JP2002193546A - Chopper folding device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable a blade to linearly move up and down without rotating in a chopper folding device. SOLUTION: In the chopper folding device is provided with a gear mechanism comprising a first internal tooth gear 23 for which rotation is restricted, a first external tooth gear 21 to engage with the first internal teeth gear 23, and a second external tooth gear 20 to engage with the first external tooth tear 21. The blade 11 arranged parallel to the traveling direction of a signature 1 is fixed on a the second external tooth gear 20. The distance from the center of the first internal tooth gear 23 to the center of the first external tooth gear 21 and the distance from the center of the first external tooth gear 21 to the center of the second external tooth gear 20 are set to be equal. A driving means rotatively drives the first external tooth gear 21 around the central axis of the first internal tooth gear 23 while controlling means 12, 13, 24, 25 restricting movement of the position of the center of the second external tooth gear 20 to be on a line extending in a diameter direction of the first internal tooth gear 23.

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 which raises and lowers a blade using a gear mechanism, and vertically folds a signature that travels along a horizontal plane into two along the traveling direction. The present invention relates to a chopper folding device that raises and lowers a blade using a gear mechanism whose surface is perpendicular to the blade.

[0002]

2. Description of the Related Art As shown in FIG. 4, a folding machine includes a plurality of upper conveying belts 2 divided above a conveying line of a signature 1, and an upper conveying belt 2 below the conveying line of the signature 1. A plurality of lower conveying belts 3 corresponding to each other are provided.
The upper and lower conveyor belts 2 and 3 run at a constant speed (in a direction perpendicular to the paper surface), and the signature 1 is caught between the upper and lower conveyor belts 2 and 3 while the chopper folding device 50 is being held.
It is to be transported to.

[0003] Various types of conventional chopper folding devices of a folding machine are known, such as a device in which a blade is fixed to the tip of an oscillating arm, and a device in which a blade is moved up and down using a gear mechanism. Chopper folding device 50 shown in FIGS.
Among the conventional types of raising and lowering the blade using a gear mechanism, in particular, a gear mechanism provided at one end of the drum 53 by suspending the blade 51 on a drum 53 disposed in parallel with the traveling direction of the signature 1. The drum 53 is rotated by 52 to move the blade 51 up and down, and at the same time, the blade 51 is kept in a predetermined posture.

A rotating shaft 55 extending in parallel with the traveling direction of the signature 1 is fixed to the side surface 53a of the drum 53.
The rotating shaft 55 is rotatably supported by a neighboring machine frame 60 via a bearing 61, and the drum 53 can rotate around the rotating shaft 55. Further, the drum 53 is formed to be hollow, and a predetermined range of the peripheral surface thereof is open. The blade 51 is disposed inside the drum 53 on the side where the peripheral surface is open, and its upper end is fixed to a support shaft 54 extending in parallel with the rotation shaft 55 of the drum 53. The support shaft 54 is a rotary shaft 55 of the drum 53
The drum 53 is rotatably supported via bearings 62 on both sides 53a and 53b of the drum 53 at both ends thereof. From the rotation shaft 55 to the support shaft 5
The distance to 4 is set equal to the distance from the support shaft 54 to the tip of the blade 51.

[0005] One end of the support shaft 54 is
3a, and a planetary gear 56 is fixedly provided at the tip thereof. A support shaft 57 is fixed to the outside of the side surface portion 53a in parallel with the rotation shaft 55 of the drum 53, and an intermediate gear 58 is rotatably supported on the support shaft 57 via a bearing 63. This intermediate gear 58 is a planetary gear 5
6 and is disposed closer to the rotation shaft 55 of the drum 53 and is meshed with the planetary gear 56. Further, a sun gear 59 is provided on the machine frame 60 supporting the drum 53.
Is fixed. The sun gear 59 is concentric with the rotating shaft 55 of the drum 53 and is meshed with the intermediate gear 58. The ratio of the diameter of the sun gear 59 to the diameter of the planetary gear 56 is 2:
It is set to 1.

With such a configuration, the other side surface portion 53
6b, the drum 53 rotates around the rotation shaft 55. As shown in FIGS. 6A to 6E, the intermediate gear 58 and the planetary gear 56
Around the sun gear 59 (clockwise in the figure). At this time, since the sun gear 59 is fixed, the intermediate gear 58 meshing with the sun gear 59 rotates (rotates) in the same direction as the revolving direction.
8, the planetary gear 56 meshes with the intermediate gear 58 in the opposite direction,
That is, it rotates in the direction opposite to the revolving direction with respect to the sun gear 59 (counterclockwise in the drawing).

The diameter of the sun gear 59 and the planet gear 56
When the planetary gear 56 revolves around the sun gear 59 at a predetermined angular velocity, the planetary gear 56 itself has the same direction in the stationary system in the opposite direction to the revolving speed. It will rotate at the angular velocity. Planetary gear 5
6 moves as described above, and since the distance from the rotation shaft 55 to the support shaft 54 is set equal to the distance from the support shaft 54 to the tip of the blade 51, the planetary gear 5
The blade 51 integrally fixed to 6 moves with its tip always positioned on a fixed straight line. In particular, by performing the initial setting so that the tip of the blade 51 faces directly below when the planetary gear 56 is at the lowest point,
As shown in FIG. 6A to FIG.
Moves linearly in the vertical direction.

The conventional chopper folding device 50 includes a drum 53
The rotation speed of the blade 53 is synchronized with the traveling speed of the upper and lower transport belts 2 and 3 so that the timing of raising and lowering the blade 53 is adjusted to the transport timing of the signature 1. And
When the signature 1 is conveyed to just below the blade 53 and positioned by the stopper 4, the blade 5
3, a pair of rotating rollers 7, 7 parallel to the traveling direction of the signature 1 disposed under the table 6 by the linear movement of the tip of the rotating roller 7.
The signature 1 is folded in between, and the signature 1 is vertically folded in two along the traveling direction.

[0009]

The table 6 disposed below the upper and lower conveyor belts 2 and 3 functions as a guide when the signature 1 is conveyed. It also has the function of maintaining the posture of the signature 1. Therefore, in order to accurately hold the signature 1 by the table 6, the opening 6a of the table 6 provided on the rotating rollers 7, 7 should be kept to a minimum size.

In the conventional chopper folding device 50, the tip of the blade 51 linearly moves in the vertical direction, but the blade 51 itself moves up and down while rotating with the rotation of the planetary gear 56. In the opening 6a of the table 6, FIG.
When the drum 53 rotates clockwise, the blade 51 enters the opening 6a while tilting to the right, reaches the lowest point, pushes the signature 1 between the rotating rollers 7, 7, and then tilts to the left. While coming out of the opening 6a.

If the blade 51 moves up and down linearly in the vertical direction, the opening 6a may be set to a size corresponding to the thickness of the blade 51. However, since the blade 51 rotates while drawing a locus as shown in FIG. 7, in order to prevent interference with the blade 51, the opening 6a of the table 6 is moved up and down linearly in the vertical direction. It is necessary to open wider than the case. For this reason, in the conventional chopper folding device 50, the signature 1 cannot be accurately held by the table 6, and there is a possibility that the folding accuracy of the signature 1 may be deteriorated.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and has as its object to provide a chopper folding device which can move a blade up and down linearly without rotating it.

[0013]

In order to achieve the above object, a chopper folding device according to the present invention is characterized in that it is configured as follows. That is, the chopper folding device of the present invention includes a first internal gear whose rotation is restricted, a first external gear that meshes with the first internal gear, and a second external gear that meshes with the first external gear. A gear mechanism comprising a tooth gear; a blade disposed in parallel with the traveling direction of the signature on the second external gear; fixing the blade of the first external gear from the center of the first internal gear; The distance to the center and the distance from the center of the first external gear to the center of the second external gear are set to be equal. Then, while the movement of the center position of the second external gear is restricted to a straight line extending in the diametric direction of the first internal gear by the restricting means, the first external gear is driven by the driving means while the first external gear is being moved. The blade is driven to rotate about the central axis of the gear, so that the blade is moved up and down linearly.

More specifically, when a rotational driving force is input to the first external gear from the driving means, the first external gear rotates along the inner circumference of the first internal gear ( However, the second external gear that meshes with the first external gear also rotates in the direction opposite to the rotation direction of the first external gear with respect to the first external gear. Here, for example, assuming that the diameter of the first external gear is D _a and the diameter of the second external gear is D _b , the distance from the center of the first internal gear to the center of the first external gear And the first
Diameter of the first internal gear from the distance are equal from the center of the external gear to the center of the second external gear becomes 2D _a + D _b.

At this time, the first external gear revolves N degrees.
And the first external gear is −N × (2D_a
+ D_b) / D_aIt will rotate every time. This from a static system
As seen, the first external gear is −N × (2D_a+ D_b) / D_a
+ N = −N × (D_a+ D_b) / D_aYou have rotated
You. On the other hand, the second external gear is moved by the position regulating means to the second external gear.
1 The position of the internal gear is regulated on a straight line extending in the diameter direction.
So that the first external gear rotates along with the revolution of the first external gear.
While moving on the straight line while meshing with the car, the first internal teeth
The distance from the center of the vehicle to the center of the first external gear;
Distance from the center of the external gear to the center of the second external gear;
Are equal, the second external gear is viewed from a stationary system.
-N around the first external gear for the first external gear
It will orbit once. However, the first external gear is-
N × (D_a+ D_b) / D_aRelatively to rotate,
The second external gear surrounds the first external gear with -N + N * (D_a
+ D _b) / D_a= N × D_b/ D_aRevolves around, viewed from the center of revolution
Will rotate N times. When viewed from a stationary system
Has a rotation angle of NN = 0 degrees, and the second external gear
It is not rotating well. Thus, the second external tooth
Fixed to the second external gear because the car does not rotate at all
The blade to be cut is one in which the direction of the cutting edge is regulated in one direction.
You will move up and down linearly while maintaining a fixed posture.

Preferably, a first link arm rotatable about one end, and one end rotatably connected to the other end of the first link arm having the same length as the first link arm and being rotatably connected to the other end. The regulating means comprises a second link arm rotatably supported by the second external gear, and means for rotating the first link arm and the second link arm at the same angular velocity and in opposite directions. A center of rotation of the first link arm is disposed concentrically with a center axis of the first internal gear;
The rotation center of the link arm is disposed concentrically with the center axis of the first external gear. Thus, the second external gear moves on a straight line extending in the diameter direction of the first internal gear while being guided by the first link arm and the second link arm.

More preferably, a second internal gear whose rotation is restricted is disposed at the rotation center of the first link arm, and a third external gear meshing with the second internal gear is connected to the second link. The ratio of the diameter of the second internal gear to the diameter of the third external gear is set to 2: 1.
By rotatably supporting the second external gear by a support member fixed to the external gear, the first link arm and the second link arm are rotated at the same angular velocity and in opposite directions, respectively. I do. Thereby, the second external gear supported by the support member rolls while the third external gear meshes with the second internal gear, so that the diametrical direction of the first internal gear is increased. Periodically reciprocate on a straight line extending to More preferably, the third external gear and the first external gear are arranged on the same support shaft, and a rotational driving force is input to the support shaft. Thus, the third external gear and the first external gear can be rotationally driven while being completely synchronized.

[0018]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 3 show a chopper folding device as one embodiment of the present invention. For more information,
FIG. 1 is a schematic side sectional view showing a configuration of the present chopper folding device,
FIG. 2 is a schematic diagram (partially omitted) of FIG. 1 viewed from the II-II direction,
FIG. 3 is a diagram illustrating the operation of the present chopper folding device. Here, first, a specific configuration of the present chopper folding device will be described with reference to FIGS. 1 and 2.

As shown in FIG. 1, the present chopper folding device 10
Is provided with a blade 11 arranged 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 11 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 10 includes two rotating drums 12 and 13 in parallel with the traveling direction of the signature 1.
A large-diameter first drum 12 and a small-diameter second drum 13 are provided. The first drum 12 and the second drum 13 are both hollow and formed so as to open a predetermined range on the peripheral surface. The second drum 13 is provided inside the first drum 12, and the blade 11 is provided inside the second drum 13.

A sleeve 12c is formed on the side surface 12a of the first drum 12. Inside the sleeve 12c, a cylindrical surface 30a formed on the machine frame 30 is inscribed via a bearing 31, and when the sleeve 12c rotates around the cylindrical surface 30a, the first drum 12 moves in the figure. Is rotated about an axis indicated by a chain line. In addition, a rotational driving force is input to the other side surface portion 12b from a driving source such as a motor (not shown).

Both side portions 13a, 13b of the second drum 13
, Support shafts 14a and 14b parallel to the rotation center line of the first drum 12 are fixed outward. The two support shafts 14a and 14b are concentric, and are arranged eccentrically from the rotation center line of the first drum 12 to the opening side of the peripheral surface. Of these, the support shaft 14b fixed to the side surface 13b
The bearing 15 is formed by the side surface portion 12 b of the first drum 12.
It is rotatably supported via. One side 13
In a, a sleeve 13c concentric with the support shaft 14a is formed outward. Side portion 12 of first drum 12
a is formed with a circular opening 12d concentric with the sleeve 13c and slightly larger in diameter than the outer diameter of the sleeve 13c.
8 so as to be rotatable. That is, the second drum 13 is rotatably supported inside the first drum 12 via the support shaft 14b and the sleeve 13c.

The upper end of the blade 11 is the first drum 1
2 is fixed to a support shaft 16 extending parallel to the rotation center line. The support shaft 16 is a support shaft 14 of the second drum 13.
The second drum 13 is rotatably supported via bearings 17 and 17 on both side portions 13 a and 13 b of the second drum 13. The distance from the axis of the support shafts 14a and 14b of the second drum 13 to the axis of the support shaft 16 of the blade 11 is defined by the distance between the rotation center line of the first drum 12 and the support shaft 14 of the second drum 13.
The distance is set to be equal to the distance between the axes a and b.

One end of the support shaft 16 of the blade 11 protrudes from the side surface 13 a of the second drum 13. Then, the second end of the support shaft 16 protruding from the side surface portion 13a is provided.
The external gear 20 is fixed. The second drum 13
Support shaft 14a also protrudes outside the side surface 12a of the first drum 12 through the inside of the circular opening 12d. Support shaft 1
A third external gear (planetary gear) 24 is fixedly mounted at the tip of 4a, and a first external gear 24 is provided between the third external gear 24 and the side surface 13a.
An external gear (planetary gear) 21 is rotatably supported via a bearing 22. The axial position and the diameter (number of teeth) of the first external gear 21 are set so as to mesh with the second external gear 20. Here, the first external gear 21 and the second external gear 20 have the same diameter. Is formed.

On the other hand, a first internal gear 23 (ring gear) and a second internal gear (ring gear) 25 are fixedly provided inside the cylindrical surface 30 a supporting the first drum 12. . The first internal gear 23 and the second internal gear 25 are both concentric with the rotation center line of the first drum 12, and the first internal gear 23 is meshed with the first external gear 21 and the second internal gear is used. 25 is meshed with the third external gear 24. The distance from the center of the first internal gear 23 to the center of the first external gear 21 and the distance from the center of the first external gear 21 to the center of the second external gear 20 are set equal to each other. Internal gear 25
Of the third external gear 24 is set to 2: 1. The distance from the center of the first external gear 21 to the center of the second external gear 20 is equal to the radius of the second internal gear 25. In this chopper folding device 10, as shown in FIG. 2, when the first external gear 21 is at the lowest point of the first internal gear 23, the second external gear 20 is moved to the first external gear 21. The initial position is set so that the blade 11 is located directly below the vertical direction and the cutting edge of the blade 11 is directly below the vertical direction.

Next, the operation of the present chopper folding apparatus 10 configured as described above will be described with reference to FIG. FIG. 3 schematically shows how the blade 11 moves up and down in the chopper folding apparatus 10 by 45 degrees at the revolving angle of the first external gear 21. Here, the blade 11 and each Only the gears 20 to 21 and 23 to 25 are shown. FIG. 3 is a diagram for simply illustrating the operation state of the chopper folding device 10 in an easy-to-understand manner, and exemplifies an arbitrary state while the chopper folding device 10 is continuously operated. . In addition, a black dot 4 shown in each figure.
Reference numerals 0 to 42 are provided for the sake of convenience in order to clearly show the rotation states of the first external gear 20, the second external gear 21, and the third external gear 24, and are not related to the actual configuration.

First, as shown in FIG.
When the first external gear 21, the third external gear 24, and the second external gear 21
The external gears 20 are arranged on a vertical line indicated by a chain line in the figure. When the rotation driving force is input to the first drum 12 and the first drum 12 rotates, the second drum 13 supported by the circular opening 12d of the first drum 12 via the sleeve 13c also moves together with the first drum 12. Rotate. At this time, the second drum 13 rotates around the axis of the circular opening 12d, but since the support shaft 14a is disposed at the center of rotation of the circular opening 12d, the second drum 13 rotates. Even in this case, the position of the support shaft 14a with respect to the first drum 12 does not change, and the support shaft 14a rotates integrally with the first drum 12.

When the support shaft 14a rotates integrally with the first drum 12, the first external gear 21 and the third external gear 24 supported or fixed on the support shaft 14a are also rotated. It rotates (revolves) together with it. At this time, since the third external gear 24 meshes with the fixed second internal gear 25, the third external gear 24 rotates in the direction opposite to the revolving direction.
Since the ratio between the diameter of the second internal gear 25 and the diameter of the third external gear 24 is set to 2: 1, the third external gear 24 has an angular velocity equal to the revolution angular velocity when viewed from a stationary system. It will rotate in the opposite direction.

The third external gear 24 has a support shaft 14a.
The second drum 13 connected through the third external gear 2
4 and rotates in the direction opposite to the direction of revolution at an angular velocity equal to the revolution angular velocity. A support shaft 16 is supported by the second drum 13, and the distance from the axis of the support shaft 16 to the axis of the support shaft 14 a is determined by the rotation center of the first drum 12 (revolution of the support shaft 14 a). (Center) to the axis of the support shaft 14a. Therefore, the support shaft 1 at this time
The movement of the first link arm is the same as that of the first link arm (the line connecting the rotation center of the first drum 12 and the axis of the support shaft 14a) with the first link arm being rotatable about one end. In a link mechanism composed of a second link arm (a line connecting the axis of the support shaft 14a and the axis of the support shaft 16) whose one end is rotatably connected to the other end, both link arms are connected at the same angular velocity and Second when rotated in the opposite direction
Equivalent to the movement of the other end of the link arm, the support shaft 16 moves linearly on a vertical line. Here, the first drum 12 corresponds to a first link arm, and the second drum 13 corresponds to a second link arm. The second drum 13
Is also fixed to the third external gear 24 and also functions as a support member that rotatably supports the second external gear 21.

On the other hand, since the first external gear 21 revolving integrally with the third external gear 24 is engaged with the fixed first internal gear 23, the first external gear 21 rotates in the direction opposite to the revolving direction. I do. For example, as shown in FIG.
When 1 rotates clockwise by 45 degrees, the ratio of the diameter of the first external gear 21 to the diameter of the first internal gear 23 is 1: 3. It rotates by -135 degrees as viewed from the center of one internal gear 23). When this is viewed from the stationary system, the first external gear 21 has rotated by -90 degrees.

On the other hand, since the second external gear 20 meshes with the first external gear 21, the second external gear 20 has a direction opposite to the rotation direction of the first external gear 21 with respect to the first external gear 21, that is, the second external gear 21. The first external gear 21 rotates in the same direction as the revolving direction. At this time,
Since the movement of the support shaft 16 of the second external gear 20 is restricted in the vertical direction as described above, the first external gear 21
Moves along the vertical line while meshing with the first external gear 21 along with the revolution of the first external gear 21, the distance from the center of the first internal gear 23 to the center of the first external gear 21 and the center of the first external gear 21. Is equal to the center of the second external gear 20, the second external gear 20 is positioned around the first external gear 21 with respect to the first external gear 21 when viewed from a stationary system. It will revolve at -45 degrees. However, the first external gear 21 is -9.
The second external gear 20 relatively rotates to the first
The periphery of the external gear 21 revolves by 45 degrees, and rotates by 45 degrees when viewed from the center of the revolution. The rotation angle when this is viewed from the stationary system is 45-45 = 0 degrees, and the second external gear 2
0 means no rotation. By moving the second external gear 20 on the vertical line without rotating at all in this way, the blade 11 fixed to the second external gear 20 via the support shaft 16 also has a blade edge as in the initial state. Ascend on the vertical line with the vertical direction directly below.

Similarly, when the first external gear 21 further revolves clockwise by 45 degrees from this state, the phases and positions of the third external gear 24 and the second external gear 20 are changed as shown in FIG. ), The blade 11 rises linearly further in the vertical direction with the cutting edge directed right below. When the first external gear 21 further revolves clockwise by 45 degrees, the blade 11 linearly moves up to the position shown in FIG.

Then, the first external gear 21 further revolves clockwise, and as shown in FIG.
When the blade 11 revolves to the position of 0 degrees, the blade 11 reaches the highest point. At this uppermost point, the second external gear 20 is located directly above the first external gear 21 and the first internal gear 23 in the vertical direction. Therefore, the moving distance (stroke) from the lowest point to the highest point of the blade 11 is equal to the first internal gear 23.
And the diameter of the second external gear 20.

After reaching the uppermost point shown in FIG. 3 (e), the blade 11 gradually descends as the first external gear 21 rolls downward. And the first external gear 2
When 1 returns to the initial position again, the blade 11 also reaches the lowest point again as shown in FIG. During the movement from the uppermost point to the lowermost point, the blade 11 also moves linearly with the cutting edge directed straight downward. Then, as the first external gear 21 rolls up again, the blade 11 also rises again toward the uppermost point. In other words, while the rotational driving force is being input to the first drum 12, the blade 11 repeats the above-described elevating operation periodically.

The signature 1 includes upper and lower conveyor belts 2, 2 at a predetermined timing after the blade 11 starts descending.
3 transports the blade 11 directly below the blade 11 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 11 being swung down to the opening 6 a of the table 6, and the signature 2 is divided into two. It is discharged outside in a vertically folded state.

While the configuration and operation of the chopper folding device 10 according to one embodiment of the present invention have been described above, according to the present chopper folding device 10, the blade 11
It is possible to move up and down linearly in the vertical direction while turning the blade vertically downward without rotating the blade. Therefore, the size of the opening 6a of the table 6 is set to the minimum necessary size corresponding to the thickness of the blade 11. Can be set to Therefore, according to the present chopper folding device 10, the blade 11
Can be held by the table 6 with high accuracy at the time of folding, and the effect of improving the folding accuracy of the signature 1 can be obtained.

Although the embodiment of the chopper folding device of the folding machine according to the present invention has been described above, the embodiment of the present invention is not limited to this. For example, in the above embodiment, the ratio between the diameter of the first external gear 21 and the diameter of the second external gear 20 is set to 1: 1. Distance to Center of External Gear 21 and First External Gear 21
If the distance from the center of the second external gear 20 to the center of the second external gear 20 is equal, the ratio between the diameter of the first external gear 21 and the diameter of the second external gear 20 may be set to an arbitrary ratio.

The restricting means for restricting the movement of the center position of the second external gear 20 in the diametrical direction of the first internal gear 23 is not limited to the one using the above link mechanism. The second external gear 20 is fixed by a fixed guide.
May be restricted in the direction of movement of the center position. Further, even when the link mechanism is used, the means for rotating the first link arm and the second link arm at the same angular velocity and in the opposite directions, respectively, may be the second link arm as in the above-described embodiment.
It is not limited to the gear mechanism using the internal gear 25 and the third external gear 24 meshing with the second internal gear 25,
It can be realized using various mechanisms.

[0038]

As described above in detail, according to the chopper folding device of the present invention, the blade can be moved up and down linearly with the cutting edge directed in one direction without rotating the blade.
Therefore, according to the chopper folding device of the present invention, it is possible to set the size of the opening of the table corresponding to the folding opening of the signature to the minimum necessary size according to the thickness of the blade, and to fold by the blade. At times, it is possible to improve the folding accuracy of the signature by holding the signature with a table with high accuracy.

[Brief description of the drawings]

FIG. 1 is a schematic side sectional view showing a configuration of a chopper folding device as one embodiment of the present invention.

FIG. 2 is a view taken in the direction of arrows II-II in FIG. 1 and omits first and second drums.

FIG. 3 is a diagram showing the operation of the chopper folding device as one embodiment of the present invention, and shows the operation in the order of (a) to (e).

FIG. 4 is a schematic sectional side view showing a configuration of a conventional chopper folding device.

FIG. 5 is a view as seen in the direction of arrows XX in FIG. 4;

FIG. 6 is a view showing the operation of a conventional chopper folding device,
The operation is shown in the order of (a) to (e).

FIG. 7 is an explanatory diagram for explaining a problem of a conventional chopper folding device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Signature 2 Upper conveyance belt 3 Lower conveyance belt 4 Stopper 6 Table 6a Opening 7 Rotary roller 10 Chopper folding device 11 Blade 12 First drum 12c Sleeve 12d Circular opening 13 Second drum 13c Sleeve 14a, 14b Support shaft 16 Support shaft 20 Second external gear 21 First external gear 23 First internal gear 24 Third external gear 25 Second internal gear 30 Machine frame 30a Cylindrical surface

Claims (4)

[Claims] 1. A chopper folding device comprising a blade disposed in parallel with the direction of travel of a signature and periodically raising and lowering the blade to perform chopper folding of the signature. An internal gear; a first external gear that meshes with the first internal gear; a second external gear that meshes with the first external gear; and a first internal gear that includes the first external gear. And a regulating means for regulating the movement of the center position of the second external gear on a straight line extending in the diameter direction of the first internal gear. Fixed to a second external gear, a distance from the center of the first internal gear to the center of the first external gear and a distance from the center of the first external gear to the center of the second external gear; Chopper folding device characterized in that: 2. A control device comprising: a first link arm rotatable about one end; a first 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 second link arm rotatably supporting the second external gear at an end; and means for rotating the first link arm and the second link arm at the same angular velocity and in opposite directions, respectively. The rotation center of the one link arm is disposed concentrically with the central axis of the first internal gear, and the rotation center of the second link arm is disposed concentrically with the central axis of the first external gear. The chopper folding device according to claim 1, characterized in that: 3. The means for rotating the first link arm and the second link arm at the same angular velocity and in opposite directions, respectively, is disposed concentrically with the center of rotation of the first link arm. A constrained second internal gear; a third external gear arranged concentrically with the rotation center of the second link arm and meshing with the second internal gear; fixed to the third external gear A supporting member rotatably supporting the second external gear, wherein a ratio of a diameter of the second internal gear to a diameter of the third external gear is 2:
3. The chopper folding device according to claim 2, wherein the setting is set to 1. 4. The apparatus according to claim 1, wherein the third external gear and the first external gear are arranged on the same support shaft, and a rotational driving force is input to the support shaft. The chopper folding device according to claim 3, wherein