US2961947A

US2961947A - Duplicating machine

Info

Publication number: US2961947A
Application number: US623492A
Authority: US
Inventors: Edward M Springer
Original assignee: Heyer Inc
Current assignee: Heyer Inc
Priority date: 1956-11-20
Filing date: 1956-11-20
Publication date: 1960-11-29
Anticipated expiration: 1977-11-29

Description

Nov. 29, 1960 E. M. SPRINGER DUPLICATING MACHINE '7 Sheets-Sheet 1 Filed Nov. 20, 1956 INVENTOR.

N 1960 E. M. SPRINGER 2,961,947

DUPLICATING MACHINE Filed Nov. 20, 4 1956 7 Sheets-Sheet 2 i M A I a; 82 m, E 11 W 90 Q W a w y I 'z 1.90 ig/l/jfo/ l 70 12.9 128 I. in p I I 94 I 154 158 132 133 126' 1 f R J80 NOV. 1960 E. M. SPRINGER 2,961,947

DUPLICATING MACHINE 7 Sheefis-heet 3 H1913 NOV. 20, 1956 www %N% W? %\\Q% Raw IN VEN TOR. awry/w! 43." MM) v 43W Nov. 29, 1960 E. M. SPRINGER DUPLICATING MACHINE Fil ed Nov. 20, 1956 '7 Sheets-Sheet 4 Nov. 29, 1960 E. M. SPRINGER DUPLICATING MACHINE '7 Sheets-Sheet 5 Filed Nov. 20, 1956 IN VEN TOR. /z/m(/ Wang a2 Nov. 29, 1960 Filed Nov. 20, 1956 \llilllllllll E. M. SPRINGER DUPLICATING MACHINE '7 Sheets-$heet 6 WITNVENTOR.

Nov. 29, 1960 E. M. SPRINGER 2,961,947

DUPLICATING MACHINE Filed Nov. 20, 1956 7 Sheets-Sheet 7 IN VEN TOR.

United States Patent "ice DUPLICATING MACHINE Edward M. Springer, Chicago, Ill., assignor, by mesne assignments, to Heyer Inc., Chicago, 111., a corporation of New York Filed Nov. 20, 1956, Ser. No. 623,492

14 Claims. (Cl. 101-132) The present invention relates to duplicating machines.

The duplicating machine to which the present invention is applicable, includes a master carrying drum and means for pressing copy sheets against the master as the drum is rotated. In the use of the machine, the copy sheets are arranged in a stack, and are fed therefrom successively to the drum in synchronism with rotation of the drum, one sheet being so fed in each revolution of the drum.

An object of the invention is to provide novel means for feeding copy sheets to the master carrying drum in a duplicating machine of the character indicated.

Another object is to provide sheet feeding means of the character indicated and unidirectional drive means therefor operated by the master carrying drum.

A further object is to provide feed means and unidirectional drive means therefor of the character indicated in which the feeding elements are operated intermittently, during only a portion of the period of a rotation of the master carrying drum, and only so long as is necessary to feed the copy sheets to the drum which thereafter continues impelling the sheets through the machine.

Another object is to provide feed means and unidirectional drive means therefor in a duplicating machine of the character indicated, in which the feed means feed the copy sheets to the master carrying drum and the sheets are thereafter drawn by the drum, wherein novel construction is provided whereby the feed means are active for so feeding the sheets to the drum and thereafter become inactive but allow the sheets to be drawn therethrough.

Another object is to provide in a duplicating machine of the character noted, in which feed means feed the copy sheets to the master carrying drum and thereafter the drum draws the sheets therethrough, wherein the feed means includes serially arranged portions relative to the travel of the sheets, and the portions are rendered active individually and during only that portion of the travel of the sheet necessary to feed it to the next portion of the feed means or to the drum, respectively.

A further object is to provide in a duplicating machine, feed means and drive means of the character indicated, and novel clutch means in the drive means for actuating the feed means intermittently as noted.

A further object is to provide novel friction gripping means for controlling feeding copy sheets from a stack on a table through the machine.

A further object is to provide novel tensioning means for varying the pressure on certain rolls in the machine which operate to feed the copy sheets through the machine.

A still further object is to provide novel clutch means.

Other objects and advantages of the invention will appear from the following detail description taken in conjunction with the accompanying drawing in which:

Figure 1 is a perspective view of a duplicating machine embodying the improvements of the present invention;

Fig. 2. is a top plan view of the duplicating machine;

Fig. 3 is a partial plan view of a corner of the dupe. licating machine, but showing the use of a motorfor driving the machine rather than a crank;

Fig. 4 is a vertical longitudinal sectional view taken on line 4-4 of Fig. 2, but on an enlarged scale;

Fig. 5 is a view similar to Fig. 4, but showing a copy sheet in a different position of feeding through the' machine;

Fig. 6 is a side elevational novel drive means of the invention;

Fig. 7 is a partial side elevational view SllIlllElFtO Fig. but showing a portion of the drive and certainelements in different positions relative to Fig. 6;

Fig. 8 is a plan view of a portion of V Fig. 6 also showing the novel drive means;

Fig. 9 is a plan view of the novel clutchmeans incorporated in the drive means; 7 v

Fig. 10 is a side elevational view of the novel clutch means, being taken Fig. 8;

Fig. 11 is a vertical axial sectional view of the clutch means, taken on line 11-11 of Fig. 13; Fig. 12 is a sectional view taken on Fig. 2.

In the following detailed description reference is made 1 to the co-pending application of the present Springer,- and Francis K. Moore, filed April 1, 1954, Serial No...

420,232, now U.S. Patent No. 2,830,534. In that application is disclosed and claimed a duplicating machine having a number of structural features common with the present duplicating machine, and for details of the machine-in.

the present case that are not described herein reference may be had to said co-pending application.

Referring first to Figs. 1, 2 and 3, it will be seen that.

the duplicating machine is adapted to operation by a crank, or manual operation, or by power means such as an electric motor. In Figs. land 2 a crank 10 is shown operatively connected with a drive shaft 12 on which is mounted a drum 14. However, if it is desired to utilize power means such as an electric motor 16, such may be connected directly to the drive shaft 12 and utilized with exactly the same result as in using the crank 10. The other features of the duplicating machine are equallyadaptable to hand-operated or power-operatedmachines. The shaft 12 on which the drum 14 is mounted is journaled by suitable means in the machine, such as side plates 18 and 20' which are interconnected by suitablemeans such as tie rods for imparting rigidity to the structure. Side casing members 22 provided for ornamentation may be utilized for covering the operatingelements mounted on the side plates.

At one end of the machine is a feed table 24- for holding a supply of'copy sheets 26 which are fed automatically 2 in succession into the machine as it is operated, the rate of feed being one sheet to each cycle of operation of the,

drum 14. At the other end of the machine is aftraylS for receiving the imprinted sheets issuing from the machine. The drum 14 is provided with suitable means for clamping the end portion of a master sheet 28: to the drum, the master carrying the imprinted matter to be;

, Patented Nov. a9, 196

view of the machine with the adjacent side casing element removed showing the the machine of from the side of the observer inf line 12-12 of duplicated in hectographic or copying ink, the matter being typed, written or drawn in reverse as usual. The specific means for so clamping the master sheet to the drum does not enter into the present invention but is indicated generally at 30 (Figs. 4 and 5).

In the initial portion of the cycle of operation of the drum 14, the topmost copy sheet 26 of the stack on the table 24 is fed forwardly until the leading end or edge of the sheet is pressed into the bight of a pair of contacting upper and

lower rolls

32 and 34, which at that time are stationary. These rolls 32 and 34 are respectively a moistening roll and a presser roll. The feeding of the sheets in succession from the stack is effected by feed means shown as comprising a pair of rubber feed wheels 36 on a shaft 38 which is driven positivelfat the beginning of the cycle of operation from a starting or initial position to advance the top sheet until the forward end or edge is firmly fed into the bight of the

rolls

32 and 34, whereupon the feed wheels 36 become inactive or non-driven, due to the novel drive means of the invention, but can free-wheel in the same rotative direction as the sheet is advanced by the

rolls

32 and 34. The wheels 36 are of suitable dimension in axial direction but together may be referred to generally also as a roll, serving the function of a roll. Following the interruption in positive feed of the feed wheels 36 and shaft 38, the

rolls

32 and 34 become positively driven, by the novel feed or drive means of the invention, during the succeeding portion of the same cycle of operation of the drum, and advance the sheet between those rolls (32 and 34) and into the bight between the drum 14 and the subjacent contacting impression roll 40. The roll 32 applies moisture to the upper surface of the sheet as it advances between the

rolls

32 and 34. The means for applying moisture to the roll 32 is not shown herein but is shown and described in detail in the copending application mentioned above. As the forward end of the sheet passes into initial engagement between the rotating drum 14 and the impression roll 40, the

rolls

32 and 34 become free-wheeling and are rotatable in the same direction by the remainder of the sheet passing there between, the sheet being drawn forwardly by the engagement therewith by the drum and impression roll. Moisture is applied to the sheets as they pass in contact with the roll 32, but when a sheet has passed out of engagement with the

rolls

32 and 34, rotation of the rolls ceases until positively driven during a corresponding portion of the next cycle. The interruption of the operation of the

rolls

32 and 34 as just described avoids the needless and disadvantageous application of fluid by the moisture roll 32 to the presser roll 34 and thus not only conserves fluid supply, but avoids the application of fluid to roll 34 and by the latter to the rear surface of the sheets passing between the rolls.

From the foregoing brief general description of operation of the machine it will be seen that the feed wheels 36 and the moistening roll 32 are positively driven only during a portion of the cycle of operation in which a sheet is sent through the machine. The roll and drive means of the present invention, which will be described in detail hereinbelow, effects the desired operation of the wheels 36 and roll 32 in the manner mentioned. Referring to Figs. 4 and 5 attention is directed to the top one of the copy sheets 26, designated 26a. During the first portion of a cycle of operation, as determined by the rotation of the drum 14, the feed wheels 36 are positively driven, as stated, and feed forwardly the top sheet 26a.

This sheet is fed forwardly until its leading end or edge.

is within the bight of the

rolls

32 and 34. At this time the latter rolls are stationary. The feed wheels 36 are rotated to such extent that the sheet 26a is bowed upwardly to an appreciable extent, as shown in Fig. 4. At about this time the feed wheels 36 cease rotating, but are held against reverse rotation, and pressure in the bowed portion of the sheet 26a biases the forward edge of the sheet into engagement with the

rolls

32 and 34. Also at .4 about this time, the roll 32 becomes positively driven and this roll and the cooperating ,roll 34 engage the leading edge of the sheet and draw it through toward the drum 14 and impression roll 40. As this is being done the bowed portion of the sheet flattens out, as shown in Fig. 5. The roll 32 in cooperation with the roll 34 continues to feed the sheet forwardly until its leading edge is brought into the bight between the drum 14 and the impression roll 40 (see Fig. 5) into engagement with the drum and roll. At this time the drum is rotating, as it has been throughout the cycle, and the leading edge of the sheet is gripped between the drum and the roll and carried therebetween in a manner similar to that of the

rolls

32 and 34. At about the time the sheet is so gripped, the roll 32 becomes nondriven, but it is enabled to free-wheel in the same direction of rotation. Thereupon the sheet 26a is drawn by the drum 14 and impression roll 40 for the remainder of the passage of the sheet through the machine, the feed wheels 36 and rolls 32 and 34 being rotated by the move ment of the sheet therebetween. The novel drive means of the present invention efiects this driving movement of the feed wheels and moistening roll, and the cessation thereof.

The various elements of the machine heretofore described may be mounted in any suitable manner, except certain specific elements as will be described in connection with the novel drive means hereinbelow, and for additional details of the mounting thereof, reference may be had to the co-pending application mentioned above.

A fluid tank 42 is provided (Figs. 4-7) for supplying fluid to the moistening roll 32, as fully described in the above mentioned co-pending application. This tank is mounted in a suitable manner as in the

side plates

18 and 20.

able journal hearings in the

side plates

18 and 20 receiving the shaft 12. The shaft 12 extends through one side of the machine, as indicated above, for mounting of the crank 10 or motor 16 thereon, while the end opposite this end extends through the respective side plate 18 into the spaceenclosed by the associated side casing member 22 in operative relation with the novel drive means of the present invention shown most clearly in Figs. 6 and 7.

At this location of the machine a gear 44 is secured to the shaft 12, outwardly of the associated side plate 18. This gear is fixed to the shaft for rotation therewith and in unison with the rotation of the drum 14. It might be noted at this point that one cycle of operation is that portion of the operation during one complete revolution of the drum 14.

Also mounted on the shaft 12, and preferably outwardly from the driving gear 44 is a clutch control means which in the preferred form of the invention takes the form of a pair of

cams

46 and 48 which are generally of plate-like shape and mounted on the shaft in any suitable manner, e.g., as by set screws 49. These cams may be interconnected, for purposes of rigidity, by suitable means such as screws 50 with spacers 52 between the cams. These cams rotate in unison with the shaft 12 and drum, and hence make one revolution for each revolution of the drum and driving gear 44, and thus one revolution in a cycle of operation. 1

Attention is directed to Figs. 6 and 7 for the shape of the

cams

46 and 48. Each of these cams has a circular portion 54 and a flat portion 56. The circular por-.

tion extending a substantial distance therearound while the flat portion extends through a substantially smaller angular dimension. The purpose of these cams, which will be explained more fully hereinbelow, is for controlling the novel clutch means of the drive. Each of the fiat portions 56 is provided with a projection 58. at the trailing edge thereof, with respect to the direction of rotation of the cams, which is clockwise (Figs. 6 and 7) and adjacent the leading end of the circular portion 54. The novel clutch means is indicated in its entirety by The mounting of the drum 14 may be by means of suit the numeral 60 in Figs. 6 and 7, in which it is shown adjacent the cams, and shown isolated therefrom in Figs. 9-14. The clutch 60 derives its drive from the main "driving gear 44 through the intermediary of a gear set '62 secured for conjoint rotation and mounted on a stub shaft 64 suitably supported as in the adjacent side plate '18. The gear set 62 includes a smaller gear 66 in mesh with the main gear 44 and a larger gear 68 in mesh with a gear 70 on the clutch 60.

The clutch 60 transmits drive from the main gear 44 to the feed wheels 36 and the m oistening roll 32. For purposes of facilitating observation of the various figures, it is pointed out that the moi'stening roll 32 is coaxial with the clutch 69, being mounted on a shaft 72 (Figs. 6, 7, and 13) journaled in the side plates of the machine and supporting the clutch means 61) at its outer end, as explained in detail hereinbelow. The shaft 38 on which the feed wheels 36 are mounted is shown in Fig. 6 at the far right of the series of gears constituting a drive means and designated gene-rally by the reference numeral 74.

Attention is direction to Figs. 9 to 14 showing the details of construction of the novel clutch means 60 re ferred to above in connection with Figs. 6, 7, and 8. Fig. 9 is oriented similarly to the clutch in Fig. 8, where it will be seen it is interposed between the main gear 44 and the chain of drive gears 74. The clutch means 60 is a double clutch and includes two portions, one for controlling the drive to the moistening roll 32 and the other for controlling the drive through the drive means 74 to the feed wheels 36. The clutch means may be mounted in any suitable manner but preferably is mounted on the shaft of the moistening roll 32. In Fig. 13 it may be seen that the moistening roll 32 includes an outer resilient element 76 secured to a shaft 78. The shaft 78 has a counter bore 80 in which is disposed one end of a reduced shaft 82 fixed for rotation with the shaft 73 by suitable means such as a pin 84 extending diametrically through the shafts. The stub shaft 82 is mounted in the side plate 18 by means of a suitable bearing 86 which may be a ball hearing or roller bearing. On the outer end of the stub shaft 82, as clearly shown in Fig. 13 the clutch means 60 is mounted. The

shafts

78 and 82 make up the shaft 72 mentioned above.

The clutch means 60 includes a clutch housing 88- which is made up of a cylindrical wall element 90 form-- ing the housing proper and a central disc 92 having an aperture 94 in which is fitted a bearing element 96, the bearing element receiving the stub shaft 82 in bearing support of the housing member 88 in free rotative relation to the shaft. The central disc 92 defines side recesses 98 and 1130, respectively, in which are disposed clutch sections 102 and 104, respectively, for transmitting drive from the clutch housing 83 to the feed wheels 36 and moistening roll 32. Mounted on the exterior of the clutch housing 88 is the gear 70 referred to above which is in mesh with the gear 68 (Figs. 6 and 7). The gear 70" is preferably a high wear resistant gear of such material as nylon and is secured to the clutch housing by any suitable manner such as by molding it thereon and providing it with interlocking elements 106 (Fig. 13). The remainder of the clutch housing may be of suitable metal.

The clutch section 102 includes a center disc 108, disposed in the recess 98, from which extends a hub por tion 111 terminating in a reduced portion 112, a shoulder 114 being formed between the latter two portions. A suitable bearing element 116 is fitted in the aperture 117 in the center disc 102 in bearing engagement with the stub shaft 32 for free rotation between the center disc 1112 and the stub shaft. A gear 118 is fixed on the portion 112 of the center disc for rotation therewith. The

gear 118 may be of any desired construction but pref} erably includes a center portion 120 of suitable material such as metal and an outer gear ring 122 of high wear resistant material such as nylon.

assist-2 The clutch section 104 includesa center disc 124 lar to the center disc 168 but opposite and symmetrical thereto in arrangement of elements, as fully explained below. The center disc 124 is disposed in the recessltN). in the clutch housing 88 and extending from the center disc 124, outwardly with respect to the recess, is a cy-. lindrical Wall 126 defining a recess128, The cylindrical wall 126serves as a clutch member in another clutch means designated generally at 129 transmitting free' wheeling drive to the stub shaft 82 and hence to the moistening roll 32. A bearing element 130 is fitted in the central bore 131 of the clutch section 104 and provides bearing support on the stub shaft 82 for free rotation of the clutch section thereon. The clutch section cooperating with the wall or housing 126, designated 132, includes a disc 133 disposed in the recess 128 and having an extension or sleeve 134 secured to the stub shaft 82 for rotation therewith as by means of a pin 136, secured therein in a customary manner. The sleeve 134 provides the support for the stubshaft in the bearing 86. referred to above. If. desired a shoulder 138 may be formed on the stub shaft 82 for. engagement by the clutch: section 132. The clutch means including the cylindrical wall 126 and section 132 pro-vides a clutching func- The center discs108 and 124 in the clutch sections'102 and 104 are oppositeand symmetrical, being arranged for rotation in the same direction and for clutching engagement when rotating in that direction. I The

center discs

108 and 124 are provided with notches 140 (Figs. 10. and 11) each having a floor surface 142 and a rear- Wall surface 144. These notches in both portions of the clutch are all oriented in the same direction, as viewed axially from theclutch means, asfrom the left of Fig. 13 and as shown in Figs. 10 and 11. 'Fig. 10 indicates the; notches in the center disc 108 while the, notches 140 of Fig. 11 are of the center disc 124. The center discs are arranged for rotating clockwise, as viewed in Figs. 10. and 11 and from the left of Fig. 13. The drive is transmitted from. the

center discs

108 and 124 by means of rollers 146 disposed one in each of the notches 14d and biased by a compression spring 148 inter posed between the respective roller and rear wall 144. The springs 148 serve to bias the rollers 146 (relative-i 1y speaking) toward the opposite end of the floor sur-l face 142 where that surface converges with the inner, surface of the cylindrical wall 90. Uponrotation of the cylindrical wall 90 (i.e., housing 83) in clockwise direction, as is the directionof its movement, the rollers .146 are gripped between those surfaces, and the center discs 1&8 and 124 are rotated therewith. Upon retraction of the rollers 146 in the opposite direction, in a manner to" be explained here-inbelow, the gripping engagement between those surfaces is released and the cylindrical wall" 90 (housing 88) is permitted to rotate relative to the center disc. H

Each roller 146 is in the form of a sleeve rotatably fitted on a clutch spacer 150 (Fig. 13) having reduced end por tions 152 fitted in apertures respectively in an inside disc 154, 156 and an

outside disc

158, 160. u j I p Each inside disc 154, 156 is disposed innermost in the?

respective recess

98 and 100, and inwardly of the

corresponding center disc

108, 124. Each disc 154, 15;6 isi provided with a central, aperture for freely receivingth e;

stub shaft 82 and bearing elements thereon and is an outer diameter to be freely received in the

corresponding recess

98, 100 for free movement therein.

Each

outside disc

158, 160 has a central aperture for cooperate with the earns 46 and 48 on the drum shaft 12,

in a manner to be explained fully hereinbelow. h For convenience in identification of the portions of the clutch means 60 it is pointed out that the left half portion of the clutch means as viewed in Fig. 13 will be referred to as the feed portion while the latter half will be referred to as the moistening portion since it is utilized for controlling the rotation of the moistening roll 32.

The clutch spacers 150 serve to rigidify the respective inside and outside discs in assembly which prevents binding of any of the parts thereof. The assembly receives its bearing support through the rollers 146 which bear on a surface of the notches 140, or the inner surfaces of the cylindrical wall 90, or both.

Each outside disc 158, 160 (Figs. 6, 7, 10, and 11) is provided with a notch 162 having a shoulder 164 facing in counterclockwise direction for engagement by a respective finger 166 (Fig. 6) biased about a stud 168, on which it is pivoted, to a holding position in which the extended end 170 thereof rides on the other periphery of the disc and falls into the notch 162 in position, as in Fig. 6, for engagement by the shoulder 164 therewith to prevent retrograde, or counterclockwise, rotation of the disc. The fingers 166 are so biased by a leaf spring 172 secured at one end to the finger 166 and having its other end slidably received in a slot in a bracket 174 mounted in a suitable location, as on the side plate 18. The leaf spring tends to assume a straight position and hence biases the finger extension 170 upwardly to a position to be engaged by the shoulder 164. The spring further has the advantage that it moves the finger to its upper position without snapping against the disc at the inner extremity of the shoulder, and hence avoids a clicking sound that may otherwise occur.

The

outside discs

158 and 160 are provided with

trip levers

180 and 182, respectively, mounted on the outer surface of the discs. The trip arms are also opposite and symmetrical, being arranged on the respective

outside discs

158 and 160 in accordance with a common direction of rotation and corresponding control by the

cams

46 and 48.

The trip levers 180 and 182 are pivoted at one end to the respective discs by means of pins 184 of suitable character. The trip levers at their opposite and swinging ends extend toward the

respective cams

46 and 48 when the clutch means is in stationary position. In the swinging end portion of each trip lever is a slot 186 receiving a pin 188 secured in the respective

outside discs

158, 160 for guiding and limiting the swinging movements of the trip levers. On the swinging ends of the trip levers 180 and 182 are cam followers 190 which preferably are in the form of rollers mounted on pins or studs 192. These cam followers directly engage the

respective cams

46 and 48 in a certain portion of the rotation of the cams.

The trip levers 180 and 182 directly control the clutching and de-clutching function of the main clutch means 60. This is done by means of projections or pins 194 on the trip levers extending into the notches 140 in the

respective center discs

108 and 124 and engageable with the surfaces 142 of the notches for relatively moving the

center discs

108 and 124 with respect to the cylindrical wall 90 or clutch housing 88. This operation is accomplished by swinging movement of the trip levers 180 and 182 about their axes in the pins 184. Upon downward swinging of the swinging ends of the trip levers, as viewed in Figs. 10 and 11 the pins 194 engage the surfaces 142 of the notches and produce relative rotary movement between the center discs and the

outside discs

158 and 160. These relative positions are shown in full and dotted lines, respectively in Fig. 11. In the full line position of the notches 140, the rollers 146 are in engagement with the surfaces 142 of the notches and the inner surface of the cylindrical wall 90, and rotation of the cylindrical wall 90, acting through the rollers 146, produces rotation of the center disc 124 in the same direction (clockwise). Such is the position when the corresponding trip lever is in upper or raised position shown in full lines in Fig. 11. Upon downward swinging of the swinging end of the trip lever the center disc (124 Fig. 11) is rotated relatively to the position indicated in the dotted lines, which represents the new position of the notches. In such new position the rollers 146 are disposed in a wider portion of the notch wherein gripping action by the cylindrical wall on the rollers is lost. Since the rollers 146 are secured to the

outside discs

158, 160, relative rotation between the outside discs and center discs, by the trip arms, produces relative rotation between the

center discs

108, 124 and cylindrical wall 90 (housing 88). Upon release of the trip levers 180 and 182 they are raised to the upper position (Figs. 10 and 11) by means of the compression springs 148 which react between the rollers 146 and the rear wall surfaces 144 of the notches 140. The action of these springs is exerted between the rollers 146 attached to the outside discs 158, and the

center discs

108, 124.

The

outside discs

158 and 160 are provided with notches 196 for receiving the cam followers 190 in the swinging movements of the latter. These notches 196 are of appropriate dimension and shape to accommodate the swinging movements of the cam followers 190.

The clutch means 60 is associated with the

cams

46 and 48 in such manner that the drive to the clutch means is provided through the

gears

44, 66 and 68 to the clutch means, while the control of the clutch, for clutching and de-clutching it, is provided by the cams acting on the trip arms and 182.

Rotation of the drum shaft 12 and consequent rotation of the main gear 44 results in rotation of the clutch housing 88 which normally is continuous and constant throughout the period of use of the machine, rotation of the clutch housing being clockwise as viewed in Figs. 6, 7, 10 and 11. Considering first a non-rotating condition of the clutch means, or released condition, there is no drive engagement between the clutch housing 88 and the remainder of the clutch means. This stationary or nonacting condition is brought about by the engagement of the

cams

46 and 48 with the cam followers on the trip levers 180 and 182. The connections and relative locations of the cams and the clutch means 60 is such that the circular portions 54 on the cams extend beyond the orbit of the cam followers 90 when the respective trip arms are in extended or outwardly disposed position such as shown in full lines in Figs. 10 and 11. This condition is indicated also in Fig. 6 wherein the trip lever 180 (which is the one exposed to view) is disposed in inwardly swung position by engagement with the respective cam 46. The orbit of the cam follower is indicated by a line 198 (Fig. 11) this being such orbit when the trip levers are in extended position. When the circular portion of the cam (referring to the cam 46 and trip lever 18'0 specifically, for convenience) engages the cam follower 190, the trip arm is swung inwardly to clutch releasing position shown in dotted lines in Figs. 10 and 11. In such position of the trip lever, as explained above, the clutch is released and the clutch housing 88 rotates freely while the clutch sections 102 and 104 remain stationary.

The latter elements are held against rotation by the

cams

46 and 48 acting on the trip levers 180 and 182. Referring to Fig. 6 it will be noted that the cam follower 190 is disposed in trailing position relative to a line 200 drawn through the axes of the

cams

46 and 48 and the clutch means 60, this trailing position being with respect to the direction of rotation of the clutch means. In order for the

outside discs

158 and 160 to rotate, it is necessary for the cam followers, 190 to move through their orbits 198, but since these orbits overlap the curved portion 54 of the cams, rotation of the discs is prevented. It will be remembered at this point that restraint of the

discs

158 and 160 against rotation results also in restraint of the clutch sections 102 and 104 from rotation in view of the connections of the rollers 146 with both the discs and the clutch sections (compare Figs. 11 and 13).

Continued rotation of the cam 46, for example, moves the flat or cut-off portion 56 thereon into register with the cam follower 190 and enables the latter to swing outwardly relative to the clutch means, which is toward the axis of the cams, i.e., from the dot-dash line position to the full line position of Figs. and 11. This outward swinging movement of the trip arms, as explained above provides a clutching effect between the cylindrical wall 90 (clutch housing 88) and the corresponding clutch section 102 or 104 through the rollers 146. So long as the trip levers 180 and 182 are free of control of the earns 46 and 48 the intended portions of the clutch means rotate for transmitting drive from the clutch means to the respective feed means in the machine.

Upon continued rotation of the cam 46 and clutch means 60 from the position shown in Fig. 7 the circular portion 54 of the cam again comes into action in engaging the cam follower 190. For this purpose the projection 58 on the cam comes into play and engages the respective cam follower for facilitating interengagement between the circular portion of the cam and the cam follower, the cam follower riding up on the projection and onto the circular portion 54. As the cam continues to rotate and the projection '58 on the cam approaches the position where it engages the cam follower a relation is established as shown in Fig. 11, where just below the line 200 the projection 58 is shown about to engage the cam follower 190. Rotation of the cam in clockwise direction and similar rotation of the clutch means results in opposite linear movement of the related portions of these two elements such that the cam followers ride onto the curved portions 54 of the cams, to the relative position of Fig. 6, which results-in inward swinging movement of the trip anns, relative to the clutch means, for de-clutching the clutch means and establishing the holding relation between the circular portion 54 of the cam follower at a point in trailing relation to the line 200 with respect to the direction of rotation of the cam, as explained above. The tendency of the cams when engaging the trip arms, which are on the

outside discs

158 and 160, is to rotate the outside discs in retrograde direction (counterclockwise, Figs. 6 and 7) but but the shoulders 164 of the notches 162, in response to engagement with the fingers 166, prevent such retrograde movement. The resulting effect is entire elimination of backlash and otherwise accurate control of the feeding means.

As mentioned above the right-half portion of the clutch means 60 (Fig. 13) controls the drive to the moistening roll 32, and the left-half portion controls the drive to the feed wheels 36. Since the moistening roll and feed wheels 36 are driven at different periods, the

cams

46 and 48 are disposed in relatively angularly displaced positions for accomplishing the timing of the periods of drive. This angular relation of the cams is clearly shown in Figs. 6 and 7.

The drive between the moistening roll half of the clutch means 60 and the moistening roll is transmitted through the second clutch means 129, as indicated above, which includes the clutch section 104 and the clutch section 132. The disc 133 is provided with notches 205 (Figs. 10 and 12), each having a floor surface 208 and a rear wall surface 210, these notches being similar to the notches 140 referred to above in the clutch sections 102 and 104. Rollers 212 are disposed in the notches and are biased by compression springs 214, compressed between the rollers and the respective rear wall surfaces 210, into the portions of the notches where the surfaces 208 converge with the inner surface of the circular wall 126. This form of clutch is known, and constitutes a free-wheeling or over-running clutch. The notches 206 are oriented similarly to the notches 140 as viewed axially of the moistening roller shaft (Fig. 10) and are thus arranged for transmitting drive between the clutch section 104 and the clutch section 132 in clockwise direction when viewed in the direction mentioned. Compari-' son is made with Figs. 4 and 5, oriented oppositely to Fig. 10, in which the direction of rotation of the moisten- 10 ingroll 32 and feed wheels 36 is counterclockwise") Upon cessation of rotation of the clutch section 104,. the clutch section 132, which is connected with the moistening roll, is enabled to continue rotation in the same direction, or in free-Wheeling or over-running direction.

The drive means 74 referred to above for transmitting drive from the clutch means 60 to the shaft 38 and feed wheel-s 36 includes a series of gears designated 216, 218, 220, and 222. The gear 216 is mounted on a stub shaft 224 suitably secured in the frame of the machine, as in the'side plate 18. This shaft is fixed in location, and'the gear is in constant mesh with the gear 118 on the clutch means 60. The remaining

gears

218, 220, and 222 are mounted in a swinging arm 226 pivoted at one end on the stub shaft 224 carrying the

gears

218 and 220 on

pins

228 and 230, respectively. The arm 226 is one of a pair of arms, the other being on the opposite side of the machine and not shown herein, the swinging ends of the arms journalling the shaft 38 on which the feed wheels 36 are mounted. The ends of the shaft 38 extend through appropriate slots 232 in the side plates, one of which is shown (Fig. 6) and the gear 222 is secured to the adjacent end of the shaft 38 through the medium of a free-wheeling or over-running clutch 233 (Fig. 8). The clutch 233 is essentially identical with the freewheeling clutch 129 between the clutch means 60 and moistening roll 32 (Figs. 12 and 13). In fact, Fig. 12 may be considered as taken on line 1212 of Fig. 8, as well as where first indicated. The arrangement formounting the gear 222, clutch 233, and shaft 38 may: be conventional, such as providing a stub shaft element in the shaft 38 which serves as the means for supporting the shaft in the arm 226 and on which the driven portion of the clutch is fixed for rotation therewith. The gear 222 and the driving portion of the clutch are fixed together for conjoint rotation on and relative to the stub shaft. It is believed that further details need not be illustrated or described. Upon rotation of the train of gears mentioned, namely, 118, 216, 218 and 220, drive is transmitted to the gear 222 and hence to the shaft 38 for rotating the feed wheels 36, which are secured on" the shaft for that purpose. The feed wheels 36. of course rotate in the same direction as the moistening rolls 32, in sheet feeding operation, and such direction is indicated clearly in Fig. 6, where it is shown that the gear 222 rotates in clockwise direction. The same is true as shown by the arrow indicating direction of rotation of the gear 118 and clutch means 16.

The arms 226 have upwardly extending projections 234 (Fig. 6) in which are secured the ends of a tie rod 236 (see also Figs. 1, 2 and 8) extending through the slot 232. The tie rod serves to rigidify the assembly including the swinging arms, shaft 38 and the tie rod. The tie rod also serves as a means for grasping the assembly and raising it, and the feed wheels 36, up out of engage' ment with the table 14, for insertion of copy sheets under the feed wheels. Latch means is provided for releasably' holding the arms 226 and thus the feed wheels 36 in raised position. This latch means may take the form of a lever 238 pivoted on a pin 240 mounted in the side plate 18' and having a turned-over lower portion 242 engageable' in a notch 244 in the swinging end of the arm 226. At

the opposite and upper end a turned-over top portion 246 extends through a slot 250 in the side plate to the interior of the machine for grasping it by the fingers. The lever 238 is biased in clockwise, latching direction by a spring 254, having a central portion looped about the pin 240, with one leg engaging a stop or pin 256 mounted on the frame and the other end engaging the;

turned-over lower portion 242. Upon raising the arms 226, as by grasping the tie rod 236 and lifting it, the lower turned-over portion 24-2 rides on and engages the end of the associated arm 226 and is cammed into the slot 244,

and after the latching operation thereof and release of the tie rod 236, the latter is retained in elevated"position."

When it is desired to lower the feed wheels 36 the upper turned-over portion 246 is grasped by fingers and the lever 238 rotated counterclockwise to unlatch the lower turnedover portion 242 and remove it from the notch 244. The arms 226 are then permitted to drop, lowering the feed Wheels 36 into engagement with the copy sheets on the table 14.

The unidirectional and intermittent drive is utilized in connection with a continuously rotating counter to produce the elfect of a trip counter. A counter is shown at 216 which is of conventional continuously rotating type, utilized for registering the number of sheets passing through the machine in the operation thereof, having normally uniformly rotating discs. The counter being of conventional nature need not be described in detail, but it includes a driving wheel 262 having suitable gear teeth thereon for coaction with a belt 264, such as a rubber belt, having teeth for engaging with the gear teeth. The belt is also trained over another gear 266 on the stub 'shaft 224 (see Figs. 6 and 8) and secured for rotation with the gear 216. For this purpose the two gears may "be interconnected by a sleeve 268 rotatably mounted on the stub shaft. A bolt tightener 270 may be provided, "having a roller 272 mounted on a bracket 274 secured at a convenient location on the machine, which for convenience may be on a bracket 276 which mounts the ad- .jacent end of the fluid tank 42. The bracket 270 is provided with an elongated slot 278 through which screws 280 project and are secured in the bracket 276, for adjusting the bracket 274, and consequently the roller 272, into belt tightening relation with the belt 264.

During each cycle of operation of the machine the gear 118 is rotated a predetermined number of times (one complete revolution) and during the remainder of the cycle of operation it remains stationary. The period in which it is stationary is longer than the period in which it rotates, as evidenced by the relative angular dimensions of the flat portions 56 and circular portions 54 of the

cams

46 and 48, whereby the counter after moving to indicate one unit increment remains stationary for a substantial period, with the effect of a trip counter. It will be understood that the ratio of the various drive transmitting elements including the gear 266 and the gear on the wheel 262 is such as to produce the desired increment of rotation of the counter in each cycle of operation of the machine.

The drive means, as is evident from the foregoing description, provides for independent drive of the feed wheel 36 and the moistening roll 32. Each is positively driven during that portion of the cycle of operation necessary for feeding the copy sheets the desired distance to the next succeeding phase or stage, i.e., the feed Wheels 36 feed the sheets to the

rolls

32 and 34, and the

rolls

32 and 34 feed the sheets to the drum 14 and impression roll 40. After the feed wheels 36 and moistening roll 32 feed the sheets the necessary distance the positive drive thereto ceases, by virtue of the relation between the

cams

46 and 48 and the clutch means 60, While the respective clutch means 129 and 233 enable free-wheeling or over-running of the feed wheels and moistening roll for drawing the sheets therethrough by the means thereahead. As soon as either the feed wheels 36 or the moistening roll 32 has accomplished its purpose in feeding the copy sheets, the drive imparted thereto is interrupted.

The unidirectional nature of the drive from the drum shaft 12 to the feed wheels 36 and the moistening roll 32 is of decided advantage in preventing backlash between any of the operating parts, as compared with reciprocating or oscillating parts. Any inaccuracy due to lack of precision in the manufacture of the parts is completely obviated since any play taking place between the parts has effect in only one direction and once accurate relation has been established between the moving parts the accurate relationis maintained throughout the operation of the machine.

As brought out in the co-pending application mentioned above, it is desired to provide for yieldable tensioning of the rolls 34 and 40 into operative engagement with the corresponding driving elements, namely, the moistening roll 32 and drum 14. For this purpose, the rolls 34 and 40 are mounted in supporting members 282 and 284, (Figs. 4 and 5) there being two of each of these members, one at each of opposite sides of the machine and supporting the adjacent end of the respective roll. These two supporting members are similar and are pivotally supported by suitable means such as

pins

286 and 288 mounted in theside frames of the machine. The supporting members have arm portions 290 and 292 directly supporting the ends of the rolls and disposed eccentric to the pivotal supporting means 286 and 288. A tension spring 294 interconnects the supporting members. Upon swinging movement of the supporting members in counterclockwise direction (Figs. 4 and 5) the corresponding rolls 34 and 40 are brought into greater pressure engagement with the corresponding driving members, namely, the moistening roll 32 and the drum 14.

The means for varying the pressure of the rolls 34 and 40 in the manner mentioned includes a shaft 296 journaled in the side plates of the machine bearing an eccentric or cam 298 fixed thereon and rotatable therewith. Engaging and partially surrounding the eccentric 298 is a spring steel member 300 similar to a clock spring (see Figs. 5 and 8) and having its end portions secured to a release device indicated generally at 302 connected to the supporting member 284. The release device includes an L-shaped bracket 304 secured as by a bolt 306 to a bar 308 extending across the machine and mounted on the supporting members 284. The bracket 304 may be adjusted by means of the bolt 306 toward and from the bar 308 for providing major adjustment or tensioning effect such as by making an original adjustment. A piece 310 is secured to the cross bar 308, having a horizontal portion which supports a slide member 312 extending through an aperture in the cross bar 308 and having upturned

portions

313 and 314 at its ends. The horizontal portion of the piece 310 has an aperture 316 adapted to receive a depressed tongue 318 on the member 312. The ends of the spring member 300 are secured to the

elements

304 and 312 by suitable means such as by rivets, or by spot welding, etc.

Normally, the tongue 318 is disposed in the aperture 316 and in a normal setting of the device the spring 300 retains the supporting 284 in a position for imposing a predetermined pressure of the impression roll 40 on the drum. The spring 294 interconnecting the supporting members 284 and 282 biases the latter supporting member in direction for imposing pressure by the presser roll 34 on the moistening roll 32. In order that this pressure not be constantly maintained, and to facilitate releasing it, at such times as overnight or over a week end, the pressure may be released by raising the member 312 to remove the tongue 318 out of the aperture 310 and enable the piece 312 to slide through the cross bar 308 until the upturned portion 34 engages the cross bar 308. When it is again desired to re-establish the pressure the operator merely places his thumb on the cross bar 308 and his finger on the upturned portion 313 and slides the member 312 to the left (Fig. 5) until the tongue 313 enters the aperture 316.

Pressure exerted by the rolls 34 and 40 may be varied by the shaft 296 which is rotated for rotating the eccentric 298. Rotation of the eccentric, as will be understood, varies the pressure of the roll 40 through the supporting member 284, and of the roll 34 through the spring 294 and supporting member 282. Means is provided for access from the exterior for this purpose and includes a pulley 320 on the end of a shaft 296 at a convenient locatron such as exteriorly of the side plate 18 (Figs. 6 and 8 A belt or flexible cord 322 is trained over the pulley 320- and its ends are secured in lugs 324 on a lever 326 pivoted on the'drum shaft 12. The lugs 324 are respectively on opposite sides of the axis of the shaft and upon swinging or pivoting of the shaft on its pivot the belt 322- effects rotation of the pulley 320 and hence of the shaft 296 for rotating the eccentric 298, as explained. The lever'326 includes a finger grip 328 (Fig. 8) working in an arcuate slot 330 in the side plate 18. The finger grip element 328 is exposed in the machine at a convenient location for the operator to grasp it and swing the lever for varying the pressure on the rolls 34 and 43 as described.

The spring 300 is a flexible piece of steel and is unyielding. Its flexibility readily accommodates the eccentric 298, in curvature and in swinging movements of the eccentric. When the desired pressure produced by the rolls 34 and40 is established, the operator is assured that this pressure will be maintained due to the nonyielding character ofthe spring 300.

Novel means is provided for tensioning or yieldably gripping the side edges of the copy sheets 26 on the table 24. This gripping action is such as to prevent more than one sheet being withdrawn at a time by the feed wheels 36.- The gripping means indicated in its entirety at 332 is-shown most clearly in Figs. 1, 2, l4, l and 16. One such gripping means is disposed at each side of the table 24. The gripping means are mounted in side guides 334, each of which is L-shaped in cross section (Figs. and 16) having a base portion 336 and an upstanding flange 338. The flanges 338 are provided with notches 340 adjacent the ends thereof for receiving the shaft 38 (Fig. 1) in the lowering movement of the latter in response to lowering of the stack of copy sheets 26. It will be noted that the notches are at both ends of the flanges, whereby to enable the table 24 to be reversed end-forend in the machine, as explained in the co-pending application mentioned above. The side guides 334 are adjustable laterally of the table, toward and from each other and are controlled in such adjusting movements by a means such as shown in Fig. 16. For this purpose, the table 24 is provided with transverse slots 342 which re- Ceive blocks 344 secured to the under surface of the side guides as by means of rivets 346. The outer end portion of each block portion 344 is provided with a tapped hole for receiving a thumb screw 348. The thumb screw is threaded through the hole and engages the lower end of a gripping element 350 which is pivoted at 352 on the block. The gripping element 352 may be U-shaped, at least at its lower end, for engagement by the thumb screw 3,48,, and at its upper end has fingers forming a surface 354disposed at an appropriate angle for engaging the under surface of the table 24 at each of opposite sides of the block 344. Upon turning the thumb screw 348 downwardly, the gripping element 354 is moved clock- Wise (Fig. 16) and the surface 354 is brought into gripping engagement with the under surface of the table 24, and upon turning the thumb screw in the opposite direction the gripping pressure is released. Thus upon loosening the thumb screws 348 the side guides 332 may be movedv inwardly toward and from each other and when moved to the desired adjusted positions, the thumb screws are tightened for locking the side guides in such positions. The blocks344 serve as guides in the slots 342 for guiding the movements of the side guides.

The gripping means 332 is shown in detail in Figs. 14 and 15 and each includes a resilient pad 356 which may be of sponge rubber, for example, mounted on a backing plate 358 in a suitable manner. The plate 358 is provided with a screw 360 fitted thereto in a suitable manner by means of a head 362 secured to the screw and spot welded to the plate 358. The pad is mounted in a case 364, generally of cup-shaped formation secured to the flange 338 as by rivets 366. The screw 360 extends through a sleeve 368 disposed in a central aperture of the case 364 and also extending through a central aperture in a controlknob 370, the sleeve 368 having a flange 372; engaging the outersurface of the web 374' of the control;

inwardly from the side of thetable and toward the middle thereof, or toward the stack of copy sheets on the table. Upon turning the adjusting knob 376 inwardly the screw 360 and the gripping pad 356 secured thereto are drawn outwardly, and upon adjusting of the screw in the opposite direction the spring means 378 operates to move the pad inwardly into gripping relation with the stack of sheets on the table. Preferably the base portion 336 of the side guide isprovided with an opening or aperture 380 to enable the pad to extend below the upper surface of the portion 336 and thus extend below the bottom sheet in the stack on the table for full gripping effect.

Upon placing the stack of copy sheets 26 on the table the pads 356 are retracted and the side guides are ad justed inwardly-toward each other so that the flanges 338 are adjacent to but preferably spaced slightly from the side edges of the sheets. Thereafter, the adjusting knobs 336 are adjusted outwardly to enable the pads 356 to be moved inwardly-under the influenceof the spring means 378, into friction gripping enegagement with the side edges of the sheets. This pressure may be of any desired. degree, and is such as to retain the sheets against movement from the table, except the topmost sheet under the influence of the feed wheels 36.

If it is desired to release the friction pads from gripping engagement with the copy-sheets, to remove the stack of sheets, but to have the same degree ofgripping effect established after the stack is replaced on the table, the pads 356 may be moved bodily out of an adjusted position, and again moved into the same adjusted position. This means includes cam means interacting between the control knob 370 and the outer wall 365 of the case 364. Such means is best shown in Fig. 16 and includes a p=rojection 382 formed on the wall 365 and a recess 384 in the control knob 370. The recess 384 may be in the form of a groovedisposed radially, and is on the inner surface of the-knob. In one position'o-f rotation of the knob 370, the projection 382 is received in the recess or groove 3 84, and the inner surface of the knob engages the surface of the wall 365. Rotation of the control knob 370 from suchposition, the side surfaces of the recess ride up on the projection 382 and lift the control knob out of engag-ement with the wall 365, against the action of the spring means 378. This movement of the control knob, of course, acts through the flange 372 and the adjusting knob 376, for moving the screw 360 and friction pad 356 out of engagement with the stack of copy sheets. When it is desired to release the friction pad 356, as when a stack of copy sheets is replaced on the table after having been removed, the control knob 370 is again rotated, into thefirst position mentioned, in which the recms 384 receives the projection 382. The control knob then falls into engagement with the wall 355 and the friction pad 356moves inwardly under the action of the spring means 378 tothe exact position it occupied previously, according the position of the adjusting knob 376.

It is thought that the invention and many of its attendant advantages will be understood from the foregoing description, and it will. beapparent that various changes may be made in the form, construction and arrangement of the parts without departing from the spirit and scope of the invention or sacrificing all of its material advantages, the form hereinbefore described being merely a preferred embodiment thereof.

I claim:

1. A machine of. the character disclosed comprising, a.

sheets, feed means for successively feeding sheets from the stack to the drum, unidirectional rotary drive means interconnected between the drum and feed means, rotary clutch means interposed in the drive means, the clutch means including a first element constantly driven by the drum and a second element driven by the first element, means biasing the elements to relatively engaged position, a trip lever carried by the second element pivoted on an axis parallel with the clutch axis and swingable for moving the clutch elements to relatively disengaged position, and cam means driven by the drum for engaging the swinging end of the trip lever and moving the clutch elements to relatively disengaged position during a predetermined portion of a rotation of the drum, said cam means when so engaging said trip lever being operative for preventing rotation of the second element of the clutch.

2. A duplicating machine, a rotatable drum, means for supporting a stack of copy sheets, a first feed roll for successively feeding sheets from the stack toward the drum and including a roll frictionally engaging the sheets, second feed means receiving copy sheets from the first feed means and feeding them to the drum and including a roll frictionally engaging the sheets, rotatable clutch means, a first member in the clutch means constantly driven by the drum, a second member in the clutch means for each feed means including a disc, spring biased wedge means for establishing drive between the first member and each second member, drive means connected between each second member and the respective one of the feed means, each second member having a disc, trip means mounted on the disc for moving the first member and associated second member out of driving engagement, and cam means driven by the drum for each said second member and engageable with the respective trip means and disengaging the second member and first member and operative for retaining the second member against rotation.

3. The construction set out in claim 2 in which the drive between the clutch means and first feed means includes a series of meshed gears, a first one of which is fixed in location on the machine and meshes with a gear on the clutch means and the remaining gears are on an arm swingable on the axis of the first gear, and the swinging end of the arm carries the first feed means.

4. In a machine of the character disclosed, a rotatable drum, means for supporting copy sheets, means for successively feeding copy sheets from the supporting means to the drum, drive means connected between the drum and feed means, clutch means in said feed means and including a housing member constantly rotated by the drum, a center disc, an outer disc, rollers secured to the outer disc for wedging engagement between the housing member and center disc, means biasing the center disc and outer disc to relative positions for roller engagement as mentioned, a trip arm pivoted on the outer disc and having a pin engageable with the inner disc and when swung inwardly operative for disengaging the housing member and center disc, and cam means driven by the drum operative for swinging said trip lever inwardly in a predetermined position of rotation of the cam means and of the outer disc and operative for restraining rotation of the outer disc while the trip lever is in inward position.

5. The construction of claim 4 in which the cam means in engaging the trip lever tends to rotate the outer disc in direction opposite that of the housing member, and detent means is provided for restraining rotation of the outer disc in said opposite direction.

6. A machine comprising, driving means including a rotatable shaft, driven means including rotatable elements such as rolls, and drive transmitting means interconnecting the drive means and driven means including clutch means, said clutch means including a first member constantly driven in a first direction by the shaft, 3. pair of second members, means biased into wedging engagement between the first member and each second member, means carried by each second member and rotatable therewith for disengaging the second member from the first member, and

cam means driven by the shaft for each disengaging means for actuating the same and restraining the respective second member against rotation during a predetermined portion of a rotation of the shaft.

7. The construction of claim 6 in which the cam means are angularly relatively oifset whereby the drive transmitted through the drive means to the respective rolls is interrupted during different portions of the rotation of the shaft. T v

8. Clutch means comprising an outer housing having an exterior gear thereon, drive means constantly driving the housing through the gear, a center disc in said housing having notches in its periphery providing wedging surfaces cooperating with the inner surface of the housing, an outer disc having rollers mounted thereon disposed in said notches, means reacting between the center disc and outer disc biasing the rollers in direction for wedging engagement between the center disc and housing, a trip lever pivoted on the outer disc and having a pin extending into one of the notches and operative on inward swinging movement thereof for relatively moving the housing and center disc for disengaging the same, and cam means carried by the drive means having a portion for engaging the trip lever and moving it inwardly and having another portion enabling the lever to swing outwardly and the outer disc with the trip lever to rotate with the first member of the clutch.

9. Clutch means comprising an outer housing having an exterior gear thereon, drive means constantly driving the housing through the gear, a pair of center discs in the housing each having notches in its periphery providing wedging surfaces cooperating with the inner surface of the housing, a pair of outside discs having rollers mounted thereon disposed in said notches in respective center discs, means reacting between the center discs and the outside discs biasing the rollers in direction for wedging engagement between the center discs and housing, a trip lever pivoted on each outside disc and having a pin extending into one of the notches in the respective center disc and operative on inward swinging movement of the trip lever for relatively moving the housing and center discs for disengaging the same, and cam means carried by the drive means for engaging the trip lever on each outside disc for moving it inwardly and having a cutaway portion enabling the lever to swing outwardly and the outside discs with the trip levers to rotate with the first member of the clutch.

l0. Clutch means for use in transmitting drive from an operating member such as a shaft comprising a housing having an exterior gear thereon, means operated by the shaft for constantly rotating the housing, a center disc in the housing having notches forming wedging surfaces cooperating with the housing, an outside disc having rollers fixedly mounted thereon disposed in said notches, means biasing the rollers into wedging engagement with the housing and center disc, a trip lever pivoted on the outside disc and having a pin disposed in one of said notches and operative on inward swinging of its free end for relatively moving the center disc and housing of wedging engagement with the rollers, the free end of the trip lever being in trailing position relative to the direction of rotation of the clutch means, and cam means on said shaft rotatable in the same angular direction as the clutch means and the cam and clutch means having adjacent peripheral portions movable linearly in opposite directions, the cam having a circular portion engageable with the swinging end of the trip lever and operative for moving it inwardly and the swinging end when so engaged extending in trailing directionbeyond the line connecting the axes of the cam means and clutch means, and the cam means having a cutaway portion enabling the lever to swing outwardly and the outer disc 17 with the trip lever to rotate with the first member of the clutch.

11. A duplicating machine comprising means for supporting a stack of copy sheets, a rotatable drum, rolls for successively feeding sheets from a stack on said supporting means to the drum, drive means interconnected between the drum and the rolls all portions of which are movable solely in forward direction, rotary clutch means in said drive means, means biasing the clutch means to a normally connected position, a member rotatable in a predetermined orbit coaxial with the clutch means, and clutch control means driven by the drum and including a cam concentric with the drum and with an orbit overlapping the orbit of the rotatable member of the clutch, said cam being rotatable in a single direction and including a circular portion and a flat portion, said circular portion being engageable with said rotatable member and thereby operative for moving it to position disconnecting the clutch, and the flat portion enabling the rotatable member to move to a position connecting the clutch.

12. The invention set out in claim 11 wherein the clutch means includes a rotary driving element constantly driven by the drum, and a rotary driven element engageable by the driving element, each rotatable in a single direction.

13. The invention set out in claim 11 in which a plurality of feed means are provided operative in sequential 18 relation for feeding copy sheets from the stack to the drum, drive means is provided for each feed means, and one of each said clutch means and cams is provided in each drive means.

14. The invention set out in claim 13 in which each drive means includes an over-running clutch next adjacent the respective feed means for enabling overrunning of the feed means and drawing of the sheets therethrough in the direction of feed of the sheets.

References Cited in the file of this patent UNITED STATES PATENTS 503,311 Dahl Aug. 15, 1893 1,889,527 Barber Nov. 29, 1932 2,185,682 Pittman Jan. 2, 1940 2,192,414 Reed Mar. 5, 1940 2,238,359 Copeland Apr. 15, 1941 2,266,068 Peterson Dec. 16, 1941 2,268,045 Marchev Dec. 30, 1941 2,442,574 Storck June 1, 1948 2,573,810 Rundblad Nov. 6, 1951 2,594,179 Keil Apr. 22, 1952 2,613,597 Rutishauser Oct. 14, 1952 2,622,518 Peterson et a1. Dec. 23, a 2,674,183 Bergman Apr. 6, 1954 2,740,353 Levin Apr. 3, 1956 2,753,791 Thurmann July 10, 1956 2,785,893 Ford Mar. 19, 1957