup I35 is directly over a socket on the holding pin 5I in the path of the descending setting head 48. The downward movement of the setting head 48 carries the cup bar I38 downward against the action of the coil spring I39 until the movement of the cup bar I38 is stopped by a stop I III. The continued descent of the plunger 48 causes the spring arms I35, I31 to swing outwardly (Fig. 6) to release the cap when it is in position directly over the end of the socket on the socket pin 5|. The continued movement of the setting head 43 applies pressure to the positioned cap, thereby expanding the upper end of the socket member within the cap and looking the same in position therein so that the socket I4 is securely locked within the cap I25 which is tightly seated against the material I 4|, thereby completing the operating cycle of the machine.

The adjustable eccentric stud 38 may be turned to adjust the limit of travel of the plunger 45 and the setting head 48, so that the effective pressure on the cap I25 may be regulated and in this way, the operation of the machine may be adjusted for various sized caps and heights of sockets, or it may be adjusted to control the degree of flattening of the upper end of the sockets.

It will be observed that in the operation of the machine, a socket is fed from one side of the machine to arrive at the anvil in an upright position where it is held by the socket pin in the center of the anvil, and that a cap is fed from the other side of the machine in an upright position with the opening of the cap downward so that the cap is set down upon the upper end of the socket and the plunger continues its downward descent to apply pressure to crush or flatten the upper end of the socket and expand the same within the cap, thereby locking the parts together.

Having described my invention, I claim:-

1. In a machine of the class described comprising a pedestal frame, an anvil on said frame, a head frame mounted on said pedestal frame, means to feed sockets downwardly to a socket feed slide so that said sockets reach said socket feed slide in an upright position, a socket feed slide for positively holding one of said sockets and moving the same forwardly to position the same over said anvil, means to hold said socket in position on said anvil when the said socket is released from said slide, feed mechanism to feed a cap upright over said socket on said anvil, and plunger means adapted to apply pressure to said cap and said socket to expand said socket within said cap and lock said cap and socket member together.

2. A machine of the class described comprising a frame, an anvil, socket feed mechanism to feed sockets one at a time to said anvil, a holding pin for said sockets at said anvil, a rocker arm, a stop lever pivoted on said arm and engaging said pin, a cam to operate said arm and said lever to remove said pin from the passageway of a socket when a socket is being positioned at the anvil, a spring operative on said pin to insert said pin within a socket to hold said socket over said anvil during riveting operations, and means to expand said socket to rivet the same in place.

3. In a machine of the class described comprising a frame, an anvil on said frame, means to feed sockets one at a time to said anvil, a socket holding pin mounted to be reciprocated through said anvil, a rocker arm, a stop lever pivoted on said arm and engaging said pin to lower the same, a spring to raise said pin, and means to change the normal angular relation between said arm and said lever, to adjust the effective length of the path of reciprocation of said pin.

4. In a machine of the class described comprising a frame, an anvil on said frame, means to feed sockets one at a time to said anvil, a socket holding pin mounted to be reciprocated through said anvil, a spring to urge said pin upward, positively operated means to draw said pin downward, and means to adjust the upward limit of movement of said pin.

5. A machine of the class described comprising a socket feed mechanism adapted to feed socket members to a slide carrier, means on said slide carrier to hold a socket member and to move the same to a riveting station, an anvil at said riveting station, and means to hold said socket in position at said riveting station when said slide carrier is withdrawn.

6. A machine of the class described comprising a frame, socket feed means to feed sockets with the stems thereof upright, a slide member adapted to engage and hold a socket and transport the same to a riveting station, an anvil at said riveting station, and means comprising a socket pin adapted to enter a socket and hold the same over said anvil when said slide is Withdrawn.

7. In a machine of the class described, a frame, means carried by said frame to feed sockets with the stems thereof upright, a socket slide comprising a body portion and a gripping jaw, means to cause said gripping jaw to engage a socket and clamp the same against said body portion, means to move said slide to transport said socket to a riveting station, an anvil at said riveting station, a socket holding pin, means to cause said socket holding pin to be brought into engagement with the opening in said socket when said socket is positioned at said anvil to hold said socket over said anvil, and means to compress said socket against said anvil to rivet the same.

8. In a machine of the class described, the combination of a frame; a socket feed mechanism on said frame and adapted to feed sockets with the stems upright; a socket feed slide; and means to reciprocate said slide, said means comprising a bell crank, an arm mounted on the axis of said bell crank, and a spring operatively connecting said arm and said bell crank whereby said spring may yield should said slide encounter resistance thereby obviating breakage.

JULIUS GUAL'I'IERE.

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