US3176069A - Type wheel mechanism for printing telegraph page printer - Google Patents

Description

March 30, 1965 w. J. ZENNER 3,175,059

TYPE WHEEL MECHANISM FOR PRINTING TELEGRAPH PAGE PRINTER Filed Dec. 14. 1961 9 Sheets-Sheet 1 INVENTOR WALTER J. ZENNER ATTORNEY FIG. I

March 30, 1965 w. J. ZENNER 3,176,069

TYPE WHEEL MECHANISM FOR PRINTING TELEGRAPH PAGE PRINTER Filed Dec. 14. 1961 I 9 Sheets-Sheet .2

Ilium! INVENTOR WALTER J. ZENNER ATTORNEY March 30, 1965 w. J. ZENNER 3,176,069

TYPE WHEEL MECHANISM FOR PRINTING TELEGRAPH PAGE PRINTER Filed. Dec. 14. 1961 9 Sheets-Sheet 3 INVENTOR WALTER J. ZENNER BY m2 ATTORNEY March 30, 1965 w. J. ZENNER 3,176,069

TYPE WHEEL MECHANISM FOR PRINTING TELEGRAPH PAGE PRINTER 9 Sheets-Sheet 4 Filed Dec. 14. 1961 mmm wamL

ATTORNEY March 30, 1965 w. J. ZENNER 3,176,069

TYPE WHEEL MECHANISM FOR PRINTING TELEGRAPH PAGE PRINTER Filed Dec. 14. 1961 9 Sheets-Sheet 5 INVENTOR 467 469 WALTER J. ZENNER 5|6 ATTORNEY March 30, 1965 w. J. ZENNER 3,176,069

TYPE WHEEL MECHANISM FOR PRINTING TELEGRAPH PAGE PRINTER Filed Dec. 14. 1961 9 Sheets-Sheet 6 535 FIG. 7

54 I I I F 2 INVENTOR WALTER J. ZENNER ATTORNEY March 30, 1965 w. J. ZENNER 3,176,069

TYPE WHEEL MECHANISM FOR PRINTING TELEGRAPH PAGE PRINTER Filed Dec. 14. 1961 9 Sheets-Sheet 7 FIG. ll

gfiunnummmlr INVENTOR WALTER J. ZENNER ATTORNEY March 30, 1965 w. J. ZENNER 3,176,069

TYPE WHEEL MECHANISM FOR PRINTING TELEGRAPH PAGE PRINTER Filed Dec. 14. 1961 9 Sheets-Sheet 8 INVENTOR WALTER J. ZENNER BY MM ATTQRNEY March 30, 1965 w. J. ZENNER TYPE WHEEL MECHANISM FOR PRINTING TELEGRAPH PAGE PRINTER 9 Sheets-Sheet 9 Filed Dec. 14. 1961 FIG. l8 FIG. I8A

INVENTOR WALTER J. ZENNER United States Patent C) 3,176,069 TYPE WHEEL MECHANISM FOR PRINTING TELEGRAPH PAGE PRINTER Walter J. Zenner, Des Plaines, 11]., assignor to Teletype Corporation, Skokie, Ill., a corporation of Delaware Filed Dec. 14, 1961, Ser. No. 159,330 9 Claims. (Cl. 178--28) This invention relates to printing telegraph apparatus wherein a type bearing member is selectively positioned and then oscillated to drive an inked ribbon against a web, and more particularly to a page printer having a type wheel movable across a platen and reciprocated and rotated to bring type on the wheel into selected alignment with a web to be printed and then oscillated to effect printing.

It is an object of the present invention to provide a printing telegraph printer capable of high speed operation and of the simplest construction commensurate with precision and long service.

Another object of the invention is to provide a printing telegraph type wheel printer having simple type wheel positioning mechanism.

A still further object in the invention is the provision of a type wheel page printer having a minimum of complex mechanical devices wherein the type wheel may be positioned with a high degree of accuracy.

A feature of the invention is a type wheel which may be reciprocated and rotated to select a type thereon for printing and which may then be bodily rocked to effect printing without moving any portion of the mechanism which positioned it.

In accordance with one embodiment of the invention a printing telegraph apparatus of the type wherein a type wheel is mounted on a carriage movable transversely of the apparatus to space it across a page of paper fed over a nonreciprocatory platen includes a type wheel which is fixed to a plate that is slidable on three guide posts that are in turn fixed to a rotatable cage that may be rotated in accordance with received permutation code signals to transmit motion through the guide posts to the plate. The plate may be reciprocated in response to received permutation code signals to select a level on the type wheel and align the selected level with a printing position and also rotated to align a type on it with the printing position. The type wheel and plate on which the type wheel shaft is mounted may then be oscillated with respect to the guide posts to effect printing as controlled by the rotary and reciprocatory motion which have been imparted to the type wheel. In the preferred embodiment of the invention disclosed herein the rotary and reciprocatory positioning of the type wheel is controlled by a selector mechanism which responds to signals either generated in the apparatus through the cooperative operation of a keyboard and a distributor or which receives signals transmitted over a telegraph line. The selector mechanism in turn controls coded selector levers which govern the positioning of function code bars that in turn position stops for controlling the degree and direction of movements to be imparted to the type wheel by instrumentalities interconnecting the function code bars and the rotatable cage reciprocating mechanism which effect the ultimate positioning of the type wheel.

A complete understanding of the invention may be had by reference to the following detailed description when considered in conjunction with the accompanying drawings wherein:

FIG. 1 is a perspective view looking down at the right side of the apparatus;

FIG. 2 is an end elevational view looking at the right side of the apparatus, with the keyboard portion of the apparatus broken away, and with other parts broken away, more clearly to illustrate those parts which would otherwise be covered by the parts broken away;

FIG. 3 is a longitudinal, vertical sectional view through the left side of the apparatus, taken just inside of the left edge of the apparatus;

FIG. 4 is a vertical sectional view, looking toward the rear of the printer, taken substantially along the line 4-4 of FIG. 2, in the direction of the arrows;

FIG. 5 is an irregular fragmentary horizontal sectional view taken substantially along the line 55 of FIG. 3, in the direction of the arrows, showing the main drive shaft for the apparatus and various parts associated with it;

FIG. 6 is a fragmentary detailed sectional view showing the clutch trip mechanism for the distributor and taken just behind the corresponding area shown in FIG. 2 as projected upwardly;

FIG. 7 is an irregular, fragmentary plan sectional View on an enlarged scale taken substantially along the line 77 of FIG. 2 in the direction of the arrows, showing details of construction of the mechanism for controlling the positioning of the type wheel;

FIG. 8 is a vertical sectional view taken substantially along the line 8-8 of FIG. 7, in the direction of the arrows in which some of the supporting structures have been omitted, more clearly to show other parts of the mechanism;

FIG. 9 is a fragmentary horizontal sectional view taken along the line 9-9 of FIG. 8, in the direction of the arrows;

FIG. 10 is a fragmentary detailed sectional view of a portion of the apparatus shown in FIG. 3 taken just behind the corresponding area shown in FIG. 3 as projected upwardly;

FIG. 11 is a fragmentary vertical sectional view taken substantially along the line 11--11 of FIG. 5 in the direction of the arrows;

FIG. 12 is a longitudinal, vertical sectional view taken substantially along the line A-A of FIG. 5 in the direction of the arrows 12-12 looking toward the left side of the apparatus;

FIG. 13 is a longitudinal, vertical sectional view also taken substantially along the line AA of FIG. 5 but taken in the direction of the arrows 1313 looking toward the right side of the apparatus;

FIG. 14 is a fragmentary sectional view taken substantially along the line 1414 of FIG. 12 in the direc tion of the arrows;

FIG. 15 is a transverse vertical sectional View taken substantially along the line 1515 of FIG. 5 in the direction of the arrows showing a portion of the function code bar mechanism.

FIG. 15-A is a view similar to FIG. 15 but taken farther to the rear of the apparatus substantially along the line 15A-15A of FIG. 11 in the direction of the arrows, to show configuration of a print suppression code bar;

FIG. 16 is a fragmentary sectional view taken substantially along the line 16-16 of FIG. 5 in the direction of the arrows;

FIG. 17 is a fragmentary vertical sectional view taken substantially along the line 17I7 of FIG. 8 in the direction of the arrows, showing part of the type wheel controlling mechanism which controls its rotary position;

FIG. 17A is a view similar to FIG. 17 but taken farther to the front of the apparatus showing part of the type controlling mechanism which is obscured in FIG. 17;

FIG. 18 is a fragmentary vertical sectional view taken along the line 18-48 of FIG. 8 in the direction of the arrows showing part of the mechanism for controlling the reciprocatory positioning mechanism which is obscured in FIG. 18;

FIG. 19 is a fragmentary vertical sectional view taken substantially along the line 1919 of FIG. 7 in the direction of the arrows, and

FIG. 20 is a fragmentary plane view taken substantially along the line 20-20 in the direction of the arrows showing some of the drive mechanisms.

General Description In the preferred embodiment of the invention, which is illustrated herein, the apparatus includes a base 21 having suitable standards extending upwardly from it such as standards 22 and 23 (FIG. 1), 24 and 25 (FIG. '5 26 and 27 (FIG. 4), 28 (FIGS. 3 and 4) and 29 (FIG. 3) for supporting various components of the apparatus. As will be seen by reference to FIG. 1, these components, generally speaking, comprise a selector mechanism 31 (FIGS. 3, 5, and 10); a keyboard mechanism 32 (FIG. 1), which may indirectly control the selector mechanism 31; a distributor mechanism 33 (FIGS. 1 and 2) which is interposed between the keyboard mechanism 32 and the selector mechanism 31 when the apparatus is used for transmitting messages and thereby serves to provide a home copy for the transmitting station; a type wheel positioning mechanism 34 (FIGS. 2, 3, 5, 7, 8, and 9), and a ribbon mechanism 35 (FIGS. 1, 3 and 4). The selector mechanism 31 includes a range finder or orienting device 36 as illustrated in FIGS. 3, 5 and 10.

The basic design of the selector mechanism 31 is shown and claimed in the patent to W. J. Zenner, No. 2,595,745 issued May 6, 1952, to which reference may be had for details of operation and structure of the selector, similarly, the basic design of the range finder for the selector is disclosed and claimed in the patent to C. W. Swan, No. 2,642,799 issued January 6, 1953. Details of construction of the keyboard which it is preferred to use in the present invention and of the distributor mechanism also preferred for use in the present invention may be had by reference to the copending application of L. C. Anderson and A. A. Hagstrom, Serial No. 159,324 filed Decemher 14, 1961, and the co-pending application of K. Alonas, A. A. Hagstrom and B. J. Sobczak, Serial No. 159,328 filed December 14, 1961. The disclosures of these patcuts are incorporated herein by reference insofar as may be necessary to understand the structure and operation of the apparatus to be claimed herein.

The various components of the apparatus receive their motive power from a motor 37 (FIG. 1) which through suitable gearing designated generally by the numeral 38 drives a main power shaft 39 of the apparatus. When the apparatus is in operating condition the motor 37 will continuously supply power to the shaft 39 on which there are mounted three clutches 40 (FIGS. 3 and 5), 41 and 42 (FIGS. *1 and 5). The clutch 46 (FIGS. 3

and 5) is operable to connect the selector mechanism 31 to the main power shaft 39. Another clutch 43 which is mounted on an intermediate shaft 44 serves to connect the distributormechanism 33 to the power source. The clutch 41 on the main power shaft 39 serves to supply power for operating the various mechanisms which are selectively set up for operation by the selector mechanism 31 and the clutch 42 serves to supply power for restoring some of the mechanisms in timed relation to other operations of the apparatus. All of these clutch mechanisms 40, 41-, 42 and 43 are of the type shown and claimed in the patent to A. N. Nilsen et al., No. 2,568,249 issued September 18, 1951.

The present application is primarily concerned with improved mechanism in the type wheel supporting and actuating mechanisms and the following detailed description will be directed to such apparatus and only so much of the components shown and described in the aforementioned applications and patents will be described as is necessary to a complete understanding of the present invention.

The correspondence between the various elements of the present application and the elements of the patents and applications mentioned hereinbefore will be quite apparent and reference may be had to them for an understanding of the operation of those components.

Selector Mechanism The main power shaft 39 is mounted for rotation in a pair of bearings 46 (FIG. 5) and 47 (FIG. 20) fixed in the main support plate 48 and a bearing plate 49 and carries adjacent to its right end a drive pinion 50 which meshes with a gear 51 freely rotatable on the intermediate shaft 44. The gear 51 is fixed to a toothed pulley wheel 52 also freely rotatable on the shaft 44 and driven by a belt 53. A second pulley 54 for driving the belt 53 is fixed to a pinion gear 55 which is meshed with a gear 56 formed on the shaft of the motor 37. The pulley 54 and gear 55 are freely rotatable on a stud shaft 57 mounted on the motor 37. The main power shaft 39 (FIGS. 3, 5, and 10) has a selector cam sleeve 61 (FIGS. 3, 5, and 10) mounted on it for selective rotation with it. The clutch 40 has its driven element fixed to the main power shaft 39 and as pointed out hereinbefore, is of the type disclosed in detail in the patent to A. N. Nilsen et al. and is rendered effective to connect the selector cam sleeve 61 to the shaft 39 when a stop projection 62 of a clutch shoe lever such as disclosed in the aforementioned Nilsen et al. patent is released by an end portion 63 of a stop bail 64.

The stop bail 64 (FIGS. 3, 5 and 10) is provided with a pair of arms 65 and 66, the end portion 63 of the stop bail being at the extreme end of the arm 65. An arcuate slot 67 (FIG. 10), concentric with the axis of the shaft 39 is formed in the arm 66 of the stop bail 64 for slidably receiving a pin 68. The stop bail 64 is pivoted on a.

pivot shaft 69 and is normally urged to rock in a counterclockwise direction (FIGS. 3 and 10) about the pivot shaft 69 by a contractile spring 70 which is attached to the Web portion of the stop bail 64 and to an arm 71 of an orientation plate '72. The pivot shaft 69 is fixed to the orientation plate 72 and in addition to pivotal-1y supporting the stop bail 64 also supponts a clutch latch lever '7 The orientation plate '72 is adjustably mounted on a support plate 74 in which there is formed an a-rcuate slot 75 and on which there is scribed a suitable scale 76 for cooperation with a pointer 77 on the orientation plate 72. The pivot shaft 69 which is fixed to the orientation plate 72 extends through the slot 75 and through both the arm 65 and the arm 66 of the stopbail 64. The pivot shaft 69 cooperates with a shouldered screw 78 and a knurled thumb nut 79 to adjustably position the orientation plate 72 with respect to the support plate 74 without changing the concentric position of the stop bail 6-4. Thus, the stop bail 64 may be adjusted about the shaft 39 to determine the time at which the stop bail will release the clutch 49 with respect to the rotative position of the cam sleeve 61. As pointed out hereinbef'ore, the pivot shaft 69 also pivotally supports the clutch latch lever 73 which is urged to rock in a clockwise direction about the pivot shaft 69 by a contractile spring 81 to effect the operation of the clutch 40 in the manner described in detail in the patent to C. W. Swan, No. 2, 624,799, mentioned hereinbefore.

The selector mechanism also includes a selector magnet coil 91 which is suitably supported between the support plate 74 and a second sup-port plate 92 (FIG. 5) and both of these plates are in turn supported by posts 93, 94 and 95 which extend outwardly to the left side of the apparatus from the main supporting plate 48. Upon receipt of a marking or current impulse either from the signal line (not shown) or from the distributor mechanism 33, the selector magnet coil 91 will be energized and will attract an armature 96 which is provided with pivot extensions 97 (FIG. 3), one of which extends into the support plate 74 and the other of which extends into supo-rt plate 92. Upon the receipt or" a spacing or no-current impulse, the coil 91 will be de-energized and will release its armature 96 which will then rock in a clockwise direction (FIG. 3) under the urging of a contractile spring 93 which is attached to the armature 96 and to a suitable bracket attached to the support plate 92.

As is usual in printing telegraph systems, the normal condition of the signal line to the selector coil 91 when no message is being received or transmitted, is "a current or marking condition and consequently, the selector magnet coil 91 normally is energized to hold its armature 96 in the position shown .in FIG. 3. When the armature 96 is in the position shown in FIG. 3, it blocks a start lever 99 (FIGS. 3 and on which the stud or pin 68 is fixed and prevents the start lever 99 from rocking counterclockwise (FIGS. 3 and 10) about the post 93 under the influence of a contractile spring 100 which is attached to the start lever 99 and to a plate 101 which extends between the support plates 74 and 92.

In the normal or nonselecting position of the cam sleeve 61, an indentation 102 in the cam sleeve is in alignment with a camming projection 103 formed on the arm 66 of the stop bail 64. Thus, if a no-current or spacing pulse is transmitted to the selector magnet coil 91, the start lever 99 will be permitted to rock counterclockwise (FIG. 10) about the post 93 and will carry the camming projection 103 into the indentation 102. Thus, due to the fact that the pin 68 on the start lever 99 is riding in the slot 67 of the arm 66 of stop bail 64, the stop bail 64 will rock counterclockwise (FIG. 10) about the pivot shaft 69. As soon as the selector cam sleeve 91 starts to rotate, a start cam 104 in which the identation 102 is formed, in rotating with the cam sleeve 61, will present the high portion of its surface to the camming projection 103 on the arm 66 of stop bail 64. Consequently, the start lever 99, due to its connection with the stop bail 64, cannot move back to engage the armature 96 until the selector cam sleeve 61 has completed one complete revolution at which time the cam projection 103 on the arm 66 will again be aligned with the indentation 102 in the start earn 104.

In addition to the start cam 104 the cam sleeve 61 has on it six selector cams 105, a control cam 106, a stripper earn 107, and a function clutch tripping cam 108. These cams are arranged on the selector cam sleeve 61 as shown in FIG. 5 and these cams are substantially the same as the cams described in detail in the patent to W. J. Zenner, No. 2,595,745, mentioned hereinbefore, and have associated with them various cam levers which are spring urged to engage camrning projections on them with the sur fiace of their respective cams. Each of the selector cams 105 has associated with it, and individual to it, a selector cam lever 109 and each of the selector cams 105 has an indentation or low portion in it into which a carnming projection 110 on the respective selector cam levers 109* may move at predetermined times in the cycle of rotation of the cam sleeve 61. These indentations in the cams for the various selector cam levers 109 are spiralled about the cam sleeve 61 so that the selector cam levers 109 will be permitted to move their respective carnming projections 110 into the indentation in the selector cam; sequentially unless at the time in the cycle of rotation of the cam sleeve 61 that a camming projection 110 is aligned with an indentation in its associated selector cam 105, the armature 96 has been released by the selector magnet coil 91. When the armature has been released, it will block the right end (FIGS. 3 and 10) of the seleot-or or cam levers 109. The selector cam levers 109 have push bar engaging shoulders 112 and 113 formed. on them when the apparatus is in its normal condition a push bar lever 114 will have an edge of it urged into engagement with the push bar engaging shoulder 112 by a contractile spring 115. If, however, in a cycle of operation of the selector cam sleeve, the selector magnet coil 91 is energized at a time when the camming projection of one of the selector cam levers 169 is aligned with an indentation in the selector cam 105, the spring 111 for that particular selector cam lever will be permitted to rock its lever 10'9 counterclockwise (FIG. 3), a sufficient distance to permit the end of the push bar lever 114 to move beneath the end of the selector carn lever 109 and into alignment with the shoulder 113. Thus, when the cam sleeve 61 rotates a small distance from the point where the project-ion 110 entered the indentation in the cam, to move the high portion thereof into engagement with the carnming projection 110, the push bar lever 114 will be pushed downwardly (FIG. 3) against the action of its associated spring 115 which tends to rock it counterclockwise (FIG. 3) and to hold it in its upper position as shown in. the drawings. When any of the push bar levers 114 are permitted to rock counterclockwise, they will engage an edge of a reset bail 116 which at a predetermined time in the cycle of operation of the apparatus will be oscillated in a clockwise direction (FIG. 3) to engage those push bar levers 114 that had been selected and depressed and to rock the levers 114 clockwise (FIG. 3) until the ends of them are disengaged from the shoulder 113 and permit the spring 115 to return those levers 114 which had been depressed, to the position shown in FIG. 3.

Code bar mechanism Each of the push bar levers 114 has associated with it a code transfer arm 117 and these code transfer arms 117 are pivotally mounted on the post 95' and are urged to rock in a clockwise direction (FIG. 3) by contractile springs 118 individual to them. The right. ends (FIG. 3) of all of the code transfer arms 117 are guided for movement in slots in a guide plate 119 which extends across the printer and is suitably supported on guide posts 120 at opposite sides of the apparatus. The guide post at the left side of the apparatus 120 is supported on standards 121 and 122 which extend upwardly from the main supporting plate 48 (FIG. 3) and the post 120 at the right side of the apparatus (FIG. 2) is supported on standards 123 and 124 extending upwardly from the base 21.

The code transfer arms 117 have coded notches and projections 136 formed on them in accordance with a permutation code for selectively controlling the actuation of a series of siX function code bars 137. The function code bars 137 are provided adjacent to their ends with angularly disposed slots 138 (FIG. 15) which slide on reduced portions 139 formed on the posts 120 by cutting annular grooves in the posts to provide guide shoulders 140 as seen more clearly in FIGS. 2 and 3. The function code bars 138 are normally urged upwardly and toward the left side of the printer by contractile springs 141 individual to them but are selectively blocked from moving toward the left side of the apparatus by the projections 136 on the function code bars. The six function code bars 137 toward the front of the machine are individually controlled by the projections 13 6 and notches 135 on the code transfer arms 117 Whereas the seventh function code bar 134 is a print suppression code bar controlled by other function mechanisms. The code bars 134 and 137 control the movement of the various devices in the printing mechanism.

Printing mechanism.

The printing mechanism includes a casting 145 which is movable transversely of the printer on a guide rod 146 and a guide plate 147. The guide rod 146 (FIGS. 2, 3 and 4) is supported on a pair of side plates 148 and 149 (FIG. 4) formed integrally with the base 21 and the guide plate 147 is supported on the main support plate 48 and on a support bracket 150 (FIG. 1) extending upwardly from the base 21. The casting 145 (FIG. 7) has a. grooved guide roller 151 and a flat guide roller 152 rotatably mounted on an extension 153 of the casting 145 and a matching pair of grooved and flat guide rollers 154 and 155 on an extension 156 at the opposite side of the casting 145. These rollers roll on the guide rod 146 and.

cooperate with a pair of flat guide rollers 176 and 157 which ride upon the edges of the guide plate 147 to guide: the printing carriage which includes the casting in. its travel across the printer.

Mounted upon an upper surface of the casting 145 is a: stop plate 158 (FIGS. 7 and 8) which has its ends bent upwardly to provide vertically extending portions 159 and 160 for supporting a floating guide member 161- This floating guide member 161 has a reduced rear end portion 162 which extends through an aperture 163, in: the vertically extending portion 159, that will permit a slight amount of rocking and reciprocation of the floating guide member 161 with respect to the stop plate 158. The floating guide member 161 has a plurality of slots 163 cut in its opposite edges for guiding the upper, blfllb: cated end portions of four slides 164, 165, 166 and 167 for vertical movement with respect to the guide member: 161.

The front vertically extending portion 160 of the stop plate 158 has an opening as shown at 168 (FIG. 0),. formed in it to permit the front end of the floating guide member 161 to extend through it. The guide member" 161 is normally urged upwardly toward the upper edgeof the opening 168, so that, if the slide 164 is moved upwardly a sufficient distance to move the edges 169 of formed-over portions 170 of the slide 164 past a pair of lips 171 formed on the stop plate 158, the floating guide member 161 will be latched in its rearward position by a shoulder 172 formed on it engaging the rear edge of the vertical extending portion 160. A coiled spring urges the front end of the floating guide member 161 upwardly and a coiled compression spring 173 urges the floating guide member 161 toward the front of the printer, being interposed between the inner surface of the vertically extending portion 159 and a surface 174 of the floating guide member 161.

A support plate 181 (FIGS. 2 and 8) is fixed to the underside of the casting 145 and has the shafts for the rollers 176 and 157 mounted on it. This support plate 181 serves to guide four slides 182, 183, 184 and 135 which cooperate with the slides 164, 165, 166 and 167 n controlling the selection of type on a type wheel 186 in printing operations. The slides 164, 165 and 166 extend through an opening 187, in the support plate 181, which has its sides slotted to guide the slides 182, 183, 184 and 105. Each of the slides 164, 165, 166, 182, 183, 184 and 185 has a slot 178 formed in its lower end into which a guide post 179 extends to guide the lower ends of these slides. The guide post 179 is mounted on vertically extending portion of the support plate 181.

As shown in FIG. 8 the type wheel 186 is cylindrical and has type on its outer face, which type, as indicated by the two rows 138 and 189, are arranged in four levels and the figures and letters characters are in alternate rows. The type wheel 186 is mounted on a shaft 190 which is in turn fixed to a three-armed plate or spider 191 that is slidably mounted on three posts 192 (FIGS. 8 and 9) forming part of a cage-like structure which includes top and bottom annular plates 193 and 194. The posts 192 are fixed to the plates 193 and 194- and the upper plate 193 is suitably fixed to a bearing ring 195 which is rotatably mounted in a bearing 196 formed in the casting 145. An annular gear 197 is fixed to the bearing ring 195 and serves to impart oscillation to the cage-like structure when driven by either one of a pair of racks 198 and 199. The central openings in the annular plates 193 and 194, and in the annular gear 197 and bearing ring 195 are. all appreciably larger than the outside diameter of the shaft 190 so that the shaft 190 may be rocked to a limited extent without engaging the upper edge of the opening in the annular gear 197.

The lower end of the shaft 190 (FIG. 8) is articulated to the upper end of a push rod 200 which has its lower end pivotally connected to an actuator lever 201 that "is oscillatably mounted on a pivot post 202. The pivot post 202 is fixed in downwardly projecting slide plates .203 and 204 formed on the casting 145. The pivot post :202 also pivotally supports a main rocker member 205 and a rack driving lever 206. The main rocker member .205 (FIG. 2) has a pair of horizontally extending plates 207 and 208 formed adjacent to its lower end for rotatably supporting a pair of rocker rollers 209 and 210, Iespectively.

When the casting 145 is moved transversely of the printenthe rollers 209 and 210 will ride along a main oscillating bail 211 which will serve to rock the main rocker member 205 at any position the casting 145 may assume. The main oscillating bail 211 is pivoted for oscillation on a pair of stud shafts 212 and 213 (FIG. 4) fixed in the side plate 148 and in a standard 214, respectively. Power for oscillating the main oscillating bail .211 is supplied through a main oscillating link 215 (FIG. 2) connected to a pivot pin 216 that is mounted in a bracket 217 (FIG. 4) attached to the underside of the main oscillating bail 211.

The main oscillating link 215 extends toward the rear of the apparatus and has an eccentric collar 227 (FIG. 5) formed on it which encircles an eccentric 228 on a scam sleeve 229 that will be driven through one complete revolution each time the clutch 41 is tripped. Thus, each time the clutch 41 is tripped the main oscillating bail 211 will be oscillated through one complete cycle, first moving counterclockwise from the position shown :in FIG. 2 and then returning to that position to rock the :main rocker member 205 about the pivot post 202.

The main rocker member 205 (FIGS. 2 and 8), has a. Iearwardly extending arm 230 which carries an adjustable eccentric 231 adjacent to its free end for driving engagement with the upper edge of the actuator lever 201. Intermediate the free end of the arm 230 and the pivot post 202, the arm 230 has a tab 232 formed on it (FIG. 8) to which one end of a contractile spring 233 is attached. The other end of the spring 233 is attached to :a tab 234 formed on the actuator lever 201. With this arrangement the actuator lever 201 is positively rocked in a clockwise direction (FIGS. 2 and 8) by the main rocker lernber 205 and is resiliently urged to follow the memher 205 when that member is rocked counterclockwise.

The extent to which the actuator lever 201 is permitted to follow the main rocker member 205 when the main rocker member 205 rocks counterclockwise (FIG. 8) ionay be limited by the ends of three bell crank levers 235, 236, 237 and consequently, the height to which the push rod 200 and the type wheel 186 are moved will be contrplled by the lower ends, of the three bell crank levers 255, 236 and 237. The bell crank levers 235, 236 and 237 are controlled by the slides 184 and 185 which determine the extent of movement of the type wheel 186 in accordance with the signal received in the selector mechanism 31. The slides 164, 165, 166, 182, 184 and 185 have, suitably attached to their lower ends, slotted members 238 which ride on the function code bars 137. Consequently, when any one of the function code bars 137 is permitted to move upwardly and to the left (FIGS. 5 and 15) by the code transfer arms 117, it will lift its associated slide with it. The function code bar 134 associated with the slide 182 controls print suppression the function code bar 137 associated with the slide 164 controls the shift or figures function. The next two function code bars toward the front of the printer control the extent of rotation of the type wheel, the function code bar 137 associated with the slide 183 controls the direction in which the type wheel 186 will be rotated and the function code bars 137 associated with the slides 184 and 185 control the extent to which type wheel 186 will be elevated.

The bell crank levers 235, 236, 237 and a direction controlling lever 239 are pivoted on a shaft 240 which- 9 is carried in a pair of downwardly extending side members 241 and 242 formed on the plate 181.

The substantially horizontally extending arm of bell crank lever 235 extends into an L-shaped slot 220 in the slide 185 (FIGS. 18 and 18A). Consequently, when the slide 185 is moved upwardly by its associated function code bar 137, the bell crank 235 will be rocked counterclockwise (FIG. 8) from the position shown in the drawing. The bell crank lever 237 has its horizontally extending arm extending into the L-shaped slot 220 and into a rectangular slot 221 in the slide 184 and in the slide 185, respectively, and consequently when either the slide 184 or the slide 185 is moved upwardly, the bell crank lever 237 will be rocked counterclockwise (FIG. 8). The bell crank lever 236 extends freely through the slot 220 in slide 185 and into an actuating relation to the slot 221 in slide 184. Consequently, when the slide 184 moves upwardly, the bell cranks 235 and 236 will be rocked counterclockwise (FIG. 8). Thus, if either the slide 184 or 135 or both of them are moved upwardly, the bell crank lever 237 will be rocked counterclockwise out of the path of the laterally extending projection 243 on the actuator lever 201.

If neither of the slides 184 or 185 is moved upwardly by its associated function code bar 137, the projection 243 on lever 201 will strike the bottom edge of the bell crank 237 to stop the upward movement of the lever 201 and will thereby, through the push rod 200 raise the type wheel 186 to a position where the upper level of it will be in alignment with the printing position. If the slide 185 is moved upwardly by its associated code bar 137 and the slide 184 is not moved upwardly by its associated function code bar, the bell crank levers 235 and 237 will be rocked counterclockwise (FIG. 8) about the shaft 240, but the bell crank 236 will not be so rocked and consequently the projection 243 on lever 201 will strike the lower edge of the bell crank lever 236 to stop the type wheel 186 with the second level of type from the top in printing position. If the slide 184 is moved upwardly and the slide 185 is not moved upwardly by their associated function code bars 137, the bell crank levers 236 and 237 will be rocked counterclockwise (FIG. 8) about the shaft 240 but the bell crank lever 235 will not be so rocked and the projection 243 will be permitted to move up until it engages the bottom edge of the bell crank lever 235 thereby to raise the type wheel 186 to a position to carry the third level from the top of it into printing position. If both of the slides 184 and 185 are moved upwardly by their associated function and code bars 137 all three bell cranks 235, 236 and 237 will be moved to position to carry the lower edges of them out of the path of the projection 243 on lever 201 which will consequent- 1y move the type wheel 186 to the uppermost position where the bottom level of it will be in printing position.

As pointed out hereinbefore the slide 183 (FIGS. 8 and 17) controls the direction in which the type wheel 186 will be rotated and when the slide 183 is moved upwardly by its associated function code bar 137, it will rock the direction controlling lever 239 about the shaft 240 in a counterclockwise direction. The direction controlling lever 239 has a link 244 pivotally connected to it and the upper end of the link 244 is pivotally connected to a pull bar 245 that is pivoted on a pivot shaft 246. The pull bar 245 has a pair of driving tabs 247 and 248 formed on its right end (FIGS. 7 and 8) for selective engagement with shoulders 249 and 250, respectively, on the pair of racks 199 and 198, respectively. When the link 244 and consequently the pull bar 245 is in the position shown in FIGS. 7 and 8, the tab 248 will be aligned with the shoulder 250 on rack 198. If the slide 183 is moved upwardly by its associated function bar 137, the direction controlling lever 239 will be rocked counterclockwise (FIG. 8) about the shaft 240 and will pull the link 244 and the right end of the pull bar 245 downwardly to align the tab 247 with the shoulder 249 on rack 199.

The shaft 246 (FIG. 8) is mounted at the upper end of the rack driving lever 206 and the rack driving lever 206 is urged to follow the movement of the main rocker 205 by a contractile spring 253 that is attached to the horizontally extending arm of the lever 206 and to a transversely extending portion 254 of the main rocker member 205. The transversely extending portion 254 of the member 205 has threaded into it an adjustment screw 255 which engages a bent-over portion 256 of the lever 206 to restrict the movement of the lever 206 in a counterclockwise direction (FIG. 8).

The racks 198 and 199 are slidably mounted on the upper surface of a ribbon support plate 263 which has four shouldered buttons 264 fixed to it for supporting and guiding the racks while holding both of them in engagement with the teeth of the annular gear 1.97. From the foregoing it is believed to be apparent that upon oscillation of the rack driving lever 206 in a counterclockwise direction (FIG. 8) either the rack 198 or the rack 199 will be pulled toward the front of the machine depending upon the position to which the pull bar 245 has been rocked by the link 244 to position either the tab 247 or the tab 248 in operative association with either the shoulder 249 or the shoulder 250, respectively. When one of the racks 198 or 199 is moved toward the front of the printer, the other rack, of course, will be forced to move toward the rear of the printer due to the engagement of both racks with annular gear 197.

The pivot shaft 246 also has mounted on it a pair of rack restoring members 265 and 266 which engage the left ends (FIG. 7) of the racks 199 and 198, resepectively, to push a rack which has been drawn back by the pull bar 245 into the position shown in FIG. 7. These rack restoring members 265 and 266 are loosely pivoted on the shaft 246 and have their rack engaging ends concavely rounded so that they will center themselves properly on a rack which has been pulled forward by the pull bar 245 and as the rack driving lever 206 rocks clockwise (FIG. 8), the rack restoring member 265 or 266 which engages its rack will push the rack to the position shown in FIG. 7. As pointed out hereinbefore the rack driving lever 206 is resiliently urged to move with the main rocker member 205 by the spring 253 and when the rack driving lever 206 is moved counterclockwise about the pivot post 202 (FIG. 8) it will resiliently urge one or the other of the racks 198 or 199 to move to the left (FIG. 7) thereby to move the other rack to the right. The rack which is drawn toward the front of the printer by the pull bar 245 will move the other rack toward the rear of the printer until the rack is stopped by its right end (FIG. 8) contracting one or the other of the slides 167, 166, or 164.

The slides 164, 165, 166 and 167 operate under control of the function code bars 137, the slides 164, 165 and 166 being directly actuated by the function code bars 137 and the slide 167 being jointly controlled by the two slides 165 and 166. It will be understood that in the operation of the apparatus the slides 164, 165, 166, 167, 183, 184 and 185 are selectively raised by their associated function code bars 137 at a time in the cycle of operation of printer prior to the time when the main rocker member 205 is rocked in a counterclockwise direction by the main oscillating bail 211.

As pointed out hereinoefore the direction in which the type Wheel 186 is to be rotated is selected under control of the slide 183 operating in conjunction with the pull bar 245. The amount of rotation imparted to the type Wheel 186 is controlled by the function code bars 137 associated with the slides 164, 165, and 166. If the signal received in the selector mechanism 31 is such that a figures character rather than a letters character is to be printed by the type wheel, the slide 164 will be pushed upwardly by its associated function code bar 137 and in being pushed upwardly will move the edge 169 of the formed-over portion on the slide 164 above the lip 171 of the stop plate 158. Then, when the rack 198 or 199 which has been selected to move toward the right (FIGS. 7 and 8) contacts any one of the slides 167, 166, 165 or 164, it will move the floating guide member 161 a short distance until the right side (FIG. 8) of the slide 164 engages the left face of the lip 171, thus, to rotate the type wheel 186 one increment of rotary movement to present the figures character to printing position. If, however, the slide 164 is not moved upwardly by its associated function code 137 but any one of the code bars 165, 166 or 167 is moved upwardly by its associated function code bar 137, the selected rack 198 or 199 which is moved toward the slides 164 to 167, inclusive, will rotate the type wheel 186 in two-row increments.

If in the reception of a message by the printer, a signal is [received in the selector mechanism 31 which results in either the slide 165 or the slide 166 being moved upwardly, then the slide 167 will also be moved upwardly since the slides 165 and 166 are provided with shoulders 268 and 269, respectively, which are aligned with horizontally extending arms 278 and 271 formed on the slide 167. The slide 167 is urged downwardly to the position shown in FIG. 8 by a contractile spring 272 but, as pointed out, will be moved upwardly when either the slide 165 or the slide 166 is raised by its associated function code bar 137. When either the slide 165 or the slide 166 is moved upwardly and as a result carries with it the slide 167, the slide 167 will be carried to a position where the end of the rack 198 or 199 which has been selected for movement toward the slides 164 to 167 will pass under a shoulder 273 on the slide 167, The slides 165 and 166 also have shoulders 273 formed on them which may be raised above the level of the racks 198 and 199 and in the event that both slide 165 and slide 166 are raised and carry with them slide 167, the rack moving toward the slides will move all the way over and engage the slide 164.

From the foregoing it is believed to be apparent that the type wheel 186 may bemanipulated to place any one of 64 different discrete areas on it to a printing position. This is effected by selecting any one of the four levels of the type Wheel 186 under control of the slides 184 and 185, selecting the direction of rotation of the type wheel under control of the slide 183 thereby to present either one-half or the other half of the wheel 186 to printing position, and by selecting either the letters or figures characters under control of the slide 164 and then selecting from the four rows of figures characters or four rows of letters characters one discrete row under control of the slides 165 and 166.

After the type wheel 186 is operated to position a specific type on it at the printing position, the type wheel 186, shaft 190 and spider 191 must be rocked to move the type wheel 186 toward a platen 271 (FIGS. 1 and 2) in order to drive a ribbon 272 against a web of paper on the platen. The ribbon which is of the usual type is fed from one of a pair of reversible spools 273 and 274 to the other spool as is usual in such printing mechanisms as that presently being described. The ribbon 272 in moving from one to the other of the pair of spools 273 and 274 is guided in the path of the type wheel 186 by a pair of ribbon guides 275 (FIG. 1) which are mounted on a ribbon guide plate 276. In order that an operator may read the complete line which has last been typed on a sheet of paper on the platen 271, the type Wheel 186 is moved down by the actuator lever 201 to a point below the last line printed on the tape and since the ribbon 272 would obscure a portion of the message printed on the paper it too is moved downwardly. In order to accomplish this result the ribbon guide plate 276 is slidably mounted on a pair of posts 27 7 (FIGS. 2 and 7) that are mounted on the ribbon support plate 263. The ribbon guide plate 276 has upwardly extending arms 278 formed on it, the tops of which are bent inwardly to form bearings 279 through which the posts 277 extend thereby to insure that the ribbon guide plate 276 will travel in a straight line path when it is reciprocated. The plate 276 is normally urged upwardly against a shoulder 280 on the shaft 196, by springs 281 that encircle the posts 277 and engage the top of the ribbon support plate and the underside of the ribbon guide plate 276. Upward movement of the ribbon guide plate 276 is limited by a snap-on type collar 282 fixed to the posts 277 adjacent to their upper ends thereby to block the movement of the ribbon guide plate 276 upwardly beyond a predetermined point under the influence of springs 281.

When the type wheel 186 is moved to its lowermost position as shown in FIG. 8 the collar or shoulder 280 on the shaft 190 will engage with the upper surface of the ribbon guide plate 276 to move the ribbon guide plate 276 downwardly against the action of the springs 281. The shaft 190 extends through a slot 283 (FIG. 7) formed in the ribbon guide plate 276. a width that it is just slightly larger than the diameter of the shaft 199 thereby serving to restrict the shaft 190 from rocking transversely of the machine while permitting it to oscillate longitudinally of the machine in the direction of the arrows 284 (FIG. 8). A downwardly projecting arm 285 of the ribbon guide plate 276 has a hori- Zontally extending lip 286 formed on it for engagement with the upper surface of the left-end of FIG. 8 of the floating guide member 161 whereby, when the type wheel is retracted to its lowermost position, the lip on the arm 285 will push the left end of the floating guide member 161 downwardly to release the shoulder 172 from the edge of the vertically extending portion 160 of the stop plate 158.

In addition to supporting the ribbon 272 and thetwo spools 273 and 274, the ribbon support plate 263 also supports a ribbon feeding mechanism which is of the same general type as that shown in the patent to R. E. Arko et al., No. 2,951,902, issued September 6, 1960. The details of construction of this ribbon feeding mechanism are not pertinent to the present invention and consequently will not be described in detail, it being suflicient to say that the ribbon is moved one increment of movement each time the main rocker member 205 is oscillated due to the fact that a ribbon feed lever 291 (FIG. 3), which is fixed to the main rocker member 205, engages and actuates a feed pawl reciprocating lever 292.

In each cycle of operation of the printer, after the type wheel 186 has been positioned to align a specific type on it in printing position, a print hammer 293 will drive the type wheel 186 into engagement with the ribbon 272 and carry the ribbon over to print a character on a sheet or web of paper on the platen 271. The details of construction and mode of operation of the hammer 293 are disclosed and claimed in the copending application of N. A. Jacobs, Serial No. 159,327, filed December 14, 1961. As may be seen most clearly in FIG. 2 and FIG. 19, the print hammer 293 is mounted at the free end of a hammer supporting bail 294. The bail 294 is osc-illatable about a shaft 295 that is supported in a pair of upwardly extending bearing arms 296 and 297 which are formed upwardly from the ribbon supporting plate 263. The righthand leg of the bail 294 (FIG. 19) has formed integrally with it a latch plate 298 which has on it a pivot stud 299. The hammer supporting bail 294 is urged to rock in a clockwise direction (FIG. 2), by a coiled spring 381) which encircles the shaft 295 and has one of its ends bearing against the side of the bearing arm 296 and has its other end 302 extending upwardly to engage with the web of the bail 294. The end 302 of the coiled spring 300 is also bent over to strike against an edge of the bearing arm 297 whereby when the bail is rocked clockwise (FIG. 2) by the coiled spring 300, the end 382 of the coiled spring 300 will first move the bail 294 in a clockwise direction and then the upper extremity of the end 302 will strike the arm 297 permitting the bail 294 to be thrown in a clockwise direction beyond the distance which the spring forces it to move, thus to impart an overthrow motion to the bail and consequently to the printing hammer 293.

This slot 283 is of such A print bail actuating link 303 (FIG. 2) has its left end pivotally attached to a post 304 mounted on the main rocker member 205 and has its right end slotted as shown at 305 whereby, when the main rocker member 205 is oscillated, the print bail actuating link 303 will rock the hammer supporting bail 294 in a counterclockwise direction against the action of the spring 300 due to the engagement of the base of the slot 305 with the pivot stud 299. When the main rocker bail 205 is rocked in a clockwise direction (FIG. 2), to the position shown in FIG. 2, the print bail actuating link 303 Will rock the hammer sup porting bail 294 in a counterclockwise direction (FIG. 2), against the action of the spring 300 to a position as shown in FIG. 2. A latching shoulder 306 on the latch plate 298 will latch the bail 294 in the position shown in FIG. 2 by moving under a latching edge 307 formed on a latch lever 308. The latch lever 308 is pivoted on the shaft 240 and is normally urged to rock in a clockwise direction (FIG. 2), about the shaft 240 by a spring 309.

In the normal position of the apparatus, the main rocker member 205 will be in the position shown in FIG. 2 where the latching lever 308 will have its latching edge 307 in engagement with the latching shoulder 306 on the latch plate 298 of bail 294. As soon as the main oscillating bail 211 begins to rock the main rocker member 205 counterclockwise (FIG. 2) the print bail actuating link 303 will move with the main rocker member 205 but the latching edge 307 will prevent the hammer sup porting bail 294 from rocking clockwise (FIG. 2). As the main rocker member 205 approaches the end of its oscillation in a counterclockwise direction (FIG. 2) a bent over portion 310 of the link 303 will engage the edge 307 of the latching lever 308 to disengage the edge 307 from the latching shoulder 306 of the latch plate 298, thus to permit the coil spring 300 to snap the print hammer supporting bail 294 in a clockwise direction (FIG. 2). This will effect the actuation of the type wheel 180 unless print suppression is called for because of the receipt in the selector mechanism 31 of a signal calling for a function other than printing.

If printing is to be effected, the print suppression function code bar 187 will be permitted to move upwardly under the influence of its associated spring 141 thereby to raise the slide 182 associated with it. The slide 182 has a projection 311 formed on it (FIGS. 2 and 8), which is entered into the bifurcated end of a print suppression bell crank lever 312 that, as shown in FIG. 2, is directly behind the latch lever 303 and that has a laterally ex tending latching portion 313 formed on it. If a signal is received in the selector mechanism 31 which calls for a function other than a printing function the print suppression function code bar 137 will not move upwardly, the bell crank lever 312 will not be rocked counterclockwise (FIG. 2) and the laterally extending latching portion 313 of the bell crank lever 312 will be engaged by the latching shoulder 306 on the latch plate 2% even though the latch lever 308 is rocked out of latching engagement with the shoulder 306. Thus, printing will be suppressed unless a signal is received in the selector mechanism which calls for a printing function.

Function mechanisms-general Power for effecting the functions of the apparatus, such, for example, as the line feeding function, carriage return function, and spacing function is supplied by a rocker shaft 325 (FIGS. 2 and which is mounted for oscillation in the main support plate 48 and in the support bracket 150 (FIG. 1) which is adjacent to the right side of the apparatus. This rocker shaft 325 is driven by an eccentric ring 326 on an eccentric 327 (FIG. 5). The eccentric 327 is fixed to the cam sleeve 229 and consequently whenever the clutch 41 is tripped, the eccentric 327 will impart reciprocation to the eccentric ring 326 (FIG. 11) which has an extension on it pivotally connected to a rock lever 328 fixed on the shaft 325 by 14 means of a collar 329. Adjacent to the opposite ends of the shaft 325 there are collars 330 fixed to it which have levers 331 (FIGS. 2 and 5), fixed to them. The forwardly extending ends of the levers 331 have links 332 pivotally attached to them and to function drive levers 333 which are pivoted on a shaft 334.

The shaft 334 extends substantially all the way across the printer and, in addition to pivotally supporting the function drive lever 333, also pivotally supports a line feed function lever 335, an automatic line feed function lever 336, a carriage return function lever 337, a carriage return actuating function lever 333, a space function lever 339, a letters function lever 340, a figures function lever 342, and a blank function lever 343. The function drive levers 333 have inwardly extending arms 344 formed on them to which there is attached a stripper bail 345 that extends over the upper surface of all of the function levers 335 to 341, inclusive, and 342 and 343. Thus, when the function drive levers 333 are rocked in a clockwise direction (FIG. 2) they will rock the bail 345 downwardly.

The function code bars 137 and the print suppression code bar 134 are normally urged upwardly to the left by their associated springs 141 and they are restored to their normal unoperated position, as illustrated in the drawings, by a restoring bail 350 (FIGS. 2, 4, 5 and 15), which is pivotally mounted on a pivot shaft 351 fixed to the standards 24 and 25. The bail 350, at a predetermined time in the cycle of the operation of the printer is rocked in a clockwise direction (FIG. 4), to engage its web portion 352 with cam surfaces 353 formed on the underside of each of the function code bars 137 and the print suppression code bar 134. The bail 350 has an arm 354 (FIGS. 2 and 5) positioned in the path of a cam roller 355 mounted on the free end of a cam lever 356. The cam lever 356 has a hub portion 357 which is freely rotatable on the rocker shaft 325 and the cam lever 356 has associated with it a cam lever 358 which is pinned to the cam lever 356 by means of pin 359 so that the two levers 356 and 358 will oscillate about the cam shaft 325 as a unit. The cam lever 358 has a cam roller 360 at its upper end which bears against a cam 361 on a cam sleeve 362. The cam sleeve 362 is mounted on the main power shaft 39 and may be connected thereto upon the tripping of the clutch 42 which as pointed out hereinbefore is of the type shown and claimed in the patent to A. N. Nilsen et 211., 2,568,249, issued September 18, 1951.

The tripping of the clutch 42 (FIG. 5) is controlled by the function clutch trip cam 108 on the selector cam sleeve 61. A cam follower lever 370 rides the function clutch trip cam 108 and is mounted on a function clutch shaft 371 to which the lever 370 is fixed by means of a collar 372 whereby when the high point of the function clutch trip cam 108 engages the cam follower lever 370 oscillation will be imparted to the function clutch shaft 371. The function clutch shaft 371 is mounted in a pair of bearings 373 mounted in a pair of brackets 374 (FIGS. 1, 2 and 5). One of the brackets 374 is mounted on the main support plate 48 at the left side of the printer and the other bracket 374 is mounted on the hearing plate 49 at the right side of the printer. The function clutch shaft 371 has fixed to it a clutch stop lever 375 (FIGS. 5 and 16), which is normally in a position such that the end portion 376 thereof will engage a stop projection of a clutch shoe lever 377 to hold the clutch 42 disengaged thereby to maintain the cam sleeve 362 stationary on the shaft 39. A clutch latch lever 378 is spring biased to effect the operation of the clutch in the manner described in connection with the selector clutch 40. When the shaft 371 rotates in a counterclockwise direction (FIG. 16), by the function clutch trip cam 108, it will rock the end portion 376 of the clutch stop lever 375 out of the path of the stop projection 377 thus to trip the clutch 42 and connect the cam sleeve 362 to the shaft 39 for one cycle of rotation.

As the cam sleeve 362 is rotated through one complete cycle of rotation, it will effect the oscillation of the restoring bail 35b andin addition will effect the tripping of clutch 41. The cam sleeve 362 has a cam 379 (FIG. 5), formed on it for cooperation with a cam roller 33% which is mounted on the free end of a cam lever 381. The cam lever 381 is fixed to a sleeve 382 that is freely rotatable on the shaft 371 and that also has fixed to it a function clutch tripping lever 383 which has a projecting portion 384 for engagement with a stop projection 385 of the clutch shoe lever of the clutch til. When the cam roller 38% engages a high portion of the earn 379, it will rock the cam lever 381 and the function clutch tripping lever 383 to move the projecting portion 384 of the lever 383 out of the path of the stop projection 385 of the clutch 41 thus to release the clutch 41 to drive the cam sleeve 229 through one cycle of rotation.

In addition to the eccentrics 223 and 327, the cam sleeve 391 has associated with it a cam roller 393 which is mounted on the end of a bell crank lever 394. The bell crank lever 394- is oscillatably mounted on a pivot shaft 395 (FIGS. 2, ll, 12 and 13) which is in turn supported in a slotted casting 3% that is suitably secured to the support plate 48 and the support plate 15% by machine screws such as the machine screws 327 (PEG. 1). The vertically extending arm of the bell crank 394 has a function pawl restoring bail 398 attached to it for unlatching function pawls from their respective function levers. For example, as shown in FIG. 11, a function pawl 399 will be unlatched from the letters function ever 340 when the bail 398 is rocked in a clockwise direction. The slotted casting 3% has a pair of transversly extending web portions 400 and 401 (FIG. 11), and two slotted portions 402 and 403 formed on it. The slotted portion. 4% of the casting 3% extends in a hori- Zontal direction and serves to guide the upper ends of the various function pawls whereas the slotted portion 4% extends diagonally downwardly and in addition to serving to guide the lower ends of the various function pawls also serves to guide the function levers which extend into the slots in it.

Line feed function.

All of the function levers 335, 336, 337, 33%, 33-9, 3%, 342 and 343 are individually urged to follow the movement of the stripper bail 34S and to rock about the shaft 334 by coil springs 41th, as best seen in FIG. 5. These coil springs 41th are attached to the individual function levers and have their upper ends attached to a bracket 411 which is mounted on the stripper bail 345. Thus, the function levers are all urged to follow the movements of the stripper bail 345.

When a signal is received in the selector mechanism 31 which calls for the performance of one of the various functions of the apparatus, the function code bars 137 will be set in a position to permit the function lever for that particular function to be moved upwardly as viewed in FIG. 5 due to the arrangement of projections or wards and notches on the underside of the respective function code bars 137. Thus, any function lever which is selected for operation under control of the function code bars 137 will follow the movements of the stripper bail 345.

If the signal received in the selector mechanism 31 calls for a line feeding operation, the line feed function lever 335 will be permitted to follow the movement of the stripper bail 345 and in so doing will rock in a counterclockwise direction (FIG. 12) about the shaft 334. In rocking counterclockwise about the shaft 334 the line feed function lever 335 will rotate a line feed blocking lever 412 about a pivot shaft 4-13 by engagin a laterally extending arm 414- on the line feed blocking lever 412. The shaft 413 is mounted on a pair of standards 415 and 416 (FIG. 5) which extend upwardly from the base 21. When the line feed blocking lever 412 is rocked in a counterclockwise direction (FIG. 12), a shoulder 4-17 on it will be disengaged from a laterally extendingprojection 418 on a line feed drive link 419. The line feed blocking lever 412 is normally urged to rock in a clockwise direction (FIG. 12) about the pivot shaft 413 by a contractile spring 420 and consequently when the line feed blocking lever 412 is rocked counterclockwise by the line feed function lever 335 and later the line feed function lever 335 is rocked in a clockwise direction about the pivot shaft 33 the lower edge of the line feed blocking lever 412 will come to rest on the laterally extending projection 418 of the line feed drive link 419. The line feed drive link 419 is urged to move upwardly by a contractile spring 422 and is urged to rock in a clockwise direction about a pivot stud 423 by a contractile spring 424-.

When the line feed drive link 419 is released by the line feed blocking lever 412, a notch 425 on it will, when the rocker shaft 325 approaches its extreme point of oscillation in a clockwise direction (PEG. 12), move into reg istry with a drive pin 426 on a lever arm 427 so that when the rocker shaft 325 begins its movement in a counterclockwise direction the notch 425 will catch under the pin 42a; and the link 4119 will be moved downwardly against the action of its spring 422. The upper end of the link 419 is attached to a bell crank lever 423 by means of the stud 423. This bell crank lever 428 is pivotally mounted on a stud shaft 429 which is in turn fixed to a bracket 439 (FIG. 2) that extends toward the front of the machine from a main cross plate 431. As may be best seen in FIGS. 2 and 4, the main cross plate 431 extends substantially all the way'across the printer and is mounted between a pair of platen supporting plates 432 and 433. The platen supporting plates 432 and 433 are in turn mounted on brackets 434 and 435, respectively, which are supported on the standards 22 and 23 and on the side plate 149. The bell crank lever 423 (FIG. 12) has a pin 436 mounted on it which is entered into the bifurcated end of a lever 437 fixed to a sleeve 438 (FIG. 4) that is pivoted on a shaft 439 which extends inwardly from the platen supporting plate 432. The sleeve 438 has a driving lever 440 fixed to it at the end. of which there is pivotally mounted a drive pawl 441.

The drive pawl 441 is normally urged to rock in a counterclockwise direction about its pivot by a coiled spring 442 which is stretched between a projection on the pawl 441 and projection on the lever 440 to urge the pawl 44-1 to engage with teeth on a platen roll 445; In the position shown in FIG. 12, the pawl 441 has been cammed out of engagement with the teeth on platen roll 443 by a post 444 which extends into the path of the upper end of the pawl 441. Thus, when the link 4-19 is drawn downwardly, it will rock the bell crank lever 428 in a clockwise direction (FIG. 12) thereby to impart counterclockwise rotation to the driving member 448 to engage the pawl 44! with the teeth on the platen roll 4-43 to drive the platen roll in a clockwise direction (FIG. 12). The platen roll 443 is journalled in the platen supporting plates 432 and 433 and carries the platen 271 about which a web of paper may be guided by a guide plate 445 and presser members 446. The guide plate 445 is fixed in position between the platen supporting plates 432 and 433 and the presser members are mounted on a bail 447 which is urged to hold the members 446 in engagement with paper on the platen 271 by a coiled spring 448.

When the function pawl restoring bail 3% is rocked in a counterclockwise direction (FIG. 12), it will rock a function pawl 4S1 (FIGS. 12 and 14) counterclockwise (FIG. 12) about the pivot shaft 395. The function pawl 451 is urged to rock toward the front of the printer by a coiled spring 452 (FIG. 14) (clockwise FIG. 12) but when it is driven in a counterclockwise direction (FIG. 12), it will carry a laterally extending portion 453 on it into engagement with an upwardly projecting portion of an arm 454 on the link are to disengage the pin 426 from the notch 425 on the link 419 thereby to permit the line feed blocking lever 412 to relatch the link 419 in its normal position.

Spacing function- The type wheel positioning mechanism 34 on the casting 145 is moved step-by-step across the printer to associate the type wheel 186 with successive areas of a web of paper on the platen 271. In order to accomplish this movement the entire casting 145 is, as pointed out hereinbefore, supported on the guide rod 146 and drive plate 147. The casting 145 is stepped across the platen 271 by an endless belt 460 which has teeth 461 formed on it for driving engagement with a toothed roller 462. The toothed roller 462 is mounted at the upper end of a shaft 463 at the left side of the apparatus (FIG. 4). A guide roller 464 mounted on a bracket 465, which is in turn mounted on the side plate 148, cooperates with the toothed roller 462 to guide the endless belt 460 in its movement. The inner course of the endless belt 460 is suitably attached to the casting 145 and as the endless belt 460 is moved step-by-step it will carry the casting 145 and the mechanisms supported theron across the platen 271. The lower end of the shaft 463 has fixed to it a ratchet 466 which may be driven step-by-step in a clockwise direction (FIG. by a driving pawl 467 and will be held in a position to which it is rotated by a detent pawl 468 (FIGS. 4 and 5).

The driving pawl 467 is pivoted on a pivot stud 469 which is fixed on a link 470 that is in turn pivotally mounted on a pivot pin 471. The driving pawl 467 and the link 470 thus form a toggle which is urged to break toward the rear of the printer by a contractile spring 472 which is attached to the driving pawl 467 and urges the link 470 to follow an actuator roller 473. The detent pawl 468 is also pivoted on the pivot pin 471 and is urged to rock in a clockwise direction (FIG. 5) by a contractile spring 474 which resiliently holds the detent pawl 468 in engagement with the ratchet 466. A bell crank lever 475 is also pivoted on the pivot stud 471 and upon oscillation in a clockwise direction (FIG. 5) will rock a space blocking lever 476 in a counterclockwise direction (FIG. 5) about an adjustable pivot 477 to carry a blocking shoulder 478 on the space blocking lever out of the path of a downwardly extending arm 479 of the driving pawl 467. A pawl release lever 480 is also pivoted on the pivot stud 471 and has a pawl release arm 481 on it for stripping both the driving pawl 467 and the detent pawl 468 out of engagement with the teeth of the ratchet 466 when the pawl release lever 480 is rocked in a counterclockwise direction (FIG. 5) about the pivot stud 471.

When both the driving pawl 467 and the detent pawl 468 are moved out of engagement with the teeth of the ratchet 466, a coiled spring 488 (FIG. 4) will return the casting 145 to the left side of the apparatus. The spring 488 is atached to a stud 489 extending downwardly from the casting 145 and to a post 490 (FIG. 3) suitably fixed on an upstanding portion of the main support plate 48. The upper course of the coiled spring 483 is attached to the stud 489 and the lower course is attached to the post 499. Intermediate the two courses of the coiled spring, it passes around a guide roller 491 that is freely rotatable about a stud shaft 492 fixed in an upstanding portion of the base casting 21. The stud shaft 492 also supports a space function restoring lever 493 (FIGS. 3, 4 and 5) which is urged to rock clockwise about the shaft 492 (FIG. 4) by a contractile spring 494. The lower end of the space function restoring lever 493 is bifurcated to receive the free end of a latch lever 495 (FIG. 5) which is oscillatably mounted on the shaft 463. The latch lever 495 is thus biased by the space function restoring lever 493 to rotate about the shaft 463 in a counterclockwise direction (FIG. 5) to carry a shoulder 496 on it into blocking relation with a downwardly extending arm 497 of the pawl release lever 480. Thus when the pawl .release lever 480 is rocked counterclockwise (FIG; 5)

about the pivot stud 471 to disengage the pawls 467 and 468 from the teeth of the ratchet 466, the pawls will both be latched out of engagement with the ratchet 466 by the shoulder 496 on the lever 495. t

In the normal operation of the apparatus the casting will be stepped one step to the right of the printer each time a character is selected and printed on the web of paper carried by the platen 271. This spacing operation occurs automatically due to the fact that each time a character is to be printed because of the code combination received in the selector mechanism 31, the print suppression code bar 134 is selected for operation and is permitted to move upwardly and to the left to engage an upwardly extending arm 487 on the lever 476 (FIGS. 5 and 15) to rock the lever 476 counterclockwise (FIG. 5) to move the shoulder 478 out of the path of the arm 479 on the driving pawl 467. This will permit the driving pawl 467 and the link 470 to move toward the rear of the printer (upwardly as seen in FIG. 5), to follow the actuator roller 473 which, when it is rocked toward the front of the printer, will drive the driving pawl 467 and link 470 to the position shown in FIG. 5 thereby to effect a spacing operation.

When the selector mechanism 31 receives a signal which calls for a spacing operation, the coding of the function code bar 137 and the print suppression code bar 134 are such that the only one of the function levers which is permitted to move upwardly will be the space function lever 339 and this function lever 339 has formed on its lower edge, a projection 498 (FIG. 13) which extends over a lip 499 formed on a bell crank lever 500 that is pivoted on the pivot shaft 413 and urged to rock clockwise (FIG. 13) about the pivot shaft 413 by a contractile spring 501. The bell crank lever 500 has a link 502 pivotally connected to it and to the end of the bell crank lever 475 (FIG. 5). Thus, when the space function lever 339 is permitted to move upwardly by the coding of the function code bars 137 and 134, the bell crank lever 500 will be permitted to rock in a clockwise direction (FIG. 13) thereby to rock the bell crank lever 475 in a clockwise direction (FIG. 5) to move the space blocking lever 476 out of the path of the arm 479 on the driving pawl 467. This will permit the pawl 467 to follow the actuator roller 473 in its oscillation thus to move the driving pawl 467 into engagement with the next succeeding tooth on the sprocket or ratchet 466 whereby when the actuator roller 473 moves back to the position shown in FIG. 5, the shaft 463 will be stepped one rotational step in a clockwise direction (FIG. 5). This stepping of the shaft 463 will occur whenever a space signal is received in the selector mechanism 31 or whenever a signal is received in the selector mechanism 31 calling for the printing of a character. Hence, in either event the space blocking lever 476 will be rocked to a position to move the shoulder478 on it out of the path of the arm 479 on the driving pawl 467. The spacing function will be suppressed at all times when a signal is received in the selector mechanism 31 calling for the performance of a function rather than calling for the printing of a character or a space function due to the fact that the space blocking lever 476 will not be moved from the position in which it is shown on the receipt of signals representing various functions other than spacing or character printing.

Carriage return function Upon receipt in the selector mechanism 31 of a signal which calls for a carriage return function, that is, return of the carriage to its extreme left-hand position in the printer, the print suppression code bar 134 will not be shifted to its left (FIG. 5) and the carriage return function lever 337 will be permitted to move to its upper position by the coding of the function code bars 137. The left end of the carriage return function lever 337 is formed exactly the same as the left end of the automatic carriage return lever 336 which is shown in full lines in FIG. 13 and the carriage return function lever 337 has associated with it a carriage return function pawl 503 (FIG. 13) which is oscillatable about and slidable on the pivot shaft 395. When the carriage return function pawl 503 is permitted to rock in a counterclockwise direction (FIG. 13) about the pivot shaft 395 under the influence of its spring 504 due to the fact that its associated carriage return function lever 337 has been permitted to raise up wardly, i.e., clockwise about the shaft 334 (FIG. 13), to a point where the left end of the carriage return function lever 337 has moved above the shoulder 505 on the pawl 503. The pawl 503 will be positioned to be driven downwardly by the carriage return function lever 337 when the stripper bail 345 is rocked downwardly.

The carriage return function pawl 503 has a rearwardly projecting arm 506 formed on it which extends out over a web 507 (FIGS. 5 and 13) formed on an automatic carriage return function pawl 508. The automatic carriage return function pawl 508 has a horizontally extending tab 509 (FIGS. 5 and 13), formed on it which is disposed over the rear end of the carriage return actuator lever 333. Thus, when the carriage return function pawl 503 is moved downwardly by the carriage return function lever 337, it will carry the automatic carriage return function pawl 508 downwardly with it and will rock the carriage return actuator lever 333 about the shaft 334. The carriage return actuator lever 338 has a downwardly extending projection 510 (FIG. 13) formed on it which, when the lever 338 is rocked counterclockwise (FIG. 13) about the shaft 334, will rock a bail 511 counterclockwise about the pivot shaft 413 since the bail 511 has an arm 512 in alignment with the downwardly extending projection 510 on the lever 338. An upwardly extending arm 513 (FIG. 5) of the bail 511 has a link 514 pivotally connected to it which is also pivotally connected to the pawl release lever 480.

As described hereinbefore, the pawl release lever 480 is pivoted n the pivot stud 471 and when the bail 511 is rocked in a counterclockwise direction (FIG. 13) to move the link 514 to the left (FIG. 13) (upwardly in FIG. the pawl release lever 480 will be rocked in a counterclockwise direction (FIG. 5) about the pivot stud 472 to disengage the driving pawl 467 and the detent pawl 468 from the teeth of the ratchet 466. When the pawl release lever 48% is rocked in this manner, the pawls 467 and 468 will be latched out of engagement with the teeth of the ratchet 466 by a latch lever 515 which has a latching shoulder 516 that will engage the pawl release arm 481 to prevent the pawl release lever 480 from rocking clockwise (FIG. 5) about the pivot stud 471. The latch lever 515 has an upwardly extending arm 517 (FIGS. 3, 4 and 5), which is positioned in the path of a projection 518 on the driving pawl 467 whereby when the driving pawl 467 is moved toward the rear of the machine and rocked counterclockwise (FIG. 5) with respect to the pivot stud 469, the projection 518 will engage with the arm 517 to 'rock the latch lever 515 counterclockwise against the action of its spring 519 which is connected tothe latch lever 515 and to the space blocking lever 4'76.

When the pawl release lever 480 is rocked counter clockwise (FIG. 5) about the pivot stud 471, the pawls 467 and 468 will be disengaged from the teeth of the ratchet 466 and the spring 488 will then be permitted to snap the casting 145 and the type wheel positioning mechanism 34 carried by it back to the left side of the printer. When the casting 145 nears the end of its travel to the left under the influence of the spring 288, it will strike the upper end of the space function restoring lever 493 to rock this lever about the stud shaft 492 (FIG. 4), to move the shoulder 496 out of blocking engagement with the arm 497. However, the pawl release lever 481) will not be permitted to move back to the position shown in FIG. 5 immediately but will be blocked by the shoulder 516 on latch lever 515 until the start of the next step of operation'of the driving pawl 467 which, as it is rocked counterclockwise relative to the pivot stud 469 will also be drawn to the right (FIG. 5) and will carry the projection 518 on it into operative engagement with the arm 517 on the lever 515 to rock the lever 515 slightly in a counterclockwise direction thereby to completely release the driving pawl 467 and detent pawl 468 back to engagement with the ratchet 466.

Automatic carriage return function An automatic carriage return slide 530 is mounted for horizontal reciprocation on the guide posts and is normally urged to the left (FIG. 15) by one of the contractile springs 141. The automatic carriage return slide 530 has an upwardly extending projection 531 formed on it which lies in the path of travel of a horizontally extending portion 532 formed on the support plate 181 which portion also serves as a tie bar for springs 533 individual to the slides 164, 165, 166, 182, 133, 184 and 185. When a casting is moved to the extreme right-hand end of the printer, the horizontally extending portion 532 of the support plate 181 will strike the upwardly extending projection 531 on the automatic carriage return slide 539 to move this slide to the right against the action of its spring 141 .to align a code notch 534 (FIG. 15), in it with the automatic carriage return function lever 336. When the stripper bail 345 moves upwardly and the automatic carriage return function levers 336 is thus permitted to move upwardly into the notch 534, the automatic carriage return function lever 336 will permit its function pawl 508 (FIG. 13) to be rocked about the pivot shaft 395 and to be caught by the bottom edge of the automatic carriage return lever 336. When the stripper bail 345 moves downwardly, the automatic carriage return function pawl 508 will be moved downwardly with it thereby to rock the carriage return actuator lever 338 and through the cooperative operation of the lever 338 and ball 511, link 514 and pawl release lever 480 will strip the driving pawl 467 and detent pawl 468 out of engagement with the teeth on the ratchet 466 to permit the spring 438 to return the carirage including the casting 145 to the left-hand side of the printer. In addition to thus returning the carriage including the casting 145 to the left side of the printer the automatic carriage return function lever 336 will engage the laterally extending arm 414 (FIGS. 5 and 12) of the line feed blocking lever 412, to disengage the shoulder 417 from the laterally extending projection 418 to permit the line feed drive link 419 (FIG. 12) to move to position to be actuated by the drive pin 426 thus to effect a line feeding operation on each operation of the automatic carriage return mechanism.

The casting 145 has a plunger or piston 535 mounted on it for cooperation with a dash pot cylinder 536 for reducing the shock of the carriage return and when the carriage including the casting 145 is moved rapidly of the left (FIG. 4) by the spring 488 the piston or plunger 535 will enter dash pot cylinder 536 to check the movement of the casting gradually.

Miscellaneous functions In addition to the function levers 335, 336, 337, 338 and 339 whose functions have been described in detail hereinbefore there are provided a letters function lever 340, a figures function lever 342 and a blank function lever 343 as described hereinbefore. However, these latter function levers 340, 342, 343 do not control regular functions of the printer being described herein but are provided to prevent false operation of the printing mechanism in the event that signals representative of letters, figures or blank code combinations are received in the selector mechanism 331. These function levers 341 342 and 343 through their associated function pawls, such as the function pawl 399, associated with the etters function lever 3419 may be used to control contacts (not shown) and perform stunts in the known manner.

i In order to insure that the print suppression code bar 134 will suppress printing on all functions other than the printing functions, the print suppression code bar 134 is provided with a ward or projection S37 (FIGS. 15 and 15-A), for cooperation with a blocking lever 538 which is adjustably connected to a bell crank cam lever 539 by an adjustment screw 540 (FIG. 11). The bell crank cam lever 539 carries at its upepr end a cam roller 541 for cooperation with a cam 392 (FIG. on the cam sleeve 2.29. The cam 392 is so shaped that it will rock the blocking lever 538 clockwise against the action of a contractile spring 542 (FIG. 11) for only a short interval of time and at a time when the function levers 335, 336, 337, 338, 339, 342 and 343 have been released for clockwise rotation aobut the shaft 334 (FIG. 11) under the influence of their springs 410 due to the fact that the stripper bail 345 is raised to its upper position. Thus, when the function drive links 333 move the stripper bail 345 downwardly to perform any of the various functions, the print suppression code bar 134 will be blocked from moving upwardly and to the left by the blocking lever 538 engaging a shoulder 543 on the ward 537 unless all of the function levers 335, 336, 337, 338, 339, 340, 342 and 343 were blocked from moving upwardly upon their release by the restoring bail 351). If all of the function levers had been blocked from moving upwardly when they were released by the bail 351), the print suppression code bar 134 would be permitted to move past the blocking lever 53% to rock the latch lever 3118 counterclockwise (FIG. 2) to permit the latch plate 293 to rock clockwise and operate the print hammer 293. At the time in the cycle when the code bars 134 and 137 have been fully reset the blocking lever 538 will be in the path of a shoulder 544 on the ward 537 but the lever S38 is rocked downwardly to permit the print suppression code bar 134 to move upwardly and to the left at the time when the function levers are sensing the code notches and projections on all of the code bars 137.

Operation In the operation of the apparatus permutation code signals may be received over a telegraph signal line to control the operation of the printer by feeding current marking or no-current spacing pulses to the distributor 31. On the other hand, if the apparatus as disclosed in the drawings is being used as a transmitting apparatus, manipulation of various keys on the keyboard 32 will control the permutative setting of a series of contact springs 545 (FIG. 1) which in turn will control the supply of current to segments 546 of the distributor mechanism 33. The distributor 33 through its brush 537 will transmit these signals sequentially to the selector magnet coil 91 of the selector mechanism 31 which will then control the operation of the printer.

The keyboard 32 maybe of any suitable design but preferably is of the design disclosed and claimed in the co-pending application of L. C. Anderson and A. A. Hagstrom, Serial No. 159,324 filed December 14, 1961, which controls the application of current or no-current conditions to the segments 546 of the distributor 33. The distributor may be of any suitable type but preferably is of the type disclosed in the co-pending application of K. Alonas, A. A. I-lagstrom and B. J. Sobczak, Serial No. 159,328 filed December 14, 1961, which in addition to controlling sequential application of marking and spacing signals to a telegraph line also supplies the same signals to the selector mechanism 31.

The permutation code signal thus applied to the selector mechanism 31 will control the setting of the code transfer arms 117 and at a point of the cycle of operation of the selector mechanism 31, which will trim the clutch 42. As pointed out hereinbefore the selector mechanism 31 is driven through a single cycle of operation upon the tripping of the selector clutch 41 which receives its power from the motor 37 through the gearing 38 and main power shaft 39. The tripping of the clutch 42 occursnear the end of the cycle of operation of the selector mechanism 31 when the function clutch cam 108 actuates the cam follower lever 370 (FIG. 5) to rock the function clutch shaft 371 in a counterclockwise direction (FIG. 16). The tripping of the clutch 42 connects the cam sleeve 362 to the main power shaft 39 to be driven by it through one complete cycle of rotation. As the cam sleeve 362 starts torotate, it presents a low portion on its surface to the cam roller 380 thus to permit the spring 548 associated with the bail 350 to rock the bail 350 in a counterclockwise direction (FIG. 4) to release the function code bars 134 and 137 and to permit them to move to the left (FIG. 5) under the influence of the springs 141 unless the function code bars 137 are blocked by wards or projections on the transfer arms 117, and unless the print suppression code bar 134 is blocked by either the blocking lever 538 or one of the function levers 335 through 340, 342 or 343. As the function code bars are released by the bail 351) they will start to rise and move to the left (FIG. 5). At this. time the print suppression code bar 134 will be blocked by the engagement of the blocking lever 538 with shoulders 544 on the ward 537. If the permutation code signal received by the selector mechanism 31 calls for a character to be printed, none of the function code levers 335, 336, 337, 338, 340, 342 or 343 will be permitted to move upwardly. Consequently, as soon as the blocking lever 538 moves completely out of the path of the Ward 537, the print suppression code bar 134 will be permitted to move to its extreme left-hand position where its left end will strike the arm 497 on the space blocking lever 476 to rock this lever counterclockwise about the adjustable pivot 477. This will move the shoulder 478 on the space blocking lever 476 out of the path of the arm 479 on the driving pawl 467 to permit a spacing operation to take place later in the cycle. When the print suppression code bar 134 moves to its extreme left-hand position during the short interval that the blocking lever 538 was in its lowermost position, the return of the blocking lever 538 to the position shown in FIGS. 15 and 15A will not result in suppressing printing but will permit the print suppression code bar 134 to unlatch the latch plate 298 (FIG. 2), thereby to premit the latch plate to make its full swing to effect printing of the character which has been set up by the combined action of the function code bars 137 and the slides 164, 165, 166, 182, 183, 184, and 135.

In the event that the signal received in the selector mechanism 31 calls for the performance of a function rather than a printing operation one or the other of the code levers 335, 336, 337, 338, 339, 340, 342, or 343 will be permitted to move upwardly by the coding arrangement on the underside of the function code bars 137 and con sequently, will move into the path of one: of the wards on the print suppression code bar 134. Then when the blocking lever 538 completes its downward movement and completely releases the print suppression code bar 134 this code bar will be blocked by the function lever which had been premitted to move upwardly. Hence, in the operation of effecting any of the functions the stripper bail 345 will move the selected function lever downwardly to a position where the selected function lever will be out of the path of the wards on the print suppression code bar 134. The return of the blocking lever 53 8 to blocking position is effected early enough in the cycle to catch the print suppression code bar 134 which had been momentarily blocked by the selected function lever, thus to suppress printing on any function other than a printing function.

In the event that the signal received in the selector mechanism 31 calls for a printing function, the print suppression code bar will be permitted to move to the left as pointed out hereinbefore and in so doing will rise to unlatch the printing mechanism. The selection of a particular type on the type wheel 186 will be effected by the

Claims (1)

1. IN A PRINTING TELEGRAPH PRINTER, SIGNAL RESPONSIVE MEANS FOR RECEIVING PERMUTATION CODE SIGNALS, CODED TRANSFER MEANS SETTABLE TO SELECTED POSITIONS BY SAID SIGNAL RESPONSIVE MEANS, FUNCTION CODE MEMBERS SELECTIVELY OPERABLE UNDER CONTROL OF SAID CODED TRANSFER MEANS, A TYPE BEARING MEMBER HAVING A TYPE ARRANGED THEREON IN A COORDINATE PATTERN, MEANS SELECTIVELY ACTUATED BY SAID FUNCTION CODE MEMBERS FOR POSITIONING SAID TYPE BEARING MEMBER TO PRESENT ONE TYPE THEREON IN A PREDETERMINED POSITION, SAID LAST-MENTIONED MEANS INCLUDING A SHAFT ON

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