JP2002096289A - Shredder - Google Patents

Abstract

PROBLEM TO BE SOLVED: To perform fine shredding including the longitudinal shredding and the transverse shredding so that leak-out of secrets can be completely prevented in disposing important documents only by engaging cutting blades of one roll cutter 4 and a fixed blade 3. SOLUTION: This shredder is based on a cutting mechanism constituted by a mechanism in which a paper to be shredded is fed with a predetermined principle to a cutting blade engagement unit of one roll cutter 4 with a plurality of slice cutters for satisfying a cutting process of one element so that the paper to be shredded can be alternately subjected to the longitudinal shredding and the transverse shredding are set up on a cutter shaft 4c with the angular phase difference of the cutter division angle ζ deg./plural number (2 if two slice cutters are provided) with the fixed blade 3 having the same cutting blade shape as the geometrical projected shape of the cutting blade of the roll cutter 4, and its control method.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pair of paper feed guide rollers (1), which are driven to rotate by a single motor, for the purpose of finely cutting a cut sheet in a manner combining vertical cutting and horizontal cutting. (2) and a cutting mechanism composed of a single roll cutter (4) and a fixed blade (3).
And two sets of rotary drive control systems (guide roller side rotary drive series and roll cutter side rotary drive series) incorporating an electromagnetic clutch, etc., and a (shaft free side) guide roller (2) rotary drive mechanism etc. , A shredder capable of completely preventing confidential leakage in the disposal of important documents, etc., and the cutting blades of two slice cutters (A) (4a) and (B) (4b) constituting the roll cutter (4) The present invention relates to various shapes and manufacturing methods.

[0002]

2. Description of the Related Art A conventional shredder generally cuts into a noodle shape (vertical cutting method) using a pair of roll cutters or a fixed blade and a paper feed guide roller. More detailed cutting (horizontal cutting method)
In order to do so, it is necessary to engage another roll cutter with a fixed blade or a pair of special cross-cut blades. The former noodle type cutting method is Japanese Patent Publication No. 6-38925 and Japanese Patent Publication No. 6-47080, and the latter is the horizontal cutting method is Japanese Patent Publication No. 7-87901 and Japanese Patent Publication No. 8-2.
No. 4,853, JP-A-11-169737, and those based on the cross-cut method are described in JP-A-9-99247 and the like.

[0003] The following two methods are generally known as methods for dealing with an excess cutting load. That is, as a means for removing the cut paper sandwiched between the cutters for vertical cutting or horizontal cutting, one method is to rotate the system main body in the reverse direction and return the jammed cut paper in the reverse direction. In this case, the cutting method is a method in which both the vertical cutting and the horizontal cutting cutter are rotated in reverse. Another method is a method in which only the vertical cutting cutter is rotated in the reverse direction without rotating the horizontal cutting cutter in the reverse direction, and the jammed paper to be cut is returned in the reverse direction, similarly to the former (Japanese Patent Laid-Open No. 11-169737). Regarding these two methods, the former causes a slight deviation in the meshing portion of the cutting blade due to the reverse rotation of the cutter more than necessary, which is a factor that shortens the cutting life of the cutter. In the latter case, since the cut paper sandwiched between the horizontal cutting cutters is forcibly pulled out as it is, it is supposed that, as in the former case, the meshing portion of the cutting blade is disturbed and the cutting life of the cutter is impaired.

[0004] Next, regarding the cutting method, see Japanese Patent Application Laid-Open No. 9-992.
Japanese Patent Application Laid-Open No. 11-1697 discloses that the cross-cut cutting method disclosed in Japanese Patent Application Laid-Open No. 47-16747 is capable of performing cutting including horizontal cutting only by engaging two roll cutters.
No. 37, etc., there is an improvement element compared to the two-cut system in which the meshing of two roll cutters and the meshing of one roll cutter and the fixed blade are combined, but two roll cutters are constituted. In order to align the cutting blades of the two types of slice cutters (the starting point of the cutting and the gap between the cutting blades, etc.), a high processing accuracy and assembling accuracy of 1: 1 are required for each divided blade. It is considered that the cutting method is undeniable.

In the noodle type vertical cutting method disclosed in Japanese Patent Publication No. 6-38925, the cost of the cutter itself constituting the cutting mechanism can be expected to be low. There is room for consideration in the balance between the buckling phenomenon and the cutting life of the cutter. In the case of a shredder, it is impossible as a practical matter to set it in expectation of only a standard cut sheet (in size and number of sheets inserted) such as a copying machine. Further, the cutting method is a cutting performed by one cutter blade, and the cutting life (= cutting main length mm / duration h per exchange) due to the wear of the cutting edge is relatively determined based on the configuration of the blade. It is low, and the cutting force of the blade becomes a wedge effect due to the degree of wear of the cutting edge, deteriorating the cutting function of the blade, and it is easily assumed that the buckling phenomenon of the cut paper will occur before and after the contact position of the pair of transport rollers. In addition, since it is extremely difficult to grasp the cutting load in the cutting method, the industrial use range is considered to be extremely limited.

[0006]

As described above, in the conventional shredder, a vertical cutting method is generally used. To add a horizontal cutting, a cutter is further added, or a cutter structure is formed by engaging a special cross-cut blade. Otherwise, it is impossible to prevent confidential disclosure when discarding important documents. In any case, it is unavoidable that the cost required for the cutter (the production cost and the maintenance cost for adjusting the meshing blade, etc.) will increase. Furthermore, subtle irregularities that occur in the engagement of the cutter due to the failure of the treatment for cutting load over, etc. are the biggest factor in shortening the cutting life of the cutter.

[0007]

In order to solve the above-mentioned problem, the present invention is to feed paper by a pair of guide rollers (1) and (2) and fix it to only one roll cutter (4). It is based on a system that incorporates a number of special components described below as a shredder that can cut the paper to be cut into fine pieces combining vertical cutting and horizontal cutting only by engaging with the blade (5).

The pair of guide rollers (1) and (2) are to change the roller interval in accordance with the sheet feeding thickness and to feed the cutting sheet to the engaging portion while firmly holding the sheet to be cut. In addition, the roll cutter (4) is configured as a cutter capable of performing fine cutting that combines vertical cutting and horizontal cutting, so that not only the manufacturing cost of the cutter but also the maintenance cost of the apparatus as well as the cost is low, and the cutter can be cut finely. When discarding important documents, you can expect a high confidentiality leakage prevention effect.

[0009] When the cutting paper is relatively thick and the cutting resistance is higher than an allowable value with respect to the cutting load over, the cutting paper becomes the cutting blade of the roll cutter (4) and the fixed blade (3). , The rotation of the motor (5) stops, and the motor (5) is switched to reverse rotation by the overload current control signal. The reverse rotation driving force acts on the gear rotation drive system of the shredder. However, the control system of the gear rotation drive system makes the reverse rotation drive force a rotation drive mechanism that first acts only on the roll cutter (4). We are.

[0010] The above-mentioned reverse rotation driving force causes the roll cutter (4) to exert a minimum necessary reverse rotation angular displacement before the cut sheet is released from being caught between the roll cutter (4) and the fixed blade (3). A reverse rotation driving device by a system control of a mechanism for returning the cut sheet to the original insertion opening position by the reverse rotation of the pair of guide rollers (1) and (2) after the cut sheet is released from being caught. Since the shredder is equipped with a cutting blade, no unnecessary external force is applied to the engaging portion of the cutting blade between the roll cutter (4) and the fixed blade (3), so that the engagement of the cutting blade may be slightly disturbed or the cutting blade may be damaged. It is not coming.

[0011]

BEST MODE FOR CARRYING OUT THE INVENTION The present invention provides a pair of paper feed guide rollers and a one-roll cutter side with a single motor to give synchronized rotation angles to a pair of paper sheets to be cut. Paper is fed by the guide rollers (1) and (2), and one of the roll cutters (4) incorporated in the one-roll cutter drive system and the fixed blade (3) engage with the cutting blade to discard important documents and the like. With a shredder that uses a so-called “one-roll cutting system”, it is possible to perform a fine cut that combines vertical cutting and horizontal cutting with a single cut to the extent that confidential leakage can be completely prevented. There is. The ratio of the angular displacement between the roll cutter (4) and the guide rollers (1) and (2) is a constant value and is one of the important factors that determine the size of the cut paper.

The outer peripheral portions of the pair of paper feed guide rollers (1) and (2) for feeding the paper to be cut are made of rubber lined with a thickness of several mm and having a high coefficient of friction.
One is a fixed shaft type and the other is a shaft free type bearing. The gap between the roller shafts is generated according to the thickness of the cut paper, and the cut paper is constantly held down by the spring pressure. ， It has a structure that can surely fulfill the paper sending function.

The so-called "ball rolling contact drive system" is adopted for rotating and driving the paper feed guide roller (2) on the free bearing side by contacting 4 to 6 balls most easily adapted to both the drive side and the driven side. , And guide rollers (1) and (2) adopt a structure that does not cause phase unevenness in the rotation angle of both.

The roll cutter (4) is constituted by a combination of two slice cutters (A) (4a) and (B) (4b) having different cutting blade shapes. It is set up on the cutter axis (4c) with a rotation angle phase difference (= blade division angle ζ ° / 2) between two slice cutters. On the other hand, the fixed blade (3) is formed by grinding with the same cutting blade shape as the geometric projection shape of the cutting blade of the roll cutter (4).

The cutting blade shapes of the slice cutters (A) and (B) are conceptual blade shapes capable of sufficiently performing a cutting function capable of performing fine cutting combining vertical cutting and horizontal cutting. Cutting blade shapes such as straight blades, R-shaped blades, corrugated blades, single shapes consisting of a circle, a part of a circle, an ellipse, a part of an ellipse, etc., and composite shapes consisting of combinations thereof are conceivable. However, in FIG. 32, as an example, as one example, the slice cutter (A) is a composite cutting blade shape combining the simplest semicircle and two straight lines, and the slice cutter (B) is a simpler cutter. It is shown with a single cutting blade consisting of one straight blade.

One of the key points in the configuration of the roll cutter (4) is to reduce the cutting load, so that the cutting blades of both the slice cutters (A) (4a) and (B) (4b) have scissors effects. That is, when adopting a cutting blade shape provided with a scissor effect (= cutting edge angle: α °) and a cutting angle (β °), when assembling to the cutter shaft (4c),
The configuration is such that the helical angle (θ °) based on the setting value of the cutting blade is adopted for each row of the slice cutters (A) and (B).
Therefore, it is possible to drive the gear rotation drive system of the whole system with the motor (5) whose output (KW) of the rotation drive motor is relatively small.

Since the cutting blades of the two slice cutters (A) and (B) shown in the examples of the present invention have simple shapes, it is possible to reduce the manufacturing cost. And these two slice cutters (A)
It is also possible to relatively easily adjust the engagement of the cutting blade between the roll cutter (4) composed of the combination of (4a), (B) and (4b) and the fixed blade (3).

On the other hand, the paper feed guide rollers (1) and (2)

By providing a rotation angle corresponding to the amount of the ratio synchronized with the rotation angle phase difference described in the section, the cutter blade meshing portion between the roll cutter (4) and the fixed blade (3) is provided with one of the cutters. Since the cut paper is always sent with a constant paper feed length per blade engagement, fine cutting becomes possible.

When a large amount of paper is fed and a load exceeding the cutting capability is generated, the roll is caught between the roll cutter (4) and the fixed blade (3) by electric control by an overload current detecting device. In order to release the cut paper from being pinched, the reverse rotation angular displacement necessary for releasing the cut paper is given only to the roll cutter (4), and the cut paper is divided into two cutters, namely, the roll cutter (4) and the fixed blade (3). ) Will be free from the state sandwiched between. During this time, the paper feed guide rollers (1) and (2) are a control mechanism that stops standby while the shaft is electrically fixed. Therefore, it is possible to avoid damage to the cutting blade or subtle irregularities that occur at the cutting blade meshing portion due to forcible pulling out of the cut paper while being held between the two cutters.

After the roll cutter (4) is given the reverse rotation angular displacement within the set range, the roll cutter (4) is electrically fixed to the shaft and does not transmit the rotational driving force. I will wait while doing. The roll cutter (4) should be inverted more than necessary to prevent the engagement of the fixed sword (3) and the roll cutter (4) from being damaged or out of order in the course of the countermeasure for the cutting load over treatment. A rotation drive control method that does not rotate is adopted.

At the same time as the roll cutter (4) is electrically fixed and stopped, the pair of guide rollers (1) and (2), which have been fixed electrically, are released from the fixed shaft and cut while rotating backward. Return the paper to the shredder insertion slot position. This reverse rotation is performed within a minimum time necessary to return the cut sheet to the cut sheet insertion slot with a set range of angular displacement, and thereafter, the guide rollers (1) and (2) are automatically turned. Will stop rotating. At the same time as the rotation of the guide rollers (1) and (2) stops, the roll cutter (4), which has been electrically fixed to the shaft, is released from the fixed shaft and the system main body returns to the standby state for restart.

The contact surfaces of the pair of guide rollers (1) and (2) can be generally classified into two types: line contact and surface contact. The former is a contact surface formed of a non-planar concave / convex meshing surface which is a flat cross section obtained by developing the outer periphery. As an example of the latter, it is conceivable that meshing teeth such as corrugated teeth, chevron teeth and rack teeth are engaged, and it is assumed that the self-advancement function of the remainder of the previous cut paper by the subsequent cut paper will be added. Also, the cut paper considered as a shredder cannot be limited to a fixed form, and it is necessary to meet the needs of the range of use and to make surface contact according to what kind of cut paper is targeted. It is necessary to choose whether to make contact or line contact. In particular, when surface contact is required, it is necessary to select the type of meshing teeth and the size of the shape within the range that does not hinder the cutting function from the size of the cutting piece, that is, the configuration size of the cutting blade. .

FIG. 17 shows, as an example of surface contact, a pair of guide rollers (1) and (2) each having a corrugated meshing surface.
Shows the state where the roll cutter (4) and the fixed blade (5) are assembled to the shredder as a means of sending the cut paper to the meshing portion of the cutting blade. Guide rollers (1) and (2)
The contact surface has a certain malleability ξ (= wave pitch P / wave height W) and a helical angle δ ° (= lead angle) in order to add a function of self-feeding the remaining cut paper. The shape of the wave engagement surface is made of hard rubber, and the cut paper will be plasticized and fed into a shape similar to the cross-section of the developed outer surface of the guide roller (see Fig. 18). In addition, the helical angle (δ °) adopted together with the malleability ξ is the same as the shape of the sheet to be cut developed on the outer peripheral surface of the guide roller due to the engagement of the pair of guide rollers (1) and (2) formed by surface contact. The purpose is to avoid the occurrence of curl phenomena that are plasticized to a similar shape and hinder the self-feeding function of cut paper.

When the guide rollers (1) and (2) are removed from the system for maintenance of the system, especially for the free bearing side guide roller (2), the set bolts (31c) and (33c) are loosened to loosen the roller. The structure is such that it will not hinder reassembly even if it is removed with the spring pressure of the shaft holder (18).

[0025]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments will be described with reference to the accompanying drawings. FIG. 1 shows a case where the cut paper is a pair of guide rollers (1),
Based on (2), the cutting mechanism is fed into the cutting blade meshing portion between the fixed blade (3) and one roll cutter (4), and is capable of fine cutting in which vertical cutting and horizontal cutting are alternately performed. This is a diagram showing a cross section where the paper to be cut is finely cut at the cutting section of the shredder.

FIG. 2 is a diagram showing a mechanical rotation drive system mainly composed of a system. The rotary drive system consists of two drive systems, both of which are rotationally driven by one motor (5). Fine cutting is achieved by the synchronous operation of these two elements. The two elements, namely, one is a drive system of a pair of guide rollers (1) and (2) for sending the cut paper to the meshing portion of the cutting blade, and the other is the sent cut paper. This is the drive system of one roll cutter (4) that cuts the roll. In order for these two elements to function synchronously, a pair of guide roller side drive trains (M-3-
4-5-G1-G2) and the drive system on the roll cutter side (M-
1-2-C) and the rotation ratio that enables fine cutting is set. Further, double clutches U and W and an electromagnetic clutch (1) by a mechanical mechanism for reverse rotation drive control are included in each drive system.
3) The clutch shaft incorporating (25) (the clutch shaft (12) for the guide roller side drive system and the clutch shaft (26) for the roll cutter side drive system) is incorporated.

Further, in FIG. 2, the guide roller (2) in the guide roller side drive system is free of axis in a linear direction connecting two guide roller shaft centers G1 and G2.
Depending on the thickness of the cut paper, a pair of paper feed guide rollers (1)
The structure is such that the gap between (2) and (2) changes.

FIG. 3 is a diagram showing a drive system on the guide roller side and the roll cutter side. The rotational driving force on the guide roller is transmitted in the order of M-3-4-5-G1-G2. The clutch shaft (12) has a clutch function consisting of a mechanical mechanism type double clutch U and an electromagnetic clutch (13), and performs on / off operation of reverse rotation drive.

Similarly, the rotational driving force in the gear rotary driving system on the roll cutter side is transmitted in the order of M-1-2-C. The clutch shaft (26) has a clutch function that includes a mechanical mechanism type double clutch W and an electromagnetic clutch (25), and performs reverse rotation drive on / off operation.

The clutch function of the double clutches U and W is performed by a double clutch of a saw tooth clutch engagement tooth (A) and a chevron clutch engagement tooth (B). The details of the double clutch U and W parts and the clutch meshing teeth (A) and (B) are shown in Figs.

When it is necessary to release the cut paper sandwiched between the roll cutter (4) and the fixed blade (3) due to an excessive cutting load, the roll cutter (4) is reversed by a certain rotation angle. You need to rotate it. During the reverse rotation of the roll cutter (4), the cut paper sandwiched between the fixed blade (3) and the roll cutter (4) is forcibly pulled out by the rotation of the guide rollers (1) and (2). Guide rollers (1) and (2)
It is necessary to stop the rotation of. In order to satisfy these two functions, the electromagnetic clutch (13) of the clutch shaft (12) should be provided at the same time as the reverse rotation start by the overcurrent detecting device for the overload of the cutting of the motor (5), or before the necessary minimum time. ) To ON and clutch shaft (12)
To the shaft fixed state.

The reverse rotation driving force from the motor (5) is applied to the gear (M2) -gear (3) in the guide roller side drive system.
A / 3B) -gear (4A) and the spline shaft (3
5) is rotated in the reverse direction, but since the clutch shaft (12) is fixed, the clutch meshing tooth (B) resists the frictional force due to the tension of the coil spring (36), causing a slip phenomenon and causing a spline. Since the shaft (35) moves in the OFF direction, only the gears (4A) and (10) rotate, and the gear (4) rotates.
B) Since the rotational force is not transmitted to (11), the guide rollers (1) and (2) cannot rotate in reverse (Fig. 7,
9, 10).

The electromagnetic clutch (1) of the clutch shaft (12)
While 3) is ON, the electromagnetic clutch (25) of the clutch shaft (26) on the roll cutter drive system side is OFF, so that the clutch shaft (26) is in the shaft free state and the motor ( The reverse rotation driving force from 5) to the clutch shaft (26) is the frictional force of the clutch meshing teeth (B) due to the tension of the coil spring (36), and is the driven gear (1B).
(24) and from the gears (2) and (22) to the gears (C) and (20), so that the roll cutter (4) rotates in the reverse direction (see Figs. 8, 9 and 10). ).

The amount of reverse rotation angular displacement required to release the applied cut paper to the roll cutter 4 is applied to the roll cutter shaft (4).
c) The electromagnetic clutch (25) of the clutch shaft (26) of the cutter side gear drive system is turned on by reading by the rotational angular displacement detecting device (21) incorporated at the end of the drive side shaft of (c). To the shaft fixed state. Simultaneously or after the minimum necessary time, turn off the electromagnetic clutch (13) of the clutch shaft (12) of the guide roller side gear drive system.
To make the clutch shaft (12) free.

The reverse rotation driving force from the motor (5) is applied to the gears (M1) and (6) in the roll cutter side gear drive system.
From the gear (1A) (23) to the spline shaft (3
5) is rotated in the reverse direction, but since the clutch shaft (26) is fixed, the clutch meshing tooth (B) slides on the meshing tooth surface against the frictional force caused by the tension of the coil spring (36). A phenomenon occurs, and the spline shaft (35) moves in the OFF direction, so that only the gears (1A) and (23) rotate, and the rotational force is not transmitted to the gears (1B) and (24), and the roll cutter (4) rotates in reverse. Is no longer possible (Fig. 8,
9, 10).

On the other hand, in the guide roller side gear drive system, the reverse group rotation driving force is expressed by the gear (M2) -the gear (3A) /
(3B)-transmitted to the gear (4A) to reversely rotate the spline shaft (35). The reverse rotation force of the spline shaft (35) is generated by the frictional force of the clutch meshing tooth (B) due to the tension of the coil spring (36) because the clutch shaft (12) is in the shaft free state. 4
B) The gear (4A) / (4B) -gear (5) -gear (G1A) /
It is transmitted in the order of (G1B) -gear (G2) and reverses the guide rollers (1) and (2) (see FIGS. 7, 9, and 10).

The cut paper, which has been released from being caught between the fixed blade (3) and the roll cutter (4), is rotated by the aforementioned reverse rotation of the guide rollers (1) and (2), so that the insertion position of the cut paper in the shredder is changed. Will be returned to During this time, that is, while the guide rollers (1) and (2) are rotating in reverse, the clutch shaft (26) of the gear rotation drive system on the roll cutter side
However, since the shaft is fixed by the electromagnetic clutch (25), the reverse rotational force is transmitted from the gears (1A) (23) to the gear (1B).
Regardless of (24), the roll cutter (4) is kept on standby in a stopped state.

For a set period of time,

From

While the roll cutter (4) is in a standby state of stopping the rotation, the pair of guide rollers (1),
(2) rotates in the reverse direction to return the cut paper with the cutting load over to the position of the cut paper insertion slot of the shredder. After a series of corresponding actions are completed, the motor (5) is stopped, and the clutches of both drive systems are stopped. The electromagnetic clutch (1) of shafts (12) and (26)
3) and (25) are both in the OFF state, the main system of the shredder system is stopped, and the control system is kept in standby until the next start.

The pair of guide rollers (1) and (2) are formed so that the free shaft side guide roller (2) is formed of two guide roller shaft centers G1 and G in order to cope with a change in the thickness of the cut paper.
It is a guide roller with a free adjustable style bearing structure that can move on the extension of the straight line connecting 2. One of the features of the shredder is that it supports the function of fine cutting with such a structural style.

FIG. 4 is a view showing a rotation driving mechanism of the shaft-free guide roller (2) of the pair of guide rollers (1) and (2). Since the thickness of the cut paper is not always constant, a free-adjustable type bearing structure in which the distance between the axes of the pair of guide rollers (1) and (2) can be changed according to the thickness of the cut paper. If you do not, you will not be able to send the paper with the cut paper firmly held down. In order to transmit the rotational driving force to the shaft-free guide roller (2) having a bearing structure of this type, the ball is easily adapted to the displacement of the distance between the shafts of the two guide rollers and has a small rotation angle displacement unevenness. (29) and guide ring (2
8) The most preferable method is to use a method using a rotational driving force that acts at a right angle on the locus of movement of the contact point with the point of contact, that is, the “ball rolling contact drive method”.

The device has a structure in which the rotational driving force is transmitted by contacting four to six balls. The rotation driving ball (29) is supported by a ball base (27) embedded in the end surface of the shaft-free side guide roller (2), and is supported on the inner surface of a guide ring (28) embedded in the housing (31d) on the bearing side. The structure adopts a mechanism that transmits the rotational driving force by moving the ring inner surface while contacting and rolling.

FIG. 5 is a view showing a state in which a pair of guide rollers (1) and (2) are incorporated as components of the apparatus. The outer periphery of the guide roller is characterized by line contact, and the guide rollers (1) and (2) are each lined with a rubber layer having a thickness of several mm, so that the paper to be cut and the guide rollers (1) and (2) are separated. I try not to slip. The axial thrust of the guide roller (2) has a ball friction thrust structure with the lowest coefficient of friction. Further, a roller shaft retainer (18) and stopper retainers (19), (34) and the like are incorporated in the bearing portion of the guide roller (2), and the guide is guided as described in the above-mentioned "Embodiment of the invention". The structure is such that the roller (2) can be easily attached and detached.

FIG. 6 shows a state in which the roll cutter (4) is incorporated as a component of the device.
This roll cutter (4) is composed of two types of slice cutters (A) (4a) and (B) (4b). The slice cutters (A) (4a) and (B) (4)
b) is attached to the cutter shaft (4c), an angular phase difference corresponding to the helical angle (θ °) according to the setting value of the cutting blade is provided in both the cutter rows of (4a) and (4b), and (4a). ) And (4b), the cutting blade division angle ζ ° / 2
The roll cutter is set up alternately with an angle phase difference of, and meets the cutting function that can alternately cut the cut paper vertically and horizontally.

In order to avoid an error in reading the reverse rotation angular displacement in the measures for overloading the cutting force of the roll cutter (4), the rotation angular displacement detection device (21) is directly mounted on the drive-side shaft end of the roll cutter (4). You. In addition, roll cutter (4)
Can be attached and detached by removing the bearing nut (4f) on the non-drive side and pulling out the bearing together with the drive side, and the flange (B) from the cutter shaft (4c).
By removing (4e), the slice cutters (A) (4a) and (B) (4) are independent of the drive-side bearing.
b) can be removed from the cutter shaft (4c).

The left side of FIG. 11 is a diagram showing the rotation drive mechanism of the guide roller (1) and the guide roller (2) having a free-adjustable type bearing structure. The rotational driving force is expressed as gear (15) / (16) -gear (G2) (1).
It is transmitted to 7).

The rotational driving force to the shaft fixed side guide roller (1) is drawn by pulling the guide roller (1) toward the shaft (G1A) (30a) with a set bolt (30c), and the shaft side rotational drive key (30b). ) Transmits the turning drive force from the gear (G1A) (15). The rotation driving force to the shaft free side guide roller (2) is transmitted from the gears (G2) and (17), but the transmission from the gears (G2) and (17) is performed through the ball (29). The ball (29) is supported by a ball base (27) embedded in the side surface of the guide roller on the shaft free side, and the guide ring (2) embedded in the housing (31d) of the bearing (31) on the fixed shaft side.
8) It has a structure to transmit the rotational driving force while contacting the inner surface. It is preferable to provide four to six balls so that phase unevenness in rotational angular displacement between the driving side and the driven side does not occur.

The guide roller (2) has a drive-side bearing (G
2A) A roller housing (18) comprising a spring housing (18d), a stopper socket (18b), a coil spring (18c), a stopper piece (18a), etc. incorporated in a sleeve (G2A) (31a) of (31). It can be pressed against the guide roller (1). Therefore, the cut paper inserted into the shredder does not slip or slip between the two guide rollers (1) and (2), and the fixed blade (3)
The paper can be reliably fed to the area where the roller and the cutter (4) engage.

When it is necessary to remove the guide roller (2) from the apparatus for maintenance reasons, the drive-side bearing (G2A) is set so that the stopper piece (18a) of the roller retainer (18) is not exposed more than necessary. One of the features of this device is that the stopper (G2A) (19) is incorporated in the sleeve in (31).

The right side of FIG. 11 shows the non-drive side bearings (G1B) (3) of the pair of guide rollers (1) and (2).
It is a figure showing the details of 2), (G2B) (33).
The bearing structure adopts the same method as that of the drive side, and the roller shaft retainer (18) and the stopper retainer (G2B) (34) are incorporated in the bearing (G2B) (33) to form the shaft-free side guide roller (2). Supports a free-adjustable bearing function.

When the guide roller (2) is removed from the apparatus for maintenance of the shredder, the stoppers are suppressed by loosening the set bolts (31c) and (33c) (G2A) (19) and (G2B). (34)
Is pushed out to the roller shaft holding (18) side by the tension of the coil springs (31b) and (33b) while being in close contact with the shaft end of the guide roller (2), and the stopper piece (18) is pressed.
a).

When assembling the guide roller (2) to the shredder again, if the guide roller (2) is inserted while being pressed against the stopper (G2A) (19) at the shaft side end surface, the stopper of the roller shaft retainer (18) is inserted. Peace (18a)
Is mounted on the outer circumference of the shaft of the guide roller (2), and the tension of the coil spring (18c) acts on the guide roller (2) via the stopper piece (18a). The same mechanism on the non-drive side supports the bearing function of the shaft-free guide roller (2).

FIG. 12 shows the drive-side bearings (G1A) (30) when the guide rollers (1) and (2) are removed.
(G2A) (31) and bearing on opposite side of drive (G1B)
It is a figure showing the details of (32) and (G2B) (33). To remove the guide roller (1), use the bearing (G1
A) Set bolts (3) of (30) and (G1B) (32)
0c) and (32b), and remove the bearing (G1B)
After pulling out (32), the guide roller (1) can be pulled out from the bearing (G1A) (30) and removed.

To remove the guide roller (2), the set bolts (31c) and (33c) of the bearings (G2A) (31) and (G2B) (33) are loosened to the maximum extent, and the bearing (G2B) ( After removing the set bolt (33d) of 33) and pulling out the bearing (G2B) (33),
The guide roller (2) can be removed by pulling it out from the bearing (G2A) (31).

The bearing (G2B) (33) is moved from the system frame, and the guide roller (2) is moved from the bearing (G2A).
When pulling out from (31) respectively, bearing (G2A)
(31), (G2B) (33), and (G2A) (19) and (G2B)
B) Pull out the end surface of (34) so as not to be separated from both shaft end surfaces of the guide roller (2), and hold down both roller shafts (18).
Of the stopper piece (18a)
A) It is necessary that it is mounted on the outer circumference of the shaft of (19) and (G2B) (34) in order to reassemble.

FIG. 13 is a diagram showing a clutch mechanism that performs switching operation between reverse rotation and stop, which have a lower required torque value than normal rotation, in a plurality of general rotary drive series mechanisms. The clutch mechanism comprises a double clutch U (W), a clutch shaft (12) and a clutch shaft (26) by a mechanical system including clutch meshing teeth (A) and (B) shown in FIGS. Electromagnetic clutch (1)
3) and (25). The concept of the meshing mechanism of the electromagnetic clutch is to fulfill its function by joining and disengaging concave and convex articles (including holes).

In the present invention, meshing teeth such as a radial rack type and a spiral rack type formed in the radial direction as shown in FIGS. FIG.
The electromagnetic clutch shown in FIG. 2 has two clutch teeth composed of such meshing teeth, that is, the moving clutch teeth (A) (13).
f) and fixed side clutch teeth (B) (13g).

The armature (13d) guided by the spline shaft (13c) against the tension of the coil spring (13i) by the magnetic force when the excitation coil (13a) is energized causes the moving-side clutch teeth (A) (13f) to energize. , The clutch teeth (A) (13)
(f) and (B) (13g) mesh with each other, and the clutch shaft is fixed, and the rotational driving force cannot be transmitted.

The moving clutches (A) and (13f) generate no magnetic force unless the excitation coil (13a) is energized. Therefore, the armature (13) is tensioned by the coil spring (13i).
d) is pressed until it comes into contact with the stopper (13e), and the clutch teeth (A) (13f) are engaged with the clutch teeth (B) (1).
3g) is disengaged from the clutch shaft, and the clutch shaft becomes free and the rotational driving force is transmitted.

The clutch teeth (A) (13f) and (B)
(13g) are both made of non-ferrous agents (rubber, resin or aluminum alloy, etc.) that are hard and have high wear resistance.
Amateur (13d) and clutch base (1
3h) Molded by baking mold or casting. Therefore, a large molded product is expected to be used in terms of manufacturing costs, because a molded product that is not machined is used as the clutch component.

In this shredder, in particular, the clutch shaft (26) needs to engage the clutch teeth (A) (13f) and (B) (13g) during rotation. Since the impact of the rotational force including the inertia torque acting on the meshing teeth (C) is buffered by the coil spring (36) of the mechanical clutch W, the stress applied to each tooth of the meshing tooth (C) is extremely small. This is one of the features of the clutch shaft configuration.

FIG. 16 is a diagram showing a detection head portion of a rotational angular displacement detecting device for reading the amount of reverse rotational angular displacement given to the roll cutter (4). The disk (21a), the sensor head (21b) and the sensor ( 21c). The disk (21a) is provided with micro-holes or graduations at equal angular intervals at a certain angle, and is incorporated into the roll cutter shaft (4c) to form the roll cutter (4).
It will rotate at the same time. The sensor (21c) reads the amount of rotation angular displacement based on the fine hole or graduation line that is moved by the rotation of the disk (21a), and sends a pulse signal corresponding to the amount of displacement to rotate the roll cutter (4). We adopt a method to detect the amount of angular displacement. The detection performance required to control the rotation function of the shredder is a detection accuracy of ± 1 ° in angle units is sufficient, so there is no need to use a high-resolution rotation angle displacement detection device including a known encoder.

FIG.

DETAILED DESCRIPTION OF THE INVENTION

Based on the contents described in the paragraph, the cut sheet is plastically deformed into a shape similar to the developed shape of the cross section of the roller contact surface by bringing the roller contact surface into surface contact. This is an example showing the state of assembling a pair of guide rollers (1) and (2), which is a feature.

The roller surface has a certain value of malleability ξ (= wave pitch P / wave height) and helical angle δ °
(= Lead angle), which is lined with a rubber layer having a thickness of several mm consisting of a wave surface formed with a lead angle. The roller surface is a wave surface, and the contact surface between the pair of guide rollers (1) and (2) is a wave meshing surface. Guide rollers (1),
This will enhance the paper feed function of (2). In addition, by adding a helical angle (δ °), the self-feeding function of the cut paper produced by plastically deforming the cut paper into a wave shape with a certain malleability (ξ) is impeded. It is possible to avoid the occurrence of such a curl phenomenon (Fig. 1
8).

FIG. 19 is a diagram showing the outer shapes of the cutting blades of the slice cutters (A) (4a) constituting the roll cutter (4). This shape is

DETAILED DESCRIPTION OF THE INVENTION

As described in the section, this is an example of a composite-shaped cutting blade that can sufficiently fulfill a one-cut function based on a fine cutting mechanism that combines vertical cutting and horizontal cutting.

As the cutting blade, one R-section cutting blade and two straight-section cutting blades are continuously formed, and the scissors effect, that is, the scissors effect, the cutting blade angle (α °) and the cutting angle (β °) are used. It is that it is formed by grinding. Furthermore, since the outer circumference of the R-section cutting blade is maintained at the cutter outer dimensions, the cutting blade does not change its shape due to refinishing grinding. If necessary, a relief pocket for machining for grinding is formed in advance on the inside of the cutting blade surface as required, so that grinding can be easily performed (see FIG. 20).

FIG. 21 is a view showing a cutting blade section of a slice cutter (A) which satisfies a mechanism of a cutting mechanism capable of performing fine cutting combining vertical cutting and horizontal cutting.

FIG. 22 is a view showing the positional relationship between the cutter and the grinding wheel when grinding the R portion of the slice cutter (A) (4a). The cutter must be shifted steplessly while maintaining the relative position between the 180 ° rotation about the center of the R-section cutting blade and the vertical movement of the cutter (movement corresponding to the sword angle α ° of the cutting knife). With this, it is possible to perform the grinding process to add the cutting edge angle (α °) to the cutting blade surface of the R section ((b)-(c) cutting section in FIG. 21) (FIG. 23). reference).

FIG. 24 shows the slice cutter (A) (4a).
It is a figure which shows the positional relationship between the cutter and the grindstone when grinding the straight part cutting blade. The cutter is set at a position perpendicular to the grinding wheel axis. The grindstone head is moved along a grindstone base with an inclination angle (α °) equal to the angle of the cutting edge (α °) of the cutting blade. When grinding the left straight cutting edge (c)-(d) of FIG. 21, the grindstone head is turned to the left at the position where the slice cutter (A) (4a) is turned to the left by 90 ° in FIG. When grinding the right side straight cutting edge (a)-(b) of No. 21, move the grindstone head to the right at the position where it is turned 90 ° clockwise to perform the grinding. The movement of the grinding head to the left and right is performed along the grinding wheel base with the inclination angle α ° shown in FIG. By adjusting this basic relative movement with the stepless shift of the slice cutter (A) (4a) in the vertical direction, the cutting blades of the R portion and the straight portion can be performed from rough grinding to finish grinding. It is possible.

FIG. 25 is a graph showing the angle (α °) of the cutting edge attached to the cutting blade of the slice cutter (A) (4a) ground by the method described above, that is, the scissors effect (α) of the cutting blade.
°).

FIG. 26 is a diagram showing the external shapes of the cutting blades of the slice cutters (B) and (4b) constituting the roll cutter 19 (4). This shape is

DETAILED DESCRIPTION OF THE INVENTION

As described in the section of FIG.
Based on the mechanism of the cutting mechanism that can perform fine cutting shown in
This is an example of a single shaped blade that can fully fulfill the one-cut function. The cutting blade is a single straight cutting blade, which is ground and formed with a cutting edge slur angle (α °) and a cutting angle (β °) as a scissors effect, similar to the slice cutter (A) (4a). . Further, since the trajectory of the straight cutting blade on the circumference has the shape of a cutting blade, the cutting blade does not change its shape due to the refinish grinding of the cutting blade.

FIG. 27 shows the slice cutter (B) (4b).
FIG. 4 is a view showing a positional relationship between a cutter and a grinding wheel when grinding the linear cutting blade of FIG. Slice cutter (B) (4
Since the cutting blade of b) is a single-shaped blade composed of a straight blade, the cutting blade portion grinding and shaping operation does not require the turning operation of the cutter as in the slice cutters (A) and (4a). Thus, the grindstone head only has to move along the grindstone head base having an inclination angle (α °) equal to the cutting edge angle (α °) of the linear cutting blade. The relative movement between the left and right shift of the grindstone head and the stepless up and down shift of the cutter at the relative position between the slice cutter (B) (4b) and the grindstone head as described above results in rough grinding of the cutting blade. Grinding can be performed (see Figs. 28 and 29).

FIG. 30 is a diagram showing an example of the blade shape of the cutting blade of the fixed blade (3). This shape is

DETAILED DESCRIPTION OF THE INVENTION

[0015] As described in the above section, the two slice cutters described above as an example of single and compound blades capable of sufficiently fulfilling the one-cut function based on the fine cutting mechanism shown in FIG. (A) (4a) and (B) (4
b) The cutting edge of the cutting blade having the same shape as that of the geometric projection of the cutting edge of the roll cutter (4) whose component is (b), and a female cutter comprising an R portion and a straight portion. It is a figure.

FIG. 31 is a diagram showing the fixed blade (3) corresponding to each blade point of the slice cutter (A) (4a) shown in FIG. 21, that is, the cutting blade point of the female blade.

In the above-mentioned female cutter, that is, the fixed blade (3),
A so-called one-cut, in which vertical cutting and horizontal cutting are alternately performed by meshing a male cutter, ie, a roll cutter (4), which is formed with a cutting edge angle (α °) of the cutting blade. Fine cutting by function is possible. The fine cutting mechanism (Fig. 32) is the most important feature of the shredder based on the "one roll cutting system".

FIG. 32 shows a pair of guide rollers (1),
It is a figure which shows the basic element of the cutting process performed by the cutting blade meshing of the fixed blade (3) and the roll cutter (4) driven by the motor (5) of the same rotary drive source as (2). This cutting blade shape is the same cutting blade shape as the geometric projection of the cutting blade based on an example of the composite shape of the roll cutter (4). 1) In the X section position (1), the cut sheet has a width of t ₂ × L ₂
It is cut by the slice cutter (B) to the size of. From the start of cutting of 2) position (1), further, a roll cutter (4) is, during the rotation by blades division angle zeta ° / 2, will come L ₁ only to be cut paper is sent. The feed position of the cut sheet at this time is position (2), and in this position, the slice cutter (A) (4a)
The shaded portion of the cutting blade is cut. From the start of cutting of 3) Position (2), further to be cut paper while the roll cutter (4) is rotated by blades division angle zeta ° / 2 will come only sent L _1. The feed position of the cut paper at this point is position (3), and in this position, the diagonal lines of the straight cutting blade are cut by the slice cutters (B) and (4b). 4) from the start of cutting positions (3), the cut paper is fed by L ₁ while the further roll cutter (4) is rotated by blades division angle zeta ° / 2, a sheet conveying length of R cutting blade portion Is L ₂
= Become 2L _1. The feed position of the cut paper at this point is position (4), and in this position, the shaded portion of the R cutting blade is cut by the slice cutter (A) (4a). This is the same as cutting at position (2).

The shredder employs a cutting mechanism in which vertical cutting and horizontal cutting are alternately performed by the above-described cutting process. One roll cutter (4) and fixed blade (3)
The shredder system is capable of fine-cutting paper to be cut with a one-cut function by engaging the cutting blade with the cutting blade.

FIG. 33 shows a mechanism of a cutting mechanism capable of performing fine cutting combining both vertical cutting and horizontal cutting by a one-cut function by engagement of a cutting blade between a single roll cutter (4) and a fixed blade (3). Control system including measures for overcutting the cutting paper for cutting paper, with the aim of reducing the size of equipment and the size of the equipment, and reducing the assembly work cost. All of the various components of the equipment are integrated into the printed wiring board (37).

[0078]

The present invention is embodied in the form described above, and has the following effects.

Since only one roll cutter (4) and the fixed blade (3) are engaged with the cutting blade, the paper to be cut can be finely cut by alternately performing vertical cutting and horizontal cutting. Of course, it is possible to greatly reduce the work cost for assembly adjustment and maintenance, etc.
Maintenance costs are reduced along with manufacturing costs.

Since fine cutting can be performed, it is possible to completely prevent leakage of confidential information after cutting important documents to be discarded.

In this system, a pair of guide rollers (1). The drive source for the two drive trains on the (2) side and the roll cutter (4) side is driven by one motor 5, and in the two rotary drive trains, a double clutch and an electromagnetic clutch are used respectively. By adopting a clutch shaft that has a countermeasure against overloading of the cutting blade, there is no need for subtle deviations caused by the engagement of the cutting blade and damage to the cutting blade caused by these. That is.

Among the two slice cutters constituting the roll cutter (4), the cutting edge shape of the slice cutters (A) (4a) consists of one R cutting blade and two straight cutting blades.
Further, since the cutting edge shape of the slice cutters (B) and (4b) is made of an extremely simple shape consisting of one linear cutting blade, the maintenance cost due to the re-grinding molding cost is small along with the manufacturing cost.

Slice cutter (A) (4a), (B)
In the manufacturing process of (4b), the grinding after the heat treatment
Both are possible with the same equipment and machines. In particular, the finish grinding of the outer periphery including the R portion of the slice cutter (A) (4a) can be made with a very simple geometric shape of the cutting blade. By using a formal whetstone, it is possible to form a cutting blade with better processing accuracy.

Slice cutter (A) (4a), (B)
(4b) shows that the cutting edge has a knurl angle (α
°) and when setting up the cutter shaft (4c),

As described in the section, the helical angle (θ °) according to the set value of the cutter cutting blade is defined as (4a) and (4a).
b) For each cutter row, also (4a) and (4b)
The roll cutter (4) is designed to be set up with an angular phase difference of 位相 ° / 2 between the cutting blades and the cutting load applied to the roll cutter (4) is relatively small. It is low, so it is possible to drive the shredder system with a low power (KW) motor.

One of the pair of guide rollers is fixed, the other is free of the shaft, and the shaft portions on both sides of the shaft-free side guide roller (2) are respectively held by separate roller shafts (1).
8) The spring is pressed against the guide roller (1) by applying a constant spring pressure, so that the gap between the guide roller (2) and the guide roller (1) is adjusted according to the thickness of the sheet to be cut. It is possible to send the cut paper to the engaging portion of the cutter at a predetermined speed.

The guide roller (2) on the shaft-free side employs a "ball rolling contact drive system" to rotate the guide roller (2). Therefore, when the gap between the guide roller (1) and the guide roller (1) corresponding to the thickness of the sheet to be cut is changed. Even if the degree of parallelism between the guide rollers (1) and (2) deviates slightly, the rotational angular velocity of the guide roller (2) always rotates at the same value as the angular velocity of the guide roller (1). There is no.

The contact surface between the guide rollers (1) and (2) is brought into contact with a helical angle (for example, a certain value of the malleability ξ
In this case, the paper to be cut is fed into a cutting blade meshing portion between the roll cutter (4) and the fixed blade (3), and a pair of guide rollers (1),
The improvement of the paper feed function of (2) can be expected.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing a cutting portion of a shredder capable of performing fine cutting combining vertical cutting and horizontal cutting by only engaging a single roll cutter and a fixed blade.

FIG. 2 is a cross-sectional view showing a two-line gear drive system of a shredder adopting a cutting method capable of performing fine cutting with only one roll cutter and a fixed blade.

FIG. 3 is a sectional view showing a drive side of a gear drive system on a guide roller side and a roll cutter side.

FIG. 4 is a cross-sectional view showing a rotation driving mechanism (ball rolling contact drive system) of a shaft-side guide roller.

FIG. 5 is a sectional view showing an assembly portion of a pair of guide rollers.

FIG. 6 is a cross-sectional view showing an assembly portion of the roll cutter.

FIG. 7 is a cross-sectional view showing a U portion shown in FIG. 3, that is, a mechanical clutch portion incorporated in a rotary drive system on a pair of guide rollers side.

FIG. 8 is a cross-sectional view showing a W portion shown in FIG. 3, that is, a mechanical clutch portion incorporated in the rotary drive system on the roll cutter side.

FIG. 9 is a development view of a mechanical clutch meshing tooth (A) portion of U and W portions shown in FIG. 3;

FIG. 10 is a development view of a mechanical clutch meshing tooth (B) portion of U and W portions shown in FIG. 3;

FIG. 11 is a cross-sectional view showing bearing portions on a guide roller rotation drive side and a driven side.

FIG. 12 is a cross-sectional view showing the drive side and driven side bearings when a guide roller is removed.

FIG. 13 is a sectional view showing components of the electromagnetic clutches (13) and (25).

FIG. 14 is a diagram showing tooth shapes (radial rack tooth shapes) of clutch teeth adopted for meshing teeth (C) of the electromagnetic clutches (13) and (25).

FIG. 15 is a view showing tooth shapes (spiral rack tooth shape) of clutch teeth to be adopted in meshing teeth (C) of the electromagnetic clutches (13) and (25).

FIG. 16 is a cross-sectional view showing a sensor head of the rotational angular displacement detection device (21).

FIG. 17 is a cross-sectional view of the guide rollers (1) and (2) in which the contact surfaces of the pair of guide rollers (1) and (2) are engaged with each other at a certain lead angle.

FIG. 18 is a diagram showing a cross section in a feed direction of a cut sheet waved by a pair of guide rollers having a wave meshing surface as a contact surface.

FIG. 19 is a diagram showing the external shapes of the slice cutters (A) and (4a).

FIG. 20 is a diagram showing the blade shapes of a cutting blade portion of a slice cutter (A) (4a).

FIG. 21 is a diagram showing, as an example of the cutting blade section of the slice cutter (A) (4a), a cutting blade section as a composite shape composed of one R portion and two linear portions.

FIG. 22 is a diagram showing the swing angle of the slice cutter (A) (4a) with respect to the grindstone head when performing cutting blade grinding.

FIG. 23 is a view showing a vertical movement relation with respect to a grinding wheel head when a cutting blade of a slice cutter (A) (4a) is formed by grinding.

FIG. 24 shows the inclination angle α ° (=) of the grindstone head base when the cutting blade of the slice cutter (A) (4a) is formed by grinding.
It is a diagram showing the relationship between the movement of the cutting edge (edge angle) and the movement.

FIG. 25 is a diagram showing the relationship between the configuration of the cutting blade shown in FIG. 21 of the slice cutter (A) (4a) and the cutting edge angle (α °).

FIG. 26 is a diagram showing the external shapes of the slice cutters (B) and (4b).

FIG. 27 is a view showing the blade shapes of a cutting blade portion of a slice cutter (B) (4b).

FIG. 28 is a diagram showing a moving relationship with a grinding wheel head when a cutting blade of a slice cutter (B) (4b) is formed by grinding.

FIG. 29 shows the inclination angle α ° (=) of the grindstone head base when the cutting blade of the slice cutter (B) (4b) is formed by grinding.
It is a diagram showing the relationship between the movement of the cutting edge (edge angle) and the movement.

FIG. 30 is a view showing the projected blade shapes of the cutting blade of the fixed blade (3).

FIG. 31 shows a slice cutter (A) (4) shown in FIG.
It is a figure which shows the cutting blade structural division of the fixed blade (3) corresponding to the cutting blade structural classification of a).

FIG. 32 shows a mechanism of a cutting mechanism capable of performing fine cutting combining vertical cutting and horizontal cutting by a cutting process of one element of the cutting blade by engagement of the cutting blade with the roll cutter (4) and the fixed blade (3). It is a figure.

FIG. 33 is a printed wiring board which is based on a cutting mechanism capable of performing fine cutting with only one roll cutter (4) and a fixed blade (5) and a control method therefor, and various equipment elements related to the system control of the shredder. It is a figure that is centrally equipped.

[Explanation of symbols]

1 axis fixed side guide roller 2 axis free side guide roller 3 fixed blade 4 roll cutter 4a slice cutter (A) 4b slice cutter (B) 4c cutter shaft 4d flange (A) 4e flange (B) 4f bearing nut 5 motor 6 gear (M1) 7 Gear (M2) 8 Gear (3A) 9 Gear (3B) 10 Gear (4A) 11 Gear (4B) 12 Clutch shaft (4 shaft side) 13 Electromagnetic clutch (4 shaft side) 13a Excitation coil 13b Clutch core 13c Spline shaft 13d Amateur 13e Stopper 13f Moving clutch tooth (A) 13g Fixed clutch tooth (B) 13h Clutch base 13i Coil spring 14 Gear (5) 15 Gear (G1A) 16 Gear (G1B) 17 Gear (G2) 18 Roller Shaft hold 18a Stopper piece 18b Stopper socket 18c Coil spring 18d Spring housing 19 Stopper holding (G2A) ··· Detachment device 20 Gear (C) 21 Rotational angular displacement detection device 21a Disk 21b Sensor head 21c Sensor 22 Gear (2) 23 Gear (1A) 24 Gear (1B) 25 Electromagnetic clutch (1 shaft side) 26 Clutch shaft (1 shaft side) 27 Ball base 28 Guide ring 29 Ball 30 Bearing (G1A) 30a Shaft (G1A) 30b Rotation drive key 30c Set bolt 31 Bearing (G2A) 31a Sleeve (G2A) 31b Coil spring 31c Set bolt 31d Housing 32 Bearing (G1B) 32a Shaft (G1B) 32b Set bolt 33 Bearing (G2B) 33a Sleeve 33b Coil spring 33c Set bolt 33d Set bolt 34 Stopper restraint (G2B) ··· Detachment device 35 Spline shaft 36 Coil spring 37 Printed wiring base 38 Grinding head λ Guide roller (2) Displacement (mm) PS Cut paper Pm Cut paper feed direction Mgr2 Axis free side guide roller shaft Center movement M Motor (5) shaft center C Roll cutter (4) shaft center 1 Clutch shaft (26) center (electromagnetic clutch of guide roller side gear drive system (25) ... clutch W mounting shaft) 4 Clutch shaft (12) ) Center (electromagnetic clutch of guide roller side gear drive system (13) ... clutch U mounting shaft) G1: shaft center fixed side guide roller (1) shaft center G2 (G2-1) shaft free side guide roller (2) shaft Center G-2 Shaft free side guide roller after shaft displacement (2) Shaft center U Double clutch U (Gear roller side gear rotation drive system) W Double clutch Hdr Guide roller side gear rotation drive series Hdc Roll cutter side gear rotation drive series N (1) Moves only during reverse rotation of spline shaft Hca Clutch meshing teeth (A) Hcb Clutch meshing teeth (B Hcc Clutch meshing teeth (C) Hcam Moving-side clutch teeth (A): Drive-side Hcaf Fixed-side clutch teeth (A): Driven side Hcbm Moving-side clutch teeth (B): Drive-side Hcbf Fixed side Clutch tooth (B): driven side S Sliding part (outer peripheral spline tooth part) F Clutch ON (Electromagnetic clutch OFF) B Clutch OFF (Electromagnetic clutch ON)
・ Slip on the sliding surface Moca Movement of clutch teeth (A) N Forward rotation R Reverse rotation δ: Helical angle (in the case of guide roller meshing teeth due to surface contact) ：: Wave malleability (= wave pitch P / wave height) w) P: Wave pitch (mm) w: Height of cut paper (mm) ε: Thickness of cut paper (mm) Doa: Outer diameter value of slice cutter (A) (mm) Dob: Outer diameter value of slice cutter (B) (mm) Dr: Outer peripheral portion R of slice cutter (A) Starting circle diameter (mm) Dc: Minimum diameter of cutting blade of slice cutter (A) (circumferential locus of starting point A) Por: starting point of the outer peripheral portion R of the slice cutter (A) (b) Porcs: starting point of the outer peripheral portion R of the slice cutter (A) (b) locus (circumference) Porce: end point of the outer peripheral portion R of the slice cutter (A) (c) Locus (circle Periphery) Poc: Starting point of the cutting blade of the slice cutter (A) (A) Pocc: Starting point of the cutting blade of the slice cutter (A) (A) Locus (circumference) ：: Cutting angle of the cutting blade (°) α: Slicing Slice angle (°) of the cutting edge of the cutter β: Cutting angle (°) of the slice cutter θ: Spiral angle (°) given to each row of the slice cutters (A) and (B) of the roll cutter component Lr: Slice cutter ( A) Outer circumference R part cutting blade length (lower) (mm) Lal: Left side straight section cutting blade length (Iro) (mm) of slice cutter (A) Lar: Right side of slice cutter (A) Straight part cutting blade length (Hani) (mm) Pscr: Center of the rotation axis of the slice cutter Tul: Slice cutter (A) Turn left when grinding the cutting blade Tur: Slice cutter (A) When grinding the cutting blade (A) Turn right u: "B" position (ascent limit) Sd: "ha" position (lowermost) Ls: the left (left) Rs: right (rightward) t1: The thickness of the R portion cut slice cutter (A) (m
m) t2: thickness (m) of the horizontal cutting slice cutter (B)
m) Th: Horizontal cutting blade Tv: Straight portion vertical cutting blade (Ero, Honey) L1: Cutter blade division angle (ζ °) / 2 Feed amount of cut paper during rotation (mm) Position (1) From position to position (2) L2: Feed amount of cut paper during rotation of cutter blade and angle (ζ °) L: Fixed blade depth (mm) <2 × L2 Fr: Shredder device frame N (1) : Moves only when the spline shaft rotates in the reverse direction. N (2): Grinds the left straight cutting blade (low) N (3): Grinds the right straight cutting blade (honey) N (4): The X section position N (5) in FIG. 30: The cutting of the B1 and B2 sections is shifted by a phase difference corresponding to the same kind of slice cutter mounting angle (helical angle θ °). N (6): The position marked with * indicates the repetitive cutting process between (Cutter split angle ζ °) / 2 rotations of (A) in position (1). * 1: The swivel angle of the cutter when grinding the outer periphery R (lower) portion of the slice cutter (A) * 2: Move to the left while raising the grinding wheel head * 3: Move to the left from the position of the cutting blade "C" * 4: Move to the right from the position of the cutting blade "B". * 5: Move to the right while descending the grindstone head. * 6: Inclination angle of the grindstone head base (= cutting blade smooth angle α °). * 7: (Ro-ha). Vertical movement of the cutter synchronized with turning on the cutter side during part grinding * 10: Insertion position of cut paper * 11: Storage space for cut paper pieces

────────────────────────────────────────────────── ───

[Procedure amendment]

[Submission date] October 11, 2001 (2001.10.
11)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] [Claims]

[Correction method] Change

[Correction contents]

[Claims]

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] [Explanation of symbols]

[Correction method] Change

[Correction contents]

[Description of Signs] 1 axis fixed side guide roller 2 axis free side guide roller 3 fixed blade 4 roll cutter 4a slice cutter (A) 4b slice cutter (B) 4c cutter shaft 4d flange (A) 4e flange (B) 4f bearing Nut 5 Motor 6 Gear (M1) 7 Gear (M2) 8 Gear (3A) 9 Gear (3B) 10 Gear (4A) 11 Gear (4B) 12 Clutch shaft (4 shaft side) 13 Electromagnetic clutch (4 shaft side) 13a Excitation coil 13b Clutch core 13c Spline shaft 13d Amateur 13e Stopper 13f Moving clutch tooth (A) 13g Fixed clutch tooth (B) 13h Clutch base 13i Coil spring 14 Gear (5) 15 Gear (G1A) 16 Gear (G1B) 17 Gear (G2) 18 Roller shaft holding 18a Stopper piece 18b Stopper socket 18c Coil spring 18d Spring housing 19 Stopper restraint (G2A) ・ ・ ・ Attachment device 20 Gear (C) 21 Rotational angular displacement detection device 21a Disk 21b Sensor head 21c Sensor 22 Gear (2) 23 Gear (1A) 24 Gear (1) 1B) 25 Electromagnetic clutch (1 shaft side) 26 Clutch shaft (1 shaft side) 27 Ball base 28 Guide ring 29 Ball 30 Bearing (G1A) 30a Shaft (G1A) 30b Rotation drive key 30c Set bolt 31 Bearing (G2A) 31a Sleeve (G2A) 31b Coil spring 31c Set bolt 31d Housing 32 Bearing (G1B) 32a Shaft (G1B) 32b Set bolt 33 Bearing (G2B) 33a Sleeve 33b Coil spring 33c Set bolt 33d Set bolt 34 Stopper Suppression (G2B) ・ ・ ・ Attachment / detachment device 35 Spline shaft 36 Coil spring 37 Printed wiring board 38 Grinding head λ Guide roller (2) Displacement (mm) PS Cut paper Pm Cut paper feed direction Mgr2 Shaft free side guide Roller shaft center movement M Motor (5) shaft center C Roll cutter (4) shaft center J1 Center of clutch shaft (26) (electromagnetic clutch of guide roller side gear drive system (25) ... Clutch W mounting shaft) J4 Clutch shaft (12) Center (Electromagnetic clutch of guide roller side gear drive system (13) ... clutch U mounting shaft) G1 Shaft fixed side guide roller (1) Shaft center G2 Axis free side guide roller (2) Shaft center G2-1 Shaft free side guide roller (2) Shaft center G2-2 Shaft free side guide roller (2) shaft center after shaft displacement U Double clutch U (Guide roller side gear rotation drive system) W Double clutch W (Roll cutter side gear rotation drive system) Hdr Guide roller side gear rotation drive system Hdc Roll cutter side gear rotation drive system Hca Clutch meshing tooth (A) Hcb Clutch meshing tooth ( B) Hcc clutch meshing teeth (C) Hcam Moving-side clutch teeth (A): Drive side Hcaf Fixed-side clutch teeth (A): Driven side Hcbm Moving-side clutch teeth (B): Drive-side Hcbf fixed Side clutch teeth (B): driven side S Sliding part (outer peripheral spline tooth part) F Clutch ON (Electromagnetic clutch OFF) B Clutch OFF (Electromagnetic clutch ON)
・ ・ Slip on the sliding surface Moca Movement of clutch teeth (A) N Forward rotation R Reverse rotation P Wave pitch (mm) δ Helical angle (°) ... In case of guide roller meshing tooth form by surface contact ε Thickness of cut paper Thickness (mm) 展 Wave malleability (= wave pitch P /
Wave height w) w Wave height of cut paper (mm) Doa Outer diameter value of slice cutter (A) (mm) Dob Outer diameter value of slice cutter (B) (mm) Dr Slice cutter (A) Outer peripheral portion R starting circle diameter (mm) Dc Minimum diameter of cutting blade of slice cutter (A) (m
m) (Circumferential locus of cutting blade starting point A) Por Peripheral portion R starting point of slicer (A) (B) Porc Locus of outer peripheral portion R starting point (B) of slice cutter (A) (circumference) ... The trajectory (circumference) of the peripheral portion R end point (C) of the Porcs slice cutter (A) ... the starting point of the cutting blade of the Porce Poc slice cutter (A) (a) The starting point of the cutting blade of the Pocc slice cutter (A) (a) Locus (circumference) 分割 Slicing cutter cutting angle (°) α Slicing cutter cutting angle (°) β Slicing cutter cutting angle (°) θ Slice cutter of roll cutter (A), ( B) Spiral angle given to each row (°) Lr Cutting blade length of outer peripheral R portion of slice cutter (A) (lo) (mm) Lal left straight portion of slice cutter (A) Cutting blade length (a) -B) (mm) Right Right straight part of the slice cutter (A) Cutting blade length (Hani) (mm) Psct Slice cutter rotation axis center Tul Left rotation during cutting of the cutting blade of slice cutter (A) Tur Slice cutter (A) Right turning during grinding of cutting blade Su “B” position (upper limit) Sd “C” position (downward limit) Ls Left side (left direction) Rs Right side (right direction) t1 R section cutting cutter (A) Thickness (m
m) t2 Thickness (m) of horizontal cutting slice cutter (B)
m) Th horizontal cutting blade Tv straight section vertical cutting blade (Ero, Honey) L1 cutter blade division angle (ζ °) / 2 Cut paper to be cut between two revolutions Feed amount (mm): From position (1) to ( To 2) L2 Cutting paper during rotation of cutter blade division angle (ζ °) Rotation amount (mm): From position (1) to (3) L Fixed blade depth (mm) <2 × L2 Fr Shredder frame N1 Spline Moves only when the shaft rotates in the reverse direction (only when the electromagnetic clutch is ON) N2 Grinding of the left straight cutting blade (low) N3 Grinding of the right straight cutting blade (honey) N4 N4 position in Fig. 30 The cutting of the portions N5 B1 and B2 is shifted by a phase difference corresponding to the same kind of slice cutter mounting angle (helical angle θ °). N6 Position (6) shows the repetitive cutting process after (Cutter blade division angle ζ °) / 2 rotations of (A) in position (1). C1 Swinging angle (°) of the slice cutter at the time of outer circumference R (lower) grinding of the slice cutter (A) C2 Vertical movement of the slice cutter in synchronization with the rotation of the slice cutter at the time of (lower) part grinding C3 Wheel head raising C4 Move to the left from the position of the cutting blade "C" C5 Move to the right from the position of the cutting blade "B" C6 Move to the right while the grindstone head descends C7 Grinding wheel head base inclination angle (= Cutting blade Sumi angle α °) C10 Cutting paper insertion slot position C11 Cutting paper piece storage space

[Procedure amendment 3]

[Document name to be amended] Drawing

[Correction target item name] All figures

[Correction method] Change

[Correction contents]

FIG.

FIG. 2

FIG. 3

FIG. 4

FIG. 5

FIG. 6

FIG. 7

FIG. 14

FIG.

FIG.

FIG. 8

FIG. 9

FIG. 10

FIG. 11

FIG.

FIG. 13

FIG.

FIG.

FIG.

FIG. 21

FIG.

FIG. 23

FIG. 24

FIG. 25

FIG. 26

FIG.

FIG. 27

FIG. 28

FIG. 29

FIG.

FIG. 31

FIG. 32

FIG. 33

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification code FI Theme coat ゛ (Reference) B65H 35/08 B65H 35/08

Claims (18)

[Claims] An object of the present invention is to provide a cutting mechanism capable of performing fine cutting combining vertical cutting and horizontal cutting with only a single roll cutter (4) and a fixed blade (3) for the purpose of fine cutting of a sheet to be cut. A shredder whose basic component is the control system. 2. A plurality of slice cutters capable of sufficiently satisfying a function of a cutting mechanism characterized by fine cutting performed by allowing only one roll cutter (4) and a fixed blade (3) to engage with a cutting blade. For each of the cutting edge division angle (ζ °) / a plurality of numbers (2 in the case of two slice cutters (A) and (B)) and a plurality of slice cutter rows. The cutter axis (4) has an angular phase difference corresponding to the helical angle (θ °) based on the setting value of the cutting blade.
2. A shredder according to claim 1, wherein a roll cutter (4) constituted by alternately setting up in c) is incorporated into the apparatus as a component of the shredder. 3. A cutting process of one element of a cutting mechanism by engagement of a cutting blade between a roll cutter (4) and a fixed blade (3).
Regarding the types of slice cutters (A) and (B)), at 1) × part position (1), the cut sheet is width t2 (width of slice cutter (B)) × L2 (slice cutter division angle (ζ °) It is cut by the slice cutter (B) (4b) to the size of the feed length of the cut paper during rotation). 2) After starting the cutting of the position (1), while the roll cutter (4) further rotates by the blade division angle (ζ °) / 2, the cut paper is sent by L1 (= L2 / 2). You. The cutting paper advance position at this point is position (2).
In this position, the slice cutter (A) (4)
According to a), the shaded part of the R cutting blade is cut. 3) After starting cutting at position (2), while the roll cutter (4) rotates by the blade division angle (ζ °) / 2, the cut paper is fed by L1. The feed position of the cut sheet at this point is position (3), and in this position, the diagonal lines of the straight cutting blade are cut by the slice cutters (B) and (4b). 4) After starting the cutting at the position (3), while the roll cutter (4) further rotates by the blade division angle (ζ °) / 2, the cut paper is fed by L1, and the R cutting blade is fed. The length is L2 (= 2 × L1). At this point, the sheet to be cut is fed at position (4), where the slice cutters (A) and (4a) cut the hatched portion of the R cutting blade. This position is the same as position (2). 2. The shredder according to claim 1, wherein a mechanism of a cutting mechanism capable of performing fine cutting combining vertical cutting and horizontal cutting by such a cutting process is used as a basic base of the apparatus. 4. A method for feeding a sheet to be cut to a cutting blade meshing portion between a fixed blade (3) and a roll cutter (4).
2. A shredder comprising a pair of guide rollers (1) and (2), each having a fixed shaft type bearing and the other having a shaft free type bearing mechanism.
Shredder described. 5. A guide roller having a free shaft.
5. The shredder according to claim 4, wherein a rotary driving system using a "ball rolling contact drive" is incorporated in the rotary driving system for the purpose of transmitting the rotary driving force to the motor. 6. Bearings (31), (33) of a guide roller (2) which is a shaft-free rotating shaft among a pair of guide rollers.
In addition, roller shaft holding (18) and stopper holding (1
5. A shredder according to claim 4, wherein said shredder incorporates (9) and (34). 7. A double clutch (U), (U) by a mechanical mechanism comprising clutch meshing teeth (A) and (B) in two rotation drive systems in which switching operation between reverse rotation and stop is required to be performed alternately. W) and clutch shafts (12), (2)
A clutch mechanism for switching between reverse rotation and stop, which is constituted by electromagnetic clutches (13) and (25) incorporated in 6). 8. In a clutch engagement mechanism (corresponding to an engagement tooth (C)) of an electromagnetic clutch, in order to sufficiently fulfill its function, a moving clutch tooth which is splined by a spline on a field core (13b) side. (A) (13f)
And the fixed-side clutch teeth (B) (13g) fixed to the clutch shaft side, the clutch teeth formed into meshing teeth in a radial rack shape or spiral rack shape. An electromagnetic clutch incorporating (A) and (B) as components of a clutch engagement mechanism in a device. 9. The clutch mechanism according to claim 7, wherein an electromagnetic clutch having the clutch engagement mechanism according to claim 8 is incorporated as a component of the device. 10. A field core (13) which is a component of a clutch meshing tooth (C) of an electromagnetic clutch (13).
The moving-side clutch teeth (A) (13f) guided by the spline on the b) side and the fixed-side clutch teeth (B) (13g) fixed to the clutch shaft side are both hard and wear-resistant. Highly non-ferrous materials (rubber, resin or aluminum alloy, etc.) are molded from each
d) and baking mold on clutch base (13h),
Or molded by casting. 9. The electromagnetic clutch according to claim 8, wherein the movable clutch teeth (A) and (13f) and the fixed clutch teeth (B) and (13g) are incorporated as components of the clutch meshing teeth (C) of the device. 11. A sheet to be cut sandwiched between the cutting blades of the roll cutter (4) and the fixed blade (3), that is, the engagement between the roll cutter (4) and the fixed blade (3) due to an excessive cutting load. In order to pull out the cut paper that could not be inserted from the pinch, the minimum necessary reverse rotational angular displacement by reading the rotational angular displacement detection device (21) incorporated in the cutter (4c) was applied only to the roll cutter (4). During this period, the pair of guide rollers (1) and (2) are kept in a stopped state with their rotation stopped, and the cut paper is cut off from being caught between the roll cutter (4) and the fixed blade (3) by the cutting blade. After the release, the reverse rotation of the roll cutter (4) is stopped, the pair of guide rollers (1) and (2) is changed from the stopped state to the reverse rotation operation, and the cut sheet released from the jam is inserted into the original insertion slot. After returning to the position, some settings 8. The clutch mechanism according to claim 7, wherein a pair of guide roller side and roll cutter side two gear rotation drive systems are provided as countermeasures for a cutting load over measure in which the system main body returns to a stop standby state before starting. 2. The shredder according to claim 1, wherein the shredder is incorporated as a component of the device. 12. An outer peripheral surface of a guide roller is lined with a hard rubber having a thickness of several mm so that a cut sheet does not slip on a contact surface with a guide roller, and a contact surface between the rollers is made a line contact. 5. A shredder according to claim 4, wherein the pair of guide rollers (1) and (2) are incorporated as one component as a means for feeding the cut sheet. 13. A contact surface between a pair of guide rollers is formed with a certain helical angle (δ ° = lead angle) based on a surface contact (such as a wave shape, a mountain shape, or a rack shape). A curl phenomenon that impedes the transportability of the cut paper by plasticizing the cut paper into a shape similar to the cross-sectional shape of the developed outer peripheral surface of the guide roller by lining a hard rubber layer consisting of several mm thick And the self-propelling action of the remainder of the previous cut sheet by the subsequent cut sheet occurs,
A pair of guide rollers (1) and (2), which are capable of improving the paper feeding function of the guide roller, are incorporated as one component as a paper feeding means of the shredder. Shredder. 14. A cutting blade shape capable of sufficiently fulfilling a one-cut cutting function based on a cutting mechanism capable of performing fine cutting by combining vertical cutting and horizontal cutting of a sheet to be cut. Conceptual shapes include straight blades, R-shaped blades, corrugated blades, single cutting blades consisting of a circle, part of a circle, ellipse, part of an ellipse, etc., and compound cutting consisting of combinations of these. As an example of them, including the blade shapes, the slice cutter (A) is a composite cutting blade shape combining a simple semicircular blade and two straight blades, and the slice cutter (B) is a simpler one. A plurality of slice cutters including a cutting blade (A) and a slice cutter (B) each having a cutting blade constituted by a straight cutting blade. Combined as a component of (4) Shredder according to claim 2, wherein I do. 15. A roll cutter (4) constituted by a setup of a plurality of slice cutters according to claim 14.
And the fixed blade (3), which is constituted by a cutting blade having the same shape as that of the geometrical projection of the cutting blade, engages the cutting blade in vertical and horizontal cutting. 2. A fixed blade (3), which is capable of performing fine cutting combined with the above, is incorporated as a component of the apparatus.
Shredder described. 16. A plurality of slice cutters (including the slice cutters (A) and (B) as examples) according to claim 14 irrespective of the shape of the single and compound cutting blades. The circumferential trajectory of the geometric projection contour forms the outer shape of the cutting edge of the slice cutter, so it is possible to avoid changes in the outer shape due to the refinish grinding of the cutting blade. Also, the cutting edge angle (α °) over the main length of the cutting edge
And the cutting edge is formed with a cutting angle (β °), so it is possible to cut with extremely low cutting load. 3. The shredder according to claim 2, wherein a plurality of slice cutters having a cutting blade characterized by such a point are incorporated as components of the roll cutter (4). 17. A vertical moving mechanism corresponding to a slicing angle (α °) of a slice cutter cutting blade synchronized with a turning angle displacement of the center of the R portion cutting blade of the slice cutter (A) (4a) as a turning center. 16. The relative movement relationship between the cutter mounting base and the grinding wheel head mounting base that slides at an inclination angle (α °) having a gradient equal to the slicing angle (α °) of the slice cutter cutting blade. Manufacturing method that can perform the slice cutters (A) (4a), (B), (4b), etc. from rough grinding to finish grinding. 18. A shredder according to claim 11, wherein a cutting mechanism capable of performing fine cutting, which combines vertical cutting and horizontal cutting of a cut sheet, is used as a basic base. 2. The shredder according to claim 1, further comprising: a printed wiring board (37) in which control-related various components of the control system and its wiring are integrated into a panel for the purpose of reducing the size of the device and reducing the assembly work cost. .