US3767098A - Printing apparatus - Google Patents

Abstract

There is disclosed a printing, feeding and severing method and apparatus for carrying out the method. The apparatus includes a print head assembly and a platen assembly movable relatively toward and away from each other into and out of printing cooperation, mechanism for inking the print head assembly, mechanism for feeding a web of record members to between the print head assembly and the platen assembly, the web being in roll form and there being means to assist the gradual unwinding of the roll with gradual paying out of web material from the roll to the feeding mechanism, an idler contacting the web and disposed at a slight angle to the direction of feed of the web to cause the web to follow a feed edge, record severing means disposed downstream of the print head assembly and the platen assembly, and a modular support assembly of a print head of the print head assembly.

Description

United States Patent M w Wm Pabodie Oct. 23, 1973 [54] PRINTING APPARATUS Inventor: Robert M. Pabodie, Dayton, Ohio Pr'mary Exammer-Anen Knowles Att0rneyJoseph J. Grass [73] Assignee: Monarch Marking Systems, Inc.,

Dayton Ohm 57 ABSTRACT Filedi J 1972 There is disclosed a printing, feeding and severing [21] AppL No: 215,820 method and apparatus for carrying out the method. The apparatus mcludes a print head assembly and a platen assembly movable relatively toward and away UnSl 6 from each other into and out of printing cooperation [5 Int. 6 t mechanism for the print head assembly mechaof Search l 17, nism for feeding a web of record members to between 183, 25, 44, 186, 189, 118, the print head assembly and the platen assembly, the 1 271/52 web being in roll form and there being means to assist I the gradual unwinding of the roll with gradual paying References Cited out of web material from the roll to the feeding mech- UNITED STATES PATENTS anism, an idler contacting the web and disposed at a 3,561,655 2 1971 Yasukawa 226/113 Slight angle to the direction of fwd of the Web to 2,628,834 2 1953 Craib 226/191 ux cause the Web to follow a feed edge, record Severihg 2,674,456 4/1954 Gibson, Jr 271/52 means disposed downstream of the print head assem- 2,729,581 1/1956 Pascoe et al 271/52 X bly and the platen assembly, and a modular support 3,677,455 7/1972 Johnson ..L 226/117 assembly of a print head of the print head assembly 2,287,768 6/1942 Eckstein 226/191 X 3,285,484 ll/l966 Johnson 226/195 X 4 Claims, 35 D awing Figures PATENIEflucrza mm 3.767; 098 sum mar 13 PAIENTEUUCI 23 I973 SHEET UQUF 13 I: I: I

PAIENTEB 8U 23 I973 SEE] 12 0F 13 aw wav mcmmamam 3.767.098

SMEI 13M 13 PRINTING APPARATUS SUMMARY OF THE INVENTION The invention comprises improved printing apparatus in which a print head and a platen are mounted for relative movement toward and away from each other and a stop arrangement is used to limit the amount of travel of the print head and the platen toward each other. Apreferred arrangement is to provide a resilient drive connection which yields when a stop is abutted. Specifically, either the print head or the platen assembly is movably mounted and the movable one is connected to an eccentric by a connecting rod having a pair of relatively movable sections and a spring yieldably urging the sections apart. Impression control is thus effected.

The invention also comprises structure providing a fixedly mounted print head, a movable platen assembly with a platen cooperable with the print head, feeding and severing means mounted by the movable platen assembly, and means for driving the platen assembly, the feeding means and the severing means.

The invention also comprises printing means for printing on a web with improved means downstream of the printing means for selectively automatically or manually severing printed records from the web.

The invention also comprises an improved mechanism for unwinding a roll by gradually paying out web material from the roll by using an improved rotary feeding means which comprises a plurality of flexible members in driving engagement with the web material; the flexible members are preferably resilient and have a relatively high coefficient of friction.

The invention also comprises an idler roll in pressure contact with a web and disposed at a slight angle with respect to the direction of web movement to cause the web to follow a guide edge.

PRIOR ART The following U.S. Pats. are made of record: Nos. 458,945; 2,888,261; 3,180,254; 3,228,601; 3,350,091; 3,494,525; and 3,662,681.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a side elevational view showing one side of printing apparatus in accordance with the invention;

FIG. 2 is a top plan view generally along lines 2-2 of FIG. 1;

FIG. 3 is a partial front elevational view generally along line 3-3 of FIG. 2;

FIG. 4 is a sectional view taken along line 4-4 of FIG. 2;

FIG. 5 is a rear elevational view taken along line 5-5 of FIG. 1;

FIG. 6 is a sectional view taken along line 6-6 of FIG. 5;

FIG. 7 is a sectional view taken along line 7-7 of FIG. 2;

FIG. 8 is a partly diagrammatic side elevational view showing the platen assembly in printing cooperation with the print head assembly, showing the inking mechanism in a position in which the ink roll is in engagement with the ink transfer roll, and showing the severing mechanism as having severed a record member from the web;

FIG. 9 is a fragmentary side elevational view similar to FIG. 8, but showing the ink roller as having inked the printing members during its forward stroke and showing exaggerated-16 the platen in its downward position;

FIG. 10 is a fragmentary view showing part of the linkage of the inking mechanism in both solid and phantom line positions;

FIG. 11 is a sectional elevational view showing the manner in which the ink roll is mounted for travel relative to the print head assembly;

FIG. 12 is an enlarged fragmentary elevational view illustrating the severing mechanism in both solid and full line positions;

FIG. 13 is a fragmentary elevational view showing the inking mechanism in section;

FIG. 14 is a sectional view taken generally along line 14-14 of FIG. 13;

FIG. 15 is a sectional view taken generally along line 15-15 of FIG. 14;

FIG. 16 is a sectional elevational view of apparatus by which ink is delivered to the fountain from the sump and excess ink is returned to the sump;

FIG. 17 is a fragmentary sectional view on an enlarged scale showing a wiper blade andink return ducts 1 and a header;

FIG. 18 is an elevational view showing the feeding mechanism by which the record members are fed;

FIG. 19 is a sectional view taken along line 19-19 of FIG. 18;

FIG. 20 is an elevational view through the print head assembly showing the manner in which the printing bands are mounted;

FIG. 21 is an elevational view taken generally along line 21-21 of FIG. 20, but omitting the printing bands;

FIG. 22 is an exploded perspective view of the modular printing band support assembly shown in FIG. 21;

FIG. 23 is a sectional view taken along line 23-23 of FIG. 21;

FIG. 24 is a sectional view taken along line 24-24 of FIG. 21;

FIG. 25 is an elevational sectional view taken along line 25-25 of FIG. 21;

FIG. 26 is a view taken generally along the line 26-26 of FIG. 25;

FIG. 27 is a diagrammatic view showing the manner in which the functions of the printing apparatus are timed;

FIG. 23 is a sectional view taken generally along line 28-28 of FIG. 27;

FIG. 29 is a schematic circuit diagram showing a manner in which the record severing function can be accomplished;

FIG. 301s a schematic circuit diagram for the record feed mechanism;

FIG. 31 is a perspectiveview of an alternate form of drive and mounting mechanism for the ink roll;

FIG. 32 is a side elevational view of the mechanism shown in FIG. 31;

FIG. 33 is a sectional view taken along line 33-33 of FIG. 32;

FIG. 34 is a sectional view taken along line 34-33 of FIG. 33; and

FIG. 35 is a sectional view taken along line 35-35 of FIG. 33.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to FIG. 1, there is shown a printing apparatus generally indicated at 30 including a frame generally indicated at 31. Aprint head assembly 32 is fixedly mounted to theframe 31 and a platen assembly generally indicated at 33 is pivotally mounted to theframe 31 by apivot pin 34. An inking mechanism or inker generally indicated at 35 is provided for inking theprint head assembly 32. Aroll 36 ofrecord members 37 arranged in web form is mounted by arotatable reel 38 mounted by theframe 31. The web ofrecord members 37 passes under and partly around arotary feed member 98, from there it passes into contact with, over and partly around theroll 36 ofrecord members 37 and from there onto theupper surface 39 of theplaten assembly 33 beneath a hold-down plate 40 and analigning roll 41. From there the web ofrecord members 37 passes between afeed wheel 42 and aroll 43. From there the web ofrecord members 37 is advanced to arigid platen 44 of theplaten assembly 33. Thefeed wheel 42 operates near the end of each machine cycle to advance the printing record member ormembers 37 to a position in which the trailing edge of the advanced record member ormembers 37 are at a fixedknife 45 ofa severing mechanism generally indicated at 46. Thesevering mechanism 46 which is downstream of thefeed wheel 42 also includes amovable knife 47. The

movable knife 47 is pivotally mounted about apivot 48 and is cooperable with the fixedknife 45 to sever the previously printed record member ormembers 37 from the remainder of the web.

Anelectric motor 49 is mounted to theframe 31. Theelectric motor 49 drives aspeed reducer 50 which in turn is connected to the input of a clutch indicated diagrammatically at 51. Theclutch 51 is shown in greater detail at 153 in U.S. Pat. No. 3,180,254. The output of the clutch 51 is connected to adrive shaft 52 journaled in abearing 53. An eccentric generally indicated at 54 in the form of acrank 55 has an eccentrically mounted crankpin 56. Thepin 56 is received by aball 57 received in a socket 57'. The socket 57' forms part of a connecting rod generally indicated at 58.

With reference to FIG. 3, the connectingrod socket 57 is shown to threadably receive arod 59. Alock nut 60 threadably received by the rod orrod section 59 maintains the adjusted position of therod 59 relative to the socket 57'. Therod 50 also threadably receives a pair of nuts 61. Acompression spring 62 is received about therod 59 between the nuts 61 and a socket orsocket section 63. The nuts 61 are adjusted so that thespring 62 is always under some compression irrespective of the position of thecrank pin 56. Therod 59 has anenlarged section 64 received in an elongated recess 65 in thesocket 63, thereby permitting relative movement between therod 59 and thesocket 63. Thesocket 63 movably mounts aball 66 in asocket hole 67. Theball 66 has ahole 68 in which ashaft 69 is received. Theshaft 69 is rigidly connected to theplaten assembly 33. Before the clutch 51 is engaged,shaft 56 is in the phantom line position indicated at 56 in FIG. 3. In this position, theplaten 44 of theplaten assembly 33. is spaced from printingmembers 70 of theprint head assembly 32. As theshaft 52 rotates clockwise (FIG. 3), theplaten assembly 33 continues to move away from theprint head assembly 32 until thecrank pin 56 rotates clockwise to its lowerest position (FIG. 3). As theshaft 52 continues to rotate clockwise, theplaten assembly 33 starts moving toward theprint head assembly 32. Before thecrank 56 reaches the highest position shown by solid lines in FIG. 3, stop screws 71 engage a stop provided by astop plate 72 rigidly mounted to theframe 31 by abracket 73. Thebracket 73 is considered to be part of theframe 31. While the stop screws 71 are in contact with thestop plate 72 the record member is in contact with theprinting members 70. The stop screws 71 are adjustable to effect adjustment of impression control.

With reference to FIGS. 1 and 5, theelectric motor 49 has agear 74 secured to itsoutput shaft 75. Thegear 74 drives agear 76 secured to apully 78. Thegear 76 and thepulley 78 are rotatably mounted on ashaft 77. Thepulley 78 drives apulley 79 viabelt 80. Thepulley 79 is secured to ashaft 81. Abracket 82 secured to theframe 31 mounts theshaft 77 and astationary bearing 83. Thegear 76 and thepulley 78 are secured to ahub member 77. Theshaft 81 is rotatably mounted by thebearing 83 and drivespulleys 84 and 85 and 99. Thepulley 84 drives apulley 86 viabelt 87. Thepulley 86 and apulley 88 are keyed together so that they rotate as a unit aboutstationary shaft 89. Theshaft 89 is secured to theframe 31 by abracket 90. Thepulley 88 drives a pulley 91 (FIG. 15) viabelt 92. Thepulley 91 drives themechanism 35.

The pulley 85 (FIG. 5) drives apulley 94 viabelt 95. Thepulley 94 is secured to ashaft 96 rotatably mounted by abearing 97. A rotaryfrictional feed member 98 is secured to theshaft 96.

Apulley 99 secured to theshaft 81 drives apulley 100 viabelt 101. Thepulley 100 and anotherpulley 102 are keyed together so that they rotate as a unit about astationary shaft 103. Thepulley 102 drives a pulley 104 (FIGS. 18 and 19) viabelt 105. As best shown in FIGS. 18 and 19, thepulley 104 drives the record feeding mechanism generally indicated at 107.

With reference to FIG. 18, theplaten assembly 33 is shown to be comprised of aplaten frame 108 in which theshaft 103 is adjustably mounted to tension thebelt 105. The tension on thebelt 101 is maintained by a pair of springs 109 (FIGS. 2 and 18). A pair ofplates 110 and 111 are shown to be mounted in spaced parallel fixed relationship with respect to each other byspacer rods 112, 113 and 114. The ends of therods 112, 113, and 114 are suitably secured to theplates 110 and 111 to provide a unitaryfeed assembly frame 115. Theplates 110 and 111 of thefeed assembly frame 115 are pivotally mounted bystuds 116 and 117 carried by a bracket 33' secured to theplaten frame 108. Thestuds 1 l6 and 117 pivotally mount thesolenoid housing 157. The entirefeed assembly frame 115 is accordingly piv oted by thestuds 116 and 117 with respect to theplaten frame 108. Theplate 1 10 is shown to be in abutment with astop screw 1 18 threadably mounted by theplaten frame 108. Thestopscrew 118 adjustably limits the position to which thefeed assembly frame 115 can be pivoted by atension spring 119, thereby adjusting the amount of pressure which thefeed wheel 42 exerts on the underside of the record web. Thetension spring 119 is connected at one end to therod 114 and at its other end to theplaten frame 108.

With reference to FIG. 19, there is shown a wrappedspring clutch generally indicated at 120. The clutch 120 includes atubular sleeve 121 having a flat 122. Thepulley 104 matingly receives thesleeve 121 at the flat 122 so that thepulley 104 and thesleeve 121 rotate as a unit. An annular tubular drive member 123 is pressfitted onto thesleeve 121 so that thesleeve 121 and the drive member 123 rotate as a unit. Acontrol sleeve 124 is received about the drive member 123. Thesleeve 124 can be constructed of suitable plastic material. Thesleeve 124 has an annularexternal groove 125 which receives a resilient O-ring 126, composed of a material having a relatively high co-efficient of friction such as rubber. As the O-ring 126 is snugly received in thegroove 125 in a slightly stretched condition, the O-ring 126 does not rotate relative to thesleeve 124. An output driven member generally indicated at 127 has an enlargedannular section 128, the diameter of which is illustrated as being equal to the diameter of the drive member 123. Thefeed wheel 42 is shown to be formed integrally with the enlargedannular section 128. Aspring 130 is shown to be received about a portion of the outer surface of the drive member 123 and about the outer surface of theannular section 128. One end of thespring 130 is turned out to provide atang 131 received in an open-ended slot 132 in thesleeve 124. Thesleeve 124 is shown to have an enlarged internal diameter as indicated at 133 to provide clearance between thespring 130 and thesleeve 124. The output drivenmember 127 has a reduceddiameter section 134 which extends through thesleeve 121, a spacing and retainingsleeve 135, abushing 136,washers 137 and 138, an O-ring 139, and into theknob 140. The output drivenmember 127 also has astub end 141 received by abushing 142. Thebushing 142 is non-rotatably mounted by the plate 111. Aset screw 143 threadably mounted by thesleeve 135 and received in a groove 144 of thesection 134 prevents the drivenmember 127 from shifting in a direction perpendicular to theplates 1 and 1 11, but allows themember 127 to be rotated. Thebushing 136 is non-rotatably mounted by theplate 110. In the solid line position shown in FIGS. 18 and 19, acontrol member 145 is shown to have a pair of blunt, spaced-apart teeth146; thecontrol member 145 is shown in contact with the O-ring 126, thereby holding thesleeve 124 and thespring 130 uncoiled or expanded so that it has a larger internal diameter than when the clutch 120 is engaged. As thepulley 91 rotates continuously, thesleeve 121 and the drive member 123'rotate continuously'relative to thesleeve 124 and thespring 130. While thecontrol member 145 is in contact with the O-ring 126, thespring 130 is expanded thereby preventing the drive member 123 from driving theannular section 128 of. theoutput member 127. When thecontrolmember 145 is moved to the phantom-line position (FIG. 18) out of contact with the O-ring 126, thespring 130 coilsup, that is, its internal diameter is reduced, thereby gripping the drive member 123. The clutch 120 is now engaged as thespring 130 drivingly connects the input member 123 and theoutput member 127. When the clutch 120 is engaged, thefeed wheel 42 rotates. The web ofrecord members 37 is fed between thefeed wheel 42 and aroll 43 which is rotatably mounted in ablock 148 by abearing 150. Theblock 148 is suitably mounted to theplaten frame 108. The outer surface of thefeed wheel 42 is provided with straight knurls 42' which engage the underside of the web ofrecord members 37. Thefeed wheel 42 is considerably narrower than the width of the web being fed. However, theroll 43 is long enough to engage the upper surface of the web across a considerable portion of its width. Thus, theroll 43 serves to hold the web down against the upper surface of theplaten frame 108 immediately upstream of theplaten 44. When thecontrol member 145 is moved to the phantom line position coil or expand. Uncoiling of thespring 130 effects disengagement of the clutch by causing the spring to move outwardly away from the outer surface of the drive member 123. Accordingly, thefeed wheel 42 is no longer driven and the movement of the web ofrecord members 37 stops. It is noted that the control member contacts the O-ring 126 above the center of thecontrol sleeve 124 at an obtuse angle A relative to the direction of travel of the O-ring at the point of contact. Moreover, considering a first line between the point of contact and thepivot 113, a second line perpendicular to the first line and intersecting the first line between the point of contact and thepivot 113 passes through the center line of thesleeve 124. This results in effective disengagement at the clutch 128 when themember 145 contacts the O-ring 126.

Theend section 149 of the drivenmember 127 has a flat 150'. Theknob 148 is received by theend section 149 and has a flat 151 which cooperates with the flat 1511 of theend section 149 to prevent rotation of theknob 148 relative to theend section 149. Afriction clutch 152 includes the washer 138 which is keyed to thesection 149, the O-ring 139, thewasher 137 and the end surface of thebushing 136. Ascrew 153 threadably received by theend section 149, is adjustable to adjust the amount of frictional drag of the clutch 152. It is apparent that thefeed wheel 42 can be driven either through torque applied by thepulley 104 when the clutch 120 is engaged, or manually by rotation of theknob 140 but the clutch 152 frictionally holds thefeed wheel 42 in the position into which it has been advanced, either as a result of the engagement of the clutch 1211 or as the result of manually rotating theknob 140.

A solenoid 154 (FIG. 18) mounted by theplate frame 108 has anarmature 155. Acompression spring 156 is received about the armature between the end of thesolenoid housing 157 and aflange 158 on thearmature 155. Thearmature 155 is connected to thecontrol member 145 by apin 159. Thespring 156 normally holds thecontrol member 145 in the solid line position (FIG. 18). Energization of thesolenoid 154 causes thearmature 155 to shift,therebypivoting control member 145 clockwise into the phantom line position (FIG. 18) out of contact with O-ring 126. Energization and deenergization of thesolenoid 154 is controlled by a circuit shown in FIG. 30.

Thefeed wheel 42 advances the web once during each machine cycle so that arecord member 37 is presented to the printing position or zone between theplaten 44 and theprinting members 70. When therecord member 37 arrives at the printing zone, the clutch 120 is disengaged and thefeed wheel 42 stops rotating. However, as theoutput shaft 75 of theelectric motor 49 rotates continuously, the rotary feed member 98is continuously driven. Therotary feed member 98 is shown in FIGS. 5 and6 to have ahub 160 secured to the drivenshaft 96. Thehub 160 is shown to be provided with four dove-tail slots 161 for receivingrespective drive members 162. Thedrive members 162 are in the form of outwardly extending vanes or blades. Thedrive members 162 are composed of a flexible, resilient material preferably having a high co-efficient of friction, such as rubber. When thedrive members 162 are in driving engagement with a section of the web which has been paid out of theroll 36, thedrive members 162 flex slightly as they engage the web. As therotary feed member 98 continues to rotate, additional web material is paid out of theroll 36 until gradually slackness develops. As the slackness increases, the contact between therotary feed member 98 and the web decreases and it can decrease to such an extent that the paid out web section looses contact with thefeed member 98 as indicated by phantom lines. As rotation of therotary feed member 98 continues, thefeed wheel 42 and theroll 43, together with thefeed member 98 provides a simple arrangement for feeding the web material from theroll 36. As theroll 36 has a relatively large amount of inertia, and as the feeding by thefeed wheel 42 is intermittent, the construction, arrangement and location of thefeed member 98 prevents an undue amount of web material from being paid out of theroll 36. This is accomplished without applying any braking force either to thereel 38, to theroll 36, or to the paid out web material, although the art is replete with such devices. As best shown in FIG. 5, it is noted that thereel 38 and therotary feed member 98 are disposed at the same slight angle with respect to the horizontal. Assuming the apparatus is mounted on a generally horizontal surface, theroll 36 will not come off thereel 38 and yet therotary feed member 98 can make full contact with the underside of the web. The peripheral speed of thedrive members 162 is greater than the peripheral speed of thefeed wheel 42.

With reference to FIGS. 2 and 7, there is provided an aligning mechanism generally indicated at 163. The aligningmechanism 163 includes anarm 164 pivotally mounted by thepivot pin 34. Atension spring 165 is connected at one end to thearm 164 and at its other end to a plate 108' secured to theplaten frame 108. Ashaft 166 secured to thearm 164 is disposed at a slight angle with respect to the direction of travel of therecord members 37 and to aplate 108" secured to theplaten frame 108. An aligningroll 41 is comprised of abushing 167 rotatably mounted by theshaft 166 and a one-piece molded annularfrictional member 168 having a plurality of externalannular flanges 169. Thespring 165 urges theroll 41 towardplaten surface 39. As the web advances, the web rotates theroll 41 which causes the web to move into alignment with an upstanding guide edge provided by theplate 108".

Theplaten 44 is shown in FIG. 7 to be adjustably mounted to theplaten frame 108 byscrews 170. The

screws 170 pass throughelongated slots 171 in theplaten frame 108 and are rotatably received by respective nuts 172. In this manner, theplaten 44 and theknife 45 formed at the terminal end of theplaten 44 can be adjusted relative to themovable knife 47.

Abracket 173 is suitably secured to theplaten frame 108. Thebracket 173 threadably receives the adjusting screws 71.Lock nuts 71 lock therespective screws 71 in their adjusted positions. Thebracket 173 mountspivot 48. Themovable knife 47 has a pair of flanges orarms 176 and 177 which are pivotally mounted by thepivot 48. Alink 178 is connected to thearm 176 by apivot pin 179, and alink 180 is connected to thearm 177 by apivot pin 181. Thelinks 178 and 180 are identical and have respective elongatedslots 182 and 183 and respective stop shoulders 184 and 185. Asolenoid 186 is secured to thebracket 73. Armature 187 (FIG. 7) is shown to be received in acompression spring 188.

Thespring 188 is compressed between the end of thesolenoid 186 and awasher 189 which bears against apin 190. A generallyU-shaped yoke 190 is secured to the end of thearmature 187 by ascrew 191 has a pair of forwardly extendingarms 192 and 193. Thearm 192 is pivotally connected to thelink 178 by apivot pin 194, and thearm 193 is pivotally connected to the link by apivot pin 195.Arms 192 and 193 have respective stop shoulders 192' and 193'.

Thesevering mechanism 46 is only effective when thesolenoid 186 has been energized. Thesolenoid 186 is energized during the time in the machine cycle when theshoulders 184 and are below astop face 196 provided by aplate 197 secured to thebracket 73. Energization of thesolenoid 186 drives thelinks 178 and 180 against theend 198 of theplate 197. As theplaten assembly 33 moves upwardly, theshoulders 184 and 185 of therespective links 178 and 180 engage the stop face 196 (FIG. 8) to pivot themovable knife 47 counter-clockwise into severing cooperation with theknife 45, thereby severing arecord member 37 from the web. During the remainder of the machine cycle, theplaten assembly 33 moves away from theprint head 32. Upon deenergization of thesolenoid 186, thesprings 199 and 200 respectively connecting thelink 178 and thebracket 173, and thelink 180 and thebracket 173 cause themovable knife 47 to pivot to its clockwise position shown in FIG. 9.

Thespring 188 normally holds the yoke and thepins 194 and in the position shown for example in FIG. 7. Assuming that thesolenoid 186 is not energized, theshoulders 184 and 185 will not engage thestop face 196 as theplaten assembly 33 moves upwardly. Accordingly, themovable knife 47 will remain in its initial position relative to the knife 45 (FIGS. 1 and 7).

Themovable knife 47 has a manually engageable upstanding tab or handle 47' by which themovable knife 47 can be moved into record severing relationship with respect to theknife 45. As themovable knife 47 pivots, theslots 182 and 183 allow the links 178'and 180 to be moved downwardly as viewed in the drawings. Thesprings 199 and 200 thereafter return themovable knife 47 to its initial position shown in FIGS. 1 and 7.Flange 177 has a projection 177' which is urged into control with a step 177' bysprings 199 and 200 to define the initial position.

With reference to FIGS. 3 and 7, thebracket 173 is shown to have anextension 201. A resilient deflector generally indicated at 202 includes inwardly and upwardly extendingspring fingers 203 which in their normal positions extend to immediately adjacent and slightly below the cutting edge of theknife 45. The marginal ends 204 of thespring fingers 203 are turned away from the edge of theknife 45. Thespring fingers 203 are integrally joined to a mountingportion 205 disposed in underlying relationship to theextension 201.Screws 206 secure the mountingportion 205 to theextension 201. When themovable knife 47 is actuated into cutting relationship with theknife 45 to sever arecord member 37 from the web, themovable knife 47 deflects thespring fingers 203 from the position shown in FIG. 7 to the position shown in FIG. 8. As the movable knife returns from the position shown in FIG. 8 to the position shown in FIG. 7, thespring fingers 203 also return to the position shown in FIG. 7. Thefingers 203 not only prevent the severedrecord member 37 from falling out of reach in theapparatus 30, but they also serve to propel the individual record members into a discharge chute indicated byphantom lines 206 in FIG. 7. Thechute 206 is disposed betweenarms 176 and 177 of themovable knife 47. I

Referring to FIGS. 11 and 13 through 17, and initially to FIG. 13, there is shown the inking mechanism generally indicated at 35. The inking mechanism includes a reservoir orfountain 211 by which anink supply roll 212 and anink transfer roll 213 are mounted. Theink transferring roll 213 is an anilox roll having typically microscopic geometric shaped holes or cells in its surface. These holes or cells carry the ink to anink roll 251. Thefountain 211 has a fountain cover 211'. Theink supply roll 212 has ahub 214 and an inkreceptive cover 215 made of rubber. Thehub 214 is keyed to ashaft 216 by a key 217. Ascrew rod 218 threadably received by theshaft 216 is shown to be tightened to drive the key 217 into keying engagement with thehub 214. Theshaft 216 is rotatably mounted near one end by abearing 219 in anarm 220 of a U- shaped frame generally indicated at 221. Theshaft 216 is also mounted near its other end by abearing 222 received by theother arm 223 of theU-shaped frame 221. Theframe 221 is pivotally mounted by a shaft or pivot 224 mounted at opposed ends 225 and 226 by thefountain 211. Aset screw 227 prevents theframe 211 from shifting axially along theshaft 224.

Theframe 221 has anextension 228 with ahole 229. Ascrew 230 passes through ahole 231 in thefountain 211 and thehole 229 in theextension 228. Arod 232 having a threadedbore 233 threadably receives thescrew 230. A compression spring 234 is received about thescrew 230 between the screw head 235 and thefountain 211. Tightening thescrew 230 causes theink supply roll 212 to be pressed more tightly against theink transferring roll 213, thereby diminishing the amount of ink which is transferred to theink transferring roll 213 by theink supply roll 212. Loosening thescrew 230 results in more ink being transferred to theink transferring roll 213.

Theink transferring roll 213 is secured to a mountingshaft 236 by asetscrew 237. Theshaft 236 is rotatably mounted inbearings 238 and 239. Theshaft 236 is driven by thepulley 91. Apinion 240 secured to theshaft 236 is in meshing engagement with agear 241 secured to theshaft 216. As the external diameter of theink supply roll 212 and theink transferring roll 213 are the same, thegears 240 and 241 cause theink supply roll 212 to be driven at a slower rate of speed than theink transfer roll 213. This difference in the peripheral speeds of therolls 212 and 213 results in a slight wiping action or slippage as therolls 212 and 213 rotate in the directions of arrows 212' and 213' (FIG. 13). This wiping action is found particularly beneficial with inks of relatively high viscosities in effecting diminuation in the amount of ink transferred to theink transferringroll 213. As the amount of pressure adjustment between therolls 212 and 213 is relatively small upon the loosening or tightening ofthescrew 230, the correct meshing engagement between thegears 240 and241 is not affected. 1

Awiper blade 242 secured to thefountain 211 is slightly longer and thus extend slightly beyond both ends of theroll 212. Theblade 242 both limits the amount of ink which is transferred to theroll 213 and distributes the ink relatively evenly over the surface of theroll 212. As best shown in FIG. 17, the amount of ink I in thefountain 211 is limited by aweir 244. Excess ink in thefountain 211 pours over theweir 244 and gravitates throughopenings 245 between a plurality ofbosses 246 which receive screws 243. Fromopenings 245 the ink flows gravitationally through a plurality of drain holes 247 (one of which is shown) intoink return header 248 from which the excess ink is returned viaflexible tube 250 to a sump in the form of aglass jar 249.

Anink roll 251 is shown in FIG. 13 to be in inking cooperation with theink transferring roll 213. Theink roll 251 includes atubular sleeve 252 having a covering 253 of ink receptive material such as rubber.Guide rollers 254 and 255 are secured to ashaft 258. The

sleeve 252 is rotatable on theshaft 258 bybearings 256 and 257.

Aknurled wheel 259 is secured to theshaft 236 by a set screw 259'. Thewheel 259 drivingly engages anannular rubber wheel 260 secured to thesleeve 252 when theroll 251 is in inking relationship with theroll 213 as shown in FIG. 13. A gap 261 between the covering 253 and thewheel 260 to prevent any ink from being transferred to thewheel 260 from the covering. 253.

With reference to FIG. 11, therolls 254 and 255 are shown to be in contact with guide means in the form ofrespective cams 262 and 263. The diameter of thewheel 260 is slightly larger than the diameters of therolls 254 and 255. Thewheel 260 is shown to be in contact with aplate 262A the lower surface of which is spaced slightly above the lower surface of thecam 262 as viewed in FIG. 11. Theink roll 251 is normally in the position shown by phantom lines 251' in FIG. 13. As theplaten assembly 33 pivots downwardly, theink roll 251 is driven from the position shown by phantom lines 251' to the position shown byphantom lines 251". The cam tracks 262 and 263 can be individually and independently adjustable upwardly and downwardly relative to the printing members carried by theprint head assembly 32. Adjustment of the cam tracks 262 and 263 by screws 262' and 263' whichextend throughenlarged slots 262" and 263" adjusts the amount of pressure or inking contact between theroll 251 and theprinting members 70, thereby controlling the application of ink to theprinting members 70. While theink roll 251 is moving from the position shown by phantom lines 251' to the position shown byphantom lines 251", theink roll 251 is driven by theplate 262A which is in driving engagement with thewheel 260. The fact that thewheel 260 has a slightly larger diameter than the covering 253 of the ink roll is of no practical consequence in that the contact area between theprinting members 70 and the covering 253 is many times greater than the contact area between theplate 262A and thewheel 260. Accordingly, the ink roll'251 rolls across theprinting members 70 without slipping.

With reference to FIG. 1, agear section 264 specifically in the form of a gear segment, the center of rotation of which is the axis of thepivot 34, is secured to theplaten frame 108 byscrews 265. Accordingly, therack 264 rotates as a unit with theplaten frame 108.. Apinion 266 is secured to ashaft 267 pivotally mounted in astationary bracket 26%. Thebracket 268 is secured to theframe 31. An arm 269secured to theshaft 267 carries aroller 270. With reference to FIG. 9, as theplaten assembly 33 moves generally downwardly, the

rack 264 drives thepinion 266 and thearm 269 counterclockwise. Theroller 270 is received in acam slot 271 of acam follower 272. Thefollower 272 is secured to ashaft 274 pivotal about abearing 273 suitably secured to theframe 31. Arocker 275 secured to theshaft 274 carries a spaced apart pair ofball joints 276 and 277. The ball joints 276 and 277 are received byrespective sockets 278 and 279. Theballjoints 276 and 277 and thesockets 278 and 279 are identical in construction. Accordingly, only the ball joint 277 and itsrespective socket 279 are shown in detail in FIG. 10.

With reference to FIG. 10, the ball joint 277 is shown to have a threadedshank 280 threadably received in a threadedbore 281 in therocker 275. The ball joint 277 includes aspherical ball 282 joined to theshank 280. The distance between theball 282 and the centerline of theshaft 274 can be varied by turning the ball joint 277. This changes the length of the are through which theball 282 travels. Alock nut 283 andwasher 284 lock theshank 280 in its adjusted position. Thesocket 279 includes ahousing 285 and an opposed pair ofsocket members 286 and 287. Thehousing 285 has a threadedbore 288 which receives ascrew 289. Acompression spring 290 is compressed between thesocket member 286 and thescrew 289. Thesocket member 287 is suitably rotatably mounted in thehousing 285, but thesocket member 286 is slidable generally to the left (FIG. 10) away from thesocket member 287 to further compress thespring 290 as shown by phantom lines in FIG. 10 during the inking of theink roll 251.Rods 291 and 292 are suitably secured at their one ends to thesocket members 287 of therespective sockets 278 and 279. The other ends of therods 291 and 292 are threadably received byrespective connectors 293 and 294. Theconnectors 293 and 294 are connected bypivot pins 295 and 296 torespective carriages 297 and 298. The carriage 297 (FIG. 8) rotatably mountsrollers 299, 300 and 301 by respective pivot pins 299', 300' and 301 The carriage 298 (FIG. 1) rotatably mountsrollers 302, 303, and 304 by respective pivot pins 302', 303 and 304'. Therollers 299, 300 and 301 are in guided rolling contact with aguide track 305 shown in detail in FIG. 11. Therollers 299, 300 and 301 make three-point contact with thetrack 305. Therollers 302, 303 and 304 are in guided, rolling, three-point contact with a guide track 306 (FIG. l).Links 307 and 308 are mounted tocarriages 297 and 298 byrespective pivots 309 and 310. The opposite ends of theshaft 258 are mounted by thearms 307 and 308.Springs 309 and 310 connected torespective links 307 and 308 andcarriages 297 and 298urge rollers 254 and 255 against respective cam tracks 262 and 263.

With references to FIG. 16, thejar 249 is mounted by a holder 311 secured to theframe 31. Acap 312 is threadably secured to thejar 249. Thecap 312 has a large opening 313. Ametal plate 314 and acompressible liner 315 are clamped betweenend wall 316 of thecap 312 and the terminal end of thejar 249. A pump generally indicated at 317 is shown to include atubular pump body 318. Thepump body 318 has an enlarged external diameter section orflange 319 and a threaded section 320. Anut 321 received by the threaded section 320 bears against theline 315 and draws theflange 319 against theplate 314 to mount the pump in an upright position. Spaced slightly above the lowerterminal end 322 of thepump body 318 are a plurality ofinlet ports 323. Aball 324 is received in a recess in the lower end of thepump body 318. Ahelical spring 325 receives arod 326. One end of thespring 325 contacts theball 324 which acts as a bearing for thespring 325. The other end of therod 326 extends to about the end of thepump body 318. Thespring 325 exerts a gripping force in the rod as the outside diameter of therod 326 is greater than the internal diameter of thespring 325 before therod 326 is inserted into thespring 325. Accordingly, thespring 325 and therod 326 are rotatable as a unit. There is only a slight amount of clearance between outside of thespring 325 and theinside bore 327 of thepump body 318. Thespring 325 extends all the way from the lower end of the rod 326 (FIG. 16) to the slotted marginal end 328 (FIG. 15) of aconnector 329 secured to theshaft 216. The end of thespring 325 has atang 330 which extends into theslot 331 of the slottedend 328, thereby connecting or keying thespring 325 to theconnector 329. As theshaft 216 and theconnector 329 rotate, thespring 325 rotates within a flexibleplastic tube 332. Theflexible tubes 250 and 332 are curved and thespring 325 conforms generally to the internal contour of thetube 332. The portion of thespring 325 in thebore 327 is not in the same axis as thedrive shaft 216. Thetube 332 is received about atubular extension 333 of thefountain 211. Awire stiffener 334 is wrapped about themarginal end portion 335 of thetube 332. Thestiffener 334 insures that theportion 335 of thetube 332 between the upper andlower passes 92 and 92" of the continuously movingbelt 92 does not come into contact with thebelt 92. Similarly, awire stiffener 336 is wrapped about themarginal end portion 337 of thetube 250. Thestiffener 336 insures that theportion 337 of theflexible tube 250 does not come into contact with thelower pass 92" of thebelt 92.

The lower end of thetube 250 is connected to a tubular fitting 338 (FIG. 16). The fitting 338 has aflange 339 and a threadedsection 340. Anut 341 secures the fitting 338 to theplate 314.

With reference to FIG. 14, as theshaft 216 rotates continuously, thespring 325 is also continuously rotated Within theflexible tube 332. Thespring 325 extends into thetubular pump body 318 and rotates together with therod 326. Therod 326 fills up the space within the coils of thesprings 325. As thespring 325 rotates, ink l in thejar 249 is drawn through theinlets 323. As the ink I has a relatively high viscosity, the ink l trapped between therod 326 and thebore 327 of thepump body 318 and between the coils of thespring 325 is conveyed upwardly. The ink I in thetube 332 above therod 326 completely fills the space in thetube 332 which is not occupied by thespring 325. Accordingly, the continuous rotation of thespring 325 causes ink to be delivered continuously through thepump body 318, through theflexible tube 332 and through the fitting 333 (FIG. 14) into thefountain 211 as indicated byarrow 1. The ink Isupplied to thefountain 211 always exceeds the amount required so that excess ink is continuously returning through theheader 248 to thejar 249 via thetube 250. The inside of thejar 249 is at atmospheric pressure because of aligned vent holes 314' and 315 in theplate 314 and theliner 315, respectively.

With references to FIG. 20, theprint head assembly 32 is shown to include a pair ofprint heads 341 and 342 mounted by a printhead assembly frame 32". The

Claims (4)

1. Web feeding apparatus, comprising: means for mounting a roll of web material, means for intermittently feeding web material from the roll, rotary feeding means disposed below and spaced from the web roll, means for continuously driving the rotary feeding means, the web material extending (a) beneath and partly around the rotary feeding means, (b) from there parly around, over and in contact with the web roll, and (c) from there to the intermittent feeding means, tautness in the web material enabling rotary feeding means to pay additional web matrail out of the roll and increased slackness in the web material decreasing the amount of web material which the rotary feeding means pays out of the web roll, wherein the rotary feeding means comprises yieldable means which yield during frictional contact with the web material.

2. Web feeding apparatus as defined in claim 1, wjherein the rotary feeding means comprises a plurality of flexible members in riving engagement with the web material.

3. Web material apparatus as defined in claim 1, wherein the rotary feeding means comprises a plurality of outwardly extending flexible, resilient elements having a relatively high coefficient of friction.

4. Web feeding apparatus, comprising: means for mounting a roll of web material, means for intermittently feeding the web from the roll, rotary feeding means comprising a plurality of flexible resilient frictional members for gradually paying the web out from the roll, the rotary feeding means being disposed relative to the roll and to the intermittentt feeding means that a portion of the web freely depends from the roll to form a free-hanging loop section between the web roll and the intermittent feeding means, with the loop section passing under and partly around the flexible resilient frictional members, and means for continuously driving the rotary feeding means to effect increased contact and flexure of the flexible resilient frictional members to increase the rate of feed of the web as the web becomes taut in response to feeding by the intermittent feeding means and to effect decreased contact with the flexible resilient frictional members to decrease the rate at which the web is paid out in response to increased slackness in the web.

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