US3918336A

US3918336A - Trimmer drive assembly

Info

Publication number: US3918336A
Application number: US455629A
Authority: US
Inventors: Keith S Macey; John J Marciniak
Original assignee: Harris Intertype Corp
Current assignee: AB Dick Co
Priority date: 1974-03-28
Filing date: 1974-03-28
Publication date: 1975-11-11
Anticipated expiration: 1992-11-11
Also published as: CH593195A5; GB1504581A; DE2511342A1; JPS50130084A

Abstract

A trimmer mechanism has an improved drive assembly for intermittently moving sheets of material relative to trim knives. The drive assembly includes a single cam member having a pair of cam surfaces which operate two linkages to rotate a crankarm. Each linkage includes a follower link on which a cam follower is mounted in engagement with an associated one of the cam surfaces and a drive link which is connected with the crankarm. Upon rotation of the cam member, the follower links are moved in such a manner as to move the two drive links to apply transversely directed forces to the crankarm. These transversely directed forces cause the crankarm to move along a circular path. The cam surfaces have a configuration such that the two linkages are ineffective to drive the crankarm once the sheets of material have been moved into position relative to the trim knives. During the time in which the crankarm is stationary, the trim knives are moved to trim the sheets of material.

Description

United States Patent [191 Macey et a].

[451 Nov. 11,1975

[ TRIMMER DRIVE ASSEMBLY [57] ABSTRACT [75] Inventors: i f g gf' rf g Rockby i 613 A trimmer mechanism has an improved drive assemc a area 0 0 bly for intermittently moving sheets of material rela- [73] Assignee: Harris-lntertype Corporation, tive to trim knives. The drive assembly includes a sin- Cleveland, Ohio gle cam member having a pair of cam surfaces which operate two linkages to rotate a crankarm. Each link- [22] Filed 1974 age includes a follower link on which a cam follower is [21] Appl. No.: 455,629 mounted in engagement with an associated one of the cam surfaces and a drive link which is connected with I the crankarm. Upon rotation of the cam member, the 8 follower links are moved in such a manner as to move [58] Fieid 83/255 257 258 the two dn've links to apply transversely directed forces to the crankarm. These transversely directed forces cause the crankarm to move along a circular [56] References Cited path. The cam surfaces have a configuration such that UNITED STATES PATENTS the two linkages are ineffective to drive the crankarm 1,076,726 10/1913 Welch 83/255 once the sheets of material have been moved into po- 3.301,l14 1/1967 10am 83/255 X sition relative to the trim knives. During the time in 1424944 1/ 1969 Thumm i 83/255 which the crankarm is stationary. the trim knives are 3,461,766 8/1969 Anderson 83/255 moved to trim the sheets of material.

Primary Examiner-Willie G. Abercrombie 15 Claims1 5 Drawing Figures 46 48 32 I I I 1 |l 1l44 551 58 I 64 28 k- 38 I l 34 V 66 l 24., 5'4 .l' 62 1' US. Patent Nov. 11, 1975 Sheet 1 of5 3,918,336

FIG. I

Sheet 2 of 5 U.S. Patent Nov. 11, 1975 US. Patent Nov. 11, 1975 Sheet 3 of5 3,918,336

FIG. 3

Sheet 4 of 5 US. Patent Nov. 11, 1975 Nov. 11, 1975 Sheet 5 015 3,918,336

US. Patent m GE EQRQRQQ SEQ kQ WMWQQMQ m uuk tbyu uk TRIMMER DRIVE ASSEMBLY BACKGROUND OF THE INVENTION ming sheets of material is disclosed in US. patent applilo cation Ser. No. 270,980, filed July 12, 1972, by John J. Marciniak and entitled Sheet Material Trimming Method and Apparatus, now US. Pat. No. 3,811,350. Although, this known trimming mechanism is very satisfactory in its operation, difficulty has been encountered in economically manufacturing and assemblying a drive mechanism for effecting intermittent movement of conveyer belts which sequentially index booklets relative to trim knives. Although there are many different things which contribute to the relatively high cost of the known drive mechanism, part of the relatively high cost is due to the use of a generally H-shaped drive member in combination with two sets of cam plates or members which are engaged by actuator pins mounted on a pair of drive chains.

SUMMARY OF THE PRESENT INVENTION The present invention provides a new and improved drive assembly which is reliable in operation and is relatively inexpensive to construct. This improved drive assembly includes cam surfaces which are effective to actuate linkages. These linkages are connected with a crankarm. Upon rotation of the cam surfaces, the linkages rotate the crankarm.

When the drive assembly is used in a trimmer mechanism, the rotation of the crankarm is utilized to index sheet material drive belts to move a trimmed sheet material assemblage away from a trimming station and to move a next succeeding sheet material assemblage to the trimming station. The cam surfaces have a dwell period during which the crankarm remains stationary and the trim knives are operated to trim a sheet material assemblage. Once the knives have been moved clear of the trimmed sheets, the cam surfaces are again effective to rotate the crankarm to move the trimmed sheet material assemblage. .Although the drive assembly is disclosed herein in connection with a trimmer mechanism, it should be understood that the drive assembly could be utilized in many different environ-- ments. 7

Accordingly, it is an object of this invention to provide a new and improved intermittent drive assembly which is relatively inexpensive to fabricate and is reliable in operation.

Another object of this invention 'is to provide a new and improved intermittent drive assembly which includes cam surfaces for effecting operation of linkages to rotate a crankarm.

Another object of this invention is to provide a new and improved apparatus which includes a drive assembly for effecting intermittent movement of sheet material articles along a sheet feed path and wherein the drive assembly includes a cam arrangement which is effective to operate linkages to move a drive member along a circular path to effect movement of the sheet material articles, to interrupt operation of the linkages so as to stop the movement of the sheet material articles, and to subsequently effect operation of the linkages to again move the sheet material articles.

BRIEF DESCRIPTION OF THE DRAWINGS The foregoing and other objects and features of the present invention will become more apparent upon a consideration of the following description taken in connection with the accompanying drawings wherein:

FIG. 1 is a pictorial illustration of a trimmer mechanism having a drive assembly constructed in accordance with the present invention;

FIG. 2 is a pictorial illustration of a drive assembly constructed in accordance with the present invention;

FIG. 3 is an elevational view, taken generally along the line 3-3 of FIG. 2, further illustrating the construction of the drive assembly and schematically depicting its relationship to trim knives and a plurality of conveyer belts for moving sheet material articles relative to the trim knives;

FIG. 4 is an enlarged schematic illustration of the drive assembly; and

FIG. 5 is a graph depicting intermittent movement of the conveyer belts relative to the trim knives during cutting and return strokes of the trim knives.

DESCRIPTION OF ONE SPECIFIC PREFERRED EMBODIMENT OF THE INVENTION A trimmer mechanism 20 constructed in accordance with the present invention is illustrated in FIG. 1 and is utilized to trim sheet material assemblages, such as pamphlets formed of one or more folded sheets, magazines or books. The trimmer mechanism 20 includes a front or face knife 22 having a movable blade 24 which is reciprocated through cutting and return strokes relative to a fixed or stationary blade 26 by vertical movement of a frame assembly 28 to trim the face or front edge portion of a sheet material assemblage. While the sheet material assemblage is being trimmed, it is clampingly held in registration with the face knife 22 by a first set of conveyer timing belts 32 which grip the sheet material assemblage adjacent to its head portion at a second set of conveyer timing belts 34 which grip the sheet material assemblage adjacent to its foot portion.

After the face edge portion of the sheet material assemblage has been trimmed, the two sets of

conveyer belts

32 and 34 are activated to move a sheet material assemblage from a first or front trimming station 38 to a second rear trimming station 42. At the second trimming station 42, a head knife 44 trims a head end portion of the sheet material assemblage and a foot trim knife 46 trims a foot or tail portion of the sheet material assemblage. A split knife 48 is provided intermediate the head and

foot trim knives

44 and 46 for two-up trimming operations.

Movable blades

54, 56 and 58 of the head, foot and

split knives

44, 46 and 48 are all reciprocated through cutting and return strokes relative to associated stationary or

fixed blades

62, 64 and 66 by vertical movement of the frame assembly 28. Thus, all four

trim knives

22, 44, 46 and 48 are operated simultaneously by reciprocation of the frame assembly '28 so that trimming operations on a leading sheet matetrimming station 42 toward a delivery station 70 and to move a partially trimmed trailing sheet material assemblage from the first trimming station 38 toward the second trimming station. During operation of the trimmer mechanism 20, a continuous stream of untrimmed sheet material assemblages is transported from a collator or other source to the trimmer mechanism by a known chain type conveyer 78. The manner in which the

conveyer belts

32 and 34 move the sheet material assemblages relative to the

trim knives

44, 46 and 48 and the manner in which the frame 28 is reciprocated to move the trim knives through cutting and return strokes is the same as disclosed in the aforementioned US. Pat. application Ser. No. 270,980, filed July 12, 1972, by John J. Marciniak and entitled Sheet Material Trimming Method and Apparatus, and will not be further described herein to avoid prolixity of description.

In accordance with a feature of the present invention, an improved drive assembly 88 (FIGS. 2 and 3) is provided to effect intermittent operation of the

conveyer belts

32 and 34 to sequentially move sheet material assemblages to and from the

trimming stations

38 and 42 along a sheet feed path. The improved drive assembly 88 includes a circular cam member 94 (FIG. 2) which is rotated by a drive shaft 96 to effect operation of a pair of

linkages

100 and 102 to intermittently rotate a crankarm 104 (FIG. 4). The crankarm 104 is connected with the two sets of

conveyer belts

32 and 34 by a chain and sprocket drive arrangement 106 (see FIG. 3).

Upon rotation of the crankarm 104, a drive chain 110 is effective to rotate conveyer

sprocket drive shafts

112 and 114 which are connected with sprockets 116 and 118 (FIG. 3). Rotation of the

sprockets

116 and 118 causes the

continuous conveyer belts

32 and 34 to be moved through a forward operating stroke to index a sheet material assemblage relative to the trim knives. It should also be understood that although only the drive sprockets 116 and 1 18 for the conveyer belts 32 have been shown in FIG. 3, similar sprockets are mounted on the

shafts

112 and 114 to drive the conveyer belts 34.

A single circular cam member 94 is advantageously utilized to effect operation of the two

linkages

100 and 102 in a timed relationship with each other. Thus, the circular cam member 94 is provided with a pair of continuous cam tracks 122 and 124 (see FIG. 4) which are disposed in opposite major circular face sides 126 and 128 (see FIG. 3) of the cam member 94. Since the two

cam tracks

122 and 124 are formed in a single member 94, they are maintained in a predetermined positional relationship with each other.

Upon rotation of the cam member 94 by a drive shaft 96 which is continually rotated during operation of the trimmer mechanism 20, a cam follower 134 cooperates with the cam track 122 to effect operation of the linkage 102. Simultaneously therewith, a second cam follower 136 cooperates with the cam track 124 to effect operation of the linkage 100. The two

linkages

100 and 102 are effective to rotate the crankarm 104 to effect rotation of a short drive shaft 140 about a central axis which extends parallel to the axis of rotation of the drive shaft 96. The drive shaft 140 is connected with a sprocket 144 in the chain drive arrangement 106 to effect rotation of the conveyer belt drive shafts 112 and l 14.

Upon rotation of the cam 94 in a counterclockwise direction from the position shown in FIG. 4, the

cam followers

134 and 136 initially move along constant radius or dwell portions of the cam tracks 122 and 124 as the cam 94 moves through the arcuate distance indicated at 150 in FIG. 4. During this rotational movement of the cam 94, the

cam followers

134 and 136 remain substantially stationary so that the linkages and 102 are ineffective to move the crankarm 104. Therefore, the drive assembly 106 is ineffective to move the

conveyer belts

32 and 34 so that sheet material assemblages gripped by the conveyer belts remain stationary relative to the

trim knives

22, 44, 46 and 48. The stationary position of the

belts

32 and 34 relative to the trim knives is represented by a portion 154 (FIG. 5) of a curve 156 which indicates the manner of movement of the

conveyer belts

32 and 34 during each trim cycle.

While the

conveyer belts

32 and 34 are stationary, a crank drive mechanism 160 (see FIG. 3) is driven by a continuously rotating shaft 96 to continue movement of

trim knife blades

24, 54, 56 and 58 downwardly from a position immediately above a booklet and represented by a point 166 on a curve 168 (FIG. 5). While the

conveyer belts

32 and 34 remain stationary, the

movable knife blades

24, 54, 56 and 58 move downwardly past the stationary knife blades. The point at which the stationary and movable knife blades initially cross is represented by a point of intersection 172 (FIG. 5) of the curve 168 with a line 174 representing the stationary knife blades.

While the

conveyer belts

32 and 34 remain stationary, the

trim knives

24, 54, 56 and 58 continue to move downwardly through the cutting stroke and move back upwardly in the manner indicated by the curve 168. A second intersection 178 (FIG. 5) of the curve 168 with the stationary knife blade line 174 indicates when the movable knife blades begin to move clear of the stationary knife blades. During the time in which the movable knife blades are in engagement with the stationary knife blades and the booklets, the

conveyer belts

32 and 34 remain stationary, as indicated by the portion 154 of the curve 156. As this is occurring, the cam 94 is moving through the arcuate distance 150 (see FIG. 4).

After the movable knife blades have moved upwardly out of engagement with the trimmed booklets, the cam tracks 122 and 124 effect operation of the

linkages

100 and 102 to move the crankarm 104 through a complete revolution in a clockwise direction (as viewed in FIG. 4). This movement of the crankarm 104 rotates the output shaft to which it is connected and effects movement of the

conveyer belts

32 and 34. The

conveyer belts

32 and 34 move through a distance sufficient to move a booklet from the forward trim station 38 to the rearward trim station 42 and to move a booklet from the rearward trim station 42 to the delivery station 70.

To effect an indexing of the

conveyer belts

32 and 34, the cam 94 rotates in a counterclockwise direction (as viewed in FIG. 4) so that arcuate portions 182 of the cam tracks are effective to operate

linkages

100 and 102 to accelerate the crankarm 104 in the clockwise direction. Arcuate portions 184 of the cam tracks 122 and 124 then cooperate with the

followers

134 and 136 to effect operation of the

linkages

100 and 102 to rotate the crankarm 104 at a constant velocity. Finally, arcuate portions 188 of the cam tracks 122 and 124 cooperate with the

cam followers

134 and 136 to decelerate the crankarm 104 as it approaches the dwell or trim position shown in FIG. 4.

During this movement of the cam 94 and crankarm 104, the conveyer belts 32 are moved thorugh a forward operating stroke in the manner indicated by the curve 156 in FIG. 5. In addition, the movable knife blades are moved to the end of their return stroke, indicated by the point 194 on the curve 168 in FIG. 5 and begin to move back downward. When the cam 94 has again reached the dwell position shown in FIG. 4, the knife blades are immediately above the booklets in the position indicated by the right end of the curve 168 in FIG. 5. While the

conveyer belts

32 and 34 remain stationary, the knife blades move downwardly as indicated by the left portion (as viewed in FIG. 5) of the curve 168.

When the cam 94 is moving through the arcuate dwell or trim distance 150, the cam tracks 122 and 124 have the constant radius so that the

cam followers

134 and 136 remain stationary. However, as soon as the cam has been rotated through the arcuate distance 150, the cam track 122 causes the cam follower 134 to move radially inwardly toward the central drive shaft 96. This pivots a follower link 200 on which the cam follower 134 is mounted about a support shaft 204 which extends parallel to the main drive shaft 96. As the follower link 200 of thelinkage 102 pivots in a counterclockwise direction (as viewed in FIG. 4) about the shaft 204, the drive link 206 is effective to apply the rightward directed force (as viewed'in FIG. 4) to a crankpin 210 of the crankarm 104. This rightward force component applied by the drive link 206 to the crankpin reaches a maximum when an arm 212 is at the top dead center position, indicated in dashed lines at 216 in FIG. 4.

As the cam follower 134 is being moved inwardly by the cam track 122 to move the crankarm 104 toward the top dead center position indicated in dashed lines 216 in FIG. 4, the cam follower 136 is moved radially outwardly, away from the center of the drive shaft 96 by the cam track 124. The cam follower 136 is mounted on a follower link 220. Therefore, the follower link 220 of the linkage 100 pivots in a clockwise direction about the shaft 204 (as viewed in.FIG. 4). This clockwise pivoting movement of the follower link 220 moves a drive link 222 to apply an upwardly directed (as viewed in FIG. 4) force to the crankpin 210. As the crankarm 104 approaches the top dead center position indicated in dashed lines at 216 in FIG. 4, the force applied to the crankpin 210 gradually decreases until it is a minimum force when the crankarm 104 is in l the top dead center position.

Continued rotation of the cam 94 activates the

linkages

100 and 102 to move the crankarm from the top dead center position shown at 216 in dashed lines in FIG. 4 to a right dead center position, shown in dashed lines at 226 in FIG. 4. As the crankarm 104 approaches the right dead center position, the cam track 122 continues to move the cam follower 134 inwardly and the drive link 206 is effective to apply a decreasing force to the crankpin 210 tending to move the crankarm 104 in a clockwise direction. As this is occurring, the cam track 124 is effective to move the cam follower 136 inwardly to effect a counterclockwise (as viewed in FIG. 4) pivoting of the follower link 220 about the support shaft 204. As this occurs, the drive link 222 is effective to apply an increasing downward force to the crankpin 6 210. The downward force applied to the crankpin 210 by the drive link 222 reaches a maximum when the crankarm 104 is at the right dead center position 226.

Continued movement of the cam 94 results in the

cam followers

134 and 136 being moved to effect operation of the linkages and 102 to rotate the crankarm 104 from the right dead center position to the bottom dead center position, shown in dashed lines at 230 in FIG. 4. To accomplish this, the cam track 122 moves the cam follower 134 radially outwardly so that the follower link 200 pivots in a clockwise direction (as viewed in FIG. 4) about the stationary support shaft 204. As this is occurring, the force applied to the crankpin 210 by the drive link 206 increases and reaches a maximum when the crankarm 104 is in the bottom dead center position shown at 230 in FIG. 4.

While the cam follower 134 is moving radially outwardly, the cam follower 136 is being moved radially inwardly by the cam track 124. Since the cam follower 136 is connected to the generally triangular shaped link 220, inward movement of the cam follower 136 pivots the follower link 220 in a counterclockwise direction about the support shaft 204. This causes the drive link 222 to apply a decreasing downward force to the crankpin 210 as the crankarm 104 moves from the right dead center position to the bottom dead center position shown at 230 in FIG. 4.

Further rotation of the cam 94 effects operation of the

linkages

100 and 102 to move the crankarm 104 from the bottom dead center position shown in dashed lines at 230 in FIG. 4 to a left dead center position shown in dashed lines at 232 in FIG. 4. As the crankarm 104 approaches the left dead center position, the cam track 122 effects movement of the cam follower 134 outwardly to cause the follower arm 200 to pivot about the shaft 204 and the effect movement of the drive link 206 to apply gradually decreasing force to the crankpin 210. In addition, the cam track 124 effects movement of the cam follower 136 outwardly to pivot the follower link 220 in a clockwise direction about the support shaft 204. As the follower link 220 is pivoted in a clockwise direction, the drive link 222 is effective to apply increasing upward force to the crankpin 210. This upward force reaches a maximum when the crankarm 104 is at the left dead center position indicated in dashed lines at 232 in FIG. 4.

Continued rotation of the cam 94 moves the crankarm 104 back to the dwell or trim position shown in solid lines in FIG. 4. During this relatively small amount of movement, the cam track 122 is effective to move the follower 134 radially inwardly and to move the cam follower 136 radially outwardly to continue the rotational movement of the crankarm 104 in the manner previously explained. When the crankarm 104 reaches the trim or dwell position shown in solid lines in FIG. 4, the cam 94 is in the position shown in FIG. 4 so that the constant radius or dwell portions of the cam tracks 122 and 124 engage the

cam followers

134 and 136 to hold the crankarm 104 stationary. This causes the

conveyer belts

32 and 34 to remain stationary while the movable knives trim the booklets at the forward and rearward trim

stations

38 and 42.

To insure that the

conveyer belts

32 and 34 and the

trim knives

22, 44, 46 and 48 are operated in the desired sequential relationships, the cam drive shaft 96 is driven through a gear mechanism 240 from the continuously rotating drive shaft 162. Since the trim knife drive linkage and the cam drive shaft 96 are both crankpin 210 on the same side of the arm 212 as the drive link 206. Of course, if the drive link 222 engaged the crankarm 104 on the opposite side of the arm 212, the link 222 would interfere with the short drive shaft 140. To provide this offset in the link 222, the link is formed in two

parts

250 and 252 which are interconnected by a block 254 in the manner shown in FIGS. 2 and 3.

In view of the foregoing description, it may be seen that the drive assembly 88 is effective to intermittently rotate the crankarm 104 to effect imtermittent movement of the

conveyer belts

32 and 34. The improved drive assembly 88 includes a pair of cam tracks 122 and 124. The cam tracks 122 and 124 effect operation of the

linkages

100 and 102 to effect rotation of the crankarm 104 as the trim knives are being moved upwardly away from the stationary knife blades and downwardly toward the knife blades. Before the movable knife blades engage a booklet disposed adjacent to the stationary knife blades, the

cam followers

134 and 136 engage dwell portions of the cam tracks 122 and 124 to interrupt rotation of the crankarm 104 and movement of the

conveyer belts

32 and 34 so that the booklets remain stationary as they are engaged by the movable trim knives. Although the drive assembly 88 is advantageously utilized in the trimmer mechanism 20, it is contemplated that the drive assembly will be utilized in other environments in association with other mechanisms.

Having described a specific preferred embodiment of the invention, the following is claimed:

1. An apparatus comprising means for moving sheet material articles along a sheet feed path, drive means for effecting intermittent operation of said means for moving sheet material articles, said drive means including a drive member connected with said means for moving sheet material articles, means for supporting said drive member for movement along a circular path, first and second linkage means for applying transversely directed forces to said drive member, said first linkage means includes a first link mounted for pivotal movement about a first axis and a second link pivotally connected with said first link and drive member, said second linkage means including a third link mounted for pivotal movement about said first axis and a fourth link pivotally connected with said third link and drive member, and cam means for effecting operation of said first and second linkage means to move said drive member along said circular path through a predetermined arcuate distance, for interrupting operation of said first and second linkage means and movement of said drive member along said circular path upon movement through of said drive member the predetermined arcuate distance, and for effecting operation of said first and second linkage means to continue movement of said drive member along said circular path, said cam means including first cam surface means for effecting operation of said first linkage means and second cam surface means for effecting operation of said second linkage means.

2. An apparatus as set forth in claim 1 wherein said cam means includes a single rotatable cam member having opposite side portions, said first cam surface 8 means being disposed on one of said side portions of said cam member and said second cam surface means being disposed on the side portion opposite from said one side portion.

3. An apparatus as set forth in claim 2 further includ ing means for supporting said cam member for rotation about an axis extending parallel to the central axis of the path along which said drive member moves.

4. An apparatus as set forth in claim 1 further including knife means for trimming at least one edge portion of the sheet material articles, and means for effecting movement of said knife means into and out of engagement with a sheet material article during the interruption of movement of said drive member along said circular path.

5. An apparatus as set forth in claim 4 wherein said means for moving sheet material articles includes first and second belt means for grippingly engaging the sheet material articles and first and second sprocket means for supporting said first and second belt means, said drive means further including means for effecting rotation of said first and second sprocket means upon movement of said drive member along said circular path.

6. An apparatus as set forth in claim 1 further including first follower means mounted on said first link for engaging said first cam surface means, second follower means mounted on said third link for engaging said second cam surface means, and means for effecting movement of said first and second cam surface means relative to said first and second follower means to thereby effect operation of said first and second linkage means.

7. An apparatus comprising a crankarm, means for supporting said crankarm for rotation about a first axis, first and second cam surfaces, means for supporting said first and second cam surfaces for rotation about a second axis extending parallel to said first axis, a first link mounted for pivotal movement about a third axis extending parallel to said second axis, first cam follower means connected with said first link and disposed in engagement with said first cam surface for effecting pivotal movement of said first link about said third axis upon rotation of said first cam surface about said second axis, a second link interconnecting said first link and said crank arm and movable by said first link to effect rotation of said crank arm through at least a portion of a circular'path about said first axis upon movement of said first link about said third axis, a third link mounted for pivotal movement relative to said first link about said third axis, second cam follower means connected with said third link and disposed in engagement with said second cam surface for effecting pivotal movement of said third link about said third axis upon rotation of said cam surface about said second axis, a fourth link interconnecting said third link and crank arm and movable by said third link to effect rotation of said crank arm through at least a portion of said circular path about said first axis upon movement of said third link about said third axis, and means for effecting simultaneous rotation of said first and second cam surfaces about said second axis to thereby effect simultaneous pivotal movement of said first and third links about said third axis to rotate said crankarm about said first axis.

8. An apparatus as set forth in claim 7 wherein said second link has a longitudinal axis extending between a pivot connection with first link and a pivot connection with said crankarm, said fourth link having a longitudinal axis extending between a pivot connection with said third link and a pivot connection with said crankarm, said longitudinal axis of said second link extending transversely to said longitudinal axis of said fourth link to enable said second and fourth links to effect rotational movement of said crankarm about said first axis upon rotation of said first and second cam surfaces about said second axis.

9. An apparatus as set forth in claim 8 further including a single cam member mounted for rotation about said second axis and having a pair of major side portions extending generally perpendicular to said second axis, said first cam surface being formed in one of said major side portions and said second cam surface being formed in the other of said major side portions.

10. An apparatus comprising means for moving sheet material articles along a sheet feed path, drive means for effecting intermittent operation of said means for moving sheet material articles, said drive means including a drive member connected with said means for moving sheet material articles, means for supporting said drive member for 360 degrees of arcuate movement in one direction along a circular path, first and second linkage means for applying transversely directed forces to said drive member to move said drive member through 360 degrees of arcuate movement in said one direction along said circular path, and cam means for effecting operation of said first and second linkage means to move said drive member in said one direction along said circular path through a predetermined arcuate distance, for interrupting operation of said first and second linkage means and movement of said drive member in said one direction along said circular path upon movement of said drive member through the predetermined arcuate distance, and for effecting operation of said first and second linkage means to continue movement of said drive member in said one direction along said circular path, said cam means including first cam surface means for effecting 10 operation of said first linkage means and second cam surface means for effecting operation of said second linkage means.

1 1. An apparatus as set forth in claim 10 wherein said cam means includes a single rotatable cam member having a pair of opposite major sides, said first cam surface means being disposed on one of said major sides of said cam member and said second cam surface means being disposed on the major side opposite from said one major side.

12. An apparatus as set forth in claim 11 further including means for supporting said cam member for rotation about an axis extending parallel to the central axis of the path along which said drive member moves.

13. An apparatus as set forth in claim 10 further including knife means for trimming at least one edge portion of the sheet material articles, and means for effecting movement of said knife means into and out of engagement with a sheet material article during the interruption of movement of said drive member along said circular path.

14. An apparatus as set forth in claim 13 wherein said means for moving sheet material articles includes first and second belt means for grippingly engaging the sheet material articles and first and second sprocket means for supporting said first and second belt means, said drive means further including means for effecting rotation of said first and second sprocket means upon movement of said drive member along said circular path.

15. An apparatus as set forth in claim 10 wherein said first linkage means includes a first link mounted for pivotal movement about a first axis and a second link pivotally connected with said first link and drive member, said second linkage means including a third link mounted for pivotal movement about said first axis and a fourth link pivotally connected with said third link and drive member.

Claims

2. An apparatus as set forth in claim 1 wherein said cam means includes a single rotatable cam member having opposite side portions, said first cam surface means being disposed on one of said side portions of said cam member and said second cam surface means being disposed on the side portion opposite from said one side portion.

3. An apparatus as set forth in claim 2 further including means for supporting said cam member for rotation about an axis extending parallel to the central axis of the path along which said drive member moves.

7. An apparatus comprising a crankarm, means for supporting said crankarm for rotation about a first axis, first and second cam surfaces, means for supporting said first and second cam surfaces for rotation about a second axis extending parallel to said first axis, a first link mounted for pivotal movement about a third axis extending parallel to said second axis, first cam follower means connected with said first link and disposed in engagement with said first cam surface for effecting pivotal movement of said first link about said third axis upon rotation of said first cam surface about said second axis, a second link interconnecting said first link and said crank arm and movable by said first link to effect rotation of said crank arm through at least a portion of a circular path about said first axis upon movement of said first link about said third axis, a third link mounted foR pivotal movement relative to said first link about said third axis, second cam follower means connected with said third link and disposed in engagement with said second cam surface for effecting pivotal movement of said third link about said third axis upon rotation of said cam surface about said second axis, a fourth link interconnecting said third link and crank arm and movable by said third link to effect rotation of said crank arm through at least a portion of said circular path about said first axis upon movement of said third link about said third axis, and means for effecting simultaneous rotation of said first and second cam surfaces about said second axis to thereby effect simultaneous pivotal movement of said first and third links about said third axis to rotate said crankarm about said first axis.

10. An apparatus comprising means for moving sheet material articles along a sheet feed path, drive means for effecting intermittent operation of said means for moving sheet material articles, said drive means including a drive member connected with said means for moving sheet material articles, means for supporting said drive member for 360 degrees of arcuate movement in one direction along a circular path, first and second linkage means for applying transversely directed forces to said drive member to move said drive member through 360 degrees of arcuate movement in said one direction along said circular path, and cam means for effecting operation of said first and second linkage means to move said drive member in said one direction along said circular path through a predetermined arcuate distance, for interrupting operation of said first and second linkage means and movement of said drive member in said one direction along said circular path upon movement of said drive member through the predetermined arcuate distance, and for effecting operation of said first and second linkage means to continue movement of said drive member in said one direction along said circular path, said cam means including first cam surface means for effecting operation of said first linkage means and second cam surface means for effecting operation of said second linkage means.

11. An apparatus as set forth in claim 10 wherein said cam means includes a single rotatable cam member having a pair of opposite major sides, said first cam surface means being disposed on one of said major sides of said cam member and said second cam surface means being disposed on the major side opposite from said one major side.