US3892304A - Single print element print carrier with self-contained selection function - Google Patents

Single print element print carrier with self-contained selection function Download PDF

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Publication number
US3892304A
US3892304A US375277A US37527773A US3892304A US 3892304 A US3892304 A US 3892304A US 375277 A US375277 A US 375277A US 37527773 A US37527773 A US 37527773A US 3892304 A US3892304 A US 3892304A
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US
United States
Prior art keywords
cam
rack
print
rotation
follower
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US375277A
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English (en)
Inventor
Iraj D Shakib
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IBM Information Products Corp
Original Assignee
International Business Machines Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by International Business Machines Corp filed Critical International Business Machines Corp
Priority to US375277A priority Critical patent/US3892304A/en
Priority to FR7414337A priority patent/FR2234992B1/fr
Priority to IT22003/74A priority patent/IT1010172B/it
Priority to GB2219774A priority patent/GB1436668A/en
Priority to IL44924A priority patent/IL44924A/en
Priority to AU69761/74A priority patent/AU473005B2/en
Priority to JP6300774A priority patent/JPS5314009B2/ja
Priority to NLAANVRAGE7407583,A priority patent/NL175889C/xx
Priority to CA201,975A priority patent/CA1005781A/en
Priority to CH793174A priority patent/CH570270A5/xx
Priority to SE7407784A priority patent/SE399019B/xx
Priority to DE2429931A priority patent/DE2429931C3/de
Priority to AT520774A priority patent/AT340960B/de
Priority to ES427680A priority patent/ES427680A1/es
Priority to DK350974*A priority patent/DK350974A/da
Priority to BR5389/74A priority patent/BR7405389D0/pt
Application granted granted Critical
Publication of US3892304A publication Critical patent/US3892304A/en
Assigned to MORGAN BANK reassignment MORGAN BANK SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: IBM INFORMATION PRODUCTS CORPORATION
Assigned to IBM INFORMATION PRODUCTS CORPORATION, 55 RAILROAD AVENUE, GREENWICH, CT 06830 A CORP OF DE reassignment IBM INFORMATION PRODUCTS CORPORATION, 55 RAILROAD AVENUE, GREENWICH, CT 06830 A CORP OF DE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: INTERNATIONAL BUSINESS MACHINES CORPORATION
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41J—TYPEWRITERS; SELECTIVE PRINTING MECHANISMS, i.e. MECHANISMS PRINTING OTHERWISE THAN FROM A FORME; CORRECTION OF TYPOGRAPHICAL ERRORS
    • B41J7/00—Type-selecting or type-actuating mechanisms
    • B41J7/54—Selecting arrangements including combinations, permutation, summation, or aggregation means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41J—TYPEWRITERS; SELECTIVE PRINTING MECHANISMS, i.e. MECHANISMS PRINTING OTHERWISE THAN FROM A FORME; CORRECTION OF TYPOGRAPHICAL ERRORS
    • B41J7/00—Type-selecting or type-actuating mechanisms
    • B41J7/50—Type-face selected by combinations of two movements of type carrier

Definitions

  • ABSTRACT A carrier for a printer, having a single type element, is disclosed.
  • the selection apparatus contained within the carrier is one whereby only a rotary power force plus control signals need be introduced into the carrier.
  • the selection apparatus is comprised of barrel cams having a plurality of channels formed into the periphery of the barrel cams to cause lateral displacement thereof on their drive shaft. The lateral displacement of the barrel cams is converted into a linear motion which is in turn transmitted and converted into rotary motion to position the type element about its rotate and tilt axes.
  • the controls for transmitting signals to the carrier are pneumatic and the pneumatic impulses received by the carrier logic block and actuator blocks activate mechanical latches to insert selector pins into the grooves of the barrel cams.
  • a dual rack and single pinion arrangement is disclosed to convert the linear motion to rotary motion of the type element.
  • the foregoing objects are accomplished by the inclusion of the entire selection mechanism in the print carrier and the connection of the keyboard to the selection mechanism through either electrical or pneumatic means.
  • the print carrier is provided with a translator to translate or decode the input signals which are in the form of pneumatic or electromagnetic signals and the decoding of those signals such that the keyboard originated output is converted into a plurality of signal pulses one corresponding to rotation of the type element. a second corresponding to the tilt of the type element. a third corresponding to a print/no print condition and a fourth corresponding to rotate direction. This converts the keyboard output to a set of signals capable of interpretation at the carrier and conveyed thereto through either pneumatic tubes or electrical conductors. This eliminates the rotate and tilt bands,
  • rotate and tilt mechanisms necessary to decode the keyboard originated logic signals of the prior art.
  • the tilt and rotate signals are then fed to latches which unlatch selector pins and allow the pins to drop into a barrel cam.
  • the rotation of the rotate barrel cam causes alateral translation thereof with a corresponding lateral translation of a follower linkage which is part of a linear to rotary motion convertor.
  • the linear to rotary motion convertor translate the relative displace ment of the barrel cam into a rotary motion of the keyboard thus selecting the column of characters desired.
  • rotation of the tilt barrel cam results in lateral displacement of the tilt barrel cam as a result of its rotation and engagement with a fixed selector pin and is converted through bell cranks and linkages to a pushpull action causing the tilt ring of the print element rocker assembly to rotate about a horizontal axis thus positioning one of the characters within the previously selected row in the proper position for printing.
  • FIG. 1 is a single element typewriter having a carrier of the type disclosed herein.
  • FIG. 2 is a left front perspective of part of the carrier of the typewriter illustrated in FIG. 1.
  • FIG. 3 is a partial simplified end view of the print cam and print rocker of the carrier of FIG. 2.
  • FIG. 4 illustrates the selector pin latch assembly together with the barrel cams in their home position.
  • FIG. 5 is a section view along 5-5 in FIG. 4.
  • FIG. 6 illustrates the escapement linkage and the escapement cam carried within the carrier.
  • FIG. 7 shows the no right control for controlling the cam follower of the print cam.
  • FIG. 8 illustrates a partial top view of the escapement cam and follower mechanism together with the velocity and no print control.
  • FIG. 9 illustrates the selection rack and pinion together with the reset control and detenting cam follower and detenting mechanism of the print carrier.
  • FIGS. 10, 11, I2, and 13 are respective end and section views of the barrel cams.
  • FIG. 14 Isa plane view of the rotate selection cam.
  • FIG. 15 is a cam diagram of the rotate cam of FIG. 14.
  • FIG. 16 is a plan view of the tilt control cam.
  • FIG. 17 is the cam diagram for the tilt barrel cam of FIG. I6.
  • FIG. [8 is an exploded view of the motion conversion and transmission portion of the selection apparatus.
  • FIG. 19 is perspective view of a single selector pin selector control and a partial view of a single track branched groove barrel cam.
  • FIG. is a schematic block diagram of a suitable control network to provide signals to the carrier of FIG. 2.
  • FIG. 21 is schematic of the single selection pin embodiment with the cam associated therewith stretched out to a cam diagram.
  • FIG. 22, 23, 24 and are sections of the cam of FIG. 21 showing depth of various grooves at various cam stations.
  • FIG. 26 is a plan view of the cam represented by the cam diagram of FIG. 2].
  • a carrier 10 is provided within the typewriter 12. This carriage is translatable across the print line of typewriter 12 on print shaft 14.
  • the print shaft 14 is a rotatable shaft which provides the driving forces to the carrier 10 to cause activation of single print element 16.
  • the control signal for the selection of the character on print element 16 are transmitted from keyboard 18 to the carrier 10 by means of control signal lines 20.
  • type element 16 is rotated and tilted to present the desired character in position opposite 22 such that when the type element 16 is impacted into platen 22 a printing operation occurs and a character or other symbol is deposited on page 24.
  • a keyboard 18 is provided. Keyboard 18 interacts with a keyboard signal generator 26. Keyboard signal generator 26 may take the form of pneumatic valves actuated by mechanical motion of the keyboard or it may be an electrical signal generator which is activated as a result of the mechanical operation of keyboard 18. Keyboard generator 26 provides the capability of producing plurality, n, of output signals. The signals generated by the keyboard signal generator are transmitted to a logic block 28 which then converts these signals into a series of m processed signals which are then outputed from the logic block 28 into an actuator block 30. The actuator block 30 receives the logic block outputs and converts these logic block outputs into a binary coded output of the keyboard key depression.
  • the actuator block converts the pneumatic or electrical signal into a mechanical movement.
  • the mechanical movement is the control of the rotate and tilt by selection latches 32-4I.
  • additional signals representing such functions as rack switch, no print, and dead key. The utilization of these signals, directly by the mechanisms of the carrier, will be described in detail below.
  • the keyboard signal generator 26 may be either pneumatic or electronic or any other technique which allows the conversion ofa mechanical physical motion of the keyboard 18 to be converted into a series of binary signals. These signals are then passed into a logic block 28.
  • the function of the logic block is to convert a small number of signals from the keyboard generator 26 into a larger more comprehensive series of signals m which are outputed by the logic block and directly used in a signal to mechanical motion convertor or actuator block 30. Also, there are signals outputed from the logic block 28 which are used directly by the carrier I0 to control ancillary nonselection functions such as dead key, no print and rack switch.
  • Actuator block 30 which is a signal receiving means, reference is made to FIGS. 4 and 5.
  • Actuator block 30, for sake of illustration, is shown as a pneumatic block in section view in FIG. 5 and in broken away view in FIG. 4 is made up of several components.
  • the block member 32 is formed with a depression 34. This depression is sealed by flexible pneumatically distensible membrane 36 at points 38 in FIG. 5. Points 38 in fact are edge sealing regions as opposed to physical points.
  • the chamber 40 formed by distensible membrane 36 and depression 34 is connected to the logic block through conduit 42. Conduit 42 provides a path to transmit signals from the logic block 28 into the chamber 40.
  • the depression of the keys of keyboard 18 provide a series of output signals from the keyboard signal generator 26. These signals are received by and decoded by logic block 28 to provide signals for the actuator block 30.
  • the logic block 28 through the logic net work contained therein, provides an output signal in a pneumatic pulse form and absence of pneumatic pulses in the event that a tilt or a rotate function or both are required of the print element 16.
  • a pressurized pulse of air is transmitted through conduit 42 and pressurizes cavity 40, as illustrated in FIG. 5.
  • a pressurized pulse of air is transmitted through conduit 42 and pressurizes cavity 40, as illustrated in FIG. 5.
  • Latch shoe 44 is pivotally attached by pin 46 to a latch lever 48.
  • Latch lever 48 is pivotally mounted on pivot point 50 and biased in a counterclockwise direction by biasing spring 52.
  • Latch lever 48 is further provided with a latching surface 54. Also provided on latch lever 48 is an extending tab portion 56.
  • Tab 56 extends into a ballsometer or a ball tube interlock 57 which provides a technique for preventing more than one latch lever 48 from being activated in response to a single set of rotate signals and likewise only one tilt latch member 48 may be activated by a single set of tilt signals.
  • the ball tube interlock technique is well known and well disclosed as a keyboard interlocking technique in other U.S. patents, such as U.S. Pat. No. 3,086,635 to L. E. Palmer.
  • Selector pin 60 is provided with a spring bias 62.
  • Spring bias 62 is a compression spring tending to force selector pin 60 in a leftward direction in FIG. 5 and in a downward direction in FIG. 4.
  • Selector pin 60 is provided with a flatened blade portion 64. This flatened blade portion 64 is adapted to engage with and ride in the selection groove -76 and 170-173 of the selection and tilt barrel earns 68, 168.
  • the selector pins 60 and their associated latches may be considered as selection means or positioning means as they provide selection of grooves and a fixed position for earns 68, 168 to rotate with respect to.
  • the blade portion 64 of selector pin 60 engages its respective track in the rotate or tilt earns 68, 168 illustrated in FIGS. and 17.
  • the rotate cam illustrated in FIG. 15, there are a plurality of selection grooves 70-76.
  • the grooves are indicated with 70-76, however, the units of relative selection displacement or units of rotation of the head, is indicated by the unit digit of the reference numeral.
  • the groove labeled 70 is a zero displacement, home row or zero rotate condition.
  • Groove 71 is a one unit rotate groove
  • groove 72 is a two unit rotate groove
  • groove 76 which is a six unit rotate groove
  • Groove 78 is the groove into which a follower is inserted to provide translatory motion to the follower as a result of the translational movement of the barrel cam 68.
  • Each of the grooves 71 through 76 has a widened portion 80 to facilitate the entrance of selector pin blade 64 into the respective grooves.
  • Rotate barrel cam 68 is coaxially, slideably mounted on keyed rotating shaft 82 by means of projections 84 on shaft 82 and mating recesses 86 in barrel cam 68. This mounting technique provides a capability for barrel cam 68 to rotate in response to the shaft rotation of shaft 82.
  • Zero select groove 70 is likewise a circular groove with no radial dwells, rises, or falls.
  • Engaged in cam groove 70 is a zero select homing pin 92, illustrated in FIG. 4.
  • Homing pin 92 is spring biased by compression pin 94 thus exerting a force on the homing 92 to cause it to move downward in FIG. 4. This maintains engagement between pin 92 and zero rotate groove 70.
  • Pin 92 remains engaged with groove 70 unless one of the pins 60 is released by its appropriate latch arm 48, and allows to engage its respective groove. In the event that one of the selector pins 60 is allowed to extend and engage its respective rotate groove 71-76 in cam 68, the cam will rotate and pass the pin until it reaches approximately 90 of rotation.
  • the pin will deviate from a straight path and attempt to follow the track. Since the pin 60 is fixed and the cam 68 is coaxially slideable on shaft 82. the cam 68 will translate in response to the deviation of the respective groove from the straight course. This causes a direct translational movement of groove 78 and thus causes follower tab 88 and follower 90 to move therewith.
  • the rotate grooves or selection grooves 71-76 are cut into cam 68 in such a way as to provide a proportional lincar displacement corresponding to one through six units of translational motion, the groove with the largest cam shift will thus be the six unit rotate while the groove with the smallest shift will be the one unit rotate.
  • FIG. 11 is a cross-sectional view of rotate cam 68 in track 71, it can be understood how the blade portion 64 of a selector pin 60 can engage the track and be reset.
  • the blade portion 64 of selector pin 60 is inserted into groove 71 at a point approximately at the 0 axis in FIG. 11.
  • the cam profile of the bottom of groove 71 forces the pin 60 and blade portion 64 radially outward during the rise and dwell portion of that camming action.
  • lobe I02 passes the 0 axis of FIG.
  • the radial distance from the center of shaft 82' to the rise 102 is sufficient to compress spring 62 on pin 60 and allow bias spring 52 to rock latch arm 48 in a counterclockwise direction thus engaging latching surface 54 with pin latching surface 58.
  • cam 68 continues to rotate lobe 102 terminates at approximately 345 of rotation thus allowing pin 60 to be positively latched by latch arm 48.
  • the cam has been rotated through one complete cycle of rotation and the cam has translated one unit of translation which will ultimately correspond to one unit of rotate.
  • the selector pin 60 has been inserted into the groove 71, the selector pin 60 has guided cam 68 and has then raised out of the groove 71 and allowed to relatch in a retracted position.
  • the rotate cam 68 is forced toward the right on shaft 82 as shaft 82 rotates.
  • follower tab 88 of cam follower 90 is engaged in follower groove 78.
  • follower 90 is slideably supported on shaft 110.
  • follower 90 includes a slot 112 for receiving rack tab 114.
  • Rack tab 114 engages slot 112 to receive the translatory motion of follower 90 in response to the translatory motion of cam 68 transmitted through tab 88.
  • Shaft is rigidly fixed into rocker 116 which is in turn pivoted upon a pivot pin 118.
  • Rack tab 114 is rigidly attached to or formed into switchable rack 120.
  • Rack 120 is pivotally mounted on and slideable on shaft 122 which is likewise carried by rocker 116.
  • Cam follower 90 is likewise slideably mounted on shaft 122 as well as 110 as indicated earlier. Referring to FIG. 18.
  • Rack 120 has a dual arm arrangement with gear teeth formed in each arm.
  • Rack 120 has gear racks 124 and 126.
  • Each rack 124 and 126 is formed on a separate portion of overall rack 120.
  • the respective racks 124 and 126 are angularly disposed such that when rack 120 is tilted as far as it can be displaced in one angular direction, one of the racks. for example, 124 will be co-planar with and engage the teeth on pinion 128.
  • Pinion 128 is fixedly mounted on the lower ball socket shaft 130.
  • Lower ball socket shaft 130 extends up through the yoke 132 to the lower ball socket 134 which is formed as a part of the lower ball socket shaft 130.
  • a shifter tab 136 is formed into the non-used edge of rack 124.
  • a rack shift mechanism 138 is provided.
  • Rack shift mechanism 138 is comprised of an actuator lever 140. This lever may be actuated by either pneumatic or electromagnetic means. For the sake of illustration, a pneumatic actuation mechanism will be described. referring to FIG. 9 and 18.
  • the pneumatic actuation mechanism is comprised of a bellows block 142 with an input port 144.
  • bellows member 150 Formed into the underside of bellows block 142 and communicating with input port 144 is chamber 146 which is sealed with a distensible membrane 148. Engaging the atmosphere side of membrane 148 is bellows member 150. Bellows member 150 is pivotally mounted on and spring biased around pin 152 by spring 154. Rack switch lever 140 may be attached to or formed at a part of bellow member 150. The inflation of the bellows 138 will cause engagement between rack switch lever 140 and rack switch tab 136 causing rack switching or shifting around shaft 122 in a counterclockwise direction as viewed in FIG. 9.
  • Reset leaf spring 160 is attached to rocker 162 which is pivotally attached to shaft 100. Extending from rocker 162 are follower arms 164 and 166 as viewed in FIG. 18.
  • cam profiles are cut into the ends of ro tate cam 68. These cam profiles 77 and 79 can best be observed in FIGS. 12 and 13.
  • follower arm 166 is positioned to engage cam profile 77 when the home or zero rotate pin 92 is engaged with its homing track 70. As cam profile 77 in FIG. 13 is rotated under follower arm 166, the follower arm will ride up the cam profile 77 thus causing rack switch spring 160 to engage the lower portion of rack 120.
  • Cam lobe 77 is positioned at a location such that when enlarged portions on the rotate cam 68 are presented to the blade 64 of selector pin 60, the highest dwell of cam 77 is under follower 166 thus causing rotation and transmission of force through rocker 162 and leaf spring or rack switch spring 160.
  • the rack switch cam follower 166 and the rack switch spring 160 act to always engage rack teeth 124 with pinion 128. This provides the capability of returning the rack 120 to a minus rotate condition upon the completion of each revolution of rotate cam 68.
  • Cam follower arm 164 is positioned on shaft to cause rocker 162 and hence, rock switch spring 160 to rotate.
  • the distance between follower arm 166 and 164 is equal to the cummulative distance equal to the length of cam 68 between cam surfaces 77 and 79 plus the distance which cam 68 will laterally translate when a selector pin 60 and blade 64 are caused to engage rotate slot 76 corresponding to six units of rotation.
  • Cam 68 will translate on keyed shaft 82 but will only translate far enough for cam follower 164 to engage cam lobe 79, illustrated in FIG. 12, when a selector pin 60 and blade portion 64 are unlatched and engaged respectively into the groove 76 corresponding to six units of rotation.
  • cam surface 79 will cause cam follower 164 to rotate about the axis of shaft 110, thus causing pivotal rotating movement of rack switch spring 160.
  • the engagement of rack switch spring 160 with the underside of rack at the point of the highest rise on the cam lobe 79, will cause rack 120 to change its position such that rack teeth 124 will engage pinion 128 and rack teeth 126 will disengage pinion 128.
  • Cam lobe 79 is relatively position with respect to the other cam surfaces of rotate cam 68, to present its rise and dwell to cam follower 164, at a time corresponding generally to the beginning of the dwell in the translational motion of cam 68.
  • a tilt cam 68 of the configuration illustrated in FIG. 16 and its cam diagram illustrated in FIG. 17, is mounted coaxially on keyed shaft 82 for coaxial sliding motion thereon.
  • Tilt cam 168 is formed with five grooves in the generally cylindrical exterior surface. Grooves 170 through 173 denote selection or tilt increment grooves. Groove 174 is the cam follower groove and has no translatory control over cam 168.
  • a latch and selector pin assembly such as illustrated in FIG. is provided with a composite of three latches and selector pins, one each for grooves 171, I72, and 173.
  • the three selector pins '60 associated with the three grooves 171-173 are interlocked through a ball tube interlock 57 among themselves but are not interlocked with respect to the selector pin latch assemblies for the rotate cam 68.
  • the tilt cam 168 has a home or zero tilt groove 170.
  • a non-latching, spring-biased, homing selector pin 180 engages groove 170 to home the tilt barrel cam 168 in its zero tilt or home location and thus control the position of the printing element 16 in its zero tilt condition.
  • camming surfaces 182 and 184 Extending from the track 170 of cam 168 are camming surfaces 182 and 184.
  • Camming surface 182 can be viewed in FIGS. and 16 and 184 in FIG. 10.
  • the function of camming surfaces 184 and 182 are respectfully the same as the functions of camming surfaces 96 and 99. They provide a rise and fall for the spring biased homing and zero tilt selection pin 180 thereby allowing that pin to ride out of track 170 when a selector pin 60 and blade section 64 have been engaged with tracks 171, 172, or 173.
  • the notation convention utilized with respect to the rotate cam 68 is likewise utilized with respect to the tilt cam wherein track 170 represents zero units of tilt. Tracks or grooves 171, 172, and 173 respectively correspond to one, two, and three units of tilt movement.
  • Track 174 provides a track for cam follower tab 186 which is formed as a part of bell crank 188.
  • Bell crank 188 is pivotally mounted on supporting carrier frame 192 by pin 190.
  • bell crank 188 is provided with an output arm 194 which contains a connection 196 to tilt link 198.
  • Tilt link 198 to output its motion is pivotally connected to tilt ring 200 by pivot point 202.
  • Tilt ring 200 is pivotally attached to yoke 132 by pivot member 204.
  • the tilting of the tilt ring 200 which carries type element 16 on the upper bail socket 206 is accomplished by selection of one of the selector pins 60 forcing the blade 64 into engagement with one of the tilt grooves 171-173 representing one, two. or three units of tilt. 0n the unlatching of one selection pin 60 in the pin block assembly corresponding to the tilt function.
  • the homing or zero tilt selection pin 180 will be cammed up surface 184 and the tilt cam 168 will translate in a leftward direction as viewed in FIGS. 4 and 8. This left ward translation in response to the rotation of the cam 168 and further response to the rotation of shaft 82, causes cam follower tab 186, in FIG. 8 to translate leftwardly around pivot point 190.
  • selector pin 60 is unlstched by latch arm 48, acted upon by membrane 36 and shoe 44 in re sponse to a pneumatic signal from logic block 28. to cause blade portion 64 to drop into groove 172. As groove 172 is progressively rotated past blade 64, cam
  • the tilt detent mechanism comprises a series of detent notches 206 respectively corresponding to the angular position of the tilt ring 200 for proper positioning of each of the four rows of characters on typehead 16. These detent notches 206 are formed into an arcuate lower surface of tilt ring 200.
  • tilt detent 208 is formed as a part of tilt detent lever 210. Tilt detent lever 210 is spring biased by spring 212 to be normally engaged, through tilt detent 208, with one of the plurality of detent notches 206.
  • Detent crank 214 is pivotaily mounted on yoke 132 by means of a mounting pin or screw 216.
  • Detent lever 210 has a pivot point at pivot means 218.
  • Detent lever 210 has a depending leg 211 which is in turn engageable by crank 214.
  • the movement of crank 214 around pivot point 216 engages depending leg 211 of detent lever 210acting against the bias of spring 212 to withdraw the detent 208 from detent teeth 206 and allow free movement of the tilt ring 200 in response to the tilt ring 198.
  • the withdrawal of detent 208 from detent teeth 206 also acts to move rotate detent 218 downward, as viewed in H6. 9, to remove the detent surface 220 from the detent teeth of type element 16. This allows the rotation of type element 16 in response to the rotate selection mechanism.
  • Crank 214 is moved pivotaily around pivot point 216 in response to forces exerted on it by cam follower 222.
  • Cam follower 212 is pivotally mounted to the frame of the carrier 192 by pivot 224.
  • Cam follower 222 has a follower tab 226 which engages detenting cam 228 keyed to and mounted on rotary force receiving print sleeve 230.
  • Print sleeve 230 is positively driven rotationally by print shaft 232.
  • a gear 234 is fixedly attached to print sleeve 230.
  • Gear 234 is engaged through idler gear 236 which is mounted on carrier frame 192 with cam shaft drive gear 238.
  • Cam shaft drive gear 238 is fixedly attached to cam shaft 82 upon which tilt barrel cam 168 and rotate barrel cam 68 are slideably mounted.
  • the print sleeve 230 may be described as the power receiving means and the gear train keyed shaft and cams together with linkage driven by the cams translation may be described as the power utilizing means.
  • rocker assembly 116 To impart the necessary arcuate impacting movement for printing, to type element 16, and yoke assembly 132, rocker assembly 116 must be moved pivotally about pivot points 118. This is accomplished by transmission of a short duration force being applied to the rocker assembly 116. This force is applied through a stud member 250 in FIG. 3. The force is provided to stud member 250 by print cam follower 252 which in turn is pivotally mounted at pivot 254 to carrier frame member 192. Print cam follower 252 further includes a cam roller 256 which is in rolling engagement with print cam 258. Print cam 258 has a high lobe for imparting movement through print cam follower 252 to stud 250. Print cam 258 is keyed to and rotates with print sleeve 230 which in turn is powered by intermittently rotating print shaft 232.
  • Print cam roller 256 is, in addition to being rotatably mounted on the end of print cam follower 252, slideably mounted upon mounting pin 260 for translational movement along the axis of pin 260.
  • a latch member 264 presents a flat force surface 266.
  • Flat force surface 266 is in contacting arrangement with plunger 268 of pneumatic actuator 270.
  • Biasing spring 272 retains force surface 266 in contact with plunger member 268.
  • Latch member 264 also acts to move latch 274 by physical interference therewith, and thus withdraw both their respective pawls from the latching surface 276 of slide member 262.
  • Spring member 278 provides a constant bias on follower arm 280 and thus on slide member 262 which is engaged by follower arm 280.
  • Slide member 262 has upturned tab shift yoke member 282 which straddle the print cam follower roller 256. Any movement of slide member 262 is thereby translated into a corresponding lateral translation of print cam follower roller 256. With the withdrawal of latch members 264 and 274 from latching surface 276, slide member 262 is thereby freed to translate leftward as in FIG. 7 thus moving cam follower roller 256 out of engagement to the left and away from the cam rise of print cam 258. This lateral translation of roller 256 out of engagement with any of the cam lobes of cam 258 has the effect of disconnecting the motion normally accorded print cam follower 252, due to rotation of print shaft 232 and print cam 258.
  • follower arm 280 is provided with a cam follower lug 286.
  • This cam follower lug is acted upon by restore cam 288 which is in turn mounted upon and rotates with print sleeve 230.
  • the rotation of the print shaft 232 and the print sleeve 230 causes the restore cam 288 to engage cam follower stud 286 and thus move follower arm 284 thus pushing slide member 262 rightward restoring the print cam follower wheel 256 to its normal operative position.
  • escapement cam 300 To normally cause escapement of the carrier with respect to the print line, and an escapement cam 300 is rigidly fixed to print sleeve 230, as illustrated in FIGS. 6 and 8. Escapement cam 300 rotates with print sleeve 230 and print shaft 232. Escapement cam follower 302 in the form of a bell crank. is provided with a follower wheel 304 in engagement with the periphery of escapement cam 300. Escapement cam follower 302 is pivotally mounted on a pivot pin 306 which in turn is supported by carrier frame member 192. Pivotally attached to the other arm of the cam follower bell crank 302 at pivot point 308, is escapement link 310.
  • Escapement link 310, escapement follower bell crank 302, and escapement follower wheel 304 are all biased into a position, whereby escapement follower wheel 304 is in engagement with periphery of escapement cam 300, by means of a spring 312.
  • Escapement link 310 includes depending and upstanding tabs 314 and 316 respectively.
  • Depending tab 314 of escapement link 310 engages escapement pawl tab 316 which is formed on the end of the escapement pawl 318. This is to provide a means for extracting the escapement pawl from the escapement rack to cause escapement of the carrier with respect to the print line.
  • tab 316 to escapement pawl 318 is a modification made to the escapement pawl assembly as disclosed in US. Pat. No. 3,l26,998 issued to L. E. Palmer.
  • Pneumatic actuator 318 has a plunger 320 which extends under air pressure being introduced into pneumatic actuator 318 through inlet port 322 from the logic block 28.
  • the extension of plunger 320 will displace escapement link 310 laterally to disengage depending tab 314 from escapement pawl tab 316 and trap the escapement link 310 in its displaced position by spring 317. With the disengagement of depending tab 314 from escapement pawl tab 316, any movement of the escapement linkage will be ineffective to cause escapement.
  • a keyboard signal generator 26 upon the depression of a key member of the keyboard 18, a keyboard signal generator 26 generates an electrical, or pneumatic signal representing that character. These signals are then transmitted to a logic block 28 where the signals are decoded and recoded providing m outputs. The number of the outputs is dependent upon the number of functions that are to be effected as a result of direct signals from the logic block.
  • the signals are split, some of the signals going to an actuator block 30 where each signal from the output block is received and utilized to actuate a mechanical mechanism for further control of the typehead l6 and carrier 10.
  • actuator block 30 will receive nine signals, one for each of the three tilt selection latch/selection pin assemblies and one for each of the six rotate selection latch/selection pin assemblies. Additional signals for dead key, no print, and rack switch are routed directly from the logic block to the appropriate transducer on the carrier to 13 effect those functions. Other signals may be provided as needed or desired.
  • the operator of the typewriter selects the letter lowercase r by depressing the keybutton corresponding to r.
  • This generates signals which are passed through logic block 28 and result in output signals from the logic block in the form of two pneumatic pulses.
  • One pneumatic pulse is directed to the selector pin 60 corresponding to groove 74 in rotate cam 68.
  • the other pneumatic pulse is outputed through the actuator block 30 and latch assembly corresponding to the selector pin 60 mating with tilt groove 172 of tilt cam 168.
  • the pulses are received in inlet port 42 of actuator block 30.
  • the pressure in chamber rises sharply distending diaphragm 36 and applying a force onto shoe 44 thus forcing latch lever arm 48 in a clockwise direction around pivot point 50.
  • Rocking latch lever 48 in a clockwise direction withdraws latching surface 54 from latching surface 58 of selector pin 60.
  • blade 64 extends into groove 74 of rotate cam 68.
  • selector pin 60 and blade 64 will extend likewise into groove 172 of tilt cam 168.
  • the depression of the print key corresponding to the letter r acts to release a single cycle clutch (not shown) to cause the print shaft 232 to begin to rotate.
  • print sleeve 230 rotates therewith causing gear 234 to rotate.
  • the angular motion of gear 234 is transmitted through idler gear 236 in matched relationship therewith, to the driven gear 238.
  • Gear 238 is fixedly attached to keyed shaft 82.
  • the rotation of gear 238 causes rotation of shaft 82.
  • the keying of shaft 82 is complimentary to the keyed core or holes through the centers of tilt cam 168 and rotate cam 68
  • tilt cam 168 and rotate cam 68 revolve with keyed shaft 82.
  • Selector pins 60 having previously been inserted under the influence of compressed springs 62, into grooves 74 and 172 respectively, the rotate and tilt cams begin a lateral displacement in cor respondence to the displacement of the cam grooves 74 and 172.
  • the rotate cam 68 and the tilt cam 168 translate on shaft 82 generally in opposite directions and toward their respective ends of keyed shaft 82. This direction of translation of each cam 68, 168 prevents an interference in the center of the shaft 82.
  • tilt link 198 corresponds to a down ward leftward motion of tilt link 198.
  • This extension of tilt link 198 acting through pivot pin 202 causes tilt ring 200 to rotate in a clockwise direction around pivot pin 204.
  • This rotation of tilt ring 200 around pivot pin 204 is permitted by the extraction of tilt detent 208 from detent notches 206.
  • the extraction of detent 208 from detent notches 206 is accomplished by the timed relation of cam 228 which is directly driven by print shaft 232 through print sleeve 230.
  • the rise and high dwell of cam 228 acts through follower stud 226 to rock the follower 222 about pivot 224.
  • the rocking of follower 222 about pivot 224 acts through detent crank 214 and pivots it about its pivot point 216.
  • the pivoting of detent crank 214 around 216 engages depending leg 211 of detent latch member 210.
  • the exertion ofa force by detent crank 214 through detent latch leg 21] rotates detent latch 210 about pivot point 218 against the force of spring 212 and lowers the detent 208 out of the detent teeth 206 in tilt ring 200. This frees the tilt ring 200 for relatively free moving motion about pivot point 204.
  • the high dwell of detent cam 228 is formed and positioned to allow the entire tilting operation to occur and to maintain detent member 208 out of engagement with detent teeth 206 except at that point in the cycle where the head is to be detented in a particular position for printing. At all other times of the cycle, the high dwell of detent cam 228 acts through the above described linkages and relationships to remove and keep removed from detent teeth 206, the detent 208. As detent cam 228 rotates during the printing cycle, the low dwell will allow detent cam follower 222 to swing out of the way from detent crank 214 thus releasing the forces against pending leg 211 of detent member 210.
  • the homing pin 180 engages slot 170 or groove 170 and re tains the tilt cam in its home position.
  • cam follower tab 186 is forced to the right as observed in H0. 8 thus rotating Cam follower bell crank 188 in the opposite direction to which it had previously been rotated and extending tilt link 198 in a downward direction.
  • the downward direction corresponds in FIG. 9 to an up and to the right motion thus returning pririthead 16 and tilt ring 200 to its home or zero tilt position.
  • the detent member 208 remains out of teeth 206 and detent member 218 and detent surface 220 remain out of engagement with the detenting teeth on the periphery of the lower edge of typehead 16.
  • a typehead carrying 96 characters in four rows will of necessity have 24 columns of characters.
  • the 24 columns of characters are divided into upper and lower case of 12 columns each. In each case, there have been designated for the sake of reference a zero row and six rows of negative or minus rotation and five rows of positive or plus rotation.
  • the letter lower case s In the event that the letter lower case s is selected. its position on the typehead is such as to require a two increment tilt, the same as the lower case r used in the immediatie preceding example.
  • the lower case 5 also requires four units of rotate but unlike the lower case r used above, the lower case s requires four units of plus rotate as opposed to four units of minus rotate.
  • a signal indicating a positive rotate is derived from the logic block 28 in the form of a rack switch signal.
  • the rack switch pulse is a direct output of the logic block 28 to a rack switch bellows assembly 138.
  • a pneumatic pulse is received through input conduit 144 through bellows block 142 into chamber 146.
  • Distendable diaphragm 148 is forced to balloon outward from chamber 146 thus forcing bellows member 150, FIG. 9, to pivot around its pi vot point 152.
  • Rack switch bellows tab 140 being part of bellows member 150, is forced downward and engages rack tabs 136
  • the force exerted by the pneumatic pulse introduced to rack switch bellows 138 forces rack tab 136 downward rotating rack 120 about pivot shaft 122.
  • cam lobe 77 illustrated in FIGS. 13 and 14 is presented to follower arm 166.
  • follower arm 166 is engaged by cam lobe 77, it is rotated about shaft in a counterclockwise direction as viewed in FIG. 9. The effect of this is to rotate rocker 162 and spring 160 in a movement counterclockwise and concentric to shaft 110.
  • spring 160 is rotated counterclockwise it engages the lower portion of the rack approximately directly below rack teeth 124.
  • rack 120 is shifted such that rack teeth 124 again engage pinion 128.
  • This operation is accomplished upon the return to home position of rotate cam 68 after any operation of the print carrier which places the rack 120 in what has been referred to a plus rotation configuration.
  • the plus rotation configuration is anytime that rack teeth 126 are engaged with pinion 128.

Landscapes

  • Transmission Devices (AREA)
  • Character Spaces And Line Spaces In Printers (AREA)
  • Common Mechanisms (AREA)
US375277A 1973-06-29 1973-06-29 Single print element print carrier with self-contained selection function Expired - Lifetime US3892304A (en)

Priority Applications (16)

Application Number Priority Date Filing Date Title
US375277A US3892304A (en) 1973-06-29 1973-06-29 Single print element print carrier with self-contained selection function
FR7414337A FR2234992B1 (en, 2012) 1973-06-29 1974-04-19
IT22003/74A IT1010172B (it) 1973-06-29 1974-04-29 Meccanismo di selezione perfezio nato per una stampatrice o macchi na per scrivere dotata di un uni co elemento di scrittura
GB2219774A GB1436668A (en) 1973-06-29 1974-05-17 Printer
IL44924A IL44924A (en) 1973-06-29 1974-05-30 Selection mechanism for prints from the type of a single element
AU69761/74A AU473005B2 (en) 1973-06-29 1974-06-04 Printer
JP6300774A JPS5314009B2 (en, 2012) 1973-06-29 1974-06-05
NLAANVRAGE7407583,A NL175889C (nl) 1973-06-29 1974-06-06 Selectiemechanisme voor een schrijfmachine met enkel typenelement of dergelijke drukinrichting.
CA201,975A CA1005781A (en) 1973-06-29 1974-06-07 Single print element print carrier with self-contained selection function
CH793174A CH570270A5 (en, 2012) 1973-06-29 1974-06-11
SE7407784A SE399019B (sv) 1973-06-29 1974-06-13 Utveljningsmekanism for en skriv- och tryckanordning
DE2429931A DE2429931C3 (de) 1973-06-29 1974-06-21 Typenträger-Einstellvorichtung für Schreib- und ähnliche Maschinen mit einem einzigen Typenträger
AT520774A AT340960B (de) 1973-06-29 1974-06-24 Typentrager-einstellvorrichtung fur schreib- und ahnliche maschinen mit einem einzigen typentrager
ES427680A ES427680A1 (es) 1973-06-29 1974-06-26 Mecanismo de seleccion para una impresora del tipo de ele- mento unico.
DK350974*A DK350974A (en, 2012) 1973-06-29 1974-06-28
BR5389/74A BR7405389D0 (pt) 1973-06-29 1974-06-28 Mecanismo e dispositivo de selecao para uma impressora tipo elemento unico

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US375277A US3892304A (en) 1973-06-29 1973-06-29 Single print element print carrier with self-contained selection function

Publications (1)

Publication Number Publication Date
US3892304A true US3892304A (en) 1975-07-01

Family

ID=23480237

Family Applications (1)

Application Number Title Priority Date Filing Date
US375277A Expired - Lifetime US3892304A (en) 1973-06-29 1973-06-29 Single print element print carrier with self-contained selection function

Country Status (16)

Country Link
US (1) US3892304A (en, 2012)
JP (1) JPS5314009B2 (en, 2012)
AT (1) AT340960B (en, 2012)
AU (1) AU473005B2 (en, 2012)
BR (1) BR7405389D0 (en, 2012)
CA (1) CA1005781A (en, 2012)
CH (1) CH570270A5 (en, 2012)
DE (1) DE2429931C3 (en, 2012)
DK (1) DK350974A (en, 2012)
ES (1) ES427680A1 (en, 2012)
FR (1) FR2234992B1 (en, 2012)
GB (1) GB1436668A (en, 2012)
IL (1) IL44924A (en, 2012)
IT (1) IT1010172B (en, 2012)
NL (1) NL175889C (en, 2012)
SE (1) SE399019B (en, 2012)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3983984A (en) * 1975-06-26 1976-10-05 International Business Machines Corporation Ball and groove motion converting apparatus and typewriter selection apparatus embodying same
US4008794A (en) * 1975-01-16 1977-02-22 Triumph Werke Nurnberg A.G. Type carrier print deflection blocking means for a single-element printer
US4022312A (en) * 1975-12-24 1977-05-10 International Business Machines Corporation Semi-automatic centering control
US4046246A (en) * 1974-11-27 1977-09-06 Lrc, Inc. Serial impact calculator printer
US4059184A (en) * 1977-01-03 1977-11-22 International Business Machines Corporation Single print element selection apparatus with multiple selection inhibiting means
DE2812057A1 (de) * 1977-03-25 1978-09-28 Silver Seiko Druckeinrichtung
US4218151A (en) * 1976-10-14 1980-08-19 Lrc, Inc. Serial impact calculator printer
US4277188A (en) * 1979-07-05 1981-07-07 International Business Machines Corporation Direct keyboard controlled rack shift device for a single element typewriter
US4297041A (en) * 1979-04-02 1981-10-27 International Business Machines Corporation Variable cam profile selection system for single element typewriter
US4302118A (en) * 1977-05-27 1981-11-24 International Business Machines Corporation Typewriter cartridge and feed mechanism therefor
US4351618A (en) * 1979-12-26 1982-09-28 International Business Machines Corporation Selection controlled print impression control for single element impact printers

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4991341A (en, 2012) * 1972-12-29 1974-08-31

Citations (7)

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Publication number Priority date Publication date Assignee Title
US2774816A (en) * 1953-04-27 1956-12-18 Kleinschmidt Lab Inc Printing telegraph receiver
US3151547A (en) * 1961-01-27 1964-10-06 Hamann Rechenmaschinen G M B H Oscillating print wheels on movable carriage
US3302765A (en) * 1959-10-14 1967-02-07 Ibm Character selection for single element printing mechanism employing cam pairs
US3455428A (en) * 1967-06-07 1969-07-15 Nippon Electric Co Typewriter receiver means
US3572486A (en) * 1967-11-28 1971-03-30 Grundig Emv Pneumatic setting arrangement for a type head
US3625331A (en) * 1968-06-20 1971-12-07 Triumph Werke Nuernberg Ag Type head positioning apparatus
US3666070A (en) * 1970-06-29 1972-05-30 Ibm Differential mechanism for positioning a type character on a type element

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Publication number Priority date Publication date Assignee Title
US752795A (en) * 1904-02-23 Type writer
US1932763A (en) * 1932-05-12 1933-10-31 Int Communications Lab Inc Mechanism for high speed tickers
US3352398A (en) * 1966-06-29 1967-11-14 Ibm Character selection mechanism without return to home position

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2774816A (en) * 1953-04-27 1956-12-18 Kleinschmidt Lab Inc Printing telegraph receiver
US3302765A (en) * 1959-10-14 1967-02-07 Ibm Character selection for single element printing mechanism employing cam pairs
US3151547A (en) * 1961-01-27 1964-10-06 Hamann Rechenmaschinen G M B H Oscillating print wheels on movable carriage
US3455428A (en) * 1967-06-07 1969-07-15 Nippon Electric Co Typewriter receiver means
US3572486A (en) * 1967-11-28 1971-03-30 Grundig Emv Pneumatic setting arrangement for a type head
US3625331A (en) * 1968-06-20 1971-12-07 Triumph Werke Nuernberg Ag Type head positioning apparatus
US3666070A (en) * 1970-06-29 1972-05-30 Ibm Differential mechanism for positioning a type character on a type element

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4046246A (en) * 1974-11-27 1977-09-06 Lrc, Inc. Serial impact calculator printer
US4008794A (en) * 1975-01-16 1977-02-22 Triumph Werke Nurnberg A.G. Type carrier print deflection blocking means for a single-element printer
US3983984A (en) * 1975-06-26 1976-10-05 International Business Machines Corporation Ball and groove motion converting apparatus and typewriter selection apparatus embodying same
US4022312A (en) * 1975-12-24 1977-05-10 International Business Machines Corporation Semi-automatic centering control
US4218151A (en) * 1976-10-14 1980-08-19 Lrc, Inc. Serial impact calculator printer
US4059184A (en) * 1977-01-03 1977-11-22 International Business Machines Corporation Single print element selection apparatus with multiple selection inhibiting means
FR2375991A2 (fr) * 1977-01-03 1978-07-28 Ibm Dispositif de selection de caracteres pour imprimante a element d'impression unique
DE2812057A1 (de) * 1977-03-25 1978-09-28 Silver Seiko Druckeinrichtung
US4225252A (en) * 1977-03-25 1980-09-30 Silver Seiko Co., Ltd. Character selection for single element printer
US4302118A (en) * 1977-05-27 1981-11-24 International Business Machines Corporation Typewriter cartridge and feed mechanism therefor
US4297041A (en) * 1979-04-02 1981-10-27 International Business Machines Corporation Variable cam profile selection system for single element typewriter
US4277188A (en) * 1979-07-05 1981-07-07 International Business Machines Corporation Direct keyboard controlled rack shift device for a single element typewriter
EP0022171B1 (en) * 1979-07-05 1984-08-22 International Business Machines Corporation Direct keyboard controlled character selection rack shifting device for a single element typewriter
US4351618A (en) * 1979-12-26 1982-09-28 International Business Machines Corporation Selection controlled print impression control for single element impact printers

Also Published As

Publication number Publication date
NL175889B (nl) 1984-08-16
AU473005B2 (en) 1976-06-10
DK350974A (en, 2012) 1975-02-10
JPS5314009B2 (en, 2012) 1978-05-15
IT1010172B (it) 1977-01-10
DE2429931C3 (de) 1980-02-07
FR2234992B1 (en, 2012) 1976-06-25
IL44924A (en) 1977-07-31
ATA520774A (de) 1977-05-15
AU6976174A (en) 1975-12-04
GB1436668A (en) 1976-05-19
DE2429931A1 (de) 1975-01-09
NL175889C (nl) 1985-01-16
JPS5021816A (en, 2012) 1975-03-08
BR7405389D0 (pt) 1975-01-21
NL7407583A (en, 2012) 1974-12-31
IL44924A0 (en) 1974-07-31
DE2429931B2 (de) 1979-05-17
AT340960B (de) 1978-01-10
FR2234992A1 (en, 2012) 1975-01-24
CH570270A5 (en, 2012) 1975-12-15
CA1005781A (en) 1977-02-22
SE7407784L (en, 2012) 1974-12-30
SE399019B (sv) 1978-01-30
ES427680A1 (es) 1976-09-01

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