KR100337015B1 - Automatic press with reinsertion control - Google Patents

Abstract

The automatic printing machine 10 of the present invention is provided with a plurality of printing stations each having a printing mechanism 60 for printing at least one component image at a spaced position along the web 11. Each printing mechanism 60 is also arrangeable on one side of the printing press to facilitate inspection. Computers 400 and 405 are used for accurate and repeatable control operations of printing mechanism 60 at internal and external locations to accurately match and print component images to be printed by multiple print stations 13. Each station 13 has a micro for accurately matching the printing roller 61 between each station 13 to a preprinted component image of the composite image of the web 11 to be reinserted or removed into the printing press 10. With a computer controller 407 based on the processor, the repetitive length of the preprinted image to deform in the processor varies and varies with the length of the web 11. The measurement is made by a series of repeat length sensors 350 on the web 11 and the return analysis is performed and shown as a processing component in the predicted integer or the next image to be calculated at each station 13. The circumferential speed of the printing roller 61 at each station 13 is individually controlled in accordance with each error prediction to control the length of the image printed at the station on the web 11. The speed is controlled by pulses that are transmitted from each station 13 to the stepper motor 327 of the harmonic driver 275. The pulses are evenly spaced across the print length of the image.

Description

Automatic press with reinsertion control

FIELD OF THE INVENTION The present invention relates to rotary printing presses having multiple printing stations, and more particularly to an automated form of such a rotary printing press, in particular an automatic rotary press for processing continuous substrates.

Background of the Invention

Rotoprinters with multiple print stations of various computer controlled automation handling webs (printing papers) or continuous substrates are known. The printing stations of such presses are often arranged in a row, fixed to each other, and usually each station has its own gear train driven by a drive shaft common to all stations. Each station applies a form, such as a printing roller, to apply at least one component image of the ink or other transferable image forming fluid at locations spaced along the length of the web (ie, per rotation of the rotatable printing element). Has a printing mechanism comprising a rotatable printing element. An impression mechanism with a backside treatment is used to support the web while the image is being applied. In many rotary presses, such as rotoflexographic presses, the printing mechanism is a printing plate mounted on a printing roller that applies an image to a web, and a weighing that dispenses a predetermined amount of ink or other fluid to the printing plate. and metering rollers or doctor blade assemblies and anilox rollers having some form of ink mechanism. The pressing mechanism is generally a rotatable impression cylinder roller. The gear train of each station usually drives the rotation of each of the rollers. In such a multi-station printer, the monochrome (i.e. component image) of the final composite image is printed at each station. Each component image is adapted to be printed in registration with one another in the transverse and longitudinal directions on the web.

Once one print job is completed, the printing mechanism of each print station (to be used for the next print job) needs to be changed or otherwise functioned and repositioned for printing. For example, the printing roller can be replaced and the printing mechanism is moved to a new position for printing. Such a press must be paused to set up or prepare an applicable print station for the next print job. Often, the time it takes for the operator to set up the printer for the next print job is longer than the print run itself time. The time that the press stops to set up for the next print job is not the time it takes to start the print job and generate profit.

Many conventional presses have included an automated system to reduce the set up time. These systems vary according to their degree of automation. Some of these automatic setting systems include positioning mechanisms for the automatic moving roller of the printing mechanism at and from various positions during preparation of the printing press. These two systems are disclosed in US Pat. Nos. 4,413,560 and 5,060,570.

Attempts to reduce the setting time include combining the printing mechanism of each print station in a removable unit or cassette, which can be replaced with another unit, prepared in advance for the next print job. See, for example, US Pat. Nos. 4,462,312 and 5,060,569.

While previous attempts to reduce set-up time have been somewhat successful, there is still a need for a more automated multi-station operating printer that can proceed from one print job to another in a shorter time period.

The main problem with multi-station rotary presses is to maintain consistent quality of the printed image, that is, print quality and image registration. Problems of print quality, such as barring, are known to be chronic for multi-station rotary presses. The registration of each partial or component image must be monitored and maintained to ensure the quality of the final composite image. Many conventional printing presses include a computer controlled matching system for automatically maintaining registration. Success in maintaining consistent registration over the length of the web (ie positioning of component images) has generally been found to vary from system to system. Mismatches in maintaining print quality and registration control can increase the length of the web to be scraped (ie, scrap ratio) and limit the types of print jobs that can be run properly on a given press.

The assignee of the present invention is a species of component image on web 501 in a prefabricated multi-station flexographic printing press 502 for processing narrow webs (ie, webs having a width of about 19 inches (48 cm) or less). A computer controlled matching system 500 was used to control directional positioning (ie, circumferential registration of the printing rollers). Flexographic printing presses typically have two sets 503, 504, each consisting of six print stations 505-510, and 511-516, each set having one computer 550 controlling circumferential registration. Has Each station includes a frame 517 consisting of a gear train side 518 and an operator side 519 provided with printing mechanism rollers 520 and 521 therebetween. In each station, the shaft 525 mounting the pressure roller 520 is in a power interruption state of the common drive shaft 526 via a worm gear set 527 located outside of the gear train side of the station frame. The print plate rollers 521 of each print station are individually rotated by a common drive shaft through separate branches 528 of the station gear train that drives the gears 535 on the print rollers 521. The circumferential registration of the component images of each station is controlled by slowing or accelerating the rotation of the printing roller 521 while maintaining the speed of the web 501 through the station. A single coordinating gear assembly 530 similar to that disclosed in US Pat. No. 3,724,368 is connected in a separate gear train branch 528. The single coordinating gear assembly 530 is mounted to one end of the jack shaft 531 downstream of the pressure roller 520 and outside of the gear train side 518 of the station frame 517. The jack shaft 531 is connected to either cross section of the side of the station frame 517. A gear 532 fixed to the pressure roller shaft 525 between the gear train side 518 of the station frame 517 and the worm gear set 527 is coupled to an external gear 533 on a single coordinating gear assembly 530. Driven. The single coordinating gear assembly 530 rotates the jack shaft 531 and also drives a tooling gear 534 fixed to the jack shaft inside the gear train side 518 of the station frame 517. The jack shaft press gear 534 drives another press gear 535 fixed to the shaft of the printing roller 521 via an idle press gear 536 mounted for free rotation about the press roller shaft. . Only the printing roller 521 is driven by the single coordinating gear assembly 530. The three press gears 534, 535, and 536 are all spur gears and are generally located on the non-working plane only inside the gear train side 518 of the station frame 517. The single harmonic gear assembly 530 has a 1% difference in gear ratio. To compensate for this difference, the gear ratio between the pressure roller gear 532 and the external gear 533 on the single coordinating gear assembly 530 is 100: 101. The standard DC motor 537 is connected to the drive shaft 526 inside the single coordinating gear assembly when the jack shaft 531 is activated, so that the printing roller 521 is connected to the common drive shaft 526 or the pressure roller 520. Rotate at a different speed than Pressure roller 520 assists in transporting web 501 through print stations 505,... 516. Thus, activation of the single coordinating gear assembly 530 affects the phase change between the rotational speed of the printing roller 521 and the speed of the web 501.

In order to initially circumferentially match (ie preliminary) the component image in the form of the assignee's Flexographic Rotary Printing Press, the operator may operate a DC motor of a suitable single coordinating gear assembly 530 at the switch 539. By activating 537, the relative circumferential position of each printing roller 521 must be adjusted. Preliminary matching is performed manually and the printing press is stopped. In controlling the circumferential registration in the web 501 operating through the printer 502, the plate roller 521 of the first printing station 505 is placed on the web 501 for every rotation of the printing roller 521. A mark 538 (horizontal bar) is printed. The print roller 521 at each subsequent print station 506-516 downstream of the first station has individual marks 540 rotated along the print roller. Two optical seals 541, 542 are mounted to each station frame 517, the sensor 541 monitors it as the web mark 538 passes, and the sensor 542 prints the station's printing roller mark ( Monitor the rotation of 540. The encoder 544 is connected to the common drive shaft 526 of the printer 502. This encoder 544 generates any number of electric pulses per rotation of the common drive shaft 526 as well as the driven roller including the print roller 520. Each computer 550 has a counter 551 that counts these pulses. Each sensor 541, 542 is basically a switch that is powered on or off when the marks 538, 540 are detected. Each computer 550 directly from its counter 551 whenever the marks 538, 540 activates the individual sensors 541, 542 for any one of the six stations connected to each computer 550. It is programmed to read the pulse coefficients. Each computer 550 is programmed to read one pulse coefficient and then to read the other pulse coefficients for the pair of marks 538 and 540 per rotation of the printer 521 at each of its six stations. These pulse coefficient readings are then stored in registers or memory portions 561 and 562 respectively corresponding to the relative positions of the marks 538 and 540 relative to the individual stations connected to each computer 550. After obtaining the pulse coefficients for each mark from the station, the appropriate computer 550 subtracts the two numbers to obtain a difference coefficient equal to the number of pulses between the two marks. This difference coefficient is also stored in a register 563 for each station. The order in which the computer 550 obtains and analyzes the pulse coefficients for the marks 538 and 540 at each other print station depends on the order in which the marks at each station are detected. Until the mark is analyzed at each station during the previous cycle, the computer does not start a new cycle of searching for the mark and obtaining pulse coefficients and data analysis at all six stations, or three unsuccessful attempts to search for the mark. . If no two marks are detected in one revolution at a given station, for any reason, the computer 550 has been programmed to continue searching until three revolutions of the print roller 521 before giving up and starting a new cycle.

The optimal circumferential positioning of each print roller in a given set of stations with respect to the web is determined by the number of pulses (ie, coefficients) between the print roller mark 540 and the detection of each web mark 538. The memory 555 in the computer 550 is stored as a corresponding position. This optimal position has been subtracted from the difference coefficient to generate the error value stored in register 564 or the memory location corresponding to each station. The optimum position of each printing roller 521 is a characteristic already determined by the operator. The error coefficient is compared with the tolerance range stored in the memory 556. When the pulse coefficient between the marks is stored out of the acceptance range initially determined by the operator and stored in the memory 556 by the operator, the computer 550 is connected to the DC motor 537 on the appropriate single harmonic gear assembly 530 of the corresponding station. By sending a corresponding signal to the driver 565 which has activated, it affects the phase change and rotates the applicable plate roller 521 to a mating state. In making these registration corrections, the appropriate DC motor 537 is powered by the applicable computer 550 at the beginning of the repetition length (ie, the distance between successive web marks) and the number of pulses (ie Will continue to operate for a period programmed to approximately equal The period programmed to correspond to one coefficient is variable. Thus, each computer 550 obtains data (ie, pulse coefficients) for marks 538 and 540 at each of the six stations 505 to 510 and 511 to 516 and analyzes the data (ie, optimal coefficients). Compensate accordingly.

It is often desirable to use webs for one or more print runs. For example, it is desirable to run the web through a flexographic press and to reinsert the web through the flexographic press for another print run using the web in an intermediate print operation. When a web is used for multiple print runs, the web is likely to experience dimensional changes that change along the length of the web. As the web changes dimensionally, the image is already printed on the affected web area. Therefore, in addition to the circumferential registration control, a computer control system capable of correcting such a dimensional change in a continuous printing operation (ie, reinsertion control) is desired.

The assignee's already manufactured multi-station flexographic rotoprinter 502 of the present invention includes a reinsertion control system. In a conventional reinsertion control system, a central computer includes one or more registrations from each working print station in the press. You will get a readout of the error and flatten all of these values to reach a reinsert error. The mean of successive match errors represents the repeated difference between the space between the preprinted web marks (ie, the actual repeat length) and the repeat length of the printer. This difference is due to dimensional changes in the web and is defined as reinsertion error. The original web mark 538 is printed while the initial print run is detected for reinsertion control during continuous print run. These central reinsertion computers are alternately provided with programming options that value the reading at each station or provide a current reading that is heavier than the older reading. Based on the average of these readings, the reinsertion control computer simultaneously performs the same reinsertion error correction for this mean error at each operating print station on a continuous basis. The correction is applied as a signal added to the circumferential matching control signal. In conventional circumferential matching control correction, reinsertion correction is performed by adjusting a suitable printing roller 521 around with a single harmonic gear assembly 530 driven by a motor responsive to the analog pulse width control signal.

Despite the conventional technology, multiple webs can be fully automated and cost-effective, keeping print quality and image registration consistent when the web is reinserted and reducing the set-up time it takes to run from one print job to another. There is a continuing need for station rotary presses.

Summary of the Invention

It is an object of the present invention to provide a more fully automated and cost effective multi-station rotary press.

Another object of the present invention is to provide a printing machine which can more consistently maintain print quality and image registration even during printing of a preprinted web.

It is another object of the present invention to provide a printing press which reduces the setting time for changing from one print job to another.

The rotoprinter of the present invention, which achieves the above object, comprises a plurality of print stations for transferring at least one composite image at a position apart along the length of a continuous substrate operated through the plurality of print stations. Each printing station of such a printing machine comprises a printing mechanism performed by a frame, a frame applying at least one component image at a position along the length of the continuous substrate, and a continuous substrate whenever a component image is applied to the printing apparatus. It has a pressing mechanism performed by the frame to return to. The continuous base layer is performed in the frame with a path oriented through the station between the printing mechanism and the pressing mechanism.

The printing mechanism of such a printer includes some form of rotatable printing element, such as a printing roller, mounted for rotation within a frame for applying at least one component image of a transferable image forming fluid such as ink to a continuous substrate. do. It is expected that the rotatable printing element can be any one of a variety of printing rollers, such as those used for flexographic printing, offset printing, rotary printing and other forms of printing. The use of tubular stencils such as those used for rotary screen printing is also expected. The printing mechanism includes some form of fluid dispensing system for dispensing a transferable image forming fluid to a rotatable printing element. For example, anilox rollers can be used to supply a measurable amount of fluid, such as ink, to a printing roller in an ink supply mechanism (such as an egg roller or doctor blade assembly and ink container).

Each station includes a circumferential adjustment mechanism, such as a coordinating gear assembly, that adjusts the rotational speed of the rotatable printing element independently of the speed of the continuous substrate, as it operates through the printing station. The computer controlled circumferential matching system controls the operation of the circumferential adjustment mechanism to automatically change the circumferential direction of the rotatable printing element with respect to the continuous substrate. The rotatable printing element is automatically adjusted in the circumferential direction to compensate for the circumferential matching error of the component image applied to the continuous substrate. The circumferential adjustment of the rotatable printing element with respect to the continuous substrate is preferably achieved by operating the circumferential adjustment mechanism with the appropriate number of correction pulses through the DC stepper motor. Such pulse generation of the stepper motor increases or decreases the rotational speed of the rotatable printing element sufficient for the continuous substrate to match the printing of the image.

The computer controlled circumferential matching system maintains a more accurate image registration than conventional computer controlled circumferential matching systems. Such a system may make the correction within or less than about one repetition length after error detection.

The computer controlled matching system of the present invention is provided with specific reinsertion characteristics for situations where the continuous substrate experiences a dimensional change along the length of the substrate. For example, this occurs when continuous substrates are used for multiple print runs. The same applies to previous composite images preprinted in the affected area of the substrate, as the substrate changes with respect to dimensions. The reinsertion property can correct for the dimensional change with respect to the continuous substrate. In order to circumferentially align the newly printed component image more closely to the previous composite image, the reinsertion feature enlarges or reduces the newly printed component image when applied to the continuous substrate. This is accomplished by independently measuring the space between the web marks at each print station and statistically analyzing the error with a separate print station computer to determine the reinsertion error component. The reinsertion error is corrected by uniformly spacing the circumferential registration correction pulses over the repetition length in the individual print station and changing the speed at which the rotatable printing element is rotated relative to the running speed of the continuous substrate. The host computer is a monitoring system that can be adjusted (ie, variable changed) in the program of each print station. Preferably, the host computer does not control the logical operations of the individual print stations. The host Kimputer also selectively analyzes data from each print station and supplements the logic from the individual computers to better predict the progress of error change and reinsertion errors at each station through the printer's print station.

Preferably, each printing station of such a press also includes a positioning mechanism for guiding the printing mechanism to a good position relative to the pressing mechanism. One such location is the printing location where the printing mechanism is positioned to apply at least one component image of the transferable image forming fluid to the continuous substrate upon rotation of the rotatable printing element. The other position includes at least one non-print position that is not the position at which the printing mechanism applies the component image to the continuous substrate. A computer controlled positioning system is used to control the operation of the positioning mechanism to automatically guide the printing mechanism into and out of the printing position.

The positioning mechanism includes a first positioning mechanism for moving the rotatable printing element with respect to the pressing mechanism and a second positioning mechanism for moving the fluid dispensing system with respect to the rotatable printing element. The computer controlled positioning system of the present invention controls the operation of each positioning mechanism to guide the printing mechanism into and out of the printing position.

In a preferred embodiment, the positioning mechanism comprises two spaced apart upper carriages that can slide along two planar straight slides mounted above each lower carriage. The lower carriage is in turn slidable along two planar straight slides mounted on one side of the base platform. The rotatable printing element has one end mounted to the lower carriage. The fluid distribution system is mounted between the upper carriages. In a printing mechanism wherein the rotatable printing element is a printing roller, the fluid dispensing system includes a rotatable fluid dispensing element of some type such as anilox roller and an ink supply mechanism of some type, the pressurizing mechanism being a press roller, and the carriage being At least the pressure roller, printing roller and anilox roller are designed to be located on the same plane. This coplanar relationship has been shown to facilitate computer controlled positioning of the printing apparatus. DC stepper motors are used to position each carriage. The encoder is connected to each stepper motor to provide feedback to the computer controlled positioning system on whether each stepper motor is operating and the degree of positioning of each carriage.

Each print station has a gear train with individual branches that drive the rotation of the rotatable printing element. In the gear train for reducing the possibility of gear backlashing and the problem of print quality occurring, it is desirable to include a gear assembly movable in and out of position for engaging and driving a gear mounted on the rotatable printing element. . Preferably, the movable gear assembly includes a leading gear capable of oscillating in and out of position for engaging and driving a gear mounted to the rotatable printing element. When both the printing element and the fluid dispensing element of the printing mechanism are rotatable and on the same plane, the gear train can drive the rotation of the fluid dispensing element in the print position or the non-print position while continuing to maintain the coplanar relationship. Include another branch that exists. In one embodiment, the other branch of the gear train includes an articulating gear assembly having a separate motor that drives the rotation of the rotatable fluid dispensing element regardless of the gear train balance.

In a preferred embodiment, each print station also includes an axial adjustment mechanism for simultaneously adjusting the transverse position of the fluid distribution system and the rotatable printing element in the frame. The computer controlled axial registration system controls the operation of the axial adjustment mechanism to automatically and simultaneously move the fluid distribution system and the rotatable printing element relative to the web substrate. The rotatable printing element and the fluid dispensing system are moved to the transverse position required to correct the axial registration error of the component image applied to the continuous substrate. Thus, in the embodiment of the printing press of the present invention, the matching of the component images (axial and circumferential matching) and the adjustment of the printing mechanism (in / out of the printing position) can be controlled automatically.

In each printing station of the printing press of the present invention, it is preferable to include an auxiliary frame having a base platform carrying a rotatable printing element and a fluid dispensing system transversely through the frame from side to side. The off-line adjustment mechanism is used to move the base platform laterally. The base platform can be moved to an operational position in which the rotatable printing element and the fluid dispensing system are positioned within the frame. The base platform may also be moved to a stand-aside position in which a sufficient portion of the base platform extends beyond one side of the frame so as to check at least the fluid distribution system and the rotatable printing element. Also, the base platform is self-supporting in the frame when in the out of position position. The rotatable printing element and fluid distribution system are completely carried on the base platform when in the out of position position. The computer controlled off-line adjustment system is used to control the operation of the off-line adjustment mechanism to automatically move the auxiliary frame relative to the operating position and the out of position position.

Most color print jobs usually use only six print stations (ie six different color component images). The printing press of the present invention typically includes 12 print stations. Thus, in one embodiment of the printing press of the present invention, a printing mechanism (at least, a rotatable printing element and a fluid dispensing system) may be used to drive a plurality of printing mechanisms for the next printing operation while running printing jobs with different balances of the printing station. It can be moved automatically beyond one side of the frame that can be used and set and out of the print position.

It is also desirable to include a computer controlled pre-matching system in each print station. Such a system controls the operation of the circumferential adjustment mechanism to automatically rotate a pre-programmed circumferentially rotatable printing element that aligns the rotatable printing element approximately with the other rotatable printing element. This automatic pre-matching occurs before the printer starts a print job.

The above and other objects, features and advantages of the present invention will become more apparent upon reading the following detailed description taken in conjunction with the accompanying drawings.

1 is a side view seen from the operator side of an embodiment of an automatic printing machine of the present invention.

FIG. 2 is an enlarged side view of the operator's side of a portion of one of the printing stations of the automatic printing machine of FIG.

3 is a plan view of the printing station of FIG.

4 and 5 are cross sectional views taken along line 4-4 of FIG. 3 showing the auxiliary frame of the invention in the operating position and in the deviated position, respectively.

6 is a cross-sectional view taken along line 6-6 of FIG. 3 showing the gear train side of the rotatable gear assembly and roller positioning mechanism in one branch of the gear train of the present invention.

7 is a partially enlarged view of the roller positioning mechanism of FIG.

8 is a cross-sectional view taken along line 8-8 of FIG. 7 showing the upper and lower slide assemblies in detail.

9 is a sectional view taken along line 9-9 of FIG. 7 showing the structure of the metering roller pressure adjusting system in detail.

10 is a cross-sectional view taken along line 10-10 of FIG. 7 showing the structure of the anilox roller drive shaft attachment portion in detail.

11 is a perspective view of a gear train of one of the printing stations of the printing machine of FIG.

12 is a cross-sectional view of the connected gear assembly in another branch of the gear train of the present invention taken along line 12-12 of FIG.

13 is a side view of the oscillable gear assembly according to the invention as seen on line 13-13 of FIG.

14 is a plan view of the connected gear assembly of FIG. 12 in an enlarged position as a whole for clarity.

14A to 14C are side schematic views showing various connection structures of the linked gear assembly of the printing press of the present invention.

FIG. 15 is a cross-sectional view taken along line 15-15 of FIG. 6 showing the swingable gear assembly and the dual harmonic gear assembly of the present invention.

FIG. 16 is a cross-sectional view showing details of an attachment portion and a pressure roller encoder to the roller of the present invention as seen along line 16-16 of FIG.

17 is a cross-sectional view of the axial adjustment mechanism of the present invention taken along line 17-17 of FIG.

18 is a plan view showing a structure with a web mark sensor taken along line 18-18 of FIG.

19 is a cross-sectional view taken along the 19-19 line of FIG.

FIG. 20 is a cross sectional view taken along line 20-20 of FIG. 18;

21 is a diagram showing web marks detected in a print job;

Figure 22 is a block diagram of a prior art circumferential match control system of assignee.

Figure 23 is a plan view containing a block diagram of one preferred embodiment of a computer control system of the printing press of Figure 1;

24 is a block diagram of a preferred embodiment of a positioning controller of the computer control system of FIG.

25 is a flow chart schematically showing the main loop of the operation of the positioning controller of FIG.

FIG. 25A is a flowchart of a gear pitch setting routine of the flowchart of FIG. 25; FIG.

FIG. 25B is a flowchart of an anilox roll diameter setting routine of the flowchart of FIG. 25; FIG.

25C is a flowchart of a repeat length setting routine of the flowchart of FIG. 25. FIG.

FIG. 25D is a flowchart of a paper thickness setting routine of the flowchart of FIG. 25. FIG.

FIG. 25E is a flowchart of the CALIBRATE routine of the flowchart of FIG. 25. FIG.

25F or 25 is a flow chart of a zero print head routine.

FIG. 25G is a flowchart of the RETRACT PRINT HEAD routine of the flowchart of FIG. 25. FIG.

FIG. 25H or FIG. 25 is a flowchart of a manual throw-off routine.

FIG. 25I is a flowchart of the AUTO PRINT routine of the flowchart of FIG. 25. FIG.

FIG. 25J is a flow chart of the ADJUST PRINT HEAD routine of the flowchart of FIG. 25. FIG.

Flow chart of the ADJUST ANILOX ROLL routine of the flow chart of FIG. 25K or FIG.

26 is a block diagram of a preferred embodiment of a registration controller of the computer control system of FIG.

FIG. 27 is a flowchart schematically showing a main loop for the operation of the match controller of FIG.

27A is a flowchart of an interrupt processing routine of the controller of FIG. 26 in response to detection of a printing roll mark.

27B is a flowchart of an interrupt processing routine of the controller of FIG. 26 in response to detection of a web mark.

27C is a flowchart of an interrupt processing routine of the controller of FIG. 26 in response to a pulse from an operator adjustment dial.

FIG. 27D is a flowchart of a registration setting routine initialized by the operator's selection of the next mark button when called by the main loop of FIG. 27. FIG.

FIG. 27E or FIG. 27 is a flow chart of a button press routine that interprets button press commands from an operator when invoked by the main loop of FIG. 27 and informs the operator display.

FIG. 27F or a flowchart of a display setting routine for selecting a display subroutine corresponding to an operation selected by an operator when called by the routine of FIG. 27E.

FIG. 27G or a flowchart of a button press interpretation routine that determines the action selected by an operator when invoked by the routine of FIG. 27E.

FIG. 27H or FIG. 27 is a flow chart of a linear matching routine that determines and controls the circumferential match of a printer when called by the main loop of FIG. 27. FIG.

FIG. 27I is a flow chart of a lateral matching routine that determines and controls the axial term matching of a printing machine when called by the main loop of FIG. 27. FIG.

27J is a flow chart of the acquisition (GAIN) indication, adjustment, and setup subroutines invoked by the routines of FIGS. 27C, 27F, and 27G.

27K or 27C, 27F, and 27G are flow charts of the irradiation zone window indication, adjustment, and setting subroutines invoked by the routines of FIGS.

27L or 27C, a flowchart of the DEAD ZONE indication, adjustment and setting subroutines invoked by the routines of FIGS. 27F and 27G.

27M is a flowchart of the PREREGISTRATION indication and setup subroutines invoked by the routines of FIGS. 27F and 27G.

27N or 27C, a flowchart of the LINEAR AVERAGE indication, adjustment, and setting subroutines invoked by the routines of FIGS. 27F, 27F, and 27G.

27P or 27C, a flowchart of LATERAL AVERAGE indication, adjustment, and setting subroutines invoked by the routines of FIGS. 27C, 27F, and 27G.

27Q or a flowchart of a SPECIAL function subroutine called by the routine of FIG. 27G.

27R or 27C, a flowchart of the REPEAT LENGTH indication, adjustment and setting subroutines called by the routines of FIGS. 27F and 27G.

27S or 27C, 27F, and 27G are flowcharts of the NUMBER OF REPEAT indication, adjustment, and setting subroutines called by the routines of FIGS.

27T or 27C, a flow chart of the STATION ADDRESS indication, adjustment and setting subroutines invoked by the routines of FIGS. 27F and 27G.

27U or 27C, 27F, and 27G are flow charts of the LINEAL REGISTRATION indication, adjustment, and selection subroutines invoked by the routines of FIGS.

27V or 27C, a flowchart of the LATERAL REGISTRATION indication, adjustment, and selection subroutines invoked by the routines of FIGS. 27C, 27F, and 27G.

27W or 27C, a flowchart of the CEC indication, adjustment and selection subroutines invoked by the routines of FIGS. 27F and 27G.

27C or a flowchart of the CEC decision subroutine called by the routine of FIG. 27H.

With reference to FIG. 1, an automatic rotoprinter 10 for printing at least one composite image at a spaced position along the length of the web 11 or continuous substrate is shown in accordance with the present invention. As an example, a particular printing press 10 disclosed herein is a flexographic rotoprinter 10 for processing a web 11 having a width of about 19 inches (48 cm) or less. As will be described in detail later, it is contemplated that the basic design of the printing press 10 of this embodiment would be suitable as a printing press capable of processing webs 11 up to 40 inches (101 cm) wide. The web 11 used in this flexographic press 10 is passed to a spool (not shown). The press 10 has an unwind station 12 which carries a spool of the web 11 while the web 11 is unwound and an infeed station 14 which feeds the web 11 into the press 10. It includes. Such a unwinding station 12 and a supply station 14 are already known in the art. The printer 10 also has a plurality of print stations 13 arranged in a line with the first print station 13a and a number of subsequent print stations 13b to 13n downstream thereof. Downstream as used herein refers to the direction in which the web 11 moves (ie away from the unwinding station 12) through the printing press 10, and upstream refers to the direction in which the web 11 moves (ie, unwinding station ( 12) direction. Each print station 13 applies at least one component image of a transferable image forming fluid, such as a single color printing ink, at locations spaced along the length of the web 11. The single color component image applied to the print station 13 is matched or matched and printed in longitudinal terms (ie circumferential registration) and transverse (axial registration) on the web 11 to form a final composite image. As used herein, the transverse direction refers to the direction of travel from one edge of the web 11 to the other edge, and the longitudinal direction refers to the direction from one end to the other end of the web 11 (ie, the web 11). ) Parallel to the direction of movement. Typically, up to six print stations 13 (ie, single color component images) are used to provide the desired multicolor composite image. As will be apparent below, this flexographic rotoprinter 10 typically includes up to twelve print stations 13. In the printing press 10 of the present invention, a desirable number of print stations 13 are used when the web 11 passes through, with the balance of the print station 13 not being used (i.e. without applying a component image). Can be.

The printer 10 also includes a curing system 19 for curing each component image applied to a given print station 13 before the next component image is applied by the subsequent printing station 13. Any system currently on the market can be used to cure an image printed with a particular fluid. When dryable ink is used, the curing system 19 may use high speed heated air to dry the applied component image. This ink drying system 19 is preferably located above the station 13. The common air intake branch 20 is connected to each print station 13 via a combustion chamber 21. Air passing from the suction branch pipe 20 through the chamber 21 is heated by the gas burner 22. The newly printed web 11 at each print station 13 moves through the drying chamber 23. Heating air from the combustion chamber 21 flows through multiple nozzles 24 located in the drying chamber 23. The nozzle 24 is positioned so that the heated air is directed against the printed surface of the web 11 as the web passes through the chamber 23. At this time, the air outlet nozzle 24 is pulled from the chamber 23 maintained at the negative pressure through the port 26 common to all the stations 13 to the return branch pipe 25 to discharge the air. Although a hot air drying system has been described herein, it can be appreciated that any curing system may be used that properly cures the component image before subsequent component images are applied.

The printer 10 may include a die station 30 after the last print station 13n. Such a die station 30 is already known in the art and is used to separate the portion of the web 11 where the component image is printed from the surrounding balance of the web 11. At this time, the currently processed web 11 is also rewound to the spool at a rewind station 31 already known in the art. The printer 10 uses a plurality of idler rollers 32 to route the web 11 through the printer 10.

Printing station frame

1 to 5, each print station 13 comprises a frame comprising a first vertical support panel 37 and a second vertical support panel 38 spaced apart on opposite sides of the printing press 10. Has 36. As used herein, the reference to the front or operator side of the printer 10 refers to the side shown in FIG. The reference to the rear or gear train side of the printing press 10 refers to the opposite side of the side shown in FIG. The first base member 39 and the second base member 40 are fixed to the bottom of each support panel 37, 38. The first horizontal support rod 41 and the second horizontal support rod 42 are fixed in the middle of the respective support panels 37 and 38 above the base members 39 and 40. The print stations 13 are bundled together in a row by fixing the corresponding base members 39 and 40 and the supporting rods 41 and 42 together. The distance between successive print stations 13 is thus maintained. A cross beam 43 is fixed between each pair of support panels 37 and 38 wherever there is a need to maintain space therebetween.

In a preferred embodiment of the printing press 10 of the present invention, each print station 13 comprises an auxiliary frame 47 having a base platform 48 which can move transversely through the frame 36. . As used herein, the transverse direction refers to the direction of travel from one edge of the printing press 10 to the other edge, and the longitudinal direction refers to the direction from one end of the printing press 10 to the other end (that is, the unwinding station ( 12) and the rewind station 31]. The auxiliary frame 47 is located adjacent to the top line from the support panels 37 and 38. The auxiliary frame 47 passes through the supporting rods 41 and 42 by means of a first or upline linear bearing assembly 49 and a second or a downline linear bearing assembly 50. It is installed through the base platform 48 so as to slide-drive in the transverse direction. The base platform 48 has a transverse depth or length that is approximately twice the distance between the support rods 41, 42 of the frame 36. Each linear bearing assembly 49, 50 includes first and second linear ball bushings 51, 52 and a bearing shaft 53. Each shaft 53 is slidably arranged in a pair of separate bushings 51, 52. The bearing shaft 53 of the upper linear bearing assembly 49 is longitudinally fixed below its base platform 48 along its upper linear edge. The bearing shaft 53 of the underline linear bearing assembly 50 is longitudinally fixed below its base platform 48 along its underline edge. The ball bushings 51, 52 of the topline bearing assembly 49 are individually mounted in topline slots 54 formed in the first and second support rods 41, 42. The ball bushings 51, 52 of the underline bearing assembly 50 are similarly mounted in the slots 55 formed in the individual support rods 41, 42 of the underline from the underline bearing assembly 49, respectively. The single stop plate 58 is fixed to the operator side end of both bearing shafts 53. One of the two retaining plates 59 is fixed to the other side (gear row side) end of each bearing shaft 53 of the bare runk assembly 49, 50. The stop plate 58 and the two retaining plates 59 effectively limit the lateral movement of the bearing shaft 53 (ie the base platform 48) over the frame 36.

Printing station printing apparatus

Each print station 13 is a printing mechanism or print head 60 for applying at least one component image of the transferable image forming fluid to a spaced apart position along the length of the web 11 as the web 11 passes. Has In the exemplary flexographic printing press 10, the printing mechanism 60 is a printing roller equipped with a printing plate 62 for applying at least one component image to the web 11 according to each rotation of the roller 61. And (61). The measured amount of ink or other fluid is distributed to the printing plate 62 by an anilox roller 63. The anilox roller 63 has ink by some form of ink supply mechanism, such as a metering roller 64 which is immersed in the ink container 55 (shown in FIG. 3 only and shown in phantom in FIG. 5). Is supplied. Typical structures and functions of the ink container 65 and the rollers 61, 63, and 64 are already known to those skilled in the flexographic printing art, and thus detailed descriptions thereof are omitted herein. Other ink supply mechanisms (not shown), such as doctor blades and ink reservoir assemblies known in the art, may also be used. Such doctor blade assemblies are disclosed in US Pat. No. 4,590,855, which is incorporated herein by reference in its entirety.

Each print station 13 also includes an impression mechanism 66 having a backing face 67 for supporting the web 11 while the component image is applied by the printing mechanism 60. do. Preferably, the pressing mechanism 66 is a pressure roller whose outer surface is a supporting surface. The printing mechanism 60 is completely carried by the base platform 48 of the auxiliary frame 47. The end of the pressure roller 66 is journalically supported for rotation between the printing mechanism 60 and the vertical support panels 37 and 38 of the lower line. The ends of the other rollers 74 are journalized for rotation between the panels 37, 38 at a slightly lower line above the pressure rollers 66. During a normal printing operation, the web 11 passes through a nip between the printing roller 61 and the pressure roller 66, as shown in FIG. 1 (stations 13a, 13b). 66, 74) wound in an S-shape. In addition, in the case where printing on the opposite side of the web 11 is desired, the web 11 is arranged between the printing roller 61 and the pressure roller 66, as shown in FIG. 1 (station 13n). Is transported down and wound around roller 66, bypassing roller 74 completely.

Each print station 13 includes a gear train 68 driven by a drive shaft 69 common to each print station 13. The common drive shaft 69 also powers the die station 30 via a planetary output gear box (not shown) in a conventional manner. While in the operating position, the rear end of the base platform 48 is fixed past the gear train side of the print station 13, and the front end of the platform 48 is generally flush with the operator side of the station 13. Thus, while the platform 48 is in the operating position, the platform 48 does not disturb the operator moving along the operator side of the printer 10. As will be described later, the common drive shaft 69 drives the rotation of the impression roller 66, thereby driving not only the roller 74 but also the respective rollers 61, 63, and 64 of the printing mechanism 60. . Since it is driven in this way, the roller 74 can feed the web 11 through each station 13 set for general printing as described above.

Offline Inspection of Printing Equipment

The base platform 48 can be moved to the desired transverse position, including the operating position shown in FIGS. 3 and 4 and the deviated position shown in FIG. To achieve the transverse movement of the base platform 48, a double-acting air motor 70, such as Monee, III., Part No. 1731-DP, manufactured by Bimba Manufacturing Co., is used. The double acting air motor 70 includes a fixed cylinder 71 and an actuating rod 72. The cylinder 71 is laterally mounted between the supporting rods 41 and 42 and is positioned longitudinally between the two bearing assemblies 49 and 50. The rear end of the cylinder 71 is fixed to the second support rod 42, and the front or operating end of the cylinder 71 is fixed to the first support rod 41, so that the operating rod 72 is supported through the support rod 41. Through the formed hole 73, it is free to move in the lateral direction from the operator side of the printer 10. The tip of the actuating rod 72 is fixed to the stop plate 58. As such, it can be seen that the operation of the air motor 70 causes the base platform 48 to move laterally, thereby moving the printing mechanism 60 over the support rods 41 and 42. According to the base platform 48 in the operating position (see FIGS. 3 and 4), the printing mechanism 60 is positioned transversely between the supporting rods 41, 42. Depending on the base platform 48 in the out of position position (see FIG. 5), the printing mechanism 60 extends beyond the operator side of the frame 36 with a sufficient portion of the base platform 48 to be checked. Preferably, the printing mechanism 60 extends beyond the operator side of the frame 36. Such checks may include replacing or cleaning one or all of the elements of the printing mechanism 60. While in the out of position position, the base platform 48 may be positioned along the press 10 such that an individual support frame (not shown) or a cart (not shown) is received and supported under the base platform 48. There is no need for self-support. As will be clear from the figure, the printing mechanism 60 is completely carried on the base platform 48 when in the out of position position.

The out of position position is obtained by operating the air motor 70 to extend the actuation rod 72. The movement of the actuating rod 72 out of the cylinder 71 and the movement of the base platform 48 beyond the operator side of the frame 36 are preferably retained on the rear end of the bearing shaft 53. The plate 59 is stopped by limiting the withdrawal length of the actuation rod 72 such that only the plate 59 is positioned relative to each second ball bushing 52. The retaining plate 59 prevents the shaft 53 from being removed out of the ball bushing 52. From the out of position position, the base platform is moved to the operating position by reversing the operation of the air motor 70 to pull the operating rod 72 back into the cylinder 71. When the rear face of the stop plate 58 contacts the stop screw 77 installed extending beyond the front of the first support rod 41, the movement of the platform 48 from the deviated position is stopped and an operating position is obtained ( 2 and 3 and 17). As will be described later in the Axial Adjustment Mechanism section of this specification, the extent to which the stop screw 77 extends beyond the front of the support bar 41 may vary.

Positioning of the printing apparatus roller

As shown in Figs. 1 to 4, 6, 7, and 8, each print station 13 of the present printer 10 can be operated while the base platform 48 is in the operating position. And positioning mechanisms 78 for moving the respective rollers 61, 63, and 64 of the printing mechanism 60 in the longitudinal direction to a desired position with respect to each other and with respect to the pressure roller 66. As described in detail in the individual items below, the operation of the positioning mechanism 78 is controlled by a computer controlled positioning system to automatically move the printing mechanism rollers 61, 63 and 64 into and out of the printing position.

The positioning mechanism 78 is Elk Grove Village, III., Part No. Manufactured by THK America, Inc. First and second lower carriages 81, 82 which can be individually longitudinally slid along the lower plane rectilinear slide assemblies 83, 84, such as KR 3306B + 500LP. It includes. Each lower slide assembly 83, 84 is secured to the base platform 48, and non-driven or driven bearings fixed longitudinally spaced apart from the upper and lower lines, respectively, for the bottom of each of the lower carriages 81, 82. Block 85 and drive bearing block 86; Each bearing block 85, 86 is moved along the bearing or sliding surface 87 by a ball screw 88, the ball screw 88 of each lower slide assembly 83, 84 rotates at its end. Possibly mounted and disposed in a longitudinal borehole formed through each bearing block 85, 86 of each lower carriage 81, 82. The drive bearing block 86 includes a recirculating ball nut (not shown) in which the individual ball screws 88 are screwed. The bearing blocks 85, 86 of each lower carriage 81, 82 are moved longitudinally along the bearing surface 87 of each lower slide assembly 83, 84 by rotating the ball screw 88.

The first and second upper carriages 89, 90 can slide longitudinally along the first and second upper straight slide assemblies 91, 92, respectively. The upper slide assemblies 91 and 92 are secured to the top of the lower carriages 81 and 82 respectively. Each upper carriage 89, 90 also includes longitudinally spaced non-driven and drive bearing blocks 85, 86 as fixed to the bottom of the lower carriage 81, 82. The upper slide assemblies 91 and 92 are similar but shorter to the lower slide assemblies 83 and 84 and include a bearing or sliding surface 93 and a ball screw 94. The upper slide assemblies 91, 92 are THK part No. KR 3306B + 300LP. Lower slides 83, 84 are mounted laterally spaced to the base platform 48. The first lower slide 83 is mounted adjacent to the front edge of the base platform 48, and the second lower slide 84 is mounted at approximately an intermediate point along the length of the base platform 48. Preferably, the first carriages 81, 89 and the first slides 83, 91 are generally in the first vertical support panel 37 when the base platform 48 is in the operating position (see FIG. 4). Are arranged longitudinally on the same plane. The second carriages 82, 90 and the second slides 84, 92 are preferably generally coplanar with the second vertical support panel 38 when the base platform 48 is in the operating position. Are arranged.

Referring to FIG. 7, the printing roller 61 is journal-supported at its end between the first and second lower carriages 81, 82. The printing roller 61 preferably has a sintered sleeve bearing 95 (eg oil impregnated sintered bronze) mounted to rotate about its respective end. Upper and lower split bearing caps 97 and 98 are mounted with a pivot assembly 99 relative to the top of the lower line ends of each lower carriage 81 and 82. The pivot assembly 99 allows each pair of bearing caps 97 and 98 to rotate freely around the central vertical shaft 100. Each pivot assembly 99 includes a threaded bearing stud 105 and a capture bolt 106. One bearing stud 105 is screwed into a threaded hole formed in the upper portion of the lower end of each of the lower carriages 81 and 82. Each lower split bearing cap 98 is secured using one catch bolt 106 to a bearing stud 105 secured to each lower carriage 81, 82. The shank of each capture bolt 106 passes through a hole formed through the lower split bearing cap 98 and is screwed onto the top of each bearing stud 105. The upper end of each bearing stud 105 extends beyond each lower carriage 81, 82 such that a space is formed between each lower split bearing cap 98 and each lower carriage 81, 82. Satisfactory results can be obtained with a space of about 0.002 inches (0.0508 mm). Each capture bolt 106 is fixed in place relative to each bearing stud 105. Each pair of split bearing caps 97, 98 defines an opening 96 to receive and secure one bearing 95 in place. The upper and lower split bearing caps 97, 98 on each lower carriage 81, 82 are joined along the adjacent bottom line edge by hinge 101. The first actuated closure mechanism 102 is used to quickly secure or release the top line ends of the caps 97 and 98. The closure mechanism 102 includes an eye bolt 103 pivotally mounted at its eye end relative to the lower cap 98. The threaded end of the eye bolt 103 is disposed in a threaded bore hole formed in the handle 104.

Each end of the printing roller 61 is connected to each lower carriage 81, 82 by first placing each sleeve bearing 95 on the end of the roller 61 between one of the upper and lower caps 97, 98. Is supported journalically. Each opening 96 formed by the cap 97 has a smaller effective diameter than each sleeve bearing 95. In order to secure the bearing 95 in place between each of the caps 97 and 98, the eye bolt 103 is formed in the slot 103a at the top line end of the upper cap 97 as shown in FIG. ), Typically in a vertical direction. While in this position, rotating each handle 104 forces the upper cap 97 toward each lower cap 98 which in turn applies a compressive force to secure the bearing 95 in place. With the bearing 95 fixed in place, the end of the printing roller 61 rotates freely in each sleeve bearing 95. If the ends of the printing roller 61 are excessively operated radially (i.e., longitudinally in the frame) within each bearing 95, the handles are applied to apply an additional compressive force sufficient to deform the bearing 95. 104 can be further pivoted to reduce the amount of operation. It can be seen that reducing such radial actuation improves the repeatability of roller positioning by maintaining smaller tolerances between relative roller positions. Generally, the printing roller 61 can be removed by opening the closing mechanism 102 by reversing the advancing steps.

7, 8, 9 and 10, the ends of the anilox roller 63 and the metering roller 64 are journalized between the upper carriages 89, 90. A roller bearing 108 having an inner and outer race and a plurality of bearings (not shown) therebetween is mounted at one end of the anilox roller 63. A wedge shaped roller bearing assembly 111 is mounted to each end 110 of the metering roller 64. Each bearing assembly 111 comprises a roller bearing 112 similar to the bearing 108 captured in a wedge shaped block 113 with a snap ring 114. The first and second upper carriages 89, 90 comprise a set of upper and lower split dual bearing caps 117, 118, respectively. Each set of top and bottom caps 117, 118 is joined along an adjacent bottom line edge by hinge 119. The second manual closure mechanism 120 is used to quickly secure the caps 117 and 118 together. The closure mechanism 120 includes a threaded stud 121 having a non-threaded end secured to the handle 122. As shown in FIG. 7, when the upper cap is secured above the lower cap 118, the caps 117, 118 form a lower line opening 126 and an upper line opening 127 therebetween. The shank of the stud 121 is located in a hole 128 formed between the openings 126, 127 through the upper double bearing cap 117 and screwed into a threaded hole 129 formed in the lower double bearing cap 118. Combined. The through hole 128 is sized to allow the shank of the stud 121 to pass freely. Thus, by rotating the handle 122 to urge the stud 121 deeper into the threaded hole 129 and pressing the caps 117 and 118 together, the upper cap 117 is removed from the lower cap 118. Is fixed in position. The caps 117, 118 can be opened by rotating the handle 122 such that the stud 121 is pulled back from the threaded hole 129. Once the stud 121 is outside the hole 129, the upper cap 117 can pivot away from the lower cap 118 at the hinge 119 to the open position. While in this open state, the bearing 108 on the end 109 of the anilox roller 63 and the wedge-shaped bearing assembly 111 on the end of the metering roller 64 are between the caps 117, 118. It may be located at or removed from.

When the anilox and metering rollers 63, 64 are mounted between the upper carriages 89, 90, the bearing 108 on the end of the anilox roller 63 is captured in the lower line opening 126 and weighed The bearing assembly 111 in the form of a wedge on the end of the roller 64 is captured in the upper line opening 127. While the bearing 108 is properly secured in place at the bottom line opening 126, the wedge-shaped bearing assembly 111 can slide longitudinally by the desired distance within each top line opening 127. Each of the upper line openings 127 has upper and lower bearing surfaces 130 and 131, a vertical upper line end surface 132, and a vertical lower line end surface 133. Top line end face 132 is a flat bearing surface formed by the vertical top line end of bottom cap 118. Bottom line end surface 133 is formed by a portion of two double bearing caps 117, 118. The wedge shaped block 113 of each bearing assembly 111 has upper and lower bearing surfaces 138, 139, a bottom line end face 142 and a top line end face 143. The wedge shaped block 113 is sized to fit within each topline opening 127, where the block 113 is sized to continue to slide in the longitudinal direction. Each of the wedge shaped blocks 113 has an inner flange 146 (see FIG. 8) which prevents lateral movement of the metering roller 64 when the bearing assembly 111 is mounted to the upper carriages 89, 90. Have The upper line end face 143 of the block 113 is inclined in a vertical state and has a similarly inclined ridge 144 (see FIG. 9) with a bearing surface 145 formed thereon. Satisfactory results are obtained with a surface 143 angle of about 15 °.

The double acting air motor assembly 151 is used to longitudinally move each of the wedge-shaped bearing assemblies 111 within each topline opening 127. Each air motor assembly 151 has an air cylinder 152, a piston 153 and an actuating shaft such as those manufactured by Beambar Manufacturing Corporation (Bimba Manufacturing Co., Monee, Illinois, model No. Fo-17-2). 154. One air motor 151 is mounted on the upper double bearing cap 117 of each upper carriage 89, 90 such that the shaft 154 is operated vertically up and down generally under the cylinder 152. The shaft 154 is disposed in a hole 158 formed into the upper line opening 127 through the top of the bearing cap 117. The hole 158 is sized to allow the shaft 154 to move freely. The tip of shaft 154 extends into top line opening 127 and mounts a camming bearing assembly 159. The bearing assembly 159 is a two-prong yoke 160, a small diameter roller bearing 161 (McGil Manufacturing Co. Inc, Valparaiso, Indiana, such as manufactured by McGill Manufacturing Corporation). , part No. CYR-3 / 4-S) and two equally sized roller bearings 162 (such as those manufactured by McGill, Inc., larger than the bearing 161 (McGil, part No. CYR-7 / 8-) S)]. With the smaller bearing 161 positioned between the two large diameter bearings 162, the nut 163 and the bolt 164 or similar fastening member are placed between the roller bearings 161 between both sides of the yoke 160. 162). Each bearing 161, 162 is free to rotate around the shank of the bolt 164. The yoke 160 is mounted to the tip of the actuating shaft 154 of the air motor 151 so that the longitudinal axis of the bolt 164 lies laterally. The upper line end face 143 of the bearings 161, 162 and the wedge shaped block 113 has only a smaller bearing 161 in contact with the bearing surface 145 of the surface 143, and a larger bearing 162. Is sized to contact only the flat vertical bearing surface 132 of the lower double bearing cap 118. The compression coil spring 168 is mounted between the bottom line end face 133 portion of the opening 127 formed by the lower bearing cap 118 and the bottom line end face 142 of the wedge shaped block 113. This spring 168 provides a lifting force that pushes the block 113 to the top line end face 132 of the opening 127, thereby the vertical position of the cam bearings 161, 162 at the top line opening 127. Regardless, it maintains contact between the bearings 161, 162 and each of the bearing surfaces 145, 132. Because of this bearing arrangement, frictional forces are minimized to allow a more direct relationship between the force applied to the wedge shaped block 113 through the bearing assembly 159 and the air pressure applied to the air cylinder 152. Satisfactory results can be obtained with an air pressure of about 30 psi.

The movement of each wedge shaped block 113 and the movement of the end of the metering roller 64 thereby actuate each air motor 151 in the longitudinal direction within the top line opening 127 and diverge bearing surface 132. 145, by operating the shaft in the vertical direction. When the roller bearings 161 and 162 are exerted downward by the operation of the air cylinder shaft 154, the wedge-shaped bearing assembly 111 is exerted in the longitudinal direction in the downward direction to apply the spring 168. Compress and move the metering roller 64 towards or towards the anilox roller 63. In the anilox and metering rollers 63 and 64 added in this way, a significant amount, but not all, of the radial actuation in each of the roller bearings 108 and 112 is eliminated. Reducing this radial operation improves roller positioning repeatability by maintaining smaller tolerances between roller positions. When the action of the air cylinder 152 is reversed, the roller bearings 161 and 162 are moved upwards, so that the natural elasticity of the coil spring 168 and the metering roller 64 pushes the upper line of the wedge-shaped block 113. The measuring roller 64 is moved from the anilox roller 63 by this.

Movement of the respective upper carriages 89, 90 along each slide assembly 91, 92 is made by the upper gear box assembly 170. Each gear box assembly 170 includes a DC stepper motor 171 including an encoder 172 coupled to generate an electronic pulse when the stepper motor 171 is actuated. This stepper motor 171 / encoder 172 combination is manufactured by Superior Electric (Superior Electric, Bristal, Connecticut, part No. M062-LF-509C2006). As shown in FIG. 7, a roller positioning stepper motor 171 is installed on a gear box housing 173 mounted on a guide actuator bracket on the top line ends of the upper slide assemblies 91, 92. respectively fixed to the box housing. Each stepper motor 171 is a two-piece collar 180 (two; such as manufactured by IOM Industries, Inc., IMO Industries Inc., Boston Gear Division, Quincy, MA, catalog No. 2SC 37). and a shaft 178 having a spur gear 179 fixed to the end with a piece collar. Each driven gear 179 meshes with another spur gear 181 fixed to an end of an actuating shaft 182 that is rotationally mounted in the gear box housing 173 by a double bearing 183. The other end of each actuating shaft 182 is a flexible coupling such as manufactured by W. Amber Inc. (WM Berg Inc., East Rockaway, NY, part No. CO41A-1 "Modified Bore" size). (187; flexible Coupling) is connected to the adjacent upper line end of one ball screw 94. The top line end of each ball screw 94 is rotatably mounted in a hole 188 formed through the bottom line end of each guide actuator bracket 174.

Operation of each stepper motor 171 causes rotation of each drive gear 179 which alternately drives rotation of each actuating shaft 182 through each gear 181. Rotation of each shaft 182 drives rotation of each ball screw 94 through coupling 187. Each coupling 187 is preferably bent in the axial direction rather than in the direction of rotation when each shaft 182 and ball screw 94 are misaligned (ie, no longer in a coaxial axis). By rotating each ball screw 94 through a recirculating ball nut of individually driven bearing block 86, the longitudinal direction of the upper carriages 89, 90 along each of the upper slide assemblies 91, 92 as described above. Slide drive is caused.

Movement of each lower carriage 81, 82 along each lower slide 83, 84 is made by a lower gear box assembly 190 having a stepper motor 191 and an encoder 192. The gear box assembly 190 is almost identical to the gear box assembly 170 except that the drive shaft 178 is directed below the actuating shaft 182. In addition, each gear box assembly 190 is associated with each lower slide assembly together with the guide actuating bracket 184 in the same way that the gear box assembly 170 described above is connected to each upper slide assembly 91, 92. 83, 84). Similarly, by rotation of each ball screw 88 by each gear box assembly 190, the lower carriages 81, 82 of the lower carriages 81, 82 along each lower slide assembly 83, 84 in a manner as described above. Longitudinal slide drive is caused. The carriage (using Superior Electric's stepper motors / encoders (171/172 and 191/192) described above and their respective THK slide assemblies 91, 92, 83, 84) 89, 90 and 81, 82 can be moved in increments as small as about 0.005 mm (0.0002 inch).

Accordingly, the printing roller 61 operates one or two of the stepper motors 191 of the gear box assembly 190 to rotate one or two of the ball screws 88 to support the surface 67 of the pressure roller 66. Can be moved to the desired spatial location for. Similarly, the anilox roller 63 may operate on one or two of the stepper motors 171 of the gear box assembly 170 to rotate one or two of the ball screws 94 to the desired print roller 61. Can be moved to a spatial location. Encoder 172, 192 associated with each stepper motor 171, 191 provides feedback to a computer controlled positioning system described later. This feedback allows the computer control system to know whether a particular stepper motor 171 or 191 is actually operated in the desired amount. The metering roller 64 actuates or stops one or two of the double-acting air motor assembly 151 (ie, pressurizes or depressurizes) the anilox roller by moving one or two of the cam bearing assemblies 159 up and down respectively. Can be moved to a desired position with respect to 63. The air pressure supplied to each air cylinder 152 may vary depending on how much pressure is applied by the metering roller 64 against the anilox roller 63.

The positioning mechanism 78 has the rotational axis of the printing, anilox and metering rollers 61, 63 and 64 the same as the rotational side of the pressure roller 66 when the various rollers 61, 63 and 64 are moved relative to the hour. It is designed to be on a plane. Keeping the printing mechanism rollers 61, 63, and 64 on the same plane makes programming of the computer controlled positioning system easier.

Print station gear train

3, 10 to 12, 14 and 14A to 14C, the gear train 68 of each print station is defined by the anilox roller and the metering rollers 63 and 64. A first branch 193 for driving rotation and a second branch 194 for driving rotation of the printing roller 61 alone. The two branches 193, 194 of the gear train 68 are driven by a helical gear 196 mounted at the rear end of the pressure roller 66 behind the second support panel 38. The roller 74 also has a gear 199 driven by the pressure roller gear 196. The pressure roller gear 196 is driven in engagement with the helical drive gear 197 which is alternately driven by the common drive shaft 69 via the print station gear box 198. The first branch 193 is an articulating gear assembly 195 capable of keeping the anilox and metering rollers 63, 64 in the same plane as the printing roller 61 and the pressure roller 66. 14 and 14A to 14C). The gear assembly 195 also allows the rollers 63 and 64 to be driven continuously regardless of the longitudinal position relative to the rollers 61 and 66.

The linked gear assembly 195 includes a first air actuated clutch assembly 200 mounted on the first fixed drive shaft 201. The first drive shaft 201 is journalically supported at one end between the rear panel 203 and the front panel 204. The panels 203, 204 are laterally spaced apart and mounted vertically above the base platform 48 behind the second carriages 82, 90. The first clutch gear assembly 200 is manufactured by Hutton Manufacturing Corporation Inc. with a slidable housing 206 filled in the shaft 201 by a key 207 (Horton). Manufacturing Co. Inc., Minneapolis, MN, part No. 5H30P) includes a claw clutch 205 and a hub 208 fixed to the shaft 201. The key 207 prevents the rotation of the housing 206 around the shaft 201, but the housing 206 can continue to slide along the shaft 201. During printing, the clutch assembly 200 is actuated to apply air pressure to the clutch 200, forcing the housing 206 and the teeth 209 on the hub 208. The spring return is used to detach the teeth 209 when the clutch assembly 200 is stopped and air pressure is shut off from the clutch 200. The helical ring gear 210 with teeth inclined on the front edge is concentrically fastened to the hub 208. The ring gear 210 is driven in engagement with the pressure roller gear 196. The ring gear 210 has teeth that are inclined on the rear edge. A first fixed helical gear 211 for driving the balance of the assembly 195 is fixed to the first drive shaft 201 between the clutch gear assembly 200 and the front panel 204. When the base platform 48 is moved to the operating position, the printing press 10 is stopped. Since the pressure roller gear 196 and the ring gear 210 of the first clutch assembly 200 are helical gears with teeth that are inclined on the engaged side, the base platform 48 is exemplified by the air cylinder 70. For example, the clutch gear 210 is more easily engaged with the pressure roller gear 196 when moved from the out of position shown in FIG. 5 to the operating position (see FIGS. 3 and 4).

The linked gear assembly 195 also includes a second air actuated clutch assembly 215 mounted to a second fixed drive shaft 216, one end of which is journalically supported between the panels 203, 204. The second drive shaft 216 is mounted to the top line below the first drive shaft 201. The second clutch assembly 215 is similar to the clutch assembly 200 having a housing 217 that can be slid, a fixed hub 218 and mating teeth 219. The clutch assembly 215 is filled in the shaft 216 with a second key 220. The clutch assembly 215 operates in a manner as described above with respect to the assembly 200. A first timing pulley 222 is fastened to the hub 208 and second timing by the timing belt 224. Is connected to the pulley 223. The second pulley 223 is rotatable by a motor 225 mounted to the base platform 48. The second fixed helical gear 229 is mounted to the second shaft 216 and engages the first helical gear 211 between the second clutch assembly 215 and the front panel 204.

The intermediate pivot plate 230 is mounted at one end to rotate about the second drive shaft 216. One end of the movable first drive shaft 232 is journalically supported at the other end of the intermediate pivot plate 230. The movable first helical gear 234 is engaged with the drive shaft 232 and engages with the second fixed helical gear 229. Front and rear tip pivot plates 238 and 239 are mounted with one end with a helical gear 234 therebetween so as to rotate around drive shaft 232. The rear pivot plate 239 is journalically supported in the middle of the movable second drive shaft 232. Plate 238 is journalized on the free end of shaft 232. The movable second helical gear 244 is engaged with the first helical gear 234 which is fixed to the drive shaft 242 and is movable between the pivot plates 238 and 239. The other end of the second drive shaft 242 is mounted to rotate in a bearing cup assembly 248 extending beyond the front of the pivot plate 238 and mounted to the other end of the pivot plate 238. The bearing cup assembly 248 includes a bearing cup 249 having a shoulder 250 fitted for rotation in a hole 251 formed through the other end of the pivot plate 238. Assembly 248 also has a pair of spaced bearings 252, 253 mounted inside the assembly about shaft 242. The integral key 257 extends outwardly concentrically from the front end of the second drive shaft 242 to engage the engagement slot 258 concentrically formed at the rear end 109 of the anilox roller 63. .

With the key 257 coupled to the slot 258, the bearing cup assembly 248 passes through a hole 260 formed through, for example, the lower bearing cap 118 of the second upper carriage 90. A bolt 259 is fastened to the rear side of the second upper carriage 90 and screwed into the threaded bore hole 261 formed in the bearing cap 249. The helical gear 265 is mounted to the front end of the anilox roller 63 to engage another helical gear 266 mounted to the front end of the metering roller 64. Gears 265 and 266 are located in front of the first upper carriage 89. Gears 265 and 266 may each have a variety of relative gear ratios, such as 1: 3 gear ratios. The gear ratio of the anilox roller to the metering roller can be varied according to the change in the diameter of the metering roller 64 (generally, the diameter of the anilox roller 63 remains the same). This gear ratio may also vary to change the ink supply and dispensing characteristics of the metering rollers and anilox rollers 64, 63.

During printing, when the anilox roller 63 is driven by the common drive shaft 69 through the linked gear assembly 195, the base platform 48 is in the operating position and the first clutch assembly 200 is Actuated by the interlocking teeth 209, the second clutch assembly 215 is stopped by the separate teeth 219 (see FIG. 14). With teeth 209 of clutch assembly 200 engaged, rotation of ring gear 210 by pressure roller gear 196 causes rotation of drive shaft 201, and in turn helical gear 211,. Causing rotation of 229, 234, and 244). In the state where the teeth 219 of the clutch assembly 215 are not engaged, the rotation of the second fixed gear 229 does not cause the rotation of the first pulley 222 mounted to the hub 218 so that the motor 225 It remains inoperable. The rotation of the helical gear 244 causes the drive shaft 242 to rotate, and when the key 257 and the slot 258 are engaged, the anilox roller 63 also rotates. When the metering roller 64 is positioned by the air cylinder assembly 151 to engage the helical gears 265 and 266, the metering roller 64 rotates by the rotation of the anilox roller 63.

The structure of the linked gear assembly 195 described above is metered with the anilox roller 63 regardless of its relative position to the printing roller 61 or the pressure roller 66 when the respective gears 265 and 266 are engaged. The roller 64 can be rotated. That is, the linked gear assembly 195 can move longitudinally along the second carriages 82, 90 while maintaining a continuous engagement between the drive gears 211, 229, 234, and 244. As evident from FIGS. 14A-14C, the linkage gear assembly 195 maintains the anilox and metering rollers 63, 64 while maintaining the coplanar relationship between all the rollers 61, 63, 64, and 66. Can be moved and driven.

When a particular print station 13 is stopped for inspection, such as replacement of the print roller 61, it is desirable that the anilox and metering rollers 63, 64 are often kept in rotation to prevent the ink from drying out. . The clutch assembly 200 215 does not depend on the pressure roller gear 196 (ie, common drive shaft 69) when the respective gears 265, 266 are engaged, and the anilox roller 63 and the metering roller 64 ) Can be rotated. Independent rotation of the ink supply rollers 63, 64 stops the printer 10, stops the first clutch assembly 205 so that the teeth 209 are disengaged, and the second clutch so that the teeth 219 engage. This can be accomplished by operating the assembly 215. With the first clutch 205 detached and the second clutch 215 engaged, the printer 10 rotates the anilox roller 63 rather than the common drive shaft 69 (via the pressure roller gear l96). It can be returned to the operation state without making a change. With the base platform 48 in the operating position, the pressure roller gear 196 will continue to drive rotation of the ring gear 210. However, since the teeth 209 of the first clutch 205 are separated, the rotation of the ring gear 210 does not affect the balance of the first gear branch 193. With the first clutch 205 detached and the second clutch 215 engaged, the motor 225 does not depend on the balance of the common drive shaft 69, ie, the printer 10, but without the anilox and metering roller 63. , 64) can be used to drive the rotation.

11, 13, and 15, the second branch 194 of each print station gear train 68 engages and drives the spur gear 269 mounted on the print roller 61. Swing gear assembly 268 that is movable to an internal and external position. Because it is movable to the fully engaged position, the swing gear assembly 268 allows the printing roller gear 269 to fully engage the second branch 194 of the gear train 68 regardless of the thickness of the web 11. Can be. The complete and maintained engagement of the gears with respect to the common drive shaft 69 in the printing roller gear 269 via the second gear train branch 194 may result in a backlash and consequent deterioration in print quality (e.g. barring (barring)]. To this end, the gears in gear train 68 are preferably machined to meet or exceed grade 10 of the American Gear Manufacturer Association (AGMA) gear standard. To meet class 10, the interlocking gears are allowed to backlash up to about 0.0005 inches.

The oscillating gear assembly 268 is spaced forward and rear mounted below the pressing roller 66 to rotate about a first drive shaft 273 whose one end is journalically supported between the vertical support panels 37 and 38. Housing 270 having side plates 271 and 272. The rear end of the shaft 273 extends behind the second support panel 38 and is driven by the pressure roller gear 196 via a dual harmonic gear assembly 275, which will be described in detail below. The first spur gear 278 is fixed to the shaft 273 by the key 279 between the plates 271, 272. One end of the second drive shaft 280 is journalically supported at each plate 271, 272 at the other end or tip of the housing 270. The second spur gear 282 is fixed to the shaft 280 by the key 283 between the plates 271 and 272. The second gear 282 is driven in engagement with the first gear 278. The other end of the second shaft 280 extends beyond the side plate 271 and mounts an integral bearer ring 287. The tip spur gear 288 is fixed along the side of the transfer ring 287. The arcuate spur gear rack 290 is fastened to one end of the housing 270. Rotation of the oscillating gear assembly 268 around the shaft 273 is effected by the gear rack 290 and other spur gears 291 that are engaged by and rotated by the housing 270. The length of the arc in which the housing 270 can be rotated is defined by limiting the stroke of the actuator 292. The third spur gear 291 is a double-acting air such as manufactured by Beambar MenuFacing Corp. through the third drive shaft 293 (Bimba Manufacturing co., Monee, Illinois, Series 247PT-247-270-A1). It is driven by a motorized rotary actuator 292. The third gear 291 is filled with a key in the third shaft 293. The front end of the shaft 293 extends beyond the support panel 37 and is manufactured by IMO Industries, Inc. (IMO Industries, Inc., Boston Gear Div., Quincy, MA, catalog No. 1). It is connected to the rotatable shaft 294 of the actuator 292 by an SCC7 / 8 × 7/8 coupling 295. The rotary actuator 292 may rotate the third drive gear 291 in one direction.

Accordingly, the tip gear 288 can be swung to and from the engaging portion with the printing roller gear 269 by operating the actuator 292 and rotating the gear 291 in one direction. As a result, the housing 270 is rotated around the shaft 273 in a direction opposite to the rotation of the gear 291. Full engagement of the leading gear 288 and the printing roller gear 269 will cause the transfer ring 287 to contact the other transfer ring 297 mounted axially apart from the gear 269 on the printing roller 61. When it is done. As described in more detail below, the printing roller gear 269 and the transfer ring 297 are obviously narrower in width than the corresponding gear 288 and the transfer ring 287 in the swinging gear assembly 268, such that the printing roller 61 can be adjusted laterally to maintain axial registration without being separated. With the gears 288 and 269 fully engaged, the printing roller 61 passes through the second branch 194 of each of the pressure roller gears 196 and the gear train 68 as described above to the common drive shaft. 69 can be driven. The balance of the gear train branch 194 between the pressure roller gear 196 and the printing roller gear 269 is designed to maintain a 1: 1 gear ratio between the gears 196, 269.

Circumferential adjustment mechanism

The double roughening gear assembly 275 is a circumferential adjustment mechanism that adjusts the rotational speed of the printing roller 61 regardless of the speed of the web 11 when operated through the printing press 10. As will be described in detail below, each print station 13 has its own computer controlled circumferential matching system that controls the operation of the dual harmonic gear assembly 275. Assembly 275 includes a housing 299 mounted to rotate about a rear end of drive shaft 273 by bearing 300. The housing 299 has a helical gear 301 which is driven in engagement with the pressure roller gear 196 and integrally formed outside. Assembly 275 also includes a pair of linkage drive gears 302, 303 positioned coaxially in parallel, similar to the linkage drive drive gear disclosed in US Pat. No. 4,363,270, which is incorporated herein by reference. Each gear 302, 303 has a first stiffness positioned to engage a central elliptical waveform generator 304, 305, a flexible male threaded spline 306, 307, and a corresponding flexible spline 306, 307. Female threaded outboard splines 308 and 309. The second rigid female threaded inboard spline 310 is provided as a bridge to engage between each gear 302, 303 and is disposed such that the internal teeth engage with the flexible splines 306, 307 simultaneously. Outboard spline 308 is secured to flange 311 so that all elements rotate together around shaft 273. The flange 311 is fixed in place with respect to the inner race of the bearing 300 by a bearing nut 312 screwed to the rear end of the shaft 273. The other outboard spline 309 is secured to an end plate 313 secured to the rear end of the housing 299.

Waveform generator 305 is rigidly filled with a fixed annular or tubular sleeve 317. Sleeve 317 is mounted with bearing 318 in a hole formed through end plate 313. The rear end of the sleeve 317 is fixed to the frame 36 and prevented from being rotated by means not shown. The bearing 318 can rotate the housing 299 around the fixed sleeve 317. A stepped trim shaft 319 extends through the sleeve 317 and is rotatable. Waveform generator 304 is firmly keyed to trim shaft 319. The innermost end of the shaft 319 is rotatably supported by a roller bearing 320 mounted concentrically within the rear end of the shaft 273. The outermost end of the shaft 319 mounts a first pulley 321 connected to the second pulley 322 by a belt 323. The DC stepper motor 327 is mounted to the frame 36 and mounts a second pulley 322 on its drive shaft. The stepper motor 327 is basically the same as the stepper motor 171 except that there is no encoder 172.

The dual coordinating gear assembly 275 functions as a power transmission device in a generally 1: 1 ratio when the shaft 319 is held stationary (ie, when the motor 327 is not operated). When it is desired to change the circumferential position or phase between the rotation of the anilox roller, the metering roller and the pressure rollers 63, 64 and 66 and the printing roller 61, the stepper motor 327 moves the shaft 319 in the desired direction. Is rotated. The shaft 273 is rotated by the rotation of the shaft 319, so that the printing roller 61 is rotated quickly or slowly in accordance with the rotation direction of the shaft 319. This operation is described in detail in US Pat. No. 4,363,270. In this way a circumferential registration change can be made.

Axial adjustment mechanism

Referring to FIG. 17, each print station 13 preferably has an axis for simultaneously adjusting the transverse position of the printing tool rollers 61, 63 and 64 within the frame 36 to correct for axial registration errors. It includes a direction adjustment mechanism. The instrument 330 includes a mounting bracket 331 fixed to the rear side of the horizontal support rod 41. The shaft 332 is rotatably mounted to the bracket 331 at two longitudinal points by two spaced bearings 333 and 334. The wide spur gear 338 is a part fixed to or integrally formed with the shaft 332 in the middle of the bearings 333 and 334. The rear end of the shaft 332 extends beyond the bare rungs 334 and W.M. Drive shaft of DC stepper motor 340 by coupling 339, such as manufactured by Berg Incorporated (WM Berg Inc., East Rockaway, NY, Part No. Co41A-3 "Modified Bore" size). Is connected to. The stepper motor 340 is basically the same as the stepper motor 327. The narrow spur gear 342 is fixed to the rear end of the stop screw 77, such as a set screw. The narrow gear surface of the gear 342 is driven in mesh with the gear 338. The set screw 77 is screwed into a threaded sleeve or nut 343 that is secured to and extends through the hole 343a formed through the horizontal support rod 41. The front end of the stop screw 77 extends beyond the front of the support bar 41 to stop the transverse movement of the platform 48 from the out of position position. When the front end of the melee screw 77 contacts the stop plate 58, the platform 48 is located at or near the operating position. The contact between the stop plate 58 and the stop screw 77 is maintained by operating the double acting air cylinder 70 to continue pulling the rod 72 into the cylinder 71.

By fine adjustment of the transverse position of the platform 48, the axial position of the printing roller 61 (also anilox roller and metering rollers 63, 64) rotates the shaft 332 by an increased amount. It can be made by operating the stepper motor 340 so that. The rotation of the shaft 332 causes the gear 342 to rotate the threaded set screw 77 in and out of the sleeve 343 in the rotational direction. When the stop screw 77 is screwed out of the sleeve 343, the stop plate 58 and thus the platform 48 are driven by the continued pressure exerted by the air motor 70. Follow the move. When the stop screw 77 is inserted into the sleeve 343, the pressure exerted by the air motor 70 to pull the rod 72 into the cylinder 71 prevents the transverse outward movement of the stop plate 58. You must overcome it. The gear 342 has a gear face that is much narrower than the gear 338 so that when the stop screw 77 moves within the sleeve 343, it remains engaged. This is also because the transfer ring 297 and gear 269 of the printing roller 61 are narrower than the transfer ring 287 and engagement gear 288 of the swinging gear assembly 268. Thus, the axial registration error of the printing plate 62 relative to the component image preprinted on the web 11 may cause the stepper motor 340 to move the platform 48 and thus the printing roller 61 in the manner just described. Can be corrected by operating

Many advantages of the printer 10 incorporating the principles of the present invention include increased structure (e.g., frame 36) to improve overall stiffness, i.e. resistance to deflection, and tightly controlled printing elements (e.g., For example, it can be realized better by constructing a printer 10 having tolerances and tolerances of the meshed gears and roller bearings 108 and 112]. By increasing the overall structure of the printing press 10, maintaining tighter tolerances and limiting the tolerance wherever practical, the printing press 10 operates with less vibration and noise. Reducing vibration and noise can help you achieve faster print speeds. The flexographic printing press 10 of this embodiment can reach print speeds up to about 3 to 4 times faster than conventional flexographic printing presses manufactured by the assignee of the present invention while continuing to maintain satisfactory print quality. .

Computer control system

Referring to Fig. 23, a preferred embodiment of the automatic printing machine of the present invention is described in particular in the figure showing a computer control system. The computer control system has a master computer 400 that includes a keyboard 401 for data entry, a display 402, a removable or fixed disk storage medium 403, and a central processor 404. Preferably, display 402 and keyboard 401 are combined into a touch screen display / input device.

The master computer 400 provides the operator with an interface with all the standard control features for the printer 10. In addition, the master computer 400 monitors and controls a number of individual station control computers 405a through 405n at each of the stations 13a through 13n, each of which is generally referred to as an individual or station computer 405.

At each station 13 the computer 405 is determined by relative roller positioning, preliminary pre-matching of the printing roller 61 with respect to all other stations 13, preferably printed by the first station 13a of the station 13. Automatic circumference (ie, longitudinal or lineal) registration of the printing roller 61 relative to the longitudinal reference point on the web 11, and preferably also printed by the first station 13a of the station 13. Control the automatic axial (ie transverse) registration of the printing roller 61 with respect to the transverse reference point on the web 11.

In the automation or computer controlled functions executed by the station computer 405, the data is obtained from corrections and measurements made under the control of the computer 405. This data is temporarily stored by the computer 405 and transmitted up and down or periodically read by the master computer 400 for analysis, system maintenance and system setup and design.

The computer control system achieves the object of the present invention by providing roller positioning properties that fully automate the relative positioning of the rollers 61, 63, 64 and 66 with respect to each other at each station 13. The computer control system also provides registration characteristics for setting and maintaining the printing roller position of the other station 13 relative to the web 11. The registration characteristics also include preliminary registration (initial total registration of the rollers of the other stations 13 with respect to each other), circumferential or linear registration (optimal longitudinal registration of the printing roller 61 with respect to the image printed on the web 11). Automatic retention of the < RTI ID = 0.0 > and < / RTI >

In addition, the characteristics of the computer control system are provided in combination as described herein to maintain and quickly remember the proper relationship between the rollers within each station 13 to thereby enhance the advantages of each of the other computer control characteristics, thereby Advantages of other computer control features can be realized more fully. This property is also combined with the mechanical properties described above. For example, the mechanical offline check feature functions in combination with the positioning feature as well as the axial match feature to preserve the positioning and registration settings when the offline check is performed. Also with computer controlled positioning, certain adjustments are made in progress without disturbing the automatically maintained circumferential registration.

The master or host computer 400 can provide control of all input and output functions that can be operated, watched and executed on an individual computer 405 from a central location. The setting variable can be made from the host computer 400 by sending the entire command to every computer 405 of the station 13 or optionally by sending the command to an individual computer in the computer 405. The operator from the host computer 400 can observe and compare the progress data related to the match at each station 13 and compensate for the adjustment taking into account the performance analysis of all stations 13. The analysis can be performed by software or an operator at the host computer 400.

The individual computer 405 at each station 13 is preferably divided into two physically distinct processing units, including a positioning controller 406 and a matching controller 407, with reference to FIG. Each of the controllers 406, 407 are interconnected or preferably both connected to the master computer 400 to communicate bi-directionally, the master computer being between the controllers 406, 407 of each station 13 or other stations 13. Control communication between the controllers 406,407. The positioning controller 406 includes a processor 408 configured as a microprocessor, an interface and a driver for controlling or watching hardware, and related devices and circuits. Similarly, match controller 407 includes a similarly equipped processor 409. Each controller 406, 407 also has 16 button capacity 4 × 4 array input panels 410, 411, a 2-line LED display 412, 413, and an incremental dial 414, 415. It includes. If the command includes numerical settings (such as setting web thickness or repeat length), displays 412 and 413 display the current numerical value to the operator. If the numerical value changes, the increase in the displayed value is a clockwise click of the dial, and the decrease in the displayed value is a counterclockwise click of the dial 414, and the dials 414, 415 are rotated.

At each station 13, the positioning control processor 408 of the positioning controller 406 controls the operation of the stepper motors 171, 191 and the air cylinder 151 and reads the encoders 172, 192. It may also include other outputs and inputs, such as, for example, limit switch inputs to confirm the position of the air cylinder 151. In the figure of FIG. 23, the air cylinder 151 includes an operator side air cylinder 151a and a gear side air cylinder 151b, and the stepper motors 171 and 191 also have an operator side motor 171a and 191a and a gear, respectively. Side motors 171b and 191b. Similarly, encoders 172 and 192 include operator side encoders 172a and 192a and gear side encoders 172b and 192b, respectively.

Processor 408 preferably has at least five outputs. One output 418 is preferably connected to the control line inputs of the metering roller air cylinders 151a and 151b to simultaneously operate the cylinders, and the four outputs 419 are stepper motors 171a, 171b, 191a and 191b respectively. Is connected to. Sensor outputs from respective encoders 172a, 172b, 192a, and 192b respectively corresponding to stepper motors 171a, 171b, 191a, and 191b are connected to an input 420 of the positioning controller processor 408.

The match processor 409 of the match controller 407 at each station 13 preferably has at least six inputs and at least two outputs. It includes a web longitudinal motion input 421 that receives a pulse from the encoder 344 on the axis of the pressure roller 66. These pulses each represent a fixed increase in the angular rotation of the pressure roller 66 and are proportional to the fixed increase in the length of the web 11 moving through the station 13. The other input 422 is connected to the output of the optical sensor 347 and reads the pulse corresponding to the angular position of the printing roller 61 that aligns the mark 349 on the printing roller 61 with the sensor 347. . A similar input 423 is connected to the output of the optical sensor 350 and one adjacent sensor 350 of the plurality of marks 350a on the web 11 printed at the first station 13a with the first image. The pulse corresponding to the presence is read out and positioned on the web 11 relative to the image printed at the first station. Output 424 is coupled to stepper motor 327 which directs harmonic drive 275 to communicate control pulses.

Control pulses are sent from the processor 409 to the stepper motor 340 on the output line 426 for axial matching.

The structure, logic and operation of the computer control system are more fully described in connection with the individual functions of the computer control features described later.

Determine computer controlled location

In the base platform 48 in the operating position, the computer controlled positioning system sets the relative position by moving the printing press rollers 61, 63 and 64 relative to each other and with respect to the pressure roller 66 of the station 13. To control. The printing mechanism rollers 61, 63 and 64 are movable between the printing position and at least one, preferably a plurality of non-printing positions. In the printing position the rollers 61, 63 and 64 are in place to apply to the web 11 at least one component image of the transferable image forming fluid at each rotation of the printing roller 61. In the non-printed position, the rollers 61, 63 and 64 of the printing mechanism 60 are positioned in place so as not to apply the component image to the web 11.

When the roller of the printing mechanism 60 is in the printing position, the metering roller 64 is in intimate contact with the anilox roller 63 to properly supply the transferable image forming fluid or ink to the roller 63. In addition, when the ink can be dispensed in sufficient quantity from the anilox roller 63 to the printing plate 62 at every rotation of the printing roller 61, the anilox roller 63 is placed at the fluid dispensing position with respect to the printing roller 61. Is located in. In addition, if at least one satisfactory quality component image can be applied to the web 11 by the printing plate 62 at every rotation of the printing roller 61, the printing roller 61 is formed of the pressing roller 66. It is located at an image application position relative to the support surface 67 (ie web 11). When the printing mechanism 60 is in the printing position, the anilox and the metering roller gears 265 and 266 are engaged, and the transfer ring 287 and the tip gear 288 of the swing gear assembly 268 are also engaged to print, respectively. It comes into contact with the roller gear 269 and the transfer ring 297 (see FIGS. 6, 11 and 15).

One non-printing position of the printing mechanism 60 is the starting position. In this position, the anilox and metering rollers 63, 64 move out of the fluid dispensing position to the blocking position. In the closed position, the stepper motors 171a, 171b of the gear box assembly 170 (see FIG. 7) are operated to move the upper carriages 89, 90 to the upper line. The upper carriages 89, 90 are moved slightly behind the anilox roller 63 far enough from the printing roller 61 so that ink is no longer dispensed on the printing plate 62. In addition, the stepper motors 191a and 191b are operated to move the lower carriages 81 and 82 and thus the entire printing mechanism 60 to the upper line. The carriages 81 and 82 are slightly moved behind the printing roller 61 far enough from the pressure roller 66 to deviate from the position at which the image is applied to the web 11 (ie, out of the printing position). In addition, the manually controlled air cylinders 151a and 151b remain in operation, whereby the anilox and the metering roller maintain proper ink supply contacts.

The printing mechanism rollers 61, 63 and 64 are automatically moved from the printing position to the starting position each time the printing press 10 is stopped or stopped. The operator can also manually operate the printing mechanism rollers 61, 63 and 64 from the printing position to the starting position while the printer 10 is in operation. This feature allows the operator to separate one or more colors during the initial setup of the print operation (i.e. while determining the quality of the initial image). Preferably, during the movement to the starting position with the printer 10 still in operation, the motors 191a, 191b are activated, and the anilox and metering rollers 63, 64 move out of the fluid dispensing position to the blocking position. After being moved, the lower carriages 81 and 82 are moved. By first interrupting the supply of ink before moving the printing roller 61, ink remaining in the printing plate 62 before the printing roller 61 is moved can be transferred to the web 11. In this way the ink can be cleaned rather than dried on the plate 62.

When the upper carriage is moved from the printing position to the starting position, the upper carriages 89 and 90 are moved by the same distance by simultaneously operating the stepper motors 171a and 171b in the same number of increments or steps. Similarly, the lower carriages 81 and 82 are moved the same distance from the print position to the start position by operating the motors 191a and 191b in the same manner. Thus, the relative positions of the printing mechanism rollers 61, 63, and 64 (i.e., the distance between the printing mechanism rollers) can be varied, but the relative angular direction of each roller axis is typically maintained in a parallel direction.

In the state of starting, the printing roller 61 continues to be in close contact with the swing gear assembly 268 sufficiently to keep the gears 269 and 288 and the transfer rings 297 and 287 fully engaged. The pneumatic rotary actuator 292 (see FIG. 6) rotates the tip gear 288 and transfer ring 287 toward the upward arc around the shaft 273 and the retracted printing roller 61 as described above. As the torque is continuously applied to the shaft 293 delivered to the swing gear housing 270 as described above, the swing gear assembly 268 remains engaged when the roller 61 is retracted to the starting position. In addition, once the start position is reached, the clutch assembly 200 is stopped, the clutch assembly 215 is activated, and the motor 225 is turned on (see FIG. 14). In this way the anilox and metering rollers 63, 64 are separated from the common drive shaft 69. At the same time, the rollers 63 and 64 are continuously rotated by the motor 225 to prevent the ink from drying on the surface of the rollers 63 and 64.

Another non-printed position of the printing mechanism 60 is the withdrawn or withdrawn position. In this position, the upper carriages 89, 90 (anilox and metering rollers 63, 64) are moved to the upper line or to the near full possible output of the upper slide assemblies 91, 92. Lower carriages 81 and 82 (ie, printing rollers 61) are also moved to the upper line, but only about half of the possible output of lower slide assemblies 83 and 84. This movement of the upper and lower carriages 89, 90 and 81, 82 is an additional simultaneous and identical operation of each stepper motor 171a, 171b, 191a and 191b in the same manner as described above for the movement to the starting position. Is made by. Before the carriages 89, 90 and 81, 82 start moving from the starting position to the withdrawn position, the printing press 10 is stopped and the operation of the rotary actuator 292 (see FIG. 6) is reversed, and the oscillating gear The tip gear 288 of the assembly 268 is rotated downward away from the print roller gear 269. While in the retracted position, the printing roller 61 is not only out of position to apply the component image to the web 11, but also the roller 61 also has the oscillating gear 288 even though the oddity 288 is returned. Too far from swinging gear assembly 268 to engage and drive gear 269. While in this withdrawn position, the anilox and metering rollers 63, 64 are preferably rotated by the motor 225 to preferably prevent the ink from drying on the surface.

When the carriages 89, 90 and 81, 82 (i.e. rollers 63, 64 and 61) are moved from the withdrawn position to the printing position, the printer 10 is well stopped (i.e., gear train 68 ) Is not driven. When the printing mechanism rollers 61, 63, and 64 reach the starting position, the actuator 292 pivots the leading gear 288 of the swing gear assembly 268 upwards to fully engage the printing roller gear 269. It works automatically. Thereafter, the rollers 61, 63, and 64 are moved to each printing position with the swing gear 288 pressed slightly downward. However, when the printer 10 is in operation, the rollers 61, 63 and 64 do not move past the starting position to the printing position, and the actuator 292 is engaged with the printing roller gear 269 so as to engage the front gear 288. It does not work to swing upwards. With the printer 10 running and the printing mechanism rollers 61, 63, and 64 positioned at the printing position, when the printer 10 is stopped, the rollers 61, 63, and 64 automatically move to the starting position. do.

The operation of the stepper motors 171, 191 consists of the communication of control signals on the line 419 to transmit the same number of pulses to each motor 171, 191. Each pulse is caused by a fixed movement of each carriage 89, 90 and 81, 82 when received by each stepper motor 171a, 1712b, 191a and 191b. Processor 408 maintains an accurate position track of stepper motors 171a, 171b, 191a, and 191b with pulses from each encoder 172a, 172b, 192a, and 192b communicated over corresponding line 420. Each pulse received from encoders 172a, 172b and 192a, 192b represents a fixed increment for the movement of each carriage 89, 90, 81, and 82 and each roller 63, 64, and 61. Encoders 172a, 172b, 192a, and 192b associated with stepper motors 171a, 171b, 191a, and 191b provide feedback to the computer controlled positioning system. This feedback allows processor 408 primary host computer 400 to know whether a particular stepper motor 171 or 191 is substantially operated and moved by a desired amount. The combination of the structure of the positioning mechanism 78 described above and the present computer controlled positioning system allows the printing mechanism rollers 61, 63 and 64 to be moved out of a specific printing position and returned to that printing position with very high accuracy. .

The stepper motors 171a, 171b, 191a and 191b also allow the operating position of the printing roller 61 relative to the pressure roller 66 and the operating position of the anilox roller 63 relative to the printing roller 61 to be adjusted. It can be operated in adjustment mode. This adjustment can be performed to set the roller spacing by sending the same number of pulses to each of the pair of stepper motors (171 or 191) and thereby moving the rollers away from each other and towards each other. The adjustment can also be carried out by operating each of the stepper motors 171a, 171b, 191a and 191b and thereby adjusting the relative inclination or inclination of the roller axis with respect to each other. This adjustment can be performed when the printing press 10 is stopped or during the operation of printing an image on the web 11.

The block diagram of FIG. 24 and the flowchart of FIG. 25 illustrate the operation of the positioning controller 406. Generally, processor 408 is a microprocessor, such as the Motorola MC68HC711E9FS, programmed to transmit button actions executed by the operator and also by the pulses from encoders 172 and 192 at panel 410 or on dial 414. 430. Microprocessor 430 also executes processing operations to convert input information into appropriate control signals on lines 418 and 419.

Symbolically, referring to FIG. 24, buttons 410a through 410p of the control panel 410 are connected via an interface 431 such as a programmed array logic chip PAL, for example, industry standard part number GAL-22V10. May be considered to be connecting. The microprocessor 430 is provided to the memory unit 432 of the processor 408 which stores the state as a plurality of logical variables 432a to 432p respectively representing the state of one of the buttons 410a to 410p in which the interface 431 is pressed. The state of the button can be checked by communicating the state periodically, for example every 1/50 second. For example, when one of the variables 432a through 432p is zero, this indicates that the corresponding buttons 410a through 410p were not pressed. For example, when one of the variables 432a through 432p is 1, this indicates that the corresponding buttons 410a through 410p have been pressed. For buttons that are interpreted as pressed, the interface should return to 1 for 4 consecutive question cycles. In one embodiment, when one button press is detected, microprocessor 430 compares the bit pattern in memory 432 with a valid setting that identifies the selected function while ignoring the invalid combination. When a valid pattern is identified, the appropriate routine is executed as shown in FIG. The program executed by the microprocessor 430 may determine which button is pressed on the panel 410 and alternately execute the loop shown in FIG. 25 so that only one button can be pressed at a time. Such a program only needs to recognize one button at a time. When one of the buttons is pressed, all other buttons that have already been pressed are off or otherwise cleared by the program. In this embodiment, the multi-button command is selected by successively pressing the combination of buttons on panel 410.

The processor 408 also stores a number of integer variables 433a through 433d and represents a memory increment or decay coefficient accumulated by pulses received across one of the lines 420 from each of the encoders 172 and 192. A portion 433 is included. Input line 420 is via an interface 434 such as an RS485 interface chip that functions in conjunction with a separate processor or microprocessor 430 that counts pulses received from encoders 172 and 192 via line 420. Each may be considered to be connected. The microprocessor 430 interprets the signal for the increase or decrease coefficient and the direction stored in the memory locations 433a to 433d corresponding to one of the encoders 172 and 192 in which the pulse was received. Each encoder 172, 192 generates one pulse every 1/200 of each encoder rotation and corresponds to a fixed increase in motion of each carriage 81, 82, 91, and 92. These pulses are out of 90 ° from the encoder through each of the two channels. The identification of the encoder with this phase shift pulse is 1/800 of the axis rotation. After gearing in, this is the amount of carriage movement 0.005 mm, 0.197 mil or approximately 0.0002 inches per phase change pulse. The encoder is also directional responsive. For example, when a signal on one channel is shifted from 0 to 1 state at a time when the signal on another channel is zero, or when a signal on one channel is changed from 1 to 0 when the signal on another channel is 1, forward movement is stopped. Is directed. The directional responsiveness of the encoder provides a means for identifying the actual rotation of the stepper motors 171, 191 and external pulses due to vibrations generated when the motor is stationary. The default value of the variables 433a through 433d is zero. Variables 433a through 433d reflect the accumulated arithmetic sum of the pulses counted from each encoder 172, 192, which can be considered a counter variable.

Dial 414 is also coupled to memory variable 436a via interface 435 at memory location 436. Dial 414 rotates in any direction to continuously provide a series of direction sensitive pulses to interface 435 that increases or decreases the current integer value of variable 436a for clockwise or counterclockwise rotation, respectively. It is clicked every moment. As such, variable 436a reflects the accumulated arithmetic sum of the pulses counted from dial 414 since the last reset or clear of variable 436a. Thereby the variable 436a can also be considered a counter variable.

The additional memory unit 438 stores a variable of an output integer indicating the number of pulses to be transmitted to the stepper motors 171 and 191. Corresponding variables 438a through 438d are stored in the memory portion 438, and under the control of the microprocessor 430, when the output signal is generated on the line 419 via the driver 439, each of the memory variables The pre-set coefficient of is increased or decreased to zero, thereby generating a forward or reverse pulse on the corresponding stepper motor which increases or decreases the current position coefficient to the appropriate target coefficient. The drive interface chip or driver 439 is suitable for powering the particular stepper motors 171, 191 being driven.

In one embodiment, the counters 433, 436, and 438 are examples of microprocessors 430, such as chips manufactured by Xilinx, which may be programmed to include counters 433, 436, and 438, for example. For example, they may be separated from memory in a field programmable gate array (FPGA). Such a counter can only interrogate the counter, since only an interruption request from the microprocessor 430 will respond to the encoder for interrupt.

Other memory locations include repeat length 440a; REPEAT LENGTH (proportional to print roller diameter), paper thickness 440b; PAPER THICKNESS, anilox roller diameter 440c; ANILOX ROLLER DIAMETER, and gear pitch 440d; GEAR PITCH. Is provided to remember the settings. The memory 432, 433, 436, 438, 440 is a nonvolatile memory connected to the microprocessor 430 or contained within the microprocessor chip as an interface and driver through the computer bus 441. Additionally, one or a pair of output drivers 441 connected to the microprocessor 430 provide for operating the air cylinder 151 moving in or out of the metering roller in accordance with a bidirectional signal on the line 418. Can be. In addition, the display 412, which is also connected to the microprocessor 430, is provided with LED displays 412a, 412b. A display that outputs two line alphabets or digital data to the operator indicating an action or function selected by the operator, such as an output setting, can display the current setting compared to the new setting when incremented or decremented by the dial 414. have.

Additional volatile memory 442 and programmable read-only memory 443, such as EEPROM, are provided for storing numerical values, constraints, calibration settings, intermediate variables, and programs. Additional drivers 444 are provided for actuating anilox roller clutches (200, 215), oscillating gear drivers, and other functions.

In operation, depending on the initial installation of the printer 10 or the power loss to the controller 406, any settings must be made. When the controller 406 is first excited, all values may default to zero or to default values that are any standard values that can be programmed into the memory 443, which may be read-only memory. At this time, the operator can press the gear pitch setting button (410m). The gear pitch is the number of teeth per inch according to the pressure roller gear 196 driving the printing roller 61. Since the value changes only when a physical gear change is made to the machine 10, the setting may be formed in a blank key coded manner that can only be accessed by the inspector, and such a value is also stored in the EEPROM 443. Can be programmed. The gear pitch information is needed to calculate the repeat length size possible by the program, which repeat length is the ratio of the gear tooth count of the printing roller gear 269 to the press roller gear 196 along the press roller circumference. Is preferably equal to That is, the repeating length or the circumference of the printing roller 61 can be changed only by increasing as the circumference of the pressure roller 66 divided by the number of teeth on the pressure roller gear 196. Thus, the pressure roller circumference must be known in the program and well programmed in the EEPROM 443.

As shown in the flowchart of FIG. 25, the program scans the memory 443, recognizes the buttons, and executes the SET GEAR routine described in FIG. 25A. The preset or default gear pitch is initially loaded by the microprocessor 430 into the memory variable 440d and displayed to the operator on the display 412a and the display 412b. The routine may check the setting, and if the check is not made, it is desirable to set a default value as shown in FIG. 25A or execute it upon start of the program. When the present value is displayed, the operator adjusts the dial 414. The display 412b may be programmed to step through a programmed list of gear pitches stored in the memory 443. Optionally, such a program can retrieve the number of gear teeth on the pressure roller gear 196 from the memory and increase it directly up or down from the pulse of the dial. The display can reflect the number of gear teeth and preferably reflects the calculated number reflecting the pressure roller circumference divided by the number of pressure roller gear teeth. As another option, the display can directly increase the representative number of gear pitches according to the pulse of the dial. When the proper pitch has been selected, the operator presses button 410m again to set it, to load a new value into variable 440d. Instead, pressing another button cancels the setting and returns to the start (fig. 25),

Depending on the gear pitch setting, the operator can check and reset the ANilox roll diameter, if desired. The setting procedure is initialized by pressing a button 410i for selecting SET ANILOX ROLLER DIAMETER, as shown in FIG. The routine is the same as that of FIG. 25A, as described in detail in the flowchart of FIG. 25B. Default setting routing is preferably performed at startup. The present or default value for the anilox roller diameter is shown on the displays 412a and 412b. The numerical value on display 412b can be stepped through the programmed size list by actuating dial 414, while changing the display of display 412b to increase up and down with dial pulses. When so selected, the operator presses the button 410i again to set the diameter for the selected diameter for the anilox roller 63 which stores the value of the memory variable 440c.

Each time the start of initialization and additional print jobs are started on the printer 10, the operator checks and resets the REPEAT LENGTH related to the diameter of the print roller 61, which should be known for positioning. The operator presses the SET REPEAT LENGTH button 410g and is recognized by a program such as that shown in FIG. 25, and in the same manner as in FIG. 25A, the repeat length setting (SET) described in FIG. REPEAT LENGTH) routine. The default setting section of the routine is preferably executed at the start section other than as described. Such a default value is preferably the largest printing roller size that can be mounted to the printer 10. This prevents inadvertent crashing of the printing roller 61 and the pressing roller 66. The current or default value for the repetition length is then shown on the displays 412a and 412b. The numerical value of the display 412b multiplies the pulse pitch generated by the operation of the dial 414 through the magnitude list, multiplies by the current value, and changes the display of the display 412b. When the desired repetition length is selected, the operator presses button 410g again to set the repetition length to the selected length. The new value is stored in the memory 440a and derived from the diameter of the printing roller for use in the position calculation.

Web thickness is also set similarly by pressing button 410h. The program recognizes the button, initiates the SET PAPER THICKNESS operation, and executes the routine of FIG. 25D. The currently set value or the viable default value for the thickest paper for the web thickness is displayed in the display 412a, 412b in thousands of inches, and the value of the display 412b operates the dial 414 to display a list of preprogrammed thicknesses. Step through and increment up and down to 1 / 1000th of an inch of display 412b. When the desired web thickness has been selected, the operator again presses button 410h to set the current value of the web thickness to the selected value. The new value is stored in memory 440b.

At the initial setting stage of the printing press 10 and at rare intervals, the position of the printing mechanism 60 is calculated. This is accomplished by pressing the CALIBRATE button 4101, whereby the program initiates the CALIBRATE routine described in FIG. 25E. Thereafter, the operator presses the plate roll adjustment button 410d or anilox roll adjustment button 410c to select the roller to be measured. When the routine is executed, the stepper motors 191a, 191b or 171a, 171b are excited so that the entire printing mechanism 60 (e.g., lower carriages 81, 82) or anilox and metering rollers 63, 64 ) (Eg, upper carriages 89, 90) are separated from the pressure roller 66 and moved to the extreme position relative to each mechanical stop 184a, 174a. Mechanical stops 184a and 174a may be respective surfaces on respective guide actuation brackets 184 and 174 (see FIG. 7). Motors 191 and 171 are excited by pulses through corresponding drivers 439. When the stepper motor 191 or 171 moves, the encoder 192 or 172 returns a pulse through the corresponding interface 434. Even when a pulse is being transmitted to the stepper motor 191 or 171, when the microprocessor 430 detects that the pulse from the encoder 192 is stopped, the determination is made to the respective lower or upper carriage 81, 82 or 89, 90 causes their respective stops 81, 82 or 89, 90 to engage and lock in their respective stops 184a or 174a. In this case, the coefficients of each of the counters 433 are stored in the memory 442. The stepper motor 191 or 171 then drives a fixed number of pulses to move each lower or upper carriage 81, 82 or 89, 90 to the retracted position towards the pressure roller 66. The number of pulses is determined by the back-off number preprogrammed in the memory 443.

From each retracted position, the number of calibration pulses required to contact the printing roller 61 to the pressure roller 66 or the anilox roller 63 to the printing roller 61 is determined by the respective stepper motors 191a and 191b. Or 171a and 171b, respectively. Since the running length or longitudinal distance between one roller and the other roller can be different from one side to another side of the printing press 10, the number of the calibration pulses is determined individually. The operator uses the calibration calipers or gauges to provide anilox roller 63 (for anilox roller calibration) or pressure roller 66 for the print roller 61 and each carriage 81, 82 or 89, 90 ( The running length between one of the printing roll scales) is measured. The operator then presses each button 410a or 410b that recognizes the side (eg, gear or operator side). For each side, the dial 415 is pivoted by an amount corresponding to the measured length. The pulse of dial 415 increments each counter 438c, 438d or 438a, 438b individually and modifies the pulse of each stepper motor 191a, 191b or 171a, 171b. When the operator satisfies the given setting, the operator presses button 410n to memorize the scale adjustment setting from each counter 438c, 438d or 438a, 438b. The program then proceeds to a zero print head routine. Preferably, instead of the printing roller 61 being provided, a calibration bar (not shown) is used to perform calibration. The rod is sized to allow additional tolerance of the custom gauge used. Both the rods and gauges adjust the space for a standard printing roller 61 of, for example, a 16.5 inch (74.9 cm) circumference. For actual printing rollers 61 of different sizes, the position is calculated from the calibrated number and the repeat length measurement.

The zero print head routine automatically shifts to subsequent scale adjustment by pressing the zero print head button 410k at the time of power supply by the operator's choice. By pressing the button 410k, the program is executed to execute the zero print head routine described in FIG. 25F. The routine zeroes both the printing roller 61 and the anilox roller 63 at the same time. The routine pulses the stepper motors 191a, 191b and 171a, 171b backwards until the stops 184a, 174a meet, and advances forward by a programmed amount that adds the scale adjustment value to define the retracted position. do. This defines the retracted position as a point spaced apart from the stops 184a, 174a sufficient fixed distance to prevent the carriages 81, 82, 91, 92 from engaging the stops 184a, 174a in operation. Thereafter, the counter 433 is set to zero at the retracted position. The setting sets the zero reference position from a program for calculating the various positions of the printing roller 61 and the anilox roller 63. In the movement between these positions, the cooperation of the clutch assembly 200, 215 and the swinging gear assembly 268, and the printing roller 61 and the anilox roller (which occurs when the print head 60 moves through various positions) Other functions such as positioning of 63) are also controlled.

In operation of the printing press 10, the printing mechanism 60 can be moved with precise repeatability between the retraction, start and print positions. In the retracted position, the operator can check the printing mechanism 60 and change the plate 62, the clean roller, and the printing roller 61, or the base platform 48 between the operating position and the out of position. (Refer to FIGS. 4 and 5, respectively.) The movement of the print head 60 to the retracted position can be performed by using the RETRACT PRINT HEAD button 410j. This is accomplished by pressing and thus the program executes the RETRACT PRINT HEAD routine described in FIG. 25G. The routine transmits the pulses causing the movement to the stepper motors 191a, 191b and 171a, 171b so that the lower carriages 81, 82 (e.g., the printing roller 61) and the upper carriages 89, 90 [ For example, each of the anilox rollers 63 is moved to the retracted position. The withdrawal position is identified when the contents of the respective counters 433c, 433d and 433a, 433b are equal to zero, and the calculated position is obtained as a result of the calibration and zero print head routines. In addition, the operation, relay, and other functions of the clutch to be executed are in response to signals from the microprocessor 430 and are actuated through the driver 444.

The movement of the print head 60 to the start position is accomplished by pressing the THROW-OFF button, whereby the program executes the THROW-OFF routine shown in FIG. 25H. The routine pulses the stepper motors 191a and 191b with the driver 439 until the counters 433c and 433d are stored in the memory 443 and instructed the coefficients to be smaller by a pre-programmed amount than the calculated print position. The printing mechanism 60 is moved by sending. In addition, pulses are transmitted to the stepper motors 171a and 171b to move the anilox roller 63 together with the metering roller 64 in a direction separated from the printing roller 61 or in a forward direction. However, as the print head 60 is moved to the retracted position, the start position or the print position, the control signal controls other functions or other corresponding functions via the driver 444 which drives the anilox roller 63. To the engagement or release clutches 200 and 215 for the purpose of transmission. From the printing position to the starting position, the stepper motor 171 is first operated according to the operation of the stepper motor 191 when it is desirable to transfer ink to the web 11 to remove any excess ink from the plate 62. Can be.

The movement of the printing mechanism 60 to the print position is accomplished by pressing the AUTO PRINT button 410e, thereby executing the AUTO PRINT routine, as in the flowchart illustrated in FIG. 25I. . In the automatic printing routine, the microprocessor 430 monitors whether the printer is running, i.e. whether the web 11 is driven through the station 13 or not. This may be accomplished by detection of the presence and movement of the web 11 at each print station 13 or by a signal from the host computer 400. When the web 11 is in the moving state, the printing mechanism 60 is moved or held to the start position. When the web is not moved, the stepper motor 191 is activated to move the printing roller 61 to zero or printing position, where the plate 62 is in print relation with the web 11. The motor 171 is also driven to make the anilox roller 63 in fluid distribution relationship with the plate 62 on the printing roller 61. When the manual start button is pressed in the auto printing state, auto printing is canceled and the print head 60 is moved to the start position.

The adjustment of the printing roller 61 changes the zero positional relationship to the position commanded by the offset of the positive or negative value. Such adjustment is performed by pressing the plate roll adjustment button 410d, whereby the microprocessor executes the plate roll adjustment routine as shown in FIG. 25J. The adjustment can be performed at any position of the printing mechanism 60, but at the printing position where the print head 60 is printing on the web 11, the operator monitors the quality of the printed matter. When the adjustment is selected, zero is displayed on the displays 412a and 412b. Then, when the operator adjusts the dial 414, both the stepper motors 191a and 191b are moved to the same field. As the motor 191 moves, the displays 412a and 412b increase or decrease in accordance with the pulses received from the encoders 192a and 192b respectively. Those changes are made immediately, and the operator can immediately observe the effects on the printed matter if printing proceeds. At any time during this process, when the operator presses one of the gear side or operator side buttons 410a or 410b, the web 11 is moved from the point where the dial 414 is adjusted. Only the stepper motor 191a or 191b on the selected side is affected. In this way, the operator can compensate for non-uniformity or non-equilibrium of the printing roller 61 with respect to the pressure roller 66. If only one side is selected, press the button for the other side to switch the adjustment for the other side. Pressing the PLATE ROLL ADJUST button 410d returns the same adjustment back to both sides. The pulse of the dial 414 pulses each stepper motor 191 directly. The adjustment value is stored in the volatile memory 442 and displayed on the displays 412a and 412b for each side. These adjustments can be changed or cleared by the operator by immediately returning the motor 191 to its zero position. This routine remains in the plate roller adjustment loop until another button is pressed to select another function.

The adjustment by the operator of the anilox roller 63 relative to the printing roller 61 proceeds similarly by pressing the anilox roll adjustment button 410c as shown in FIG. The difference is that the motor 171a or 171b is adjusted and feedback is received from each of the encoders 172a or 172b to verify the motion.

A CONFIRM button 410n for starting to cancel the current adjustment and returning to the ADJUST PRINT ROLL routine, a clear button 410o for clearing all button functions and displays, and the anilox roller 63 Other functions are also provided, such as a METERING ROLLER MOVE button 410p that allows the metering roller 64 to be pushed in or out of the cylinder 151 to start or stop ink flow.

Computer controlled matching

Computer controlled matching, including semi-automatic pre-matching characteristics and the more fully automatic circumferential and axial matching characteristics, is managed by an operator from either station or host computer. These are described in relation to the match controller 407 at each station 13. This operation can be controlled from the host computer 400 in whole or separately for the selected station.

The block diagram of FIG. 26 and the flowchart of FIG. 27 show the operation of the matching characteristics and logic of the matching controller 407. The controller 407 consists of the same type of components as the positioning controller 406 described above, in addition to adding an interrupt drive routine to simultaneously accommodate operator interfacing and fast match control, and has the same general structure and similar logic. Function accordingly. In general, processor 409 cooperates with a PAL equal to that of processor 406 to query microprocessor 450 for interrupts triggered by button operations performed by an operator at panel 411 and by dial 415. ). The microprocessor 450 also interprets pulses from the encoder 328 and electric eye sensors 347 and 350. Microprocessor 450 also performs processing operations to convert operator input information into appropriate control signals on lines 424 and 426.

As shown in FIG. 26, buttons 411a through 411p of the control panel 411 store a plurality of logical variables 452a through 452p through the interface 451 in the memory unit 452 of the processor 409. Are considered to be connected to, each of the logical variables indicating the state of the push buttons 411a to 411p. When any variable 452a through 452p is zero, for example, this indicates that the corresponding buttons 411a through 411p are not pressed. When any of the variables 452a through 452p is 1, this indicates that the corresponding buttons 411a through 411p have been pressed. The default setting for variables 432a through 432p is zero.

Processor 409 also includes a memory portion 453 that acts as a counter, which displays the coefficients of pulses received from encoder 344 via line 423. The input line 423 is connected via an interface 454 which is, for example, an RS485 chip, which in turn cooperates with the microprocessor 450 to receive two channel direction sense pulses received from the encoder via the input line 423. Count. The counter 453 increases or decreases the stored coefficient according to the rotation direction of the encoder 344. Pulses on encoder 344 are generated every 1/5000 of encoder rotation. This encoder rotation corresponds directly to a fixed increment of the linear motion of the web 11, corresponding to a fixed increment of the angular motion of the pressure roller 66. According to the encoders 172, 192 for the positioning controller 406, these pulses are generated on two channels and are out of phase by 90 °. The discriminating force of the encoder 344 is 1 / 20,000 of one revolution of the encoder shaft. Thus, this encoder 344 is directional responsive. Counter 453 reflects the cumulative logarithm of the pulses counted from encoder 344. One encoder 344 is coupled to the shaft of the pressure roller 66 which rotates continuously. The count from encoder 344 starts again at zero count when counter 453 has exceeded the maximum value.

The dial 415 is also connected to the memory portion 456 through the interface 455. The dial 415 is in either direction to continuously generate a series of direction sense pulses to the interface 455 to increase or decrease the current integer value of the variable in the memory portion 456 clockwise or counterclockwise, respectively. Click on every fraction of the rotation. This reflects the cumulative algebraic sum of the pulses counted from the dial 415 because the memory unit 456 finally resets or erases the variables stored therein. In addition, each pulse traveling from the dial 415 to the counter 456 through the interface 455 trips an interrupt in the microprocessor 450.

Sensors 347 and 350 connect to microprocessor 450 and corresponding memory portions 459a and 459b through interfaces 457a and 457b, respectively, where each sensor 347, 350 is connected to web 11. Logic 1 is stored when each mark 349 is detected on the printing roller 61 of the image. Operating each of the sensors 347 and 350 also trips each interrupt in the microprocessor 450.

The additional memory unit 458 stores an output integer variable indicating the number of pulses to be transmitted to the stepper motors 327 and 340 to perform circumferential and axial matching, respectively. Corresponding variables 458a and 458b are stored in the memory unit 458 and an output signal is generated on the line 419 via the driver 459 under the control of the microprocessor 450, and preset coefficients for each memory variable. Is increased or decreased to zero at corresponding intervals spaced over a single repetition length in the form of forward or reverse pulses, respectively, for the corresponding stepper motor 327 or 340.

Like the controller 408, in one embodiment, the counters 453, 456, and 458 are separate from the memory in the microprocessor 450, for example a field programmable gate array (FPGA) as manufactured by Xilinx Corporation. This FPGA can be programmed to include counters 453, 456 and 458, for example. Such a counter can conveniently query the counter after responding to an interrupt from the encoder without requiring interruption of the microprocessor 450.

The memory 406 also includes a repetition length 460a (REPEAT LENGTH), an inspection area or window 460b (INSPECTION ZONE or WINDOW), deadband tolerance 460c (DEAD ZONE TOLERANCE), number of repetitions per print roller rotation (460d; NUMBER). It is provided to remember settings such as OF REPEATS PER PRINT ROLLER ROTATION, gain 460c (GAIN), linear error average (460f) and LINEA ERROR AVERAGING (Axial ERROR AVERAGING). The memories 452, 453, 456, 458, 460, 463, 464 are connected to the microprocessor 450 via a computer bus 461 as an interface and driver, or a micro like form when using a Motorola MC68HC711E9 microprocessor. It may be included in the volatile memory of the chip including the processor 450. However, certain variables displayed as memorized in the memory 460 are recorded in the nonvolatile memory when the printer 10 is stopped so as to be utilized when the printer is started after the printer is stopped. Display 413, which is also connected to microprocessor 450, has two LED display lines 413a and 413b that operator an alphanumeric character that indicates the operation and settings selected by the operator. Output to. Program and pre-programmed variables and settings are stored in read-only memory 463.

The program executed by the match control microprocessor 450 is somewhat different from the program of the position control microprocessor 430 because of the monitoring functions and settings that interface with the operator through the panel 411 and the display 413. This is because it not only handles the change, but also automatically controls the match when the match is selected and the printer runs. While other program portions of the microprocessor 450 are executed, this is accomplished by utilizing keyboard input and setting changes made by the operator and interrupts that initiate the routine so that the roll and web mark readings are made. A program that accomplishes this purpose is typically represented by the MAIN LOOP program shown in FIG. 27 and in the interrupt processing routines shown in FIGS. 27A to 27C.

The main loop program of FIG. 27 is initialized at the START point when the microprocessor 450 is powered on. Initially, a programmable gate array logic chip is described in FIG. As described above, an initiation routine for downloading to the forming program is executed.

After initialization, the program executes the loop from the MAIN LOOP ENTRY point in FIG. This loop first checks to see if any setting or setting change has been made by any operator. If done, they are stored in volatile memory 464 and written to nonvolatile memory 460 when the printer is not running. Therefore, the program checks for web motion and stores any settings made for nonvolatile memory 460. The loop then consults memory 464 to check that the ROLL MARK coefficients and the WEB MARK coefficients are read. Moreover, when the WEB MARK is read, the program also checks to determine if the WEB MARK coefficient includes three crossings of the Z-mark 350a in FIG. The MAIN LOOP then checks to see if there is a preliminary match, and if so, performs a preliminary match of each station without the printer running. It retrieves the web distance from the memory to the current station from the first station, divides the distance by the repetition length or print roll circumference, and pulses the stepper motor 327 with the harmonic sphere 275 according to the remainder of the division operation. This is done by advancing the printing roll in relation to the same reference rotation direction as that of the first station.

The MAIN LOOP also checks to see if the manual setting of the linear match to select the linear match by pressing the NEXT MARK button is selected and the automatic linear match is stopped. If so, the interrupt is stopped while the roll and web mark space is determined and used to set the LINEAL REGISTRATION variable, which is the automatic linear match set point for the station. The setting routine initialized by pressing the NEXT MARK button 411f by the operator is shown in the flowchart of FIG. 27D.

Once the ROLL MARK and WEB MARK coefficients have been determined, the MAIN LOOP is the LINEAL REGISTRATION of FIG. 27H which embodies the actual performance of automatic linear matching as described in more detail below. Call the subroutine. Then, when the entire Z-mark data is read, the MAIN LOOP also calls the LATERAL REGISTRATION subroutine of FIG. 27I, which subroutines as described in more detail. Implement actual performance. Thereafter, the main loop MAIN LOOP returns to the MAIN LOOP ENTRY point and executes again if not interrupted by the interrupt routines of FIGS. 27A-27C, which is the button press routine of FIG. 27E. To run The button printing routine of FIG. 27E sends information to the display 413 according to the currently selected routine, as shown in the flowchart of FIG. 27F, to retrieve button press and setting adjustment data from the panel 411 and the dial 415. FIG. This routine also interprets button presses or combinations thereof to select various operations as shown in the flowchart of FIG. 27G.

The button press routine (BUTTON PRESS ROUTINE) determines whether the button has been pressed on the panel 411 to recognize the button or button combination. The program can be set so that only one button is pressed. Thus, the program is set to recognize only one button and to stop another button pressed when any one of the buttons is pressed. In such an embodiment, the multi-button command is selected by sequentially pressing the buttons on panel 411.

Optionally, in this embodiment, the program is configured such that the multi-button command is selected by simultaneously pressing one or more buttons. In this case, the release of the button assumes that the button has been pressed and resets all other print buttons recorded in the memory. Upon release of the button, if another button is still pressed, the final release of the simultaneously pressed button sets another previously released and simultaneously pressed button in the memory 452. The program then checks all the button combinations and compares the button combinations with all valid combinations ignoring others as shown in the flow chart of FIG.

The call of the button press routine (BUTTON PRESS ROUTINE) of FIG. 27E occurs at a predetermined interval of, for example, 1/50 second. During the other time, the main loop (MAIN LOOP) is executed to call the auto matching routine. In particular, when the printing press 10 is operated, an automatic matching routine in which the program controls the printing press 10 matching is continuously executed. Thus, each of the routines initiated by the button cloud mentioned in the flow chart of FIG. 27G is interrupted every 1/50 second to test another button press.

Preliminary matching

According to the setting of the printing mechanism 60 of the printer 10 for the print job as described in relation to the positioning control, the operator moves the print roller 61 to the web for each of the stations 13. Pre-match to the predicted position of (11). The preliminary registration is based on the geometric knowledge of the printing press 10, including the relative position of the interrelated print stations 13 and the length of the web 11 extending therethrough. For example, the length of the web 11 extending from the nip of the printing roll at the first station to the nip of each station according to the first station matched at any zero orientation from the geometry of the entire printing press 10 is It is predetermined and stored in the nonvolatile memory 264. This length is divided by the repeating length or circumference of the printing roller 61 to indicate irrelevant quotient and circumferential adjustment and generate the remainder, which is the number of pulses to be transmitted to the harmonic driver 275 of each station 13. The printing roller 61 is preliminarily matched with the printing roller of the first station 13a.

Typically the preliminary registration is performed without the web 11 in the printing press 10. In the preliminary registration, the printing roller 61 of each of the stations 13 to be used is characterized in that the respective roughening driver 275 steps the pulse number calculated by the sensor 347 through the detection of the printing roller mark 349. Is rotated in a predetermined direction relative to the frame 36.

In order to select the circumferential preliminary registration, the operator presses the preliminary registration button 411e. Since this function is generally desirable when the printer 10 is not running, the MAIN LOOP gradually waits for an event, which is typically the button press routine of FIG. 27E. Consume 1/50 second time on a timer that runs. In this routine, when a preliminary match is desired, the other setup routine bypasses the subroutine of FIG. 27F by default without pre-call and cues display 413 a matching error that may be zero. The microprocessor 450 calls the subroutine of FIG. 27G to scan for a combination of valid buttons 411a to 411p to match or return the pressed button or combination of buttons. A program in the microprocessor 450 as shown in FIG. 27 responds to the pressing of the preliminary match selection button 411e by executing the SET PREREGISTRATION routine of FIG. It is entered at the entry point to select the preliminary matching function. Depending on the preliminary registration function selected, when the MAIN program is tested for this selection, PREREGISTRATION is automatically executed to rotate the print roller 61 in the programmed relative rotational direction for each station. The 61 is preliminarily matched in the circumferential direction. When the preliminary match is completed, the preliminary match function is not automatically selected.

When preliminary matching is performed, the repetition length used to determine each station preliminary matching setting is finally stored in memory. Often, after setting up the printer and before the preliminary registration is performed, the new REPEAT LENGTH is set in the manner described according to the discussion of circumferential matching below.

Axial registration is typically not performed without a web. Rather, the overall adjustment of the axial registration is carried out so that the roller is centered in the transverse direction. This is accomplished by physically adjusting the transverse position of the sensor 350. In order for the web sensor 350 to be optimally centered on the web mark 350a, the sensor 350 is moved laterally on the support to align with the center of the mark 350a. Movement of sensor 350 is made manually by adjusting knob 356 (shown in FIG. 18). Optionally, automatic movement of the sensor 350 on the support may be provided using a stepper motor or other device under the control of the microprocessor 450 or other device.

Circumferential registration

As shown in FIG. 16, the front end of the pressure roller 66 in each print station 13 is an optical device such as a model H25D manufactured by BEI Motion Systems Company of Carlsbad, CA. The encoder 344 is mounted. This encoder 344 generates a pulse indicating the fixed length of the web 11. By mounting each roller 66 with its encoder 344, the difference in web speed along the station 13 has little adverse effect on the accuracy of the circumferential matching control. In particular, the clearance of the gears, the torsion of the axes and strains of the various drive train elements and the relative movement between them are almost entirely eliminated. The optical encoder 344 is manufactured by Rexnord Mechanical Power Division (Rexnord, Mechanical Power Divsion, Warren, PA) of Warren, PA. It has a shaft 345 connected to the stub at the front end of the pressure roller 66 by a CC37 in-coupling 346.

The computer controlled circumferential matching system includes a first optical sensor 347 (see FIG. 2) mounted to the front end of the stop plate 58. The sensor 347 is mounted in place under the front end of the printing roller 61 to match each rotation of the roller 61 by sensing the mark 349 (FIG. 3), and the front end of the roller 61. It has an optical fiber optical lens 348 in the form of a transverse rod formed on the minor surface. 2, 4, 5 and 18-21, the second optical sensor 350 is a web mark 350a originally printed on the web 11 in the first print station 13a. Is positioned over the nip between the printing roller 61 and the pressure roller 66 and mounted between the vertical support panels 37, 38 to match the passage of the < RTI ID = 0.0 >

The web sensor 350 is mounted on a rectangular suspension rod 351 held from the printing side of the web 11 over the nip between the printing roller 61 and the pressure roller 66. Rod 351 has ends 352 and 353 mounted to respective retaining brackets 354 and 355. The end 352 of the rod 351 is threadedly disposed on an axial positioning knob 356 that is captured and freely rotated in a hole formed through one end of the bracket 355. The rectangular cross section of the other end 353 of the rod 351 is oblique along each edge. Each adjustment plate 360 is fixed to the shear shaft of the bracket 355 by bolts 361. The bolt 361 is disposed through the exact semicircular slot 362 formed in the plate 360 and fitted to the bracket 355. The plate 360 has a rectangular hole 363 formed in alignment with the circular hole 356. The rod 351 of the square cross section is sized to fit through the hole 363, and the edge end 353 is obliquely arranged to be arranged through the circular hole 356. The other ends of the brackets 354 and 355 are fixed to the second supporting rods 367 having a circular cross section by fixing screws 366. Brackets 354 and 355 are positioned sufficiently spaced laterally along rod 367 and supported by rectangular rods 351 which are sufficiently far from circular rods 367 to allow passage of web 11 therein. The rod 367 is normally held vertically from the upper line edge of the vertical support panels 37, 38 by the support brackets 368, 369. The rear end of the rod 367 can be disposed in a hole and slide in a hole formed in the upper end of the bracket 369. The brackets 354 and 355 are disposed along the rods 367 between the brackets 368 and 369. One end of the pin 370 is fixed relative to the bracket 368 parallel to the bottom line of the rod 367. Pin 370 is slidably received in a hole formed through one end of bracket 371. The other end of the bracket 371 is fixed by a set screw 372 with respect to the rod 367. The bracket 371 prevents the rod 367 from rotating about its central longitudinal axis. Rod 351 and web sensor 350 remain suspended over web 11.

The wed sensor 350 mounts a rectangular channel bracket 358 mounted to the rectangular rod 351 with a fixing screw 359. The set screw 359 is loosened to allow maximum adjustment of the transverse position of the web sensor 350 along the length of the rod 351. Fine adjustment of the lateral position of the web sensor 350 relative to the web 11 can be achieved manually by rotating the knob 356, thereby moving the rod 351 laterally. Each direction of the web sensor 350 relative to the web 11 can be adjusted by loosening the bolt 361 and rotating the rod 351. Rod 351 is rotated, plate 360 is similarly rotated, and slot 362 is moved by bolt 361 until the desired sensor orientation is obtained. Bolt 361 is tightened to secure web sensor 350 in place. When the image is printed on the opposite side of the web 11, i.e. on the support side (see the last print station 13n in FIG. 1), the rod 351 must be repositioned at the bottom line from the rod 367. This can be accomplished by loosening the set screw 366 to reposition the rod 351 and rocking the brackets 354 and 355 around the rod 367. The sensor bracket 358 is then removed and repositioned toward the top line. Each direction of the web sensor 350 relative to the web 11 is readjusted in the same manner as described previously (comparison of the solid and imaginary lines in FIG. 2).

Before performing automatic matching, any parameter is set if no default setting is required. The setting of parameters for matching is accomplished from the operator's point of view in the same way as the positioning procedure described above is made. The setting is initialized by the operator pressing a button on the panel 411 to select the setting to be made. When the controller 407 is operated, all values are zero or any reference default value programmed in the nonvolatile memory 463, which is an electrically erasable pyrom (EEPROM), reprogrammable only by inspection personnel. And is read by the operator.

To make a setting that affects the operation of the automatic registration, the operator can press the SET DEAD ZONE button 411g, for example. The dead zone is a variable that defines a matching error for both circumferential and axial matching. The described embodiments provide the same settings available for both circumferential and axial registration, and individual settings can be provided. As shown in the flowchart of FIG. 27G, when the SET DEAD ZONE button is pressed, the PAL interface 451 memory variable 452g is set to one. From this variable setting, the program recognizes the button pressed after the inquiry of the PAL memory 452 by the subroutine of FIG. 27G when the button was last called by the button pressing routine of FIG. 27E. This initializes the SET DEAD ZONE routine described in FIG. 27L.

As illustrated in FIG. 27L, when the SET DEAD ZONE button is recognized, the SET DEAD ZONE input point of the routine is that the pressing of this button is SET DEAD ZONE. Recorded to check to determine if it is the second of two consecutive presses of the button. On the first press of button 411g, the deadband setting function is selected so that the ADJUST DEAD ZONE input point is called by the dial pulse interrupt processing routine of FIG. 27C. Is selected as. The BUTTON PRESS routine returns to the call point in the main program to handle any match control operation in progress. Then, at 1/50 second time-out, the BUTTON PRESS routine calls the display subroutine of FIG. 27F indicating that the SET DEAD ZONE is selected, and line 1 of the LED 413a. Cues the current DEZ ZONE value for C, and cues a new setting (NEW SETTING) to default to the current value on line 2 of LED 413b.

The dead zone value represents an integer number of stepper motor pulses in which the dead zone size is defined, and is equal to 1 / 20,000 times the pressure roller circumference. For example, if the circumference is equal to 16.5 inches (74.9 cm), each pulse represents 0.825 mils (ie, 0.000825 inches or 0.00210 cm). The deadband setting is the minimum error in the pulses necessary to make the correction, and very small errors are ignored. Optionally, the DEAD ZONE value may be displayed and increased as some value representing the length, expressed in inches or centimeters, of the web described below with the REPEAT LENGTH and INSPECTION ZONE. have.

To change the setting from the initial value, the operator rotates the dial 415 which generates a pulse. These pulses detect the direction of rotation of the dial and initiate the intervention of the interrupt processing routine of FIG. 27C which initially increases the coefficient to zero, up or down as the dial 415 rotates. The interrupt routine then calls the ADJUST DEAD ZONE routine of FIG. 27L which adjusts the value for the previous setting to define the new setting value.

On the next 1/50 second time-out, display 413b will display one for each click of the dial corresponding to an increase or decrease of one pulse to the DEAD ZONE value above the current setting shown on display 413a. The value is updated to the value of the new setting increased by the digit. When the appropriate dead zone is selected, the operator presses the button 411g again. This second button press is detected in the same way as the first at the next 1/50 second time-out. The second successive press of the button 411g causes the SET DEAD ZONE of FIG. 27L to replace the new setting with the previous current setting of the dead zone in the volatile memory 464. Is detected. The next time the press stops, this value is written into variable 460c in nonvolatile memory.

As a DEAD ZONE setting, the operator in some cases inspects and resets the INSPECTION ZONE window. The inspection zone window is the number of pulses before and after one repetition length from a previous detection coefficient that identifies the position of the web mark 350a while the sensor 350 is operating. Providing selective operation of the sensor 350 allows printing outside the inspection area window on the web 11 with the sensor 350. Preferably, the inspection window limitation is not used when there is no need to print in the line of web mark 350a. This is done by setting the test zero to zero, which is the default setting. The operator sets the inspection area value by pressing the SET INSPECTION ZONE button 411i. As shown in the flowchart of FIG. 27G, when the SET INSPECTION ZONE button is pressed, the program confirms the button and initializes the SET INSPECTION ZONE routine shown in FIG. 27K. In some cases, if not the default test area value, the preset test area value is initially loaded by the microprocessor 450 from the memory variable 460b that is presented to the operator on the display 413a and the initial display 413b. do. The displayed number may be expressed in inches or centimeters. The adjustment routine also displays the value indicated by, for example, a quarter inch increment or a pre-programmed increment stored in memory 463 forming a new setting shown on display 413b. Is set to an inspection area adjustment (ADJUST INSPECTION ZONE) to be called by the dial interrupt routine of FIG. 27C executed when the operator rotates the dial 415. When the inspection area window size is selected and the operator presses the button 411i again, the new setting value is a variable in the memory 464 which will be written as a variable 460c in the nonvolatile memory unless it is changed further when the printer is stopped. Is remembered.

The operator can choose to change the gain setting. This is a setting that controls the amount of detected matching error that has been corrected. Further, the operator selects the gain setting button 411j. As shown in the flow chart of FIG. 27G, when the gain setting button is pressed, the microprocessor 450 recognizes the button and initializes the gain gain routine shown in FIG. 27J. For example, in the absence of a default gain setting of 5 (which indicates a value of 0.5 or 1/2 of error correction), the pre-set gain value is stored by the microprocessor 450 in the volatile memory 464 by the nonvolatile memory variable. Initially loaded from 460e and shown to the operator on display 413a, when the display routine of FIG. 27F is executed with the next 1/50 second time-out by the main loop program of FIG. 27, on display 413b. It is initialized. The gain value is the logarithmic scale indicated by the programmer. Where 1 is evil 10 percent error correction, 9 is 100 percent error correction, and numbers 2 to 8 specify the percentage in between. To change the setting from the initial value, the operator rotates the dial 415 and the display routine of FIG. 23F increases up or down for each click of the dial in an amount corresponding to each percentage increase or decrease in gain setting. In order to update the adjustment value and new setting (NEW SETTING) queued by the display 413b, the interrupt routine of FIG. 27C executes the gain adjustment (ADJUST GAIN) subroutine of FIG. 27J. As illustrated in FIG. 27J, the integers 1 to 9 are indicated. Optionally this is converted to a percentage for display. When the appropriate gain reached by the operator rotating the dial 415 is selected, the operator presses the button 411j to reload the new value into the volatile memory 464 and is set accordingly. As in other settings, in gain setting, the second button press does not release the setup routine. Thus, the operator can observe the performance of the printing press after the setting effect is effected by the second continuous button presses, and the dial 415 can be moved to make further adjustments which can be effectively made by the third push button 411j. Can be.

The SET REPEAT LENGTH function is the same as the result described with respect to the positioning control when the matching controller 407 operated in the above-described setting manner is used. However, the repeat length setting is not usually necessary when the printer is running. If the station 13 is moved on the line when the printing press, which can be done with the current printing press 10, is started, the repeat length REPEAT LENGTH can be set, and the printing roller 61 can be changed so that the printing press Can be matched without stopping.

The REPEAT LENGTH setting specifies the circumference of the print roller 61 rather than the length of the actual image printed on the web 11, which may be one or more per print roller rotation. In the case where one or more plates 62 must be positioned on the circumference of the printing roller 61 or one or more web mark supporting images are to be spaced around the plate, the release button 411k is the number of images per rotation of the printing roller. Is provided to the match control panel 411 to assist the operator in entering. The repeat length REPEAT LENGTH is stored in memory location 460a, which may be coupled to memory location 440a (see FIG. 24) of positioning controller 408.

In particular, the operator may change the number of repeats to specify the number of images per rotation of the printing roller. This may be equal to the number of individual plates 62 spaced around the circumferential direction of the printing roller 61. This setting is used when each of the images typically includes a registration mark 350a printed at the first station. In such a situation, the repetition length (REPEAT LENGTH) of the print roll in the calculation made by the registration control routine is divided by the number of repetitions. However, multiple images are formed on a single plate only when a single web mark is printed by multiple image plates, and the NUMBER OF REPEATS is set to one. Therefore, NUMBER OF REPEATS is actually the number of web marks 350a per revolution of the printing roller 61. This number is a positive integer from 1 to 9. The microprocessor 450 divides the REPEAT LENGTH setting, specified as a pulse, from the encoder 344 by an integer number of REPEATS. The parameter setting function is selected by the operator pressing the SET NUMBER OF REPEATS button 411h.

As shown in the flow chart of FIG. 27G, when the button 411h is pressed, the microprocessor 450 recognizes the button and initializes the SET NUMBER OF REPEATS routine shown in FIG. 27S. If the default setting is 1 and not, the preset number is loaded by the microprocessor 450 from the memory variable 460d, and the printer is started from the memory 464, so if the number is updated, the display ( Displayed to the operator on 413a) and initialized on display 413b. To change the setting from the initial value, the operator rotates the dial 415 where the interrupt routine of FIG. 27C queues the display 413b to increment up or down by one integer for a dial click. When the appropriate number of iterations is selected, the operator presses button 411h again to load a new setting into memory 464 which will later be stored in nonvolatile memory variable 440d when the printer is stopped. The change in NUMBER OF REPEATS occurs in an environment similar to the change in the REPEAT LENGTH setting described above.

The operator can choose to set or change the LINEAL ERROR AVERAGING setting. The setting can be zero to stop linear averaging, or a nonzero amount of less than 30 that controls the number of the most recent continuous circumferential match error measurements that the current match error measurement is averaged when the correction amount is based. It may be an integer. When the number is set at each read, the oldest read is ignored and the current one is added to drive the calibration made during the execution of the automatic linear match. Preferably, a linear or other statistical curve approximation technique is used rather than a simple geometric mean. The selected values are read and stored in the memory 464, respectively. The setting is made by the operator pressing the SET LINEAL AVERAGE button 411l. As shown in the flow chart of FIG. 27G, when the SET LINEAL AVERAGE button is pressed, the microprocessor recognizes the button and initializes the SET LINEAL AVERAGE routine shown in FIG. 27N. do. If the default setting is 1 and otherwise, the preset linear error mean value is initially loaded by the microprocessor 450 from the memory variable 460f, and the memory variable is displayed on the display 413a and by the operator. Initially displayed on display 413b. In order to change the setting from the initial value, when the operator rotates the dial 415, the interrupt routine of FIG. The error will be averaged up and down by the count of each click of the dial. When the appropriate number is selected, the operator sets again by pushing button 411 l to load a new value into memory 464. When the printer stops, the value will be stored in the variable 460f of the nonvolatile memory.

In order to perform the matching automatically, it is necessary for the operator to define the desired match. This is accomplished by driving the printer 10 very slowly and examining the printed product by adjusting the linear registration in the passive linear registration mode. Automatic linear matching is turned off when the printer is driven so that no linear matching is selected, which mode is selected by pressing only the LINEAL REGISTRATION button 411a. If automatic linear matching is ON, it must be OFF by pressing the LINEAL REGISTRATION button 411a and the MANUAL button 411d. The MANUAL routine allows the operator to roughly set the match. As shown in FIG. 27U, the click of the dial 415 causes the pulse to be sent to the stepper motor 327 of the harmonic driver 275 when the passive linear matching mode is activated. When the operator is satisfied with the registration, the next mark (NEXT MARK) button 411f is pressed, which causes the next mark (NEXT MARK) to be selected to execute the next routine of FIG. 27G. Once selected, the MAIN loop program of FIG. 27 is next executed, and the routine of FIG. 27D is called to set the LINEAL REG. And the circumferential match is set, and the current coefficient difference is It is calculated by subtracting the ROLL MARK coefficient from the WEB MARK coefficient. This establishes the circumferential registration maintained when LINEAL REGISTRATION is run in automatic mode.

In particular, the routine of FIG. 27D, which is called when the NEXT MARK button is pressed, indicates that the signal from the sensor 347 indicates the passage of the leading edge of the printing roller mark 349 and starts the interrupt routine of FIG. 27A. Generates a roll mark (ROLL MARK), which is a count from the pressure roll counter 453, which is read when subtracted from the web mark, where a pulse from the sensor 350 detects the first front edge of the web mark 350a. And the count from the press roll counter 453 read out at the start of the interrupt routine of FIG. 27B.

As shown from the MAIN LOOP flow chart of FIG. 27, the web is moved and the ROLL MARK and WEB MARK are read out, and the LINEAL REGISTRATION routine of the flow chart of FIG. Is executed. At run time, a survey window is set, and the microprocessor 450 has a difference between the WEB MARK and ROLL MARK coefficients (DIFFERENCE) of the LINEAR REG. Determines whether it is within +0.5 or -0.5 of). The microprocessor 450 is also inspected to investigate the difference in DIFFERENCE, which occurs when noise is read as a web mark or when paper tear or split occurs. In that case, the first "shift" of the read is stored and checked for the next read to see if the read repetition changes. If LINEAL AVERAGING is turned on, the error determined by subtracting the DIFFERENCE from the LINEAL REG. Value is a number of past error measurements equal to the LINEAL AVERAGING setting. Is averaged.

If the coarse match setting is performed in the MANUAL mode, the operator proceeds to the automatic mode to precisely set the match. This is a print drive mode in which the circumferential registration is continuously and automatically corrected.

In order to position the machine in the automatic circumferential matching mode, the operator presses the AUTO button 411a, which is coupled with the LINEAL REGISTRATION button 411c, which causes the button check routine of FIG. (AUTO LINEAL) Set the matching mode to ON. This is because the LINEAL REGISTRATION routine in FIG. 27H, called for MAIN LOOP, multiplies the number of pulses calculated by multiplying the error (ERROR) or average error (GAIN) by gain (GAIN). Send to driver 275.

The automatic linear registration mode allows the print roller 61 oriented relative to the web 11 so that pulses from the sensors 347 and 350 can be separated by the number of pulses stored in the LINEAL REGISTRATION variable 460h. In this mode, precise tuning of the LINEAL REGISTRATION setting can be achieved by the operator rotating the dial 415. This causes the interrupt routine of FIG. 27C to call the ADJUST LINEAL REGISTRATION routine of FIG. 27U. This has the effect of immediately increasing or decreasing the value of LINEAL REGISTRATION of volatile memory other than the value stored in nonvolatile memory variable 460h. The value of LINEAL REGISTRATION can be flagged to be stored permanently, and then the printer is stopped by pressing the NEXT MARK button 411f. The change in LINEAL REGISTRATION causes an error to be calculated for the new value and then the LINEAL REGISTRATION routine in FIG. 27H is executed.

When automatic circumferential matching is executed, the program routine of FIG. 27H is executed each time the MAIN LOOP is executed, and an error (ERROR) is sent to the stepper motor 327 of the harmonic driver 275 in the form of a pulse stream. Lose. If LINEAL AVERAGE is selected, the error ERROR is averaged to the number of past measurements indicated by the setting of LINEAL AVERAGE as described above. If the calculated linear error ERROR is smaller than the dead zone setting stored in the variable 460c, no pulse is sent to the harmonic driver 275. If the error is greater than the DEAD ZONE setting, the error is determined according to the gain GAIN (by multiplying the error by one-ninth of the gain of 1-9) and the determined error is a pulsed harmonic driver 275. Is sent).

The choice of LINEAL REGISTRATION allows the operator to adjust the circumferential match whether only linear or linear and lateral match are currently driven with automatic matching.

To stop the automatic circumferential registration, the operator presses the MANUAL button and then the LINEAL REGISTER button.

Axial registration

When the axial registration mechanism 330 (see FIG. 17) is operated to correct the axial registration between the web 11 and the printing plate 62, the web sensor 350 moves the printing roller 61. It needs to be moved accordingly. That is, for axial registration, the axial position of the printing roller 61 is directly related to the mark 350a on the web 11. In the circumferential registration described above, the printing roller 61 for the mark 350a on the web 11; That is, the relative circumferential position of the mark 349 is indirectly measured by measuring the sensors 347 and 350 fixed to the frame 36. To achieve axial or lateral registration, the base platform 48 is mechanically connected to the rod 367 so that the rod 367 and the web sensor are moved when the platform 48 is moved by the axial adjustment mechanism 330. 350 is moved in the same direction (see FIG. 18). The mechanical connection can be achieved by securing the vertical bracket 375 to the stop plate 58 of the base platform 48. The upper end of the bracket 375 mounts a screw sleeve 376 with a threaded rod 377 disposed thereon. Threaded rod 377 is generally oriented coaxially with rod 367. The magnet 378 is fixed to the free end of the rod 377 and engageable with the front end of the rod 367. The relative position between the web sensor 350 and the base platform 48 can be further adjusted by adjusting the depth of the rod 377 of the sleeve 376. If the desired depth is obtained, a locking nut 379 disposed along the rod 377 may be tightened with respect to the sleeve 376 to fix the relative position.

Thus, a magnet 378 is attached to the end of the rod 367, and the base platform 48 by the axial adjustment mechanism 330; That is, the lateral movement of the printing roller 61 generates the same lateral movement of the web sensor 350 relative to the web 11. As described above, when the base platform 48 is moved to a position laterally away from the operating position (see FIG. 4) (see FIG. 5), the bracket 354 is moved laterally so that the bracket ( Magnet 378 and rod when in contact with 368, stopping the transverse movement of rod 367, and moving the bracket 375 continuously laterally with platform 48 to a laterally separated position. Let the magnetic coupling between 367 be separated. When the relative position between the screw rod 377 and the vertical bracket 375 is fixed by the locking nut 379, the base platform 48 returns to the operating position and the magnet 278 reconnects with the rod 367. Connected to the base platform 48; The relative position between the printing roller 61] and the web sensor 350 is set again.

The web mark 350a has two rods 385 and 386 horizontally aligned with a diagonal rod 387 and axially spaced apart. The middle diagonal rod 387 is located at about 45 ° angle from the transverse rods 385 and 386. When matching the leading edge of the transverse rod 385 introduced by the web sensor 350, a counter is established in memory so that the pulse from the encoder 344 is the leading edge of the diagonal rod 387 being the sensor 350. It counts upwards from 0 until it is matched by. The counter is then counted downward until the leading edge of the end transverse rod 386 is mated. If the end transverse rods 386 are mated before the counter is counted down to zero, the computer of the appropriate station to perform an axial mating correction checks if there is an axial mating error in one transverse direction. You will know if it works.

The means of axial matching are connected with the circumferential matching and the setting of the factors described above is required. These are the DEAD ZONE and GAIN factors and the INSPECTION ZONE factor which functions in the same way as the circumferential matching. If the irradiation area window is used, that is, set to nonzero, the repeat length and the number of repeats are related to the axial registration. This is because the web mark 350a read by axial registration is the same mark as the mark read by circumferential registration. These are set as described above. In addition, LATERAL AVERAGING is set. The lateral averaging function performs the averaging of the set number of past measurements and the current axial error in such a way that it can perform the averaging of the circumferential errors described above.

The LATERAL AVERAGING setting is set by pressing the SET LATERAL AVERAGING button 411m. As shown in FIG. 27G, this executes the SET LATERAL AVERAGING routine shown in FIG. 27P. The setting can be zero and this can be a lateral mean of zero or a non-zero positive integer less than or equal to 30, which is the most recent continuous axial match error measurement averaged with the current measurement being made. Control the number of, and the amount of correction is the basis. When the number is set, the entire driving of the last five axial errors of the axial error is stored in the memory. In each successive error measurement, the oldest reading is ignored, the current one is added to the whole, and then divided by 5 to make the correction. For linear means, linear or other statistical curve approximation techniques are used more than simple arithmetic means. The selected number of values is stored in the temporary variable memory 464, respectively.

The setting is made by the operator pressing the SET LATERAL AVERAGE button 411m of the set. As shown in the flow chart of Figure 27G, when the SET LATERAL AVERAGE button is pressed, the program recognizes the button and executes the SET LATERAL AVERAGE routine as shown in Figure 27P. Instruct. If the button is a different button than the previously pressed button, the routine selects LATERAL AVERAGING and the side as an adjustment subroutine to be called by the interrupt handling routine of FIG. 27C responding to a pulse from the operator adjustment dial 415. Select the ADJUST LATERAL AVERAGING routine.

Once LATERAL AVERAGING is selected, the button pressing routine of FIG. 27F is executed, and the DISPLAY LATERAL AVERAGE routine of FIG. 27P is executed, which examines the preset lateral error averaging setting. . The setting of 0 to indicate LATERAL AVERAGING is stopped. The investigated or default value is queued on line 1 of display 413a and initially queued on line 2 of display 413b. To change the setting from the initial value, the operator rotates the dial 415. The pulse from the dial is interrupted by the interrupt routine of FIG. 27C, which calls the adjustment subroutine of LATERAL AVERAGING. Then, the display routine (FIG. 27F) is executed, and the new setting is displayed on the display 413b and increased by the net pulse accumulated from the dial 415. When the appropriate number is selected, the operator presses the button 411m again. This is the routine of FIG. 27G, and causes the SET LATERAL AVERAGING routine of FIG. 27P to be executed. This recognizes the second consecutive button press of the button 411m and sets the LATERAL AVERAGE number to NEW SETTING. The setting is stored in the nonvolatile memory variable 460g when the printer is stopped.

In order to perform the axial registration automatically, the operator needs to define the desired lateral registration. The LATERAL REGISTRATION is the difference in the pressure roll decoder pulse coefficients between the diagonal rod of the web mark 350a and the leading and distal transverse portions of the web mark. This setting is accomplished by slowly driving the printer 10 to examine the printed product and to adjust the lateral registration in the passive lateral registration mode. If the printer is driven, automatic lateral registration is OFF and no lateral registration is selected, the mode is selected by pressing the LATERAL REGISTRATION button 411b. When automatic linear matching is ON, it is turned off by pressing the LINEAL REGISTRATION button 411b and the MANUAL button 411d. The MANUAL routine allows the operator to roughly set the match. As shown in FIG. 27V, the rotation of the dial 415 causes a pulse to be sent directly to the lateral stepper motor 340 when passive lateral matching is activated. When the operator is satisfied with the registration, the NEXT MARK button 411f is pressed and the value of the variable LATERAL REG. Is stored in the volatile memory, which is not lit when the printer is next stopped. It is stored as the volatile memory variable 460i. LATERAL REG. Is a lateral match that can be maintained when the lateral match is driven in AUTO mode.

As shown in the MAIN LOOP flow chart of FIG. 27, when the web is moved and the ROLL MARK and WEB MARK are read, the LINEAL REGISTRATION routine of the flow chart of FIG. 27H is read. Is executed. After execution, the complete Z-mark is read and the LATERAL REGISTRATION routine of FIG. 27I is executed. The routine calculates a LATERAL ERROR. If the LATERAL AVERAGING function is selected, it is averaged with the previous error measurement.

After the coarse lateral match setting is made in the MANUAL mode, the operator proceeds to the automatic mode to precisely set the match. This is a print drive mode in which axial registration is continuously and automatically corrected.

In order to place the machine in the automatic axial registration mode, the operator presses the AUTO button 411a together with the LATERAL REGISTRATION button 411d, which means that the AUTO LATERAL registration mode is It is a button inspection routine of FIG. 27G for setting to ON. This causes the LATERAL REGISTRATION routine of FIG. 27I, then multiplies the error (ERROR) or average error (AVERAGED ERROR) by the gain (GAIN), and calculates the number of pulses calculated by the stepper motor 340. Called by MAIN LOOP to transmit. The automatic lateral registration mode is a run mode, which is an axial registration characterized by automatically calibrating the printing roller 61 at the transverse position relative to the web 11, and thus from the LATERAL ERROR. Is equal to LATERAL REGISTRATION. In this mode, fine movement of the LATERAL REGISTRATION setting can be achieved by the operator rotating the dial 415. This causes the interrupt routine of FIG. 27C to call the ADJUST LATERAL REGISTRATION routine of FIG. 27V. This immediately increases or decreases the value of LATERAL REGISTRATION in volatile memory other than the value stored in nonvolatile memory 460h. The value of the lateral registration can be flagged to be stored permanently, and the printer is stopped by pressing the next NEXT MARK button 411f. The change in LATERAL REGISTRATION causes a LATERAL ERROR to be calculated for the new value, and the LATERAL REGISTRATION routine of FIG. 27I is executed.

When the automatic axial matching is driven, the program routine of FIG. 27I is executed whenever the MAIN LOOP is looped as described above, and a LATERAL ERROR is generated for the stepper motor 340. It is sent in the form of a stream of pulses. If LATERAL AVERAGING is selected, the LATERAL ERROR is averaged to the number of past measurements indicated by the setting of LATERAL AVERAGE as described above. If the calculated lateral error ERROR is smaller than the dead zone setting stored in 460c, no pulse is sent to the stepper motor 340. If the lateral error is greater than the DEAD ZONE setting, the LATERAL ERROR multiplies the error ERROR by 1/9 of the gain GAIN [gains 1 to 9]. The lateral error is sent to the stepper motor 340 as a pulse.

When lateral or linear and lateral matching is activated with automatic matching enabled, the choice of lateral matching allows the operator to adjust the axial matching.

To stop automatic axial registration, the operator presses the MANUAL button and then the LATERAL REGISTER button.

Unlike the circumferential registration feature in which the direction of the printing roller mark 249 and the position of the web mark 350a are detected with respect to a fixed frame with two sensors 347 and 350, the axial registration is measured by the sensor 350. It is mounted so as to move in the lateral direction with the printing roller 61 when the lateral registration adjustment takes place. The transverse position of the roller 61 relative to the web 11 is measured by interpreting the position of the sensor 350 relative to the asymmetric web mark 350a. This is shown in FIG.

Referring to FIG. 21, web mark 350a is shown on web 11, and arrow 350b is on web 11 when the web is moved opposite to the direction indicated by arrow 11a. The relative direction of movement of the sensor 350 to FIG. As the printing roller 61 is adjusted in the axial direction, it is moved transversely with respect to the web 11 and the mark 350a, and the position of the scan line 350b is similarly moved with respect to the mark 350a. In FIG. 21, scan line 350b is shown in a well adjusted position at the center of mark 350a. This position preferably prevents the sensor 350 from deviating from the side of the mark 350a when the printing roller 61 is not engaged, which reduces the loss of axial registration control. The position is mechanically set by positioning the sensor 350 at the mounting site in relation to the preliminary mating characteristics described above.

When centered at a position across the mark 350a of the scan line 350b, the sensor 350 will first detect the leading edge of the leading transverse rod 385 of the mark 350a. This is the position of the WEB MARK and is used for circumferential registration. Since the rod 385 is a lateral web 11, it is not affected by the axial registration adjustment. In addition to the WEB MARK, the configuration of the counter 453a when the leading edge of the diagonal rod 387 is detected by the sensor 350 is stored as the variable WEB MARK 2. It is also additionally stored as a variable web mark 3 when the sensor encounters the leading edge of the transverse rod 386. The microprocessor 350 calculates the ratio of the difference between successive leading edges by dividing {web mark-web mark 2} by {web mark 2-web mark 3} and then converting it to the same axial error pulse coefficient. do. However, the difference between the pulse configuration between the pair of marks, namely {web mark-web mark 2} and {web mark 2-web mark 3}, is subtracted. Thereafter, LATERAL REG. Adjustment is also subtracted. The difference is used to define an axial error or LATERAL ERROR, i.e. {web mark-web mark 2}-{web mark 2-web mark 3}.

The calculation of the LATERAL ERROR counts the pulses from the encoder 344 on the pressure roller 66 which starts the detection of the web mark, and detects the detection of the web mark 2. This can be done simply by reversing the starting coefficient, i.e. by subtracting the pulse and ending the detection of WEB MARK 3. The remaining coefficients can then be taken as difference values.

Before selecting the AUTO-LATERAL REGISTER, if the operator presses the auto register and side register buttons to initiate automatic circumferential matching, linear matching is performed every cycle even if lateral auto matching is currently selected. Run or repeat length. Lateral registration selection allows the operator to adjust the axial registration with automatic matching performed and lateral matching or linear and lateral matching performed automatically.

To end the automatic axial registration, the operator must press the manual register and lateral register buttons.

With circumferential and axial registration adjustments, stepper motors 327 and 340 pulse under the control of microprocessor 450 at a high rate at which the stepper motor can respond.

Computer Controlled Reinsertion Compensation

In accordance with the principles of the present invention, computer-controlled matching, in particular circumferential matching, is provided with a special reinsertion feather for situations in which the web 11 repeats a printing run. Often other types of printing presses (eg, operating web 11 through one form of printing press 10 (eg flexographic), removing webs 11 from printing press 10 and receiving intermediate print jobs For example, it is desirable to insert the web 11 through a flexographic press 10 for another printing run. When the web 11 is subjected to such repeated printing execution, the web 11 is likely to cause dimensional changes such as stretching or shrinking. These dimensional changes are uniform along the length of the web 11, but these dimensional changes are likely to change along the length of the web 11.

In addition, such dimensional change may occur when no intermediate printing operation is performed. It is also easy to memorize the web 11 in roll form between printing runs to the same printer 10, which can lead to similar twisting of the web 11 by changing the weight of the web and other atmospheric factors. As the dimensions of the web change, the preprinted image on the operating area of the web 11 changes. When a new image is printed on the already printed web 11, the reinsert element makes a correction for the dimensional change of the web 11 and therefore a correction of the dimensional change of the old composite image printed during the previous run is made. As a result, new images printed during continuous execution are closer to the circumferential registration of the old composite image. When the web 11 (old composite image) is stretched or shrunk, the distance between the continuous web marks 350a is also stretched or shrunk.

The computer controlled reinsertion element can recognize the change in web mark in web mark distance relative to the original repeat length. The original repeat length generally refers to the repeat length of the plate on the printing press 10 in which the web 11 is inserted. Computer-controlled reinsertion control can control the printer 10 by changing the shape of the new image, thereby compensating for the change in shape of the old composite image due to the torsion of the web 11.

The shape of the new image is changed by changing the rotational speed of the printing roller 61 which is rotated relative to the moving speed of the web 11 (ie, the length is increased or decreased). The rotation of the printing roller 61 is slowed to lengthen or stretch the new image, and speeds up to shorten or shrink the new image. If this reinsertion element helps to compensate for dimensional changes in the old composite image (i.e., the web is printed and removed and reinserted into the printer 10), then this insertion element is generally not needed and the web 11 May be used in some circumstances, even if the initial printing execution is performed through the printer 10. The reinsertion control may unnecessarily introduce other variables if the dimensional change of the web 11 during the first run is nearly constant over the entire length of the web 11. Accordingly, the present invention provides for the selective enabling and disabling of reinsertion control, the constant monitoring of reinsertion errors and the adjustment of the operation of the reinsertion control between print response and setting and during printing.

With the computer controlled reinsertion element of the present invention, the originally printed web mark 350a is reused during continuous execution through the printer 10. The computer-controlled matching described above is also provided with additional parameter settings that are used to influence what is used herein by reference as a constant error correction in the matching control described above. The constant error correction element operates to analyze error corrections made over the current number of repetition lengths and to predict certain components of the overall correction to be made. Then, a constant error correction is made at the next iteration length before the circumferential match error measurement. Otherwise the error correction made in the circumferential match will be made based on the measurements already corrected by the constant correction element, and then the circumferential match correction is added to the constant error correction.

Effective constant error correction varies with the actual repeat length of the web 11 (ie, the actual distance between the continuous web marks 350a originally printed on the web 11). The actual repetition length is not equal to the repetition length that the printing press 10 is subjected to due to the dimensional change of the web 11 after the original printing. With the insertion element and its error correction facility, compensation is made for the dimensional change of the actual repeat length. This change is made by slightly changing the rotational speed of the printing roller 61 and by evenly distributing the calibration pulses at intervals equal to the period necessary to make a constant error correction over each actual repetition length of the web 11. "Constant" error correction means that the intended correction is not constant over all repetition lengths, but rather that each repetition length is periodically reevaluated and adjusted.

The installation of the reinsertion element requires the setting of the variables described above in conjunction with the match, and in addition to the number of repeat lengths over which the error is analyzed for the calculation of constant error correction, by means of averages, error suppression analysis or other statistical methods, or CEC average is required. The CEC error suppression number is the number of repeat lengths in which an error is analyzed to expect a constant error correction to be made at a particular station 13 when the next repeat length is printed. The calibration need not be identical at each station, but can be based on an independent analysis at each station 13 or at a host computer 400 that can take into account data from each matching computer 450 and reinsert The number may vary from 1 to 29 in the embodiments described above.

The linear suppression method of this embodiment best fits a straight line to the error value point as a function of continuous measurement and establishes a trend to extrapolate or predict the error value for the next measurement. The best-fit statistical method may be, for example, a least squares method that derives a line that minimizes the sum of the squares of the distances of each point in the line.

Performed alone at an individual station 13, microprocessor 450 will independently collect data based on locally made measurements at that station. In this way, the torsion of the web, which may occur during the current printing operation, will be considered independently at each station 13. In addition, it is noted that the CEC error varies along the length of the web 11, for example 50 or 100 feet. For a twelve station press, the amount of web 11 passing through the press 10 from the first station 13a to the last station 13n is 400 or 500 feet. Thus, the calibration to be made at station 13a will be different from the calibration to be made at station 13n and station 13 between them.

The interaction between the individual microprocessor 450 and the host computer 400 provides a particular advantage with reinsert control. The dimensional change occurring in the web 11 as a function of the length of the web 11 proceeds progressively through the station 13 as the web 11 advances through the printing press 10. Thus, errors due to web twist occurring during reinsertion into the printer 10 are first detected at the first station 13a and then at station 13b and through the stations 13 to the last station. It proceeds to 13n and is detected. By communication between the host computer 400 and the individual computer 450, the data read at the upper station, such as the station 13a, can be beneficial in predicting a "constant" error, which correction of the error Can be made at a downstream station such as 13n.

In order to use a CEC element, a CEC suppression number must be set, and this setting is accomplished by pressing the CEC AVERAGING button 411o. As shown in Fig. 27G, the detection of the button by the button printing press routine results in the execution of the CEC AVERAGING routine shown in Fig. 27W. This allows you to select the CEC AVERAGING function and set the ADJUST CEC AVERAGING as the adjustment subroutine for the dial pulse interrupt routine of FIG. 27C. Next, at the next execution of the display routine of FIG. 27F, the DISPLAY CEC AVERAGING routine of FIG. 27W is activated, which is presently present on line 1 413a and also initially on line 2 413b. Navigate to the CEC average or suppression number setting. The suppression number setting or CEC setting can be one, which implies that reinsertion correction or constant error correction is stopped, which means that the reinsertion of the preprinted web 11 is not made in the setting of the print operation and the web is This is a good setting when (11) is printed first. If set to an integer greater than 1 and less than 30, the CEC setting analyzes the number of the most recent successive match error measurements and controls to reach a constant error correction that should be imposed on the next cycle. In the illustrated embodiment, the CEC is performed with respect to circumferential matching.

In general, CEC devices are used when errors can be predicted based on prior error measurements or when the next error is more likely to change from the prior error than the absolute value. The CEC function performs another inhibition analysis with each measurement over a cumulative average or past number of measurements set by the CEC. In each successive error measurement, the oldest reading is ignored and the current is considered as the whole. Preferably, a linear or other statistical curve approximation technique is used rather than a simple arithmetic mean. The selected number of value reads are each stored in the temporary variable memory 464.

To change the setting from the initial value, the operator rotates the dial 415 and causes the interrupt routine of FIG. 27C to increase or decrease the pulse coefficient and execute the ADJUST CEC AVERAGING subroutine of FIG. 27W. After the display routine (FIG. 27F) is executed, the display 413b is loaded with a new setting, and the new setting is the current setting in line 1 of the display 413a improved by cumulative adjustment. When the proper number is selected by the operator rotating the dial 45, the operator pushes the button 411n again. If the routine of FIG. 27G confirms the button, executes the CEC AVERAGING routine of FIG. 27W again. This detects the second consecutive press of the button and sets the CEC AVERAGING to the NEW SETTING. When the press stops, this is set by loading a new value into variable 460j in nonvolatile memory.

In order to perform constant error correction for the reinsertion application, the operator presses the CEC button 411n together with the AUTO button 411c as shown in FIG. 27G. To stop the CEC, the operator presses the CEC button 411n and the MANUAL button 411d. By pressing the CEC button 411n while printing with a printing press, the operator can see on the display 413 the constant error being measured and the calibration that occurs or is being calculated.

Figure 27H is a subroutine of Figure 27X that includes program steps for constant error correction in the course of automatic matching. In this routine, the analysis consists of past error measurements equivalent to the set suppression number, the oldest memory error is ignored and the most recent error is read as each error. Moreover, as shown in FIG. 27, when the printing press 10 is stopped, the average array AVERAGING ARRAYS is reset. This includes resetting the stored suppression number of the error, including setting a series of measurements to zero or some other error value. This step is caused by stress and other causes of dimensional changes acting on the web 11 during the stop and start of the printing press 10 or by the floating of the web 11 or by possible manual repositioning of the web 11. This is taken because of past error readings of error short justification. The step of erasing the error value may be connected to one of a number of controls of the printer 10 indicative of web floatability.

Additional checks provide a special SPECIAL key, for example a button 411p that can be used in combination with other keys that provide rarely used adjustments or provide functions not normally available to the operator. Can be obtained. In addition, other key combinations may be assigned program code to perform additional functions. Suitably, when the key 411p is pressed alone, it functions as an escape or cancel key, and erases all button press values and adjustment values. This cancel key can also return the selection to an error mode where all selections are canceled, and the display returns to an error selection where linear and axial matching errors are indicated on display lines 413a and 413b.

This special function provided here is a station station setting function (SET STATION ADDRESS) which is selected by pressing button 411p in combination with button 411n. This function is provided for entry of an address so that the microprocessor at station 13 can selectively communicate with host computer 400. This setting is made by the method of the other setting described above, wherein the detection of the button combination is performed by executing the SET STATION ADDRESS routine of FIG. 27T, thereby selecting the station address for the interrupt processing routine of FIG. 27C. Function and the ADJUST STATION ADDRESS subroutine, the second press of the button combination changes the STATION ADDRESS to a NEW SETTING made according to the adjustment of the dial 415.

From the disclosure that discloses the general principles of the invention and the foregoing detailed description, those skilled in the art can readily make various modifications belonging to the invention. Therefore, the spirit of the present invention is limited only by the following claims.

Claims (21)

A plurality of printing stations (13) for printing a composite image along a continuous substrate (11), Advancing means 14 for continuously advancing the continuous substrate through each print station 13 at the selected substrate speed, Each of the print stations 13, (a) a fixed frame 36, (b) printing means 60 comprising a printing element rotatably mounted relative to the frame 36, and (c) drive means 194 for rotating the printing element 61 with respect to the frame 36 at a circumferential speed having a controlled relationship to substrate speed, (d) circumfernential adjustment means (275) for changing the circumferential position of the rotatable printing element relative to the substrate (11), (e) In an automated printing press (10) comprising sensing means (347, 350) and computer control means (405) for controlling the operation of the circumferential adjustment means (275), Each sensing means detects the circumferential position of the printing element 61 of the individual station 13 with respect to the image on the continuous substrate 11 at the respective station and derives a measurement error value according to the position, Each computer control means 405 comprises processor means 408 responsive to a derived measurement error value for calculating a calibration value of an individual station 13, and the station 13 in accordance with the calculated calibration value. To individually control the operation of the circumferential adjustment means 275 of Each of the print stations 13 is adapted to adjust the circumferential position of the circumferential adjustment means 275 to automatically change the circumferential position of the rotatable printing element 61 with respect to the continuous substrate 11 in accordance with the sensing means 347, 350. And a computer controlled circumferential matching means for controlling the operation. The method of claim 1, The processor means 408 in each print station 13 calculates a calibration value corresponding to the individual print station 13 from the storage means for storing a plurality of measurement error values and the measurement error values so stored. An automatic printing machine comprising a calculating means. The method of claim 1, The processor means 408 predicts the error values of the images to be printed at each of the individual print stations 13 and controls the operation of the circumferential adjustment means 275 of the individual print station 13 in accordance with the foreseen error values. And respond to the plurality of derived measurement error values to produce a plurality of distinct control pulses needed to. The method of claim 1, The circumferential adjustment means 275 responds to the distinguished control pulses to gradually change the circumferential position of the rotatable printing element 61 with respect to the substrate position at the print station 13, Computer control means 405 at each of said print stations 13 is responsive to the measurement error value derived at said individual station 13 to generate a number of distinct pulses proportional to said measurement error value. Automatic printing machine made. The method of claim 4, wherein Each image deserves a constant repetition length value, and the computer control means 405 calculates and calculates the interval of the pulses for the next image to be printed from the repetition length value and the number of distinct calibration pulses. And means for generating said distinguished calibration pulses at predetermined intervals. The method of claim 1, Each print station 13 has a gear train 68 comprising a branch 194 of gear means for driving only the rotatable printing element 61, the circumferential adjusting means 275 being rotatable. A dual harmonic gear assembly 275 for changing the rotational speed of the printing element 61 and motor means 327 for operating the dual harmonic gear assembly 275 according to the calculated calibration value and the control means. ), Wherein the dual coordinating gear assembly (275) is part of a branch (194) of the gear means. The method of claim 1, Each station 13 additionally includes a pressure roller 66 rotatable within the frame 36, the pulses of which are each reciprocated through the print station 13 to the length of the continuous substrate 11. The associated digital pulse generating means (344) is connected to the pressure roller (66) at the station (13) to generate a number of pulses for the computer control means (405) when the pressure roller rotates. The method of claim 1, And further comprising first positioning means 78 for positioning the printing means 60 to a predetermined position with respect to the pressing means 66 supporting the continuous base layer 11 in the state where the component image is applied, The pressing means 66 is a printing position which is a position for the printing means 60 to apply at least one component image of the transferable image forming fluid to the continuous substrate 11 at every rotation of the rotatable printing element 61. The printing means 60 has a non-printing position, not a position for applying the component image to the continuous substrate 11, Further comprising computer controlled second positioning means 406 for controlling the operation of the positioning means 78 to automatically position the printing means 60 in and out of the print position and non-print position. Auto printing machine featured. The method of claim 8, The first positioning means comprises a base platform (48) for carrying two first carriages (81, 82) laterally spaced apart, Each of the first carriages 81, 82 is installed to slide along any one of two first slides 83, 84 mounted on both sides of the base platform 48, and the rotatable printing element ( 61 is supported between the first carriages 81 and 82, Each of the first carriages along one of the first slides 83, 84 to move the rotatable printing element 61 to a predetermined position relative to the support surface 67 of the pressing means 66. And a means (190, 191) for sliding 81, 82 independently. The method of claim 9, The second positioning means 406 comprises two second carriages 89, 90 laterally spaced apart, Each of the second carriages 89 and 90 is installed to slide along any one of two second slides 91 and 92, and each of the second slides 91 and 92 is formed of the first carriage. 81, 82), Fluid distributing means (63) supported between the second carriages (89, 90), Independently of each second carriage 89, 90 along one of the second slides 91, 92 to move the fluid dispensing means 63 to a predetermined position relative to the rotatable printing element 61. And a means (170, 171) for sliding to the side. The method of claim 10, The means for sliding each carriage independently is a stepper motor 170, to which pulse means 172 and 192 are connected which generate electronic pulses when the stepper motors 171 and 191 are actuated. 190; an automatic printing machine comprising a stepper motor. The method of claim 11, The second computer-controlled positioning means 406 includes a motor means 191 for gradually moving the printing means 60 in accordance with a digital positioning control signal, and precisely and repeatedly between the printing position and the non-printing position. A microprocessor 430 programmed to actuate the positioning means 78 by generating the positioning control signal to move the printing means 60, wherein the motor means 191 comprises the pressing means ( Automatic control device comprising at least two control signal responsive motors mounted to individually adjust opposite ends of the rotatable printing element (61) with respect to (66). The method of claim 1, Axial adjustment means 330 for simultaneously adjusting within the frame 36 the transverse position of the rotatable printing element 61 and the fluid dispensing means 63 for dispensing the transferable image forming fluid; , The rotatable printing element 61 to correct an axial registration error of the component images applied by the printing means 60, with the continuous substrate 11 running through the print station 13; Operation of the axial adjustment means 330 to move the fluid dispensing means 63 automatically simultaneously in the transverse direction to a desired transverse position between the sides of the frame 36 And a computer control axial registration means (450) for controlling. The method of claim 13, The plurality of print stations 13 includes a first print station 13a and a plurality of subsequent print stations 13b to 13n located downstream of such a first print station 13a and the rotatable print element 61. A web mark having a Z shape having a diagonal rod 387 printed on the continuous substrate 11 at the first printing station 13a and disposed between two transverse rods 385 and 386 at each rotation of ( 350a; a web mark), Each subsequent print station 13b to 13n comprises computer controlled axial mating means comprising sensing means 350 for detecting the transverse drift of the web mark 350a as the continuous substrate 11 travels. Automatic printing machine characterized in that it comprises. The method according to any one of claims 1 to 14, Each of the plurality of printing stations includes a gear train 68 which drives the rotation of the rotatable printing element 61, the gear train being a gear mounted to the rotatable printing element 61. And a movable gear means 268 movable in and out of a position for driving in engagement with 269, the movable gear means 268 for engaging and driving with a gear 269 mounted to the rotatable printing element 61. And an end gear 288 oscillable in and out of position. The method of claim 15, The movable gear means 268 is a housing 270 mounted to support the leading gear 288 and to rotate about a first drive shaft 273 driven by the gear train 68; A first drive gear 278 fixed to the first drive shaft 273, a second drive gear 282 driven by the first drive gear 278, Rotating the housing 270 around the first drive shaft 273 to oscillate the tip gear 288 into and out of a position for engaging and driving with a gear 269 mounted to the rotatable printing element 61. Swing means (290), The second drive gear 282 is fixed to a second drive shaft 280 that is journalally supported relative to the housing 270, wherein the tip gear 288 is connected to the second drive shaft 288. Automatic printing machine, characterized in that fixed to the drive shaft (280). The method of claim 16, The swing means includes a swing gear 290 fixed to the housing 270 and driven by a third drive gear 291, wherein the third drive gear 291 is And a third drive shaft (293) which can be rotated by a drive means (292) separate from the gear train (68). In a method for controlling the registration of a plurality of component parts of a plurality of composite images printed along the length of a continuous substrate (11) , Providing a printer having a plurality of printing stations (13) rotatably mounted with a printing element (61) having a fixed repeat length on the circumference; Inserting a continuous substrate 11 having a plurality of at least one component image of a pre-printed composite image along its length into a printer continuously through a plurality of print stations 13, Each of said preprinted component images is located on a linear repeating length of a continuous substrate that tends to vary from a constant repeating length of a printing element, A plurality of prints are rotated at each print station at individual circumferential speeds in each print station to print individual additional component images of the composite image for each of the at least one component image previously printed along the substrate 11. Driving the continuous substrate 11 continuously inserted through the station 13 at a predetermined linear speed, Measuring a series of linear repetition lengths along the continuous substrate 11 running through the print station 13 and generating a measurement signal indicative of the measurements of the plurality of linear repetition lengths thus measured; , A correction value representing a predicted difference between the linear repetition length of the component image to be preprinted and the constant repetition length of at least one next to be run through the individual print station 13 is determined according to the measurement signal. Generating a control signal which is calculated separately for the print station 13 and conveys the calibration values for each station 13 so calculated; The above-mentioned substrate of the continuous substrate 11 may be used to correct a deviation between the linear repetition length of the component image printed by the printing element 61 at the individual print station 13 and the at least one component image previously printed as described above. The operation of the circumferential adjustment means 275 at each print station 13 in accordance with the control signal and the respective calibration value is adapted to automatically change the circumferential speed of the individual printing elements 61 with respect to the linear speed. And controlling each of them separately. The method of claim 18, The measuring and generating step includes sensing at each print station 13 a relative linear position of at least one component image preprinted with respect to the circumferential position of the printing element at a separate print station 13; , The calculating and generating step includes separately calculating the circumferential matching error for each print station 13 from the detected relative linear position, The controlling step is based on the relative circumference of the printing element 61 at the individual print station 13 relative to the detected linear position of the at least one component image pre-printed to correct the individual circumferential matching error. And individually controlling the operation of the individual circumferential adjustment means in each individual print station (13) to automatically change the position of the direction. The method of claim 18 or 19, The measuring and generating step comprises digitally displaying each measurement in the distinct measurement data, The control step automatically adjusts the average circumferential speed of the individual printing elements 61 relative to the linear speed of the continuous substrate 11 by a series of distinct rotational movements spaced apart with respect to the rotation of the printing element 61. Progressively controlling the operation of the circumferential adjustment means at each print station (13) in accordance with individual control signals in order to change it. The method of claim 18, Wherein said calculating and generating step includes calculating a recurrence portion of each of the series of measurements from the plurality of measurements and statistically deriving the predicted difference from the calculated recurrence portion.