JPH0753090A - Signature carrying out device of saddle stitching machine - Google Patents

Abstract

PURPOSE:To realize a smooth high speed operation and a high speed operation of the whole body of the device, by combining a crank mechanism, a cam having a cam groove including a circular arc, and a link mechanism. CONSTITUTION:This signature carrying out device is composed of a carnk mechanism 11 synchronized to a converyng chain to carry out a folding copy book, a cam 12 to limit the tip of the rod 11 a of the crank mechanism 11 by its cam groove 12b including a circular arc through a cam follower 12a, a link mechanism 13 to rotate a driving shaft 11 a regularly and reversely by the cam follower 12a, and a thrust blade 16 connected to the driving shaft 11a through a parallel link 15. The cam 12 has the cam groove 12b with a circular arc form making the length of a link 13a as its radius, and can thrust up the thrust blade 16 to the upper side operating position in a specific rotating angle scope out of one rotation of the driving wheel 11c, and can reset it to the lower side waiting position.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a saddle-stitching machine used in a bookbinding process, and to a signature carrying-out device for a saddle-stitching machine for carrying a signature folded into a predetermined bookbinding unit to the next step.

[0002]

2. Description of the Related Art In a bookbinding process, a saddle stitching machine is used to fold signatures corresponding to a predetermined page unit of a book in a predetermined order and perform a saddle stitching process into a bookbinding unit as needed. Has been done.

The saddle-stitching machine horizontally feeds an endless transport chain provided with a large number of saddle-shaped receivers, and supplies signatures corresponding to predetermined page units on the receivers in order. At the terminal end of the transport chain, the supplied signatures are bound in a predetermined form and then delivered to the next step. here,
The signature is carried out by a push-up blade that intermittently projects upward from between the receiving tools. That is, since the push-up blade can project upward in accordance with the arrival timing of the signatures conveyed by the transport chain and can push the signatures on the transport chain upward, the pushed-up signature is
It can be carried out in order by the carrying-out conveyor arranged above the carrying chain.

Since such a push-up blade must push up a signature on the transport chain properly,
It is usually driven through a plate cam that rotates in synchronization with the sprocket of the transport chain and a cam follower that is constrained by the cam groove of the plate cam.

[0005]

However, the conventional technique has a problem that there is a limit in increasing the operating speed of the saddle stitching machine and improving the overall work performance. That is, the push-up blade must increase the operating speed of the saddle stitching machine, and as the traveling speed of the transport chain increases, the operating time required to push up the signature and return to the original standby position must be shortened. Therefore, it is indispensable to increase the pressure angle of the cam groove for the plate cam that drives the push-up blade.However, if the pressure angle is too large, the impact and wear will be excessive, and smooth operation as a whole will not be possible. Because it will be.

Therefore, in view of the problems of the prior art, an object of the present invention is to combine a crank mechanism, a cam having a cam groove including an arc, and a link mechanism to enable smooth high speed operation. It is an object of the present invention to provide a signature unloading device for a saddle stitching machine that does not hinder the speeding up of the whole.

[0007]

SUMMARY OF THE INVENTION To achieve the above object, the structure of the present invention is a crank mechanism that synchronizes with a transport chain for transporting a signature, and a rod of the crank mechanism via a cam follower with a cam groove including an arc. The gist of the present invention is to include a cam that restrains the tip of the drive shaft, a link mechanism that rotates the drive shaft forward and backward by a cam follower, and a push-up blade that is connected to the drive shaft via a parallel link.

The link mechanism may include a bell crank.

[0009]

According to the structure of the invention, the crank mechanism can reciprocally drive the rod back and forth in synchronization with the transport chain, and therefore the cam moves the tip of the rod up and down in accordance with the shape of the cam groove. Can be made.
Therefore, the link mechanism can push the push-up blade upward through the drive shaft and the parallel link to return it to the standby position below, and the operating curve of the push-up blade at this time is also defined by the shape of the cam groove. can do.

On the other hand, since the cam groove includes an arc, the link mechanism does not drive the drive shaft during the period when the cam follower is in the arc portion of the cam groove (hereinafter referred to as the rest period), and the cam follower is outside the arc portion. The drive shaft can be driven only during a period (hereinafter referred to as an operation period). Therefore, the push-up blade returns to the standby position during the rest period of one revolution of the driving shaft that drives the crank mechanism, and is quickly pushed upward during the operation period to return to the standby position. Can be activated to This is because the push-up blade is connected to the drive shaft via a parallel link, and can be driven up and down by the link mechanism rotating the drive shaft in the forward and reverse directions.

When the link mechanism includes a bell crank,
Since the bell crank can change the input / output operation direction of the link mechanism, the overall degree of freedom in design can be improved.

[0012]

Embodiments Embodiments will be described below with reference to the drawings.

The signature output device of the saddle stitching machine is a crank mechanism 1.
1, a cam 12, a link mechanism 13, a drive shaft 14, a parallel link 15, and a thrust blade 16 (FIG. 1).

The saddle-stitching machine comprises, as main members, endless transport chains 21 and 21 having a large number of receiving members 21a, 21a, ... Projected therefrom (FIGS. 2 and 3). The transport chains 21 and 21 are wound around the sprockets 22 and 22 on the common drive shaft 22a and run in the direction of arrow K1 in FIG.
The front ends of 1a, 21a, ... Are obliquely bent inward so that the pair of facing members form a saddle shape in cross section. Note that pusher plates 21b, 21b, ... Are attached to each transport chain 21 at a predetermined pitch, and each pusher plate 21b comes into contact with a guide rail (not shown) to transport the transport chains 21, 2
In the vicinity of the end portion of No. 1, it can be tilted backward in the traveling direction.

A push-up blade 16 and carry-out conveyors 23, 23 ... Are arranged at the end portions of the transport chains 21, 21.

The push-up blade 16 has a rough tooth 16 on the upper side.
It is a deformed plate material having a, 16a, ..., And is arranged between the transport chains 21, 21. Thrust blade 1
6 has a standby position (the solid line in FIGS. 2 and 3) in which the entirety is sunk between the receiving members 21a, 21a ... And an upper end portion including the teeth 16a, 16a. A projecting operating position (two-dot chain line in the figure) can be taken.
It should be noted that the push-up blade 16 is assumed to move up and down in parallel so that the upper side including the teeth 16a, 16a.

In each of the carry-out conveyors 23, a conveyor belt 23b is wound around a pulley 23a, and a pair of front and rear is arranged above the push-up blade 16 in a double row. However, the front and rear carry-out conveyors 23, 23 face each other with the conveyor belts 23b, 23b facing each other with an appropriate gap g, and each carry-out conveyor 23 has the same speed in the direction in which the facing surface of the conveyor belt 23b moves upward. Driven (Fig. 3
Arrow K2, K2 direction).

The saddle-stitching machine is provided with the transport chains 21, 21.
During the running of the, the signature W of the page unit is sequentially received 2
1a, 21a, etc. are supplied so as to be hung on top, and just before the push-up blade 16 and the carry-out conveyors 23, 23, ..., the supplied signatures W can be bound in a bookbinding unit by a binding mechanism (not shown). After that, when the signature W advances above the push-up blade 16, the push-up blade 16 is pushed up to the operating position, so that the push-up blade 16 moves from the lower end of the carry-out conveyors 23, 23 ...
The signature W can be supplied to the lower ends of the carry-out conveyors 23, 23 ... By inserting the signature W within the gap g (two-dot chain line in FIG. 3). Therefore, the carry-out conveyors 23, 23 ... Can carry out the signature W upward.

The transport chains 21, 21 are assumed to continuously run at a constant speed. Therefore, the push-up blade 16 pushes up the signature W and then immediately lowers it to the standby position to prepare for the arrival of the next signature W. In addition, the pusher plate 21 on the transport chains 21, 21
.. push the rear end of the signature W on the transport chains 21, 21 to prevent the mounting pitch of the signatures W, W ... on the transport chains 21, 21 from being disturbed. However, each pusher plate 21b has a push-up blade 16
The thrust blade 16
The signature W that has been pushed up by is not damaged.

The crank mechanism 11 has a rod 11a (FIG. 1). One end of the rod 11a is eccentrically connected to the drive wheel 11c on the drive shaft 11b. However, it is assumed that the driving shaft 11b is connected to a drive shaft 22a that drives the transport chains 21, 21 of the saddle stitching machine via a gear mechanism (not shown). That is, the drive shaft 11b
Can rotate in one direction in synchronization with the transport chains 21, 21 with an appropriate speed ratio. In addition, rod 1
The tip of 1a is restrained by the cam groove 12b of the cam 12 via the cam follower 12a. However, cam 1
Reference numeral 2 is a fixed plate member having a cam groove 12b which is long in the moving direction of the rod 11a. The cam follower 12a at the tip of the rod 11a is engaged with the cam groove 12b.

The link mechanism 13 has a link 13a,
The arm 1 protruding from the tip of the rod 11a and the drive shaft 14
The tip of 4a is flexibly connected. On the other hand, the parallel link 15 includes arms 14b, 14 protruding from the drive shaft 14.
c, the auxiliary shaft 15a parallel to the drive shaft 14, and the auxiliary shaft 15
arms 15b and 15c protruding from a, and an arm 14b,
And a link 15d connecting the respective ends of 15b. The arms 14b and 15b and the arms 14c and 15c are
They are parallel to each other and set to the same length. A push-up blade 16 is connected to the tips of the arms 14c and 15c (FIGS. 1 and 2).

Now, the drive shaft 11b is the carrier chain 2
4 and 5, the cam follower 12a is connected to the cam 1 through the rod 11a which is eccentrically connected to the drive wheel 11c.
It is possible to reciprocate left and right in the second cam groove 12b.

Therefore, the cam follower 12a is replaced by the cam groove 1
2b, the drive shaft 11b and the drive wheel 1 are referenced with reference to the time point of moving closest to the drive shaft 11b side (solid line in FIG. 4).
Determine the rotation angle θ of 1c. Further, the cam groove 12b has a θ =
From the position (same) of the cam follower 12a corresponding to 0 (degrees) to the position of the cam follower 12a corresponding to θ = θ1 (two-dot chain line in the figure), centering on the connection point A between the link 13a and the arm 14a, It is assumed that the link 13a is formed of an arc having a radius as its length. Also, the cam groove 12b
Is a slightly upward curve from the position of the cam follower 12a corresponding to θ = θ1 to the position of the cam follower 12a corresponding to θ = 180 (degrees) (solid line in FIG. 5). Here, θ1 is 0 <θ1 <18
It is a constant defined as 0 (degrees).

The cam follower 12a is driven via a link mechanism 13 including a link 13a and an arm 14a according to a rotation angle θ by moving a driving shaft 11b and a driving wheel 11c to move right and left in the cam groove 12b. The shaft 14 can be rotationally driven in the forward and reverse directions to drive the thrust blade 16 between the standby position and the operating position (FIG. 6). However,
The vertical axis of the figure shows the rotation angle δ of the drive shaft 14 and the thrust amount h of the thrust blade 16.

First, the cam follower 12a has 0 (degrees) ≤
Even if it moves along the cam groove 12b corresponding to θ ≦ θ1,
The arm 14a is not moved via the link 13a, and the drive shaft 14 is not rotated. The cam groove 12b in the meantime is an arc centered on the connection point A and having a radius of the length of the link 13a.
2a is in a rest period, and the connection point A is the cam follower 12
This is because even if a moves, it does not move up and down and is kept immobile.

Next, the cam follower 12a operates as follows: θ1 <θ
When ≤180 (degrees), the link 13a and the arm 14a
The drive shaft 14 can be rotated in the positive direction (direction of arrow K4 in FIG. 1) by the rotation angle δ via the. Cam follower 1
2a advances to a position farthest from the drive shaft 11b and the drive wheel 11c along the cam groove 12b that bends upward (two-dot chain line in FIG. 1, solid line in FIG. 5), and this period corresponds to the operation period. Therefore, the drive shaft 14 can be normally rotated through the link 13a and the arm 14a.

Next, the cam follower 12a has 180
(Degree) <θ ≤ θ2 (where θ2 = 360-θ1
At (degrees), the drive shaft 14 is reversed by the rotation angle δ (two-dot chain line in FIG. 5). This is because the cam follower 12a is in the operating period and moves in the opposite direction along the cam groove 12b. Further, at the subsequent θ2 <θ ≦ 360 (degrees), the cam follower 12a enters the rest period and the drive shaft 1
Keep 4 dormant.

On the other hand, in this way, the cam follower 12
When the drive shaft 14 is rotationally driven in the forward and reverse directions corresponding to θ1 <θ ≦ θ2 by a, the parallel link 15 can move the push-up blade 16 up and down in parallel. Drive shaft 1
4 rotates in the forward direction, the arm 14b and the link 15
d, the auxiliary shaft 15a is rotated by the same angle in the same direction via the arm 15b (two-dot chain line in FIG. 1), and therefore the links 14c, 15c are simultaneously rotated by the same angle in the same direction to move the thrust blade 16 up. This is because the push-up blade 16 can be returned to the lower standby position when the drive shaft 14 rotates in the opposite direction while the push-up blade 16 is pushed upward (two-dot chain line in FIGS. 1 and 2) (solid line in the same figure). .

The thrust amount h of the thrust blade 16
Is the rotation angle δ of the drive shaft 14 in the forward and reverse directions, the arm 14c,
Determined by the length of 15c, the former is cam follower 1
It depends on the shape of the cam groove 12b corresponding to the operation period of 2a, the length of the link 13a and the arm 14a forming the link mechanism 13, and the like. Therefore, by appropriately selecting these parameters, it is possible to set the optimum push-up amount h = hm for pushing up the signature W.

Further, generally, the driving shaft 11b and the driving wheel 11 are
c is one of the rotations, in which θ1 <θ ≦ 180 (degrees), the push-up blade 16 is pushed up to the operating position,
When (degree) <θ <θ2, it is returned to the standby position. Therefore, the drive shaft 11b is connected to the transport chains 21, 21.
, So that the sprocket 22 is rotated once while the pusher plates 21b, 21b ...
The speed ratio between the drive shaft 22a and the drive shaft 22a may be determined. In addition,
θ = θ1 determines the end of the rest period and the start of the operation period of the cam follower 12a, and the timing of the ascending start of the thrusting blade 16. Also, θ = θ2 = 360−θ1
Defines the end of the operation period of the cam follower 12a, the start of the rest period, and the timing at which the thrust blade 16 returns to the standby position. Therefore, θ1 and θ2 are respectively the pusher plate 2 to which the push-up blade 16 is adjacent.
Appropriate timing may be set so that the signature W between 1b and 21b can be pushed up accurately.

In this mechanism, since the cam groove 12b has a smooth curved shape as a whole, the transport chains 21, 2
Even if No. 1 is operated at high speed and θ2−θ1 ≦ 90 (degrees) is set and the push-up blade 16 is rapidly moved up and down, no substantial trouble occurs.

[0032]

Other Embodiments The link mechanism 13 includes a bell crank 13
b can be included (FIG. 7).

Cam follower 12a and bell crank 13b
Is connected to one end of the drive shaft 14 via the link 13a. The other end of the bell crank 13b is connected to the arm 14b of the drive shaft 14.
And are connected via another link 13c. The arm 14a is omitted here.

The cam groove 12b is composed of a portion corresponding to a rest period of the cam follower 12a and a portion corresponding to a continuous operation period of the cam follower 12a. The former is centered on a connection point A between the link 13a and the bell crank 13b. And link 1
It is composed of an arc having a radius of 3a, and the latter is composed of a slightly downward curve. So, cam follower 12
When a moves to a portion corresponding to the operation period (direction of arrow K5 in FIG. 7) without rotating the drive shaft 14 while moving the portion corresponding to the rest period, the link 13a,
The drive shaft 14 can be rotated in the forward rotation direction (direction of arrow K6 in the figure) via the bell crank 13b, the link 13c, and the arm 14b, and the push-up blade 16 can be pushed up to the operating position via the parallel link 15.

[0035]

As described above, according to the present invention, the crank mechanism, the cam for restraining the tip of the rod of the crank mechanism through the cam follower by the cam groove including the arc, the link mechanism, the drive shaft, and the parallel shaft. By providing the link, the cam groove is made up of a combination of a portion corresponding to the rest period of the cam follower, which is an arc, and a portion corresponding to the operation period, which is a continuous smooth curve, so that the push-up blade is rapidly moved. Even if it is moved up and down, there is no need to include a large pressure angle, and therefore there is an excellent effect that there is no possibility of causing any particular trouble when the overall speed is increased.

[Brief description of drawings]

FIG. 1 is an overall perspective explanatory view

[Figure 2] Usage status explanatory diagram

3 is an enlarged cross-sectional view taken along the line XX of FIG.

[Fig. 4] Operation explanatory diagram (1)

[Fig. 5] Operation explanatory diagram (2)

[Fig. 6] Operation explanatory diagram

FIG. 7 is a schematic explanatory view showing another embodiment.

[Explanation of symbols]

 W ... signature 11 ... crank mechanism 11a ... rod 12 ... cam 12a ... cam follower 12b ... cam groove 13 ... link mechanism 13b ... bell crank 14 ... drive shaft 15 ... parallel link 16 ... thrust blade 21 ... transport chain

Claims (2)

[Claims] 1. A crank mechanism synchronized with a transport chain for signature transportation, a cam for constraining a tip of a rod of the crank mechanism via a cam follower by a cam groove including an arc, and a drive shaft forward and reverse by the cam follower. A signature output device for a saddle-stitching machine, comprising a link mechanism that rotates in a vertical direction and a push-up blade that is connected to the drive shaft via a parallel link. 2. The signature output device for a saddle stitch machine according to claim 1, wherein the link mechanism includes a bell crank.