Horizontal perforation forming apparatus for rotary press

A horizontal perforation forming apparatus for a rotary press includes an interaxial distance adjusting unit for adjusting a distance between axes of perforation and mating cylinders. The apparatus also includes a phase adjusting unit having a phase adjusting shaft which is axially moved to pivot the perforation cylinder. The phase adjusting shaft is moved upon pivotal movement of an operation shaft of the interaxial distance adjusting unit.

BACKGROUND OF THE INVENTION 
The present invention relates to a horizontal perforation forming apparatus 
attached to a folder of a web rotary press to form horizontal perforations 
extending in a widthwise direction of a traveling web. 
A folder is attached to a web rotary press to fold a printed web in its 
widthwise or longitudinal direction. A horizontal perforation forming 
apparatus is arranged in the folder to form horizontal perforations 
extending in the widthwise direction of the web in a perspective folding 
portion so as to facilitate a subsequent folding operation. 
FIG. 16 is a schematic side view of a conventional horizontal perforation 
forming apparatus of this type. This apparatus will be described with 
reference to FIG. 16. A horizontal perforation forming apparatus 2, upper 
and lower nipping rollers 3 and 4, and a rubber roller 5 and a press 
roller 6 which are respectively in rolling contact with the nipping 
rollers 3 and 4 are arranged in the traveling path of a web 1 which is 
traveling between a former (not shown) for folding the printed web in the 
widthwise direction and a folding cylinder (not shown) for folding the 
printed web in the longitudinal direction. In the horizontal perforation 
forming apparatus 2, a perforation cylinder 7 and its mating cylinder 8 
are spaced apart from each other by a small gap. A perforation blade case 
14 is fixed in a perforation blade groove 7a formed in the axial direction 
of the perforation cylinder 7. The perforation blade case 14 includes a 
perforation blade base 9 having a length corresponding to a generator of 
the perforation cylinder 7, a press plate 10 and a shim 11 which surround 
the perforation blade base 9, a paper holder 12 dovetailed with the 
perforation blade base 9, and an elongated plate-like perforation blade 13 
held by the central perforation blade groove. The distal end of the 
perforation blade 13 extends outward from the paper holder 12. An 
elongated perforation blade seat 15 is fixed in a perforation blade 
receiving groove 8a extending in the axial direction of the mating 
cylinder 8. The cylinders 7 and 8, the nipping rollers 3 and 4, and the 
like are driven from folding paper cylinders through gears in directions 
indicated by arrows. 
With the above structure, the web 1 conveyed upon printing is fed out by 
the upper nipping roller 3 and is guided to a gap between the cylinders 7 
and 8. When the web 1 has passed between the cylinders 7 and 8, it is 
guided to the lower nipping roller 4 by the folding paper cylinders. In 
this case, during passing of the web 1 between the cylinders 7 and 8, 
horizontal perforations are formed in the web 1 by the perforation blade 
13 every predetermined interval corresponding to the circumferential 
length of the cylinder 7 or 8, i.e., every perspective folding position. 
In this horizontal perforation forming apparatus, if a gap between the 
paper holder 12 and the perforation blade seat 15 is not appropriate when 
they oppose each other, perforations are excessively formed and the web is 
torn during folding. Alternatively, when perforations are not 
satisfactory, predetermined folding precision cannot be assured. 
Therefore, this gap between the paper holder 12 and the perforation blade 
seat 15 must be appropriately determined. In a conventional perforation 
forming apparatus, when the distal end of the perforation blade 13 is worn 
and an extension amount from the paper holder 12 is reduced, when the 
thickness of printed matters is changed, or when the strength of the 
perforation portion is changed due to influences of printing conditions 
(e.g., printing dampening water, an ink, and an image pattern), a drying 
temperature, an ambient temperature, and paper quality, the perforation 
blade case 14 as a whole must be removed, and the shim 11 is replaced with 
a new one or the extension amount of the perforation blade 13 is adjusted. 
In addition, when printing matters are changed to ones without requiring 
horizontal perforations, the perforation blade case 14 as a whole is 
removed, and a balance weight is mounted in place of the perforation blade 
case 14 so as to prevent unbalance. 
In this conventional horizontal perforation forming apparatus described 
above, the extension amount of the perforation blade 13 must be adjusted. 
In addition, every time the printed matters are changed to ones which do 
not require horizontal perforations, the printing press must be stopped or 
the perforation blade case 14 as a whole must be removed, thus requiring 
much labor and a time-consuming operation, degrading operation efficiency 
of the press and the productivity. As the perforation blade case 14 is 
frequently removed, its fastening bolts are damaged or loosened, or an 
operator may forget to tighten these bolts. If this occurs, the 
perforation blade 13 may accidentally be displaced due to centrifugal 
force from the perforation cylinder 7 rotating at high speed, and an 
accident may occur. In addition, when the above operations are not 
properly performed, the web may be torn, and folding precision may be 
degraded. 
SUMMARY OF THE INVENTION 
It is an object of the present invention to provide a horizontal 
perforation forming apparatus for a web rotary press, capable of improving 
operability and eliminating downtime of the rotary press since fine 
adjustment can be performed during operation at high speed while an 
operator is observing an actual folding operation. 
It is another object of the present invention to provide a horizontal 
perforation forming apparatus for a web rotary press, capable of reducing 
waste of paper. 
It is still another object of the present invention to provide a horizontal 
perforation forming apparatus for a web rotary press, capable of 
shortening printing preparation time, increasing productivity, and 
reducing labor. 
In order to achieve the above objects of the present invention, there is 
provided a horizontal perforation forming apparatus for a rotary press in 
which a perforation blade extending in an axial direction of a perforation 
cylinder is set to oppose a perforation blade seat extending in an axial 
direction of a mating cylinder upon rotation of the perforation and mating 
cylinders, and horizontal perforations are formed by the perforation blade 
in a web which is traveling between the perforation and mating cylinders, 
which has an interaxial distance adjusting unit for adjusting a distance 
between axes of the perforation and mating cylinders. 
When the perforation blade is, worn or printed patterns are changed to ones 
which do not require horizontal perforations, an interaxial distance 
between the perforation cylinder and its mating cylinder is adjusted and a 
gap between the perforation blade seat and the paper holder of the 
perforation blade case can be automatically adjusted to consider changes 
in conditions without removing the perforation blade case as a whole. 
When an operation shaft of an interaxial distance adjusting unit is pivoted 
to adjust the interaxial distance between the perforation cylinder and its 
mating cylinder, the interaxial distance is adjusted, and at the same 
time, a phase adjusting axis is moved to automatically correct a 
horizontal perforation phase error caused upon adjustment of the 
interaxial distance between the perforation cylinder and its mating 
cylinder. Even when the phase adjusting shaft is pivoted to adjust the 
phase of the horizontal perforations, the operation shaft for the 
interaxial distance adjustment is not moved.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
FIGS. 1 to 5 show a horizontal perforation forming apparatus according to 
an embodiment of the present invention. 
Referring to FIGS. 1 to 5, a folding cylinder 21 constituted by folding 
paper cylinders brought into in rolling contact with a cutting cylinder 
(not shown) are rotatably supported by right and left frames 20 of a 
folder. A folding cylinder gear 22 coupled to a driving source is mounted 
on an end portion of the folding cylinder 21. A shaft 23 is stationarily 
supported on the frame 20 above the folding cylinder 21. A helical gear 24 
meshed with the folding cylinder gear 22 is fitted on the shaft 23. A 
phase adjusting shaft 26 of a phase adjusting unit (to be described in 
detail later) at its end portion is axially movable above the shaft 23 so 
that rotation of the phase adjusting shaft 26 is restricted. A helical 
gear 27 meshed with the helical gear 24 and a helical gear 28 are 
integrally fixed on the phase adjusting shaft 26 so as to be rotatable but 
not to be slidable on the phase adjusting shaft 26. A gear shaft 29 
extends on the frame 20 obliquely above the phase adjusting shaft 26. A 
helical gear 30 meshed with the helical gear 28 is pivotally fitted on the 
gear shaft 29. Reference numeral 31 denotes a lower nipping roller, both 
ends of which are rotatably supported by the left and right frames 20 and 
one end of which is located below the gear shaft 29. A helical gear 32 
meshed with the helical gear 30 is mounted on the end portion of the lower 
nipping roller 31. The lower nipping roller 31 is driven by the folding 
cylinder 21 and is rotated in a direction indicated by an arrow. A pair of 
cylinder support shafts 33 extend on the frames 20 obliquely below both 
end portions of the lower nipping roller 31. Air cylinders 35 are 
supported by brackets 34 fixed on the cylinder support shafts 33 by split 
fastening, respectively. Reference numerals 36 denote a pair of right and 
left roller arms pivotally supported by the cylinder support shafts 33, 
respectively. Operation ends of piston rods 37 reciprocated by air 
pressures of the air cylinders 35 are supported at free end portions of 
the roller arms 36, respectively. Holder rollers 38 each having the same 
length of the lower nipping roller 31 are rotatably supported in the axial 
holes of the left and right roller arms 36, respectively. The holder or 
press rollers 38 again about the lower nipping roller 31 upon pivotal 
movement of the roller arms 36 and forward movement of the piston rods 37 
of the air cylinders 35. A gear 39 at the shaft end portion is meshed with 
a gear 40 integrally mounted with the gear 32, so that the press roller 38 
is rotated in a direction opposite to that of the lower nipping roller 31 
in a direction indicated by an arrow. 
A pair of right and left eccentric bearings 41 are pivotally supported on 
the frames 20 above the lower nipping roller unit having the above 
arrangement. Each eccentric bearing 41 is eccentric by an amount indicated 
by symbol t between an axis F of an outer circumferential circle 41a and 
an axis F1 of an inner circumferential circle 41b. A perforation cylinder 
42 is rotatably supported by the inner circumferential circles 41b of the 
right and left eccentric bearings 41 through roller bearings 43. A 
cylinder gear 44 meshed with the helical gear 30 is mounted on the shaft 
end portion of the perforation cylinder 42. The perforation cylinder 42 is 
driven by the helical gear 30 and rotated in a direction indicated by an 
arrow in FIG. 1. The structure and pivotal mechanism of the perforation 
cylinder 42 will be described in detail later. 
A gear 46 meshed with the cylinder gear 44 and located above the 
perforation cylinder 42 is rotatably fitted on a gear shaft 45 extending 
on one of the frames 20. An upper nipping roller 47 is rotatably supported 
by the right and left frames 20. A gear 48 fixed on its shaft end portion 
is meshed with the gear 46, so that the upper nipping roller 47 is rotated 
in a direction indicated by an arrow in FIG. 1. A lever shaft 49 is 
pivotally supported by the right and left frames 20 at a lateral position 
from the upper nipping roller 47. A lever 50 is fixed at one side end 
portion of the lever shaft 49 by split fastening. Reference numeral 51 
denotes an air cylinder supported by the frame 20 on the lever 50 side. An 
operation end of a piston rod 52 of the air cylinder 51 is supported by 
the free end portion of the lever 50. Rubber rollers 54 are rotatably 
supported by roller arms 53 fixed at both ends of the lever shaft 49. With 
this arrangement, when the piston rod 52 of the air cylinder 51 is moved 
forward, the lever shaft 49 is pivoted through the lever 50. The rubber 
rollers 54 are brought into tight contact with the upper nipping roller 47 
through the roller arms 53. 
The gear 46 is meshed with a gear 56 mounted on a gear shaft 55 extending 
on the frame 20 at a lateral position of the gear shaft 45. A pair of 
right and left eccentric bearings 57 are pivotally supported on the frames 
20 immediately below the gear shaft 55. Each eccentric bearing 57 is 
eccentric by an amount represented by reference symbol t1 between an axis 
F2 of an outer circumferential circle 57a and an axis F3 of an inner 
circumferential circle 57b. A mating cylinder 58 mating with the 
perforation cylinder 42 is rotatably supported by the inner 
circumferential circles 57b of the right and left eccentric bearings 57 
through roller bearings 59. A cylinder gear 60 meshed with the gear 56 is 
mounted at an end portion of the mating cylinder 58. The mating cylinder 
58 is driven by the gear 56 and is rotated in a direction indicated by an 
arrow in FIG. 1. That is, the mating cylinder 58 is not directly coupled 
to the perforation cylinder 42 driven by the driving source and is driven 
by the driven gear 46 of the perforation cylinder 42. A horizontal 
perforation forming line obtained by connecting the axis F3 of the mating 
cylinder 58 driven as described above and the axis F1 of the perforation 
cylinder 42 is set to be horizontal. Horizontal perforation forming is 
performed by the perforation cylinder 42 and the mating cylinder 58. A 
perforation blade groove 42a (best shown in FIG. 5) having a rectangular 
section is formed in the outer circumferential portion of the perforation 
cylinder 42 so as to extend in the axial direction. A perforation blade 
case 61 is stored in the perforation blade groove 42a. The perforation 
blade case 61 has an elongated perforation blade base 64, both end 
portions of which are fixed on the bottom surface of the perforation blade 
groove 42a by bolts 63 through an elongated plate-like shim 62; a paper 
holder 65 having the same length as that of the perforation blade base 64 
and dovetailed with the base 64; a holder plate 66 screwed on the 
perforation blade base 64 to hold the perforation blade base 64 and the 
paper holder 65 from both sides of the holder plate 66; and an elongated 
plate-like perforation blade 68 which is engaged with the perforation 
blade groove 42a formed between the perforation blade base 64 and the 
paper holder 65 and is fixed by a plurality of bolts 67. The distal end of 
the perforation blade 68 extends from the paper holder 65. Reference 
numeral 69 denotes an adjusting screw which is threadably engaged with a 
screw hole formed in the bottom surface of the perforation blade base 64 
so as to be reciprocated therein. A perforation blade receiving groove 58a 
having a rectangular section is formed in the outer circumferential 
portion of the mating cylinder 58 so as to extend in the axial direction 
thereof. Elongated perforation blade seats 71 split in the widthwise 
direction and formed integrally by a bolt 70 are stored in the perforation 
blade receiving groove 58a and are fixed on the bottom surface of the 
perforation blade receiving groove 58a. A groove 71a is formed on the 
outer end face of the perforation blade seat 71 to receive the distal end 
of the perforation blade 68. With this arrangement, when the web 1 passes 
between the perforation cylinder 42 and the mating cylinder 58, and the 
perforation blade case 61 opposed the perforation blade seat 71, the 
perforation blade 68 is engaged with the groove 71a to form perforations 
at a prospective folding portion of the web 1. 
The horizontal perforation forming apparatus having the above arrangement 
includes an interaxial distance adjusting unit for simultaneously moving 
the perforation cylinder 42 and the mating cylinder 58 to adjust an 
interaxial distance between these cylinders. That is, an operation shaft 
75 is pivotally supported in a bracket 74 fixed outside one frame 20 near 
the perforation cylinder 42 and the axial hole formed in the other frame 
20. A handle 76 is fixed to an extended end portion of the operation shaft 
75. Arcuated stud holders 77 are fixed on outer circumferential portions 
of the right and left eccentric bearings 41 by pluralities of bolts 78, 
respectively. Studs 79 are respectively engaged with the central portions 
of the stud holders 77 such that polygonal heads of the studs 79 extend 
outward from the stud holders 77. Arcuated stud holders 80 are fixed on 
the outer circumferential portions of the right and left eccentric 
bearings 57 by pluralities of bolts 81, respectively. Studs 82 are 
respectively engaged with the central portions of the stud holders 80 such 
that polygonal head portions of the studs 82 extend outward from the stud 
holders 80. Reference numeral 83 denotes a bearing located between the 
corresponding pair of studs 79 and 82 and fixed to the corresponding frame 
20. Screw shafts 84 are pivotally supported by the bearings 83, 
respectively. A counterclockwise screw 84a of each screw shaft 84 is 
threadably reciprocated in a screw hole of the corresponding stud 79. A 
clockwise screw 84b of each screw shaft 84 is threadably reciprocated in a 
screw hole of the corresponding stud 82. A bevel gear 85 fixed to one end 
of each screw shaft 84 is meshed with a corresponding bevel gear 86 on the 
operation shaft 75. When the operation shaft 75 is pivoted with the handle 
76 to pivot both the screw shafts 84 through meshing between the bevel 
gears 85 and 86, the stud holders 77 and the stud holders 80 are moved in 
opposite directions through the studs 79 and 82 by the threadable action 
of the counterclockwise and clockwise screws 84a and 84b. As a result, the 
eccentric bearings 41 and 57 are pivoted at fitting portions of the outer 
circumferential circles 41a and 57a. The axes F1 and F3 of the inner 
circumferential circles 41b and 57b are pivoted about the axes F and F2 of 
the outer circumferential circles 41a and 57a by eccentric action. The 
perforation blade case 61 and the perforation blade seat 71 are moved in 
opposite directions, so that a gap between the paper holder 65 and the 
perforation blade seat 71 can be adjusted. In this apparatus, positions of 
the gears 30, 46, 60, and 56 are determined such that a line obtained by 
connecting the center of the driving gear 30 for the perforation cylinder 
42 and the center of the driven gear 46 and a line obtained by connecting 
the cylinder gear 60 of the mating cylinder 58 and the upper gear 56 are 
almost perpendicular to a line obtained by connecting the centers of the 
perforation cylinder 42 and the mating cylinder 58. The axes F1 and F3 are 
moved to the eft and right from a position corresponding to a state (FIG. 
1) in which the axes F1 and F3 are located immediately below the axes F 
and F2. Reference numerals 85b denote stoppers for limiting movement of 
both ends of each of the stud holders 77 and 80 fixed on the frame 20. 
A phase adjusting unit 25 will be described below. The phase adjusting 
shaft 26 is supported so that pivotal movement is restricted and axial 
movement toward the frame 20 is allowed by a key 87. A screw shaft 90 
having a handle 89 and supported by a bearing 88 on the frame 20 is 
threadably engaged with a screw hole 26a formed at one end of the phase 
adjusting shaft 26 such that axial movement of the screw hole shaft 90 is 
inhibited. With this arrangement, when an operator holds and turns the 
handle 89 to pivot the screw shaft 90, the phase adjusting shaft 26 is 
axially reciprocated by the threadable action, and the cylinder gear 44 is 
slightly pivoted through the helical gear 30 by the helical gear action of 
the helical gear 28. The perforation cylinder 42 is slightly pivoted 
accordingly, and the phase of the perforation cylinder 42 with respect to 
the stationary folding cylinder 21 can be adjusted. Reference numeral 91 
denotes a lock handle for fixing the screw shaft 90 upon pivotal movement. 
The helical gear 24 on the shaft 23 is formed to be axially movable. Upon 
axial movement of the helical gear 24, lap adjustment for one parallel 
folding operation is performed. 
An operation of the horizontal perforation forming apparatus having the 
above arrangement will be described below. The printed and conveyed web 1 
is fed out by the upper nipping roller 47 and is guided between the 
perforation cylinder 42 and the mating cylinder 58. After the web 1 passes 
through the perforation cylinder 42 and the mating cylinder 58, the web 1 
is guided to a gap between the folding cylinder 21 and the cutting 
cylinder by the lower nipping roller 31. Horizontal perforations are 
formed by the perforation blade 68 in the web 1 passing through the 
perforation cylinder 42 and the mating cylinder at intervals each 
corresponding to a circumferential length of each of the perforation 
cylinder 42 and the mating cylinder 58 every time the perforation blade 
seat 71 opposes the groove 71a. The web 1 is folded at a perforation 
position by the folding cylinder 21. Therefore, excellent folding 
precision can be easily obtained. 
When the thickness of the web 1 is changed or a distal end of the 
perforation blade 68 is worn, a gap between the paper holder 65 and the 
perforation blade seat 71 must be adjusted. In this case, the operator 
holds and turns the handle 76 to pivot the operation shaft 75. When both 
the screw shafts 84 are synchronously rotated through meshing between the 
bevel gears 85 and 86, the studs 79 and the stud holders 77 on the 
perforation cylinder 42 side are circumferentially moved in a direction 
opposite to that of the studs 82 and the stud holders 80. As a result, the 
eccentric bearings 41 and 57 are pivoted at the fitting portions of the 
outer circumferential circles 41a and 57a. The perforation cylinder 42 and 
the mating cylinder 58 are pivoted in opposite directions such that the 
axes F1 and F3 of the inner circumferential circles 41b and 57b are 
pivoted about the axes F and F2 of the outer circumferential circles 41a 
and 57a. The perforation blade case 61 and the perforation blade seat 71 
are moved, and a gap between the paper holder 65 and the perforation blade 
seat 71 is adjusted. 
In this case, in the apparatus of this embodiment, a direction of eccentric 
direction obtained by connecting the axes F1 and F and a line of eccentric 
direction obtained by connecting the axes F3 and F2 are almost 
perpendicular to a horizontal perforation forming line obtained by 
connecting the axes of the perforation cylinder 42 and the mating cylinder 
58. When a state of FIG. 4(a) is changed to that of FIG. 4(b), a change in 
interaxial distance by eccentricity is effectively applied as an extension 
amount of the perforation blade 68, as indicated by .DELTA.x. In addition, 
since the perforation cylinder 42 and the mating cylinder 58 are 
simultaneously moved in the opposite directions, a difference in 
rotational phase generated in the drive gear upon movement by the distance 
.DELTA.x is canceled. The perforation blade 68 will not be removed from 
the groove 71a of the perforation blade seat 71. 
A line obtained by connecting the driven gear 46 and the driving gear 30 
meshed with the cylinder gear 44 of the perforation cylinder 42 and a line 
obtained by connecting the driving gear 56 and the cylinder gear 60 of the 
mating cylinder 58 are almost perpendicular to a line angularly spaced 
apart from the vertical axis by the distance .DELTA.x. A change .DELTA.a 
in interaxial distance a between the cylinder gear 44 and the driving gear 
30 by an eccentric amount t and an adjusting angle .phi. shown in FIG. 
4(b) can be minimized. Similarly, an interaxial distance between the 
cylinder gear 44 and the driven gear 46 and an interaxial distance between 
the driving gear 56 and the cylinder gear 60 of the mating cylinder 58 can 
be minimized. In addition, the perforation cylinder 42 is not directly 
coupled to the mating cylinder 58, i.e., the mating cylinder 58 is driven 
by the gear 56 located in almost the same direction as the eccentric 
direction. Therefore, a change in interaxial distance between the 
cylinders cannot be directly transmitted as a change in interaxial 
distance between the gears. 
Referring to FIGS. 4(a) and 4(b), when the perforation cylinder 42 is 
displaced by the eccentric amount t and the adjusting angle .phi., a 
change in angle .theta. occurs between the perforation cylinder 42 and the 
driving gear 30 for driving the driving force to the cylinder gear 44, 
thus causing a rotational phase error .psi. of the perforation blade 68. 
In the apparatus of this embodiment, since the same amount of change 
occurs in the mating cylinder 58 in a direction opposite to that of the 
perforation cylinder 42, a phase error .psi. also occurs in the mating 
cylinder 58. In this case, however, the perforation blade 68 will not be 
removed from the groove 71a of the perforation blade seat 71 by the phase 
error .psi.. 
This embodiment employs involute gears. Even if an interaxial distance 
between the gears is changed, proper meshing can be achieved. When the 
normal interaxial distance a is changed, a pressure angle .alpha. is 
changed and backlash c is also changed. If the interaxial distance is 
increased by .DELTA.a, the pressure .alpha. and the backlash c are also 
changed. In this embodiment, as described above, since the direction 
corresponding to the distance a is set to be almost perpendicular to a 
direction corresponding to the distance .DELTA.x, a change .DELTA.c in 
backlash of the gear can be minimized with respect to a change .DELTA.x. 
In addition, since the pivotal limitations of the eccentric bearings 41 
are restricted by the stoppers 85b, the backlash will not exceed a 
predetermined backlash range. 
The paper holder 65 in the perforamtion blade case 61 is made of a soft 
elastic material and is extendible in the radial direction of the 
perforation cylinder 42. Even if a distance between the mating cylinder 58 
and the perforation blade case 61 including the paper holder 65 is 
changes, this change can be absorbed as a change in the paper holder 65 
and, therefore, does not have an amount which adversely affects quality of 
the printed matters. 
FIG. 6 is a side view of a gear train according to another embodiment of 
the present invention when viewed from the same side as in FIG. 1 in 
correspondence with FIG. 3. In the embodiment of FIG. 6, the gear 56 is 
eliminated, and instead, a gear 56A coaxial with a gear 39 and a gear 56B 
meshed with a gear 60 are provided to drive a mating cylinder 58 from the 
driving side of a perforation cylinder 42. A line obtained by connecting 
the centers of the gears 60 and 56B is set to be almost perpendicular to a 
horizontal perforation forming line. With this arrangement, the same 
effect as in the previous embodiment can be obtained. 
FIGS. 7 to 9 show still another embodiment of the present invention. More 
specifically, FIG. 7 shows a horizontal perforation forming apparatus when 
viewed in correspondence with FIG. 1, FIG. 8 shows it in correspondence 
with FIG. 2, and FIG. 9 shows a state when viewed from the same side as in 
FIG. 1 so as to explain gear meshing. The same reference numerals as in 
FIGS. 1 to 3 denote the same parts in FIGS. 7 to 9, and a detailed 
description thereof will be omitted. 
In the embodiment of FIGS. 7 to 9, an operation shaft 100 corresponding to 
the operation shaft 75 of the previous embodiment is located obliquely 
below a perforation cylinder 42 and is supported by right and left frames 
20. A handle 76 is attached to the operation shaft 100. A pair of bevel 
gears 101 are mounted on the operation shaft 100 near the right and left 
frames 20. The bevel gears 101 are meshed with bevel gears 103 mounted on 
worm shafts 102 extending parallel to the frames 20, respectively. A 
cylinder gear 44 of the perforation cylinder 42 meshed with and driven by 
a gear 30 in the previous embodiment is disengaged from the gear 30. The 
cylinder gear 44 is driven by a driving gear 46 through gears 104 and 105 
which are sequentially meshed with the gear 30. A gear 60 on the side of a 
mating cylinder 58 is driven by a driving gear 56 meshed with the gear 46. 
A line obtained by connecting the centers of the gears 46 and 44 and a 
line obtained by connecting the centers of the gears 56 and 60 are almost 
perpendicular to a horizontal perforation forming line as in the previous 
embodiment. A right pair of gear shafts 45 and 55 and a left pair of gear 
shafts 45 and 55 are fixed on the right and left frames 20, respectively. 
Sector-shaped levers 107 and 108 are respectively pivotally supported by 
the gear shafts 45 and 55 inside the corresponding frame 20. The 
perforation cylinder 42 and the mating cylinder 58 are rotatably supported 
by free end portions of the levers 107 and 108 through bearings. Worm 
wheels 109 and 110 are formed at the free ends of the levers 107 and 108, 
respectively. These worm wheels 109 and 110 are respectively meshed with 
clockwise and counterclockwise worm gears 111 and 112 mounted on the 
corresponding worm shaft 102. Reference numerals 113 denote stoppers for 
defining pivotal limitations of the levers 107 and 108. 
When the thickness of the web 1 is changed or the distal end of a 
perforation blade 68 is worn, the gap between a paper holder 65 and a 
perforation blade seat 71 must be adjusted. In this case, with the above 
arrangement, the operator holds and turns the handle 76 to pivot the 
operation shaft 100, and the worm shafts 102 are rotated through meshing 
between the bevel gears 101 and 103. The levers 107 and 108 are swung upon 
meshing with the clockwise and counterclockwise worm gears 111 and 112, 
thereby adjusting an interaxial distance between the perforation cylinder 
42 and the mating cylinder 58. As a result, the perforation blade case 61 
and the perforation blade seat 71 are moved to adjust a gap between the 
paper holder 65 and the perforation blade seat 71. In this case, a line 
obtained by connecting the centers of the gears 46 and 44 and a line 
obtained by connecting the centers of the gears 56 and 60 are symmetrical 
with each other about the traveling line of the web 1. Even if the 
perforation cylinder 42 and the mating cylinder 58 are moved, the phase of 
the perforation blade case 61 in the circumferential direction is always 
matched with the phase of the perforation blade seat 71 in the same 
direction, as in the previous embodiment. It is, therefore, readily 
understood that the perforation blade case 61 need not be removed when 
printing is to be changed to printed matters which do not require 
horizontal perforation formation or the interaxial distance is to be 
adjusted. In addition, since the levers 107 and 108 are pivoted about the 
gear shafts 45 and 55, no problem is posed in meshing between gears 46, 
44, 56, 60, and 105 and the like. 
FIGS. 10 to 12 show still another embodiment of the present invention. More 
specifically, FIG. 10 shows a horizontal perforation forming apparatus in 
correspondence with FIG. 7, FIG. 11 shows it in correspondence with FIG. 
8, and FIG. 12 shows a gear train when viewed from the same side as in 
FIG. 1 in correspondence with FIG. 9. The same reference numerals as in 
FIGS. 7 to 9 denote the same parts in FIGS. 10 to 12, and a detailed 
description thereof will be omitted. 
In the embodiment of FIGS. 10 to 12, each worm shaft 102 coupled to an 
operation shaft 100 through corresponding bevel gears 101 and 103 has 1/2 
the length of the worm shaft 102 of the embodiment of FIGS. 7 to 9. Each 
lever 107 connected to the corresponding worm shaft 102 through a 
corresponding worm gear 111 and a corresponding worm wheel 109 is pivoted 
on only the side of a perforation cylinder 42. A cylinder gear 44 of the 
perforation cylinder 42 is meshed with a driving gear 30 and a driven gear 
46 and also meshed with a cylinder gear 60 of a mating cylinder 58. Both 
ends of the perforation cylinder 42 are supported by the levers 107 
through bearings, respectively. One end of the perforation cylinder 42 is 
connected to a shaft fixed to the cylinder gear 44 through an eccentric 
shaft coupling 114 generally called a Schmitt coupling. In the eccentric 
shaft coupling 114 called the Schmitt coupling, a support portion on the 
perforation cylinder 42 side and a support portion on the side of the 
shaft to which the cylinder gear 44 is fixed are formed to be eccentric. 
Even if the levers 107 are swung, the angular phase of the perforation 
cylinder 42 is not changed with respect to the cylinder gear 44. 
Assume that a gap between the paper holder 65 and a perforation blade seat 
71 must be adjusted because the thickness of a web 1 is changed or the 
distal end of a perforation blade 68 is worn. In this case, with the above 
arrangement, the operator holds and turns a handle 76 to pivot the 
operation shaft 100 and then worm shafts 102 through meshing with the 
bevel gears 101 and 103. The levers 107 are swung upon meshing between the 
worm gears 111 and the worm wheels 109 to adjust a gap between an 
interaxial distance between the perforation cylinder 42 and the mating 
cylinder 58. As a result, a perforation blade case 61 and the perforation 
blade seat 71 are moved to adjust a gap between the paper holder 65 and 
the perforation blade seat 71. In this case, since only the eccentric 
shaft coupling 114 is made eccentric, no angular phase error occurs 
between the perforation cylinder 42 and the cylinder gear 44. A total 
eccentric error between the perforation blade case 61 and the perforation 
blade seat 71 is caused by only the eccentric action. That is, only a 
small error occurs, and the phase of the mating cylinder 58 need not be 
adjusted. Note that the perforation blade case 61 need not be removed when 
printing is to be changed to printed matters which do not require 
horizontal perforation formation or an interaxial distance is to be 
adjusted. Since the levers 107 are pivoted about the gear shafts 45, no 
problem is posed in meshing of the gears 46, 44, and 60. 
In this embodiment, the perforation gear 44 is coupled to the perforation 
cylinder 42 through the eccentric shaft coupling 114. The number of gears 
can be reduced, and the structure can be simplified. If a Schmitt coupling 
is used as the eccentric shaft coupling, the angular velocity is not 
changed even if an eccentric operation is performed, thus coping with 
high-speed operation with a high torque. 
FIG. 13 is a view showing a gear arrangement according to still another 
embodiment of the present invention. In this embodiment, a timing belt 117 
is looped between an upper nipping roller 47 and a mating cylinder 58 
while the timing belt 117 is kept taut by tensioners 115 and 116. The 
number of gears can be further reduced. 
FIG. 14 is a longitudinal sectional view of a horizontal perforation 
forming apparatus according to still another embodiment of the present 
invention. The same reference numerals as in the embodiment of FIG. 2 
denote the same parts in the embodiment of FIG. 14, and a detailed 
description thereof will be omitted. The gear arrangement of this 
embodiment is the same as that of FIG. 3 and will be described with 
reference to FIG. 3. The embodiment of FIG. 14 aims at eliminating a phase 
error of the horizontal perforation during interaxial distance adjustment. 
The phase error will be described with reference to the gear layout of 
FIG. 15. 
Referring to FIG. 15, a phase error .phi. will be defined as follows: 
EQU .phi.=.theta..sub.1 (1+Z.sub.1 /Z.sub.2) (1) 
where Z.sub.1 is the number of teeth of a driving gear 30, Z.sub.2 is the 
number of teeth of a perforation cylinder gear 44, and .theta..sub.1 is an 
angle obtained by moving the perforation cylinder. 
A moving amount x of the perforation cylinder is defined as follows: 
EQU x={m.sub.n (Z.sub.1 +Z.sub.2)2 cos .beta..sub.0 }tan.theta..sub.1(2) 
where m.sub.n is the gear angle module, and .beta..sub.0 is a torsion 
angle. When the angle .theta..sub.1 is sufficiently small, the following 
condition is established: 
EQU tan.theta..sub.1 .apprxeq..theta..sub.1 (rad) 
therefore, the phase error can be rewritten as follows: 
EQU .theta..sub.1 =[2x cos .beta..sub.0 /{m.sub.n (Z.sub.1 +Z.sub.2)}](3) 
When a substitution of equation (3) into equation (1) eliminates 
.theta..sub.1 and yields the following equation of the phase error: 
EQU .phi.={2 cos .beta..sub.0 /m.sub.n Z.sub.2 }x=C.sub.1 x (rad)(4) 
EQU for C.sub.1 =2 cos .beta..sub.0 /m.sub.n Z.sub.2 
That is, it is apparent that the horizontal perforation phase error .phi. 
caused by the moving amount x of the perforation cylinder is proportional 
to the moving amount x of the cylinder. 
The arrangement of this embodiment will be described with reference to FIG. 
14. A phase adjusting shaft 26 is divided into two parts from the center 
in the axial direction, and clockwise and counterclockwise threaded 
portions are formed in a split portion and are engaged with a wide gear 
120. Reference numeral 122 denotes a guide pin integrally formed with one 
phase adjusting shaft 26 and slidably fitted in a hole 26b formed in the 
other phase adjusting shaft 26. A gear 123 meshed with the gear 120 is 
mounted on an operation shaft 75. Reference numeral 74 denotes a bracket 
for slidably supporting a shaft end portion of the phase adjusting shaft 
26. When the operation shaft 75 is pivoted, the phase adjusting shaft 26 
whose pivotal movement is restricted by a key 87 is moved upon meshing 
between the gear 120 and the gear 123. Other arrangements are the same as 
those of FIG. 2, and a detailed description thereof will be omitted. 
With the above arrangement, when the thickness of a web 1 is changed or the 
distal end of a perforation blade 68 is worn, a gap between a paper holder 
65 and a perforation blade seat 71 must be adjusted. In this case, an 
operator holds and turns a handle 76 to pivot the operation shaft 75, and 
a screw shaft 84 is synchronously rotated through meshing between bevel 
gears 85 and 86. The studs 79 and 82 and stud holders 77 and 80 of a 
perforation cylinder 42 and its mating cylinder 58 are moved in opposite 
circumferential directions by the action of counterclockwise and clockwise 
threaded portions 84a and 84b. The perforation cylinder 42 and the mating 
cylinder 58 are pivoted in opposite directions, and a perforation blade 
case 61 and the perforation blade seat 71 are moved to adjust the gap 
between the paper holder 65 and the perforation blade seat 71. 
In this apparatus, upon pivotal movement of the operation shaft 75, the 
phase adjusting shaft 26 whose pivotal movement is restricted by the key 
87 is axially moved upon meshing between the gears 120 and 123. The 
cylinder gear 44 is slightly pivoted through the gear 30 by the action of 
the helical teeth of a gear 28, so that a phase of the perforation 
cylinder 42 with respect to a stopped folding cylinder 21 is adjusted. 
A phase adjustment amount .PHI. of the perforation cylinder given by an 
axial displacement amount y of the phase adjusting shaft 26 in interaxial 
distance adjustment and phase adjustment is given as follows: 
##EQU1## 
where Z.sub.24, Z.sub.27, Z.sub.28, and Z.sub.44 are numbers of teeth of 
gears 24 and 27 and the gears 28 and 44, respectively, m.sub.i is the 
quadrature module of teeth of each of the gears 24 and 27, m.sub.0 is the 
quadrature module of teeth of each of the gears 28 and 44, .beta..sub.i is 
the torsion angle of each of the gears 24 and 27, and .beta..sub.0 is the 
torsion angle of each of the gears 28 and 44. 
In this case, the phase can be changed in proportion to the displacement 
amount y. 
As is apparent from equations (4) and (5), when the perforation cylinder is 
moved by x (mm), the phase adjusting shaft 26 is moved by y=(C.sub.1 
/C.sub.2)x (mm), thereby correcting the perforation phase error. 
When a handle 89 is pivoted to adjust only the horizontal perforation 
phase, the divided phase adjusting shafts 26 are simultaneously moved 
through the gear 120 in the axial direction, so that the phase can also be 
changed. In this case, since the gear 120 is moved only in the axial 
direction, axial movement of the gear 120 does not cause circumferential 
movement of the gear 123. 
According to the present invention as has been described above, the 
interaxial distance adjusting unit for adjusting an interaxial distance 
between the perforation cylinder and the mating cylinder is included in 
the horizontal perforation forming apparatus for a rotary press wherein 
the perforation blade extending in the axial direction of the perforation 
cylinder of the rotary press is located to oppose the perforation blade 
seat extending in the axial direction of the mating cylinder upon rotation 
of the perforation and mating cylinders, and horizontal perforations are 
formed by the perforation blade in a web which is traveling between the 
perforation and mating cylinders. At the time of movement of the 
perforation blade case, e.g., at the time of a change in paper thickness, 
the perforation blade case need not be removed unlike in the conventional 
apparatus wherein a shim plate is replaced. After initialization is 
completed, fine adjustment can be performed at high speed while the 
operator checks an actual folding operation. Operability can be improved, 
and the downtime of the press can be greatly reduced. At the same time, 
waste of paper can be reduced. When printing is changed to printed matters 
which do not require perforations, the perforation blade case need not be 
removed unlike in the conventional apparatus. The perforation blade case 
is moved away from the traveling web while the perforation blade case is 
kept attached to the press, thus providing a large advantage. In addition, 
the moving amount of the cylinder is effectively given as an adjustment 
amount of the extension of the perforation blade. 
The horizontal perforation forming apparatus for a rotary press includes 
the phase adjusting unit for moving the phase adjusting shaft in the axial 
direction to pivot the perforation cylinder so as to adjust the phase of 
the perforation cylinder in the circumferential direction. At the same 
time, the operation shaft of the interaxial distance adjusting unit is 
interlocked with the phase adjusting shaft, so that the perforation phase 
will not be deviated from the proper phase while phase adjustment is 
synchronized with adjustment for a distance between the axes of the 
perforation cylinder and the mating cylinder. The preparation time can be 
reduced, productivity can be increased, and the labor can be reduced. At 
the same time, waste of paper can be reduced.