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EP1369369B1 - Compensateur d'élargissement avec un courant de fluide - Google Patents

Compensateur d'élargissement avec un courant de fluide Download PDF

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Publication number
EP1369369B1
EP1369369B1 EP03405400A EP03405400A EP1369369B1 EP 1369369 B1 EP1369369 B1 EP 1369369B1 EP 03405400 A EP03405400 A EP 03405400A EP 03405400 A EP03405400 A EP 03405400A EP 1369369 B1 EP1369369 B1 EP 1369369B1
Authority
EP
European Patent Office
Prior art keywords
body structure
rotational
fan
web
compensator according
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
EP03405400A
Other languages
German (de)
English (en)
Other versions
EP1369369A1 (fr
Inventor
Robert Langsch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wifag Maschinenfabrik AG
Original Assignee
Wifag Maschinenfabrik AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wifag Maschinenfabrik AG filed Critical Wifag Maschinenfabrik AG
Publication of EP1369369A1 publication Critical patent/EP1369369A1/fr
Application granted granted Critical
Publication of EP1369369B1 publication Critical patent/EP1369369B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/02—Conveying or guiding webs through presses or machines
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H23/00—Registering, tensioning, smoothing or guiding webs
    • B65H23/02—Registering, tensioning, smoothing or guiding webs transversely
    • B65H23/022—Registering, tensioning, smoothing or guiding webs transversely by tentering devices
    • B65H23/025—Registering, tensioning, smoothing or guiding webs transversely by tentering devices by rollers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/13—Details of longitudinal profile
    • B65H2404/131—Details of longitudinal profile shape
    • B65H2404/1311—Undulations, wavy shape
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/13—Details of longitudinal profile
    • B65H2404/136—Details of longitudinal profile with canals
    • B65H2404/1363—Details of longitudinal profile with canals air supply or suction
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2406/00—Means using fluid

Definitions

  • the invention relates to the compensation of the FanOut by influencing the width of a web which is printed in the printing press.
  • the invention relates both to a fan-out compensator and to a method for compensating the fan-out.
  • the FanOut compensator can already be installed in the printing press or, outside the printing press, for installation for the purpose of FanOut compensation.
  • the printing press is a machine that prints wet, preferably using a dampening solution. Offset printing should be mentioned here as an example.
  • the printing press may be a newspaper printing machine for printing large newspaper editions.
  • the web is preferably endlessly passed through the machine and unwound from a roll, i. the printing machine is in such an embodiment a web-fed printing press and more preferably a web-fed rotary printing press.
  • FanOut In printing presses occur due to liquid penetrated into the web transverse strain changes. This phenomenon known as FanOut has the unfortunate consequence that the width of the web measured transversely to the web conveying direction changes between two printing nips in which the web is printed one after the other. Although the phenomenon of fan-out can basically be caused solely by the color that has penetrated, the FanOut is of practical significance, in particular in the pressure working with dampening solution because of the associated dampening of the web. The web moistened in the upstream print nip swells on its way and becomes the next downstream web nip of the two Pressure column wider. If measures for compensation of the change in width are not taken, this leads to printing errors in the web transverse direction.
  • EP 1 101 721 A1 devices for compensating the FanOut for the web-fed rotary printing are known, with which the web is wavy deformed transversely to its conveying direction, before it enters a subsequent printing nip in which it is printed.
  • the width of the web is corrected in advance for the width change that is expected due to fanout, i. compensated.
  • the invention also relates to fan-out compensators, as are known from EP 1 102 721 A1, and more particularly also relates to the fan-out compensation method that can be carried out therewith.
  • FanOut compensation should not adversely affect the printing process.
  • the invention relates to the FanOut compensation in a printing press with the aid of a FanOut compensator, which comprises a rotary body structure, which is wrapped by a web to be printed.
  • the wrap angle should be at least 3 °. However, a wrap angle of 5 ° or more, for example 10 °, is preferred.
  • the wrap angle can be up to 180 °. Due to the looping and the web longitudinal tension acting in the conveying direction, the web is embossed by the rotary body formation transversely to the conveying direction into a wave profile. The width of the web is reduced by impressing the wavy profile in accordance with the amplitude of the wavy profile to compensate for the enlargement of the width caused by the FanOut.
  • the web should, to the best possible approximation, have the same width in each case in the two printing gaps next to the fanout compensator in the path of the web, ie in the printing gaps between which the fan-out compensator is arranged.
  • a fluid gap is created between the surface of the rotating body structure and the web, so that the web has as small a contact area as possible and preferably no direct contact with the rotating body structure, but is spaced from the surface of the rotating body structure according to the thickness of the fluid gap.
  • An inventive FanOut compensator comprises a rotary body formation, which along its longitudinal axis side by side alternately foot portions and head portions which form a wave-shaped surface to wave shaped to be printed web transverse to the web conveying direction.
  • the foot sections form the wave troughs and the head sections the wave crests of a wave profile.
  • fluid channels are formed, which open at the surface of the rotary body structure.
  • the rotary body structure further has at least one fluid connection connected to the fluid port, via which the fluid channels can be supplied with a pressurized fluid.
  • the pressurized fluid introduced into the fluid passages via the fluid port is guided by the fluid passages to the undulating surface of the rotational body formation and exits under pressure at the estuaries on the surface so that a fluid cushion in the form of said fluid gap exists between the surface and the underside of the web forms.
  • the pressurized fluid is preferably a pressurized gas.
  • Compressed air is particularly preferred.
  • the mouth points of the fluid channels can be distributed over the surface of the rotating body evenly distributed in the axial direction and uniformly in the circumferential direction be.
  • the density of the lands per unit area of the surface may vary periodically with preferably uniform distribution in the circumferential direction in the axial direction with the period of the head and foot portions.
  • the area density of the mouth locations in the surface portions formed by the head portions may be denser than in the surface portions formed by the foot portions to compensate for axial flows from the head portions into the foot portions.
  • the fluid channels may be formed as bores and extend from their mouth points on the surface through the head sections and / or foot sections of the rotary body formation radially inwardly into one or possibly more cavities through which they are connected or connectable to a fluid source.
  • Such holes can be formed in particular straight and unbranched. Holes can be drilled in the immediate sense of the word or can be obtained by another type of machining, for example by means of a laser.
  • Each of the fluid channels may be separate from each of the other fluid channels and each form a single port.
  • the fluid channels or a part of the fluid channels can also branch off to the surface of the rotational body structure and there each form a plurality of mouth points. There may also be cross connections between the fluid channels.
  • the porosity is preferably an open porosity such that the interconnected pores of the porous material form the fluid channels.
  • Particularly suitable for the formation of porous head sections and / or foot sections is the primary shaping by molding a powder, preferably a metal powder, with subsequent or simultaneous sintering of the compact. If the foot sections and / or the head sections form fluid channels due to material porosity, it is also possible subsequently to incorporate bores be so that the fluid channels are in their entirety to a part of pore channels and to another part holes.
  • the head portions and foot portions may be formed separately and arranged alternately along the longitudinal axis side by side.
  • the head portions and the foot portions may be formed by rollers rotatably mounted about the longitudinal axis.
  • the head sections may be mounted rotatably about a common, longitudinal axis and the foot sections about a common, other longitudinal axis, wherein the two longitudinal axes in turn for movement of the wave profile of the rotary body relative to each other are parallel movable, as in particular in EP 1 101 721 A1 is described.
  • the head portions and the foot portions would be rotatably supported in such training about a single, common hollow axis or about two mutually parallel hollow axes, through which the fluid can be supplied.
  • the wave profile acting on the web is not changeable.
  • the rotary body structure is freely rotatable.
  • the rotation body structure does not have to follow the web speed.
  • a rotary bearing of the rotary body structure is nevertheless advantageous, namely to be able to adjust the wave profile formed by the surface of the rotary body structure.
  • a rotational movement of the rotary body structure takes place in a particularly preferred embodiment, however, only for the purpose of adjustment, while the rotational body structure then stands still in the optimally set state, that does not rotate about its longitudinal axis.
  • the longitudinal axis is referred to as the axis of rotation, this may basically also denote a freely rotatable about the rotational axis mounted rotary body structure, but primarily a rotational body structure is meant that only for Purposes of the adjustment of the surface profile formed by it is rotated about its axis of rotation.
  • the rotary body formation is a one-piece rotary body with a surface that is rotationally symmetrical along the longitudinal axis.
  • the wave profile of this body of revolution can not be changed.
  • this rotary body can be freely rotatably mounted about its longitudinal axis, it is preferably not rotatably mounted in a frame of the printing press.
  • the term "body of revolution" is in the case of non-rotatable mounting on the preferably round, particularly preferably rotationally symmetrical about the longitudinal axis surface of the rotating body.
  • a rotary body which forms the radially projecting head portions and the radially rearward foot portions alternately along the longitudinal axis side by side also in one piece, rotatably mounted about the longitudinal axis to change the formed by the head and foot sections wave profile can.
  • the integrality and adjustability features are brought together by increasing the radial height differences between the head portions and the foot portions from minimum values along a first straight line offset parallel to the rotation axis in the circumferential direction around the rotation axis to maximum values , The maximum values have the radial height differences along a second straight line offset parallel to the axis of rotation.
  • the first straight line and the second straight line are preferably tangents to all head sections, if all the head sections have the same radial height with respect to the axis of rotation. If this is not the case, the two straight lines are in each case the tangent to the furthest projecting head section or the group of the furthest projecting head sections. For the adjustment of the rotary body, a rotational movement about the uniform rotation axis for the entire rotary body is sufficient.
  • a rotary body according to the second embodiment is easy to install in the printing press and can be rotatably mounted in the same manner as other rotary body of the printing press, for example, guide rollers.
  • a single, one-piece rotating body forms the entire body of the rotational body FanOut compensator, it should not be excluded that a few such rotary body, such as two or three rotating body or torsionally rigid connected head and foot sections, along a common longitudinal axis, which coincides with the axis of rotation in the second embodiment, are arranged side by side.
  • the acting on the web surface of the rotary body structure is preferably rounded in the circumferential direction everywhere.
  • the surface along the longitudinal axis of the rotary body structure in particular form a circle everywhere.
  • the surface portions formed by the head portions are curved radially outward with respect to the longitudinal axis and the surface portions formed by the foot portions are curved radially inwardly approximately with respect to the longitudinal axis. This preferably applies everywhere over the circumference of the rotational body image.
  • the head and foot portions should smoothly merge on the surface, i. be continuously differentiable at the transition points in the axial direction by passing tangentially into each other.
  • the surface sections formed by head sections are straight in the axial direction over part of their length or over their entire length.
  • the junctions between the surface sections formed by the leg sections and the head sections should smoothly merge into each other over the circumference of the rotary body.
  • a rotary body of head portions and foot portions which are not rotatable relative to each other and are formed in preferred embodiments, all or in part of one or a few bodies of revolution in one piece, facilitates the supply of the surface with the pressurized fluid considerably. While in individual rotatably mounted head and foot sections for each of these head and foot sections a separate fluid rotary connection must be created, sufficient for the relatively non-rotatable head and foot sections a common connection.
  • Such a connection is preferably provided by a hollow axle, on which the head and foot sections, which are not rotatable relative to one another, are mounted.
  • the head and foot sections can each be formed separately and not rotatably mounted on the hollow shaft.
  • the head and foot portions are formed in one piece in a rotating body internally having a cavity, for example a central bore, of sufficient length to supply the fluid to the entire effective surface of the body of revolution.
  • a rotary body which forms all or part of the head andfilabschhitte in one piece, be rotatably mounted on the hollow shaft.
  • the hollow axle may alternatively be replaced by a hollow shaft, i. the rotating body itself forms the one or both bearing journals for its pivotal mounting.
  • Fig. 1 shows a four-high tower with four printing units.
  • the four printing units are arranged in the printing tower one above the other to form two H-bridges.
  • Each of the printing units comprises two blanket cylinders and two plate cylinders, i. one plate cylinder each for one of the blanket cylinders.
  • the blanket cylinders form pressure gaps 1 to 4 between them, through which a web W is conveyed and printed on both sides by the pressing blanket cylinders.
  • an outlet roller is arranged in a known manner, which may be formed as draw rollers to set a specific web tension.
  • the web W is printed in wet offset. In this case, the web W absorbs moisture and swells. Without corrective measures, the transverse to the conveying direction of the web W would measured web width increase from printing nip to printing nip, and it would not match the printed images in the printing columns 1 to 4 consecutively printed images in the transverse direction of the web, ie there would be registration errors in the transverse direction. This phenomenon is known as fanout. The increase in width would be greatest between the two H-bridges, ie between the pressure gaps 2 and 3, since the distance from gap to gap is longer there than between two pressure gaps of a bridge.
  • the web width is reduced on the path of the web W from the printing nip 2 to the printing nip 3 immediately following in the illustrated printing production.
  • a fanout compensator is arranged between the pressure gaps 2 and 3.
  • the fanout compensator comprises a rotary body 6, which can also be used as a deflection roller at the same time.
  • the rotary body 6 is arranged immediately in front of the printing nip 3 and, in this arrangement, simultaneously fulfills the function of the straight guide for the web W, so that the web W enters the printing nip 3 without looping.
  • Fig. 1 an alternative printing position is indicated, in which the web W is guided only by the two lower pressure gaps 1 and 2, while another web W 'guided over the rotary body 6 and just after turning into the next printing gap 3 enters.
  • the rotary body 6 is cylindrical, but unlike a simple, smooth roller has a longitudinally corrugated surface. Wrap and web tension cause the web to deform in accordance with the surface wave pattern of the rotating body 6, thereby reducing the web width.
  • a guide roller 5 via which the web W is guided at an angle to the straight connecting line between the rotary body 6 and the next succeeding pressure gap 3 to the rotary body 6.
  • the web W ' is already angled to this straight Connecting line enters and the rotary body 6 serves in double function as a deflection roller, additional deflection are not required.
  • rotary body 6 is shown in a first embodiment, each in the same cross-section, but in two extreme rotational angle positions.
  • Fig. 4 shows the rotary body in a longitudinal view and partly in longitudinal section.
  • the rotary body 6 is rotatably mounted about a longitudinal axis D in a frame of the printing press.
  • the longitudinal axis D is therefore hereinafter referred to as the axis of rotation.
  • the rotary body 6 is formed in one piece in a process of primary forming or forming, for example, forging in the die, and finished on the surface, preferably only smoothly worked smoothly.
  • the rotary body 6 as a whole with respect to the axis of rotation D is not rotationally symmetrical.
  • the surface of the rotary body 6 forms a straight line T 1 parallel to the axis of rotation D for a single value of a rotational angle running about the axis of rotation D. In all other angles of rotation, the surface has a waveform with a regularly rounded, sinusoidal wave contour in the axial direction.
  • the axial sections of the rotary body 6, which form the wave troughs, are referred to below as foot sections 7 and the axial sections which form the wave crests are referred to below as head sections 8.
  • the radial height difference H D of the wave contour in circumferential direction about the axis of rotation D increases continuously in both directions of rotation up to a second straight line T 2 .
  • the straight lines T 1 and T 2 are diametrically opposite each other with respect to the rotation axis D, ie, the straight lines T 1 and T 2 extend in a plane with the rotation axis D.
  • the radial height difference H D is the amplitude of the wave contour.
  • the radial height differences H D are 4 mm. These maximum height differences, which are the same in the embodiment, should be at least 2 and not more than 10 mm.
  • the straight lines T 1 and T 2 are tangents to the head sections 8, ie they touch the head sections 8 just in their vertices. They come from a head enveloping sections 8 enveloping, straight envelope cylinder. If the tangent T 1 is displaced in parallel on the surface of the enveloping cylinder, the height difference H D , which is measured radially on the axis of rotation D between the vertices of the foot sections 7 and the crests of the head sections 8, increases continuously until the tangent T 2 is reached.
  • FIGS. 2 to 4 Also drawn in FIGS. 2 to 4 is a circular cylinder jacket surface N, behind which the foot sections 7 protrude radially and over which the head sections 8 protrude radially.
  • the cylindrical surface N divides the surface profile into the foot sections 7 and the head sections 8 in each longitudinal section.
  • the foot portions 7 form surface portions 9, and the head portions 8 form surface portions 10.
  • the surface portions 9 and 10 are rounded in the axial direction and in the circumferential direction, preferably continuously curved everywhere. They converge tangentially in the cylindrical surface N, so that in the axial direction everywhere a uniform waveform with continuous, i. continuously differentiable transitions between the surface sections 9 and 10 is obtained.
  • the surface of the rotating body 6 forms a circle throughout the axis of rotation D in cross section.
  • the circle radius in the vertices of the foot portions 7 with r 3 and in the vertices of the head portions 8 with r 4 is designated.
  • the central axes of these vertex circles, designated L 7 and L 8 are eccentric with respect to the axis of rotation D, each with the eccentricity "e”.
  • the central axes L 7 and L 8 extend in the same plane as the rotation axis D.
  • the arcs formed by the surface portions 8 are the same length as the arcs formed by the surface portions 10. These arcs of the surface sections 8 and 9 are particularly preferably the same if the arcs of the surface sections 8 are folded onto the side of the respective straight line of the cylindrical surface N on which the arcs of the surface sections 10 run. This is the case in the exemplary embodiment.
  • the tangent T 1 along which the radial height difference H D has the value "0", extends in the neutral cylinder jacket surface N.
  • a mean web path does not change when the rotary body 6 makes a rotational adjustment movement about the stationary rotation axis D, for example from the rotational angular position of minimum ripple shown in FIG. 2 into the rotational angular position of maximum ripple shown in FIG.
  • the middle path of the web W runs in each rotational angular position of the rotating body 6 on the neutral cylindrical surface N, which is for this reason referred to as "neutral".
  • the rotary body 6 is a hollow body with a central, circular-cylindrical bore 11 extending over its entire length.
  • the hollow bore 12 extends through the bore.
  • the rotary body 6 is rotatably mounted on the hollow shaft 12 about the axis of rotation D. ,
  • the fixed mounting of the hollow axle 12 is designated 16 in FIG.
  • the adjusting rotational movement of the rotary body 6 relative to the hollow shaft 12 is effected by motor means of an electric motor 17 which rotatably drives the rotary body 6 via a gear reduction gear 18.
  • the motor 17 is the actuator of a controller 19 which controls the actuator 17 for the adjustment of the rotating body 6, for example as described in EP 1 101 721 A1, which is incorporated herein by reference.
  • the rotary body 6 is lubver Robinson only for the purpose of adjustment, ie, to change its acting on the web W surface contour. Incidentally, it is locked in the current print production via the gear 18 of the actuator 17.
  • a central, axial bore 13 is formed continuously, which serves to supply the rotary body 6 compressed air. Furthermore, the hollow axle has a longitudinal opening 14.
  • the rotary body 6 is provided with fluid channels 15 which extend radially through the annular jacket of the rotary body 6. Each of the fluid channels 15 is formed as a straight through-hole extending into the inner cavity formed by the bore 11 and secured to the shell outer surface of the rotating body 6, i. on its surface, opens.
  • the fluid channels 15 are arranged distributed uniformly in the circumferential direction about the axis of rotation D of the rotating body 6. They can be incorporated, for example with the aid of a laser in the annular shell of the rotating body 6.
  • the fluid channels 15 are also distributed uniformly along the axis of rotation D.
  • the fluid channels 15 are connected via the hollow shaft 12 with a compressed air source.
  • the compressed air is introduced into the bore 13 of the hollow shaft 12 and passes through the longitudinal opening 14 in the bore 11 and the fluid channels 15.
  • the longitudinal opening 14 extends over a length which is sufficient, the fluid channels 15 over the entire axial length of the wave contour evenly supply the compressed air.
  • the longitudinal opening 14 is widened from the bore 13 to the outer shell surface of the hollow shaft 12 and covers in the circumferential direction more of the fluid channels 15. It opens and spreads towards the bottom of the looping web W.
  • the compressed air thus passes through the bore 13 and the longitudinal opening 14 directly radially under the fluid channels 15, which are covered by the web W.
  • An annular gap formed between the hollow axle 12 and the shell inner surface of the rotary body 6 preferably forms a sealing gap in order to keep compressed air leakage as low as possible.
  • fluid channels 15 are drawn only in the foot section 7 of the relevant cross-section.
  • fluid channels 15 are formed in particular in the head sections 8, as can be seen in the cross section through the apex of a head section 8 in FIG. 5.
  • FIGS. 7 to 14 each show a rotational body 6 of a second exemplary embodiment which has been obtained by machining from an output body 6 'which is rotationally symmetrical about its longitudinal axis and which FIG. 6 shows.
  • Figures 7 to 14 each show a view of an end face of this rotating body 6 and a view on its longitudinal side.
  • the figures show the rotation body 6 in a sequence of angles of rotation, in which the rotation body 6 is rotated by 180 ° in each case in a step of 30 ° from the first position shown in FIG. 7 to the position shown in FIG. In FIGS. 10 and 11, however, the rotational angle position is the same.
  • the output body 6 ' shows a rotationally symmetrical starting body 6 'with respect to the axis of rotation D, from which the adjustable rotational body 6 of the second exemplary embodiment has been produced.
  • the output body 6 ' has along its axis of symmetry S everywhere the same, regular wave contour on its surface. It can be obtained, for example, by compression molding and sintering. Likewise, it can be obtained from a circular cylindrical casting by a material-removing machining.
  • the starting body 6 ' can be obtained by clamping the previously smooth cylindrical casting body with its axis of symmetry S as the axis of rotation into a lathe and axially traversing a lathe of the machine along a template corresponding to the wave contour and thereby forming the wave shape.
  • the output body 6 'thus obtained is rotatably clamped in a subsequent operation about a parallel to the axis of symmetry S processing axis B rotatably.
  • the axis of symmetry S is the central axis L 7 through the vertex circles of the foot sections 7, and the machining axis B is the central axis L 8 through the vertex circles of the head sections 8.
  • the machining axis B therefore has the eccentricity "2e" with respect to the axis of symmetry S of the starting body 6 '.
  • the output body 6 ' is driven in rotation about the machining axis B.
  • the Drehmeisel along the machining axis B is axially straight and on the machining axis B moved radially, so that after introduction of the bore 11 of the asymmetric adjustable rotary body 6 is obtained.
  • the pitch of its wave contour is indicated by way of example for the output body 6 '.
  • the pitch is the distance measured in the axial direction between two adjacent vertices of the head sections 8 - and of course, the axial distance between two adjacent vertices of the foot sections 7. This distance or the pitch is one quarter of the measured width in the axial direction of one in the current Printed production used printing form.
  • the wave contour of the rotating body 6, which was obtained from the starting body 6 ', is of course also a quarter of the printing form width.
  • the rotational body 6 of the second exemplary embodiment has a wave contour that is uniformly uniform in the axial direction only along a single straight line along which the radial height differences H D have their maximum values.
  • the wave contour with the maximum values of the radial height differences H D can be seen in the longitudinal views of FIGS. 7 and 14. Diametrically opposite creates a single, exact line on which consequently the minimum values of the radial height differences H D are again "zero". Over the circumference between these two straight lines, the wave contours in the axial direction in the apex regions of the head sections 8 have straight plateaus, as can be seen from FIGS. 8 to 13.
  • the two inner circles drawn in the end views of FIGS. 7 to 14 are, on the one hand, the vertex circle of the foot sections 7 and, on the other hand, the vertex circle of the head sections 8. All cross sections which lie in the axial direction between the vertex circles of the foot sections 7 and the vertex circles of the head sections 8, deviate from the circular shape according to the manufacturing process.
  • the transitions between the straight plateaus of the head sections 8 and the round foot sections 7 are preferably circular in the circumferential direction and axial direction by surface finishing, for example by grinding and polishing.
  • the fluid channels 15 may only have been incorporated into the asymmetric rotary body 6. They may also be incorporated after receipt of the starting body 6 'in these, or they may finally alternatively have already been incorporated into the straight-cylindrical, smooth cast body, if the starting body 6' was obtained from, for example, such a body. Instead, the starting body 6 'may, for example, have been obtained by pressing and sintering and already form the fluid channels as pore channels due to a correspondingly set material porosity.
  • FIG. 15 shows such a rotary body, which is designated by the reference numeral 60 for the purpose of distinction.
  • the shape and arrangement of the fluid channels 15 in the longitudinal direction and in the circumferential direction of the rotary body 60 are the same as those of the variable rotary body 6.
  • the rotary body 60 may be rotatably supported to reduce the friction with the wrapping web. However, it is also completely sufficient and is even preferred if the rotary body 60 is not rotatably mounted in the machine frame.
  • the symmetry and longitudinal axis is therefore not denoted by D, but to distinguish it from an axis of rotation with L. Incidentally, however, the same reference numerals as used in the variable rotation body 6 are used.
  • an air cushion or a cushion of another gas is not only advantageous in connection with a one-piece rotary body 6 or 60, but also in a rotary body of a plurality of axially juxtaposed rollers and in principle also in other embodiments of rotary bodies.
  • a further embodiments which may be adjustable or not adjustable, but the fluid loading of the invention having wavy surface
  • EP 1 101 721 A1 which is also incorporated herein by reference.
  • the embodiments described there would have to be made of integral rotary bodies or multi-part rotary body formations in the jacket of the rotary body or in the sheaths of the plurality of rotary bodies of a rotary body structure with fluid channels and a fluid connection for the fluid channels.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)
  • Centrifugal Separators (AREA)
  • Discharge By Other Means (AREA)
  • Feeding Of Articles By Means Other Than Belts Or Rollers (AREA)
  • Rotary Presses (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (22)

  1. Compensateur d'allongement en éventail pour une machine d'impression, lequel comprend une structure (6 ; 60) formant corps de révolution qui possède des parties (7) de pied et des parties (8) de tête qui sont alternativement juxtaposées le long d'un axe (D ; L) longitudinal et qui forment une surface (9, 10) ondulée, afin de déformer de manière ondulée, transversalement à une direction de transport d'une feuille (W) continue, la feuille (W) continue qui enlace la structure (6 ; 60) formant corps de révolution,
    caractérisé en ce que des canaux (15) de fluide sont formés dans la structure (6 ; 60) formant corps de révolution, qui débouchent sur la surface (9, 10) de la structure (6 ; 60) formant corps de révolution,
    et en ce que la structure (6 ; 60) formant corps de révolution comporte un raccord (13, 14 ; 11) de fluide relié aux canaux (15) de fluide, afin de diriger un fluide sous pression vers les canaux (15) de fluide et, par les canaux (15) de fluide, sur la surface (9, 10) de la structure (6 ; 60) formant corps de révolution.
  2. Compensateur d'allongement en éventail suivant la revendication 1, caractérisé en ce que la structure (6 ; 60) formant corps de révolution comporte une cavité (11) intérieure dans laquelle débouchent les canaux (15) de fluide.
  3. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que tous les canaux (15) de fluide ou une partie des canaux de fluide sont des perçages.
  4. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que les canaux de fluide sont formés par la porosité du matériau.
  5. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que la structure (6) formant corps de révolution est montée à rotation sur un axe (12) creux ou est fixée sur un arbre creux en étant bloquée en rotation et l'axe (12) creux ou l'arbre creux constitue le raccord (13, 14) de fluide, de sorte que le fluide peut être apporté aux canaux (15) de fluide à travers l'axe (12) creux ou l'arbre creux.
  6. Compensateur d'allongement en éventail suivant la revendication précédente, caractérisé en ce qu'une enveloppe de l'axe (12) creux ou de l'arbre creux est interrompue par une ouverture (14) longitudinale qui s'ouvre en direction radiale directement vers une région en forme de bande, étendue en direction longitudinale et traversée par des canaux (15) de fluide en direction radiale, de la structure (6) formant corps de révolution.
  7. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que les parties (7) de pied et les parties (8) de tête ne sont pas rotatives les unes par rapport aux autres autour de l'axe (D ; L) longitudinal de la structure (6 ; 60) formant corps de révolution.
  8. Compensateur d'allongement en éventail suivant la revendication précédente, caractérisé en ce que la structure (6 ; 60) formant corps de révolution forme les parties (7) de pied et les parties (8) de tête dans une même pièce.
  9. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que les parties (8) de tête dépassent des parties (7) de pied de différences (HD) de hauteur radiales, et les différences (HD) de hauteur radiales augmentent en direction circonférentielle depuis des valeurs minimales, qu'elles prennent le long d'une première droite (T1) décalée parallèlement à l'axe (D) longitudinal, jusqu'à des valeurs maximales qu'elles prennent le long d'une deuxième droite (T2) décalée parallèlement à l'axe (D) longitudinal.
  10. Compensateur d'allongement en éventail suivant la revendication précédente, caractérisé en ce que les valeurs minimales sont égales entre elles, de préférence sont égales à zéro.
  11. Compensateur d'allongement en éventail suivant l'une des deux revendications précédentes, caractérisé en ce que les valeurs maximales sont égales entre elles.
  12. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que les parties (7) de pied forment des parties (9) de surface concaves radialement vers l'extérieur, qui sont différentiables en direction axiale de préférence de manière continue.
  13. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que les parties (8) de tête forment des parties (10) de surface concaves radialement vers l'intérieur, qui sont différentiables en direction axiale de préférence de manière continue.
  14. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que les différences (HD) de hauteur radiales, qui se modifient en direction circonférentielle autour de l'axe (D) longitudinal, sont continues en direction circonférentielle autour de l'axe (L) longitudinal, de préférence continûment différentiables.
  15. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que les différences (HD) de hauteur radiales, qui se modifient en direction circonférentielle autour de l'axe (D) longitudinal, sont égales entre elles le long de tangentes (T1, T2) qui touchent les parties (8) de tête et sont parallèles à l'axe (D) longitudinal.
  16. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que les parties (7) de pied et les parties (8) de tête forment des parties (9, 10) de surface qui se rencontrent sur une surface (N) d'enveloppe cylindrique circulaire neutre, et en ce que l'axe (D ; L) longitudinal de la structure (6 ; 60) formant corps de révolution est un axe médian longitudinal de la surface (N) d'enveloppe cylindrique circulaire neutre.
  17. Compensateur d'allongement en éventail suivant la revendication précédente, caractérisé en ce que les parties (7) de pied, radialement en dessous de la surface (N) d'enveloppe cylindrique circulaire neutre, et les parties (8) de tête, radialement au-dessus de la surface (N) d'enveloppe cylindrique circulaire neutre, forment en direction axiale des arcs d'un contour ondulé de surface de la structure (6 ; 60) formant corps de révolution, et en ce que, dans chaque coupe axiale de la structure (6) formant corps de révolution incluant l'axe (D ; L) longitudinal, les arcs formés par les parties (7) de pied ont la même forme que les arcs formés par les parties (8) de tête, si l'on rabat les arcs formés par les parties (7) de pied sur le côté des arcs formés par les parties (8) de tête.
  18. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que la structure (6 ; 60) formant corps de révolution est disposée dans une machine d'impression, entre une emprise (2) d'impression amont et une emprise (3) d'impression aval dans lesquelles la feuille (W) continue passant lors d'un tirage est successivement imprimée, d'un côté de la feuille (W) continue, et la feuille (W) continue l'enlace.
  19. Compensateur d'allongement en éventail suivant l'une des revendications précédentes, caractérisé en ce que la structure (6) formant corps de révolution est reliée, pour un mouvement de rotation d'ajustement commandé ou régulé autour de son axe (D) longitudinal, à un actionneur (17) d'un dispositif (17, 18, 19) de commande et de régulation.
  20. Compensateur d'allongement en éventail suivant l'une des revendications 1 à 18, caractérisé en ce que la structure (60) formant corps de révolution est fixée dans un bâti d'une machine d'impression sans possibilité de rotation autour de son axe (L) longitudinal.
  21. Compensateur d'allongement en éventail suivant la revendication précédente, caractérisé en ce que la structure (60) formant corps de révolution est à symétrie de révolution par rapport à son axe (L) longitudinal.
  22. Procédé pour compenser l'allongement en éventail dans une machine d'impression, suivant lequel
    a) la feuille (W) continue, dans une première emprise (2) d'impression puis dans une deuxième emprise (3) d'impression, est chaque fois imprimée avec de l'encre d'imprimerie et de préférence mouillée,
    b) et la feuille (W) continue, entre les emprises (2, 3) d'impression, enlace une structure (6 ; 60) formant corps de révolution qui possède une surface (9, 10) qui est ondulée transversalement à une direction de transport de la feuille (W) continue, de sorte que la feuille (W) continue est déformée de manière ondulée transversalement à la direction de transport,
    caractérisé en ce que
    c) la feuille (W) continue, lors de l'enlacement, est sollicitée sur sa face inférieure, tournée vers la structure (6 ; 60) formant corps de révolution, par un fluide sous pression qui émerge sur la surface (9, 10) de la structure (6 ; 60) formant corps de révolution, de sorte qu'un interstice fluidique est produit et maintenu entre la surface ondulée (9, 10) de la structure (6 ; 60) formant corps de révolution et la feuille (W) continue.
EP03405400A 2002-06-06 2003-06-03 Compensateur d'élargissement avec un courant de fluide Expired - Lifetime EP1369369B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10225199 2002-06-06
DE10225199A DE10225199B4 (de) 2002-06-06 2002-06-06 Fluidbeaufschlagter FanOut-Kompensator

Publications (2)

Publication Number Publication Date
EP1369369A1 EP1369369A1 (fr) 2003-12-10
EP1369369B1 true EP1369369B1 (fr) 2006-01-04

Family

ID=29432681

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03405400A Expired - Lifetime EP1369369B1 (fr) 2002-06-06 2003-06-03 Compensateur d'élargissement avec un courant de fluide

Country Status (7)

Country Link
US (1) US6729232B2 (fr)
EP (1) EP1369369B1 (fr)
JP (1) JP2004066808A (fr)
AT (1) ATE314993T1 (fr)
DE (2) DE10225199B4 (fr)
DK (1) DK1369369T3 (fr)
ES (1) ES2254898T3 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10359113A1 (de) * 2003-12-17 2005-07-21 Voith Paper Patent Gmbh Breitstreckvorrichtung
DE102004007378B4 (de) * 2004-02-16 2007-03-01 Koenig & Bauer Ag Vorrichtungen zur Beeinflussung der Breite und/oder Lage einer Bahn
DE102005048246B4 (de) * 2005-10-07 2009-09-10 Maschinenfabrik Wifag Rotationsdruckmaschine mit Längendehnungs-Kompensator und Verfahren zum Bedrucken einer längsgeschnittenen Bahn
FR2964343B1 (fr) * 2010-09-07 2014-02-28 Goss Int Montataire Sa Ensemble d'impression et utilisation correspondante
JP2017078826A (ja) * 2015-10-22 2017-04-27 コニカミノルタ株式会社 画像形成装置及び画像形成システム
CN115724262A (zh) * 2021-08-31 2023-03-03 宁德时代新能源科技股份有限公司 辊组件、电池单体的制造设备及辊的调节方法

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4696230A (en) * 1986-09-25 1987-09-29 Barkley Corporation Adjustable bustle-forming apparatus for maintaining registration of multicolor images on printing webs
US5553542A (en) * 1991-11-06 1996-09-10 Rockwell International Corporation System for controlling a web in a printing press
US5347928A (en) * 1992-10-29 1994-09-20 Sakurai Graphic Systems Corporation Plate clamping unit for offset press
US5365847A (en) * 1993-09-22 1994-11-22 Rockwell International Corporation Control system for a printing press
DE4447859B4 (de) * 1994-10-04 2007-02-22 Maschinenfabrik Wifag Rollenrotationsdruckmaschine
DE59706517D1 (de) * 1996-10-25 2002-04-11 Koenig & Bauer Ag Anordnung zur korrektur des fan-out-effektes an rollenrotationsdruckmaschinen
DE29718907U1 (de) * 1996-10-25 1997-12-18 Koenig & Bauer-Albert Aktiengesellschaft, 97080 Würzburg Vorrichtung zur Korrektur des Fan-Out-Effektes an Rollenrotationsdruckmaschinen
JP2964238B2 (ja) * 1998-03-06 1999-10-18 株式会社東京機械製作所 オフセット印刷機構及びこの印刷機構を有するオフセット印刷機
US6186064B1 (en) * 1998-05-22 2001-02-13 Heidelberger Druckmaschinen Ag Web fed rotary printing press with movable printing units
US6082261A (en) * 1999-03-10 2000-07-04 Heidelberger Druckmaschinen Ag Narrow-gap plate cylinder with plates attached to partially cylindrical shells
DE19955099B4 (de) * 1999-11-16 2010-02-11 Maschinenfabrik Wifag Rotationskörpergebilde für eine Bahnbreitenkorrektur
US6553908B1 (en) * 2000-09-29 2003-04-29 Heidelberger Druckmaschinen Ag Web fanout control system

Also Published As

Publication number Publication date
DE10225199A1 (de) 2004-01-08
JP2004066808A (ja) 2004-03-04
DE50302117D1 (de) 2006-03-30
US20030226459A1 (en) 2003-12-11
ES2254898T3 (es) 2006-06-16
DK1369369T3 (da) 2006-05-15
DE10225199B4 (de) 2004-05-06
ATE314993T1 (de) 2006-02-15
US6729232B2 (en) 2004-05-04
EP1369369A1 (fr) 2003-12-10

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