IMPROVEMENTS IN AND RELATING TO SEWING MACHINES
Year: 1883

page_text: LETTERS PATENT to William Robert Lake of the firm of Haseltine Lake
"
& Co., Patent Agents, Southampton Buildings London for an Invention of
"IMPROVEMENTS IN AND RELATING TO SEWING MACHINES communicated to
him from abroad by Charles E Tibbles of Burlington, Iowa, United States
of America, Mechanical Engineer,
COMPLETE SPECIFICATION filed by the said William Robert Lake at the
Office of the Commissioners of Patents on the 13th March 1883.
WILLIAM ROBERT LAKE, of the firm of Haseltine, Lake, & C° Patent Agents,
Southampton Buildings, London "IMPROVEMENTS IN AND RELATING TO SEWING
MACHINES" communicated to me from abroad by Charles E. Tibbles of Burlington,
Iowa, United States of America, Mechanical Engineer
This invention relates to sewing machines and comprises various improvements
as hereinafter set forth.
DESCRIPTION OF THE DRAWINGS.
Figure 1. is a side elevation of the working parts of the machine
Figure 2. is a bottom plan view.
Figure 3. is a bottom plan view shewing modifications.
Figure 4. is a side elevation shewing the feed mechanism.
Figure 5. is a section on the line x-x of figure 3 shewing modifications of feed
nechanism.
Figures 6. and 7, are elevation and plan of the tension devices.
Figure 8 shews details of the feed cains.
Figures 9 and 10 shew details of modifications of the feed cams.
Figure 11 is a side elevation of the same with feed bar and yoke
Figure 12 is a vertical section on the line x-x, of figure 11.
Figure 13. is a vertical section through the balance wheel, shaft, and fastenings.
Figure 14, is a detail of the fastening plate on the balance wheel.

page_text: Figure 15 is a vertical section through the feed cams, shaft and fastening
device.
Figure 16 is a vertical section on line y-y, of figure 17
Figure 17 is a vertical sectional view on line y-y, of figure 16
Figure 18. shews the split end of the shuttle lever in detail.
Figure 19. is a top plan of the bed-plate.
Figure 20 is a detail view of the double-crank driving-shaft
Figure 21 is an enlarged side elevation of the feed points.
Figure 22 is a vertical sectional view through the shuttle lever pivot.
Figure 23 is a vertical sectional view of the head of the machine shewing the
take-up arm mechanism.
Figure 24. is a section through the hub of the take-up arm.
Figure 25 shews the take-up arm in elevation, and its adjustable stops.
Figure 26 is a plan shewing the oil reservoirs in the bed plate
Figures 27, 28 and 29 are details of construction
Figure 30, is a perspective view of the shuttle enlarged
Figure 31 is a diagram shewing the shuttle applied to the race.
Figures 32 and 33 are views of the compensating bearings
Figure 34 is a vertical section through the lower end of the needle-bar and
adjustable cap.
Figure 35 is a bottom view of the same.
Figure 36 is a view of the lower end of the needle-bar.
Figure 37 is a view of the removable cap of the needle-bar.
Figure 38 is a vertical section through the cap journal for the driving shaft.
Figure 39. is a detail view of the pin to secure the fly wheel.
Figure 40. is a horizontal section through the arms and gibs of the shuttle lever
in Figure 3.
Figure 41. is a perspective view of the gibs removed.
Figure 42. is a section on line y-y. Figure 23.
Figure 43. is a perspective view of the treadle mechanism and dress-guard.
Figure 44 is an enlarged view of one of the adjustable bearings of the driving
shaft
Figure 45. is a vertical sectional view through the treadle shaft and dress-
guard
Figure 46. is a detail view of the pedal mounting.
Figure 47. is a detail of the fastening of the pedal to its supporting rod.
In the said drawings A is the bed plate of the machine and B the main shaft,
C is the shuttle op-rating lever which is held to the bed plate by means of a
compensating journal D, secured to said bed plate and upon which said shuttle
lever oscillates. The main shaft B carries two feed cams F, G, the cam G being
rigidly keyed to the shaft and has on its inner face a semi-circular slot or groove H
about one hundred and eighty degrees in length. The cam F has projecting from
it at a point shewn a stud I which when said cam is placed loosely upon the
shaft B enters the slot or depression H so that there is lost motion as between the
two cams equal to the distance of half a revolution.
The cam G is laid out as follows; The working face of the cam for about three
eighths of a circle struck from the centre K that is from J to L is on a true circle.
The portion from M to N is also a true circle struck from centre K on a radius
about three thirty-seconds of an inch less than the opposite curve.
The points
from J to M and L to N are joined on a curve of greater radius than either of the
other radii.
The cam F is laid out as follows; The working face is divided into four equal
parts, two on different radii, and two on the same radii.
The portion O. P is struck from the centre Q on a radius equal to the radius
of J, L, in cam G. The portion R. S. is struck on a radius one quarter of an inch
less than the portion O, P, and these two curves O, P, and R, S are joined in curves
of equal radii but of greater radii than the radii of curves O, P and R, S.

page_text: Consequently it will observed that there is a decided difference in the shapes
of cams F and G and this lack of identity of shape has a very important
bearing on the successful practical operation of the invention when these cams
are used.
The feed cams work in a yoke T attached to the feed bar U surrounding the
cams on all sides so that the cams shall have four bearing points in the yoke on its
interior surface; one bearing lifting the feed bar, the next point of contact
throwing the feed bar forward, the third point of contact carrying the feed
bar downward by a positive movement and the fourth point of contact retracting
the feed bar.
Within the yoke attached to the feed bar is a movable cross-head V which forms
one of the bearing faces for the cams and which by means of an adjusting screw-
bar W can be made to approach and recede from the fixed end of the yoke T
thereby diminishing or increasing the throw of the feed bar. The outer end of
this adjusting bar W in the throw of the feed bar and yoke, strikes at each
reciprocation an abutment X in one direction whilst the feed bar itself strikes
an abutment Y at the opposite end to limit the throw of the feed bar in the
opposite direction.
By this construction the relative movement caused by the throw of the cams is
always maintained as between the two abutments and thereby the length of the
stitch is made absolutely certain at each throw regardless of the direction and
length of the stitch or the direction in which the machine is moving and at what
speed the machine may be running, for there is no lost motion in the throw of
the feed bar, it being made absolute by bringing up against the abutments X and Y
as before described
The lost motion occurring between the feed cams by means of slot or groove H
and stud I enables the cam F to adjust itself automatically so that regardless of the
direction in which the fly-wheel may be turned the feed bar will always feed the
goods in the same direction in time.
When it is desired that the feed shall be in the direction in which the fly-wheel
moves, that is, from the operator when the fly-wheel turns from the operator and
to the operator when the wheel turns towards him, the loose cam F is fixed to
the driving shaft by means of a set screw Z which passes into the centre of the
end of the shaft and operates a spring pin a which has cross-pin b passing through
slots d d in the shaft and beyond its circumference which cross-pin b is made to
enter a recess e in the outer face of said loose cam and allow a very limited amount
of lost motion as particularly seen in Figures 8 and 15.
When the cams are in this position the feed of the machine will invariably be in
consonance with the direction in which the fly-wheel is turned and on account of
the limited lost motion due to recess e being larger than cross-pin b the feed in
both directions is in perfect time with the other operating parts of the
machine.
When it is desired that the feed shall always be from the operator when the
fly-wheel turns from him and always toward him when the fly-wheel turns toward
hin, as may be the case in machines driven by steam power, or in other machines,
I make the feed cams in one solid piece and rigidly fix such cans to the driving
shaft. This modification of my invention is particularly shewn in Figures 9. 10.
and 11. and laid out in the following manner, and I refer especially to Figure 9
which is an enlarged view of the cams with dotted lines to specifically point out
the construction, all the measurements having a basis in a vertical central line f, g,
drawn on the face of the cams h, i.
From the centre ; the cam face which raises the feed bar is laid out on a true
circle m an arc of about 105°, to hold the feed bar up whilst it is being
projected the length of the stitch. The cam face that reciprocates the feed bar is
coincident through an arc of about 75° n, l, g, with the curve k, l, m.
On one
side of the centre, commencing at a point n about 45° from the central line, fg,
the working face of the cam is struck on a curve n, o, which gradually nears the

page_text: centre until at the point o it has approached to about a distance equal to three
quarters of the radius j. l.
On the opposite side of the central line and about 30° from it, commencing at a
point g the other reciprocating face is struck passing toward a point p approaches
the vertical central line so that all the points of said curve g, p measured by direct
lines at right angles to central line f g shall be nearer the vertical central line
than the points of the curve n, o. At the point p the curve gp is precisely the
same distance from the centre j as the point o. From p to q the curve is flattened
so that the points p and q are equi-distance from the centre j.
The tension for the upper thread consists of the plates . sustained by posts on
a rigid bar 8 which is centrally tapped to receive the thread of a thumb-screw t.
The outer tension plates uu are supported on the ends of a rigid bar v which has
a central opening w through which loosely passes a thumb-screw and pins 2, 2,
which project through slots in a curved flat spring 3 which is compressed beneath
the head of the thumb screw and the tension plate bar v.
The wear and lost motion are taken up by compensating journals provided with
conical threaded openings in which fit split bushings, 4, 4, provided with tapering
exteriors and cylindrical interiors corresponding in dimension to the moving
piece. By screwing the bushing 4 down into the tapering hole in the bearing
(see Figure 32) the interior dimension of the bushing is contracted. The moving
portions are cut away as seen at 5, 5, for a short distance when this bushing is used.
Modifications of this compressible bearing are seen in Figures 23 and 33.
A modification of the stitch controlling mechanism is shewn particularly in
Figures 3, 5, 11 and 12, where the feed bar has a depending arm A¹ which lies in
the way of the travel of the can face which reciprocates the feed bar, and
by it the feed bar is thrown in one direction and the feed bar is thrown
in the opposite direction by the face of the feed can striking the periphery
of a variable eccentric B₁ which is pivoted to a hanger C which depends
from the feed-bar. Stops or abutments similar to those before described limit
or control the throw of the feed bar. A spiral spring may be used, as shewn,
to insure the downward impulse of the feed bar. The variable eccentric B¹ is
pivoted on a pin D¹ projecting from C¹ and through a sleeve E' wherein a spring Fl
tends to keep the eccentric B' continuously pressed towards C¹ so that a pin G¹
projecting from C¹ will enter one of the holes H'H' in the eccentric and hold it
in any desirable position within the limits circumscribed by a stop piu I' which
projects from the face of the eccentric and strikes the edge of hanger C. It is
quite obvious that as the longest radius of the eccentric B¹ is made to approach
the centre of motion of the feed eam and more quickly comes in contact with the
cam face which horizontally reciprocates the feed bar, the longer will be the contact
of this cam face with the eccentric and hence the greater will be the throw given
the feed-bar. As the eccentric B' is thrown towards or retracted from the feed
cain, so is the length of stitch increased or diminished the abutments X. Y always
limiting the throw of the bar.
On the shaft B adjacent to the fly-wheel may be placed an eccentric J₁ for
operating a needle bar by means of a strap and arm, or the main shaft may be
made with two cranks, quartering or standing in an are of 90° from each other so
one crank drives the needle har and the other one drives the shuttle lever all of
which will be hereinafter fully described.
When I use the eccentric J' I place next to it an operating mechanism for the
shuttle lever C, constructed as follows. Two eccentrics K' K' are fixed to the
shaft B and upon these ride a reciprocating cross-head composed of the vertical
pieces LL", having bearing faces for said eccentrics and secured at the top and
bottom by horizontal screws M', provided with jam nuts to hold the cross-head or
frame in an absolutely rigid condition. The vertical piece L" is provided with
projecting ears to which is hinged one end of a link N which passes through the
opening in L", straddles the shaft B and passes out through the opening in L said
opening being larger than the link so as to perinit the latter to have some lateral

page_text: play. The link N' has a bifurcated end 0' through which passes the screw P¹
that engages with the split end of the shuttle lever that rests in said bifurcation:
Where the shuttle lever and link N' are joined all lost motion is compensated
for by screw P drawing together the bifurcated end of link N' said screw forming
the connecting pivot for lever G and the set screw Q' which draws together the
split end of lever C around the screw pin.
By this construction I am enabled to get a direct longitudinal thrust on the
operating eccentrics for the shuttle lever and there is no rising or falling or
irregular movement whatever to produce irregular wear.
When a double crank
shaft is to be used shewn in modification of my invention illustrated in Figures 3
and 20. I provide the end of the shuttle lever with two arms R₁ having concave
interior surfaces in which slide two separate and distinct gib S¹ whose interior
surfaces are convex to fit over the straight wrist T₁ on the driving shaft and their
interior surfaces are courave to fit against the interior of arms R'. As the wrist T
turns the gibs S₁ slide back and forth and oscillate the shuttle-lever.
The shuttle-lever is sustained by a double cone bearing whereby any lost
motion can be taken up and the shuttle lever may be raised or lowered for purposes
of adjustment. This bearing consists of two centrally bored truncated cones U U!
which fit an opening of corresponding shape in the shuttle lever and having passing
entirely through them the bolt V₁ which depends from the bed-plate and is threaded
at each end in order that jam-nuts W₁ may raise and lower the pivot. If the cone
bearings U were allowed to turn with the shuttle lever they would soon work off
the jam-nuts. In order to avoid this I provide the bolt V₁ with a longitudinal
groove E and have a pin X' projecting from each of the cones into the groove E so
as to prevent the cones from turning on the bolt.
In order that the bobbins may be wound with facility by a friction device
bearing against the fly wheel and without wearing the moving parts of the machine
I have provided a means for readily rotating the fly wheel independently of the
main shaft. The end of the driving shaft is made hollow or tubular and is partially
internally threaded at 6. A sliding bolt 7 having a transverse drive pin 8 through
it, is placed in this hollow end of the shaft and moved back and forth by means
of screw 9 and hand wheel 10. The ends of drive pin 8 project through slots 11, 11;
in the shaft and enter a chamber 12 formed between the balance wheel 13 and a
plate 14 which is secured to the back of the wheel by screws. Immediately around
the centre and on the interior face of the plate 14 are a series of radial ribs or
projections 15, 15, (see Figure 14) with which pin 8 engages or intermeshes when
driven against plate 14 by screw 9 and hand wheel 10. When screw 9 is with-
drawn the drive pin projects into chamber 12 and the balance wheel can be rotated
without turning the main shaft.
I will now proceed to describe my take up mechanism. On the end of the
needle-bar rock shaft is a vibrating head or lever 16 projecting away from the
needle bar and travelling in the are of a circle. At the ends of the curved portion
of a lever 16 are projections 17, 18, at right angles to the face of the lever. The
projection 17 is provided with a cushion 19, made of raw-hide and adjusted by a
set-screw. The projection 18 is bored to receive a plunger 20 backed by a coiled
spring 21. Between the projections 17 and 18 lies one end, 22, of the take-up
arm 23, which vibrates on a pivot 24, supported by the face plate of the machine
or some frame specially introduced into the head of the machine for the purpose.
Properly cushioned stops 25, 25, limit the travel of the take-up armn. The operation
is as follows: As the needle-arm raises the projection 17 on the curved portion of
lever 16 passes downward and carries with it the end 22 of the take-up arm until
the thread carrying end reaches its highest elevation where it is sustained and
retained by a coiled tension 26 enclosed in the hub of the take-up bar. The needle
bar there starts downward leaving the take-up bar at its highest throw where it
remains until the spring plunger, 20, strikes beneath end 22 and with a yielding
spring pressure starts the take-up arm downward just at the moment the needle

page_text: enters the cloth whereby the necessary slack is given to the thread at this particular
moment.
In sewing machines heretofore used much annoyance has been experienced owing
to the necessity for raising the bed plate on the hinges to oil the lower bearings of
the machine. I avoid this by casting my bed-plate with a cross-shaped raised
portion 27 having sliding sections 28, 28 which are over the main bearings of the
machine. By this construction I am enabled to oil the shuttle-race, carrier and
feed mechanism as well as the needle-bar and shuttle-lever actuating devices
without having to raise the bed-plate. To avoid frequent use of the oil-can I
provide the bed-plate at desired points with recesses cut into the surfare of said
plate to contain oil and have minute ducts to convey the oil to the surfaces to be
lubricated. For illustration, I have shown these recesses at 29, 29 provided with
covers 30, 30, and having ducts 31, 32, leading to the shuttle race and the bearings
of the feed bar. To partially destroy or counteract the noise caused by the
vibration of the bed-plate I provide recesses in the bed-plate with a packing of
fibrous or other material calculated to destroy the resonance of the machine and
in this particular in-tance, for purposes of illustration, I show the recesses 29, 29,
filled with felt or wool 33, through which the oil percolates after saturation.
I use a cap-journal box (shown in Figure 38) to sustain the driving shaft and for
like purposes the box being provided with a groove 34, and the cap being provided
with a rib 35 which tightly fits in said groove and prevents any tendency of the
cap to move around either of the securing screws as a centre of motion
In order to insure a truly vertical reciprocation of the presser foot bar and guard,
against it turning so the needle hole will not register with the needle hole in the
throat plate, I provide a presser-bar yoke 36 rigidly fast to the presser-bar and
having a split end 37 which projects through slot 38 in the casting of the head.
A set screw 39 is adapted to spread the halves of this split equally from a central
line and compensate for wear of the slot or yoke
The lower end of the needle bar is bored at 40 with a cylindrical hole the size
The shell of the end of
of the shank of any desired needle known to the trade.
the needle bar is then cut out to form a semi-circular slot 41 for a purpose herein-
after set forth. Over the lower end of the neelle har by means of a set screw 42,
1 fit a cylindrical cap 43 the lower face of which is so constructed as to cover a
portion of the entrance to hole 40 and thereby make it of irregular shape so that
a needle having a shank whose cross-sectional area corresponds in shape and
dimension to the uncovered portion of hole 40 can only be set in one position and
that the proper one, thereby providing a certain guide for properly inserting the
needle. After the needle is inserted, the shank is held by a set screw 44 which
passes through semicircular slot 41 through which means the cap can be adjusted
around the end of the needle bar without interfering whith the hold of the screw
on the needle. For convenience I provide a cap 43 with a slot thread guide 45.
The feed points 46 are arranged in pairs, each tooth having a straight side and
an inclined side, each pair having like sides of the teeth adjacent (see Figure 21).
By this construction the straight sides of the teeth hold and force along the
material in either direction as the direction of the feed may change.
The shuttle (Figures 30 and 31) is an open faced shuttle dressed at the heel and
point in a curve parallel to the curve of the race whilst intermediately the face is
either straight or a curve of a larger radius than the curve of the race whereby
the face of the shuttle does not touch the race between the heel and the point and
the shuttle thread 50 may be passed without danger of abrasion directly over the
face of the shuttle to the friction devices. These friction devices consist of a set
of pins 47, 47, set in a line, around which the thread is laid, in and out, and
another pin 48, out of line, around which the thread is last passed, so that the
thread passing the pins in opposite directions will not rub or chafe as in other
shuttles now in use where pins are used. A latch 49 hinged near the point of the
shuttle and provided with a slight bend near its hinge and with a spring 51 closes

page_text: down over the tops of the pins and rests its free end on a flat projection 52 so as to
prevent the latch from coming in contact with the top of the shuttle and binding
the thread. A spring end, 53, of the latch catch-s in hole 54 and the same kind
of a device on the end of spring arm 51, catches in hole 55. This spring arm 51,
prevents the thread getting between the shuttle and the race.
The upper edge, 56, of the face of the shuttle is made convex to compensate by
its curvature for the irregular unwinding of the bobbin as has been before done by
curved devices but none that I am aware of where the edge of the shuttle proper
has been cut away
I have also invented sundry details of construction of the treadle and table and
proceed to describe the same, as follows
In the said drawings A is the framework supporting the treadle and the other
working parts and shafts and in it is supported a centrally arranged four arm
casting D D D D D
A shaft or rod B having bearings in the frame at
where it is held
stationary by nuts affords a bearing for the treadle C which is cast with two side
ribs having half round bearings which rest on said shaft or rod B¹¹¹.
Through the top of the half round bearings on the ribs are cut slots C in the arc
of the circle and the said slots have bevelled sides (as shown in Figure 46) and
through them pass screws c¹ll surrounded by blocks or washers cl having the
same bevel as the slots C. The screws c, by means of proper threads, hold the
blocks rigidly to the shaft B and the treadle oscillates back and forth on
the shaft being held in place by the screw and blocks c. The tapering blocks
are made as frustra of pyramids (see Figure 47) and are shorter somewhat than
the depth of slots C, so that the treadle shall bear against their sides only and
the tapering blocks can be fed down into the beveled slot as the bearing surfaces
wear away.
The pitman is connected with the treadle and crank in any desirable manner.
The crank shaft or driving shaft F does not extend entirely across the frame work
and has bearings at one end in the frame and at the other end in the central
piece D of the four arm casting or brace
The bearings for the ends of this shaft form an important feature of my invention
and are designed to take up all lost motion caused by wear. The bearings at each
end of the shaft are alike and for illustration I will describe the one on the central
frame piece D
Cast with the frame piece is a sleeve M having an interior screw thread.
Into this is screwed a bushing K™ the interior of which is partially cylindrical and
partially conical (see Figure 44) and the tip of the cone cut away into a
cylindrical recess. This bushing forms the bearing in which the crank shaft
turns, the said shaft having its ends turned down to a cone, as seen at 71111
Figure 44.
For a portion of the surface, the threads on the exterior of bushing K¹ are
turned off, as seen at oo, Figure 44, so as to forin a wide shallow groove
entirely around the bushing and between it and the sleeve M. At sundry points
around the circumference, holes p" connect the groove o with the interior of the
bushing or bearings K. On the top of the sleeve M is an opening or hole !!!
communicating with the groove o¹ in bushing K. By introducing oil through
opening or hole mit Hows into and fills groove o and thence passes through
holes pp to the interior of bushing K and lubricates the crank shaft.
jam-nut around bushing K serves to fix said bushing in any relation to
sleeve M
A
As the end thrust bearing of crank shaft F wears away the lost motion is taken
up by withdrawing by means of a wrench, or other device, the bushings K™ from
their sleeves so as to properly centre the crank
A pan L, to catch all drip oil is secured at
side of rod B and extends towards and beneath
by an abutment to the lower
the fly wheel, where it has an
enlargement projecting beneath the travel. of the pitinan bearings and has its

page_text: outer edge, m, bent upward outside of the lower braces of the frame. The pitch
of pan L is towards the point q so all the waste oil will collect at that point
which is the most accessible for its removal
Between the front of the machine the driving wheel, and the bearings, I
interpose a solid combined dress guard and oil deflecting pan G having its
general formation triangular in outline, one side supported at t on the central
brace and the other end at any desired point on the upright framework, as, the
guard plate G may extend downward any distance whatsoever without departing
from my invention. The plate or guard G has a general curve conforming to
the outline of the driving-wheel and on its outer and lower edges gg it is
provided with turned up edges to direct the oil to its lowest point q where tho
drip or waste oil will be collected in a cup provided for the purpose or drop
upon pan Land be removed at proper intervals. The construction of the
guard plate G¹ insures absolute immunity from soiling or entangling the dress of
the operative.
Having thus fully described the said invention as communicated to me by my
foreign correspondent and the manner of performing the same I wish it understood
that I claim
First In a sewing machine the combination with the feed-bar and driving-shaft
of the feed cams consisting of the cam G keyed to the shaft and provided with a
semi circular groove or depression H and the cam F provided with the stud I
entering the groove H whereby a lost motion between the cams, of a half revolution,
is permitted, for the purpose set forth
Second. The cams F, G, having an engaging groove and stud, the cam F
being provided with a recess e in combination with a movable locking pin b
and a set screw Z for operating the same through the interior of the shaft, as
described
Third In a sewing machine having a variable direction of feed, a feed bar in
combination with a stitch regulating device and the abutments X, Y, substantially
as specified
Fourth The main shaft provided with the eccentrics K' K' in combination with
the crosshead reciprocating in a horizontal plane connected to and in combination
with the shuttle lever C substantially as set forth
Fifth The actuating cross head consisting of the vertical pieces L¹ L" in
combination with the horizontal screws M¹ and eccentrics K', K' substantially as
set forth
Sixth The vertical piece L", having ears to which is keyed link N', in
combination with the horizontal link N₁ having a bifurcated end, and projecting
through an opening in piece L' laterally larger than the link N¹ whereby said
link has a lateral play entirely independent of the cross head, substantially as
described
Seventh The cross head L¹³, L", M', and the link N' having a bifurcated end
and screws M¹ projecting through the pieces L' L" in combination with the
shuttle lever C baving a split end all constructed, arranged, and operated as set
forth
Eighth. The bed plate A provided with recesses to contain oil, and ducts 31, 32
to conduct the oil to the surfaces to be lubricated, substantially as set forth
Ninth In a sewing machine the bed plate provided with chambers, in combination
with the inclosed fibrous or other non-resonant material for the purpose of
deadening the sound, as described
Tenth The compressible tapering bushing 4 provided with a slit as described
Eleventh In a sewing machine shuttle, the pins 47, 47, in line, in combination
with the pin 48 out of line as described
Twelfth In a sewing machine shuttle the latch 49 provided with a slight
upward bend at its hinge, in combination with a flat projection 52 to prevent the
lutch binding the thread, as set forth.

page_text: Thirteenth An open-faced shuttle having the upper edge of the face convex, for
the purpose set forth
Fourteenth An open faced shuttle having its heel and point dressed to coincide
with and bear against the curvature of the race, and the intermediate face cut so
as not to come in contact with the race in combination with a curved race
substantially as described
Fifteenth In a sewing machine the shuttle lever provided with two projecting
arms R R having their interior faces curved as shown, in combination with the
crank T having a cylindrical wrist and two independent gibs S₁ having convex
surfaces to conform to the curvature of the interior of arms R' and concave surfaces
to conform to the curvature of the cylindrical wrist all constructed and arranged
to operate substantially as set forth
Sixteenth The compensating pivot consisting of the double cones U¹, U¹ provided
with pins Xbolt V₁ provided with groove E and jam-nuts W₁ substantially as
described
Seventeenth In combination with a feed bar adapted to be moved positively
both forward and backward a cam for horizontally moving the said feed bar by a
positive motion in either direction in time said cam having one working face l, p
with all its points cut nearer, in direct lines, to the vertical central line f g than
the points of the other working face n o, substantially as and for the purpose set
forth
Eighteenth In a sewing machine, the combination of the main shaft Ba cam
and a feed bar U, eccentric B¹ provided with sleeve E' pin D¹ spring F¹ and stop-
pin G adapted to enter holes H³ in the eccentric all constructed and arranged to
operate as described
Nineteenth The feed dog provided with feed points or teeth 46 having one
side vertical and the other side inclined and arranged in a series of pairs so that the
same shaped sides of each pair are adjacent substantially as described
Twentieth The bed plate A provided with the cross shaped raised portion 27
having removable slides 28 for the purpose specified
Twenty first The compressible bushing provided with a groove around its base
in combination with the bearing provided with screw for the purpose set forth
Twenty second In a tension device for a sewing machine two rigid friction
surfaces in combination with two movable friction plates u u, supported on
rigid bar spring 3 and set screw t all constructed arranged and operated as
described
Twenty third The balance wheel 13 and plate 14 provided with central radial
corrugations 15 in combination with the hollow end shaft B having slots 11 bolt 7
provided with cross pin 8 and thumb screw 10 provided with a threaded sleeve 9
which enters the hollow end of the shaft substantially as described
Twenty fourth An arm attached to the needle bar rock shaft and provided
with head carrying projections in combination with a take up arm 22 pivoted
independently within the head for the purpose set forth
Twenty fifth The take-up bar having a hollow hub in combination with an
inserted coiled detent spring substantially as described
Twenty sixth The take up bar 23 in combination with an operating lever, and
a spring device for starting the take up downward with a yielding spring pressure
substantially as set forth
Twenty seventh The lever head 16 having projections 17 and 18 adjustable
stop 19 and spring device 20, 21, in combination with the take up arm 23 having a
projecting end 22 detent spring and stops 25, 25 all constructed arranged and
operated as set forth
Twenty eighth The needle bar having the cylindrical needle-hole 40 in com-
bination with a removable cap or guide 43 provided with a face which partially
covers the entrance to needle-hole 40, substantially as set forth
Twenty ninth The needle-bar provided at its lower end with a cylindrical

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opening and the semicircular slot 41 in combination with the removable cap 43
provided with a set screw 44 entering slot 41 for the purpose set forth
Thirtieth The sewing machine treadle cast with the bevelled slots C and the
half round bearings B₁₁ in combination with the tapering blocks c¹¹¹ and screws cl
for the purpose set forth
Thirty first. The sewing machine driving shaft having conical ends, and adapted to
be operated by treadle C in combination with the sleeves provided with holes n
and threaded interiorly, and bushings Khaving partially cylindrical recesses 7111
grooves o and holes p all constructed and arranged substantially as described
Thirty second. The oil pan L bolted to rod B through abutment n¹ its
outer end turned up at m and secured to the frame, and provided with the
enlargement L" and standing so as to have a general pitch to a lowest point q¹¹¹,
as specified.
111
Thirty third. The solid, imperforate guard G constructed and secured
substantially as set forth.
In witness whereof I the said William Robert Lake have hereunto set my
hand and seal this Thirteenth day of March in the year of our Lord One
thousand eight hundred and eighty three.