JP2007119105A - Web processing device for rotary printing machine, folding machine, variable cut-off rotary printing machine and circumferential speed changing method of barrel for rotary printing machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To perform folding processing, or the like of the cut sheet at high accuracy in a variable cut-off type rotary printing machine. <P>SOLUTION: The web processing device provided in a downstream side of a printing device in the rotary printing machine and performing cutting to the web 10 conveyed on a traveling route is provided with a first barrel 21 having a blade 23 for applying cutting and rotating at a rotation speed according to rotation of a printing barrel of the printing device; and a second barrel 22 having a receiving part 25 arranged so as to be opposed to the first barrel 21 and installed with a receiving surface for receiving a blade tip of a blade 23 and rotating in synchronization with the first barrel 21. Any first barrel 21 and second barrel 22 are provided with a means for changing a radial position of the blade tip or the receiving surface to an axis of a rotation shaft 101 for supporting the blade or the receiving part; and a means for changing an axis position of the rotation shaft 101. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a web processing apparatus for a rotary printing press that can be used in a variable cut-off type rotary printing press capable of changing the cut-off (cutting length) of the web, and a folding machine equipped with the web processing device. And a variable cut-off rotary printing press and a method for changing the peripheral speed of the cylinder of the rotary printing press.

FIG. 13 is a schematic configuration diagram showing an example of a commercial offset rotary press as one of rotary presses, and FIG. 14 is a folding machine (web cutting device and paper discharge device) employed in the commercial offset rotary press. FIG. 15 is a schematic configuration diagram for explaining an example of the folding device unit of the folding machine.
As shown in FIG. 13, a general commercial web offset press includes, as main constituent units, a sheet feeding device unit 1, an infeed device unit 2, a printing device unit 3, a drying device unit 4, a cooling device unit 5, and the like. The web path unit 6, the folding machine 7, and the paper discharge unit 8 that carries out the folded book formed in the folding machine 7 to the outside. In the paper feeding unit 1, a new web roll 1b to be used next to the currently used web roll 1a is kept waiting. The printing apparatus unit 3 includes an appropriate number (here, four) of printing units 3a to 3d for each printing color.

  As shown in FIG. 14, the folding machine 7 and the paper discharge device unit 8 include a drag roller 11, a triangular plate 12, a pair of lead-in rollers 13 a and 13 b, a pair of nipping rollers 14 a and 14 b, a web cutting device (simply a cutting device). 20 ', an acceleration conveyor belt device 30, a folding device 40B, a paper discharge conveyor 46, a sheet alignment stacking device 80 (not shown), and the like (see FIG. 13).

  Further, the configuration and function of each part will be described. The triangular plate 12 is a state in which the web 10 fed through the drag roller 11 is folded in half along the traveling direction and is overlapped through the lead-in rollers 13a and 13b. Is sent downstream. The downstream nipping rollers 14a and 14b sandwich and rotate the web 10 and press the web 10 folded in two layers to form a more reliable vertical fold.

  The cutting device 20 ′ is a device that cuts the two webs 10 with a predetermined cut-off (cutting length), and includes a pair of saw cylinders 21 and a receiving cylinder 22 that rotate opposite to each other. The saw body 21 is provided with a saw base 24 in which a saw-like knife (saw blade) 23 ′ is incorporated along the axial direction on the outer peripheral surface. The receiving cylinder 22 is provided with a rubber base 25 formed of an elastic body such as rubber as a receiving member for the saw blade 23 '.

  The phase position is set so that the saw blade 23 ′ provided in the saw cylinder 21 and the rubber base 25 provided in the receiving cylinder 22 mesh with each other, and the web 10 that has been fed in is rotated by synchronously opposing rotation. It cut | disconnects in a horizontal direction (width direction of the web 10), and forms the single sheet | seat (folded book) 10a. In this example of the apparatus, a pair of saw blades 23 ′ and a pair of rubber bases 25 are provided on the saw cylinder 21, and the pair of the saw cylinder 21 and the receiver cylinder 22 are thus paired. Cutting once per rotation can be performed.

  The acceleration conveyor belt device 30 includes a pair of opposed conveyor belts 31 and 32, and each of the conveyor belts 31 and 32 travels while being wound around a plurality of guide rollers 33 arranged in a set. It is configured to be arbitrarily changeable to some extent. The transport belts 31 and 32 receive the sheet 10a cut by the cutting device 20 '(here, a sheet obtained by cutting the web 10 which is continuous paper is referred to as a sheet) 10a, and then sandwiches the sheet 10a. The sheet 10a is raised to the traveling speed corresponding to the speed of the downstream folding device 40 at the moment when it is nipped and transferred to the folding device 40.

  As shown in FIG. 15, the folding device 40 includes a gripping cylinder 42 provided with a clamping device 41, and a folding cylinder 45 provided with a claw device (hereinafter simply referred to as a claw) 43 and a folding blade 44. In the process of gripping the tip of the sheet 10a fed through the conveyor belts 31 and 32 with the claw 43 and rotating it, the folding blade 44 of the folding cylinder 45 and the clamping device 41 of the clamping cylinder 42 are transferred. The sheet 10a delivered to the gripping device 41 at this engagement position is folded and folded at a fold line perpendicular to the conveying direction.

The illustrated folding device 40 is provided with two sets of gripping devices 41 on the gripping cylinder 42 and two sets of claws 43 and two sets of folding blades 44 on the folding cylinder 45 side. Two sets of origami 10b can be formed by rotating each cylinder 42, 45 once.
The paper discharge conveyor 46 is configured to transfer the folded book 10b formed as described above to the next process, that is, the sheet alignment stacking device 80 (see FIG. 13). As the sheet aligning and stacking unit, for example, as shown in FIG. 13, the folded book 10b is transferred to the impeller 81 and transferred to the next paper discharge conveyor 82 to be stacked (not shown). There is a form such as sending to.

With such a configuration, when the printed continuous paper web 10 is cut to a predetermined cut-off by the saw cylinder 21, the cut-off: C, the web traveling speed (conveying speed): Vo, and the saw cylinder rotation speed: Assuming Nc and the number of saw blades: n, the cutoff C is
C = Vo / (Nc · n)
It becomes.

The cut sheet 10a is accelerated at a stretch from the traveling speed Vo of the web 10 to the speed of the folding device 40 (that is, the peripheral speed of the folding cylinder 45) Vb by the conveyor belts 31 and 32, and is folded at the traveling speed Vb. 45.
Subsequently, the sheet 10a sent out from the conveyor belts 31 and 32 is transferred to the claw 43 of the folding cylinder 45, and the next folding (bending folding) is performed.

  In addition, as a folding machine (that is, a folding machine for a variable cut-off type rotary printing press) that can cope with a change in cut-off, there is one disclosed in Patent Document 1, for example. In this folding machine, a cutting cylinder and a delivery cylinder for cutting the ribbon (web) into a signature having a desired cut-off length in cooperation with the cutting cylinder are provided. An adjustable diameter portion is provided having a central axis and a peripheral surface region and disposed in the peripheral surface region of the transfer cylinder, the adjustable diameter portion being connected to the transfer cylinder and a desired signature In order to adjust the cut-off length, it is movable toward and away from the barrel center axis. Further, a jaw cylinder is provided. The jaw cylinder has a trunk jacket and a jaw provided on the trunk jacket. Further, the jaw cylinder is provided in the peripheral surface area of the delivery cylinder and the signature is folded into the jaw. For this purpose, a pushing blade that cooperates with each other is provided, so that it can cope with a change in cut-off.

Further, as a method of folding the sheet, as described above, the folding device 40 including the gripping cylinder 42 including the gripping device 41 and the folding cylinder 45 including the claw 43 and the folding blade 44 is used. In addition to the method, there is a method using a chopper, such as a chopper folding device disclosed in Patent Document 2, for example.
However, when the cutting length of the web 10 is changed by the conventional rotary press for a rotary press as shown in FIGS. 13 to 15, in the rotary press for the rotary press, the acceleration conveyance belt device 30 is provided with a web. The sheet 10a is operated at a constant speed so that the sheet 10a is conveyed at a conveying speed (peripheral speed of the folding cylinder 45) Vb of the folding device 40 that is higher than the traveling speed Vo of 10. For this reason, when the sheet 10 a is received from the cutting device 20 ′ by the acceleration conveyance belt device 30 immediately after being cut by the cutting device 20 ′, the sheet 10 a traveling at the traveling speed Vo of the web 10 is transferred to the acceleration conveyance belt device 30. At the moment of reception, the traveling speed is accelerated from the speed Vo to the higher speed Vb.

  Therefore, even if a slight deviation of the cutting completion timing in the cutting device 20 ′ occurs, the delivery of the sheet 10 a from the cutting device 20 ′ to the variable speed conveyance belt device 30 is displaced, and this causes the deviation from the variable speed conveyance belt device 30. It is difficult to ensure sufficient folding accuracy (folding position or folding phase accuracy) due to a shift in the delivery timing of the sheet 10a with the folding device 40.

In particular, when each of the above deviations accumulates, not only the folding accuracy is lowered, but also a poor delivery between the accelerating and conveying belt device 30 and the folding device 40 may be caused and the operation of the device may be forced to stop.
In view of this, the present applicant has proposed a technology for a folding machine for a rotary printing press that can perform folding processing on a cut sheet with high accuracy even in a variable cut-off type rotary printing press ( Patent Document 3).

  This rotary machine for a rotary printing press is provided downstream of the printing device in the rotary printing press, and as shown in FIG. 16, includes a plurality of conveyor belt devices 51, 52, 53, and conveys the web 10 at a predetermined speed. A cutting device 20 that includes a device 50, a first cutting mechanism 20A, and a second cutting mechanism 20B, and cuts the web 10 into a predetermined cut-off (cutting length). 40 and a paper discharge conveyor belt 46. Hereinafter, each of these components will be described in order from the upstream side.

  The upstream conveyor belt device 51 includes a pair of endless conveyor belts (nipping belts) 51a and 51b, and the web 10 fed by being overlapped by the triangular plate 12 (see FIG. 14) is fed between the conveyor belts 51a and 51b. It is pinched and conveyed at the same speed as the upstream web conveyance speed V0. Each of the conveyor belts 51a and 51b includes a plurality of belts that are separated in the width direction and arranged in parallel, and is guided by a guide roller 51c and driven by a driving roller 51d.

  The first cutting mechanism 20A is a mechanism that partially cuts the two stacked webs 10 with a predetermined cut-off, and includes a pair of saw cylinders 21 and a receiving cylinder 22 that rotate opposite to each other. The saw body 21 is provided with a saw base 24 in which a saw-shaped knife (saw blade) 23a is incorporated in the outer peripheral surface along the axial direction. The receiving cylinder 22 is provided with a rubber base 25 formed of an elastic body such as rubber as a receiving member of the saw blade 23a. In particular, the knife 23a is an intermittent knife having a cutting edge intermittently, and the web 10 is partially cut into a perforation with a predetermined cut-off (this cutting is also referred to as intermittent cutting or partial cutting). It has become.

  The midstream portion conveyor belt device 52 includes a pair of endless conveyor belts (also referred to as nipping belts) 52a and 52b, and is fed by being cut into a perforated shape by the first cutting mechanism 20A with a predetermined cut-off. 10 is sandwiched between the conveyor belts 52a and 52b and conveyed at the same speed as the upstream web conveyance speed V0. Each of the transport belts 52a and 52b of the midstream transport belt device 52 is a belt in which a belt having a predetermined width or less is separated in the width direction and arranged in parallel, and is a cut portion cut by the first cutting mechanism 20A. Are arranged so as not to protrude in the width direction from the cut portion, and are guided by the guide roller 52c and driven by the drive roller 52d.

  The second cutting mechanism 20B is intermittently cut in a perforation with a predetermined cut-off by the first cutting mechanism 20A, and is not cut by the first cutting mechanism 20A with respect to the web 10 conveyed by the conveying belt device 52. This is a mechanism that cuts the remaining portions and completes the cutting, and includes a pair of saw cylinders 21 and a receiving cylinder 22 that rotate opposite to each other. The saw body 21 is provided with a saw base 24 in which a saw-shaped knife (saw blade) 23b is incorporated along the axial direction on the outer peripheral surface. The receiving cylinder 22 is provided with a rubber base (receiving portion) 25 formed of an elastic body such as rubber as a receiving member of the saw blade 23b. It should be noted that the intermittent cutting phases of the first and second cutting mechanisms 20A and 20B coincide with each other so that the intermittent cutting position by the first cutting mechanism 20A and the intermittent cutting position by the second cutting mechanism 20B are aligned. Adjusted to

  In this way, in the cutting device 20, the web 10 fed in by the first and second cutting mechanisms 20A, 20B of the upstream and downstream two stages including the first cutting mechanism 20A and the second cutting mechanism 20B is horizontal ( The sheet is cut in a direction orthogonal to the traveling direction) to form a single-leaf sheet (folded book) 10a. In the example of this apparatus, the saw cylinder 21 and the receiving cylinder 22 of the first and second cutting mechanisms 20A and 20B are cut once per rotation.

  The downstream conveyance belt device 53 provided downstream of the cutting device 20 includes a pair of endless conveyance belts (also referred to as nipping belts) 53a and 53b, and is cut with a predetermined cut-off by the second cutting mechanism 20B. The sheet 10a is nipped between the guide belts 53a and 53b from the midstream conveyance belt device 52 and conveyed to the downstream folding device 40. The guide belts 53a and 53b of the downstream conveyance belt device 53 are also a plurality of belts having a predetermined width or less arranged in parallel, and the guide belts 52a and 52b of the midstream conveyance belt device 52 have a predetermined width or less. The belts are arranged with a space therebetween, and are guided by the guide rollers 53d, 53e, 53f, 53g and driven by the drive roller 53c.

  However, the sheet 10a is conveyed at the same speed as the web conveyance speed V0 in the midstream conveyance belt device 52 that receives the sheet 10a, whereas it is different from the web conveyance speed V0 in the folding device 40 that delivers the sheet 10a. Since the sheet 10a is transported at the speed Vb, the downstream transport belt device 53 needs to shift (accelerate) the sheet 10a received at the transport speed V0 to the transport speed Vb and transfer it to the folding device 40. Therefore, the downstream conveyance belt device 53 is configured as a variable conveyance belt or a transmission belt. That is, the roller 53c at the lower end of the conveyor belt 53a is a transmission roller that drives the conveyor belts 53a and 53b to change speed, and the speed of the guide belts 53a and 53b is changed by changing the rotational speed of the transmission roller 53c. It is like that.

  According to this technique, the printing device and the cutting device perform web printing at a constant speed for printing and cutting, and the cut sheet 10 a is transferred from the middle-stream conveyance belt device 52 in the downstream conveyance belt device 53. When the sheet 10a is received, the sheet 10a is received at a speed substantially the same as the sheet conveyance speed of the midstream conveyance belt device 52, and then the sheet conveyance speed is changed during conveyance of the sheet to the folding device 40. When handing 10a, the paper is delivered at a speed substantially equal to the sheet conveying speed of the folding device 40. Therefore, the sheet 10a is received at a constant speed when it is transferred from the midstream conveying belt device 52 to the downstream conveying belt device 53 and when it is transferred from the downstream conveying belt device 53 to the folding device 40. As a result, the cut sheet can be processed with high accuracy.

In particular, in a rotary printing machine (so-called variable cut-off rotary press) configured to be able to cut by changing the cutting length of the web fed from the printing apparatus, the conveyance speed of the web 10 is set to the cutting apparatus. Is set to a speed corresponding to the cutting length (cut-off length) of the sheet to be cut, and the sheet conveying speed of the midstream conveying belt device 52 is set to be equal to the web conveying speed. The web cut-off length can be appropriately changed.
JP 2001-233545 A Japanese Patent No. 2532507 WO2005 / 056451

  However, according to the technique of Patent Document 3, although the cut-off length of the web 10 can be appropriately changed, the conveyance speed of the web 10 is changed to a speed corresponding to the cut-off length of the web 10. By doing so, the cut-off length of the web 10 is changed, so that the traveling speed (conveying speed) of the web 10 does not match the rotational speed (circumferential speed) of the saw cylinder 21 and the receiving cylinder 22. .

That is, in order to increase the cutting length of the web 10 while keeping the rotation speed (circumferential speed) of the saw cylinder 21 and the receiving cylinder 22 constant, the conveyance speed of the web 10 is increased and the cut-off length of the web 10 is decreased. For this purpose, the conveyance speed of the web 10 is reduced.
As a result, the cutting edges of the knives (saw blades) 23a and 23b of the saw cylinder 21 and the receiving surfaces of the rubber base (receiving part) 25 of the receiving cylinder 22 cut the web 10 with a speed difference. The following problems arise.
(1) If there is a speed difference, the web is torn or damaged because the web is cut by hooking the web with a saw blade.
(2) Since the cutting is performed while the web is sandwiched between the blade edge of the saw blade and the receiving surface of the rubber base (receiving portion), if there is a speed difference, the web is likely to wrinkle.
(3) Since the web is sandwiched between the blade edge of the saw blade and the receiving surface of the rubber base (receiving part), if there is a speed difference, the web tension will fluctuate and the web will be cut (paper cut). There is a risk of inviting.

Such a problem occurs not only when the web is cut by a folding machine or a sheeter, but also by a device that generates a binding force on the web, such as a machine that perforates the web.
The present invention was devised in view of the above problems, and in a rotary printing machine, the web cut-off length and the perforation interval are set while matching the peripheral speed of the cutting device with the peripheral speed of the printing cylinder of the printing device. An object of the present invention is to provide a web processing apparatus for a rotary printing press, a folding machine, a variable cut-off rotary printing press, and a method for changing the peripheral speed of a cylinder of the rotary printing press that can be changed.

  In order to achieve the above object, a web processing apparatus for a rotary printing press according to the present invention is provided downstream of a printing apparatus in a rotary printing press, and is fed from the printing apparatus and conveyed by a conveying apparatus (for example, a conveying belt apparatus). A web processing apparatus that performs any cutting of a full cut and a partial cut including perforation on a web conveyed on a running route, the web processing device being provided along the running route, wherein the cutting is performed on the web A first cylinder that rotates at a rotational speed corresponding to the rotation of the printing cylinder of the printing apparatus, and is disposed to face the first cylinder across the travel path, and when the web is cut A receiving portion equipped with a receiving surface for receiving the cutting edge of the blade, and a second cylinder that rotates in synchronization with the first cylinder, the first cylinder and the second cylinder both having the blade Or a rotating shaft that supports the receiving portion; A radial position changing means for changing the radial position of the cutting edge or the receiving surface with respect to the axis of the rotating shaft, and an axis position changing means for changing the axis position of the rotating shaft. It is characterized (claim 1).

It is preferable that the rotary shaft is equipped with a balancer weight for the blade or the receiving portion (Claim 2).
Further, an eccentric shaft having an axis that is eccentric with respect to the axis of the rotating shaft is equipped so as to rotate integrally with the rotating shaft, and the blade or the receiving portion is coupled to the eccentric shaft, The radial position changing means is preferably configured to change the radial position of the cutting edge or the receiving surface by rotating the eccentric shaft relative to the rotating shaft. 3).

  In this case, the rotating shaft is configured to be hollow, the eccentric shaft is provided in the hollow so as to be rotatable relative to the rotating shaft, and the blade or the receiving portion protrudes outward from the eccentric shaft. Preferably, the rotating shaft is provided with a first notch portion that allows relative rotation of the first leg portion during the relative rotation of the eccentric shaft. Claim 4).

Further, the rotary shaft is equipped with a balancer weight with respect to the blade or the receiving portion via a second leg portion protruding outward from the eccentric shaft, and the rotary shaft has the relative position of the eccentric shaft. It is preferable that a second cutout portion that allows relative rotation of the second leg portion during rotation is provided.
Even if the radial position of the cutting edge or the receiving surface with respect to the axis of the rotating shaft is changed by the radial position changing means, the balancer weight, the blade or the receiving portion, the eccentric shaft, and the rotation The weight balance of each part is set so that the rotational center of gravity of the first cylinder or the second cylinder including the shaft always coincides with the rotation center. It is preferable that it can always be rotated without causing rotational shake (claim 6).

In particular, depending on the setting of the center of gravity and weight of the eccentric shaft that is a part of the rotating body, it is possible to prevent the weight balance of the saw cylinder and the entire receiving cylinder from changing even if the eccentric shaft is rotated. The center of gravity and the weight of the eccentric shaft are preferably set in this way.
It is preferable that a relative position fixing means for fixing the eccentric shaft at a predetermined relative rotational position with respect to the rotation shaft is provided. For example, a bolt is provided on one of the eccentric shaft and the rotating shaft in parallel with the axial direction, and on the other side, a bolt hole that is concentric with the bolt at a predetermined relative rotational position is provided. The relative position fixing means can be configured so that the eccentric shaft and the rotary shaft are fastened together by being inserted and fastened by a nut. Alternatively, a bolt hole is provided on both the eccentric shaft and the rotating shaft so as to be concentric at a predetermined relative rotational position, the bolt is inserted into the bolt hole, and the eccentric shaft and the rotating shaft are fastened by a nut. The relative position fixing means can be configured so as to be fastened together. Of course, a plurality of predetermined relative rotational positions are provided.

A bearing supporting member for supporting the rotating shaft; and a bearing supporting member for supporting the bearing eccentrically, wherein the shaft center position changing means changes the rotational position of the bearing supporting member to change the shaft of the bearing. It is preferable that the center position is changed (claim 8).
In this case, it is preferable that an actuator for changing the rotational position of the bearing support member and a bearing support member fixing means for fixing the bearing support member at a predetermined rotational position are provided. For example, an air cylinder can be used as the actuator. As for the bearing support member fixing means, for example, the actuator biases the bearing support member in the forward rotation direction or the reverse rotation direction by an actuator, and a stopper that resists this biasing force is provided. It may be fixed.

  A first gear disposed coaxially with a rotation center of the first cylinder or the second cylinder, a second gear fixed to the rotation shaft, and rotatably supported by the eccentric shaft; An intermediate gear that meshes with both the first gear and the second gear; and a rotational force that is input to the first gear when the axial position is changed, and the rotary shaft via the intermediate gear and the second gear. It is preferable to provide a motor that changes a relative phase with the eccentric shaft.

  Further, the folding machine for a rotary printing press of the present invention is provided downstream of the printing device in the rotary printing press, provided with a cutting device for cutting a web fed from the printing device, and downstream of the cutting device, A folding machine having a processing device for processing a sheet cut by the cutting device, wherein the web processing device for a rotary printing press according to any one of claims 1 to 10 is provided as the cutting device. (Claim 11).

  In this case, the processing device is provided with a rotating drum for processing the sheet, and the cutting device is configured to change the radial position of the blade edge or the receiving surface by the radial position changing means and the axial position. The change means is configured to be able to cope with a change in the cutting length of the web by changing the axial center position of the rotating shaft, and the processing device can change the cutting length of the web by changing the rotation speed of the rotating drum. The sheet conveying path from the cutting apparatus to the processing apparatus is configured to be able to cope with a change, and the sheet conveying speed is changed from a speed synchronized with the cutting apparatus in the course of conveying the sheet. It is preferable that the axis position of the rotating shaft is set by a changing means provided with a variable speed transfer device that changes the speed to a speed synchronized with the rotation speed.

Further, the variable cut-off rotary printing of the present invention includes the folder for a rotary printing press according to claim 11 or 12, and is configured to be capable of being cut by changing the cut length of the printed web. (Claim 13).
The method for changing the peripheral speed of the cylinder of the rotary printing press according to the present invention corresponds to the cylinder that processes the web conveyed on the travel path of the printing apparatus and the travel speed of the web. A rotation radius changing means for changing the rotation radius of the cylinder surface with respect to the rotation axis of the cylinder, and an axis position changing means for changing the axis position of the rotation axis of the cylinder. The circumferential speed of the cylinder is changed by changing the rotation radius and changing the axial position by the axial position changing means (claim 14).

  The cylinder has a rotation shaft provided concentrically with the rotation axis of the cylinder, and an axis that is eccentric with respect to the rotation axis of the cylinder, and is eccentric so as to rotate integrally with the rotation shaft. And a bearing supporting member for supporting the rotating shaft eccentrically and a bearing support member for supporting the bearing eccentrically, and the turning radius changing means rotates the eccentric shaft relative to the rotating shaft. The shaft surface position changing means is configured to change the shaft position of the bearing by changing the rotation position of the bearing support member. (Claim 15).

According to the web processing apparatus for a rotary printing press of the present invention, the first cylinder and the second cylinder are synchronously rotated with respect to the web printed by the printing apparatus in the rotary printing press and conveyed on the travel path by the conveying device. Then, cutting such as full cutting, partial cutting (intermittent cutting), or perforation is performed by cooperating the blade of the first cylinder and the receiving part of the second cylinder.
At this time, the first cylinder and the second cylinder are rotated at a rotation speed corresponding to the rotation of the printing cylinder of the printing apparatus, that is, the peripheral speeds of the first cylinder and the second cylinder (that is, the blades of the first cylinder). Since the speed difference between the blade edge and the receiving surface and the web is eliminated by making the blade edge and the receiving surface speed of the receiving portion of the second drum coincide with the traveling speed of the web, it is likely to occur when there is a speed difference during cutting. It is possible to avoid the occurrence of problems such as web tears, scratches, web wrinkles, and web cutting (paper breaks).

  The first cylinder and the second cylinder both have a radial position changing means for changing the radial position of the blade edge or the receiving surface with respect to the axis of the rotary shaft that supports the blade or the receiving portion, and the rotary shaft. In order to change the cutting length of the web (so-called cut-off length or perforation interval in the web traveling direction), the blade edge is provided. In addition to changing the radial position of the blade edge and the receiving surface so that the circumferential length of the rotating circle of the receiving surface corresponds to the cutting length of the web, according to this, if the axial center position of the rotating shaft is changed, Even if the cutting length of the web is changed, the circumferential speed of the first cylinder and the second cylinder and the traveling speed of the web can be matched, and at the time of cutting, the web is torn, scratched, web wrinkles, Occurrence of problems such as web cutting (breaking paper) can be avoided. Above, claim 1).

In addition, by providing a balancer weight for the blade or the receiving portion on the rotating shaft, even when the radial position of the blade or the receiving portion is changed, the center of gravity of the first body or the second body is made to coincide with the rotational axis. Therefore, each cylinder can be rotated smoothly (claim 2).
In addition, by coupling the blade or the receiving portion to an eccentric shaft that has an axis that is eccentric with respect to the axis of the rotating shaft and rotates integrally with the rotating shaft, and rotating the eccentric shaft relative to the rotating shaft, If the radial position changing means is configured so as to change the radial position of the blade edge or the receiving surface, the radial position can be easily adjusted by simply rotating the eccentric shaft relative to the rotation axis without attaching or detaching the blade or the receiving portion. Can be changed (Claim 3).

  In particular, the rotating shaft is hollow, the eccentric shaft is provided in the hollow so as to be rotatable relative to the rotating shaft, and the blade or the receiving portion is provided via a first leg portion protruding outward from the eccentric shaft. If the first cutout portion that allows the relative rotation of the first leg portion during the relative rotation of the eccentric shaft is provided on the rotation shaft, the eccentric shaft is rotated with respect to the rotation shaft as described above. It is possible to reliably realize the change of the radial position by only (claim 4).

  In addition, when providing a balancer weight for the blade or the receiving portion on the rotary shaft, the balancer weight is equipped via a second leg portion protruding outward from the eccentric shaft, and the rotary shaft is provided with the relative rotation of the eccentric shaft. If the second cutout portion that allows the relative rotation of the second leg portion with time is provided, the radial position of the radial position can be obtained simply by rotating the eccentric shaft with respect to the rotation shaft, as described above. The change can be surely realized (claim 5).

In addition, since the weight balance of each part is set so that the rotational center of gravity of the first cylinder or the second cylinder always coincides with the center of rotation, the first cylinder or the second cylinder does not always cause rotational blurring. It can be rotated (claim 6).
In addition, by providing relative position fixing means for fixing the eccentric shaft at a predetermined relative rotational position with respect to the rotation axis, the blade or the receiving portion is set at a predetermined radial position in the first and second cylinders. Each cylinder can be operated smoothly (claim 7).

Further, if a bearing support shaft that eccentrically supports the bearing that supports the rotation shaft is provided, and the shaft center position changing means is configured to change the shaft center position of the bearing by changing the rotation position of the bearing support shaft, The axial center position of the rotating shaft can be changed smoothly (claim 8).
Furthermore, if the rotational position of the bearing support shaft is changed by an actuator, the bearing support shaft that supports the heavy rotational shaft can be easily rotated. Also, by providing a bearing support shaft fixing means for fixing the bearing support shaft at a predetermined rotational position, the rotational position of the bearing support shaft is adjusted to a predetermined position, and the axial center position of the rotational shaft is set to a predetermined state. Thereafter, the rotating shaft can be reliably supported (claim 9).

  A first gear disposed coaxially with the rotation center of the first cylinder or the second cylinder; a second gear fixed to the rotation shaft; and a first gear rotatably supported on the eccentric shaft; An intermediate gear meshing with both the second gear and a rotational force is input to the first gear when the axial position is changed, and the relative phase between the rotary shaft and the eccentric shaft is changed via the intermediate gear and the second gear. By providing the motor, it is possible to automatically change the position of the shaft center by rotating the eccentric shaft with respect to the rotation shaft.

  Further, according to the folding machine for a rotary printing press and the variable cut-off rotary printing press according to the present invention, the web processing device does not generate a speed difference between the blade edge and the receiving surface and the web, and the web is torn at the time of cutting. , While avoiding the occurrence of defects such as scratches, web wrinkles, and web cutting (sheet breakage), the sheet cut by the processing device can be folded into a high-quality printed product (claim) Item 11, 13).

  When the processing apparatus is provided with a rotating drum for processing the cut sheet, the cutting apparatus changes the radial position of the blade edge or the receiving surface by the radial position changing means and the axis of the rotating shaft by the axial position changing means. The processing apparatus responds to the change in the cutting length of the web by changing the rotation speed of the rotating drum. In the sheet conveyance path from the cutting device to the processing device, a variable speed conveyance device that changes the conveyance speed of the recording sheet from a speed synchronized with the cutting apparatus to a speed synchronized with the processing apparatus during the sheet conveyance. Therefore, in the cutting apparatus, not only the speed difference between the sheet and the blade is eliminated, but also in the processing apparatus, the speed difference between the sheet and the rotary drum is eliminated. Folding or the like can be performed while avoiding the occurrence of problems such as tearing, scratching, and wrinkles (claims 12 and 13).

  Further, according to the method for changing the peripheral speed of the cylinder of the rotary printing press according to the present invention, the rotation radius of the cylinder surface with respect to the rotation axis of the cylinder is changed according to the traveling speed of the web, and the axis of the rotation axis of the cylinder is changed. By changing the center position, it is possible to easily change the peripheral speed of the cylinder, and this makes it possible to nest without the speed difference between the blade edge and the receiving surface and the web, so the speed difference required at the time of cutting is It is possible to avoid the occurrence of problems such as web breaks, scratches, web wrinkles, and web cuts (paper cuts) that are likely to occur.

  Further, the barrel is configured to have a rotation shaft provided concentrically with the rotation axis of the barrel, and an eccentric shaft equipped to be eccentric with respect to the rotation axis of the barrel and rotate integrally with the rotation shaft. The bearing surface is supported by changing the radius of rotation of the barrel surface by rotating the eccentric shaft relative to the rotating shaft so that the bearing supporting the rotating shaft and the bearing supporting member supporting the bearing eccentrically are provided. If the axial position of the bearing is changed by changing the rotational position of the member, the peripheral speed of the cylinder can be changed more easily (claim 15).

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
1 to 7 show a web cutting device (also simply referred to as a cutting device) as a web processing device for a rotary printing press according to an embodiment of the present invention, and FIG. 1 shows the configuration of the cylinder of the web cutting device. 2 is a longitudinal sectional view showing the configuration of the barrel of the web cutting device, FIGS. 3 and 4 are perspective views showing the configuration of the barrel of the web cutting device, and FIGS. FIG. 7 is a longitudinal sectional view showing the configuration of the drive system of the web cutting device. Further, a rotary machine and a rotary printing machine equipped with the web cutting device will be described with reference to FIGS. 13, 14, and 16 described as the prior art.

  For example, as shown in FIG. 13, the rotary printing press according to the present embodiment includes, as main constituent units, a sheet feeding device unit 1, an infeed device unit 2, a printing device unit 3, a drying device unit 4, and a cooling device unit 5. , Web path unit 6, folding machine 7, and paper discharge unit 8 for carrying out the folded book formed in folding machine 7 to the outside. In the paper feeding unit 1, a new web roll 1b to be used next to the currently used web roll 1a is kept waiting. The printing apparatus unit 3 includes a number of printing units 3a to 3d as appropriate for each printing color.

  In addition, the web conveyance speed V0 in the sheet feeding device unit 1, the infeed device unit 2, the printing device unit 3, the drying device unit 4, the cooling device unit 5, the web pass unit 6, and the folding machine 7 is the cutoff of the web 10 ( The speed is set according to the cutting length. For example, to make the cut-off relatively long, the web transport speed V0 is set to a relatively high speed, and to make the cut-off relatively short, the web transport speed V0 is set to a relatively low speed.

  The rotary printing press folding machine 7 according to the present embodiment is disposed downstream of the drag roller 11 and the triangular plate 12 (see FIG. 14), and is configured in the same manner as that of Patent Document 3 already described. That is, as shown in FIG. 16, the rotary machine 7 for a rotary printing press includes a transport device 50 that includes a plurality of transport belt devices 51, 52, and 53 and transports the web 10 at a predetermined speed, and a first cutting mechanism 20A. A cutting device 20 that includes the second cutting mechanism 20B and cuts the web 10 to a predetermined cut-off (cutting length), a folding device 40 that grips and folds the cut sheet, and a paper discharge conveyance belt 46. I have it. Hereinafter, each of these components will be described in order from the upstream side.

  The upstream conveyor belt device 51 includes a pair of endless conveyor belts (nipping belts) 51a and 51b, and the web 10 fed by being overlapped by the triangular plate 12 (see FIG. 14) is fed between the nipping belts 51a and 51b. And is conveyed at the same speed as the upstream web conveyance speed V0. Each of the nipping belts 51a and 51b is composed of a plurality of belts separated in the width direction and arranged in parallel, and is guided by the guide roller 51c and driven by the driving roller 51d.

  The first cutting mechanism 20A is a mechanism that partially cuts the two stacked webs 10 with a predetermined cut-off, and includes a pair of saw cylinders 21 and a receiving cylinder 22 that rotate opposite to each other. The saw body 21 is provided with a saw base 24 in which a saw-shaped knife (saw blade) 23a is incorporated in the outer peripheral surface along the axial direction. The receiving cylinder 22 is provided with a rubber base 25 formed of an elastic body such as rubber as a receiving member for the saw blade 23. In particular, the knife 23a is an intermittent knife having a cutting edge intermittently, and the web 10 is partially cut into a perforation with a predetermined cut-off (this cutting is also referred to as intermittent cutting or partial cutting). It has become.

  The midstream conveyance belt device 52 includes a pair of endless conveyance belts (nipping belts) 52a and 52b, and feeds the web 10 that has been cut into a perforation by the first cutting mechanism 20A and sent out. It is sandwiched between the nipping belts 52a and 52b and conveyed at the same speed as the upstream web conveyance speed V0. Each of the nipping belts 52a and 52b of the midstream conveyance belt device 52 is a belt having a predetermined width or less separated in the width direction and arranged in parallel, and is cut by the first cutting mechanism 20A. Corresponding to the portion and arranged so as not to protrude from the cut portion in the width direction, the guide roller 52c guides and is driven by the drive roller 52d.

  The second cutting mechanism 20B is intermittently cut in a perforation with a predetermined cut-off by the first cutting mechanism 20A, and is not cut by the first cutting mechanism 20A with respect to the web 10 conveyed by the conveying belt device 52. This is a mechanism that cuts the remaining portions and completes the cutting, and includes a pair of saw cylinders 21 and a receiving cylinder 22 that rotate opposite to each other. The saw body 21 is provided with a saw base 24 in which a saw-shaped knife (saw blade) 23b is incorporated along the axial direction on the outer peripheral surface. The receiving cylinder 22 is provided with a rubber base (receiving portion) 25 formed of an elastic body such as rubber as a receiving member for the saw blade 23. It should be noted that the intermittent cutting phases of the first and second cutting mechanisms 20A and 20B coincide with each other so that the intermittent cutting position by the first cutting mechanism 20A and the intermittent cutting position by the second cutting mechanism 20B are aligned. Adjusted to

  In this way, in the cutting device 20, the web 10 fed in by the first and second cutting mechanisms 20A, 20B of the upstream and downstream two stages including the first cutting mechanism 20A and the second cutting mechanism 20B is horizontal ( The sheet is cut in a direction orthogonal to the traveling direction) to form a single-leaf sheet (folded book) 10a. In the example of this apparatus, the saw cylinder 21 and the receiving cylinder 22 of the first and second cutting mechanisms 20A and 20B are cut once per rotation.

  The downstream conveyance belt device 53 provided downstream of the cutting device 20 includes a pair of endless conveyance belts (nipping belts) 53a and 53b, and the sheet 10a cut at a predetermined cutoff by the second cutting mechanism 20B. Is sandwiched between the nipping belts 53a and 53b from the midstream conveying belt device 52 and conveyed to the downstream folding device 40. The nipping belts 53a and 53b of the downstream conveyance belt device 53 are also configured by arranging a plurality of belts having a predetermined width or less in parallel, and the predetermined widths constituting the nipping belts 52a and 52b of the midstream conveyance belt device 52. The following belts are arranged with a space therebetween, and are guided by guide rollers 53d, 53e, 53f, 53g and driven by a driving roller 53c.

  However, the sheet 10a is conveyed at the same speed as the web conveyance speed V0 in the midstream conveyance belt device 52 that receives the sheet 10a, whereas it is different from the web conveyance speed V0 in the folding device 40 that delivers the sheet 10a. Since the sheet 10a is transported at the speed Vb, the downstream transport belt device 53 needs to shift (accelerate) the sheet 10a received at the transport speed V0 to the transport speed Vb and transfer it to the folding device 40. Therefore, the downstream conveyance belt device 53 is configured as a variable conveyance belt or a transmission belt. In other words, the roller 53c at the lower end of the nipping belt 53a is a transmission roller that drives the nipping belts 53a and 53b to change speed, and the speed of the nipping belts 53a and 53b is changed by changing the rotational speed of the transmission roller 53c. The gear is changed.

The web processing apparatus (cutting apparatus) for a rotary printing press according to the present embodiment is applied to each of the first cutting mechanism 20A and the second cutting mechanism 20B of the cutting apparatus 20.
A saw cylinder (first cylinder) 21 and a receiving cylinder (second cylinder) 22 of the web processing apparatus (cutting apparatus) are configured as shown in FIGS. 1 and FIG. 2 show a saw cylinder 21 and a receiving cylinder 22, FIG. 3 shows a saw cylinder 21, and FIG. 4 shows a receiving cylinder 22. These saw cylinder 21 and receiving cylinder 22 have a knife ( Saw blades 24a and 23b (hereinafter referred to as reference numeral 23 without distinguishing between them) and a rubber base (receiving part) provided with an elastic body 25a such as rubber detachably by a bolt 25c. 25 is different (see FIG. 1, FIG. 2, FIG. 4), and the others are configured in the same manner, so that the description will be made with reference to FIGS.

As shown in FIG. 1 to FIG. 3, the saw barrel 21 rotates with respect to the rotary shaft 101 in the hollow portion of the rotary shaft 101 and a rotary shaft 101 having a cylindrical hollow portion that is eccentric with respect to the rotary shaft center. The rotating shaft 101 and the eccentric shaft 102 are integrally rotated by providing an eccentric shaft 102 having an axial center O ₂ that is provided and eccentric with respect to the axial center O ₁ of the rotating shaft 101. The saw table 24 is mounted on the eccentric shaft 102 via legs (first legs) 103a and 103b. The saw base 24 and the leg portions 103a and 103b are integrally formed, are detachably fixed to the eccentric shaft 102 by bolts 24a, and the knife 23 is detachably fixed to the saw base 24 by bolts 23a.

  On the other hand, the rotating shaft 101 is formed with a notch portion (first notch portion) 101a so as not to interfere with the leg portions 103a and 103b protruding in the circumferential direction from the eccentric shaft 102 provided in the hollow portion. . In particular, the notch 101a is formed in an arc shape having a predetermined length in the circumferential direction so that the eccentric shaft 102 does not interfere with the legs 103a and 103b even when rotating in the hollow portion of the rotating shaft 101. Yes. That is, the legs 103a and 103b can move from one circumferential end to the other circumferential end of the notch 101a, and the eccentric shaft 102 can move the legs 103a and 103b by the notch 101a. It is rotatable with respect to the rotating shaft 101 within an allowable range.

Here, the eccentric shaft 102 can rotate 180 degrees with respect to the rotating shaft 101, the leg portions 103a and 103b are positioned at one end in the circumferential direction of the notch portion 101a, and the eccentric direction of the eccentric shaft 102 (that is, rotation) When the saw base 24 is positioned in a direction in which the axis O ₂ of the eccentric shaft 102 is located with respect to the axis O ₁ of the shaft 101, the tip (that is, the cutting edge) of the saw blade 23 of the saw base 24 is shown in FIG. ), The leg portions 103a and 103b are located at the other circumferential end of the notch portion 101a, and the saw base 24 is located on the opposite side to the eccentric direction of the eccentric shaft 102. Is positioned, the tip (blade edge) of the saw blade 23 of the saw base 24 rotates along a small circle C21 as shown in FIG.

  Similarly, in the receiving cylinder 22, when the leg portions 103 a and 103 b are positioned at one end in the circumferential direction of the notch portion 101 a and the rubber base 25 is positioned in the eccentric direction of the eccentric shaft 102, the surface (receiving surface) of the rubber base 25. As shown in FIG. 1 (a), it rotates along a large circle C12, the leg portions 103a and 103b are located at the other circumferential end of the notch 101a, and the eccentric direction of the eccentric shaft 102 When the rubber base 25 is positioned on the opposite side, the surface (receiving surface) of the rubber base 25 rotates along a small circle C22 as shown in FIG.

Thus, the structure which makes the eccentric shaft 102 rotatable with respect to the rotating shaft 101 corresponds to the radial position changing means of the present invention.
Further, the eccentric shaft 102 is equipped with a balancer weight 105 via a leg portion (second leg portion) 104 on the opposite side of the saw base 24 (that is, 180 degrees out of phase with the saw base 24). . The balancer weight 105 is for balancing the weight with respect to the saw base 24 and the leg portions 103a and 103b protruding from the eccentric shaft 102 in the outer circumferential direction.

That is, the saw table 24 supported by the eccentric shaft 102 protrudes outward from the outer peripheral surface of the rotary shaft 101, and the rotation with the eccentric shaft 102 built in by the saw table 24 and the leg portions 103a and 103b. The center of gravity of the shaft 101 deviates from the rotation center O ₁ of the rotation shaft 101. Therefore, a balancer weight 105 is provided on the opposite side of the eccentric shaft 102 from the saw base 24 and the leg portions 103a and 103b to balance the saw base 24 and the leg portions 103a and 103b.

In this case, the saw barrel 21 and the receiving shaft in which the rotating shaft 101, the eccentric shaft 102, the saw base 24 or the rubber base 25 and the leg portions 103a and 103b, the balancer weight 105 and the leg portion 104 thereof rotate together. In the body 22, even if the phase relationship between the rotation shaft 101 and the eccentric shaft 102 is changed, the weight distribution of each component is set so that the rotation center of gravity always coincides with the rotation center O ₁ .

  Depending on the setting of the center of gravity and the weight of the eccentric shaft that is part of the rotating body, it is possible to prevent the weight balance of the saw cylinder and the entire receiver cylinder from changing even if the eccentric shaft is rotated. Then, the position of the center of gravity and the weight of the eccentric shaft are set in this way. That is, with respect to the eccentric shaft, the weight balance (the center of rotation of the cylinder coincides with the center of gravity) of the saw and the receiving cylinder is divided into two stages. That is, first, the weight balance is achieved without the rotating shaft 101 in FIG. 3B, and the center of gravity and the center of gravity of the eccentric shaft 102 coincide. Further, the center of the axis of the rotating shaft 101 coincides with the center of gravity of the entire shaft with the rotating shaft 101 attached as shown in FIG.

  Thus, the balance is divided into two stages (that is, even if the eccentric shaft 102 alone or the eccentric shaft 102 is combined with the rotating shaft 101), the radial position changing means Even if the eccentric shaft of FIG. 3B rotates within the rotating shaft of FIG. 3A, the center of gravity position does not always change. Thereby, even if the radial position is changed, it is not necessary to perform balance adjustment again, and it is not necessary to prepare a plurality of types of balance weights.

As the configuration of the balancer weight 105, weights corresponding to the movement of the center of gravity of the rotating shaft 101 due to the rotation of the eccentric shaft 102 with respect to the rotating shaft 101 are prepared, and these can be selected and used. It is conceivable to adjust the center of gravity of the rotating shaft 101 by changing the length of the leg 104 using a single one, but as in this structure, the rotating shaft 101 and the eccentric shaft 102 Even if the phase relationship is changed, if the rotation center of gravity of the saw cylinder 21 and the receiving cylinder 22 is always coincident with the rotation center O ₁ , the operation of the saw cylinder 21 and the receiving cylinder 22 can be performed without any work. Problems such as rotational blur can be prevented.

  The rotary shaft 101 is formed with a notch (second notch) 101b that is 180 degrees out of phase with the first notch 101a, and extends outward from the eccentric shaft 102 that is installed in the hollow portion. It does not interfere with the protruding leg 104. The notch 101a is also formed in an arc shape having a predetermined length in the circumferential direction so that the eccentric shaft 102 does not interfere with the leg 104 even when rotating in the hollow portion of the rotating shaft 101.

  Further, as shown in FIG. 3B, a wheel portion 106 is provided at an end portion of the extending portion 102 a extending from one end of the eccentric shaft 102, and at an end portion of the extending portion 101 c extending from one end of the rotating shaft 101. Is provided with a flange portion 107, and by using the wheel portion 106 to rotate the eccentric shaft 102 relative to the rotating shaft 101 and adjust the relative phase relationship between the rotating shaft 101 and the eccentric shaft 102, a saw blade The radial positions of the cutting edge 23 and the receiving surface of the rubber base 25 can be changed. After the relative phase relationship is adjusted in this way, the eccentric shaft 102 and the rotating shaft 101 are fastened by the bolt 108, whereby the eccentric shaft 102 is fixed to the rotating shaft 101 in a desired relative phase relationship. Thereby, the cutting edge of the saw blade 23 and the receiving surface of the rubber base 25 are set to predetermined radial positions, and the eccentric shaft 102 is set so as to rotate integrally with the rotating shaft 101.

  The diameter of the locus circle of the cutting edge of the saw blade 23 changes according to the angle of the eccentric shaft 102 with respect to the rotation axis 101, and the circumference of the locus circle of the cutting edge changes, but in this embodiment, the locus circle of the cutting edge of the cutting edge changes. The circumference is adjusted so as to coincide with the cut length (cut-off length) of the web 10. As a result, it is possible to cope with several types of cut-off lengths within a certain range. For example, if only three types of cut-off lengths Lco1, Lco2, and Lco3 need to be dealt with, the cut length Corresponding to each of the three types of off lengths Lco1, Lco2, and Lco3, 3 bolt holes for inserting bolts 108 are inserted into both flange portions 106 and 107 so that the angle of the eccentric shaft 102 with respect to the rotation shaft 101 is set. If a set is provided, the corresponding bolt holes are aligned, and the bolts 108 are inserted and tightened, it may be configured to correspond to each cut-off length.

Such a change in the radial position and fixation can be achieved by manually rotating the wheel portion 106 to adjust the relative phase relationship between the rotating shaft 101 and the eccentric shaft 102, as well as a motor (electric motor or fluid pressure motor), etc. The relative phase relationship between the rotating shaft 101 and the eccentric shaft 102 may be adjusted using the actuator.
In this case, in the saw cylinder 21 and the receiving cylinder 22, an apparatus configuration in which the eccentric shaft 102 is rotated relative to the rotating shaft 101 by a motor (not shown) to change the radial position can be considered. In other words, is to be performed. That is, as shown in FIG. 7, the rotation is performed around the axis O ₂ of the eccentric shaft 102 (here, the extended portion 102 a of the eccentric shaft 102 is shown). Since the axis of the rotating shaft 101 is different from the center of rotation S, the relative phase of the rotating shaft 101 with respect to the eccentric shaft 102 is adjusted during the rotation of the cylinders 21 and 22. It is necessary to make sure that there is no problem.

Therefore, as shown in FIG. 7, a shaft 124 is fixed to the support plate 111 concentrically with the rotation center (axial center) O ₂ of the eccentric shaft 102, and a first gear (first gear) is rotatably provided on the shaft 124. (Rotating member) 125 is provided. On the other hand, a second gear (second rotating member) 121 is coupled to the shaft end of the eccentric shaft 102 so as to rotate integrally with the eccentric shaft 102. Further, a shaft 122 is provided on the support plate 111, and an intermediate gear 123 that meshes with both the first gear 125 and the second gear 121 is rotatably provided on the shaft 122 as a power transmission member.

Further, since the eccentric shaft 102 has its axial center O ₂ eccentric with respect to the axial center O ₁ of the cylinders 21 and 22, the eccentric shaft 102 (axial center O ₂ ) does not rotate when the cylinders 21 and 22 are rotated. Although will be around blur to 21 and 22 the axis O ₁ around the, so that the axis 124 and 122 also rotates the axis O ₁ about the eccentric shaft 102 and the positional relationship keep the torso 21 and 22, the support plate An interlocking mechanism (not shown) that moves 111 in conjunction with the rotation of the eccentric shaft 102 around the axis O ₁ is provided.

  The first gear 125 includes an input gear portion 125b and an output gear portion 125a, the intermediate gear 123 also includes an input gear portion 123b and an output gear portion 123a, and the input gear portion 125b of the first gear 125 has a diameter. It is connected to a gear (not shown) so as to receive the rotation from the motor for changing the direction position, and the output gear portion 125a of the first gear 125 and the input gear portion 123b of the intermediate gear 123 mesh with each other, and the output gear portion of the intermediate gear 123 123a and the second gear 121 mesh with each other.

Thus, when the rotation of the radial position changing motor is input to the first gear 125, the second gear 121 is rotationally driven via the first gear 125 and the intermediate gear 123, and the eccentric shaft 102 and the rotary shaft 101 are driven. The relative phase relationship with is changed.
As a result, the relative phase relationship between the eccentric shaft 102 and the rotating shaft 101 can be changed by remote operation without requiring manual operation.

Note that the radial position changing motor does not normally rotate and input to the input gear portion 125b, but rotates only when adjusting the radial position of the cutting edge of the saw blade 23 and the receiving surface of the rubber base 25. Therefore, normally, the shaft 124 of the first gear 125 and the shaft 122 of the intermediate gear 123 follow the eccentric shaft 102 and rotate around the axis O ₁ of the barrels 21 and 22, while the first gear 125 and the intermediate gear 123. 123 is always rotated by meshing with the second gear 121.

Thereby, even when the cylinders 21 and 22 are rotating, the relative phase relationship between the eccentric shaft 102 and the rotating shaft 101 can be freely changed.
If there is no input from the radial position changing motor, the shafts 124 and 122 move following the rotation of the eccentric shaft 102 around the axis O ₁ , and the first gear 125 and the intermediate gear 123 are connected to the second gear 121. While interlocking, the relative phase relationship between the eccentric shaft 102 and the rotating shaft 101 is maintained in an adjusted state.

In addition, as shown in FIG. 2, the rotating shaft 101 in which such an eccentric shaft 102 is integrated includes bearings 109a to 110a on support members 110a, 110b, and 110c (indicated by reference numeral 110 when each support member is not distinguished). 109e (indicated by reference numeral 109 when each bearing is not distinguished) is rotatably supported.
By the way, even when the angle of the eccentric shaft 102 with respect to the rotation shaft 101 is changed and the diameter of the locus circle of the cutting edge of the saw blade 23 is changed, the locus circle of the cutting edge must be along the traveling path of the web 10. Cutting cannot be performed. For this reason, along with a change in the angle of the eccentric shaft 102 relative to the rotation shaft 101, the shaft center position of the rotation shaft 101 can be changed by an amount corresponding to the deviation of the locus circle of the blade edge from the travel path of the web 10. It is like that.

Here, a configuration as shown in FIG. 5 is provided so that the position of the shaft 109 of the rotating shaft 101 is changed by moving the position of the bearing 109 that supports the rotating shaft 101. FIG. 5 shows the rotation shaft 101 of each cylinder corresponding to the first cutting mechanism 20A and the second cutting mechanism 20B. As shown in FIG. 5, the support body 110 that supports the bearing 109 is configured as a shaft-like member (bearing support shaft as a bearing support member), and the bearing support shaft 110 rotates eccentrically with respect to the bearing 109. The shaft center position of the rotating shaft 101 is changed by pivoting with a bearing (not shown) so as to have the shaft center O ₃ and rotating the bearing support shaft 110.

As described above, the bearing 109 that supports the rotating shaft 101 is supported by the bearing support shaft 110 that is eccentric with respect to the bearing 109, and the shaft supporting position can be changed by rotating the bearing supporting shaft 110. Corresponds to the axial center position changing means of the present invention.
Here, an actuator 113 such as an air cylinder is connected to the outer periphery of the bearing support shaft 110, and the bearing support shaft 110 is rotated by the actuator 113. In addition, the actuator 113 is provided only in one of the saw cylinder 21 and the receiving cylinder 22, and flange portions 112b and 112c are provided on the outer circumferences of the bearing support shafts 110 of the saw cylinder 21 and the receiving cylinder 22, respectively. The outer periphery of 112c is frictionally engaged with each other so that the bearing support shaft 110 of the saw cylinder 21 and the bearing support shaft 110 of the receiving cylinder 22 rotate synchronously in opposite directions. Accordingly, the bearing support shafts 110 of the saw cylinder 21 and the receiving cylinder 22 can be rotated by one actuator 113 (see the arrows with the axis O ₁ as a base point).

Here, the bearing support shaft 110 can be fixed to the support 111 at the same time that the bearing support shaft 110 is set at a predetermined angle. Also in this case, the angle of the bearing support shaft 110 is set according to the angle (relative phase) of the eccentric shaft 102 with respect to the rotation shaft 101 corresponding to the cutoff length.
That is, the other bearing support shaft 110 of the saw cylinder 21 and the receiving cylinder 22 is further provided with a flange portion 112a having teeth formed on the outer periphery, and the gear 114 is meshed with the outer teeth of the flange portion 112a. The shaft 114 a of the gear 114 is rotated according to the rotation state of the bearing support shaft 110, that is, the axial center position of the rotation shaft 101. As shown in FIG. 6, a rotating plate 201 rotatably supported by a support plate 200 is provided at the end of the shaft 114a. The rotating plate 201 is provided with a lever 201a protruding outward in the radial direction. ing. The support plate 200 is provided with stoppers 203 and 204 that abut against the lever 201a and restrict the rotation of the lever 201a. In this example, the stopper 203 is attached to the fan-shaped bracket 202 with a plurality of sets (here, two sets) of bolts or the like, and the bracket 202 is attached to a plurality of sets (here, using the mounting holes 200 a formed in the support plate 200. The stopper 203 is fixed to the support plate 200 by being fastened and fixed by two sets of bolts 202a and the like. A plurality of mounting holes 200a are provided so that the position of the stopper 203 can be selected and fixed. The stopper 204 is directly fixed to the support plate 200 by a plurality of sets (here, two sets) of bolts. A plurality of mounting holes for attaching the stopper 204 are provided so that the position of the stopper 204 can be selected and fixed.

With such a configuration, the actuator 113 urges the bearing support shaft 110 in the forward rotation direction or the reverse rotation direction and presses the bearing support shaft 110 against the stopper 203 or 204, and the urging force of the actuator 113 and the reaction of the stopper 203 or 204 against this force. The bearing support shaft 110 can be clamped and fixed by the force.
Note that, as indicated by the arrows in FIG. 5, the change of the axial center position of the rotating shaft 101 is performed so as to draw an arcuate locus, so that the axial center position of the rotating shaft 101 is relative to the travel path of the web 10. The direction is changed not only in the direction of separation and contact but also in the direction parallel to the travel route. This can be dealt with by correcting the rotational phase of the rotating shaft 101 in accordance with the amount of movement in the direction parallel to the travel route.

The rotary printing press is also configured as a so-called variable cut-off type rotary printing press that can change the cut-off (web cutting length) of the web 10 by changing the outer diameter of the printing cylinder (plate cylinder or blanket cylinder) of the printing unit 4. Has been.
Therefore, as described in the prior art, in the folding machine 7, when the web traveling speed (conveying speed) is Vo, the saw cylinder rotational speed is Nc, and the number of saw blades is n, the cut-off (web cutting length). C is
C = Vo / (Nc · n)
It becomes.
Further, the cut sheet 10 a is accelerated from the traveling speed Vo of the web 10 to the speed Vb of the folding cylinder 45 by the variable speed conveying belt 53, transferred to the folding cylinder 45, and delivered to the claws 43 of the folding cylinder 45. Then, the next folding is performed.

  A web cutting device (cutting device) as a web processing device for a rotary printing press according to an embodiment of the present invention, and a rotary press folding machine and a rotary printing press equipped with the web cutting device are configured as described above. Therefore, at the start of printing, each part of the first cutting mechanism 20A and the second cutting mechanism 20B is adjusted to the cut-off.

  That is, the first cutting mechanism 20 </ b> A and the second cutting mechanism 20 </ b> B adjust the rotation angle of the eccentric shaft 102 with respect to the rotation shaft 101 for each saw cylinder (first cylinder) 21 and receiving cylinder (second cylinder) 22, The circumferential length of the rotation trajectory of the cutting edge of the saw blade 23 and the receiving surface of the rubber base 25 is made equal to the cut-off length of the web 10. In response to this, the counterweight 105 is balanced with respect to the saw blade 23 or the rubber base 25. Furthermore, the position of each rotating shaft is adjusted according to the cut-off length.

  The cutting device 20 performs intermittent cutting (intermittent cutting) at a predetermined cutoff in the first cutting mechanism 20A on the web 10 fed from the upstream conveying belt device 51 at a predetermined web conveying speed Vo. After that, the web 10 that is still in the web state is fed to the midstream conveyance belt device 52 and is conveyed intermittently by the first cutting mechanism 20A in the second cutting mechanism 20B while conveying the web 10 at the same speed as the web speed Vo. The remaining portion of the cut portion is cut (intermittent cutting). As a result, the web 10 is completely cut and separated into sheets 10a.

The separated sheet 10 a is nipped by the midstream conveyance belt device 52, transferred at the same speed as the web conveyance speed Vo, and delivered to the downstream conveyance belt device 53. In the downstream conveyance belt device 53, at the time of reception, the guide rollers 53c and 53d at the entrance are held and operate at the same speed as the web conveyance speed Vo. In the downstream conveyance belt device 53, after the sheet 10a is received, the guide rollers 53c and 53d at the entrance are opened, and then the guide belts (transmission belts) 53a and 53b and the transmission roller 53c are connected to the folding cylinder 45. Control is performed so that the sheet speed is increased by ΔV up to the sheet conveyance speed Vb, the sheet is transferred to the claw 43 of the folding cylinder 45 at the folding cylinder 45 sheet conveyance speed Vb, and then returned to the original speed Vo.
When the speed Vo is reached, the guide rollers 53c and 53d at the entrance portion are nipped, and the next sheet 10a enters between the guide belts 53a and 53b of the downstream conveyance belt device 53. Thereafter, the same operation is repeated.

According to the present embodiment, as a result, the following effects can be obtained.
(1) When changing the cut-off length of the web, the radial position of the blade edge and the receiving surface is changed so that the circumferential length of the rotation circle of the blade edge and the receiving surface corresponds to the cutoff length. Even if the cut-off length of the web is changed, the circumferential speed of the saw cylinder 21 and the receiving cylinder 22 and the traveling speed of the web can be matched, and the speed difference between the cutting edge and the receiving surface and the web is eliminated. Occurrence of problems such as web breaks, scratches, web wrinkles, and web cuts (paper breaks), which are likely to occur when there are speed differences sometimes, can be avoided.

(2) Even when the radial position of the saw blade 24 or the rubber base 25 is changed by installing the balancer weight 105 with respect to the saw blade 24 or the rubber base 25 on the rotating shaft, the saw cylinder 21 and the receiving cylinder. It is possible to make the center of gravity of 22 coincide with the rotational axis, and each cylinder can be smoothly rotated.
(3) The saw blade 24 or the rubber base 25 is coupled to the eccentric shaft 102 that has an axis that is eccentric with respect to the axis of the rotating shaft 101 and rotates integrally with the rotating shaft 101, and the eccentric shaft 102 is connected to the rotating shaft 101. By simply rotating the eccentric shaft 102 relative to the rotating shaft 101 by configuring the radial position changing means to change the radial position of the cutting edge or the receiving surface by rotating relative to the saw blade, the saw blade The radial position can be easily changed without attaching or detaching the 24 or the rubber base 25.

(4) In addition, since the bearing support shaft 110 that eccentrically supports the bearing 109 that supports the rotating shaft 101 is provided and the rotational position of the bearing supporting shaft 110 is changed, the axial position of the bearing 109 is changed. The axial center position 101 can be changed smoothly.
(5) Furthermore, the radial position of the cutting edge or the receiving surface with respect to the rotation axis of the barrels 21 and 22 is changed and fixed, that is, the relative phase relationship between the rotation shaft 101 and the eccentric shaft 102 is adjusted and fixed (relative phase relationship). As shown in FIG. 7, by using an actuator, the radial position can be easily changed, and a drive system (gear) that drives the eccentric shaft 102 relative to the rotating shaft 101 as shown in FIG. The relative phase relationship between the eccentric shaft 102 and the rotary shaft 101 can be freely set even when the cylinders 21 and 22 are rotating, for example, by moving the shafts 124 and 122 of the 125 and 123 and the actuators to follow the eccentric shaft 10. It is also possible to change to
Further, gear mechanisms 121, 123, and 125 are provided between the rotary shaft 101 and the motor, and the shaft 122 of the intermediate gear 123 is provided on the bearing support shaft 110 that supports the rotary shaft 101, and a shaft that supports the first gear 125. 124 is arranged concentrically with the axis O ₃ , so that even if the bearing support shaft 110 rotates, the meshing relationship between the second gear 121 and the intermediate gear 123, the first gear 125 and the intermediate gear 123, The power transmission between the rotating shaft and the motor can be performed without changing the motor position even if the shaft center position is changed.

(6) Further, since the sheet 10a is always held by any one of the upstream, middle and downstream conveyance belt devices 51, 52 and 53 and is transported in a restrained state, the sheet 10a slips on the sheet 10a during conveyance. Is less likely to occur, and can be delivered to the folding cylinder 45 with accurate timing. For this reason, stable folding accuracy can be ensured and the printed surface is not soiled.
(7) To change the cut-off, it is only necessary to change the web conveyance speed Vo and to change and adjust the speed change patterns of the speed change roller 53c and the speed change belts 53a and 53b accordingly. No change device is required. Therefore, the drive unit space is greatly reduced, the operation control is easy, and the print quality is stabilized.

[Others]
Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.
For example, the present cutting device may be applied to a folder as shown in FIGS. 8 to 10 or a folder as shown in FIG.
That is, as shown in FIGS. 8 to 10, as in the embodiment (FIG. 16), from the upstream side, the upstream conveyance belt device 51, the first cutting mechanism 20 </ b> A, the midstream conveyance belt device 54, and The second cutting mechanism 20B is provided, and a chopper folding device 65 unique to the present embodiment and a paper discharge conveyor belt 46 similar to the embodiment are provided downstream thereof. Since the cutting devices 20 such as the first cutting mechanism 20A and the second cutting mechanism 20B are the same as those in the embodiment, description thereof will be omitted.

The upstream conveyor belt device 51 is composed of a pair of nipping belts 51a and 51b facing each other, and the midstream conveyor belt device 54 is composed of a pair of nipping belts 54a and 54b facing each other, and these nipping belts 51a and 51b. , 54a and 54b are configured by arranging a plurality of belts in parallel.
The midstream conveyance belt device 54 operates on the downstream side of the pair of endless conveyance belts 54a and 54b that convey the web 10 to be cut by the second cutting mechanism 20B and the cut sheet 10a, and the chopper folding device 65. The endless conveying belts 54a and 54c are paired as described above. That is, the conveyance belt 54a cooperates with the conveyance belt 54b to convey the web 10 and the cut sheet 10a before and after the second cutting mechanism 20B, and cooperates with the conveyance belt 54c. It also has a function of conveying the sheet 10a after chopper folding downstream. The conveyor belt 54a is guided by guide rollers 54d and 54e, the conveyor belt 54b is guided by guide rollers 54d and 54f, and the conveyor belt 54c is guided by guide rollers 54d. The guide belt 54c also has a plurality of belts arranged in parallel, like the guide belts 54a and 54b.

As shown in FIG. 8, the chopper folding device 65 includes a chopper folding blade 65a and a pair of folding rollers 54g and 54h that also function as guide bell rollers, and the chopper folding blade 65a is paired with a pair of folding rollers 54g and 54h. It is configured so as to swing and contact toward and away from the engagement portion entrance.
Note that a predetermined gap is provided on the facing surfaces of the conveyor belts 54a and 54c so that the leading edge of the sheet 10a can enter without any restriction prior to the chopper folding.

Further, a single individual motor is used as the swing drive source of the chopper folding blade 65a, and the swing timing of the chopper folding blade 54a can be freely set.
The configuration of the cutting device shown in FIGS. 1 to 7 may be applied to the first cutting mechanism 20A and the second cutting mechanism 20B of the folder configured as described above.
Further, the folding machine shown in FIG. 11 includes, from the upstream side, an upstream conveyance belt device 55, a downstream conveyance belt device (second conveyance belt device) 56, and a folding device (not shown, reference numerals in FIG. 16). 40) and a paper discharge conveyor belt (not shown, see reference numeral 46 in FIG. 16).

  The upstream transport belt device 55 is composed of a pair of nipping belts 55a and 55b facing each other, and the downstream transport belt device 56 is composed of a pair of guide belts 56a and 56b facing each other. Each of 55b, 56a, and 56b has a plurality of belts arranged in parallel, and operates by being guided by guide rolls 55c and 56c.

  In the conveyance area by the upstream conveyance belt device 55, the first cutting mechanism 20A and the second cutting mechanism 20B are provided in substantially the same manner as shown in FIGS. On the upstream side of the mechanism 20A, a horizontal sewing mechanism 84 is provided adjacent to the first cutting mechanism 20A. The horizontal sewing mechanism 84 is a mechanism for inserting a two-layered uncut web 10 into a predetermined position with a horizontal sewing machine (horizontal perforation) and a pair of sewing cylinders 84A that are arranged opposite to each other and rotate synchronously. It is comprised from the trunk | drum 84B. The sewing body 84A is provided with a comb blade base (not shown) in which a comb blade-like knife (comb blade for sewing machine) 84a is incorporated along the axial direction on the outer peripheral surface. The receiving cylinder 84B is provided with a rubber base 84b formed of an elastic body such as rubber as a receiving member of the knife 84a.

A folding device 90 is provided downstream of the downstream conveying belt device 56. The folding device 90 is also provided with a configuration unique to the variable cutoff machine.
First, the upstream conveyance belt device 55 sandwiches the web 10 between the nipping belts 55a and 55b and conveys the web 10 at a speed equal to the upstream web conveyance speed V0. These nipping belts 55a and 55b are guided and driven by a plurality of guide rollers to sandwich and convey the web 10 while applying nip pressure from both sides thereof. In addition, upstream of these nipping belts 55a and 55b, adjacent nipping rollers 14a and 14b sandwich the web 10, and are arranged so as to convey at the same speed as the upstream web conveyance speed V0. .

  Further, in order to drive the nipping rollers 14a and 14b and the nipping belts 55a and 55b together, a nipping roller driving motor and a belt driving motor (for example, a shaftless motor can be used as these motors. (Also simply referred to as a motor M4) 85d, and the motor 85d drives the peripheral speed of the nipping rollers 14a and 14b and the traveling speed of the nipping belts 55a and 55b to be equal to the web conveyance speed V0. .

Further, in order to drive together the sewing cylinder 84A, the saw cylinder 22a of the first cutting mechanism 20A, and the saw cylinder 22b of the second cutting mechanism 20B, a sewing machine cylinder and a shaftless motor for driving the saw cylinder (hereinafter also referred to as a motor M3). ) 85c, and the motor M3 drives the sewing machine cylinder 84A and the saw cylinders 22a and 22b to rotate in synchronization with each other.
Phase changing devices 89A and 89B are interposed between the adjacent sewing cylinder 84A and the saw cylinder 21a, and between the saw cylinder 21a and the saw cylinder 21b. Here, the sewing machine cylinder 84A is directly driven by a shaftless motor (motor M3) 85c, and the rotary shaft of the sewing machine cylinder 84A and the rotary shaft of the saw cylinder 22a are connected by a first power transmission mechanism (here, a gear mechanism) 86A. A phase changing device 89A is interposed in the first power transmission mechanism. The rotating shaft of the saw cylinder 21a and the rotating shaft of the saw cylinder 21b are connected by a second power transmission mechanism (here, a gear mechanism) 86B, and a phase changing device 89B is interposed in the second power transmission mechanism. .

  Thus, the sewing machine cylinder 84A is driven by the shaftless motor (motor M3) 85c so that the knife 84a is at the same speed as the web conveyance speed V0 in a phase state corresponding to the web printing position. Then, the saw cylinder 21a rotates in synchronization with the sewing machine cylinder 84A by the first power transmission mechanism 86A, and the saw cylinder 21b rotates in synchronization with the saw cylinder 21a by the second power transmission mechanism 86B. At this time, the mutual phase of the sewing machine cylinder 84A and the saw cylinder 22a is appropriately adjusted by the phase changing device 89A so that the relative phase according to the cutoff length is obtained, and the saw cylinder 21a and the saw cylinder 21b are also set to the cutoff length. The mutual phase is appropriately adjusted by the phase changing device 89B so as to obtain a corresponding relative phase.

  The power transmission mechanisms 86A and 86B and the phase change devices 89A and 89B will be described in further detail. A gear (not shown) is provided at one end of the rotary shaft 87a of the saw barrel 22a, and one end of the rotary shaft 87b of the saw barrel 22b. Are also equipped with gears (not shown), and a phase changing device 89B is interposed between these gears. These gear and phase changing device 89B constitute power transmission mechanisms 86A and 86B.

The phase changing devices 89A and 89B include a gear (not shown) that meshes with the gear of the rotary shaft 87a, a gear (not shown) that meshes with the gear of the rotary shaft 87b, and a difference (not shown) that changes the rotational phase of these gears. A moving device (DFG) and a servo motor (motor m2) 89d for driving the differential shaft of the differential device are provided.
Next, the downstream conveyance belt device 56 will be described. As shown in FIGS. 11A and 11B, the downstream conveyance belt device 56 is guided and driven by a plurality of guide rollers 56 c to move the web 10. Nipping belts (acceleration belts or transmission belts) 56a and 56b, which are endless belts that are nipped and conveyed while applying nip pressure from both sides, are provided. This is an acceleration belt that is nipped between the cut sheet 1a nipping belts 56a and 56b and conveys the sheet 10a while accelerating from the web conveyance speed V0 to a predetermined speed.

  In other words, in the downstream conveyance belt device 56, the sheet 10a that has been cut to the required cut-off length while being conveyed by the upstream conveyance belt device 55 at a speed equal to the web conveyance speed V0 is between the nipping belts 56a and 56b. The nipping belts 56a and 56b are set to the web conveyance speed V0 in the same manner as the nipping belts 55a and 55b while the sheet 10a is held by the guide belts 55a and 55b of the upstream conveyance belt device 55. The sheet 10a is conveyed at a constant speed. Then, when the sheet 10a is released from between the nipping belts 55a and 55b, the sheet 10a is accelerated and separated from each other by an appropriate distance according to the cut-off length. Finally, the sheet 10a is transferred to the gripping device 90 by accelerating to a speed synchronized with the peripheral speed of the downstream folding device 90. The driving of the nipping belts 56a and 56b is performed by an acceleration belt driving shaftless motor (motor M2) 85b.

  As shown in FIGS. 11 (a) and 11 (b), the tail folding device 90 includes a gripping barrel 92 having a gripping device 91 and a claw device (hereinafter simply referred to as a claw) 93, as in the conventional example. And a folding cylinder 95 provided with a folding blade 94. While the leading edge of the sheet 10a fed through the acceleration belt 56 is gripped by the claws 93 and rotated, the folding cylinder 95 is folded. With the engagement between the blade 94 and the gripping device 91 of the gripping drum 92, the sheet 10a delivered to the gripping device 91 at this engagement position is gripped at a fold line perpendicular to the conveying direction. ing.

In addition, the folding device 90 illustrated here includes three sets of gripping devices 91 on the gripping cylinder 92, and includes three sets of claws 93 and three sets of folding blades 94 on the folding cylinder 95 side. As a result, three sets of folded books 10b can be formed by rotating each of the cylinders 92 and 95 once.
Further, the folding cylinder 95 and the gripping cylinder 92 are driven to rotate in synchronization with each other by a folding cylinder / pinning cylinder driving shaftless motor (motor M1) 85a. Here, a power transmission mechanism similar to the power transmission mechanisms 86A and 86B is interposed between the folding cylinder 95 and the tailing cylinder 92, and the folding cylinder 95 is directly driven by a shaftless motor 85a. The tail barrel 92 is driven by a shaftless motor 85a through a power transmission mechanism.

In the apparatus shown in FIG. 11, a motor may be provided for each drive system.
That is, as shown in FIG. 12, a shaftless motor (also simply referred to as a motor) is used to drive the sewing cylinder 84A, the saw cylinder 21a of the first cutting mechanism 20A, and the saw cylinder 21b of the second cutting mechanism 20B. M31, M32, and M33 are individually provided, and the motor cylinder 31A and the saw cylinders 21a and 21b are driven by these motors M31, M32, and M33 so as to rotate in synchronization with each other.

The configuration of the cutting apparatus shown in FIGS. 1 to 7 may be applied to the first cutting mechanism 20A, the second cutting mechanism 20B, and the horizontal sewing mechanism 84 in the folding machine cutting apparatus configured as described above.
Also, the radial position changing means for changing the radial position of the cutting edge or the receiving surface with respect to the axis of the rotating shaft and the axis position changing means for changing the axis position of the rotating shaft have each function. What is necessary is just and it is not limited to the thing of the said embodiment. For example, the radial position may be changed by exchanging a saw blade or a rubber stand, and the axial center position of the rotary shaft may be configured to be changeable by a slide type instead of the rotary type. .

In the above-described embodiment, the folding device 40 has been described as an example of a processing device that processes a cut sheet. However, the folding device is not limited to this, and various devices can be applied to process a cut sheet. The processing device to be used is not limited to the folding device, and can be applied to various devices such as a discharge device for discharging a cut sheet to the outside of the printing press.
That is, the method or apparatus according to the present invention is characterized in that the peripheral speed of the cylinder is changed by changing the rotation radius and the axial center position. In the above embodiment, as a typical example, the saw of the cutting apparatus is used. A cylinder in which a cylinder and a receiving cylinder are raised, and a cylinder that performs some processing on a web before cutting and a sheet after cutting in a printing machine is not limited to this.

For example, by installing a cylinder with a plate (hanko) instead of a saw cylinder, printing with different cut-offs (different paper speeds) can be performed on a web or sheet.
Further, in the above-described embodiment, the description has been made on the case where two cylinders, the saw cylinder and the receiving cylinder, which are opposed to each other, are described, but the present invention is not necessarily intended for the two cylinders facing each other.
For example, in the case of a cutting device, a receiving cylinder is provided for the saw cylinder capable of changing the peripheral speed according to the present invention. However, instead of the receiving cylinder, a fixed receiving apparatus in which the receiving surface is configured by a fixed plane. You may make it provide a member. Considering such a case, the present invention can be applied to a single cylinder (for example, only the first cylinder).

  The apparatus of the present invention is suitable for use in a folding device as a processing device for processing a cut sheet in a rotary printing press, but is not limited to a folding device, and a discharge device that discharges the cut sheet to the outside of the printing press. It can be applied to various devices such as a printing apparatus itself.

It is a cross section which shows the structure of the trunk | drum of the web cutting device as a web processing apparatus for rotary printing machines concerning one Embodiment of this invention, and is sectional drawing corresponding to the AA arrow line of FIG. 3, FIG. (A) shows a state where the cutting edge rotates along a great circle, and (b) shows a state where the cutting edge rotates along a small circle. It is a longitudinal cross-sectional view which shows the structure of the cylinder of the web cutting device as a web processing apparatus for rotary printing presses concerning one Embodiment of this invention. It is a perspective view which shows the structure of the saw cylinder of the web cutting device as a web processing apparatus for rotary printing machines concerning one Embodiment of this invention, (a) shows the hollow rotating shaft provided with the eccentric shaft, (b) ) Shows only the eccentric shaft. It is a perspective view which shows the structure of the receiving cylinder of the web cutting device as a web processing apparatus for rotary printing machines concerning one Embodiment of this invention, (a) shows the hollow rotating shaft provided with the eccentric shaft, (b) ) Shows only the eccentric shaft. It is a side view which shows the structure of the bearing part of the web cutting device as a web processing apparatus for rotary printing presses concerning one Embodiment of this invention. It is a side view which shows the structure of the bearing part of the web cutting device as a web processing apparatus for rotary printing presses concerning one Embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the drive system of the web cutting device as a web processing apparatus for rotary printing presses concerning one Embodiment of this invention, and respond | corresponds to the principal part (left upper part) of (2). It is a typical side view of the folding machine for rotary printing presses which can apply the web processing apparatus for rotary printing presses concerning one Embodiment of this invention. It is a B arrow view of FIG. It is C arrow line view of FIG. It is a typical side view of the other folding machine for rotary printing presses which can apply the web processing apparatus for rotary printing presses concerning one Embodiment of this invention. It is a typical side view of the other folding machine for rotary printing presses which can apply the web processing apparatus for rotary printing presses concerning one Embodiment of this invention. It is a typical block diagram which shows a common commercial offset rotary press by a side view. It is a typical side view which shows the structure of the folding machine for rotary presses of a prior art. It is a typical side view which shows the principal part structure (border folding apparatus part) of the folding machine for conventional rotary printing presses. It is a typical side view which shows the structure of the folding machine for rotary printing presses concerning a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Paper feeder apparatus 1a, 1b Web roll 2 Infeed apparatus part 3 Printing apparatus part 3a-3d Printing unit 4 Drying apparatus part 5 Cooling apparatus part 6 Web pass part 7 Folding machine 8 Paper discharge apparatus part 10 Web 10a After chopper folding Sheet 10b Origami 11 Drag roller 12 Triangle plate 20, 220 Cutting device 20A First cutting mechanism 20B Second cutting mechanism 21 Saw cylinder 22 Receiving cylinder 23, 23a, 23b Knife (saw blade)
24 Saw table 25 Rubber table 40 Folding device 41 Clamping device 42 Clamping cylinder 43 Claw device (claw)
44 Folding blade 45 Folding drum 46 Discharge conveying belt 51, 55 Upstream conveying belt device 52, 54 Midstream conveying belt device 53, 56 Downstream conveying belt device 65 Chopper folding device 65a Chopper folding blade 84 Horizontal sewing machine mechanism 84A Sewing drum 84B Cylinder 84a Knife (comb blade for sewing machine)
84b Rubber base 85a Shaftless motor (motor M1)
85b Shaftless motor for driving acceleration belt (motor M2)
85c Shaft and saw barrel drive shaftless motor (motor M3)
85d Nipping roller, beltless shaftless motor (motor M4)
86A 1st power transmission mechanism 86B 2nd power transmission mechanism 89A, 89B Phase change device 90 Folding device 91 Cranking device 92 Cranking cylinder 93 Claw device (claw)
94 Folding blade 95 Folding cylinder 101 Rotating shaft 101a Notch (first notch)
102 Eccentric shaft 103a, 103b Leg (first leg)
104 Leg (second leg)
105 Balancer weight 106, 107 Flange part 108 Bolt 109a-109e, 109 Bearing 110a, 110b, 110c, 110 Support body (bearing support shaft)
111 Support body 112a, 112b, 112c Flange portion 113 Actuator 114 Roller 121 Second gear 122, 124 Shaft 123 Intermediate gear 125 First gear M31, M32, M33 Shaftless motor (motor)

Claims (15)

Cutting either a full cut or a partial cut including perforation for a web provided downstream of a printing device in a rotary printing press and fed from the printing device and conveyed on a travel path by a conveying device A web processing device for performing
A first cylinder that is provided along the travel path, has a blade that cuts the web, and rotates at a rotation speed corresponding to the rotation of the printing cylinder of the printing apparatus;
A receiving portion provided with a receiving surface for receiving the blade edge of the blade when the web is cut, and disposed opposite to the first drum across the travel path, and rotating in synchronization with the first drum; With two bodies,
The first cylinder and the second cylinder are both
A rotating shaft that supports the blade or the receiving portion;
A radial position changing means for changing a radial position of the cutting edge or the receiving surface with respect to an axis of the rotating shaft;
A web processing apparatus for a rotary printing press, comprising: an axis position changing means for changing an axis position of the rotating shaft. The web processing device for a rotary printing press according to claim 1, wherein the rotary shaft is equipped with a balancer weight for the blade or the receiving portion. An eccentric shaft having an eccentricity with respect to the axis of the rotating shaft is equipped to rotate integrally with the rotating shaft, and the blade or the receiving portion is coupled to the eccentric shaft;
The radial position changing means is configured to change the radial position of the cutting edge or the receiving surface by rotating the eccentric shaft relative to the rotating shaft. The web processing apparatus for a rotary printing press according to claim 1 or 2. The rotating shaft is configured to be hollow, and the eccentric shaft is provided inside the hollow so as to be rotatable relative to the rotating shaft,
The blade or the receiving portion is equipped via a first leg portion protruding outward from the eccentric shaft,
4. The rotary printing press according to claim 3, wherein the rotary shaft is provided with a first cutout portion that allows relative rotation of the first leg portion during the relative rotation of the eccentric shaft. Web processing device. The rotary shaft is equipped with a balancer weight for the blade or the receiving portion via a second leg portion protruding outward from the eccentric shaft,
5. The rotary printing press according to claim 4, wherein the rotary shaft is provided with a second notch portion that allows relative rotation of the second leg portion during the relative rotation of the eccentric shaft. Web processing device. Even when the radial position of the cutting edge or the receiving surface with respect to the axis of the rotating shaft is changed by the radial position changing means, the balancer weight, the blade or the receiving portion, the eccentric shaft, and the rotating shaft 6. The rotary printing press according to claim 5, wherein the weight balance of each part is set so that the rotational center of gravity of the first cylinder or the second cylinder including the head always coincides with the rotation center. Web processing device. 7. The rotary printing press according to claim 3, further comprising a relative position fixing unit that fixes the eccentric shaft at a predetermined relative rotational position with respect to the rotation shaft. Web processing device. A bearing for supporting the rotating shaft; and a bearing supporting member for supporting the bearing eccentrically, wherein the shaft center position changing means changes the rotational position of the bearing supporting member, thereby changing the shaft center position of the bearing. The web processing device for a rotary printing press according to any one of claims 1 to 7, wherein the web processing device is configured so as to change the speed. 9. The rotary printing press according to claim 8, further comprising an actuator that changes a rotational position of the bearing support member and a bearing support member fixing unit that fixes the bearing support member at a predetermined rotational position. Web processing device. A first gear disposed coaxially with a rotation center of the first cylinder or the second cylinder;
A second gear fixed to the rotating shaft;
An intermediate gear supported rotatably on the eccentric shaft and meshing with both the first gear and the second gear;
A motor for inputting a rotational force to the first gear when the axial position is changed and changing a relative phase between the rotary shaft and the eccentric shaft via the intermediate gear and the second gear; The web processing apparatus for a rotary printing press according to any one of claims 1 to 9, wherein the web processing apparatus is a rotary printing press. A cutting device that is provided downstream of a printing device in a rotary printing press and cuts a web fed from the printing device, and a processing device that is provided downstream of the cutting device and processes a sheet cut by the cutting device. A folding machine equipped with
A rotary machine for a rotary printing press comprising the web processing device for a rotary press according to any one of claims 1 to 10 as the cutting device. The processing apparatus includes a rotating drum for processing the sheet,
The cutting device is configured to change the cutting length of the web by changing the radial position of the cutting edge or the receiving surface by the radial position changing means and changing the axial position of the rotary shaft by the axial position changing means. Configured to respond to changes in
The processing device is configured to be able to cope with a change in the cutting length of the web by a change in the rotation speed of the rotating drum,
In the sheet conveyance path from the cutting apparatus to the processing apparatus, the sheet conveyance speed can be changed from a speed synchronized with the cutting apparatus to a speed synchronized with the processing apparatus during the sheet conveyance. The rotary machine for a rotary printing press according to claim 11, further comprising a variable speed conveyance device. A variable cut-off rotary printing press comprising the rotary machine for a rotary printing press according to claim 11 or 12, and configured to be cut by changing a cut length of a printed web. In a rotary printing press, a cylinder for processing a web conveyed on a traveling path of a printing apparatus, and a rotation radius of the cylinder surface with respect to the rotation axis of the cylinder is changed in accordance with the traveling speed of the web. A rotating radius changing means for changing the axis position of the rotating shaft of the trunk,
A cylinder of a rotary printing press characterized in that the rotational speed of the cylinder is changed by changing the rotation radius by the rotation radius changing means and changing the axial center position by the axial center position changing means. To change the peripheral speed. The cylinder has a rotation shaft provided concentrically with the rotation axis of the cylinder, and an axis that is eccentric with respect to the rotation axis of the cylinder, and is eccentric so as to rotate integrally with the rotation shaft. Along with the axis,
A bearing that supports the rotating shaft; and a bearing support member that eccentrically supports the bearing;
The turning radius changing means is configured to change the turning radius of the body surface by rotating the eccentric shaft relative to the rotating shaft,
The rotary printing press according to claim 14, wherein the shaft center position changing means is configured to change the shaft center position of the bearing by changing the rotational position of the bearing support member. To change the peripheral speed of the torso.

Images