U.S. patent number 3,869,950 [Application Number 05/338,659] was granted by the patent office on 1975-03-11 for apparatus for transverse cutting or perforating a continuously advancing web.
This patent grant is currently assigned to Societe Herve & Fils, Papeteries du Sentier (Societe Anonyme). Invention is credited to Arthur Bienvenu Dalla Serra.
United States Patent |
3,869,950 |
Serra |
March 11, 1975 |
APPARATUS FOR TRANSVERSE CUTTING OR PERFORATING A CONTINUOUSLY
ADVANCING WEB
Abstract
In an apparatus for repetitively cutting or perforating, in a
transverse direction, a continuously advancing web by means of a
rotating blade that cooperates with a stationary counterblade
having a cutting edge that lies in the plane of motion of the web;
the counterblade being inclined with respect to the axis of
rotation of the rotating blade by an angle of approximately
2.degree. maximum, the angular orientation of the apparatus with
respect to the direction of motion of the paper can be varied
precisely by micrometric means in order to compensate for
intentional differences between the tangential speed of the
rotating blade and the translational speed of the web.
Inventors: |
Serra; Arthur Bienvenu Dalla
(Aulnay sur Bois, FR) |
Assignee: |
Societe Herve & Fils,
Papeteries du Sentier (Societe Anonyme) (Paris,
FR)
|
Family
ID: |
26216962 |
Appl.
No.: |
05/338,659 |
Filed: |
March 7, 1973 |
Foreign Application Priority Data
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|
|
|
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Mar 7, 1972 [FR] |
|
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72.07826 |
Feb 19, 1973 [FR] |
|
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73.05792 |
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Current U.S.
Class: |
83/341;
83/349 |
Current CPC
Class: |
B26D
1/385 (20130101); Y10T 83/4847 (20150401); Y10T
83/4824 (20150401) |
Current International
Class: |
B26D
1/01 (20060101); B26D 1/38 (20060101); B26f
001/00 (); B41g 001/00 () |
Field of
Search: |
;83/341,349 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Meister; J. M.
Attorney, Agent or Firm: Greigg; Edwin E.
Claims
What is claimed is:
1. An apparatus for performing periodic, sequential penetrations in
a continuously advancing material web, comprising:
a. a supporting frame including first drive means for the material
web;
b. a transversely extending assembly pivotally mounted on said
supporting frame and including:
1. laterally associated bracket members;
2.
2. a straight shaft extending between and associated with the
bracket members, said shaft being positioned parallel to the plane
of the material web and further having an axis of rotation and
provided with second drive means;
3. a straight-edged rotatable cutter blade having a cutting edge
and mounted on and rotatable about said shaft in parallelism to
said axis of rotation so that, when rotated, the cutting edge
generates a rectangular cylinder of revolution; and
4. a flexible straight-edged counterblade having a cutting edge
including terminal end points and being held in its operative
position solely by attachment of said end points to said bracket
members and at an angle with respect to said axis of rotation and
in such a position that at least said two end points of the cutting
edge of the counterblade always lie on the surface of said cylinder
of revolution, that portion of said counterblade between said end
points being free of support; whereby during operation of the
apparatus, the cutting edge of the counterblade cooperates with the
cutting edge of the rotatable blade to perform the periodic,
sequential penetrations of the material web and the flexibility of
the counterblade alone permits the passage of the rotating blade
beyond the counterblade.
An apparatus as claimed in claim 1, wherein at least one of the
cooperating cutter means has a longitudinal extent of lesser length
than the width of the material to be severed to thereby retain
parallel uncut areas on oppositely disposed edges of the material
to thereby sustain continuous, uninterrupted travel thereof.
3. An apparatus as claimed in claim 1, wherein movement of the
counterblade means relative to its longitudinal extent is limited
by adjustable means.
4. An apparatus as claimed in claim 3, wherein the adjustable means
limits the degree of local bending of said counterblade means to a
predetermined value, said adjustable means including plural
elements.
5. An apparatus as claimed in claim 1, wherein the rotatable cutter
means has a tangential speed relative to the speed of travel of the
advancing material which may vary from 0.5 to 10 and preferably
from 2 to 8.
6. An apparatus as claimed in claim 1, wherein the rotatable cutter
means and the counterblade means from an angle which has a value in
radians at most equal to (10.sup..sup.-2 .sqroot.56R/L), R being
the radius of rotation of the rotary cutter and L being said
longitudinal extent of the counterblade means.
7. An apparatus as claimed in claim 6, wherein the angle between
the counterblade and the line perpendicular to the direction of
motion of the continuously advancing material is effectively equal
to .alpha./3 and is approximately equal to 0.003 radians.
8. An apparatus as claimed in claim 1, wherein at least one of the
bracket members is mounted adjustably relative to the direction of
motion of the continuously traveling material by a micrometric
means to thereby control the angle of cut with respect to the
travel of the material, with the angle .alpha. formed by the rotary
blade and the counterblade remaining constant.
Description
BACKGROUND OF THE INVENTION
The invention concerns an apparatus permitting the severing or the
making of detachable perforations on a continuously advancing web
or strip. It is also to be understood that the invention
contemplates the cutting and piercing of stacks of material. In the
specification, the word "cut" will have the meaning "cut or
detachable perforations."
DESCRIPTION OF PRIOR ART
Progressive sheet cutters are well known in this connection, see
the U.S. Pat. No. 3,401,585, Schmermund, the cutting as disclosed
in this patent being achieved by a device which has one rotatable
straight edged blade arranged to turn on an axis and cooperate with
another straight fixed blade, the two blades being adapted to cross
each other at all of their surface points during each revolution of
rotating blade. In a construction, such as that disclosed by
Schmermund, the blade and the counterblade are both inclined at
equal angles but in opposite sense with reference to the axis of
rotation at the moment where they cross at their midpoints.
Furthermore, the tangential speed of the rotating blade is equal to
the speed of advance of the web.
SUMMARY OF THE INVENTION
Now, on the one hand, it has been found, that these speeds can be
very different, i.e., that the tangential speed of the rotating
blade can be as much as 10 times the linear speed of advance of the
web or can be as little as one half that speed without reducing the
sharpness of the cut or of the perforation.
Furthermore, the elasticity of the steel blade permits the
application of certain elastic deformations by stress at the moment
of the shearing, without causing inconvenience. The permissible
limits of such deformations are, of course, very small near the
points of fixation or attachment points, and attain their maximum
value at the midpoint between two successive attachment points. It
is clear that the deformations of the two blades are additive when
these blades cross each other forcibly. Moreover, the very
structure of the frame supporting the rotating blade is susceptible
of elastic deformations and, further still, the rotational axis of
such rotating blade is mounted in its bearings with necessary and
non-negligible mechanical tolerances.
All these tolerances are additive and one may say that the blades
are pushing progressively against one another and repulse each
other and each assumes an arc-shape. This is the same as saying
that a given point of the edge of the lower blade might be situated
at a distance from the axis of rotation which is smaller than the
radius of the rotating blade; this difference at its maximum being
equal to the sum of the admissible flexures for the blade at this
point of their crossing. In order to avoid a damaging shock to the
blades and to the entire machine, it is necessary that the two
blades begin their engagement at the first point of crossing by
gliding without stress; the stress increasing progressively
beginning at this null value. By the same token, it is preferable
that the stress be essentially zero at the moment when the rotating
blade leaves the fixed blade, that is to say, at that end of this
fixed blade which is opposite the last point of engagement. Since
these considerations have been duly verified by a large number of
tests, it is possible to construct a rotating cutting apparatus of
simpler form, whose particular construction permits the solution of
problems in format changes, that is to say, in the variation of the
spacing of the cut.
One of the objects of the present invention is, therefore, to
specify a rotating cutting apparatus with straight, inclined blades
and in which the rotating blade is parallel to its axis of rotation
so that its edge describes around that axis a cylinder of
revolution which is effectively tangent to the moving plane of the
web, while the counterblade which is obliquely positioned with
reference to said axis of rotation has a slightly offset edge with
reference to the plane of motion of the web, the two ends of said
counterblade being situated on the surface of the imaginary
cylinder described by the edge of the rotating blade. Preferably,
the counterblade is mounted as rigidly as possible at its ends,
whereas the adjustment screws 15 which are placed along its entire
length, form stops to limit its flexing to a predetermined value
which is a function of the angle of inclination of said blade with
reference to the axis of rotation and also of the dimensional
characteristics of the machine.
It is of advantage to mount the counterblade on the frame of the
cage of the moving blade and the entire assembly is mounted so that
it may be pivoted with respect to the direction of motion of the
web in such a way as to permit adjustment of the angle which the
cutting line makes with respect to that direction.
The invention will be better understood by the following
description which makes reference to the attached drawing in
which:
FIG. 1 is a perspective schematic view of the device according to
the invention;
FIG. 2 shows the determination of the maximum flexure of the blade
without respect to the angular scale;
FIG. 3 shows the web as seen from above at the time of the cut; the
angles being considerably enlarged.
TURNING NOW TO THE DRAWINGS
In FIG. 1 a device for progressive cutting is placed on a conveyor
table on which a continuous web 1 having marginal perforations is
fed in the direction of arrow F1. For greater clarity, the only
elements of the table which are shown are a roller 2 and two pin
conveyors 3a and 3b which engage the perforations in the margins of
the web. It is to be understood, however, that additional conveyors
are spaced transversely of those identified as 3a and 3b, the
driving pins thereof being visible in the drawings of FIG. 1. The
cutting device is placed on a support 4 which is a part of the
frame of the table between the two pairs of conveyors 3a and 3b as
will be understood from the drawing.
This device comprises a frame or cage of which only the rectangular
brackets 5a and 5b are represented, but it should be noted that
those brackets are, in fact, rigidly connected with one another.
One of them, 5a, slides freely on the support 4, and the other, 5b,
carries a pivot 6 which is free to rotate in a seat provided in the
support 4. By means not shown, any lifting of the frame 5a, 5b with
reference to support 4 is prevented.
A shaft 7, parallel to the plane of the transport table, rotates in
bearings within brackets, 5a, 5b, and extends through bracket 5b. A
toothed wheel 8 is keyed to the end of shaft 7. This wheel 8 is
intended to be driven in rotation in the direction of arrow F2 by
means of a toothed belt, which is not shown, and by the same motor
which also drives the conveyors 3a and 3b. The driving pulleys (not
shown) of these conveyors and that of the belt are preferably
arranged respectively on the two "takeoffs" of a gear box 16.
The shaft 7 carries two flanges 9a and 9b between which blade 10
extends parallel thereto. Hence, this blade is rotated around shaft
7, and its edge generates the lateral surface of an imaginary
cylinder of revolution of radius R. The shaft 7 is placed at a
distance R from the plane of motion of the web so that the edge of
the mobile blade 10 brushes said plane at each revolution.
A fixed counterblade 11 is mounted transversely between the
brackets 5a, 5b of the device within an opening extending
transversely of the transport table with its ends being mounted as
rigidly as possible on the base plates of said brackets 5a and 5b.
This counterblade includes an edge portion that extends the entire
length of the spacing between the two flanges 9a and 9b. The end
11b of said edge is located within the plane of motion of web 1 and
also lies on the line representing the geometrical projection of
the axis of rotation of the mobile blade 10 onto the plane of
motion. The blade 11 and this projection of the axis of rotation
form a small angle whose maximum value will be evaluated
hereinafter and the other end of the edge 11a is then slightly
raised with reference to the plane of motion in such a way as to
bring it back, as exactly as possible, to a distance R from the
axis of rotation. In the example shown, the end 11a is displaced in
the direction of arrow F1 relative to the end 11b.
It is believed that it will now be clear that in each revolution of
shaft 7, the end 10b of the mobile blade comes into shockless
contact with the end 11b of the counterblade. Since the blades are
angularly displaced, they cross one another and glide over one
another in a shearing movement which determines the angle of the
cut of web 1. During the course of this gliding motion, the edge of
the counterblade 11 represents a secant to the cylinder generated
by the edge of blade 10; the two blades press against each other
and flex lightly, these flexures attaining their maximum values
when the blades cross each other midway of their length and then
the flexure thereof decreases uniformly until it becomes null, this
being achieved when the cooperation of the blades corresponds to
the contact of extremities 10a and 11a, which are both situated at
a distance R from the axis of rotation. An instant after attaining
this position, the blades are no longer in contact until the
following rotation.
In order to obtain a clean and regular cut, it is necessary that
the blades 10 and 11 be sufficiently rigid so as not to vibrate. In
order to accommodate these contradictory demands, rigidity and
applied flexure, it is necessary that the angular displacement of
these blades be small.
Referring now to FIG. 2, there is shown a geometric construction
which permits the calculation of the maximum value of this
displacement (for greater clarity, the angular scale has been
considerably enlarged). In this drawing, O represents an end view
of the axis of rotation, P is the plane of motion of the web, C
represents the cylinder of radius R which is generated by the edge
of the rotating blade, Oa represents the projection of axis O onto
the plane of motion. In the plane of that figure the extremity 11b
of the counterblade lies in Oa. The other extremity (11a) of the
counterblade is first displaced in the direction of arrow F1 and
arrives at 11a' and then is brought to a distance R from O, at
point 11a. For a better understanding of this, one could let
.theta. be the angle between O Oa and O 11a and let d be the
distance Oa 11a'. If .alpha. is the angle which the counterblade 11
makes with the axis O, and L is the length of the blades:
d = L tan .alpha. = R tan .theta.
where the sagitta f of the arc Oa 11a is given by:
f = 2R Sin.sup.2 (.theta./4)
This sagitta corresponds to the sum of the maximum flexures of the
two blades as they cross medially of their length. Since all these
angles are small, one may, as a first approximation, equate their
value in radians to those of their sines or their tangents, which
results in:
.theta. = L/R .alpha.
and
f = L.sup.2 .alpha..sup.2 /8R (.alpha. in radians)
Experience shows that f may have a maximum value of 7 .times.
10.sup. .sup.-4 L, which corresponds to a maximum value of .alpha.
such that:
.alpha..sup.2 = 56 .times. 10.sup. .sup.-4 .times. R/L
or
.alpha. = 10.sup..sup.-2 .sqroot.56 R/L
R is limited mechanically and L depends on the width of the webs
(less than 80 cm). The ratio R/L may be as high as one-fourth. In
that case, .alpha. can be at most 0.0374 radians, or .alpha. <
2.degree.10'.
It is obvious that in order to obtain a cut in the strip or webs
which is perpendicular to the direction F1 of the motion thereof,
the mobile blade 10 can be perpendicular to F1 only if its
tangential speed is equal to the speed of motion thereof. This is
possible if the apparatus is intended to make cuts of predetermined
format. But, to make use of the aforementioned fact that the speeds
can be made quite different, and in order to effect changes in the
spacing of the cuts by varying the ratio of said speeds,
particularly by means of a gear box with two take-offs, (as has
already been mentioned before), the mobile blade 10 is inclined by
an angle .beta. with respect to the perpendicular to F1.
The view of FIG. 3 shows the web 1 resting on the counterblade 11
and the projection of the mobile blade 10 on said web at the moment
where the two blades cross at A at the starting edge of the web. As
in FIG. 2, the angles are greatly exaggerated for greater clarity.
Let .gamma. be the angle of inclination of the counterblade with
respect to the straight line P which is perpendicular to F1. As the
mobile blade moves, the web 1 is cut progressively beginning at A
until the blade 10 crossses the counterblade 11 at C. During this
time the web has travelled in the direction of F1 and the point A
of the web has arrived at A', the line of cut is therefore A'C. The
ratio of the tangential speed of the blade 10 to the lateral speed
of motion of the web is therefore given by .rho. = BC/AA'.
In order that the cutting line be perpendicular to F1, i.e.
parallel to P, which is generally desired, it is sufficient that
AA' = a tan .gamma. (a is the width of the web) and since
BC = a (tan .beta. + tan .gamma. )
P = tan .beta. + tan .gamma./tan .gamma.
Since these angles are small, it is possible to set with sufficient
accuracy .rho. = .beta. + .gamma./.gamma. = .alpha./.gamma.
(.alpha. equals the angle between the two blades which is constant
by construction).
If .beta. = 0, then .rho. = 1; the two speeds are equal and the
length of the cut equals 2.pi. R if the device carries a single
moving blade. Starting with this format one can, therefore, obtain
a format which is n times smaller by multiplying the tangential
speed of the blade by n without changing the speed of lateral
motion of the web; this can be done, for example, with the aid of a
gear box with the two take-offs mentioned above. The ratio of
speeds is, therefore, equal to n and in order that the cut be
parallel to P, it is necessary that n = .beta./.gamma. or .gamma. =
.alpha./n. To achieve that, it is sufficient to pivot the entire
device around pivot 6 on support 4 (FIG. 1). In order to permit a
precise regulation, pivoting is achieved with the aid of a
micrometric screw 12 connected to the frame of the device and
travelling in a nut 13 which is part of support 4.
If it is required to cut thick stacks of sheets having, for
example, six sheets and five carbons, it is necessary that the
shearing angle .alpha. be at least 1.degree. so that by approaching
the limiting angle of 2.degree. 10' calculated beforehand and
beginning with a format 2.pi. R with .beta. = 0 and .gamma. =
.alpha. = 2.degree., it is easy to obtain a format which is 5 times
smaller, for example, all this while maintaining the
perpendicularity of the cutting line, by taking .gamma. =
2.degree./5 = 24' (.beta. = 1.degree. 36') and by multiplying the
tangential speed of the mobile blade by a factor of 5.
In practice, the usual formats vary between 3 inches and 12 inches,
i.e. a ratio of 1:4.
Since .rho. = .beta. + .gamma./.gamma., it would also be possible
to vary .rho. by varying .gamma. without varying .beta., i.e. by a
different mechanical construction, namely that of leaving the frame
of the mobile blade fixed with respect to the table and by making
only the counterblade pivot around one of its extremities, the
other extremity held by suitable means at a point within a portion
of the surface of the cylinder described by the edge of the
rotating blade. In this case, of course, angle .alpha. must vary.
It is clear that the variation of .gamma. alone allows less
flexibility for adjustment since .gamma. appears in both the
numerator and the denominator of the ratio .rho., (for example, if
at the outset .beta. = .gamma. = 1.degree. then to obtain .alpha.
< 2.degree. 10' one has .rho. = 2, but in order to obtain .rho.
= 8, one must put .gamma. .apprxeq. 8' and the total angle .alpha.
is 1.degree. 8', which is insufficient for thick stacks. This
arrangement is, therefore, only possible with very small angles
and, therefore, only for single sheets or very thin stacks.
One could also vary only .beta., which would entail the same
inconveniences; in this case, the counterblade would remain fixed
and the frame of the mobile blade would pivot as described
before.
If it is necessary to cut (or to perforate) only webs which are not
very thick, the shearing angle can be very small and, therefore, it
is possible to do without the control of the inclination of the
device on its support in order to reduce the cost.
Further, by looking at FIG. 3, one sees that if the speed of
rotation of blade 10 increases from the value which makes the trace
of the cut A'C perpendicular to F1, then the point A of the web
relocates to A'1 which lies between A and A'. If .rho. diminishes,
A'1 passes beyond A' with respect to A. In any case, this
displacement equals A.sub.1 ' A' = AA' - AA.sub.1 ' and A.sub.1 'A'
= a[.gamma. - .alpha.1.rho.] , where .gamma. and .alpha. are in
radians and the displacement is positive if A.sub.1 ' is between A
and A' and it is negative if A.sub.1 ' is to the right of A' in
FIG. 3.
Since .rho. should vary within the ratio 1:4, for example, by
passing through the values between 0.5 and 2, or 1 and 4, or 1.5
and 6, or 2 and 8, without ever exceeding the value 10, it is easy
to make a table or a graph which gives the various absolute values
of the coefficient .gamma./.beta. - 1/.rho., and one finds that the
best possible combination consists in taking .gamma. = .alpha./3
while .rho. varies between 2 and 8 in order that the maximum value
of this coefficient be as small as possible, and this maximum value
is then 5/24.
For example, if .alpha. equals 6 minutes of arc, i.e. 18 .times.
10.sup..sup.-4 radians, then the maximum displacement is: a .times.
18 .times. 10.sup..sup.-4 .times. 5/24 or a .times. 3.75 .times.
10.sup..sup.-4 and for a strip width of 400 mm, for example, this
maximum displacement will be 0.15 mm, which is quite acceptable for
commercial printing material, even if it is intended for an optical
reader. (As a matter of fact, any type of reader may be used.)
One should note that when detachable perforations are desired, one
of the blades is provided with teeth which are generally of the
order of 4 mm long and whose spacing is of the order of one
millimeter (almost always equal to 1.2 mm). Since the edges of the
blades have a width of at least approximately 0.3 mm, the flat
blade will always bear against at least two teeth of the toothed
blade as long as the angle .alpha. is less than the limit for which
tan .alpha. = 0.3/1.2 = 1/4, that is to say, as long as .alpha. is
less than 14.degree.. The values of .alpha. encountered in all the
preceding examples are very much smaller than this limit and there
is no fear that the crossing of the blades will take place between
two teeth which would, of course, be unacceptable since the flexure
could not be maintained and a lateral shock on each tooth would
result.
Naturally, numerous modifications could be made to the
aforementioned construction of the device, either in the mode of
transport of the web or their disposition, or in the arrangement of
the cutting device. Thus, for example, it could be advantageous to
reverse the elements previously described and place the mobile
blade in the lower position beneath the traveling web while the
counterblade would be in the superior or upper position. It is also
contemplated that where it is desirable to have a double cut in the
web, i.e., the blade would include an edge which gives two cutting
lines, with one each of the cutting lines straddling the line of
folding, such an arrangement would permit the faster removal of the
narrow strips as they fall down.
It could be useful in certain cases, in order to facilitate the
motion of the paper, that the pairs of conveyors such as 3a and 3b
(FIG. 1) be replaced by one single conveyor extending across the
cut, or at least one of the conveyors 3b may be in frictional
engagement with the paper above it. In order to achieve this, it is
necessary only that the marginal zones of strip 1 not be cut, that
is to say, one makes a cut between the edges by limiting the length
of the edge of at least that blade which is located underneath the
web, so as to perform a cut of predetermined length across the
web.
* * * * *