Improvements in Knitting Machines.
Year: 1896

page_text: Date of Application, 21st Jan., 1896-Accepted, 6th June, 1896
COMPLETE SPECIFICATION.
Improvements in Knitting Machines.
I, EDWIN RUBY BRANSON, of 2714 Montgomery Avenue, in the City of
Philadelphia, in the County of Philadelphia, in the State of Pennsylvania, United
States of America, Manufacturer, do hereby declare the nature of this invention
and in what manner the same is to be performed, to be particularly described
and ascertained in and by the following statement:-
Prior to my present invention, knitting machines of the class known as "circular"
have been provided with mechanism for simultaneously lifting or throwing out of
gear with their actuating slots in the cam cylinder, a prescribed number-generally
one-half-of the needles preparatory to "turning" the heel or toe of a stocking;
during which operation, the needles thus withdrawn retain their loops passively,
while those not so withdrawn are actuated and knit as usual; the cam and needle
cylinders being, however, at such times, reciprocated, instead of revolving con-
tinuously in relation to each other as they ordinarily do when engaged in producing
the tubular web which constitutes the leg and foot of the fabric. These machines
have, moreover, been provided with mechanisms by means of which the terminal
needles of the row or scries of those that do not remain in action, during the relative
reciprocations of the needle and cam cylinders when "turning," are alternately and
individually put out of operation, in order to effect the goring or narrowing of the
web; also with other mechanisms by means of which the number of needles finally
remaining in action can be augmented one by one, as it were, conversely bringing
back into gear the terminal needles of the row or series which have been, as above
mentioned, put out of gear; this being in order to "widen" the fabric.
Now the chief object of my invention is, in rendering the whole operation of the
machine automatic, to establish a more positive connection and interaction of the
parts, not only between the primary parts constituting the knitting machine proper,
but also between them and those which may be designated the secondary,
,,parts,
viz. the "former" or pattern wheels and the "turning," "narrowing and
"widening" ancillary attachments; so that the whole may be united into a well
constructed, light running machine. Subsidiary to this, it is my object to adapt
and provide not only special and suitable mechanism for carrying out the individual
features of this improved machine, but also to combine and mount the moving parts
in a frame calculated to give an orderly and simple distribution to these various
component devices; together with improved mechanism for controlling their
connection with the motive power.
In addition, my further objects are, in carrying these improvements into practice
to devise and construct an improved mechanism for reciprocating the moving
cylinder, and preferably so as to impart a varying angular velocity to said cylinder,
viz. a slow movement prior to and just after each reverse; to combine the same
with an improved clutch mechanism for controlling said circular reciprocations of
the moving cylinder, whereby it shall be started or stopped without unnecessary
lash or lost motion, and always from a constant or fixed point in the relative
movements of the main driving parts as they describe their function; to devise and
construct an improved controlling connection between the former wheel train and
the driving mechanism, so that the whole machine may be normally brought to
rest upon the completion of the prescribed stocking or sock; and also, so that,
during certain periods of rest occurring between the continuous and the recipro-
cating circular motions of the cylinders in the "head" of the machine, said former
wheels and secondary cam train shall be brought automatically into operation; to

page_text: provide suitable mechanism therefor; and to arrest and disconnect the action of
the same when the several ancillary mechanisms having been put in train, they
are, in their respective turns, to be withdrawn therefrom preparatory to the
machine's resuming its ordinary, continuous, tubular knitting of the leg or foot;
as well as in combining and connecting with the primary parts of the machine
those mechanisms by which the secondary operation of turning, narrowing and
widening are accomplished in such a way as to adapt them to perform and repeat
in substantially the same way and order their several functions when knitting a
foot and toe respectively, as they originally performed them in the substantially
similar duty of knitting the leg and heel; to provide improved mechanisms for
carrying the same into practical effect; to construct the head of the machine in
such a way that while the needle cylinder is normally fixed and secured to a chuck
or seat, it may readily be detached, and, if need be, replaced by one adapted for
finer or coarser work by having a greater or lesser number of needles, &c., and to
devise and construct suitable mechanism therefor.
Lastly, my object is also in setting forth the Specification for the above as a
whole, to, at the same time, describe and secure certain novel improvements among
said several devices and mechanism which while they may be taken as complete in
themselves, are yet so far ancillary in making the specific machine described
automatic, that they may seem have lost their distinctive characters as novel
and useful features in other forms of construction were it not for this mention of
my purpose of securing them in that aspect, and the subsequent claims which aim
at that end.
Circular knitting machines of this class (in which a hollow cam-cylinder
"jackets" a concentrically-enveloped needle cylinder, having the above described
alternate, continuous and reciprocating, circular motious whereby the knitting
needles are, each in its own guide slot, reciprocated vertically by the engagement
of their heels or off-set lower ends in the slots of the cam cylinder) being well
understood, only as much of one of them provided with my above mentioned
improved devices is set forth and shown in the following description and drawings
as serves to describe, distinguish and connect therewith my invention. And, in the
light of that qualification, reference now being had to said accompanying drawings,
forming a part of this Specification, in which similar letters of reference indicate
corresponding parts throughout all the figures, they will be found to illustrate the
mechanism by which I have, in practice, attained the above recited objects, with
the most useful results.
Figure 1 is an elevation of what I designate the back of a circular knitting
machine provided with my above mentioned improvements throughout. In this
view, a portion of one of the legs (X) of the stand is removed in order to show the
structural relation of the reversing gears clutch, of which hereafter.
Figure 1 is a detail view showing a modification of the driving mechanism in
similar elevation.
Figure 2 is an elevation of the driving end of said machine; upon which there
is carried the cylinder reciprocating mechanism. It shows the parts external to
the adjacent leg (X) of the stand, as well as an end elevation of the secondary, or
external cam train and former wheels; together with the preferred relative
distribution from this point of view of these two mechanisms not only to each
other, but also to the vertical "head" of the knitting machine. For the sake of
clearness however, the driving gear of the secondary cam train and the main spur
gear of the continuous circular-cylinder-rotating device are chiefly given in broken
lines: a portion of the circular segment rack (U) with its intermeshing pinion (U¹)
are likewise thus represented; also oue of the cams (E) with its bent actuating
rock arm (el), other parts, however, are not shown as they, for the most part, lie
back of, coincide in outline with, or otherwise would tend to confuse those already
represented.
Figure 2 is a detail view showing a modification of the mechanism for producing
reciprocatory circular motion.

page_text: Figure 3 is a plan view on a larger scale of the machine without indicating the
legs of its stand. It shows the preferred distribution of the table, cylinder head,
secondary cam train, and reciprocating mechanism; this figure also, the principal
parts, underlying the table (T) are indicated in broken lines, the more minute detail
being reserved for other figures and descriptive matter.
Figure 4 is a rear elevation partly in section of the cam, cam-lever, and clutch
mechanism governing the above mentioned relative movements and temporary
arrests of the needle cylinder's rotation.
Figure 4 is a detail view of a feature shown in Figure 4.
Figure 5 represents a partly sectional end view of a portion of the structure
shown in Figure 4; also showing a convenient method of attaching locking pawls
for opposing the ratchet wheels W W' shown in Figures 2, 7 and 8.
Figure 5A is an isometric view of the clutch, discs, and "head" locking
device.
Figure 6 shows a detail of a portion of the cam and slide rod with thrusting
lever for said clutch, as seen in plan.
Figures 7 and 8 are fragmentary views of the details of the devices for
actuating the secondary cam train and former-wheels, in end and rear elevation
respectively.
Figure 7 is a perspective view, shown fragmentary, of a modification of the
secondary cam-train.
Figure 84 is a side elevation on a larger scale of one of the wheels of the modified
cam train shown in Figure 74.
Figure 9 is a vertical sectional elevation of the cylinder head and mitre gear
actuating mechanism taken on the central line indicated by the dot and dash lines
in Figures 10 and 11.
Figure 94 shows one of my detaching wedge lugs, of which hereafter.
Figure 10 is a plan view of the bottom of the needle cylinder. This view in
connection with Figure 9 is especially adapted to show the spring stud device by
which I render the needle cylinders not only normally securely fixed to their seats,
but also on occasion, readily detachable as well as interchangeable.
Figure 11 is a plan view of the top of the cam cylinder, showing my improved
needle lifting rest, and compact automatically-operated cam-train, for which
purpose the needle depressor attachment is removed.
Figures 12 and 13 are vertical sectional elevations of the two halves of said cam
cylinder, taken on the dot and dash line of Figure 11.
Figure 14 is a side elevation of the cam cylinder showing the external detail of
the mechanism for lifting out of gear a number of needles simultaneously preparatory
to "turning" as aforesaid.
Figures 15 and 16 are respectively a side elevation and a plan of a fragmentary
detail of the mechanism for lifting out of gear individual needles for "narrowing.'
Figures 17 and 18 are, in relation to the cam cylinder, respectively, external
and internal views of the mechanism for changing the length of a stroke of the
needles in their passage through the cam train, forming an auxiliary tension
device.
Figure 19 is a side elevation of the mechanism for throwing a large number of
groups of the needles simultaneously and automatically back into gear preparatory
to the resumption of continuous circular knitting.
Figures 20 and 21 are fragments respectively, external and internal, of the cam
cylinder provided with the mechanism for returning individual needles at each
reciprocation of the needle cylinder during the operation of widening, Figure 20 also,
shows, as do Figures 14 to 19 (saving Figure 18) inclusive, the cam wheels and
cam levers of the secondary or external cam train which throw their irrespective
mechanisms, at designated intervals, in or out of gear.
Figure 20 is an isometric projection of a portion of the structure shown
in Figures 20-21; having chief details off-set, the point of view being
approximately opposite the point of view from which Figure 21 was taken.

page_text: Figure 20 is a similar view of one of the depressor tumblers with the spring g
and p therefor.
Figure 22 shows a detail of the cam and rider forming automatic belt shipper-
bar actuating devices.
Figure 23 is a representation of a vertical side elevation of the internal structure
of the cam area of the cam cylinder developed upon a plan; showing details of the
cams; and indicating in the heavy dot and dash line, the normal path of the
needles heels when passing from left to right through the cam system as shown.
Broken lines indicate certain movements described and positions occupied by the
needle lifter levers and the swinging nose of the central depressing cam when
knitting continuous tubular web.
The dot and dash outlines designated no, no, no are positions assumed by the
tumblers n n when engaged in narrowing or "goring" the web as hereinafter
described.
Figure 24 is a plan view of said area of the cam cylinder, showing detail.
Figure 24 shows the form of needle best adapted to work in conjunction with
the devices herein described and illustrated.
Figure 25 is a representation of a modified, continuous tubular stocking fabric
which the machine herein described can be adapted to produce.
Figure 26 shows an individual stocking blank when severed and shaped from
such continuous fabric as is shown in Figure 25.
In the drawings, the legs X X', banger X', table T, brackets or journal
housings OO, and cross bar O', together with the pawl bearing lug N', constitute
the frame proper of the machine; the whole being rigidly secured together and
carrying, in cylindrical bearings, xa, 3 of the leg X, and hanger X², parallel
cylindrical shafts S S', of which S being the power driving shaft, is preferably
fitted, within its bearings, with a fast belt pulley W (provided near its hub with a
projection tappet or stud w), a corresponding but "loose" pulley W1, and fast spur
wheel V; and, outside of bearing a, there is secured to this shaft, in the construction
shown, a crank s¹, provided with a crank pin p, pivotally connecting therewith one
end of a connecting rod s, the other or outer end of which is provided with a
knuckles, and pivotally connected, by a pin p2, with an upright rock arm R. The
lower end of this arm is also pivotally connected near the foot of the leg X by a
pin p', passing through its eye r, and preferably kept clear of its stand by a
washer (see Figure 1); while the upper end of rock arm R extending above the
summit of the circle described by the crank s ends in another cylindrical eye
through which a pin p³ passes and serves, by means of the knuckle, to connect it
pivotally with a drag link r; the other end of said link being pivoted by a pin p
to a circular segmental rack U (preferably one of the general form and contour
shown in Figures 1 and 2). This rack is likewise pivoted upon a trunnion or
boss formed on the outside of the leg X by a pintle P so that the teeth of the
rack, which are, as indicated Figure 1, cut upon the periphery of its arc, gear with
a pinion U of which hereafter. The rack U like the rock arm R, together with
all the moving parts immediately connected therewith is adapted to vibrate or
swing in vertical planes; that is to say, substantially at right angles to the axles
of the driving shaft S S'. These parts may be dispensed with, and a slider crank
substituted, as in the mechanism shown in Figure 24, wherein U has a rigid
middle member provided with a radial slot in which the crank wrist of the crank s¹
is engaged and operates to vibrate said rack about the pivot P and drive the
pinion U with a reciprocatory circular motion. This is a modification, however,
which involves a sacrifice of the even angular motions of the former; being, as is
well known, productive of a reciprocatory motion swifter in one direction than in
the other. Otherwise it is equally practical in combination with the remaining
mechanism.
The shaft S' is provided between its bearings with a loose pinion wheel Vi
intermeshing with the spur-wheel V fixed to the shaft S; between said pinion and
the bearing a, it carries a face plate or disc V2, divided into two flanges of different

page_text: diameters by a peripheral annular groove; said disc being provided with a slot
or keyway lengthwise of and in its eye whereby the disc, engaging on a suitable
keys, either integral with or driven into a seat in the shaft S' as shown.
in Figures 4 and 5, is prevented from revolving independently of, but remains
free to move end wise along said shaft, between the pinion Vi and bearing 4,
motion of this latter sort being occasionally communicated to V' by means of the
thrusts offered it through the straddling leg », of a U-shaped slider piece U2, which
is adapted to ride loosely in said groove v2.
The shaft X is equipped preferably outside the bearing X with a substantially
similar disc Us, provided with a corresponding groove and a key-way for a
similar key fixed in shaft S', the adjacent. pinion wheel U like its fellow V₁, is.
secured from motions end wise of the shaft S', upon which it is carried either by
means of its respective keys (s) end and a plain collar; or preferably by such a-
collar as either $20 or 30 respectively (see outlines thereof in Figure 5, and more
fully in Figure 4); said collars are fixed to the shaft S₁, and provided with
flanges and 3, respectively, to each of which are secured by screws S7 and
steady pins S two or more circular segmental flange clips S of the character
best seen in Figure 44. These clips being adapted to engage in annular grooves
formed in the hubs of the pinion wheels U₁, V', serve to maintain them loosely as.
regards radial motion, as well as in their working positions without rubbing against
the ends of their keys.
The inner sides of said pinion wheels are further provided each with a hole u10, 10,
adapted to engage and register with studs P3 P3, projecting equal distances from
the adjoining sides of their respective slider discs. One of these discs is also formed
with a slot or gap J, in the rim of the flange which carries said stud; the width
of said flange being equal to the projection of said stud; and adapted to work in
connection therewith, there is secured to the bearing a fixed finger J', so formed
and located as to admit of the disc which has this gap to pass its inwardly pointing
finger tip j, which is the converse male part of said gap in form and dimensions,
laterally along the shaft S', only when they two, viz.: the gap J and finger point j,
are in radial alignment.
The slider U has a suitable hole represented in dotted lines in Figure 4, through
its connecting body, which save for the spiral springs Q Q', would permit it to
freely slide on a bar S which, lying with its axis parallel to the shafts S S', is
itself also adapted to slide end wise through suitable eyes formed in lugs t t', bolted
to the under side of the table T. Said slide bar S is provided with certain
abutments as the washers and pins po pl p22, shown in Figure 4; whereon
the spiral springs QQ and Q, with which it is helically wrapped in part, react ;.
it is also further provided with another abutment preferably made adjustable, as
by the jam nuts t t and washer 8 (Figure 6), for the purpose of opposing the
adjoining horizontally swinging end of a cam lever composed of two diverging
arms, Aa; (see Figure 6); the swinging end of the longer of which being
preferably crotched and provided with discs a' a" adapted to embrace the shaft S
(as shown in Figures 5 and 6) permits this lever to lie practically in the same
general plane as the axis of the slide rod S*; the whole lever A¹ a, being pivotally
connected to the table T (see Figure 3) on a downwardly pointing pivot pin P. The
pivot P is conveniently formed, as shown in Figure 5, with a main cylindrical
shank terminating at its lower extremity in a flat flange or head which serves as a
support to the lower side of said lever's eye; after passing through which said
pivot is enveloped freely in a tubular washer or sleeve preaching to the adjoining
under surface of the table T; through which the pivot P³ then passes with_a
reduced diameter of stem, and its shoulder, banking against bottom of table T,
establishes the relative distance therefrom of the pivot's above mentioned head.
And, taking advantage of a protrusion of said stem's upper end, I secure here to
the upper side of the table T, by means of a screw thread and nut on said pivot, as
shown in Figure 5, a hinge bearing lug piece N adapted to carry pawls P Po
which, extending outwards beyond the back of table T engage upon and lock

page_text: the ratchet wheels W W' against accidental back slidings; (see Figure 2).
Thence, viz. from Ps the shorter arm a of this lever passes and lies across in
rubbing contact with the face of the secondary cam wheel A; in which position
the spring Q (being normally under compression) is adapted to maintain it. Thus
these two thrusting agents in conjunction with the above described gap J in the
disc V2, and the finger J' bolted to the side of the bearing as above described
(and shown in Figure 5A) define the position of the stud bearing clutch discs V2 Us
in relation to the pinion wheels Vi U₁ and their respective driving spur gears
as is hereinafter more fully set forth in the narration of their mode of operation.
It will be merely pointed out at this stage that as the reciprocating rack U and
the revolving spur gear V₁ are concurrently in motion during all operations of the
machine, the connections "in" and "out of gear" between them and cylinder
shaft S', which this clutch mechanism effects, take place when the pinion about to
be engaged is already moving in the direction in which the cylinder driving
shaft S is to be itself then driven in. By this means lost motion is avoided
between the intermeshing gear teeth of the actuating spurs and pinions at the
moment of beginning their actuating duty.
The spur wheel V and the reciprocating rack U serve when one or the other is
connected through the gear wheels V U on the shaft S' to that shaft by the
clutch, to impart to the shaft S' corresponding motions, but as great variety of
mechanical equivalents may be substituted for a spur wheel or reciprocating rack,
and also as many suitable clutches could be substituted for the one specifically
shown, I do not wish myself to be considered as limiting myself to the particular
form of connections here shown.
Said cam wheel A is fixed to a shaft S2 carried in cylindrical bearings o³ 0%
(see Figure 3) of dependent arms projecting from and forming parts of the
brackets OO respectively. The axis of this shaft lies parallel to that of
shafts S S', and carries within its bearings, what I have designated the "former"
wheels, or secondary cam train, viz.: the cam wheels B, C, D, E and F. Also
upon a projection of shaft S extending outside the bearing o³, there are fixed the
ratchet wheel W (provided with occasional higher teeth, as W in Figure 7) and
the sliding clutch's cam wheel A. Also, between these a loose or idle ratchet
wheel W', provided likewise with occasional higher teeth, as W; and, journalled
upon a suitable eye, a bent armed pendulous lever to¹ (see Figures 1 and 2) of
which the dependent lower end is adapted to gravitate and rest normally against
the front side of the power shaft S (see Figure 2) as well as within the range of
the above mentioned tappet to; while, above said eye, it extends upwards, and is
provided on its side adjoining the ratchet wheels W W7, with a pin p (Figures 7
and 8). Upon which pin are pivoted pawls P P provided with upwardly
extending lugs, the ends of which being formed oblique, are provided with detents
or notches to wll into one or other of which the hooked edge of a curved plate
spring w is adapted, on occasion to register and engage. Said spring is secured
to a convenient right-angled off-set w in which the oscillating tappet lever w' here
preferably terminates.
In other cylindrical bearings o¹ 02, (see Figures 1, 2 and 3) in the brackets O O
there is journalled parallel to the shaft S2, a rock shaft S³; also in journals o o
paralleling and almost immediately over the former, there is a second rock shaft S;
both of these rock shafts, it is to be noted, lie between the shaft S and the cylinder
head H-L (see Figure 2). Upon these shafts are carried rock arms or levers
adapted to come into contact with and play over and be actuated by the cam
bearing peripheries of the wheels B C D E F as follows, viz.:
(1) A depending arm b', preferably of the form and contour, best observed by
taking Figures 3 and 14 in conjunction, is fixed to and points downward from
shaft S3: an off-set b, in its lower end lies normally in contact with the periphery
of the cam wheel B. Rigidly connected with arm b, by the shaft S³, are two other
inwardly-pointing lever arms 6 6; to the swinging extremities of which is secured
a bridle B loosely girding the opposite exterior (front) wall of the cam cylinder H.

page_text: Said girdle is provided with screws 68 69 which projects not only through it, but
also pass loosely through ports 60 61 in the cam cylinder H, and thence extend
towards and are screwed fast to a detached semi-circular vertically movable needle
sent or rest B2, as clearly shown in Figures 11 and 13. Also upon the periphery
of the wheel B there is formed a cam or buffer 6 preferably of the profile shown
in Figure 14.
(2) Adjoining arm 61 and loosely pivoted upon the rock shaft S³ by a suitable
journal c, arms etc project respectively to the front and rear; of these c is the
heavier, and preferably provided with a friction wheel c, which, being at a proper
place for that purpose, reposes by gravitation, upon the adjoining cam wheel C,
which is provided with peripheral high and low levels C, c7 c, as shown in profile
in Figure 15. Otherwise the outer arm c, of said lever may be kept in contact
with said cam wheel under the constraint of a compressed spiral spring extending
between the upper side of an arm co, and the cross tie rod O', as shown in Figure 1.
The inner extremity of the arm c is provided with a bent whisker c³, the ends of
which after spanning a proper angular distance on the cam cylinder H, enter the
same loosely through suitable port holes cc (Figures 11, 15 and 16) and form
seats as hereinafter described for the "narrowing" needle lifters.
(3) Next to cam wheel C upon shaft S2, there is fixed a cam wheel D having a
depression d in its otherwise unbroken circular periphery, as shown in side elevation.
in Figure 17. Over this, a rock lever loosely pivoted by a suitable eye about the
shaft S³, and composed of arms d' d², likewise lies and plays. Of course the outer
arm d', has substantially similar equipments of friction wheel and either spring or
gravitation means of contact with cam wheel D, as the lever d and cam C, last
mentioned had. But the inner arm d² forks near the wall of the cam cylinder and
passes loosely through the same by opening or ports as shown at d³ d in Figures 17
and 18; the projecting inner ends thereof being provided with down cast stitch
cams N7 N° of which hereafter. And between cams N7 N8 I locate the nose of the
downward pointing "V-cam" N', preferably provided with a swing point or
switch n', as shown in Figures 12 and 23.
(4) Fixed to the shaft S2 is another cam wheel E, provided with a projection or
boss, shown at e (Figure 19) on its otherwise circular periphery; and upon E the
buffer like lower end e of rock arm e', plays. The upper end of said arm is rigidly
secured to the rock shaft S5; from which and ut right angles to its axis, two other
rigidly fixed lever arms e² e project under the upward constraint of spiral springs q
(as shown in Figure 2) and pass inward over the cylinders H and I. The ends of
said arms, which, in plan view, lie as it were, tangentially to the sides of these
cylinders, are united by a thin flat plate e of Figures 3 and 19; preferably of such
an outline and size that it shall, during its vibrations overlie the full number or
more of needles which the sliding rest B2, above mentioned, is calculated to raise
or "lift" as hereinafter described.
(5) A cam wheel F is fixed to the shaft S2 and provided with high and low
levels, the surfaces f³f whereof are simply arcs, described with radii of different
lengths ff, and joined to each other by easy slopes; in contact therewith, and in
manner substantially similar to that of cams C and D with their respective lever
arms, there is another rock arm f; the inner part f, of which, as shown in
Figures 3 and 20, is fashioned into or provided with a fixed curved part the end of
which registers with and engages loosely in a slot f in a backwardly swinging
forked flap piece F' hinged at its lower extremities ho ho, to projections, on the
adjacent exterior rear wall of the can cylinder H. This is preferably so that the
centre of form of this flap F1 is approximately opposite the centre of the cam
system of the cylinder H.
Upon the upper or cross member of flap F, there are carried inwardly projecting
lugs FF; to the flat inner faces of which pivot screws pop support pendulous
needle depressor tumblers F F which, when the flap F is up in contact with the
side of the cam cylinder, hang downward within the same and alternately present
their notched or detent bearing lower extremities in the path of the off-set heels of

page_text: such of the knitting needles as may be elevated out of range of the slots of their
actuating cam system into their non-acting level, to wit, the dot and dash line of
Figure 21. Spring catches for these needle depressor levers are indicated in
Figures 20 and 21, at q g; wherein h also represent raised shelves or seats
fixed to the rim of H, upon which Ff3 repose when retracted.
Again, outside the bearing o, the shaft S extends and carries fixed upon it,
a wheel Z, (Figures 1, 3 and 22) the otherwise continuous even circular face of
which is provided with a projection or stud z, having oblique faces, as shown in
Figure 22; while, between said wheel Z and the hearing o, there is threaded on
the shaft S by an oblong hole so, a flat plate Z¹ provided on its upper part with a
stud projecting at right angles over and resting upon the periphery of said
wheel whereon it rides idly save only, when the same may, in the course of its
revolutions, bring the cam stud z into contact with it as bereinafter described.
The lower extremity of the plate Z is also connected with or formed into, a
crooked depending rod 3, which, passing through a suitable bridle or guide,
is pivoted to a shipper bar Z2. This bar passes horizontally across the legs of the
machine, viz. from X' to X in Figure 1, and is provided with slots, adapted
to allow said shipper bar to slide end wise under the heads and along the stems of
two shoulder screws 2 211, which, passing through these slots are screwed at
suitable intervals into an underlying fixed cross bar Z. Of these slots it is to be
noticed that the one nearest the rod after extending for a distance preferably
about equal to the width of the driving belt, in a straight course parallel to the
axis of said shipper bar, thence extends in a zig-zag having angles 2 2 27 &c.,
forming as it were a capital letter "W" sloping gradually in the direction of the
slot while the other slot 2, is simply an elongated right angled parallelogram
upon which the shipper bar can either slide endwise, as above described, or else,
if swung in a vertical plane, oscillate and pivot.
The shipper bar Z2 is further provided with a downwardly projecting fork 10
adapted to guide the driving belt to the belt wheels W W in the usual way while
to and between the side or tine of said fork nearest leg X there is attached, under
tension, a spiral spring L. The whole is shown in Figure 1 in the position assumed
at the outset of the knitting operation, where the screw 28, being engaged in the
terminal angle of the zig-zag continuations of slot 3, maintains the shipper with
the fork 20 opposite to the fixed or driving belt wheel W despite the sidelong pull
or spring L.
Passing now to the head of the machine itself, Figure 9 shows the method
I prefer to employ in attaching the same to the table T, viz.: by means of two
annular flanges, one H', projecting at right angles to the shell of the cam
cylinder is attached by screws T¹ to the table T; the other H2 passing downward
through a suitable circular hole therein is provided on its lower face with three or
more tapped holes &c., into which screws h' &c., provided with inwardly
projecting clip-pieces h² &c., are screwed and support the annular chuck or cylinder
socket I, so that it may revolve freely in its corresponding annular chamber h³
formed for that purpose in the lower extremity of the cam cylinder H. Said
socket I¹ extending downwards, terminates upon its lowest outer periphery, with a
mitre gear adapted to intermesh with and be driven by the teeth of the mitre
gear carried upon the shaft S¹; internal socket I is chambered out into a right
angled annular chuck seat i, into which the needle cylinder I is adapted to fit
snugly. I lock the needle cylinder in position by means of the following device;
holes are formed radially and preferably, diametrically opposite each other in
the side walls of said seat. I also secure to and near the base of the inner wall
of the needle cylinder I, a curved spring 13, as by the screws indicated at m m
in Figure 9, the ends of said spring extend more than 180° and being of such a
"set" that they may normally press against the adjoining cell of the cylinder I,
are provided with outwardly projecting studs m² m³ which pass freely through
holes registering therewith, and pierce the shell of cylinder I. The length of
the studs m² m³ is such as to allow them, when forced outwards by the spring I³

page_text: through the shell of the needle cylinder I, to project into the holes in the
socket I' with which they also register and normally engage; but from which they
can on occasion be disengaged and withdrawn by means of two downwardly
projecting pull lugs M M. These I preferably make of thin strips of metal
inserted respectively between the adjacent walls of the shell I, and the respective
bearing ends of the curved plate spring I where they are normally maintained,
pushed flat against such wall until such time as they may be drawn further down.
(This "drawing down" it is to be noted, forms no part whatever of the duty of
the machine so far as knitting is concerned, but is only for the purpose of either
putting in a needle cylinder when assembling the machine, or else in order to
change one needle cylinder for another; which, being desired to be done, said lugs
are pulled down by hand until their involuted upper ends, acting as wedges push
the extremities of the plate springs 13 towards each other and retract the studs in m³
until they clear the holes, respectively, when the cylinder is unlocked and may
be lifted up and taken out of its seat I.) In Figure 10 the lug M is shown drawn
down, and the stud m² retracted, as is also the case in Figure 9; while the lug M¹
is in each of the illustrations, shown in its normal position with its end of the
spring close to the wall and the stud m³ protruding into the hole .
All the remaining structure of the needle cylinder being substantially such as is
well known, they are here passed by, merely referring the fact that while
Figure 9 shows the summit of the needle cylinder I capped by a row of sinkers I*
of the general nature and character best adapted to work in combination with the
remaining parts of the machine herein described, yet other sinkers adapted to work
in conjunction with presser wheels may also be used if desired.
The cam cylinder H (Figures 9, 11, 12, 13, 14, 16, 17, 18, 20 and 21) is also, in
general, of well known type. Its flanges H H have already been described
together with the means of attaching thereto the needle cylinder I. Likewise
much of its external ancillary mechanism has already been minutely set forth in
the preceding matter so that all which now remains is to show the combination
thereof together with the preferred distribution of its internal mechanism. In
doing this, it will be observed, First, that the dot and dash line of Figure 11
indicates the division of the cam cylinder into what may be called the knitting and
the idle zones; of these, the latter, the idle zone, designated as B2, is commonly
known as the needle rest or seat, along which the heels or off-set lower ends of the
needles normally slide in continual undisturbed succession one after another as they
describe their course carried by their slots in the needle cylinder. Said rest I form
of a separate semi-circular seginent B2, adapted to repose, as shown in Figures 13
and 14 with the stems of the screws resting in the bottom of their respective
port holes in the vertical shell of the cam cylinder. And so B2, by its upper surface
serves normally to connect into a continuous path the two ends of the actuating
car zone shown at n n in Figure 12. Second: That into the half of the cam
cylinder H, which, lies between the termini n n as shown in Figure 12, there is
compressed and adapted the entire needle actuating cam system.
Save for the automatic actuating mechanisms combined therewith for the purpose
of changing the length of the needles' stroke, or of bringing into or out of action
as the case may be, the "secondary" devices for throwing in or out of gear
individual needles, or possibly the somewhat unusually short central return cam N¹
with its recessed lower extremity and loosely pivoted switch point n', said cam
system is substantially composed, first, of the ordinary cam path for reciprocating
the needles normally during continuous tubular knitting; second, of other avenues
or by paths (the approaches to which are controlled by the secondary cam train)
into which certain of the needles' heels are automatically delivered during the
reciprocations of the needle cylinder. Said by paths are constituted by
incorporating with the cams of the above mentioned cam-path, 1st, pivoted
needle lifted tumblers n' no, acting in conjunction with fixed switch cams N N
for passing individual needles from the active to the non-active ranks; 2ud, fixed
outlying guard cains N N for returning needles accidentally displaced to their
B

page_text: normal level prior to their entering the actuating cam zone proper; automatically
movable downcast cam lobes N' N°, best seen in Figures 18 and 23, secured to the
inner faces of the ends of their respective actuating lever arms d³ d, forming the
auxiliary stitch tightening device, and 4th, on occasion, to wit, when F is swung
up into action, dependent oscillating depressor tumblers F F acting in conjunction
with laterally-extending free-standing wings of the central fixed cam N¹, to return
non-acting needles into action. All of which devices, both in form and location
when associated as above referred to and as illustrated in the accompanying
drawings, can be best taken up and explained during a consideration of their
respective duties as they jointly or severally succeed and occur. Therefore,
passing now to the operation of the whole as above set forth and combined, it will
be seen that the various parts in operation.act as follows:
The shipper being placed as in Figure 1, guides, by means of the fork 210, an
endless belt supplying motive power in the usual way to wheel W, from which it
is transmitted by shaft S to gear wheel V, which, by its intermeshing teeth,
also revolves the smaller pinion wheel V₁ with a more rapid continuous circular
motion.
This motion, the machine being now supposed to be upon the point to begin its
duty of knitting a stocking, is transmitted to the shaft S₁ as follows. The slide
disc V2 being at this stage of the operation in its normal position, banked close
against the side of the gear wheel V', as shown in Figure 1 and indicated in the
dotted outline of the disc given in Figure 4; the laterally projecting stud P³
entering into its corresponding hole in the side of the gear Vi locks the two
together radially and drives the shaft S¹ by the feather s'. And the whole
revolves together in the bearings, and drives by means of the feathers, the
second slider clutch disc Us, which, under the constraint of the fork u of the
U-shaped slider piece U2, is now held longitudinally near to the bearing a, and
has its clutch stud P, free of the pinion wheel U; which (U), being loose upon
shaft. S so far as regards radial motion :rides idle. Its longitudinal relation
to U is correctly maintained by the inward pointing flanges of the segmental slips
of the fixed face plate So (see Figures 4 and 44).
The shaft S¹ being connected in this way revolves continuously and carries with
it the band wheel and the bevel gear which latter, gearing with the mitre
teeth i, revolves the annular needle cylinder socket I and with it, the cylinder
which may have been secured thereto by the studs m² m³. Said cylinder being
equipped with needles as.above mentioned (one of which.is shown in Figure 244,
or with some other variety equally suitable) when thus continuously rotated, causes
them to pass their heels successively along the upper surface of the cam rest B2;
which rest, at this stage of the operation, is in its lowest position, shown in
Figure 13. For the cam wheel B (Figure 14), being still at rest presents a part
of its continuous circular periphery in contact with the buffer end b, of the rock
arm b (as shown in Figure 14) thus permitting gravity or a spring as shown at
Figure 14 at L, to cause the lever arms 263 together with the needle rest actuating
bridle B' to occupy at this stage their corresponding lowest position.
From the upper surface of B when in this position, (also shown in Figures 11
and 13) the needles' heels moving to the right or left according to the direction in
which the cylinder I may be revolved, cross the line dividing the knitting zone
from the idle zone and pass on to and along the lifting tumbler n', or no, as the
case may be; which tumblers are now both in their normal position; that is to
say, as they are to be placed preferably by the constructor on assembling the
machine, both as shown at n' no in Figure 23, which is in words, lying so, as to
form a bridge or inclined way connecting the upper surface of the cam zone
designated n n and the adjacent can surface of the downcast stitch cams N' or NB;
and thence said needles' feet pass successively to and up one or other of said cams,
as the case may be:-if N', in the path indicated in the dash and dot line of
Figure 23, until they reach its suminit, from which the angular motion of the
needle cylinder swings them across the gap between said cam (say N') and the

page_text: central depressing cam N1, under the lowest extremity of which they meet and
swing the switch point n' from its normal (perpendicular) pendulous position,
above the pivot po until it occupies the position indicated by broken lines in said
Figure 23 (also indicated in the dotted outline designated n³ in Figure 12)
whereby the needles are forced downwards as they are further swung onwards
towards the other stitch cam N" (or N, if the knitting be carried on in the
opposite direction in which case also the point n' would assume the other dotted
position designated n in said Figure 12). Along said cam they then move as is
further indicated in the aforesaid dot and dash line of Figure 23, until having
cleared its lowest extremity they are swung across the gap between it and the
adjoining ascending portion of the fixed cam N. The first of them, when it
encounters the remaining lifter tumbler (viz.: either n or n³, also inclined inwards
and resting against its adjacent stitch cams as no rests on N8 in said Figure 23)
causes this lifter to revolve upon its pivot and take the position shown in broken
lines at n in Figure 23. Such position being allowed to either of these lifter
fingers by reason of the cam wheel C being in its assembling position with the
highest level e in contact with friction roller c, whereby lever c is swung upon
its fulcrum S3 and the whisker is "on either hand" depressed towards the
bottom of the ports cc10: and these ports being formed so as to extend sufficiently
far down towards the table T, allow said whisker's inwardly protruding ends to
now lie so low that the needles' heels, passing from the active to the non-active
cam zone, can, uninterruptedly move outward over such non-active tumbler, viz.: one
in the position shown at n in Figure 23. But should n and n not actually, lie
below the horizon of the upper surface N when thus turned outwards, the pressure
of the needles' heels passing and thrusting them downwards towards the rest B³,
I have found is sufficient to raise the outer end of the lever c by crowding said
whisker c² still farther down towards the bottom of its port and so force the back
of such lifter tumbler to the level of the needle rest B2 along which the needles are
next again to successively pass.
The vertical throws represented in the dot and dash lines of Figure 23 thus
administered to the needles, constitute what is easily recognised as the ordinary
wave motion necessary to be imparted to their hook bearing upper ends (see the
needle shown in Figure 244) to operate in conjunction with any of the ordinary
bobbin rests, bobbins, tensions and yarn feeding devices with which the machine is
presumably equipped. And when a tubular web of the prescribed length has been
produced by their well understood interaction to form the leg of the stocking, the
knitting operation of my improved machine then comes automatically to rest for a
certain period by the intervention of pattern wheels, and this, as follows, viz.:
During every revolution of the belt wheel W (see Figure 1) the tappet w has
struck and swung the rocking lever to' and thereby carried the pawls P P in an
are back and forth an equal number of times over the ratchet wheels W W7; and,
as at the outset of the knitting operation, these pawls are assembled so that the
pawl P has its detent in the oblique face of the upper end of the lug w³ free
of the spring catch w (see Figures 7 and 8) gravity then causes it to occupy
substantially the position in which its companion pawl P and lug w are represented
as-occupying in said Figure 7.
Now, while in said position the nose of the pawl P engaging the teeth of the
idle ratchet wheel W' drove said wheel by the space of say 100th for each
revolution of the shaft S: But said idle ratchet wheel having now arrived at a
point where one of its above mentioned abnormally high teeth (W of Figure 7)
meets the pawl P, said tooth rotates the same through such an arc upon its
pivot p that the upward extending lug w sliding its wedge like upper surface
under the edge of the plate spring to lifts said spring until first the notch w of
the lug of the pawl P is disengaged; then second, when said high tooth W
has passed from under pawl P, "hooks" itself "up" on said catch spring wby
engaging the downward turned edge thereof with its own detent 10. Meanwhile
gravity acting upon pawl P drops it into action on the driving ratchet wheel We

page_text: and the shaft S, hitherto motionless, begins to receive from the pawl P, with each
revolution of the belt wheel W, an intermittent circular motion, whereby it will be
seen that the wheels W W' are not only a means of communicating intermittent
movements, but also in point of fact, are pattern wheels as well.
That is to say, the function of these fast and idler ratchet wheels is, in accordance
with the pattern, to alternately and automatically "put in motion" or again "to
leave at rest" the shaft S carrying the former or pattern wheels or secondary cam
train. For example, if the pattern of hose to be knit calls for a leg having 550 rows
of stitches, a number of ratchet teeth equal to the number of impulses which
the tappet w delivers to the lever W₁ during the operation of revolving the movable
cylinder 550 times is counted off upon the teeth of the idle ratchet wheel. The
count commences with the tooth initially registering with the pawl P and then a
higher tooth is introduced. When the back of this tooth is automatically brought,
by action of the tappet lever and consequent advances of the idle ratchet wheel W,
underneath its pawl 'Ps it will not only effect the throw off and latching out of genr
of that pawl as above described, but it will simultaneously release and bring into
operation the previously non-active pawl P, and thus cause the tappet lever W',
through the medium of the fixed ratchet wheel W, to set the secondary cam train
in motion. This done, certain of the secondary cams operate, as hereinafter fully
described to modify the normal action of the machine and then, as soon as these
cam wheels have been driven by the ratchet wheel W through a sufficient arc of
revolution to accomplish their present duty, the tappet having also brought said
"fixed" ratchet wheel at the same moment to a position where it presents a
"pattern" or higher tooth than its ordinary series within range of the tappet
pawl P as it swings back to take a new actuating stroke, then this tooth by lifting
it higher than usual puts that pawl back out of gear; and locking it upon the
tappet lever spring latch, simultaneously for the coming stroke, drops into gear
upon the idle ratchet wheel the other pawl P. And this wheel re-commencing
from the high tooth which lately put it out of gear is driven idly while the pawl Pa
.counts off upon its periphery a tooth for each forward stroke of the tappet lever
towards its own next higher tooth-which, in conformity with the pattern, is also
.contrived to be distant just as many teeth as there are strokes of the tappet to be
made, before the secondary cam train shall be again required to act in any of its
various functions. But, as soon as that occurs, another higher tooth of the idle
ratchet wheel meets its pawl and a shift of the ratchet pawls takes place auto-
matically, and so on.
By this means I accomplish the duty of actuating the secondary cam train only
as is required in conformity to the pattern: and that by a very compact mechanical
arrangement. By this means, viz.: alternating the thrust of tappet lever wo
between a loose wheel as W7, and a wheel as W, which is fixed to the drive
shaft S of the secondary cam train-l accomplish the duty of actuating said
secondary cam train only when, in conformity to the pattern, the same is required
to be in action. It is moreover, a very compact mechanical arrangement, to wit:
by it I am able to make intermittently actuated cam wheels of comparatively small
diameter take the place of more cumbersome and practically continuously actuated
devices; of which sort of devices there is an illustration in Figures 74 wherein, in
place of cam wheel B, there are placed within range of a cam reading lever end b',
such as is shown in Figure 14, cams & fixed at proper intervals to the face of an
endless chain 100 rove upon a sprocket wheel B fixed to shaft S. And for
operatively connecting said cam chain modification to the general driving parts of
the machine a substantially continuous rotary driving mechanism is indicated in
Figure 74 by the outline of toothed wheel Woo; and an actually continuous one as
shown in the same view by the sprocket wheels WW00 and chain W con-
necting shafts S and S. The rotation of the cam or pattern wheel A, brings it from
the position of having the lowest part in its periphery, viz.: a³, in contact with the
bent arm a of the lever A¹ into that of having the arm a forced outward by the
adjoining incline or cam which connects said lowest part a' with the slightly higher

page_text: circular portion, designated a in Figure 5. This passage of the arm a from
surface as to a', forces the lever A' to revolve horizontally through
small angle,
upon its pivot, in the direction shown by the curved arrow near said pivot P³, in
Figure 6, and by said movements, to thrust its discs a10 all against the abutment 08.
and force the slider rod S* not only endwise through the lugs t2 t, but outwards
towards the hand wheels; thereby compressing the springs Q and Q' between
their respective abutments, viz.: Q between and the adjoining face of the eye t*;.
and Q between 7 and the adjoining side of the eye t³. The spring Q is also, by
this same motion of the rod S', compressed between its abutment and the
adjoining end of the slider U, and so forces said slider in the same outward direction.
as the rod S moves in (see Figure 1). In addition the slider U2, by the sidewise
drag of the straddling legs uv on the flauges of the grooves urspectively,.
carries with it the discs V2 Us along the shaft S₁ and keys ss respectively, and
by so doing causes the stud P³ to begin to be retracted from the hole in the
pinion V until, while it is still partially inserted therein, its further retraction is-
temporarily arrested by reason of the inwardly turned tip j of the stationary
finger J coming into contact with a part of the adjoining side of the large flange-
of the said disc V2; and against this flange the tip now continues to rub until the
pin Ps, which is still locked to and driven by the pinion V₁, turns the disc V2 so-
that the gap J comes into alignment with said tip j. Then as soon as that takes
place, the spring Q, pressing against its fixed abutment v, forces the slider U
still further in the same outward direction, until the disc V sliding its gap J,
over, finally envelopes the finger j, thereby locking, not only itself, but also by the
agency of the key the shaft S' from rotary motion. At the same time the
complete releasing of the stud P3 from the hole 10, which takes place concurrently
with and by virtue of said lateral thrust of the spring Q, permits the pinion V¹ to-
run idly about the now motionless shaft S'. Thus all parts which previously
derived their motion (including the head H-1 &c.,) from shaft S', come not only
to rest, but also, as often as this part of the operation may be repeated, to rest in
precisely the same relative alignment. But since the belt wheel W is still revolving,
the pawl P continuing in action drives the secondary cam train, and in it the cam
wheel B now comes into operation. That is to say, during this arrest of the
knitting operation, the cam projecting from the wheel B (see Figure 14) is
revolved against the buffer b and causes it to rotate the shaft S through such an
are that the arms 63 63 (attached thereto) rise from the positions shown in Figures 2
and 14, until the screws 68 (uniting the bridle B' and the needle rest B³) are
forced upwards to the tops of the ports 610 611 in which position they cause the
needle rest B2 and all the needles which may then be reposing their feet upon it
to come above the active level of the cam train in the cam cylinder H, viz.: to the
non-active level, designated by the dot and dash line in Figure 21. The cam 6 is.
preferably of the form shown in profile in Figure 14, to wit: consisting of an easy
incline, the cam proper, and a radial connecting surface leading back to the other--
wise continuous circular periphery of the wheel B: whereby the buffer 6 having
once been acted upon and passed by said incline cam 64, it immediately under the
action of gravity or the aforesaid spring L³, swings back into its normal position of
contact with said circular periphery of B; thereby the needle rest B³ under the
attachment of the screws 6 6, is also dropped back into the position shown in
Figure 14; but the needles which were raised by it are maintained in the usual.
manner by the friction of the stitches and a compress girdle encompassing their
shafts in the ordinary way in the annular groove I' of the needle cylinder I (see
Figure 9) and remain for the time lifted out of gear.
At the same time the aforesaid action of pawl P and ratchet wheel W* having
brought the notch connecting the levels c and c of the cam wheel C not only
under, but clear of the friction roller c, has permitted gravity to drop said roller c
from the previous position which it was maintained in on the high level of the
wheel C to the next lower one c, and thereby lifting the whisker bearing end c
through a sufficient angle causes the inner ends of the whisker to rise in the

page_text: ports co co and raise the recumbent lifter tumblers or rather that one of them
which is then turned outwards as n in Figure 23 is so that it (and also its
fellow (n) when that one subsequently becomes turned into a corresponding prone
position) is lifted at its free or swinging, and notch bearing extremity, so far
above the level of the normal needle path (see n Figure 12) that the heel of the
first needle which swings along it in inward direction (viz.: from N³ towards N')
may be caught in and engage with the same; t the end that as it is further swung
onwards by the needle cylinder in its now reciprocating rotating motion, said
needle may be, first deflected and carried in an upward are until its heel is discharged
(preferably while still ascending) upon the overlying inclined way formed by the
slanting upper side of the fixed cam N2; whereby it is, second, shuuted up into the
non-active level above the cams. And joining the ranks of those that had previously
been placed in a similar condition by the above described action of the sliding
needle rest B2, it also remains out of action for the time being. Then after said
duty by the cams B and c, the shaft S by a still further partial revolution (see
Figure 5) causes the highest level a' of the wheel A to come opposite the arm a.
In doing this the incline surface connecting the levels at and a', acting as a cam
again pushes said arm a further outwards from the shaft S3 and swings the lever A¹
still further in the direction indicated by the curved arrow in Figure 6 and makes
the lever, in substantially the same way as it previously acted, shove the slider U
with the parts connected thereto, not only in a continuation of the same path_and
direction which was previously given them, until said disc V2 clears its gap J of
the finger j, but also moves the other disc U3 so far towards the pinion U that the
stud P2, having first come in contact with and banked against some part of the
adjoining side of this pinion U¹, remains milling there in rubbing contact until
the same has revolved sufficiently about the shaft S¹ (upon which it had, up to
this stage, ridden idly with a reciprocating circular motion, imparted to it as
hereinafter set forth,) to bring the hole uinto registering alignment with the
aforesaid stud P2. Then that stud entering therein, by means of the disc U³ and
key locks the pinion U to the shaft S¹, substantially as shown in Figure 4.
The necessary additional lateral throw of the slider U requisite for the above
described entering of the stud P2 in the hole u10 when the two are thus brought
into alignment, is furnished the slider U2 by the spring Q thrusting against the
abutment, which is, in its turn, banked by the slide rod S forcing its other
abutment to tv8, against the now stationary-discs a¹0 all of the arm A'.
Referring once more to the shaft S, it will be seen on inspecting Figures 1 and 2,
that it has during every revolution of the belt wheel W, caused the rock arm-R to
vibrate back and forth upon its pivot p¹ by means of the crank s', pivot p
knuckles and pin p². Said vibrating arm it will be readily understood, has a
varying annular velocity imparted to it by the connecting rod s, to wit: one which
is swiftest when said rock arm R is passing a line drawn vertically through its
point of oscillation (the centre of the pivot pl), and the slowest, just as it either
approaches or leaves the lateral limits of the circular arc through which it springs
or in other words, slowing to its movements of reversal. And as the pivot p
connects the upper end of said arm R by means of the knuckle to the drag link r,
said link has also thereby been reciprocated back and forth in curves a number of
times equal to the-revolutions described by said: main driving shaft S, by the
pin p, and causes-the-segmental toothed rack U to oscillate to and fro upon its
pivot P a similar number of times. And its teeth-intermeshing with those of
the pinion wheel U₁ have imparted to it a reciprocating rotary motion of
corresponding varying angular velocity upon the shaft S¹. This, as aforesaid,
has been merely an idle-function-while VA was in the position relative to the
slider U shown in Figure 1, but which on the coming into contact of the
stud P, and the sides of said-pinion U', has, as above described; served to
first align said stud with the hole u; and second, when they were coupléd
together, to then impart, by virtue of the disc Us and key s8, the peculiar
rotary motion which it now has to the shaft S₁ and by it, through the mitre

page_text: gears and i, to the needle cylinder 1. Moreover, at the time when the stud P³
enters the aforesaid hole 10, the original assembling of the various parts of the
machine having been calculated so that the pinion U¹ shall be at said moment,
intermeshed on the central portion of the segmental rack U; the first movement
imparted to the cylinder I by the revolution of the crank s is to cause the
needle cylinder to take exactly one half of a complete revolution (the number of
teeth on the rack and pinion respectively being adapted to impart that much
angular motion to such needle cylinder by such a swinging from said central point
of the rack to either end of its throw) and by this half revolution to cause all the
needles that were left (after the action of B2) in the active zone to move practically
uninterruptedly, outwards over a needle-lifter-tumbler in the latent position
indicated by dot and dash line at n in Figure 23, and come momentarily to rest
with their heels upon said needle rest B2. From this position, they pass by the
succeeding reciprocations of pinion wheel U', as above mentioned to and fro through
the cam system and lose their terminal needle with each passage of the cams until
finally, they arrive at the desired point, say when one sixth () of the whole
number of needles with which the cylinder I may be equipped remain in action.
Then the designated time for "turning" the heel having arrived, the wheel C,
further revolving, causes the roller c to fall from the level e to c and assume the
position shown in Figure 15, in which the whisker 2 raises the lifter-tumblers'
points of repose sufficiently high to elevate their entire notch bearing ends above
the level in which the needles' feet sweep along nn as indicated at n in Figure 23.
This causes the first needle which meets with either of them thus elevated as said
needle passes from the needle rest B2 into the cam area of the cylinder H to swing
said tumbler about its pivot and leave it in the position shown at n in Figure 23.
That is to say, the tumblers are made to automatically reassume the primary
function of bridges leading to their adjoining stitch cams n' or N°. This takes
place without deflecting said first needle, which thus met the lifter, from its normal
path, the dot and dash line of Figure 23. Concurrently with this reversion to the
normal arrangement of the cam system of the cylinder H the shaft S2 also brings
the high level of the cam F from under the friction roller bearing end of the
lever f and thereby rotating it upon the axle S³, raises f and swings the hinged
flap Fup into the position of contact with the external wall of cylinder H, as
shown in Figure 20; thereby bringing the upper ends F and F thereof not only
above and within the upper rim of said cylinder but also causing the depressors F³ Es
to slide forwards and clear shelves ', under the influence of gravity to come
into range of such of the needles' heels as are now in the non-active level indicated
in the dot and dash line in Figure 21. These depressors thereupon during the
still continued reciprocations of the cylinder head, begin and continue to act with
their notch bearing lower extremities, as follows, to wit:
It is to be noted that these depressor fingers shown in Figures 20 and 21 are
substantially alike in shape but assembled so that their bevelled upper portions
fall inwards toward each other as "rights and lefts"; that they both terminate
upon their upper and unnotched extremities in rounded summits, while their inner
or adjoining parts then slope away in oblique faces F F extending downwards
approximately to the level of their points of suspension on the pivots po p70; that
otherwise their sides are substantially parallel and equidistant from said pivots;
that immediately above said pivots the set springs are located, the inwardly
projecting free ends of which lie in range respectively of the arcs described by said
depressor fingers' rounded summits whenever they may be swung past them, the
said springs qy being constructed of such a stiffness as to prevent either of said
fingers passing under them by virtue of the momentum they may acquire in
falling by themselves from say a horizontal to a perpendicular position in either
direction. The object of these arrangements are that F2 F3 can be so brought into
action that while one of them lies inclined towards the direction in which the
way-going series of non-active needles shall first approach them, yet the other

page_text: then hangs straight downwards, whereby it is obvious that they thus extend their
notch bearing lower extremities to different levels in the cam cylinder H. To wit:
that one which now banks its oblique face against its spring catch, being sub-
stantially perpendicular hangs deeper down; and on either hand, presents its
straight flat sides in the non-active level, the dot and dash line of Figure 21; while
its mate F of said figure, banking the upper portion of its outer flat side against
its catch spring (the length of both F3, and F3 being not only the same, but also
proper for such purpose) it hangs at an angle calculated to bring its notch bearing
extremity into range of the non-active needle heels. The first of which heels,
meeting said notch, is swept in a downward arc and delivered to the under-.
side of the adjoining free standing wing of the central depressor cam N'; which
leads said needle into the normal cam path. Meanwhile, the next succeeding
needle's heel meeting the side of this depressor finger and swinging it further
onwards forces its summit under the overlying catch spring. Then when all the
following needles have ridden under it, said depressor drops back and reposes
with its oblique face against its catch spring, and thereby said depressor finger
becomes as it were, temporarily idle. That is to say, idle until after it be swung,
by the return of the needle cylinder, back to its active or angular positions
substantially as its nate is now forced by what has become the leading non-active
needle, when its heel (meeting F2 similarly hanging straight down) bears against
said depressor's flat inner side, and rotating it under the overlying spring catch q³,
suffers it on the passage of the whole non-active series of needles' heels from under
it, to drop back and repose turned outwards with its notch lying in wait at its
operative angle for the non-active needle's return. Such position is defined by
virtue of the straight outer side of said depressor finger then banking against q³.
So that when these needles again return from the idle zone by the reciprocations
of the cylinder I, they then cause these depressors to perform substantially the
same act or duty which its nate went through on the last prior passage; and so on,
alternately active and passive, the depressor fingers put back into gear single
needles and thereby cause the fabric to "turn and widen." Said widening is
continued until such time as the machine's head is brought by the revolution of the
driving parts, to a second period of rest.
This occurs by the wheel A which is rotated by shaft Snow being brought-so
that the high level a passing from in front of the lever a, allows it to be forced
by the springs Q3Q' against the next adjoining lower level a; and, in consequence
to allow said springs to retract the stud P2 from the hole u0 and then subsequently
to hook the finger tip into the gap J (substantially in the converse way that said
two parts were before brought into conjunction when U was thrust in the opposite
direction by the lever A¹). Said engagement now similarly locks the head driving
mechanism in the predetermined and constant alignment, and allows the wheel E
to force its cam e under the extremity e of the lever el, and by the consequent
partial revolution of the shaft S to depress the arms e e³, and with them the flap e
which, coming down upon the heads of such needles as may now be left unactive
forces them down their respective slots in the needle cylinder until their heels
once more repose upon the needle rest B. Then the cam e having cleared the
buffer e the spring 9 retracts the whole system e e e S and e¹ e, back into the position
shown in Figures 2 and 19. Moreover, during the last reciprocation of the head
as aforesaid, while the non-active needles had their heels under and supported the
depressor fingers FF, the shaft S brought the cam F so that the high level f
was forced by the incline or cam surface connecting said level with low level ƒ³
under the friction roller bearing end of the leverf, and consequently, depressing f
caused the flap F to drop back and retract the depressor fingers FF from their
active position to that of repose-on the shelves has shown in Figure 21. After
the widening has been finished to complete the heel the cam C is turned to such a
position that the roller c rides on the portion of the cam and the tumblers n' n
are dropped to their lowest position out of the way of the heels of the needles.

page_text: But before completing the description of their operation, I take this opportunity
to state that while I have, in most of the several inechanisms herein before set forth
described and shown only that form which I preferred for each instance I do not
mean to thereby disclaim the right to attain my objects by the substitution therefor
of equivalents operating, whether singly or conjointly, in substantially similar ways
to the same ends. However, as a distinct and separate modification of the driving
mechanism, I do hereby point out that power may also be advantageously
applied, especially with a comparatively high speed belt, through the pinion
wheel V, without changing its position in relation to the spur wheel V. This is as
follows, to wit:
By substituting in lieu of the fast and loose belt wheels WW, two loose belt
wheels W0 W30, journalled upon the shaft S', as shown in Figure 14. In this
modification it is to be noted that the wheel W20 is rigidly secured to or formed
integral with the pinion wheel V'; and when actuated by the belt, becomes the
main driving agent. Also that the train composed of spur wheel V, shaft S,
crank s, pitman s, rock arm R, link r, and toothed rack U, instead of driving, is,
in this combination, employed merely as a driven velocity and motion changing
device. Furthermore, that with the removal of the belt wheel W and consequent
loss of the tappet w, that the oscillating tappet lever w¹ would become motionless;
but this I readily prevent by means of locating said tappet on the spur wheel V
as indicated in dotted outline at 2020 in Figure 1; and then by bending or other-
wise-adjusting the parts, so as to bring the lower member of the lever w¹ within
range of it.
For the purpose of knitting hosiery continuously one stocking immediately after
another without break-for which my present improved machine is well adapted-
I prefer to employ this last mentioned modification of the driving mechanism in
combination with the rest of the machine substantially as herein described and
illustrated, save only that I then either disconnect or wholly remove the belt
shipper bar Z and for that reason have given Figure 14 divested of it.
In this case, while it may seem a departure from the preceding specified object,
the fabric produced, consisting of a series of leg sections, A, Aheel bags, 6, 6**
foot sections, and toe-hags d successively repeated-substantially as
illustrated in Figure 25-affords upon cutting. apart, as it is well understood
among hosiers, stocking blanks such as are illustrated in Figure 26, and these only
differ from the sort that the machine with its belt shipper attached produces in that
fact that the blanks when cut from the continuous fabric have to be finished at
their tops as well as to have their toe-section united.
And therefore, lastly, remarking that the cams No No of Figure 12 are placed
within the cam zone of the cylinder H not merely for the purpose of returning the
heels of any needles which, either by an untoward stiffness of the lifters n' nº, or
any other similar accidental cause, may have been at any time in the knitting
operation, lifted above the normal level of the needle rest B2, back to the upper
surface of nn; but also for the purpose of giving the needle rest B freedom for
its automatic movements. I now proceed to point out that the wheel A, once
more under the continued revolution of the shaft S', which, it is to be borne in
mind, is now in motion, brings its lowest level, the notch a, into a position opposite
the arm a (as in Figure 5) against which level springs Q Q' immediately thrust
said arm; and also, by this thrusting, cause the disc V2 to clear the finger from
its gap J, and thrust the stud Ps into rubbing contact with the adjoining side of
the pinion V and there remain until it, milling idly about the shaft S', first aligns
with, and then enters the hole ; and brings the machine once more into
substantially that functional condition in which it was described as first being.
Save only that the "higher' or pattern teeth of the fixed and idle ratchet
wheels WW' are now arrived by their mutual interactions at the commencement
of those portions of their spacings upon which the higher or pattern teeth are laid
off with reference to the number of rows of stitches in the stocking's foot, and also
0

page_text: save that the cam z upon the cam wheel Z being carried by the shafts S³ in a
position very slightly in angular advance of the radial notch connecting the inter-
mediate (a) and lowest (a) levels of the change of motion cam wheel A, it (the
cam 2) just prior to this apparent reversion having first rotated under the stud
lifts that stud upon its back; and then the rod 23 moves the shipper bar upwards.
This causing the banking screw to clear the terminal notch of the zig zag
aperture in which it had hitherto reposed, as shown in Figure 1 the shipper bar is
then drawn sidewise by the pull of the spring L. That is, it is pulled towards the
leg X until the shank of the screw 28 fetches up and arrests this movement by
engaging in the adjoining notch Z. To this engagement the immediately following
drop back of the stud 22-as the shaft S3 continues to revolve-upon the circular
periphery of the cam wheel Z, the gravitation of the shipper, its pivotal connection
at Z, and the upward inclined slope of the walls of the zig-zag which connect the
notches Z and Zo, all co-operate. Now, in this position, while the fork Z has
begun to pass toward the idle wheel W', it still delivers the belt to the fast driving
wheel W and remains doing so until the next revolution of the secondary cam train
as hereinafter set forth.
If at any time during any of the aforesaid knitting operations, it is desired to
tighten or loosen the stitch, I further combine with said machine, the device
shown in Figures 17 and 18, in which the cam wheel D, being secured at a proper
part of the shaft S2 and having suitable high and low levels (see d) in its other-
wise circular periphery, actuates thereby, on such occasion, the lever d¹ and thus
swinging the inner ends of d³ d simultaneously, raises or lowers as the case may
be, the lobes N7 N8 which are attached thereto (see Figure 18) thereby causing
the needles' heels to take unusually long or short throws and correspondingly
loosening or tightening the stitches which they make. After the resumption of
the original working the machine continuing in operation, and knitting a tubular
web forms the foot of the fabric. This foot completed, a high tooth as W, having
put an end to the activity of the secondary cam train at the commencement of said
second tubular knitting in the way which is now obvious, the original high
tooth W repeating its first action, now brings shaft S into activity once more,
and makes said secondary cam train perform and actuate the parts generally
connected therewith in precisely the same order and way in which they acted in
their first revolution as aforesaid; and fashion, by successive "narrowing,"
turning, and widening, a "toe"; save always that when the belt shipper mechanism
illustrated in Figure 1, is employed in said operation, the cam Z for the second
time meeting and lifting the stud 22, moves the shipper bar upwards and thereby
causes the notch 2 to clear the banking screw into which the prior or first
lifting of said shipper had, under the sidewise pull of string L and the weight of
the bar, drawn and left it; so that the shipper bar is now drawn by said
(the screw being in the notch 25, the inclined connecting way, and "straight" z12
successively) over towards the leg X (see Figure 1); and the fork 210 controlling
the direction of the belt, guides the same on to the idle wheel W', and brings all,
save it, to rest.
spring
""
L
In conclusion although obvious to machine kuitting hosiers, it may be proper to
note that in so far as the needles which are out of action in the narrowing or
goring process above referred to are concerned, each has its shank passed through
a loop of the fabric, they therefore upon their return to activity interweave the
same loops with the gored or narrowed part and produce what initially has the
appearance of a pocket; which, as indicated in Figure 25, the machine being
without the shipper and run continuously thereupon form the successive heel and
toe sections of the continuous product. These sections being cut, as upon the
line y-y of Figure 25, are readily shaped to the stocking form Figure 26, etc. On
the other hand, the fabric made, when the machine has the shipper attached, but
before the union of the top edge of the toe to the corresponding extremity of the
foot, is, in every particular, a finished piece of hosiery.

page_text: Having now particularly described and ascertained the nature of my said inven-
tion, and in what manner the same is to be performed, I declare that what I
claim is :-
1. In a knitting machine the combination with a cam cylinder and a needle
cylinder relatively rotatable, of a shaft as S¹ operatively connected therewith,
means adapted to drive said shaft with a continuous rotary motion, means to drive
said shaft with a reciprocatory motion and means adapted to connect the shaft St
alternately with either of, the motion transmitting devices and also to hold it out
of engagement with both, and a lock arranged to hold the shaft locked in a certain
definite position when not held in connection with the motion transmitting devices;
whereby the shaft S¹ and the needle actuating mechanism operated thereby may
be given alternately a continuous rotary and a reciprocatory rotary motion and
when not so rotating may be held locked from rotation in a certain definite
position.
2. In a knitting machine the combination of a needle and a cam cylinder
relatively rotatable, a shaft S' operatively connected therewith, a main driving
shaft S, means for transmitting continuous circular motion adapted to connect the
two shafts, means for transmitting reciprocatory circular motion also adapted to
connect the two shafts, a member driven from the main shaft and operating in
conformity with the pattern of hosiery to be knit, means operated by said member
and adapted to put the shaft S¹ in connection with the shaft S through one or the
other of the motion transmitting devices and to hold it disconnected from said
shaft S and a lock preventing the rotation of shaft S¹ during such time as it is
held out of connection with the shaft S whereby the shaft Sher with the
needle actuating cylinder actuated thereby, may be given successive continuous and
reciprocatory circular motions corresponding to those of the motion transmitting
devices and held from movement when not connected to the driving shaft S
substantially for the purpose specified.
3. In a knitting machine the combination of a needle and a cam cylinder relatively
rotatable, a shaft S¹ operatively connected therewith, a mai driving shaft S,
ineans for transmitting continuous, circular motion adapted to connect the two
shafts, means for transmitting reciprocatory circular motion and also adapted to
connect the two shafts, a cam A of a contour to operate in conformity with the
pattern of hosiery to be knit, mechanism operated from the main shaft s for turning
said cam, means operated by said cam and adapted to put the shaft S¹ in connection
with the shaft S through one or the other of the motion transmitting devices and
to hold it disconnected from said shaft S, and a lock preventing the rotation of
shaft S¹ during such time as it is held out of connection with the shaft S, whereby
the shaft S¹ together with the needle actuating cylinder actuated thereby may be
given successive continuous and reciprocatory circular motions corresponding t
those of the motion transmitting devices and held from movement when not
connected to the driving shaft S' substantially for the purpose specified.
4. In a knitting machine the combination of a needle and a cam cylinder
relatively rotatable, shaft S' operatively connected therewith, a main driving
shaft S, means for transmitting continuous circular motion adapted to connect the
two shafts, means for transmitting reciprocatory circular motion also adapted to
connect the two shafts, a clutch member adapted to put the shaft S' in connection
with the shaft S through one or other of the motion transmitting devices and to
hold it disconnected from said shaft S, a lock preventing the rotation of said
shaft S during such time as it is held out of connection with the shaft S, a
shaft S revolved from the driving shaft S by suitable means, a cam A fast on
the shaft S' of contour corresponding to the pattern of hosiery to be knit and
operatively connected with the clutch device, all operating together in such a
manner that the shaft S¹ together with the needle actuating cylinder connected
therewith is given alternately continuous and reciprocatory circular motion in
accordance with the pattern of hosiery to be knit.

page_text: 5. In a knitting machine the combination of a needle and a cam cylinder
relatively rotatable, a shaft S' operatively connected therewith, gear wheels
as VU loosely mounted on said shuft S', a driving shaft S, a gear V, and recipro-
cating rack operatively connected to the driving shaft S and adapted to transmit
the one continuous and the other reciprocatory circular motion, a clutch member
adapted to connect 'the shafts S and Si alternately through the two gears and to
hold them disconnected, a lock adapted to lock the shaft S' from motion when it is
not connected with the shaft S, a shaft S operatively connected to the driving
shaft S by suitable means, a pattern cam A fast on said shaft S and operatively
connected to the clutch member, all operating in such a manner that the shaft S¹
together with the needle actuating cylinder connected therewith will be given
alternate continuous and reciprocatory circular motion in accordance with the
pattern of hosiery to be knit.
6. In a knitting machine the combination of a needle and a cam cylinder
relatively rotatable, a shaft S¹ operatively connected therewith, gear wheels V₁
and U journalled loosely on said shaft, a driving shaft S, two gears on said shaft
meshing with gear wheels V₁ and U₁ and adapted to continuously revolve them
during the operation of the machine, the one with continuous and the other with
reciprocatory circular motion, a clutch member adapted to alternately connect the
shaft S¹ to one or the other of said gear wheels and to hold it disconnected from
both, a lock operating to hold the shaft S¹ from rotation during such times as it is
not connected to either of the gear wheels, a shaft S3 operatively connected to the
driving shaft S by suitable means, a pattern cam A fast on said shaft S³ and
operatively connected to the clutch member, all operating in such a manner that
the shaft S together with the needle actuating cylinder connected therewith will
he given alternate continuous and reciprocating circular motion in accordance with
the pattern of hosiery to be knit.
7. In a knitting machine the combination of a needle and a cam cylinder
relatively rotatable, a shaft S' operatively connected therewith, gear wheels V₁ U
loosely journalled on said shaft S', a driving shaft S, means as a gear wheel V
and a reciprocating rack U continuously in gear with the wheels V U whereby
these gear wheels V₁ U are adapted to be continuously revolved during the
operation of the machine, one with a continuous and the other with a reciprocatory
circular motion, a clutch member revolving with, but longitudinally movable along
said shaft S and adapted to connect the said shaft and cause it to revolve with one
or other of said gear wheels and also to disconnect the shaft from both gear
wheels, a lock arranged to hold the shaft S¹ from rotation when it is not connected
with either gear wheel, a shaft S' operatively connected to the driving shaft by
suitable means, a pattern cam A fast on said shaft S and operatively connected to
the clutch member, all operating in such a manner that the shaft S together with
the needle actuating cylinder connected therewith will be given alternate
continuous and reciprocatory eircular motion in accordance with the pattern of
bosiery to be knit.
8. The combination with a needle and a cam cylinder relatively rotatable, of a
shaft S operatively connected therewith, gear wheels VU loosely jourualled on
said shaft and provided with clutch grips, a driving shaft S, means as a spur
wheel V, and reciprocating rack U operatively connected with the driving shaft
and in gear with the gear wheels VU and adapted to rotate said wheels
concurrently, the one with continuous and the other with reciprocating circular
motion, a clutch member arranged to turn with, but movable lengthwise of the
shaft S, said clutch member having clutches to take with the grips on the gear
wheels VU and also a flange as the disc Vs having a peripheral notch adapted to
envelop when mutually registering, a fixed lock as the inwardly projecting tip of
the finger J'; and said fixed lock, the whole co-operating so that the sliding clutch
member can pass through the intermediate portion of its lengthwise slide between
said wheels when said shaft is in a certain definite alignment substantially as and for
the purposes herein before described.!

page_text: 9. The combination with a needle and a cam cylinder relatively rotatable, of a
shalt S operatively connected therewith, gear wheels V'U' loosely journalled on
said shaft and provided with clutch grips, means for driving gear V₁ with a
continuous and gear U with a reciprocating circular motion, a clutch member
arranged to turn with but movable lengthwise of said shaft S having clutches
adapted to take with the grips on the aforementioned wheels and also a flange as
the disc V2 having a peripheral indentation adapted to envelop when mutually
registering, a fixed lock as the inwardly projecting tip j of the aligning finger Ji,
said finger J having the lock, a cam shaft S2 rotated from the driving shaft by
suitable means as a tappet lever want a ratchet wheel W fast on the main
shaft S, a cam wheel A fast on and rotating with said shaft S³, a slider rol for
moving the clutch member having springs QQQ and operated from the cam
wheel A all substantially as and for the purposes described.
10. The combination in a knitting machine of a needle and a cam cylinder relatively
rotatable, a shaft S' operatively connected therewith, a main driving shaft S, means
operated from the main driving shaft adapted to drive the shaft S1 with a continuous-
rotary motion; and means, also operated from the main shaft, adapted to drive the
shaft S with a reciprocatory rotary motion, a clutch member operating to connect
the two shafts by means of either one or the other of the motion transmitting
devices, a cam shaft S2, fast and loose ratchet wheels W W' secured thereon,.
pawls P P reciprocated from the driving shaft S and operatively connected with
the ratchet wheels W W respectively, means as relatively high teeth on the
ratchet wheels for throwing one or the other of the pawls out of operation, a cam
wheel A fast on the shaft S and a lever operated by the cam wheel A adapted to
operate the clutch member so that it will connect the shafts S and S¹ by means of
one or the other of the motion transmitting devices.
11. The combination in a knitting machine of a needle and a cam cylinder
relatively rotatable, a shaft S' operatively connected therewith, a driving
shaft S, gear wheels V₁ U₁ loosely journalled on the shaft S' and provided with
clutch grips and rotated from the main driving shaft S the one with continuous-
and the other with reciprocatory circular motion, a clutch member arranged to
rotate with but free to slide lengthwise of said shaft S' and adapted to alternately
connect the shaft with one or the other of said gear wheels so that the shaft will
rotate with a motion corresponding to that of the gear wheel with which it is
connected, means consisting of a slide rod S, a block slidingly carried by rod Sa
spring and stops for holding said block in position on the rod S, for
moving said clutch and holding it in proper position, means for moving the rod and
lock such as the finger J' having tip for holding the gear wheels VU' in a fixed
position when not rotating, all operating to connect and disconnect the gear wheels.
and shaft when the parts are in a definite alignment.
12. In a knitting machine the combination of a needle and a cam cylinder
relatively rotatable, a shaft S' operatively connected therewith, gear wheels V₁ U
loosely journalled on said shaft and provided with clutch grips and rotated from
the driving shaft S, the one with continuous and the other with reciprocating
circular motion, a clutch member arranged to rotate with, but free to slide length-
wise of said shaft S' and adapted to connect the shaft alternately with one or the
other of said gear wheels and having a flange as the disc V3 with peripheral
indentation J adapted to envelop when mutually registering, a fixed lock as the
projecting tip of an aligning finger J'; the said finger, means consisting of a
slide rod S, a block slidingly carried by the rod S, a spring Q and stops and v
for holding said block in position on the rod S for moving said clutch, and holding
it in proper position, a cam wheel A for moving said slide rod, having a contour-
corresponding to the style of hosiery to be knit, all operating to connect and
disconnect the gear wheels and shaft S¹ and lock the shaft S¹ when not so
connected, all movements being made when the parts are in a definite alignment.
13. In a knitting machine the combination of a needle and a cam cylinder
relatively rotatable, a shaft S' operatively connected therewith, gear wheels V¹ U¹

page_text: journalled loosely thereon and provided with clutch grips and rotated from a
driving shaft S the one with continuous and the other with reciprocating circular
motion, a clutch member rotating with but capable of sliding lengthwise of said
shaft S, adapted to connect the shaft alternately with either gear wheel, a
shaft S2, a fast and an idle ratchet wheel mounted thereon, said wheel being
provided with relatively high teeth as described in conformity with the pattern,
the main driving shaft, an oscillating lever w¹ operatively connected therewith and
having a latch spring, pawls P P having detent bearing lugs pivotally connected
to said lever and adapted ou meeting said relatively high teeth to interchange
periods of activity and of rest by alternately latching upon and disengaging each
other from said latch spring and the cam wheel A fast on the shaft S and adapted
to move the clutch member in accordance with the pattern of hosiery to be knit all
operating substantially as described.
14. In a knitting machine the combination of a needle and a cam cylinder
relatively rotatable, a shaft S¹ operatively connected thereto, gear wheels V₁ U₁
loosely mounted on said shaft S', a driving shaft s a spur wheel V and a
reciprocating rack U, operated by the driving shaft S and in gear with the
gear wheels VU₁ so as to rotate, one with a continuous and the other with a
reciprocatory circular motion, a clutch member adapted to connect the shaft S¹
consecutively with one or the other of the gear wheels V₁ U', a shaft S2, means for
rotating said shaft from the said driving shaft S, a cam wheel A mounted on the
shaft S³, a lever A' a operated thereby and adapted to actuate the clutch member,
substantially as described.
15. The combination in a knitting machine with relatively movable cam and
needle mechanism as set forth, of a suitably journalled shaft as S, means for
rotating it, a lever wo¹, means, as a tappet, operatively connected so as to move with
said shaft for oscillating lever w¹ located so that one end thereof comes within
range of the means whereby said lever is oscillated, pawls pivotally connected at
the other end, each provided with a wedge lug and detent, a spring latch arranged
so as to alternately engage said detents, two ratchet wheels, each provided with
occasional higher teeth forming pattern surfaces and operating to lift said pawls,
and mounted, the one fast, and the other loosely on a shaft S and said shaft, all
operating substantially as set forth.
16. The combination in a knitting machine with relatively rotatable cam and
needle cylinders, of a driving shaft S, fast and loose pulleys W W' mounted side by
side thereon, a pattern surface formed in accordance with the style of hosiery to be
knit and mounted on a shaft S2, said shaft S2 means for rotating it from the driving
shaft, a cam wheel Z rotating with said shaft S2, a link provided with a rider for
reading said cam wheel and operative to raise and unlatch from a banking stud a
shipper bar, said shipper bar having a zig-zag W shaped slot as shown, a stud in
said slot and a spring tending to pull the shipper bar in a direction to shift an
operative belt from the fast to the loose pulley, the whole operating to free said
shipper bar and shift the belt from the fast to the loose pulley only at the second full
revolution of said sbaft S substantially as and for the purpose described.
17. The combination with relatively movable needle and cam cylinders of
rotatable pinions U V¹; a shaft S', a rod as S4 adapted to slide endwise in
suitable fixed eyes and provided with one longitudinally adjustable and three fixed
abutments, one of said fixed abutments being located upon an extension of said rod
outside of both of said fixed eyes and the remaining abutments located between them
substantially as described; springe as QQ helically coiled along said rod and
operative to thrust the same end wise in the direction of said exterior fixed
abutment, as p20; a sliding piece as U2 adapted to engage with a change of motion
clutch and adapted to be guided by said sliding rod, spring helically coiled along
said sliding rod and adapted to thrust said sliding piece away from the central and
towards the remaining internal fixed abutment ; a lever as A' a, provided with a
forked disc bearing end adapted to thrust against said adjustable abutment in a
direction contrary to that in which the two first mentioned springs act upon said

page_text: rod; a cam wheel as A adapted to rotate in rubbing contact with the other end of
said lever, and a clutch member provided with an intermitted part as J, a fixed
finger as J adapted to register with the intermitted part of said clutch member,
the whole operative in conjunction to slide said clutch member end wise, align, lock
and release the same radially, substantially as and for the purposes herein before
described.
18. The combination in a knitting machine of a stationary cylinder as H having
needle actuating cam paths located wholly within one half side of said cylinder, a
series of kuitting needles engaging therewith, a rotating needle cylinder as I, a
needle rest as B movably secured in the side of the cam cylinder opposite to that
containing the cam paths and adapted to underlie the heels of all such active
needles as are not at any given time within said semi-cylindrical area, levers
pivoted outside of the said cylinders, a cam for actuating said levers, connections
uniting said levers with said needle rest, and mechanism for automatically actuating
said cam, the whole operative to occasionally reciprocate said needle rest and
cause a group of needles to become non-active, substantially as and for the
purposes herein before described.
19. The combination in a knitting machine of a cam cylinder as I having a
needle actuating cam path located wholly within one half of said cylinder and
adapted for the production of a tubular and gored web, a series of needles adapted
to engage with said cam path, a needle cylinder as I arranged concentrically with
the cam cylinder, the cylinders operating when one is rotated relatively to the
other to reciprocate the needles in stitch wayes, a vibrating needle depressor flap
as e located over the non-active area of the cam cylinder. a pivoted lever actuated
by a cam and connected at one end to the flap e, a cam E adapted to actuate said
lever to depress the flap, means for actuating said cam and means for retracting
said flap after the cam has ceased to act, the whole operating to depress needles
after "turning "heels and toes of hosiery substantially as and for the purpose
specified.
20. In a knitting machine the combination with a fixed cam cylinder and a
rotatable needle cylinder designed on rotation of said needle cylinder to operate a
series of knitting needles in stitch weaves of a driving shaft as S, a shaft S2 located
externally to said cylinders, means for driving said shaft S from the driving
shaft S, a series of cams on the shaft S and adapted to be rotated thereby, a series
of pivoted levers adapted to read and be actuated by said cams and needle lifters
and depressors in the cylinders connected with the pivoted levers and actuated
thereby all operating to raise and depress needles in the cylinders in accordance
with the designed pattern.
21. In combination with the rotative needle cylinder I, an annular driving chuck
seat I, and a spring latch adapted to lock said cylinder to, and unlock it from said
seat, substantially as and for the purpose hereinbefore described.
22. The combination of the needle cylinder I provided with radially projecting
latches, a rotative driving chuck I', adapted to seat said cylinder and engage said
latches, the whole operating to alternately lock and release said cylinder, aud
said driving chuck at will, substantially as and for the purpose hereinbefore
described.
23. In a circular knitting machine the combination of the cam cylinder, a
flap F1 pivoted to said cylinder, and adapted when swung upward, to present its
upper part within and above the top of said cylinder, a pendulous needle depressor
finger F pivoted to the upper part of said flap, and means for latching said finger
with its needle engaging part in range of the non-active needles, a cam F, and
lever operative to swing said flap on its pivot, and bring said needle depressor
finger into active position within said cam cylinder preparatory to, widening,
substantially as and for the purpose described.
24. In a circular knitting machine the combination of the cam cylinder, a flap F¹
pivoted to said cylinder, and adapted when swung upward, to present its upper part
within and above the top of said cylinder, pendulous depressor fingers F F

page_text: pivoted to said flap, and means for latching said fingers alternately with their
needle engaging parts in range of the non-active needles, a V shaped central
depressor cam N located between said depressors and adapted to pass non-active
needles received from said depressor fingers into, the knitting cam paths, a cam
as F and a pivoted lever adapted to be actuated by said cam and connected to
said flap and operative to swing said flap on its pivot and bring said needle
-depressor fingers into active position within said cam cylinder, the whole operating
to return needles from either end of a non-active series to activity substantially
for the purpose described.
25. In a knitting machine the combination of the stationary cylinder H, provided
below a non-active level with cams, adapted to form a normal stitch wave cam
path in either direction, a pivoted flap F¹ adapted when swung upward to present
its upper part within and above the top of said cylinder; a cam as F, a lever
actuated thereby and operative to, vibrate said flap, automatic inechanism for
intermittently operating said cam and lever in conformity with the pattern of
hosiery to be knit, pendulous depressor fingers F F pivoted to the upper part of
said flap, and means for latching said fingers alternately with their needle
engaging parts in the path of non-active needles, the whole operative automatically
to return needles alternately from either end of a non-active series to activity
substantially for the purpose described.
26. The combination in a knitting machine of a rotatable needle cylinder and a
fixed cam cylinder provided with a normal stitch wave cam path, of a shaft S¹
operatively connected with the needle cylinder, gear wheels V' U' journalled
loosely on said shaft, a driving shaft, means operated thereby as a spur wheel V
and a reciprocating rack U adapted to transmit respectively continuous and
reciprocatory circular motion to the shaft S', a clutch member operating to connect
the shafts S and S successively through each of the motion transmitting devices, a
cam wheel A connecting with the clutch member and operating in accordance with
the pattern of hosiery to be knit whereby the shaft S¹ and the needle cylinder
operated thereby are given motions corresponding to those of the motion trans-
mitting devices, a shaft S' operated from the driving shaft in accordance with the
pattern, a cam wheel C fixed to said shaft S2, a fulcrumed lever having one end c
adapted to read the periphery of the cam wheel C and having whiskers as e
extending through slots in the cam cylinder, and pivoted needle lifter tumblers nn³
each provided on its free swing extremity with notches adapted to engage with the
knitting needle actuating parts, the whole operating automatically to move said
tumblers notched extremities in or out of the cam path substantially for the purpose
.specified.
27. In a circular knitting machine the combination of the cylinder driving
shaft S', the change of motion wheels V₁ U₁ journalled loosely on said shaft, and
a clutch member located medially between said wheels and arranged to turn with
said driving shaft but free to move longitudinally thereon, said clutch member
being provided on either end respectively with outwardly projecting studs P3 P3
arranged to engage with holes u 10 in the side of wheels VU and intermediate
thereto, with a circumferential disc as V having a gap J, said studs each sub-
stantially equal in length to the width of said gap bearing disc V, and a fixed
finger Ji provided with an inwardly projecting tip, the converse of said gap, the
whole being arranged substantially as and for the purpose specified.
28. In a circular knitting machine the combination of the movable needle
cylinder I, mechanism operative to drive the same with continuous and with
reciprocating circular motion, the fixed cam cylinder H provided with a system of
-cams, said cam system adapted to produce the normal stitch wave when traversed
in either direction and located wholly below a non-active level, a series of knitting
needles mutually engaging with said cylinders and operative for continuous or
reciprocating knitting, right and left by path cams N' N³ outlying said system and
adapted to pass needles delivered to them into said non-active level, right and left
.needle. lifter tumblers pivoted beneath the cam path of said cam system within

page_text: range respectively of aforesaid by-path cams and adapted to engage on the actuating
part (heels) of said needles, outlying guard cams N° N operative to replace
accidentally displaced needles prior to entering the cam system proper, adjustable
seats for said needle lifter tumblers, a pivoted lever connected to the needle lifter
tumblers and a cam for actuating said lever and controlling the tumblers and pattern
surfaces, actuated automatically from the driving mechanism, controlling the
relative positions of said cam and lever in conformity with the progress of the
knitting function, the whole operating to suffer said tumblers to lie passively below
the cam system of said cam cylinder during continuous circular knitting of the leg
or foot, but operative between changes from continuous to reciprocating motion in
said needle cylinder to lift said tumblers into active positions for narrowing and
finally on the completion of said operation, to return them to their normal position,
substantially as and for the purposes herein before described.
29. In a circular knitting machine the fixed cam cylinder H provided with
ancillary devices for turning and lifting depressing groups of needles simultaneously
and means for lifting and depressing single needles, the movable needle cylinder
an endless pattern surface, mechanism for actuating the same with an intermittent
motion from the driving mechanism, said driving mechanism consisting of a drive
shaft S adapted to drive the shaft S₁ with a continuous and reciprocating circular
motion with intervals of rest between said motions by means of gears V₁ U', said
gears, spur wheel V and reciprocating rack U substantially as specified, said shaft
or its equivalent, the secondary rotatable cam system secured upon a common shaft
as an axis, said shaft S suitably journalled aud located externally to said fixed
cam cylinder, means for operating said shaft conformably to the movements of said
pattern surface, a system of levers pivoted so as to read the cams of said secondary
cam system and automatically actuate by the vibrations produced thereby, aforesaid
ancillary devices for widening and narrowing in accordance with the reading of
said secondary cam system when called into activity by said pattern surface
substantially as and for the purposes hereiubefore described.
Dated this 21st day of January 1896.
HASELTINE, LAKE & Co.,
45 Southampton Buildings, London, W.C., Agents for the Applicant.