US3735554A

US3735554A - Festooning machine

Info

Publication number: US3735554A
Application number: US00117485A
Authority: US
Inventors: J Maggio
Original assignee: Elastic Systems Corp
Current assignee: Elastic Systems Corp
Priority date: 1971-02-22
Filing date: 1971-02-22
Publication date: 1973-05-29
Anticipated expiration: 1990-05-29

Abstract

A festooning machine having: A. INDEPENDENTLY ADJUSTABLE, VARIABLE-SPEED MATERIAL FEEDING MEANS; B. INDEPENDENTLY ADJUSTABLE, VARIABLE-SPEED, VARIABLE-DISTANCE RECIPROCATING DRIVE MEANS WHICH CAUSES THE MATERIAL FEEDING MEANS TO RECIPROCATE LONGITUDINALLY; AND C. INDEPENDENTLY ADJUSTABLE, VARIABLE-SPEED, VARIABLE-DISTANCE RECIPROCATING DRIVE MEANS WHICH CAUSES THE MATERIAL FEEDING MEANS TO RECIPROCATE TRANSVERSELY CONCURRENTLY WITH ITS LONGITUDINAL MOVEMENT.

Description

[ 1 May 29, 1973 United States Patent Maggio [54] FESTOONING MACHINE Inventor: Joseph P. Maggie, Farmingdale, Primary Examiner-Travis MCGehee N Y Att0rneyStoll Stoll Assignee: Elastic Systems Corporation, Farm- ABSTRACT ingdale, N.Y.

Feb. 22, 1971 A festooning machine having:

a. independently adjustable, variable-speed material [22] Filed:

Appl. No.: 117,485 feeding means;

b. independently adjustable, variable-speed, variable-distance reciprocating drive means which [52] US. Cl. ........................53/116, 53/245, 270/62,

270/79 causes the material feeding means to reciprocate longitudinally; and c independently adjustable, variable-speed,

variable-distance reciprocating drive means which NM 32 6 U B.6 H 3 5 m r a e S m d l .1.. F

causes the material feeding means to reciprocate transversely concurrently with its longitudinal movement.

[56] References Cited UN lTED STATES PATENTS 9 Claims, 13 Drawing Figures 3,487,421 Ruppelet al.....i.................53/l16X 3,599,393 Read.................................,....53/l l6 .PATENIED 3,735,554

SHEET 1 OF 8 A TTOIENEVS PAIENIE m 2 9 I975 SHEET 2 BF 8 JNVENTOR. JOSEPH P MAGGIO ATTORNEYS PAIENI W29 I973 SHEET 3 UF 8 INVENTOR. JOSEPH P NAG'G'ID ATTORNEY PATENIEDHAYZSIQH 3 735,554

IN V EN TOR. JWSEPH P MAGGIO A TTORNEYS' PATENTED HAY 2 91973 SHEET 6 OF 8 INVENTOR. JOSEPH P MAGGIO ATTORNEYS PATENTED MAY 2 9 I973 SHEET 7 BF 8 INVENTOR; JOJEPH P. MAGGIO BY 5 9 9 lrrr llllllllll .1

A TTORNEYS PATENTELMAYZSIHYS v 735,554

SHEET 8 UF 8 ELEC TI? oMA GNE 11 c NORMALDY NoRMALL-v CLUTCHES OPEN OPEN NORMALLV NORMAL LY CLOSED CLOSED IIOV TOGGLE JIWIrcH 0 7 Low vownas CONTROL ELECTROMAGNETIC NORMALLY NORMALLY CLUTCHES' OPEN OPEN 706 1.8 swzrcn 110v r 8 '1 LOW VOLTAGE CONTROL INVENTOR JOSEPH P MAGGIO w/ rm ATTORNEY rEsTooNmG MAC BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to the festooning and packaging of flexible material such as rubber tape, textile binding and ribbon, cord, yarn and thread of various materials. Festooned strip material, as distinguished from rolled strip material, may be packaged in rela tively long continuous lengths and may be fed under relatively constant tension to sewing machines and other machines in which such material is used, processed or applied.

2. Description of the Prior Art The closest prior art known to applicant is shown in Zimmerman US. Pat. No. 3,109,643 issued on Nov. 5, 1963 and the prior art patents cited therein. The festooning machines of the prior art feed strip material both longitudinally and transversely, and in this sense all festooning machines are alike. However, strip material comes in different widths, thicknesses and lengths, and it is deposited in receptacles of different widths and lengths, and the prior art festooning machines are incapable of adjusting to these variables.

There are other variables, as for example the speed of feeding material to the festooning machine. Reference is here made to the combination of a festooning machine with another machine such as a slitter or an extruder, the latter machine feeding to the festooning machine. It is essential that the speed of operation of the festooning machine be synchronized with the speed of operation of the slitting or extruding machine. This requires adjustment of the speed of operation of the material feeding mechanism of the festooning machine, adjustment of the speed of longitudinal movement thereof, and adjustment of the speed of transverse movement thereof. Where there are variations in the dimensions of the receptacles into which the festooning machine feeds, it is also necessary to adjust the length of the longitudinal stroke and the length of the transverse stroke of the feeding mechanism of the festooning machine. In short, adjustments must be made as to both time (speed) and distance(length of stroke). Each adjustment must be independent of the others. None of the festooning machines of the prior art are capable of all of these adjustments. The festooning machine of the present invention is.

There is another adjustment which is required for uniform festooning of strip material. In the prior art no account is taken of festooning variations resulting from SUMMARY OF THE INVENTION The invention comprises a festooning machine having an elevated frame, a longitudinally movable carriage on said frame, a transversely movable carriage on the longitudinally movable carriage, strip material feeding means on said transversely movable carriage, and a vertically movable receptacle platform below said longitudinally and transversely movable carriages and said strip material feeding means. Independently adjustable variable-speed, variable-distance reciprocatory drive means are provided between the elevated frame and the longitudinally movable carriage. Additional independently adjustable variable-speed, variable-distance reciprocatory drive means are provided between the longitudinally movable carriage and the transversely movable carriage. The strip material feeding means is operated by independently adjustable variable-speed drive means and the vertically movable receptacle platform is also operated by independently adjustable, variable-speed reciprocatory drive means.

As is above indicated, the festooning machine which is herein described and claimed may be operated and synchronized with another machine, such as a slitting machine, which may have a constant or variable feed. In either case, the material feeding means of the present festooning machine is adjustable to the speed of operation of the slitting machine. This may require an adjustment of the speed of operation of the longitudinally and transversely movable carriages, as well as an adjustment of the speed of operation of the receptacle platform mechanism.

In the operation of this machine, one or more ends of strip material are fed to the machine from a conventional source, say a slitting machine. This material is then fed by the feeding mechanism of the festooning machine into one or more receptacles, one for each end. Since the feeding mechanism is reciprocated both longitudinally and transversely of the receptacles, the material is laid therein in festooned arrangement.

The key feature of the present machine is its flexibility and versatility. It is adaptable to different materials, different feeding machines, different receptacles, different operating speeds and conditions.

BRIEF DESCRIPTION OF THE DRAWING FIG. I is a side view of a festooning machine made in accordance with the present invention.

FIG. 2 is an opposite side view thereof.

FIG. 3 is a top view of said festooning machine.

FIG. 4 is an enlarged fragmentary vertical section on the line 4-4 of FIG. 3. I

FIG. 5 is an enlarged vertical section on the line 5-5 of FIG. 1.

FIG. 6 is a fragmentary vertical section on the line 6-6 of FIG. 1.

FIG. 7 is a fragmentary vertical section on the line 7--7 of FIG. 1.

FIG. 8 is a fragmentary perspective schematic view showing the relative position of the two carriages and the receptacle-supporting platform at the commencement of a strip material festooning and packaging operation.

FIG. 9 is a similar view showing the relative positions of said carriages and receptacle-supporting platform at the end of a strip material festooning and packaging operation.

FIG. 10 is a detailed view of an electromagnetic clutch-operated reversing mechanism which drives, and reverses the direction of travel of, the longitudinally movable carriage, the electromagnetic clutchoperated reversing mechanism which drives, and reverses the direction of travel of, the transversely movable carriage being identical.

FIG. 11 is a schematic plan view showing the switch control means for controlling the travel and reversal of direction of travel of the twin carriages.

FIG. 12 is a circuit diagram relating to the longitudinally movable carriage.

FIG. 13 is a circuit diagram relating to the transversely movable carriage.

DESCRIPTION OF A PREFERRED EMBODIMENT OF THE INVENTION Referring now to the details of the invention as illustrated in the accompanying drawing, it will be observed that most, if not all, of the moving parts of the festooning machine are supported on a frame 10. This frame consists, essentially, of a plurality of legs 12 and horizontal side rails 14 and end rails 16. Mounted on side rails 14 are longitudinally extending tracks 20, which support a first carriage 22. More specifically, carriage 22 has a generally rectangular frame 24 to which four bearings 25 are secured, one adjacent each corner. These bearings rotatably support stud shafts 26 and wheels 28 are mounted on said stud shafts. It will be noted, for examples in FIG. 5, that these wheels are annularly grooved to engage tracks 20. It will be apparent, therefore, that carriage 22 is adapted to move longitudinally of frame by reason of the rolling engagement of wheels 28 with tracks 20.

Mounted on frame 24 of said first carriage 22 is a pair of tracks 30. See, for example, FIG. 4. These tracks support a second carriage 32, which, like the first carriage, has a generally rectangular frame 34, bearings 36 adjacent each corner of said rectangular frame, stud shafts 38 rotatably supported by said bearings, and wheels 40 mounted on said stud shafts. As will be seen in FIG. 4, wheels 40 are annularly grooved to engage tracks 30, and it is by means of these wheels, rolling on said tracks, that the second carriage is adapted to move transversely of the first carriage and hence transversely of frame 10. For convenience in referring to these two carriages, the first will be designated the longitudinally movable carriage and the second will be designated the transversely movable carriage. The drive mechanisms which cause the first carriage to travel longitudinally of the frame and the second carriage to travel transversely of the frame will now be described.

A rack and pinion drive coupled with an electromagnetic clutch-actuated reversing mechanism 39 operates the longitudinally movable carriage 22. More particularly, secured to the frame 24 of the longitudinally movable carriage is a pair of racks 40 which are engaged by a pair of pinions 42 fixed to a shaft 44. The shaft is joumaled into bearings 46 which are secured to side rails 14 of frame 10. Also fixed to said shaft is a sprocket wheel 48, which is connected by a drive chain 50 to a second sprocket wheel 52 secured to a shaft 54. This shaft is joumaled into bearings 56 which are supported on frame 10. A third sprocket wheel 58 is secured to shaft 54, and a second drive chain 60 connects said sprocket wheel 58 to a fourth sprocket wheel 62 secured to a shaft 64. Shaft 64 is a reversible drive shaft supported on a subframe 66 by means of bearings 68. Another drive shaft 70 is joumaled into bearings 72 which are also supported by subframe 66.

It will now be observed that drive shaft 70 is connected by means of a sprocket 74, a drive chain 76 and another sprocket 78 to the shaft 80 of a motor 82. This motor, like subframe 66, is supported on a framework 84 which is secured to the legs 12 of frame 10.

Drive shaft 70 is driven by motor 82 in one direction. Secured to drive shaft 70 is a gear 90, which directly engages a second gear 92 on shaft 64. Gear is fixed to shaft 70, but gear 92 is rotatably mounted on shaft 64. It will be understood that a clutch element 94 is splined to shaft 64 such that it is relatively free to move longitudinally of said shaft but is fixed against rotational movement relative to said shaft. Gear 92 has a clutch face 96 which is engageable with clutch element 94. These two

clutch elements

94 and 96 comprise an electromagnetic clutch by which gear 92 may be locked to shaft 64 for rotary movement therewith or disengaged from said shaft so that either may rotate relafive to the other. Assuming that shaft 72 rotates in clockwise direction (as viewed in FIG. 1) when driven by motor 82, gear 90 will also rotate in the same direction, but gear 92, being directly engaged by gear 90, will rotate in counterclockwise direction. When

clutch elements

92 and 94 are energized, gear 92 will be locked to shaft 64 and cause said shaft to rotate in counterclockwise direction, also as viewed in FIG. 1.

In order to cause shaft 64 to rotate in clockwise direction, an indirect drive between

shafts

64 and 70 is provided. This indirect drive consists of a sprocket 100 which is fixed to shaft 70, a second sprocket 102 which is freely mounted on shaft 64, a chain 104 which joins said

sprockets

100 and 102, and a second clutch element 106 on shaft 64. As is the case with sprocket 92, sprocket 102 is free to rotate on and relative to shaft 64. As is the case with clutch element 94, clutch element 106 is splined to shaft 64, being free to move axially thereof but being locked against rotary movement relative to said shaft. Also as is the case with sprocket 92, sprocket 102 is provided with a clutch face 108 opposite clutch element 106, and these two clutch elements comprise an electromagnetic clutch which, when energized, locks sprocket 102 to shaft 64.

It follows, therefore, that when

clutch elements

94, 96 are deenergized and disengaged, and

clutch elements

106, 108 are energized and engaged, rotation of shaft 70 in clockwise direction (as viewed in FIG. 1) will cause shaft 64 to rotate in the same direction (also as viewed in FIG. 1).

The above described reversing mechanism, consisting of shaft 70 which is driven in a constant direction and shaft 64 which is driven in opposite directions, the

gear drive

90, 92 and

clutch elements

94, 96 which drive shaft 64 in one direction, and the sprocket-

sprocket chain drive

100, 102, 104 and

clutch elements

106, 108 causing shaft 64 to rotate in the opposite direction, may herein be designated as the reversible clutch mechanism which drives the longitudinally movable carriage in opposite directions. This drive is accomplished through sprocket 62 on shaft 64, sprocket 58 on shaft 54, chain 60 which joins sprockets 62 and 58, sprocket 52 on shaft 54, sprocket 48 on shaft 44, and chain 50 which joins

sprockets

48 and 52, and pinions 42 on shaft 44 engaging racks 40 on frame 24 of the longitudinally movable carriage. When

clutch elements

92, 94 are energized and engaged, shaft 64 will rotate in the opposite direction from the direction of rotation of shaft 70 and, through the transmission train last above described, this will cause shaft 44 to rotate in one direction and the rack and pinion connection between said shaft and the longitudinally movable carriage 22 will cause said carriage to move longitudinally in a given direction relative to frame 10. When

clutch elements

92, 94 are deenergized and disengaged, and before

clutch elements

106, 108 are energized and engaged, shaft 64 will be disengaged from shaft 70 and will remain stationary. This, of course, means that the entire transmission train between shaft 40 and the longitudinally movable carriage will also remain stationary, as will the longitudinally movable carriage itself. To reverse the direction of travel of said longitudinally movable carriage,

clutch elements

106, 108 will be energized and engaged and shaft 70 will now drive shaft 64 by means of

sprockets

100 and 102 and sprocket chain 104. Shaft 64 will now rotate in the opposite direction from its direction of travel when driven by

gears

90, 92, and so will the entire transmission train which drives the longitudinally movable carriage. Said longitudinally movable carriage will thereby be caused to travel longitudinally of frame in the opposite direction from its travel last above described.

The mechanism for driving the transversely movable carriage transversely of frame 10 (and hence of the longitudinally movable carriage) will now be described.

It will be noted that an electromagnetic clutchactuated reversing mechanism 110, similar to the electromagnetic clutch-actuated reversing mechanism 39 last above described, is mounted on the longitudinally movable carriage. See FIG. 3. Accordingly, there is no need to describe reversing mechanism 110 in detail, since the description of reversing mechanism 39 applies equally here. For the purposes of the drawing, the same reference numerals which are applied to reversing mechanism 39 will be applied to reversing mechanism 110, with the added suffix a.

Reversing mechanism 110 drives a longitudinally extending shaft 112, which is supported by bearings 114 mounted on the longitudinally movable carriage. Secured to shaft 112 is a pair of pinions 116 which engage a pair of racks 118 on frame 34 of the transversely movable carriage 32. See FIG. 6. When reversing mechanism 110 operates in one direction, it causes shaft 112 to rotate in clockwise direction as viewed on FIG. 6. This causes the transversely movable carriage 32 to move to the right as viewed in FIG. 6. When reversing mechanism 1 10 operates in the opposite direction, shaft 112 is caused to rotate in counterclockwise direction, thereby causing the transversely movable carriage to move to the left as viewed in FIG. 6.

Mounted on the transversely movable carriage is a material-feeding device 130. This device includes a bracket 132 and a plurality of material guides 134. In the illustrated form of the invention, fed to guides 134 from a conventional source of supply, e.g., a slitter, is strip material 136, which is a relatively narrow rubber tape, for example, a tape approximately l% inch wide and 0.010 inch thick. This merely illustrates the various kinds of material that may be used on the present machine and is not intended as a limitation of any kind on the mechanism of the machine or scope of the disclosure and claims.

Guide elements 134 guide the strip material to the machine and, more particularly, to

rollers

138 and 140 mounted, respectively, on

shafts

142 and 144. These shafts are journaled into

bearings

146 and 148 mounted on a supporting frame 150 on the transversely movable carriage. As will shortly be seen,

rollers

138 and 140 are driven rollers and their function is to assist in feeding the strip material through the festooning machine. After the strip material passes over

rollers

138 and 140, it engages another pair of

guide elements

152 and 154 mounted on bracket 156. This bracket is also supported on the transversely movable carriage. The strip material which passes over roller 140 now passes between

feed rollers

158 and 160, which are mounted, respectively, on

shafts

162 and 164. Shaft-162 is journaled into bearings166, and shaft 164 is journaled into bearings 168.

By the same token, the strip material which passes over roller 138 now passes between

feed rollers

170 and 172 after engaging still another guide element 174. This last mentioned guide element is supported on bracket 176, which is mounted on the transversely movable carriage.

Rollers

170 and 172 are themselves mounted, respectively, on

shafts

178 and 180, and these shafts are journaled into bearings 182 and 184.

A motor 186 mounted on the transversely movable carriage provides the power for driving

rollers

138, 140, 158 and 170. This motor includes a speedreducing gear box with an output shaft 188 to which a sprocket 190 is secured. Shaft 142 also carries a sprocket 192, shaft 144 carries a sprocket 194, shaft 162 carries a sprocket 196, and shaft 178 carries a sprocket 198. Inter-connecting all of these sprockets,

' 190, 192, 194, 196 and 198 is a drive chain 200, and

it will be noted that an idler sprocket 202 is also engaged by said chain. This idler is adjustably mounted to apply adequate tension to the drive chain and to hold it in operative engagement with the several sprockets last above listed. The result is that motor 186 causes synchronized rotation of

sprockets

192, 194, 196 and 198 and their

respective rollers

138, 140, 158 and 170.

Rollers and 172 are neither driven nor driving rollers, except to the extent that they frictionally engage rollers 158 and (or the strip material between them, that is between

rollers

158 and 160 and between rollers 170 and 172). Such frictional engagement causes

rollers

160 and 172 to rotate at the same surface speed as

rollers

158 and 170.

Rollers

160 and 172 are pressure rollers which hold the strip material in nonslipping engagement with said

rollers

158 and 170. The pressure which

rollers

160 and 172 exert upon the strip material is effected by means of

inclined planes

204 and 206, respectively. Shafts 164 and are provided with collars 210 and 212, which ride, respectively, on

inclined planes

204 and 206. Gravity urges them in the direction of

rollers

158 and 170, and a relatively tight engagement is provided between

rollers

158 and 160, as well as between

rollers

170 and 172. Leaf springs 214 and 216 bear upon collars 210 and 212 and

springurge rollers

160 and 172 in the direction of

rollers

158 and 170. When feeding device 130 operates, one or more ends of strip material are fed between

rollers

158 and 160, and one or more ends of strip material are fed between

rollers

170 and 172, and the frictional engagement of said strip material between said rollers causes the strip material to be pulled from its source and fed downwardly toward the receptacle-supporting platform 220.

Receptacle-supporting platform 220 is a generally rectangular platform which is provided at its four corners with nut elements 222. These nut elements engage threaded rods 224. These threaded rods are journaled into bearings 226 at their lower ends and bearings 228 at their upper ends, these bearings being supported by frame of the machine. It will be seen that each threaded rod 224 has a sprocket 230 at its lower end, and interengaging all of said sprockets is a chain 232. This chain is driven by a motor 234 having speedreducing and reversible gears and a sprocket 236 which engages said chain. The motor is mounted on frame 10.

What has now been described is an elevating mechanism for raising and also lowering the the receptaclesupporting platform. When motor 234 is energized, it causes chain 232 to rotate the sprockets on the threaded rods, and it thereby causes rotation of said threaded rods. When the reversing mechanism causes rotation of the sprockets on the threaded rods in one direction, platform 220 will be caused to rise. When the reversing mechanism causes said sprockets to rotate in the opposite direction, platform 220 will be caused to descend. As has above been indicated, at the commencement of a container-filling operation platform 220 is moved to an elevated position as shown, for example, in FIG. 8. Containers 240, shown in FIG. 8, are, of course, in their upper-most positions at the commencement of the filling operation, since they are supported by the elevated platform. At the end of a filling operation the pladorrn is at its lowermost position, as shown in FIG. 9, and so are containers 240. FIG. 8 shows the containers empty and FIG. 9 shows them full.

The switch control mechanism for controlling the travel of the longitudinally and transversely movable carriages will now be described. Starting with the longitudinally movable carriage 22, it will be observed that there are four

switches

250, 252, 254 and 256, on frame 10 adjacent said longitudinally movable carriage. A switch-actuating element 258 is mounted on carriage 22 for engagement with

switches

250, 252, 254 and 256.

Switches

250 and 254 are in circuit with electromagnetic clutch element 94.

Switches

252 and 256 are in circuit with electromagnetic clutch element 106.

The sequence of operation of these four switches is as follows: When switch 250 is actuated it closes the circuit to electromagnetic clutch element 94 and energizes said element and causes it to engage element 96 on gear 92, thereby causing longitudinally movable carriage 22 to move in one direction, say rightwardly as viewed in FIG. 8. When carriage 22 approaches but does not actually reach its extreme rightward position as viewed in FIG. 8, switch 254 is actuated, and this deenergizes clutch element 94 and disengages it from clutch element 96. The longitudinally movable carriage will continue its rightward movement under its own momentum until it reaches a spring bumper or cushioning element 260 which will shortly be described in greater detail. This cushioning element absorbs the kinetic energy of the moving carriage and operates to reverse its direction of travel.

Synchronized with the operation of this cushioning device is switch 256. Switch-actuating element 258 engages switch 256 and thereby closes the circuit to electromagnetic clutch element 106, energizing said element and causing it to engage clutch element 108. This, in cooperation with spring cushioning element 260, reverses the direction of travel of carriage 22 and causes it to move leftwardly as viewed in FIG. 8. When the carriage approaches but before it reaches its extreme leftward position as shown in FIG. 9, switch-actuating element 258 will engage switch 252 and thereby deenergize electromagnetic clutch element 106 and disengage said clutch element from clutch element 108. The longitudinally movable carriage will continue its leftward movement under its own momentum until it reaches and engages another spring bumper or cushioning device 262. As has above been described with respect to spring cushioning element 260, spring cushioning element 262 performs the function of absorbing the kinetic energy of the longitudinally movable carriage and reversing its direction of travel.

Synchronized with this action of the spring cushioning element 262 is switch 250. When this switch is engaged by the switch-actuating element 258, it closes the circuit to electromagnetic clutch element 94 and thereby energizes said clutch element and causes it to reengage clutch element 96. This, coupled with the action of spring cushioning element 262, has the effect of reversing the direction of travel of longitudinally movable carriage 22. This sequence is repeated as long as the machine is in operation, and the longitudinally movable carriage 22 is thereby caused to reciprocate relative to the frame of the machine.

It will now be understood that the motor drive which drives the longitudinally movable carriage through

clutch elements

94, 96 and 106, 108 is a variable speed drive which may be set to operate at any suitable or required speed. Illustrative is a rheostat-controlled electric motor drive. This is a conventional device for increasing or decreasing the speed of rotation of an electric motor. There are other conventional devices for achieving the same result, and they may be used for the same purpose, as desired.

No special kind of bumper or spring cushioning device is needed to absorb the impact of the longitudinally movable carriage at the time its direction of travel is reversed. However, a fully adjustable cushioning device is preferred for synchronization with the reversing

switches

250 and 256 and for resonance, so to speak, with the motion of the carriage. In the preferred form of this invention this adjustment is two-fold: It adjusts tension and it adjusts position. More specifically, each cushioning device 260, 262 (there may be one or more at each end of travel of the longitudinally movable carriage) consists of a coiled compression spring 264 secured to the end of a bolt 266 threaded to a nut-type mounting 268 which is bolted or otherwise secured to the frame 10 of the machine. Bolt 266 may be rotated in either direction relative to mounting 268 in order to adjust the axial position and tension of spring 264. The length of the spring, its build-in spring tension, the time of its engagement with the longitudinally movable carriage, and other obvious factors will determine the cushioning effect of the bumper relative to the mass and momentum of the carriage. In the preferred form of this invention, two such spring cushioning devices are mounted at each end of the frame of the machine, but this and the type of cushioning device used are both matters of machine design and may be modified in accordance with the requirements of each particular installation.

Referring now to the switch control mechanism for controlling the travel of the transversely movable carriage 32, it will be understood that this carriage normally moves at a far slower rate of speed than the longitudinally movable carriage. Consequently, a less elaborate reversing mechanism is required for the transversely movable carriage, since it develops relatively little momentum during the course of its travel in both transverse directions. Accordingly, there is no need of providing a bumper or spring cushioning element to absorb the kinetic energy of the transversely movable carriage at the end of each passage in either direction.

The reversing action with respect to the transversely movable carriage is direct: Two switches, 270 and 272 respectively, are mounted on the frame of the longitudinally movable carriage 22, and switch-actuating element 274 is mounted on the frame of transversely movable carriage 32. As the transversely movable carriage moves in one direction and reaches its extreme position in that direction, switch-actuating device 274 will engage switch 270 which is in circuit with one of the electromagnetic clutches which drive said carriagef'lhis actuation of switch 270 will deenergize said electromagnetic clutch and energize the reversing electromag-, netic clutch, thereby producing a reversal of movement of the transversely movable carriage without the momentum of interval previously discussed in relation to the longitudinally movable carriage. When the transversely movable carriage reaches its extreme position traveling in the opposite direction, switch-engaging element 274 will engage switch 272 and deenergize the second mentioned electromagnetic clutch and reenergize the first mentioned electromagnetic clutch. This will produce a reversal of direction of movement of the transversely movable carriage, again without the momentum phase of the longitudinally movable carriage.

It will also be understood that in many instances it is necessary for the longitudinally movable carriage to make a number of reciprocatory passes longitudinally of the frame of the machine and each single transverse pass of the transversely movable carriage. Also,

many instances a dwell time for the transversely mov able carriage is needed at each extreme end of its travel in either direction. This would be necessary in these instances in order to prevent uneven laying of the festooned material in the receptacles. More specifically, it would prevent a build-up of layers of material centrally of the receptacles, with relative voids along the sides.

In the preferred form of this invention time delay devices 276 are incorporated into the circuits controlled by

switches

270 and 272. Thus, when switch 270 is actuated to deenergize the first mentioned electromagnetic clutch which drives the transversely movable carriage, the second mentioned electromagnetic clutch driving the same carriage but in the opposite direction will not concurrently be energized. Instead, time delay device 276 will operate to prevent energizing of the second mentioned electromagnetic clutch for a time interval which is selected by the operator of the machine. The same time delay operation will occur when switch 272 is actuated to deenergize the second mentioned electromagnetic clutch and energize the first mentioned clutch. I

The several carriage travel control elements which have above been discussed are individually adjustable in various respects. For example, each of the motor drives is adjustable as to speed of operation. This feature applies to the motor drive on the material-feeding section of the machine, the motor drive which operates the longitudinally movable carriage, the motor drive which operates the transversely movable carriage, and the motor drive which operates the platform elevator mechanism. As has above been mentioned, rheostatcontrolled motors may be used for this purpose, but

other speed-increasing or reducing means may be'used, electronic, mechanical and, hydraulic. These are conventional devices which are available to machine designers.

Another series of adjustments relates to the distance of travel of each of the two'carriages. Switches 250, 252,254 and 256 may be adjustably located on frame 10 of the machine, to lengthen or shorten the extent of travel of the longitudinally movable carriage in either direction. This may be done by adjustably mounting these switches on a rod 251, which is secured to the frame of the machine. Similarly, switches 270 and 272 may be adjustably located on the frame of the longitudinally movable carriage 22, in order to lengthen or shorten the travel distance of the transversely movable carriage. Again, this may be done by adjustably mounting these switches on a rod 271, which is secured to the frame of the longitudinally movable carriage. The time delay devices 276 are, of course, obviously adjustable to provide for greater or smaller time intervals at each reversal of direction of travel of the transversely movable carriage.

The operation of the machine is apparent from the above description. As strip material is fed to the machine from a conventional source e.g., a slitting machine it passes through and is fed by the feeding section of the machine into receptacles 240 which are located on platform 220. As this feeding operation takes place, the longitudinally movable carriage reciprocates in longitudinal direction and the transversely movable carriage reciprocates in transverse direction, and platform 220 moves downwardly to keep pace with the filling of the receptacles. When each group of receptacles is filled with festooned material, it is removed from platform 220 and a group of empty receptacles is substituted therefor. The platform is raised to its elevated position, and the above described procedure is repeated.

The foregoing is illustrative of a preferred form of this invention, and it will be understood that it may be modified and altered for design purposes and to fill individual needs and requirements within the broad scope and spirit of the appended claims.

WHAT IS CLAIMED IS:

1. A machine for festooning stn'p material and feeding it into a container, said machine comprising:

a. an elevated frame;

b. a container platform mounted below said elevated frame;

0. a first carriage mounted on said elevated frame above said container platform for longitudinal reciprocating movement on said elevated frame;

d. reciprocatory drive means between said elevated frame and said first carriage, causing longitudinal reciprocating movement of said carriage relative to said elevated frame and said container platform;

e. a second carriage mounted on said first carriage above said container platform for transverse reciprocating movement on said first carriage;

f. reciprocatory drive means between said first and second carriages, causing transverse reciprocating movement of the second carriage relative to the first carriage and the container platform; and

g. stn'p material feed means mounted on said second carriage for integral movement therewith above and relative to said container platform;

h. whereby strip material may be fed both longitudinally and transversely into at least one container on said container platform and laid therein in horizontal layers of longitudinal courses;

i. the reciprocatory drive means between the elevated frame and the first carriage comprising adjustable, infinitely -variable speed reciprocatory drive means; and

j. the reciprocatory drive means between the first and second carriages comprising adjustable, infinitely variable speed reciprocatory drive means;

k. each of said infinitely variable speed reciprocatory drive means being independently adjustable, so that the speed of longitudinal movement of the first carriage and the speed of transverse movement of the second carriage may be independently adjusted, to adjust the spacing between the longitudinal courses.

2. A machine in accordance with claim 1, wherein each of the variable speed reciprocatory drive means comprises:

a. a rheostat-controlled electric motor having speedreducing drive gears; and

b. electromagnetic clutch-operated gear-reversing means.

3. A machine for festooning strip material and feed ing it into a container, said machine comprising:

a. an elevated frame;

b. a container platform mounted below said elevated frame;

c. a first carriage mounted on said elevated frame above said container platform for longitudinal reciprocating movement on said elevated frame;

g. strip material feed means mounted on said second carriage for integral movement therewith above and relative to said container platform;

i. the reciprocatory drive means between the elevated frame and the first carriage comprising adjustable, infinitely variable speed reciprocatory drive means; and

k. each of said infinitely variable speed reciprocatory drive means being independently adjustable, so that the speed of longitudinal movement of the first carriage and the speed of transverse movement of the second carriage may be independently adjusted to adjust the spacing between the longitudinal courses;

. each of the variable speed reciprocatory drive means comprising:

i. a rheostate-controlled electric motor having speed-reducing drive gears, and

ii. elecu'omagnetic, clutch-operated gear-reversing means; A

m. each electromagnetic clutch-operated gearreversing means comprising:

i. forward gears;

ii. reverse gears;

iii. a first electromagnetic clutch engageable with the forward gears to connect them to the speedreducing drive gears of the associated motor in order to drive the associated carriage in one direction; and

iv. a second electromagnetic clutch engageable with the reverse gears to connect them to the speed-reducing drive gears of said associated motor in order to drive "said associated carriage in the opposite direction.

4. A machine in accordance with claim 3, wherein for each electromagnetic clutch-operated gear-reversing means:

a. first switch means are provided in circuit with the first electromagnetic clutch to disengage it from the forward gears adjacent the end of travel of the associated carriage in each direction; and

b. second switch means are provided in circuit with the second electromagnetic clutch to cause said clutch to engage the reverse gears at the end of travel of said associated carriage in each direction;

c. whereby each variable speed reciprocatory drive means is disengaged from its associated carriage before said carriage reaches the end of travel in each direction and said variable speed reciprocatory drive means reengages the carriage at the end of such travel in each direction in order to reverse its direction of travel.

5. A machine in accordance with claim 4, wherein:

a. the switch means connected to the electromagnetic clutch-operated gear-reversing means which is associated with the first carriage operate between the elevated frame and the first carriage; and

b. the switch means connected to the electromagnetic clutch-operated gear-reversing means which is associated with the second carriage operate between the first and second carriages.

6. A machine in accordance with claim 4, wherein:

spring cushioning means are provided between the elevated frame and the first carriage to cushion the impact between them between the time the first electromagnetic clutch of the electro-magnetic clutch-operated gear-reversing means associated with the first carriage is disengaged from the forward gears thereof adjacent the end of travel of said first carriage in each direction,,and the time the second electromagnetic clutch of said electromagnetic clutch-operated gear-reversing means engages the reverse gears thereof at the end of travel of said first carriage in each direction.

7. A festooning machine having:

a. independently adjustable, infinitely variable-speed material feeding means;

b. independently adjustable, infinitely variablespeed, variable-distance reciprocating drive means which causes the material feeding means to reciprocate longitudinally; and

c. independently adjustable, infinitely variable-speed, variable-distance reciprocating drive means which said material receptacle support. v

9. A festooning machine in accordance with claim 7,

wherein:

a. an adjustable time delay means is connected to the reciprocating drive means which causes the material feeding means to reciprocate transversely;

b. said time delay means being operative to delay the transverse reciprocation of the material feeding means for selected time intervals at each change of direction of travel thereof.

Claims

1. A machine for festooning strip material and feeding it into a container, said machine comprising: a. an elevated frame; b. a container platform mounted below said elevated frame; c. a first carriage mounted on said elevated frame above said container platform for longitudinal reciprocating movement on said elevated frame; d. reciprocatory drive means between said elevated frame and said first carriage, causing longitudinal reciprocating movement of said carriage relative to said elevated frame and said container platform; e. a second carriage mounted on said first carriage above said container platform for transverse reciprocating movement on said first carriage; f. reciprocatory drive means between said first and second carriages, causing transverse reciprocating movement of the second carriage relative to the first carriage and the container platform; and g. strip material feed means mounted on said second carriage for integral movement therewith above and relative to said container platform; h. whereby strip material may be fed both longitudinally and transversely into at least one container on said container platform and laid therein in horizontal layers of longitudinal courses; i. the reciprocatory drive means between the elevated frame and the first carriage comprising adjustable, infinitely variable speed reciprocatory drive means; and j. the reciprocatory drive means between the first and second carriages comprising adjustable, infinitely variable speed reciprocatory drive means; k. each of said infinitely variable spEed reciprocatory drive means being independently adjustable, so that the speed of longitudinal movement of the first carriage and the speed of transverse movement of the second carriage may be independently adjusted, to adjust the spacing between the longitudinal courses.

2. A machine in accordance with claim 1, wherein each of the variable speed reciprocatory drive means comprises: a. a rheostat-controlled electric motor having speed-reducing drive gears; and b. electromagnetic clutch-operated gear-reversing means.

3. A machine for festooning strip material and feeding it into a container, said machine comprising: a. an elevated frame; b. a container platform mounted below said elevated frame; c. a first carriage mounted on said elevated frame above said container platform for longitudinal reciprocating movement on said elevated frame; d. reciprocatory drive means between said elevated frame and said first carriage, causing longitudinal reciprocating movement of said carriage relative to said elevated frame and said container platform; e. a second carriage mounted on said first carriage above said container platform for transverse reciprocating movement on said first carriage; f. reciprocatory drive means between said first and second carriages, causing transverse reciprocating movement of the second carriage relative to the first carriage and the container platform; and g. strip material feed means mounted on said second carriage for integral movement therewith above and relative to said container platform; h. whereby strip material may be fed both longitudinally and transversely into at least one container on said container platform and laid therein in horizontal layers of longitudinal courses; i. the reciprocatory drive means between the elevated frame and the first carriage comprising adjustable, infinitely variable speed reciprocatory drive means; and j. the reciprocatory drive means between the first and second carriages comprising adjustable, infinitely variable speed reciprocatory drive means; k. each of said infinitely variable speed reciprocatory drive means being independently adjustable, so that the speed of longitudinal movement of the first carriage and the speed of transverse movement of the second carriage may be independently adjusted to adjust the spacing between the longitudinal courses; l. each of the variable speed reciprocatory drive means comprising: i. a rheostat-controlled electric motor having speed-reducing drive gears, and ii. electromagnetic, clutch-operated gear-reversing means; m. each electromagnetic clutch-operated gear-reversing means comprising: i. forward gears; ii. reverse gears; iii. a first electromagnetic clutch engageable with the forward gears to connect them to the speed-reducing drive gears of the associated motor in order to drive the associated carriage in one direction; and iv. a second electromagnetic clutch engageable with the reverse gears to connect them to the speed-reducing drive gears of said associated motor in order to drive said associated carriage in the opposite direction.

4. A machine in accordance with claim 3, wherein for each electromagnetic clutch-operated gear-reversing means: a. first switch means are provided in circuit with the first electromagnetic clutch to disengage it from the forward gears adjacent the end of travel of the associated carriage in each direction; and b. second switch means are provided in circuit with the second electromagnetic clutch to cause said clutch to engage the reverse gears at the end of travel of said associated carriage in each direction; c. whereby each variable speed reciprocatory drive means is disengaged from its associated carriage before said carriage reaches the end of travel in each direction and said variable speed reciprocatory drive means reengages the carriage at the end of such travel in each direction in order to reverse its direction of travEl.

5. A machine in accordance with claim 4, wherein: a. the switch means connected to the electromagnetic clutch-operated gear-reversing means which is associated with the first carriage operate between the elevated frame and the first carriage; and b. the switch means connected to the electromagnetic clutch-operated gear-reversing means which is associated with the second carriage operate between the first and second carriages.

6. A machine in accordance with claim 4, wherein: spring cushioning means are provided between the elevated frame and the first carriage to cushion the impact between them between the time the first electromagnetic clutch of the electro-magnetic clutch-operated gear-reversing means associated with the first carriage is disengaged from the forward gears thereof adjacent the end of travel of said first carriage in each direction, and the time the second electromagnetic clutch of said electromagnetic clutch-operated gear-reversing means engages the reverse gears thereof at the end of travel of said first carriage in each direction.

7. A festooning machine having: a. independently adjustable, infinitely variable-speed material feeding means; b. independently adjustable, infinitely variable-speed, variable-distance reciprocating drive means which causes the material feeding means to reciprocate longitudinally; and c. independently adjustable, infinitely variable-speed, variable-distance reciprocating drive means which causes the material feeding means to reciprocate transversely concurrently with its longitudinal movement.

8. A festooning machine in accordance with claim 7, wherein: a. a material receptacle support is mounted below the material feeding means for movement toward and away therefrom; and b. drive means is connected to said material receptacle support for moving it away from said material feeding means as the material is fed from said material feeding means to a material receptacle on said material receptacle support.

9. A festooning machine in accordance with claim 7, wherein: a. an adjustable time delay means is connected to the reciprocating drive means which causes the material feeding means to reciprocate transversely; b. said time delay means being operative to delay the transverse reciprocation of the material feeding means for selected time intervals at each change of direction of travel thereof.