EP0363228B1 - Rouleaux des presses - Google Patents

Rouleaux des presses Download PDF

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Publication number
EP0363228B1
EP0363228B1 EP19890310321 EP89310321A EP0363228B1 EP 0363228 B1 EP0363228 B1 EP 0363228B1 EP 19890310321 EP19890310321 EP 19890310321 EP 89310321 A EP89310321 A EP 89310321A EP 0363228 B1 EP0363228 B1 EP 0363228B1
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EP
European Patent Office
Prior art keywords
roller
oscillating
shaft
axially
annular
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP19890310321
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German (de)
English (en)
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EP0363228A3 (en
EP0363228A2 (fr
Inventor
James R. Kemp
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Advanced Graphics Technologies Inc
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Advanced Graphics Technologies Inc
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Publication of EP0363228A2 publication Critical patent/EP0363228A2/fr
Publication of EP0363228A3 publication Critical patent/EP0363228A3/en
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Publication of EP0363228B1 publication Critical patent/EP0363228B1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F7/00—Rotary lithographic machines
    • B41F7/20—Details
    • B41F7/24—Damping devices
    • B41F7/36—Inking-rollers serving also to apply ink repellants
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F31/00—Inking arrangements or devices
    • B41F31/15—Devices for moving vibrator-rollers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F7/00—Rotary lithographic machines
    • B41F7/20—Details
    • B41F7/24—Damping devices
    • B41F7/26—Damping devices using transfer rollers

Definitions

  • the present invention relates to a printing press roller.
  • the present invention relates to an oscillating roller for use in inking and dampening systems of printing presses.
  • oscillating form rollers have been developed which are frictionally axially driven by the oscillating motion of an adjacent transfer or vibrating roller. See U.S. Patents Nos. 4,493,257 and 4,718,344 for disclosures of such oscillating form rollers.
  • pneumatically oscillated and mechanically rotated vibrating rollers have been previously developed. See Japanese Patent No.57-93150 for a disclosure of such a roller.
  • Another form of fluid motor powered oscillating roller for the fluids in ink and dampening systems is shown in U.S. Patent No.2,242,214. It is also known to mechanically axially oscillate a roller. See U.S.
  • Patent Nos.3,625,148; 4,509,426 and 4,672,894 and British Patent application GB 2078172A It is also known to use a mechanically rotated and mechanically axially oscillated form roller in conjunction with an oscillating vibrating roller wherein both rollers are oscillated at different frequencies. See U.S. Patent No. 4,397,236.
  • each of these prior art rollers while solving some of the problems of inking or dampening fluid distribution, often created other problems or were not a complete solution to the fluid distribution problem.
  • frictionally axially driven oscillating form rollers when the form roller is being dragged in one direction by the adjacent axially moving vibrating roller, there is usually a period of time when the two rollers move axially essentially in unison so that little or no axial ink shearing action takes place in the nip of these two rollers. Consequently, the new ink being supplied to the form roller by the vibrating roller is only radially transferred and not axially redistributed on the form roll, and the likelihood of "ghosting" occurring increases.
  • Patent No. 4,397,236 introduces yet another variable in ink and/or dampening fluid distribution. That is to say for different portions of a complete cycle, different degrees of shearing action would take place between the two rollers oscillated at different frequencies, which will cause ink delivery, and consequently printing quality, to vary.
  • FR-A-2 283 780 discloses a pneumatically operated roller construction which has a pair of pistons which are moveable in cylinders, with a piston/cylinder being arranged at each end of the roller.
  • the cylinders are however outside the roller body and the roller shaft does not extend through the pistons or completely through the cylinders. Additionally the cylinders are pressurized and/or exhausted through air channels formed in the press side frames and the outer heads of the cylinders must abut with the side frames to connect to these air channels.
  • this prior construction is usable only in a custom built assembly.
  • an oscillating roller for use in one of the ink and dampening fluid systems of a printing press
  • a plurality of cylindrical heads being located on and concentric with the roller shaft, said cylindrical heads being axially spaced apart along the roller shaft and wholly within a hollow roller body so as to be axially slidable on the roller shaft, at least one of the cylindrical heads being located adjacent to each axial end region of the hollow roller body, a plurality of separate pistons which are also axially slidably mounted on the roller shaft and within the roller body, each piston being axially slidable within a cylindrical wall which extends within the roller body between said piston and an adjacent cylindrical head, the respective pistons, cylindrical walls and cylindrical heads forming a plurality of annular axially variable volumes about said roller shaft and within the roller body, control means being provided for admitting and exiting pressurised fluid from said annular axially variable volumes for causing
  • the oscillating roller of the present invention can be used as a form roller or in another roller position such as a vibrating roller in the dampening or inking system of a press.
  • the press can be of any type that has an ink train or dampening train and includes lithographic offset and flexo offset presses.
  • the oscillating roller of the present invention comprises an axially extending roller shaft that is adapted to be mounted to the press frame.
  • This roller shaft can be either a dead shaft, i.e., non-rotating, or a live shaft, i.e., rotating.
  • To the roller shaft is fitted a piston element which is axially located on the shaft.
  • the roller has a covering, generally of any suitable material used in ink or dampening trains, such as metal (chrome plated), rubber or plastic compounds, or ceramic materials.
  • the piston co-operates with a cylinder element or structure and forms therewith an axially variable volume.
  • the roller cover and cylinder structure are arranged in a manner that expansion or contraction of the variable volume causes the roller covering to axially move or oscillate.
  • a reverse construction can be used, that is with the cylinder structure axially located on the shaft and the piston moving the roller covering.
  • the cylinder structure and piston are located within the roller between the roller shaft and roller convering in a manner not to interfere with the press frame, to retard roller rotation, or to cause roller deflection.
  • the piston and cylinder structure are independent of the roller shaft and the roller covering and its core.
  • the piston and cylinder structure can utilize the outer surface of the shaft and the inner surface of the roller covering or its backup core to form the variable volume.
  • the piston and cylinder structure is located very close to the ends of the roller and not at or near its centre.
  • the roller of the present invention is particularly suited to long rollers, say for 91.44 cms (36 inch) paper or press widths or larger, and to slender rollers (a high ratio of length to diameter).
  • the piston and cylinder structure of the roller can be stacked double, triple or as many as necessary to develop sufficient force to oscillate the roller against any forces resisting oscillation, such as from an adjacent roller oscillating in the opposite direction.
  • the stacked piston-cylinder structure is spaced from the roller body or core, kept to the ends of the roller, and does not extend to the centre to minimize deflection problems.
  • roller shaft, piston and cylinder structure do not use close tolerances, but are made to freely fit one another. Where it is necessary to provide a tight seal or to prevent rotation of parts, "O" rings are used instead of heretofore tight pressed fits.
  • the oscillating roller of the present invention can be used in conjunction with another, adjacent oscillating roller, and in such a case, the roller of the present invention can be oscillated at the same cyclic rate or frequency, either in the same or opposite direction of the adjacent oscillating roller with the same, greater or lesser stroke.
  • the oscillating roller of the present invention when used in the form position, can be used with an adjacent vibrating or distributing roller so that these two rollers oscillate at the same frequency but move axially in different directions.
  • Such construction and operation provides for consistent axial shearing between these two rollers and between the form roller and the plate cylinder to ensure that the exact and precise relationship are repeated each time the plate is inked and/or moistened.
  • the resultant transfer of fluid be it ink or dampening moisture, between the vibrating roller and form roller and, also, between the form roller and plate cylinder is in a desirable diagonal pattern. That is the relative axial motions and rotational motions of the two respectively adjacent rollers always forms a diagonal pattern.
  • the oscillation of the rollers of the present invention is controlled by a control means which senses the oscillation of the adjacent roller, such as the change of direction of the axial motion, and controls the admission and venting or exiting of pressurized fluid or compressed air from the piston-cylinder structure to cause the roller of the present invention to oscillate, preferably in the above manner.
  • the control system gives the roller of the present invention a variable length stroke, and can axially move the roller of the present invention at the same speed as the adjacent roller, a slower speed than the adjacent roller, or at a faster speed with a dwell time, if desired, that can be varied.
  • the wiping action between the oscillating roller of the present invention and the adjacent oscillating roller, and with the plate cylinder can be optimized.
  • the motion of the oscillating roller of the present invention is achieved by supplying compressed air at a regulated high air pressure to the piston-cylinder structure on one side of the roller and exhausting or venting the piston-cylinder structure on the opposite side of the roller through a variable area orifice. Changing the size of the exhaust orifice will change the roller speed. Of course, a higher or lower supply pressure will also change the oscillation speed. Adjustment of the supply pressure and/or venting can also be used to provide, eliminate, or adjust a dwell time. The length of the oscillation or stroke is determined by its speed. For a long stroke a high speed is used, and for a short stroke a low speed is used.
  • Another aim of the present invention is to provide an air piston-cylinder construction in an oscillating roller, which causes an axial motion without restricting rotational motion.
  • Yet another aim of the oscillating roller and method of the present invention is to provide an air piston-cylinder construction spaced from the outside of the roller body or core and/or confined to the ends of the roller to eliminate and minimize roller deflection.
  • Still another aim of the present invention is to provide a construction which permits more than one piston-cylinder structure to be provided at each end of the roller, so that even small diameter rollers can develop sufficient force to provide the desired oscillation.
  • Yet another aim of the present invention is to provide a roller that can be used in conjunction with another adjacent oscillating roller so that both rollers are synchronized to operate at the same cyclic rate or frequency, moving in the same or opposite directions, with speeds and/or strokes to provide optimum wiping action for the printing job at hand.
  • Yet a further aim of the present invention is to provide a form roller which can be used in conjunction with an adjacent vibrating roller so that both rollers are synchronized to operate at the same cyclic rate or frequency, moving in axially opposite directions to maximize fluid distribution for eliminating "ghosting".
  • Still another aim of the present invention is to provide a structure for pneumatically oscillating a roller in the ink or dampening system of a press.
  • a further aim of the present invention is to provide an oscillating roller structure particularly suited to retrofitting into a press in place of a non-oscillating roller.
  • Fig.1 one type of printing press on which the oscillating roller of the present invention can be used, is illustrated. While the press shown is a lithographic or offset press having both an ink train and a dampening fluid train, the press could be of the type wherein these two systems, ink and dampening, merge, or of a different type press, such as gravure or flexopress.
  • the web 9 runs through between two offset or blanket cylinders or rollers 10, each of which run against its own plate cylinder or roller 11.
  • Each plate cylinder is fed ink fluid from a fountain 12 and dampening fluid from a tray 13 by roller trains which include rollers 14, which in some presses may be ductors, distribution rollers 15, axially oscillating vibrating rollers 17 and form rollers 18 which ride against the plate cylinder.
  • rider rollers 20 are shown on the form rollers 18.
  • the oscillating roller of the present invention could be utilized for any of the rollers in the positions indicated by the reference numerals 17,18 and/or 20.
  • FIG.2 a first embodiment of oscillating roller 30 of the present invention is illustrated.
  • the figure actually shows only one end (the left) of roller 30, the other end of the roller being of generally similar construction, and what differences there are will be verbally described or may be observed in Fig.6.
  • the roller 30 is mounted in a press hanger or frame 32, only partially shown.
  • this roller is used in position numbered 20 in Fig.1.
  • the roller 30 was retrofitted to replace a live shaft roller, and that is why the press frame 32 has a bearing cavity 34, which, in this instance, to make the conversion, is fitted with a dummy bearing 36.
  • the dummy bearing 36 is clamped or located in the press frame 32 by conventional means (not shown) to prevent its rotation.
  • the reduced diameter pilot end 38 of a roller shaft 40 extends into the dummy bearing and is retained by a roll pin 42.
  • the other end (not shown) of shaft 40 is similarly mounted on the press frame. Roller shaft 40 is dead, i.e., it does not turn.
  • the major part of the roller shaft which extends completely across the press to the hanger or frame on the opposite side, is enlarged, i.e. it has a larger diameter than the pilot end 38 to better resist the bending loads imposed on the shaft by the contact with one or more adjacent rollers (See Fig.1).
  • an axially extending centrally located blind bore 44 is drilled in each end of the shaft 40. While in some instances the outer end of a bore 44 could be utilized to connect with an air supply/vent, in this instance because of the solid press frame 32, such is not possible, and the outer end of bore 44 is closed, by a pipe plug 46.
  • a short radial passage 48 is provided in the shaft 40 and fitted with an appropriate fitting 50 and a hose or tube 52 to connect it to the control system, suitable control systems being shown in Figs. 6 or 7.
  • a radial passage 54 is provided to supply or vent air from the passage 44, it being understood that passage 54 is in fluid communication with the air supplied or vented through hose 52.
  • the outer periphery of shaft 40 is provided with an annular groove for receiving a circle clip 56, this groove being located closer to the central region of the length of the shaft than the radial passage 54.
  • Slidably fitting on the shaft is an annular piston member 58 which abuts against the side of the circle clip 56 facing the end 38 of the shaft 40.
  • the piston 58 is grooved on its radially inner and outer surfaces to receive sealing "O" rings 60 and 62 to seal the piston 58 to adjacent surfaces.
  • An annular cylindrical member 64 also slides on the roller shaft 40 and has a cylindrical head portion 66 and a connected cylinder wall portion 68 into which the piston 58 can slide.
  • the axial motion of the cylindrical members 64 is transferred to an annular sleeve 72, made of oil impregnated bronze, also slidable on the roller shaft 40. As is shown in Fig. 2, the right hand end of this sleeve 72 abuts the left end of the cylindrical member 64 for this purpose.
  • the axial sleeve 72 carries, in this instance, an inner race 74 for a roller bearing 76.
  • Both the inner and outer surfaces of the annular sleeve 72 are grooved to accommodate "O" rings 78,80 and 82 which provide a secure fit for the sleeve 72 on the shaft 40, and prevent any tendency for the inner race 74 to rotate on the annular sleeve 72, and the annular sleeve 72 to rotate on the shaft 40.
  • the annular sleeve 72 and the inner race 74 are only subject to axial motion and not rotational motion.
  • the roller bearing 76 has an outer race 84 which engages with a roller body or core 86 carrying a roller covering 88.
  • the roller covering 88 and core 86 are rotatably mounted by the roller bearing 76 for free rotation.
  • the core 86 is grooved to accommodate an "O" ring 90 which makes for a tight fit with the outer race 84 without the need for extremely close tolerances and also causes the outer race 84 and core 86 to rotate together, the outer race 84 and core 86 being freely rotatable with respect to the roller shaft 40.
  • a thrust bearing 92 consisting of rollers 94 which extend radially with respect to the roller shaft 40, an inner race 96, and an outer race 98, abuts the end of the annular sleeve 72 adjacent to the end of shaft 40.
  • the outer end of the annular sleeve 72 is stepped, in this instance, to accommodate the inner race 96.
  • the outer race 98 is carried on an end ring 100, which engages against an outer circle ring 102 located in an annular groove provided on the inner surface of the end region of the cylindrical roller core 86.
  • an "O" ring 103 is provided in the radially outer surface of the end ring 100 to prevent relative rotation between the end ring 100 and the roller core 86.
  • the end ring 100, the outer race 84 of the roller bearing 76, and an "L" shaped cross-section keeper 104 are all located in an enlarged diameter section 105, formed in the outer end of the core 86, with the end ring 100, outer race 84 and keeper 104 being held together between the circle clip 102 and a shoulder formed where the enlarged diameter section 105 of the core 86, finishes.
  • the keeper 104 is provided to ensure that the annular sleeve 72 and inner race 74 are captured and that the thrust bearing rollers 94 and inner race 96 remain supported at all times on the annular sleeve 72.
  • a seal 106 is provided between the end ring 100 and the shaft 40 to close the roller and to keep the lubrication for the thrust bearing 92 and roller bearing 76 in place.
  • a grease fitting 108 and grease passage 110 can be provided in the end ring 100 to lubricate the roller bearing 76 and thrust bearing 92.
  • the axial oscillation of the roller of the present invention may be controlled by the control system shown in Figs. 6 or 7.
  • the roller 30 of the present invention is assumed to be in a form position (See reference numerals 18 of Fig.1) in contact with both the plate cylinder (not shown in Fig.6) and a vibrating roller 120 which is mechanically axially oscillated by the press drive.
  • the oscillation of the adjacent oscillating vibrator roller 120 is sensed by proximity switches 122 and 124 (such as cylindrical AC or DC type, made by Furnas) which monitor two adjustable collars 125 fitted to the opposite ends of the shaft of roller 120, and thus sense the roller's change of direction at the end of its axial motion (trigger points).
  • proximity switches 122 and 124 such as cylindrical AC or DC type, made by Furnas
  • other types of devices than proximity switches 122 and 124 could be used, such as microswitches or pneumatic logic devices, or the timing signal could be taken from somewhere on the press drive or vibrating roller drive.
  • the roller 120 instead of monitoring the adjustable collars 125, the roller 120 itself can be monitored. However, the use of adjustable collars 125 permits these trigger points to be easily changed. Likewise, the proximity switch locations could be changed to adjust the trigger points.
  • a signal is sent to a solenoid operated 4-way directional control valve 126 (such as of a type similar to a Directair 2 valves, direct pipe port 4-way double solenoid spool valve made by the Schrader Bellows division of Parker Hannifin), causing that valve to pressurize the axial variable volume on one end of the roller 30 and to vent the axial variable volume chamber on the other end of the roller 30.
  • a solenoid operated 4-way directional control valve 126 such as of a type similar to a Directair 2 valves, direct pipe port 4-way double solenoid spool valve made by the Schrader Bellows division of Parker Hannifin
  • a slidable body 121 in the valve 126 is moved by one or the other of the solenoid's coils 123 so that the one variable volume is pressurized and the other is vented.
  • the left side variable volume is being pressurized while the right is being vented, as indicated by the solid arrows 125A, so that the roller 30 and its covering 86 will move to the left until the piston 58 and cylindrical head 64 of the right variable volume contact each other and limit further movement or there is a subsequent reversal of the direction of the roller 120.
  • the roller 120 When the right end of the roller 120 reaches its rightmost end of travel, it triggers the proximity switch 124, which, in turn, will energize and cause the right side coil 123 to move the valve body 121 from its shown leftmost position, to the right, as partially shown in dotted lines at the right end of body 121, so that the right variable volume is pressurized and the left vented, as indicated by the arrows 127 in dotted lines.
  • the core 86 and covering 88 of the roller 30 begins to move and will continue to move to the right until the piston 58 and cylindrical head 64 of the left variable volume contact or there is a subsequent change of direction of the roller 120.
  • the roller 120 While the roller 30 was moving to the right, the roller 120 was moving to the left, and upon reaching the leftmost end of its stroke, it triggers the switch 122 and then starts to return to the right.
  • the triggering of switch 122 energizes the left coil 123 to, again, reverse the valve body 121, to cause the core 86 and covering 88 of the roller 30 to again move left.
  • the above operation is repeated in succession as long as it is desired to oscillate the roller 30.
  • the control system of Fig.6 causes the core 86 and covering 88 of the oscillating roller 30 to change direction substantially at the same time the adjacent oscillating vibrating roller 120 changes direction.
  • the oscillating roller 30 of the present invention moves in the opposite direction to the adjacent oscillating roller 120, it could, if desired, alternatively move in the same direction as the adjacent oscillating roller 120, depending upon which ends of the oscillating roller 30 of the present invention are being pressurized and vented.
  • the speed of the oscillation of the roller 30 of the present invention can be made greater than, less than, or equal to the speed of that of the adjacent oscillating vibrating roller 120. Of course, if the speed is greater, there may be a dwell period at the ends of the strokes. Likewise, the length of the oscillation can also be controlled.
  • the roller 30 of the present invention were moved slowly, such that a full stroke was not completed before a change of direction occurred, it would have a shorter oscillation than were it moving faster, assuming the axial speed of the adjacent oscillating roller 120 (triggering the oscillation of the roller 30 of the present invention) is being kept constant.
  • the axial speed of the oscillating roller 30 of the present invention can be increased by increasing the supply pressure via a conventional regulator 128 and/or by decreasing the restriction of valves 130 inhibiting venting.
  • the speed, of couse could be decreased by decreasing the supply presssure, and/or by increasing the restriction (reducing the flow area) of valves 130.
  • the roller 30 can be prevented from oscillating and be simply biased toward one end or other of the press.
  • one of the solenoid coils 123 could be kept energized to keep the valve body 121 in the position shown in Fig.6 so that the roller covering 88 would be biased to the left.
  • biasing could be achieved pneumatically as by supplying pressure to only the left side variable volume.
  • Another alternative would be to use a different type valve, instead of valve 126, which also provides a centred position.
  • roller 30 of the present invention never leaves the vibrating roller 120 as the latter is longer, and never leaves the edges of the forms on the plate cylinder, as the forms are inside the edges of the covering 88 of the roller 30.
  • a second form of control system is shown, and unlike the system shown in Fig.6 which synchronizes oscillations to an adjacent roller, the system of Fig.7 is self oscillating.
  • a system like that shown in Fig.7 is ideal where there is no need or desire to synchronize oscillations of the roller of the present invention to that of another roller, such as would be the case for a roller shown in the position indicated by the numeral 15 in Fig.1.
  • the system of Fig.7 could be used to self oscillate one roller and a system of Fig.6 used to oscillate an adjacent roller, such as a form roller and vibrating roller for the dampening or ink system.
  • Such arrangement would be particularly useful in retrofitting two adjacent oscillating rollers to a press which had non-oscillating rollers.
  • the roller 30 has the same right and left air supply/vent line 52L and 52R for the right and left variable volumes in the ends of the roller.
  • These air lines are connected to two function valves 140 and 141 (such as model No. 7818-5420 made under the trade name Legris) which detect the presence or absence of pressure in the lines 52L and 52R, respectively, to self oscillate the roller.
  • each of the lines 52L and 52R bifurcate into a first part having a variable area restriction valve 142 or 143 (such as the valve 130 shown in Fig.6) and a second part with a one-way valve 144 or 145, only permitting flow in a direction towards its respective variable volume, when its ball is off its seat.
  • a variable area restriction valve 142 or 143 such as the valve 130 shown in Fig.6
  • a one-way valve 144 or 145 only permitting flow in a direction towards its respective variable volume, when its ball is off its seat.
  • the one-way valve 142 or 143 and the restriction valve 144 or 145 can both be incorporated in a single body, such as in a SCl sold by Humphrey.
  • valve 146 having a slidable partitioned valve body 147, similar to that of valve 126 with valve body 121, but different in that the valve body is air operated, instead of electrically operated.
  • a valve 146 is sold as a 4PP valve by Humphrey.
  • each end of the valve body 147 is provided with a piston-cylinder construction 148 and 149 (such as model 34A made by Humphrey, air operator for valve 146) which, in turn, is connected back to one or the other of the two function valves.
  • the function valves 140 and 141 and the 4-way valve 146 are all connected to a source of high pressure, such as the pressure regulator 128.
  • the right function valve 141 As the pressure in the right variable volume in roller 30 drops, the right function valve 141, due to its construction, opens to permit flow from the regulator through the right function valve to the piston cylinder 149 on the left side of the valve body 147, tending to cause it to move to the right. At the same time, the increasing pressure in the line 52L causes the left function valve 140 to close off pressure to the piston cylinder 148 on the right side of the valve body.
  • valve body 147 slides to the right (as partially shown by dotted line at the right) to pressurize the roller's right variable volume and vent the roller's left variable volume (just as in the description of the operation illustrated in Fig.6) to cause the roller core 86 and covering 88 to then return to the right and the position shown in Fig.6.
  • the subsequent rise in pressure in the left function valve 140 and the drop in pressure in the right function valve will again slide the valve body 147 to cause another stroke. This procedure is repeated for as long as desired to self oscillate the roller.
  • any suitable roller biasing or centering arrangement such as those described in conjunction with Fig.6, could be adapted to the Fig.7 self-oscillating control system.
  • roller 30 Just as either control system is shown used with roller 30, either, depending upon application, could be used with the subsequently described embodiments of rollers of the present invention.
  • a second embodiment roller 150 of the present invention is shown.
  • This roller is generally similar to the roller shown in Fig.2, and to the extent similar parts will be given the same reference numerals as shown in Fig.2.
  • the principal difference between the roller 150 shown in Figs. 2 and 3, is that the roller 150 of Fig .3 has a stacked piston and cylinder structure to develop additional axial force to oscillate the roller.
  • this construction is particularly advantageous where the roller is of small diameter, and it is difficult to install a large cross-sectional area variable volume chamber to develop adequate force to oscillate the roller, particularly against the opposite direction axial oscillation of an adjacent roller.
  • a second identical inner piston 152 is provided on each end.
  • Each second piston co-operates with a second circle ring 154, provided in a second circle ring groove on the roller shaft 151, located axially inwardly of the outer circle ring 56 and its groove.
  • Each second piston 152 is relatively slidable in a second idential cylindrical member 156, located axially inwardly of the first cylindrical member 64.
  • Both the second piston 152 and second cylindrical member 156 have similar "O" rings as the said first piston 58 and first cylindrical member 64.
  • the second cylindrical head 156 merely abuts the first cylindrical member 64.
  • the air supply or vent for the second piston and cylindrical member is merely a continuation indicated by the numeral 158, of the passage 44, and a radial passage 160 in communication therewith, the second axial variable volume being formed between the said second cylindrical member 156 and the said second piston 152.
  • the force generated in the second piston-cylindrical member is added to the force generated by the first piston-cylindrical member to double its force output.
  • additional piston-cylinder constructions could be stacked on each side of the roller.
  • a third embodiment of oscillating roller 180 of the present invention is illustrated and described and is particularly suited for small diameter rollers.
  • the roller 182 rotates directly on the roller shaft 184.
  • the roller shaft could be hardened or heat treated in the area beneath the roller, if desired. The result is that the structure can be adapted to considerably smaller diameter rollers. As is shown, this type of construction is used with the stacked piston-cylindrical member structure described above.
  • two or more axial variable volumes are defined between two or more pistons 186 and 188 and cylinders 190 and 192 at each end of the roller to provide sufficient axial force.
  • This construction is particularly suited for a small diameter roller (small area between the roller's core 192 and shaft 184).
  • the thrust bearing 194 is nearer to the centre of the length of the shaft than the rollers 182, whereas before the thrust bearing was axially outside of the rollers 76. Either location is satisfactory and works well as long as the parts that rotate are separated from the parts that do not rotate, by the thrust bearing.
  • roller bearing and the axial load capability of the combination of the roller thrust bearing could be met in another manner, such as with tapered roller bearings, angular contact ball bearings, or even plain ball bearings.
  • the use of a roller bearing with a separate thrust bearing gives a great radial load capability with a more compact diameter.
  • suitable sleeve bearings such as of the oil impregnated type, could also be used.
  • the fourth embodiment of axially oscillating roller 198 is shown. Unlike the prior described embodiments which had dead or non-rotating shafts, the fourth embodiment has a live or rotating shaft. As is shown, the shaft 200 is mounted by a pair of ball or roller bearings 202 held to the press hanger or frame 204. Thus, the entire shaft 200 is free to be rotated by an adjacent roller, be it a plate cylinder or other adjacent rotating roller. Of course, with this construction the shaft 200 could be easily adapted to be mechanically rotated, as by a gear (not shown) on one end driven by the press drive.
  • the roller shaft 200 has an axially extending air passage 206 therein which has a first radial connecting passage 208 leading from an air coupling 210, and a second radial passage 211 communicating with the variable volume piston and cylindrical member structure, which will be hereinafter described.
  • the air coupling 210 itself is stationary and is capable of supplying air to or venting air from the rotating roller shaft 200 and its passage 208.
  • the coupling comprises a body 212 having an opening 214 to rotatably receive the shaft 200.
  • the body 210 itself, can act as a bearing and may be made of a suitable bearing material, such as oil impregnated bronze.
  • the body has two portions 216 which bearingly engage the shaft.
  • annular collector chamber 218 is formed in the body so as to always maintain communication with the rotating passage 208.
  • the annular chamber 218, in turn, is connected via a passage 220 and fitting 222, to an air supply/vent line 224 from the control system.
  • a pair of seals 226 are provided on the ends of the body which seal to the shaft 200. The seals 226 are held in place by two washer rings 228, which in turn are secured by two circle clips or rings 230 located in grooves on the shaft 200.
  • the seals 226 may be omitted and a close tolerance shaft bore can be provided in the air coupling body 210 to make the body function as an air bearing with a small flow of air escaping around the shaft 200 so that the shaft's rotation is not restricted by air pressure on the seals.
  • the body 210 itself, is prevented from rotation by the air line 224, and preferably by a torque strap (not shown) connecting the body 210 to the press frame.
  • each axial variable volume chamber is provided by a piston and cylindrical member structure.
  • the piston 232 is an annular member slidably fitting on the shaft 200. Again, no close fits are needed as the piston 232 has an inner "O" ring 234 and an outer “O” ring 236 to both seal the piston with the shaft 200 and cylinder 238, respectively.
  • the cylinder itself is formed by one end of the roller core 240, which is stepped as indicated at 242 to form a shoulder 244 to limit piston travel.
  • Piston travel relative to the shaft in one axial direction, i.e. inwardly, is likewise limited by circle ring 246 engaged in a groove in the roller shaft 200.
  • the other end of the annular, axial variable volume cylinder structure is closed by another annular ring 250 or cylindrical member slidable on the roller shaft 200.
  • the annular ring 250 is, likewise, sealed to both the shaft 200 and cylinder wall 238 by a pair of "O" rings, 252 and 254, respectively. While the annular ring 250 can slide on the roller shaft 200, the annular ring is prevented from moving further relatively outward of the roller core 240 as it abuts a circle ring 256 held in a groove formed in the outer end of the core 240.
  • the core 240 itself, is covered with a roller covering 258 suitable for the position in which the roller is to be operated.
  • the use of the "O" rings 234 and 236 on member 232 and the “O” rings 252 and 254 on the member 250 cause these two members and the shaft 200 to rotate with the core 240 and covering 258. Thus all relative rotation occurs in the bearings 202.
  • the foregoing structure is, preferably, duplicated on the other end of the roller and the two air supply/vent lines are connected to the control system in the manner such as shown in Figs.6 or 7.
  • air under pressure may be supplied to the end shown in Fig.5 to cause the variable volume on that side to axially expand, while air under pressure is being released or vented from the variable volume on the other end of the roller (not shown) so that the roller core 240 and its covering 258 move left.
  • the air connections are reversed so that the end shown in Fig.5 is subsequently vented and the end not shown is pressurized to cause the core and covering to move to the right to complete a cycle. This operation is repeated to cause the required oscillation and may be varied as has been described above.
  • the roller shaft diameters could go from 1.905 cm (3/4 inch) to 7.62 cm (3 inch), the roller covering outside diameter could be from 5.08 cm (2 inches) to 20.32 cms (8 inches).
  • the smaller sizes are particularly applicable to the embodiment 180 shown in Fig.4. While the construction of the present invention is particularly advantageous in rollers of lengths of 91.44 cms (36 inches) or greater, it could also be used in smaller rollers such as 30.48 cm (12 inches) in length or greater lengths such as 203.2 cms (80 inches) or more.
  • control systems are shown using a 4-way valve, two 3-way valves could be used instead.
  • a suitable timing device such as a multicontact relay or the like, a plurality of single solenoid valves could be used instead to perform the various functions.
  • Fig.1 illustrates a web press having a dampening and inking system wherein the ink and dampening fluids are provided to at least one common form roller
  • the present invention is applicable to any type dampening and/or inking system, such as those with more rolls in common, no rolls in common or even just an inking system.
  • the present invention could be incorporated in just one of the systems or both, or for just one, a few or many rollers on the web press. All of the foregoing, of course, should be considered as falling within the claims.
  • the speed of oscillation of the roller is caused by pressurizing the variable volume at one end and venting the variable volume at the other end of the roller, and more particularly by being able to adjust the restriction in the vented line
  • This approach provides the advantage of a smoother operation and avoids jumpy type operation which frequently occurs where the speed is controlled merely by regulating the high pressure input.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Rotary Presses (AREA)

Claims (18)

  1. Rouleau oscillant pour l'utilisation dans l'un des systèmes de fluides d'encrage et de mouillage d'une presse à imprimer comprenant un arbre de rouleau s'étendant axialement (40; 151; 184; 200) adapté pour être monté sur la largeur d'une presse à imprimer, une pluralité de têtes cylindriques (66, 190, 192; 250) étant situées sur l'arbre de rouleau et concentriquement à celui-ci (40; 151; 184; 200) lesdites têtes cylindriques (66; 90; 192; 250) étant espacées axialement le long de l'arbre de rouleau (40; 151; 184; 200) et entièrement au sein d'un corps de rouleau creux (86; 192; 240) de manière à pouvoir être coulissées axialement sur l'arbre de rouleau (40; 151; 184; 200), au moins une des têtes cylindriques (66; 90; 192; 250) étant contiguë à chaque région axiale d'extrémité du corps de rouleau creux (86; 192; 240), une pluralité de pistons séparés (58, 152; 186, 188, 232) qui sont aussi montés de manière coulissante axialement sur l'arbre de rouleau (40; 151; 184; 200) et au sein du corps de rouleau, chaque piston (58, 152; 186, 188, 232) pouvant être coulissé axialement au sein d'une paroi cylindrique (68, 242) qui s'étend au sein du corps de rouleau entre ledit piston (58, 152; 186; 188, 232) et une tête cylindrique contiguë (66, 90, 192; 250), les pistons respectifs (58; 186; 188; 232) parois cylindriques (68; 242) et têtes cylindriques (66, 156; 190, 192; 250) formant une pluralité de volumes annulaires variables axialement autour dudit arbre de rouleau (40; 151; 184; 200) et au sein du corps de rouleau, un moyen de commande (122, 124, 125, 126; 146) étant fourni pour admettre et expulser un fluide pressurisé provenant desdits volumes annulaires variables axialement pour provoquer un mouvement axial relatif entre lesdites têtes cylindriques (66; 190, 192; 250) et lesdits pistons (58, 152; 186, 188; 232), l'une des têtes cylindriques (66, 156; 190, 192; 250) et l'un des pistons (58; 186, 188; 232) à chaque région, d'extrémité de l'arbre de rouleau (40; 151; 184; 200), étant capables de déplacer axialement le corps de rouleau (86; 192), et l'autre tête cylindrique (66, 156; 190, 192; 250) et l'autre piston (58, 152; 186, 188; 232) étant limités en ce qui concerne le mouvement coulissant axial disponible sur l'arbre de rouleau (40; 151; 184; 200) dans un sens vers la région médiane de l'arbre de rouleau (40; 151; 184; 200), de sorte que l'admission et l'expulsion de fluide pressurisé provenant desdits volumes variables axialement entraînent le déplacement axial du corps de rouleau (86; 192) relativement audit arbre de rouleau (40, 151; 184; 200).
  2. Rouleau oscillant selon la revendication 1, dans lequel ledit arbre de rouleau (40; 151; 184) est un arbre fixe, chaque dite région d'extrémité dudit arbre de rouleau (40; 151; 184) étant adaptée pour être fixée de manière non rotative dans la presse à imprimer, un roulement (72,74,76,84,92,94) étant disposé pour déplacer axialement ledit corps de rouleau creux (86;192) avec l'une desdites parois cylindriques (68) et l'un desdits pistons (58;186) ledit roulement (72,74,76,84,92,94) montant de manière rotative et coulissante ledit corps de rouleau creux (86;192) sur ledit arbre de rouleau (40;151;184).
  3. Rouleau oscillant selon la revendication 1, dans lequel ledit arbre de rouleau (200) est un arbre mobile, chaque dite région d'extrémité dudit arbre de rouleau (200) étant adaptée pour être fixée de manière rotative dans la presse à imprimer par un roulement (202).
  4. Rouleau oscillant selon la revendication 1, 2 ou 3, dans lequel ledit rouleau oscillant a au moins quatre desdits pistons (58;186), au moins quatre desdites parois cylindriques (68) et au moins quatre des têtes cylindriques (66,156;190,192) qui forment au moins quatre desdits volumes annulaires variables axialement, deux desdits volumes annulaires variables axialement étant contigus à chacune desdites régions d'extrémité extérieures dudit arbre de rouleau (40;151;184).
  5. Rouleau oscillant selon la revendication 1, 2 ou 3, dans lequel ledit rouleau oscillant a deux desdits pistons annulaires (58), deux desdites parois cylindriques (68) et deux desdites têtes cylindriques annulaires (66) qui forment deux desdits volumes annulaires variables axialement, l'un desdits volumes annulaires variables axialement étant contigu à,chacune desdites régions d'extrémité extérieures dudit arbre de rouleau (40).
  6. Rouleau oscillant selon la revendication 1, 2 ou 3, dans lequel ledit rouleau oscillant a une pluralité desdits pistons (58;186,188), une pluralité desdites têtes cylindriques (66,156;190,192) et une pluralité de parois cylindriques (68) contigus à chacune desdites extrémités extérieures dudit rouleau oscillant pour fournir une pluralité de volumes annulaires variables axialement contigus à chacune des extrémités dudit rouleau oscillant, et ledit moyen de commande (122,124,125,126;146) comprend un moyen (126;146) pour en alternance pressuriser et décharger ladite pluralité de volumes annulaires variables axialement contigus à chacune desdites extrémités dudit rouleau oscillant pour osciller ledit rouleau oscillant.
  7. Rouleau oscillant selon la revendication 2, dans lequel ledit roulement (72,74,76,84,92,94) a une partie intérieure (72) pouvant être coulissée sur ledit arbre de rouleau (40;151) et pouvant être déplacée axialement par lesdits volumes annulaires variables axialement.
  8. Rouleau oscillant selon l'une quelconque des revendications 2 à 7, dans lequel ledit roulement (72,74,76,84,92,94) comprend un roulement (76;94) [capable] de prendre des charges radiales (76) et axiales (94) sur ledit noyau de rouleau creux (40;151).
  9. Rouleau oscillant selon la revendication 8, dans lequel ledit roulement (72,74,76,84,92,94) comprend un roulement de charge radiale séparé (76) et un roulement de charge axiale séparé (94).
  10. Rouleau oscillant selon la revendication 2 ou 3, dans lequel ledit roulement (72,74,76,84,92,94) comprend des roulements à rouleaux (76,94).
  11. Rouleau oscillant selon la revendication 2 ou 3, dans lequel ledit roulement comprend des roulements à billes.
  12. Rouleau oscillant selon la revendication 1, dans lequel sont fournis une pluralité de pistons (56;186,188), une pluralité de têtes cylindriques (66,156;190,192), une pluralité de parois cylindriques (68), et une pluralité de volumes annulaires variables axialement, tous fournis en nombres égaux.
  13. Rouleau oscillant selon la revendication 2, dans lequel ledit rouleau oscillant a une pluralité desdits pistons (56;186,188), une pluralité desdites têtes cylindriques (66,156;190,192) et une pluralité de parois cylindriques (68) contigus à chacune desdites extrémités extérieures dudit rouleau oscillant pour fournir une pluralité de volumes annulaires variables axialement contigus à chacune des extrémités extérieures dudit rouleau oscillant, ledit moyen de commande (122,124,125,126;146) comprend un moyen (126) pour en alternance pressuriser et décharger ladite pluralité de volumes annulaires variables axialement contigus à chacune desdites extrémités extérieures dudit arbre de rouleau (40;151;184) pour osciller ledit rouleau oscillant, ledit roulement (72,74,76,84,92,94) ayant une partie intérieure (72) pouvant être coulissée sur ledit arbre de rouleau (40;151;184) et pouvant être déplacée axialement par lesdits volumes annulaires variables axialement, ledit roulement étant capable de prendre des charges radiales et axiales sur ledit corps de rouleau creux (86;192) et étant l'un des roulements à rouleaux et à billes.
  14. Rouleau oscillant selon la revendication 1 ou 2, dans lequel une pluralité de têtes cylindriques (66,156;190,192), une pluralité de pistons (58,152;186,182) et une pluralité de parois cylindriques (68) sont empilables sur ledit arbre de rouleau (40;151;184) pour former une pluralité de volumes annulaires variables axialement, de sorte que la force requise pour osciller le rouleau oscillant peut être augmentée en empilant lesdits volumes annulaires variable axialement sur ledit arbre de rouleau (40;151,184).
  15. Rouleau oscillant selon la revendication 1, dans lequel chacune desdites têtes cylindriques (66,156;190,192) est intégralement formée avec sa dite paroi cylindrique contiguë coopérante (68), chacun desdits pistons annulaires séparés (58,152;186,188) pouvant être coulissé dans ses dites parois cylindriques contiguës coopérantes (68) ladite tête cylindrique, ladite paroi cylindrique et ledit piston étant empilables sur ledit arbre de rouleau (40;151;184).
  16. Rouleau oscillant selon la revendication 1 ou 3, dans lequel une paroi intérieure (242) dudit corps de rouleau creux (240) forme lesdites parois cylindriques.
  17. Rouleau oscillant selon l'une quelconque des revendications précédentes, dans lequel ledit moyen de commande (122,124,125,126) comprend en outre un moyen (122,124,125) pour déterminer le mouvement oscillant d'un rouleau immédiatement contigu (120) ladite couverture de rouleau (86) dudit rouleau oscillant étant libre de tourner et d'être adaptée pour être tournée par la rotation du rouleau immédiatement contigu (120), ledit moyen de commande oscillant ledit rouleau oscillant en fréquence avec les oscillations du rouleau immédiatement contigu (120), mais substantiellement dans un sens opposé à celui-ci, de sorte que la rotation et le mouvement d'oscillation axiale combinés entraînent le transfert de l'un desdits fluides d'encrage et de mouillage sur ledit rouleau oscillant dans une configuration substantiellement diagonale.
  18. Rouleau oscillant selon l'une quelconque des revendications précédentes, dans lequel lesdits pistons (58,152;186,188;232) et têtes cylindriques (66,156;190,192;250) sont formés par des organes annulaires montés sur ledit arbre de rouleau (40;151;184;200).
EP19890310321 1988-10-07 1989-10-09 Rouleaux des presses Expired - Lifetime EP0363228B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US25515388A 1988-10-07 1988-10-07
US255153 1988-10-07

Publications (3)

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EP0363228A2 EP0363228A2 (fr) 1990-04-11
EP0363228A3 EP0363228A3 (en) 1990-09-19
EP0363228B1 true EP0363228B1 (fr) 1995-01-04

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EP (1) EP0363228B1 (fr)
JP (1) JP3018081B2 (fr)
CA (1) CA1330636C (fr)
DE (1) DE68920395T2 (fr)

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DE19603765A1 (de) * 1996-02-02 1997-08-07 Heidelberger Druckmasch Ag Vorrichtung zum axialen Bewegen einer Reibwalze
DE19942984A1 (de) * 1999-09-09 2001-03-15 Schaeffler Waelzlager Ohg Radial-Axial-Lagereinheit
US7398731B2 (en) * 2004-08-04 2008-07-15 Heidelberger Druckmaschinen Ag Press containing an oscillating doctor and oscillating roller moved together
DE102005030127A1 (de) 2005-06-28 2007-01-04 Maschinenfabrik Wifag Gegenläufige Farbreiber
DE102006042959B4 (de) * 2006-05-17 2012-06-06 Officine Meccaniche Giovanni Cerutti S.P.A. Verfahren und Vorrichtung zum Reduzieren von Schwingungen eines rotierenden Zylinders einer Druckmaschine
DE102007004411A1 (de) * 2007-01-30 2008-07-31 Hydac System Gmbh Walze mit axial oszillierend bewegbarem Mantelkörper, insbesondere Verreibwalze
FR2940177B1 (fr) * 2008-12-24 2013-01-11 Goss Int Montataire Sa Ensemble de support et unite d'encrage ou de mouillage correspondante
US8850976B2 (en) * 2012-01-11 2014-10-07 James M. Jeter Inker assembly for cylindrical can decorators
CN107627729A (zh) * 2017-10-20 2018-01-26 北京中标新正防伪技术有限公司 一种取墨辊
KR102103208B1 (ko) * 2018-06-12 2020-04-22 홍인석 포장필름 인쇄장치의 압동로울러
CN109664600B (zh) * 2018-12-27 2020-09-01 重庆富美包装印务有限公司 食品包装袋的多级颜色印刷生产线

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Also Published As

Publication number Publication date
DE68920395T2 (de) 1995-05-11
CA1330636C (fr) 1994-07-12
JPH02194953A (ja) 1990-08-01
EP0363228A3 (en) 1990-09-19
EP0363228A2 (fr) 1990-04-11
JP3018081B2 (ja) 2000-03-13
DE68920395D1 (de) 1995-02-16

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