JP2002154745A - Chopper folding device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To elevate a blade straight by using a mechanism with the simple structure having high reliability in a chopper folding device. SOLUTION: A sun gear 12 is arranged at the center of rotation 10a of a first link arm 10, and an epicyclic gear 13 integrated with a second link arm 11 engaged with the sun gear 12 and to be rotated around the periphery of the sun gear 12 is arranged at the center of rotation 11a of the second link arm 11. A blade is suspended at the other end 11b of the second link arm 11. A rotating direction of the sun gear 12 and a revolving direction of the epicyclic gear 13 are set in the same direction, and in case of setting a ratio of a diameter of the sun gear 12 to that of the epicyclic gear 13 at n:1, a ratio of a rotating angular velocity of the sun gear 12 to that of the revolving angular velocity of the epicyclic gear 13 is set at (n+2)/n:1.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a chopper folding device for vertically folding a signature that proceeds along a horizontal plane into two along the traveling direction.

[0002]

2. Description of the Related Art FIG. 11 is a schematic view showing a configuration of a conventional chopper folding device of a general folding machine. As shown in FIG. 11, the folding machine includes a plurality of upper conveying belts 2 divided above the conveying line of the signature 1, and a plurality of upper conveying belts 2 corresponding to the upper conveying belt 2 below the conveying line of the signature 1. It has a separate lower conveyor belt 3. The upper and lower transport belts 2 and 3 run at a constant speed (in a direction perpendicular to the paper surface), and the signature 1 is transferred to the chopper folding device 80 while being sandwiched between the upper and lower transport belts 2 and 3. It is designed to be transported.

[0003] A conventional chopper folding device 80 comprises a blade 81 arranged parallel to the traveling direction of the signature 1 and a blade 8.
1 and an oscillating mechanism 83 for oscillating the arm 82. Blade 81 is arm 82
The arm 82 has a rear end thereof rotatably attached to a machine frame 87. The swing mechanism 83 includes a first crank 84 having one end fixed to the crankshaft 84a, a second crank 85 having one end rotatably attached to the other end of the first crank 84, and a second crank 85 And a third crank 86 fixed at the rear end of the arm 82 at the other end. With such a configuration, when the crankshaft 84a rotates in a predetermined direction, the arm 82 integrated with the third crank 86 swings about the swing center 82a, and the blade fixed to the distal end of the arm 82 is fixed. 81
Is going up and down while drawing an arc up and down.

The conventional chopper folding device 80 synchronizes the rotational speed of the crankshaft 84a with the traveling speed of the upper and lower conveyor belts 2 and 3 so that the rising and lowering timing of the blade 81 is adjusted to the conveying timing of the signature 1. ing. When the signature 1 is conveyed to a position immediately below the blade 81 and positioned by a stopper (not shown), the blade 81 is moved to a pair of rotating rollers 7, 7 parallel to the traveling direction of the signature 1 disposed below the table 6. By swinging the signature down, the signature 1 is folded vertically in two along the direction of travel.

[0005]

The problem of the conventional chopper folding device 80 is that the blade 81 is supported by the arm 82. That is, the arm 82 supporting the blade 81 is required to have strength, but the weight increases at the same time to satisfy the strength. Therefore, the blade 8
In order to raise and lower the arm 1, the arm 82 having a large overhang and heavy weight must be swung, and a large power corresponding to the magnitude of the inertia of the arm 82 is required during operation. Further, since the overhang of the arm 82 is large, when the blade 81 is overloaded, the arm 82 may be broken. In particular, at the time of high-speed operation, since the elevating speed of the blade 81 is high, there is a high possibility that the arm 52 may be broken due to overload.

[0006] In order to solve the above problem, there is a technique in which the blade is raised and lowered in a vertical direction (ie, vertical direction) with respect to a table using rotation of a gear or the like, instead of raising and lowering the blade by swinging an arm. Various proposals have been made for some time. For example, in Japanese Patent Publication No. 59-26577, as shown in FIG.
A planetary gear 91 having a diameter of half of 0 is meshed with the planetary gear 91, and the planetary gear 91 is rotated inside the ring gear 90, so that a support member 92 integrally fixed to the planetary gear 91 is formed.
A technique is disclosed in which the tip of the support member 92 is moved in the vertical direction, and the blade 93 suspended from the tip of the support member 92 is moved up and down.

In Japanese Utility Model Laid-Open No. 5-64168,
As shown in FIG. 13, the stationary sun gear 95 and sun gear 9
5 between the planetary gear 97 and the intermediate gear 96
To rotate the planetary gear 97 in the direction opposite to the revolving direction, thereby moving the distal end of the support member 98 integrally fixed to the planetary gear 97 in the vertical direction, There is disclosed a technique in which a blade 99 suspended from a portion is vertically moved up and down.

Further, Japanese Utility Model Laid-Open No. 4-96463 discloses that a stationary sun gear 100 and a planetary gear 102 revolving around the sun gear 100 are connected via a toothed belt 101 as shown in FIG. By the planetary gear 1
02 is rotated in the direction opposite to the revolving direction, whereby the distal end of the support member 103 integrally fixed to the planetary gear 102 is moved in the vertical direction, and the blade 104 suspended from the distal end of the support member 103 is moved. There has been disclosed a technique for vertically moving up and down.

[0009] Each of these techniques uses the blades 93, 9
Only the actuators 9, 104 are moved up and down linearly in the vertical direction. Therefore, there is no need to swing the arm 82 having a large inertia as in the conventional chopper folding device 80. Can withstand enough. However, any of the above techniques has some problems as described below, and there is still room for improvement.

In other words, the technology disclosed in Japanese Patent Publication No. 59-26577 uses a ring gear 90 as a constituent element, but an internal gear such as the ring gear 90 is processed more easily than an external gear. There is a problem that it is difficult, processing cost is high, and processing accuracy is difficult. In addition,
The technology disclosed in Japanese Patent No. 64168 does not have the problem of the technology disclosed in Japanese Patent Publication No. 59-26577 because only the external gear is used. However, the presence of the intermediate gear 96 causes imbalance during rotation. High-speed stability may be reduced. Also, the provision of the intermediate gear 96 complicates the component configuration. Further, the technology disclosed in Japanese Utility Model Laid-Open No. 4-96463 is a technology in which the intermediate gear 96 in the technology described in Japanese Utility Model Application Laid-Open No. 5-64168 is replaced with a toothed belt 101. There is a problem that reliability is somewhat lacking, such as a change in tension.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and provides a chopper folding apparatus which has a simple component configuration and enables a blade to linearly move up and down by a highly reliable mechanism. The purpose is to:

[0012]

In order to achieve the above object, a chopper folding apparatus according to the present invention is configured as follows. That is, the chopper folding device of the present invention comprises a first link arm rotatable around one end and a second link arm having the same length as the first link arm and one end rotatably connected to the other end of the first link arm. A link mechanism having a link arm, and a blade arranged in parallel with the traveling direction of the signature is suspended from the other end of the second link arm, and the first link arm and the second link arm are respectively The basic configuration is that the blade is periodically and linearly moved up and down by rotating the blade at the same angular velocity and in the opposite direction to perform chopper folding of the signature.

In addition to the above basic structure, the chopper folding device according to the present invention, as shown in the conceptual views of FIGS. 1A to 1H, has a sun gear at the rotation center 10a of the first link arm 10. And a planetary gear 1 integral with the second link arm 11 that meshes with the rotation center 11a of the second link arm 11 and rolls around the sun gear 12.
3 is provided. In FIG. 1, white circles and black circles are shown at each end of the first link arm 10 and the second link arm 11, and white circles indicate rotatable link connections, and black circles indicate rotation. It indicates that you are being restrained.

In addition to the above features, the chopper folding device of the present invention further comprises a rotation direction of the sun gear 12 and a revolving direction of the planetary gear 13 set in the same direction, and a diameter of the sun gear 12 and a planetary gear. 13 has a further feature that the ratio of the rotation angular velocity of the sun gear 12 to the revolution angular velocity of the planetary gear 13 is set to (n + 2) / n: 1 when the ratio to the diameter of the sun gear 13 is n: 1. I have.

The setting of the ratio will be described in detail. The other end 11b of the second link arm 11 on which the blade is suspended
1 (a) to 1 (h) in order to move linearly.
As shown in the order, during one revolution around the sun gear 12, the planetary gear 13 needs to rotate twice in the direction opposite to the revolving direction on the revolving system (that is, as viewed from the revolving center). In order to rotate the planetary gear 13 twice on the revolving system, when the ratio of the diameter of the sun gear 12 to the diameter of the planetary gear 13 is n: 1, the sun gear 12 is rotated by 2 on the revolving system.
/ N times, and on a stationary system, 1 + 2 / n times, ie, one revolution of the planetary gear 13 is added, that is,
It is necessary to rotate (n + 2) / n times. From the above, when the ratio between the rotation angular velocity of the sun gear 12 and the revolution angular velocity of the planetary gear 13 is set to (n + 2) / n: 1, the order is shown in FIG. 1 (a) to FIG. 1 (h). The other end 11a of the second link arm 11 is moved linearly as
This makes it possible to linearly raise and lower the blade suspended from 1a.

As described above, according to the chopper folding device of the present invention, a complicated device configuration is not required, and the reliability can be ensured by the gear mechanism. The blade can be moved up and down linearly by a highly reliable mechanism with a component configuration. 1 (a) to 1 (h) are only used to show the concept of the present invention, and the specific configuration of the chopper folding device of the present invention is shown in FIGS. 1 (a) to 1 (h). It is needless to say that the present invention is not limited to the one represented by ()). For example, FIG.
1 (a) to 1 (h), straight lines 10 and 1 connecting the connecting portions as the first link arm and the second link arm, respectively.
Although FIG. 1 is illustrated, this straight line merely indicates the concept of connecting the connecting portions, and means that the first link arm and the second link arm are limited to linear members. It does not do.

Preferably, a first input gear coaxially with the sun gear and rotating integrally with the sun gear, and a second input gear rotatable relative to the sun gear and rotatably supporting the planetary gear. An input gear is provided. A first output gear meshing with the first input gear; and a second output gear coaxially integrated with the first output gear and meshing with the second input gear. When the speed ratio between the first input gear and the second input gear is 1, the driving mechanism includes a driving mechanism in which the speed ratio between the second output gear and the second input gear is set to (n + 2) / n. The link mechanism is rotated by transmitting rotation from the output gear and the second output gear to the first input gear and the second input gear, respectively. In this way, by rotating and driving the link mechanism using only the gear mechanism to move the blade up and down, more certainty and reliability can be ensured. In addition, since the first output gear and the second output gear are coaxially integrated, the rotational relationship given to the first input gear and the second input gear is always constant, and the sun gear The relationship between the rotation angular velocity of the planetary gear and the revolution angular velocity of the planetary gear does not collapse.

It is also preferable that a pair of the link mechanisms are arranged in parallel along the traveling direction of the signature, and the blades are suspended from the second link arms of the pair of link mechanisms. By moving the blade up and down by the pair of link mechanisms arranged side by side along the traveling direction of the signature, the blade can be moved while always being horizontal. In this case, the rotation direction of the first link arm (or the second link arm) may be set in the same direction as the pair of link mechanisms arranged in parallel, or may be set in the opposite direction. In particular, when the rotation direction of the first link arm (or the second link arm) is set to the same direction, one drive mechanism is provided on the center line between the pair of link mechanisms, and One output gear, the second
The output gear is meshed with each of the first input gear and each of the second input gears of the pair of link mechanisms, so that the one drive mechanism drives the pair of link mechanisms to rotate. Is preferred. In this way, by sharing the one drive mechanism between the pair of link mechanisms, the pair of link mechanisms can be reliably synchronized, and the movement of the blade while maintaining the level can be realized more reliably. become able to.

Further, at least the blade and a mechanism for moving the blade up and down (ie, the link mechanism and the drive mechanism)
Is preferably configured as a single device unit, and further provided with a retracting means for retracting the device unit from the line of progress of the signature. Thus, when a paper jam or the like occurs in the signature, the blade is quickly evacuated from the line of progress of the signature to prevent an overload from acting on the blade or a mechanism for moving the blade up and down. it can.

[0020]

Embodiments of the present invention will be described below with reference to the drawings. 2 to 5 show a chopper folding device according to a first embodiment of the present invention. More specifically, FIG. 2 is a plan view of the chopper folding device cut along a horizontal plane, FIG. 3 is a schematic front view of the chopper folding device, and FIGS.
FIG. 5 is an operation explanatory view of the chopper folding device. Here, first, a specific configuration of the present chopper folding apparatus will be described with reference to FIGS.

As shown in FIG. 3, the chopper folding device 20
Is provided with a blade 23 disposed in parallel with the traveling direction of the signature 1 (that is, the traveling direction of the upper and lower transport belts 2 and 3). The disposition position of the blade 23 is set on the downstream side of the stopper 4 in the traveling direction of the upper and lower transport belts 2 and 3. The chopper folding device 20 raises and lowers the blade 23 to perform chopper folding of the signature.
As shown in FIGS. 2 and 3, a pair of left and right link mechanisms 21 and 21 for supporting the blade 23 and both link mechanisms 21 and 21 are provided.
And a driving mechanism 22 for applying a driving force to the motor. In this specification, a pair of left and right link mechanisms 21 and
Of 1 and its components, the symbol R is attached to the symbol particularly for the right side, and the symbol L is appended to the symbol for the left side. In addition, in the case where the left and right sides are not particularly distinguished from each other, the symbols are not distinguished between R and L.

The link mechanisms 21 and 21 are arranged along the traveling direction of the signature 1 with their rotating surfaces parallel to the traveling direction of the signature 1 (the traveling direction of the upper and lower conveyor belts 2 and 3). They are juxtaposed at a distance. Each link mechanism 21 includes a sun gear 25, a planetary gear 26, a first input gear 27, and a second
It is mainly composed of each external gear of the input gear 28 and the support rod 29. Among them, the sun gear 25 and the first input gear 27 are formed concentrically and integrally, and the first rotating shaft 30
Is rotatably supported around a bearing 31. Here, the first input gear 27 is formed to have a larger diameter than the sun gear 25, and the first input gear 27
The input gear 27 is on the rear end side of the first rotating shaft 30, that is,
It is arranged on the back side of the casing 35.

A rotary cylinder 36 is fixedly provided at the tip of the first rotary shaft 30. The rotary cylinder 36 has a cylindrical surface 36 a concentric with the first rotation shaft 30, and the cylindrical surface 36 a is supported by the casing 35 via a bearing 37. That is, the first rotating shaft 30 is formed by the cylindrical surface 36 a and the bearing 37.
Through the casing 35. Further, the inner side of the casing 35 from the cylindrical surface 36a of the rotating cylinder 36,
That is, the second input gear 28 is formed on the side where the sun gear 25 and the first input gear 27 are provided. Second
The input gear 28 is concentric with the sun gear 25 and the first input gear 27. Here, the second input gear 28 is formed to have a larger diameter than the first input gear 27.

The rotary cylinder 36 has a through hole 36b parallel to the first rotary shaft 30 inside the cylindrical surface 36a and outside the center of rotation. A second rotating shaft 38 is inserted into the through hole 36b, and is supported by the rotating cylinder 36 via a bearing 39. At the rear end of the second rotating shaft 38, that is, at the end where the sun gear 25 and the first input gear 27 are disposed, the planetary gear 26 is fixed concentrically and integrally with the second rotating shaft 38. Has been established. On the other hand, the second rotating shaft 38
A support rod 29 is fixedly mounted at the tip of the. Thereby, the planetary gear 26 and the support rod 29 are connected to the second rotating shaft 3.
8 and rotates together.

The planetary gear 26 meshes with the sun gear 25, and the planetary gear 26 rotates relative to the sun gear 25 in a direction opposite to the sun gear 25. In the chopper folding device 20, the ratio of the diameter D ₂ of diameter D ₁ and the planetary gear 26 of the sun gear 25 (gear ratio) is 2: 1 is set to the sun gear 25 is relatively one rotation (rotation) During this operation, the planetary gear 26 rotates twice (rotates) in the opposite direction. The planetary gear 26 and the sun gear 25 are
The second input gear 28 is disposed so as to be accommodated substantially inside the second input gear 28, thereby making the device compact in the axial direction.

The support rod 29 is a member for supporting the blade 23, and has a support pin 29a provided at one end thereof in parallel with the second rotation shaft 38. Blade 23
Are provided with sleeves 23a, 23a at upper right and left ends thereof, respectively.
0 supports the support pin 29a. In other words, the blade 23 is suspended from the support pin 29a via the bearing 40.

In this chopper folding device 20, the second rotating shaft 3
The distance L ₂ from the center of 8 to the center of the support pin 29a is:
It is set equal to the distance L ₁ from the center of the first rotating shaft 39 to the stop of the second rotating shaft 38 (that is, L ₁ = L ₂ ).
As a result, a line (first link arm) connecting the center of the second rotation shaft 38 and the center of the support pin 29a is formed by the first rotation shaft 3
The support pin 29a can be periodically linearly moved by rotating in a direction opposite to a line (second link arm) connecting the center of the second rotation shaft 38 and the center of the second rotation shaft 38 at the same angular velocity. Has become. Here, the rotating cylinder 3
6 corresponds to the first link arm, and the support rod 29 is the second link arm.
It corresponds to a link arm.

The support rod 29 has the second rotating shaft 3
A counter weight 42 is attached to the end opposite to the support pin 29a with respect to the support pin 29a. A moment acts on the second rotating shaft 38 by suspending the blade 23 on the support pin 29a. By providing the counter weight 42 in this manner, the moment acting on the second rotating shaft 38 can be canceled or reduced. Will be able to Similarly, the first rotating shaft 30 is also provided on the surface of the rotating cylinder 36 on the side where the support rod 29 is provided, in order to cancel or reduce the moment acting on the first rotating shaft 30 via the second rotating shaft 38. A counterweight 43 is attached to a peripheral end opposite to the second rotation shaft 38 with the interposition therebetween.

The link mechanism 21 according to the present chopper folding device 20 has been described above. In the present chopper folding device 20, as shown in FIG. 3, when the planetary gear 26 is located directly below the sun gear 25 in the vertical direction. , Sun gear 25, planetary gear 2
The initial positions of the left and right link mechanisms 21 and 21 are set such that the support pins 29 and the support pins 29a of the support rod 29 are arranged in a straight line in order from above. In other words, a line (first link arm) connecting the center of the second rotation shaft 38 and the center of the support pin 29a is a line (first link arm) connecting the center of the first rotation shaft 39 and the stop of the second rotation shaft 38. The initial positions of the left and right link mechanisms 21 and 21 are set so as to be parallel (one straight line) to the two link arms). The initial position is the lowest point of the blade 23. In this initial position, the blade 23 is pushed under the table 6 between the rotating rollers 7, 7 (only the near side is shown in FIG. 3). As a result, the position of the entire apparatus is adjusted.

In the chopper folding apparatus 20, the left and right link mechanisms 21, the initial positions of which are set as described above,
21 is synchronously rotated by a drive mechanism 22 described below. The drive mechanism 22 mainly includes a first output gear 44, a second output gear 45, and a motor 46.
The first output gear 44 and the second output gear 45 are coaxially integrated, are rotatably supported by a rotation shaft (not shown) disposed in parallel with the first rotation shaft 30, and have the left and right link mechanisms 2.
It is arranged on the center line between 1 and 21. Here, the first output gear 44 is formed to have a larger diameter than the second output gear 45, and the first output gear 44 is disposed on the inner side of the casing 35, and the second output gear 45 is disposed on the near side. . The first output gear 44 is meshed with each of the first input gears 27 of the left and right link mechanisms 21 and 21, and the second output gear 4
5 is the second input gear 2 of each of the left and right link mechanisms 21 and 21
8, 28. The motor 46 is connected to the first output gear 4 on the center line between the left and right link mechanisms 21 and 21.
4, disposed above the second output gear 45 and fixed to the casing 35 (the fixed state is not shown). A motor gear 47 fixed to an output shaft 46 a of the motor 46 is meshed with the second output gear 45.

The driving force output from the motor 46 is input to the second output gear 45 via the motor gear 47 due to the meshing relationship between the respective gears as described above. To the input gears 28, 28,
From the first output gear 44 integrated with the output gear 45, the first left and right
The data is input to the input gears 27, 27, respectively.

In the chopper folding apparatus 20, the ratio of the diameter D _O1 of the first output gear 44 to the diameter D _I1 of the first input gear 27 is 1:
The ratio of the diameter D _O2 of the second output gear 45 to the diameter D _I2 of the second input gear 28 is set to 1: 2. In other words, the diameter D _O1 of the first output gear 44 and the first input gear 27
The gear ratio with the diameter D _{I1 of} the second output gear 45 is 1
The gear ratio between the diameter D _O2 of the second input gear 28 and the diameter D _I2 of the second input gear 28 is 2. First output gear 44 and second output gear 45
Are coaxially integrated and rotate at the same speed (same angular speed), the first input gear 27 is rotationally driven at twice the angular speed of the second input gear 28 by setting the gear ratio as described above. Will be.

Next, the operation of the chopper folding apparatus 20 configured as described above will be described with reference to FIGS. FIGS. 4 and 5 schematically show the state in which the planetary gear 26 rotates around the sun gear 25 in the chopper folding device 20 by the revolving angle of the planetary gear 26 by 45 degrees. For simplicity, only the blade 23 and the left and right link mechanisms 21 and 21 are shown, and the link mechanism 21
About the sun gear 25, the planetary gear 26, the support rod 2
9 (including the support pin 29a and the counter weight 42),
Only the second input gear 28 and the counterweight 43 are shown. FIGS. 4 and 5 are merely diagrams for simply illustrating the operating state of the present chopper folding device 20, and exemplify an arbitrary state in which the present chopper folding device 20 is continuously operated. Things. That is, the present chopper folding device 20 does not operate stepwise by 45 degrees at the revolving angle of the planetary gear 26 as illustrated in FIGS. 4 and 5, but operates continuously and smoothly. Make sure that. The black dots 49 shown in each figure are provided for convenience in order to clearly show the rotation state of the sun gear 25, and are not related to the actual configuration.

First, as shown in FIG.
Starting from a state where 3 is in the initial position (the lowest point), in this state, the sun gear 25, the planetary gear 26, the support pin 29
a are arranged in a straight line in order from the top. When the motor 46 rotates in this state, the first output gear 44 and the second
The driving force is input from the output gear 45 to each of the first input gear 27 and the second input gear 28 of the left and right link mechanisms 21 and 21, respectively. The driving force input to the first input gear 27 causes the sun gear 25 to rotate (spin), and the driving force input to the second input gear 28 causes the planetary gear 26 to revolve around the sun gear 25. At this time, the rotation direction of the sun gear 25 and the revolving direction of the planetary gear 26 are opposite to the rotation directions of the first output gear 44 and the second output gear 45, and the left and right link mechanisms 2
The directions are the same in 1 and 21, respectively.

When, for example, the planetary gear 26 revolves clockwise by 45 degrees, the first input gear 27 becomes the second input gear 2.
The sun gear 25 integrated with the first input gear 27 rotates clockwise by 90 degrees because it is rotationally driven at twice the angular speed of 8. Thus, the sun gear 25 will be rotated relatively 45 degrees clockwise with respect to the planetary gear 26 on the revolving system of the planetary gear 26, the diameter D ₂ of diameter D ₁ and the planetary gear 26 of the sun gear 25 Is 2: 1 so that the planetary gear 2
6 rotates counterclockwise by 90 degrees with respect to the sun gear 25.

As a result, the sun gear 25, the planetary gear 26,
The respective phases and positions of the support pins 29a are shown in FIG.
, And the blade 23 is attached to the left and right support pins 29.
a, 29a rises with the linear movement in the vertical direction. Also, during this time, since the left and right link mechanisms 21 and 21 are rotating in synchronization, the left and right support pins 29a and 29a also move linearly in synchronization, and the blade 23 suspended from the left and right support pins 29a and 29a Ascend while keeping level.

Similarly, when the planetary gear 26 further revolves clockwise 45 degrees from this state, the sun gear 25,
The phase and position of each of the planetary gear 26 and the support pin 29a are as shown in FIG. 4C, and the blade 23 rises linearly while keeping horizontal in the vertical direction. Then, when the planetary gear 26 further revolves clockwise by 45 degrees, the blade 23 moves up to the position shown in FIG.

Then, the planetary gear 26 is further rotated clockwise.
Revolves, 180 degrees from the initial state as shown in FIG.
Blade 23 reaches the highest point when it revolves to the position
I do. At this highest point, the support pin 29a, the planetary gear 2
6, sun gear 25, planetary gear 26, support pin 29a is up
They are lined up in a straight line from top to bottom. Therefore, the blade
Moving distance (stroke) from the lowest point to the highest point of 23
L_SIs located between the center of the first rotation shaft 39 and the second rotation shaft 38.
Distance L to stop₁And a support pin from the center of the second rotating shaft 38
Distance L to the center of 29a_TwoIs equal to twice the sum of
Chi, L_S= 2 × (L ₁+ L_Two)].

After reaching the uppermost point shown in FIG. 5 (a), the blade 23 rotates the planetary gear 26 downward, as shown in FIGS. 5 (b) to 5 (d). It descends gradually according to. Then, when the planetary gear 26 returns to the initial state again, as shown in FIG.
Reaches the lowest point again. During the movement from the uppermost point to the lowermost point, the blade 23 moves linearly while maintaining the horizontal position. Then, as the planetary gear 26 rolls up again, the blade 23 also rises again toward the uppermost point. That is, while the rotational driving force from the motor 46 is being input to the left and right link mechanisms 21 and 21, the blade 23 periodically repeats the above-described elevating operation.

The signature 23 has a blade 23 as shown in FIG.
At a predetermined timing during the descent from the position shown in FIG. 4D to the lowest point shown in FIG.
3 transports the blade 23 directly below the blade 23, and is positioned by the stopper 4. The signature 1 positioned by the stopper 4 is folded between the rotating rollers 7 arranged below the table 6 by the blade 23 being swung down to below the table 6, and is vertically folded into two. Is discharged to the outside in the

The configuration and operation of the chopper folding device 20 according to the first embodiment of the present invention have been described above. The chopper folding device 20 revolves the planetary gear 26 around the sun gear 25 as described above. While rotating the sun gear 25, the blade 23 is moved up and down linearly in the vertical direction. Therefore, there is no need to use internal gears that are difficult to machine as compared with external gears as in some conventional techniques, so that machining costs can be reduced and machining accuracy does not decrease. In addition, since it is not necessary to interpose an intermediate gear between the sun gear and the planetary gear as in some conventional technologies, high-speed stability is reduced due to imbalance during rotation, and the component configuration is complicated. Not even. Further, since the belt is not used for transmitting the driving force unlike some prior arts, there is no lack of reliability in long-term use or continuous operation. In other words, according to the present chopper folding device 20, the blade 2 has a simpler component structure and a highly reliable mechanism than the conventional technology.
3 can be realized to be moved up and down linearly in the vertical direction.

Next, a chopper folder according to a second embodiment of the present invention will be described with reference to FIGS. Here, FIG. 6 is a schematic front view of the present chopper folding apparatus, and FIGS.
FIG. 4 is an explanatory view of the operation of the present chopper folding device. Here, first, a specific configuration of the present chopper folding apparatus will be described with reference to FIG. The same parts as those in the first embodiment are denoted by the same reference numerals.

As shown in FIG. 6, this chopper folding device 50
A blade 23 disposed in parallel with the traveling direction of the upper and lower conveyor belts 2 and 3; a pair of left and right link mechanisms 21 and 21 supporting the blade 23;
1 is provided with a driving mechanism 51 for applying a driving force to the driving mechanism 1. Since the blade 23 and the left and right link mechanisms 21 and 21 have the same configuration as in the first embodiment, a duplicate description is omitted, but the chopper folding device 50 is characterized by the arrangement of the left and right link mechanisms 21 and 21. The second input gears 28, 28 are arranged so as to mesh with each other.

The drive mechanism 51 according to the chopper folding device 50 includes a first output gear 44, a second output gear 45, and a motor 46 as its constituent elements, similarly to the drive mechanism 22 of the first embodiment. A reversing gear 52 is provided as a new component. The first output gear 44 and the second output gear 45 are coaxially integrated, are disposed above the left link mechanism 21 (L), and have the first input gear 27 and the second input gear 27 of the left link mechanism 21 (L). Input gear 2
And 8 respectively. Then, the first output gear 44 and the first input gear 27 of the right link mechanism 21 (R) are connected.
, A reversing gear 52 is interposed. Reversing gear 5
2 is rotatably supported by a rotating shaft (not shown) arranged in parallel with the first rotating shaft 30, and meshes with both the first output gear 44 and the first input gear 27. Motor 46
Is disposed further above the first output gear 44 and the second output gear 45, and a motor gear 47 fixed to an output shaft 46 a of the motor 46 is meshed with the second output gear 45.

The driving force output from the motor 46 is input to the second output gear 45 via the motor gear 47 due to the meshing relationship between the respective gears as described above.
Then, the driving force input to the second output gear 45 is further transmitted from the second output gear 45 to the left second input gear 28 (L).
The first output gear 44 integrated with the second output gear 45
Are input to the left first input gear 27 (L) and the reversing gear 52, respectively. The reversing gear 5
2 is input to the first right input gear 27 (R), and the second input gear 28 (L) to the right second input gear 28 (L).
The driving force is input to the input gear 28 (R). In addition, between the first output gear 44 and the first input gear 27,
The setting of the gear ratio between the second output gear 45 and the second input gear 28 is the same as in the first embodiment.

Next, the operation of the present chopper folding apparatus 50 configured as described above will be described with reference to FIGS. FIGS. 7 and 8 schematically show how the planetary gear 26 rotates around the sun gear 25 in the present chopper folding device 50 by 45 degrees at the revolving angle of the planetary gear 26. FIG. 6 is a diagram corresponding to FIGS. 4 and 5 used in the description of the operation of the embodiment. Also, in order to clearly show the rotation state of the sun gear 25, the black dots 4
9 is shown.

First, as shown in FIG.
3 will be described from the initial position (the lowest point). In this initial state, the sun gear 25, the planetary gears 26, and the support pins 29a are arranged in a straight line from the top in the same manner as in the first embodiment. When the motor 46 rotates, the left and right link mechanism 2
The driving force is input to each of the first input gear 27 and the second input gear 28 of the first and second 21 and the first output gear 44 to the left first input gear 27 (L) and the second input gear 28 (L). , The driving force is directly input from the second output gear 45, and the reversing gear 5 is supplied to the right first input gear 27 (R) and the second input gear 28 (R).
2, the driving force is input via the left second input gear 28 (L). Therefore, the left first input gear 27
(L), the rotation direction of the second input gear 28 (L) is opposite to that of the first output gear 44 and the second output gear 45 as in the first embodiment, whereas the right first input gear 27 ( R), the rotation direction of the second input gear 28 (R) is the first output gear 44,
The direction is the same as that of the second output gear 45.

Thus, as shown in FIGS. 7 (a) to 7 (d) and FIGS. 8 (a) to 8 (d), the left and right sun gears 25 and the planetary gear 26 move in opposite directions. It rotates or revolves. However, even in this case, since the left and right support pins 29a, 29a perform only a linear movement in the vertical direction while synchronizing with each other, the blade 23 suspended by the left and right support pins 29a, 29a is horizontal in the same manner as in the first embodiment. Up and down while keeping While the rotational driving force from the motor 46 is being input to the left and right link mechanisms 21 and 21,
The blade 23 repeats the above elevating operation periodically.

The configuration and operation of the chopper folding device 50 according to the second embodiment of the present invention have been described above. As described above, the chopper folding device 50 also includes the planetary gear 26 and the sun gear as in the first embodiment. The blade 23 is moved up and down linearly in the vertical direction by rotating the sun gear 25 while revolving around the periphery of the sun gear 25. Therefore, according to the present chopper folding device 50, the blade 23 can be vertically moved up and down linearly in a vertical direction by a highly reliable mechanism with a simpler component configuration than the conventional technology. The same effect as in the embodiment can be obtained. Further, according to the present chopper folding device 50, since the left and right link mechanisms 21 and 21 are rotated in opposite directions, the moments generated in the respective link mechanisms 21 can be canceled each other, and the vibration can be suppressed. There is also an effect.

Next, a chopper folder according to a third embodiment of the present invention will be described with reference to FIG. FIG. 9 is a schematic side view of the chopper folding apparatus. The chopper folder according to the present embodiment is characterized by a support mechanism of an apparatus unit that accommodates a link mechanism for driving the blade up and down and a drive mechanism. Further, the configuration of the link mechanism and the drive mechanism is not a characteristic part of the present embodiment, and the configuration of the first embodiment or the second embodiment can be applied. Note that FIG.
In the following description, the same parts as those in the above-described first and second embodiments are denoted by the same reference numerals, and redundant description will be omitted.

As shown in FIG. 9, this chopper folding device 55
The chopper folding unit (equipment unit) 60 in which a mechanism for elevating and lowering the blade 23 such as the link mechanism 21 is integrally accommodated in a casing 35, and a supporting mechanism 61 for supporting the chopper folding unit 60. I have.
The support mechanism (evacuation means) 61 is composed of an arm 56 and an actuator 58. The arm 56 extends from below the table 6 onto a line for conveying signatures, and has a lower end rotatably supported by a rotary shaft 57 and a lower end. A casing 35 is attached. The actuator 58 is interposed between the upper end of the arm 56 and a machine frame 59 disposed above the arm 56, and suspends the arm 56 from the machine frame 59. The arm 56 swings about the rotation shaft 57 by the operation of the actuator 58. The chopper folding unit 60
9A, the operating position close to the table 6 as shown in FIG. 9A and the table 6 as shown in FIG.
It is designed to move between a shunting position and a shunting position.

The operating position shown in FIG. 9A is a normal position at the time of chopper folding, and the first position in this operating position is as follows.
By performing the elevating operation of the blade 23 as described in the embodiment or the second embodiment, the signature is folded between the rotating rollers 7 under the table 6. On the other hand, the retracted position shown in FIG. 9B is a position at the time of occurrence of a paper jam or the like in the signature, and a paper jam of the signature in the gap between the rotating rollers 7 and the table 6 by a paper jam detection sensor (not shown). When the overload detection sensor (not shown) detects that the blade 23 is overloaded, the actuator 5
8, the chopper folding unit 60 is retracted to the retracted position.

Since the chopper folding device 55 according to the third embodiment of the present invention is configured as described above, even if a paper jam occurs between the rotating rollers 7, 7, etc.
The operation of the actuator 58 causes the chopper folding unit 6 to operate.
0 can be evacuated from the line of the signature, thereby preventing the blade 23 from being overloaded. Therefore, according to the present chopper folding device 55, it is possible to prevent the blade 23, the link mechanism 21, and the like from being damaged due to the overload, and to improve the durability.

Although the three embodiments of the chopper folding device of the folding machine according to the present invention have been described above, the embodiments of the present invention are not limited to these. For example, the first
In the embodiment and the second embodiment, the ratio between the diameter D ₁ of the sun gear 25 and the diameter D ₂ of the planetary gear 26 is set to 2: 1 and the rotation angular velocity of the sun gear 25 and the revolving angular velocity of the planetary gear 26 are determined. the ratio 2: is set to 1, the ratio of the diameter D ₂ of diameter D ₁ and the planetary gear 26 of the sun gear 25 n: 1 and the time, the revolution of the rotational angular velocity and the planetary gear 26 of the sun gear 25 What is necessary is that the ratio with the angular velocity is (n + 2) / n: 1.

Therefore, for example, the diameter D _{1 of the} sun gear 25
And the ratio of the diameter D ₂ of the planetary gear 26 is 1: 1 (ie,
In the case of n = 1), the ratio between the rotation angular velocity of the sun gear 25 and the revolution angular velocity of the planetary gear 26 may be 3: 1. In this case also the support rod 29 is fixed to the planetary gear 26, and the distance L ₂ from the center of the distance L ₁ and the planetary gear 26 from the center of the sun gear 25 to the center of the planetary gear 26 to the support pins 29a etc. Set to distance. With such a setting, the blade 23 can be moved up and down linearly in the vertical direction as shown in the order of FIG. 10A to FIG. 10D as in the first and second embodiments. Note that FIG.
FIGS. 10A to 10D are views showing the manner in which the blade 23 moves up and down every time the planetary gear 26 revolves 90 degrees (the sun gear 25 rotates 270 degrees).

[0056]

As described above in detail, according to the chopper folding apparatus of the present invention, while the planetary gear revolves around the sun gear, the sun gear itself rotates by a predetermined amount in the same direction as the revolving direction of the planetary gear. With the configuration of rotating at the angular velocity ratio, there is an effect that the blade can be linearly moved up and down with a simpler component configuration and a highly reliable mechanism than the conventional technology.

[Brief description of the drawings]

FIG. 1 is a conceptual diagram for dynamically explaining features of the present invention, showing movement in the order of (a) to (h).

FIG. 2 is a plan view of the chopper folding device according to the first embodiment of the present invention, cut along a horizontal plane.

FIG. 3 is a schematic front view of the chopper folding device as the first embodiment of the present invention.

FIG. 4 is a view showing the operation of the chopper folding device as the first embodiment of the present invention, and shows the operation in the order of (a) to (d).

FIG. 5 is a view showing the operation of the chopper folding device as the first embodiment of the present invention, and shows the operation in the order of (a) to (d).

FIG. 6 is a schematic front view of a chopper folding device as a second embodiment of the present invention.

FIG. 7 is a view showing the operation of the chopper folding device as a second embodiment of the present invention, and shows the operation in the order of (a) to (d).

FIG. 8 is a view showing the operation of the chopper folding device as the second embodiment of the present invention, and shows the operation in the order of (a) to (d).

FIG. 9 is a schematic side view of a chopper folding device according to a third embodiment of the present invention.

FIG. 10 is a diagram showing a configuration and operation of another embodiment of the present invention, and shows operations in the order of (a) to (d).

FIG. 11 is a schematic side view showing the configuration of a conventional general chopper folding device.

FIG. 12 is a schematic front view showing the configuration and operation of a conventional vertical ascent / descent type chopper folding device, and shows the operation in the order of (a) and (b).

FIG. 13 is a schematic front view showing the configuration and operation of a conventional vertical ascent / descent type chopper folding device, and shows the operation in the order of (a) and (b).

FIG. 14 is a schematic front view showing the configuration and operation of a conventional vertical ascent / descent type chopper folding device, showing the operation in the order of (a) and (b).

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 signature 2 upper conveyance belt 3 lower conveyance belt 4 stopper 6 table 7 rotating roller 20, 50, 55 chopper folding device 21 link mechanism 22, 51 drive mechanism 23 blade 25 sun gear 26 planetary gear 27 first input gear 28 first 2 input gear 29 support rod 29a support pin 30 first rotating shaft 35 casing 36 rotating cylinder 38 second rotating shaft 42 counter weight 43 counter weight 44 first output gear 45 second output gear 46 motor 47 motor gear 52 reversing gear 56 arm 59 Actuator 60 Chopper folding unit 61 Support mechanism

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3F108 AA01 AB01 AC10 BA02 BB27 CD04 3J027 FA19 FB40 GA01 GC13 GD04 GD08

Claims (4)

[Claims] 1. A blade disposed in parallel with a traveling direction of a signature, a first link arm rotatable around one end, and a second link arm having the same length as the first link arm and having the same length as the other end of the first link arm. A link mechanism having one end rotatably connected to a second link arm, wherein the blade is suspended from the other end of the second link arm, and the first link arm and the second link arm are respectively In a chopper folding device that rotates the blade periodically and linearly by rotating at the same angular velocity and in the opposite direction to perform chopper folding of the signature, a sun gear is provided at the rotation center of the first link arm. Arranged,
A planetary gear integrated with the second link arm that meshes with the sun gear and rolls around the sun gear is disposed at the center of rotation of the second link arm. When the revolution direction of the planetary gear is set to the same direction and the ratio of the diameter of the sun gear to the diameter of the planetary gear is n: 1, the rotation angular velocity of the sun gear and the revolution of the planetary gear A chopper folding device, wherein a ratio with respect to an angular velocity is set to (n + 2) / n: 1. 2. A first input gear coaxially rotating with the sun gear and a second input gear rotatable relative to the sun gear and rotatably supporting the planetary gear. And a first output gear meshing with the first input gear and a second output gear coaxially integrated with the first output gear and meshing with the second input gear. Assuming that the speed ratio between the gear and the first input gear is 1, the speed ratio between the second output gear and the second input gear is set to (n + 2) / n,
From the output gear and the second output gear to the first input gear and the second
2. The chopper folding device according to claim 1, further comprising a drive mechanism for rotating the link mechanism by transmitting rotation to the input gears. 3. A pair of said link mechanisms are provided in parallel along the direction of travel of said signature, said blades are suspended by respective second link arms of said pair of link mechanisms, and said drive mechanism is composed of said pair of link mechanisms. One is provided on the center line between the link mechanisms, and the first output gear and the second output gear are meshed with the first input gear and the second input gear of the pair of link mechanisms, respectively. 3. The chopper folding device according to claim 2, wherein the one drive mechanism is configured to rotate the pair of link mechanisms. 4. The apparatus according to claim 1, wherein at least the blade and a mechanism for moving the blade up and down are configured as one device unit, and a retracting means is provided for retracting the device unit from the line of progress of the signature. , Claims 1 to
Item 3. The chopper folding device according to any one of Items 3.