US3759456A - Ribbon feed and correction device for a high speed printer - Google Patents

Ribbon feed and correction device for a high speed printer Download PDF

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Publication number
US3759456A
US3759456A US00155925A US3759456DA US3759456A US 3759456 A US3759456 A US 3759456A US 00155925 A US00155925 A US 00155925A US 3759456D A US3759456D A US 3759456DA US 3759456 A US3759456 A US 3759456A
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Prior art keywords
web
pawl
cam
ratchet
sensing
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US00155925A
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English (en)
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O Moneagle
K Svatek
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International Business Machines Corp
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International Business Machines Corp
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H23/00—Registering, tensioning, smoothing or guiding webs
    • B65H23/02—Registering, tensioning, smoothing or guiding webs transversely
    • B65H23/032—Controlling transverse register of web
    • 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
    • B41J17/00—Mechanisms for manipulating page-width impression-transfer material, e.g. carbon paper
    • B41J17/02—Feeding mechanisms
    • B41J17/14—Automatic arrangements for reversing the feed direction
    • 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
    • B41J17/00—Mechanisms for manipulating page-width impression-transfer material, e.g. carbon paper
    • B41J17/30—Constructions of guides for the impression-transfer material

Definitions

  • ABSTRACT A ribbon correction device aligns a web by deliberately skewing a pair of pivoted winding spools to steer the ribbon continuously toward a given median point along the axis of a spool.
  • the device automatically compensates for the effect of a change in the direction of rotation of the winding spool, by means of a single sensing device.
  • the high speed printers employed as input/output equipment for computers run at speeds of 2,000 plus printed lines per minute.
  • the ribbons employed in such printers are as wide as the document printed, and must move longitudinally across the print line at speeds comparable to that of the document itself.
  • Such ribbons 'repeatedly'exposed to high impact hammer blows during the course of the printing operation, have a wear rate which exceeds that in less demanding applications.
  • trail-off correction techniques which induce tension gradients across the width of the ribbon in order to correct for lateral displacements, the wear rate of the ribbon increases.
  • An object of the invention is to provide a simplified A SUMMARY OF THE INVENTION
  • the trail-off of the broad ribbon web in a high speed printer is simply and effectively compensated for by the subject invention, by means of controllably changing the state of relative skew between the play-out spool and the take-up spool.
  • the play-out spool and the takeup spool are pivotally and rotatably mounted in a twistable frame such that alternate states of twist in the frame will impart alternate states of relative skew between the spools.
  • Each of the two spools can alternately assume the role of take-up spool or play-out spool.
  • the spools are rotatably driven by a motor, and an end of web reversing means reverses the direction of drive of the motor when the end of the web is detected before playing off either spool.
  • the twist which imparts the trail-off correction is brought about by a rotary-to-reciprocating motion conversion means which is intermittently driven by an intermittent clutch means at such times when a web axial-position detection means senses a change in the axial position of the web as it is wound upon either the first or the second spool.
  • the web is thereby steered into alternate directions of axial motion as the take-up spool and the playout spool assume their alternate states of relative skew, as is controlled by the web axial-position detection means.
  • the invention accomplishes the web axial trail-off correction function in an improved manner by not imparting a gradient in the longitudinal tension across the web, thus conferring a longer life to printer ribbons. Furthermore, the axial trail-off correction function is accomplished by the invention with a smaller number of mechanical parts than has heretofore been accomplished by prior art devices. In addition, the invention accomplishes the trail-off correction function automatically, without regard to changes in the winding direction.
  • FIG. 1 is a simplified diagram of the relative position of the first and second winding spools during botha winding and unwinding operation.
  • FIG. 1a through ld show the preferred web winding configuration.
  • FIG. 1e shows an alternate web winding configuration
  • FIG. 2 is a detailed drawing indicating the relative position of the spools, correction cam, and sensing arm.
  • FIG. 3 is a semi-schematic diagram depicting the working relationship of the elements of the invention.
  • FIG. 4 depicts in detail the relative positions of the double pawl clutch, correction cam, sensing cam, sensing arm, web and lower spool.
  • FIG. 5 is a timing diagram indicating how the trail-off correction is effected for counter-clockwise motion of the lower spool.
  • FIG. 6 is a timing diagram indicating how the trail-off direction is effected during clockwise rotation of the lower spool.
  • FIG. 7 is a timing diagram indicating how the 180 phase shift correction is effected when the edge of the web is not at the reference point.
  • FIG. 8. is a timing diagram indicating how the simultaneous 180 phase shift correction and the web trailoff correction are effected when the edge of the web is at the reference point at the time of the change in direction of rotation.
  • FIG. 9 is an exploded view of the elements in the ribbon correction device.
  • the trail-off correction is accomplished by imparting a relative skew between the take-up and the play-off spools.
  • a twistable frame means mounted to the machine frame is employed.
  • the spools are pivotally and rotatably mounted in a first base plate which is rigidly attached and a second base plate which is pivotally mounted to the machine frame.
  • the pivot point for the second base plate is located substantially midway between the mounting position for the first and second spools.
  • FIG. 1 is a simplified diagram showing the relative position of the spools during the trail-off correction sequence.
  • upper spool 2 and lower spool 4 are rotatably and pivotally mounted on fixed plate 6 and are rotatably and pivotally mounted in pivoted plate 8 such that when plate 8 is rotated about the pivot 10, spools 2 and 4 assume a skew position with respect to one another.
  • the web 16 is wound about the upper spool 2 in a clockwise direction and proceeds thence over backing surface 26 and is then wound in counterclockwise fashion about the lower spool 4.
  • FIGS. la through d The preferred embodiment for the wound web configuration is that shown in FIGS. la through d, that is where the web winds off of the first spool and onto the second spool at those respective spool surfaces closest to one another.
  • FIG. 1c shows an alternate embodiment where the web is wound off of the first spool and onto the second spool at those respective spool surfaces which are at the extreme distances from one another.
  • the trail-off correction sequence for both configurations will be the same since the relative direction of rotation of the upper and lower spools at any one time is always the same for each of these configurations.
  • FIG. 2 shows an end view of the twistable'frame means and the relative positions of the web, the web axial-position detection means, the end-of-web reversing means, the driving means and the rotary-toreciprocating motion conversion means.
  • the web wound between the upper and lower spools, is periodically sampled by the web axial-position detection means for its presence or absence at a reference point midway between the extreme axial displacements of the web.
  • the amplitude of the periodic displacements of the detection means changes, ultimately causing the rotary-to-reciprocating motion conversion means to displace the twistable frame means into its alternate state of twist.
  • the state of relative skew between the first and second spools is thereby changed imparting the desired trailoff correction to the axial motion of the web.
  • the lower spool 4, onto which is wound the web 16 is concentric with the shaft 36 for the correction cam 32.
  • the sensing arm 38 whose oscillations are derived from the rotary motion of shaft 36, causes the sensing finger 20b to periodically pass through the reference point 40 such that when the web is absent from reference point 40, the sensing finger will remain in the standing position 201). However, when the web is present over reference point 40, the sensing finger will assume the fallen position 200.
  • the consequent change in the magnitude of the displacement of the sensing arm 38 institutes a rotation of correction cam 32 effecting the displacement of the pivot plate 8 about pivot thus effecting the change in the relative skew of spools 2 and 4.
  • FIG. 2 shows the relative position of the ribbon reversing arm 46, motor reversing switch 50, the motor for upper spool 2 and the motor for lower spool 4.
  • the ribbon drive is accomplished by two motors designated upper 112 and lower 110. While one motor is driving or winding, a limited voltage is provided to the opposite motor to control the ribbon tension. The ribbon only moves during printing and stops approximately 120 ms after the end of printing, at which time one half of the voltage is supplied to both ribbon drive motors, urging them in opposite directions to maintain tension in the ribbon.
  • the ribbon reversing function is accomplished by the pivoted reversing arm 46 which is shifted by reversing bars attached to each end of the ribbon near the point were the ribbon attaches to the respective spools 2 and 4. When the arm 46 is operated, it in turn actuates motor reversing switch 50 that determines which motor will wind the ribbon in the proper direction.
  • the ribbon reversing arm 48 is pivoted at 52.
  • FIG. 3 the semi-schematic diagram depicts the working relationship of the various elements of the invention.
  • the sectional view is taken along the axis of pivot 10 in FIG. 1.
  • Mounted on machine frame 120 is fixed base plate 6 and pivoted base plate 8, together which make up the twistable frame means.
  • the pivoted base plate 8 can undergo angular displacements with respect to the machine frame 120, about the pivot 10.
  • the lower spool shaft 36 is mounted in fixed base plate 6 through a universal coupling 122 and is mounted in pivoted base plate 8 by universal coupling 124 such that said twistable frame means can undergo twistdisplacements without binding the shaft 36.
  • Driving means 110 is mounted to the twistable frame means and drives shaft 36 through universal coupling 122.
  • correction cam shaft 36a rotatably mounted on the twistable frame means and not directly connected to the lower spool shaft 36, carries the pawl carrier 86 and the correction cam 32, which rotate in unison with the correction cam shaft 36a. Pivotally mounted on pawl carrier 86 are pawls 90 and 94.
  • Link lever 72 connected with sensing arm 38, periodically actuates pawls 90 and 94 in timed relation with the rotation of ratchet 54.
  • link lever 72 causes pawl 90 or 94 to engage ratchet 54.
  • Pawl carrier 86 is thereby caused to rotate with the engaged ratchet until the detent 104 causes the-pawl carrier 86 to cease its rotation after 180, at which time link lever 72 causes the engaged pawl 90 or 94, to disengage the ratchet 54.
  • the correction cam follower 34 within which the correction cam 32 rotates, is rigidly fixed to the machine frame.
  • correction cam 32 rotates within cam follower 34, the correction cam shaft 36a, and therewith the twistable frame means, undergoesa lateral displacement with respect to the machine frame, base plate 8 pivoting about pivot 10. Since correction cam 32 rotates in unison with pawl carrier 86, when sensing arm 38 causes the pawls or 94 to engage ratchet. 54, pawl carrier 86 thereby undergoes rotation causing correction cam 32 to rotate within correction cam follower 34 by 180. This induces the desired twist displacement in the twistable frame means.
  • the change in the relative skew between the upper and the lower spooling means induced by the twist displacement in the twistable frame means imparts the necessary lateral steering correction to the web as it winds upon either the upper or the lower spool.
  • FIG. 3 has been simplified with respect to the relative position of the parts in the preferred embodiment.
  • the driving means is mounted on the pivoted base plate 8 and the correction cam shaft 36a is hollow, the lower spool shaft 36 passing therethrough and directly connected with the driving means 110.
  • the sensing arm 38, sensing cam follower 66, and link lever 72 together comprise the web, axial-position de tection means.
  • the ratchet 54, the pawl carrier 86 and its associated pawls 90 and 94, together with the detent 104 comprise the intermittent clutch means.
  • the correction cam 32 and the correction cam follower 34 together comprise the rotary-to-reciprocating motion conversion means.
  • the combination of the intermittent clutch means and the rotary-to-reciprocating motion conversion means constitutes the reciprocating drive means.
  • FIG. 4 shows the elements comprising the web axialposition detection means, the intermittent clutch means, and the rotary-to-reciprocating motion conversion means.
  • the web axial-position detection means comprises the sensing cam 60, a sensing arm means, and the sensing finger 20.
  • the sensing arm means comprises the sensing arm 38, link lever 72, spring 34, and lever 82.
  • the intermittent clutch means comprises the ratchet 54, pawl carrier 86, pawls 90 and 94, and detent 104.
  • the rotary-to-reciprocating motion conversion means comprises the correction cam 32 and the correction cam follower 34.
  • the web axial-position detection means senses the traversal of the edge of the web across the reference point 40, and at such time undergoes a change in the amplitude of its periodic displacements causing the engagement and rotation of the intermittent clutch means. Since the pawl carrier of the clutch means and the correction cam of the rotary-to-reciprocating motion conversion means are mounted together, they rotate in unison and thus impart the desired controlled displacement to the twistable frame means.
  • shaft 36 which is the shaft of the drive motor which is mounted to the pivot plate 8 and which drives the lower spool 4, drives the ratchet 54 and sensing cam 60.
  • Sensing cam 60 has the lobes 62 and 64 diametrically opposed to one another and aligned with the the teeth 56 and 58 of ratchet 54.
  • the lobes 62 and 64 on sensing cam 60 periodically engage the sensing cam follower 66.
  • Sensing cam follower 66 is attached by pin 68 to the sensing arm 38.
  • Sensing arm 38 is pivoted on stud 70 which in turn is mounted on pivot plate 8. Sensing finger 20 mounted on sensing arm 38 and loaded by spring 30 is periodically displaced through the reference point 40. When the web 16, which is drawn across the backing surface 26, covers the reference point 40, the sensing finger collapses thus causing the sensing arm 38 to traverse a larger magnitude displacement than it does when web 16 is absent from reference point 40.
  • the periodic displacements of sensing arm 38 are coupled to link lever 72 through the pin 68.
  • Link lever 72 is biased by spring 74 so that sensing cam follower 66 will always engage sensing cam 60.
  • Link lever 72 is connected to lever 82 through pin 80 and lever 82 is pivoted about stud 84 which in turn is anchored to the plate 8.
  • Pawl carrier 86 is fixedly attached to correction cam 32.
  • Correction cam 32 engages the surface 88 of correction cam follower 34 which is rigidly attached to the machine frame.
  • pawl carrier 86 is counter- '-clockwise pawl 90 which pivots on pin 92 and clockwise pawl 94 which pivots on pin 96.
  • Pawls 90 and 94 are spring loaded in the engagement position by pawl spring 98.
  • Detent pins 100 and 102 engage the detent 104 at 180 intervals on the pawl carrier 86.
  • the assemblage of pawls 90 and 94 mounted on pawl carrier 86, with the detent 104 and ratchet 54, comprises a double pawl clutch.
  • counterclockwise pawl 90 will not engage the teeth 56 or 58 of ratchet 54 as it rotates with the spool 4.
  • sensing finger 20 will remain at a standing position preventing sensing arm 38 from undergoing its larger displacement.
  • lobe 106 of link lever 72 will not contact the tail of counterclockwise pawl 90.
  • the objective of the operation of the invention is to impart a correction to the trail-off direction of the web as it traverses a given median point in the axial direction.
  • the web axial-displacement detection means undergoes a periodic displacement through the reference point.
  • the periodic displacements are larger than when the web is absent from the reference point.
  • the consequent change in the amplitude of the periodic displacements triggers the intermittent clutch means to engage, thereby rotating the correction cam in the rotary-toreciprocating motion conversion means.
  • the motion conversion means induces a twist displacement in the twistable frame means, and thereby a change in the relative skew of the first and second spools upon which the web is wound.
  • the web is thereby steered such that the direction of axial trail-off is reversed, the net eflect of which is to accomplish an even winding of the web onto either spool.
  • FIG. 7 illustrates the sequence of events that occurs when the direction of rotation of the spools is reversed at a time when the web is not at a transition point.
  • Period P1 in FIG. 7 is identical to period P1 in FIG. and period P2 in FIG. 7 is identical to period P2 in FIG. 5 up to the time tl2.
  • the direction of rotation of the lower spool is reversed from counterclockwise to clockwise, as is the direction of rotation of the upper spool.
  • the direction of motion of the web can be seen to immediately reverse, illustrating the 180 phase shift phenomenon at time tl2.
  • Clockwise pawl 94 engages tooth 56 or 58 of ratchet 54 in the first stage of the commencement of clockwise rotation of ratchet 54.
  • Clockwise pawl 94 remains engaged with ratchet 54 until pawl carrier 86 has rotated 180 at which time clockwise pawl 94 engages lobe 106 of link lever 72.
  • sensing arm 38 is undergoing large displacements thus, lobe 106 will be in position to disengage clockwise pawl 94 for every 180 rotation of ratchet 54 until the web undergoes a transition point at t 19.
  • the sequence of events is identical to that in normal clockwise rotation of spool 4, as is shown in FIG. 6.
  • 180 phase shift correction upon a change in the direction of rotation of the v spool is accomplished automatically by virtue of the interaction of the double pawl clutch assembly, the sensing cam, and the sensing arm.
  • FIG. 8 illustrates the sequence of events that occur when the direction of rotation of the spools is reversed at a time when the edge of the web is traversing reference point 40.
  • Periods P1 and P2 in FIG. 8 are identical to periods P1 and P2 in FIG. 5 and period P3 in FIG. 8 is identical to period P3 in FIG. 5 up to the time :14.
  • the direction of rotation of the lower spool is reversed from counterclockwise to clockwise, as is the direction of rotation of the upper spool.
  • the direction of axial motion of the web can be seen to immediately reverse.
  • sensing arm 38 commences its smaller magnitude displacements, causing lobe 108 of link lever 72 to contact the disengage clockwise pawl 94 from its potential engagement position with ratchet 54.
  • Clockwise pawl 94 remains in the disengaged position during the period required for the edge of web 16 to return to reference point 40 under the influence of the reversed direction of rotation of spool 4.
  • sensing arm 38 After the edge of web 16 is detected by sensing finger 20, to have traversed reference point 40, which occurs at time tl6 in FIG. 8, sensing arm 38 recommences its larger magnitude displacements causing lobe 108 to link lever 72 to disengage the tail of clockwise pawl 94, at which time ratchet 54 is engaged and correction cam 32 is rotated for a normal clockwise trail off correction.
  • the nomal clockwise correction sequence obtains as is shown in FIG. 6.
  • the period of time between [14 and r16 in FIG. 8, is the period for suppression of the 180 phase correction.
  • the motor 110 which drives lower spool 4 is mounted on pivot plate 8.
  • Motor 112 also mounted on plate 8 drives the upper spool.
  • Pivot plate 8 rotates about pivot 10 which is affixed to the machine frame.
  • Sensing cam 60 and ratchet 54 are fixedly attached together and are in turn fixedly attached to shaft 36.
  • Pawl carrier 86 to which is fixedly attached correction cam 32, are rotatably mounted on shaft 36.
  • Correction cam follower 88 is mounted at points 114 and 116 to the machine frame and thus serves as the fixed reference point for the lateral displacement of shaft 36.
  • Sensing cam follower 66 mounted on sensing arm 38, is driven by sensing cam 60 such that sensing finger 20 periodically engages the web, when present.
  • Link lever 72 attached to sensing arm 38, oscillates as the sensing arm is actuated by the sensing cam, and successively actuates clockwise pawl 94 and counterclockwise pawl 90 as the shaft 36 rotates.
  • the state of relative skew between the spools as mechanically controlled by the position of the web, causes the web to be evenly wound upon the spools, regardless of the direction of rotation.
  • FIG.9 depicts the ribbon dirve and sense system.
  • the ribbon drive and sense system consists of three functions: the ribbon drive, ribbon reversing and ribbon skew correction.
  • the ribbon drive is accomplished by two motors designated upper 112 and lower 110. While one motor is driving or winding a limited voltage is provided to the opposite motor to control the ribbon tension. The ribbon only moves during printing and stops approximately 120 ms after the end of printing. At this time, one half voltage is supplied to both ribbon drive motors to maintain tension.
  • the ribbon reversing function is accomplished by a pivoted reversing arm 42 which is shifted by reversing bars attached to each end of the ribbon near the point where the ribbon attaches to the spools.
  • a switch 50 that deterl mines the motor that will wind the ribbon in the proper direction.
  • the ribbon reversing arm is pivoted at 52.
  • the ribbon skew correction is accomplished by pivoting the ribbon drive unit to change the line of ribbon winding in relation to the direction of ribbon feed.
  • the operation is controlled by the sensing finger 20 and arm 38.
  • the sensing finger mechanically checks to see if the moving ribbon is beneath it. If the ribbon is under the arm, the movement of the ribbon causes the finger to pivot which in turn allows the arm to drop.
  • the twistable frame means stays in the pivoted position as long as the finger continues to sense the ribbon.
  • the sensing arm again sets the drive pawl and rotates the twistable frame means back to the starting position by turning the correction cam 180.
  • a sensing cam 60 is provided to raise the finger, via the sensing arm, twice each spool revolution, to permit the ribbon to feed under the finger eliminating the possibility of the ribbon rolling up against the finger instead of moving under it.
  • a device for evenly winding a web onto a spool of the type comprising a fixed machine frame, a twistable frame means mounted on said machine frame, said twistable frame means capable of assuming either of two states of twist, a first and a secnd spooling means, said first and second spooling means pivotally and rotatably mounted in said twistable frame means, said two states of twist imparting alternate states of relative skew between said first and said second spooling means, said first spooling means winding said web from said second spooling means and said second spooling means winding said web from said first spooling means, a rotary driving means for rotatably driving said first and second spooling means, a web axial-position detection means, a reciprocating drive means, said reciprocating drive means intermittently actuated by said detection means when a change is de- 65 tected in the axial-position of said web as it is wound upon either said first or said second spooling means, said twist
  • a ratchet means continuously driven by said rotary driving means, a pawl means opposed to said ratchet means and intermittently engagable therewith under the control 5 of said web axial-position detection means,
  • a rotary-to-reciprocating motion conversion means connected to said pawl means, said motion conversion means being intermittently driven by said pawl means when said detection means causes said pawl means to engage said ratchet means,
  • said web axial-position detection means further comprises:
  • a sensing cam rotatably mounted on said twistable frame means and continuously driven by said rotary driving means
  • sensing cam having at least one lobe
  • sensing arm mounted on said twistable frame means and resiliently urged into engagement with said sensing cam, said sensing arm periodically displaced by the lobes on said cam, through an are over said reference point,
  • sensing arm undergoing relatively large displacements when said web is present and relatively small displacements when said web is absent from said reference point
  • said reciprocating drive means further comprises:
  • said ratchet means possessing a number of teeth equal to the number of lobes on said sensing cam
  • said carrier means rotatably mounted on said twistable frame means in a position coaxial with and opposed to said ratchet means
  • said first pawl mounted so as to be resiliently urged into engagement with said ratchet means when said ratchet means undergoes clockwise rotation
  • said second pawl mounted so as to be resiliently urged into engagement with said ratchet means when said ratchet means undergoes counterclockwise rotation
  • a resilient detent means mounted on said twistable frame means and positioned so as to stop the rotation of said pawl carrier means at every 180,
  • said sensing arm periodically contacting and pivot/ally displacing said first and said second pawls, as it is driven by said sensing cam in timed rotation with the rotation of said ratchet means
  • said sensing arm omitting contact with said first pawl during clockwise rotation of said ratchet or omitting contact with said second pawl during counterclockwise rotation of said ratchet, when a change in the magnitude of said periodic displacements of said sensing arm occurs,
  • said pawl carrier means remaining stationary in its new state as long as said periodic sensing arm displacements retain their new magnitude.
  • said reciprocating drive means further comprises:
  • said web being steered into alternate directions of axial motion along said first and second spooling means, by the controlled changes in said relative skew,
  • the rotary driving means further comprises:
  • said first motor when driving said first spooling means so as to wind said web thereupon, being fully energized to advance the web, while said second motor being energized in the direction opposing the advance of the web, at a magnitude of substantially one half that of said first motor, thus imparting a drag force on the web
  • an end-of-web reversing means for detecting the end of the web before it unwinds from the spooling means supplying said web, said reversing means automatically reversing the driving direction of said first and second motors, said second motor becoming fully energized so as to advance the web in the direction reversed to its preceding motion and said first motor becoming energized at one half its preceding magnitude and in the direction opposed to the new direction of advance for the web, whereby said web remains in tension without regard to its direction of advance.
  • the web axial-position detection means further comprises:
  • sensing arm mounted on said twistable frame means so as to be resiliently urged into engagement with said sensing cam
  • sensing arm being periodically lifted and lowered over said reference point by means of said sensing cam
  • said finger means located substantially over said reference point
  • said finger means frictionally engaging said web when present at said reference point, when said cam lowers said sensing arm
  • said finger means following the advancing motion of said web, when frictionally engaging the web causing the finger means to collapse and the sensing arm to undergo a relatively large displacement
  • said finger means remaining in a standing position on a supporting surface for said web, when said web is absent from said reference point, when said sensing cam lowers said sensing arm, thereby limiting the sensing arm to a relatively small displacement
  • sensing arm periodically actuating said pawl means as said sensing cam lifts and lowers said sensing arm
  • said rotary-to-reciprocating motion conversion means being driven by said pawl means when the magnitudes of the periodic displacements of said sensing armchange
  • pawl means further comprises:
  • said carrier means rotatably mounted on said twistable frame means in a position coaxial with and opposed to said ratchet means
  • said first pawl being resiliently urged intoengagement with said ratchet means when said ratchet means undergoes clockwise rotation
  • said second pawl being resiliently urged into engagement with said ratchet means when said ratchet means undergoes counterclockwise rotation
  • a first spool pivotally and rotatably mounted between said plate and said machine frame
  • a second spool pivotally and rotatably mounted between said plate and said machine frame
  • said plate imparting a relative skew between said first and said second spool when displaced about its pivot point
  • a reversible motor mounted on said plate for rotatably driving said first and said second spool in either direction
  • a switching means mounted on said plate for reversing the direction of drive of said motor when the end of said web is detected unwinding from either of said spools;
  • a double pawl clutch rotatably mounted on said plate and continuously driven by said motor;
  • said detection means periodically actuating said double pawl clutch in timed relation with the rotation of said clutch
  • said cam rotatably engaging said cam follower and being intermittently driven by said double pawl clutch when said detection means senses a change in the axial position of said web as it is wound upon either said first or said second spool;
  • pivot plate being driven through an angular displacement about its pivot point as said cam is controllably driven into rotation by said double pawl clutch;
  • said web undergoing a trail-off correction due to the change in the relative skew of the first and second spools as controlled by said detecting means sensing the presence or absence of said web at a reference point substantially midway between the extreme axial displacements of said web;
  • said web may be evenly wound on either said first or said second spool, automatically.

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  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Impression-Transfer Materials And Handling Thereof (AREA)
US00155925A 1971-06-23 1971-06-23 Ribbon feed and correction device for a high speed printer Expired - Lifetime US3759456A (en)

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US15592571A 1971-06-23 1971-06-23

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US (1) US3759456A (enExample)
CA (1) CA971146A (enExample)
FR (1) FR2151260A5 (enExample)
GB (1) GB1364741A (enExample)
IT (1) IT950707B (enExample)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3889893A (en) * 1974-01-14 1975-06-17 Computer Peripherals Ribbon drive and control system
US3902585A (en) * 1973-05-07 1975-09-02 Data Products Corp Electric switch actuated printer ribbon reversing mechanism
US3942735A (en) * 1974-12-26 1976-03-09 Levi Strauss & Co. Viewing table
US4000804A (en) * 1975-02-10 1977-01-04 Ing. C. Olivetti & C., S.P.A. Arrangement for transferring a ribbon from a feed spool to a take-up spool
US4003460A (en) * 1974-06-21 1977-01-18 Honeywell Information Systems, Inc. Type ribbon deskewing means for a type ribbon feed apparatus
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US4919555A (en) * 1987-06-09 1990-04-24 Kabushiki Kaisha Sato Carbon ribbon supply apparatus for a printer
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US20050144330A1 (en) * 2003-12-30 2005-06-30 Richardson John J. Multi-threaded synchronization adapter
US20090078137A1 (en) * 2007-09-20 2009-03-26 Ryobi Ltd. Method of Winding Up Transfer Film and Device for Performing Transfer Printing on Printed Sheets of Paper

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Cited By (15)

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US3902585A (en) * 1973-05-07 1975-09-02 Data Products Corp Electric switch actuated printer ribbon reversing mechanism
US3889893A (en) * 1974-01-14 1975-06-17 Computer Peripherals Ribbon drive and control system
US4003460A (en) * 1974-06-21 1977-01-18 Honeywell Information Systems, Inc. Type ribbon deskewing means for a type ribbon feed apparatus
US3942735A (en) * 1974-12-26 1976-03-09 Levi Strauss & Co. Viewing table
US4000804A (en) * 1975-02-10 1977-01-04 Ing. C. Olivetti & C., S.P.A. Arrangement for transferring a ribbon from a feed spool to a take-up spool
US4173929A (en) * 1977-11-29 1979-11-13 Documation Incorporated Printer ribbon anti-fold mechanism
US4919555A (en) * 1987-06-09 1990-04-24 Kabushiki Kaisha Sato Carbon ribbon supply apparatus for a printer
US20020154206A1 (en) * 2001-04-23 2002-10-24 Ullenius Kenneth F. Ribbon drive and tensioning system for a print and apply engine or a printer
US20050105950A1 (en) * 2001-04-23 2005-05-19 Ullenius Kenneth F. Ribbon drive and tensioning system for a print and apply engine for a printer
US7071961B2 (en) 2001-04-23 2006-07-04 Zih Corp. Ribbon drive and tensioning system for a print and apply engine for a printer
US7079168B2 (en) 2001-04-23 2006-07-18 Zih Crop. Ribbon drive and tensioning system for a print and apply engine or a printer
US20050144330A1 (en) * 2003-12-30 2005-06-30 Richardson John J. Multi-threaded synchronization adapter
US7406698B2 (en) 2003-12-30 2008-07-29 Microsoft Corporation Driver framework component for synchronizing interactions between a multi-threaded environment and a driver operating in a less-threaded software environment
US20090078137A1 (en) * 2007-09-20 2009-03-26 Ryobi Ltd. Method of Winding Up Transfer Film and Device for Performing Transfer Printing on Printed Sheets of Paper
US8205548B2 (en) * 2007-09-20 2012-06-26 Ryobi Ltd. Method of winding up transfer film and device for performing transfer printing on printed sheets of paper

Also Published As

Publication number Publication date
CA971146A (en) 1975-07-15
FR2151260A5 (enExample) 1973-04-13
DE2229906B2 (de) 1977-05-12
GB1364741A (en) 1974-08-29
IT950707B (it) 1973-06-20
DE2229906A1 (de) 1972-12-28

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