JPS5815279B2 - Seimitsuuchinukigatasetsudanouchi - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION This invention relates generally to cutting devices and more particularly to a rotary tool having a rotating resilient rotating anvil backup surface.

Problems associated with precision punch cutting discussed in commonly owned U.S. Pat. Most of the problems are solved by this.

However, this invention requires significant electrical control equipment, particularly to cause the anvil roller to follow the speed of the die roller and to provide a variable proportional speed between the two rollers to achieve the desired high precision. did.

The present invention uses a more complex and more reliable mechanical transmission system than the previously described inventions, thereby providing a higher degree of accuracy that can be obtained quantitatively.

Furthermore, it has been found that the use of a variety of punch cutting blades, particularly multiple laterally extending blades for making horizontal cuts, often creates significant forward resistance to the anvil roller as the blades engage the anvil cover. Ta.

Advancing resistance is especially true when the anvil roller is rotating about 1% more than the die roller speed.

Because of the tight connection between the two rollers, the duck rollers sometimes tear or at least wear the bars excessively.

SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a device for controlling the accuracy of punch cuts made in paperboard stock, both in terms of length and position.

This object of the invention is to drive the die roller at a selected angular or tangential velocity and drive the cooperating annobil roller at a tangential velocity selectively proportional to the velocity of the die roller to pass between the two rollers. Controls the speed of the material, thus compensating for irregular velocities imparted to the material by the characteristics of the cutting blade and other factors, and even if the circumference of the anvil roller is smaller than the standard with respect to the effective diameter of the cutting blade, the tie roller This is achieved by controlling the speed of the anvil roller to be approximately equal to the speed of .

Preferably, the selected proportional speed of the anvil roller is maintained during overall machine speed changes.

A desirable device follows the speed of the die roller and includes a first force connected to the die roller and a second force connected to the anvil roller for rotating the anvil roller at a speed approximately corresponding to the speed of the die roller. Includes mechanical transmissions, such as those of the Monique Drive type, with an output responsive to one person's power.

The device is also responsive to the speed of the die roller and provides a second manual power to said transmission to selectively control the proportional speed of the ambi roller with respect to the die roller and selectively variable output with respect to the first manual power. Any type of mechanical transmission may be used as the first drive of the anvil roller, including variable ratio mechanical transmissions.

Their common feature is that their output provides speed tracking and selectively variable control of power in response to both primary and secondary human power.

However, the preferred transmission for use as the first transmission in the present invention is of the gnomonic drive type.

Such a transmission can be determined by those skilled in the art to provide the desired input-to-output speed ratio,
The second gives the second manual power to the first transmission to change the speed difference of the output of the first transmission, which can be easily modified to provide gear mounting structure, transmission mounting structure, etc. The preferred mechanical transmission for use as a transmission for
P.1. V.

It is a continuously variable transmission.

The above-described apparatus preferably provides cutting dimension and positional accuracy of the stock to at least 0.038 inch (0.9652 mm) accuracy on a 38 inch (96.52 cm) long stock, with an accuracy of at least 0.95 mm. It provides a means of controlling accuracy down to 1%, which accuracy is simply not achievable with known punch-cutting machines.

These and further objects and novel features of the present invention will become more fully apparent from the following detailed description taken in conjunction with the accompanying drawings.

However, it should be readily understood that the drawings are not intended to limit the invention, but are merely for the purpose of illustrating the embodiments.

Identical parts in the figures are indicated by the same reference numerals.

FIG. 1 schematically depicts a conventional rotary punch-cutting machine adapted to operate in conjunction with the apparatus of the present invention.

The punch-cutting machine is shown generally at 10 and includes a set of spaced side frames 12.
and 14, between which a set of cooperating rollers is mounted, the upper side being a die roller 16 and the lower side an anvil roller 18.

A crossbar 20 rigidly connects frames 12 and 14.

Rollers 16 and 18 have individual journals 2 extending through conventional bearings 32 in frames 12 and 14.
4,26°28 and 30.

The die roller 16 is configured to carry a conventional cutting blade and struts attached to an arcuate plywood backing or die plunket 35 fixed to the roller, and the anvil roller is typically made of polyurethane plastic. It is completely covered by a relatively thin resilient cover 36.

This cover may be glued to the metal drum portion 38 of the roller 18, but is preferably mechanically secured so that it can be replaced when it becomes subject to significant wear.

A device with such characteristics is disclosed in U.S. Pat. No. 3,577,822.
Disclosed and explained in the issue.

As rollers 16 and 18 rotate, paperboard stock 40 (FIG. 2) is continuously advanced between the rollers at a linear velocity matched to blade 34, which cuts and braces the stock.

The radial height of the bar blade (which is well known and not shown in detail) is such that its outer periphery creates a notch in the material that allows the final material to be folded along the score lines.

The cutting blade 34 typically has a serration (not shown), which is radially elevated (from the surface of the die roller 16) such that its outer serrations are serrated as shown in FIG. The height is such that it passes through the blank 40 and slightly into the cover 36 as it passes in radial alignment with the axis of the anvil roller.

The length of the longitudinal cut made in the material 40 (the length of the cut along the direction of travel of the material) is primarily determined by the arcuate length of the cutting blade.

However, the actual length cut may be longer or shorter than required if the material is accelerated or decelerated as it passes between rollers 16 and 18.

For example, when the die roller 16 is driven by a drive motor 56 (described below) at a constant desired speed, the cutting blade 34 rotates at a constant speed, but the tip of the blade 34 enters the material 40, causing the material 40 to - If accelerated, a length of paperboard greater than the length of the blade 34 passes through the roller gap before passing through the stock.

As a result, the cutting length becomes longer than the length of the blade.

Conversely, if the material 40 were to be decelerated, the cutting length would be shorter than the blade length.

Acceleration or deceleration of the material 40 is similarly performed by horizontal cutting (
(extending transversely to the direction of movement of the material) in the direction of movement of the material is made too long (in the case of acceleration) or too short (in the case of deceleration).

In accordance with the present invention, the velocity of the surface of the anvil roller cover is an angular velocity selected such that the cover 36 exerts a sufficient effect on the velocity of the stock to eliminate inaccuracies in cut length and location of the stock. It is controlled by driving anvil roller 18.

This is achieved by the following explanation. Referring again to FIG. 1, the journal 24 of the roller 16 includes a rotationally driven spur gear 50 fixed to the journal, which gear 50 is fixed to the output shaft 54 of the main drive motor 56 of the punch-cutting machine 10. It is driven by another gear 52 that is

Activation of motor 56 thus rotates die roller 16 at a selected speed using a conventional acceleration resistor motor controller 56a.

The die roller 16 normally rolls the material 40 one after another.
．． 18 is driven by gears connected to a conventional feeder (not shown).

For example, in FIG. 2, a pair of retracting rollers 58 and 60 conventionally sandwich the stock 40 as it is fed between these rollers and transfer the stock to roller 1.
Feed between 6 and 18.

These retraction rollers may be driven by a gear train adjacent to the stock feeder, and a similar conventional gear train may drive the die rollers.

This gear train has been omitted for clarity and the rollers 16 are simplified as it is not important to the invention whether the rollers 16 are driven synchronously by a motor or by an adjacent mechanism. It is shown as being driven by a motor 56 for the purpose of achieving this.

Similarly, conventional gear protection devices, lubrication devices, etc. have been omitted as they do not form part of the invention and are well known to those skilled in the art.

Journal 28 of anvil roller 18 extends into and is coupled to a mechanical transmission or harmonic drive 70.

The harmonic drive is shown in detail in FIG.

Harmonic drive 70 includes a first human-powered spur gear 76 that meshes with gear 50 (see FIG. 1).

Thus, while the motor 56 rotates the roller 16, the motor 56 rotates the roller 18 via the harmonic drive 70.
Rotate.

Thus, the speed of roller 18 follows the speed of roller 16 when motor 56 is accelerated or decelerated.

Generally, an operating speed is selected for the motor 56 and the anvil roller follows the selected speed.

However, the output speed of the harmonic drive 70 is varied relative to the speed of the roller 16, i.e. the output journal 28 of the transmission, which is also the input to the anvil roller 18, is faster or slower than the input from the motor 56 to the die roller 16. It can be made to rotate.

This is a chain gear type continuously variable transmission, namely P, 1. This is accomplished by rotating the second human power shaft 130 from the V-type continuously variable transmission 90 (hereinafter referred to as P, 1.V) at a speed selected to add to the speed of the output journal 28 as described below.

P.1. Before discussing V, 90 in detail, it is best to understand the structure and operation of harmonic drive 70 shown in FIG.

The harmonic drive 70 is inserted into the screw 106 in the usual manner.
includes a flanged rigid toothed barrel 102 mounted on the side of the first human power gear 76 .

Gear 76 is mounted on a roller bearing 108 fixed to the end of journal 28 for free rotation and is driven by gear 50 (first
(as shown in the figure).

This arrangement constitutes the primary power of harmonic drive 70.

A flexible toothed cylinder 112 is incorporated within the rigid toothed cylinder 102.

One end of the flexible toothed barrel 112 has a radially extending end 1 having a central opening surrounding the reduced diameter shoulder 116 of the journal 28.
It is closed by 14.

End 114 is mounted for rotation with journal 28, with washers 118 placed on either side of the end, and screw 120 passed through both washers 118 and end 114 and into the journal.

This structure also axially secures the bearing 108 to the reduced diameter shoulder 116 of the journal 28.

The open end of the flexible toothed barrel 112 has outer teeth 122 on its outer periphery.
including.

These teeth correspond to and mesh with inner teeth 124 formed on the inner peripheral surface of the rigid toothed cylinder 102.

This is further illustrated in FIG.

P.1. P, 1. V2
O includes an output shaft 130 that extends in coaxial alignment with the central axis of the flexible toothed barrel 112 .

The shaft 130 has a reduced diameter shoulder 140 and a conventional shaft key 144.
．． A washer 146 and a screw 148 secure the wave generating cam 142 to the reduced diameter shoulder 140 in a conventional manner for rotation with the shaft 130.

An oval bearing 150 is secured to the outer circumferential surface of the cam 142, such as by a force fit, and the cam is also oval as shown in FIG.

The long diameter portion of the bearing 150, that is, the portion corresponding to the protruding portion of the cam 142 pushes the outer teeth 122 and meshes with the inner teeth 124.

The details of the operation of the harmonic drive 70 are as follows.

The first manually driven gear 76 is fixed to the rigid toothed cylinder 102 as described above, and is rotatable around the journal 28 by means of a bearing 108.

The journal 28 is fixed to rotate together with the flexible toothed cylinder 112.

The wave generator (consisting of a cam 142 and a bearing 150) is P, 1. P,1.extending from V,90. V, is continuously rotated by the output shaft 130 and changes the angular velocity between the gear 76 and the anvil roller 18 when the anvil roller 18 is to be rotated faster or slower than the die roller 16.

The flexible toothed cylinder 112 is made of thin flexible metal (however, planar material can be used in cases where the transmitted torque is small), and the wave generator connects the outer teeth 122 to two opposite sides of the cam 142. It is understood that the protrusions can be deflected into engagement with the inner teeth 124 of the rigid toothed barrel 102.

Therefore, due to the rotation of the wave generator, the flexible toothed cylinder 11
2 is transmitted with a continuously moving waveform.

This causes the flexible toothed barrel 112 to rotate with a tangential motion that is greatly reduced.

One complete revolution of the wave generator by the output shaft 130 (which can also be thought of as a second human input to the harmonic drive 70) consists of the circumference of the rigid toothed cylinder 102 and the circle of the flexible toothed cylinder 112. The flexible toothed cylinder 112 is rotated by a distance equal to the difference from the circumference.

As a result, the actual reduction ratio is obtained by dividing the circumference of the flexible toothed barrel 112 by the difference between the two circumferences.

Since the teeth of both the flexible toothed cylinder 112 and the rigid toothed cylinder 102 have the same circumferential pitch, the actual number of teeth of each can be used as the circumferential measurement.

The reduction ratio of any unit is calculated by dividing the number of teeth on the output member (flexible toothed tube 112) by the difference in the number of teeth on the two toothed tubes.

For example, if the rigid toothed cylinder 102 has 202 teeth and the flexible toothed cylinder 112 has 200 teeth, the reduction ratio is such that the rigid toothed cylinder 102 is fixed and the harmonic drive is fixed. When used in a conventional manner where the input is the wave generator 142, the output of the flexible toothed barrel 112 rotates one revolution for every 100 revolutions of the input shaft 130.

However, when used in the present invention, the wave generator 142 is continuously rotated by the shaft 130 and the rigid toothed tube 10 is
2 is continuously rotated by gear 76.

Thus, the rigid toothed cylinder 102 constitutes a first manpower section which rotates at the machine speed, i.e. the same speed as the die roller 16, and the cam or wave generator 142 rotates at P, 1. The output shaft 130 of the second human power section rotates at a selected speed.

The flexible toothed barrel 112 constitutes the output part, the rotation of which is transmitted to the anvil roller 18 via the journal 28, as previously explained.

Therefore, the output of the flexible toothed barrel 112 is 202:200.
(i.e. 101:100), i.e. rigid toothed cylinder 102
101 rotations for every 100 rotations of the input section.

Since the rollers 16 and 18 theoretically rotate with the same peripheral speed as the linear speed of the material being printed, it is necessary to create the opposite ratio between the roller drive gears 50 and 76.

For example, if the gear 50 of the die roller 16 has 100 teeth, the gear 76 of the anvil roller 18 will have 100 teeth.
101 to reduce the speed of gear 76 by the same amount that flexible gear 112 is increased by rigid gear 102.
It is necessary to have several teeth.

However, as configured in the present invention, P,
1. The output shaft 130 from V,90 rotates continuously as its external input rotates continuously.

Which input is provided by a conventional spur gear 51 mounted for rotation with the journal 24 of the die roller 16, with a similar gear 53 connected to P, 1 . V:9
It is mounted in a conventional manner for rotation with an input shaft 55 extending from the input shaft 55.

P.1. V, is attached to the support body 129, and the input gear 53
meshes with the drive gear 51 and is driven by the drive gear.

The ratio of gears 51 and 53 is selected to provide the required output speed by shaft 130 to Mononic Drive 70, with the output speed of shaft 130 being constant input speed provided by input shaft 55. P.1. It is understood that manual selections can be made over the entire design range of V.

Manual selection is P,1. V, 90 band wheel 5
This is done by rotating 7.

P.1. The internal structure and operation of the V: type continuously variable transmission are well known and need no further explanation.

As mentioned above, the anvil roller 18 should rotate slower or faster than the die roller 16 depending on the nature of the punch cut being made on the stock.

The amount of underspeed or overspeed is less than ±10% of the speed of the die roller, however, less than ±2% is usually effective and readily obtained with the transmission of the present invention.

However, P,1. It should be understood that the output shaft 130 of V,90 always rotates in one direction.

Therefore, P,1. When the ratio of V, is set by band wheel 57 for minimum input-to-output speed change,
- the ratio of gears 50 and 76 may be selected such that the output speed from monic drive 70 to journal 28 is such that it rotates anvil roller 18 at less than 2% of the speed of die roller 16; is necessary.

Thus, using the band wheel 57, P,1. V,
Increasing the output speed of 90 increases the speed of harmonic drive 70 which increases the speed of anvil roller 18.

P.1. The design ratio of V,90 is such that P,1. When manually adjusting V, 90, the output shaft 130 rotates at a sufficient speed to increase the output speed to the anvil roller 18.
plus the roller speed by 2% of the speed of die roller 16
Selected to increase front and rear speed.

In accordance with the embodiments detailed above, the required gear ratios for the various gears can be readily selected by one skilled in the art to obtain the required output speed of the moniker drive 70.

A gnomonic drive with a 100:1 ratio provides high resolution phase adjustment.

For example, one revolution of the wave generator 142 causes a 36 degree angular phase displacement of the toothed tube 112 with respect to the toothed tube 102.

If the roller 18 has a nominal circumference of 50 inches (12.7 cm), the wave generator 14 by the second human power shaft 130
2 produces a circumferential displacement of roller 18 of 0.5 inch (1.27 cm) relative to the nominal circumference of roller 16.

As shown in FIG. 1, drive gear 52 on main motor shaft 54 meshes with and drives gear 50 on journal 24 of die roller 16 to drive the roller at the desired speed.

Gear 50 also meshes with and drives first human power gear 76 of harmonic drive 70 .

As already explained, the outer gear 51 of the journal 24
is P, 1. V, drives input gear 53 to 90 and P
The IV output shaft 130 adds to the output speed of the monic drive 70 by the amount selected by the non-drive wheel 57 of the PIV 90.

In this manner, anvil roller 18 follows the speed of the die roller at a selected rate.

Even if the speed of the die roller 16 is changed by changing the speed of the motor 56, for example by a conventional leonutat controller 56a, the anvil roller follows the newly selected speed of the die roller 16 at a selected percentage speed. continue.

However, the direct engagement of gear 50 and gear 76 creates a tight bond between the die roller and anvil roller.

As previously noted, the array of punching cutting blades causes considerable wear and damage to the rollers 18 while the cutting blades 34 are embedded in the cover, especially when there is a significant speed difference between the rollers. It has been known to even tear the upper resilient cover 36.

To alleviate this condition, the hard connection between gears 50 and 76 may be replaced with a soft connection.

This is preferably accomplished by the arrangement shown in FIG.

In this configuration, motor drive gear 52 drives die roller gear 50a which is keyed to journal 24 as shown.

However, the gear 50a is the first manual gear 76 of the transmission.
do not drive.

Instead, the other gear 50b on the journal 24 meshes with the input gear 76 and drives it.

To achieve a soft connection, gear 50b is mounted for free rotation about a conventional bearing or bushing 61 on journal 24.

A conventional electromagnetic clutch 63 is mounted on journal 24 next to gear 50b.

The clutch 63 includes a driven hub 65 keyed to the journal 24 and a driving hub 67 fixed to the gear 50b by screws 69 or the like.

The driven hub 65 rotates together with the journal 24, and when current is supplied to the clutch 63, the drive knob 67 rotates with the gear 5.
0b, which rotates the transmission input gear 76.

However, if cutting blade bite or other factors create significant drag on the anvil roller 18 and this roller requires excessive torque to rotate it, the required torque will be transferred to the clutch. When the rated torque is exceeded, the clutch knobs will slip against each other.

In this state, the die roller 16 continues to rotate, but the anvil roller 18 can slip because the gear 50b momentarily stops rotating.

When the torque demand decreases, clutches 65 and 67 re-engage and proper operation continues.

Although any torque limiting device, even a purely mechanical limiting device, could be chosen to provide the desired soft coupling, the electromagnetic clutch shown in the clamp drawing was chosen as the most suitable, and this For example, an electromagnetic multi-plate clutch is preferable.

It should also be understood that the apparatus shown in FIGS. 1 and 2 are simplified schematic diagrams to facilitate explanation and understanding of the invention.

In practice, in order to mount the transmission within the available space and obtain the desired gear ratio, it is necessary to connect the transmission indirectly to the die and anvil rollers through a series of idler gears. There might be.

Also, as previously mentioned, the transmission may be coupled to the main drive gear train rather than to the drive motor as shown.

However, positioning and coupling arrangements, such as the use of idler gears, are common and understood by those skilled in the art, and do not adversely affect the structure and operation of the invention shown in the figures.

To operate the apparatus of the present invention, the desired parts and cutting blade die 35 are selected and mounted on the die roller 16 in the conventional manner.

placing a stack of material 40 in a feeder (not shown);
For example, the material is pulled out one by one using rollers 58 and 60.
It is advanced through the punch cutting device 10 between rollers 16 and 18 by advancing means such as.

Preferably, the first few blanks are fed into the apparatus at a working speed to ensure that the cutting die is approximately in line with the desired score and cutting location of the blank.

Drive motor 56 using Leonutat controller 56a
control the speed of

If the score and cut do not match, reposition the die around the circumference of the roller and/or along the length of the roller until they do.

Thereafter, the production rate of the equipment is selected and the material is fed to the equipment.

When the first die-cut blanks emerge, they are visually inspected for correct cutting, for example by comparing the cut position to printed indicia appearing on the blank.

However, a more accurate procedure would be to stop the equipment (to prevent incorrect material from accumulating) and check whether the folds and cut locations are accurate using, for example, a tape measure. If the measurement results in one of the materials being cut too far forward than, for example, where the cut should be made, then the kneading may be due to one or more of the reasons mentioned above. This indicates that the speed of the material is being impeded as it passes through the device due to .

Therefore, P,1. Rotate the handwheel 57 of V, 90 in the appropriate direction--increase the output speed of the Monique Drive γ0 to cause the anvil roller 18 to run faster as previously described.

This step is repeated until the cut is made at the exact desired location.

Once the operator has become proficient in using the device of the invention, he or she will know which position the band wheel 57 should be rotated in order to move the cut along the material to the desired position without having to make many trial and error selections. You can immediately determine whether

Of course, if the cut is made behind the desired position, this indicates that the material is being accelerated as it passes between rollers 16 and 18, and therefore the band wheel is moved to the retracted position in a manner similar to that described above. This indicates that you should rotate towards the target.

The input-to-output ratio of transmissions 70 and 90 is such that the output of transmission 90 is in its full addition or full subtraction states, as previously explained, and of course any portion of these states between maximum and minimum. When adjusted, the anvil roller 18 is preferably selected to run at least 2% faster or 2% slower than the speed of the die roller 16.

Although the ability to provide 2% overspeed or underspeed is usually sufficient, if desired, the transmission may be selected with ratios to provide as much as 10% overspeed and 10% underspeed. It is understood that it is good.

Therefore, by following the extremely simple operating procedure described above, extremely accurate punching and cutting can be easily achieved.

Although the present invention is advantageous for an anvil cover 36 rigidly clamped to an anvil roller drum 38, the speed of the blank 40 can also be controlled when using a conventional freewheeling anvil cover. .

This is because the cover experiences advancement resistance on the roller drum and thus the surface speed of the cover is influenced by increasing or decreasing the speed of the anvil roller.

It is recognized that the surface speed of the anvil cover affects the overall speed of the material passing between the rollers, thus controlling the accuracy of the cuts made in the material.

It should therefore be understood that the output of the transmission 70 may be coupled to the cover of the anvil roller such that the cover rotates itself about the anvil roller which is held stationary.

[Brief explanation of the drawing]

FIG. 1 is a front schematic illustration of a rotary die-cutting device including a pair of cooperating die rollers and anvil rollers, with the anvil roller being moved at a speed proportional to and relative to the die roller speed; 2 is a schematic side view of the device of FIG. 1; and FIG. 3 is an enlarged cross-sectional view of a portion of the roller of FIG. 1 showing the majority of the transmission. FIG. 4 is a cross-sectional view of the harmonic drive shown in FIG. 3 taken along line I'I. 10... Punching and cutting machine, 12, 14... Side frame, 16.
...Die roller, 18...Anvil roller, 20
...Horizontal bar, 24, 26, 28, 30... Journal, 32... Bearing, 34... Creasing, cutting blade,
36... Cover, 38... Drum, 40... Paperboard material, 51... Drive gear, 53... Output gear, 50
, 52, 53... Gear, 54... Output shaft, 55...
- Input shaft, 56...Motor, 57...Band wheel, 58.60...Retraction roller, γ0...Harmonic drive, 76...Gear, 90・P, 1. V
: Type continuously variable transmission (P, 1.V,), 122.124...
・Teeth, 102,112...Toothed tube, 108.150・
... Roller bearing, 118° 146 ... Washer, 129 ... Support body, 130 ... Second human power shaft,
142... Wave generation cam, 144... Axis key.

Claims (1)

Claims: 1. An apparatus for controlling the precision of punch cuts made in paperboard material passing between a pair of cooperating die rollers and anvil rollers, comprising: a drive for rotating said die rollers; a mechanical transmission that uses the output of the drive device as an input to selectively provide a variable output; It has a harmonic drive that receives P as a second human power,
A precision punching and cutting device characterized in that the anvil roller is rotated by the output of a harmonic drive.