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Патент USA US3081052

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March 12, 1963
‘ 3,031,046
Filed May 19. 1960
4 Sheets-Sheet 1
March 12, 1963
Filed May 19, 1960
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4 Sheets-Sheet 2
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March 12, 1963
4 Sheets-Sheet 3'
Filed May 19, 1960
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March 12,‘ 1963
Filed May 19, 1960
4 Sheets-Sheet 4
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United States Patent 0 "
3,081 ,046
Patented Mar; 12, 1963
ple, when the package has grown to the desired ultimate
size, prevention of the winding of additional yarn thereon
is obviously important. Since the package drive roll was
constantly rotating in the patented machine, this could
Porter I. Barnes, Jr., Johnston, and Thomas E. Pitts,
Cranston, R.I., assignors to Leesona Corporation,
Cranston, R.I., a corporation of Massachusetts
Eiled, May 19, 1960, Ser. No. 30,347
19 Claims. (Cl. 242-36)
be achieved only by moving the package away from the
roll. However, as already explained, the main package
This invention relates to a control mechanism for the
delivery package of a Winding machine and is more par
ticularly concerned with a mechanism for latching the
necessary in order to disengage the package from the
drive roll.
Again, the traveling yarn may accidentally become
attracted to the drive roll and wind therearound instead
of upon the package, forming what is known in the art
arm was very effectively restrained against movement by
the arm control cam, and to resort to a rather complicated
lift mechanism acting on a package arm extension was
delivery package of a winding machine in winding posi
tion and for releasing the package from that position upon
the occurrence of any one of a plurality of conditions.
In US. Patent 2,764,362 to Goodhue et al., entitled,
“Winding Machines,” issued September 25, 1956, there
is disclosed and claimed a fully automatic winding ma
chine for winding yarn or the like into various forms of
packages, especially cones.
In essence, the machine of this patent consists of a
winding section including a rotatable winding mandrel
mounted for controlled movement between a winding
position, a braking position, and a reverse rotation posi~
tion and a drive roll for rotating the package in winding
position and provided with a groove to traverse the yarn
15 ' as “roll lap,” which can build up to such an extent between
two rigidly mounted adjacent parts as to exert su?icient
force to actually bend one of those parts. The patented
machine lacked a device for sensing the build-up of a
roll lap and, due to the inability of the main package arm
to pivot to lift the package away from the constantly
rotating drive roll, the addition to that machine of a
knock-off motion effective to halt the delivery of the yarn
and to disengage the package from the roll would be
most di?icult, except through the utilization of a com
25 plicated arrangement similar to the lift mechanism al
ready described.
From these considerations, it will immediately be ap
parent that the direct relationship between the main
package arm and the package arm control cam, whereby
which section includes a knotter and separate means for
?nding the respective free ends of the broken yarn and 30 the position of the former was determined exclusively
by the latter, constituted a rather serious practical defect
conveying them to the knotter to be joined together; a
in the design of the patented machine; and a principal
preliminary yarn servicing section including means for
object of the present invention is to divorce from the
detecting, tensioning, and cleaning the yarn supplied to
control cam operable during the end-?nding and re
the mandrel; and an enclosed control section for super
uniting cycle, the function of maintaining the main pack-.
intending the other sections and controlling the function
age arm and the package carried thereon in operative
ing thereof. It was contemplated in this machine that the
_ being wound upon the package; an end-?nding and re
uniting section operable in the event of thread breakage,
position during normal winding, while still allowing that
winding mandrel was carried by a main package arm
mounted for pivotal movement on one side of the control
section adjacent the rear end thereof, the arm being moved
by means of a control cam.
The control cam was pro
cam to govern the position of the main package arm
and package during the end-?nding and re-uniting cycle.
vided with an arrangement of consecutive camming sur
faces operable during rotation thereof to move the arm
from a normal winding position to a braking position,
with a sufficient dwell at the braking position to allow
the rotating package to be brought to a halt, and then 45
to a reverse rotation position, where the package was ro~
tated in a direction opposite to that of normal winding
to enable the free end of a broken thread to be extricated
from the convolutions on the package, engaged by a
A further object of the invention is a main package
arm latch operative to maintain the main package arm in
normal winding position, which latch is wholly inde
pendent of the main package arm control cam and is
adapted to be disengaged from the main package arm to
permit the arm to move the package away from the drive
roll in the event of either of breakage of the thread, the
occurrence of a roll lap, or the attainment of ultimate
package size.
Another object of the invention is to provide the winding
delivery end-?nding means and conveyed to the knotter 50 machine with a main package arm capable of limited
for connection to the free supply end, the dwell at reverse
movement independently of the package control cam to
rotation position being sut?cient for the end-?nding means
disengage the package from the package drive roll, such
the opposite direction to bring the package ?rst to braking
cycle is institute-d.
package through the stages just described was instigated
disengaged prior to the beginning of an end-?nding and re
uniting cycle to permit the package to move to braking
position immediately and in advance of the rotation of
movement of the main package arm being eifective to
to perform its function. After this dwell at the reverse
sever the yarn being delivered to the package, except when
rotation position, during which the cam continued to ro
tate, the main package arm was moved by the cam in 55 thread breakage occurs and an end-?nding and re-uniting
An additional object of the invention is a winding ma
position to halt its reverse rotation, at which time the ends
chine including a latch for positioning the main package
were re-united, and then to normal winding position and
arm in operative position for normal winding independent
into peripheral contact with the drive roll.
Rotation of the package control cam to move the main 60 ly of the main package arm control cam, which latch is
as a result of thread breakage and, when the thread was
running properly, the cam was locked against rotation,
the control cam.
the main package arm being held in normal winding
position by the corresponding camming surface on the 65 In the course of re-designing the control section of the
control cam.
machine to achieve the above objectives, it was found
possible to effect a major simpli?cation in the mechanism
While it is virtually essential for the package to be
for bringing the winding operation to a halt when the
moved between these several positions during the end
?nding and re-uniting cycle of the machine, this is not
package had achieved the desired ultimate size and, ac
the only time at which movement of the package away
cordingly, the present invention also embodies novel fea
from normal winding position is desirable. For exam
tures in the package sizing mechanism.
Thus, another object of the invention is the provision
of a package sizing latch operatively associated with the
main package arm positioning latch for automatically dis
engaging the positioning latch at the moment the desired
ultimate package size is attained, whereby the main pack
20 designates a U-shaped frame for the control section of
the winding machine, which frame comprises a generally
rectangular base 21 and side-walls 22 and 23 upstanding
from opposite side edges of the base. Located above
frame 20 adjacent the front thereof is a package drive
age arm and the package carried thereby are released from
roll D and a reverse rotation roll R, the means for sup
normal winding position to remove the package from driv
ing contact with the package drive roll and to sever the
porting and driving these two rolls being omitted, and
a braking member B arranged between rolls D and R and
yarn being delivered to the package.
supported by means which will be described later. Brak
A further object of the invention is a winding machine 10 ing member B may be in the form either of an elongated
including a package sizing latch of the type just described,
cylindrical rod, as shown in FIG. 1, or a ?at plate, as
which, after releasing the main package arm from the
shown in the aforesaid patent. Drive roll D, braking
package arm positioning latch to permit the main package
member B, and reverse rotation roll R constitute three
arm and package to move away from winding position, is
of the four positions assumed by the package during the
effective to stop the arm and package in a position inter 15 operation of the machine (the fourth position being seen
mediate normal winding and braking positions, whereby
in FIG. 2) and in FIG. 1, the package being wound is
the package remains in an essentially forward location and
shown in the ?rst of these positions, namely, in frictional
is readily accessible to the machine attendant.
contact with the periphery of roll D. The normal posi
A still further object of the invention is the provision
tion of the package, when winding, proceeds in a regular
of a package sizing latch of the type described which is
easily adjustable to permit the size of the ultimate pack
As illustrated, the machine is set up to wind a conical
age to be varied.
These and other objects and advantages of the present
’ invention will be apparent from the following detailed
package or cop upon a conical paper tube or core held
on a winding mandrel or cop holder 24, which is likewise
conical, although other shapes of mandrels and tube
description when read in conjunction with the accompany 25 could be substituted. Winding mandrel 24 is rotatably
ing drawings, in which:
FIG. 1 is a right side elevation of the control section
mounted on a winding spindle (not visible in the draw
ings) which is, in turn, supported on a generally trans
of the winding machine of U.S. Patent 2,764,362 embody
versely extending arm (also not visible in the drawings)
ing the improvements of the present invention, the com
capable of pivotal movement at its end about a substan
ponents of the section being shown in normal winding posi 30 tially vertical axis. The end of this arm is ?tted within a
FIG. 2 is a view similar to FIG. 1, but with the com
ponents shown in the position assumed thereby when the
package has achieved the desired ultimate size and the
winding operation is halted;
FIG. 3 is a top plan view, looking down on the control
section of the machine, certain of the elements normally
in this section being omitted for sake of clarity;
FIG. 4 is a detailed view, partly in elevation and partly
in section, showing the operating means for the yarn
severing means and also certain elements of the locking
means for the control cam unit;
FIG. 5 is an enlarged detailed view of the yarn sever
ing means of FIG. 4 in the position assumed thereby when
the yarn is severed;
FIG. 6 is an enlarged detailed view of the cam unit
locking means of FIG. 4, with the end severing means and
its associated operating means omitted, the locking means
being shown in disengaged position;
REG. 7 is a view similar to FIG. 6, but with the cam
unit locking means shown in engaged position; and
FIG. 8 is a view similar to FIG. 2, showing the package
socket 26 provided for that purpose at the free end of an
extension arm 28 disposed in approximate vertical align
ment with frame side 22‘. The end of extension arm 28
opposite socket 26 is rotatably held in two spaced-apart
35 bearing collars 30 and 32 formed as an integral part of
an irregularly shaped joint member 34. At its lower end,
member 34 is pivoted on a stud shaft 36 extending hori
zontally and inwardly of the upper end of a massively con
structed, elongated link 38, which is herein designated the
“main package support arm.” It will be seen that, in
effect, joint member 34 functions as a kind of universal
joint permitting package extension arm 28 to pivot with
respect to both the horizontal axis of stud shaft 36 and
the upwardly and forwardly inclined axis of spaced-apart
bearings 30, 32, whereby the winding spindle and mandrel
can swing upwardly as a unit about shaft 36 away from
drive roll D, as well as to pivot backwardly and for
wardly with respect to socket 26 and to cant upwardly
with respect to bearings 30, 32. In this way, the winding
spindle is adapted to recede from the driving roll in a
manner suitable for the building of a conically shaped
positioning and supporting components in the position
assumed after either thread breakage or roll lap has
jacent the upper rear corner of frame side 22 on the
Before proceeding with the detailed description of the
invention, it should perhaps be explained that the im
provements of the present invention are essentially con
?ned to the winding section and control section of the
Main package arm 38 is pivoted at its lower end ad
exterior end of a shaft 40 extending transversely the full
width of frame 29 and journaled in suitable hearings in
the frame sides (FIG. 3). Located adjacent the upper
' edge of frame side 22 intermediate the ends thereof is
winding machine of the previously identi?ed patent. As 60 an outwardly projecting stud 4-2 on which is pivoted an
elongated plate 44 extending parallel to side 22 and ad
the other sections of the machine form no part of the
jacent the inside face of arm 38, which plate constitutes
invention, they will neither be described nor illustrated
the main package arm positioning latch, termed for con
here. Similarly, some of the elements normally forming
1 venience the “main package latch” or simply “main latch.”
a part of the control section of the patented machine have
no real relationship to the details of the invention and have 65 At its extreme rear end, main latch 44 terminates in a
downwardly curved tail 46, for a purpose to be described
likewise been omitted. Thus, for an over-all understand
later. Slightly forwardly of tail 46, the upper edge there
ing of a complete operating machine, reference should
of is formed with a shoulder v48 adapted to be engaged by
be made to the aforesaid Patent 2,764,362. It will be
a pin 59 rigidly embedded in main package arm 38 at
understood that the parts of the patented machine which
are absent from this description and the accompanying 70 a point thereon somewhat closer to stud shaft 36 than
to ‘shaft 40. Pin 59 projects a short distance inwardly of
drawings will ordinarily be present in a complete working
arm 38, the adjacent portions of the arm being cut away
machine and may be the same as shown and described in
i in FIG. 1 to show pin 50 in section, and the rear face of
that patent.
the pin is preferably ?attened for better engagement with
Turning now to a detailed description of the draw
ings, with initial reference to FIGS. 1 and 3, the numeral 75 shoulder 48. Also, on the upper edge of the main pack
age latch, at a point spaced forwardly ‘and slightly above
position, both before and after the arm is moved to nor
the level of ‘shoulder '48, is a second shoulder 52 whose
mal wiiiding position, and a portion ‘88 of minimum
radius opposite salient portion 84 for moving the arm
function will be described in connection with the package
sizing mechanism.
The portion of main latch 44 forwardly of pivot stud
42, i.e., to the left of that stud in FIG. 1, is provided with
two spaced-apart clamping bolts 53, which clampingly
and package to reverse rotation position. The control
cam unit of the machine, including package control cam
82, is ?xed ‘on a main control shaft 90 for rotation there
with, and it will be seen that as shaft 90 rotates, the
main package arm will be moved by the peripheral por
tions of control cam 82 in a cycle between the three
engage the foot portion 54 of a generally upwardly pro
jecting support arm 56, the lower edge of foot portion 54
being correspondingly slotted, as at 58, to slip over bolts 10 operating positions.
In accordance with the patented machine, the maxi~
53 when loosened. The free upper end of support arm
56 rigidly holds the outer end of package braking mem- .
mum radius salient portion was extended circumferential
her B. Below the front end of the foot portion 54 of the
braking member support, the main package latch is con
nected to one end of a tension spring 60 having its other
tion a somewhat greater extent than is the case with the
end fastened on a post 62 projecting laterally on the out
side of frame side 22. Spring 60 exerts constant counter
clockwise bias on main latch 44 to urge the rear end
ly in the direction opposite to the direction of cam rota
corresponding portion of the present cam, with the result
that the salient portion of the previous cam remained in
engagement with follower roller 80, 'while the main pack
age arm and the package were in normal ‘winding position.
.t should perhaps be explained that, vafter rotation to
thereof upwardly into engagement with pin 50 on main
package support arm 38. The extreme forward end of 20 bring the salient portion into engagement with the main
package arm follower to shift the main package arm and
package to normal winding position, shaft 90 was re
strained against further rotation until the initiation of a
further end-?nding cycle. The same is true of the pres
downwardly to afford a certain amount of lost motion
to pin 66 in that direction. Pin 66 is carried at the end 25 ent arrangement, except that, once the main package arm
main latch ‘44 is pivotally joined to the upper end of a
downwardly extending link 64 having-its lower end con
nected to a pivot pin '66 by a slot 68 which is elongated
of a crank 70 ?xed to the exterior end of a shaft 72 for
rotation therewith.
From the mechanism thus far described, it will be
seen that, assuming the components are in normal operat
ing position as shown in’ FIG. 1 with shoulder 48 on main
latch 44 being engaged by pin 50 on main package sup
has been brought to normal winding position by salient
portion 84, it is now latched or locked in that position
by engagement of pin 50 with shoulder 48, on main latch
44, and further rotation of shaft 90, to the position to
which it is checked at the finish of an end-?nding cycle,
carries salient portion 84 out from under roller 80,
port arm 38 to hold the arm in forward position with
package P in frictional contact with drive roll D, if a
whereby roller 80 and follower arm 78 are free to move
shoulder 48 from pin 50, freeing main package support
main package arm in normal winding position, this func
tion being exercised instead by main latch 44.
inwardly towards shaft 90 until contact is made with
the trailing intermediate radius cam portion 86. Thus,
rearwardly directed force is exerted on braking member
B, main latch 44 will be pivoted clockwise to disengage 35 salient portion 84 no longer serves as the keeper for the
arm 38 for rearward pivotal movement. Braking member
An understanding of the actuation of main latch 44 in
response to breakage of the thread requires a discussion
be contacted in the event the yarn being delivered to the 40 of the thread breakage-lever and the control shaft lock
ing means, which are best shown in FIGS. 3, 4, 6 and
package should accidentally become lapped around roll
7. Breakage-lever 100 takes the form of a generally
B is positioned in close proximity, say 1/16—3/32 inch, to
the peripheral surface of drive roll D and will, therefore,
D. Thus, braking member, in addition to functiomng to
L-shaped .rod having its foot portion 102 extending in
brake the package, serves as the roll lap detector, being
spaced parallel relation to the forward end of frame 20
forced to the rear away from the periphery of roll D in
across and at right angles to the path of the yarn and
the event of a roll lap to disengage main package support 45 its
leg portion ‘104 extending rearwardly alongside frame
arm 38 and allow the package to fall backwardly to a
side 23. At its rear end, leg portion 104 of the breakage—
position resting upon the braking member (shown in FIG.
lever is affixed to a connecting plate 106 (FIG. 3) pivoted
8) and out of driving engagement with drive roll D.
on a shaft 108 and extended rearwardly of that shaft
By virtue of the lost motion connection between slot
to assist in counter-balancing the breakage-lever. In
68 on link 64, and pin 66 on crank 70, main latch 44
normal running position, breakage-lever is maintained in
is free to pivot clockwise the necessary distance away
a depressed position (as in FIG. 1) by the thread passing
from pin 50 without affecting crank arm 70.
thereover, but, in the event of thread breakage, will tilt
1 As already explained in the introduction, one ofthe
upwardly about the axis of shaft 108, the balance of the
important features of the present invention is the ability
breakage-lever being selected to cause such tilting move
of main package arm 38 to retrogress almost immediately 55 ment.
in the event of thread breakage without waiting for
Shaft 108 passes through a bearing in frame side 23 to
the beginning of an end-?nding cycle. To fully com
about the mid-point of the housing and is supported at its
prehend this feature, it is necessary that the difference
inner end -in__a bearing provided in an intermediate parti
in the relationship of the main package support arm and
60 tion wall 110 rigidly upstanding from frame base 21.
the control cam for that arm between the patented ma
A?ixed on shaft 108 for rotation therewith intermediate
chine and the present invention be appreciated.
partition wall 110 and side 23 is a generally Y-shaped
Main package support arm 38, as already stated, 15
breakage-lever yoke 1112 having two rearwardly extend
mounted on the exterior end of a rotatable shaft 40 ex
ing arms, only one of which (114) is shown in the draw
tending between the frame sides. Carried on shaft 40
ings, one forwardly extending arm 116, and a common
for rotation therewith adjacent side 2 is a collar or 65 hub 1'18 axially bored to receive shaft 108. The break
hub 76 (see FIG. 3) formed with an integral down
age-lever and the breakage-lever yoke, therefore, pivot
wardly and forwardly curved follower leg 78 having a
follower roller ‘80 at its free ends. Roller 80 is adapted
to engage the peripheral edge of a, plate cam 82, termed
with shaft 108, downward movement _of the breakage
lever being limited by engagement of the upper edge
and package to normal winding position, two portions
Freely dangling from a stud 122 on the rear end of
yoke arm 114 is a pawl >124, herein referred to as the
of rear arm 114 with a tubular brace 120 stretching be
the main package control cam, which forms a part of 70
frame side 23 and partition wall 110 and connected
the control cam unit of the machine. Cam ‘82 includes
at its ends thereto adjacent the upper edges thereof.
a salient portion 84 for moving main package arm 38
86 of intermediate radius, one on either side of salient
portion 84, for moving the main package arm to braking 75 “package-lifting pendant,” which is adapted, under certain
conditions, to engage a convex rear edge at the upper
end of a generally vertical latch lever 126 to rock that
72 will be rocked in a counterclockwise direction in FIG.
lever forwardly about a horizontal shaft 128 supported
tioning latch 44 to unlatch the main package arm.
The arrangement by which drive plate 140 is coupled
at its ends in frame side 23 and partition wall 116 a con
siderable distance below brace 12%. Adjacent its forward
edge, the upper end of latch lever 126 is pivoted to a
forwardly extending connecting link 130, the other end
of which is pivoted to the upper end of a normally up
standing crank 132 ?xedly carried on the inner end of
shaft 72.
6, this motion being transmitted to main package posi~
to shaft 90 will now be described. Fixed on shaft 90 at
a location spaced slightly from drive plate 140‘ in a direc
tion toward the observer in FIG. 6 is an actuator disc 154
which bears a pivot pin 156 at a point spaced slightly in
wardly of its periphery, and pivoted on pin 156 between
10 actuator disc 154 and drive plate 140 is an inverted L
Shaft 72 is supported in bearings in partition i118 and
shaped driver-pawl 158. Intermediate pivot axis 156, on
frame side 22 ‘at a level spaced downwardly and forwardly
‘the forward edge of driver-pawl 153, and its lower end is
of breakage-lever shaft 168 and is biased in a clockwise
a laterally directed lug 16ft adapted to engage with one of
direction (FIG. 6) by means of a torsion spring 134 (see
the notches 162 provided at equally spaced points around
FIG. 3), encircling a portion of the shaft adjacent frame 15 the periphery of drive plate 140‘. The lower end of
side 22, one of the ends of spring v134 being embedded
driver-pawl 158 is connected to one end of a tension spring
in that side and the other anchored ‘on a collar 136 ?rmly
164, the other end of which is anchored on a post 166
secured to shaft 72 by means of a set screw 38. It will
on ‘actuator disc 154, so that spring 164 urges driver-pawl
be recalled from the discussion of FIG. 1 that shaft 72
158 in a counterclockwise direction labout pin 156. Thus,
carries on its exterior end a normally horizontally ex
when driver-pawl 158 is free to rotate, it will be urged
tending crank 70 which is connected through pin 66 and
inwardly by spring 164 into engagement with one of the
slotted link 64 to the front end of main latch 44. It will
notches 162 on driver plate 140 to couple that plate to
now be seen that forward rocking motion of latch lever
‘actuator disc 154 ‘for simultaneous rotation.
126 will impart a corresponding movement to shaft 72
In order to hold lug 160 on driver-pawl 158 out of en
and exterior crank 7 0, forcing the front end of main pack
gagement with a peripheral notch on the drive plate, the
age positioning latch 44 upwardly to lower the rear end
upper end of driver-pawl 158 includes 1an outwardly pro
thereof and disengage shoulder 48 from pin 58 on the
jecting beak 167 having a straight, lower edge 168 which
main package support arm. As before, when shoulder 48
is‘ adapted to engage a detent shoulder 170 at the upper
is disengaged from pin 50, the main package arm is free
end of a laterally directed ?ange 172 on latch lever 126.
to swing rearwardly until follower roller 80 on package 30 In approximately the same radial plane as the axis of
arm follower leg 78 engages the trailing intermediate
pivot pin 156, the peripheral edge of actuator disc 154 is
radius portion 86 of package arm control cam 82, posi
formed with a radial shoulder 174, the remainder of the
tioning package P with its periphery in frictional contact
disc periphery being substantially circular in con?gura
with braking member B.
tion. Shoulder 174 is also adapted to engage shoulder
The conditions, or more precisely, the condition under 35 170 1at the upper edge of ?ange 172. It will ‘be seen that
which breakage-lever pendant 124 engages latch lever 126
as long as edge 168 on driver-pawl 158 and radial shoul
to rock shaft 72 is closely interrelated with the drive for
der 174 on actuator disc 154 are in contact with shoulder
the main control shaft 90 of the control section. For sim
170 on the latch lever (the position shown in FIG. 6),
pli?cation, the main driving element for shaft §tl may be
the lug of the driver-pawl will be held away from the
deemed to be a notched disc plate 140 (see FIGS. 4 and
periphery ‘of drive plate 14%} to uncouple actuator disc
6) which is arranged for free rotation on shaft 96‘ around
154 therefrom [and disc 154 will be restrained against ro
a bushing 142, plate 148 being termed herein as the
tation by the engagement of shoulder 174 on the cooper
“drive plate” for shaft 90. For the purposes of this in
ating latch lever shoulder 170. However, when latch
vention, it is enough to know that drive plate 148 is con
lever 126 is forced forwardly in the manner already ex
stantly driven at a suitably selected speed, the driving
plained, detent shoulder 170 of the latch lever will be
means for that plate forming no part of the invention and
moved out from beneath radial shoulder 174 on actuator
being explained in the aforementioned Goodhue et al.
disc 150, as well ‘as the edge 168 of driver-pawl beak 167,
releasing the actuator disc for rotation ‘and allowing
patent. In essence, however, drive plate 149 is driven
through a friction clutch comprising a circular plate 144
driver-pawl 158 to pivot under the in?uence of spring
(see FIG. 3) rigidly coupled to plate 140 and frictionally 50 v164 about its pivot pin 156 to engage driver-‘pawl lug 160
engaged by means (not shown) yieldably supported with
with the ?rst notch 162 on driver plate 140 that ap~
in a cylindrical housing 14.6 having an integrally formed
peripheral gear 148 which is, in turn, driven by a gear train
proaches the lug. As soon as the lug is engaged with a
notch, actuator disc 154 and drive plate 140 are coupled
(not shown) deriving power from the main drive shaft
and rotate as a unit.
(also not shown) of the machine.
Mounted on drive
tary rotation will occur, however. This ‘follows from the
plate 140 is a plurality of laterally projecting pins 1581
fact, that as driver-pawl 158 swings inwardly to couple
the disc and plate together, edge 168 on the driver-pawl
beak will be projected in leading relationship to radial
located at equally spaced points therearound on a com
mon radius.
When the thread breaks, or is broken, during the wind
Only one revolution of such uni;
shoulder 174 on the actuator disc (FIG. 7), so that as
ing operation, breakage-lever 108 swings upwardly to 60 the revolution is completed, edge ‘168 will contact the
rock breakage-lever shaft 108 land breakage-lever yoke
latch lever 170 slightly in advance of radial shoulder 174.
When this occurs, actuator disc 154, being still coupled
ing breakage-lever pendant 124 into the space between
to drive plate 140, will continue to rotate to bring its
plate 140 and clutch plate 144 to a position at which the
radial shoulder 174 into engagement with the latch lever
pendant will intrude between the moving pins 156‘ and 65 shoulder, since the latch lever is subject to a constant
inward bias from spring 134 through shaft 72, crank
the rear edge at the upper end of latch lever 126. As can
be seen in FIG. 6, the radius of pins 150 on plate 140 is
132 and link 130. Driver-pawl shoulder 168, however,
112 downwardly to the position shown in FIG. 7, thrust
so selected that insufficient clearance exists between the
upper rear edge of latch lever 126 and a pin 150, when
is no longer free to move and relative rotation between
the driver-pawl and actuator disc must take place, dis
proximate to that edge, to accommodate pendant 124. 70 engaging the driver-pawl lug from the peripheral notch of
the drive plate, stopping the rotation of the actuator
Consequently, as ‘an oncoming pin engages breakage-lever
disc with the parts back in rest position, as shown in
pendant 124 the pendant will be swung forwardly about
FIG. 6.
its pivot 122 to permit the pin to pass, and latch lever 126
To prevent backward rotation of the actuator disc as
will likewise be swung forwardly with the result that shaft 75 radial shoulder 174 engages shoulder 170, an arm 169,
which is pivoted on shaft ‘40, carries a cam follower 1711
for engagement with a second cam 173 on control shaft
90, arm ‘169 being biased upwardly against the periphery
of cam 173.
Cam 173 includes on inclined peripheral
of the package for which the sizing lever is set, entry of
the shoulder tip onto surface 186 as package extension
arm 28 is lifted upwardly, as during a mandrel change
over, or the like, being facilitated by the inclination of
upper edge 208 at the tail portion terminal. Latching
lever 196 .is biased in a counterclockwise direction (in
FIGS. 1 and 2) by a torsion spring 216 anchored on pivot
pin 198, iwth one end seating against the upper face of
portion 175 at a point suitable for engagement with fol
lower 171 when the two shoulders approach contact, the
inclination of portion 175 being such as to oppose, under
the bias of follower 171, clockwise rotation of the cam
lug 212 and the other against pin 50 on main package
and disc. In addition, when the actuator disc is released,
inclined portion 175 tends to initiate the rotation of the 10 support arm 38, and the tip of shoulder 206 will, there
fore, be urged against peripheral surface 186 on the siz
‘disc to eliminate any possibility of the shoulders re
ing lever. As long as the shoulder tip and surface are
engaging before the drive-pawl is effectively released.
in contact, lug 212 on the foremost arm of the latching
Package arm control cam 82, along with a plurality of
lever will be held vertically spaced above the upper edge
additional cams, including cam 173, seen between cam ‘82
and actuator disc 154 in FIG. 3, is formed as a unitary 15 of main package positioning latch 44.
During the winding operation, package P will, of
cam assembly, preferably constructed of' plastic, such as
course, grow 'in size, pivoting extension arm as well as
nylon, or the like, and the entire assembly is secured to
joint member 34 and sizing lever 180 about stud shaft 36,
main control shaft 90 for rotation therewith. These
the shoulder tip riding all the while against surface 186,
additional cams play various roles during the end-?nd
ing cycle of the machine, their speci?c function having 20 until the rear end of surface ‘186 passes the shoulder tip,
freeing the tail of the latching lever for upward movement
no essential bearing on the present invention and being
until the upper edge thereof forwardly of shoulder 206
explained in the aforementioned Goodhue et al. patent.
meets surface 186. The upward motion of tail 206, aided
It is obviously desirable for the machine to be capable
by the thrust of spring 216, imparts a sui?cient downward
of winding various size packages and for terminating the
winding operation once the particular package size con 25 motion to arm 202 as to cause its lug 212 to strike the
upper edge of main package positioning latch 44, driving
templated has been achieved. The mechanism by which
the main latch downwardly and disengaging shoulder
these ends are achieved will be described next, with par
ticular reference to FIGS. 1 and 2.
Mounted on stud
_ 48 from pin 50. This enables the main package support
arm to fall rearwardly under the weight of the package.
shaft 36 between the upper end of main package support
arm 38 and the outer face of joint member 34, for pivotal 30 However, lug 212 on forward arm 202 of the latching
lever is now proximate to the upper edge of main latch
movement with respect to that shaft is a package-sizing
lever plate 180 of highly irregular con?guration. At the
lower rear end of lever 180 is a generally downwardly
44 and will engage the foremost shoulder 52 on that lever
as the main package arm falls rearwardly. This halts
the rearward movement of the arm at a point on its path
‘directed tail portion -182 terminating in an outwardly
directed lu-g 184 and along the lower edge of lever ‘180 35 intermediate normal winding position and braking posi
tion with the package in repose at a similar intermediate
slightly forwardly of tail portion 182 is an elongated, out
position, which is su?iciently close to the front end of
wardly rolled lug 185 extending to about the mid-point
the frame as to be readily accessible to the machine at
of’that lower edge to present an elongated, downwardly
tendant for purposes of removal.
facing peripheral surface 186. An arm portion ‘188
From what has been said above, it follows that growth
stretches forwardly from the lower front corner of lever 40
of the package is discontinued when the tip of shoulder
180, by means of which the lever may be manipulated,
206 coincides with the rear end of peripheral surface 186
on sizing lever 180 and that the actual size of the package
at this time will be a function of the distance on surface
Slot 190 is penetrated by a threaded bolt 192 ?xed on
joint member 34, a nut 194 being threaded on the ex 45 186 between the initial location of shoulder tip 206 and
the rear edge of the surface. The ability of sizing lever
terior end of bolt 192 to clamp lever 180 relative to joint
180 to be moved to a variety of positions corresponding
member 34 in any position within the limits of slot 190.
and upwardly and inwardly of arm portion 188' is a
generally vertical, slightly curved, elongated slot 190.
i i Cooperating with sizing lever .180 is a sizing latch 196
pivoted at approximately its mid-point on a pin 198
rigidly embedded in the inner face of main package sup
to the desired range of package sizes has already been
alluded to and the length of surface 186 from front to
rear is so chosen as to accommodate the shoulder tip
throughout all of its positions corresponding to the range
of package sizes.
The arrangement of the sizing lever and cooperating
rected arms 20.2 and 204. Adjacent the rear end of the
sizing latch just described includes a “built-in” safety
upper edge of tail portion 200 is a vertical shoulder 206. 55 feature, operable in 'the event the latch fails to actuate
From shoulder 206 rearwardly, the upper edge of tail
‘upon leaving the end of surface 186 in order to prevent
200 is downwardly inclined, as at 208, and the adjacent
the package from growing to a size that would damage
lower edge portion is preferably upwardly and rearwardly
the machine. If the package should continue to grow
inclined, at at 210, so that the tail terminates in the
beyond that size indicated in FIG. 2, sizing lever 180
shape of a V. The foremost arm 202 of the two arms 60 ‘will continue to pivot with joint member 34 ‘around stud
of sizing latch 196 terminates in an inwardly bent lug 212..
shaft 36 and, ultimately, lug 184 on sizing lever tail 182
Preparatory to the Winding operation, bolt 194 is
‘will engage the lower inclined edge 210 at the rear end
loosened and arm ‘188 manipulated to position the sizing
‘of sizing latch tail 200, forcing tail 200 upwardly or
lever in accordance with the size of the package which
counterclockwise around pivot pin ‘198 to disengage pin
,is to be wound, the forward face of joint member 34 65 50 from shoulder 48 in the same manner as before. For
being provided with a scale,’ indicated at 2114, for gauging
this purpose, the length of tail 182 in relation to the
the package size, after which bolt 194 is tightened to
position of edge 210 on the sizing latch is such that lug
clamp the sizing lever to the joint member so that they
184 will engage that edge as package extension arm‘ 26
rotate as a unit about stud shaft 36 as the package grows
swings upwardly before the maximum permissible limit
in size. The downwardly facing peripheral surface 186 70 of package sizes is exceeded.
on the sizing lever is of su?icient length that when the
During the course of an end-?nding cycle, package P
package arm extension 28 is in downward position, as
not only moves bodily into engagement with braking
port arm 38. Sizing latch 196 is of roughly Y-shaped
con?guration having a rearwardly directed tail portion
200 and two forwardly and somewhat downwardly di
would inevitably be the case at the start of the winding
member B but into engagement with reverse rotation roll
operation, the tip of shoulder 206 on the sizing latch tail
R as well, and the function of tail portion 46 on main
portion will contact surface 186 irrespective of the size 75 package positioning latch 44 is to maintain pin 50 on
the main package arm in engagement with the upper edge
is an extension 260, of reduced transverse dimension,
of the main latch when the main package arm is in max
imum rearward position with package P in contact with
reverse rotation roll R. The relationship of the co1n~
ponents of the machine in this position is indicated in
dotted lines in FIG. 8. The upper edge of tail 46 is
which is engaged within the hook end 246 of pendant leg
roughly of inverted V-shape, with its ends lying sub
244. Lever 252 is biased forwardly against a stop 262 on
the inside face of frame side 23 by means of a tension
spring 264 anchored at one end to L-shaped portion 256 of
lever 252, and at its other end to a post 266 on frame side
23 adjacent its front edge.
stantially on the path followed by pin 50 as main pack
When the breakage-lever yoke 112 is in normal operat
age arm 38 swings to and from extreme rearward posi
ing position (shown in FIG. 4), as would be the case when
tion and the apex of the V is disposed above that path 10 the thread was running properly, and holding the thread
so that as the pin approaches the ‘apex, main latch 44
breakage-lever in depressed position, pendant 238 is sus
will be pivoted clockwise, lifting its front end and raising
pended with lug 242 of its U-shaped extension 240 in
braking member B a slight extent to more easily engage
engagement with shoulder 234 on the toe end of operating
the package. Tail 46 is constructed long enough that pin
link 224. Hence, as shaft 40 rocks with main package
59 remains on the upper edge of main latch 44 at all 15 arm 38, pendant 238 will be pulled rearwardly about its
pivot pin 236 by operating link 224 and will, in turn, pull
lever 252 rearwardly about its supporting shaft 250, swing
When the package has reached the desired size, or a
ing the exterior front end portion 258 of lever 252 rear
roll lap has built up on the drive roll, and the package
wardly and downwardly to the position shown in FIG. 5.
has been moved as a result thereof away from the drive
roll, the disadvantage in having the thread run uninter 20 Lever end potrion 258 is connected by a link 270 to the
operating arm 272 of a knife blade 274 suspended in a
rupted will be apparent. In the ?rst case, the package
frame 276 for downward and rearward swinging move
will continue to spin under its own momentum after
ment to bring its cutting edge into contact with a ?xed
movement to the intermediate package-sizing position and
anvil 277 and normally biased away from the anvil. The
cause additional convolutions of yarn to be wound there
yarn Y, being delivered to the winding section, passes be
around, while, in the second case, the thread, unless
tween the knife edge and anvil 277 and when link 270 is
severed, will continue to wrap around the drive roll even
pulled downwardly, the knife swings against the anvil to
though the pack-age is no longer in engagement therewith.
sever the yarn. Frame 276 is mounted on a forward sec
On the other hand, interruption of the yarn during the
tion 278, c.g., the yarn servicing section, of the machine.
end-?nding cycle is both unnecessary and undesirable
since the thread is already broken and the operation of 30 In the event the yarn breaks to institute an end-?nding
a cutter might tend to interfere with the reunion of the
cycle, the breakage-lever swings upwardly, rocking shaft
broken ends and the return of the yarn to running posi
tion. The machine of the invention is, therefore, equipped
108 and breakage-lever yoke 112 counterclockwise from
the position shown in FIG. 4 to the position shown in
FIG. 7. This lifts pendant 238 to a level at which lug
with means operable to sever the yarn under the ?rst two
242 on extension 240‘ is held clear of shoulder 234 on toe
conditions, but not under the third, which means is best
232 of operating link 224. Consequently, as link 224 is
seen in FIGS. 4 and 5.
pulled rearwardly as main package arm 38 swings away
Fixed on shaft 40, about mid-way between frame sides
from normal running position, pendant lug 242 is not en
22 and 23 (see FIG. 3), is a crank 220 connected at its
gaged by toe 232 and lever 252 is held by spring 264 in
upper end to the angularly extending upper end 222 of an
operating link 224 shaped generally in the manner of a 40 normal and knife blade 274 remains away from anvil 277,
allowing the yarn to travel uninterrupted during the end
dogleg and disposed below the cam unit driving and com
?nding cycle.
ponent latching. Link 224 is guided by means of a pin
It will therefore be seen that the yarn will be severed
226 passing through a slot 228 formed in the horizon
when the main package arm is unlatched and swings
tally extending front portion 23f) of link 224, slot 228
rearwardly as a result either of either of package-sizing,
being upwardly and forwardly inclined to a slight extent,
i.e., attainment of the proper size by the package, or roll
whereby link 224 will reciprocate in an essentially straight
lap but will not be severed when the package arm is un
line path as crank 220 is rocked incidentally to the move
latched and swings rearwardly as a result of thread break
ment of main package arm 38. At its extreme front end,
age. In view of the rather limited movement of main
operating link 224 is formed with ‘an upwardly projecting
package arm 38 when package-sizing takes place, moving
toe 232, the inner edge of which de?nes a shoulder 234.
the package only part of the way to breaking position,
Reference has already been made, in connection with the1
the effective leverage of the several levers of the yarn
description of the thread breakage-lever and the actuating
severing mechanism must be such as to operate the knife
thereby of the cam unit latch, to the existence of a front
with this limited movement.
arm 116 on breakage~lever yoke 112. At its forward end,‘
Yarn knife 274 and frame 276 may, and preferably
arm 116 carries a pin 236 on which is pivoted a down 55
wardly hanging pendant 238. The extreme lower end of
pendant 238 is provided with a generally U-shaped ex
tension 240, including a laterally bent lug 242, which lug
is adapted to engage shoulder 234 on toe 232 of link 224.
do, form a part of a slub catcher for the yarn, as shown
and described in the commonly assigned application of
Pitts and Steele, entitled, “Automatic Supply Package
Indexing Mechanism for Winding Machines,” and for
Projecting forwardly of the main body of pendant 238, at 60 a more complete understanding of the construction of the
slub catcher, as well as of the forward section of the wind
right angles to the length thereof, is a leg 244 reversely
ing machine, reference may be made to that application.
For present purposes, it is merely enough to know that the
Extending between frame sides 22 and 23 and journaled
movement of lever 252 to the position shown in FIG. 5
therein is a shaft 250‘ located directly above the hook end
is effective to operate a knife which cuts or otherwise
246 of pendant leg 244 and at a point on this shaft adja
interrupts the ?ow of yarn to the winding section of the
cent side wall 23 is mounted, for free swinging movement
with respect thereto, a combination yoke and L-shaped
Adjacent frame side 23 and in front of the entire frame,
lever 252. The upper or yoke portion 254 of lever 252 is
in a position readily accessible to the machine attendant,
bent in U-shape, with its arms penetrated by shaft 250‘. 70 is a manually operated starting lever 280 constructed in
The lower L-shaped portion 256‘, formed as an extension
tegrally with, or otherwise connected to, shaft 250, where
of the outside arm of the yoke portion, i.e., the arm adja
by that shaft will be rocked in a counterclockwise direction
cent side 23, stretches downwardly and then forwardly
(in FIG. 1) when lever 289 is pulled downwardly. Arm
to terminate outside the front of frame 2t), as at 253. At
280 and shaft 256 are biased in the opposite direction
the lower end of the inside arm of the yoke portion 254 75 by means of a torsion spring 282 (see FIG. 3) encircling
bent ‘at its front end, as at 246, in the manner of a hook.
the shaft adjacent frame side 22 and anchored at one
‘end in a collar 284 fast on shaft 250, and at the other
in frame side 22. On the end of shaft 250 outside frame
side 22 is a?ixed a crank 286 extending generally verti
cally and terminating at its upper end above the top of
side 22. A pin 288 is a?ixe-d on the upper end of crank
286 for engagement with an elongated slot cut in the
front end of a connecting link 292. Link 292 extends
As an explanation of the operation of each of the
major mechanisms involved in the present invention was
provided in connection with the description of these
mechanisms. Further discussion of the operation thereof
is considered unnecessary. However, from what has been
stated, it will be seen that the invention achieves each of
the objectives set forth in the introduction to the speci?
cation and constitutes a highly satisfactory solution to
the postulated dii?culties inherent in the control section
above frame side 22 from a point at its front end to a
point adjacent its rear end, being offset laterally, as at 10 of the winding machine disclosed in Goodhue et a1.
‘294, to clear other members, in particular support arm
The precise embodiment described and illustrated here
56 for braking member B, and is pivoted at its rear end
is provided for purposes of example only, as the con
to the lower end of the rearmost arm 204 of sizing latch
struction and cooperation of various elements is obviously
It will be seen that as starting lever 280 is rocked 15 subject to modi?cation and variation without departing
from the spirit of the invention. Accordingly, the scope
downwardly to re-start the machine, as when a com~
of the invention should be measured by the appended
pleted package has been removed and a fresh tube placed
claims rather than by the details of the exemplary em
on the winding mandrel, counterclockwise rotation of
crank 86, after pin 288 has reached the forward limit
of slot 290, will rock sizing latch 196 clockwise to dis 20
Having thus described my invention, that which is
claimed is:
engage shoulder 206 on the sizing latch tail ‘from the
1. In a winding machine for winding yarn upon a ro
rear end of lug ‘185, permitting package extension arm
tating package wherein the package is rotated by fric
28 to be lowered into winding position with the package
tional contact with a drive roll and is supported on an
tube in peripheral contact wit-h driving roll D, and will
at the same time pull \main package arm 38 forwardly 25 arm mounted on a :frame :for movement to and from
an operative position with said package contacting said
to bring pin 50 into engagement with shoulder 48 on
the upwardly ‘biased end of main package positioning
roll, said arm being ‘biased to move away from said
operative position to separate said package from said roll,
latch 44 to lock the main package arm in normal Wind
the improvement comprising latch means for said arm,
ing position. The presence of the lost motion connec
tion between crank 286 and connecting link 292 allows 30 said latch means comprising a movable latch element
main package arm 38 to move freely to its various po
and a surface of abutment for said latch element, one
of said element and surface being carried on said frame
sitions without affecting crank 286. Manipulation of
and the other on said arm, said element engaging said
starting lever 280 during re-starting of the machine per
surface to maintain the arm in said operative position
forms various additional functions in connection with
components not shown and described here, knowledge 35 against said bias during normal winding, means for
detecting the presence of yarn wound upon said drive roll
of which may be derived from the aforementioned Good
instead of said package, means for detecting an inter
hue et al. patent.
ruption in the ?ow of yarn to said package, means for
A further point of interrelationship between the im
detecting the completion of a package, and means re
provements of this invention and the Goodhue et al.
patent concerns an L-shaped lever 296 pivoted on a stud 40 sponsive to each of said detecting means for moving said
latch element out of engagement with said surface where
298 and seen in FIGS. 4 and 5. This lever forms a part
by the arm is free to move away ‘from said operative
"of the so-called “memory unit” of the machine fully de
position under the influence of said bias and thereby
scribed and claimed in that patent, which unit ‘functions
separate said package from said driving roll.
automatically to repeat the end-?nding cycle once in the
2. A winding machine as in claim 1 including means
event the end is not found on the first attempt and then 45
for severing the yarn traveling to said package, means
halt’the machine should the second attempt fail also.
normally operative to connect said severing means to said
In order to assure that this lever remains in proper posi
arm to actuate said severing means when said arm moves
tion during operation of the end-severing means so as
away from said operative position to move said package
not to give a false indication at a later time, it is extended
away from said roll, and means for rendering said severing
downwardly as at 299 and provided with a laterally bent
means inoperative in response to the operation of said
lug 300 on extension 299. Hence, as pendant 238 is
second mentioned detecting means whereby said severing
{pulled rearwardly by operating link 234, it will engage
means is operated by movement of said arm as a result
lug 300 to rock lever 296 counterclockwise (in FIGS. 4
‘of yarn wound on the roll and completion of a package
and 5). When the pendent and operating lever return
but not by movement of the arm as a result of inter
to normal running position, lever 296 will return also
and will be ready for the next end-?nding cycle.
One advantage not previously alluded to, in divorcing
ruption of yarn ?ow.
the means for positioning the main package arm in nor
means for detecting the presence of yarn wound on said
3. A winding machine as‘ in claim 1, wherein said
driving roll includes an elongated member mounted in
mal running position from the cam for controlling the
movement of that arm during an end-?nding cycle is that 60 spaced parallel relationship to the axis of said roll and
in close proximity to the roll periphery, whereby said
this arrangement enables one to vary the delay between
member will be contacted and moved by yarn woundv
the actuation of the thread breakage lever and the be
on said roll, and said mean-s for moving said latch ele
ment is a connection ‘between said elongated member
spatial relationship between the notches and pins thereon, 65 and said element whereby movement of the member re
ginning of the end~?nding cycle by replacing drive-plate
140, as shown, with a similar plate having a diiferent
by virtue of the fact that the positioning of the main
package supporting arm takes place immediately and in
dependently of the end-?nding cycle. Obviously, if each
leases the element.
4. A winding machine as in claim 1 including a cam
follower connected to said arm for unitary movement
therewith; a cyclically rotatable cam cooperating with
notch on plate 140 were spaced farther behind the corre
said follower for controlling the pivotal movement of
sponding pin a longer interval will exist between the 70 said arm and the package supported thereby in a cycle
actuation of the latch lever by the breakage-lever pendant
from said operative position to an intermediate position
and the coupling of the drive plate and actuator disc to
spaced ‘from said operative position, then to a remote
'start the cam cycle. In this way, the timingof the end
position spaced farther from said operative position, next
?nding cycle can be retarded or advanced as desired.
75 back to said intermediate position, and ?nally to said
operative position, said cam having a maximum radius
member is pivoted on said package supporting arm for
portion corresponding to said operative position, inter
bodily movement therewith, said machine including a
mediate radius portions on either side of said maximum
?xed detent located adjacent a predetermined point on
radius portion corresponding to said intermediate posi
the path of said member when moving bodily with said
tion, and a minimum radius position corresponding to
‘arm, said member having means for engaging said detent
said remote position, all of said portions being contacted
when in projected position upon bodily movement thereof
by said follower as the cam rotates and serving to- move
with said arm, engagement of said detent and engaging
the follower accordingly; means responsive to detec
means halting further pivotal movement of said arm and
tion of a yarn interruption by the corresponding detec
package away from said drive roll, said predetermined
tion means for initiating rotation of said earn coinciden 10 point being so selected that the package when so halted
tally with the disengagement of said latch means to per
is in a position of easy accessibility adjacent said opera
mit said arm to pivot and for rotating the cam to move
tive position but with the package disengaged from said
said arm and package through said cycle; means opera
driving roll.
tive while said maximum radius cam portion returns to
11. A winding machine for winding yarn upon a rotat
a position contacting said follower to re-engage said 15 ing package wherein the package is rotated by frictional
latching means with said arm, whereupon said arm and
contact with a drive roll, said machine comprising a frame,
follower are held in operative position; said cam rotat—
an arm supporting said package from one end thereof,
ing means being operative to continue cam rotation until
said arm being pivoted in said frame at its other end for
the maximum radius position has passed out of contact
movement of the package from and to an operative posi
with the follower, and means then effective to halt rota
tion contacting said roll, said arm being biased to move
tion of the cam so that an intermediate radius portion
said package away from said roll, a latch lever pivoted to
is in position to be contacted by said follower upon
said frame, said lever having an abutment thereon spaced
pivotal movement of said arm; whereby when said latch
from its pivot axis, a detent on said arm adapted to be
ing means is next dis-engaged in response to any detect
engaged by said abutment to latch said arm against pivotal
ing means, said follower immediately moves into- contact ' movement due to said bias while said package is in opera
with said intermediate radius portion as said arm and
tive position during normal winding, means for detecting
package pivot due to said bias, bringing said arm and
the occurrence of at least one abnormal condition during
package to intermediate position.
winding, and means operative in response to said detect
5. A winding machine as in claim 4 including means
ing means to pivot said latch lever to disengage said abut
adapted to contact said package when in said remote
ment from said detent, whereby said arm pivots due to
position to rotate said package in a direction reverse to
said bias to remove said package from said roll and halt
that of normal winding.
the winding operation in the event such abnormal condi
6. A winding machine as in claim 4 wherein said
means for initiating rotation of said cam includes means
for dis-engaging said cam rotation halting means, said
last-named means being controlled by said yarn inter
ception detecting means, and means connecting said last
named means to said latch~means to disengage the latter
substantially simultaneously with the disengagement of
the cam-halting means.
7. A winding machine as in claim 1 wherein said pack
age supporting arm is articulated intermediate its ends
and includes a main supporting portion and a package
tion occurs.
12. A winding machine as in claim 11 wherein said
detecting means is adapted to move when said abnormal
condition occurs, and said means operative in response
to said detecting means comprises mechanical means for
transmitting the movement of said detecting means of said
latch lever to pivot the same.
13. A Winding machine as in claim 11 including sep
arate means for detecting an interruption in the supply
of yarn, an accumulation of yarn upon said drive roll,
and the attainment of ultimate package size, said means
carrying extension, said main supporting portion being
operative to pivot said latch means being responsive to
engaged by said latch means during normal winding and 45 each of said detecting means.
maintained in operative position with the package contact
14. A winding machine as in claim 13 wherein each of
ing the drive roll, said extension being adapted to pivot
said detecting means is adapted to move upon the occur
about the axis of articulation to permit said package to
rence of the condition detected thereby, and including a
separate mechanical means associated with each detecting
means for transmitting the movement of said detecting
grow; said package completion detection means com
prises a sizing plate connected to said extension for piv
otal movement therewith, a member disposed adjacent
means to said latch lever to pivot the same.
said sizing plate for movement from and to a retracted
position to and from a projected position, said member
yarn accumulation detection means comprises an elon
being maintained in said retracted position during nor
gated bar disposed in closely adjacent parallel relation
15. A winding machine as in claim 14 wherein the
mal Winding, and means provided at a ?xed point on said 55 ship to the roll surface and said mechanical means asso
sizing plate for engaging and moving said member to
said projected position when said arm and said plate pivot
ciated therewith comprises a rigid connection between
said rod and said latch lever, said connection constituting
an extent corresponding to ultimate package size; and
the support for said bar, whereby yarn accumulating upon
said means for dis-engaging said latch means in response
said roll forces said bar away from the roll surface, such
to said package completion means is operated by the 60 movement of the bar being transmitted through said con
movement of said member to projected position.
nection, causing said latch lever to pivot.
8. A winding machine as in claim 7 wherein said siz
16. A winding machine as in claim 14 wherein the
ing plate is adapted to be adjusted relative to said exten_
yarn interruption detection means comprises a feeler piv
sion in advance of the winding operation to vary the ex
otally mounted on said frame for engagement with the
tent of pivotal movement of said arm and plate required 65 moving strand of yarn in advance of said package, means
to bring said means on said sizing lever into engagement
biasing the feeler for pivotal movement in the absence of
with said member to move the same to projected posi
said strand thereat; and said mechanical means comprises
tion, whereby the ultimate package size at which the
a rockable mechanical linkage connected at one end to
latch means is dis-engaged may be varied.
said latch lever so that rocking of the linkage pivots said
9. A winding machine as in claim 7 wherein said means 70 latch lever, said linkage terminating in a free end at the
for dis-engaging said latch means comprises a rigid ex~
tension on said member, said extension contacting said
other end, a positively-driven impulse element periodically
passing in close proximity to but out of contact with said
free end, and a pendant movable upon pivotal movement
of said yarn-engaging feeler to a position interposed be
10. A winding machine as in claim 7 wherein said 75 tween said impulse element and said free end, said pen
latch means as said member moves to projected position
and dis-engaging said latch means.
dant having a dimension exceeding the clearance between
latch lever when said sizing latch rocks so as to pivot said
latch lever.
18. A winding machine as in claim 17 wherein said siz
ing latch includes a detent adapted for engaging with the
the impulse element and free end, whereby said linkage
is rocked by ‘the movement of the impulse member trans
mitted through said pendant to the free end thereof,
pivoting said latch lever.
17. A winding machine as in claim 14 wherein said
package supporting arm is articulated intermediate its
ends and includes a main supporting leg provided with
termination of the sizing plate abutment when said sizing
latch rocks, engagement of the same locking said support
ing arm extension against pivotal movement relative to
said main supporting leg in the direction of said drive roll.
said abutment and an extension carrying said package at
19. A winding machine as in claim 17 wherein said
its free end, said extension being adapted to pivot about
the axis of articulation to permit the package to- grow
while said main leg is held against movement; said pack
sizing latch is pivoted on said main supporting leg for
bodily movement with said leg as the latter pivots under
said bias when said latch lever is pivoted to disengage the
age size detecting means comprises a sizing plate con
nected to said extension for pivotal movement therewith,
latch lever abutment from said detent on said main leg,
said latch lever is provided with a further abutment in the
said plate having an elongated abutment terminating at
path of said sizing latch during bodily movement thereof
with said leg and said sizing latch extension is formed
a predetermined point selected in accordance with the
desired ultimate package size, a sizing latch rockably '
with a detent to engage said further abutment as said siz
ing latch moves along said path when said sizing latch
disposed adjacent said abutment, means biasing said
rocks to impinge said extension on the latch lever and
sizing latch against said abutment, said sizing latch
being restrained against rocking movement by said 20 said main leg pivots, engagement of the extension detent
and further abutment stopping further pivotal movement
abutment as said sizing plate and extension pivot until
of said main leg with said package in a predetermined
the abutment termination is reached coincidentally with
position out of contact with said driving roll.
the attainment of ultimate package size, whereupon said
sizing latch undergoes rocking movement under the in
References Cited in the tile of this patent
?uence of said biasing means; and said mechanical means 25
associated with said package size detecting means com
prises a rigid extension on said sizing latch, extending to
said latch lever, said extension being held away from said
latch lever while the sizing latch is restrained by the
sizing plate abutment and being impinged against said 30
McKean _____________ __ June 25, 1935
Goodhue et al _________ __ Sept. 25, 1956
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