EP0028539A2 - Ensemble de marteau d'impression - Google Patents

Ensemble de marteau d'impression Download PDF

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Publication number
EP0028539A2
EP0028539A2 EP80303951A EP80303951A EP0028539A2 EP 0028539 A2 EP0028539 A2 EP 0028539A2 EP 80303951 A EP80303951 A EP 80303951A EP 80303951 A EP80303951 A EP 80303951A EP 0028539 A2 EP0028539 A2 EP 0028539A2
Authority
EP
European Patent Office
Prior art keywords
hammer
print
plunger
assembly
actuator
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.)
Granted
Application number
EP80303951A
Other languages
German (de)
English (en)
Other versions
EP0028539B1 (fr
EP0028539A3 (en
Inventor
Andrew Gabor
Richard G. Crystal
Enrique J. Klein
Michiel Frankhuizen
William D. Rempel
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.)
Xerox Corp
Original Assignee
Xerox 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
Priority claimed from US06/091,605 external-priority patent/US4327639A/en
Priority claimed from US06/091,657 external-priority patent/US4324497A/en
Application filed by Xerox Corp filed Critical Xerox Corp
Publication of EP0028539A2 publication Critical patent/EP0028539A2/fr
Publication of EP0028539A3 publication Critical patent/EP0028539A3/en
Application granted granted Critical
Publication of EP0028539B1 publication Critical patent/EP0028539B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • B41J9/00—Hammer-impression mechanisms
    • B41J9/02—Hammers; Arrangements thereof
    • B41J9/04—Hammers; Arrangements thereof of single hammers, e.g. travelling along printing line

Definitions

  • This invention relates to print hammer assemblies and, more particularly, to a print hammer assembly employing an electromagnetic actuator to drive a hammer element against an adjacent print element, to thereby cause the print element to strike an adjacent platen.
  • Such print hammer assemblies are used in impact serial printers of the type including a platen, a plurality of print elements and a marking medium interposed between the print elements and the platen.
  • An example of an impact serial printer of this type is disclosed in US Patent No 4 091 911, whereas an example of a print hammer assembly used in such a printer is disclosed in US Patent No 4 037 532.
  • the print hammer assembly disclosed in US Patent No 4 037 532 includes a guide housing through which a hammer element is propelled upon being forced in a forward direction by urging of an armature of an electromagnetic actuator following energization thereof.
  • the electromagnetic actuator is of a conventional type, wherein a portion of the armature is normally spaced apart from each of a pair of legs of a C-shaped yoke, the connecting portion of which contains an electrically conductive coil wound thereon. A gap is thus defined between the armature and each leg.
  • the magnetic field created through each gap forces the armature into contact with the two legs. This movement in turn propels the hammer element through its guide housing in order to impact an adjacent print element, and any interposed recording medium (e.g. paper) and marking material (e.g. inked ribbon) against an adjacent platen.
  • any interposed recording medium e.g. paper
  • marking material e.g. inked ribbon
  • the initial gap distance with the armature in a non-energized position must be precisely adjusted so that the requisite force is achieved upon impact of the armature against the actuator legs, to thereby fire the hammer element with the requisite level of force against the print element.
  • Printers where the dwell time of a print element forcing a marking medium against an adjacent platen due to the force of a hammer element against the print element can be increased by increasing the mass of the hammer element. This necessarily increases the quantity of marking material released.
  • this arrangement has the disadvantage of increasing the flight time of the hammer element, thereby correspondingly decreasing the maximum printing speed.
  • a further disadvantage is that of increasing the kinetic energy of impact, which may result in decreased life of the print elements, or require that the print elements be fabricated of a more durable, and thus more costly, material.
  • the platen is inclined in a vertical plane from left to right, the top area of print elements impacting the left portion of the platen might be at least partially deleted, the reverse being true with respect to impacts occurring at the right portion of the platen. This, of course, will lead to an uneven, and perhaps unintelligible print.
  • the present invention is intended to provide a print hammer assembly in which those disadvantages of known assemblies may be alleviated.
  • the assembly of the invention is characterised by a structure having one of the five features enumerated below.
  • a print hammer assembly comprising a support structure having a hammer element supported at a first location thereon and a plunger supported at a second location thereon; an electromagnetic actuator including a pair of magnetizable members displaced apart a predetermined distance to define a space of sufficient dimensions to enable the movement of said plunger therethrough, said actuator including first means capable of being selectively energized for creating a magnetic field in said space to control the movement of said plunger through said space; and second means for'movably mounting said support structure adjacent said electromagnetic actuator such that said plunger is in a position to be forced through said space without touching either magnetizable member upon energization of said first means, whereby said support structure and thus said hammer element will each be moved in a respective predetermined direction and predetermined speed upon energization of said first means.
  • the relative distance between the plunger and each of the magnetizable members is not critical, since the total force will be substantially the same regardless of whether or not these two distances differ. More specifically, the driving force is related to the addition of the two gap distances on either side of the plunger and the geometry of the plunger. If the distance between plunger and each of the magnetizable members is different, the driving force will essentially be the same as when the plunger is centered, since the sum of the two distances will always be the same.
  • a print hammer assembly comprising a first mass; a second mass including a hammer element; a hammer actuator capable when energized of directing said hammer element under force toward an adjacent platen; and means coupled between said first mass and second mass and cooperating with said first mass for increasing the dwell time of said hammer element against said platen or an interposed print element against said platen in response to a single energization of said actuator.
  • the mass of the hammer element is not increased to effect an increased dwell time. Rather, a dual mass system is employed, wherein the means for coupling together the two masses includes means cooperating with the first mass for increasing the dwell time. There is thus no decrease in the flight time of the hammer element and increase in kinetic energy of impact.
  • a print hammer assembly comprising a support structure defining a first mass and including a plunger at a first location thereon; a second mass including a hammer element; first means for coupling said second mass to said support structure at a second location thereon; and second means for movably mounting said support structure with its plunger adjacent and electromagnetic actuator capable of being selectively energized such that, when said actuator is energized, the resultant magnetic field acting upon said plunger will cause said plunger and thus said support structure and hammer element to each travel along predefined paths at predetermined speeds, said first means including third means cooperating with said first mass for increasing the dwell time of said hammer element against an adjacent platen or an interposed print element against said platen in response to a single energization of said actuator.
  • a spring assembly is used to couple the first mass, which includes the support structure, to the second mass, which includes the hammer element.
  • a print hammer assembly comprising a hammer element; a hammer actuator capable when energized of directing said hammer element under force toward an adjacent platen; and means coupled to said hammer element for causing said hammer element to impact an adjacent platen or an interposed print element against said platen more than once in response to a single energization of said actuator.
  • the provision of multi-impact per single energization also contributes to a reduction in noise, since the peak impact forces are less. Further, the two impacts occur relatively rapidly, thereby reducing or avoiding settling of the print element and incumbent in accuracy problems. Still further, there is no transverse movement of the print element between multiple strikes per single energization which could cause "ghosting" and the like, due to the control achieved by impacting more than once per single energization.
  • the multi-impact approach of this invention is less susceptable to voids of the marking medium in the printed character, i.e., the second impact fills in at least some of the voids that may have been left in the printed character following the first impact.
  • This advantage provides another basis for using lower cost print elements.
  • a print hammer assembly comprising a hammer element; a hammer actuator capable when energized of directing said hammer element under force toward an adjacent platen; and means coupled to said hammer element for altering the location of maximum impact force of said hammer element against said platen or an interposed print element against said platen, said means for altering including a plurality of adjacent, non-parallel spring members each coupled at one end to said hammer element.
  • a pair of normally planar leaf springs are employed.
  • the effect of altering the location of maximum impact force following initial impact may be amplified over the effect achieved by using parallel leaf springs.
  • This is accomplished due to the trapezoidal configuration of the offset leaf springs as connected to the hammer element at one end and to support structure at the other end.
  • the trapezoidal configuration imparts a more pronounced shift in maximum impact force location following initial impact than would a strict parallelogram formed by parallel leaf springs. Consequently, more pronounced misalignments of the platen axis may be compensated for through the use of offset leaf springs in the arrangement above-described.
  • a print hammer assembly 10 in accordance with the present invention is shown in Figure 1 mounted to a carriage assembly 12, which may be of the general type disclosed in the aforementioned U.S. Patent No. 4,037,532.
  • the carriage assembly 12 is thus adapted to transport not only the hammer assembly 10, but also a rotable print wheel 14 of the "daisy-wheel” type and a ribbon cartridge (not shown) to selected positions along a predefined linear path parallel to the axis of rotation of a cylindrical support platen 16 mounted adjacent the carriage assembly 12.
  • the carriage assembly 12 comprises an outer carriage frame 18 and an inner carriage frame 20.
  • the inner carriage frame 20 may be pivotably mounted to the outer carriage frame 18 by means of a suitable pivot bolt 22 extending through the side walls of the frames 18 and 20.
  • the outer carriage frame 18 is preferably fixed in position in a manner to be described below, and the inner carriage frame 20 is pivotable about bolt 22 relative to frame 18. This pivoting action enables replacement and substitution of print wheels in a manner well known in the art.
  • Suitable means (not shown) are provided for locking the inner carriage frame 20 in each of two positions, i.e., a print wheel loaded position (shown in Figure 1) and a print wheel loading position (not shown), wherein the frame 20 would be pivoted clockwise relative to the position shown in Figure 1.
  • the outer carriage frame 18 has a pair of aligned openings 24 formed in the respective side walls of frame 18 adjacent the front end of the carriage assembly 12, and a pair of aligned recesses 26 formed in such respective side walls adjacent the rear end of the carriage assembly 12.
  • the openings 24 and recesses 26 are each adapted to receive in locked relation a linear bearing assembly (not shown) which may be of the type disclosed in U.S. Patent No. 3,985,404.
  • the pair of linear bearing assemblies are adapted to receive a corresponding pair of guide rails (not shown) mounted parallel to the axis of the platen 16 and along which the carriage assembly 12 rides.
  • a print wheel motor 28 is mounted by suitable means (not shown) to the inner carriage frame 20.
  • the motor 28 controls the speed and direction of rotation of the print wheel 14 in order to bring a desired print or character element 30 thereon to a stationary printing position in alignment with the platen 16 and a hammer element 32 included in the hammer assembly 10.
  • the motor 28 has a shaft 34 projecting forwardly of the inner carriage frame 20.
  • a hub portion 36 forms part of the shaft 34 and is adapted to be received in the central opening (not shown) of the print wheel 14.
  • An exemplary print wheel is generally disclosed in U.S. Patent No. 3,954,163.
  • the hammer assembly 10 includes a support structure or frame 38 which defines a first mass and is desirably of generally trapeziodal shape with a pair of inwardly projecting finger portions 40 and 42 coupled at their upper ends by a bridge portion 44.
  • a plunger 46 is attached to the outer surface of the bridge 44, or formed as an integral part thereof, which is a plunger 46, which is desirably of a ferromagnetic material, such as soft iron.
  • the finger portions 40 and 42 are coupled at their lower ends by generally U-shaped attachment portion 48 having opposing side wall flange portions 50 and 52.
  • the flange portions 50 and 52 include respective aligned openings 51 and 54 formed therein.
  • the openings 51 and 54 are adapted to accommodate a pivot rod (not shown) that projects through both openings 51 and 54 and a corresponding pair of openings 56 ( Figure 1) in the side walls of the inner carriage frame 20. In this manner, the support frame 38 is pivotably mounted to the inner carriage frame 20.
  • the side wall flange portions 52 and 50 of the attachment portion 48 further include respective aligned openings 53 and 55 formed therein. Each such opening is adapted to retain an end of one of a pair of springs 57 (only one shown in Figure 1).
  • the other ends of the springs 57 are mounted to the inner frame 20.
  • the springs 57 cooperate to bias the support frame 38 in a clockwise direction (as shown in Figure 1) such that the support frame 38 is normally biased against a stop (not shown) also mounted to the inner frame 20.
  • the support frame 38 may be pivoted counterclockwise about the pivot rod through openings 56 against the bias of springs 57 upon energization of an electromagnetic actuator 59 forming part of the hammer assembly 10 in a manner to be described below.
  • the hammer assembly 10 further includes the hammer element 32, which forms part of a second mass 58 that is coupled to the support frame 38 by at least one, and preferably two, leaf springs 60 and 62.
  • the hammer element 32 preferably has a grooved impacting surface 33 that is matable with a corresponding wedge (not shown) formed on the rear surface of each character element 30. In this manner, minor misalignments between the hammer element and the selected character element can be corrected.
  • the hammer assembly 10 further includes the electromagnetic actuator or solenoid 59.
  • the solenoid 59 has a C-shaped yoke 74 with a pair of depending legs 76 and 78 each containing an electrically conductive coil 80 and 82, respectively, mounted thereon.
  • the space 84 between the portion of each leg 76 and 78 projecting downwardly from the respective coil 80 and 82 mounted thereon is of sufficient dimensions to accommodate the plunger 46 therein, as shown in Figure 3. With the plunger 46 positioned within the space 84, gaps 86 and 88 are defined between the sides of the plunger 46 and the adjacent legs 76 and 78, respectively.
  • the gaps 86 and 88 need not be identical in dimensions, thereby reducing the necessity of critical adjustments with respect thereto. Additionally, the spacing 85 between the upper surface of the plunger 46 and the lower surfaces of the coils 80 and 82 is not critical. The reasons for these non-critical relationships will be described in more detail below.
  • the solenoid 59 is mounted to the inner carriage frame 20 by affixing, through a pair of screws 90, the legs 76 and 78 to a solenoid frame 92, which is itself affixed by means (not shown) to the side walls of the inner carriage frame 20.
  • the support frame 38 and solenoid 59 are normally positioned relative to one another such that a front surface 94 of the plunger 46 normally lies just to the rear of the legs 76 and 78 in alignment with the space 84.
  • the plunger 46 begins to move through the space 84, thereby causing the support frame 38 to pivot about rod 56 and thus hammer element 32 to move toward the platen 16.
  • the hammer element 32 will engage the rear surface of the print element 30 and begin forcing it toward the platen.
  • the hammer element 32 will force the print element 30 and an interposed marking medium and record medium, such as an inked ribbon and paper (both not shown), against the platen 16.
  • the hammer element 32, and thus print element 30, will each experience a first rebound a predetermined distance from the platen 16.
  • the rebound distance of the hammer element 32 is determined by the stiffness and length of the springs 60 and 62, as well as by the ratio of the two masses separated by the springs 60 and 62, and the force of impact, whereas the rebound of the print element 30 is determined by the resiliency of the print wheel spoke bearing the print element 30 and force of theimpact.
  • the hammer element 32 will rebound a second time, mainly due to the energy released after impact by the viscoelastic material of platen 16. Additionally, the plunger 46 and thus support frame 38 will continuetheir retract due to the bias of the springs 57 and prior deenergization of the solenoid 59. It must be made clear that the solenoid 59 can be deenergized at any point in time following initial energization, provided the forward driving force imparted to the hammer element 32 is sufficient to achieve the desired multi-impact and consequent desired release of marking material.
  • the overall dwell time of the print element 30 against the platen 16 may be increased by continuously energizing the solenoid 59, including for a finite time after the second impact, thereby further increasing the total quantity of marking material (e.g., ink) released.
  • the dwell time of the first impact may also be increased by stiffening the springs 60 and 62 or increasing the mass of the hammer element 32 and/or the plunger 46. If desired, the springs 60 and 62 may be stiff enough so that there is no rebound of the hammer element 32 at ail following initial impact. In accordance with the preferred embodiment, however, two distinct impacts are preferred.
  • Oscilloscope traces showing the relationships among travel of the hammer element 32, level of current flow through the coils 80 and 82, level of impact force by the hammer element 32, and time, are shown in Figures 9 and 10, for two different profiles of coil current.
  • Hammer element travel was measured with an optoelectric device in which hammer element movement is proportional to output voltage, as shown in Figures 9 and 10.
  • Current flow was measured with a current probe measuring current through the solenoid coils 80 and 82.
  • impact force was measured by piezo-electric force transducer positioned beneath the platen covering.
  • Yet another feature of the hammer assembly 10 is occasioned by the parallelogram defined by the pair of parallel springs 60 and 62 connected at one end to the mass 58, which includes tha hammer element 32, and at its other end to the attachment portion 48 of the support frame 38, which defines an additional mass.
  • the hammer element 32 could impact the print element 30 against the platen 16 at different impact angles for each of the multiple (e.g., two) impacts as described above. Whether or not this "heel-toe" effect actually takes place depends upon the stiffness of the leaf springs 60 and 62 and the overall realtionship of the springs to the two masses to which they are connected.
  • a trapezoidal configuration is thus defined by the springs 60'and 62', mounting blocks 64', 66' and 68', and the attachment portion 48 of the support frame 38 to which the lower ends of the springs 60' and 62' are mounted by suitable interposed mounting blocks (not shown).
  • This trapezoidal shape has been found to amplify the counter-clockwise movement, or "heel-toe" effect.
  • the heel-toe effect reduces the need for critical adjustments of the platen 16 to insure that its axis of rotaion is completely parallel to the rails (not shown) on which the carriage assembly 12 rides. For example, if the platen axis is skewed relative to the rails in a vertical direction, the top half of characters might not be printed at one end of the paper while the bottom half might be deleted from the other end.
  • By striking each print element twice, once low and once high, minor misalignments in a vertical direction will be compensated for in the embodiment of Figures 1-6, and more major misalignments will be compensated for in the embodiment of Figures 7 and 8.

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  • Impact Printers (AREA)
EP19800303951 1979-11-05 1980-11-05 Ensemble de marteau d'impression Expired EP0028539B1 (fr)

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
US9165879A 1979-11-05 1979-11-05
US9164579A 1979-11-05 1979-11-05
US06/091,605 US4327639A (en) 1979-11-05 1979-11-05 Print hammer assembly with multi-location impacts
US91645 1979-11-05
US91605 1979-11-05
US06/091,657 US4324497A (en) 1979-11-05 1979-11-05 Print hammer assembly with amplified multi-location impacts
US9164679A 1979-12-19 1979-12-19
US91646 1979-12-19
US91658 1987-09-01
US91657 1987-09-01

Publications (3)

Publication Number Publication Date
EP0028539A2 true EP0028539A2 (fr) 1981-05-13
EP0028539A3 EP0028539A3 (en) 1982-05-26
EP0028539B1 EP0028539B1 (fr) 1986-04-09

Family

ID=27536610

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19800303951 Expired EP0028539B1 (fr) 1979-11-05 1980-11-05 Ensemble de marteau d'impression

Country Status (2)

Country Link
EP (1) EP0028539B1 (fr)
DE (1) DE3071538D1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0139903A1 (fr) * 1983-09-14 1985-05-08 International Business Machines Corporation Mécanisme de marteau pivotant d'impression actionné par solénoide
US4525086A (en) * 1983-09-14 1985-06-25 International Business Machines Corporation Solenoid actuated pivotal printer hammer mechanism
EP0207781A1 (fr) * 1985-07-02 1987-01-07 Xerox Corporation Mécanisme à impact pour une imprimante
EP0209291A1 (fr) * 1985-07-02 1987-01-21 Xerox Corporation Imprimante à impact
EP0210000A1 (fr) * 1985-07-02 1987-01-28 Xerox Corporation Imprimante à impact
EP0226398A2 (fr) * 1985-12-05 1987-06-24 Xerox Corporation Imprimante à percussion à force de frappe oblique
US4737043A (en) * 1985-07-02 1988-04-12 Xerox Corporation Impact mechanism for quiet impact printer
EP0538998A2 (fr) * 1991-10-24 1993-04-28 Smith Corona Corporation Mécanisme d'impression par impact silencieux
EP0540145A2 (fr) * 1991-10-28 1993-05-05 Smith Corona Corporation Mécanisme d'impression à marteau avec insonorisation

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3472352A (en) * 1967-06-28 1969-10-14 Burroughs Corp High speed serial printer
US3643594A (en) * 1968-06-11 1972-02-22 Sits Soc It Telecom Siemens Print hammer for high-speed printer

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3472352A (en) * 1967-06-28 1969-10-14 Burroughs Corp High speed serial printer
US3643594A (en) * 1968-06-11 1972-02-22 Sits Soc It Telecom Siemens Print hammer for high-speed printer

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0139903A1 (fr) * 1983-09-14 1985-05-08 International Business Machines Corporation Mécanisme de marteau pivotant d'impression actionné par solénoide
US4525086A (en) * 1983-09-14 1985-06-25 International Business Machines Corporation Solenoid actuated pivotal printer hammer mechanism
US4678355A (en) * 1985-07-02 1987-07-07 Xerox Corporation Print tip contact sensor for quiet impact printer
EP0209291A1 (fr) * 1985-07-02 1987-01-21 Xerox Corporation Imprimante à impact
EP0210000A1 (fr) * 1985-07-02 1987-01-28 Xerox Corporation Imprimante à impact
EP0207781A1 (fr) * 1985-07-02 1987-01-07 Xerox Corporation Mécanisme à impact pour une imprimante
US4681469A (en) * 1985-07-02 1987-07-21 Xerox Corporation Quiet impact printer
US4737043A (en) * 1985-07-02 1988-04-12 Xerox Corporation Impact mechanism for quiet impact printer
EP0226398A2 (fr) * 1985-12-05 1987-06-24 Xerox Corporation Imprimante à percussion à force de frappe oblique
EP0226398A3 (fr) * 1985-12-05 1988-12-14 Xerox Corporation Imprimante à percussion à force de frappe oblique
EP0538998A2 (fr) * 1991-10-24 1993-04-28 Smith Corona Corporation Mécanisme d'impression par impact silencieux
EP0538998A3 (en) * 1991-10-24 1993-06-23 Smith Corona Corporation Quiet impact printer mechanism
EP0540145A2 (fr) * 1991-10-28 1993-05-05 Smith Corona Corporation Mécanisme d'impression à marteau avec insonorisation
EP0540145A3 (en) * 1991-10-28 1993-06-23 Smith Corona Corporation Printing mechanism with print hammer having noise dampener

Also Published As

Publication number Publication date
EP0028539B1 (fr) 1986-04-09
EP0028539A3 (en) 1982-05-26
DE3071538D1 (en) 1986-05-15

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