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Патент USA US2122092

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June 28, 1938.
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A. J. EN'GEL '-
'
MANUFACTURE OF ARTIFICIAL SILK
Filed Dec. 6, 1955
v
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2,122,092‘
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2 Sheets-Sheét 1
$9.41‘
SKIMMW
_June28,1938.
A__,_ENGE._
.
'
2,122,092
MANUFACTURE OF ARTIFICIAL SILK
Filed Dec. 6, 1955
,
2 Sheets-Sheet 2
1/115
Qwucmkon
' Shame/x5
Patented June 28, 1938
2,122,092 '
or Anemia s
Antonie Jacobus Engel, Arnhem, Netherlands,
Corporation,
assignor to American
N. 0., a corporation of Delaware
Erika,
Application December 6, 1935, Serial No. 53,254
In the Netherlands December 8, 1934 .
(501 242-43)
8 C a: 1 Ms
having a frusto-conical shape. However, the
This invention relates to traverse mechanism
of the type generally used in the production of
form of the spool or bobbin ends does not de
pend upon‘ the number of rotations of the auxil- ,
bobbins and more particularly to means for
iary movement but exclusively upon the speed
forming the tapered winding on the end of the
v
bobbin spools.
5
.
pattern of the auxiliary movement.
‘Therefore, an object of this invention is the
provision of mechanism whereby thread can be
wound upon bobbins to form a package having
end edges thick enough for‘ proper washing, dye
-
When winding textile materials, particularly
arti?cial silk, as is known, a traverse varying
device is employed by means of which the ma
terial obtained from the spinning process is
guided so as to be deposited on bobbin spools in
ing, or drying.
a predetermined form. Traverse mechanisms
whereby a spool or package of thread is formed
which will‘ be free from noticeable ridges.
winding on the end of the spool a conical shape,
but these have not proved to be satisfactory be
cause of the difference in density between'the
end edges of the winding and the main body.
This invention further contemplates the pro-'
vision of a mechanism whereby a number of the 15
above described movements may be combined
to give the desired type of winding.
Spools or bobbins formed in
Other objects, advantages and characteristic
this manner cannot be washed, dyed, or dried
features of the invention will become apparent
evenly.
as the description of the disclosed embodiment _
progresses, reference being had to the annexed '
When winding bobbins with freshly spun
rayon the traverse movements most generally
drawings in which:
Figs. 1, 2 and 3 are diagrammatic representa
tions of fragmentary‘longitudinal sections of cy
lindrical windings showing the different eiiects 25
produced in forming the winding with different
arrangement of traverse mechanism; ./
used are almost always made up of one main
movement combined with one or two auxiliary
movements. The main movement being that ob
tained by allowing the roller of the thread guide
25
arm to roll around the periphery of a cam of
predetermined shape. The auxiliary movements
I
employed are, ?rst, the simple stroke displace-- ‘
ment and the regular stroke shortening move
10’
This invention also contemplates, apparatus
have been employed heretofore which give the
portion thereof.
r
Fig. 4 is a diagrammatic illustration of ‘the
" traverse guide as taught by this invention show
30 ment that takes place during the spinning pe
ing the position of the cams while eifecting 30
maximum displacement of the thread guide to
riod, and secondly, the “Pilgrim Step”. These ,
right;
movements are distinguished one from the other theFig.
5 is similar to Fig. 4 but showing the
by the ratio between the number of rot'ations'of
the auxiliary movements and the rotations of the
main movement. When using the ‘stroke short
ening movement as referred to above, then dur
ing‘ the entire‘ winding on period‘ the auxiliary
movement moves only once causing the ampli
tude of traverse to change from a maximum in
starting the winding on period to a minimum on
40
the completion of the winding on period. Then
when the “Pilgrim Step” is employed the auxil
iary movement may make twenty times as many
rotations as the main movement thereby caus
ing the guide to oscillate backward and forward
45
in its path across the spool or bobbin a corre-v
sponding number of times. Using the stroke dis
placement movement the auxiliary movement
may turn as much as one twentieth the speed
of the main movement thereby causing the am
50
plitude of traverse to decrease to a minimum and
build up to a maximum during 20 cycles of the
,
guide.
In winding yarn into packages the effect of
55 the auxiliary movement is to form packages
thread guide at its maximum displacement to
the left;
'
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.
v
‘Fig. 6 is a front detail elevation of the traverse
_ mechanism}
Fig. '7 is a detail vertical longitudinal section
along the line 'l-,-'l of Fig. 6 showing the gear
train employed in driving the auxiliary cam;
Fig. 8 is a vertical section of a modi?cation of
the gear train shown in Fig. '1, showing the use
of a different gear ratio;
I
Fig. 9 is a vertical section of a second modi?ca
45
tion of the auxiliary cam driving mechanism.
Referring‘to the drawings, particularly Figs. 6
and "l, the mechanism is driven by a main drive
shaft III that is connected to a suitable source of
power not shown. A hub I l is ?tted on the oppo
site end of shaft I0 and adapted to turn with 50
the shaft to drive the main eccentric or cam I2.
Eccentric I2 is substantially heart-shaped in‘ '
form and the periphery thereof serves as a track
on which the roller \end of a bell crank, which
‘serves as the thread guide arm, is adapted to
2
'
move.
‘
"
2,122,092
The eccentric I2 is secured to a guidev
member l3 which is adapted to move in a
line which is at right angles. to the shaft.
Provisions for such movement are made by
slotting member l3 as shown at M and IE to
receive the driving crank pine l6 and the hub
II respectively. The‘ crank pin 16 is secured to
a crank arm I‘! vwhich is made integral with hub
H, by means of a bolt l8. Such'an arrangement
10 is provided to permit the .main cam I2 to ‘move
and may only be altered by changing the con
tours of v‘cam 22.
Heart-shaped camsmountedand adapted to
turn on eccentric bushings have been usedhere
tofore on traverse mechanisms.
In operation the
cam is driven at a constant speed while the eccen
tric bushing is rotated at any desired speed de
pending upon the form-‘of movement that is to ‘
be employed in forming the winding. First let
along its center line i. e., its line of symmetry, _ us suppose that the bushing turns very slow as 10
with respect to the main drive shaft l0. Springs compared to the main cam, for example, no more
I 9 are connected to hub I I and the cam I2 and
thereby normally tend to force the point of cam
15 I 2 toward the main shaft In. This movement,
however, is limited by roller 22 that is mounted
upon the guide member l3 by means ‘of bolt 2|.
A second or auxiliary cam or eccentric member
22, the periphery of which forms the path for
20 roller 20, governs the movement of the main cam
with respect to the shaft. Thus it can be read
ily seen that although the main cam I2 is adapted
to slide on the shaft along its center line, it is
also caused to rotate by the shaft... Cam‘ 22 is
25 keyed to and adapted to be driven by bushing,23.
Bushing 23 is driven by means of gears 24, 25,
26 and-21 from the main shaft l0. These gears
obviously may be given any desired ratio to obtain
varying relative speeds between cam 22 and cam
As shown in Fig. 8 a gear ratio may be se
lected which will cause the cam 22 to be driven
30 I 2.
at a relatively higher speed than cam l2, while
on the other hand should it be desirable to drive
cam 22 at a somewhat lower speed than cam I2,
35 an arrangement of gears'such as is shown in
Fig. 9 may be employed. The gears 24-21 must
have then e. g. 34, 34, 29 and 39 teeth respectively.
The form that the winding will take on the
spool is directly dependent upon the speed pat
40 tern of cam 22. Therefore, the shape of ,cam 22
must be of such contours as will give the desired
form to the winding. In operation if it is desired
to employ the “Pilgrim Step" movement in wind—
ling a thread on a spool or bobbin the cam 22
must, of'necessity, be driven at a higher speed
than cam. I2. This will effect an oscillatory
movement of the thread guide arm which will
cause the thread to move forward and backward
a number of times corresponding to'the ratio of
the speeds of the respective cams during each
traverse of the spool or bobbin. It is to be un
derstood that cam 22-will have the desired con
tours to effect a proper shape of winding. The
than ‘180° per “wind on”.
Then, the cam will
move with respect to the driving shaft in such
a way that during the winding on period the
stroke of the cam decreases regularly. The
eccentric bushing thus determines the speed at
which the stroke will decrease and if it is as
sumed that the relative rotation of the eccentric
bushing as compared to the cam is of a uniform
speed, then it follows that the displacement of 20
the cam during the beginning of the winding on
period takes place very slowly. However, during
the winding on period it will increase, then to
ward the middle of this period, the speed of dis
placement will reach a maximum. Thereafter 25
thevspeed of displacement will decrease and to
ward the end of the winding on period will ap
proach zero as a limit.
Thus it can be seen that
the speed pattern of displacement will assume the
form of a sine curve.‘ 'In this case the frusto
conical ends of the spool package will appear as
indicated in Fig. 1 by the heavy line.
Alterations in the relative speed of the cam
and bushing will not change the theoretical form
of the spool end. When the eccentric bushing is 35
turned 360° instead of 180° relative to the cam
‘during one winding on period the stroke is as
indicated above throughout the ?rst part of the
period, but twice as fast.
The package thus
formed up to this point will only,have one-half
the thickness of that discussed above. However, 40
during the movement of the eccentric bushing
through the remaining 180° of the winding on
period the stroke will increase again and the
movements will be exactly opposite to the ones
in the first half. I The changes of the stroke are 45
equal, but opposite, consequently the package
is built up exactly as in the ?rst instance. In
either case the package retains the same form
regardless of whether the eccentric bushing makes
one revolution or many relative to the cam. So 50
Fig. 1 illustrates ,also the form of the spool or
“Pilgrim Step” movement may be accomplished package formed by the simple stroke displace- '
55 by utilizing a gear trainv such as that disclosed ment or “Pilgrim Step” traverse produced by the
auxiliary movement derived from‘ the eccentric
in Fig. 8, the gears 2t-_21 having for example I bushing
55
in the cam.
,
respectively 45, 23, 45 and 23 teeth.
If it is desired to wind the bobbins by the stroke ,
shortening movement, then, of necessity, cam 22
80 must be driven at a much slower speed than cam
l2. A gear train such as shown in Fig. 7 ‘may
be employed to effect this movement, the number
of teeth of gears 26-2'I being respectively 151,
150, 149 and 150. Driving cam 22 slower than
cam i2 will cause'the thread guide arm to move
through a path traversing the spool from maxi
mum amplitude or the longest stroke to an am
plitude which approaches zero as a limit or the
minimum stroke in the first 180° movement of
70 cam 22. As cam 22 completes one revolution or
the second 180° the amplitude of traverse of the
thread guide will increase to a maximum. Re
gardless of the number of revolutions made by
the cam 22 relative to the cam l2 the shape of
M the winding on the ‘spool will remain the same
Due to the fact that the thread lags on making
the return stroke relative to the thread guide,
one does not get the theoretical form ofspool end.
The lagging of the thread relative to the guide 60
on returns will result in an extra turn of yarn
being deposited on all points of the return and
with a given number of returns these surplus
turns will amount to a substantial quantity of
yarn. It can readily be seen that whenever the
change in the length of stroke is small there will 65
be a greater number of reverses that will come
together and the amount of yarn built up as a
result of the lag will increase accordingly. In
Fig. v1 a dotted line illustrates how the shape of 70
the end of the spool is changed by this phenom
enon and further explains how ridges in the wind
ing originate.
Another auxiliary movement that has been. pro
posed for reducing the stroke is one which effects '
2,122,002
a constant speed displacement of a main cam
along a line at right angles to the axis of rota
'
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3
driven in the same direction at uniformly differ
ent speeds by reason of the gears 24, 25, 26 and
21 which transmit power from the shaft II), with
tion. A spool produced when utilizing this move
which the main cam is operatively connected,
ment is of the form, theoretically, as illustrated to the bushing 23, to which latter the auxiliary
by
the
fulllines
in
Fig.
2.
The
lagging,
of
the
cam is keyed. The main cam i2 is thus free'to
Ur
thread, however, will cause the shape of the spool move me line corresponding to its line of sym
to assume a form such as is indicated by dotted metrys-that is, in a line which bisects the cam
line in this same ?gure. Although the ridges are into two symmetrical parts-and is held by'
much smaller than those illustrated in Fig. l springs IS in, contact with the auxiliary cam‘ 22. 10
in dotted line,'they are, nevertheless, of substan
Therefore, the displacement of the roller riding
tial size and, of course, are objectionable. Other upon the periphery of the main cam and control
difficulties encountered in using such a move
ling the traverse mechanism will be the result
ment are, that the winding on the end‘ of the ant of two different movements of the main cam,
spool'is too thin and introduces difficulties when namely, the displacement imparted to the roller 15
subjected to suction or pressure wash due to the by the throw of the main cam rotating about the
fact that the permeability of the end of the wind
axis of drive shaft Ill, and the displacement re
ing is so much greater than’that of the mid
sulting from shifting of the main cam along its
line of symmetry .under'the in?uence of the‘
section.
'
.
'
20
A spool or package of thread formed by utilizing ,
auxiliary cam.
,
The main cam being heart-shaped, the shape
20 the mechanism and method set out herein may .
have a form such as is illustrated by‘ Fig. 3 i. e. of the auxiliary cam is preferably so selected that
the sectional contour of the end ‘of the winding the main cam moves smoothly along its line of
can be of a form corresponding to a logarithmic symmetry between its two extremes of travel
curve. This form has the‘ advantage, that it gives with a speed of movement that increases with a 25
an even permeability in pressure- or suction
decrease in the distance between the highest point
washing and that it is free of ‘ridges. This is of the main cam and its axis of rotation,‘ and vice
possible because the thread lags when it reverses versa. Also the auxiliary cam is so formed that
and a crossing different from that in the cylin
the cam throws of successive points of its pe
drical part results, thereby effecting a lesser de
riphery vary in accordance with a logarithmic 30
30 gree of permeability per unit thickness of pack
age, which provides the necessary equalizing fac
tor. The varying of the thickness after a loga
rithmic curve'is obtained by making the speed
of the'auxiliary motion for stroke reduction in
crease regularly from the beginning to the end
of the wind on period. The constructions here
to known. can not give such a form, as they have
'40
not the characteristic of my invention, that the
two traverse movements are combined in such
a way that the auxiliary movement is employed
only to move the main cam or eccentric member
in its position relative to the shaft, while in each
position this main ‘cam alone determines the
length of the stroke. So the form of the auxiliary
cam can be chosen freely, as at any moment only
.one point of.it is working.
The shape of the extreme ends of the spool is
only a?ected by the change in shape of the aux
iliary cam in the ‘vicinity of the point which has
the greatest radius, and that portion of the spool
50 end de?ned by the extreme outer end of the spool
and the cylindrical portion thereof is dependent
. for its shape on the shape of the auxiliary cam
curve.
‘
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_
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In this way the thread guide carried by the
traverse mechanism travels back and forth along
the spool or bobbin with the speed of the auxiliary
motion imparted by the auxiliary cam regularly -
increasing during the period of the shortening
of the stroke of the thread guide. 1 This results
in a package having the general form indicated
in Fig. 3 in which the‘end edges are substantially
free from ridges and are of a suitable density for 40
proper washing, dyeing and drying. While the
invention in-its preferred form contemplates the
employment of an auxiliary cam of the logarith
mic character described above, it will‘ be apparent
that in its broadest aspect the invention is not 45
limited to any particular shape of auxiliary cam,
and that the shape of ‘such cam may be suitably
selected according to. the desired form vof the
package to be wound.
,
, Although for purpose of illustration and ex
no
planation this invention has been described in
connection with a thread guide that is fastened to '
the end of a swinging lever of the bell crank type,
the invention is equally applicable to the recipro
in‘ the vicinity of its smallest radius. Therefore, eating form of guide member. In fact, it would as
' it is obvious that regardless of the movement ?nd application to substantially all forms of tra
55 employed any desired shape of winding can be
verse mechanisms employed in the spinning art.
obtained by the selection of an auxiliary cam
"Permeability" as used herein is de?ned as
having the desired contours.
that quantity of water which will flow through
The position of the thread guide has been dia
one square centimeter of the surface of the pack
grammatically indicated in Figs. 4 and 5 for age at a given pressure in a, given interval of‘
60 maximum strokes. Its position is de?nable in
time, while "wind‘ on” or “winding on" period, I
one extreme position by the dimension “A” of as used herein, refers to a period in which the
the main cam plus dimension "a” of the auxiliary
cam and in the other extreme, position by “28" ’ spool or package is completely wound.
minus “11". Therefore, the total stroke is (“A” I What I claim is:
_ 1. In an apparatus for winding spools or bob
plus “a.") minus (“3” minus "113’) and is equal to
a traverse actuating mechanism comprising
“A” minus “3” plus 2 “a”. Minimum stroke may bins,
a
main
cam of symmetrical shape and adapted to
be obtained by rotating the auxiliary cam 180°
guide arm of the traverse
(see Figures 4 and.5). In this case the roller is control the thread
then closer to the shaft and the stroke is "A" mechanism, an auxiliary cam located adjacent
the main cam and independently rotatable with
minus “13” plus 2 “b”.
‘
The operation of the apparatus will be readily respect thereto, means supporting the main cam
apparent from the foregoing description. Dur
75
ing rotation of the drive shaft in, the main heart
shaped cam l2 and the aumliar'y cam 22 will be
_
65
,
70
for displacement along its line of symmetry,
means extending between the main cam and aux
iliary cam whereby relative rotation between the 75,
4
2,122,092
cams causes displacement of the main cam along
its line of symmetry and means for rotating the
‘cams at relatively different speeds.
2. In an apparatus for winding spools or bob
bins, a traverse actuating mechanism comprising
a main cam of symmetrical shape and adapted
to control the thread guide arm of the traverse
mechanism, an auxiliary cam located adjacent
'10
the main cam and independently rotatable with
respect thereto, a roller supported by the auxiliary
cam, means yieldingly retaining the roller in en
gagement with the periphery of the auxiliary
cam whereby relative rotation between the cams
causes displacement of the main cam along its line
15 of symmetry and means for rotating the cams at
relatively di?erent speeds.
3. In an apparatus for winding spools or bob
bins, a traverse actuating mechanism comprising
a rotary drive shaft, a main cam‘ operatively con
20 nected for rotation to the drive shaft, said main
cam being of symmetrical shape and adapted to
‘control the thread guide arm of the traverse
mechanism, an auxiliary cam located in closely
spaced parallel relation to the main cam and
independently rotatable with respect thereto,
means supporting the main cam for displacement
along its line of symmetry, means extending be
tween the main cam and auxiliary cam whereby
relative rotation between the cams causes dis
30 placement of the main cam along its line of sym
metry and means for rotating the drive shaft and
auxiliary cam.
'
4. In an apparatus for winding spools or bob
bins, a traverse actuating mechanism comprising
35, ,a rotary drive' shaft, a main cam operatively con
nected for rotation to the drive shaft, said main
"cam being of symmetrical shape and adapted to
control the thread guide arm of the traverse
mechanism, an auxiliary cam‘ located in closely
40 spaced parallel relation to the main cam and in
dependently rotatable with respect thereto about
cam and independently rotatable with respect
thereto, means supporting the main cam for dis
placement along its line of symmetry, means ex
tending between the main cam and auxiliary cam
whereby relative rotation between the cams causes
displacement o'f the main cam along its line of
nected to the drive shaft for rotating the auxiliary
cam at a diiferent speed relative to the drive
shaft.
I
6. In an apparatus for winding spools or bob
bins, a traverse actuating mechanism compris
ing a main cam of symmetrical shape and
adapted to control the thread guide arm of the
traverse mechanism, an auxiliary cam located
adjacent the main cam and independently rotat
able with respect thereto, means supporting the '
main cam for displacement along its line of
symmetry, means extending between the main 20
cam and auxiliary cam whereby relative rota
tion between the cams causes displacement of the
main cam along its- line of symmetry, said auxili
ary cam being so shaped thatthe cam throws of
successive points upon its periphery vary in ac-'
cordance with a logarithmic curve, and means
for rotating the cams at relatively different
speeds.
_
7. In an apparatus for winding spools or bob
bins, a traverse actuating mechanism compris- .
ing a rotary drive shaft, a hub ?xed to the drive
shaft and having a crank arm‘ extending radially
therefrom, a main cam of symmetrical shape
loosely associated with the hub, and adapted to
control the thread guide of the traverse mecha 35
nism, a guide member rigidly ?xed to the main
cam and having an elongated slot therein dis
posed parallel to the line of symmetry of the main
cam, a pin extending laterally from the crank
arm and receivable in the slot for imparting rota 40'
an axis corresponding to the axis of said drive' tion to the guide member and main cam, a bush
shaft, means supporting the main cam fordis
placement along its line of symme'try,>means ex
tending from the main cam‘ and yieldingly main_
tained in engagement with the periphery of the
auxiliary cam whereby relative rotation between
the cams causes displacement of the main cam
along its line of symmetry and means for rotat
50 ing the drive shaft and auxiliary cam at relatively
different speeds.
>
.
5. In an apparatus for winding spools or bob
' , - bins, a traverse actuating mechanism‘ comprising
a rotary drive shaft, a main cam operatively
55 connected for rotation to the drive shaft, said
CH
symmetry, means for rotating the drive shaft
and speed change mechanism operatively con
ing surrounding the drive shaft and independ
ently rotatable with respect thereto, an auxiliary
cam ?xed"to said bushing and located adjacent
the guide member, a roller' carried by said guide
member, spring means yieldingly urging said
roller into engagement with the periphery of the
auxiliary cam whereby relative rotation between
‘the'cams causes displacement of the main cam
along its line of symmetry, and means for rotat
ing the drive shaft and bushing at different 50
speeds.
8. A traverse actuating mechanism as set
forth in claim 7 in which the auxiliary cam is so
main cam being of symmetrical shape and' shaped'that the cam‘ throws of successivelpoints 55
upon its periphery vary in accordance with a
adapted to control the thread guide arm of the logarithmic
curve.
.
,
traverse‘ mechanism, an auxiliary cam located
in closely spaced parallel relation to the main
ANTONIE JACOBUS ENGEL.
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