JPH077934U - Sheet-fed rotary printing machine with reversing mechanism - Google Patents

Abstract

(57) [Summary] [Purpose] To increase the durability of the constituent members and to eliminate the reduction of the paper holding force by the paper tail holding member when the paper is turned over. A paper trailing edge holding device for holding and transporting the paper trailing edge of the paper delivered from the impression drum 63 at the time of double-sided printing is provided on the outer peripheral portion of the reversing cylinder 65, and has a suction port 129 for holding the paper trailing edge and a feed cam 11.
The reversing cylinder 65, which consists of 3 etc.
The rotating device that reciprocates in the circumferential direction of (1) and the moving device that includes the feed cam 106 and the like and that causes the suction port 129 to project from and retract to the circumferential surface of the reversing cylinder 65. Stop cams 164, 166, 177, and 179 that press or separate the cam followers 112 and 105 of the rotating device and the moving device against the cam surfaces of the feed cam 113 and the upper and lower cams 106 are supported on the frame side. Provided.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention is provided with a paper transport cylinder arranged between the upstream cylinder and the downstream cylinder in the paper transport direction so that the both surfaces are in contact with each other, and one machine can perform single-sided printing and double-sided printing. The present invention relates to a sheet-fed rotary printing press with a reversing mechanism that makes it possible.

[0002]

[Prior art]

 Along with the diversification of printing, various types of sheet-fed rotary printing presses with various types of reversing machines that can perform single-sided printing and double-sided printing with a single machine have been proposed. Japanese Patent Application Laid-Open No. 62-268644 discloses a transfer cylinder, a double-diameter cylinder having a double diameter thereof, and a reversing cylinder as a paper transport cylinder provided between the impression cylinder and the downstream impression cylinder. Therefore, this will be described below.

FIG. 19 is a cylinder arrangement diagram showing a single-sided printing state of a sheet-fed rotary printing press with a reversing mechanism disclosed in this publication, and FIG. 20 is a cylinder arrangement diagram also showing a double-sided printing state. An outline of this printing machine will be described. For example, a blanket cylinder 1 that is provided in a printing unit for the first color and is in contact with a plate cylinder (not shown) on which a printing plate is mounted has a claw 2 and a claw base 3 that are aligned in the axial direction. A first impression cylinder 5 having a plurality of gripper claw devices 4 (hereinafter, simply referred to as claws 4) formed in the outer peripheral notch is contacted with the gripper device. A second impression cylinder 10 having a plurality of gripping jaw devices 9 (hereinafter simply referred to as “claws 9”) including a pawl 7 and a pawl base 8 which are arranged in parallel in the axial direction is provided in the outer peripheral notch. It is touched.

Between the first impression cylinder 5 and the second impression cylinder 10, a transfer cylinder 11, a double-diameter cylinder 13 having a diameter twice that of the transfer cylinder 11, and a reversing cylinder 12 are arranged so that their circumferential surfaces are in contact with each other. In the outer peripheral notch of the transfer drum 11, a gripper device 16 (hereinafter, simply referred to as a pawl 16) composed of a pawl 14 and a pawl base 15 is arranged in parallel in the axial direction.

Further, in each notch provided at a position that divides the outer peripheral portion of the double-diameter cylinder 13 into two in the circumferential direction, a gripper device 19 (hereinafter, simply referred to as a claw) composed of a claw 17 and a claw base 18. A gripper device 19 and a gripper device 20 (hereinafter simply referred to as the “claw 20”) are arranged side by side in the axial direction so as to be movable in the circumferential direction.

In addition, at the location where the outer peripheral portion of the double-diameter cylinder 13 is divided into two equal parts and where the phase is different from the pawls 19 and 20 by approximately 45 ° in the circumferential direction, the suction ports 21 and 22 have blowers (not shown). And a gripper device 25 (hereinafter, simply referred to as a claw 25) including a claw 23 and a claw base 24 in the outer circumferential notch of the reversing cylinder 12. And a reverse claw device 28 (hereinafter simply referred to as a reverse claw 28) including a claw 26 and a claw base 27 are provided with a slight phase difference in the circumferential direction.

Therefore, the structure of the claw 25 and the reversing claw 28 will be described with reference to the sectional view of the reversing cylinder shown in FIG. 21 and the partially cutaway side view of the reversing cylinder shown in FIG. In the outer peripheral cutout 12a, two claw base shafts 31 and 32 extending in the axial direction are rotatably mounted in parallel with each other, and a plurality of not shown fixed to the claw base shafts 31 and 32 are provided. Claw shafts 33 and 34 formed in a hollow shape are rotatably mounted on the individual claw shaft holders.

The nail holders 35, 36 fixed to the nail holder shafts 31, 32 are fixed with the plurality of nail holders 24, 27 arranged in parallel in the axial direction, respectively. The nail holders 37 and 38 fixed to 34 include a plurality of claws 23 that form the claws 25 with the respective claw bases 24 and a plurality of claws that form the reverse claws 28 with the respective claw bases 27. 26 and 26 are fixed in parallel in the axial direction.

A torsion bar 39 is provided through the inner holes of the claw shafts 33 and 34, and the claws 23 and 26 are clawed by the cooperation of the torsion bar 39 and a cam mechanism including a cam lever 40 and the like. The pawl 25 and the reversing pawl 28 are opened and closed by rotating with respect to the bases 24 and 27, and the paper 29 is gripped at a predetermined timing and released from the grip.

On the other hand, in another notch 12b provided in the reversing cylinder 12, two cam lever shafts 41 and 42 extending in the axial direction are rotatably supported, and one of the cam lever shafts is rotatably supported. A cam lever 43 formed in a dogleg shape is split and fixed to one end of 41, and a cam follower 44 pivotally attached to one free end portion of the cam lever 43 of a reversing cam 45 fixed to the frame side. It is in contact with a cam surface composed of a small diameter portion 45a and a large diameter portion 45b.

The segment gear 46 formed at the other free end portion of the cam lever 43 meshes with the pinion 47 on the side of the pawl base shaft 31, and the cam lever 43 has a spring force of a torsion spring (not shown). As a result, the cam follower 44 is urged in a direction to press it against the cam surface of the reversing cam 45. As a result, when the reversing cylinder 12 rotates and the cam follower 44 circulates along the cam surface of the reversing cam 45, the cam lever 43 swings and the entire pawl 25 moves at a predetermined angle in the forward and reverse directions at a predetermined timing. It is configured to rotate only.

Although the rotating device for the claw 25 has been described above, a rotating device (not shown) having the same structure as that of the reversing claw 28 is provided on the opposite end surface of the reversing cylinder 12, and The rotation of the transfer cylinder 12 causes the entire reversing claw 28 to rotate in the forward and reverse directions by a predetermined angle at a predetermined timing.

A stop lever 48 is provided on a protruding portion of the claw table shafts 31 and 32 from the body end surface. A stop lever 49 is screwed into a screw hole 12c of the body end portion so as to advance and retreat. Are fixed to each other by splitting, and a compression coil spring 51 for urging the stopper 50 toward the stop lever 48 is interposed between the stopper 50 and the step portion of the stop pin 49. By doing so, when the stop pin 49 is adjusted back and forth, the stopper 50 swings the stop lever 48 to regulate the swing end thereof.

The operation of the sheet-fed rotary printing press with the reversing mechanism configured as described above will be described. In the case of single-sided printing, when the stop pin 49 is rotated to be screwed into the screw hole 12c, the swing end of the stop lever 48 is restricted, and the cam follower 44 via the pinion 47, segment gear 46, and cam lever 43. However, it is in a state of floating from the cam surface large diameter portion 45b of the reversing cam 45 for the claw 25.

When the printing operation is started after the preparation as described above, the paper 29 on which the first color is printed between the blanket cylinder 1 and the impression cylinder 5 is the same as the paper of the first impression cylinder 5 as shown in FIG. It is gripped from the claw 4 to the claw 16 of the transfer cylinder 11 and conveyed, and further gripped from the claw of the transfer cylinder 11 to the claw 20 (19) of the double-diameter cylinder 12 and conveyed.

The paper 29 conveyed along with the peripheral surface of the double-diameter cylinder 12 is conveyed by being gripped by the claw 19 (20) and the claw 25 of the reversing cylinder 13 and conveyed in this case. Since the reversing cam 45 and the reversing cam (not shown) for the reversing claw 28 are in the locked state as described above, the rotation operation of the claws 25 and 28 is stopped.

The paper 29 conveyed along with the reversing cylinder 13 is conveyed by being gripped by the claw 9 of the second impression cylinder 10 and conveyed between the blanket cylinder 6 and the second impression cylinder 10. When doing, a second color is printed on the same surface as before.

When switching from such single-sided printing to double-sided printing, the cylinder group on the paper conveying direction improving flow side including the double-diameter cylinder 12 is circled around the reverse cylinder 13 by the length of the paper 29 approximately in the vertical direction. In addition to phase adjustment in the direction, the stop pin 49 is pivotally operated in a loosening direction to release the regulation of the rotation of the stop lever 48, and then the printing operation is started.

In this way, as shown in FIG. 20, the paper 29 having the surface printed between the blanket cylinder 1 and the first impression cylinder 5 has the nails 4 of the first impression cylinder 5 to the nails of the transfer cylinder 11. After being gripped by 16 and conveyed, it is gripped by the claw 20 (19) of the double-diameter cylinder 12 and continued to be conveyed. By this conveyance, the gripping end of the paper 29 by the claw 20 (19) passes through the paired contact points of the two drums 12 and 13, and the paper 29 is attached to the lower circumferential surface of the double-diameter drum 12 along its entire vertical direction. To be done.

In this way, when the trailing edge of the paper 29 reaches the pair of contact points of the drums 12 and 13, the claw 19 (20) and the reversing claw 28 are opened and closed so that the front end of the paper 29 is reversed. The paper 29 is gripped and conveyed, and at this time, the paper 29 is turned upside down. Further, the leading end of the paper 29 is gripped by the reversing claw 28 to the claw 25, then gripped by the claw 9 of the impression cylinder 10 and conveyed, and when passing between the blanket cylinder 6 and the impression cylinder 10. Printing is performed on the back side to make double-sided printing.

[0021]

[Problems to be solved by the device]

 However, in the conventional sheet-fed rotary printing press with the reversing mechanism that operates in this way, in the case of single-sided printing, the stop pin 49 is pivotally operated as described above to stop the pawl 25 and the reversing pawl 28. By restricting the rotation of the lever 48, the cam lever 43 is restricted from rotating, and the cam lever for the reversing claw 28 (not shown) is restricted from rotating. In this case, the claw base shaft 31 of the claw 25 and the reversing claw 28 are restricted. It is necessary to rotate the stop pin 49 against the torsion spring force accumulated in the torsion bar (not shown) provided in each of the nail base shafts 32 of the above, so that the burden on the operator is large and the workability is poor. There's a problem.

Further, since the stopper 50 must be moved to a predetermined regulation position by operating the stopper pin 49 against the large biasing force of the torsion bar, this stopper 50 is located before the predetermined regulation position. If the stopper pin 49 is stopped and the reversing cylinder 13 continues to rotate in this state, the cam follower 44 or the cam follower (not shown) on the reversing claw 28 side may come into contact with the reversing cam 45 or the like. 46, the pinion 47, etc. are loaded and the durability thereof is deteriorated.

Further, in the conventional apparatus, in FIG. 20 for explaining the double-sided printing operation, after the trailing edge of the paper 29 reaches the paired contact points of both cylinders 12 and 13 and is gripped by the reversing claw 28, both cylinders 12 , 13 continue to rotate, but at this time, when the reversing claw 28 goes around while the gripping side of the paper 29 by the claw 19 (20) is in close contact with the peripheral surface of the double-diameter cylinder 12, this contact causes the paper 29 to be attached to the paper 29. There is a problem that a large tension is generated and the holding force of the paper 29 by the reversing claw 28 is weakened and slips, the paper 29 is dropped and an accident is caused, and the gripping after that becomes inaccurate and a waste paper is generated. . This is particularly likely to cause a problem when a mouthpiece is used instead of the claw 19.

The present invention has been made in view of the above points, and improves the operability of the switching operation between single-sided printing and double-sided printing and eliminates the reduction in the paper holding force of the holding member at the time of reversing. It is an object of the present invention to provide a sheet-fed rotary printing press with a reversing mechanism that makes it possible.

[0025]

[Means for Solving the Problems]

 In order to achieve such an object, according to the present invention, a reversing cylinder having a paper holding device and a paper tail holding device provided on the outer peripheral portion is disposed between the both cylinders with their circumferential surfaces facing each other. In a sheet-fed rotary printing press equipped with a reversing mechanism, a paper tail holding device is provided with a paper tail holding member that holds the paper tail, and a cam follower that is pressed against the cam surface of the reversing cam by the biasing means. The paper trailing edge holding member driving means is configured to move the member in the circumferential direction of the reversing cylinder so as to be retracted and rotated with respect to the circumferential surface of the reversing drum, and the cam follower of the paper edge holding member driving means is configured. , Between an operating position in which it is separated from the cam surface of the reversing cam against the urging force of the urging means, and a retracted position in which it is pressed against the cam surface of the reversing cam by the urging force of the urging means. A stop cam that can be freely supported is provided.

According to a second aspect of the present invention, there is provided a reversing cylinder having a paper holding device and a paper tail holding device provided on the outer peripheral portion between the two drums with their circumferential surfaces facing each other. In a sheet-fed rotary printing press with a reversing mechanism, a paper tail holding device is provided with a paper tail holding member that holds the paper tail and a cam follower that is pressed against the cam surface of the first reversing cam by a biasing means. A rotating device for rotating the trailing edge holding member, and a moving device having a cam follower pressed against the cam surface of the second reversing cam by the biasing means to move the trailing edge retaining member into and out of the peripheral surface of the reversing cylinder. And an operating position that separates the cam followers of the rotating device and the moving device from the cam surfaces of both the reversing cams against the biasing force of the biasing means, and the biasing means. Between the retracted position where it is pressed against the cam surfaces of both reversing cams by the biasing force A stop cam is provided that is movably supported by.

According to a third aspect of the present invention, in the sheet-fed rotary printing machine with a reversing mechanism according to the first or second aspect, a plurality of the stop cams are supported and the operating member and the retracted position are simultaneously operated by operating an operating member. A support member is provided for moving between and.

[0028]

[Action]

 When switching from double-sided printing to single-sided printing, the phase is adjusted in the circumferential direction by the length of the paper in the top-bottom direction with respect to the upstream cylinder group paper-conveying cylinder including the cylinder facing the paper-conveying cylinder. When the stop cam is moved, the cam follower of the paper trailing edge holding member drive means separates from the large diameter portion of the cam surface of the reversing cam, so that the paper edge holding member may rotate or move even if the paper transport cylinder rotates. There is nothing to do.

According to the second aspect of the present invention, when the double-sided printing is switched to the single-sided printing, the upstream cylinder group including the cylinder that is in contact with the paper transport cylinder is arranged in the substantially vertical direction of the paper with respect to the paper transport cylinder. When the stop cam for the rotating device and the stop cam for the moving device are moved against the biasing force of the biasing member while the transfer is adjusted in the circumferential direction only, the cam follower moves to the reversing cam for the rotating device. The large-diameter portion of the cam surface and the large-diameter portion of the cam surface of the reversing cam for the moving device are separated from each other, so that the paper edge holding member does not rotate or move even when the paper transport cylinder rotates.

According to the third aspect of the present invention, when the operating member is operated, the plurality of stop cams move to the operating position all at once, and the plurality of cam followers simultaneously separate from the large diameter portion of the cam surface of the reversing cam.

[0031]

【Example】

 1 to 17 show an embodiment of a sheet-fed rotary printing press with a reversing mechanism according to the present invention. FIG. 1 is a partially exploded front view of a left half portion of a reversing cylinder shown in a partially developed state, and FIG. A partially cutaway front view of the right half of the reversing cylinder shown partially expanded, FIG. 3 is a sectional view taken along the line III-III of FIG. 2, FIG. 4 is a sectional view taken along the line IV-IV of FIG. 1, and FIG. VV cross-sectional view, FIG. 6 is a partially exploded front view of the left half of the reversing cylinder, and FIG. 7 is a partially fractured front view of the right half of the reversing cylinder, which is partially expanded. 8 is a side view taken along line VIII of FIG. 6, FIG. 9 is a sectional view taken along line IX-IX of 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. Side view of the reversing cylinder shown to explain the operation of the cam mechanism, FIG. 13 is a cross-sectional view of the mouthpiece, and FIG. 14 is a front view of the claws, claw holders, and mouthpieces shown to explain the paper gripping operation. FIG. 15 illustrates the operation of the mouthpiece and the reverse claw. FIG. 16 and FIG. 17 are perspective views of the stop cam, respectively, for the sake of clarity, in the vicinity of the reversing cylinder.

In the figures, the left and right frames 61, 62 have a double-diameter first impression cylinder 63, which is a cylinder on the upstream side with respect to the rotation direction of the cylinder indicated by the arrow in the drawing, that is, the paper transport direction, A double-sided second impression cylinder 64, which is a flow-side cylinder, is rotatably supported on both end shafts, and the circumferential surface is formed between these impression cylinders 63, 64. A double-diameter reversing cylinder 65 as a paper conveying cylinder, which is in contact with the paper, is rotatably supported by a rolling bearing 66. The reversing cylinder 65 has an outer peripheral portion that is cut over almost the entire length of the cylinder. The notch 65a is provided.

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

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

As shown in FIG. 2, the claw base moving cam 73 has a gear 174a that meshes with the gear 173 at one end, and is provided at the other end of the pin 174 rotatably supported by the frame 62. By rotating the hexagonal head 174b with a wrench, the claw base moving cam 73 is rotated together with the gear 173 via the gear 174a, and a predetermined double-sided printing and single-sided printing is performed. It is configured to be movable between positions.

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

On the other hand, on the bottom surface of the notch 65a, a long stop bar 77 as a restricting member having a rectangular cross section and extending in the axial direction of the notch 65a is provided with a claw against a claw base 81 (described later). It is positioned and fixed on a pressure contact line 92 (described later), and a pair of left and right brackets 78, 79 are fixed on the bottom surface of the notch 65 a adjacent to the bearer 68.

Further, a claw base bar 80 having a through hole extending in the axial direction is rotatably supported on both the left and right brackets 78, 79 through rolling bearings so that both end shafts thereof are rotatable. On one swing end of the base bar 80, a plurality of claw bases 81 as claw base members are arranged in parallel so as to correspond to the respective claws 92.

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

As a result, the claw base bar 80 abuts the stop bar 77 by the torsion spring force stored in the torsion bar 82, so that the cam follower 72 is pressed against the cam surface of the claw base moving cam 73. It is configured so that the rotation limit to the is restricted.

Between the rotating portion 67 b of the drive shaft bracket 67 and the connecting lever 76, the same direction as the direction of the torsion spring force of the torsion bar 82, that is, the cam follower 72 is connected to the cam of the claw base moving cam 73. A compression coil spring 84 that urges the surface to press it is interposed.

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 notch 65a. A compression coil spring 86 is interposed between the base bar 80 and the cam follower 72 in a direction to press the cam follower 72 against the cam surface of the claw base moving cam 73.

As a result, when the cam follower 72 on the reversing cylinder 65 side is in pressure contact with 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. The claw base bar 80 swings at a predetermined timing by the cooperation of the height of the surface and the spring force of the compression coil springs 84 and 86 and the torsion bar 82, and the claw base 81 is reversed as shown by the solid line in FIG. To move between the operating position where the peripheral surface of the body 65 is flush with the tip end surface and the retracted position where it tilts and retracts from the peripheral surface of the reversing body 65 as shown by the chain line in FIG. It is configured.

Next, the claws that compose the gripper device together with the claw base 81 and the moving device thereof will be described. Bearings 87 and 88 located diagonally below the nail base 81 and fitted in the 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 each of the bearings 89, and a plurality of claw holders 91 are fixed in parallel on the claw shaft 90 in the axial direction. To the holder 91, claws 92 serving as a claw member for holding the paper with the claw base 81 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 rotationally adjustable in the circumferential direction has an inner hole of the claw shaft 90. A hexagonal head 94a formed at one end of a torsion bar 94 penetrating through is fixedly fitted, and a hexagonal head 94b formed at the other end of the torsion bar 94 is formed at one end of the pawl shaft 90. It is fitted into a hexagonal hole.

As shown in FIGS. 8 and 14, a pawl opening / closing cam 95 serving as a pawl opening / closing device having a cam surface including 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, a cam follower 97 pivotally attached to the free end of the lever 96 with a gear fixed to the end of the claw shaft 90 is widened by the torsion spring force of the torsion bar 94. The half of the direction is pressed.

As shown in FIGS. 1 and 14, the pawl opening / closing cam 95 has a boss portion having a cam surface including a large diameter portion 172a and a small diameter portion 172b. 172 is rotatably supported, and the pawl moving cam 172 is fixed by a bolt to a gear 175 rotatably supported by a boss portion of the pawl opening / closing cam 95 so as to rotate integrally with the gear 175. It is configured to move.

On the other hand, a pin 176 having a hexagonal head 176b formed at one end is rotatably supported on the frame 61, and a gear 176a meshing with a gear 175 is fixed to the other end of the pin 176. Has been done.

Further, the pawl moving cam 172 has a large diameter portion 172 a formed to have a larger diameter than the large diameter portion 95 a of the pawl opening / closing cam 95, and a small diameter portion 172 b to the small diameter portion 95 b of the pawl opening / closing cam 95. Is also formed with a small diameter. 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 at the remaining half portion in the width direction by the torsion spring force of the torsion bar 94.

By doing so, when the reversing cylinder 65 rotates, while the cam follower 97 corresponds to the small diameter portion 172b of the claw moving cam 172, the cam follower 97 is rotated while being pressed against the cam surface of the claw opening / closing cam 95. Therefore, the claw holder 91 swings with the claw 92 due to the height of the cam surface and the torsion spring force of the torsion bar 94, and the claw 92 moves to the closed position where the paper is gripped as indicated by reference numeral 92a in FIG. , As shown by reference numeral 92b, the paper is moved to a position where the paper is released from the grip, and the pawl 92 opens and closes to replace the paper.

Further, when the reversing cylinder 65 rotates from this state and the cam follower 97 corresponds to the large diameter portion 172a of the pawl moving cam 172, it is separated from the cam surface of the pawl opening / closing cam 95 and the large size of the pawl moving cam 172. Since it circulates while being pressed against the diameter portion 172a, the claw holder 91 rotates together with the claw 92 against the torsion spring force of the torsion bar 94, and the claw 92 moves from the operating position shown by reference numerals 92a and 92b in FIG. As shown by 92c, the reversing cylinder 65 is configured to move to a retreat position where the reversing cylinder 65 is retracted.

Further, by rotating the pin 176 by applying a spanner to the hexagonal head 176b, the gear 175 is rotated via the gear 176a, and the claw moving cam 172 is moved to a position corresponding to double-sided printing and a single-sided printing. It is configured to rotate with respect to the position corresponding to the printing.

In FIG. 15, gripper devices 98 and 99 (hereinafter, referred to as claws 98 and 99), which are composed of claws and claw bases, are provided on the impression cylinders 63 and 64 along the circumference of the impression cylinders 63 and 64. The gripper device 100, which is provided in a notch at a position that divides it into two equal parts in the direction, comprises the claw 92 of the reversing body 65 and the claw base 81, and 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 to the bearers 68 on both sides extends in the widthwise direction of the machine base through the notches 65b and 65c of the reversing cylinder 65 shown in FIGS. One ends of the vertical lever drive shafts 102 are rotatably supported, and the other ends of the vertical lever drive shafts 102 are respectively formed on the bottom surfaces of the notches 65b and 65c at the axial center of the reversing cylinder 65. It is rotatably supported by the main body 103a of the fixed torsion bar holder 103.

An L-shaped upper and lower lever 104 is fixed to the protruding portion of each of the upper and lower lever drive shafts 102 to the outside of the disk 68 by split clamping, and one free end of the upper and lower levers 104 is fixed. The cam follower 105 pivotally attached to the portion is in contact with the outer peripheral cam surface of the upper and lower cams 106, which are fixed to the frames 61 and 62 and are composed of a large diameter portion 106a and a small diameter portion 106b.

The hexagonal hole of the lid 103 b fixed to the main body 103 a of the torsion bar holder 103 so as to be rotatable in the circumferential direction is provided with a torsion bar 107 penetrating the inner hole of the vertical lever drive shaft 102. A hexagonal head 107a formed at one end is fitted and fixed, and a hexagonal head 107b formed at the other end of the torsion bar 107 is formed in a hexagonal hole formed at one end of the vertical lever drive shaft 102. It is fitted.

As a result, when the lid body 103b is fixed with the torsion spring force accumulated in the torsion bar 107, the cam follower 105 is pressed against the cam surfaces of the upper and lower cams 106, and when the reversing cylinder 65 rotates, The height of the cam surface of the cam 106 and the spring force of the torsion bar 107 cooperate with each other so that the vertical lever 104 swings at a predetermined timing.

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. Direction, and one end of the feed lever drive shaft 109 that is divided into two in the center is rotatably supported. The other ends of the feed lever drive shafts 109 are respectively in the axial direction of the reversing cylinder 65. The main body 110a of the torsion bar holder 110 fixed to the bottom surfaces of the notches 65b and 65c in the central portion of the is pivotally supported.

An L-shaped feed lever 111, which is formed into an outward protrusion of each of the feed lever drive shafts 109, is fixed by split tightening. The cam follower 112 pivotally attached to the end 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. .

The hexagonal hole of the lid 110 b fixed to the main body 110 a of the torsion bar holder 110 so as to be pivotally adjustable in the circumferential direction has a torsion bar 114 penetrating the inner hole of the vertical lever drive shaft 102. A hexagonal head 114a formed at one end is fitted and fixed, and a hexagonal head 114b formed at the other end of the torsion bar 114 is fitted into a hexagonal hole formed at one end of the feed lever drive shaft 109. It is fitted.

As a result, when the lid 110b is fixed with the torsion spring force accumulated in the torsion bar 114, the cam follower 112 is pressed against the cam surface of the feed cam 113, and when the reversing cylinder 65 rotates, The feed lever 111 swings at a predetermined timing in cooperation with the height of the cam surface of the cam 113 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. Is provided with a suction driving lever 116, and the other end of the connecting link 118 pivotally attached at one end to the free end of the feed lever 111 by a pin 117 is connected to the other end of the suction driving lever 116. A pin 119 is rotatably pivotally attached near the base.

Further, as shown in FIGS. 7 and 9, on the outside of the other bearer 68 of the reversing cylinder 65, a suction port pivotally attached to the free end portion of the vertical lever 104 by a connecting pin 120. The drive lever 121 and the gear holder 122 are provided so as to overlap each other, and the other end of the connecting link 124 pivotally attached at one end to the free end of the feed lever 111 by a pin 123 is A pin 125 is rotatably pivotally attached to the vicinity of the base of the mouthpiece driving lever 121.

An arc-shaped segment gear 125 is fixed to the outer periphery of the gear holder 122, and an intermediate gear 126 that meshes with the segment gear 125 rotates at the free end of the suction drive lever 121. It is freely pivoted.

The intermediate gear 126 is provided between the free end of the suction drive lever 116 provided on 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 with both ends closed and a gear 127 that meshes with the shaft end is rotatably supported, and a plurality of suction ports 129, which will be described in detail later, 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, when the reversing cylinder 65 rotates and the feed levers 111 on both sides swing due to the height of the feed cam 113, the suction port drive levers 116 and 121 are connected to the connection pins 115 and 121 via the connection links 118 and 124. Since the intermediate gear 126 oscillates around 120 and rolls while meshing with the segment gear 125, the inversion cylinder 65 rotates while the suction shaft 128 and the suction port 129 rotate by the meshing of the intermediate gear 126 and the gear 127. It is configured to reciprocate in the circumferential direction.

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 integrally move up and down together with the suction port 129 and the like, and due to the combined movement with 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 to make an arc motion so as to cross the claw 92 and the claw base 81. Reference numeral 130 is a gear fixing lever whose base end is rotatably supported on the feed lever drive shaft 109 side and whose free end is 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 an intake device for the suction port 129 will be described. 6, FIG. 7 and FIG. 13, the suction port 129 is formed by a suction port holder 129a fixed to the hollow suction shaft 128 by clamping and a suction port main body 131 fixed to the suction port holder 129a. The main body 131 is provided with an intake port 131a that communicates with the inner hole 128a of the intake shaft 128 by vent holes 128b and 130a and opens to the outside.

On the other hand, on the bracket 132 fixed to the outer surface of the frame 61, a rotary valve denoted by reference numeral 133 is supported by fixing a flange portion of a cylindrical outer cylinder 134 with bolts 135. The rotary valve 133 includes an outer cylinder 134, an inner cylinder 136 fitted and fixed to the outer cylinder 134, and rotatably supported by the inner cylinder 136 so that the rotary cylinder 133 can be rotated. The end surface of the end shaft 137 is composed of the end shaft 137 and a rotary shaft 138 formed concentrically.

Reference numeral 139 denotes a nipple screwed into the screw hole of the outer cylinder 134, and a hose 140 is connected to the intake side of a pump (not shown). The nipple 139 is a peripheral surface of the inner cylinder 136. It is open to. 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, a T-shaped tube 141 having three-way openings 141a, 141b, 141c is provided on the side of the reversing cylinder 65, and a hose 142 is provided between the opening 141a and the hole 138a. It is connected. The opening 141b and one end of the suction shaft 128 are connected to each other by a hose 142a, a connecting pin 115, and an air passage 143 provided in the suction driving lever 116. Further, the opening 141c and the other end of the suction shaft 128 are communicated with each other by the hose 142b, the connecting pin 120, and the air passage 171 provided in the suction driving lever 121.

By doing so, when the reversing cylinder 65 rotates, the long hole 136a and the hole 138a are communicated with each other at a predetermined timing during one rotation of the reversing cylinder 65, the atmosphere is sucked from the suction port 129, and the paper tail is sucked. It is configured to be adsorbed by 129.

The sheet-fed rotary printing press with the reversing mechanism configured as described above is provided with an air-blowing device that blows air between the transport paper and the cylinder peripheral surface, and a print switching device between double-sided printing and single-sided printing. Before explaining them, the double-sided printing operation of the printing press will be described with reference to FIG. 15 by taking the case where both the impression cylinder and the reversing cylinder have a double diameter 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 is wound around the cylinder peripheral surface. The paper 150 thus conveyed is wound around the circumferential surface of the impression cylinder 63 without being released from the grips of the claws 98 even after the gripping ends reach the counter contacts of the cylinders 63 and 65.

When the bottom of the paper 150 thus wound reaches the counter contact point between the two cylinders 63, 65, that is, on the line connecting the center of the impression cylinder 63 and the center of the reversing cylinder 65 with the suction port 129. The air passage 138a of the rotary shaft 138 that rotates integrally with the reversing cylinder 65 corresponds to the long hole 136a of the inner cylinder 136. Since the intake port 131a and the nipple 139 are communicated with each other through the air passages 143, 171 through the air passages 142, 142a, 142b, the pump sucks the atmosphere from the suction port, so that the tail of the paper 150 is sucked by the suction port 129.

Simultaneously with the suction port 129 sucking the tail of the paper, the contact position of the cam follower 112 of the suction port rotation device is moved from the large diameter portion 113a of the feed cam 113 to the small diameter portion 113b by the rotation of the reversing cylinder 65, and the feeding is performed. Since the suction port drive levers 116, 121 swing through the swing of the lever 111 and the forward / backward movement of the connecting link 124, the intermediate gear 126 meshes with the segment gear 125 and rolls on the segment gear 125 while rotating on its own axis. The gear 127 that revolves around 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 while rotating.

In this way, while the suction port 129 moves in the radial direction of the reversing cylinder 65 while rotating, the contact position of the cam follower 105 of the suction port moving device due to the rotation of the reversing cylinder 65 causes the large diameter portion of the upper and lower cams 106 to move. 106a to the small-diameter portion 106b, the upper and lower levers 104 swing, and while rotating the gear fixing lever 130, the gear holder 122 and the segment gear 125, the suction driving lever 116, the gear 127, and the like are integrally rotated. Since the suction port 129 is projected from the circumferential surface of the reversing cylinder 65 by moving it in the radial direction of 65, the suction port 129 is formed as shown by reference numerals 129A to 129G in FIG. 15 by the combined movement with the radial movement. While rotating in a clockwise direction, the orbiting cylinder 65 orbits along the outside of the 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. Also, the paper tail does not come 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 impression cylinder 63 of the paper 150.

In this way, the suction port 129 holds the bottom of the sheet and moves to the position indicated by reference numeral 129G, whereby the sheet 150 is turned upside down. Note that the claw 98 of the impression cylinder 63 is closed and does not release the paper 150 from the grip until the suction port 129 is located at the contact point between the two cylinders 63 and 65 and sucks the bottom of the paper. At the same time when the bottom of the paper is sucked, the nail 98 is opened and the paper 150 is released from the grip. The paper 150 is in close contact with the peripheral surface of the impression cylinder 63 even after being released from the grip of the nail 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. 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. .

When the reversing cylinder 65 further rotates and the reversing claw 100 faces the claw 99 of the impression cylinder 64, the reversing claw 100 and the claw 99 are opened and closed to change the gripping of the paper 150 in the same manner as described above. The paper 150 is gripped by the nails 99 and conveyed, and the back surface is printed.

On the other hand, the mouthpiece, which has finished gripping the paper 150 on the reversing claw 100 at the position indicated by reference numeral 129G, rotates about 90 ° before reaching the counter contact point between the two drums 64, 65, and reverses it. Since it moves in the radial direction so as to be immersed in the peripheral surface of the cylinder 65, the suction port 129 does not interfere with the peripheral surface of the impression cylinder 64.

When the reversing cylinder 65 further rotates, the suction port 129 moves from the contact point of both the cylinders 64 and 65 to the contact point of both the cylinders 65 and 63. During this time, the suction port 129 is almost moved by the suction rotation device. While rotating 360 degrees, it moves in the circumferential direction of the reversing cylinder 65, and at the same time, moves in the radial direction of the reversing cylinder 65 so as to project and retract with respect to the circumferential surface of the reversing cylinder 65 so as to get over the claw 100 by the suction port moving device. To do.

In such a double-sided printing operation, the reversing claw 100 is immersed in the peripheral surface of the reversing cylinder 65 in order to prevent the reversing claw 100 from interfering with the impression cylinder 63. That is, when the reversing claw 100 comes to 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 resists the spring force of the compression coil springs 84 and 86 and the torsion bar 82, and the claw base. Since the moving cam 73 moves from the large diameter portion 73a to the small diameter portion 73b, the claw base bar 80 of the reciprocating claw 100 is rotated via the roller lever 71, the drive shaft 70, the drive rod 75 and the connecting lever 76. , The claw base 81 moves to the retracted position shown by the chain line in FIG.

Following the movement of the claw base 81 to the retracted position, the cam follower 97 moves from the cam surface of the claw opening / closing cam 95 to the large diameter portion 172a of the claw moving cam 172 against the torsion spring force of the torsion bar 94. Therefore, the claw holder 91 of the reversing claw 100 swings to move the claw 92 to the position indicated by the reference numeral 92c in FIG. 14, so that the reversing claw 100 retracts from the peripheral surface of the reversing cylinder 65 and the circumference of the impression cylinder 63. Does not interfere with the surface.

When the reversing cylinder 65 further rotates and the reversing claw 100 passes over the line connecting the centers of the two cylinders 63 and 65, the large diameter portion 172 a of the claw moving cam 172 is generated by the torsion spring force of the cam follower 97 gate torsion bar 94. 14 to the cam surface of the claw opening / closing cam 95, the claw 92 of the reversing claw 100 moves from the retracted position 92c in FIG. 14 to the position 92b.

Following the movement of the pawl 92, the cam follower 72 swings the pawl base bar 80 by the cooperation of the spring force of the compression coil springs 84 and 86 and the torsion bar 82 and the height of the cam surface of the pawl base moving cam 73. By moving and contacting the stop bar 77, the movement of the claw base bar 80 in the direction of the claws 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. To do.

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. 14 is moved to the position indicated by reference numeral 92a in FIG. 14, and the paper 150 is gripped by the gripping surface of the claw base 81 and the claw 92 from the suction port 129. 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 the gripper bar is accurately changed. It can be performed.

An air blowing device is attached to the sheet-fed rotary printing press with the reversing mechanism that operates in this manner, which will be described below with reference to FIGS. 4 to 6 and 15. 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, and the nipple 151 has an inner cylinder 136. It is opened on the peripheral surface. The inner cylinder 136 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 provided on the rotary shaft 138 integrated with the reversing cylinder 65. It is connected to 138b.

On the other hand, in the notch 65 a of the reversing cylinder 65, a hollow air blowing bar 155 connected to the air passage 138 b of the rotating shaft 138 by a hose 154 is provided between the left and right discs 68. The air blowing bar 155 is formed so as to be pivotally adjustable, and is pivotally mounted. The air blowing bar 155 is provided with a plurality of air blowing holes communicating with the inner holes thereof. 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 the air is blown between the paper 150 and the paper 150, the paper 150 is surely peeled from the peripheral surface of the impression cylinder 63, and the paper 150 does not come in close contact with the peripheral surface of the impression cylinder 63. Absent. 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, in the notch 65b, which is one of the two notches facing each other, provided by notching the peripheral surface of the reversing cylinder 65 as the paper transporting cylinder in a planar shape, as described above. The upper and lower lever drive shafts 102 and the feed lever drive shaft 109, which are each divided into two parts at the axial center of the body, are mounted in parallel with each other, and these two divided drive shafts 102, 109 are Cam levers 158 and 159, to which cam followers 156 and 157 are pivotally attached at their free ends, are fixed by splitting the bases.

Further, as described above, the cam followers 105, 105 are formed on the drive shafts 102, 109 by the spring force of the torsion bar on the suction port moving upper and lower cams 106 and the suction port turning feed cam 113 on the frames 61, 62 side. An up-down lever 104 and a feed lever 111, which are pressed against each other, are pivotally mounted.

Further, in the other notch 65c of the notches of the reversing cylinder 65, the upper and lower lever drive shafts 102 and the feed lever drive shaft 109 which are divided into two at the central portion are also provided in the notch 65b. The upper and lower lever drive shafts 102 and the feed lever drive shaft 109 are mounted in parallel with each other, and cam levers 162 and 163, to which cam followers 160 and 161 are pivotally attached at their free ends, respectively, are clamped at their bases. It is fixed.

As described above, the drive shafts 102 and 109 are provided with cam followers 105 and 112 on the upper and lower suction cams 106 on the frame 61 side and the feed cam 113 for rotating the suction ports by the spring force of the torsion bar. The upper and lower levers 104 and the feed lever 111, which are brought into pressure contact with each other, are axially mounted.

Similarly, on the bottom surface of the one notch 65b shown in FIG. 10, there are provided a pair of first stop cams 164 formed in a semicircular shape and having the cam followers 156 in contact with the end cam surfaces. It is held by a holder 165 formed in a rectangular shape when viewed from the front and is rotatably provided. Also, the bottom surface of the one notch 65b is formed in a drum shape and the cam surface of the end face has the above-mentioned shape. A pair of second stop cams 166, to which the cam followers 157 are pressed, are held by holders 167 formed in a rectangular shape in a front view and are rotatably supported.

Further, in the other notch 65c not shown in FIG. 10 but shown in side views in FIGS. 11 and 12, the holders 178 and 180 and the second stop cam 177 having the same structure as those in the notch 65b are provided. , A first stop cam 179, cam levers 162, 163, cam followers 160, 161 and the like are provided.

A hexagonally-headed connecting shaft 168 is rotatably supported by the holder 165 on the notch 65b side and the holder 178 on the notch 65c side. The connecting shaft 168 has a notch. The first stop cam 164 is fixed to the 65b side, and the second stop cam 177 is fixed to the notch 65c side. A hexagonally-headed connecting shaft 169 is rotatably supported by the holder 178 on the side of the cutout 65b and the holder 167 on the side of the cutout 65C. The second stop cam 166 is fixed to the side of the notch 65b, 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, and in FIG. 16, the first stop cam 164 (179) has a hole 164b into which the connecting shaft 168 (169) is fitted. It is composed of a boss portion 164a (179a) in which (179b) is bored, and a flange portion 164c (179c) having cam surfaces 164d (179d), 164e (179e), 164f (179f).

As shown in FIG. 16, the cam surface forming the flange portion 164c (179c) has a high horizontal surface 164f (179f), a lower horizontal surface 164d (179d), and a higher horizontal surface 164f (179d). 179f) and the lower horizontal surface 164d (179d) are connected to each other, and are formed by a gentle slope 164e (179e) of upward and downward slopes.

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. The cam lever 158 (163) is moved by moving to the inclined surface 164e (179e).

Further, when the first stop cam 164 (179) rotates, the cam follower 156 (161) moves to the horizontal plane 164f (179f) of the cam surface, so that the feed lever drive via the cam lever 158 (163). The shaft rotates, the cam follower 112 separates from the cam surface of the feed cam 113, and the rotating device of the suction port 129 becomes inoperative.

Both of the second stop cams 166 and 177 are formed in the same shape, and as shown in FIG. 17, the second stop cam 166 (177) has the connecting shaft 169 (168). It is composed of a boss portion 166a (177a) having a hole 166b (177b) to be fitted therein, and a flange portion 166c (177c) having cam surfaces 166d (177d), 166e (177e), 166f (177f). ing.

As shown in FIG. 17, the cam surface forming the flange portion 166c (177c) has a high horizontal surface 166f (177f), a lower horizontal surface 166d (179d), and a higher horizontal surface 166f (177f). And a low horizontal plane 166d (177d) are connected to each other, and an upward and downward gentle sloped surface 166e (177e) is formed.

With this configuration, 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). 177f) to the inclined surface 166e (177e) to move the cam lever 162 (159).

Further, when the second stop cam 166 (177) rotates, the cam follower 160 (157) moves to the horizontal plane 166f (177f) of the cam surface, so that the vertical lever drive via the cam lever 162 (159). The shaft is rotated, the cam follower 105 is separated from the cam surfaces of the upper and lower cams 106, and the moving device of the suction port 129 is deactivated.

As described above, since the inclined angles of the inclined surfaces 164e, 179e, 166e, 177e of the first stop cams 164, 179 and the second stop cams 166, 177 are formed to be small, these stops can be made with a small force. The cam can be easily moved against the biasing force on the cam follower side. .

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 the reversing cylinder 65 can be rotated. One of the two sets of suction ports 129 provided can be deactivated, and the other suction port 129 is closed by operating the connecting shaft 169 from the other notch 65c side of the reversing cylinder 65. Since it can be activated, the switching operation between double-sided printing and single-sided printing can be reliably performed with a small force.

With the above-described configuration, when switching from double-sided printing to single-sided printing, the upstream cylinder group including the impression cylinder 63 is set to the reversing cylinder 65 so that the length of the paper 150 in the approximately vertical direction is increased. When the pin 174 is rotated by applying a wrench to the hexagonal head 174b after the phase adjustment in the circumferential direction, the claw base moving cam 73 moves via the gears 174a and 173.

Further, when the pin 176 is rotated by applying a wrench to the hexagonal head 176b of the pin 176, the nail base moving cam 172 is rotated via the gears 176a and 175. Therefore, when the reversing cylinder 65 rotates, While the claw 100 moves from the contact point between the reversing cylinder 65 and the impression cylinder 64 to the counter contact point between the reversing cylinder 65 and the impression cylinder 63, the reversing claw 100 moves to the retracted position, and 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 with, and there is no hindrance to the conveyance of the paper during single-sided printing.

Thereafter, when the connecting shafts 168, 169 are rotated by applying a wrench to the hexagonal heads of the connecting shafts, the stop cams 164, 166, 177, 179 are rotated and the cam followers 156, 157, 160, 161 are rotated. Since the driving shafts 109, 102 rotate and the cam followers 112, 105 correspond to either the large-diameter portion of the cam surface of the upper and lower cams 106 or the large-diameter portion of the cam surface of the feed cam 113, the driving shafts 109, 102 rotate. Even when the reversing cylinder 65 rotates, the cam followers 112 and 105 do not touch these cam surfaces even when the reversing cylinder 65 rotates. Therefore, the suction port 129 does not rotate or move, and the circumference of the reversing cylinder 65 does not change. It stands still while being immersed inside the surface. Therefore, the rotation of the suction port 129 and the parts in the moving system are not worn.

FIG. 18 is a sectional view of a reversing cylinder showing an embodiment of a sheet-fed rotary printing press with a reversing mechanism according to claim 3, in which the bottom surface of the notch 65b and the notch 65c are formed. The bottom surface is communicated with through holes 65d and 65e, and a T-shaped taper cam 170 serving as a stop cam is engaged in each of the through holes 65d so as to be movable in the radial direction of the barrel. ing. The taper cam 170 is formed in a T shape by a cam bar 170a extending in the penetrating direction of the through holes 65d and 65e and a support rod 170b as a support member orthogonal to the cam bar 170a. A tapered surface 170c corresponding to the cam followers 156 and 157 is provided.

With such a configuration, by gripping one of the support rods 170b and pushing the taper cam 170 in the direction shown by the arrow in the figure, the tapered surfaces 170c on both sides move the cam followers 156, 160. Simultaneously pushing outward, the feed lever drive shaft 109 and the up-and-down lever drive shaft 102, which actuate the two sets of suction ports 129 provided in the reversing cylinder 65, rotate in opposite directions, and one suction port is the same as in the previous embodiment. The cam followers 112 and 105 that operate the 129 are separated from the cam surfaces of the feed cam 113 and the upper and lower cams 106.

Further, when the other supporting rod 170b is gripped and the taper cam 170 is pushed in the direction shown by the arrow in the figure, the tapered surfaces 170c on both sides push the cam followers 157 and 161 simultaneously to the outside. The upper and lower lever drive shafts 102 and the feed lever drive shaft 109 for activating the other one of the 129 rotate in opposite directions, and the cam followers 112, 105 for activating the other suction port 129 of the upper and lower cams 106 and the feed cam 113 as described above are operated. Separate from the cam surface. When switching from single-sided printing to double-sided printing, it suffices to grip the support rod 170b and pull the taper cam 170 forward.

As described above, in this apparatus, it is efficient because the plurality of suction ports 129 can be simultaneously brought into the operating state and the retreating state only by the operation of grasping the support rod 170b and moving the taper cam 170 forward and backward. .

In each of the embodiments, as described in claim 2, a paper tail holding member that drives the paper tail holding member by a combination of two sets of a rotating device and a moving device. Although an example of the driving means is shown, it may be applied to a structure in which the paper edge holding member is projected and retracted with respect to the circumferential surface of the reversing cylinder and rotated by one cam follower.

Further, in each of the embodiments, as described in claim 3, an example in which a plurality of stop cams are moved together by operating one operation member has been shown. A separate operation member may be provided for each cam.

In each of the embodiments, the impression cylinders 63 and 64 are illustrated as the upstream and downstream cylinders that are in contact with the reversing cylinder 65. However, instead of the impression cylinders 63 and 64, transfer cylinders may be used. Alternatively, one of the upstream cylinder and the downstream cylinder may be used as an impression cylinder and the other cylinder may be used as a transfer cylinder.

Furthermore, in each of the above-described embodiments, an example in which the paper holding device is configured by the gripper and its operating mechanism is shown, but the present invention is not limited to this, and, for example, a suction port similar to a paper tail holding member. 129, a pin that pierces a paper, or a combination of these may be used.

[0120]

[Effect of device]

 As is apparent from the above description, according to the present invention, a reversing cylinder having a paper holding device and a paper tail holding device provided on the outer peripheral portion is disposed between the both cylinders with their circumferential surfaces facing each other. In a sheet-fed rotary printing press with a reversing mechanism, the paper tail holding device is provided with a paper tail holding member for holding the paper tail, and a cam follower pressed against the cam surface of the reversing cam by a biasing means. The trailing edge holding member is configured to move in the circumferential direction of the reversing cylinder so that the trailing edge holding member moves in and out of the circumferential surface of the reversing cylinder and rotates, so that the trailing edge of the paper is held when the paper is rotated. The paper edge holding surface of the member is almost parallel to the extending direction of the paper separated from the peripheral surface of the upstream cylinder, that is, the tangential direction of the upstream cylinder, so that it is in close contact with the peripheral surface of the upstream cylinder. The paper edge may be peeled off or slipped from the paper holding surface of the paper edge holding member due to the tension of the paper. There is no Rukoto, as well as improving the quality of printed matter, there is no accident such as dropping paper, amount of waste paper is reduced.

Further, the cam follower of the rotating device and the moving device is separated from the cam surface of the reversing cam against the urging force of the urging means, and the reversing cam by the urging force of the urging means. By providing a stop cam that is movably supported between it and the retracted position where it comes into pressure contact with the cam surface of the, it is possible to switch between double-sided printing and single-sided printing by unlocking the stop cam and rotating it. Since it can be performed, the switching work becomes easy, the burden on the operator is reduced, the work time is shortened, and the operation rate of the machine is improved. Furthermore, since the cam follower is reliably separated from the large diameter portion of the reversing cam and does not come into contact with it, the durability of the members constituting the paper edge holding device is improved.

According to the second aspect of the invention, in the sheet-fed rotary printing press with the reversing mechanism, the paper tail holding device includes the paper tail holding member for holding the paper tail and the first reversing device by the biasing means. A turning device that includes a cam follower that is pressed against the cam surface of the cam and that turns the paper tail holding member, and a cam follower that is pressed against the cam surface of the second reversing cam by the biasing means to reverse the paper tail holding member. The cam followers of the rotating device and the moving device are separated from the cam surfaces of both reaction cams against the biasing force of the biasing means. By providing a stop cam that is movably supported between an operating position and a retracted position in which the cam surfaces of both reversing cams are brought into pressure contact with each other by the biasing force of the biasing means, the turning cam is provided. For stop cams and moving devices When the cam cam is moved against the urging force of the urging member, the cam follower is reliably separated from the large-diameter portion of the cam surface of the reversing cam for rotating device and the large-diameter portion of the reversing cam for moving device. Since there is no contact, the paper edge holding member does not rotate or move even if the paper transport cylinder rotates, which improves the durability of the members that make up the paper edge holding device, and Switching between printing and single-sided printing is easy and workability is improved.

Further, according to a third aspect of the invention, in the sheet-fed rotary printing press with the reversing mechanism according to the first or second aspect, a plurality of stop cams are supported and the operating member and the retracted position are simultaneously operated by operating an operating member. By providing the support member that moves between and, the rotation and movement of the paper edge holding device can be stopped by one operation, so the switching work time between single-sided printing and double-sided printing is further shortened. The operation rate of the machine is improved.

[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 sectional view taken along line IX-IX in 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 side view of an inversion cylinder showing another embodiment of the present invention.

FIG. 19 is a cylinder arrangement diagram of a conventional sheet-fed rotary printing press with a reversing mechanism, which is shown for explaining an operation of single-sided printing.

FIG. 20 is a cylinder arrangement diagram of a conventional sheet-fed rotary printing press with a reversing mechanism, which is shown for explaining a double-sided printing operation.

FIG. 21 is a sectional view of a reversing cylinder in a conventional sheet-fed rotary printing press with a reversing mechanism.

FIG. 22 is a sectional view of a reversing cylinder in a conventional sheet-fed rotary printing press with a reversing mechanism.

[Explanation of symbols]

 63 impression cylinder 64 impression cylinder 65 reversing cylinder 80 claw stand bar 81 claw stand 90 claw shaft 92 claw 95 claw opening / closing cam 96 roller lever 97 cam follower 98 claw 99 claw 100 reversing claw 102 up / down lever drive shaft 104 up / down lever 105 cam follower 106 up / down Cam 107 Torsion bar 109 Feed lever Drive shaft 111 Feed lever 112 Cam follower 113 Feed cam 114 Torsion bar 116 Suction drive lever 121 Suction drive lever 127 Drive gear 128 Suction shaft 129 Suction 150 Paper 156 Cam follower 15 Cam follower 15 Cam follower 15 Cam follower 15 Cam follower 15 Cam follower 15 Cam follower 162 cam lever 163 cam lever 164 first stop cam 166 second stop cam 168 connecting shaft 169 connecting shaft 170 taper Arm 170a supporting rod 172 plate shifting cam 177 second stop cam 179 first stop cam

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[Procedure amendment]

[Submission date] September 6, 1993

[Procedure Amendment 1]

[Document name to be corrected] Drawing

[Name of item to be corrected] Figure 2

[Correction method] Change

[Correction content]

[Fig. 2]

[Procedure Amendment 2]

[Document name to be corrected] Drawing

[Name of item to be corrected] Figure 6

[Correction method] Change

[Correction content]

[Figure 6]

[Procedure 3]

[Document name to be corrected] Drawing

[Name of item to be corrected] Figure 7

[Correction method] Change

[Correction content]

[Figure 7]

[Procedure amendment 4]

[Document name to be corrected] Drawing

[Correction target item name] Figure 9

[Correction method] Change

[Correction content]

[Figure 9]

[Procedure Amendment 5]

[Document name to be corrected] Drawing

[Name of item to be corrected] Fig. 10

[Correction method] Change

[Correction content]

[Figure 10]

[Procedure correction 6]

[Document name to be corrected] Drawing

[Correction target item name] Fig. 16

[Correction method] Change

[Correction content]

FIG. 16

Claims (3)

[Scope of utility model registration request] 1. A paper holding device and a paper tail holding device are provided on the outer peripheral portion between an upstream cylinder and a downstream cylinder with respect to the paper transport direction, with their cylinders facing each other. And a front end of the paper received from the upstream cylinder by the paper holding device for single-sided printing and delivered to the downstream cylinder, and is wound around the upstream cylinder during double-sided printing. In a sheet-fed rotary printing machine with a reversing mechanism configured to receive and hold the tail of a paper by the paper tail holding device and receive the paper by the paper holding device while reversing the paper and deliver it to the downstream cylinder. The paper tail holding device includes a paper tail holding member that holds the paper tail, and a cam follower that is pressed against the cam surface of the reversing cam by a biasing means to move the paper tail holding member in the circumferential direction of the reversing cylinder. The paper trailing edge protector that moves in and out of the peripheral surface of the reversing cylinder A holding member drive means, and an operating position for separating the cam follower of the paper edge holding member drive means from the cam surface of the reversing cam against the biasing force of the biasing means, and the biasing means. A sheet-fed rotary printing press with a reversing mechanism, comprising a stop cam movably supported between an evacuation position in which the cam surface of the reversing cam is pressed against the urging force. 2. A paper holding device and a paper tail holding device are provided between an upstream cylinder and a downstream cylinder with respect to the paper transport direction, with their circumferential surfaces in contact with each other. And a front end of the paper received from the upstream cylinder by the paper holding device for single-sided printing and delivered to the downstream cylinder, and is wound around the upstream cylinder during double-sided printing. In a sheet-fed rotary printing machine with a reversing mechanism configured to receive and hold the tail of a paper by the paper tail holding device and receive the paper by the paper holding device while reversing the paper and deliver it to the downstream cylinder. The paper tail holding device includes a paper tail holding member that holds the paper tail, and a cam follower that is pressed against the cam surface of the first reversing cam by a biasing means to rotate the paper tail holding member. Device and cam that is pressed against the cam surface of the second reversing cam by the biasing means A moving device having a follower for retracting and retracting the paper tail holding member with respect to the peripheral surface of the reversing cylinder, and a cam follower of the rotating device and the moving device resists the biasing force of each biasing means. Are movably supported between an operating position in which they are separated from the cam surfaces of both of the reversing cams and a retracted position in which they are pressed against the cam surfaces of both of the reversing cams by the urging force of each urging means. A sheet-fed rotary printing press with a reversing mechanism, which is equipped with a stop cam. 3. The reversing mechanism according to claim 1, further comprising a support member that supports a plurality of the stop cams and moves the stop cams together between the operating position and the retracted position by operating an operation member. Sheet-fed rotary printing press.