US1778433A - Adjustable apron feed for glue machines - Google Patents

Description

Oct. 14,; 1930. I w. A. SAATMAN ADJUSTABLE APRON FEED FOR GLUE MACHINES Original Filed July 24, 1926 5 Sheets-Sheet 1 Oct. 14. 1 930. w. A. SAATMAN ADJUSTABLE APRON FEED FOR GLUE MACHINES Original Filed July 24, 1926 5 Sheets-Sheet art/V704, Q. PM

Oct. 14, 1930. w, SAATMAN 1,778,433

ADJUSTABLE APRON FEED FOR GLUE MACHINES Original Filed y 1926 5 Sheets-Sheet 3 I llfllllli ijizgifl 73 F7 fl 1 W4 7' u I III 1/ Ot. 14, 1930. w. A. SAATMAN ADJUSTABLE APRON FEED .FOR GLUE MACHINES Original Filed July 24, 1926 5 Sheets-Sheet 4 Oct. 14, 1930. w. A. SAATMAN ADJUSTABLE APRON FEED FOR GLUE MACHINES Original Filed July 24, 1926 5 Sheets-Sheet 5 Patented Oct. 14, 1930 UNITED STATES PATENT OFFICE WALTER A. SAATMAN, OF ROSLYN, PENNSYLVANIA ADJUSTABLE APRON FEED FOR GLUE MACHINES Application filed July 24, 1926, Serial No. 124,650. Renewed March 12, 1930.

My invention relates to machines for gluing and delivering sheets of paper for appli cation usually to boXes in box-making machines and then called wraps, but capable of broader application, and has particular reference to the motion of the delivery mechanism used to deliver glued wraps from the gluing machine to the box-wrapping machine.

A purpose of my invention is to make ad justable the distance of movement of the conveyor apron corresponding to the gluing of each wrap.

A further purpose is to control the length of time between the application of the glue to the wrap, and the application of the glued wrap to a box, by controlling the distance of feed of the conveyor per stroke of the wrapping machine. p

29 A further purpose is to vary the number of glued wraps between the glue machine and box-wrapping machine, usually having more glued wraps upon the conveyor when the wraps are small than when they are large.

Further purposes will appear in the specification and in the claims.

Figure 1 is a transverse section through driving and feeding mechanism of a glue machine, and illustrates one form of my inven- 0 tion. The section is upon line 1-1 of Figure 2, looking in the direction of the arrows.

Figure 2-is a section taken upon the line 2-2 of Figure 1 looking in the direction of the arrows.

Figure 8 is a fragmentary section of Figure 2 taken upon the line 3-3 looking in the direction of the arrows.

' Figure 4e is a section of Figure 2 on the line looking in the direction of the arrows.

"* Figure 5 is a section of Figure 4: taken upon the line 5-5 and looking in the direction of the arrows.

Figure 6 is a section upon the line 6 -6 of F iqure 4 looking in the direction of the arrows.

Figure is a side elevation of the conveyor structure shown by me.

Figure 8 is a section of Figure 7 tak n upon theline 8 8 looking in the direction of the arrows. a

Figure 9 is a section taken on line 99 of Figure 7 looking in the direction of the arrows. 7

Like numerals refer to like parts in all figures.

Describing in illustration and not in limitation and referring to the drawings A suitable motor, F is coupled at F to a worm F mounted in bearings F 5 within gear casing F upon the left side of the gluing machine as viewed from the front.

The shaft C is extended through the gear casing and is reduced in diameter at F and also at F, see Figure 2. Upon the reduced portion F of the shaft C is mounted a 05' sleeve F 9 free to rotate on the shaft and supporting a worm gear F meshing with the worm and continuously driven by it during the operation of the motor. The gear and sleeve as a unit have bearing upon the outside 76 of the shaft when the shaft C is not in operation and travel with it at the same speed when the shaft C is driven.

The worm gear F is extended to the right in Figure 2 to form an integral gear F which also rotates continuously with themotor. The worm gear and gear F con sidered as a unit, are hollow and give place within them for a movable clutch member F having inset wooden clutch bearing faces F terminating at an angle, and for a follower disc F. The movable clutch member fits within a co-operating clutch surface F and is supported for longitudinal clutch engaging movement along the reduced portion F of shaft C by a hub sleeve F which has longitudinal movement along but no rotation on the shaft.

The follower disc F fits within a recess F upon the inside of the gear F On one face it is recessed at F at intervals to provide seats for spiral springs F by which it presses the movable clutch member towards clutch engaging position, which therefore is the normal position of this movable clutch member except as disengaged by other means. A stud F in the follower disc passes through an opening F in the clutch member and drives the clutch member. It is free to slide in the opening to accommo- 'date differences in spacing between thenn On the opposite side the disc F is grooved to form the internal cam C The .disc is hubbed at F to give additional support upon the shaft and is keyed to the shaft at F The same key is used to fasten to the shaft a gear E which rotates with the shaft.

Upon the shaft C to the right of the gear F in Figure 2, Sheet 2, is mounted a hub F upon which is carried the gripper cam C v In order to provide for continuous rotation of the gluing mechanism the teeth of gear F engage the teeth of the gear F splined at F to a shaft F rotatable and also movable lon itudinally in bearings F F in the gear case and frame respectively. The shaft F carries an enlarged end F upon which is mounted a clutch member F adapted to engage the clutch member E The end of the shaft F is grooved at F for engagement by a fork or projection F upon a hand lever arm F pivoted at F in a projection F from the gear casing. The shaft may thus be slid back out of clutch engagement with" the clutch'member E and is'hel'd'in its several positions by a latch F fitting into openings F in the shaft and spring pressed into engagement with the shaft by a spring F secured to the gear hu F by screws F When the gluing mechanism is intended to be disconnected, whether preparatory to swinging it out of its position or not, the hand lever F is thrown to the left in Figure 2 to release the clutch.

As will be seen the feed cylinder and the gluing mechanism have continuous opera-' tion during'the time the clutch member F is in engagement with the clutch surface F Thefeed cylinder is stopped atthe end of each rotation andis held until released by tripping mechanism provided. On the other hand the apron isintended to be actuated during a part only of the time of rotation of the. feed cylinder travel, and though it must start'at the same position of feed cylinder travel, we have provided adjustment of theertent'of feed to correspond with differences inthe lengths of the wraps as hereinafter described.

" "The drive for thcfaproa conveyor I With, clutch engagement the gear F 4 is driven 'continuously.- As will be seen from Figure 1, Sheet 1," 'th'egear isone of a pair of intermittent I stop-motion 7 gears whose mating. gear F is carried by astud E (Figurei5) secured in the frame of the machine by nut Ff bearing against-washer F. 1 This stud'carries also a gear F which is vrigid withand preferably integral withintermittentig a t-2 1 th Outer ge r and F, F is the driving gear.- It is also the larger gear and, through each carries the same number of teeth, the teeth occupy a smaller part of the circumference of gear F than of gear F to permit the lost motion between the two gears to take place in the second outer gear F rather than within the first which must travel'with the shaft. The outer gear F therefore, in conjunction with teeth F has a relatively large free surface F of diameter approximately the pitch diameter of the teeth, which surface engages with a small arc'uate portion F between the ends of teeth F upon gear F during which engagement gear F is held in stationary position. These gears are frequently called intermittent gears and are comparable with the intermittent gears of commerce.

The directions ofrota'tion are shown by the arrows in Figure 1. As in the case of other features of our invention the form shown is a selected form only among many which will serve the purpose, which brings the mating gears around to the same position for each turn and permits lost motion between them so that the driving gear can rotate continuously so long as the shaft rotates while the driven gear E is provided 'with a rest or dwell.

For the purpose of smoothing the beginning of the driving and driven engagement of the intermittent gears, we provide a quickening contact between the pin F carried by the rear of the disc F and the walls F of slot in projection F from the otherwise free face of gear F The projection is held against rotation upon the gear by screws F Just before engagement of the teeth of the driving intermittent gear with the teeth of the driven intermittent gear, the pin F enters the slot of the revoluble pin F and gradually increases the speed of this pin and hence of the driven intermittent gear until the teeth of the two intermittent gears have met and mesh thesame speed The lostmotion between the walls of the slot and thepin permits the driven intermittent ear to s ee'd up withrespect to-thepii in the driving ear from this point.

Each rotation of; the driven intermittent gear F causes a rotation of the gear F (Figure 2 andigure 6), rigid with it and causes considerably: more rotation f a gear F meshing with gear 1?, since F is much larger than gear F Gear F is rigid with face clutch and face clutch rotate-freely unona shaft e which is keyed at F to J to sleeve Ff 'terminating in a fa F and..,between them is a grooveorneck 1?. Both the gear clutch F is driven for a. part only of the time of rotation of the gear F The face clutch F and its integral gear F are shifted by means of an arm F mounted upon and guided by the pin F sliding in opening F and spring pressed toward clutch engaging position by a spiral spring F The spring presses against a shoulder F upon the head F of the pin F and holds the clutch faces of F and F 62 normally in engagement. The head and spring lie within a pocket F in the frame of the machine. The gear F 55 is given addi tional width to ensure continued complete engagement with the teeth of gear F The head F 68 upon pin F 64 projects beyond the frame for operating engagement by one end F of a rocking arm F pivoted upon a pin F 72 rigid with the frame for the purpose of disconnecting the two clutch faces F and F The pin F is held in position by the set screw F The lower end F of this rocking lever F engages a pin F (Figure 5) supported in sleeve F 76 which is carried by a sliding rod F 77 operated by handle F The rod is notched at F to receive a latch bolt'F pressed to position by spring F The rod slides in a guide formed between the boss F in the frame and a plate F 83 secured to the frame. As will be noted the spring pressed pin F holds the pin F normally in position shown in Figure 5 with its end F projecting beyond the plate at differing distances from the axis of the stud F 42 according to the setting of the sliding rod.

The pin end F 84 thus projects in the patch of a stepped face cam F so as to be pressed longitudinally (away from the observer as it appears in Figure 5) by any one ofthe stepped cam faces F F Figure 4, according to the radial distance from the axis of the stud which is also the axis of the cam.

The cam in the construction seen in Figure 5 is mounted upon a sleeve F integral with gear F The gear F is also mounted upon this sleeve and for convenience in assemblage the sleeve and gear F 46 are held to the pin by a separate head F screw 92 and pin F Vhatever the position of the pin F 75 corresponding to different settings of the rod F", the pin is engaged by oneof the face cam surfaces F F with the same effect of disconnecting the clutch faces F and F and, hence, stopping the conveyor apron movement. This disengagement is maintained until the cam has turned to the position shown in Figure 4: where the end'F of the pin F is released from the cam at the cam edge F when the re-engagement of the clutch faces seen in Figure 6 starts the apron conveyor action.

Because the apron conveyor should start at the same time in each movement, whatever its distance of movement, the edge F extends nearly radially to allow the pin to be released from the face cam at the same angular position of the face cam within the adjustment radially of the rod and pin F. This uniform starting position for the apron conveyor is timed to correspond with the beginning of delivery of a wrap from the glue-applying roll to the apron and the speed of the apron is arranged to correspond with the speed of movement of the wrap so that the apron will receive the length of the wrap continuously without tendency to fold or slide the wrap upon the apron.

lVith the uniform starting position of the apron as indicated, the difference in radial distance of the pin F 75 from the axis of the cam and stud pin F 43 is effective for the purpose of adjusting the length of movement of the apron conveyor before disconnection of its driving clutch F As will be seen from Figure a, the different angular distance about I the cam in a counter-clockwise direction between the edge F and the several face cam surfaces F .F represent different proportions of the time of rotation of the cam during which the conveyor feed apron is operated.

ZL an clutch tripping mechanism The disconnection of the clutch faces F from the co-operating clutch surface F the main clutch mechanism of the machine, may be accomplished in two ways, the one tripping to stop the feeding mechanism after each complete rotation of the feed cylinder and the other to stop the feeding mechanism independently of movement of the tripping lever.

The hub F is grooved at F 95 to provide a seat for a radially projecting rib F upon a pin F passing'through the sleeve F 9 and hencerotating with the worm gear F. This pin F 97 is normally spring pressed toward the left in Figure 2 by reason of the spring pres sure against the movable clutch member F but, if moved to the right, carries the movable clutch member longitudinally of the shaft C and against the pressure of the springs F Vithin the path of revolution of the rod F, is located a cam F rigid with a bearing pinF which turns within the gear casing at F The construction is best seen in Figures 2 and 3.

The cam carries a cam face F which is swung by turning of the pin F 99 into or out of the path of movement of rod F but is normally pressed into the path of movement of this rod F by a nose F spring pressed at F Upon the outer end of pinF, an operating lever F is located by which the cam face F is swung out of tripping position, the spring pressed nose returning it to tripping position so as. to throw the clutch. This releases the rod'F from the cam, permitting main clutch engagement and resulting in corresponding complete rotation of the movable clutch member F and hence of shaft C until the rod F comes around again to clutch disengaging position Where its engagement with the cam face F releases the clutch. Each tripping movement of lever F therefore permits one complete rotation of the feed cylinder with corresponding movement of the connected parts relating to the wrap feeding mechanism and including the feed apron. The extent ofmovement of the feeding mechanism is the same, but the extent of movement of the apron varies according to the setting of the pin-F When it is desired to shut off the machine so. that its feeding mechanism will not respond to movement of the tripping lever, this-is accomplished by turning a screw F as by hand wheel F so as to cause its end to bear upon rod F at the center of shaft 0 This rod engages a transverse bar F which terminates at opposite ends in sleeve F and passes through an elongated opening F in the shaft. Pressure upon the bar by reason of the screw releases the main clutch and holds it released against the pressure of springs'F -without regard to the position of the tripping lever.

If the tripping lever F be held in turned position, the feeding mechanism will operate continuously. The gluing rolls are independently controlled by lever F and in addition for their movement depend upon maintainingthe gluing mechanism in closed position to engage clutchmember E and E During each rotation of the feed cylinder, the intermittent gear F causes movement during part of the time to intermittent gear-F with corresponding rotation of the step cam F and of the gears F and F The step cam controls the movable clutch member F to permit engagement of this clutch for a part ofthe time of rotation of gear F Suitable oil cups are provided for the mechanism such as are shown at-F and drainage for the gear case takesplace by removal of plug F1 I v I V The ajoron Goiweyor-fgroup G The conveyor mechanism for the wraps is best shown in'Figures Tand 8. I J

The shaft F is sue aorted at its end 0 H i. P posits to the clutch r in a bearing Gr and adacent this bearingjcarries a roller G formone end of a conveyor support of which the opposite "roller is located Lt-G Adjacent the bearing and preferably at both sides of the 'conveyor'belt are mounted pipes Gt.

fitting in sockets G rigid with the frame. The'pipes are pinned within the sockets by horizontal pins G and maybe adjusted slightly about. the'lpins to maintain them in any desired approach to horizontal position by set screws G passing through the sockets and bearing upon the upper rear ends of the Within the pipes G telescope pipes G which carry the bearings G for the shaft G upon which the roller G is mounted. What we have called pipes G may in factbe solid or hollow providing they give abutment to one end each of springs G which press against pinsG within the pipes G so as to stretch taut an apron conveyor belt G upon which the wraps are intended to'be determinals G at the end of table-supporting members G fittin g over. the pipes G and adapting the table to be slid to any desired position.

At an intermediate point along the length of one of the pipes, I mount abracket G by means of a sleeve clamp G held in place by set screw G so as to permit longitudinal movement and suficient swinging to secure accurate alignment in planes perpendicular to the apron. The bracket is provided with a bar G upon which fits a bearing G upon a bracket G of a reservoir G. The bearing is adjustable along the bar G and is held in adjusted position as to the setting along the bar and as to pressure by set screw.

At the lower end of the reservoir are provided standards G within which a shaft G is fixed by set screws G The shaft supports a roll G whose edge is V-shaped as at G This roll and its mechanism is adjusted by movement of the reservoir and its bracket along the rod so as to'place the V-shaped Wheel at approximately the center of the wrap as it is being, delivered and is for the purpose of creasing the wrap along the center of its length so as to prevent it from curling in a longitudinal direction. Within the reservoir is placed armoistened sponge. or similar device G to wipe" the edge of the wheel so as tokeep it from sticking to the paper and from depositing any, glue received upon. the paper;

The apron s placed in'position to receive the wraps as they are discharged, the glue side up,- from the'glue-applying roll. As

previously indicated theapron feedduring the time of discharge corresponds with the speed of movement of the wrap and the length of feed is adjustable so that it may be made to correspond approximately with'the length ofthe wrap. V

Since, the wraps mustremain upon the roll apron until they have been fed to the boX wrapping or other wrap using position for use, the length of feed of the apron for each wrap must-be made great enough to prevent undue drying of the glue upon the wraps where the machine is not worked at full speed or where for any other reason the wraps are not used promptly.

This length of feed of the apron for each gluing machine feed operation is controlled as indicated by the face cam.

It will now be apparent that I have devised a new and useful adjustable apron feed for glue machines which embodies the features of advantage enumerated as desirable in the statement of the invention and the above description, and that while I have, in the present instance, shown and described a pre ferred embodiment thereof which will give in practice satisfactory and reliable results, it is to be understood that this embodiment is susceptible of modification in various particulars without departing from the spirit or scope of the invention or sacrificing any of its advantages.

Having thus described my invention what I claim as new and desire to secure by Letters Patent is 1. In gearing, a motor, a worm driven thereby, a worm gear driven by the worm and having a clutch face therein, a clutch spring-pressed to separate therewith, a shaft within the clutch and turning with it, a feed member on said shaft, an intermittent gear carried by said shaft, a stud, a pair of gears on the stud, coupled together and one an intermittent gear engaging the first intermittent gear, a slidable gear engaging the second of the pair of gears, a clutch member rigid with the slidable gear, a co-operating clutch member, and clutch operating mechanism and connections for sliding the slidable gear, timed to engage the gears in a predetermined position of the feed member.

2. In gearing, a motor, a worm driven thereby, a worm gear driven by the worm and having a clutch face therein, a clutch spring-pressed to co-operate therewith, a shaft within the clutch and turning with it, a feed member driven by said shaft, a clutch controlled conveyor, intermittent gearing be tween the shaft and the driving clutch member of the conveyor clutch and automatic means for throwing the clutch.

3. In gearing, a motor, a worm driven thereby, a worm gear driven by the worm and having a clutch face therein, a clutch springpressed to co-operate therewith, a shaft within the clutch and turning with it, a feed member driven by said shaft, a clutch controlled mechanism, intermittent gearing between the shaft and the driving clutch member of said mechanism clutch, automatic means for throwing the clutch and an adjustment between the shaft and clutch for varying the length of time the clutch is engaged.

I. In a driving mechanism, a trip-operated clutch, a feed cylinder connected therewith, driving mechanism for one of the clutch members, gearing connected with that clutch member, mechanism driven by the gearing, a clutch between the gearing driven by the driven member of the first clutch, a conveyor operated thereby, a clutch between the said gearing and the conveyor, a plurality of clutch-release automatic operating mechanism for said clutch and selective means for applying any of said release mechanism to said clutch.

5. In a machine of the character described, driving mechanism, a belt conveyor, a clutch member connected with the conveyor, a movable co-operating clutch member, a lever controlling the position of the co-operating clutch member, a pin operating the lever, and a cam operating the pin to determine by cam actuation the proportionate time of operating of the machine during which the conveyor feeds.

6. In a. machine of the character described, driving mechanism, a belt conveyor, a clutch member connected with the conveyor, a movable co-operating clutch member, a lever controlling the position of the co-operating clutch member, a pin operating the lever, a plurality of cams adapted for engagement one at a time with the pin in different positions thereof, determining difierent extents of feed of the conveyor for each article fed from the machine and means for selecting the cam which engages with the pin.

7 In a machine of the character described, a driving mechanism, feeding mechanism driven thereby, a belt conveyor, a clutch member connected with the conveyor, a movable co-operating clutch member, a lever controlling the position of the co-operating clutch member, a pin operating the lever, a plurality of cams adapted to actuate the pin in differing pin position and for different lengths of time, one end of each of the cams registering with the same position of the feeding mechanism and means for moving the pin to engage selectively any one of the cams.

WVALTER A. SAATMAN.

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