JPH0768734A - Sheet-feed rotary press with reversing mechanism - Google Patents

Abstract

PURPOSE:To obtain a sheet-feed rotary press with a reversing mechanism in which a sheet holding force of a sheet end holding member is not reduced at the time of double-side printing by providing a rotating unit for rotating the member and a moving unit for so moving as to expose and submerge it at a periphery of a sheet conveying cylinder. CONSTITUTION:In order to avoid interference of a reversing pawl 100 with an impression cylinder 63 at the time of double-side printing, the pawl 100 is submerged in a periphery of a reversing cylinder 65. That is, when the pawl 100 is moved to a position before a line for connecting a center of the cylinder 63 to that of the cylinder 65, a cam follower 72 is moved from a large-diameter part to a small-diameter part of a pawl base moving cam against spring forces of a compression coiled spring and a torsion bar, and hence a pawl base bar of the pawl 100 is rotated, and a pawl base is moved to a retracted position. Subsequently to the movement, the follower is moved from a surface of a pawl switching cam to a large-diameter part of a pawl moving cam against a twisting spring force of the torsion bar, and hence the pawl is moved due to rocking of a pawl holder of the pawl 100. Accordingly, the pawl 100 is submerged from the periphery of the cylinder 65 to eliminate interference with the periphery of the cylinder 63.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention comprises an upstream cylinder in the paper transport direction, a downstream cylinder, and a paper transport cylinder disposed between the cylinders with their peripheral surfaces facing each other. The present invention relates to a sheet-fed rotary printing press with a reversing mechanism that enables double-sided printing by reversing the paper inside out when the paper is gripped between these cylinders and conveyed.

[0002]

2. Description of the Related Art Along with the diversification of printing, various sheet-fed rotary printing presses with a reversing mechanism that enable single-sided printing and double-sided printing with one machine have been proposed and put into practical use. A sheet with a reversing mechanism provided with a double-sided pressure cylinder on the upstream side with respect to the paper transport direction, a double-sided pressure cylinder on the downstream side, and a reversing cylinder as a double-diameter paper transport cylinder arranged between both cylinders. Since a rotary printing press is disclosed in US Pat. No. 4,343,241,
This will be described below.

FIG. 18 is a cylinder arrangement diagram of a sheet-fed rotary printing press with a reversing mechanism disclosed in this publication, and FIG. 19 is a state in which the cylinder is slightly rotated from the state of FIG. FIG. 3 is an enlarged side view of the vicinity of the counter contact of FIG. In these drawings, a plate cylinder 3 on which a printing plate is mounted and a blanket cylinder 4 around which a blanket is wound are provided in adjacent printing units, for example, a first printing unit 1 and a second printing unit 2. The blanket cylinders 4 of the printing unit 1 are provided so as to be in contact with each other, and an impression cylinder 5 having a double diameter, which is an upstream cylinder in the paper transport direction, is provided in contact with each other.

Further, the blanket cylinder 4 of the printing unit 2 is provided with a double-diameter impression cylinder 6, which is a cylinder on the downstream side with respect to the paper conveying direction, in contact with the blanket cylinder 4, and between the impression cylinders 5 and 6. Is provided with a double diameter reversing cylinder 7 in contact with both impression cylinders 5, 6.

A plurality of sets of gripper devices 8 composed of a claw and a claw base are provided at a position where the outer peripheral portion of the impression cylinder 5 is divided into two in the circumferential direction.
(Hereinafter, such a gripper device is simply referred to as a nail)
A plurality of sets of claws 9 are arranged in parallel in the axial direction of the impression cylinder 6 at locations where the outer circumference of the impression cylinder 6 is divided into two equal parts in the circumferential direction. Is provided.

Further, the outer peripheral portion of the reversing cylinder 7 is circumferentially separated by 2
Reversing claws 10 are provided in parallel in the axial direction of the reversing cylinder 7 at the equally divided positions.
The positions are set so as to correspond to the claws 8 and 9 by the rotation of 6 and 7. Further, a plurality of suction ports 11 connected to a suction air source such as a pump (not shown) are provided in the vicinity of each reversing claw 10 at a position where the outer peripheral portion of the reversing body 7 is divided into two in the circumferential direction. ing.

With this configuration, in the case of single-sided printing, when the cylinders 5, 6, 7 and the like rotate, the paper 12 held by the claws 8 is conveyed to the blanket cylinder 4 and the impression cylinder. The first color is printed when passing between the paper 1 and
The claw 2 is gripped by the claw 8 and is conveyed while being wound around the lower peripheral surface of the reversing cylinder 7. Wrapped paper 1
The second gripper 2 is gripped by the gripper 10 and conveyed, and when passing between the blanket cylinder 4 and the impression cylinder 6, the second surface is printed with the second color.

When such single-sided printing is switched to double-sided printing, the upstream cylinder group including the impression cylinder 5 in the upstream side cylinder group so that the trailing edge of the paper 12 held by the nail 8 corresponds to the suction port 11. After adjusting the phase, printing is resumed and each cylinder 5,
When 6, 7, etc. are rotated, the paper 12 that is gripped by the claws 8 and conveyed is printed on the surface as it passes between the blanket cylinder 4 and the impression cylinder 5, and the paper 12 is gripped. Claws 10
It passes through the counter contacts of both cylinders 5 and 7 without being gripped, and is wound around the lower peripheral surface of the impression cylinder 5.

When the trailing edge of the wound paper 12 reaches the counter contact points of both cylinders 5, 7, the trailing edge of the paper is sucked by the suction port 11 and conveyed, and the gripping end is released from the grip of the nail 8 during the transportation. To be done. The paper 12 sucked by the suction port 11 is gripped by the reversing claw 10 and conveyed, so that the paper 12 is reversed and turned inside out, and the paper 12 is gripped by the claw 9 and conveyed by the impression cylinder 6. A blanket cylinder 4 is attached to the paper 12 to be conveyed.
When passing between the pressure roller and the impression cylinder 6, printing is performed on the back surface to obtain double-sided printing.

[0010]

However, in such a conventional sheet-fed rotary printing press with a reversing mechanism, as shown in FIG.
As shown in FIG. 8, when the paper ends of the paper 12 reach the counter contact points of the cylinders 5, 7 and are sucked by the suction port 11 and the cylinders 5, 7 continue to rotate, the state shown in FIG. At this time, when the suction port 11 circulates in a state where the gripping side of the paper 12 by the claw 8 is in close contact with the peripheral surface of the impression cylinder 5, the holding force of the paper 12 by the suction port 11 is weakened by the tension of the paper 12 and the paper 12 is absorbed on the suction surface. There is a problem that slippage and subsequent gripping of the grip result in inaccurate gripping, and paper is scraped off or paper is peeled off from the suction surface to cause paper drop.

The present invention has been made in view of the above points, and provides a sheet-fed rotary printing press with a reversing mechanism that can prevent the paper holding force of the paper edge holding member from decreasing during double-sided printing. It is intended to be provided.

[0012]

In order to achieve such an object, according to the present invention, the cylinders on the upstream side and the cylinder on the downstream side in the paper transport direction are made to have their circumferential surfaces abutted against each other. And a reversing mechanism that passes over the counter contact points between the paper transporting cylinder and the upstream side cylinder and reverses the paper attached to the upstream side cylinder and transfers it to the downstream side cylinder. In a sheet-fed rotary printing press with a reversing mechanism, a paper tail holding member that is provided in the reversing mechanism and holds the paper tail is rotatable on the paper transport cylinder and can be retracted from the peripheral surface of the paper transport cylinder. A rotating device for supporting and rotating the paper tail holding member and a moving device for moving the paper tail holding member so as to project and retract with respect to the peripheral surface of the paper transport cylinder are provided.

[0013]

In double-sided printing, when the paper tail of the paper wound around the upstream cylinder reaches the counter contact point between the paper transport cylinder and the upstream cylinder, the paper tail is used as a paper tail holding member, for example. When the mouthpiece sucks and holds, and the paper transport cylinder continues to rotate, the mouthpiece that holds the paper tail of the paper released from the holding of the paper holding member of the upstream cylinder orbits, and the paper is turned upside down. It

At the time of this reversal, the suction port orbits while rotating by the rotating device, and the paper suction surface of the suction port and the paper to be peeled off from the peripheral surface of the paper transport cylinder are substantially in line with each other. The paper will not be peeled off and the paper will not slip on the suction surface.

When the paper transport cylinder continues to rotate, the suction port that holds the paper tail of the inverted paper circulates along the peripheral surface of the paper transport drum, and in the middle of the circulation, from the suction port to, for example, a nail as a paper holding device. The gripper is replaced, but at this time, the suction port is moved in the radial direction of the cylinder by the moving device and circulates on the outer side of the peripheral surface of the cylinder, so that the gripping with the paper holding device is reliably performed together with the rotation of the suction port.

The paper that has been gripped by the paper holding device is printed on the back surface of the paper while being gripped by the paper holding member of the downstream cylinder at the counter contact point between the paper carrying cylinder and the downstream cylinder and carried by the paper holding member. Is applied. On the other hand, the used suction port continues to circulate along the peripheral surface of the paper transport cylinder toward the contact point between the upstream cylinder and the paper transport cylinder, but during this circulation, the rotation device and the moving device cooperate with each other. To get over the paper transport device and return to the original posture.

[0017]

1 to 17 show an embodiment of a sheet-fed rotary printing press with a reversing mechanism according to the present invention, and FIG. 1 is a partially cutaway front view of a left half portion of a reversing cylinder shown partially expanded. 2 is a partially cutaway front view of the right half of the reversing cylinder shown in a partially expanded state, FIG. 3 is a sectional view taken along line III-III of FIG. 2, FIG. 4 is a sectional view taken along line IV-IV of FIG. 2 is a sectional view taken along the line VV of FIG. 2, FIG. 6 is a partially cutaway front view of the left half of the reversing cylinder shown in a partially expanded state, and FIG. 7 is a part of the right half of the reversing cylinder shown in a partially expanded state. Broken front view, FIG. 8 is VIII of FIG.
FIG. 9 is a side view as seen from IX in FIG. 7, FIG. 10 is a plan view of the reversing cylinder, FIG. 11 is a sectional view taken along line XI-XI of FIG. 10, and FIG. 13 is a side view of the reversing cylinder shown for explanation, FIG. 13 is a cross-sectional view of the mouthpiece, FIG. 14 is a side view of the claw, the nail holder and the mouthpiece shown for explaining the gripping operation of the paper, and FIG. 15 is the mouthpiece and the reversing claw. FIG. 16 and FIG. 17 are perspective views of the stop cam, respectively, for explaining the operation of the above.

In the figures, on the left and right frames 61 and 62, there is provided a double-diameter first impression cylinder 63 which is an upstream side cylinder with respect to the direction of rotation of the cylinder indicated by an arrow in the figure, that is, the paper transport direction, and the downstream side. A double-diameter second impression cylinder 64, which is a cylinder, is rotatably supported on both end shafts, and the circumferential surface is contacted between these impression cylinders 63, 64. A double-diameter reversing cylinder 65 as a paper transporting cylinder is rotatably supported by a rolling bearing 66, and a notch 65a is provided on the outer peripheral portion of the reversing cylinder 65 over substantially the entire length of the cylinder. ing.

A drive shaft bracket 67 consisting of a fixed portion 67a and a rotating portion 67b pivotally attached to the fixed portion 67a is fixed to the bottom surface of the cutout 65a.
The bearer 68 is attached to the rotating portion 67b of the above and the bracket 69 fixed to the bearer 68 on one side that closes the notch 65a.
Both ends of the drive shaft 70 penetrating through are rotatably supported.

A roller-equipped lever 71 having a cam follower 72 pivotally attached to a free end thereof is fixed to one end of the drive shaft 70 at a base end thereof. The cam follower 72 of the roller-equipped lever 71 has a frame 62. The claw base moving cam 73, which is fixed to the gear 173 rotatably supported to the side and constitutes the claw base moving means, is brought into contact with the cam surface composed of the large diameter portion 73a and the small diameter portion 73b.

As shown in FIG. 2, the claw base moving cam 73 has a gear 174a meshing with the gear 173 at one end, and the pin 1 is rotatably supported by the frame 62.
When the hexagon head 174b provided at the other end of the 74 is rotated with a spanner,
It is configured to rotate together with the gear 173 via the gear 174a so as to be movable between predetermined positions for double-sided printing and single-sided printing.

A drive lever 74 is fixed to one end of the drive shaft 70 so as to be adjacent to the inside of the drive shaft bracket 69. One end of the drive lever 74 is pivotally attached to the free end of the drive lever 74. A connecting lever 76 is rotatably pivotally attached to the other end of the driven rod 75.

On the other hand, on the bottom surface of the notch 65a, a long stop bar 77 having a rectangular cross section and extending in the axial direction of the notch 65a is provided with a pawl 92 (to be described later) for a pawl base 81 (described later). The brackets 78 and 79 are fixed on the bottom surface of the notch 65a so as to be adjacent to the bearer 68.

Further, the left and right brackets 78, 79 are provided with a claw base bar 80 having a through hole extending in the axial direction.
Both end shafts are rotatably supported via rolling bearings, and a plurality of claw bases 81 as claw base members are attached to each claw 92 at one swing end of the claw base bar 80. Correspondingly installed in parallel.

Reference numeral 82 denotes a torsion bar inserted through the inner hole of the nail base bar 80.
As shown in FIG. 4, one end is formed by fitting one hexagonal head 82a into the hexagonal hole of the torsion bar holder 83 which is fixed to the one bracket 79 so as to be rotationally adjustable in the circumferential direction. Is fixed, and the other hexagonal head 82b of the torsion bar 82 is a rotatable claw base bar 80.
Is fitted in a hexagonal hole provided at the other end of the.

As a result, the claw base bar 80 is caused by the torsion spring force stored in the torsion bar 82 to cause the stop bar 77 to move.
By contacting the cam follower 72, the rotation limit in the direction in which the cam follower 72 is pressed against the cam surface of the claw base moving cam 73 is regulated.

Rotating portion 67b of the drive shaft bracket 67
A compression coil spring 84 that urges the cam follower 72 in the same direction as the urging direction of the torsion spring force of the torsion bar 82, that is, in the direction of pressing the cam follower 72 against the cam surface of the claw base moving cam 73, between the connection lever 76 and the connection lever 76. It is installed.

Further, a pair of left and right holders 85 consisting of a fixed portion 85a and a rotating portion 85b pivotally attached to the fixed portion 85a are fixed to the bottom surface of the cutout 65a.
A compression coil spring 86 for urging the cam follower 72 in a direction in which the cam follower 72 is pressed against the cam surface of the claw base moving cam 73 is interposed between b and the claw base bar 80.

With this arrangement, when the cam follower 72 on the reversing cylinder 65 side is pressed against the cam surface of the claw base moving cam 73 on the frame 62 side, the reversing cylinder 65 rotates and the cam follower 72 circulates. 14 and the spring force of the compression coil springs 84 and 86 and the torsion bar 82 cooperate to swing the claw base bar 80 at a predetermined timing, so that the claw base 81 moves as shown by the solid line in FIG. It is configured to move between an operating position in which the peripheral surface of 65 is flush with the front end surface and a retracted position in which the peripheral surface of the reversing cylinder 65 is tilted and retracted from the peripheral surface of the reversing cylinder 65 as shown by the chain line in FIG. ing.

Next, the claws that constitute the gripper device together with the claw base 81 and the moving device for the claws will be described. Bearings 87, 88 located diagonally below the nail base 81 and fitted in bearing holes of the left and right bearers 68, respectively, and a plurality of bearings fixed in parallel to the axial direction of the notch 65a on the bottom surface of the notch 65. A claw shaft 90 is rotatably supported by the bearing 89 of the C., and a plurality of claw holders 91 are fixed on the claw shaft 90 in parallel in the axial direction. The nail stand 8
The claws 92 serving as claw members for holding the paper between the first and the second sheets are fixed.

As shown in FIGS. 1, 2 and 9, the hexagonal hole of the torsion bar holder 93 fixed to one bearing 88 so as to be pivotally adjustable in the circumferential direction is provided with an inner hole of the pawl shaft 90. Hexagonal head 94a formed at one end of the penetrating torsion bar 94
The hexagonal head 94b formed at the other end of the torsion bar 94 is fitted in a hexagonal hole formed at one end of the pawl shaft 90.

As shown in FIGS. 8 and 14, a pawl opening / closing cam 95 as a pawl opening / closing device having a cam surface composed of a large diameter portion 95a and a small diameter portion 95b is fixed to one frame 61. On the cam surface of the claw opening / closing cam 95, the claw shaft 9
A cam follower 97 pivotally attached to the free end of the lever 96 with rollers fixed to the end of 0 is pressed against the widthwise half by the torsion spring force of the torsion bar 94.

As shown in FIGS. 1 and 14, the boss portion of the pawl opening / closing cam 95 has a large diameter portion 172a and a small diameter portion 172.
A pawl moving cam 172 as a pawl moving device having a cam surface composed of b is rotatably supported, and the pawl moving cam 172 is rotatably supported by a boss portion of the pawl opening / closing cam 95. The gear 175 is bolted to the gear 175.
It is configured to be able to rotate integrally with.

On the other hand, the frame 61 has a hexagonal head 1 at one end.
A pin 176 formed with 76b is rotatably supported, and a gear 176a meshing with the gear 175 is fixed to the other end of the pin 176.

Further, the pawl moving cam 172 has a large diameter portion 1
The diameter 72a is formed to be larger than the large diameter portion 95a of the pawl opening / closing cam 95, and the small diameter portion 172b is formed to be smaller than the small diameter portion 95b of the pawl opening / closing cam 95. The cam follower 97 on the side of the lever 96 with rollers is pressed against the cam surface of the large diameter portion 172a of the claw moving cam 172 by the torsion spring force of the torsion bar 94 in the remaining half portion in the width direction.

As a result, when the reversing cylinder 65 rotates, the cam follower 97 causes the small diameter portion 1 of the claw moving cam 172 to move.
While corresponding to 72b, the cam follower 97 circulates while being pressed against the cam surface of the claw opening / closing cam 95, so that the claw holder 91 is accompanied by the claw 92 by the height of the cam surface and the torsion spring force of the torsion bar 94. When the pawl 92 swings, the pawl 92 holds the paper in a closed position as indicated by reference numeral 92a in FIG.
As shown by 2b, it is configured to move between a position where the paper is released from the grip and a claw 92 is opened and closed to replace the paper.

Further, from this state, the reversing cylinder 65 rotates so that the cam follower 97 causes the large diameter portion 172a of the pawl moving cam 172.
In order to cope with the above condition, the pawl holder 91 is moved away from the cam surface of the pawl opening / closing cam 95 while being pressed against the large-diameter portion 172a of the pawl moving cam 172, so that the pawl holder 91 and the pawl 92 resist the torsion spring force of the torsion bar 94. 14, the pawl 92 is configured to move from an operating position shown by reference numerals 92a and 92b in FIG. 14 to a retracted position which is retracted into the peripheral surface of the reversing cylinder 65 as shown by reference numeral 92c.

Further, a wrench is applied to the hexagonal head 176b to rotate the pin 176, whereby the gear 175 is rotated via the gear 176a, and the pawl moving cam 172 is changed to a position corresponding to double-sided printing and single-sided printing. It is configured to rotate to and from a corresponding position.

In FIG. 15, gripper devices 98 and 99 (hereinafter referred to as the claws 9) composed of claws and claw bases are provided on the impression cylinders 63 and 64.
8 and 99) is provided in a notch at a location that divides the outer peripheral portions of the impression cylinders 63 and 64 into two in the circumferential direction, and among these, from the claw 92 and the claw base 81 of the reversing cylinder 65. The gripper device 100 is called a reversing claw 100.

Next, the paper edge holding device, its rotating device and moving device will be described. The rolling bearing 101 fitted in each of the bearers 68 on both sides has a structure as shown in FIG.
One end of an up-and-down lever drive shaft 102, which extends in the width direction of the machine base and is divided into two in the center of the notch 65b and 65c of the reversing cylinder 65 shown in FIG. 2, is rotatably supported. The other ends of the upper and lower lever drive shafts 102 are notches 65b and 65c at the axial center of the reversing cylinder 65, respectively.
Is rotatably supported by the main body 103a of the torsion bar holder 103 fixed to the bottom surface of the.

An up-and-down lever 104 formed in an L-shape is formed on a protruding portion of each up-and-down lever drive shaft 102 to the outside of the disk 68.
However, the cam follower 105 pivotally attached to one of the free ends of the vertical levers 104 is a vertical cam having a large diameter portion 106a and a small diameter portion 106b fixed to the frames 61 and 62. It is in contact with the outer peripheral cam surface of 106.

Main body 1 of the torsion bar holder 103
Lid 10 fixed to 03a so as to be rotatable in the circumferential direction
A hexagonal head 107a formed at one end of a torsion bar 107 penetrating the inner hole of the vertical lever drive shaft 102 is fitted and fixed in the hexagonal hole 3b.
The hexagonal head 107b formed at the other end of the is fitted into a hexagonal hole formed at one end of the vertical lever drive shaft 102.

By doing so, the torsion bar 10
When the lid body 103b is fixed in a state where the torsion spring force is accumulated in 7, the cam followers 105 are pressed against the cam surfaces of the upper and lower cams 106, and when the reversing cylinder 65 rotates, the upper and lower cams 10
The vertical lever 104 is configured to swing at a predetermined timing by the cooperation of the height of the cam surface 6 and the spring force of the torsion bar 107.

On the other hand, the rolling bearing 108 fitted in the bearing hole of each bearer 68 is formed in a tubular shape and is formed in the notches 65b and 65c of the reversing cylinder 65 shown in FIGS. 10 to 12 in the width direction of the machine base. One end of a feed lever drive shaft 109 that extends in the center of the feed lever drive shaft 109 and is divided into two at the center thereof is rotatably supported. The other ends of the feed lever drive shafts 109 extend in the axial direction of the reversing cylinder 65. Notch 65 in the center
Torsion bar holder 1 fixed to the bottom of b and 65c
The main body 110a of 10 is rotatably supported by a shaft.

The L-shaped feed lever 11 is formed at the protruding portion of each feed lever drive shaft 109 to the outside of the bearer 68.
1 is fixed by split tightening, and these feed levers 111
The cam follower 112 pivotally attached to one of the free end portions is in contact with the outer peripheral cam surface of the feed cam 113 having a cam surface composed of a large diameter portion 113a and a small diameter portion 113b fixed to the frames 61 and 62. Has been done.

Main body 1 of the torsion bar holder 110
Lid 11 fixed to 10a so as to be rotatable in the circumferential direction
A hexagonal head 114a formed at one end of a torsion bar 114 penetrating the inner hole of the vertical lever drive shaft 102 is fitted and fixed in the hexagonal hole of 0b.
The hexagonal head 114b formed at the other end of the is fitted into a hexagonal hole formed at one end of the feed lever drive shaft 109.

By doing so, the torsion bar 11
When the lid 110b is fixed in a state in which the torsion spring force is accumulated in 4, the cam follower 112 is pressed against the cam surface of the feed cam 113, and when the reversing cylinder 65 rotates, the feed cam 11
The feed lever 111 swings at a predetermined timing by the cooperation of the height of the cam surface of No. 3 and the spring force of the torsion bar 114.

As shown in FIGS. 6 and 8, on the outside of one bearer 68 of the reversing cylinder 65, there is an L-shape pivotally attached to the free end of the vertical lever 104 by a connecting pin 115. Of the feed lever 111, and the other end of the connecting link 118 pivotably attached at one end to the free end of the feed lever 111 by a pin 117 is at the other end thereof. A pin 119 is rotatably pivotally attached to the vicinity.

Further, as shown in FIGS. 7 and 9, the vertical lever 10 is provided outside the other bearer 68 of the reversing cylinder 65.
4, a suction drive lever 121 and a gear holder 122, which are rotatably pivoted by a connecting pin 120, are provided so as to overlap each other, and a free end portion of the feed lever 111 is provided with a pin 123 at one end. The other end of the rotatably pivoted connection link 124 is rotatably pivotally attached by a pin 180 near the base of the mouthpiece drive lever 121.

An arc-shaped segment gear 125 is fixed to the outer periphery of the gear holder 122, and the segment gear 1 is attached to the free end of the suction drive lever 121.
An intermediate gear 126 that meshes with 25 is rotatably attached.

The intermediate gear 126 is provided between the free end of the suction drive lever 116 provided on the one bearer 68 side and the free end of the suction drive lever 121 provided on the other disc 68 side. A hollow suction port shaft 128, which is closed at both ends and has a gear 127 that meshes with, is rotatably supported, and a plurality of suction ports 129, which will be described later in detail, are mounted on the suction shaft 128. However, the claw 92 and the claw 92 are arranged in parallel in the axial direction with different phases.

As a result, the reversing cylinder 65 rotates and the height of the feed cam 113 causes the feed levers 111 on both sides to move.
When oscillates, the mouthpiece drive levers 116 and 121 oscillate around the connecting pins 115 and 120 via the connecting links 118 and 124, and the intermediate gear 126 moves the segment gear 125.
Since it rolls while meshing with the intermediate gear 126 and the gear 1
The mouthpiece shaft 128 and the mouthpiece 129 are configured to reciprocate in the circumferential direction of the reversing cylinder 65 while rotating on their own axis by meshing with 27.

When the suction port 129 is moved, the vertical levers 104 on both sides are swung by the vertical cam 106, and the connecting pins 115 and 120 are vertically moved in the radial direction of the reversing cylinder 65. 121 and the segment gear 125 move up and down integrally with the suction port 129 and the like, and by the combined movement of the movement of the reversing cylinder 65 in the circumferential direction, as shown by a solid line and a chain line in FIG.
It is configured so as to make an arc motion over the claw base 81. Reference numeral 130 designates a base end portion of the feed lever drive shaft 109.
Is a gear fixing lever that is rotatably supported to the side and has its free end pivotally attached to the gear holder 122 to restrict movement of the gear holder 122 in the circumferential direction.

Next, the structure of the suction port 129 and the suction port 1
The intake device for 29 will be described. 6, FIG. 7 and FIG. 13, the suction port 129 is the hollow suction port shaft 1.
The suction port holder 129a is fixed to 28 by fastening, and the suction port body 131 is fixed to the suction port holder 129a. The suction port body 131 has a vent hole 128b between the suction port holder 128 and the inner hole 128a of the suction port shaft 128. , 130a, which are communicated with each other and open to the outside.

On the other hand, on the bracket 132 fixed to the outer surface of the frame 61, a rotary valve indicated by reference numeral 133 is supported by a flange portion of a cylindrical outer cylinder 134 fixed with bolts 135. The rotary valve 133 includes the outer cylinder 134 and the outer cylinder 1
And an inner cylinder 136 fitted and fixed to the inner cylinder 34,
A rotary shaft 138 is rotatably supported via a rotary shaft 36 and is formed on the end surface of the end shaft 137 of the reversing cylinder 65 by a rotary shaft 138 formed concentrically with the end shaft 137.

Reference numeral 139 is a nipple screwed into a screw hole of the outer cylinder 134, and is connected to the intake side of a pump (not shown) by a hose 140. The nipple 139 is opened on the peripheral surface of the inner cylinder 136. Has been done. The inner cylinder 136 is provided with a long hole 136a penetrating the inner circumference and the outer circumference thereof. The long hole 136a is an L-shaped air passage provided on the rotary shaft 138 integrated with the reversing cylinder 65. It is connected to 138a.

On the other hand, on the side of the reversing cylinder 65, there are openings 14 in three directions.
A T-shaped tube 141 having 1a, 141b, 141c is provided, and a hose 142 is connected between the opening 141a and the hole 138a. Also, the opening 141b
And a hose 142a between the suction port 128 and one end thereof.
And the connecting pin 115 and the air passage 143 provided in the suction drive lever 116 are in communication with each other. Furthermore, opening 1
41 h and the other end of the suction shaft 128 are connected to the hose 142 b.
And the connecting pin 120 and the air passage 171 provided in the suction driving lever 121.

As a result, when the reversing cylinder 65 rotates, the long holes 136a and the holes 138a are communicated with each other at a predetermined timing during one rotation of the reversing cylinder 65, and the atmosphere is sucked 129.
The paper tail is sucked from the suction port 129 and is sucked from the suction port 129.

The sheet-fed rotary printing press with a reversing mechanism constructed in this manner is provided with an air blowing device for blowing air between the conveying paper and the cylinder peripheral surface, and a print switching device for double-sided printing and single-sided printing. However, before describing these, the double-sided printing operation by the present printing press will be described with reference to FIG. 15 by taking the case where both the impression cylinder and the reversing cylinder have double diameters as an example.

In FIG. 15, when each printing cylinder rotates in the direction of the arrow, it is gripped by the claw 98 of the double-diameter first impression cylinder 63, which is the upstream cylinder in the paper transport direction, and wound around the cylinder peripheral surface. The paper 150 to be conveyed has its gripping edges on both sides of the body 6.
After reaching the counter contact points of 3, 65, it is wound around the peripheral surface of the impression cylinder 63 without being released from the grip of the claw 98.

When the paper tail of the paper 150 wound in this way reaches the counter contact points of the two cylinders 63, 65, that is,
When the suction port 129 comes on the line connecting the center of the impression cylinder 63 and the center of the reversing cylinder 65, the air passage 138a of the rotary shaft 138 that rotates integrally with the reversing cylinder 65 is the long hole 1 of the inner cylinder 136.
As the reversing cylinder 65 continues to rotate in a state corresponding to 36a, the hoses 142, 142a, 142b and the air passages 143, 171, the intake port 131a and the nipple 139.
Are communicated with each other and the pump sucks the atmosphere from the suction port, so that the trailing edge of the paper 150 is sucked into the suction port 129.

At the same time as the suction port 129 sucks the bottom of the paper, the cam follower 11 of the suction port turning device is rotated by the rotation of the reversing cylinder 65.
The contact position of 2 moves from the large diameter portion 113a of the feed cam 113 to the small diameter portion 113b, and the mouthpiece drive lever 11 is moved through the swing of the feed lever 111 and the forward and backward movement of the connecting link 124.
6, 121 swings, so that the intermediate gear 126 meshes with the segment gear 125 and rotates while rotating.
25, the gear 127 that revolves so as to roll over, and the gear 127 that meshes with the intermediate gear 126, and the suction port 129 that is integral with the gear 127 also move in the circumferential direction of the reversing cylinder 65.

In this way, the suction port 129 moves in the radial direction of the reversing cylinder 65 while rotating, and at the same time, the rotation of the reversing cylinder 65 causes the cam follower 105 of the suction port moving device to come into contact with the large diameter portion 106a of the vertical cam 106. To small diameter portion 106
The vertical lever 104 swings to move to b, and the gear holder 122, the segment gear 125, the suction drive lever 116, the gear 127, etc. are integrally moved in the radial direction of the reversing cylinder 65 while rotating the gear fixing lever 130. Since the suction port 129 is projected from the peripheral surface of the reversing cylinder 65, the suction port 129 rotates in the clockwise direction in the figure as shown by reference numerals 129A to 129G in FIG. 15 due to the combined movement with the movement in the radial direction. It circulates along the outer peripheral surface of the reversing cylinder 65.

In this case, since the suction surface of the suction port 129 holding the bottom of the paper is substantially parallel to the extending direction of the paper 150 separated from the peripheral surface of the impression cylinder 63, that is, the tangential direction of the reversing cylinder 65, The paper tail does not peel off from the suction surface of the suction port 129 due to the tension generated by the paper 150 sticking to the peripheral surface of the pressure drum 63 of the paper 150.

In this way, the suction port 129 holds the bottom of the paper and moves to the position indicated by reference numeral 129G, so that the paper 1
50 is turned inside out. It should be noted that the mouthpiece 129 has both the trunks 6
The pawl 98 of the impression cylinder 63 is closed and does not release the paper 150 from the grip until the paper tail is located at the opposite contact points of the nozzles 3, 65, and the suction port 129 sucks the paper tail of the paper 150 at the same time. 98 opens to release the paper 150 from the grip. Paper 15
0 is in close contact with the circumferential surface of the impression cylinder 63 even after being released from the grip of the claw 98.

When the reversing cylinder 65 rotates and the suction port for sucking the paper 150 reaches the position indicated by reference numeral 129G, the suction of air from the suction port 129 is cut off by the action of the rotary valve, and the suction of the paper 150 is released. At the same time, the cam follower 97 moves from the small diameter portion 95b of the pawl opening / closing cam 95 to the large diameter portion 95a against the torsion spring force of the torsion bar 94, so that the pawl holder 91 of the reversing pawl 100 swings. 92
14 moves from the position indicated by the reference numeral 92b in FIG. 14 to the position indicated by the reference numeral 92a, and the paper 150 released from the suction by the suction port 129 is gripped by the grip surface of the claw 92 of the reversing claw 100 and the claw base 81.

The reversing cylinder 65 is further rotated to rotate the reversing claw 100.
When is opposed to the claw 99 of the impression cylinder 64, the reversing claw 100 and the claw 99 are opened and closed to grip the paper 150 in the same manner as described above, and the paper 150 is gripped by the claw 99 and conveyed and printed on the back surface. Is applied.

On the other hand, the reversing claw 1 is placed at the position indicated by reference numeral 129G.
The mouthpiece that finished changing the grip of paper 150 to 00 is 6
While it rotates about 90 ° until it reaches the counter contact points of 4, 65, and moves in the radial direction so as to be immersed in the peripheral surface of the reversing cylinder 65, the suction port 129 interferes with the peripheral surface of the impression cylinder 64. There is nothing to do.

When the reversing cylinder 65 further rotates, the suction port 12
9 moves from the opposite contact point of both barrels 64 and 65 to the opposite contact point of both barrels 65 and 63, and during this time, the suction port 129 rotates about 360 ° by the suction port turning device, and the reversing barrel 65 moves.
While moving in the circumferential direction of the reversing cylinder 65, it is moved in the radial direction of the reversing cylinder 65 so as to move over the claw 100 by the suction port moving device so as to appear in and out of the circumferential surface of the reversing cylinder 65.

In such a double-sided printing operation, in order to avoid the reversing claw 100 from interfering with the impression cylinder 63, the reversing claw 10
0 is immersed in the peripheral surface of the reversing cylinder 65. That is, when the reversing claw 100 reaches the front of the line connecting the center of the impression cylinder 63 and the center of the reversing cylinder 65, the cam follower 72 moves the claw base against the spring force of the compression coil springs 84 and 86 and the torsion bar 82. From the large diameter portion 73a of the cam 73 to the small diameter portion 73
Since it moves to b, the claw base bar 80 of the reversing claw 100 rotates via the roller lever 71, the drive shaft 70, the drive rod 75 and the connecting lever 76, and the claw base 81 retracts as shown by the chain line in FIG. Move to position.

Following the movement of the claw base 81 to the retracted position, the cam follower 97 resists the torsion spring force of the torsion bar 94 and moves from the cam surface of the claw opening / closing cam 95 to the claw moving cam 1.
By moving to the large-diameter portion 172a of 72, the reversing claw 10
The claw holder 91 of 0 swings, and the claw 92 is indicated by reference numeral 92 in FIG.
Since it moves to the position indicated by c, the reversing claw 100 moves
5 does not enter and does not interfere with the peripheral surface of the impression cylinder 63.

Further, the reversing cylinder 65 rotates to rotate the reversing claw 100.
When it passes over the line connecting the centers of both bodies 63, 65, the cam follower 97, the torsion spring force of the torsion bar 94, causes the pawl opening / closing cam 95 to move from the large diameter portion 172a of the pawl moving cam 172.
14, the claw 92 of the reversing claw 100 moves from the retracted position 92c in FIG. 14 to the position 92b.

Following this movement of the pawl 92, the cam follower 72 oscillates the pawl base bar 80 by the cooperation of the spring force of the compression coil springs 84, 86 and the torsion bar 82 and the height of the cam surface of the pawl base moving cam 73. By abutting against the stop bar 77, the movement of the claw base bar 80 in the direction of the claw 92 is restricted, so that the claw base 81 moves from the retracted position shown by the chain line in FIG. 14 to the operating position shown by the solid line.

When the reversing cylinder 65 further rotates, the cam follower 97 of the reversing claw 100 moves to the small diameter portion 95b of the claw opening / closing cam 95 by the torsion spring force of the torsion bar 94 at the position indicated by reference numeral 129G in FIG. Figure 1
4 to the position indicated by reference numeral 92a and the paper 150 is sucked
The gripping surface of the claw base 81 and the claw 92 can be gripped by the gripper 29. When the paper 150 is gripped by the reversing claw 100, the stop bar 77 is positioned and fixed on the press-contact line of action of the claw 92 with respect to the claw base 81, so that the flexure of the claw base bar 80 is regulated and accurate gripping change is performed. be able to.

Since the sheet-fed rotary printing press with the reversing mechanism operating in this manner is provided with an air blowing device, this will be described below with reference to FIGS. 4 to 6 and FIG. A nipple 151, which is connected to the exhaust side of a pump (not shown) by a hose 152, is screwed into a screw hole provided in the outer cylinder 134 of the rotary valve 133. The nipple 151 is formed in the inner cylinder 136. It is opened on the peripheral surface. Inner cylinder 1
The slot 36 is provided with a long hole 153 penetrating the inner circumference and the outer circumference thereof. The long hole 153 is an L-shaped air passage 138b provided on the rotary shaft 138 integrated with the reversing cylinder 65.
Is in communication with.

On the other hand, in the notch 65a of the reversing cylinder 65,
The hose 1 is provided between the rotary shaft 138 and the air passage 138b.
A hollow air blowing bar 155 connected by 54 is formed between the left and right disks 68 so as to be pivotally adjustable, and is axially mounted. A plurality of air blowing bars 155 are connected to the inner holes thereof. No air blow holes are formed. The air blow holes of the air blow bar 155 are configured to blow air between the first impression cylinder 63 and the paper 150 separated from the peripheral surface thereof.

With such a configuration, as shown in FIG. 15, when the first impression cylinder 63 and the reversing cylinder 65 rotate in contact with each other, the peripheral surface of the impression cylinder 63 and the peripheral surface of the impression cylinder 63 are separated from each other. Since air is blown between the paper 150 and
It is possible to prevent the paper 50 from being reliably peeled from the peripheral surface of the impression cylinder 63, and the paper 150 to be closely attached to the peripheral surface of the impression cylinder 63 and not peeled off. Further, since the air-blowing nozzle is rotatably fixed so that the direction of the air-blowing nozzle can be adjusted, the air is accurately blown between the first impression cylinder 63 and the paper 150 separated from the peripheral surface thereof. Can be attached.

Next, a print switching device for switching from single-sided printing to double-sided printing and double-sided printing to single-sided printing will be described. Mainly in FIGS. 10 to 12, one of the two notches facing each other, which is provided by notching the peripheral surface of the reversing cylinder 65 as the paper transporting cylinder in a plane shape, is provided as described above. The upper and lower lever drive shafts 102 and the feed lever drive shaft 109, which are each divided into two at the axial center of the body, are mounted in parallel with each other, and these two divided drive shafts 102, 109 are A cam lever 15 in which cam followers 156 and 157 are pivotally attached to their free ends.
8, 159 are fixed by splitting the base portion.

Further, as described above, each drive shaft 10
Reference numerals 2 and 109 include a vertical lever 104 and a feed lever 111, in which cam followers 105 and 112 are brought into pressure contact with the upper and lower cams 106 for moving the suction port and the feed cam 113 for rotating the suction port on the sides of the frames 61 and 62 by the spring force of a torsion bar. Are respectively pivoted.

Further, in the other notch 65c of the notches of the reversing cylinder 65, the central portion 2 is formed in the same manner as the notch 65b.
The divided upper and lower lever drive shafts 102 and the feed lever drive shaft 109 are mounted in parallel with each other. The upper and lower lever drive shafts 102 and the feed lever drive shaft 109 have cam followers 160, 160 at their free ends. Cam levers 162 and 163, to which 161 are pivotally mounted, are fixed by clamping the base portion.

Further, as described above, each drive shaft 10
Reference numerals 2 and 109 respectively include an up-down lever 104 and a feed lever 111, in which cam followers 105 and 112 are brought into pressure contact with the up-down movement cam 106 on the frame 61 side and the up-feeding feed cam 113 by the spring force of a torsion bar. It is worn.

One notch 6 also shown in FIG.
On the bottom surface of 5b, a pair of first circular semi-circular cam surfaces are provided to contact the cam followers 156 with the cam surfaces of the end surfaces.
The stop cam 164 is rotatably provided by being held by a holder 165 formed in a rectangular shape in a front view, and the bottom surface of the notch 65b is also fan-shaped and has an end surface. A pair of second stop cams 166, whose surfaces are in contact with the cam followers 157, are rotatably supported by a holder 167 formed in a rectangular shape in a front view.

Further, although not shown in FIG. 10, FIGS.
Then, in the other notch 65c showing the side view, the notch 6
Holders 178 and 180, a second stop cam 177, a first stop cam 179, cam levers 162 and 163, cam followers 160 and 161, and the like having the same structure as those in 5b are provided.

The holder 165 on the side of the notch 65b and the notch 6
The holder 178 on the 5c side includes a connecting shaft 16 with a hexagonal head.
8 is rotatably supported, and the first stop cam 164 is fixed to the connecting shaft 168 on the side of the notch 65b and the second stop cam 177 on the side of the notch 65c.
Is fixed. In addition, the holder 17 on the side of the notch 65b
8 and a holder 167 on the side of the cutout 65C are rotatably supported by a connecting shaft 169 having a hexagonal head. The connecting shaft 169 has the second stop cam 166 on the side of the cutout 65b. Is fixed, and the second stop cam 179 is fixed to the side of the notch 65c.

Both of the first stop cams 164 and 179 are formed in the same shape as each other.
The stop cam 164 (179) has the connecting shaft 168.
A boss 164a (179a) having a hole 164b (179b) into which (169) is fitted, and a cam surface 164d.
(179d), 164e (179e), 164f (17
9f) and a flange portion 164c (179c).

As shown in FIG. 16, the cam surface forming the flange portion 164c (179c) has a higher horizontal surface 164f (179f) and a lower horizontal surface 164f (179f).
4d (179d) and these high horizontal surfaces 164f (17d)
9f) and the lower horizontal surface 164d (179d) are connected to each other, and the upper and lower slopes 164e (179e) are formed.

With this configuration, when the first stop cam 164 (179) rotates, the cam follower 156 (161) resists the torsion spring force of the torsion bar 114 from the horizontal surface 164d of the cam surface. Move to the inclined surface 164e (179e) to move the cam lever 158 (1
63) is moved.

Further, the first stop cam 164 (17
When 9) rotates, the cam follower 156 (161) moves to the horizontal surface 164f (179f) of the cam surface, so that the feed lever drive shaft rotates via the cam lever 158 (163), and the cam follower 112 moves the feed cam 113. The pivoting device for the suction port 129 is deactivated from the cam surface.

Also, both the second stop cams 166, 1
77 are formed in the same shape as each other, and as shown in FIG. 17, the second stop cam 166 (177) has a hole 166b (17) into which the connecting shaft 169 (168) is fitted.
7b) having a boss portion 166a (177a) and cam surfaces 166d (177d), 166e (177e), 166.
flange portion 166c (177) provided with f (177f)
c) and.

As shown in FIG. 17, the flange portion 16 is
The cam surface of 6c (177c) is a high horizontal surface 16
6f (177f) and a horizontal plane 166d (1
79d) and the upward and downward gentle slopes 166e (177e) connecting the high horizontal plane 166f (177f) and the low horizontal plane 166d (177d).

With this structure, when the second stop cam 166 (177) rotates, the cam follower 160 (157) resists the torsion spring force of the torsion bar 107 and the horizontal surface 166f (of the cam surface). 177
From f), the cam lever 162 (159) is moved to the inclined surface 166e (177e).

Further, the second stop cam 166 (17
When 7) rotates, the cam follower 160 (157) moves to the horizontal surface 166f (177f) of the cam surface, so that the vertical lever drive shaft rotates via the cam lever 162 (159), and the cam follower 105 moves the vertical cam 106 of the vertical cam 106. The moving device of the suction port 129 is in a non-operating state after being separated from the cam surface.

Thus, the first stop cams 164, 17
9 and the inclined surface 164 of the second stop cams 166 and 177.
Since the inclination angles of e, 179e, 166e, 177e are formed to be small, these stop cams can be easily moved against the biasing force on the cam follower side with a small force.

Further, the first stop cam 164 and the second stop cam 177 can be rotated together by the operation from the one notch 65b side of the reversing cylinder 65 by the connecting shaft 168, and it is provided on the reversing cylinder 65. 2 pairs of mouthpieces 1
One of the 29 can be deactivated, and the connecting shaft 169 is provided with the other notch 65 of the reversing cylinder 65.
By operating from the c side, the other suction port 129 can be deactivated, and the switching operation between double-sided printing and single-sided printing can be reliably performed with a small force.

With the above configuration,
When switching from double-sided printing to single-sided printing, the upstream cylinder group including the impression cylinder 63 is phase-adjusted to the reversing cylinder 65 by the length of the paper 150 approximately in the vertical direction, and then the pin 174 is used.
When a hexagonal head 174b is turned with a spanner,
The claw base moving cam 73 moves via the gears 174a and 173.

When the pin 176 is rotated by applying a spanner to its hexagonal head 176b, the claw base moving cam 172 is rotated via the gears 176a and 175, so that the reversing cylinder 65 is rotated.
When the rotation of the
The reversing claw 100 moves to the retracted position while moving from the counter contact with the reversing cylinder 65 to the counter contact between the reversing cylinder 65 and the impression cylinder 63.
The reversing claw 100 operates so that the reversing claw 100 moves to the operating position before reaching the counter contact point between the No. 5 and the impression cylinder 63, and there is no hindrance to the conveyance of the paper during single-sided printing.

Then, the connecting shafts 168 and 169 are attached to the
Stop cam 1 by turning the corner head with a wrench
64, 166, 177, and 179 rotate to push the cam followers 156, 157, 160, and 161 by pressing them, so that the drive shafts 109 and 102 rotate and the cam followers 112 and 105 move to the upper and lower cams 106. Since the cam followers 112 and 105 do not touch these cam surfaces even if the reversing cylinder 65 rotates by moving outward from both the cam surface large diameter portion and the cam surface large diameter portion of the feed cam 113,
The suction port 129 does not rotate or move, and stands still while being immersed inside the circumferential surface of the reversing cylinder 65. Therefore, the rotation of the suction port 129 and the members in the moving system are not worn.

In this embodiment, the impression cylinders 63 and 64 are used as the upstream and downstream cylinders that are in contact with the reversing cylinder 65.
Although the transfer cylinders may be replaced with the transfer cylinders 63 and 64, one of the upstream side and the downstream side may be used as the transfer cylinder and the other may be used as the transfer cylinder.

Further, in the present embodiment, the suction port 129 is exemplified as the paper tail holding member, but the invention is not limited to this, and for example, it is carried by piercing a paper tail with a needle, carried by a gripper, or carried. This pin, mouthpiece and mouthpiece 1
You may use together with 29.

Further, the reversing mechanism in this embodiment is composed of a paper tail holding member such as a mouthpiece and a paper holding member such as a gripper nail. The paper holding member pierces the mouthpiece and paper in addition to the gripper nail. It may be a pin or a combination thereof.

Further, in the present embodiment, an example is shown in which after changing the paper from the paper tail holding member such as the mouthpiece to the paper holding member such as the gripper, the paper is gripped by the gripper nail of the downstream side drum. However, you may make it hold | maintain a paper tail, invert a paper, and deliver a paper to the drum of the downstream side only with a paper tail member, such as a mouthpiece. Further, the rotating device and the moving device for the paper edge holding member are not limited to those of the embodiment.

[0102]

As is apparent from the above description, in the present invention, the cylinders are arranged between the upstream cylinder and the downstream cylinder in the paper transport direction with their circumferential surfaces facing each other. And a paper transport cylinder and a reversing mechanism that reverses the paper that has passed through the contact point between the paper transport cylinder and the upstream cylinder and is attached to the upstream cylinder and transfers it to the downstream cylinder. In a sheet-fed rotary printing press with a mechanism, a paper tail holding member that is provided in a reversing mechanism and holds a paper tail is rotatably supported by a paper transport cylinder and is retractable with respect to a peripheral surface of the paper transport cylinder. By providing a rotating device for rotating the paper tail holding member and a moving device for moving the paper tail holding member so that the paper tail holding member moves in and out with respect to the peripheral surface of the paper transport cylinder, the paper tail can be turned over when the paper is reversed. The paper edge holding surface of the holding member is the direction in which the paper is peeled from the peripheral surface of the upstream drum. Since it is almost parallel to the tangential direction of the upstream drum, the paper tail may be peeled or slipped from the paper holding surface of the paper tail holding member due to the tension of the paper that adheres to the peripheral surface of the upstream drum. In addition, the quality of printed matter is improved, accidents such as paper drop are eliminated, and the amount of waste paper is reduced.

[Brief description of drawings]

FIG. 1 is a partially cutaway front view of a left half portion of a reversing cylinder shown partially expanded.

FIG. 2 is a partially cutaway front view of a right half portion of the reversing cylinder shown in a partially developed state.

3 is a sectional view taken along line III-III in FIG.

4 is a sectional view taken along line IV-IV in FIG.

5 is a sectional view taken along line VV of FIG.

FIG. 6 is a partially cutaway front view of the left half portion of the reversing cylinder shown in a partially developed state.

FIG. 7 is a partially cutaway front view of the right half portion of the reversing cylinder shown in a partially developed state.

8 is a side view of FIG. 6 viewed from VIII.

9 is a side view taken along line IX of FIG. 7.

FIG. 10 is a plan view of an inversion cylinder.

11 is a side view taken along the line XI of FIG.

FIG. 12 is a side view of the reversing cylinder shown for explaining the operation of the paper holding cam mechanism.

FIG. 13 is a sectional view of a mouthpiece.

FIG. 14 is a front view of a claw, a claw base, and a suction port shown for explaining a gripping operation of paper.

FIG. 15 is a side view in the vicinity of the reversing cylinder shown for explaining the operation of the suction port and the reversing claw.

FIG. 16 is a perspective view of a stop cam.

FIG. 17 is a perspective view of a stop cam.

FIG. 18 is a cylinder array diagram of a conventional sheet-fed rotary printing press with a reversing mechanism.

FIG. 19 is an enlarged side view of the vicinity of the contact point between the upstream impression cylinder and the reversing cylinder, which is shown in a state where the cylinder is slightly rotated from the state of FIG. 16;

[Explanation of symbols]

 63 1st impression cylinder 64 2nd impression cylinder 65 Inversion cylinder 100 Inversion claw 102 Up / down lever drive shaft 104 Up / down lever 106 Up / down cam 107 Torsion bar 109 Feed lever drive shaft 111 Feed lever 113 Feed cam 114 Torsion bar 116 Suction drive lever 121 Suction port Drive lever 125 Segment gear 126 Intermediate gear 127 Drive gear 128 Suction shaft 129 Suction

Claims (1)

[Claims] 1. A paper transport cylinder disposed between an upstream cylinder and a downstream cylinder in the paper transport direction with their circumferential surfaces facing each other, and the paper transport cylinder and the upstream. In a sheet-fed rotary printing press with a reversing mechanism, which has a reversing mechanism that reverses the paper affixed to the upstream side cylinder and passes it to the downstream side cylinder after passing the counter contact point with the side cylinder. A paper tail holding member that is provided in the reversing mechanism and holds the paper tail is rotatably supported on the paper transport cylinder and is retractable with respect to the peripheral surface of the paper transport cylinder. A sheet-fed rotary printing press with a reversing mechanism, which is provided with a rotating device for moving the sheet-tail holding member, and a moving device for moving the paper tail holding member so as to move in and out of the peripheral surface of the paper transport cylinder.