US2659598A - Proportional sequence control for folders - Google Patents

Description

NOV. 17, 1953 R, McLAG N 2,659,598

PROPORTIONAL SEQUENCE CONTROL FOR FOLDERS Filed March 8, 1950 2 Sheets-Sheet 1 A B A A r Y 5 73 5e as 4542 27 I I o 4 5 E 3 25 '-""-26 63 e7 1 n j 1 FIG-I IN V EN TOR.

RUSSELL G. MCLAGAN ATTORNEYS 1953 R. G. MCLAGAN PROPORTIONAL SEQUENCE CONTROL FOR FOLDERS 2 Sheets-Sheet 2 Filed March 8, 1950 FIG-5 FIG-3 FIG-4 INVENTOR. RUSSELL G. MCLAGAN ATTORNEYS Patented Nov. 17, 1953 PROPORTIONAL SEQUENCE CONTROL FOR FOLDERS Russell G. McLagan, Milford, Ohio, assignor to The American Laundry Machinery Company,

a corporation of Ohio Application March 8, 1950, Serial No. 148,453

7 Claims.

The invention relates to a novel and improved sequence control device for the timed control of one or more operations on a traveling article. It will be specifically described with relation to its adaptation to the performance of proportional folding operations on flat work such as laundry towels, sheets, or the like.

The invention herein to be disclosed is especially adapted for use with a laundry flat work folding machine such as is disclosed in U. S.

Letters Patent No. 2,464,823, granted March 22, 1949, to C. S. Malott, Jr., for Folding Machine.

The Malott machine includes continuous conveyor means for conveying a series of sheets, towels, or the like to a position where the leading edge of each article feeds downwardly adjacent a reciprocatable horizontal folding arm. To perform the conventional one-quarter threequarter fold the arm remains inactive until one quarter of the article has passed it in a downward direction. At this moment the arm is rocked laterally past the plane of the descending article so that the article now drapes over the arm and continues to move downwardly on the other side of the arm. When the threequarter point of the article arrives in registry with the folder arm, the arm is again energized to move forwardly to its first described position, whereupon the last quarter of the article drapes downwardly over the first quarter. The article is then routed to pass between folding rolls.

The present invention may be adapted for controlling devices other than the folding machine just described, but for simplicity and convenience, and in no sense of limitation, my invention will be described with occasional reference to the Malott folding machine above briefly characterized.

An object of the invention is to provide a novel and improved sequence control device of positive mechanical type, electrically energized to initiate an operation on a moving article at a point or points having predetermined proportionate relationships to the length of the article.

.By the terms proportionate relationships or "proportional as used herein, I mean an operation at the quarter point, three-quarter point, or elsewhere fractionally of the article length.

A further object of the present invention is to provide a sequence control device of the type defined in the last preceding paragraph, comprising a plurality of control units, each unit distinct and complete in itself, and so disposed and operated that an operation on a Pair of 2 immediately succeeding traveling articles is effected under the control of respectively distinct units, whereby one or more operations on a leading article, for example are controlled by one such unit, and one or more operations on the next succeeding article are controlled by another such unit.

Further objects of the invention will be in part obvious, or will become apparent upon a study of the following specification, in coniunction with the accompanying drawings, in which Fig. 1 is a side elevational view of a sequence control device embodying my invention;

Fig. 2 is a top plan view as seen from above Fig. 1;

Fig. 3 is a vertical sectional view taken on the line 33 of Fig. 2;

Fig. 4 is a vertical sectional view, somewhat enlarged, taken on the line 4-4 of Fig. 2;

Fig. 5 is an end elevational view, somewhat enlarged, from approximately the position of the line 5-5 of Fig. 1; and

Fig. 6 is a wiring diagram, showing some operating parts schematically.

Referring now to the drawings, and speaking first generally, the control device is shown in Figs. 1 to 5 inclusive, and Fig. 6 indicates certain controlled elements such as a folding blade 10, a pair of folding rolls H, a blade operating solenoid I2, an endless conveyor l3, and a trip switch M which is operated by the leading and trailing edges of an article (not shown) moving to the right on the top flight of the conveyor. The folding impulses are supplied to solenoid l2 by the sequence controller shown in Figs. 1 to 5.

Referring now to Fig. 2 the folding impulses originate either in switches l5 and I6 of a first folding control unit as indicated by the bracket ".A in Figs. 1 and 2, or in switches l1 and I8 of a second folding control unit as indicated by the bracket 13 in the same figures. In the representative example to which occasional reference will be made, and wherein a one-quarter and three-quarter fold are to be applied to moving flat work laundry articles such as sheets, unit A, in conjunction with other parts of the device, controls said folds on one sheet, and unit B, also in conjunction with other parts of the device, controls the same type folds on the next succeeding sheet. Unit A then controls the operations on the third sheet, and unit B on the fourth, etc.

In the embodiment here shown the sequence control device has a continuously rotating driving shaft i9 supported on a base 20 by means of frame uprights 23 and 24. The shaft I9 has a bevel gear 25 driven by a pinion 26 on a vertical shaft 2! which has on its upper end a sprocket 28 driven by a chain 29 from the folding machine (not shown) so that there is positive synchronism between the controlling means and the folding machine. A pair of driven shafts 30 and 3| are driven at fractional arithmetically proportioned speeds relative to the driving shaft by means of a gear train 33 not herein necessary to characterize in detail, shaft 30 rotating at three-quarter the speed of the driving shaft I9, and shaft 3! at one-quarter the speed of driving shaft l9.

Through appropriate elements soon to be described shaft 38 produces intermittent energization of switch l6 in unit A for the one-quarter fold operation on sheet, or of switch 18 in unit B for the one-quarter operation on a succeeding sheet. Shaft 31 takes care of the operation of switches l5 and H in the same way, so as to respectively control the three-quarter folds on the specified sheets. The part of unit A which controls the one-quarter fold will be known as the first section of unit A, and the part of unit A which controls the three-quarter fold will be known as the second section of unit A. Similarly understandable terminology will be applied to the first and second sections of unit B.

There is substantial similarity in the operation of each unit, and in the operation of each section of each unit, so that such operation will be described for the time being with reference mainly to the first and second sections of unit A. Each of the four sections is a complete timer unit.

Secured to shaft H] are two gears 34 and 35, one for each unit, and these are in constant mesh with complementary gears 36, 31, 3B and 39 carried on shafts 3D and 3| in the positions shown best in Fig. 2. With special reference to the enlarged fragmentary view of Fig. 4 which shows the construction of one section of unit A (the one controlling the one-quarter fold) and with occasional reference to the general eonstruetion as shown in Figs. 1, 2 and 3, there is shown a cup-like clutch member 42 having an annular toothed face 43. Member 42 is pinned to shaft 35. A driven clutch member 44 is secured to a generally circular cam disk 45, both being freely rotatable on the periphery of a sleeve 46 which is free to turn on shaft 35. The clutch comprising the members 42, 44 will be hereinafter termed a positive clutch since its engagement is more mechanical than frictional. Disk has frictional contact through a compressible ring 41 with a flanged sleeve 48 having attached thereto the gear 36 which, as heretofore noted, is driven directly from main driving shaft 19 through gear 34. Sleeve 48 is free on sleeve 45. Slippage between disk 45 and ring 41 is permitted when frictional adhesion between them is overcome by differential power applications respectively applied to each during operation, as will appear. The clutch comprising the members disk 45 and ring 41 will be hereinafter termed a slip clutch. A collar 52 is also rotatable on sleeve 4'6, and it abuts a retaining ring 49 on the sleeve. A compression spring 50 maintains endwise bias against ring 41.

The sleeve 45, and all elements carried thereby, including clutch part 44, are movable slightly to the right from the position shown in Fig. l, against the bias of a compression spring 53, retained by a movable collar 54, such movement being responsive to operation of a yoke lever 55 effective through fork fingers 53 against a spool 5! slidable on shaft 35. Such movement to the right produces engagement of the ccmpleinchtary positive clutch parts 42, 44. .As previously noted, clutch part 42 rotates with the speed of shaft 30, which travels at three-quarter the speed of driving shaft I9. When the clutch parts ll, 44 are engaged, slippage occurs between disk 45 and friction ring 41, and the disk necessarily rotates with the speed of clutch parts #12, 4'5 and shaft 33. Under a certain condition when the clutch is not engaged, clutch part 44 rotates with friction ring 4i and gear 35, said gear 33 being directly driven from gear 34 on main shaft 19. Under a still further condition (as will appear) when the clutch is disengaged, and disk 45 is intentionally held so as to completely prevent its rotation, slippage also occurs between ring El and disk 45.

As shown in Fig. 4 the clutch 42, 44 is disengaged, but engagement can be effected. by the aforesaid yoke lever 55 which is pivoted at 53 on a part 23a of frame upright 23. the position shown the yoke lever, by means of a projecting finger 59, engages a stop lug 52 on disk Lever also similarly operates spool li'lu (Fig. 2) on shaft 3] so as to cause operation of the analogous and identical clutch parts, etc., in unit A on shaft 3|. Lever 55 has a second finger similar to 59, but operative on disk 45a in the second section of unit A, this second finger being indicated at 55a in dotted line on Fig. 3. Each timer disk 45, 45a, has attached thereto a cam or tripper 45c and 45d so located that in the unoperated position the tripper is slightly the operating arm for switch [6, Hi, etc. and the switch is in normally open position. Yoke lever 55 has a forked leg 62 which straddles an oper ating rod 63 operated by a solenoid M, the rod having a fixed nut 65 on its end. For unit B another solenoid 66 has an operating rod 6'! to operate a similar yoke lever 58 (Figs. 2 and 2) which controls the operation of analogous clutch members, etc., in unit B. As indicated in 3, yokes 55 and 88 have their operating legs staggered, left and right, so as to be operated by rods 63 and B1 in alignment respectively with solenoids 64 and 56.

The device for alternating units A and B in sequence is best seen in Figs. 2, 4 and 5. Its mechanical structure will now be described, and its operation will later more readily appear in conjunction with the description of the wiring diagram and the sequence of operations. It comprises a double throw switch 12, a cam 13, and means for rotating the cam at each operation. Cam [3 is mounted on the end of shaft l9 but is not secured thereto, being held in contact with a friction ring 74 by a compression spring i5 between two collars 1B and 1'! pinned to shaft l9. Stop pins 18 and 19 extend alternately to the front and rear of cam 13. A rocker 9U hav ing arms 9| and 92 is pivoted on a bracket 9-3 on frame upright 23. It has two positions, engaging either a front pin or a rear pin, either such position stopping cam 13. As the rocker is moved away from one position, releasing one pin, the cam undergoes an increment of movement before the other rocker arm is interposed in front of the next pin on the other side of the cam.

Operation of the rocker arm is effected by means of a rod 95 yieldingly urged to the right by a spring 96. Attached to rod 95 is a sleeve 9'! carrying a pin 98 which has ends projecting 9'0; Rod 95 has an abutment collar 99- engaging a plate I50 on yoke 55', the rod end abutting a similar plate I01 on yoke 6'8 in unit B. Since the rod 55 passes freely through an aperture in plate Illil, either yoke by movement to the left (Figs. 1 and 4) can operate rod 95 without affecting the position of the other yoke. The purpose of the sequence rocker of course is to permit operation of cam I3 which at certain times causes operation of double throw switch I2. Switch I2 in one position energizes solenoid 5.4 and in the other position energizes solenoid St.

The operation of the device i as follows, referring both to the structural figures, and to the diagram, Fig. 6.

The compound gear train 3'3 is. so arranged that while the rotation of driving shaft I9 is counterclockwise (Fig. 3) the rotation of shafts 38 and 3I is clockwise. In the wiring diagram the device is shown in the idle position with the double throw sequence switch in the circuit position for operation of solenoid 64 as soon as trip switch I4 is closed.

As soon as the leading edge of the first article (and we have selected as work pieces a succession of sheets to be folded) reaches trip switch I4 a circuit is completed from L1 through switch l4, conductor I04, sequence switch I2 in the position shown (by reason of its switch arm being on a low segment of cam 13) and through conductor I05, solenoid 64, and conductor I05 to L2. The solenoid 64 remains energized as long as the sheet is moving over trip I4.

Energization of solenoid 64 moves rod 63 to the left (Fig. 4) thereby swinging yoke 55 clockwise and releasing cam disk 45 while at the same time causing engagement of positive clutch parts 42 and 44. A similar result is produced in the second section of unit A. As previously described, the cam disks 45 and 45a begin to rtate, disk 45 at three-quarters the the speed of driving shaft I9 and disk 45a at one-quarter the speed of the driving shaft. This continues until the trailing edge of the first sheet passes trip It, allowing the trip switch to reopen and deenergizing solenoid 64. Spring 53 disengages clutch parts 42, 44, and cam disks 45, 45a now rotate at full speed through slip clutch 45, 41 and gears 36, 34 to the driving shaft I9.

Observing the rotation of disk 45, as soon as its cam rise portion 45c operates switch I it completes a circuit to solenoid I2 which operates folder arm It to effect the first fold. The circuit is through Ll, conductors m8 and I09, switch I6. conductors HE! and III, a switch H2 operated by a cam H3 on the folder shaft H4, conductor H5, solenoid I2, and conductors I I6 and III to L2. Operation of solenoid I2 and arm I0 energize a half revolution clutch mechanism 94 cansing the arm to move to its rear position, the folder arm contacting the dropping sheet at its one-quarter point and causing the sheet to drape over the horizontal portion of the arm. As a result of said half-revolution rotation of shaft I Is, cam I I3 opens switch I I2 and closes a switch H8. This rearranges the circuit for operation of the second fold timer of unit A.

When the cam rise 55d of disk 45a operates switch E5 the solenoid I2 is again energized through a circuit from L1 through conductors Hi3 and 39, switch l5, conductors I and I2I, switch H8, conductors I22 and H5, solenoid I2 and conductors H6 and II! to L2. Energization of solenoid I2 again operates folder arm I0, causes a half revolution of shaft H4, opens switch I I 8. and closes switch H2.

It will be understood that the folding zone is so disposed as respects the distance from the trip I4, and the cam rises c and 45d are circumferentially so disposed on disks 4'5 and 45a respectively, and the relative speeds of rotation of all shafts and the endless conveyor are so regulated. that the proper fold line of a sheet arrives at the folder arm coincidentally with energization of the solenoid I2, so. that the folds are effected as planned. Changes may be made in some of these factors to effect a one-third two-third folding arrangement, etc.

The sequence operation by means of rocker 90 is as follows.

When solenoid iiII was energized as previously described, pulling rod 63 to the left (Fig. 4) and moving yoke clockwise, plate I00 engaged collar 99 so as to push rod as to the left against the bias of spring 96, causing pin 98 to move rocker SI. As previously described this momentarily releases cam I3 to permit a segmental increment of rotation, an angular distance-equivalent to the distance between a pin on one side of cam I3 and the nearest pin on the opposite side, for example from a pin IS to a pin I8. Examination of Fig. 5 will show that this rotation (counterclockwise) is insufficient to affect the position of the arm Ha of switch 12. However, when solenoid 54 was deenergized by passing of the trailing edge of the sheet past trip I4, rod 95 moves to the right (Fig. 4) under the bias of spring 95, the collar 99 moving yoke 55 counterclockwise. Rocker 95 then moves back to its original position, again permitting the standard segmental rotation of cam I3, and at this time switch arm 72a is moved to the next high segment on cam I3 so as to cause operation of switch I2. This reversal of switch I2 now places solenoid 66 in circuit with trip switch I4, so that the next article which comes through on the endless conveyor will be under the control of solenoid 66, yoke 68, and the several timer sections of unit B.

Actuation by solenoid 56 for the one-quarter fold causes movement of cam I3 as before, but insuflicient to drop switch arm 12a or operate switch 12. The return of yoke 38 upon deenergization of the solenoid 56 causes operation of the rocker 90, permits another segmental increment of rotation of cam I3, and one cycle of operation I of units A and B has been completed.

In this specification and the appended claims, I use the words arithmetically proportioned to indicate any selected fractional increment of the standard of comparison. For example in comparing the speed of the driven shaft with the speed of the driving shaft in the embodiment disclosed, and under the relative rates of rotation disclosed, the words arithmetically proportioned mean that the driven shaft is rotating at three-quarter the speed of the driving shaft. In other possible embodiments the words would indicate the fact that a particular suitable ratio has been selected to attain the operation at the location desired.

What I claim is:

1. Control means adapted to time the execution of an operation on each of a series of spaced articles moving on a conveyor past measuring means, and wherein an operating member is energized to perform such operation responsive to rotation of a timing member past a point of registry, said control means comprising a first driving member, a second driving member, means for rotating said driving members at different rates, means for producing and continuously maintaining planar frictional driving engagement between said timing member and said rst driving member, stop means for preventing rotation of said continuous timing member despite said frictional driving engagement, means for producing positive driving engagement een said timing member and said second driving member while simultaneously rendering stop means ineffective, whereby said timing member rotates responsive to said second driving menu ber despite said continuous frictional engage" ment with said first driving member, and means for terminating said positive driving engagement while said stop means remains ineffective, to permit said timing member to be driven from said first driving member by means of the a oresaid frictional engagement until said ti ring member reaches said point of registry.

2. Control means adapted to time the execution of an operation on each of of spaced articles moving on a conveyor past measuring means, and wherein an operating member is energized to perform such operation responsive to rotation of a timing member to a point of registry, said control means comprising a driving shaft, a second driving shaft, means for rotating said shafts at different rates, slip clutch means normally disposed to eifect contini frictional driving engagement between said ing member and said first driving shalt, means for normally preventing rotation of said timing member despite such continuous frictional driving engagement, a positive clutch which, when engaged effects direct driving inter-lock between said timing member and second driving shaft, means responsive to of th leading edge of an article past said measuri means for simultaneously engaging said posi clutch and disengaging said stop means, whereby to cause said timing member to be driven from said second shaft despite said continuous frictional engagement with said firs driving shaft, through said positive clutch, and means responsive to passage of the trailing edge of an article past said measuring means for disengaging said positive clutch while said stop means remains disengaged whereby to cause said timing meinher to be driven from said first shaft through said slip clutch until said timing member reaches said point of registry.

3. Control means adapted to time the execu. tion of an operation on each of a series of spa: d articles moving on a conveyor past measuring means, and wherein an operating membe is energized to perform such operation responsive to rotation of a timing member past a poi registry, said control means comprising r driving shaft and a second driving shait, means for rotating said first driving shaft in synchronism with the movement of said conveyor, means for rotating said second driving shaft at a speed arithmetically proportional with respect to the speed of said conveyor, slip clutch means normally disposed to effect continuous frictional driving engagement between said timing member and said first driving shaft, stop means for normally preventing rotation of said timing member despite such continuous frictional driving env gagement, a positive clutch which, when engaged,

ing said sto means ineffective whereby to cause said timing member to be driven from said second shaft despite said continuous frictional engagement with said first driving shaft, and means responsive to passage of the trailing edge of the article past said measuring point for disengaging said positive clutch while said stop means remains disengaged, whereby to cause said timing member to be driven from said first shaft until said timing member reaches said point of registry.

i. Control means adapted to time the execution of a folding operation on each of a series of laundry fiatwork articles moving on a conveyor past a measuring trip switch, and wherein a folding blade is energized to perform the folding operation responsive to operation of a second switch by rotation to contact therewith by a timing member, said control means comprising a first and a second driving shaft, means for rotating said first driving shaft in synchronism with the movement of said conveyor, means for rotating said second driving shaft at a speed arithmetically proportioned with respect to the speed of said conveyor, slip clutch means normally disposed to effect continuous frictional driving engagement between said timing member and said first driving shaft, stop means for normally preventing rotation of said timing member despite continuous frictional driving engagement, a positive clutch which, when engaged, effects direct driving interlock between said timing member and said second driving shaft despite said continuous frictional driving engagement with said first driving shaft, means responsive to pa sage of the leading edge of an article past s trip switch for simultaneously engaging said positive clutch and rendering said stop means ineffective, and means responsive to passage of the trailing edge of the article past said trip switch for disengaging said positive clutch while said stop means remains disengaged, whereby to cause said timing member to rotate to contact with said second switch to thereby institute execution of said folding operation.

5. Apparatus of the character described including operation performing means for the execution of a proportional operation on each of a series of spaced articles moving on a conveyor, comprising a first driving shaft, means for rotating said first driving shaft in synchronism with the movement of said conveyor, a second driving shaft, means for rotating said second driving shaft at a speed arithmetically proportioned to the speed of said first driving shaft, a timing cam rotatable on said second driving shaft, a positive clutch operatively engageable with said timing cam and said second driving shaft, a slip clutch continuously frictionally engaging said tii ing cam and said first driving shaft, stop means normally engaging said timing cam to prevent rotation thereof despite engagement therewith of said slip clutch, means responsive to passage of the leading edge of an aforesaid article past a measuring point for engaging said positive clutch and for simultaneously disengaging said stop means to permit rotation of said timing cam, means responsive to passage of the trailing edge of said article past said measuring point for disengaging said positive clutch, while said stop means remains disengaged whereby engagement with the aforesaid slip clutch again drives said timing cam, and means thereafter responsive to operation of said timing cam and effective upon said operation performing means for initiating the performance of said proportional operation.

6. Apparatus of the character described including operation performing means for the execution of proportional operations on each of a series of spaced articles moving on a conveyor, comprising a driving shaft, means for rotating said driving shaft in synchronism with the movement of said conveyor, a first driven shaft and a second driven shaft, means for continuously rotating said first and second driven shafts at speeds arithmetically proportioned to each other and to that of the driving shaft, said first and second driven shafts each having a timing cam rotatable thereon, a first and a second positive clutch, the first positive clutch being engageable with the first driven shaft and the timing cam thereon, and the second positive clutch being engageable with the second driven shaft and the timing cam thereon, a first and a second slip clutch, each synchronously driven from said driving shaft the first said slip clutch continuously frictionally engaging the timing cam on the first driven shaft, the second said slip clutch continuously frictionally engaging the timing cam on the second said driven shaft, 9, first and a second stop respectively normally engaging the first and second timing cams to prevent rotation thereof despite engagement of the respective slip clutches, means responsive to passage of the leading edge of an aforesaid article past a measuring point for engaging both said positive clutches and for simultaneously disengaging both said stops, means responsive to passage of the trailing edge of the same article past the measuring point for 10 disengaging both said positive clutches while both said stops remain disengaged whereby frictional engagement between both the aforesaid slip clutches and their respective timing cams again drives both said timing cams, and means thereafter responsive to operation of both said timing cams, and successively effective upon said operation performing means for initiating the performance of successive proportional operations on the same article.

7. Control means as defined in claim 4 wherein the means responsive to passage of the leading edge of an article past the trip switch comprises a solenoid in electric circuit communication with said trip switch, and a lever operatively responsive to energization and de-energization of said solenoid, said lever being effective upon said positive clutch and said stop to engage said positive clutch and disengage said stop when said trip switch is closed, and to disengage said positive clutch when the trip switch is opened.

RUSSELL G. McLAGAN.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 1,607,407 Mayer Nov. 16, 1926 1,697,010 Jones et al Jan. 1, 1929 2,261,226 Clegg Nov. 4, 1941 2,291,487 Myers July 28, 1942 2,458,544 Watson Jan. 11, 1949 2,516,454 Doran July 25, 1950

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