EP0032555A1 - Mécanisme compteur ou imprimeur pour le comptage ou le numérotage consécutif - Google Patents

Mécanisme compteur ou imprimeur pour le comptage ou le numérotage consécutif Download PDF

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Publication number
EP0032555A1
EP0032555A1 EP80107725A EP80107725A EP0032555A1 EP 0032555 A1 EP0032555 A1 EP 0032555A1 EP 80107725 A EP80107725 A EP 80107725A EP 80107725 A EP80107725 A EP 80107725A EP 0032555 A1 EP0032555 A1 EP 0032555A1
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EP
European Patent Office
Prior art keywords
printing
wheel
wheels
pressure
printing unit
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
EP80107725A
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German (de)
English (en)
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EP0032555B1 (fr
Inventor
Ulf Koch
Gerhard Nagel
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.)
Esselte Pendaflex Corp
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Esselte Pendaflex Corp
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Publication date
Application filed by Esselte Pendaflex Corp filed Critical Esselte Pendaflex Corp
Priority to AT80107725T priority Critical patent/ATE12368T1/de
Publication of EP0032555A1 publication Critical patent/EP0032555A1/fr
Application granted granted Critical
Publication of EP0032555B1 publication Critical patent/EP0032555B1/fr
Expired legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41K—STAMPS; STAMPING OR NUMBERING APPARATUS OR DEVICES
    • B41K3/00—Apparatus for stamping articles having integral means for supporting the articles to be stamped
    • B41K3/02—Apparatus for stamping articles having integral means for supporting the articles to be stamped with stamping surface located above article-supporting surface
    • B41K3/04—Apparatus for stamping articles having integral means for supporting the articles to be stamped with stamping surface located above article-supporting surface and movable at right angles to the surface to be stamped
    • B41K3/10—Apparatus for stamping articles having integral means for supporting the articles to be stamped with stamping surface located above article-supporting surface and movable at right angles to the surface to be stamped having automatic means for changing type-characters, e.g. numbering devices
    • B41K3/102—Numbering devices
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06M—COUNTING MECHANISMS; COUNTING OF OBJECTS NOT OTHERWISE PROVIDED FOR
    • G06M1/00—Design features of general application
    • G06M1/04—Design features of general application for driving the stage of lowest order
    • G06M1/041—Design features of general application for driving the stage of lowest order for drum-type indicating means
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06M—COUNTING MECHANISMS; COUNTING OF OBJECTS NOT OTHERWISE PROVIDED FOR
    • G06M1/00—Design features of general application
    • G06M1/14—Design features of general application for transferring a condition from one stage to a higher stage
    • G06M1/143—Design features of general application for transferring a condition from one stage to a higher stage with drums

Definitions

  • the invention relates to a counting or printing unit for continuous numbering, in which D ruckrad for each paying a numeric or provided, and the numeric or print wheels are mounted on a common shaft and individually locked as well as by one or more switching devices in continuous Counting or printing positions can be rotated and coupled to one another in a specific switching rhythm.
  • Such a counting mechanism is suitable for pressure equipment andetikettier marn for example, in H, in which the number wheels are designed as pressure wheels.
  • a pressure device of this type is from the DE-GM 7 331 334 known, in which the printing wheels are threaded on an axis.
  • a second axis is arranged parallel to this axis, on which a ratchet wheel interacting with a ratchet and a control wheel for advancing the respective subsequent ratchet wheel are mounted.
  • This ring gear has a smaller radius than the control ring of the ratchet wheel adjacent to it.
  • a switching wheel is assigned to each printing wheel, which has a toothing whose radius is larger than the radii of the switching rings and control rings.
  • the ratchet wheel is turned by a ratchet pawl, which engages from the outside in the gear rim connected to the ratchet wheel.
  • the teeth of the gear rim in turn engage in gaps formed by teeth of the printing wheel provided with the digits to be printed.
  • Such a printing unit requires a relatively large amount of space, since two axially parallel axes and a ratchet arrangement parallel to the axis and the ratchet wheel are required, and the ratchet wheels with multiple teeth and therefore subject to wear must be fitted between the pressure wheels and the ratchet arrangement.
  • it is important to be handy and robust.
  • a switching ring is arranged on the side next to each printing wheel and is connected to the printing wheel without rotational play.
  • the printing wheel connects to the next higher digit, so that gaps of approximately the material thickness of a switching ring arise between the printing wheels.
  • Pawls rigidly connected to one another engage in these gaps in a switching comb, which interact with the switching rings for rotating the pressure wheels.
  • the switching ring diameter is the same size, while the switching comb is staggered. As the number of indexing points increases, the switching comb therefore falls ever deeper into the switching rings. This results in a limited number of digits in this device.
  • the gear ring which is assigned to the lowest-digit pressure digit, is in constant engagement with the pawl assigned to it. The corresponding pressure wheel is thereby moved by an angular step with each pressure stroke.
  • the pawls for the higher-digit printing wheels that have been switched off so far intervene when the nine of the lower-digit printing wheel are in the printing position.
  • this printing device for a hand labeling device also has other undesirable disadvantages. It is expensive due to the space requirement due to the rigidly coupled pawls arranged laterally from the pressure wheels and attacking from the periphery. Even the lowest digit gear ring is limited in its possible outer diameter by the practical requirement of manageability. Further, the arrangement of switching between the rings D jerk due wheels in the typeface is a gap between two adjacent printing type, which in its, width of at least the material thickness of the switching ring and Jack corresponds. This not only affects the typeface, but also reduces the information density of a printed label.
  • the object of the invention is to provide a wear-resistant counter or printing unit for continuous counting or numbering, which is also particularly suitable for printing devices and which, with a minimum of space, has a large number of manually preselectable, automatically advancing number or printing wheels can be arranged side by side without gaps.
  • a counter or printing unit of the type mentioned at the outset in that switching elements of the switching device (s) are provided for the immediate and step-by-step advancement of the number or printing wheels, which are force-transmitting but loosely connectable and designed to deflect one another.
  • the construction parts to a minimum.
  • the entire indexing mechanism is practically arranged within the number or printing wheel, so that the dimension of the entire counting or printing unit is essentially determined by the size of the wheels, with only one locking axis being provided on which these wheels are threaded , which are strung together without gaps, so that a full use of space of the pressure device is possible.
  • the printing unit 1a; 1b which is automatically advanced, according to the invention is combined with only manually adjustable printing wheels 2a; 2b.
  • This arrangement is used in labeling devices in which a Label with a fixed brand - for example a date or price - and at the same time printed with a consecutive number.
  • the fixed preselected printing wheels 2a; 2b which generally remain unchanged for a longer print series, are arranged on a common axis with the automatically advanced printing wheels 3a; 3b.
  • the pressure wheels are gear wheels which have the same outer diameter as their gear rings and are each operated by a common signal box (not shown).
  • the advancing pressure wheels 3a; 3b have a ten-fold symmetry and bear the digits from zero to nine on the end faces 4a; 4b of their ten teeth 5a; 5b arranged at an angular distance of 36 °.
  • the fixed printing wheels 2a; 2b can have other printing characters, alternatively or in addition to the decimal digits, and thus possibly also a different symmetry.
  • Each pressure wheel 2a, 3a or 2b, 3b is assigned an adjusting wheel of the same symmetry (not shown), which engages with its teeth in the corresponding tooth gaps 6a or 6b of the pressure wheel.
  • the setting wheels like the printing wheels, are arranged on a common axis which runs parallel to the axis of the printing wheels.
  • the adjusting wheel axis is a hollow cylinder, inside which an axially displaceable coupling shaft is guided.
  • the clutch shaft is rotated manually with the help of an adjusting knob, whereby it engages in any desired adjusting wheel via an actuator and takes it along.
  • the corresponding pressure wheel is simultaneously moved.
  • the letter of the printing wheel 2a; 3a or 2b; 3b facing the printing surface can be found in an inscription on the setting wheel, which can be read through a viewing window.
  • the printing wheels 2a; 3a and 2b; 3b are laterally supported one after the other in direct succession, but can be moved independently of one another on a common axis.
  • This axis is a locking axis 7a and 7b, which positions and adjusts the pressure wheels 2a; 3a and 2b; 3b in angular positions that are staggered from one another in stages.
  • the locking axis 7a of the embodiment according to FIG. 1 is a cylindrical sleeve 8, on the outer lateral surface 9 of which a spring comb 10 is arranged.
  • the spring comb 10 consists of a comb back 11, from which as many leaf springs 12 protrude in a prong shape as pressure wheels 2a; 3a are provided on the latching axis 7a.
  • the comb back 11 is mounted parallel to the cylinder axis of the sleeve 8 in a feather bed 13 within the lateral surface 9 of the sleeve 8 and firmly connected to it by screws or pins.
  • the ridge 11 is sunk in the lateral surface 9 of the sleeve 8, while the individual leaf springs 12 protrude tangentially from the lateral surface 9 of the sleeve 8 in a relaxed position or follow the lateral surface 9 with a radius of curvature that is somewhat larger than the circular radius of the Sleeve 8.
  • the leaf springs 12 thus protrude from the circumference of the sleeve 8 over at least part of their length in the unloaded state.
  • the feather bed 13 receiving the comb back 11 is in turn continued over the lateral surface 9 in an arc length which corresponds to the length of the leaf springs 12.
  • the leaf springs 12 are loaded by radial pressure into the feather bed 13, i.e. an area within the lateral surface 9 of the sleeve 8 is moved back, from which they spring back radially outwards by means of their inherent elasticity.
  • the outer surface 9 of the sleeve 8 forms the running surface of the printing wheels 2a; 3a.
  • the pressure wheels 2a; 3a have a central center bore 14, the inside width corresponds to the diameter of the sleeve 8 and are threaded on the sleeve 8.
  • an automatically advanced printing wheel 3a is explained in more detail, which is provided in a manner known per se with a type toothed ring 15, the teeth 5a of which bear the printing numerals from zero to nine on their end face 4a.
  • the material thickness of the type ring gear 15 is slightly less than that of the rest of the printing wheel body 16. In the manner described, an adjusting wheel engages in the type ring gear 15 (not shown).
  • the inner ring 17 formed by the central bore 14 of the pressure wheel body 16 has on its drive side a toothed ring 18 with ten identical notches 19, which are arranged at a uniform spacing and are used for decimal advancement of the pressure wheel 3a.
  • the inner ring 17 is provided with a ring gear 20 in which only a single notch 21 is left out.
  • the sprockets 18 and 20 on the drive or driven side of the printing wheel 3a serve equally for adjusting the printing wheels 3a in printing positions which are offset in steps from one another, as well as for decimal advancement of the printing unit 1a.
  • the notches 19 and 21 are preferably recesses in the solid material of the print wheel body 16 and appear in a lateral projection (FIG. 3) as approximately right-angled triangles.
  • the surface 23 to be assigned to the shorter cathete acts as a stop surface for pawls 24 engaging in the notches 19 or 21, which act against the surface 23 and thereby transport the printing wheel 3a.
  • the surface 25 to be assigned to the longer catheter acts as a slideway by means of which the pawls 24 can be lifted out of their engaged position.
  • the individual locking notch 21 of the gear ring 20 on the output side is aligned with one of the locking notches 19 of the gear ring 18 on the drive side.
  • the arrangement of the continuous locking notch 26 relative to the type toothed ring 15 is selected such that the pawls 24 engage in the continuous locking notch 26 with the number nine facing the printing surface.
  • a switching shaft 27 is inserted through the sleeve 8, through which the printing wheels 3a running on the lateral surface 9 of the sleeve 8 are advanced (FIG. 2).
  • the control shaft 27 is, for example, a cylindrical solid body, which is rotatably mounted inside the sleeve 8.
  • the rotation of the Switching shaft 27 is limited by suitable stops to an angular dimension that corresponds to an indexing stage of the pressure wheels 3a.
  • the pawls 24 are arranged, which reach through a gap 29 in the wall of the sleeve 8 into the ring gears 18 and 20 on the inner ring 17 of the pressure wheels 3a and take them along when the selector shaft 27 rotates.
  • the gap 29 with the pawls 24 is expediently arranged on the side of the latching axis 7a diametrically opposite the leaf spring 12.
  • Each of the pawls 24 consists of an essentially cylindrical joint body 30 pierced in the center and a projection 31 projecting radially therefrom, which is designed as a form negative of the locking notches 19 and 21, into which it engages as a tooth (FIG. 2).
  • the pawls 24 are pushed together with the bore 32 of their joint body 30 onto a cylindrical pin 33 as a common axis.
  • the pin 33 is mounted parallel to and in two brackets 34 and 35 fixed on the circumference of the selector shaft 27 (FIG. 1). In a particularly advantageous embodiment, these supports 34 and 35 also serve as a stop which limits the angular dimension of the shift shaft rotation.
  • the pawls 24 are each with their articulated body 30 adjacent to each other with play and aligned in lateral projection on the pin 33 and rotatable about this with movement.
  • the center of the axis of the pin 33 is positioned such that the outer dimension 36 of the joint body 30 of a pawl 24 threaded onto the pin 33 is in any case within an extended outer circumferential circle 37 of the sleeve 8.
  • the pawls 24 are thus sunk with their joint body 30 into the running surface of the printing wheels 3a.
  • a pressure wheel 3a rotating on the locking axis 7a slides over the articulated bearing of the pawls 24.
  • the center point of the axis of the pin 33 is positioned such that the outer dimension 36 of the joint body 30 of a pawl 24 mounted on the pin 38 just touches the extended outer circumferential circle 37 of the sleeve 8 in a lateral projection (FIG. 2).
  • the pressure wheels are thereby guided in the area in which the wall of the sleeve 8 is interrupted by the gap 29 for the pawls 24 on the joint body 30 of the pawls 24.
  • the pawls 24 threaded onto the pin 33 can be countersunk by rotation about the pin 33 into a recess 38 of the selector shaft 27 such that the shoulder 31 lies within the extended circumferential circle 37 of the sleeve 8. In this position, the shoulder 31 is set back under the running surface of the pressure wheels 3a and is not in engagement with the toothed rings 18 and 20. In this position, however, the pawls 24 are each independently loaded by the force of a compression spring 39, which the shoulder 31 of the pawls 24 act upon.
  • the compression springs 39 act on the surfaces 40 of the lugs 31 facing away from the switching rings 18 and 20 and thus exert a force which rotates the pawls 24 around the pin 33 and the lugs 31 radially outward into the locking notches 19 and 21 of the switching rings 18 and 20 snaps into place. The engagement is thus effected by a movement of the pawl 24 which is epicyclic relative to the rotation of the switching shaft 27.
  • the compression springs 39 are mounted in bores 41 which extend from the resting surface 42 of the pawls 24 in the recess 38 of the switching shaft 27 approximately perpendicularly into the material of the Switch shaft 27 are driven. With a view to maximum leverage, the bores 41 open at the greatest possible distance from the pivot joint of the pawls 24 onto the surfaces 40 of the projections 31 to be loaded.
  • a knob 48 on the output side and a groove 49 on the drive side are excluded from the projection 31 of each pawl 24, in which the knob 50 of the pawl 24 arranged upstream on the drive side can engage (FIGS. 7-9).
  • the knob 48 is formed axially projecting approximately centrally on the neck 31 of the pawl 24.
  • the rotary movement of the pawl 24 around the pin 33 takes place in a circular arc around the pin 33.
  • the radial side surfaces 51 and 52 of the knob 48 and the corresponding side walls 53 and 54 of the groove 49 are designed in the form of the cylinder jacket surfaces described here.
  • the width of knobs 48 and groove 49 corresponds, for example, to approximately half a pawl width.
  • the groove 49 is delimited to the side facing the switching shaft 27 when the pawls are assembled by a stop surface 55, which defines a maximum immersion depth of the knob 50 of the pawl 24 arranged on the drive side.
  • the groove depth is selected so that the pawls are aligned in the axial direction in this position of maximum immersion depth.
  • the movement of the knob 50 in the groove 49 is not limited to the opposite side, which faces the switching rings 18 and 20 of the pressure wheels 3a when the pawls are mounted.
  • the pawls 24 are thus coupled to one another only in one direction of movement about the pin 33.
  • the described printing unit 1a which decimally advances with each printing stroke, can be further developed in a simple and flexible manner to a printing unit with multiple or repetitive switching, in which the set of numbers for a sequential numbering is only incremented by one digit after each nth printing stroke.
  • the lowest-digit pressure wheel 43 which is advanced with each pressure stroke, is replaced by a suitable control curve.
  • 5 and 6 show an embodiment of a control cam 56 for a 2-step reduction printing unit.
  • the structure of the control cam 56 corresponds to that of a printing wheel 3a without a type gear rim 15, in which the reduction ratio of the gear rim on the drive side to the output side has been modified in accordance with the requirements.
  • the drive-side ring gear 57 is provided with ten drive notches 58 arranged at an angular distance of 36 °, while the drive-side ring gear 59 is provided with five drive notches 60 arranged at an angular distance of 72 °.
  • the output notches 60 are aligned with every second of the drive notches 58, so that the control cam 56 has a total of five at an angular distance of 72 ° ordered, continuous notches.
  • a pawl 24 (44) engages in the drive-side ring gear 57 of the control cam 56, which moves the control cam 56 by one switching position with each pressure stroke.
  • the pawl 44 driving the lowest-digit pressure wheel 47 directly next to the control cam 56 is now acted upon by half of its width with the gear rim 59 on the output side of the control cam 56 and therefore only comes into engagement with every second pressure stroke.
  • the printing unit 1a is thus only advanced on every second printing stroke.
  • Control curves for a repetition circuit of the printing unit 1a that is more than twice reduced are formed in an analogous manner.
  • the drive-side toothed ring of the control cam has twelve drive notches arranged at an angular distance of 30 ° (not shown). The implementation of every second, third, fourth or sixth of these notches on the driven side of the control cam then causes a correspondingly reduced multiple switching of the printing unit 1a.
  • a control cam with twelve degrees can be used with minor modifications to the locking axis or pawls together with decimally advancing pressure wheels, since the difference in the switching angle is comparatively small.
  • a control curve replaces the lowest-digit pressure wheel compared to the printing units described at the beginning.
  • a control curve can also be arranged upstream of the decimally advancing printing unit for pressure devices without multiple switching (not shown).
  • Such a control curve has ten-digit or at will twelve-fold symmetry on a ring gear with only continuous notches.
  • the first pawl 44 on the drive side only works with half its width against the drive-side ring gear 18 of the lowest-digit pressure wheel 43 or the control cam 56.
  • the other half of the pawl width runs freely and can be used in conjunction with an adjusting slide to automatically shut down the printing unit 1a.
  • the adjusting slide (not shown) is, for example, a flat part sliding in a guide and lockable in two latching positions. In one latching position, the adjusting slide has no function, in the other it acts on the otherwise free-running half of the pawl 44 on the drive side.
  • the corresponding end of the flat part is cut in the form of a circular arc, the radius of curvature of which corresponds to that of the outer lateral surface of the sleeve 8.
  • the length of the circular arc is selected so that it covers the gap 29 which is recessed for the pawls 24 in the wall of the sleeve 8.
  • the detent axis 7b is provided with a ball detent.
  • the pressure wheels 2b and 3b are bevelled on their outer circumference 61 (FIG. 13) essentially in the form of a uniform decagon.
  • the pressure type 62 are arranged approximately in the center of the tangential surfaces 63 formed in this way.
  • a rectangular groove 65 is excluded, into which suitable switching elements of a manually operated adjusting device engage (not shown).
  • This setting device can be used to preselect the setting of the pressure wheels 2b and 3b in the manner already described.
  • the pressure wheels 2b and 3b have a central axis bore 66 through which a locking axis 7b is inserted.
  • the annular surface delimiting this axis bore 66 is designed as a stepped rim 67 with ten notches 68 arranged at the same angular distance.
  • the division of tens of step ring 67 corresponds to that of the outer letter ring gear.
  • One or more spring-loaded balls or shafts (not shown) of the latching axis 7b engage in the notches 68 of the step collar 67 and position the pressure wheels 2b with 3b in their respective pressure position.
  • the notches 68 on the inner ring surface of an automatically advancing pressure wheel 3b are not acted on by advancing elements.
  • the decimal step-down indexing elements act rather against the side surfaces 69 and 70 of the printing wheels 3b.
  • Both side surfaces 69 and 70 of an automatically advancing printing wheel 3b are each provided with a concentrically rotating step shoulder 71 and 72, which is excluded from the solid material of the printing wheel 3b with a corresponding clear width.
  • the step shoulder 71 on the output side serves to receive a resilient clutch disc 73 which can be flush-lowered into the step shoulder 71.
  • the end face 74 of the stepped shoulder 72 on the drive side is provided with a plane toothing 75 (FIGS. 13, 14) into which the clutch disk 73 of the pressure wheel 3b, which is arranged with lower digits, engages.
  • the face gear 75 has a ten-fold symmetry, which corresponds to that of the outer type gear ring. It immediately adjoins the outer circumferential step 76 of the step shoulder 72 on the drive side.
  • the individual teeth 77 of the face toothing 75 are sliding planes which rise from the end face 74 of the step shoulder 72 to the height of the side face 70 of the pressure wheel 3b. The increase is based on the axis of the pressure wheel 3b over an angle of 18 ° and breaks off in a step 78.
  • the toothing 75 falls on the end face 74 of the step shoulder 72 and remains at this height over an angular range of likewise 18 °, as a result of which a gap 79 is formed in the toothing 75.
  • the following tooth 77 adjoins this gap 79.
  • the teeth 77 are sections of circular sectors and delimited radially inwards by arc sections 80 of a concentric inner ring edge 81.
  • the clutch disc 73 is essentially a flat ring 82 (FIGS. 16, 17) made of spring steel with a central circular opening 83 and two brackets 84 and 85 protruding radially outward.
  • the circular opening 83 has an inner diameter which is at least the maximum clear width of the stepped ring 67 corresponds to a pressure wheel 2b; 3b.
  • the clutch disks 73 like the pressure wheels 2b; 3b, can thus be threaded onto the locking axis 7b.
  • the outer diameter of the flat ring 82 is somewhat smaller than the diameter of the inner ring edge 81 of the face toothing 75.
  • the flat ring 82 of the clutch disk 73 of a low-position pressure wheel 3b thus always runs radially within the face toothing 75 of the next-higher pressure wheel 3b.
  • the tabs 84 and 85 are formed on diametrically opposite sides of the flat ring 82.
  • the outside diameter of the tabs 84 and 85 corresponds to the inside width of the step shoulders 71 and 72 of the pressure wheel 3b.
  • the tabs 84 and 85 act as a latching tab 84 and holding tab 85.
  • the clutch disk 73 lies flush in the output step shoulder 71 of the printing wheel 3b and is fixedly connected to the printing wheel 3b on the holding tab 85.
  • retaining tabs 85 such as pressure wheel 3b have countersunk, mutually aligned mounting bores 86 and 87, through which they can be riveted or pinned to one another.
  • the opposite R astlasche 84 engages as a further switching element in the gaps 79 of the face gear 75 of the downstream printing whostellig each wheel 3b, and is lifted therefrom over the sliding planes of the teeth 77 by its own suspension again.
  • the locking tab 84 is designed as a form negative of a gap 79 of the face toothing 75. It is provided with a pin 88 projecting axially from the plane of the flat ring 82 with a rounded tip. When the clutch disc 73 is fitted, the pin 88 runs with play in a through hole 89 (FIG. 13).
  • This through-hole 89 which is slightly oval in the illustrated embodiment, is recessed in a well-defined gap 90 of the face toothing 75 and connects the step shoulder 71 on the output side to the step shoulder 72 on the drive side of the pressure wheel 3b.
  • clutch plate so the pin engages through 88 from the output side to the input side of the D ruck wheel 3b.
  • the clutch disc 73 In the unloaded position, the clutch disc 73 is sunk in the pressure wheel 3b.
  • the length of the pin 88 is selected such that in this position it protrudes through the through hole 89 beyond the end face 74 of the step shoulder 72 on the drive side.
  • the drive for the automatic advancement of the printing unit 1b only acts on the lowest-digit printing wheel 91.
  • This printing wheel 91 is therefore modified compared to the other printing wheels 3b.
  • It carries on its drive side a switching ring 92 (FIG. 12) which is rigidly connected to the pressure wheel 91.
  • the switching ring 92 can, for example, be riveted or pinned to the pressure wheel 91 by means of flush mounting bores 93, 94, 95, 96.
  • a lever-operated pawl 97 engages in the switching ring 92 in a manner known per se, which moves the switching ring 92 and thus the pressure wheel 91 by one switching position with each pressure stroke.
  • the switching ring 92 has a through hole 98 which is aligned with the through hole 89 of the pressure wheel 91 in the mounted position.
  • the pin 99 of the clutch disk 100 of the lowest-digit pressure wheel 91 is extended such that it projects through the aligned through-bores 89 and 98 over the end face 101 of the switching ring 92.
  • the tip of the pin 99 interacts with a switching curve 102 on which the switching ring 92 runs.
  • the pin 99 describes a circle on the switching curve 102.
  • the switching curve 102 has a single cam 103 on the circumference of this circle. This is aligned with the pin 99 in the axial direction exactly at the pressure surface facing digit nine of the lowest-digit pressure wheel 91.
  • the tip of the pin 99 then slides on the cam 103 (see FIG. 10), whereby the clutch disc 100 against its internal spring tension from the output stage step 71 of the lowest-digit pressure wheel 91 is deflected.
  • the required pivoting movement of the pin 99 in the through holes 89 and 98 is made possible by their oval shape.
  • the deflected clutch plate 100 engages with its latching tab 84 in the toothing 75 of the next higher pressure wheel 104 and acts as a driver, which forces the simultaneous advancement of both pressure wheels 91, 104 during the next pressure stroke.
  • the clutch disc 100 After the end of a shifting operation, the clutch disc 100 has returned to the rest position due to the right-angled drop in the shifting curve and its self-suspension. The disengagement takes place in the catch area of the ball detent axis, i.e. while the pressure wheels are still moving.
  • the material thickness of the clutch discs 73 is to be selected in accordance with the desired spring force, a minimum thickness having to be guaranteed for a secure engagement in the face toothing 75.
  • a decimal indexing of a higher-digit pressure wheel 3b takes place when the pins 88 of all of the lower-digit clutch disks 73 with the cam 103 of the;
  • Shift curve 102 are aligned.
  • the clutch plates 73 then meet with their latching tabs 84 on those gaps 90 in the face teeth 75 of the next higher pressure wheel 3b which are provided with a through hole 89.
  • the protruding pins 88 convey the deflecting force of the cam 103 through all lower-digit pressure wheels 3b. With this form of coupling, a higher-digit pressure wheel 3b is apparently only switched at the same time as all lower-order pressure wheels 3b, that is, correct decimal indexing is achieved.
  • the second embodiment of the printing unit 3b according to the invention can also be easily equipped with a multiple or repeat circuit.
  • a feeler lever 106 is arranged on a common axis 105 with the pawl 97, which engages with a reduction curve 107 (FIG. 18).
  • Pawl 97 and feeler lever 106 are rigidly coupled to one another via axis 105.
  • the reduction curve 107 can, as shown (FIGS. 10 and 11), be mounted on the output side of the printing unit 1b in addition to the printing wheels 2b, which can only be adjusted manually. Any other arrangement is also possible.
  • the feeler lever 106 acts on a notch rim 108, the reduction curve 107, in which every second notch 109 is recessed radially inward, and moves the reduction curve 107 by one switching step with each pressure stroke.
  • the pawl 97 is staggered behind the feeler lever 106 and only engages in the switching ring 92 when the feeler lever 106 meshes with one of the recessed notches 109.
  • the printing unit 1b is therefore only every second printing stroke. switched on. Reduction curves for any other desired reduction of the counting process are used analogously.
  • the automatic indexing only acts on the printing wheels 3a in a well-defined direction of advance; 3b. This results casually from the asymmetry of the locking teeth, in which the respective indexing elements engage.
  • the partial task according to the invention of creating a low-wear printing unit is served in particular in that the manually operated signal box moves the printing wheels 3a, 3b exclusively in the same direction of advance (not shown).
  • the coupling shaft of the interlocking is provided with a freewheel that slips in the opposite direction when the control knob is turned.
  • the freewheel can consist of a wrap spring placed around the coupling shaft or can be realized in another known manner.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Theoretical Computer Science (AREA)
  • Labeling Devices (AREA)
  • Ink Jet (AREA)
  • Handling Of Sheets (AREA)
  • Handcart (AREA)
  • Character Spaces And Line Spaces In Printers (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Pinball Game Machines (AREA)
EP80107725A 1980-01-16 1980-12-08 Mécanisme compteur ou imprimeur pour le comptage ou le numérotage consécutif Expired EP0032555B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80107725T ATE12368T1 (de) 1980-01-16 1980-12-08 Zaehl- oder druckwerk zum fortlaufenden zaehlen oder numerieren.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3001321 1980-01-16
DE3001321A DE3001321C2 (de) 1980-01-16 1980-01-16 Mechanisches Fortschaltwerk zum stufenweisen Fortschalten von Zahlen- oder Druckrädern

Publications (2)

Publication Number Publication Date
EP0032555A1 true EP0032555A1 (fr) 1981-07-29
EP0032555B1 EP0032555B1 (fr) 1985-03-27

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ID=6092127

Family Applications (1)

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EP80107725A Expired EP0032555B1 (fr) 1980-01-16 1980-12-08 Mécanisme compteur ou imprimeur pour le comptage ou le numérotage consécutif

Country Status (8)

Country Link
US (1) US4343238A (fr)
EP (1) EP0032555B1 (fr)
JP (1) JPS6035277B2 (fr)
AT (1) ATE12368T1 (fr)
AU (1) AU538223B2 (fr)
BR (1) BR8100168A (fr)
CA (1) CA1157704A (fr)
DE (1) DE3001321C2 (fr)

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EP0064157A1 (fr) * 1981-04-27 1982-11-10 Esselte Pendaflex Corporation Compteur mécanique à démultiplication
EP0671330A1 (fr) * 1994-03-12 1995-09-13 Esselte Meto International GmbH Appareil manuel pour l'étiquetage ou le marquage
EP1731324A1 (fr) * 2005-06-08 2006-12-13 Kba-Giori S.A. Procédé et dispositif de numérotage de documents de valeur et procédé de transport desdits documents
EP2468522A1 (fr) * 2006-06-23 2012-06-27 KBA-NotaSys SA Unité de numérotation d'un dispositif de numérotage comprenant un mécanisme de verrouillage détachable

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JPS57110469A (en) * 1980-12-29 1982-07-09 Seiko Epson Corp Mini-printer
DE3215881C2 (de) * 1982-04-29 1985-06-13 Esselte Pendaflex Corp., Garden City, N.Y. Antrieb des Einerrades eines untersetzten mechanischen Zähl- oder Druckwerks
JP2013151146A (ja) * 2011-12-27 2013-08-08 Sato Holdings Corp 印字器および印字用連続番号見出し数字選択方法
US10823139B2 (en) * 2017-03-15 2020-11-03 General Electric Company Blade sleeve for a wind turbine rotor blade and attachment methods thereof
CN107499010A (zh) * 2017-09-07 2017-12-22 郝之奎 一种自动记录盖章次数的印章
US11781522B2 (en) 2018-09-17 2023-10-10 General Electric Company Wind turbine rotor blade assembly for reduced noise
CN109435510B (zh) * 2018-12-07 2023-09-08 湖南嘉力亚新材料有限公司 一种炭块打码装置

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0064157A1 (fr) * 1981-04-27 1982-11-10 Esselte Pendaflex Corporation Compteur mécanique à démultiplication
EP0671330A1 (fr) * 1994-03-12 1995-09-13 Esselte Meto International GmbH Appareil manuel pour l'étiquetage ou le marquage
CN1040521C (zh) * 1994-03-12 1998-11-04 梅托国际有限公司 手提标签或压印装置
EP1731324A1 (fr) * 2005-06-08 2006-12-13 Kba-Giori S.A. Procédé et dispositif de numérotage de documents de valeur et procédé de transport desdits documents
WO2006131839A3 (fr) * 2005-06-08 2007-04-12 Kba Giori Sa Procede de numerotation pour securites, procede de traitement des securites numerotees et dispositif de numerotation pour la realisation du procede de numerotation
US7975906B2 (en) 2005-06-08 2011-07-12 Kba-Giori S.A. Numbering process for securities, method for processing the numbered securities and numbering device to carry out the numbering process
EP2468522A1 (fr) * 2006-06-23 2012-06-27 KBA-NotaSys SA Unité de numérotation d'un dispositif de numérotage comprenant un mécanisme de verrouillage détachable
EP2537676A1 (fr) * 2006-06-23 2012-12-26 KBA-NotaSys SA Dispositif de numérotation pour la numérotation typographique comprenant des entraînements indépendants
US8671836B2 (en) 2006-06-23 2014-03-18 Kba-Notasys Sa Numbering device for typographic numbering
US9403354B2 (en) 2006-06-23 2016-08-02 Kba-Notasys Sa Numbering device for typographic numbering

Also Published As

Publication number Publication date
DE3001321C2 (de) 1984-12-20
DE3001321A1 (de) 1981-08-06
US4343238A (en) 1982-08-10
JPS57113096A (en) 1982-07-14
AU538223B2 (en) 1984-08-02
JPS6035277B2 (ja) 1985-08-13
BR8100168A (pt) 1981-07-28
EP0032555B1 (fr) 1985-03-27
CA1157704A (fr) 1983-11-29
ATE12368T1 (de) 1985-04-15
AU6507780A (en) 1981-07-23

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