JPH02152799A - Horizontal scoring device for rotary press - Google Patents

Abstract

PURPOSE:To quickly perform the movement adjustment of a machine blade case at the paper width changing time during operation and to improve the operating property by providing an interaxial distance adjusting device adjusting the interaxial distance between a machine barrel and machine receiving barrel. CONSTITUTION:An operation shaft 75 is operated by turning by holding a handle and when the both parts screw shafts 84 are turned via the biting of bevel gears 85, 86, stud holders 77, 80 are moved in reverse direction mutually in the circumferential direction via studs 79, 82 by the screw action of a left screw 84a and right screw 84b. As a result, eccentric bearings 41, 57 are turned at the engaging part of an outer peripheral circle 41a and the shaft centers F1, F3 of the inner peripheral circle are turned centering around the shaft centers F, F2 of the outer peripheral circle 41a by the eccentric action, so a machine blade case 61 and machine blade receiver 71 are moved in the reverse direction mutually and the gap between a paper presser and the machine blade receiver 71 is adjusted.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a horizontal perforation processing device that is attached to a folding machine of a web rotary printing press and that creates horizontal perforations in a running web extending in the width direction of the web. It is related to.

(Prior art 1) A paper web rotary printing press is equipped with a folding machine that folds the printed web in the width direction and length direction. A transverse perforation device is provided to facilitate the origami in the subsequent origami locations.

FIG. 16 is a schematic side view of a conventional horizontal perforation machine of this type, and this will be explained based on the figure.
In the folding machine, the web l runs between a former device that folds the printed web in the width direction and a group of origami cylinders (none of which are shown) that folds the web in the length direction. A horizontal perforation processing device shown by , nipping rollers 3.4 above and below it, and rubber rollers 5. attached to these. A presser roller 6 is provided, and a sewing machine cylinder 7 and a sewing machine receiving cylinder 8 are arranged in the horizontal perforation processing device 2 with a slight gap provided between their circumferential surfaces. In the sewing machine blade groove 7'a provided in the direction of the outer peripheral ridge line of the sewing machine body 7, there is a sewing machine blade stand 9 extending over its entire length, a presser plate to surrounding this, a shim 11, and a dovetail groove fitted to the sewing machine blade stand 9. paper presser 1
2 and a long plate-shaped sewing machine blade 13 held in a sewing machine blade groove in the center. I'm letting you do it. Further, a long sewing machine blade receiver 15 is fixed in a sewing machine blade receiver groove 8a extending in the ridgeline direction of the sewing machine receiver barrel 8. Both cylinders 7.8, nipping rollers 3, 4, etc. are driven by gears from the origami cylinder group side and rotate in the direction shown by the arrow in the figure.

With this configuration, the web I conveyed after printing is sent out by the upper nipping roller 3 and guided to a temperature between 7.8 and 7.8 mm, and after passing between them, the web I is conveyed by the lower nipping roller 4. You will be led to a group of origami trunks. The web l passing between the two cylinders 7 and 8 is spaced by the sewing machine blade 13 which faces and engages with the blade groove of the sewing machine blade holder 15, leaving an interval equal to the circumference of the two cylinders 7 and 8. A horizontal perforation is made at the location where the origami will be made later.

In such a horizontal perforation processing device, the paper presser 12
If the gap size between the and the perforation blade holder 15 is not appropriate, the perforations will become deep (which may cause the paper to tear during origami), or the perforations will become shallow and the desired folding accuracy may not be achieved. Therefore, it is necessary to make this gap appropriate.

Conventionally, this has been done in cases where the cutting edge of the sewing machine blade 13 is worn out and the amount of protrusion from the paper presser becomes smaller, the thickness of the printed matter changes, or the printing conditions such as dampening water, ink, and pattern etc. If the strength of the perforation changes due to differences in drying temperature, air temperature, paper quality, etc., the protrusion of the sewing machine blade 13 is adjusted by removing the entire sewing machine blade case 14 and replacing the shim 11. . Further, even when the printed matter is changed to one that does not have horizontal perforations, the entire sewing machine blade case 14 is removed and a balance weight is installed in its place to maintain the dynamic balance.

[Problem to be solved by the invention]

However, in such a conventional horizontal perforation processing device, the machine operation has to be changed every time the protrusion of the perforation blade 13 is adjusted as described above, or whenever the print is changed to a printed matter that does not require horizontal perforation processing. Since the sewing machine had to be stopped and the sewing machine blade case I4 removed, it required a great deal of labor and a long time, and there was a problem that the operating rate and productivity of the machine were reduced. In addition, as the sewing machine blade case 14 is removed more frequently, the fastening bolts are likely to break, loosen, or be forgotten to be tightened, and the sewing machine blade 13 may fly out from the sewing machine body 7, which rotates at high speed, due to centrifugal force. There was a risk of causing a major accident.

Furthermore, if such troublesome work is neglected, there are problems in that the web may be torn or the folding accuracy may be reduced.

[Means for Solving the Problems] In order to solve such problems, in the present invention, a sewing machine blade extending in the ridgeline direction of the sewing machine barrel and a sewing machine blade receiver extending in the ridgeline direction of the sewing machine receiving barrel are connected to each other. In a horizontal perforation processing device for a rotary printing press in which a horizontal perforation extending in the width direction of the web is made by the perforation blade on a web that rotates and faces each other and runs between the two cylinders, the perforation cylinder and the perforation receiving cylinder are provided. A center-to-center distance adjustment device is provided to adjust the center-to-center distance.

Further, in the horizontal perforation processing device of such a rotary printing press, a phase adjustment device is provided which rotates the sewing machine paulownia by moving the phase adjustment shaft in the axial direction and adjusts the phase A of the sewing machine barrel in the circumferential direction. In addition, the operating shaft of the inter-axis distance adjusting device and the phase adjusting shaft are configured to move in conjunction with each other.

(Function) If the sewing machine blade wears out, the thickness of the web changes, or the printed material is changed to one that does not require horizontal perforation, the distance between the centers of the sewing machine barrel and the sewing machine receiving barrel should be adjusted. When adjusted, the gap between the paper presser of the sewing machine blade case and the sewing machine blade holder is adjusted, and it is possible to respond to changes in conditions without removing the sewing machine blade case.

In addition, when the operating shaft of the center distance adjustment device is rotated to adjust the distance between the centers of the sewing machine barrel and the sewing machine receiving barrel, the phase adjustment shaft moves at the same time as the distance between the two warm centers is adjusted. ,
By adjusting the distance between the axes of the sewing machine barrel and the sewing machine receiving barrel, the phase shift of the horizontal perforations that occurs is automatically corrected. Conversely, even if the phase adjustment shaft is rotated in order to adjust the phase of the horizontal perforations, the shaft distance adjustment device No. 7 does not move.

〔Example〕

1 to 5 show an embodiment of the horizontal perforation processing device according to the present invention, FIG. 1 is a side view thereof, FIG. 2 is a partially broken developed plan view, and FIG. 3 is a gear gear. Fig. 4 is a side view of the gear train seen from the same side as Fig. 1 to explain the meshing of the sewing machine, and Fig. 4 is a side view of the gear train seen from the same side as Fig. 1. A side view of the gear, and FIG. 5 is an enlarged sectional view of the sewing machine blade case and the sewing machine blade holder. In the figure, the left and right frames 20 of the folding machine include
A folding cylinder 21 and a cutting cylinder (not shown) constituting the origami cylinder group are rotatably supported with their peripheral surfaces facing each other.
A folding drum gear 22, which is drivingly connected to the driving side, is attached to the shaft end of the shaft. Above the folding drum 21, a shaft 23 is fixedly supported by the frame 20, and a helical gear 24 that meshes with the folding drum gear 22 is fitted onto the shaft 23. Further, above the shaft 23, a phase adjustment shaft 26 having a phase adjustment device 25 at its end, which will be described in detail later, is supported so as to be movable in the axial direction with rotation restricted. A helical-toothed gear 27 that meshes with the gear 24 and a helical-toothed gear 28 are integrally fixed to each other and are fitted onto the gear 26 so as to be rotatable and non-slidable. Furthermore, a gear shaft 29 is installed in the frame 20 on the diagonal F side of the phase adjustment shaft 26, and a helical tooth gear 30 that meshes with the gear 28 is rotatably fitted onto the gear shaft 29. ing. 31 is a lower nipping roller with one end shaft positioned below the gear shaft 29 and both end shafts rotatably supported by the left and right frames 20; A toothed gear 32 is pivotally mounted, and the lower nipping roller 31 is driven from the folding drum 21 side and rotates in the direction shown by the arrow in the figure. A pair of left and right cylinder support shafts 33 are implanted in the frame 20 diagonally below both end shafts of the lower nipping roller 31, and a frame 34 is fixed to each cylinder support shaft 33 with a split clamp.
Air cylinders 35 are respectively pivotally supported. 3
Reference numeral 6 denotes a pair of left and right roller arms rotatably supported by a cylinder support shaft 33, and the active end of a piston rod 37, which moves back and forth with air pressure from an air cylinder 35, is pivotally attached to the free end of the roller arm 6. , in the shaft holes of the left and right roller arms 36,
A presser roller 38 having the same length as the lower nipping roller 31 is rotatably supported. This pressing roller 38 is pressed against the lower nipping roller 31 by the rotation of the roller arm 36 caused by advancing the piston rod 37 of the air cylinder 35, and the gear 39 at the end of the shaft is a gear integrated with the gear 32. By engaging with 40,
It rotates in the opposite direction to the lower nipping roller 31 as shown by the arrow in the figure.

A pair of left and right eccentric bearings 41 are rotatably supported on the frame 20 above the lower nearing roller device configured in this manner.
The axial center F of a and the axial center F1 of the inner circumferential circle 41b are eccentric by the amount indicated by the reference numeral in the figure. A sewing machine Wq42 is rotatably supported on the inner circumferential circle 41b of the left and right eccentric bearings 41 via a rolling bearing 43, and a body gear 44 that meshes with the gear 30 is attached to the end shaft of the sewing machine body 42. The sewing machine barrel 42 is driven from the gear 30 side and rotates in the direction shown by the arrow in the figure. The configuration of the sewing machine barrel 42 and its rotation mechanism will be explained in detail later.

A gear shaft 45 located above the sewing machine barrel 42 and implanted in the frame 20 on one side has a gear 4 that meshes with the gear 44.
6 is rotatably fitted, and an upper nipping roller 47 is disposed diagonally above the gear shaft 45, and an upper nipping roller 47 is connected to the left and right frames 20.
A gear 48 fixed to the end of the shaft meshes with the gear 46, thereby rotating in the direction shown by the arrow in the figure. Upper nipping roller 4
A lever shaft 49 is rotatably supported by the left and right frames 20 on the side of the lever shaft 7, and a lever 50 is fixedly fixed to one end of the lever shaft 49 by splitting. Reference numeral 51 denotes an air cylinder pivotally supported on the frame 20 of the lever 50 (!I!), and its piston 0 valve 1520 active end is pivotally attached to the free end of the lever 50, and both ends of the lever shaft 49 A rubber roller 54 is attached to the roller arm 53 fixed to the
is rotatably supported. By doing this, by advancing the piston rod 52 of the air cylinder 51, the lever shaft 49 is rotated via the lever 50, and the rubber roller 54 is pressed against the upper nipping roller 47 via the roller arm 53. It is configured.

On the other hand, the gear 46 is positioned on the side of the gear shaft 450 and meshes with a gear 56 on a gear shaft 55 that is implanted in the frame 20. Directly below the gear shaft 55, a pair of left and right eccentric bearings 5 is provided.
7 is rotatably supported by the frame 20, and this eccentric bearing 57 is connected to the axis F2 of the outer circumferential circle 57a and the inner circumferential circle 57b.
The axial center F, is eccentric by an amount indicated by the symbol L1 in the figure. A sewing machine catch barrel 57 is rotatably supported on the inner circumferential circle 57b of the left and right eccentric bearings 57 via a rolling bearing 59, and the end shaft of the sewing machine catch barrel 58 is connected to the gear 56 and engages with the gear 56. A mating barrel gear 60 is pivotally mounted, and the sewing machine receiving barrel 58 is driven from the gear 56 side and rotates in the direction shown by the arrow in the figure. That is, the sewing machine receiving barrel 58 is not directly connected to the sewing machine barrel 42 which is driven from the driving side, but is driven from the driven gear 46 side of the sewing machine barrel 42 . The horizontal perforation line of action, which is a line connecting the axis F of the sewing machine receiving barrel 58 driven in this way and the axis F of the sewing machine barrel 42, is set to be horizontal, Horizontal perforations are performed using these temperatures of 42.58. That is, a sewing machine blade groove 42a having a rectangular cross section and extending in the ridge direction is formed in the outer circumferential portion of the sewing machine barrel 42, and a sewing machine blade case generally designated by the reference numeral 61 is housed in the sewing machine blade groove 42a. This sewing machine blade case 61 is attached to the sewing machine blade groove 4 by bolts 63 at both ends via long plate-shaped shims 62.
A long sewing machine blade stand 64 fixed to the bottom of the sewing machine 2a, and a paper presser 6 having the same length as the sewing machine blade stand 64 and fitted with a dovetail groove.
5, which is screwed onto the sewing machine blade stand 64, and the paper presser 6.
5 from both sides, and a long plate-shaped sewing machine blade 68 that is engaged with the sewing machine blade groove 42a of the sewing machine blade stand 64 and paper presser 65 and fixed with a plurality of bolts 67.
The sharp end of the sewing machine blade 68 protrudes from the paper presser foot 65. Reference numeral 69 is an adjustment screw screwed into a threaded hole on the bottom surface of the sewing machine blade stand 64 so as to be freely adjustable forward and backward.

On the other hand, a sewing machine blade receiving groove 58a having a rectangular cross section and extending in the ridge direction is formed in the outer peripheral part of the sewing machine receiving barrel 58. Inside this sewing machine blade receiving groove 58a, a bolt 70 is divided in the width direction. An integrated long sewing machine blade holder 71 is housed and fixed to the bottom surface of the sewing machine blade holder 58a with bolts 72. The outer end surface of the sewing machine blade receiver 71 is provided with a groove 71a into which the sharp end of the sewing machine blade 68 is inserted. With this configuration, when the web I passes between the two warmers 42 and 58 and the sewing machine blade case 61 and the sewing machine blade receiver 71 face each other, the sewing machine blade 68 is engaged in the groove 71a, and the web I is inserted into the groove 71a. A perforation is made at the planned origami location in 1.

The horizontal perforation processing device configured as described above is provided with an inter-axis distance adjusting device that moves the sewing machine barrel 42 and the sewing machine receiving barrel 58 at the same time to adjust the distance between the axes of these two warmers 42 and 58. ing. That is, a bracket 74 is fixed to the outside of one frame 20 in close proximity to the sewing machine barrel 42, and a shaft hole 75 is rotatably supported in a shaft hole formed in the other frame 20. , a handle 76 is fixed to the end projecting from the frame 20. On the other hand, a stud holder 77 formed in an arc shape is fixed to the outer periphery of the left and right eccentric bearings 41 with a plurality of bolts 78, and in the center of the stand holder 77,
A stud 79 is fitted with its square head protruding. Further, a stud holder 80 formed in an arc shape is fixed to the outer periphery of the left and right eccentric bearings 57 with a plurality of bolts 81.
A stud 82 is fitted with its square head protruding. 8
3 is located between both studs 79.82 and frame 2
A screw shaft 84 is rotatably supported on the bearing 83, and a left-hand thread 84a of the screw shaft 84 is screwed into a threaded hole in the stand 79 so as to be freely retractable. has been done. In addition, the right-hand thread 84b of the screw shaft 84 is connected to the stud 8.
A bevel gear 85 is screwed into the threaded hole of No. 2 so as to be movable forward and backward, and is also rotatably attached to one end of the screw shaft 84. A bevel gear 85 is engaged with a bevel gear 86 on the operating shaft 75. With this configuration, when the handle 76 is gripped and the operating shaft 75 is rotated, and both screw shafts 84 are rotated through the engagement of the bevel gears 85 and 86, the left screw 84a and the right screw Due to the screw action with the screw 84b, the stud holder 77 and the stand holder 80 are moved circumferentially in opposite directions via the stuff door 9.82. As a result, the eccentric bearing 41.57 rotates at the fitting portion of the outer circumference circles 41a and 57a,
Due to eccentric action, the axes F+, F of the inner circumferential circles 41b, 57b
Since i rotates around the axes F and FZ of the outer circumferential circles 41a and 57a, the sewing machine blade case 61 and the sewing machine blade holder 71 move in opposite directions, and the paper presser 65 and the sewing machine blade holder 71
The structure is such that the gap between the two is adjusted. and,
In this device, a line connecting the center of the driving gear 30 of the sewing machine barrel 42 and the center of the driven gear 46, and a line connecting the barrel gear 60 of the sewing machine receiving barrel 58 and the gear 56 above it are The positions of the gears 30, 46, and 60.56 are set so that they are perpendicular to the line connecting the centers of the gears 42 and 58, and the axes F and F are different from each other. The axis Fl, F is centered on the state shown in Figure 1 located directly below.
3 is set to move left and right. Reference numeral 85b denotes a stopper fixed to the frame 20 side and regulating both ends of movement of the stud holder 77, 80.

Next, the phase adjustment device 25 will be explained.

The phase adjustment shaft 26 is rotatably supported by a key 87 on both sides of the frame 20 so as to be movable in the axial direction. a screw shaft 90 with a handle 89 pivoted on the
is screwed in with restricted movement in the axial direction. With this configuration, when the handle 89 is gripped and the screw shaft 90 is rotated, the phase adjustment shaft 26 moves forward and backward in the axial direction due to the screw action, and the gear 30 is moved forward and backward due to the action of the helical teeth of the gear 28. Since the gear 44 rotates slightly through , the sewing machine barrel 42 rotates slightly, and the phase of the sewing machine barrel 42 relative to the stationary folding drum 21 is adjusted. 91 is a lock handle that fixes the screw shaft 90 after rotation. Further, the gear 24 on the shaft 23 is formed to be movable in the axial direction, and by moving the gear 24, the wrap adjustment for one parallel fold can be performed.

The operation of the horizontal perforation processing device configured as above will be explained. The web l conveyed after printing is sent out by the upper nipping roller 47 and guided between the sewing machine cylinder 42 and the sewing machine receiver cylinder 58, and after passing between them, the web l is transferred to the folding WA 21 and the cutting cylinder by the lower nipping roller 31. It is led between the two and folded. The web 1 passing between the sewing machine barrel 42 and the sewing machine receiving barrel 58 has both 11
Since horizontal perforations are made at the same distance as the leader of 1442.58, that is, at the place where the origami is planned to be next, if you fold from this perforation on the folding cylinder 21, it will be folded easily and with good folding accuracy. is obtained.

When it is necessary to adjust the gap between the paper presser foot 65 and the sewing machine blade holder 71 due to changes in the thickness of the web l or the cutting edge of the sewing machine blade 68 is worn, grasp the handle 76 and rotate the operating shaft 75. When both screw shafts 84 are rotated synchronously through the engagement of the left gears 85 and 86, the left screw 84
Due to the action of a and the right-hand screw 84b, the studs 79, 82 and stud holders 77, 80 of the sewing machine barrel 42 and the sewing machine receiving barrel 58 move in mutually opposite circumferential directions.

As a result, the eccentric bearing 41.57 has an outer circumference 41a.

Rotates at the fitting part 57a, and due to eccentric action, the inner circumferential circle 41b,
Since the sewing machine barrel 42 and the sewing machine catch barrel 58 rotate in opposite directions so that the axes F, F3 of the outer circumferential circles 41a, 57a rotate around the axes F, Fz of the outer circumferential circles 41a, 57a, the sewing machine blade The case 61 and the sewing machine blade holder 71 move, and the paper presser foot 6
5 and the sewing machine blade holder 71 is adjusted.

In this case, in this device, an eccentric direction line connecting the shaft center F and the shaft center F, and an eccentric direction line connecting the shaft center F and the shaft center pt are horizontal lines connecting the shaft centers of both the shells 42 and 5B. What is the perforation line of action? Since they are provided in orthogonal directions, when adjusting from the state of FIG. 4(a) to the state of FIG. 4(b),
The change in the center-to-body distance due to eccentricity effectively acts as an adjustment layer for the amount of biting of the sewing machine blade 68, which is indicated by ΔX. Further, since the sewing machine barrel 42 and the sewing machine receiver barrel 58 simultaneously move in opposite directions, the difference in rotational phase that occurs in the driven gear due to the movement of ΔX is canceled out, and the rotational phase difference of the sewing machine blade receiver 71 is canceled out. M
The sewing machine blade 68 will not come off from 71a.

Further, the driving side gear 3 meshing with the body gear 44 of the sewing machine body 42
0 and the driven side gear 46 and the sewing machine receiving barrel 58
Since the line connecting the body gear 60 and the drive side gear 56 is set in a direction perpendicular to ΔX, the fourth
Change Δa in the center distance a between the body gear 44 and the driving gear 30 caused by eccentricity and adjustment angle indicated by symbols t and φ in the figure
can be kept to a minimum. Similarly, body gear 4
4 and the driven side gear 46, and the sewing machine receiving barrel 5.
Changes in the center distance between the body gear 60 and its driving side gear 56 can also be suppressed to a minimum. Furthermore, the sewing machine barrel 42
and the sewing machine receiver barrel 58 are not directly gear-coupled, and the sewing machine receiver barrel 58 is rotationally driven from the gear 56 side, which is disposed in the same direction as the eccentric direction, so that there is no direct gear connection between the barrel centers. Changes in distance are not directly affected by changes in gear center distance.

In FIG. 4, in order to adjust the biting amount of the sewing machine blade 68, when the sewing machine 11442 is displaced by the amount indicated by φ in the figure, there is , an angular change indicated by the symbol θ in the figure occurs, which causes a shift in the rotational phase of the sewing machine blade 68, indicated by the symbol φ in the figure. However, in this device, the sewing machine receiver ryi 45B is configured so that the same change ν occurs in the opposite direction at the same time due to the above-described device, so the same phase shift ψ also occurs in the sewing machine receiver barrel 58.
1M7 of the sewing machine blade holder 71 due to the phase shift ψ.
The sewing machine blade 68 does not come off from 1a.

Furthermore, this embodiment employs an involute gear, so that correct meshing can be ensured even if the center distance of the gears is changed. When the normal center distance ft1Ja changes, the pressure angle α changes and the backlash C also changes. If the center distance increases by Δa, the pressure angle α changes and the bankranche C also changes. In this embodiment, as described above, a and the ΔX direction are set to be perpendicular to each other, so that the change layer ΔC of the bank lash of the gear can be suppressed to a minimum with respect to the required ΔX. Strike the rotation end of 7.
Since the backlash is regulated by the pad 85b, the predetermined backlash range will not be exceeded.

Furthermore, the paper presser foot 65 of the sewing machine blade case 61 is made of a soft elastic material and is expandable and retractable in the radial direction of the sewing machine 1F142. Even if there is a change in the entire sewing machine blade case 61 including the sewing machine blade case 61, the change is sufficiently absorbed as a change in the paper presser foot 65, and the amount is not large enough to affect the quality of printed matter.

FIG. 6 is a side view of a gear train corresponding to FIG. 3 and showing another embodiment of the present invention seen from the same side as FIG. 1; 56 is eliminated, and a gear 56A coaxial with the gear 39 and a gear 56B meshing with the gear 56A and the gear 60 are provided in its place, so that the sewing machine receiver cylinder 5 is driven from the driving side with respect to the sewing machine cylinder 42. did. A line connecting the center of the gear 60 and the center of the gear 56B was provided so as to be perpendicular to the line of action of the horizontal perforation. With this configuration, the operation and effect are the same as those of the previous embodiment.

7 to 9 show other embodiments of the present invention, and FIG.
The figure is a side view of the horizontal perforation processing device shown corresponding to Fig. 1, and Fig. 8 is a partially broken developed front view shown corresponding to Fig. 2.
FIG. 9 is a side view of the gear train shown in a state seen from the same side as FIG. 1, corresponding to FIG. 3, for explaining the meshing of the gears. In the drawings, members having the same configuration as those of the embodiment shown in FIGS. 1 to 3 are given the same reference numerals, and their explanations will be omitted.

In this embodiment, an operating shaft 100 corresponding to the operating shaft 75 in the previous embodiment is located diagonally below the sewing machine barrel 42 and is pivotally supported by the left and right frames 20, and a handle 76 is attached to this. There is.

Also, on the working shaft 100, a pair of pale gears 10 are provided.
1 is pivoted close to each left and right frame 20,
Each lug gear lot meshes with a lug gear 103 on a worm shaft 102 mounted on the frame 20 in r-row. On the other hand, the body gear 44 of the sewing machine body gear 42, which was driven in mesh with the gear 30 in the above embodiment, is replaced by the gear 30.
Gear 10 is separated from 0 and sequentially meshes with gear 30.
It is rotationally driven from the drive side gear 46 via the 4° 05. Further, the barrel gear 60 on the side of the sewing machine receiving barrel 58 is rotationally driven from the gear 56 side on the driving side that meshes with the gear 46. A line connecting the centers of gears 46 and 44 and gear 56.
As in the previous embodiment, the lines connecting the centers of 60 are perpendicular to the horizontal perforation line. The gear shafts 45 and 55 are provided with a total of four gear shafts, two on the left and right.
are fixed to the frame 20, and each of these gear shafts 4
At 5°55, there are levers 107, 10 formed in a fan shape.
8 is located inside the frame 20 and is swingably supported, and the sewing machine barrel 42 and the sewing machine receiving barrel 58 are rotatably supported via bearings at the free ends of these levers 107 and 108. has been done. In addition, a segment-shaped worm foil 109,110 is attached to the free end of each lever 107,108.
are provided, and these worm foils 109.1
10 meshes with a right-handed twist worm tit and a left-handed twist 112 integrally formed on the worm shaft 102.

Reference numeral 113 is a stopper that restricts the rotation limit of the levers 107 and 108.

With this configuration, when the thickness of the web 1 changes or the cutting edge of the sewing machine blade 6B wears out, and it is necessary to adjust the gap between the paper presser foot 65 and the sewing machine blade holder 71, When the handle 76 is gripped and the operation shaft 100 is rotated, and the worm shaft 102 is rotated through the meshing of the pale gears 101 and 103, the right-handed worm 111 is rotated.
．． The lever 1071 is activated by the engagement of the left-handed twist worm 112.
0B swings to adjust the distance between the shafts of the sewing machine barrel 42 and the sewing machine receiving barrel 58. As a result, the sewing machine blade case 61 and the sewing machine blade holder 71 move, and the paper presser foot 65 and the sewing machine blade holder 7 move.
1 is adjusted.

In this case, a line connecting the centers of gears 46 and 44 and gear 5
6. Since the line connecting the centers of 60 and 60 is symmetrical with respect to the running line of the web 1, the circle between the sewing machine blade case 61 and the sewing machine blade holder 71 is maintained even if the two temperatures 42 and 5B move. It is the same as in the previous embodiment that the phase in the circumferential direction does not shift. Of course, it is not necessary to remove the sewing machine blade case 61 to adjust the distance between the axes. Also lever 1.0
Since the 7.10th gear rotates around the gear shaft 45.55, there is no problem in meshing the gears 46, 44, 56, 60, 105, etc.

1O to 12 further show other embodiments of the present invention, in which FIG. 1O is a side view of the horizontal perforation processing device shown corresponding to FIG. 7, and FIG. FIG. 12 is a side view of the gear train seen from the same side as FIG. 7, corresponding to FIG. 9, in order to explain the meshing of the gears. In the drawings, members having the same configuration as those in the embodiment shown in FIGS.
The worm shaft 102, which is drive-coupled via gears 101 and 103, is half the length of the worm shaft 102 of the above embodiment.
．． Lever 1 drive-coupled with worm wheel 109
07 is provided only on the sewing machine barrel 42 side. Also,
The barrel gear 44 of the sewing machine barrel 42 meshes with the drive-side gear 30 and the driven-side gear 46, and also meshes with the barrel gear 60 of the sewing machine receiving barrel 58. Both ends of the sewing machine barrel 42 are supported by levers 107 via bearings, and one end of the sewing machine barrel 42 is fixed to a gear 44 via an eccentric shaft coupling 114, which is generally called a Schmidt coupling. connected to a shaft. In this eccentric shaft coupling 114 called a Schmidt coupling, a support part on the side of the sewing machine barrel 42 and a support part on the shaft side to which the gear 44 is fixed are formed to be eccentric. The rotational phase of the barrel 42 is configured not to change with respect to the gear 44.

With this configuration, if the thickness of the web l changes or the cutting edge of the sewing machine blade 68 wears out, and it is necessary to adjust the gap between the paper presser foot 65 and the sewing machine blade holder 71, When the handle 76 is gripped and the operating shaft 100 is rotated, and the worm shaft 102 is rotated through the engagement of the bell gears 101 and 103, the lever 107 swings due to the engagement between the ohm 111 and the worm wheel 109. death,
As a result of adjusting the distance between the shafts of the sewing machine barrel 42 and the sewing machine receiver barrel 58, the sewing machine blade case 61 and the sewing machine blade receiver 71 move, and the gap between the paper presser foot 65 and the sewing machine blade receiver 71 is adjusted. . In this case, only the eccentric shaft joint 114 is eccentric, and no rotational phase shift occurs between the sewing machine barrel 42 and the gear 44, and the sewing machine barrel 42 and the sewing machine receiving barrel 58
There is no rotational phase shift between the two. Therefore, the deviation between the sewing machine blade case 61 and the sewing machine blade receiver 71 is only due to the eccentric action and is extremely small, so there is no need to take the trouble to adjust the phase of the sewing machine receiver barrel 58.

Of course, it is not necessary to remove the sewing machine blade case 61 to adjust the distance between the axes. Also, since the lever 107 rotates around the gear shaft 45, the gears 46, 44,
60. There is no problem with the meshing of the parts.

In this embodiment, by connecting the body gear 44 and the sewing machine body 42 using the eccentric shaft joint 114, the number of gears can be reduced and the structure can be simplified. Furthermore, if a Schmidt coupling is used as the eccentric shaft joint, the angular velocity will not change even if the shaft is eccentric, and it can withstand high speed and high torque.

FIG. 13 is a gear arrangement diagram as another embodiment of the present invention. In this embodiment, a tensioner 115,
The number of gears is further reduced due to the driving connection with a non-slip timing belt 117 tensioned by 116.

FIG. 14 is a longitudinal sectional view of a horizontal perforation processing device shown for explaining the invention according to claim 2. In the drawings, members having the same configuration as those of the invention according to claim 1 shown in FIG. Note that the gear arrangement is the same as the gear arrangement of the invention according to claim 1 shown in FIG. 3, and therefore will be explained using the same figure. The purpose of the present invention is to eliminate the phase shift of the horizontal perforation when adjusting the distance between the shafts, which occurred slightly in the above invention. This will be explained using an array diagram.

In the figure Z... Z2... θ1... ・Number of teeth of driving side gear 30 ・Number of teeth of sewing machine body gear 44 ・By moving the sewing machine barrel, angle caused by φ　・・・Phase shift of horizontal perforation Then Z.

φ=θ+(i+−-) ... Expressed by (1), further X...Movement amount of the sewing machine barrel m7...Gear angle modière β. ...If the torsion angle is = mn Z ” Ztanθ12 cos
β, and in the range where θ is sufficiently small, tanθ, −θ
, (radl, so... (2) When this equation is substituted into equation (1) and θ1 is eliminated, the phase shift φ is finally expressed by the following equation.

φ-” part 1' x=C, x (rad)...(
4) m, Z.

Here, C1=" is ECO h-szz. That is, it can be seen that the shift φ of the horizontal perforation phase caused by the amount of movement X of the sewing machine barrel is proportional to the amount of movement X of the cylinder.

Therefore, the configuration of the present invention will be explained based on FIG. 14.
The phase adjustment shaft 26 is divided into two parts in the axial direction from the center,
A right-hand thread and a left-hand thread are cut in the divided portion, and the right-hand thread and the left-hand thread are screwed into threaded holes of the wide gear 120, respectively. 122 is formed integrally with one of the divided phase adjustment shafts 26 and is connected to the hole 26a of the other phase adjustment shaft 26.
This is a guide bin that is slidably fitted into the guide bin. Further, a gear 123 that meshes with the gear 120 is rotatably attached to the operating shaft 75 . Reference numeral 74 denotes a bracket that slidably supports the shaft end of the operating shaft 75. By doing this, the operation axis 7
5 is rotated, the phase adjustment shaft 26 whose rotation is restricted by the key 87 is configured to move in the axial direction due to the meshing of the gears 129 and 123. The other configurations are the same as those of the invention according to claim 1, so the explanation thereof will be omitted.

With the above configuration, the J
If the gap between the paper presser foot 65, the sewing machine blade, and the receiver 71 needs to be adjusted due to a change in gamma or the cutting edge of the sewing machine blade 68 is worn, hold the handle 76 and turn the operating shaft 75. When the screw shafts 84 are rotated synchronously through the engagement of the bell gears 85 and 86, the sewing machine barrel 42 and the sewing machine catch barrel 5 are rotated by the action of the left screw 84a and the right screw 84b.
8 with each stud 79.82 and stud holder 77
．． 80 move in opposite directions with respect to the circumferential direction. As a result, the eccentric action causes the sewing machine barrel 42 and the sewing machine catch barrel 58 to
The sewing machine blade case 61 rotates in opposite directions.
and the sewing machine blade holder 71 move, and the gap between the paper presser 65 and the sewing machine blade holder 71 is adjusted.

In this case, in this device, when the operation shaft 75 rotates, the phase adjustment shaft 26 whose rotation is restricted by the key 87 moves in the axial direction due to the meshing of the gears 120 and 123, and the gear 28
Since the gear 44 slightly rotates via the gear 30 due to the action of the helical teeth, the sewing machine cavity 42 rotates slightly, and the sewing machine
The phase of is adjusted.

The amount of axial displacement of the phase adjustment shaft 26 in such inter-axle distance adjustment and phase adjustment is defined as y, and the gear 24.27.28
．． The number of teeth of 44 is Z g4+ Z Z? , Z z+
When +Z is 44, the phase adjustment amount Φ of the sewing machine movement given by y is expressed by the following equation. However, in the formula 1, m, ・
...Normal module m of gear 24.27, ...Normal module β of gear 28.44, ...Gear 24.
27 torsion angle β. ... Torsion angle Cz of gear 28.44 = 2/ Z44X (Z211S i nβi/
ZZ? 'mH + sinβo/m++) = const 1C2・y Crad] ・ ・ ・ ・ ・
(5). That is, the phase can be changed in proportion to the amount of displacement y.

As is clear from equations (4) and (5), the sewing machine body is x(
m) When moved, the phase adjustment shaft 26 is moved to y-(C+
/Cz )

Note that when the handle 89 is rotated to adjust only the phase of the horizontal perforation, the phase adjustment shaft 26 divided into two
can simultaneously move in the axial direction via gear 120 to change the phase.

In this case, since the gear 120 moves only in the axial direction, it does not have any effect on the gear 123.

〔Effect of the invention〕

As is clear from the above description, according to the present invention, the sewing machine blade extending in the ridgeline direction of the sewing machine cylinder of a rotary printing press and the sewing machine blade receiver extending in the ridgeline direction of the sewing machine receiver cylinder are made to face each other by rotation at both temperatures, In the horizontal perforation processing device of a rotary printing press that uses a perforation blade to create horizontal perforations in the web running between two temperatures, an interaxial distance adjustment device is installed to adjust the interaxial distance between the sewing machine cylinder and the sewing machine receiving cylinder. As a result, when adjusting the movement of the sewing machine blade case when changing paper thickness, etc., it is no longer necessary to remove the sewing machine blade case and adjust it, such as replacing shims as in the past. Since fine adjustments can be made quickly during operation while observing the folding operation, the ease of use is improved, machine stoppage time can be significantly shortened, and the amount of paper waste generated is reduced. Also,
When moving to prints that do not require perforations, there is no need to remove the perforation blade case as in the past, and this can be done by keeping the perforation blade case attached and moving it away from the running paper. Great effect. Furthermore, it is effective because the amount of movement of the barrel directly corresponds to the amount of adjustment of the amount of biting of the sewing machine blade.

Furthermore, in the horizontal perforation processing device of such a rotary printing press, a phase adjustment device is provided which rotates the sewing machine cylinder by moving the phase adjustment shaft in the axial direction and adjusts the phase of the sewing machine cylinder in the circumferential direction. In addition, the operation axis and the phase adjustment axis of the axis distance adjustment device are configured to move in conjunction with each other, so that the sewing machine can be adjusted in conjunction with the operation of adjusting the axis distance between the sewing machine barrel and the sewing machine receiving barrel. It is possible to adjust the phase of the machining area so that it does not shift. 'l!
Preparation time is shortened, productivity is improved, labor is reduced, and the amount of waste paper is reduced.

[Brief explanation of the drawing]

1 to 14 show an embodiment of a horizontal perforation processing device for a rotary printing press according to the present invention, and FIG. 1 is a side view thereof;
Fig. 2 is a partially cut-away developed plan view, Fig. 3 is a side view of the gear train seen from the same side as Fig. 1 to explain gear engagement, and Fig. 4 is a view of the sewing machine barrel. A side view of the sewing machine barrel and the drive side gear shown to explain changes in gear engagement due to movement, etc., FIG. 5 is an enlarged cross-sectional view of the sewing machine blade case and the sewing machine blade holder, and FIG. 6 is a diagram showing other aspects of the invention. The first example is
7 to 9 show other embodiments of the present invention, FIG. 7 is a side view of the horizontal perforation device, and FIG. FIG. 9 is a side view of the gear train seen from the same side as FIG. 1 in order to explain gear meshing, and FIGS. 10 to 12 are further illustrations of the present invention. 10 is a side view of the horizontal perforation processing device, FIG. 11 is a partially cutaway front view, and FIG.
FIG. 13 is a side view of the gear train seen from the same side as the figure, and FIG. 14 is a gear arrangement diagram as another embodiment of the present invention.
The figure is a longitudinal sectional view of a horizontal perforation processing device shown for explaining the invention according to claim 2, and FIG. 15 is a gear arrangement diagram,
FIG. 16 is a schematic side view of a conventional horizontal perforation device for a rotary printing press. 25... Phase adjustment device, 26... Phase adjustment axis,
30... Drive side gear, 41.57... Eccentric bearing, 42... Sewing machine barrel 1.44... Body gear, 46
... Driven side gear, 56 ... Gear, 58 ...
Sewing machine catch barrel, 60...Body gear, 68...Sewing machine blade, 71...Sewing machine blade receiver, 75...Operation shaft, 100
... is the operating shaft, 101,103...a, 104,105...gear, 8...lever 109,110 -mwheel, 111,112...114...eccentric shaft coupling , 117 Mingbelt, 120, 123, ... Bezarugi 107.10 ... War Warm, ... Tai ... Gear.

Claims (2)

[Claims] (1) A sewing machine blade extending in the ridgeline direction of the sewing machine barrel and a sewing machine blade holder extending in the ridgeline direction of the sewing machine catch barrel are made to face each other by rotation of these two barrels, and the sewing machine blade is applied to the web running between the two barrels. A horizontal perforation processing device for a rotary printing press that creates horizontal perforations, characterized in that the horizontal perforation processing device for a rotary printing press is provided with an interaxial distance adjusting device for adjusting an interaxial distance between the perforation cylinder and the sewing machine receiving cylinder. Eye processing equipment. (2) In the horizontal perforation processing device for a rotary printing press according to claim 1, the phase adjustment is performed by rotating the perforation cylinder by moving the phase adjustment shaft in the axial direction and adjusting the phase of the perforation cylinder in the circumferential direction. What is claimed is: 1. A horizontal perforation processing device for a rotary printing press, characterized in that a device is provided, and the operating shaft of the inter-axis distance adjusting device and the phase adjusting shaft are moved in conjunction with each other.