Patent Grant
7771336
The present application is based on International Application PCT/JP2004/18294, and claims priority from, Japanese Application Number 2003-415124, filed Nov. 18, 2003, the disclosure of which is hereby incorporated by reference herein in its entirety.
The disclosed embodiments relates to a folding machine installed in a rotary printing machine, and more particularly to a folding machine that is employed in a variable cut-off length type rotary printing machine in which the cut-off length of a web can be varied.
As shown in
As shown in
A further description will be given of the construction and function of each part. The triangular plate 12 folds the web 10 fed through the drag roller 11, in half along the traveling direction, and the web 10 folded in two is fed through the lead-in rollers 13a and 13b. The downstream nipping rollers 14a and 14b nip the web 10 folded in two, convey it while rotating, and press it between them to put a vertical crease in it reliably.
The web cutting unit 20 is used to cut the web 10 folded in two at a predetermined cut-off length position and consists of a saw cylinder 21 and a receiving cylinder 22 rotating in opposite directions. The saw cylinder 21 is provided with a saw-blade holder 24 having saw blades 23 in the outer periphery along the axial direction. The receiving cylinder 22 is provided with a rubber bed 25, made of an elastic body such as rubber, for receiving the saw blades 23.
The saw blades 23 of the saw cylinder 21 and the rubber bed 25 of the receiving cylinder 22 are arranged so that they mesh with each other. By synchronously rotating them in opposite directions, a sheet (folded sheet) 10a is cut off from the fed web 10 by cutting it in the horizontal direction (direction of the width of the web 10). In this example, the saw cylinder 21 is provided with a single saw blade 23 and the receiving cylinder 22 is provided with a single rubber bed 25. Therefore, if each of the cylinders 21, 22 makes one rotation, cutting is performed once.
The accelerating belt conveyor 30 is equipped with a pair of conveyor belts 31, 32 facing each other. Each of the conveyor belts 31, 32 passes around guide rollers 33 and is constructed such that the traveling speed can be arbitrarily varied to some degree. The conveyor belts 31, 32 receive the sheet 10a cut off from the continuous web 10 by the web cutting unit 20 and nip it between them. The moment the sheet 10a is nipped, it is conveyed to the catching-folding unit 40B at the speed corresponding to the speed of the catching-folding unit 40B.
As shown in
In the illustrated catching-folding unit 40B, the catching cylinder 42 has two catchers 41 and the folding cylinder 45 has two grippers 43 and two folding blades 44. As a result, two folded sheets 10b are formed in one rotation of each of the cylinders 42, 45.
The paper discharge belt conveyor 46 is constructed such that the folded sheets 10b, formed as described above, are transferred to the subsequent steps, that is, a sheet alignment stacker 80 (see
In the aforementioned construction, when cutting off a predetermined cut-off length from the printed continuous web 10 by the saw cylinder 21, the predetermined cut-off length C is given as
C=Vo/(Nc·n)
where Vo is the traveling speed (conveying speed) of the web, Nc is the number of rotations of the saw cylinder, and n is the number of saw blades.
The cut-off sheet 10a is accelerated in one breath from the traveling speed of the web 10 to the speed Vb (i.e., the peripheral speed of the folding cylinder 45) of the catching-folding unit 40B and transferred onto the folding cylinder 45 at the traveling speed Vb.
Subsequently, the sheet 10a fed from the conveyor belts 31, 32 is delivered to the gripper 43 of the folding cylinder 45 and catching and folding are carried out.
A folding machine capable of varying the cut-off length of a web (i.e., a folding machine for a variable cut-off length type rotary printing machine) is disclosed in Patent Document 1 by way of example. This folding machine is provided with a cut-off cylinder, and a delivering cylinder for cutting a ribbon (web) into folded sheets having the desired cut-off length in cooperation with the cut-off cylinder. This delivering cylinder has a cylinder center line and a peripheral surface region. The peripheral surface region of the delivering cylinder has an adjustable diameter portion arranged thereon. This adjustable diameter portion is connected to the delivering cylinder and is movable toward and away from the cylinder center line to adjust the desired cut-off length of a folded sheet. In addition, there is provided a jaw cylinder, which has a cylinder jacket and jaws provided in this cylinder jacket. Furthermore, the peripheral surface region of the delivering cylinder has a pushing blade for folding a folded sheet into the jaws in cooperation with the jaws so that the cut-off length of a web can be varied.
In addition to the catching-folding unit 40B consisting of the catching cylinder 42 equipped with catchers 41 and the folding cylinder 45 equipped with the gripper 43 and folding blades 44 for folding a sheet is a folder, which employs a chopper, such as a chopper folder disclosed in Patent Document 2.
Patent Document 1: Japanese Laid-Open Patent Publication No. 2001-233545
Patent Document 2: Japanese Patent Publication No. 2532507
However, the conventional folding machine for a rotary printing machine such as that shown in
That is, in the aforementioned conventional folding machine, the accelerating belt conveyor 30 operates at uniform velocity so that the sheet 10a is conveyed at the conveying speed Vb (peripheral speed of the folding cylinder 45) of the catching-folding unit 40B higher than the traveling speed Vo of the web 10. Because of this, when the sheet 10a is delivered from the web cutting unit 20 to the accelerating belt conveyor 30 immediately after it is cut off by the web cutting unit 20, the sheet 10a being traveled at the traveling speed Vo of the web 10 is accelerated in one breath to the speed Vb higher than the speed Vo when received by the accelerating belt conveyor 30.
Therefore, even a slight shift in the cut-off completion timing in the web cutting unit 20 can cause a shift in the timing at which the sheet 10a is delivered from the web cutting unit 20 to the variable speed belt conveyor 30. This can cause a shift in the timing at which the sheet 10a is delivered from the variable speed belt conveyor 30 to the catching-folding unit 40B, so it is fairly difficult to ensure sufficient accuracy of folding (accuracy of folding position or folding phase).
Particularly, accumulation of the aforementioned shifts in the timing can cause not only a reduction in accuracy of folding but also incomplete delivery between the accelerating belt convey or 30 and the catching-folding unit 40B, so that there are cases where the folding machine has to be shut down.
The disclosed embodiment has been made in view of the problems mentioned above. Accordingly, it is the object of the disclosed embodiment to provide a folding machine for a rotary printing machine that is capable of performing a folding process (such as putting a crease in a cut-off sheet in a direction perpendicular to the travel direction) on a cut-off sheet with a high degree of accuracy.
To achieve the aforementioned object, a folding machine of the disclosed embodiment is provided downstream of a printing unit of a rotary printing machine. The folding machine includes a cut-off unit. This cut-off unit comprises a cut-off mechanism for cutting off a sheet at a predetermined cut-off length position from a web fed from the printing unit, and a first belt conveyor comprising a pair of conveyor belts for nipping and conveying the sheet cut off by the cut-off mechanism. The folding machine further includes a processor, provided downstream of the cut-off unit, for processing the sheet cut off by the cut-off unit, and a second belt conveyor provided between the cut-off unit and the processor and comprising at least one pair of conveyor belts for receiving the sheet conveyed by the first belt conveyor and conveying the sheet to the processor. The aforementioned second belt conveyor varies a sheet conveying speed during the conveyance of the sheet so that in receiving the sheet from the first belt conveyor, the sheet conveying speed becomes approximately equal to a first speed at which the sheet is conveyed in the first belt conveyor, and in conveying the sheet to the processor, the sheet conveying speed becomes approximately equal to a second speed at which the sheet is conveyed in the processor.
Preferably, the aforementioned cut-off unit is constructed such that it can vary and cut a cut-off length of the web fed from the printing unit; a speed at which the web is conveyed is set according to a cut-off length of the sheet that is cut off by the cut-off unit; and the first speed at which the sheet is conveyed in the first belt conveyor is set so that it becomes equal to the web conveying speed.
Preferably, the aforementioned cut-off unit comprises a first cut-off mechanism for partially cutting the web, and a second cut-off mechanism, provided downstream of the first cut-off mechanism, for cutting off the sheet from the web by cutting the uncut portions of the web that is not cut by the first cut-off mechanism.
Preferably, the aforementioned first belt conveyor nips the web that is cut by the second cut-off mechanism, and the folding machine further includes a fourth belt conveyor comprising a pair of conveyor belts for nipping and conveying the web to the first cut-off mechanism.
Preferably, the folding machine further includes a first relative-phase changer, interposed between the first cut-off mechanism and the second cut-off mechanism, for changing relative phases of rotation of the first cut-off mechanism and the second cut-off mechanism when varying a cut-off length of the web fed from the printing unit.
Preferably, the folding machine further includes a scored-line forming mechanism, provided upstream of the first and second cut-off mechanisms, for forming a horizontally scored line in the web at a predetermined position; and a second relative-phase changer, interposed between the scored-line forming mechanism and the first cut-off mechanism, for changing relative phases of rotation of the scored-line forming mechanism and the first cut-off mechanism when varying a cut-off length of the web fed from the printing unit.
The sheet conveying speed of the processor is preferably faster than that of the first belt conveyor.
In this case, preferably, the aforementioned second belt conveyor receives the sheet at a speed approximately equal to the sheet conveying speed of the first belt conveyor, then accelerates the sheet conveying speed to a speed approximately equal to the sheet conveying speed of the processor, then delivers the sheet to the processor at a speed approximately equal to the sheet conveying speed of the processor, and decelerates the sheet conveying speed to the sheet conveying speed of the first belt conveyor and receives a sheet next cut off from the web.
The aforementioned processor preferably comprises a discharger for discharging a sheet cut off by the cut-off unit or a folder for folding a sheet cut off by the cut-off unit along a crease perpendicular to a sheet conveying direction.
Preferably, the aforementioned folder comprises a catching cylinder equipped with a catcher, and a folding cylinder equipped with a gripper for holding the sheet and a folding blade for causing the catcher to catch the sheet; and the aforementioned folding cylinder is equipped with a first frame that supports the gripper and rotates on an axis of the folding cylinder, a second frame that supports the folding blade and rotates on the axis of the folding cylinder, and a third relative-phase changer for changing relative phases of rotation of the first and second frames.
Preferably, the aforementioned first belt conveyor, the aforementioned second belt conveyor, the aforementioned cut-off unit, and the aforementioned processor are respectively driven by different motors, and a phase of each of the motors can be relatively varied.
Preferably, the folding machine further includes an abutting portion, provided between the second belt conveyor and the processor, which a front end of the sheet abuts and by which a conveying phase of the sheet in the folder can be adjusted.
Preferably, the folding machine further includes a third belt conveyor, provided downstream of the second belt conveyor and at an entrance portion to the processor, which comprises a pair of conveyor belts for receiving the sheet from the second belt conveyor and conveying the sheet to the processor at the sheet conveying speed of the processor.
Preferably, the folding machine further includes a non-circular roller (cam roller), provided at a position where the sheet is delivered from one of the two belt conveyors adjacent to each other to the other of the two belt conveyors, which guides one of a pair of conveyor belts and has a plurality of surface portions in which distances from a center of rotation to the surface portions are different.
Preferably, the conveyor belts of the second belt conveyor are driven by non-circular rollers (cam rollers) having a plurality of surface portions in which distances from a center of rotation to the surface portions are different.
A second folding machine of the disclosed embodiment is provided downstream of a printing unit of a rotary printing machine. The second folding machine includes a cut-off unit capable of varying a cut-off length of a web fed from the printing unit and cutting off a sheet from the web; and a folder, provided downstream of the cut-off unit, for folding the sheet cut off from the web by the cut-off unit along a crease perpendicular to a sheet conveying direction. The aforementioned cut-off unit has a first cut-off mechanism for partially cutting the web at a predetermined cut-off length position, a belt conveyor for nipping and conveying the web partially cut by the first cut-off mechanism, and a second cut-off mechanism for cutting off a sheet with a predetermined cut-off length by cutting uncut portions of the web conveyed by the belt conveyor. The aforementioned folder is provided downstream of the belt conveyor and comprises a pair of folding rollers and a chopper folder for chopper-folding the sheet in cooperation with the folding rollers by moving into a space between the folding rollers.
A variable cut-off length type rotary printing machine of the disclosed embodiment comprises any one of the aforementioned folding machines and is constructed such that it can vary and cut a cut-off length of a printed web.
According to the folding machine (and the variable cut-off length type rotary printing machine) of the disclosed embodiment, a sheet is cut off by the cut-off unit from a web fed from the printing unit of a rotary printing machine and is conveyed to a downstream processor by first and second belt conveyors and processed. In the printing unit and cut-off unit, the web is conveyed at a fixed speed and printing and cutting are performed. The cut-off sheet is conveyed by the first belt conveyor and is further delivered to the second belt conveyor. The second belt conveyor varies a sheet conveying speed during the conveyance of the sheet so that in receiving the sheet from the first belt conveyor, the sheet conveying speed becomes approximately equal to a first speed at which the sheet is conveyed in the first belt conveyor, and in conveying the sheet to the processor, the sheet conveying speed becomes approximately equal to a second speed at which the sheet is conveyed in the processor. Therefore, the sheet cut off by the cut-off unit is delivered at an equal speed when delivering the sheet from the first belt conveyor to the second belt conveyor and when delivering the sheet from the second belt conveyor to the processor. As a result, sheets cut off from the web can be processed with a high degree of accuracy.
Particularly, in a rotary printing machine (variable cut-off length type rotary printing machine) constructed such that it can vary and cut a cut-off length of a web fed from the printing unit, if a speed at which the web is conveyed is set according to a cut-off length of a sheet that is cut off by the cut-off unit, and the first speed at which the sheet is conveyed in the first belt conveyor is set so that it becomes equal to the web conveying speed, the cut-off length of the web can be properly varied. In addition, as set forth above, the second belt conveyor varies a sheet conveying speed during the conveyance of the sheet so that in receiving the sheet from the first belt conveyor, the sheet conveying speed becomes approximately equal to a first speed at which the sheet is conveyed in the first belt conveyor, and in conveying the sheet to the processor, the sheet conveying speed becomes approximately equal to a second speed at which the sheet is conveyed in the processor. Therefore, the sheet cut off by the cut-off unit is delivered at an equal speed when delivering the sheet from the first belt conveyor to the second belt conveyor and when delivering the sheet from the second belt conveyor to the processor. Thus, a sheet can be cut to a predetermined cut-off length and the cut-off sheet can be accurately processed. This contributes to an enhancement in print quality.
Furthermore, the aforementioned cut-off unit may be constructed such that it includes a first cut-off mechanism for partially cutting a web and a second cut-off mechanism, provided downstream of the first cut-off mechanism, for cutting off a sheet from the web by cutting uncut portions of the web other than the portions cut by the first cut-off mechanism. In this case, in the cut-off unit, the web is partially cut at a predetermined cut-off length position by the first cut-off mechanism. Thereafter, while this web is being nipped and conveyed by the first belt conveyor, a sheet with a predetermined cut-off length is cut off by cutting uncut portions of the web with the second cut-off mechanism. Therefore, cutting of the web can be performed in a stable state of conveyance and the cut-off sheets can be easily conveyed at the required phase timing. As a result, cutting of the web and processing of cut-off sheets can be performed with a high degree of accuracy.
In this case, if the aforementioned first belt conveyor nips the web that is cut by the second cut-off mechanism, and the folding machine further includes a fourth belt conveyor comprising a pair of conveyor belts for nipping and conveying the web to the first cut-off mechanism, the web can be stably and accurately cut by the first cut-off mechanism.
It is preferable that a first relative-phase changer be interposed between the first cut-off mechanism and the second cut-off mechanism, for changing relative phases of rotation of the first cut-off mechanism and the second cut-off mechanism when varying a cut-off length of the web fed from the printing unit.
It is preferable that a scored-line forming mechanism be provided upstream of the first and second cut-off mechanisms, for forming a horizontally scored line in the web at a predetermined position, and it is also preferable that a second relative-phase changer be interposed between the scored-line forming mechanism and the first cut-off mechanism, for changing relative phases of rotation of the scored-line forming mechanism and the first cut-off mechanism when varying a cut-off length of the web fed from the printing unit.
It is preferable that the sheet conveying speed of the processor be faster than that of the first belt conveyor. In this case, the second belt conveyor receives the sheet at a speed approximately equal to the sheet conveying speed of the first belt conveyor, then accelerates the sheet conveying speed to a speed approximately equal to the sheet conveying speed of the processor, then delivers the sheet to the processor at a speed approximately equal to the sheet conveying speed of the processor, and decelerates the sheet conveying speed to the sheet conveying speed of the first belt conveyor and receives a sheet next cut off from the web.
In the case where the processor is used as a discharger for discharging a sheet cut off by the cut-off unit, the sheet can be discharged at an appropriate phase or position. When the processor is used as a folder for folding a sheet cut off by the cut-off unit along a crease perpendicular to a sheet conveying direction, the sheet can be folded at an appropriate phase or position by the folder.
In this case, the aforementioned folder preferably includes a catching cylinder equipped with a catcher, and a folding cylinder equipped with a gripper for holding the sheet and a folding blade for causing the catcher to catch the sheet. The aforementioned folding cylinder is preferably equipped with a first frame that supports the gripper and rotates on an axis of the folding cylinder, a second frame that supports the folding blade and rotates on the axis of the folding cylinder, and a third relative-phase changer for changing relative phases of rotation of the first and second frames.
If the first belt conveyor, the second belt conveyor, the cut-off unit, and the processor are respectively driven by different motors, and a phase of each of the motors can be relatively varied, the speeds of components can be easily adjusted when a cut-off length is varied and the operating phases of components can be easily changed.
The folding machine may further include an abutting portion, provided between the second belt conveyor and the processor, which a front end of the sheet abuts and by which a conveying phase of the sheet in the folder can be adjusted. In this case, the sheet conveying phase in the folder can be properly adjusted.
The folding machine may further include a third belt conveyor, provided downstream of the second belt conveyor and at an entrance portion to the processor, which comprises a pair of conveyor belts for receiving the sheet from the second belt conveyor and conveying the sheet to the processor at the sheet conveying speed of the processor. In this case, the sheet can be delivered from the third belt conveyor to the folder at an equal speed and delivering of the sheet in this area can be stably performed.
The folding machine may further include a non-circular roller, provided at a position where the sheet is delivered from one of the two belt conveyors adjacent to each other to the other of the two belt conveyors, which guides one of a pair of conveyor belts and has a plurality of surface portions in which distances from a center of rotation to the surface portions are different. In this case, delivering of the sheet between two adjacent belt conveyors can be accurately performed.
Furthermore, the conveyor belts of the second belt conveyor may be driven by non-circular rollers having a plurality of surface portions in which distances from a center of rotation to the surface portions are different. In this case, although the non-circular rollers (cam rollers) rotate at a fixed speed, when the conveyor belts are driven by the surface portion in which the distance from the center of rotation is great they can be driven at a relatively high speed, and when the conveyor belts are driven by the surface portion in which the distance from the center of rotation is small, they can be driven at a relatively low speed. Therefore, the sheet conveying speed in the second belt conveyor can be easily varied from a first speed to a second speed.
According to a second folding machine and second variable cut-off length type rotary printing machine of the disclosed embodiment, the folder is constructed of a chopper folder. Therefore, when the printing unit and the cut-off unit are used in a variable cut-off length type rotary printing machine in which a cut-off length of a web can be varied, folding can be appropriately performed according to the cut-off length, if only folding timing is adjusted.
In the cut-off unit, the web is partially cut at a predetermined cut-off length position by the first cut-off mechanism. Thereafter, while the web partially cut by the first cut-off mechanism is being nipped and conveyed, a sheet with a predetermined cut-off length is cut off from the web by cutting uncut portions of the web with the second cut-off mechanism. Therefore, cutting of the web can be performed in a stable state of conveyance, cutting can be easily completed at the required timing, cut-off sheets can be easily conveyed at the required phase timing. As a result, cutting of the web and folding of cut-off sheets along a crease perpendicular to a web traveling direction can be performed with a high degree of accuracy.
a) and 10(b) are schematic diagrams used to explain the principle of a non-circular drive cam roller used in a folding machine for a rotary printing machine constructed in accordance with a third embodiment of the present invention,
a), 12(b), and 12(c) are schematic diagrams used to explain operation of the non-circular drive cam roller;
a) to 13(d) are schematic diagrams used to explain variations of the non-circular drive cam roller;
a) to 18(c) are end views showing the shapes of folded sheets that can be manufactured by the folding machine of the fourth embodiment,
a) and 19(b) are schematic side views showing a folding machine for a rotary printing machine constructed in accordance with a fifth embodiment of the present invention,
a) to 21(c) are schematic diagrams showing the folding cylinder of the folding machine of the fifth embodiment,
Embodiments of the present invention will hereinafter be described with reference to the drawings.
Initially, a first embodiment of the disclosed embodiment will be described.
For example, as shown in
Note that the web conveying speed V0 in the paper feeder part 1, infeed part 2, printing part 3, drying part 4, cooling part 5, web passing part 6, and folding machine 7 is set according to the cut-off length of the web 10. For instance, in making the cut-off length relatively long, the web conveying speed V0 can be set to a relatively high speed. On the other hand, in making the cut-off length relatively short, the web conveying speed V0 can be set to a relatively low speed.
The folding machine 7 of this embodiment is disposed downstream of the drag roller 11 and triangular plate 12 (see
The upstream belt conveyor 51A comprises a pair of endless guide belts (also called conveyor belts or nipping belts) 53a, 53b, which are driven by a plurality of guide rollers 52. The upstream belt conveyor 51A nips the web 10, folded in two and fed by the triangular plate 12, between the guide belts 53a, 53b and conveys it at a speed equal to the upstream web conveying speed V0. Although not shown, each of the guide belts 53a, 53b comprises a plurality of belts disposed parallel to each other in the direction of the width of the web 10.
The first cut-off mechanism 20A is a mechanism for partially cutting the web 10 folded in two at a predetermined cut-off length position and comprises a saw cylinder 21 and a receiving cylinder 22 rotating in opposite directions. The saw cylinder 21 is provided with a saw-blade holder 24 having saw blades 23a in the outer periphery along the axial direction. The receiving cylinder 22 is provided with a rubber bed 25, made of an elastic body such as rubber, for receiving the saw blades 23a. Particularly, as shown in
The middle belt conveyor 54A comprises a pair of endless guide belts (also called conveyor belts or nipping belts) 56a, 56b, which are driven by a plurality of guide rollers 55. The middle belt conveyor 54A nips the web 10, cut at the predetermined cut-off length position in the form of a scored line and fed by the first cut-off mechanism 20A, between the guide belts 56a, 56b and conveys it at a speed equal to the upstream web conveying speed V0. As shown in
The second cut-off mechanism 20B is a mechanism for completing cutting by cutting uncut portions of the web 10, cut at the predetermined cut-off length position in the form of a scored line by the first cut-off mechanism 20A and conveyed by the belt conveyor 54A, and comprises a saw cylinder 21 and a receiving cylinder 22 rotating in opposite directions. The saw cylinder 21 is provided with a saw-blade holder 24 having saw blades 23b in the outer periphery along the axial direction. The receiving cylinder 22 is provided with a rubber bed 25, made of an elastic body such as rubber, for receiving the saw blades 23b. Note that the intermittent cutting phase of the first cut-off mechanism 20A is adjusted to coincide with that of the second cut-off mechanism 20B so that the intermittent cutting positions by the first cut-off mechanism 20A and the intermittent cutting positions by the second cut-off mechanism 20B are on a line when superimposed.
Particularly, as shown in
Thus, in the cut-off unit 50A, the fed web 10 is cut in a horizontal direction (perpendicular to the traveling direction) by the first and second cut-off mechanisms 20A, 20B and a sheet 10a is cut off from the web 10. In the example of this unit, single cutting is performed in one rotation of the saw cylinder 21 and receiving cylinder 22 of the first and second cut-off mechanisms 20A, 20B.
The downstream belt conveyor 57A, disposed downstream of the cut-off unit 50A, comprises a pair of endless guide belts (also called conveyor belts or nipping belts) 59a, 59b, which are driven by a plurality of guide rollers 58a to 58b. The sheet 10a, cut off at the predetermined cut-off length position by the second cut-off mechanism 20B, is nipped between the guide belts 59a and 59b and conveyed to the downstream catching-folding unit 40A from the middle belt conveyor 54. As shown in
In the middle belt conveyor 54A for receiving the sheet 10a, the sheet 10a is conveyed at a speed equal to the web conveying speed V0. In contrast to this, in the catching-folding unit 40A onto which the sheet 10a is delivered, the sheet 10a is conveyed at a speed different from the web conveying speed V0. Because of this, the downstream belt conveyor 57A is constructed as a variable speed belt conveyor or speed change belt conveyor so that the sheet 10a received at the conveying speed V0 is accelerated to a conveying speed Vb and delivered onto the catching-folding unit 40A.
In this embodiment, the middle belt conveyor 54A is equivalent to a first belt conveyor of the disclosed embodiment and the variable speed belt conveyor (downstream belt conveyor) 57A is equivalent to a second belt conveyor of the disclosed embodiment. As set forth above, in the variable speed belt conveyor (downstream belt conveyor) 57A that is the second belt conveyor, the speed in receiving the sheet 10a from the middle belt conveyor 54A (first belt conveyor) is a speed equal to the web conveying speed V0 and then the conveying speed is accelerated and the speed in delivering the sheet 10a onto the folding cylinder 45 of the catching-folding unit 40A is a speed equal to the sheet conveying speed Vb of the folding cylinder 45. In this case, the equal speed contains as light speed difference. That is, in receiving and delivering the sheet 10a, it is preferable to make the speed difference smaller, but if an error in the phase of conveying the sheet 10a, caused by a speed difference at the time of delivery, is within an allowable limit, such a speed difference is allowable. The same applies to the following second, third, and fifth embodiments.
In the variable speed belt conveyor 57A of this embodiment, the lower roller 58c of the guide belt 59a is a speed change roller for changing the speed of the guide belts 59a, 59b. By changing the speed of rotation of the speed change roller 58c, the speed of the guide belts 59a, 59b can be changed.
Note that in the downstream belt conveyor 57A, a pair of guide belts 59a, 59b are asymmetrically constructed such that the direction of the sheet 10a vertically conveyed by the cut-off unit 50A is changed to a horizontal direction according to the position of the catching-folding unit 40A. That is, while the guide belt 59a is guided and rotated mainly by an upper guide roller 58a and a lower guide roller 58c, the guide belt 59b is guided and rotated by the guide roller 58c through the guide belt 59a in addition to an upper guide roller 58b and lower guide rollers 58f, 58g. With this arrangement, the path of conveyance of the sheet 10a is changed at the guide roller 58c from the vertical direction to the horizontal direction where the catching-folding unit 40A is disposed.
The guide rollers 58a, 58b, disposed opposite each other, of the entrance portion of the downstream belt conveyor 57A are switched between sheet releasing positions indicated by solid lines and sheet nipping positions indicated by dashed lines, according to the speed of rotation of the speed change roller 58c. That is, when the sheet 10a is being conveyed at a speed higher than the web conveying speed by the downstream belt conveyor 57A, the guide rollers 58a, 58b are held in the sheet releasing positions. When the sheet 10a is being conveyed at a speed equal to the web conveying speed by the downstream belt conveyor 57A, the guide rollers 58a, 58b are held in the sheet nipping positions. This can prevent the occurrence of a speed difference at the time of the delivery of the sheet 10a from the middle belt conveyor 54A to the downstream belt conveyor 57A, so that the sheet 10a can be smoothly delivered without hindrance.
In this embodiment, the conveying speed V by the downstream belt conveyor 57A is changed during sheet conveyance, as shown in
The catching-folding unit 40A, as with the conventional example, comprises a catching cylinder 42 equipped with catchers 41, and a folding cylinder 45 equipped with gripper tools (herein after referred to simply as grippers) 43 and folding blades 44. The front end of the sheet 10a fed through the variable speed belt conveyor 57A is gripped by the grippers 43, and when the sheet 10a is being rotated and transferred, the folding blade 44 of the folding cylinder 45 engages with the catcher 41 of the catching cylinder 42. At the position of the engagement, the sheet 10a transferred to the catcher 41 is folded along a crease perpendicular to the conveying direction. In this embodiment, the surface of the sheet 10a delivered from the downstream belt conveyor 57A onto the folding cylinder 45 is opposite to the conventional example (
In the catching-folding unit 40A illustrated in
The paper discharge belt conveyor 46, as with the conventional example, is constructed such that the folded sheets 10b formed as described above are transferred to the subsequent steps, that is, a sheet alignment stacker 80 (not shown), etc. For instance, as shown in
The rotary printing machine in this embodiment, as with the conventional example, is constructed as a variable cut-off length type rotary printing machine that can vary the cut-off length of the web 10 by changing the outside diameter of the first and second cut-off mechanisms 20A, 20B as in a printing cylinder (e.g., a plate cylinder or blanket cylinder) of the printing part 4.
Therefore, as set forth above, in the folding machine 7, the cut-off length C is given as
C=Vo/(Nc·n)
where Vo is the traveling speed (conveying speed) of the web, Nc is the number of rotations of the saw cylinder, and n is the number of saw blades.
The cut-off sheet 10a is accelerated from the traveling speed of the web 10 to the speed Vb of the folding cylinder 45 and transferred onto the folding cylinder 45. Next, it is delivered to the gripper 43 of the folding cylinder 45 and catching and folding are carried out.
The folding machine according to the first embodiment of the disclosed embodiment is constructed as described above. Therefore, in the cut-off unit 50A, the web 10 fed at the predetermined web conveying speed Vo by the upstream belt conveyor 51A is intermittently cut in the form of a scored line at a predetermined cut-off length position by the first cut-off mechanism 20A. Thereafter, the web 10 is fed into the middle belt conveyor 54A, and when the web is being conveyed at the same speed as the web conveying speed Vo, the uncut portions of the web 10 are intermittently cut by the second cut-off mechanism 20B. In this manner, each sheet 10a is cut off from the web 10.
The cut-off sheet 10a is nipped by the middle belt conveyor 54A and transferred at the same speed as the web conveying speed Vo and is delivered to the downstream belt conveyor 57A. In receiving the sheet 10a by the downstream belt conveyor 57A, the guide rollers 58a, 58b in the entrance portion are held in the sheet nipping positions and operate at the same speed as the web conveying speed Vo. After the sheet 10a is received, the guide rollers 58a, 58b in the entrance portion are held in the sheet releasing positions, and the guide belts (speed change belts) 59a, 59b and the speed change roller 58c are accelerated to the sheet conveying speed Vb of the folding cylinder 45 by ΔV. After the sheet 10a is delivered to the gripper 43 of the folding cylinder 45 at the sheet conveying speed Vb, the speed Vb is returned to the original speed Vo.
If the sheet conveying speed becomes equal to the speed Vo, the guide rollers 58a, 58b in the entrance portion are held in the sheet nipping positions and the next sheet 10a is fed between the guide belts 59a, 59b of the downstream belt conveyor 57A. Like operations will hereinafter be repeated.
Note that a pattern of speed changes (Vo+ΔV), in addition to a speed change indicated by a solid line in
Since the folding machine of this embodiment is constructed as described above, it has the two following advantages:
(1) Since the sheet 10a is conveyed while it is being nipped by any one of the upstream, middle, and downstream belt conveyors 51A, 54A, and 57A, slippage of the sheet 1a is less liable to occur during conveyance and the sheet 10a can be delivered onto the folding cylinder 45 at accurate timing. Therefore, in addition to ensuring stable accuracy of folding, printed surfaces have no stain.
(2) The cut-off length of a web can be varied by varying the web conveying speed Vo and adjusting the speed change pattern of the speed change roller 58c and speed change belts 59a, 59b. This makes a large-capacity phase changer for a cylinder drive unit unnecessary. Therefore, in addition to a reduction in the space for the drive part, operations can be easily controlled and print quality becomes stable.
Note that a structure for varying the length of travel of each of the speed change belts 59a, 59b may be constructed so that it can cope with a variation in a phase due to a variation in the cut-off length of the web 10.
It is also possible to omit phase change rollers, and in addition to the illustrated belt layout, various belt layouts are possible.
Next, a second embodiment of the disclosed embodiment will be described.
The folding machine 7 of this embodiment is disposed downstream of the drag roller 11 and triangular plate 12 (see
The upstream belt conveyor 51B comprises a pair of guide belts (also called nipping belts) 53c, 53d disposed opposite each other. The middle belt conveyor 54B comprises a pair of guide belts (also called nipping belts) 56c, 56d disposed opposite each other. The downstream belt conveyor 57B comprises a pair of guide belts (also called nipping belts) 59c, 59d disposed opposite each other. Each of the guide belts 53c, 53d, 56c, 56d, 59c, and 59d comprises a plurality of guide belts having a predetermined width or less and arranged parallel to each other. As with the first embodiment, the guide belts between the belt conveyors adjacent to each other in the web conveying direction are shifted in the width direction so that they do not interfere with each other. In the second embodiment, the upstream belt conveyor 51B is disposed between the upstream and downstream sides of the first cut-off unit 20A so that the first cut-off unit 20A is able to cut the web 10 that is held and conveyed by the upstream belt conveyor 51B.
Therefore, in this embodiment, the upstream belt conveyor 51B, first cut-off mechanism 20A, middle belt conveyor 54B, and second cut-off mechanism 20B constitute a cut-off unit 50B for cutting off a sheet 10a with a predetermined cut-off length from the web 10.
The upstream belt conveyor 51B nips the web 10 between guide belts 53c, 53d and conveys it at a speed equal to the upstream web conveying speed V0. Similarly, the middle belt conveyor 54B nips the web 10 between guide belts 56c, 56d and conveys it at a speed equal to the upstream web conveying speed V0.
In this embodiment, the downstream guide roller 52 of the upstream belt conveyor 51B and the upstream guide roller 55 of the middle belt conveyor 54B are coaxially disposed. Each of the guide belts 53c, 53d of the upstream belt conveyor 51B comprises a plurality of belts, regulated in width, which pass between the saw blades 23a of the first cut-off mechanism 20A and are disposed so that they do not interfere with the saw blades 23a.
Each of the guide belts shown in
In the cut-off unit 50B, a sheet 10a with a predetermined cut-off length is cut off from the web 10 by intermittently cutting the web 10 with the first cut-off mechanism 20A and intermittently cutting the uncut portions of the web 10 with the second cut-off mechanism 20B.
The downstream belt conveyor 57B disposed downstream of the cut-off unit 50B receives the sheet 10a at the conveying speed V0, accelerates it from the conveying speed V0 to a conveying speed Vb, and delivers it to the downstream side. Thus, the downstream belt conveyor 57B is constructed as a variable speed belt conveyor.
Elements peculiar to this embodiment, as shown in
The bottom belt conveyor 60 comprises a pair of endless guide belts (conveyor belts) 62a, 62b, which are driven by a drive roller 61a and a plurality of guide rollers 61. The sheet 10a with a predetermined cut-off length, cut off by the cut-off units 20A, 20B and fed by the downstream belt conveyor 57B, is nipped between the guide belts 62a, 62b and it is conveyed at the conveying speed Vb and delivered to the catching-folding unit 40A.
In this embodiment, the downstream belt conveyor 57B conveys the sheet 10a linearly, but in the bottom belt conveyor 60, the guide belts 62a, 62b are asymmetrically constructed for the purpose of changing the direction of the vertically conveyed sheet 10a toward the catching-folding unit 40A horizontally. That is, the path of conveyance of the sheet 10a, which comprises the guide belts 62a, 62b, is formed by the downstream drive roller 62a so that the direction thereof is changed around the drive roller 62a from the vertical direction to the horizontal direction where the catching-folding unit 40A is disposed.
The positioning cylinder 63 is provided in the entrance portion of the bottom belt conveyor 60 that conveys the sheet 10a at the conveying speed Vb approximately equal to that of the catching-folding unit 40A, and has a stopper 63a that the front end of the sheet 10a abuts.
The nip roller 64 is provided on the reverse side of the guide belt 56c of the middle belt conveyor 54B. In this embodiment, the upstream guide roller 58 for guiding the guide belt 59d of the downstream belt conveyor 57B is disposed in the central portion of the middle belt conveyor 54B, and the nip roller 64 is disposed near the upstream guide roller 58. The nip roller 64 is pressed against the guide belt 59c to produce nip pressure between the guide belts 56c, 56d and between the guide belts 56, 59d so that the sheet 10a is reliably nipped.
In each of the cam rollers 65a, 65b, 66, 67, and 68, a plurality of surface portions, in which distances from the center of rotation to the outer peripheral surfaces are different, are smoothly continuous and pressure applied to a belt varies according to the outer peripheral surface that the belt abuts. Operations of the cam rollers 65a, 65b, 66, 67, and 68 will be described later.
Next, a description will be given of how each part is driven. A first motor (not shown) drives the folding cylinder 45, positioning roller 63, cam rollers 65a, 65b, 66, 67, and 68, bottom belt conveyor 60 (high-speed conveyor belts 62a, 62b); a second motor (not shown) drives the downstream belt conveyor 57B (speed change conveyor belts 59c, 59d); a third motor (not shown) drives the first and second saw cylinders 21, 21 (between them, there is a mechanical phase adjustment mechanism for making a phase adjustment when changing the cut-off length of a web); and a fourth motor (not shown) drives the upstream belt conveyor 51B and middle belt conveyor 54B (low-speed conveyor belt) at a speed of rotation corresponding to a web conveying speed. Thus, the parts are driven by individual motors, respectively. Therefore, the phase adjustment and speed change between units required when changing the cut-off length of a web can be easily performed without an intricate differential mechanism, etc.
Note that each of the cam rollers 65a, 65b, 66, 67, and 68 is forcibly driven to make one rotation when the saw cylinder makes one rotation.
The folding machine in the second embodiment of the disclosed embodiment is constructed as described above and the cut-off unit 50B performs intermittent cutting in two stages, as with the first embodiment. Thus, the second embodiment can obtain the same advantages as the first embodiment.
Particularly, this embodiment is characterized by the cam rollers 65a, 65b, 66, 67, and 68 and positioning roller 63, so a description will be give of the operations of the cam rollers 65a, 65b, 66, 67, and 68 and the positioning operation of the positioning cylinder 63.
As basic operations, a sheet 10a with a predetermined length is cut off by the saw cylinders 21 of the first and second cut-off mechanisms 20A and 20B, with the web 10 held by the low-speed conveyor belts of the upstream belt conveyor 51B and middle belt conveyor 54B, and the cut-off sheet 10a is further conveyed by the middle belt conveyor 54B and advances into the nipping area where the sheet 10a is nipped between the speed change belts 59c, 59d of the downstream belt conveyor 57B. In the downstream belt conveyor 57B, the nipped sheet 10a is accelerated to the speed of the high-speed belts 62a, 62b of the bottom belt conveyor 60. After being accelerated, the sheet 10a advances into the nipping area where the sheet 10a is nipped between the high-speed belts 62a, 62b of the bottom belt conveyor 60, and is supplied to the folding cylinder 45.
In the aforementioned basic operations, as shown in
As shown in
Thereafter, the sheet 10a is nipped between the speed change conveyor belts 59c, 59d pushed down by the large-radius portions of the cam rollers 65b, 66 and is gradually accelerated to the same speed as that of the high-speed conveyor belts 62a, 62b.
Before the speed change conveyor belts 59c, 59d start acceleration, the low-speed conveyor belt 56c is in contact with the small-radius portion of the cam roller 65a and away from the low-speed conveyor belt 56d. Therefore, a difference in speed has no influence on the speed of the sheet 10a.
As shown in
Thereafter, the front end of the sheet 10a abuts the stopper 63a of the positioning cylinder rotating at a speed slightly lower than the sheet 10a. By further advancing the rear end portion of the sheet 10a with the front end abutting the stopper 63a, the position and inclination of the front end portion of the sheet 10a can be corrected with the stopper 63a of the positioning cylinder 63 as reference.
The slack of the cut-off sheet 10a produced during correction is absorbed in the space between the belts, as shown in
Thereafter, as shown in
Thus, by controlling the individual cam rollers in the aforementioned manner, the sheet 10a can be reliably delivered without slippage during conveyance in which speed changes take place. In addition, the phase of the sheet 10a can be appropriately adjusted by the stopper 63a of the positioning cylinder 63.
Next, a third embodiment of the disclosed embodiment will be described.
In this embodiment, attention is paid to the drive system for the speed change conveyor belts 59c, 59d used in the downstream belt conveyor of the first and second embodiments, and the periodic speed modulation of a speed change conveyor belt is performed without controlling the speed of a drive source such as a motor, etc. More specifically, the periodic speed modulation of a speed change conveyor belt can be realized without changing the speed of a drive source, using a non-circular drive roller (also referred to as a drive cam roller).
That is, as shown in
If the speed change conveyor belt is driven by employing this principle, the speed can be increased or decreased within one rotation of the drive roller.
In addition, if a ratio of the large-radius portion 71 and the small-radius portion 72 is varied, a ratio of a high speed and a low speed during one rotation of the drive roller can be varied to some degree.
Furthermore, as shown in
In the case of driving a belt by the roller 70 having the large-radius portion 71 and small-radius portion 72, the entire length of the belt system will vary because the length of the belt wound around the roller varies depending on the radius. Because of this, a device for absorbing a variation in the belt length becomes necessary.
Hence, as shown in
When the radius of the small-radius portion is varied, the entire belt length similarly varies. In this case, if a device, which absorbs variations with a spring or an air cylinder, is disposed somewhere in the belt system, a temporal variation immediately after the radius change can be absorbed.
As shown in
In the case where the small-radius portion 72 is formed from a block, the number of blocks is not limited to one block. The small-radius portion 72 may be formed from a plurality of blocks.
Next, a fourth embodiment of the disclosed embodiment will be described.
The folding machine 7 of this embodiment is disposed downstream of the drag roller 11 and triangular plate 12 (see
The upstream belt conveyor 51B comprises a pair of guide belts (nipping belts) 53a, 53b disposed opposite each other. The middle belt conveyor 75 comprises a pair of guide belts (nipping belts) 77a, 77b disposed opposite each other. Each of these guide belts 53a, 53b, 77a, and 77b comprises a plurality of belts disposed parallel to each other.
The middle belt conveyor 75 is equipped with a pair of endless guide belts (conveyor belts) 77a, 77b for conveying the web 10 from which a sheet 10a is cut off by the second cut-off unit 20B and also conveying the sheet 10a, and a pair of endless belts (conveyor belts) 77a, 77c operating on the downstream side of the chopper-folder 79. The conveyor belt 77a has the function of conveying the web 10 before and after the second cut-off mechanism 20B and the sheet 10a cut off from the web 10 in cooperation with the conveyor belt 77b, and the function of conveying the sheet 10a after chopper folding from the chopper-folder 79 in cooperation with the conveyor belt 77c. The conveyor belt 77a is guided by guide rollers 76, 76a, and 78a; the conveyor belt 77b is guided by guide rollers 76, 77b; and the conveyor belt 77c is guided by guide rollers 76a, 78b. The guide belt 77c, as with the guide belts 77a, 77b, comprises a plurality of belts disposed in parallel.
The chopper-folder 79, as shown in
Note that there is a gap between the conveyor belts 77a and 77c so that prior to chopper folding, the front end of the sheet 10a can be easily inserted between the conveyor belts 77a and 77c.
A drive source for the chopper-folding blade 79a employs an individual motor, so the timing at which the chopper-folding blade 79a is laterally moved can be freely set.
In this embodiment constructed as describe above, the chopper-folding blade 79a is operated according to the timing according to the cut-off length of the sheet 10a. The sheet 10a being transferred is inserted between the folding rollers 78a, 78b provided in the entrance portion of the conveyor belts 77a, 77c, and is folded in a direction perpendicular to the moving direction of the sheet 10a. A folded sheet 10b from the folding rollers 78a, 78b is inserted between the conveyor belts 77a, 77c and is nipped and conveyed.
In
θ=2π·Nr·t=Vo·t/r
where Vo is the traveling speed (conveying speed) of the sheet 10a, Nr is the number of rotations of the folding rollers 78a, 78b, t is the operating time, and r is the roller radius.
If the lateral or horizontal movement (timing at which the chopper-folding blade 79a is operated) of the chopper-folder 79 is controlled so that the lateral or horizontal movement S of the front end of the chopper-folding blade 79a becomes S=r·(sin θ+cos θ−1)/cos θ, the conveyed sheet 10a is properly folded without loosening.
This embodiment functions as described above and can obtain the following advantages:
(1) Since the sheet 10a is always nipped and conveyed between conveyor belts, there is no slippage, catching and folding can be performed at accurate timing, stable accuracy of folding can be ensured, and printed surfaces have no stain;
(2) Since the speed of conveyor belts and chopper-folding operation do not change even if a cut-off length varies, the relative positions of the sheet 10a and the front end of the chopper-folding blade 79a do not change and a variation in the position of the folding line is slight, so that accuracy of folding is stable;
(3) The cycle and operating timing of the chopper-folding blade 79a can be easily changed and the required time at the time of the cut-off length or lap width change can be shortened; and
(4) Compared with the conventional folding machine, the number of waste papers at the time of the cut-off length or lap width change can be reduced, and the folding machine of the disclosed embodiment is structurally simple, so the manufacturing costs can be considerably reduced.
If the operating timing of the chopper-folding blade 79 is varied without varying a cut-off length, not only can the lap width be varied as shown in
Next, a fifth embodiment of the disclosed embodiment will be described.
The folding machine 7 of this embodiment, as with the aforementioned embodiments, is disposed downstream of the drag roller 11 and triangular plate 12 (see
The upstream belt conveyor 51C comprises a pair of guide belts (nipping belts) 53e, 53f disposed opposite each other. The downstream belt conveyor 57C comprises a pair of guide belts 59e, 59f disposed opposite each other. Each of the guide belts 53e, 53f, 59e, and 59f comprises a plurality of guide belts having a predetermined width or less and arranged parallel to each other.
Within the web conveying area of the upstream belt conveyor 51C, there are provided a first cut-off mechanism 20A and a second cut-off mechanism 20B, which are approximately the same as those of the first embodiment. The upstream belt conveyor 51C, first cut-off mechanism 20A, and second cut-off mechanism 20B constitute a cut-off unit 50C for cutting off a sheet with a predetermined length from a web 10.
The cut-off unit 50C is equipped with components peculiar to the variable cut-off length type rotary printing machine. A catching-folding unit 90, as with the first embodiment, is provided downstream of the downstream belt conveyor 57C, but in this embodiment, it is equipped with components peculiar to the variable cut-off length type rotary printing machine.
First, the upstream belt conveyor 51C nips a web 10 between the guide belts (nipping belts) 53e, 53f and conveys it at a speed equal to the upstream web conveying speed V0. These guide belts 53e, 53f are endless belts that are guided and driven by a plurality of guide rollers 52 and nip the web 10 while applying nip pressure to both surfaces of the web 10. Upstream of these guide belts 53e, 53f and in the vicinity of them, nipping rollers 14a, 14b are disposed to nip the web 10, and the nipped web 10 is conveyed at a speed equal to the upstream web conveying speed V0.
The nipping rollers 14a, 14b and guide belts 53e, 53f are together driven by a nipping roller drive motor and a belt drive motor 85d (hereinafter referred to simply as a motor M4). The motor M4 can employ, for example, shaftless motors. With this motor M4, the peripheral speed of the nipping rollers 14a, 14b and the traveling speed of the guide belts 53e, 53f are made equal to the web conveying speed V0.
Within the web conveying area of the upstream belt conveyor 51C and upstream of the cut-off unit 50C, a scored-line forming mechanism 84 is disposed near the first cut-off mechanism 20A. The scored-line forming mechanism 84 is used to form a horizontally scored line in an uncut web 10 folded in two at a predetermined position and comprises a scored-line cylinder 84A and a receiving cylinder 84B disposed opposite each other and rotating synchronously. The scored-line cylinder 84A is provided with a comb-blade holder (not shown) having comb blades 84a in the outer periphery along the axial direction. The receiving cylinder 84B is provided with a rubber bed 25, made of an elastic body such as rubber, for receiving the comb blades 84a.
The scored-line cylinder 84A, saw cylinder 22a of the first cut-off mechanism 20A, and saw cylinder 22b of the second cut-off mechanism 20B are together driven by shaftless motors 85c (also referred to as a motor M3). With this motor M3, the scored-line cylinder 84A, saw cylinders 22a, 22b are driven to rotate synchronously with each other.
A first phase changer 86A is interposed between the scored-line cylinder 84A and the saw cylinder 22a, and a second phase changer 86B is interposed between the saw cylinders 22a, 22b. In this embodiment, the scored-line cylinder 84A is driven directly by the shaftless motor 85c (motor M3), the rotational shaft of the scored-line cylinder 84A and the rotational shaft of the saw cylinder 22a are connected together by a first power transmission mechanism (e.g., a gear mechanism in this embodiment) 86A, and the power transmission mechanism 86A is provided with a phase changer 89A. Similarly, the rotational shaft of the saw cylinder 22a and the rotational shaft of the saw cylinder 22b are connected together by a second power transmission mechanism (e.g., a gear mechanism in this embodiment) 86B, which is provided with a phase changer 89B.
With this construction, the scored-line cylinder 84A is driven by the shaftless motor 85c (motor M3) so that in a phase state corresponding to a web printing position, the speed the blades 84a becomes equal to the web conveying speed V0. The saw cylinder 22a is rotated in synchronization with the scored-line cylinder 84A by the first power transmission mechanism 86A, and the saw cylinder 22b is rotated in synchronization with the saw cylinder 22a by the second power transmission mechanism 86B. At this time, the phases of the scored-line cylinder and saw cylinder 22a are properly adjusted by the phase changer 89A so that a relative phase corresponding to a cut-off length is obtained. Likewise, the phases of the saw cylinders 22a, 22b are properly adjusted by the phase changer 89B so that a relative phase corresponding to a cut-off length is obtained.
The power transmission mechanisms 86A, 86B and phase changers 89A, 89B will be further described with the power transmission mechanism 86B and phase changer 89B as examples. As shown in
The phase changer 89B is equipped with a gear 89a meshing with the gear 88a, a gear 89b meshing with the gear 88b, a differential gear (DFG) 89c for changing the phases of rotation of these gears 89a, 89b, and a servo motor 89d (motor m2) for driving the differential shaft of the differential gear 89c.
The differential gear 89c is not shown in detail, but in the case of a differential gear employing a planetary gear, it is equipped with an input internal gear rotating integrally with the input gear 89a, an output internal gear rotating integrally with the output gear 89b, and a planetary gear meshing with the input and output internal gears. The planetary gear is rotatably installed on a differential shaft that is an eccentric rotational shaft with respect to the axes of rotation of the gears 89a, 89b, the input internal gear, and the output internal gear.
If the number of teeth of the input internal gear is represented by z2 and the number of teeth of the output internal gear is represented by z3, the number of rotations of the output internal gear is z2/z3 in one rotation of the input internal gear. If the number of teeth of each of the gears 88a, 88b is Z1, the number of teeth of the gear 89a is Z2, and the number of teeth of the gear 89b is Z3 (where Z2/Z3=z2/z3), when the number of rotations of the saw cylinder 22a (rotational shaft 87a) is N1 the number of rotations of the gear 89a and the input internal gear is N1×(Z1/Z2), the number of rotations of the output internal gear and the gear 89b is N1×(Z1/Z2)×(Z2/Z3), and the number of rotations of the saw cylinder 22b (rotational shaft 87b) is N1×(Z1/Z2)×(Z2/Z3)×(Z3/Z1)=N1.
Thus, even if the number of teeth (z2) of the input internal gear is differentiated from that (z3) of the output internal gear, the saw cylinder 22a and the saw cylinder 22b rotate at the same speed. However, if the differential shaft (eccentric shaft) supporting the planetary gear is rotated, the input internal gear and the output internal gear rotate relatively according to the rotation. Therefore, for example, if the planetary gear makes one revolution on the axis of rotation of the input and output internal gears, the number of rotations of the output internal gear is 1−(Z2/Z3) with respect to the input internal gear.
Thus, if the input internal gear and the output internal gear rotate relatively, relative phases of the gears 89a, 89b are adjusted, and consequently, relative phases of the saw cylinder 22a (rotational shaft 87a) and the saw cylinder 22b (rotational shaft 87b) are adjusted.
Although not shown, the power transmission mechanism 86A and phase changer 89A are constructed the same as the aforementioned power transmission mechanism 86B and phase changer 89B.
Next, the downstream belt conveyor 57C will be described. As shown in
That is, in the downstream belt conveyor 57C, the sheet 10a, conveyed at a speed equal to the web conveying speed V0 by the upstream belt conveyor 51C and cut off so as to have a predetermined cut-off length, is fed between the guide belts 59e, 59f, and while the sheet 10a is being nipped between the guide belts 53e, 53f of the upstream belt conveyor 51C, the guide belts 59e, 59f conveys the sheet 10a at a speed equal to the web conveying speed V0, as with the guide belts 53e, 53f. After the sheet 10a is released between the guide belts 53e, 53f, it is accelerated according to the cut-off length thereof so that there is an appropriate distance between sheets 10a. Finally, the sheet 10a is accelerated to a speed that synchronizes with the peripheral speed of the downstream catching-folding unit 90, and the sheet 10a is delivered onto the catching-folding unit 90. Note that the guide belts 59e, 59f are driven by a shaftless motor 85b (motor M2).
As shown in
In the catching-folding unit 90 illustrated in
The folding cylinder 95 and catching cylinder 92 are rotated and driven synchronously with each other by a shaftless motor 85a (motor M1). As with the aforementioned power transmission mechanisms 86A, 86B, a similar power transmission mechanism is interposed between the folding cylinder 95 and the catching cylinder 92. The folding cylinder is driven directly by the shaftless motor 85a and the catching cylinder 92 is driven by the shaftless motor 85a through the power transmission mechanism.
In the folding cylinder 95, the relative positions of the gripper 93 and folding blade 94 need to be adjusted according to the cut-off length of the sheet 10a. Hence, as shown in
As shown in
The relative positions of rotation (relative phases) of the first shell portion 96 and second shell portion 97 are changed by a phase changer 99.
This phase changer 99, as shown in
The phase changer 99 is equipped with a gear 99a meshing with the gear 98a, a gear 99b meshing with the gear 98b, a differential gear (DFG) 99c for changing the phases of rotation of these gears 99a, 99b, and a servo motor 99d (motor m3) for driving the differential shaft of the differential gear 99c.
The differential gear 99c can be constructed the same as the aforementioned differential gear 89c, so it is not illustrated in detail.
The folding machine of the fifth embodiment of the disclosed embodiment is constructed as described above and therefore can obtain the same advantages as the first embodiment by the cut-off unit 50C in which the sheet 10a is cut off in two stages from the web 10.
Particularly, in this embodiment, the horizontally scored position by the scored-line forming mechanism 84, the first cut-off length position by the first cut-off mechanism 20A, and the second cut-off length position by the second cut-off mechanism 20B are relatively adjusted according to the cut-off length of the sheet 10a by the phase changers 89A, 89B, and the relative positions of the grippers 93 and the folding blades 94 are adjusted according to the cut-off length by the phase changer 99.
Therefore, for instance, in the case where the cut-off length is relatively short, the motors m1, m2, and m3 are operated so that as shown in
While this embodiment is equipped with the scored-line forming mechanism 84, it may be omitted. In this case, the first power transmission mechanism 86A and phase changer 89A may be omitted. For instance, the shaftless motor 85c (motor M3) may be constructed to directly drive the saw cylinder 22a of the first cut-off mechanism 20A; the rotational shaft of the saw cylinder 22a and the rotational shaft of the saw cylinder 22b may be connected together by the second power transmission mechanism 86B; and the phase changer 89B may be provided in the second power transmission mechanism 86B.
While the disclosed embodiment has been described with reference to the preferred embodiments thereof, the invention is not to be limited to the details given herein, but may be modified within the scope of the invention hereinafter claimed.
For example, in the aforementioned first, second, and third embodiments, the catching-folding unit 40A, 90 has been explained as a processor for processing sheets cut off from a web. However, the folder is not limited to the catching-folding unit, but is applicable to various machines. The processor for processing sheets cut off from a web is not limited to the folder, but is applicable to various units such as a discharger for discharging the cut-off sheets outside the printing machine.
The disclosed embodiment can be suitably used in a folder that is a processor for processing sheets cut off from a web. However, the disclosed embodiment is not limited to the folder, but is applicable to various units such as a discharger for discharging the cut-off sheets outside the printing machine.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2003-415124 | Dec 2003 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2004/018294 | 12/8/2004 | WO | 00 | 3/8/2006 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2005/056451 | 6/23/2005 | WO | A |
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| Number | Date | Country | |
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| 20070018373 A1 | Jan 2007 | US |
