US2151961A - Clutching and driving mechanism - Google Patents

Description

March 28, 1939. E. ERICKSSON I CLUTCHING AND DRIVING MECHANISM Original Filed Sept. 22, 1932 3 Sheets-Sheet l March 1939. E. ERICKSSON 2,151,961

CLUTCHING AND DRIVING MECHANISM Original Filed Sept. 22, 1932 3 Sheets-Sheet 2 gwuwwtom March 28, 1939. E. ERICKSSON CLUTCHING AND DRIVING MECHANISM Original Filed Sept. 22, 1932 3 Sheets-Sheet 3 Patented Mar. 28, 1939 UNITED STATES;

CLUTGHING AND DRIVING i Emil Ericksson, Chicago, 11]., assignor to Standard Process Corporation, Chicago, 111., a corporation of Delaware Original application September 22, 1932, Serial 634,406. Divided and this application September 5, 1936, Serial No. 99,670

ZiClaims. (Cl. 101-171) The present invention relates to novel clutch ing and driving mechanism and more specifically to such mechanism as employed in the starting and driving of printing presses.

While the clutching and driving mechanisms disclosed in the present application are of particular advantage when used with a printing press it is to be understood that they are capable of wider application as for treating strip or web 10 material as by coating and the like. For the purposes of illustration, the present invention will be described in connection with a multiple impression printing press of the type shown and described in my co-pending application Serial No'. 15 634,406, filed September 22 1932, which has since matured into United States'Patent No. 2,103,812 issued December 28, 1937, wherein the present invention is described, the instant application being a division of said co-pending application. 20 A primary object of the present invention resides in the provision of novel clutching and driving mechanisms designed to advance a web or strip of material around an idling cylinder and between a plurality of positively driven cylinders. 25 A further object of the present invention is to provide novel web or strip advancing means having a normally idling cylinder and at least one positively driven cylinder between which the web or strip is drawn with a variable speed friction 30 clutch arranged to initiate drive of the normally idling cylinder and bring it and the web or strip up to operating speed independently of the positively driven cylinder.

Another object of the present invention resides 35 in the provision of novel web or strip advancing means having a centrally disposed freely rotatable cylinder and a plurality of driven cylinders spaced about the central cylinder to advance a web or strip under proper tension with means for initially starting the advancing means without imposing injurious strains on the web or strip.

A further object of the present invention resides in providing a multi-color printing press 45 having a normally idling impression cylinder and a plurality of positively driven printing cylinders positioned thereabout with a main driving gear designed to rotate the impression cylinder under certain phases of operation and to mesh with sec- 50 ondary driving gears designed to drive the printing cylinders.

Another object of the present invention is to provide a novel printing press having a normally idling impression cylinder with a planetary gear 55 system designed to provide a variable speed drive connection for said impression cylinder to initially start the press.

A further object of my invention is to provide a novel driving mechanism for use on a printing press having an impression cylinder normally free to rotate, and a plurality of driven printing surfaces circular in cross section spaced about the impression cylinder to advance and print upon a Web maintained under proper tension.

A still further object of my invention is to provide a printing press having a freely rotatable impression cylinder and positively driven printing cylinders from which rotation is imparted to said impression cylinder to propel a web therebetween with means to initially start and accelerate said impression cylinder to prevent tearing or distortion of the web.

Other objects of the invention will appear from the following description taken in connection with the attached drawings wherein:

Figure 1 is a side elevation of a printing press embodying a preferred form of the novel driving mechanism of -the present invention.

Figure 2 is a fragmentary section in side elevation of the mechanism for initially starting the impression cylinder and accelerating it to the desired operating speeds.

Figure 3 is a fragmentary section of the main driving means.

Figure 4 is a fragmentary section showing the mechanism for driving and obtaining registry of the printing cylinders.

Figure 4a is a fragmentary view partly in section illustrating the mechanism for selectively driving one of the printing cylinders.

Figures 5 and 6 are top plan elevational views of the sliding key used in the mechanism of Figure 4.

Figures '7 and 8 are side and end elevational views of the helically slotted sleeve provided for 40 cooperation with the key of Figures 5 and 6.

With continued reference to the drawings wherein like reference numerals are used to designate the same parts throughout the several figures, a multiple impression printing press ll, including a pair of spaced supporting frames I2 and an outside auxiliary frame |3.positioned on a base or sole plate It, is provided with a-preferred embodiment of the novel clutching and driving mechanism of the present invention. Frames I 2 are preferably provided with four apertures l5 positioned so that when frames l2 are mounted on sole plate M, the apertures are opposite one another. The upper right quadrant of each frame l2 (referring to Figure l) is preferably formed separately from the remainder of the frame and pivoted at l6 to permit of raising of the frame section to secure access to the impression roller within.

A normally idling impression cylinder l1 having a suitable impression surface I8 is rotatably supported on supporting frames I2 in the following manner: Impression cylinder I1 is preferably secured to hub 2| (Figure 2) which rotates on shaft 22, by spokes 23, thus providing a light, but rigid and strong structure. Shaft 22 is provided with enlarged sections 24 over which hub 2| is forced into positionagainst a shoulder 25 formed on one of srctions 24. Shaft 22 is journalled in combined radial and thrust bearings 26 supported in frame members 2. Thrust bearings 26 may, if desired, be of the type comprising cup rings 21 and cones 28 although it is to be understood that any suitable form of anti-friction hearing may be employed.

Bearing housing 29 is retained between the left hand frame member l2 (Figure 2) and cap or cover member 3|, secured to frame member |2 by suitable connection means, for example, bolts 32 (Figure 1). Bearing 26 is held in proper relation to the end of shaft 22 by cap 33 secured to shaft 22 by bolts 34. A ring member 35 is spaced from cap 33 and secured by bolts 35 to bearing housing 28 to hold the bearing assembly together. This arrangement permits the withdrawal of shaft 22 by removing cap 33, there being no necessity for disturbing the bearing assembly.

Packing 36 is provided to prevent the escape or leakage of the lubricant supplied to bearing 26. A cover 31 retained in position by suitable means, as for example, bolts 38 engaging frame member l2 and cap 3| provides a lubricant chamber 39 and maintains the entire bearing assembly in position in the frame I 2.

Right hand frame member I2 is provided with a combined radial and thrust anti-friction hearing 40 to receive the opposite end of shaft 22.

Bearing 48 is mounted on frame member |2- under cover or cap member 4| which is secured to frame l2 by suitable means. A ring 42 secured to bearing housing 48 by suitable bolts 43, holds a packing 44 against shaft 22 to prevent leakage and escape of lubricant from bearing 40. A ring 45 surrounds bearing housing 48 and ring 42 and is secured to frame member 2 and cap member 4| by suitable bolts 46.

Caps 3| and 4| are secured to frames |2 at an angle, preferably 45, as seen in Figure 1, so that cylinder I! may be removed or reground through the opening provided by the hinged quadrants of frames l2.

Frames l3 supports the ends of stub-shafts 41 journalled in webs 48 of frames |-2 (Figures 1 and 4). Shafts 4| carry frames 49 and swinging brackets 58 which in turn support printing cylinders 5|, 52, 53 and 54 and their drive mechanisms spaced about the periphery of cylinder Stub-shafts 41 are journalled in webs or projections 55 of auxiliary frame I3, the projection 55 opposite printing cylinder 54 being preferably formed on a detachable portion of auxiliary frame I 3 in order that cylinder 5| and its associated mechanism may be swung bodily around hinge l6.

The press thus far briefly described is shown and described in copending application Serial No. 634,406. Since the general press construction does not form any part of the present invention, a more detailed description thereof will not be given in this application. A novel friction clutch of the present invention as applied to the press of Serial No. 634,406 briefly described above will now be described.

Printing or treating cylinders 5|, 52, 53 and 54 in combination with impression surface I8 ad- Vance the material, preferably in the form of a web, which is to receive an impression or impressions therefrom or to be otherwise treated, and are driven by novel means to be hereinafter described in detail. For the sake of simplicity, cylinders 5|, 52, 53 and 54 will be hereinafter called printing cylinders although it will be obvious from the foregoing that the invention embraces other treating operations than printing.

A gear 56 is keyed by suitable means, as key 51 or otherwise associated in driving relationship with a hollow shaft 58 (Figure 2) which is aligned with shaft '22 and supported at its end adjacent shaft 22 in a bearing 59 in main frame member I2, and at the other end by a supporting mechanism generally indicated at 6| including brake drum 62 for a purpose to be described.

Gear "is driven from a pinion 63 which is keyed or otherwise secured on a main drive shaft 64 which is in turn driven by a pulley wheel 65. A hand wheel 66 is keyed or otherwise secured to main drive shaft 64 so that the mechanism of press may be manually moved for the purpose of threading the material to be printed or to move the printing cylinders or material for any purpose for example when making any of the necessary adjustments, described in detail in copending application Serial No. 634,406.

Shaft 22 is driven in the following manner from gear 56. A constantly engaged dog clutch member or ring 61 is secured to the end of shaft 22, between the end of shaft 22 and bearing member 59 by suitable means 68. A cover member 69 secured to frame member l2 and cap 4| by suitable means II is provided for protecting bearing 58 and clutch 61. Cover member 68 contains suitable packing as at I2 to prevent the escape of lubricant.

Hollow shaft 58 at its end opposite bearing 59 is provided with a bearing ring member 13 secured for rotation with shaft 58 by a key 14. Hollow shaft 58 is rotatably supported through bearing ring 13 and an anti-friction bearing 15 carried by a member 16. Member 16 is rotatably supported by an anti-friction bearing 11 mounted in frame member 3 and held therein by a bearing cap 18 secured to frame member |3 by suitable means 19 (Figure 1). Impression cylinder drive shaft 8| is received within shaft 58 one end thereof extending within member 16. Suitable means, for example, keys 82, in keyways 83 of member I6 and shaft 8| connect shaft 8| to rotatable member I6.

Shaft 8| is provided at its ends with spines 84 in engagement with splines 85 in clutch ring 61 for the purpose of driving impression cylinder I! when desired through mechanism 6|. The connection afforded by splines 84 and 85 provides a flexible driving connection which permits cylinder shaft 22 to be free of distorting stresses which might otherwise occur when power is transmitted from main driving gear 56, and eliminates a possible source of inaccuracy in the location of impressions received from the printing cylinders. Shafts 22 and 8|, so connected, comprise a sectional shaft through which impression cylinder I! may be driven but which is a normally idling shaft.

Hub 86 of bevel gear 81 is secured to member 16 for rotation therewith by suitable means, for example set screw 88. A shoulder 89 on member 16 insures the proper positioning of gear 81 with respect to member 16. A second bevel gear BI is mounted to rotate. on shaft 58 and is secured to the hub of gear 56 for rotation therewith by means of set screw'92. Bevel pinion 53 is in mesh with bevel gears 81 and 91 and is mounted on bevel pinion shaft 96 carried in hub 95 and an aperture in rim 96 of brake drum'62. Pinion shaft 96 is retained in position by suitable means, for example, set screw 91. Brake drum 62 is rotatably journalled on hollow shaft 58 by means of bearing bushings 98. A suitable fitting 99 provides for a supply of lubricant to 7 bearing bushings 68.

When desired brake drum 62 is restrained from rotation by brake band IIlI. Brake band IIJI is adjusted by means of bolts I62 (Figure l) and nuts I63 cooperating with ears I06. The ends of brake band IBI are connected to pins I65 (Figure 1) in levers I56. Levers I66 are carried on frame member I3 by bolts IIlI. Arms I08 of levers I 06 are connected by toggle links I69 so that they may be spread apart to tighten brake band IIII on brake drum 62.

Arm II I of toggle lever I69 may be connected to any suitable operating device or may be provided with a handle for manual operation. I have disclosed by way of example a solenoid magnet II2, core I I3 of which is operatively connected by link IIQ to arm III. Pins IE in frame member I3 serve as stops for levers I66. Impression cylinder I1 may be caused to rotate by drawing plunger H3 of solenoid II2 upwardly. Toggle ears I89 spread levers I08 which contract brake band III! by movement of arms I06 toward each other.

Rotation of brake drum 62 is thus prevented and bevel pinion shaft 66 remains stationary. Rotation is then imparted to impression cylinder I1 from gear 56 through bevel gear 9!, bevel pinion 93, bevel gear 81 and shaft BI.

With brake drum 62 free to rotate, differences in rotational speed between gear 56 and impression cylinder I1 are permitted by rotation of ,brake drum 62 at some intermediate speed. If,

for example, impression cylinder I1 is stationary, brake drum 62 will rotate at about one-half the speed of main drive gear 56 due to planetary action of pinion 93. I

Main drive shaft 56 carrying pulley 65 and drive pinion 63 is journalled in frame members I2 and I5 on anti-friction bearings H6. Bearing I I6 in frame member I2 is supported in a cup H1 and sealed with a lubricant seal H8. A divided collar II9 which is secured together by suitable means I2I retains cup II1 in position in frame I2. A seal I22 is provided for divided collar I I6. Divided collar I I9 is retained in position on frame member I2 by suitable fastening means, for example, bolts I23. Bearing H6 in frame member I 3 is mounted in a cup I24. A cover plate I25 retains cup member I25 i'n position on frame member I3. Suitable means I26 connect cover plate I25 to frame member I3, lubricant seals I21 being provided as shown.

Gear 56 also meshes with gears I28 which are adapted to drive the printing cylinders 5I 52, 53 and 56. Since the printing cylinder driving mechanisms are identical, only one of the mechanisms will be described. In this connection, the drive for printing cylinder 56 has been chosen for illustration.

Gear I28 is keyed-or otherwise securedto sleeve I29 which rotates on bearing bushings or sleeves I30 on shafts 61 between frames 59 and swinging brackets 50. Suitable lubricant fittings I36 provide for a supply of lubricant to the bearing surfaces on shaft 61.

Printing cylinder 54 is mounted upon a shaft I3! which is supported in bearings I32 and I33 carried by swingable frames 69, which are pivotally mounted on webs 68 by means of stubshafts 61. Bearing carrying frame 49 on lefthand frame member I2 (Figure 4) is made up of two parts I35 and I36 placed back to back and held together by suitable fastening or clamping means. Frame 69 on right-hand frame member I2 is made up in a like manner of parts I31 and I38 held back to back by suitable clamping means.

Parts I35 and I36 and parts I31 and I38 of swingable frames 69 form bifurcated portions which fit over and contact with webs 68, which together with shafts 51 form a pivot joint permitting frames 59 to swing freely but without twisting or lateral movement thereof. I Inaccuracies in the register of printing cylinders M, 52, 53 and 56 are prevented due to the above described pivot point.

Left hand frame 39 is provided at its end opposite pivot points61 with projections I39 and I 66 provided with apertures I II for connection with means, described in co-pending application Serial No. 634,406, for moving printing cylinders 5!, 52, 53 and 56 selectively or collectively into and out of contact with impression surface I8 of impression cylinder I1. Right hand frame 69 is provided with projections I52 and I63, apertured at I66 for a like purpose. Since such means form no part of the present invention, a detailed description thereof in the present case is believed unnecessary.

A gear I65 is keyed by means of a key M6 or other suitable means to a sleeve I61 which is provided with an aperture I68 for driving engagement with a clutch pin I619. 'Pin I ia is seated in an aperture I5I in a hub member I52 of a hand wheel I53, which is secured to hub I52 by suitable means as for example bolts I56. Clutch pin I 59 extends further into a radial aperture I55 in a sleeve I56 which is connected for rotation with hub I52 by means of a suitable key (not shown) fitting in keyway I51 in sleeve I55 and a suitable keyway (not shown) provided in hub I52. Shaft I3I is prdilided with a recess I58 and a slot I59. An elongated centrally located bore I60 is also provided in shaft I5I.

A key I6I (Figures 5 and 6) is seated within recess I58 of shaft I3I forv longitudinal reciprocation therein. A projection I 62 of key I6I projects through slot or aperture I55, and is received within a transverse notch or aperture I63 formed in end I66 of a reciprocable rod or shaft I65. Key I6I is provided with a spline I66 of relatively long pitch received in a helical slot I61 (Figures 7 and 8) of like pitch in the circumthe graduation corresponding to definite distances measured axially of impression surface I8 and hence transversely of the web of material. The graduations may, if desired, correspond to thousandths of an inch as measured on the web.

Shaft I3I is associated with printing cylinder 54 and is caused to move axially with threaded barrel I14 by anti-friction bearing ring I11 held against axial movement on reduced portion I18 of shaft I3I between collars I19 and IN, mounted on reduced portions I82 and I18 respectively of shaft I3I. Collar I19 is in abutting engagement with the edge of hand wheel hub body I12 and clutch sleeve I56. Collar I 8| engages sleeve I84 which is secured to the end of the shaft I3I by suitable means, for example, set screws I85 which permit collar I84 to be axially adjusted prior to the insertion of set screws I85. Stationary thrust bearing ring I86 engages an annular projection I81 of threaded barrel I14. Corresponding stationary thrust bearing ring I88 engages a threaded cover or cap I89 the threads of which are in engagement with threads on the interior of barrel I14.

Suitable anti-friction bearings, for example, balls I9I transmit end thrust of thrust bearing ring I11 to stationary thrust bearing rings I88 and I 88. Undesired end play of thrust bearing rings I11, I86 and I88 may be prevented by adjustment of threaded cover I89 which may besecured after adjustment by set screws I92.

From the mechanism thus far described it will be seen that as hand wheel I15 is manipulated to move threaded barrel I14 in the desired direction, shaft I3I will be moved axially by means of thrust bearing ring I11 and stationary thrust bearing ring I88 or I88 depending upon the direction of movement for the adjustment desired. Any observed transverse variations of the printed impressions on the web may be corrected by manipulation of hand wheel I15 associated with the printing cylinder to be adjusted. This may be done at any operating speed or before initial starting of the press. The graduations on hand wheel I15 facilitate the setting of the printing cylinder to the desired point when out of register. The printed web is measured to determine how much each cylinder is out of register and the hand wheel for that printing cylinder is turned through the number of graduations corresponding to the distance measured on the web.

Key I6I may be adjusted longitudinally in recess I58 on shaft I3I for the purpose of changing the angular position of gear I45 with respect to shaft I3I so that inaccuracies in the longitudinal location of the printed impression from the printing cylinder may be corrected and perfect register restored at any speed of the press or with the press at rest. To this end a hand wheel I93 having a barrel I94 formed thereon is secured in barrel I14.

Periphery I95 of hand wheel I93 is also provided with graduations, the interval between the graduations corresponding to definite distances measured longitudinally of the web. The graduations may, if desired, correspond to thousandths of an inch as measured on the web. Barrel I14, in order to receive barrel I 94, is provided with an interiorly threaded portion I96 which receives threads I96 provided on barrel I94. Barrel I94 is rotated by hand wheel I93 to effect longitudinal movement thereof with respect to barrel I14. Key I6I and shaft I65 are moved longitudinally in bore I60 by means of thrust bearing assembly I91 (similar in construction to the bearing assembly described in connection with hand wheel I15) positioned in barrel I94.

As hand wheel I93 is rotated in either direction barrel I94' will be moved longitudinally with respect to the barrel I14 on threaded connection I96. Thrust bearing assembly I91 will impart the longitudinal movements of barrel I94 to shaft I65 in a manner that will be readily apparent from the drawings.

Thrust bearing assembly I91 includes bearing ring I98 and bearing members I99 and MI be tween which are interposed suitable anti-friction bearings, for example, balls 203. Bearing members I99 and MI are retained on rod I65 by suitable means, for example, cap screws 204 and arrnular member 205.

Thrust bearing assembly I91 is positioned between shoulder 206 and cover plate 201. Cover plate 201 is retained in position by suitable fastening means, for example, cap screws 208. To prevent undesired twisting or rotation of shaft I65, key 209 may be employed to connect the end of shaft I3I to shaft I65.

Suitable means 2I I provides for a supply of lubricant to the parts. Lever 2I2 and clamping bolt 2I3 are employed to clamp barrels I14 and I 94 in fixed relationship. Links 2 I4 and 2| 5 provide for differences in position of handwheel I93 and barrel I14.

, From the description just given, it will be seen that key I6I is reciprocated in recess I58 by hand wheel I93 and shaft I65. Reciprocation of these members varies the angular relationship of gear I45 and shaft I3I thereby afiecting the longitudinal registering of the impressions on the web of material. Undesired movements of sleeve I56 on shaft I3I are prevented by a collar 2I1 secured to shaft I3I by suitable means, for example, key 2 I8, beyond the point 2I9 of slight reduction in the diameter of shaft I3I. Collar 2| 1 may, if desired, abut inner bearing sleeve 22I which in turn abuts shoulder 222 at the point of reduction in diameter of the shaft I3I thus aiding in preventing longitudinal movement of sleeves I41 and I56 on shaft I3I.

Inner bearing sleeve 22 I located on the portions of the shaft I3I within frame members 49 is of a length greater than that of bearings I32 and I33 and thus permits longitudinal movement of shaft I 3I for the purpose of obtaining accurate positioning of impressions from printing cylinders 5I, 52, 53 and 54 laterally of the web of material under control of the adjusting means previously described. Bearing I33 and outer bearing sleeve 224 are retained by cover members 225 secured to frame members I31 and I38 by suitable fastening means as for example screws 226. Hand wheel hub body I52, connected for rotation with sleeve I56 by means of pins 221 fitting within apertures 228 in sleeve I56, prevents axial movements of hand wheel hub I52 along shaft I3I.

A set screw 229 in hand wheel hub I52 frictionally engages groove'23l of clutch pin I49 to hold clutch pin I49 in position with its shank engaged in arcuate notch I48 of sleeve I56 whereby gear I45 may drive shaft I3I, or with notch 232 positioned to the left whereby sleeve I 41 is free to rotate without imparting rotational movement to sleeve I56.

Operation Power is applied to main drive shaft 64 (Figure 3) and is transmitted by means of pinion 63 and gear 56 to the several intermediate printing cylinder drive gears I28. It will be seen that as gears I28 and bearing frames 9 and brackets 50 have a common center, driving force will be applied from intermediate printing cylinder drive gears I28 to printing cylinder drive gears M regardless of the angular position of swinging frames 49 and brackets 50 within the limits of their movement. printin cylinder shafts i3l with printing cylinders 5!, 52, 53 and 55 either in or out of printing contact with the web material.

If it is desired at any time to stop rotation of any one of printing cylinders Si, 62, 53 and 5:! this may be done by loosening set screw 229 and rotating clutch pin M9 until notch 232 permits free movement of sleeve :41. Sleeve It! will then rotate idly on sleeve 156 without imparting movement to its corresponding printing cylinder shaft. It is thus possible to print at will from any one of the several printing cylinders or any group thereof. The printing cylinders not in use may remain idle.

As hereinbefore described, impression cylinder I! rotates freely during normal printing operation, being driven by the web material which in turn is advanced by the positively driven printing cylinders Si, 52, 53 and 54. It is, however, desirable that impression cylinder il be initially started and accelerated to normal operating speed by the power driven means and friction clutch previously described in order to avoid distortion or possible rupture or breakage of the Web material and possible injuries to the etched surface of the printing shells which may result from frictional contact during acceleration of printing cylinder l'l. In order to effect the positive acceleration of cylinder I! the press it, with printing cylinders 51, 52, 53 and 5 3 out of contact with impression cylinder IT, has the web of material threaded therethrough after insertion of the web between the guide rolls and tensioning means de scribed in co-pending application Serial No. 634,406. The web material is then passed between each of the printing cylinders and impression surface 18, by rotating the press slowly either by the main power drive or hand wheel 66.

Brake band liil during this time is preferably engaged so that the web is drawn around cylindcr ll, due to the positive drive imparted there to. After the material has been passed between the several printing cylinders and cylinder I1, it is taken over guide rolls and passed under a drier or led directly to a reeling stand or disposed of in the desired manner. With the press in this condition, it is ready for printing.

To initiate printing on the web material, impression cylinder 1'! is started and accelerated to normal running speed by tightening band I6! of starting mechanism 6! which will smoothly and rapidly accelerate the impression cylinder to normal operating speeds, at which speed the printing cylinders may be collectively placed in operative contact with the paper by operation of the mechanism described in co-pending application Serial No. 534,406. The brake band of starting mechanism 6| after the operating speed is reached may be released as impression drum I1 is now being driven by the several printing cylinders 5|, 52, 53 and 54 overlying the impression surface. l8. The press, due to the use of the variable friction clutch 6|, is accordingly brought up to operating speed withoutany strain on the web of material.

The invention may be embodied in other specific forms without departing from the spirit or Rotation is thus imparted to essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

What is claimed and desired to be secured by United States Letters Patent is:

1. A printing press comprising an impression cylinder, a printing cylinder, means to drive said printing cylinder, said driven printing cylinder normally driving said impression cylinder; and means to accelerate and initially drive said impression cylinder from said printing cylinder drive means.

2. A printing press comprising an impression cylinder; a printing cylinder, said impression cylinder and said printing cylinder being adapted to receive and propel a strip therebetween, means to drive said printing cylinder positively, said impression cylinder normally rotating idly in contact with the strip between said cylinders; and means to drive said impression cylinder positively, said last mentioned means comprising a variable speed clutch means.

3.A printing press comprising a normally idle impression cylinder; a plurality of positively driven printing cylinders, said impression cylinder and said printing cylinders being adapted to receive and propel a strip therebetween; and means to drive said impression cylinder positively,, said last mentioned means comprising variable speed clutch means.

4. In a printing press comprising in combination an idle impression cylinder and a plurality of driven printing cylinders, the contact or pressure between the impression cylinder and the printing cylinders propelling a webto be printed between them; means to initially start and accelerate said impression cylinder so that the impression can be thrown in while the printing cylinders are running without danger of tearing or distortion of the web, said means comprising a friction clutch and a solenoid.

5. In a printing press having an impression cylinder and a plurality of. printing cylinders adapted to engage and propel a strip of material to be printed, the combination of a main drive shaft, a driving pinion secured to said shaft, a hollow driven shaft,'a driven gear secured to said hollow shaft adapted to mesh with said driving pinion, a shaft adapted to support and drive said impression cylinder, an extension on said impression cylinder supporting shaft, said extension extending through said hollow shaft and connected in driving relation thereto by meansof a variable speed clutch, a driven shaft for each of said printing cylinders, a gear on each of said driven shafts meshing with said hollow shaft driven gear, and means to disengage said variable speed clutch and permit said impression cylinder to idle during normal operation of said press.

6. In a printing press having a normally idling impression cylinder, means for initiating operation of said cylinder comprising a driven shaft, a bevel gear secured to said driven shaft, a shaft supporting said impression cylinder, a second bevel gear secured to said supporting shaft, a housing surrounding said bevel gears, a bevel pinion mounted in said housing and designed for constant engagement with said bevel gears, and a friction band encircling said housing adapted to lock said housing against rotation and to transmit torque through said second bevel gear tosaid supporting shaft."

7. A clutch for use in initiating operation of a printing press having a normally idling impression cylinder comprising driving and driven shafts, a gear secured to said driving shaft, 9. second gear secured to said driven shaft, 9. housing surrounding said gears and rotatably supported by one of said shafts, a planetary pinion rotatably supported by said housing and in constant engagement with said gears, and means for locking said housing against rotation to establish a driving connection between said gears and their associated shafts.

, 8. The combination defined in claim 7 wherein said last-mentioned means comprises a friction band encircling said housing, a pair of crank arms, the adjacent ends of which are connected to the ends of said friction band, a toggle connection connecting the opposite adjacent ends of said crank arms and means for operating said toggle connection to engage said friction band and said housing.

9. A driving mechanism for advancing a strip or web of material through. a treating machine comprising a normally idling cylinder for supporting said web, a plurality of positively driven treating cylinders operable to grip said web between them and said first mentioned cylinder and advance said web through said machine, means for driving said plurality of cylinders and manually operable clutching elements for selectively connecting one or more of said plurality of cylinders to said driving means.

10. The combination defined in claim 9 wherein driving means is provided for said normally idling cylinder, said means including a variable speed clutch for positively driving said normally idling cylinder to initially accelerate said web to operating speed whereby injury of said web and said treating cylinders is obviated.

11. A driving mechanism for a web treating machine having a normally idling web supporting cylinder and a plurality of positively driven treating cylinders carried in pivoted swingable frames and operable to advance said web over said idling cylinder comprising a main drive shaft, a driving pinion on said drive shaft, an intermediate drive shaft, a driven gear mounted on said intermediate drive shaft for engagement with said pinion, a drive gear for each of said driven treating cylinders rotatably mounted on the pivot of each of said swingable frames and operatively engaging said driven gear, and a driven gear mounted in each of said swingable frames operable to engage said treating cylinder drive gear and transmit the driving force to said driven treating cylinders.

12. In a web printing press having a normally idling impression cylinder and a plurality of positively driven printing cylinders for normally driving said web, the combination of a main drive shaft, an intermediate drive shaft, a normally idling shaft carrying said impression cylinder, a driven shaft for each of said printing cylinders operable to drive said cylinders, means interconnecting said main drive shaft and said intermediate drive shaft and operable to establish a driving connection therebetween, means interconnecting said intermediate drive shaft and each of said driven shafts, said last mentioned means including a part of said first mentioned means, a variable speed clutch interconnecting said normally idling shaft and said intermediate drive shaft, and means for operating said clutch for positively driving said normally idling shaft to accelerate said web to normal operating speed.

13. A variable speed clutch for use in a multiple impression printing press comprising a normally idling shaft, a driven shaft, a gear secured to said normally idling shaft, a gear secured to said driven shaft, a drum surrounding said gears and rotatably supported on said driven shaft, a pinion carried by said drum and engaging said gears, and means for frictionally engaging said drum to vary its resistance to rotation whereby said normally idling shaft may be selectively driven at variable speeds rom said driven shaft.

14. The combination defined in claim 13 wherein said driven shaft is hollow and said idling shaft extends through and beyond said driven shaft and wherein said first-mentioned gear is secured to the protruding portion of said idling shaft.

15. The combination defined in claim 13 wherein one end of said driven shaft is supported by an anti-friction bearing carried in the hub of said first-mentioned gear.

16. The combination defined in claim 13 wherein said last-mentioned means includes a frictional band surrounding and engaging said drum.

17. Means for operating a variable speed clutch used to initiate operation of the normally idling impression cylinder of a multiple impression web printing press having positively driven printing cylinders for driving the web and impression cylinder comprising a brake band, crank arms connected to the ends of said brake band and pivotally supported on a stationary portion of said press, a toggl linkage interconnecting the opposite ends of said crank arms and means for operating said toggle linkage.

18. The combination defined in claim 17 wherein said means comprises a solenoid magnet secured to said stationary portion of said press, a core operatively associated with said magnet and a link connecting said core to one link of the toggle linkage.

19. A drive mechanism for a multiple impression printing press having a normally idling impression cylinder and positively driven printing cylinders comprising a main drive shaft, a drive pinion on said main drive shaft, 2. master drive gear engaging said drive pinion, a plurality of driving gears angularly spaced around said master gear and meshing therewith, means for driving said printing cylinders from said lastmentioned driving gears, a normally idling shaft carrying said impression cylinder and rotatably supporting said master gear and variable speed clutching means interconnecting said. master gear and said normally idling shaft whereby said idling shaft may be accelerated to operating speed independently of said driven printing cylinders.

20. In a printing press, a rotatable shaft, a printing cylinder mounted on said shaft, clutch means arranged upon said shaft, a second clutch means adapted to be rotated with respect to said first clutch means, means for driving said second clutch means, means preventing relative move ment of said clutch means axially of said shaft and selective means for operatively interconnecting said clutch means whereby said printing cylinder may be driven or may remain idle at will.

21. In a printing press, a rotatable shaft, a

printing cylinder mounted upon said shaft, a sleeve arranged torotate with said shaft, a second sleeve arranged to freely rotate upon said first sleeve, means for continuously driving said second sleeve, and selective means for operatively interconnecting said sleeves whereby said printing cylinder may be driven or may remain idleat will.

22.'In a printing press, a printing cylinder shaft, drive means for said shaft, clutch means carried by said shaft and manually operable to clutch said shaft to said drive means, said clutch means comprising a pair of separate concentric sleeves and a selectively adjustable pin engaging in openings in said separate sleeves, one of said sleeves being connected to the drive means and the other to the shaft.

23. In the combination above defined in claim clutch members associated with the drive to 10 each printing cylinder.

' EMIL ERICKSSON.

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