EP0519938B1 - Dispositif servant a transporter des porteurs d'enregistrements sous forme de bande dans des imprimantes - Google Patents

Dispositif servant a transporter des porteurs d'enregistrements sous forme de bande dans des imprimantes Download PDF

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Publication number
EP0519938B1
EP0519938B1 EP91904864A EP91904864A EP0519938B1 EP 0519938 B1 EP0519938 B1 EP 0519938B1 EP 91904864 A EP91904864 A EP 91904864A EP 91904864 A EP91904864 A EP 91904864A EP 0519938 B1 EP0519938 B1 EP 0519938B1
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EP
European Patent Office
Prior art keywords
clutch
machinery
accordance
gear
arrangement
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP91904864A
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German (de)
English (en)
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EP0519938A1 (fr
Inventor
Hans Kusmierz
Hans Taubenberger
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Eastman Kodak Co
Original Assignee
Mannesmann AG
Eastman Kodak Co
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Publication date
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Publication of EP0519938A1 publication Critical patent/EP0519938A1/fr
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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
    • B41J11/00—Devices or arrangements  of selective printing mechanisms, e.g. ink-jet printers or thermal printers, for supporting or handling copy material in sheet or web form
    • B41J11/24—Detents, brakes, or couplings for feed rollers or platens
    • 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
    • B41J15/00—Devices or arrangements of selective printing mechanisms, e.g. ink-jet printers or thermal printers, specially adapted for supporting or handling copy material in continuous form, e.g. webs
    • B41J15/16—Means for tensioning or winding the web

Definitions

  • the invention relates to a device for transporting web-shaped recording media in printing devices according to claim 1.
  • Modern printing devices for example ink printers, are notable for the user-friendliness when printing web-shaped recording media.
  • the user-friendliness of a printing device for the user comes to the fore in particular if, in addition to web-shaped recording media, sheet-shaped recording media are also to be printed with the printing device.
  • more complicated mechanical transport devices are required with which the sheet-shaped or web-shaped recording media are fed to a printing station.
  • the expression continuous paper or single sheet is used for the printout of sheet-like or sheet-like record carriers, whereby this is meant a record carrier which is different both in terms of its nature (e.g. paper, cardboard, film) and the degree of pretreatment (e.g. edge perforation, form).
  • a paper transport device for single sheets and continuous paper in printing devices is known from EP-A2-0 123 310.
  • the paper transport device has a change-over gear, which mechanically couples a drive motor with a platen roller or the drive motor with a paper tractor and the platen roller depending on the operating mode single sheet or continuous paper.
  • the changeover gear is designed such that when switching from the continuous paper mode to the single sheet mode or vice versa, no malfunctions, such as. B. paper jam occur.
  • the return transport of the single sheets or the continuous paper is achieved by reversing the direction of rotation of the drive motor.
  • the mechanical coupling between the paper tractor and the platen roller has to be very precise in order to transport the continuous perforated continuous paper correctly and precisely.
  • a paper feed device for printing devices is known from US Pat. No. 4,688,957, with which single sheets or continuous paper can optionally be fed to a printing station via a friction roller.
  • a paper tractor, separating rollers and the friction roller are driven by an electric motor via a gear.
  • a gear coupling is provided in the gearbox, which can be operated manually using an operating lever. Since for the known feed device in continuous paper operation, the paper tractor is constantly coupled to the friction roller for both directions of transport of the continuous paper the same disadvantages result as for the technical teaching from EP-A2-0 123 310.
  • the feed speed of the perforated folded paper is determined exclusively by the friction drive of the platen roller.
  • the friction drive is decoupled from the paper tractor in the forward direction by the effective freewheel. This is achieved in that the freewheel is driven faster by the stepper motor than the edge-punched folding paper is taken along by the friction drive. As a result, the paper tractor is pulled along with it when the folded perforated paper is drawn in.
  • the perforated folding paper in the ready position can only be moved backwards (maximum 1/6 '') by the platen roller. If the edge-punched folding paper is transported back a larger distance, the paper tractor pushes the edge-punched folding paper out of the printing device to the rear as a result of the blocked freewheel. This occurs e.g. B. when changing from continuous paper operation to single sheet operation of a printing device. Such a backward movement but occurs z. B. when printing multiple exponents on a single sheet.
  • the object of the present invention is to construct a device for transporting web-shaped recording media in printing devices, in which the web-shaped recording media inserted in the printing device can be automatically drawn in for printing with lateral guidance, transported into a target position and transported back again.
  • sheet-shaped recording media in addition, it is an object of the invention that in addition to web-shaped recording media, sheet-shaped recording media can optionally be transported with the device.
  • a cost-effective construction of the transport device is achieved with a small space requirement and a simple user interface.
  • the regulation of the voltage of the record carrier can be independent of the asynchronous transport of the record carrier by the electromotively driven transport means, for. B. perform a friction or pin drive.
  • the pin drive holding the web-shaped recording medium in a preparation position can be designed with the aid of a mechanically simple design, the tooth or claw coupling or the control lever assigned to the ratchet mechanism can be decoupled from the electric motor drive. This makes it possible to print sheet-shaped record carriers in addition to web-shaped record carriers in a printing device.
  • the operating lever can also be used to prevent the pin drive holding the web-shaped recording medium in the ready position from rotating during the single sheet operation due to any frictional connections.
  • FIG. 13 shows a side view of a ratchet mechanism for the transport device according to FIG. 1.
  • Figure 1 shows a section through an ink printing device 1, the structure of a transport device 10 for the optional transport of single sheets 2 and perforated continuous paper 3, such as folded perforated paper.
  • Characteristic of the transport device 10 is an electric motor 11 with a drive pinion 110, which is connected via a first gear transmission 12 with a second transport device in the forward transport direction of the recording medium, for example a friction drive 13, and via a second gear transmission 14 and a tooth clutch 16 with a first in the forward transport direction of the recording medium Transport device 15, for example a spiked roller (pin drive), for which continuous paper 3 is coupled.
  • the second transport device 13 as a spike or pin drive and the first transport device as a friction drive.
  • the friction drive 13 contains a paper guide trough 130, in which two paper guide rollers 131, 132 are arranged.
  • the paper guide rollers 131, 132 are arranged such that a rotatably mounted writing roller 134 forming a guide channel 133 with the paper guide trough 130 forms a roller pairing with the paper guide rollers 131, 132. Due to the roller pairing between the platen roller 134 and the paper guide roller 131 is created a roller wedge 135 into which the single sheet 2 and the continuous paper 3 must get in order to be transported by the friction drive 13 for the predetermined direction of rotation of the drive pinion 110 (solid arrow) into a printing position DP in front of a printing station 17 of the ink printing device 1.
  • the transport device 15 has two pin wheels 151 arranged on a drive shaft 150, each with radially projecting pins 152, which engage in a perforation on the left and right of the continuous paper 3.
  • the toothed coupling 16 is also arranged on the drive shaft 150 and is coupled to the gear transmission 14. How the tooth coupling 16 works and is constructed in detail is explained with reference to FIGS. 2 to 10.
  • the edge-punched continuous paper 3 for printing has reached an insertion position EP via the pin wheel 151
  • the edge-punched continuous paper 3 for the indicated direction of rotation of the drive pinion 110 (solid arrow) is first moved into the roller wedge 135 at a peripheral speed v1 of the pin wheels 151. It is then taken over by the friction drive 13 and moved past the printing station 17 at a peripheral speed v2 of the platen roller 134 and further past a tear-off edge 18 of the ink printing device 1. In this way, the edge-perforated continuous paper 3 can be brought line by line into the printing position DP, printed line by line there and transported further to a tear-off position AP.
  • the gear ratios 12, 14 are selected so that starting from a peripheral speed v0 of the electric motor 11, the peripheral speed v2 is slightly greater than the peripheral speed v1.
  • the pin wheel 151 is decoupled from the drive pinion 110 of the electric motor 11 by the tooth coupling 16. The decoupling results from the fact that the pin wheel 151 is pulled along faster over the edge-perforated continuous paper 3 transported by the friction drive 13 than is driven by the electric motor 11 via the gear transmission 14.
  • the loop formation S during the return transport is limited by the transmission ratio from the electric motor 11 to the friction drive 13 and from the electric motor 11 to the feed device 15, 16, 19 to such an extent that the pins 152 of the pin wheels 151 also continue to engage in the edge perforation of the continuous paper 3 and guide the continuous paper 3 laterally.
  • the unprinted part of the perforated continuous paper 3 still located in the guide channel 133 of the friction drive must be in a so-called readiness position BP for the next one Printing process.
  • the ready position BP is so far upstream of the roller wedge 135 that the single sheets 2 can be conveniently inserted into the roller wedge 135 by hand.
  • the loop S is formed again due to the speed relationships between the platen roller 134 and the pin wheels 151. As a result of the measures described, this is in turn only so large that the pins 152 of the pin wheels 151 continue to engage in the peripheral perforations of the continuous paper 3.
  • the transport device 10 has a z. B. manually operated lever 19 which is pivoted from a state A for continuous paper operation to a state B for single sheet operation.
  • the lever 19 is also pressed into the end positions (state A, state B) with a leaf spring 190 fastened at two points.
  • the lever 19 has a latching lug 191 which snaps into a ring gear 160 of the toothed coupling 16 arranged on the drive shaft 150.
  • Figure 2 shows a plan view of the transport device 10 with a simultaneous sectional view of the drive chain of the transport device 10 along a section line II ... II.
  • the first gear transmission 12 is designed as a composite spur gear with two spur gears 121, 122 rotatably mounted on a shaft 120.
  • the spur gear 121 meshes with the drive pinion 110 of the electric motor 11, while the spur gear 122 meshes with one on a drive shaft 136 of the friction drive 13 arranged gear 137 is engaged.
  • the transmission ratio of the drive pinion 110 to the gear 137 is calculated from the quotient of diameters d1, d3 of the spur gear 121 or gear 137 to diameters d0, d2 of the drive pinion 110 or spur gear 122.
  • the second gear transmission 14 is a dual spur gear with four two shafts 140, 141 rotatably mounted spur gears 142, 143, 144, 145. While the spur gear 142 meshes with the drive pinion 110 of the electric motor 11 and the spur gear 145 with a gear 161 of the tooth coupling 16, the mutual coupling of the composite spur gear is produced via the spur gears 143, 144.
  • the transmission ratio of the drive pinion 110 to the gear 161 is calculated from the quotient of diameters d4, d6, d8 of the spur gears 142, 144 or of the gear 161 to diameter d0, d5, d7 of the drive pinion 110 or the spur gears 143, 145.
  • the gear wheel 161 (see also FIGS. 5 and 6) consists of a bushing 162 which at one end merges into a gear wheel web 163 which is angled outwards twice.
  • a first coupling toothing 164 is arranged concentrically on the end face of this gear web 163 facing away from the bush.
  • the first clutch toothing 164 engages with a second clutch toothing 166 arranged concentrically on a toothed disk 165 in the continuous paper mode of the ink printing device 1.
  • the toothed pulley 165 together with the ring gear 160 forms a shaped element with a T-shaped cross section, which is fastened on the drive shaft 150 between a partition 100 of the transport device 10 and a first snap ring 153 arranged on the drive shaft 150.
  • the gear 161 is rotatably mounted on the drive shaft 150.
  • the gear 161 is against a spring force F of a cylindrical coil spring 167 between the snap ring 153 and a centering plate 168 for the cylindrical coil spring 167 on the drive shaft 150 by a value a axial slidable.
  • the centering plate 168 is limited in its axial displaceability by a second snap ring 154 arranged on the drive shaft 150.
  • the cylindrical coil spring 167 is arranged on the bush 162 and abuts the ends against the gear web 163 and centering plate 168.
  • a wedge-shaped projection 192 of the lever 19 presses against the gear wheel 161 and pushes it against the spring force F of the cylindrical coil spring 167 in the axial direction drive shaft 150 aside.
  • the two clutch gears 164, 166 are disengaged and the pin wheel 151 is thus decoupled from the electric motor 11.
  • the distance by which the gear wheel 161 is displaced in the axial direction of the drive shaft 150 is determined by the gradation of the wedge-shaped projection 192 of the lever 19.
  • the pin wheels 151 can be driven in spite of the decoupling from the electric motor 11 by undesirable rotary movements resulting from frictional engagement.
  • the gradation is therefore dimensioned such that the axial thrust of the gear wheel 161 on the drive shaft 150 is smaller than the value a.
  • FIG. 3 and 4 show a side view of the tooth coupling 16 with different operating positions of the lever 19 (state A, state B) for continuous paper operation (FIG. 3) or single sheet operation (FIG. 4) of the ink printing device 1.
  • the lever 19 has a segment-shaped middle part 193 , at the ends of which two lever arms 194, 195 are provided, which are arranged at an obtuse angle to the outer diameter of the middle part 193.
  • the central part 193 has a curvature in the region of the latching lug which corresponds to that of the ring gear 160.
  • Radially offset to the locking lug 191, the wedge-shaped projection 192 is arranged on the rear of the lever 19. At the transition between the middle part 193 and a first lever arm 194, the lever 19 is pivotally mounted.
  • the second lever arm 194 which tapers at an acute angle from the pivot point, rests with the inside against a pin 196 in continuous paper operation of the ink printing device 1, in which the lever 19 is pivoted away from the drive shaft 150. Since the rounded tip of the first lever arm 194 is at the same time at the base of an elevation 197 of the leaf spring 190, the pivotally mounted lever 19 is fixed in position against the spring force of the leaf spring 190.
  • the lever 19 is transferred from state A to state B by a second lever arm 195.
  • the first lever arm 194 is moved against the spring force of the leaf spring 190 via the elevation 197 to the opposite base point.
  • the locking lug 191 of the lever 19 is engaged in the ring gear 160, so that the lever 19 is again fixed in its position against the spring force of the leaf spring 190.
  • FIG. 5 shows a section through the tooth coupling 16 with interlocking coupling teeth 164, 166 according to FIG. 3 along a section line V ... V.
  • FIG. 6 shows a section through the tooth coupling 16 with disengaged coupling teeth 164, 166 according to FIG. 4 along a section line VI ... VI.
  • FIGS. 7 to 9 each show a section through the tooth coupling 16 according to FIG. 3 along a section line VII-IX ... VII-IX for different operating phases of the continuous paper operation of the ink printing device 1 according to FIG. 1.
  • the flank angles and the tooth pitch of the coupling teeth 164, 166 are adjusted with the spring force F of the cylindrical coil spring 167 so that the operating phases of the continuous paper operation of the ink printing device 1 shown in FIGS. 7 to 9 are reliably fulfilled.
  • FIG. 7 shows a state of the coupling teeth 164, 166 of the tooth coupling 16, in which the continuous perforated paper is positively advanced by the transport device 15 from the insertion position EP or the preparation position BP to the roller wedge 135 of the friction drive 13. After the roller wedge 135, the further paper feed is taken over by the platen roller 134 of the friction drive 13. Due to the paper feed difference between the friction drive 13 and the transport device 15 (circumferential speed difference between v1 and v2), a relative movement between the clutch teeth 164, 166 occurs according to FIG.
  • FIG. 9 shows a state of the coupling toothings 164, 166 of the toothed coupling 16, in which the continuous paper 3 with perforations at the edges is non-positively transported back from the tear-off position AP into the printing position DP or the ready position BP by the transport device 15, the friction drive 13 carrying the return transport up to the roller wedge 135 supported.
  • Figure 10 shows a section through the tooth coupling 16 of Figure 4 along a section line X ... X.
  • the state of the coupling teeth 164, 166 is shown when they are disengaged by pivoting the lever 19 over the wedge-shaped projection 192.
  • FIG. 11 shows, as a second exemplary embodiment of the invention, the structure of a further transport device 10a for the optional transport of single sheets 2a and perforated continuous paper 3a in an ink printing device 1a.
  • Characteristic of the transport device 10a is an electric motor 11a with a drive pinion 110a, which is via a first gear transmission 12a with a second transport device in the forward transport direction of the recording medium, for example a friction drive 13a and via a second gear transmission 14a and a claw clutch 16a with a first transport device 15a in the forward transport direction of the recording medium, for example a spiked roller, for which continuous paper 3a is coupled.
  • the first gear transmission 12a is again designed as a composite spur gear with two rotatably mounted spur gears 121a, 122a.
  • the second gear transmission 14a is again in the form of a double spur gear with four rotatably mounted spur gears 142a, 143a, 144a, 145a.
  • the friction drive 13a contains a paper guide trough 130a, in which two paper guide rollers 131a, 132a are arranged.
  • the paper guide rollers 131a, 132a are arranged such that a rotatably mounted platen roller 134a, which forms a guide channel 133a with the paper guide trough 130a, forms a roller pairing with the paper guide rollers 131a, 132a.
  • a roller wedge 135a is created, in which the single sheet 2a and the continuous paper 3a must pass in order for the friction drive 13a for a predetermined rotation direction of the drive pinion 110a (solid arrow) into a printing position DP1 of one Printing station 17a of the ink printing device 1a to be transported.
  • the mechanical coupling between the friction drive 13a and the first gear transmission 12a is achieved by a gearwheel 137a which is arranged on a common shaft with the platen roller 134a and which meshes with the spur gear 122a.
  • the transport device 15a has two pin wheels 151a, each with radially projecting pins 152a, which engage in an edge perforation on the left and right of the continuous paper 3a.
  • the transport device 15a it is also possible again for the transport device 15a to provide only one pin wheel 151a.
  • the dog clutch 16a is provided, which is coupled to the gear transmission 14a. How the dog clutch 16a functions and is constructed in detail is explained with reference to FIG.
  • the edge-punched continuous paper 3a is placed over the pin wheel 151a for printing up to an insertion position EP1
  • the edge-punched continuous paper 3a for the predetermined direction of rotation of the drive pinion 110a (solid arrow) is first moved into the roller wedge 135a at a peripheral speed v4 of the pin wheels 151a. It is then taken over by the friction drive 13a and moved past the printing station 17a and at a tear-off edge 18a of the ink printing device 1a at a peripheral speed v5 of the platen roller 134a.
  • the continuous perforated continuous paper 3a can be brought line by line into the printing position DP1, printed line by line there and transported further to a tear-off position AP1.
  • the ratios of the gear transmissions 12a, 14a are selected such that, starting from a peripheral speed v3 of the electric motor 11, the peripheral speed v4 is slightly greater than the peripheral speed v5.
  • the pin wheel 151a is briefly decoupled from the drive pinion 110a of the electric motor 11a by the claw coupling 16a after each revolution. This takes place in that the spur gear 145a lifts itself axially after each revolution on a link 162a pivotably mounted against a spring force F1 of a spring 160a from the toothing with a gear wheel 161a. As a result, pin wheel 151a is no longer driven by electric motor 11a.
  • the simultaneous further transport of the perforated continuous paper 3a through the platen roller 134a leads to the loosening of the loop S1.
  • the continuous perforated continuous paper 3a must be transported back to the printing position DP1.
  • the platen roller 134a and the pen wheels 151a are driven by the electric motor 11a in the opposite direction (dashed arrow).
  • the operator of the ink printing device 1a wishes that at least one single sheet 2a should be printed after the continuous perforated continuous paper 3a has been printed.
  • the unprinted part of the perforated continuous paper 3a still located in the guide channel 133a of the friction drive 13a must be moved into a so-called preparation position BP1 for the next printing process.
  • the preparation position BP1 is so far upstream of the roller wedge 135a that the single sheets 2a can be comfortably inserted into the roller wedge 135a by hand.
  • the spur gear 145a and the gear 161a are in engagement with one another during the return transport.
  • the pivotally mounted link 162a is pressed away from the spur gear 145a by the latter against the spring force F1 in the direction of the arrow for each revolution.
  • the backlash occurring due to hysteresis properties of the gear drive 12a, 14a is dimensioned such that the continuous perforated continuous paper 3a is removed Tear-off position AP1 can be transported to the ready position BP1.
  • the feed device 15a, 16a has a manually operated lever arrangement.
  • FIG. 12 shows a possible embodiment of the lever arrangement.
  • FIG. 12 shows a side view of the claw coupling 16a according to FIG. 11. It is characteristic of the structure and mode of operation of the claw coupling 16a that the spur gears 144a, 145a engage positively with one another via spur gear bushings 163a, 164a with axially projecting claws 168a, 169a on a shaft 141a . While the spur gear 144a with the spur gear bushing 163a is fixedly arranged on the shaft 141a, the spur gear 145a with the spur gear bushing 164a can be displaced thereon against a spring force F2 of a cylindrical helical spring 165a in the arrow directions shown. The spur gear 145a is either, as shown in FIG.
  • an elevation 166a tapering to an acute angle is provided on the side surface of the spur gear 145a facing away from the spur gear bushing 164a. For every revolution of the spur gear 145a in the direction of rotation shown, this elevation 166a runs up a run-up slope 167a of the pivotably mounted link 162a.
  • FIG. 12 also shows how the spur gear 145a can be brought out of engagement with the gear 161a by means of a lever arrangement 19a when changing from continuous paper operation of the ink printing device la to single sheet operation.
  • the lever arrangement 19 is converted from a state C to a state D for the arrow direction shown.
  • FIG. 13 shows, as a third exemplary embodiment of the invention, a side view of a transport device 15b and a ratchet switching mechanism 16b, as can be used, for example, in the ink printing device 1 according to FIG. 1.
  • Both the transport device 15b and the ratchet mechanism 16b are arranged on a drive shaft 150b.
  • the transport device 15b consists of a pin wheel 151b with radially projecting pins 152b, which engage in an edge perforation of the continuous paper 3b.
  • the ratchet mechanism 16b contains an electric motor-driven cam wheel 161b rotatably mounted on the drive shaft 150b, a rocker arm 162b rotatably mounted on the drive shaft 150b and a wheel 163b rigidly arranged on the drive shaft 150b with two radially and axially offset shoulder teeth 164b, 165b.
  • the cam wheel 161b has a radially projecting cam 160b which is latched into a recess 167b of the rocker arm 162b which is pivotably attached to a wheel 166b.
  • the rocker 162b is in the collar toothing 164b via the cam 160b or 165b of the wheel 163b pressed.
  • the rocker 162b has two latching tips 168b, 169b, which snap into the respective collar teeth 164b, 165b.
  • a spring element 170b is provided in order to positively connect the rocker 162b to the cam 160b of the cam wheel 161b in each tilted position.
  • this spring element 170b can be designed as a tension spring. The tension spring is attached to the rocker 162b and to the cam gear 161b.
  • the spring element 170b can also be designed as a resilient tab, which is fastened to the rocker 162b and is thereby pressed against the wheel 163b.
  • the cam 160b presses the latching tip 168b of the rocker 162b into the shoulder teeth 164b of the wheel 163b .
  • the gear 163b and pin gear 151b which are rigidly arranged on the drive shaft 150b, are carried along. Due to the gear ratios of the gear transmissions 12, 14 to the electric motor 11 according to FIG.
  • the pin wheel 151b is pulled along faster by the transport of the perforated continuous paper 3b after the roller wedge 135 than is driven by the gear transmission 14 and the ratchet mechanism 16b.
  • the latching tip 168b of the rocker 162b is lifted out of the collar toothing 164b and the pin wheel 151b is decoupled from the electric motor 11.
  • the continuous perforated continuous paper 3b is transported further into the printing position DP, only a frictional torque of the rotatably mounted drive shaft 150b and a further frictional torque occurring between the wheels 163b, 166b can be overcome by means of a paper pull. The latter is necessary in order to bring the rocker 162b into the current working position. If this friction torque were not present, the rocker 162b could freely rotate with the cam wheel 161b without coming into engagement with the collar teeth 164b, 165b.
  • the cam wheel 161b is driven by an electric motor in the direction of rotation shown (dashed arrow).
  • the rocker 162b initially stops together with the wheels 163b, 166b and the pin wheel 151b.
  • the locking tip 169b of the rocker 162b is pressed by the cam 160b of the cam gear 161b into the collar teeth 165b.
  • the pin wheel 151b is driven in the opposite direction and the edge-punched continuous paper 3b is transported from the tear-off position AP to the printing position DP or preparation position BP.
  • a lever arrangement according to FIG. 12 can be used again. Such a lever arrangement would axially shift the wheel 166b with the rocker 162b and the drive wheel 161b on the drive shaft 150b relative to the fixed pin wheel 151b and wheel 163b.

Abstract

Le système de transport (10, 10a) pour porteurs d'enregistrements sous forme de bande (3, 3a, 3b) contient des dispositifs de transport (13, 13a, 15, 15a, 15b) entraînés par des moteurs électriques et qui transportent le porteur d'enregistrement (3, 3a, 3b) en avant et en arrière, à partir d'une position de départ (EP, EP1, BP, BP1) vers une position finale (DP, DP1, AP, AP1), d'une façon asynchrone. Un embrayage (16, 16a, 16b) qui régule la tension du porteur d'enregistrement (3, 3a, 3b) serré entre les dispositifs de transport (13, 13a, 15, 15a, 15b) est en outre associé aux dispositifs de transport (13, 13a, 15, 15a, 15b). Si, en plus des porteurs d'enregistrement sous forme de bande (3, 3a, 3b), des porteurs d'enregistrement sous forme de feuille (2, 2a, 2b) doivent être transportés dans l'imprimante (1, 1a), on peut désaccoupler le dispositif de transport (15, 15a, 15b) du dispositif d'entraînement à moteur électrique (11, 11a) en actionnant un levier de commande (19, 19a) agissant sur l'engrenage (16, 16a, 16b).

Claims (14)

  1. Dispositif pour transporter des supports d'enregistrement, sous forme de feuilles individuelles ou de bandes, dans des dispositifs d'impression, dans lequel un premier dispositif de transport et un second dispositif de transport sont entraînés, à chaque fois, par l'intermédiaire d'une transmission, à des vitesses différentes, et un des dispositifs de transport est entraîné de plus par l'intermédiaire d'un moyen de couplage,
    caractérisé en ce que le dispositif de transport tout d'abord actif dans la direction d'avance du support d'enregistrement (3,3a,3b) est un entraînement à picots (15,15a, 15b), entraîné par l'intermédiaire d'un embrayage (16), et le second dispositif de transport actif ensuite dans la direction d'avance du support d'enregistrement (3,3a,3b) est un entraînement à friction (13,13a), entraîné sans moyen de couplage, les supports d'enregistrement (2) sous forme de feuilles individuelles pouvant être amenés directement à l'entraînement à friction (13,13a), et en ce que, dans la zone de l'embrayage (16), est agencé un levier (19) muni de deux positions d'encliquetage (A,B) qui, dans une position d'encliquetage (B), déconnecte l'embrayage (16) et, en même temps, fixe l'entraînement à picots (15,15a,15b) au moyen d'un ergot d'encliquetage (191), s'engageant dans une couronne dentée (160).
  2. Dispositif selon la revendication 1,
    caractérisé en ce que l'entraînement à friction (13) entraîne le support d'enregistrement sous forme de bande (3,3a,3b) légèrement plus vite que l'entraînement à picots (15,15b).
  3. Dispositif selon la revendication 1,
    caractérisé en ce que l'entraînement à friction (13a) entraîne le support d'enregistrement sous forme de bande (3,3a,3b) légèrement plus lentement que l'entraînement à picots (15a).
  4. Dispositif selon la revendication 1,
    caractérisé en ce que :
    a) l'embrayage (16) présente un premier agencement de couplage (165,166), qui est fixé sur un arbre d'entraînement (150) du premier dispositif de transport (15),
    b) l'embrayage (16) présente un second agencement de couplage (161,164), qui est monté de façon axialement mobile contre une force élastique (F) et en pouvant tourner sur l'arbre d'entraînement (150) du premier dispositif de transport (15) et, de plus, est couplé à la transmission (14),
    c) le second agencement de couplage (161,164) présente un premier élément de couplage (164) et le premier agencement de couplage (165,166) présente un second élément de couplage (166), grâce auxquels les agencements de couplage (161,164,165,166) sont reliés ensemble.
  5. Dispositif selon la revendication 4,
    caractérisé en ce que les éléments de couplage (164,166) sont réalisés sous forme de dentures de couplage.
  6. Dispositif selon la revendication 4,
    caractérisé en ce qu'un dispositif de commutation (19) est prévu, grâce auquel le second agencement de couplage (161, 164) peut être désembrayé par rapport au premier agencement de couplage (165,166).
  7. Dispositif selon la revendication 6,
    caractérisé en ce que le dispositif de commutation (19) est réalisé sous forme d'un levier de commande, pouvant pivoter sur l'arbre d'entraînement (150), comportant une saillie en forme de coin (192), qui, lors du pivotement du levier de commande (19) sur l'arbre d'entraînement (150), presse contre le second agencement de couplage (161,164) et déplace axialement celui-ci contre la force élastique (F) sur l'arbre d'entraînement (150).
  8. Dispositif selon la revendication 7,
    caractérisé en ce que le levier de commande (19) présente un ergot d'encliquetage (191) qui, dans l'état pivoté du levier de commande (19) sur l'arbre d'entraînement (150), s'engage dans une couronne dentée (160) du premier agencement de couplage (165,166).
  9. Dispositif selon les revendications 6 à 8,
    caractérisé en ce qu'un ressort à lames (190), serré entre deux points, est muni d'une élévation (197) qui fixe le levier de commande (19) dans un état (A) contre une butée (193) et dans un état (B) contre la couronne dentée (160).
  10. Dispositif selon la revendication 1,
    caractérisé en ce que :
    a) l'embrayage (16b) présente un premier agencement de couplage (163b,164b,165b), qui est fixé sur un arbre d'entraînement (150b) du premier dispositif de transport (15b),
    b) l'embrayage (16b) présente un second agencement de couplage (160b,161b,162b,166b), qui est monté rotatif sur l'arbre d'entraînement (150b) du premier dispositif de transport (15b) et, de plus, est couplé à la seconde transmission (14),
    c) le premier agencement de couplage (163b,164b,165b) présente un premier élément de couplage (164b,165b) et le second agencement de couplage (160b,161b,162b,166b) présente un second élément de couplage (162b), monté en pouvant basculer, grâce auxquels les agencements de couplage (160b à 166b) sont reliés ensemble,
    d) le second agencement de couplage (160b,161b,162b,166b) présente un moyen (160b,161b) couplé à la seconde transmission (14) qui, de façon dépendant du sens de rotation du moteur électrique (11), modifie la position de basculement du second élément de couplage (162b) contre la force élastique d'un élément à ressort (170b).
  11. Dispositif selon la revendication 10,
    caractérisé en ce que le premier élément de couplage (164b, 165b) est réalisé sous forme de deux dentures opposées, déplacées axialement l'une par rapport à l'autre, et le second élément de couplage (162b) est réalisé sous forme de lame comportant deux pointes d'encliquetage (168b,169b).
  12. Dispositif selon la revendication 1,
    caractérisé en ce que :
    a) l'embrayage (16a) présente un premier agencement de couplage (144a,163a) qui est monté rotatif sur un arbre (141a) et est couplé à la transmission (14a),
    b) l'embrayage (16) présente un second agencement de couplage (145a,160a,164a,166a,167a) qui est monté rotatif sur l'arbre (141a) et de façon axialement mobile contre une force élastique (F2), et peut être découplé du premier dispositif de transport (15a),
    c) le premier agencement de couplage (144a,163a) présente un premier élément de couplage (163a) et le second agencement de couplage (145a,160a,164a,166a,167a) présente un second élément de couplage (164a), grâce auxquels les agencements de couplage (144a,145a,160a,163a,164a, 166a,167a) sont reliés ensemble,
    d) le second agencement de couplage (145a,160a,164a,166a, 167a) présente des moyens (160a,166a,167a) pour le découplage temporaire du dispositif de transport (13a) du moteur électrique (11a), grâce auxquels le second élément de couplage (164a) est axialement déplacé contre la force élastique (F2) sur l'arbre (141a).
  13. Dispositif selon la revendication 12,
    caractérisé en ce que les éléments de couplage (163a,164a) sont réalisés sous forme de crabots.
  14. Dispositif selon la revendication 12 ou 13,
    caractérisé en ce que les moyens (160a,166a,167a) comportent une élévation (166a) agencée de façon opposée à l'élément de couplage (164a), qui se déplace, dans le sens de rotation direct du moteur électrique (11a), sur une coulisse (167a) précontrainte par un ressort (160a) et, dans le sens de rotation inverse du moteur électrique (11a), presse la coulisse (167a) contre une force élastique (F1) du ressort (160a).
EP91904864A 1990-03-16 1991-03-01 Dispositif servant a transporter des porteurs d'enregistrements sous forme de bande dans des imprimantes Expired - Lifetime EP0519938B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP90105029 1990-03-16
EP90105029 1990-03-16
PCT/DE1991/000197 WO1991013764A1 (fr) 1990-03-16 1991-03-01 Dispositif servant a transporter des porteurs d'enregistrements sous forme de bande dans des imprimantes

Publications (2)

Publication Number Publication Date
EP0519938A1 EP0519938A1 (fr) 1992-12-30
EP0519938B1 true EP0519938B1 (fr) 1994-05-18

Family

ID=8203761

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91904864A Expired - Lifetime EP0519938B1 (fr) 1990-03-16 1991-03-01 Dispositif servant a transporter des porteurs d'enregistrements sous forme de bande dans des imprimantes

Country Status (5)

Country Link
US (1) US5370291A (fr)
EP (1) EP0519938B1 (fr)
JP (1) JPH05506820A (fr)
DE (1) DE59101682D1 (fr)
WO (1) WO1991013764A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07256959A (ja) * 1994-03-22 1995-10-09 Sato:Kk 印字方法及びそのプリンタ
JP4639415B2 (ja) * 1999-07-02 2011-02-23 トヨタ自動車株式会社 薄膜積層装置
JP5345099B2 (ja) * 2010-04-09 2013-11-20 矢崎総業株式会社 計器ユニット

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2461015C3 (de) * 1974-12-21 1979-11-22 Triumph Werke Nuernberg Ag, 8500 Nuernberg Papierspannvorrichtung für Endlosformulare o.dgl
US4418808A (en) * 1980-05-21 1983-12-06 Nisshin Kogyo Kabushiki Kaisha Centrifugal clutch brake arrangement for farm work machinery or other apparatus
US4360279A (en) * 1980-07-02 1982-11-23 Brother Kogyo Kabushiki Kaisha Printing paper feeding mechanism
DE3481294D1 (de) * 1983-04-26 1990-03-15 Siemens Ag Papiertransportvorrichtung fuer einzelblaetter und endlospapier in druckeinrichtungen.
US4606663A (en) * 1983-11-29 1986-08-19 Siemens Aktiengesellschaft Switchable paper transport device for single sheets and continuous paper in printers
IT1196758B (it) * 1984-11-19 1988-11-25 Olivetti & Co Spa Alimentatore di supporti di stampa per una macchina per scrivere o simili macchine da ufficio
DE3606060C1 (de) * 1986-02-25 1987-04-30 Siemens Ag Papiertransportvorrichtung fuer Einzelblaetter und Endlospapier in Druckeinrichtungen
US4759649A (en) * 1987-02-24 1988-07-26 Hewlett-Packard Company Dual axis paper drive
JPS63299957A (ja) * 1987-05-30 1988-12-07 Copal Co Ltd プリンタの紙送り装置
GB2228713B (en) * 1989-02-08 1993-05-05 Brother Ind Ltd Sheet feeder for printers
DE3939991A1 (de) * 1989-12-02 1991-06-06 Benz & Hilgers Gmbh Verfahren und vorrichtung zum ein- und auskuppeln einer antriebswelle einer arbeitsstation einer maschine, insbesondere einer verpackungsmaschine

Also Published As

Publication number Publication date
US5370291A (en) 1994-12-06
DE59101682D1 (de) 1994-06-23
WO1991013764A1 (fr) 1991-09-19
EP0519938A1 (fr) 1992-12-30
JPH05506820A (ja) 1993-10-07

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