Improvements in and relating to Knitting Machines.
Year: 1889

page_text: Date of Application, 27th Aug., 1889-Accepted, 19th Oct., 1889
COMPLETE SPECIFICATION.
Improvements in and relating to Knitting Machines.
We, WILLIAM LEDYARD CATHCART, Naval Officer, of Jenkintown, in the County of
Montgomery and State of Pennsylvania, and ALEXANDER THOMAS CATHCART,
Gentleman, of Hoyt Post-Office, in the County of Montgomery and State of
Pennsylvania, United States of America, do hereby declare the nature of this inven-
tion and in what manner the same is to be performed, to be particularly described and
ascertained in and by the following statement:-
This invention relates to Knitting Machines, and, as set forth in this specification, is
an improvement upon the machine for which application for Letters Patent of the
United States was filed by William Cathcart, of Gwynedd, Montgomery County,
Pennsylvania, as administrator of the estate of Gilbert J. Cathcart, deceased, and by
William L. Cathcart, then of Philadelphia, Philadelphia County, Pennsylvania, on
the 3rd day of Feb. 1888, Serial Number, 262,911, upon which application letters
patent No. 395,214 were granted Dec. 25, 1888, to which reference may be had.
The present invention consists in additions, modifications, and in details of
construction, which will be hereinafter fully described and pointed out in the
claims.
In the accompanying drawings, which illustrate our invention and form a part
of this specification,-
Fig. 1 represents in front elevation, partly sectional, all parts of the machine
below the table, the lower portion of the framing being broken away.
Fig. 2 is a top plan of all that part of the machine below the table, except the
lever-bed, the needle-cylinder, and the parts connected to them.
Fig. 3 is a left hand end elevation of the machine, viewing the machine as in
Fig. 1, omitting all parts above the table except the needle and cam-cylinders.
Fig. 4 is a right hand end elevation of the machine, viewing the machine as in
Fig. 1, omitting all parts above the table except the needle and cam-cylinders.
Fig. is a top plan, partly sectional, of the parts above the table, all except the
actuating mechanism being omitted.
Fig. 6 is a vertical section of a portion of the machine on line NO, Fig. 5.
Fig. 6 shows in left hand side elevation the link p³, shown in right hand side
elevation in Fig. 6.
Fig. 7 is a vertical section of the auxiliary driving gear employed to revolve the
cam-cylinder at a low rate of speed.
Fig. 8 is a right hand end elevation, partly sectional, of Fig. 7, including also the
driving gear for shifting the main friction cones, the connected parts, and the means
for controlling the action of both gears.
Fig. 9 shows in front elevation and vertical section the adjusting cam v², employed
to stop the cam-cylinder at the proper places for raising (one half at a time) the
needles.
Fig. 10 is a left hand end elevation, partly in section, of the driving gear for shifting
the main friction cones, with the mechanism for controlling its action.
Fig. 11 represents front and side elevations of the cam s², employed to control the
tripping gear of the auxiliary driving mechanism.
Fig. 12 is a vertical section of the driving gear for shifting the main friction cones
of cam s².
Fig. 13 is a developement of the cylindrical cam g', by the rotation of which the
main friction cones are shifted.
Fig. 14 is a horizontal section through the needle cylinder n³, on the line P, Q,
Fig. 25, showing a top plan of the guard-band 68, and the devices for raising and
lowering it.

page_text: Fig. 15 is a horizontal section through the needle-cylinder and jack-holder, on the
line R S, Fig. 25, showing also, in top plan, the means for reciprocating the jack-
holder and needle-cylinder.
Fig. 16 is a left hand end elevation of the variable arm d' used to give motion, at the
proper time, to change-shaft D to which are attached the various mechanisms which
are operative only during reciprocating knitting.
Fig. 17 is a vertical section of the variable arm d, and of the mechanism on the
auxiliary shaft b' by whose intermittent rotation the change-shaft D is moved.
Fig. 18 is a left hand end elevation of the driving arm p' of shaft 6', and of other
portions of the mechanism on the said shaft.
Fig. 19 is a right hand end elevation of the driving arm p' when in position for
engagement with the arm d', and of a portion of the gear for locking and for throwing
into and out of action the said arm p'.
Fig. 20 is a right hand end elevation of the arm p7, when said arm is out of
action and of a portion of the parts for locking and for throwing the said arm into
and out of action.
Fig. 21 represents the jack-holder m³ in side elevation and top plan.
Fig. 22 represents the escapement lever go, and a portion of the escapement wheel e³,
in right hand, left hand, and rear elevations.
Fig. 23 represents in left hand end elevation the lower crank m, and portions of
the connecting rod n and expanding crank o, showing the method by which the
slot in said crank or arm o is described, with also a top plan of the expanding
crank o, a left hand end elevation and top plan of the secondary crank s, and the lugs
thereto bolted, and a top plan and side elevation of the crank-pin block w.
Fig. 24 is a right hand end elevation of the needle and cam-cylinders, the web-
holder, and the mechanism for actuating, and for throwing into and out of action, the
web-holder.
Fig. 25 is a vertical section, on the irregular line T, U, V, W, Fig. 26, of the
lever-bed, levers, and cam bar yg", the bar g being however shown in the position
for tubular knitting and not at the inside limit of its reciprocation, as in Fig. 26.
The figure also shows a vertical section of the needle and cam-cylinders and their
connected parts in the direction of the line T, U, V, Fig. 26.
Fig. 26 is a top plan of the levers, lever-bed, the cam-bars and their actuating
mechanism, and the escapement device for controlling the action of the said
actuating mechanism.
Fig. 27 is a vertical section through the hub of the lever 16 and shaft L, said
lever being used to lock the shaft. L when it is desired to throw the escapement
mechanism out of action.
Fig. 28 is a left hand end elevation of the cam-bars and their actuating
cams.
Fig. 29 is a front elevation, partly in section, of the lever-bed, the cam-bars
and their actuating cams, and a portion of the escapement mechanism.
Figs. 30 to 33, inclusive, are vertical sections through the centres of the cam-
bars, showing the actions of said bars at different positions of their reciprocation.
A portion of the lifting pins is omitted in Figs. 30 and 31.
Fig. 34 is a top plan of the cam-cylinder and the annular spur gear for driving
it, with all attachments.
Fig. 35 is a horizontal section through the cam-yoke, and a portion of the
cam-cylinder, and the needle actuating cams.
Fig. 36 is a developement of a portion of the exterior of the cam-cylinder,
showing the apertures through which the switch cams are operated.
Fig. 37 is a front elevation of the cam-cylinder and the annular gear for
driving it.
Fig. 38 is a developement of the interior surface of the cam-cylinder and cams,
showing the various positions of the switch cams.
Fig. 39 is a developement of a portion of the exterior of the cam-cylinder, showing
the method of elevating the horizontal section of the shoulder cam.

page_text: Fig. 40 is a front elevation, partly in section, of such parts as are above the table,
of the needle and cam-cylinders, the yarn stop-off and thread changing mechanisms,
and the devices for actuating the same, omitting the needles and the cam-cylinder
attachments.
Fig. 41 is a top plan, partly in section, of the yarn stop-off mechanism.
Fig. 42 is a top plan of the clamping plates and other parts of the thread changing
mechanism.
Fig. 43 is a top plan of the parting bar and its supports.
Fig. 44 is a top plan of the thread-cutting knife.
Fig. 45 is a front elevation of the retaining spring for said knife.
Figs. 46 to 50, inclusive, are vertical sections of portions of the thread changing
mechanism, illustrating the method of changing the thread.
Fig. 51 is a right hand end elevation of the sliding bearing which supports the
intermediate shaft, both forming a part of the thread changing mechanism.
Figs. 52 and 54 are right hand end elevations of cams which actuate portions of the
thread changing mechanism; and Fig. 53 is a developement of a third cam used for
a similar purpose.
Fig. 55 is a right hand end elevation, partly in section, of such parts as are above
the table, of the needle and cam cylinders, the yarn stop-off and thread changing
mechanisms, and the devices for actuating the same, omitting the needles and the cam-
cylinder attachments and including a portion of the web-holder spindle.
The terms "right hand" and "left hand," as used in the foregoing description, refer
to the position from which the views are taken, relatively to the position of the
observer as he faces the front of the machine in Fig. 1.
The same parts are designated by the same reference letters or figures in all the
Figures of the drawings.
A designates the power-shaft from which the mechanisms for performing the various
operations are driven. This shaft is provided with the usual fast and loose pulleys a
and c (Fig. 1. sheet 1) through which power is applied to, and taken off, the machine ;
it also carries the male part d of a double cone friction-clutch which revolves therewith,
but is free to be moved longitudinally in either direction from a central position into
engagements with the female parts e and f which are bolted respectively to the spur-
wheels g and these being of different diameters and mounted loosely on the same
shaft A, so as to be capable of revolving independently thereon, but not of moving
longitudinally upon it. These gears mesh respectively with gears and which also
differ in diameter and are keyed on shaft B which is directly below the shaft A. The
friction cone & at all times drives the machine, while knitting is progressing, except
for brief periods, as will be hereinafter explained, when the ratchet c², keyed to hub of
gear h, is in action. From the foregoing it will be understood that when cone d is in
the central or "stop" position it transfers no power to the machine, and that, which-
ever gear g or his at other times driven by it, will through the corresponding engaging
gear rotate the shaft B, while the other of said gears will rotate idly on shaft A,
according as it is driven by its corresponding gear on shaft B, and also, that a high
speed will be given by gear 1, when in engagement, and a low speed by gear g.
The motion of shaft B is communicated through crank m, connecting rod
crank 0,
to shaft C which is placed vertically above shaft A. Inasmuch as single-
crank connections are liable to stop at the dead-points, an auxiliary frictional driving
gear has been provided, consisting of a spur-gear p mounted loosely on shaft C, but
not capable of longitudinal motion thereon, the female part q of a cone-clutch bolted
to said gear, and the male part r of said clutch feathered on the shaft so as to revolve
with and to be capable of longitudinal motion thereon into or out of engagement with
the female part q. Now gears k, g, and p, are of the same diameter and in engage-
ment at all times with each other, hence the motion of gear k will at all times
coincide in speed and direction with that of gear p. If, therefore, coner he in
engagement with its female part 9 it follows that shaft C will be driven from, at the
speed, and in the direction of, shaft B, thus reinforcing the action of the crank o at
the dead points.
and

page_text: But, while shaft B rotates at all times while knitting is progressing, shaft C revolves
only during circular knitting, and during heel and toe knitting, which is performed
by reciprocation of the cam-cylinder, it oscillates.
In order that oscillating motion of shaft (may be obtained from rotary motion of
shaft B provision is made for increasing the effective length of crank o it being
apparent that, while the effective lengths of cranks o and m remain the same, shaft
will revolve with shaft B, but that if the length of crank o be increased, that of
crank m remaining the same, shaft C will oscillate while shaft B revolves still.
The expanding crank o is similar in principle to that described in the former
application and the patent granted thereon. As shown in section in Fig. 1, sheet 1
and in detail in Fig. 23, sheet 6, it consists of a plate crank o keyed to shaft C, and
having cut in it an open ended slot which is described from the centre of the pin of
crank m when it and crank o are horizontal and standing in the same direction, the
mouth of the slot being closed by a cap and bolts, as shown. Adjacent to, and on the
right of, the crank o is the secondary crank s, the hub t of which is feathered on
the shaft C, so as to revolve with said shaft, but to be capable of longitudinal motion
thereon. To crank s are bolted the blocks u and v, curved externally to fit the slot in
crank o and having a space between them; their inner faces are outwardly inclined
and parallel to each other. They receive between them the crank-pin block w, the
sides of which are inclined to correspond with the inclined faces of its blocks u and v.
The parts are so constructed and adjusted that when their hubs and touch,
cranks o and m will be equal in length and rotary motion of shaft will be possible,
but that when the hub t is moved to the right with cranks and blocks u and v
the inclined faces of the blocks will force block and pin w outward from the centre
of shaft C, thus increasing the effective length of crank o
It is evident that, as gear p always revolves, the friction cone must be out of
engagement with its female part q when it is desired to oscillate shaft C. As shown
in Fig. 2, sheet 2, and in Fig. 3, sheet 3, the hubs of the cone and of the crank s
are grasped by shifter forks y and z which are pinned to loose collars encircling said
hubs. In order to make the motions of both simultaneous the forks y and z are
threaded on the shaft a', which has a right hand thread cut on one end and a left
hand thread on the other. This shaft is supported in the bearing band is oscillated,
when required, by the crank c', eccentric rod d, and eccentric e¹, the latter being
keyed to the shaft D. The throw of the eccentric e¹ is so proportioned as to oscillate,
and not revolve, crank c¹, and, in one semi-revolution of shatt D, to separate the
forks y and z as far as required, returning them, in the succeeding semi-revolution, to
their original positions.
At the right hand end of shaft C, there is keyed a spur-gear f¹ which meshes
with gear g keyed to, and driving, the counter shaft E placed vertically above C.
Keyed also to shaft E is a mitre gear h³ which engages with, and drives, the com-
bined spur and mitre gear K' which depends from a vertical bearing in the table of
the machine and meshes with, and drives, the annular spur-gear 1, the latter being
connected with, and driving, the cam-cylinder m¹. The mitre-gear h¹ and the annular
gear are of the same diameter and pitch. Inasmuch as, in oscillating, the crank o
will pass through less than a semi-revolution, and as it is necessary to make each
movement of the cam-cylinder, while reciprocating, extend through as nearly a full
revolution as possible, in order to gain time for raising and lowering a needle in the
interval between finishing one course and beginning another, the oscillations of
shaft C are doubled in shaft E by making gear twice the diameter of gear g.
This
The position of the double cone d, whether in engagement with gear h, as in
circular knitting, in the central or stop position, or in engagement with gear g, pro-
ducing the slow speed required for reciprocating knitting, is regulated by the lever n'
(Fig. 2, sheet 2) which grasps a loose collar o encircling the neck of the cone.
lever is pivoted at pl and is vibrated by the cam path of the cylindrical cam g' (keyed
to shaft F) in which a stud 1, fixed in the inner end of lever n', bears. A
developement of the path of cam g' is shown in Fig. 13, sheet 5, said path being
so shaped as, in every quarter revolution of the cam, to move lever n' from one to

page_text: another of its three positions. The position of this cam, relatively to the lever n',
is controlled (as shown in Fig. 2, sheet 2, and in detail in Figs. 8, 10, and 12,
sheet 5) by the ratchet s¹ keyed to shaft F, the pawl t of which is in intermittent
engagement with said ratchet owing to the intervention, at certain periods, of the
shield y carried by a crank which is mounted loosely on shaft F. The pawl t'
is pivoted to the bell crank u¹, the latter being mounted loosely on the shaft F and
being oscillated continuously by the eccentric rod v' and the eccentric w¹ keyed to
shaft A.
Since our machine is so designed that the changes required in the position of
the lever n', during the knitting of a stocking, follow in the order designated by the
path of cam q¹ it is evident that to produce the change required at any period in the
making of the stocking it is simply necessary to revolve the cam g' one quarter of a
revolution forward from its position at that time. And also, if the shield y¹ be so far
retracted that one-fourth of the circumference of the ratchet s' is uncovered to the
pawl it is obvious that this ratchet with the shaft F and cam g' will be driven
forward the circumferential distance necessary to effect the change required.
As shown in section in Figure 12, there is mounted loosely on the shaft F, to the
left of bell crank u', the loose crank a¹ to which bolted the tripping shield y' which
controls the engagement of the pawl t' and ratchet s. The crank is supported by
the retaining hook 2, pivotally joined to at a², which engages with the teeth of the
reversed ratchet 2. The latter is keyed to shaft F and has four teeth set 90° apart.
In the position shown in Fig. 10, the shield y is interposed, the ratchet s¹ is out of
action, and the shaft F is at rest. If, however, the hook be tripped said hook will,
with the crank and shield y fall back to the next tooth d² of the ratchet b², thus
uncovering one-fourth of the circumference of the ratchet s¹, which ratchet, driven by
pawl t, will at once advance that amount, carrying with it shaft F and cam g¹. But
as ratchet 2 is keyed to shaft F, this ratchet will also be carried forward with the
shaft, moving with it the shield y', which, when the shaft has advanced 90°, will again
throw pawl out of action.
To change the position of cone d we have, then, to trip the retaining hook . This
is effected by the pattern chain G, rotating with the drum e² keyed to shaft H, which
at the proper time vibrates the spring actuated bell-crank m2 pivoted at n², thus
tripping hook z. The shaft FL, as shown in Figs. 1 and 3, is driven by eccentric f2
(keyed to shaft B), eccentric rod g², crank mounted loosely on shaft H, pawl k²
pivotally joined to crank 2, and ratchet 12 keyed to shaft H.
At times just previous to, and just subsequent to, the making of the heel and toe,
the machine is driven at a low rate of speed while necessary changes in the relative
positions of its parts are made. The driving mechanism, during these periods, is the
ratchet keyed to hub of gear h (see Figs. 1. and 2).
The ratchet and its connected mechanism are shown in detail in Figs. 7, 8, 9,
and 11, sheet 5. The pawl o2 is driven continuously by the eccentric w¹, keyed to
power shaft A, through the eccentric rod v¹, the bell crank u', and the link 2, con-
nected to the arm 2 to which pawl o' is pivoted, but while the cone d is in engagement
with either of the gears g or the pawl is prevented from driving the ratchet by the
shield m², which at these times is interposed. The strap n² which carries the shield m
is mounted loosely on the hub of ratchet 2 and has a lower projecting arın ² in sliding
engagement with the slotted arm of the lever 1, pivoted at 2, while the other end of
said lever bears on the cam s² keyed to shaft F. It is evident that if the slotted arm
of lever g² be forced downward, carrying with it the arm p², that the shield m² will be
retracted and the ratchet c² be brought into action. The cam s², as shown in Fig. 11,
has four divisions, two convex and two concave, the two former corresponding with
the fast and slow speed positions of cam g', and the two latter with the stop positions
of said cam.
When the lever q² bears on the convex portion of cam s² the pawl is
tripped, and when on the concave portion the ratchet is in action. The cams 2² and q
are so disposed on the shaft F, relatively to each other, that when the cone d is in
engagement the ratchet c² is out of action, and vice versa.
In our present machine, as in the one described in the application referred to, the

page_text: needle cylinder 3 is stationary and the cam-cylinder m', containing the needle actuating
cam grooves, either revolves continuously around it or, as in knitting the heel and toe,
is given a rotary reciprocating motion.
The needle cylinder n³ is shown in vertical section in Fig. 25, sheet 7, and in Fig. 6,
sheet 4, and in horizontal section in Figs. 14 and 15, sheet 5. As shown, it consists
of a single cylinder extending from above the cam-cylinder to, and through, the
lever-hed o³. At the bottom it is movably supported, for purposes to be hereinafter
explained, by the links t8 (Figs. 6 and 15), which grasp pins secured to lugs at the
lower end of the cylinder. Continuous external grooves are provided on the cylinder
for guiding the needles and jacks in their vertical motions, which grooves extend from
the top of the cylinder to within a short distance of the bottom thereof, excepting in
the lower portion of the back of the cylinder where the needles, being always in
operation, require no jacks, and hence the jack-guiding grooves are omitted. The
lower portion of the grooves, which is used for guiding the jacks, is made of larger
external diameter than the upper part thereof. The needles and jacks are similar to
those described in the application and patent previously referred to. As shown in
Fig. 25, the needles ³ are each formed with two butts, the upper ones fitting into the
needle-actuating cam-path of the cam-cylinder, and the lower ones forming projections
by which the jacks k³ and 1 can grasp the needles to pull them into, or push them out
of, action. For convenience the needles are made of the same shape throughout the
cylinder although one-third, more or less, of the back half thereof, which are always in
action, require no lower butts. The jacks K³ and are used with all the needles
except those just specified, which knit the narrowest part of the web in forming the
heel and toe pouches. They are of different shapes, as shown in Fig. 25, those
designated by being used with the front half of the needles, which are inactive
during heel and toe knitting, while those marked are used with two thirds, more or
less, of the back half of the needles, which are variably operative during that time.
The function of the jacks is twofold: first, to raise the needles out of action by lifting
their upper butts above the highest point of the needle actuating cams, in which case
the lower butts of the needles rest on the bottoms of the upper interior spaces of the
jacks; and secondly, to pull the needles down into action again i.e., sufficiently low
for the actuating cam groove to catch and operate the upper butts. The upper interior
space of the jacks is made at least equal in length to the vertical stroke of the needle,
plus the height of the lower butt.
The jacks of the front half of the needles, which are raised and lowered in a body,
are secured in a jack-holder m³ which is similar in function and design to the one
described in the application and patent previously referred to, except as to the means
for raising and lowering it. As shown in Fig. 25, and in Fig. 21, sheet 6, the
jack-holder is simply an annular semi-cylinder formed at the top with radial
notches or grooves to receive the jacks, the latter being held in place by an annular
cap secured to the jack-holder by screws, and having an inner, down turned,
knife-edged flange which rests in the notches formed in the upper sides of the out-
turned bases of the jacks and holds the latter down to the jack-holder. In the
centre of the jack-holder there is a vertical slot to through which projects one of
the two arms bolted in recesses in the exterior of the needle cylinder, said arms
supporting the standards y8y8, the functions of which will be hereinafter described.
The slot w is made of sufficient length to permit the vertical movement of the jack-
holder necessary in moving the needles into and out of action. The automatic raising
or lowering of the jack-holder just previous to, or just subsequent to, the formation of
the heel and toe is effected primarily through the semi-revolution of the shaft D at
the proper time, which shaft moves the jack-holder, through the eccentric v³ keyed
to said shaft, the eccentric rod u³, the crank 3 fixed to shaft resting in bearings s³
secured to lever-bed o³ (as shown in Fig. 26), and the arms 93 73 secured to said
shaft, which grasp pins set in two lugs at the bottom of the jack-holder. The
jack-holder is guided by the cap p³ fitted to lever bed o³, as shown in Fig. 1.
The standards y8y8, Figs. 6 and 25, support the stationary guide-band a, to lugs
on the bottom of which they are secured; they also serve as guides for the movable

page_text: guard-band 6 which is similar in function and design to the one described in the
application and patent previously referred to. These bands encircle the needle
cylinder and act as guides for the jacks in their vertical motions, the band being
made movable vertically in order that, when at the bottom of its stroke, as shown in
Figure 6, sheet 4, the jacks may be capable of being thrown outward to disconnect
them from the needles. The guard-band is reciprocated, as shown in Fig. 25, and in
Fig. 14, sheet 5, by the rod which passes through the table and grasps crank e
secured to shaft which rests in bearings made fast to front standard y; to shaft f⁹
are secured the arms g g which engage the pins he set in the guard-band. When
the band is down, as shown in Fig. 6, the sectional band (Fig. 14), pressed outward
by small spiral springs 91 set in the needle cylinder, throws the jacks outward and
downward, disengaging them from the needles."
The cam-cylinder, with the means for automatically reversing the cam-path, is
substantially the same as in the application and patent previously referred to, except
that in the present machine we have made the back part of the shoulder cam 4,
(Figs. 38 and 39, sheet 10) movable vertically, as will be hereinafter described. The
cam cylinder m¹, is shown in vertical section in Fig. 25, sheet 7, and in detail in
Figs. 34 and 39 inclusive, sheet 10. m³ is a plain cylinder with a flanged base resting
in a recess in the upper surface of the annular gear 1, the latter consisting of an
upper out-turned flanged part to which the gear proper is bolted beneath. Cylinder m¹
is connected loosely with gear through a bolt a passing through a vertical lug w³,
cast solid with gear 1, and screwing into a boss on the yoke y carried by the cam-
cylinder. A sliding connection between the yoke and cylinder is made by the
screws 33, which pass through the openings at a in the cylinder and carry on their
inner ends the switch cams and 4 which have lugs on their convex surfaces pro-
jecting through the openings at a, and which cams act in conjunction with the upper
fixed cam d' and the lower fixed cam e to change the needle actuating cam-path at
each change in the direction of the motion of the cam cylinder. It will be seen that
the switch cams b and c, being connected solidly with the annular gear l', form an
integral part of the driving mechanism; and also that as the openings at a aro
larger than the lugs of cams and c, which project into them, when, as previously
described, the direction of the motion of the annular gear is suddenly changed, as in
reciprocating knitting, the cam-cylinder will by its momentum be carried in the
direction in which it was being driven to the extent of its independent but limited
throw, thus changing the relative position of the cams d and e¹ with reference to the
switch cams.
As shown in Fig. 38, the switch cams are drawn in full lines in the
position for knitting with the cylinder driven in the direction indicated by the arrow;
when that direction is reversed, the relative position of the switch cams with reference
to the fixed cams is shown by dotted lines. The openings at and the projecting lugs
of the cams be¹ are so proportioned as to permit an amount of sliding motion of the
yoke on the exterior, and of the connected cams on the interior, of the cylinder
sufficient to close the upper and open the lower cam-paths at one side of the double
cams d and e¹ and to open the upper and close the lower paths at the other side of
said cams at each change in the direction of the motion of the cam-cylinder. The
action of the mechanism in changing the can-path being the same in every respect as
that described in the United States patent speen. No. 395,214 previously referred
to it is deemed unnecessary to discuss it further in detail herein.
In our present machine we have bolted the thread guide, which is of the ordinary
type, to the yoke y³ instead of securing it, as formerly, to the cam cylinder, the first
method having been found to give better results in feeding the yarn to the needles
than the one previously employed.
We have also, as stated, made the rear part of the shoulder cam e' movable
vertically for the purpose of facilitating the raising, en masse, of one-half, more or less,
of the needles. As shown in Figs. 38 and 39, the shoulder cam is made in two parts,
which are so formed at the joints as that the ends of the actuating section e* shall form
recessed guide-ways for the ends of the straight section which are formed to fit
said guide-ways. To facilitate the raising of section it is provided with the

page_text: attached thumb screws which are tapped into it, and by which the operator
raises the cam and secures it in position when raised, and which move in the guiding
slots cut in the cam-cylinder; section f is also fitted with a central guiding
bolt m¹ sliding in slot n', and with the retaining spring of, secured to the cam-cylinder,
which holds section f in its lowered position when knitting is progressing.
In the making of socks or such stockings as are provided with ribbed tops it is
necessary, after a stocking is completed and removed from the machine, either to
remove the needle-cylinder, with the needles, entirely from the machine, replacing it
with a similar cylinder on which a fresh ribbed top has been placed, or to raise all of
the needles in the cylinder to one level and then to transfer the ribbed top to the
needles thus raised. We propose following the latter method by the use of a trans-
ferring mechanism which forms no part of the present invention, and need not
therefore be described.
After the completion and "running off" of the stocking
the clutch shaft F is so moved automatically as to throw the double cone d out of
action while still leaving the cam-cylinder in motion, as for circular knitting, and
driven by the ratchet c²; an automatic tripping gear for the said ratchet is then
thrown into action by the operator; when a position convenient for raising out of
action a portion of the needles is reached the machine stops, the said ratchet being
automatically thrown out of gear. The needles are then raised, the operator shifts
the automatic tripping gear to another position, and ratchet c is again allowed to
drive the machine until a point 180° distant from the first stop is reached, when
ratchet 2 is again thrown out of action, the machine comes to rest, and the remainder
of the needles is raised. The stopping and starting of the machine are effected
through the auxiliary adjusting and hand operated can ², shown in Fig. 1, and in
detail in Figs. 8 and 9 sheet 5. From the lever ², previously described, depends the
link y which connects the former with one arm of the lover w² pivoted at The
outer end of the lever w² bears on the three-part cam v², feathered on the shaft B so
as to rotate therewith but to be capable of longitudinal motion thereon. The roller
end of the lever 102 is in line with the central cylindrical part of the cam while
knitting is progressing. When it is desired to elevate the needles the cam 2 is
shifted to the left and, in the course of its rotation, the roller end of lever w² is
depressed by the projection a³, lifting link y², lever q², arm p², and shield m², thus
tripping the pawl of ratchet c², and stopping the cam-cylinder. Cam f^ is then raised,
carrying with it the portion of the needles whose butts rest on it until the upper
butts of said needles strike the retaining spring h, Fig. 25 (a coil spring of the
ordinary type), said spring holding the needles out of action in their elevated position.
The guard-band 6 which has been lowered to disengage the jacks from the needles
is then again raised, cam f is lowered, and cam v² is moved to the right, bringing
the end of lever 20² on a low part of cam v³, thus retracting shield m² and starting
the machine which remains in motion until a projection 22, similar to a³, but 90°
distant from it, again raises lever w² and shield m² and stops the machine with
cam under the remainder of the needles, which are then raised, as were the others,
thus bringing all of the needles in position for the transferrer.
To the cam-yoke are attached, as in the application and patent previously referred
to, the spring latches p p (Figs. 34 and 37) which engage with the angular
studs qq in order to hold the cam-cylinder against accidental displacement while
knitting is progressing. The cam-cylinder also carries the forked standard 1 for
revolving the web-holder, which is similar in function and design to that marked 83
in the application and patent referred to.
As shown in Fig. 6, the needle-cylinder is so supported as to be capable of vertical
motion while knitting is progressing, being so arranged for the purpose of "fashioning"
or shaping the web of the leg and foot by varying the length of the stitches
throughout each knitted course. When a stocking conforms fully to the leg and
foot of the wearer some parts of said stocking, as for instance the calf of the leg,
should be straight in front while the rear should be full or curved and, conversely,
at the instep the top or front should be full and curved while the bottom or back
should be straight and tight. These variations in the shape of the web may be effected

page_text: by varying the length, relatively to each other, of the stitches of each knitted
course, i.e., in the first case above cited, beginning at the front, where the web is
straight and the stitches are shortest, they are gradually lengthened to the back of the
stocking and then gradually shortened again to the front; and again, in the scond
case above given, beginning at the front where the web is curved and the stitches are
longest, the latter are gradually shortened to the back of the stocking and then again
gradually lengthened to the front. These variations in the relative lengths of the
stitches of each knitted course, we propose to effect by varying, for each stitch fo
said course, the distance from the top of the needle-cylinder to the actuating cam-path,
and hence to the needles. As is well known the length of the stitches in circular
machines of this type usually depends entirely on the position of the needle-cylinder
relatively to the needles; for since the cam-cylinder and its actuating path are never
vertically moved it follows that the stroke of the needles in knitting will be always
between the same vertical limits, and therefore, if the distance between the top of the
needle cylinder and the tops of the needles be increased or decreased, that (as the
web within the cylinders is so secured that it cannot be drawn over the top of said
cylinder) more or less yarn per stitch will be drawn by the needles down into
the grooves, resulting in the formation of longer or shorter stitches, as the case may be.
As shown in Fig. 2, sheet 2, Fig. 6, sheet 4, and Fig. 15, sheet 5, the needle
cylinder n³ is vertically supported by the links t t which grasp pins set in
bottom of cylinder; the links 88 are pivotally joined to the arms cast solid with
the sleeve m which oscillates loosely on the shaft D, using said shaft merely as a
pivotal support. Projecting to the rear there is also cast solid with the sleeve m' the
arm n (Fig. 6) which is oscillated vertically by the two-part rod o which is pivotally
connected with, and vertically reciprocated by, the link block of a link p of the
ordinary reversing type, said link transmitting the motion of either of the eccentrics q
or which are of the same size and eccentricity and are connected with the link
by the straps and rods sand and thereby to the vertical rod o'. The eccentrics
and 9 are keyed to the shaft properly supported from and beneath the table do,
which shaft, as will be hereinafter explained, revolves continuously with the same speed
as the cam-cylinder. One of said eccentrics is so keyed to said shaft as that when
the thread-guide g¹ is passing the central point of the front half of the needle cylinder
it shall, if in gear with rod o³, raise the cylinder n³ to the highest point of the vertical
reciprocation which said cylinder must make, if in gear with either of said eccentrics,
and the other of said eccentrics is so keyed to said shaft that, when in gear with
rod o, the cylinder shall be at the highest point of its vertical reciprocation when
the thread guide is passing the central point of the rear half of the needle cylinder.
From the foregoing it will be seen that unless the link p is in the central position, as
in Fig. 6, the needle cylinder is necessarily in gear with one or the other of the two
eccentrics 9 and 70 and that, since the shaft u has a motion coincident with that of
the cam cylinder, the needle cylinder must, during the knitting of a course, make a
vertical reciprocation, consisting of a downward and an upward stroke; and also that
the highest point of this reciprocation will occur either at the centre of the front or
the centre of the back half of the needles, depending on which of the eccentrics q
and is in gear with said cylinder. Either of the eccentrics 9° or " is brought
in gear with rod 0° by so moving the link that either of the respective eccentric
rods or is in line vertically with o. The link is moved in either direction from
the centre by the rod v, which is attached to a pin a¹ which is secured to and
projects from the centre of the left hand face of the link; the rod is reciprocated
in the guide blocks ww by the bell crank, pivoted at y³ on the support m10, the
link and the bell crank a¹, pivoted at 610, the shorter end of which bears on the
pattern chain co, driven by a suitable drum keyed to shaft H. The pattern chain c¹ thus
regulates the form of the web. When it is desired that the stitches shall be of equal
length throughout the course the link is placed in the central position, as shown in
Fig. 6, in which case it oscillates idly on its link-block giving no motion to the
rod o⁹.
Since the eccentrics q³ and 79 are of equal eccentricity, it follows that the recipro-
3
B

page_text: cating stroke of the needle-cylinder will always be of constant length, no matter
which is in gear, and that consequently, with the mechanism thus far described, the
shortest stitches of one course will be equal in length to the shortest stitches in any
other course, the longest stitches in one to the longest stitches in any other,
and so on. But if we can raise or lower together, with respect to the needles,
the vertical limits between which this constant stroke of the needle-cylinder
is made, it also follows that, while the lengths of the stitches in each course will
constantly vary with respect to each other, we shall increase or decrease the average
length of the stitches in a course as the vertical limits of the stroke are raised or
lowered. The raising or lowering of the limits of the stroke is effected, as shown in
Figs. 6 and 15, by increasing or decreasing the effective length of the driving rod o'.
As before stated this is a two-part rod, one of the parts having a right hand, the other
a left hand, thread cut on its end and both being united by the hexagonal turnbuckle
or nut d, which has corresponding right and left hand threads cut in its interior.
It is evident that if do, be revolved horizontally in one direction, it will separate the
parts of rodo, and if in the other, draw them together, thus increasing or decreasing
the effective length of o³, and raising or lowering the vertical limits of the stroke of
cylinder n³. This partial revolution of nut 10, is effected through the lever e¹o, the
outer end of which has a hexagonal socket, fitting closely the nut do, and acting
both as a guide and as a means of oscillating said nut. The lever e¹0 is oscillated
on the rod o as a centre by the helical cam f which oscillates loosely ou the shaft K,
using said shaft merely as a pivotal support. In the path of cam f10 a pin gl
on the inner end of lever el fits, by which, in its oscillation, the cam moves said lever.
The lever guided by a pin fixed to it which moves in a circular slot cut in the
guide-plate (Fig. 6 and 15) which is bolted to the bottom of the guide-block 46.
The cam f is oscillated, as required, by the pattern chain 10 driven by a suitable
drum on the shaft H, through the bell-crank 1, pivoted at 60, and the link n which
grasps a pin secured to the cam.
;
The shaft u, which gives motion to the cylinder reciprocating gear is driven as
follows: On the shaft C there revolves continuously, while knitting is progressing,
the loose gear p which, as previously explained, has a motion coincident with that of
shaft B, and hence makes but one half as many revolutions as the cam-cylinder. To
the right of this gear, and keyed to its extended hub, is the sprocket wheel 010,
which through the chain belt p10 drives, without a slip, a corresponding sprocket
wheel 10, keyed to shaft 710, (Figs. 5 and 6) suitably supported from and above the
table d; on the other end of there is a sprocket wheel 100, of the same size, which
drives the chain belt $10, which in turns drives the sprocket wheel 10, of same size
as q, keyed to short shaft u, suitably supported from and above the table d'.
shaft is keyed the combined spur and mitre gear, which, through an opening
in the table, drives the spur gear w, keyed to shaft u. Inasmuch as gear w¹0, is but
one half the diameter of gear, it follows that the shaft u will while knitting
progresses, revolve at a speed coincident with that of the cam-cylinder.
On
It is apparent that any of the many well known mechanisms for transferring a recipro-
cating motion from one of two eccentrics to a rod, such as o³, or for reversing the
action of a single eccentric, a reciprocating motion from which is given to such a
rod, could be applied to the raising and lowering of the needle-cylinder, as herein
described. It will also be seen that if the object be simply to vary the general
tightness of the knitting of the various courses while a stocking is making, the
link p will remain permanently in the central position. The changes in the length
of this rod, through the action of the cam 10, will then gradually raise or lower the
needle cylinder, as may be required. Other changes in the form and arrangement of
the devices comprising this feature of our invention might be made without
departure from the nature or spirit thereof.
We have so designed our machine as to make it unnecessary to stop the cam-
cylinder, except under extraordinary circumstances, during the knitting of a complete
stocking. This is effected by connecting the parts whose relative positions require
changing (to throw them into or out of operation just previous or subsequent to the

page_text: formation of a heel or toe) to a single shaft D, the motion to the various parts being
transmitted from said shaft by eccentrics or cranks keyed to the shaft. It is obvious
that a semi-revolution of shaft D will give the eccentrics or cranks their full throw
in one direction, thus putting the attached mechanisms in gear, and that the subsequent
semi-revolution, in whichever direction it may be made, will return said eccentrics
or cranks to their originial position, thus throwing the attached mechanisms again
out of gear.
The advangages of this system are: 1st, but one motion (i.e. that of shaft D) to
effect by pattern chain, in changing from circular to reciprocating knitting, and vice
cersa; 2nd, entirely positive connections between the parts whose positions are to be
changed and the acting mechanism (shaft D) for effecting the change; and 3rd, the
ease with which, by extending the change-shaft D, one pattern chain can control the
changes for a number of knitting heads.
The change-shaft D, with its attached mechanism, is shown in Figs. 1-4,
inclusive.
As shown in Fig. 2, there are attached to this shaft, 1st, the crank of which, acting
through the yoke p° (see Fig. 3) and the hooked rod q" made fast to said yoke,
throws in and out of gear, as will be hereinafter explained, the mechanism controlling
the automatic raising and lowering of the needles out of, and into, action 2nd, the
eccentric e¹, Fig. 2, sheet 2, which, as previously explained, through rod d¹, crank c¹,
and screw shaft a', lengthens and shortens the expanding crank o and throws into and
out of action the auxiliary driving coner; 3rd, the eccentric v³, which, through rod u³,
(see Fig. 6, sheet 4,) crank t3, shaft 3, and cranks q³ q³, (Fig. 15, sheet 5) recipro-
cates vertically the jack-holder m³, thus throwing into and out of action the needles
controlled by the latter; and also through mechanism, as will be hereinafter explained,
connected with said shaft 3, throws into and out of action a yarn stop-off and a
web-holder similar in function to those described in the application and patent
previously referred to.
It will thus be seen that the shaft D controls the action of all the mechanism which
is inoperative during circular knitting and in action during reciprocating knitting;
and that an angular motion of 180° of said shaft from its position during circular
knitting will throw all of its attached mechanisms into action, while a return to its
original position will render them again inoperative.
The time at which either semi-revolution of shaft D shall occur, during either a
circular or reciprocating course of the can-cylinder, is approximately fixed by the
position of the upper switch cam d¹ (Fig. 38, sheet 10). Since the jack-holder is to
be raised or lowered by the semi-revolution of the shaft D, and since the cam d³,
must be entirely clear of the upper butts of the needles controlled by said jack-holder,
when the needles are ascending or descending, it follows that the motion of shaft D
must occur while the cam d is beneath the remaining needles, i.e. while the cam-
cylinder is traversing less than 180° of its angular motion.
The mechanism for producing this semi-revolution of the shaft D within this
As shown in
limited time is shown in detail in Figs. 16-20, inclusive, sheet 6.
Figs. 2 and 4, there is keyed on the right hand end of shaft D the crank v,
actuated by connecting rod w³, the latter being operated by crank 2 on the short
shaft y. The shaft y is revolved by the spur gear 26, keyed to said shaft, which
meshes with a similar gear a keyed to the intermittently operating shaft 67, the
latter being supported, as is the shaft y', in bearings bolted to an extension of the
frame. Since the diameters of the gears a' and are to each other as four to
, it follows that if shaft & be moved through 45° shaft D will make a semi-revolution.
The shaft ', while entirely distinct from the shaft B, is in alignment axially with
said shaft; and, as shaft B makes but one-half as many revolutions as the cam-
cylinder makes revolutions or reciprocating movements it follows that if, at the times
required, it is temporarily connected with, and revolves the shaft through an
angular distance of 45°, the necessary changes in the relative positions of the parts
will be effected while the cam-cylinder is moving through 90° of its circular or
reciprocating course.
one,

page_text: To effect this temporary connection of the shafts there is keyed (as shown in
Figs. 1, 4, 16, and 17,) to the right hand end of shaft B the radially slotted arm d
which carries in its slot or groove the L-shaped block e', the latter being pressed
outward from the centre of shaft by the spring f placed in the bottom of the slot,
which spring forces the block as far outward as the remaining strap h' (Fig. 4) will
permit.
The block is kept in place by the retaining plate g bolted to the left hand face of
the arm d²; at its outer end, in suitable bearings, the block carries the anti-friction
roller which, during a portion of the revolution of the arm, strikes against the
tripping wheel (which is to reduce the friction of the parts) mounted loosely on
the power shaft A, though it is evident that a stationary cam would serve the same
purpose, with, however additional friction and wear. The diameter of the wheel 17 is
so proportioned with reference to the extreme length of arm d', and the wheel is so
placed as, in a portion of the revolution of said arm (less than 45°), to force
roller and block e inward sufficiently to clear a block 87, in the same vertical plane
and corresponding in height, breadth, and distance from the centre, with block e, and
forged solidly with the crank or arm p', which is mounted loosely on the shaft b', and
held during circular knitting in an approximately upright position on said shaft by
the retaining hook q', pivotally joined to the crank or arm p', and engaging the
reversed ratchet 7, which is keyed to shaft b. On its left hand face arm phas
pivotally joined to it the pawl 7 which engages the ratchet n', keyed to shaft b7.
Ratchets n and have each 8 teeth set equally distant on their circumferences.
In the position shown in solid lines in Fig. 18 the blocks s is out of the range of
rotation of the projecting end m' of block e', for before the latter can touch block s
it is forced inward by the tripping wheel and is compelled to pass between block s
and the pawlo If, however, the retaining hook q' be lifted both it and the arm p² will
fall backward and downward 45°, as shown by dotted lines in Fig. 18, the pawl o
being at the same time carried backward to the next preceding tooth of ratchet n.
In this position of arm p' the projection m' will, in its next revolution, strike block s³,
carrying arm p', pawl o', ratchet n', and shaft 67, forward to the former position.
During this movement the trip wheel has gradually forced projection m² radially
inward until, when said position has been reached, the latter is just out of engagement
with block 87. As ratchet has also been carried forward with the shaft the
arm p will be held out of range of block e' by the retaining hook q' until the latter
is again tripped.
The tripping of the retaining hook g', which occurs just previous to the beginning
and the end of reciprocating knitting, is effected by projections on the pattern chain M,
(Fig. 2) which passes under an offset on the side of hook q'. The chain is driven
by drum a keyed to shaft H and passes over the pulley 68 mounted loosely on
shaft b', being led also beneath the guiding rollers cc, (Fig. 4) of the adjusting
turn-buckle d (See Fig. 4) which is suitably secured to the frame.
The ratchet n is provided with the detent t, pivoted to the suitably supported
standard u'. The shaft bis prevented from being carried, by its momentum, too
far forward by the locking bar w, which faces the ratchet, and a boss z made on
the hub of arm p'; the bar w' is pressed against the boss and ratchet 7 by the
spring acting against the standard bearing y. As shown in Fig. 20, the locking
bar effectually prevents the forward motion of ratchet when the stationary position
of arm has been reached; but when arm p' falls backward, as shown in Fig. 19,
the boss 2 forces the locking bar w' sufficiently to the rear to clear the tooth with which
it has been in engagement, and when arm preturns, carrying shaft 6' and rachet r
with it, the boss 27 is so shaped as to permit the locking bar w' to move forward and
lock and hold the next following tooth of ratchet 7. The shaft is thus held between
the detent t' and the locking bar w. As the movement made at a low rate of speed
no difficulty is experienced in picking up and stopping the shaft without the aid of
cushioning springs.
It is apparent that the actuating eccentrics and cranks on shaft D may be so
proportioned that an oscillation less than 180° of said shaft will throw the.connected

page_text: parts into action and that a return oscillation through the same angular distance will
throw them out of action. It is also obvious that the relative proportions of the
gears a and may be considerably modified without materially affecting the movement.
of shaft D within the time required.
The mechanism for automatically raising and lowering the needles which are
variably operative during heel and toe knitting is shown in Figs. 25—33, sheets 7-9,
inclusive. As shown in section, Fig. 25, the arrangement of the levers is substan-
tially the same as in the application and patent previously referred to, but we have
replaced the pattern drums described, in said application and patent for moving the
levers, by horizontally reciprocating cam-bars, moving at right angles to the parallel
levers and actuated, as shown in Fig. 29, by spring-driven helical cams whose motion
is controlled by a side escapement of the ordinary type.
The needles to be separately raised and lowered during heel and toe knitting
comprise about one-third, more or less, of the whole number, this proportion being
made up of the two one-sixths of the back needles nearest to the ends of the series of
front needles which is raised, en masse, out of action by the jack-holder at the end of
tubalar knitting. These variably operative needles are thrown out of motion
alternately from each of the two series which make up their total number, as above
specified, beginning with the ends of those series which are nearest to the front needles
and proceeding successively until the inner ends of the series are reached and all the
variably operative needles are out of action, the narrowest course in the heel or toe
pouch being then reached. The needles are then thrown into action in the inverse
order from that in which they were thrown out and widening progresses until, when the
widest part of the pouch is reached, all of the variably operative needles are in action
and tubular knitting with all of the needles is resumed.
Each of the variably operative needles is provided, as shown in Fig. 25, with a
jack ³, said jacks being each connected by a pin and slot connection with a lever st,
fulcrumed on a knife-edge bearing t, bolted to lever-bed o³, guided by slotted guide-
bars and 4, bolted to lever-bed o³ and kept in place by a cap w¹, bolted to
lever-bed, which cap has an internal boss so formed as to fit closely upon a
curved projection on the upper side of each of the levers ss. The ends of the
levers are suitably rounded and each engages the forked end of a supplementary
lever y fulcrumed at 4, and guided by the slotted guide-bars a and 7 bolted to
lever-bed o. As shown in Fig. 26, the levers y are parallel and those on the right
hand wing of the lever bed extend beyond the fulcrum ; to them, at a point c
near their extremities, and to those on the left at a point d between the fulcrum and
cylinder, where the leverage is the same as that of the left hand levers, are pivotally
attached the lifting pins which engage, through pins ³ set in their lower ends, the
cam-path of the cam-bars and go by which they are operated. These bars recipro-
cate in guide-ways k³ k³, k³, (Figs. 2 and 6), bolted to lever-bed o³, and 151 (Figs. 2
and 3), formed in the frame; during circular knitting they are separated to their
full throw, as shown in Fig. 2; during heel and toe knitting they complete oue
reciprocation, their inmost position, at the narrowest parts of the heel and toe, being
shown in Fig. 20. As shown in Fig. 25, the body of the bar is 11-shaped, and,
as shown in Fig. 30-33 inclusive, similar cam-paths are formed on the inner sides
of the vertical parts of the bar, which paths acts upon the projections 4 of the lifting
pins e. The said cam-paths are so shaped as, when the bars are widely separated
(Figs. 32 and 33) and circular knitting is progressing, to elevate the pins e³ of the
left hand parallel leversy and depress the pins of the right hand levers, thus lowering
the jacks of all the variably operative needles and throwing said needles into
operation and, when at the inmost point of their reciprocation, as in Figs. 30 and 31,
to depress the pins of the left hand levers and elevate those of the right hand, thus
raising all jacks k³ of the variably operative needles and throwing said needles out
of operation.
:
As shown in Figs. 26 and 29, the bar g³ is placed vertically over the shaft K. and
motion is given to it by a stud-pin m³ which rests in, and is actuated by, the thread
of a helical cam n keyed to shaft K, The bar is on the same level as g³ but is

page_text: placed in rear of the shaft K, motion being given to it by a curved arm o° (Fig. 28)
bolted to the bar f³, the point of which rests in, and is actuated by, the thread of a
helical camp similiar in all respects to n³ and also keyed to shaft K.
1.5
The thread in
cams and p is of constant pitch and is cut, as shown in Fig. 29, left hand in one
half of the cams and right handed on the other, in order that the actuating pins m
and may, in one revolution of shaft K, with its attached cams, cause the cam-
bars g and to make one complete reciprocation. The movement of the shaft K
being controlled, as previously stated, by an escapement, the cam-bars have, in
consequence, a step by step motion which is made equal to half the distance between
the actuating pins of two consecutive lifting pins e. Since, during a reciprocation
of the bars, the total number of the step by step movements is made equal to twice the
number of pinse it is evident that during the time specified all of the pins, with
their connected levers, will be raised and lowered once; and, since one of the bars is set,
relatively to the pins, in advance of the other by an amount equal to the space passed
over in one step by step movement, it follows that the right and left hand levers
will be alternately affected. It is also obvious, since the bars are separated to their
fullest extent in circular knitting, that when they move inward the outer levers and
needles of both series will be first affected in narrowing, and that when they move
outward the inner levers and needles will be first affected in widening. Thus, as
shown in Figs. 32 and 33, let the bar 2 be moved as far to the left, or outward, as
possible and the bar f³ be moved as far to the right as possible, the position being that
maintained during circular knitting. If now the step by step motion of the shaft K
begins the bars will move in the direction indicated by the arrows, the right hand or
outermost pin off being the first affected, then the left hand or outermost pin of 9,
and so on, successively and alternately, until the pins and bars and gare in
the position shown in Figs. 30 and 31, ie, when the narrowest point of the heet is
reached. Here the motion of the bars is reversed and they begin their return
movement in the direction indicated by the arrows, the right hand pin of g³, which
was the last to be lowered, is the first to be raised, then the left hand pin of, and so
on, successively and alternately, till all of the pins are moved in the inverse
order and direction of their movement during the first half of the reciprocation.
The step by step movement of the shaft K is primarily produced by the eccentric q
(Fig. 3) keyed to shaft B, the open-ended rod of which, when shipped on the pin s
of the crank, which is keyed on the left hand end of shaft L, gives that shaft one
vibratory movement for each rotary reciprocating movement of the cam-cylinder m'.
At the right hand end of the shaft L (Fig. 4) is keyed the crank which,
through the link, oscillates the crank mounted loosely on the shaft K. This
crank (Figs. 26 and 29,) carries the pawl which is pivotally jointed to it, and
which in turn drives the ratchet y which is keyed to the spring hub 2, the latter being
mounted loosely on the shaft. K. A detent (not shown but corresponding with the
detent p shown in Fig. 26 of the drawings of the former patent referred to) prevents
any backward movement of the ratchet y. In the projecting bosses a a of hub
are secured the rods 6° which draw forward the springs attached to their ends
and fastened also to the driving pins d d of the escapement wheel e which is keyed
to shaft K. It is evident that when the shaft L oscillating there is a constant
tension on the escapement wheel e, tending to draw forward said wheel with the
shaft K and the attached cams n' and p³. On the other side of the rim of wheel e
are fixed the semi-cylindrical pins which engage the escapement lever g keyed to
shaft L and cooperate with said lever in controlling the forward motion of the
wheel €6.
Since the shaft B makes one-half as many revolutions as the cam-cylinder m³ makes
reciprocating movement it is evident that the eccentric q, when in gear, will give to
the escapment lever gone vibratory movement for each movement of the cam-cylinder.
As shown in detail in Fig. 22, sheet 6, the lever g' is provided with two actuating projec-
tions and ke on the side next the wheel e, the inner end of one passing slightly beyond
that of the other; the pins f of the escapement wheel e strike first the projection,
passing thence, as lever g is vibrated, to the projection and escaping on the return

page_text: vibration. Since each of the pins f is thus twice caught, it follows that the total
number of them corresponds with the number of complete reciprocations which the cam-
cylinder is required to make in forming a heel or toe pouch. We have for convenience
so constructed our machine that the cams and p make but one complete revolution in
reciprocating the cam-bars and g; but if the threads cut in the said cams be
made of finer pitch so that the cams make two or more complete revolutions in
reciprocating the bars, it is evident that the diameter, and the number of pins, of the
escapement wheel may be materially reduced.
We have also provided a separate helical cam for driving each of the bars ƒ³
and but if the driving points of said bars be so formed and arranged as to enter
the thread of one of these helical cams at an angular distance of 180° apart one such
helical cam will suffice for both cam bars.
In order to preserve a constant average tension of the springs c c throughout,
and at the close of, reciprocating knitting the number of teeth on the ratchety is
made equal to the number of semi-cylindrical pins f on the escapement wheel.
Since its pawl and the lever g receive the same number of step by step impulses
from the shaft L, and since it requires a complete reciprocation of both to permit the
escape of one pin f from the lever and to force the ratchet y one tooth forward, it
follows that the initial tension given the springs will always be retained and
that the mechanism, when once set, will be always ready for action.
The means for unlocking and throwing into action the escapement mechanism just
previous to reciprocating knitting and for throwing out of action and locking the
said mechanism at the end of reciprocating knitting are shown in Figs. 2 and 3, and
in Figs. 26 and 27, sheet 8. There is mounted loosely on shaft L (Fig. 3) the
locking lever, the interior of the hub of which is slotted, as shown in Fig. 27,
in which the lever is horizontal and in position for reciprocating knitting. In the
shaft L is set the feather m which is so proportioned, relatively to the size of the
slot n of the hub of lever 1, that when said lever is horizontal shaft L will be
free to oscillate, but when lever is raised, as shown in Fig. 3, the right hand side
of slot n will press against the feather me and lock the mechanism. Again, as shown
in Fig. 3, the eccentric rod terminates in an open hook us which can be unshipped
from the pins of crank by the raising rod 76, thus depriving the escapement
mechanism of its actuating power. In Fig. 3 the rod is shown unshipped in the
position for circular knitting; when lowered the hook u rests on the pin ³, seating
itself when the proper position is reached. It is evident that the upward movement
of rod and locking lever must be made simultaneously. They are effected
primarily by the crank of keyed to the left hand end of shaft D (Fig. 3) which revolves
in the yoke p forged solid with the rod, the latter being guided at, having a
sliding connection with lever 1, and terminating in the open book which, during
reciprocating knitting, lowers the eccentric rod and during circular knitting raises
and unships the said rod, at the same time raising the locking lever 16. It is evident
that a semi-revolution of shaft D will lower rod 7%, lever 16, and rod, unlocking
and throwing into action the escapement mechanism; and that the succeeding semi-
revolution of said shaft will raise rod q, lever 16, and rod, and reverse this.
action. The crank of and the yoke p are of course but the mechanical equivalents
of an eccentric, the radius of eccentricity of which is equal to the effective length
of the crank o.
The lever bed o³, on which the system of levers is fulerumed, is suitably supported
by the framing and table of the machine.
The web-holders, shown in elevation in Fig. 24, sheet 7, being the same in
function and design as that described in the application and patent previously
referred to, to which reference may be had, is only illustrated here for the purpose
of showing its application to this machine. Its driving rod is reciprocated
vertically by a came, corresponding in function and form with the cam marked 3
in the application and patent before referred to. The cam 10 is placed on the shaft E
which reciprocates, during the kuitting of the heel and toe, at the same angular speed
as the cam cylinder. On cam 10 the driving rod is pressed by the spring 10,

page_text: acting between the collar 10 of a fixed guide-arm (secured to a standard not shown)
and a collar all secured to rod 8. Between the two upper fixed collars of the
rod is loosely mounted the arm ", terminating in a fork which engages pins elle
fixed to the loose collar d which is loosely mounted on the spindle e¹ of web-
holders. The web-holder is pressed upward by the spring placed on standard g
acting on arm ", which spring, standard, and arm correspond in function and
design with those respectively marked p³, and o³, in the application and patent
before referred to. The socket of the arm " grasps the web-holder between the
loose collar and a small fixed collar "; below the collar there is a fixed
collar between which and collar " the web-holder is grasped by the arms b
and for producing its vertical reciprocations. The spindle el is revolved by the
forked standard fixed to cam-cylinder as shown in figs. 34 and 37. The web-holder
is thrown into and out of action by the semi-revolution of shaft D which, at the
and
proper time, oscillates shaft 8, through crank e keyed to shaft, the link f³,
crank Fig. 6 keyed to shaft h³, the oscillations of said shaft being transmitted
through the crank m³ and link n³ to the lever os, pivoted at p, which engages pins
fixed in the loose collar j³ encircling rod 8. When this collar is elevated, as shown
in Fig. 24, it presses against the collar a fixed to rod, and the driving rod is
thus raised beyond the range of action of the cam 10, in which position it remains
during circular knitting. Previous to reciprocating knitting the succeeding semi-
revolution of shaft D lowers collar to the table, bringing rod again within the
range of the cam
8
The automatic stop-off for stopping the supply of yarn when, in reciprocating
knitting, the thread-guide passes the last needle which is in operation is shown in
Fig. 40, sheet 11, Fig. 41, sheet 12, and Fig. 55, sheet 13. This mechanism is
similar in function to that described in the application and patent previously referred
to. It consists essentially of two plates the first of which is fixed to a rod which,
during heel and toe knitting, is reciprocated continuously, and with a constant stroke,
by an eccentric keyed to a shaft which makes as many revolutions as the cam-cylinder
makes reciprocating movements; the second plate, between which and the first plate
the yarn passes, is capable of reciprocation when driven by the first plate and is
provided with a cushioning spring so that when the first plate, in its reciprocating
stroke, strikes the second plate, thus stopping off the supply of yarn, the second
plate yields and recedes with the first plate to the end of the stroke of the latter,
returning with said plate in its backward stroke until the second plate reaches its
former position, when the yarn is freed, until, in the course of the next reciprocation,
the first plate again strikes the second. Inasmuch as, in reciprocating knitting, the
number of needles in operation varies constantly, thus necessitating a later or earlier
stopping-off of the yarn supply, means are provided for giving the second, or spring-
pressed, plate a different initial position relatively to the acting plate for every
movement of the cam-cylinder, so that the first plate may meet the second at an earlier
or later time in its reciprocating stroke.
After the supply of yarn is checked the cam-cylinder, which has a stroke of con-
stant length, continues on beyond the last needle in operation to the end of said
stroke, when it begins to return. To prevent the yarn between the stop-off and
thread-guide from breaking, after the supply is checked, while the cam-cylinder is
finishing its stroke, and to keep it taut while the cylinder is returning and before
knitting again begins, a take-up spring of the ordinary type is employed, over which
the yarn at all times passes in going from the stop-off to the thread-guide. While
the yarn is stopped off this spring yields to the pull of the thread-guide until the
stroke is completed; and on the return stroke retracts, thus taking up the slack until
the yarn is released and knitting begins.
As the stop-off is only required during reciprocating knitting means are provided
for stopping the reciprocation of the first or acting plate while tubular knitting is
progressing.
In our present machine we have provided also for the introduction of a second thread
at any time during the formation of the stocking. Since this thread is kept entirely

page_text: separate from the first until both pass beyond the stop-off, and since (whether it
be used in combination with the first as a thickening thread or be different in weight
or color and be used in place of the first, which is cut,) in reciprocating knitting
this thread must be acted upon by the stop off exactly as is the first, the number of
plates and take up springs above described is doubled, though both sets are moved by
the same actuating mechanism.
As shown in Figs. 40 and 55, sheets 11 and 13, the spur and mitre-gear 10 which,
as previously described, makes one half as many revolutions as the cam-cylinder
makes reciprocating movements, revolves the mitre-gear marked 1, which is keyed to
and revolves the short vertical shaft 2, on the upper end of which is keyed the mitre-
gear 3 which revolves the mitre-gear 4, which is keyed to and revolves the short
horizontal shaft 5 on the front end of which is keyed the eccentric 6, which actuates
the driving plates of the stop-off. Gears 1, 3, and 4, are all of the same size, their
diameter being one half that of gear 10, hence it is evident that the eccentric 6 will
make one revolution for each movement of the cam-cylinder m¹. From the standard 7,
which is secured to the table ', the arms 8, 9, and 10 project, said arms containing,
as shown, suitable fixed bearings for the shafts 2 and 5.
The eccentric 6, through the strap and rod 11, gives a reciprocating movement to
the slotted arm 12 to which rod 11 is pivotally joined. The slotted arm, as shown
in Figs. 40 and 41, is pivotally joined to the raising rod 13, by a crow-foot lug 14,
fixed to arm 12 at a point in line with the pin 15 of the driving rod 16, which pin is
pivotally joined to a block (not shown) fitting in the slot of arm 12, and so shaped as
to permit said arm to be readily moved to and fro thereon. The slot of arm 12 being
described from the centre of the shaft 5, and the pin 17 uniting it with raising
rod 13 being so located, when the parts are in the position shown in Fig. 40, as to ho
directly opposite the centre of pin 15 and also opposite the centre of that pin's
reciprocating stroke, it will be seen that the eccentric 6 which rotates continuously
will, when the parts are in said position, rock the arm 12 idly on pin 15 as a centre,
giving no motion to rod 16; but when the raising rod 13 is elevated, carrying arm 12
with it until rod 11 is in line with rod 16, it will be evident that a reciprocating
motion will be given rod 16 equal in length to twice the eccentricity of
eccentric 6.
On rod 16 are threaded, as shown in Fig. 41, the acting plates 18 and 19 of the
double stop-off mechanism which, at the proper time, strike the spring-pressed plates 20
and 21 and check the supply of yarn. The plates 20 and 21 are placed at the same
distance apart as are plates 18 and 19 and are rigidly tied together by the guide-
bolts 22, 23, and 24, screwed into lugs on plate 20 and fastened by small screws to
similar lugs on plate 21. The guide-bolts pass loosely through similar lugs on the
adjusting plate 25, which is reciprocated horizontally by the oscillation of the screw
shaft 26, the plate being kept froin turning with the shaft by the guido bolts 27, 27,
screwed into the stationary boss 28 and passing loosely through the adjusting
plate 25.
From the foregoing it will be evident that as plate 25 cannot turn, and as
bolts 22, 23, and 24 make a sliding connection between it and plates 20 and 21, these
plates can have no rotary motion. Plate 20 is guided centrally by the rod 16
which passes through it, said rod entering also the extended hub of plate 21, into
which hub the shaft 26 enters as an additional guide. Between plates 21 and 25 is
placed the spiral spring 29 which tends to keep plate 21, and consequently plate 20,
as far from plate 25 as the heads of the screw bolts 22, 23, and 24, will permit. The
distance of plate 25 from boss 28 is regulated by the crank 30 keyed to shaft 26,
which crank is oscillated by the connecting rod 31 (Fig. 40), the crank 32 keyed to
a short shaft 33 supported in a bearing secured to table d, the crank 34, also keyed
to shaft 33, the connecting rod 35 (Fig. 55), the crank 36, keyed to a short shaft 37
supported in a bearing from the table d' the crank 38, also keyed to said shaft, and
the eccentric rod 39 of the eccentric m¹ (Fig. 29, sheet 9) keyed to shaft K.
The eccentric 6 is so set on the shaft 5 that when the rod 13 and arm 12 are
raised, in reciprocating knitting, the reciprocation of the plates 18 and 19 towards
0

page_text: and from the plates 20 and 21 begins when the centre of cam d* (Fig. 38, sheet 10)
is at or about the centre of the back, or operative, half of the needles, and ends
when cam d returns to, or near, the same point. Since in beel and toe knitting
only about one half of the needles are, at the most, in operation it follows that the
latest point of stopping off the yarn will be when one half of the needles are in
operation and just after the thread-guide bas completed one-fourth of its reciprocating
movement, i.e., when plates 18 and 19 have moved half of their stroke to the right;
and that the earliest point of release will be when, in the same movement of the cam-
cylinder, the thread-guide has completed three-fourths of its reciprocating movement,
i.e. when plates 18 and 19 have completed half of their return stroke to the left.
Also, that the earliest point of stopping off the yarn will occur (while the narrowest
course of the heel or toe pouch is being knit and only about one-sixth of the total
number of needles is in operation) when the thread-guide has passed through one-
twelfth of its reciprocating movement, i.e., when plates 18 and 19 have completed one
sixth of their stroke to the right, and that the latest point of release will be when, in
the same movement of the cam-cylinder, the thread guide has completed eleven-
twelfths of its reciprocating movement, i.e. when plates 18 and 19 have passed
through five-sixths of their return stroke to the left.
It is evident that, in the first case above cited, (that of latest stopping off, when the
widest course of the heel or toe is being knit) if the adjusting plate 25, be so set
that the plates 18 and 19 shall meet the plates 20 and 21 when the former plates
have passed through one-half of their stroke toward the right the yarn supply will
be checked at once and the plates 20 and 21 will be carried by the plates 18 and 19
toward the right, compressing the spring 29 and forcing the guide-bolts 22, 23,
and 24, through their sockets in plate 25, and also, on the return stroke of the acting
plates, that the spring 29 will foree the plates 20 and 21 against the acting plates
until the latter plates have completed one half of said return stroke, when the heads
of boits 22, 23, and 24 will bring up against the lugs on plate 25, hold the plates 20
and 21, and release the yarn.
The action in the second case cited (that of earliest stopping off and latest
release of the yarn when the narrowest course of the heel or toe is being knit) is
precisely the same, except that the adjusting plate 25 must be so set that the acting
plates shall meet the spring pressed plates when the former have passes through
one-sixth of their stroke to the right; the plates will then travel together
until the acting plates have completed five-sixths of their stroke to the left, when the
heads of bolts 22, 23, and 24, will bring up on the adjusting plate 25, the plates 20
and 21 will be held, and the yarn released.
In order then, during reciprocating knitting, to stop-off and release the yarn at points
in the movement of the thread-guide whose position depends on the number of
needles in operation, it is evident (in passing from the widest to the narrowest,
and back again to the widest, course of the heel or toe pouch,) that the adjusting
plate 25 must be gradually moved from the position shown in Fig. 40, at half stroke
of the plates 18 and 19, towards the left to a point coinciding with the sixth part of
said stroke and then back to the former position; i.e., plate 25 must complete one
reciprocation between these limits while the pouch is being knit. This movement of
the plate is effected, through the connections previously enumerated, by the
eccentric m (Fig. 29, sheet 9) keyed to shaft K, which oscillates the shaft 26
through one semi-rotary (more or less) reciprocation during that time, the pitch of
the thread on shaft 26 being so proportioned as to give the proper movement to
plate 25 for each step by step movement of shaft K.
From Figs. 40 and 41, which show the position of the parts during circular
knitting, it will be seen that the plates during that time, and consequently at the
beginning and end of reciprocating knitting, are sufficiently separated to permit
the passage of the yarn without frictional tension and that, therefore, the stopping-
off of the yarn will be a little later and the release a little earlier, throughout
reciprocating knitting, than the number of needles in use would require. The
discrepancy, however, is so slight as to prove rather an advantage than otherwise in

page_text: preventing the stopping off from occuring too suddenly after the last needle
passed.
18
As shown in Figs. 41 and 55, the main and additional threads are led from the
bobbins, through the eyes 40 40, beneath the rod 16, over the take-up springs 41 41,
back over the guide-bolts 22 28, through the double eyes 42, and thence to the
thread-changing plates, to be hereinafter described. When the yarn is clamped
between the stop-off plates the take-up springs 41 41 are drawn forward while
the cam-cylinder is completing its stroke and begin to retract as soon as the return
stroke commences, thus always keeping the yarn taut.
The boss 28 is carried by the frame-work 43, which is suitably secured by
sockets to the standards 44 and 45, fixed to the table . The frame 43 also
supports the bearing 46 for rod 16, the cross-bearing 47 for the take-up springs 41 41,
and carries the rod 48 in which the eyes 40 40 are set.
As previously stated, the acting plates of the stop-off are thrown out of gear by
lowering the arm 12 to the position shown in Fig. 40. The arm is raised and
lowered by the rod 13 which moves in guide-sockets carried by arms 49 49 supported
by standard 44. The reciprocating movements of rod 13 are effected, primarily,
through the semi-revolution of change shaft D which, just previous to, and just
subsequent to, reciprocating knitting, acts on said rod through the oscillation of
shaft 3, as previously described, the oscillation of the latter shaft being communicated
to the short shaft h³, Fig. 6, suitably supported from and beneath the table d³, by
the crank e, fixed to shaft 3, the connecting rod f8, and the crank g³; the motion
of shaft is transmitted to rod 13 by the eccentric 8, the strap of which is
pivotally joined to said rod. The several parts throughout are so proportioned and
set that one semi-revolution of the change-shaft D raises rod 13 the proper distance,
and that the succeeding semi-revolution of said shaft reverses this action.
A thread-changing mechanism is shown in Figs. 5 and 6, sheet 4, Fig. 40, sheet 11,
Figs. 42 to 54, inclusive, sheet 12, and Fig. 55 sheet 13. It is, in principle and
design, based upon the well known fact that if the loose end of a thread from a
separate bobbin be brought in contact with a second thread which is being rapidly
fed to the thread-guide in knitting the adherence of the threads will be sufficient to
enable the second thread to pick up the first and carry it through the thread
guide and to the needles, after which knitting with the double thread will progress
until one of the two threads is severed.
As shown
As shown in Figs. 46 to 50, inclusive, sheet 12, the mechanism consists essentially
of two fixed clamping plates 50 and 51 between which reciprocates a movable
clamping plate 52 (which is made capable of clamping either of the threads 53 or 54
which pass between it and plates 50 and 51, respectively), and a parting bar 55 which
separates the threads, said bar forming a sheath for a cutting knife 56 which is pivotally
joined to it and is capable, when required, of vibration in either direction and
sufficiently far out-side of bar 55 to cut either of the threads 53 or 54.
in Figs. 46 and 55, the threads are led from the yarn stop-off over the take-up
springs 41, through the double eye 42, on each side of the movable plate 52 and
between it and the clamping plates 50 and 51, outside of the parting bar 55,
through the web-holder spindle e", (which is hollow, as decribed in the application
and patent previously referred to, to which reference may be had), and thence to the
thread-guide g. In the position shown in Fig. 46, the main thread 53 is being fed
and the additional thread 54 has been cut sufficiently far below the parting bar 55,
to permit the main thread, in the diverging rotary motion given it by the revolution
of the aperture 57 (Fig. 55) of the spindle e", to wind the loose end of the additional
thread 54 about the main thread 53. The additional thread is also clamped between
the plates 52 and 51.
The operation of the mechanism in replacing the main with the additional thread
is shown in Figs. 46 to 50 inclusive. As will be hereinafter explained this is effected
during one revolution, or one reciprocating movement, of the cam-cylinder. At the
beginning of said revolution or movement the movable plate 52 is suddenly shifted to
its central position, which, as shown in Fig. 47, released the additional thread 54,

page_text: the latter being at once carried by the main thread to the thread-guide. At the same
time the parting bar 55 begins to move gradually downward, separating the threads
until, just before the close of the revolution or movement of the cam-cylinder, it
reaches the lower limit of its stroke, as shown in Fig. 49. At this point the
clamping plate 52 is suddenly moved to the left, clamping the main thread; and,
simultaneously, the knife 56 emerges from the left side of its sheath in bar 55,
thus presenting a sharp edge to thread 53, on which the pull of the thread-guide
severs it. Immediately afterwards, as shown in Fig. 50, the knife is sheathed and
the parting bar instantaneously ascends to the upper limit of its stroke, leaving the
additional thread feeding and the main thread clamped and cut. The loose end of
the latter is almost instantaneously wrapped around the additional thread, ready for
the reversal of the operation.
In replacing the additional with the main thread, which is also performed during one
revolution of the cam-cylinder, the various operations are exactly as above described,
excepting that the movable plate 52 moves sharply to the right from its central
position and the knife 56 emerges from the right hand side of its sheath, thus
cutting and clamping the additional, and leaving the main, thread free.
As shown in Fig. 40, plate 50 is threaded on bolt 58, which bolt also acts as
a guide-rod for plate 2, being reduced in diameter to pass through said plate and
enter the hollow body of a bolt 59 of the same external diameter, on which plate 51
is threaded. Both bolts pass loosely through, and are supported by, the bosses 60 60
carried by the frame 61 (Fig. 42) which is supported by standards 44 and 45.
Between the bosses 60 60 and the plates 50 and 51, the cushioning springs 62 62
are interposed, which permit a slight backward movement of the plates 50 and 51
should the plate 52 be moved too far in either direction. Through bosses 99, made
in the arms of frame 61, the screw-shaft 63 passes and is supported, on which shaft
is threaded the hub 64 which is rigidly connected with the movable plate 52 by a small
arm, and by the reciprocation of which to and fro on the shaft 63 said plate is
vibrated. Inasmuch as bolt 58 passes through plate 52, it is evident that hub 64
cannot turn with shaft 63 and must reciprocate when said shaft is oscillated. Frame 61
also carries a standard 65 which supports an arm terminating in the double eye 42.
The oscillation of shaft 63 is, when required, effected through the crank 66 secured
to said shaft, the link 67, the bell-crank 68 (Fig. 55) pivoted to frame 61, the link 69,
and the lever 70 pivoted at 71 on socket frame 72 carried by standards 44 and 45.
A projection 73, extending downward from the lever 70 and provides with an anti-
friction roller, bears on the cam 74 (Fig. 55), keyed to shaft 75 (Fig. 5, sheet 4),
by the movement of which the shaft 63 is oscillated and plate 52 reciprocated.
The parting bar 55, as shown in Figs. 43, 46, and 55, consists of an upper and
a lower part, bolted together by the screws 76 and 77, and having a space between
them which forms the sheath for the two-edged knife 56; the front portions of both
parts of the bar are made V-shaped in section to facilitate the separation of the
threads; the bar is pivoted at 78 in the centre of the socket frame 79 carried by
standards 44 and 55, and its rear end is oscillated by the link 80, and lever 81 pivoted
at 82 on a bearing carried between the two parts of the socket frame 72; a
downward projection 83 from the lever 81, provided with an anti-friction roller,
bears on the eam 84, Fig. 54, keyed to shaft 75, by the movement of which the
bar 55 is vibrated.
The cutting knife 56 (Figs. 44 and 55), as previously stated, is two-edged, that
it may cut either thread; it is pivoted on the screw bolt 77 and is sheathed, when
in inoperative position, in the space between the upper and lower parts of the
bar 55; the knife tends always to assume a central or sheathed position within the
bar, owing to the lateral pressure of the double spring 85 (Fig. 45) which is secured
to the upper part of the bar and bears on the sides of the knife; the rear end of
the body of the knife is extended laterally to project over the lower part of the bar,
which projection, when the bar descends, and at the moment when the thread is to
be cut, strikes one of the interior sides of the V-shaped cam 86, (Figs. 40 and 55).
Çam 86 is secured to the top of lever 87, said "lever being pivoted at 88 on a

page_text: stud bearing fixed to socket frame 72, and having on its lower arm an inturned
projection 89, the point of which bears in the cam-path of cum 90 (Fig. 53) keyed
to shaft 75, by the rotation of which said lever and cam 86 are vibrated. The
lever 87 is guided in its oscillation by the finger 91, secured to said lever as shown,
which guide finger bears on a curved-flanged guide-way carried by the socket
frame 92, said frame being supported by standards 44 and 45.
It is evident that the inclination, from the vertical, of the lever 87 will determine
which of the interior faces of cam 86 is to strike the rear projecting end of knife 56
and consequently the side of the parting bar on which its cutting edge shall be
unsheathed. For, if the upper arm of the lever be inclined toward the right the left
interior face of cam 86 will strike and force toward the centre of the bar the left side
of the projecting end of the knife, thus throwing outward from the centre the left
hand cutting edge, as shown in Fig. 49. Conversely, if lever 87 he inclined toward
the left the right hand cutting edge will be unsheathed. Cam 86 is so proportioned,
internally, that contact with the knife 56 shall not occur until bar 55 reaches the
end of its stroke; and that therefore as soon as the bar begins to ascend contact
will cease and the spring 85 will force the knife into its sheath.
As previously stated, the introduction of the additional thread and the severing
of the main thread are effected during one revolution or movement of the
cam-cylinder and the replacing of the main thread and the removal of the
additional thread are effected during some subsequent revolution of said
cylinder. Since the latter operation differs from the former in that cams 74
and 90 actuate their connected mechanisms differently during each of the said
operations it follows, if such rotating cams are to be used, that the acting surface of
said cams must be so formed as to effect one of the operations specified in a part of a
revolution of the cams and the other operation in some succeeding part of said
revolution.
For convenience we have so formed the cams as to perform the first series of
operations in one semi-revolution and the second series in the succeeding semi-
revolution, and have keyed the cams upon a shaft which makes but one half as many
revolutions as the cam-cylinder, and which can be intermittently revolved, a semi-
revolution at a time.
To effect this the shaft 75 (Fig. 5), to which cams 74, 84, and 90 are keyed, and
which is suitably supported from the table d', is set in alignment with the shaft 10
which, as previously stated, makes one half as many revolutions as the cam-cylinder,
being, however, separated from said shaft by the short intermediate shaft n¹ which
is supported by the bearing on, the latter being capable of reciprocation in the
guide-way p", by the rod q, attached to bearing o", (Figs. 5, 6, and 51) guided
at, and pressed by the spring s against the pattern chain 1, said pattern chain
being driven by a drum keyed to shaft n, the latter being suitably supported from
the table d. The shaft is rotated by the eccentric keyed to shaft ulo and
acting through the strap and rod wl, the crank mounted loosely on shaft ", and
the pawl y pivotally attached to the crank ", which drives the ratchet " keyed to
shaft u
While the centre of the shaft is in the same horizontal plane as the centres of
the shafts and 75 it is never in alignment, vertically, with said centres, but whether
at one end or the other of its horizontal reciprocation it is always eccentrically placed
with regard to them. Its reciprocating stroke, however, would be equally divided
by a line joining the said centres. On the shaft 75 is keyed the crank a¹ which is in
sliding connection with the slotted crank 612, keyed to shaft n", through the pin or
bolt which is made fast to crank a2 and is capable of sliding in the slot of
the crank. There is also keyed on the shaft n" the crank d" which has a projecting
lug e so shaped as to be capable of engaging a similar lug ƒ projecting from
the crank g keyed to shaft ul. The lugs el and f12 are of the same diameter; the
radial distance from centre of shaft n" to the outer extremity of lug e" is less than the
corresponding distance from the centre of shaft u¹º to the outer extremity of lug 12
by one half the radial length of either lug; and the sliding bearing or shaft n" is

page_text: capable of being moved in the guide-way p" a distance equal to the radial length of
either lug which distance is so spaced as to be equally divided by an imaginary line
joining the centres of the shafts 10 and 75. From the construction described it will
be seen that if the bearing o" with shaft n be forced to one end or the other of its
reciprocating stroke the crank g12 which revolves continuously will during its revolution
bring the lug into engagement with lug e and revolves shaft n through one
semi-revolution at which time lug (which has owing to the eccentricity of
shaft n been gradually disengaging itself from lug e12) will be fully disengaged from
lug e will pass outside of said lug and will during succeeding revolutions leave it
untouched until the shaft n is moved to the other end of its stroke when another
semi-revolution of shaft " will be in the same manner be made. The shaft 75 moves
with the shaft n through the connections previously described the slot in crank b
heing so proportioned as to admit of the horizontal movement of the pin c¹² in said
slot when the hearing o¹ is reciprocated. The bearings of the shaft 75 are
set up
tightly that the friction between them and the shaft may prevent the latter from
being carried too far forward by the moment .m of the moving parts.
65
:
By varying the eccentricity of the shaft n" and also the effective length of the
crank or arm 12 the shaft can be made to move the shaft n through any
required portion of a semi-revolution. It will also be seen that the slotted crank 12
and the crank a¹² are interchangable with regard to their respective shafts, as is also
the case with the movable and fixed projecting blocks on the arms d' and p7 Fig. 16
either of which arms can carry the movable block provided the other carries a fixed
block.
From Figs. 46, 47, 49, and 55, it will be seen that at the beginning of either
semi-revolution of shaft 75 the movable plate 52 must be at one extreme or the
other of its reciprocation and that therefore the lever 70 must be either raised or
lowered and also that as soon as the semi-revolution begins the plate must pass to
and remain at its mid-position until the close of said semi-revolution and therefore
that the lever 70 must during that time remain at mid-throw. Cam 74 (Fig. 52)
is therefore provided with an elevation 100, a depression 101, 180° from said
elevation and eccentric paths joining the two the elevations and depressions being
just large enough to contain the roller end of the projection 73 on lever 70. It will
also be seen that the parting bar 55 must be at the upper limit of its stroke at the
beginning of a semi-revolution must descend gradually to the lower limit of said
stroke and must then be suddenly elevated to its first position and that consequently
the lever 81 must at the beginning of the semi-revolution be down must ascend
gradually and at the end of said semi-revolution must suddenly descend again.
Cam 84 (Fig. 54) has therefore two low points 180° apart equally distant from the
centre with spiral paths between and approximately radial lines joining the high and
low parts of the path. It will also be seen that the knife 56 must during one semi-
revolution vibrate to the left and during the other semi-revolution to the right of the
centre line. Cam 9 (Fig. 53) is therefore provided with a straight path except
at two points 180° apart, where the path diverges respectively to the left and right.
It is evident that slight changes in the mechanisms described will fit them for
inserting the additional thread as a thickening thread merely as is often customary
in re-inforcing the heel and toe pouches. From Figs. 46-0 inclusive it will be
seen that in the first semi-revolution all that is necessary to be done is to move the
plate 52 to the central position which action will be reversed at the end of the semi-
revolution of shaft 75 hence cam 74 should be provided with but one small elevation
or depression (depending on direction of screw thread on shaft 63) the remainder of
its path being eccentric. During the first semi-revolution the parting bar 5 will
not move at all and during the second it will gradually fall until the end when it will
suddenly rise hence cam 84 should be provided with a concentric path for 180 of
its circumference which path should then gradually rise until about the end of
the second 180° of its circumference when it should suddenly fall to its former
level.
If two main threads be used with separate stop-offs and changing plates it is

page_text: carriers. In regard of the number and position of the thread clamping plates it
will also be seen that it is immaterial whether the construction be that described or
whether there be for each main and auxiliary thread a central fixed plate with a
movable plate on each side of it the latter plates being connected together and
capable when moved in one direction of coming into contact with one side of the
fixed plate and thus clamping one thread and releasing the other and when moved in
the opposite direction of coming into contact with the other side of the fixed plate
and thus reversing the clamping and releasing of the threads. Other modifications
which do not depart from the spirit of this invention will readily suggest them-
selves.
Having now described our invention we claim
No.1. The combination with the cam-cylinder of the driving shaft A; a double
clutch thereon; gearing whereby the cam-cylinder may be operated from each of
the loose members of said clutch; a rotating cam; means for rotating the same; and
devices for controlling the rotation thereof; whereby it may be left at rest or given
a movement of rotation at desired intervals; and a connection between said cam and
the engaging member of the clutch, whereby the desired loose member may be locked
to the driving for operation therewith.
No. 2. The combination with the cam-cylinder, of the main power shaft A; a
double clutch thereon; gearing whereby the cam-cylinder may be operated from
each of the loose members of said clutcli; a shaft ; means for rotating the same;
devices for controlling the rotation of said shaft, whereby it may be left at rest or
given a movement of rotation at the desired times; a cam 1, on shaft F; and a
connection between said cam and the engaging member of the clutch; whereby
the desired loose member may be locked to the shaft A; for operation there-
with.
No. 3. The combination with the cam-cylinder, of the main power shaft A; a
double clutch thereon; gearing whereby the cylinder may be operated from each of
the loose members of said clutch; a rotating shaft F; carrying a cam ; a
connection between the said cam and the engaging member of the clutch for
operating the said engaging member; a ratchet on shaft F; a pawl; means for
operating said pawl from shaft A; and means for throwing said pawl into and out of
engagement with said ratchet.
No. 4. The combination of two shafts, each carrying a gear wheel, one of said
gears being loose on its shaft an intermediate gear wheel for revolving said gears
in unison; a crank of fixed length on one shaft; a crank of variable length on the
other shaft a clutch for making the loose gear fast on its shaft; a connection
between the two cranks; the cam-cylinder, and gearing for driving the same from
one of said shafts, substantially as shown and described.
No. 5. The combination with the driving shaft A; provided with two loose gears of
unequal sizes and with a double clutch mechanism by which either of said gears is
made fast; and a driven shaft B provided with gears of unequal sizes which are in
mesh with the gears of shaft A; of a shaft C; the cam-cylinder and gearing to
drive the same from shaft (, the letter carrying a loose gear which is in mesh with
one of the gears of shaft A; and a clutch by which said gear is made fast; a crank
connection between the shafts B and C, the crank of the latter being variable in
length and devices in connection with the variable crank and the clutch of shaft C,
whereby the crank is lengthened and the clutch thrown out of gear simultaneously,
or rice versa, substantially as shown and described.
No. 6. The combination with shaft B having a driving gear ; the shaft C
having a loose gear p and a clutch by which said gear is made fast; and the cam-
cylinder and gearing to drive the same from shaft C; of an intermediate gear
between the gears and p, for imparting motion from one to the other; a crank
connection between the shafts bc, the crank of the latter being variable in length;
and devices in connection with the said clutch and the variable crank whereby the

page_text: crank is lengthened and the clutch thrown out of action, and vice versa, substantially
as shown and described.
No. 7. The combination with the cam-cylinder of two shafts; gearing whereby
the cam-cylinder is driven from one of the said shafts; a crank of fixed length on
one of said shafts and a crank of variable length on the other; a connection between
the two cranks; a clutch on one of said shafts; a connection between said clutch
and the other of said shafts, whereby when the clutch is in engagement the two
shafts will be caused to move in unison; and a connection between the said variable
crank and the clutch, whereby the effective length of the variable crank is changed,
and simultaneously therewith the clutch is made fast to, or disengaged from, its
shaft, substantially as shown and described.
No. 8. The combination with the cam-cylinder, of two shafts; gearing whereby
the cam-cylinder is driven from one of said shafts; a crank of fixed length on one
of said shafts and a crank of variable length on the other; a connection between
the two cranks; a clutch on one of said shafts; a connection between said clutch and
the other of said shafts; and means for making said clutch fast to, or disengaging it
from, its shaft and for changing the effective length of said variable crank, sub-
stantially as shown and described.
No. 9. The combination with the knitting devices, and controlling mechanism for
effecting the changes from continuous rotary knitting to reciprocating knitting, and
back again, and determining the action of the knitting devices before and after such
changes; of two rotating shafts, one of which is in connection with such controlling
mechanism; a fixed crank arm on the other of said shafts, the first shaft having
thereon a loose crank arm and a fixed ratchet; a pawl carried by said loose crank arm
in engagement with said ratchet; lugs on the said crank arms projecting towards
and into the paths of rotation of each other; and a device for moving one of said
lugs out of the path of rotation of the other as the two arms are moving in unison,
substantially as shown and described.
No. 10. The combination with the knitting devices, and controlling mechanism for
effecting the changes from continuous rotary knitting to reciprocating knitting and
back again, and determining the action of the knitting devices before and after
such changes; of two rotating shafts, one of which is in connection with such
controlling mechanism; a fixed crank arm on the other of said shafts, the first shaft
having thereon a loose crank arm and two fixed ratchet wheels, of which one is
reversed with respect to the other; a pawl on said loose arm in engagement with
one of said ratchet wheels; a retaining hook on said arm in engagement with the
other ratchet wheel; lugs on the said crank arms projecting towards and into the
paths of rotation of each other; a device for moving one of said lugs out of the path
of rotation of the other as the two arms are moving in unison; and a tripping device
for tripping the retaining hook to permit a backward movement of the loose crank
arm, as shown and described.
No. 11. The combination with the knitting devices, and controlling mechanism
for determining the action thereof; of two rotating shafts in axial alignment, one of
which is connected with such controlling mechanism and each having a crank with
lug which projects towards and into the path of rotation of the other, the lug on
one of said arms being movable; and a tripping device for moving said movable
lug to disengage it from the lug of the opposite arm at a pre-determined point
substantially as shown and described.
al
No. 12. The combination with the needles; needle-cylinder; cam-cylinder; a main
shaft means for imparting to the cam-cylinder from the main shaft either a
continuous rotary motion or a reciprocating motion, as desired means for placing,
en masse, a portion of the needles into or out of operative position, pattern devices
for successively throwing out of, and into, operation a portion of the remaining
needles, to effect narrowing and widening, and devices for changing the motion of
the cam cylinder from continuous rotary motion to reciprocating motion, and
vice versa; of the shaft D; means whereby an intermittent motion is communicated
to said shaft D from shaft A; and connections whereby said shaft D throws into

page_text: and out of operation the motion changing devices and the said means for placing
the needles, en masse, into or out of operative position, substantially as shown and
described.
No. 13. The combination with the needles; needle-cylinder; cam-cylinder;
means for giving to said cam-cylinder either a continuous rotary motion or a
reciprocating motion; means for placing, en masse, a portion of the needles in or
out of operative position; pattern devices for successively throwing out of, and into,
operation a portion of the remaining needles for narrowing and widening; and
devices for changing the motion of the cam-cylinder from continuous rotary motion
to reciprocating motion, and vice versa; of the shaft D; and connections whereby
said shaft D throws into and out of operation the motion changing devices, the
pattern devices, and the means for placing a portion of the needles, en masse, in or
out of operative position, substantially as shown and described.
No. 14. The combination with the needles; needle-cylinder; cam-cylinder;
devices for driving said cam-cylinder, embracing a crank of variable radius,
whereby either a continuous rotary motion or a reciprocating motion may be
communicated to the cam-cylinder, according to the adjustment of the crank; means
for placing in inoperative position a portion of the needles, en masse, devices
whereby the adjustinent of the variable crank may be effected; and a yarn stop-off
for gripping the yarn after the passage of the yarn-guide by the last of the needles
in operation during each of the movements of the cam-cylinder while reciprocating;
shaft D and connections whereby a movement of said shaft will effect the
adjustment of the variable crank and change the motion of the cam-cylinder from
continuous rotary to reciprocating, cause the needle raising means to elevate the
needles in connection therewith, and throw into operation the yarn stop-off, sub-
stantially as shown and described.
of
No. 15. The combination with the needles; needle-cylinder; cam-cylinder;
devices for driving said cam-cylinder, embracing a crank of variable radius, whereby
either a continuous rotary motion or a reciprocating rotary motion may be
communicated to the cam-cylinder, according to the adjustment of the crank; means
for placing in operative position, en masse, a portion of the needles that have been
raised; devices whereby the adjustment of the variable crank may be effected; a
yarn stop-off for gripping the yarn after the passage of the yarn guide by the last of
the needles in operation during each of the movements of the cam-cylinder while
reciprocating; of a shaft D and connections whereby a movement of said shaft will
effect the adjustment of the variable crank and change the motion of the cam-cylinder
from rotary reciprocating to continuous rotary cause the needle lowering means to
lower the needles in connection therewith, and throw out of operation the yarn stop-
off, substantially as shown and described.
No. 16. The combination with the needles; needle-cylinder; cam-cylinder;
devices for driving said cam-cylinder, embracing a crank of variable radius, whereby
either a continuous rotary motion or a reciprocating rotary motion may be com-
municated to the cam-cylinder, according to the adjustment of the crank; means for
placing into and out of operative position a portion of the needles, en masse, levices
whereby the adjustment of the variable crank may be effected; a yarn stop-off for
gripping the yarn after the passage of the yarn-guide by the last of the needles in
operation during each of the movements of the cam-cylinder while reciprocating; of
a shaft D and connections whereby a movement of said shaft will effect the
adjustment of the variable crank and change the motion of the cam-cylinder from
continuous rotary motion to reciprocating rotary motion, or vice versa, cause the
needle raising and lowering means to raise or lower the needles in connection
therewith, and into or out of operation the yarn stop-off, substantially as shown and
described.
No. 17. The combination with the jack-holder, and with the jacks and needles
controlled thereby; of an intermittently rotating or oscillating shaft; and an
eccentric thereon; and a connection between the said eccentric and jack-holder,
whereby the needles controlled by said jack-holder are raised out of, or lowered
D

page_text: into, operative position by a partial rotation of said shaft, substantially as shown and
described.
No. 15. The combination with the needle cylinder and the needles; the jacks k;
and mechanisins for operating the same; and with the main power shaft A; of the
shaft K, carrying actuating cams; an escapement wheel driving the said shaft ; and
escapement lever; a pawl and ratchet mechanism; spring connections intermediate
the said ratchet and escapement wheel; and connections intermediate the said
shaft A; and said pawl and escapement lever, whereby reciprocating motion is
imparted to the said pawl and slide, substantially as described.
No. 19. The combination with the needle-cylinder, of two eccentrics either of
which may be brought into action to raise and lower the cylinder during each
revolution or forward and backward reciprocation of such cam; a link; the driving
rods of said eccentrics connected to opposite ends of said link; a sliding connection
between said link and cylinder; and a cam co and connections intermediate said
link and cam for reciprocating said link, whereby the times of the upward and
downward movements of the cylinder may be changed and the limits of its recipro-
cation raised or lowered without effecting the stroke of said cylinder, substantially as
described.
No. 20. The combination with the vertically reciprocating web-holder, and with
the oscillating or intermittently rotating shaft provided with a cam v of
intermediate connections whereby the web-holder is raised out of, and lowered into,
operative position by an oscillation or semi-rotation of shaft D, substantially as shown
and described.
No. 21. The cam-cylinder provided with the fixed upper and lower needle-actuating
cams, and having the movable switch cams b, c, applied thereto; in combination
with the angular gear, having a rigid connection with the switch-cams 6, c¹, the
said gear and switeb-cams moving together to change the cam-path; and a thread-
guide connected with the annular gear, or with the said switch cams, so as to
have an independent motion relatively to cam-cylinder, substantially as shown and
described.
No. 22. The combination with the cam-cylinder, and the switch-cams, and their
rigidly attached yoke, the yoke being so connected as to have a slight independent
movement relatively to the cam-cylinder, of a thread guide attached to the yoke,
substantially as shown and described.
;
No. 23. The combination with the needle-cylinder and the needles; the jacks
the cam bars, and devices for operating the jacks from said cam bars; of the shaft K
with helical cams; an escapement wheel keyed to said shaft; a pawl and ratchet
mechanism; and intermediate spring connections between the ratchet and escape-
ment wheel; an oscillating shaft K, having operative connection with the pawl-
lever and with the fork of the escapement wheel, substantially as shown and
described.
No. 24. The combination with the needle-cylinder and needles, of a series of jacks
for raising the needles out of, and lowering them into, action; a series of compound
levers connected with the jacks to operate the latter; a reciprocating cam; and
connections between said cam and levers; a helical spring-actuated can to move the
said reciprocating cam; and an escapement to control the helical cam, substantially
as and for the purpose described.
No. 25. The combination with the needle-cylinder and needles, of a series of jacks
for raising and lowering the needles; a series of compound levers connected with the
jacks to operate the latter; and a reciprocating cam, and connections between said
cam and levers, substantially as, and for the purpose described.
No. 26. The combination with the cam and needle-cylinders, and with the needles
and jacks; of levers for moving the jacks and needles; reciprocating cam bars for
producing the required movement of the levers at pre-determined times; and cams
for reciprocating said cam-bars, substantially as shown and described.
No. 27. The combination with the cam and needle cylinder, and with the needles
and jacks; of levers for moving the jacks and needles; reciprocating cam-bars for

page_text: producing the required movements of the levers at pre-determined times; rotating
spring-pressed cams for reciprocating said cam-bars, and an escapement to control
the action of the cams.
No. 28. The combination with a needle-cylinder, of means for raising said cylinder
and lowering the same again during the knitting of each course in either continuous
circular knitting or reciprocating knitting, for the purpose of shaping the fabric by
varying the lengths of the loops in the different parts of a course, substantially as
shown and described.
No. 29. The combination with a needle cylinder, of an eccentric; means for
rotating the same; and connections intermediate said eccentric and cylinder, whereby
the latter is raised and lowered during the knitting of each course, for the purpose of
shaping the fabric by varying the lengths of the loops in the different parts of a
course, substantially as shown and described.
No. 30. The combination with a needle-cylinder, of an eccentric; means for
rotating the same; and connections intermediate said eccentric and cylinder, whereby
the latter is raised and lowered during the knitting of each course, for the purpose
of shaping the fabric by varying the lengths of the loops in the different parts of a
course, said connections being adjustable substantially as described, whereby the
average length of the loops may be varied, as described.
No. 31. The combination with a needle cylinder, of an eccentric; means for
rotating the same and connections intermediate the eccentric and the cylinder,
whereby the latter is raised and lowered during the knitting of each course for the
purpose of shaping the fabric by varying the lengths of the loops in the different
parts of a course, said connections embracing a rod adjustable in the direction
of its length, whereby the average length of the loops may be varied as
described.
No. 32. The combination with a needle cylinder, of an eccentric; means for
rotating the same; and connections intermediate the eccentric and the cylinder,
whereby the latter is raised and lowered during the knitting of each course, for the
purpose of shaping the fabric by varying the lengths of the loops in the different
parts of a course, said connections embracing a rod o made in two parts and con-
nected by a right and left hand coupling; and means for rotating said coupling
to lengthen and shorten the rod o'; substantially as shown and described.
No. 33. The combination with a needle cylinder, of an eccentric; means for
rotating the same, connections intermediate the eccentric and the cylinder whereby
the latter is raised and lowered during the knitting of each course, for the purpose of
shaping the fabric by varying the lengths of the loops in the different parts of a
course, said connections embracing a rod o made in two parts and connected by a
right and left threaded coupling; a lever for turning said coupling to lengthen and
shorten the rod o'; and a cam for operating said lever, substantially as shown and
described.
No. 34. The combination with the needle-cylinder, of two oppositely arranged
eccentrics ; the rods s³, t; the link p³, to the opposite ends of which said rods
are connected, and connections intermediate said link and the cylinder, for raising
and lowering the latter, having a sliding connection with the link, substantially as
shown and described.
No. 35. The yarn stop-off for knitting machines herein described, consisting of two
clamping plates, means for imparting to one of said plates a constant reciprocating
stroke; a spring seat for the other of said plates and means whereby a reciprocating
movement is imparted to the spring seat in order that the thread may be clamped and
released at different points in the reciprocation of the two plates, substantially as
shown and described.
No. 36. The yarn stop-off for knitting machines herein described, consisting of two
clamping plates; means for imparting to one of said plates a constant reciprocating
stroke; and means whereby the other of said plates is changed in position in order
that the thread may be clamped at different points in the reciprocation of the two
plates, substantially as shown and described.

page_text: No. 37. The yarn stop-off for knitting machines herein shown and described,
consisting of a reciprocating rod 16; a clamping plate mounted thereon; and means
for imparting reciprocating motion to said rod, a second clamping plate; a screw
shaft 26, with which the latter plate is connected ; an eccentric ml; and
connections between the screw shaft and eccentric; substantially as shown and
described.
No. 38. The combination with the yarn stop-off, consisting of fixed and movable
plates, and an eccentric for reciprocating the movable plate; of a movable link con--
nection between the said eccentric and plates, whereby the reciprocations of the latter
may be varied, and whereby the yarn stop-off may be thrown entirely out of action,
substantially as shown and described.
No. 39. The combination with the fixed and movable plates of the stop-off and the
rod 16, of an eccentric for reciprocating said rod, and an intermediate link 12
pivotally joined at one end to the rod of the said eccentric; a vertically movable
rod 13, connected at its upper end with the opposite end of the link and at its lower
end with an eccentric 8; the change shaft D with its eccentric ³, and crank
connections between the eccentrics 8, 3, substantially as shown and described.
No. 40. The combination with the yarn stop-off, consisting of fixed and movable
clamping plates, the latter being carried by a reciprocating rod 16; and an eccentric
for reciprocating said rod, of a link 12, pivotally joined at one end to the eccentric
rod and forming a connection between the latter and the rod 16, and a vertically
movable rod 13. connected with the opposite end of said link, to shift the latter,
substantially as shown and described.
No. 41. A thread inserting mechanism, consisting essentially of two relatively
fixed plates 50, 51 and an intermediate clamping plate 52, capable of being moved
into contact with either of the plates 50, 51, to claup and stop off either of two
threads and which, when standing in a central position, allows both threads to be fed
forward together, and devices for shifting said movable plate and for holding it in a
central position substantially as shown and described.
No. 42. The thread inserting mechanism consisting of plates 50, 51 fixed relatively
to each other; a movable plate 52 between the same; a screw for shifting said
movable plate towards either of the fixed plates; and a cam and intermediate con-
nections for imparting rotary movement to said screw.
No. 43. A thread inserting device, comprising two relatively fixed plates 50, 51,
and an intermediate clamping pate 52, capable of being moved into contact with
either of the plates 50, 51, to clanıp either of two threads, and a cam and intermediate
connections, substantially as, and for the purpose described.
No. 44. The thread inserting mechanism, consisting of plates 50, 51, fixed relatively
to each other; a movable plate 52 between the same and capable of being moved
into contact with either; operating devices for said plate; a thread separator and
cutter 55 56, and means substantially as described for moving the same between the
threads and for placing the cutter in and out of position for acting upon one of the
threads.
No. 45. The parting bar and separator, consisting of a vibrating bar pivoted to a
rigid frame, and a vibrating knife pivotally attached to said bar; a cam and inter-
mediate devices for vibrating said bar; and a cam for vibrating the knife, substantially
as shown and described.
No. 46. In a thread changing inechanism the combination of a series of clamping
plates adapted to clamp and stop-off either of two threads which are being fed to
the needles; a pivoted separating bar; and severing knife pivoted on said bar cams;
for operating the separating bar and severing knife; and connecting devices
intermediate the separating bar and its cam, substantially as shown and described.
No. 47. A thread inserting device, comprising two relatively fixed plates 50, 51
and an intermediate clamping plate, capable of being moved into contact with either
of the plates 50, 51, to clamp and stop off either of two threads and which, in a
central position, will allow both threads to be fed forward; and a cam and
intermediate connections to operate said clamping plate; in combination with a

page_text: pivoted separating bar carrying a pivoted knife to sever the thread a cam; to vibrate
said knife; and a cam and intermediate devices for operating said separating bar,
substantially as shown and described.
No. 48. The combination with the clamping plates 50 51 52, and the cam and
intermediate connections for operating the plate 52; of a pivoted vertically vibrating
separating bar; means for operating said bars; a double-edged knife, pivotally joined
to said bar, and shafts which normally are out of axial alignment with each other,
cach, at adjacent ends, being provided with a crank carrying a lug, the lug of each
crank projecting into the path of rotation of the lug of the other; and means whereby
the axis of one of said shafts is moved at desired intervals from one side to the other
of the axis of the other shaft.
No. 49. The combination with thread changing devices and their actuating
means, of two shafts, one of which is in operative connection with the said actuating
means the axes of the said shafts being in parallel lines but normally out of axial
alignment, each shaft being provided with a crank, and each crank with a pin which
projects into the plane of rotation of the pin of the other of said cranks, one of said
shafts being movable into and out of alignment with the other, and a cam or pattern
chain for moving said shaft, substantially as shown and described.
No. 50. The combination with the thread changing devices of two shafts in axial
alignment, one connected with the source of power and the other with the said
thread-changing devices, for actuating the latter; an intermediate shaft supported in
movable bearings so as to be capable of movement into and out of axial alignment
with the first mentioned shaft; à sliding crank connection with one of said shafts,
and with the other an intermittent connection which consists of a crank on each
shaft, and on each crank pin which projects into the plane of rotation of the other
pin, substantially as shown and described."
No. 51. The combination with thread clamping plates, and devices for operating
the same, as described, of two shafts which normally are out of axial alignment
with each other, each, at adjacent ends, being provided with a crank carrying a lug,
the lug of each crank projecting into the path of rotation of the lug of the other
and means whereby the axis of one of said shafts is moved at desired intervals from
one side to the other of the axis of the other shaft.
;
No. 52. The combination with thread clamping plates, and devices for operating
the same, as described, of two shafts и,
and whose axis are parallel but normally
out of alignment with each other, each, at adjacent ends, being provided with a
crank carrying a lug, the lug of each crank projecting into the path of rotation of
the other, one of said cranks being movable, and means whereby said movable shaft
is moved into and out of axial alignment with the other of said shafts, whereby a
continuous rotation of one shaft will impart an intermittent rotation to the other, sub-
stantially as shown and described.
Dated this 97th day of August. LAANI
ADOUST LOAN
JENSEN & SON,
77, Chancery Lane, London, W.C., Patent Agents.