Improvements in Sewing Machines.
Year: 1897

page_text: Date of Application, 5th Jan., 1897-Accepted, 8th May, 1897
Improvements in Sewing Machines.
I, FRANCIS HENRY RICHARDS, of 112 Edwards Street, in the City of Hartford,
County of Hartford and State of Connecticut, United States of America,
Mechanist, 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 :-
This invention relates to sewing-machines of that class in which a revoluble
loop-taker having a plurality of hooks is employed.
One object of the invention is to furnish a sewing-machine having an improved
construction and organization of needle-bar mechanism, presser-bar mechanism,.
loop-taking devices, feed mechanism, and tension devices, that may be readily
assembled and disassembled and at the same time secure compactness and.
durability at a comparative low cost of construction. Also to provide a
revoluble loop-taker having two sets or two series of loop-engaging books,
the hooks of one set alternating with the hooks of the other set; also to
provide a reciprocatory needle-bar carrying a needle, and to so operatively
connect the needle-bar and loop-taker that the needle will, at some point in
its reciprocatory movement, assume a neutral position relatively to two opposing
hooks of the loop-taker and also to provide, in connection with the actuating
mechanism of the needle-bar and loop-taker, a combined loop-taker locking and
reversing device adapted for effecting a change in the direction of rotation of the
loop-taker at a predetermined point in the reciprocative movement of the needle,.
or that point in the reciprocatory movement of the needle where said needle bears
a neutral relation to two opposing hooks of the loop-taker, and to lock the loop,
taker against a change in the direction of rotation thereof at all times other than
when the needle has arrived at said neutral position relatively to two opposite
hooks of the loop-taker.
A further object of the invention is to provide, in connection with the needle-bar-
actuating mechanism, an improved feed-bar and operating mechanism therefor,
whereby the feed-bar will have a movement in parallelism with the sewing-line, and
will be held in parallelism with the line of its longitudinal movement.
Referring to the sheets of drawings and to the several figures thereof, hereunto
annexed, the same characters refer to corresponding parts in all the figures.
Figure 1 is a plan view of the sewing-machine, seen from above in Fig. 2.
Figure 2 is a front elevation, partly in section, seen from below in Fig. 1.
Figure 3 is a horizontal cross-sectional view of the sewing-machine, taken in
line a-a, Fig. 4, and seen from above in said figure; a portion of the bed-plate
of the machine being broken away.
Figure 4 is a front elevation of the machine.
Figure 5 is a sectional end view of the sewing-machine, seen from the left hand
in Fig. 4, and showing the six-hook loop-taker.
Figure 6 is a rear elevation, partly in section, of a portion of the head of the
sewing-nachine, seen from the left hand in Fig. 5.
Figure 7 is a view similar to Fig. 5, of a portion of the head of the sewing-
machine, showing the needle-bar and presser-bar in their elevated positions.
Figure 8 is a side view of the loop-taker and the driver thereof, seen from the
left hand in Fig. 9; and portion of the driver being broken away, and the track-
rolls for supporting the loop-taker being partially shown in dotted lines.

page_text: Figure 9 is a cross-sectional view of the loop-taker, taken in dotted line b-b,
Fig. 8, and showing the driver therefor in side elevation, and partially in section.
Figure 10 is an end. view of the shuttle-driver, seen from the right hand in
Fig. 9.
Figure 11 is an edge view of the loop-taker.
Figure 12 is an under side view of the bed-plate of the sewing-machine, showing
the feed-lever and feed-dog, in elevation, and showing the feed-lever actuator in
cross-section.
Figure 13 is a longitudinal sectional view of a portion of the bed-plate of the
sewing-machine, showing that portion of the feed mechanism shown in Fig. 12
partly in section.
Figure 14 is a cross-sectional view, taken in dotted line c-c, Fig. 13.
Figure 15 is a plan view, partly in section, of a portion of the feed-lever and its
carrier.
Figure 16 is a longitudinal sectional view of a portion of the bed-plate of the
machine, showing the feed-lever, feed-dog, and feed-lever actuator in elevation;
and showing, by full and dotted lines, two positions of the feed-lever.
Figures 17 and 18 are sectional views showing the feed-lever-actuating device
and regulator therefor, in two different positions.
Figure 19 is a cross-sectional view of the feed-lever actuator, taken in dotted
line d-d, Fig. 17.
Figure 20 is an isometrical perspective view of the eccentric-strap of the feed-
lever-actuating device.
Figures 21 and 22 are plan and side views, respectively, of the eccentric of the
feed-lever-actuating device.
Figures 23 and 24 are cross-sectional views, taken in dotted line e-e, Fig. 16,
and showing, respectively, two different positions of the eccentric-strap and feed-
lever of the feed mechanism.
Figure 25 is a sectional view showing a loop-taker-supporting track-roll and a
track-roll carrier.
:
Figure 26 is a vertical cross-section of a portion of the sewing-machine, taken
in dotted line ƒ—, Fig. 2, and looking toward the left hand in said figure. This
figure shows the tension-actuating device in its normal or ineffective position.
Figure 7 is a similar sectional view of a portion of the mechanism shown in
Fig. 26, and showing the tension-actuating device in its elevated or effective
position.
Figure 28 is a front view of a portion of the needle-bar, showing, in cross-section,
the resistance device secured thereto.
Figure 29 is a right-hand side view of the resistance device secured to the lower
end of the needle-bar.
Figure 30 is a cross-sectional view, taken in dotted line g-g, Fig. 28, looking
downward in said figure and showing the resistance device in plan view.
Figure 31 is a longitudinal section of a portion of the reversing-driving mechanism
of the sewing-machine; said figure showing, in full and dotted lines, two different
positions of the shiftable clutch member and its actuator..
Figure 32 is a side view of the loop-taker and a portion of the needle-bar
mechanisin, showing the needle in its lower dead-center position, with a hook of
the loop-taker in the position it occupies immediately before engaging the loop;
said figure showing a portion of the framework in dotted lines, and showing a piece
of fabric being operated upon.
Figure 33 is a front view of the mechanism shown in Fig. 32.
Figure 34 is a diagrammatic view, illustrating a series of successive relative
positions assumed by the needle, loop-taker, and needle-bar-actuating crank during
one cycle of movements of the needle-bar.
Figure 35 is a diagram illustrating the relative paths of movements of the needle
and loop-taker, and also indicating their relative velocities.
Figure 36 is a diagrammatic view of the loop-taker, shown in full. and dotted

page_text: lines, of nine successive positions of one book of the loop-taker, and also showing,
in dotted lines, nine successive positions of the loop carried by said hook; said
figure also denoting the points of engagement and disengagement of the loop-taker
driver with said loop-taker.
Figure 37 is a diagrammatic view, showing the needle in a neutral position
relatively to two opposing hooks of the shuttle, and showing the clutch of the
reversing device in its shifting position; said figure being intended to show the
peedle, the shuttle, and the clutch in the proper relative positions for effecting a
change in the direction of rotation of the shuttle.
Figures 38, 39, 40, 41, 42, and 43 are detached views of the loop-taker, the
needle, and a portion of the needle-bar and needle-bar-actuating devices with a
piece of fabric in position to be operated upon; said figures illustrating,
respectively, six successive steps in the operation of said parts in forming and
drawing out one loop and drawing up a preceding loop to form a lock-stitch.
Figures 44, 45, 46, 47, 48, and 49 are views similar to Figs. 38, 39, 40, 41, 42,
and 43, respectively, showing six corresponding, successive positions of the same
parts in the operation of forming a chain-stitch.
Figures 50, 51, 52, 53, and 54 are views similar to Figs. 44, 45, 46, 47, and 48,
respectively, showing six corresponding, successive positions of the same parts in
the operation of forming a lock-chain stitch.
Similar characters designate like parts in all the figures of the drawings.
The framework F of the machine may be of any suitable character, and comprises
the horizontal bed-plate 2, having the depending bracket 2¹, the removable throat-
plate 3; the hollow upright 4; the hollow horizontal arm 5; and the vertically-
disposed needle-bar-receiving head 6 at the outer end of the arm 5 above thé
throat-plate 3.
The stitch-forming mechanism preferably comprises, in part, a reciprocatory.
needle-bar supported at opposite ends thereof in a tubular presser-bar which is in
turn supported in bearings in the head of the machine; a loop-taker supported for
rotary movement in a plane oblique to the path of movement of and below the
needle-bar and having a series of hook-formative recesses or loop-receiving spaces
in the periphery thereof, the walls of which hook-formative recesses constitute
opposing hooks adapted, respectively, for engaging the loop of the needle-thread
when the loop-taker is rotated in opposite directions; means for simultaneously
imparting relatively-varying movements of a predetermined ratio to the needle-
bar and loop-taker; and fabric-feeding mechanism controlled by the needle-bar
and loop-taker-actuating means, all of which will be hereinafter more fully
described.
The needle-bar or needle-carrier (designated by N) and the presser-bar or
fabric-clamp (designated by N2) are preferably axially coincident and practically
constitute a unitary device having separate functions, and may consistently be
termed "the combined needle-carrier and fabric-clamp."
As shown most clearly in Figs. 5 and 6 and Figs. 38 to 54, inclusive, the loop-
taker is shown as a duplex three-hook loop-taker; it having two sets or two series
of oppositely disposed loop-engaging hooks, each set comprehending three hooks,
and the hooks, of one set alternating with those of the other set, rendering the
loop-taker reversible so that it may be used in connection with the reversing
mechanism (hereinafter described) for making a lock-stitch or chain-stitch; one
set of hooks being operative for engaging the loop when the loop-taker is rotated
in one direction to form a lock-stitch, and the other set of hooks being operative
for engaging the loop when the loop-taker is rotated in the opposite direction to
form a chain-stitch; but it will be understood that the loop-taker-if to be used
for forming but one kind of stitch-might have but one set of three correspondingly-
dispused books; therefore the term "three-hook loop-taker," as hereinafter
employed, may be considered to apply to a loop-taker having either one or two sets
of three hooks.
As shown niost clearly in Figs. 2, 4, and 6 of the drawings, the loop-taker S is
✓

page_text: supported below the bed-plate and needle-bar N for rotary movement in a plane
obliquely to the path of movement of the needle-bar upon circumferentially-disposed
track-rolls 27, as hereinafter more fully described.
The loop-taker S, which is shown of discoidal conformation, comprises an
annularly-recessed or cup-shaped member 7, having an inwardly-projecting tubular
stem or
hub 7, an externally-convex member 8 having a tubular stem or hub 81
which telescopes with the hub 71 of the member 7, as shown in Fig. 9 of the
drawings. The member 7 constitutes the cop-case of the loop-taker, and the
member 8 constitutes the cap for the open side of the cop-case. The member 7 has
its hub 7 fitted to rotate freely within the hub 81 of the member 8, so that the
movements of said members may be practically independent of each other.
The cop-spool, or bobbin K, is carried within the case of the loop-taker, upon the
hub 8 of the member 8, as shown in said Fig. 9.
For securing the two members of the loop-taker together and at the same time
permit a free movement of one member relatively to the other member, a detent is
provided, which is preferably in the nature of a headed-pin 9, 'fixed at the end of
the shank within the hub 71 of the member 7, and having its opposite headed end
split longitudinally, as at 91, to form resilient holding-arms 'adapted for engaging
the interior of the hub 81 of the member 8 for holding said member in place
relatively to the member 7, as will be understood by reference to Fig. 9.
The loop-taker S is provided at one side thereof with a tension device T³,
adapted for regulating the lower thread, as will be hereinafter described.
The loop-taker S has, formed in the periphery thereof slightly at one side of the
center, a series of needle-receiving grooves 10 into which the lower end of the
needle extends during the reciprocation thereof. The loop-taker also has, formed
in the perimeter thereof, a set of three hook-formative recesses, (see Figs. 5 and 8,)
each of which extends transversely through the periphery of the loop-taker and is
designated by b. The opposite walls of each recess form two opposing loop-
engaging hooks, those hooks located at one side the successive recesses b being
designated by e, f, and g, respectively, and those hooks located at the opposite side
of said successive recesses 6 being designated by el, f¹, and g; thus it will be seen
that the walls of the successive recesses form two sets of independent hooks, one
set alternating with the other set.
The hooks e, f, and 9 are adapted, as illustrated in Figs. 38 to 43, inclusive, for
engaging the loops of the needle-thread W, as these are formed, and for carrying
the same around the loop-taker in the direction of the arrow shown in said figures,
to inclose the lower thread W₁ and form a lock-stitch; and the hooks e', f¹; and ġi
are adapted for engaging the loops of said needle-thread when the loop-taker is
rotated in the reverse direction, as indicated by the arrows in Figs. 44 to 49,
inclusive, and for carrying the same through preceding loops to form chain-stitches,
as will be hereinafter more fully described.
The member 7 of the loop-taker is shown having three pairs of circumferentially-
disposed driver-sockets 22, formed in one side thereof, said pairs being substantially
concentric to the axis of the loop-taker and equidistantly disposed relatively to one
another, as shown in full and dotted lines in Fig. 8. These pairs of sockets are
adapted for receiving corresponding pairs of driving-pins 29 upon the driving-
arms 28 of the shuttle-driver H.
For peripherally suporting the loop-taker S at an inclination to the path of
movement of the reciprocating needle N and also for holding the loop-taker against
radial or vibratory movement, an antifriction loop-taker carrier is provided, which
preferably consists of a series of track-rolls 27 (herein shown as four in number)
which are circumferentially disposed relatively to the loop-taker and are supported
for rotation upon track-roll carriers 27. These carriers, which constitute combined
supporting and adjusting means for the track-rolls, are herein shown in the nature of
crank-studs, one end of each of which constitutes the journal upon which the track-roll
is supported, and the opposite end of which is supported for rotative adjustment in
a bearing formed in the bracket 2' of the machine; and as a means for securing

page_text: the track-roll carrier. in its adjusted position, that end 27" of the carrier which is
journaled in the bracket is preferably bored and screw-threaded, axially, and said
end is also slitted, longitudinally, to render the same expansible; and a wedge-
screw 27, or a screw having wedge-like or buttress screw-threads, is screwed into.
this end of the stud 271 with its bead in bearing engagement with the bracket 21.
This screw will be of such construction that when the head thereof comes, in
bearing contact with the bracket, a slight rotative movement of the screw will
cause the wedge-like faces of the screw-thread to ride upward upon the similar
faces of the internal threads of the carrier 27', causing the resilient walls thereof to
spread outward and tightly impinge the bearing, as will be understood by reference.
to Fig. 25 of the drawings.
It will be understood, however, that the construction and organization of the
supporting device for the track-rolls and also the particular organization shown in.
the drawings may be modified without departure from this invention.
The track-rolls will, in practice, usually be of similar construction and inter-:
changeable, and will be so disposed about the periphery of the loop-taker that
during the rotation of said loop-taker not more than one hook-formative recess of the
series will come in juxtaposition to a track-roll at one time; and said track-rolls
will usually be peripherally grooved to receive the perimeter or track 12' of the
loop-taker, which track is preferably wedge-shaped in cross-section, as shown in
Fig. 9.
To provide a clear, unobstructed space at the upper edge of the loop-taker-
contiguous to the throat-plate, the upper track-rolls 27 engage the periphery of the
loop-taker at points each side of, and considerably remote from, a vertical line.
drawn through the axis of the loop-taker, thereby leaving at the upper part of the
loop-taker a clear space of considerable magnitude immediately adjacent to the
throat-plate and at each side of the path of movement of the needle, through which.
the loop of the needle-thread, after being carried around the loop-taker to inclose
the lower thread, may readily pass during the operation of forming a stitch. This:
organization leaves a considerable portion of the upper face of the loop-taker
accessible from above, which is advantageous in sewing-machines of this class.
It will also been seen by reference to Figs. 1 to 4, inclusive, that the bed-plate 2:
of the machine terminates between the upright 4 and the axial line of the needle-
bar N, and considerably remote from said needle-bar; and that the loop-taker, its
supporting means, and the driver for the loop-taker are all located forward of this
end of the bed-plate, and are readily accessible from the working end of the
machine.
To facilitate the inspection and the cleaning of the loop-taker, the throat-plate 3,.
as shown in said figuies, is removably secured by screws 31 to, and extends from
the front to the rear side of, the bed-plate of the machine, and practically constitutes.
a removable extension for the bed-plate 2; and the throat 31 of the throat-plate
is' located directly below the needle-bar. Thus it will be seen that by the removal
of the throat-plate 3, the loop-taker, the loop-taker carrier, and the driver are!
fully exposed to view and are accessible practically at all sides thereof.
The driving or actuating mechanism for the needle-bar, loop-taker and feed
device of the sewing-machine, is, to all intents and purposes, a unitary mechanism
comprising a train of three co-operatively-connected actuating mechanisms, one of
which mechanisms directly constitutes an actuating mechanism for the needle-bar,
another for the loop-taker, and another for the feed device, and all of which,
mechanisms coact to effect a predetermined comparative relation of movements
between said needle-bar, loop-taker, and feed devices.
:
The combined needle-bar, loop-taker, and feed-actuating mechanism (shown.
most clearly in Fig. 2 of the drawings) preferably comprise two remotely-disposed
shafts D and D', supported in suitable bearings on the framework one above the
other, the shaft D of which is in direct operative relation with the needle-bar N,
and the shaft D' of which is in direct operative relation with the loop-taker S;
an intermediate shaft D2; a one-to-one train of gears E, operatively connecting

page_text: the needle-bar-actuating shaft D and the intermediate shaft D²; and a two-to-
three train of gears E', operatively connecting the intermediate shaft D2 and the
loop-taker-actuating shaft D'.
As a convenient means for gradually retarding the movement of the needle-bar
through the lower part of the downward stroke thereof, and for relatively
accelerating the movement of the needle-bar through the corresponding lower part
of the upper stroke thereof, the needle-bar-actuating shaft D, which is journaled
at or near its opposite ends in suitable bearings 30 in the arm 5 of the machine, is
operatively connected with the needle-bar by means of a crank 31 and a connecting-
link 32, having their centers so located as to effect this end. The crank 31, which
is secured to the outer end of the shaft D, is shown provided at one end thereof
with a weight 31' and at the opposite end thereof with a transverse elongated
bearing 31 in which is journaled the stud or connecting-rod pin 321 on the upper
end of the connecting-rod or liuk 32, which link is pivotally connected at the lower
end thereof to the needle-bar at one side and in the rear of the axis thereof, which
connection is made by a stud or pin 3211 at the lower end of the needle-bar, and
which stud is seated in a socket formed in a strap 33, adjustably secured to the
needle-bar. (See Figs. 5, 6, and 7.)
As a means for directly actuating the loop-taker from the shaft D', and as a
means for holding said loop-taker in fixed peripheral relation with the circum-
ferentially-disposed track-roils and concentric to a fixed axis of rotation, and
thereby prevent radial movement of the loop-taker when a hook-formative recess
comes in juxtaposition to the supporting-face of a track-roll during the rotation
of the loop-taker, there is provided, in connection with the shaft D', a loop-taker-
supporting driver H, which driver, in the form thereof shown most clearly in
Figs. 2, 4, 8, 9, 10, and 33 of the drawings, has a series of radially-disposed driven-
arms 28, each having, at the free end thereof, two outwardly-projecting loop-taker-
supporting driving-pins 29; the pins of the successive arms of the driver being
adapted for successively engaging in the corresponding driver-sockets 22 of the
loop-taker for rotating the same, and also for maintaining said loop-taker as
against radial or vibratory movement during the rotation thereof.
By reference to Figs. 8 and 32 of the drawings, which clearly illustrate the
operative relation of the loop-taker and the driver, it will be seen that each pair
of driver-sockets 22 and each pair of driver-pins 29 are so disposed relatively to
two opposing hooks, one of each set of hooks, that the three pairs of driver-pins
will successively engage in their respective driver-sockets approximately midway
between two opposing hooks, and in close proximity to the perimeter of the loop-
taker. The particular location of the driver sockets with reference to the opposing
hooks will be such as to obviate the possibility of shearing or cutting off the loop
as the driver-pins engage in their respective driver-sockets.
It will also be understood by reference to Fig. 36, that, owing to the oblique
disposition of the loop-taker relatively to the driver-axis, the successive pairs of
driver-pius will successively engage the loop-taker when said pins have arrived at
the positions marked "x" in Fig. 36, and will release the loop-taker when they
have arrived at the positions marked "y" in said figure; said positions being at
opposite sides of a vertical line drawn through the loop-taker and slightly above
a horizontal line drawn through the axis of said loop-taker; and that when one of
the driver-arms is in a vertical position and out of engagement with the loop-taker,
the pins of the other two arms of said driver are fully extended into their
respective driving-sockets in the loop-taker, thereby so taking hold of said loop-
taker as to control the same against lateral or swinging movement as the hook-
formative recesses pass over the peripheries of the track-rolls, notwithstanding
only four sets of rolls are employed. This construction and organization of loop-
taker and driver materially reduces the wear to which the loop-taker would be
subjected if entirely dependent upon the track-rolls for support; and, consequently,
this construction and organization is conducive to accuracy in operation.
The one-to-one train of gears E, which operatively connects the needle-bar-

page_text: actuating shaft D and intermediate shaft D2, preferably consists of two equal
bevel-gears d and d', respectively, in intermeshing engagement and fixed one to
the needle-bar-actuating shaft and the other to the intermediate shaft.
The two-to-three train of gears E', which operatively connects the intermediate
shaft D, and the loop-taker-actuating shaft D', is shown in Figs. 2, 3, 4, 26,
and 31, in the nature of a reversing-driving device, and consists of a relatively-
small bevel-gear d, secured to the intermediate shaft D2 and two relatively-large
bevel-gears d³ and d, revolubly mounted upon the loop-taker-actuating shaft D',
and meshing with the relatively-small gear d' at opposite sides, respectively,
thereof; a clutch device C being provided for alternately locking said gears, d³
and d to the shaft D', and for locking one of said gears to the other gear and to
the said shaft before releasing said other gear from locked engagement with said
shaft, as will be hereinafter described.
It will be understood that the invention is not limited to the employment of the
particular reversing-driving device shown in Figs. 2 and 3 of the drawings as this
inay be modified without departure of my invention, or may be entirely dispensed
with without detriment to the other features of this invention.
The improved organization of driving mechanism herein before described secures
to the needle-bar-actuating and intermediate shafts simultaneous movements of
rciatively-coinciding velocities, which, for the purposes hereinafter described, is of
Inaterial importance; and it also secures to the loop-taker-actuating shaft and
intermediate shafts simultaneous movements of relatively-varying velocities, the
ratio of which is as two is to three, as is requisite for the proper operation of the
machine when a loop-taker having three-hook-formative recesses-such
described is employed therewith.
as
The intermediate shaft D2 not only constitutes a convenient operative connection
between the needle-bar-actuating shaft and loop-taker-actuating shaft, but also
constitutes a direct actuator for the feed mechanism of the sewing-machine.
From the foregoing description, and by comparison of the several figures of the
drawings, it will be seen, that the organization of driving mechanism is such that,
while the three shafts-i.e., the needle-bar-actuating shaft D, the loop-taker-
actuating shaft D¹, and the intermediate shaft D'-are practically dependent upon
each other for effective operation, each shaft has a special and independent
function to wit, the shaft D reciprocates the needle-bar; the shaft D' rotates the
loop-taker; and the shaft D2 actuates the feed mechanism; and it will further-
more be apparent that each of said shafts and the bearings therefor perform and
sustain a certain and approximately-equal proportion of the entire work, thereby
securing a more perfect balancing of the working parts and also securing a greater
accuracy in the operation, together with durability, than would be the case if one
shaft carried a larger proportion of the load than another.
The combined needle-bar and fabric-clamp, as shown in Figs. 1 to 7, inclusive,
consist of the needle-bar N and presser-bar N2, supported for independent longi-
tudinal movements, one within the other. The needle-bar is preferably in the
nature of a round rod, symmetrical from end to end, and is axially bored at the
lower end thereof to receive the needle N'; which needle is held in place in said
needle-bar in any usual manner-as by a set-screw 35. The presser-bar, which is
preferably tubular in form and which practically coustitutes a guide for the needle-
bar, is supported at the lower end thereof in a bearing 361, formed in the lower end
of the head 6 of the machine-frame; and it is preferably similarly supported at its,
upper end in an adjustable bearing member 36; which bearing 36 is in axial"
alignment with, and adapted for adjustment longitudinally of, the presser-bar and
needle-bar. (See Figs. 5, 6, and 7 of the drawings.)
This bearing member 36 is shown tubular in form, and will usually be externally,
screw-threaded and screwed into a screw-threaded opening formed in the upper
end of the head 6; and in this organization it constitutes the adjustable member of
the pressure-regulating device for the presser-bar; the other member of said.
pressure-regulating device consisting of a spiral-spring 37, surrounding that end of

page_text: the needle-bar N which projects above the upper end of the presser-bar, and has a
bearing in the upper end of the member 36; which spring is interposed between
the upper wall of the member 36 and the upper end of the presser-bar, as most
clearly shown in Fig. 5 of the drawings..
Removably secured to the lower end of the presser-bar by means of the
usual set-screw 38 is a presser-foot 39, which may be of any usual or suitable
-construction.
The adjustable. member 36 and the resistance spring 37 constitute together a
simple and effective pressure-regulating device for the presser-bar, and one by
which the pressure exerted by the spring 37, upon the presser-bar may be quickly
regulated through the simple adjustment of the member 36 inward or outward, as
will be readily understood by reference to Fig. 5.
As shown in Figs. 5, 6, and 7, the presser-bar N³ is cut away at one side near
the middle portion thereof, for a considerable distance, as shown at 39', to form a
slideway for the strap 33, which constitutes the connection between the needle-
bar N and the. link 32 of the needle-bar-actuating mechanism; said slideway 391
being of sufficient length to permit a free and unobstructed reciprocation of the
needle-bar connection, irrespective of the position of the needle-bar relatively to
the presser-bar.
As a simple and effective means for raising and lowering the presser-bar N²,
and also as a means for preventing the accidental rotation of said presser-bar, there
is provided, in connection with said presser-bar, a presser-bar-lifting shaft, or rock-
shaft 40, which carries, at the forward end thereof adjacent to said presser-bar, a
crauk-arm 41, the outer end 41' of which engages in a cam-groove 42 or between
fingers or cam-faces 421 at the outer end of a laterally-projecting arm 43,, which
is fixed at its inner end, as shown in Figs. 5, 6, and 7, to the presser-bar. Said
crank-arm 41 has bearing-faces 41" which engage, respectively, opposite side faces.
of the arm 43 and prevent accidental rotative movement of the presser-bar.
For operating or rocking said presser-bar-lifting shaft 40 to raise or lower the
presser-bar, this shaft is shown provided, at opposite ends thereof, with two
laterally-projecting arms 45 and 46, respectively; the one 45 of which extends
through a transverse opening 47 in, and is operable from the outside of, the arm 5
of the machine-frame, and will be herein termed "the presser-bar-depressing
arm"; the other arm 46, is in the nature of a cam-arm, and is adapted for not
only elevating the presser-bar through the medium of the presser-bar-actuating
shaft, but is also adapted for simultaneously actuating a tension device (designated
in a general way by T) for the upper thread, as will be hereinafter more fully
described; this arm practically constituting a presser-bar-lifting and a tension-
device operator, and may properly be so termed.
The presser-bar-depressing arm 45 is intended to be operated by hand after the
usual manner of operating the presser-bar-lifting arms or levers, in sewing-
machines of ordinary construction; whereas, the presser-bar-lifting arm 46 is
designed to be operated by the knee of the operator from below the bed of the
machine; and for this purpose, there is provided a lifting-rod 48, which usually has
-a pivotal connection, as shown at 481, at its upper end with the said lifting-arm 46,
as shown most clearly in Figs. 26 and 27 of the drawings.
The lower end of the lifting-rod 48 projects somewhat below the bed of the
machine, and is shown operated by a lifting-lever 150, fulcrumed upon a stud 151,
secured to a bracket 152, which bracket may be fixed to the table 531; a portion
of which table is shown in Figs. 2 and 4 of the drawings.
This lifting-lever 150 is shown of the so-called "bell-crank" type, one arm of
which is in bearing engagement with the lower end of the lifting-rod 48, and the
other arm of which depends into a position to be engaged and shifted by the knee
of the operator.
By a comparison of Figs. 2, 26, and 27 of the drawings, it will be seen that when
force is applied to the depending arm in the direction of the arrow in Fig. 2, the
lifting-rod 48 will, through the medium of the lifting-lever, be raised, which will

page_text: rock the lifting-arm 46 of, and partially rotate, the presser-bar-lifting shaft 40,
lifting the presser-bar from the position shown in Fig. 26 to the position showin
in Fig. 27. This operation also causes the cam-arm 46 to actuate the tension
device T, which is carried upon the arm 5 of the machine-frame at a point in
vertical alignment with the path of movement of the cam-arm 46.
In the preferred embodiment thereof shown in Figs. 2 and 4 and 12 to 24,
inclusive, the feed mechanism for the sewing-machine comprises a feed-bar. 50,
which may be of any suitable form. This feed-bar is shown serrated at its upper:
edge and extends through the throat 3" in the throat-plate 3; a feed-bar carrier
or feed-lever 51, pivotally supported for vertical and horizontal oscillation upon a
fulcrum-block or feed-lever carrier 52; a link 53, connecting the feed-lever carrier
and feed-bar, and adapted for maintaining the feed-bar in substantial parallelism
with the line of its longitudinal movement; a feed-lever actuator U, embodying
a shiftable eccentric 54, having an obliquely-disposed eccentric-strap 54' in:
operative connection with the feed-lever; rotating mechanism for said eccentric ;
an eccentric-shifting member or wedge R in operative connection with the:
eccentric 54, and adapted for shifting said eccentric to increase or decrease the
effective throw thereof; and an adjusting device or wedge-actuator R' in operative
connection with, and adapted for operating, the wedge, all of which will be,
hereinafter more fully described.
The feed-bar 50 is shown (see Figs. 12 and 13) pivotally connected at 50¹ at.
its forward end to the forward end of the feed-lever 51, and is pivotally connected
at 50 to the forward end of the link 53, which link maintains a position:
substantially in parallelism with the longitudinal axis of the forward end of the,
feed-lever 51; and the pivot-points 50 and 5011 are shown. having their common:
axis in parallelism with the line of movement of the feed-dog 50. The opposite
end of the link 53 is shown pivoted to the bed-plate of the machine in alignment.
with the vertical axis of movement of the feed-lever carrier; said link being so.
connected relatively to the feed-bar and feed-lever as to have at all times a.
parallel movement relatively to the forward end of said feed-lever,. as will be.
readily understood by reference to Fig. 3 of the drawings, in which two positions
of the feed-lever and link are shown in full and dotted lines, respectively. Said
feed-bar 50 also has an elongated opening 491 at the rear end thereof which,
receives the shoulder of a screw 49, inserted in the feed-lever; whereby a slight:
play is allowed between the feed-lever and feed-bar.
The feed-lever 51, which may be of any usual general construction, is shown.
recessed, as at 51, near the middle portion thereof, to receive the fulcrum-block or.
feed-lever carrier 52 upon which carrier the feed-lever is adjustably fulcrumed..
This feed-lever carrier is shown vertically bored, as at 521, to receive a bushing 55,.
which constitutes the pivot-bearing for said carrier, and through which is extended,,
in a vertical direction, the screw 56 by means of which said pivot-bearing is.
fixedly secured to the bed of the machine, as most clearly shown in Figs. 13, 14,.:
and 15 of the drawings; said screw being extended through the bushing or pivot-
bearing 55, and screwed into the bed-plate 2, the shank of said screw constituting..
a journal or pivot upon which the fulcrum-block swings.
The fulcrum-block or feed-lever carrier 52 is shown horizontally and trausversely.
bored at one side of the pivot-bearing, as shown at 57' in Figs. 14 and 15, to receive
the fulcrum-pin 57, which constitutes the horizontal pivot and also one element of
an adjusting device for the feed-lever.
In view of the fact that the feed-lever is herein shown directly carried upon the
fulcrum-pin and the fulcrum-pin is carried on the fulcrum-block, the fulcrum-block:
and fulcrum-pin will be hereinafter referred to as the "main feed-lever. carrier 52"
and the "auxiliary feed-lever carrying and adjusting device 57," respectively.
The fulcrum-pin or auxiliary carrier, which adjustably connects. the feed-lever
and main feed-lever carrier, is shown in the nature of a pin 57, journaled in the
transverse bore 57' of the main-carrier and has trunnions 58 and 581 at opposite.
ends, respectively thereof, which are eccentrically disposed relatively to the
B

page_text: central portion of the fulcrum-pin and are journaled in the side walls 60 and 60' of
the feed-lever.
One of the trunnions, as 58, projects beyond the outer face of the feed-lever and
is shown provided with a laterally-projecting arm 61 which constitutes an actuator
for, and by means of which the auxiliary feed-lever carrier or fulcrum-pin may be
partially rotated to effect a vertical adjustment of the feed-lever relatively to the
main-carrier 52, as will be understood by comparison of Figs. 13, 15, and 16 of the
drawings.
Stop-abutments are provided on one side of the feed-lever in position for limiting
the throw of the feed-lever carrier, as shown in Fig. 16.
As a means for clamping the fulcrum-pin to prevent accidental rotative movement
thereof after adjustment, the bearing 57' in which the fulcrum-pin is journaled is
slotted or divided at one side thereof, as shown at 62, to form resilient walls; and
a clamp-screw 63 is extended through one wall and screwed into the adjacent wall
to draw said walls together and impinge the fulcrum-pin sufficiently to prevent
accidental movement of said pin. This clamp-screw also constitutes a key for
holding the fulcrum-pin against longitudinal movement in its bearing. Said
fulcrum-pin is peripherally grooved, as shown at 57", and the shank of said screw
engages in said groove, as shown in Figs. 14 and 15. This forms a simple and
convenient means for locking the fulcrum-pin against longitudinal movement and
facilitates the assembling and disassembling of the parts.
In Figs. 13 and 16, the feed-lever fulcrum is shown in full lines adjusted so as
to bring the feed-lever into a position for operating upon thick material, the feed-
dog being shown in its highest position; the dotted lines representing the feed-lever
in position to operate upon thin material.
When it is desired to effect an adjustment of the feed-lever, or shift the same-
for instance, from the full-line to the dotted-line position shown in Fig. 13-it is
simply necessary to shift the actuator 61 from the position shown in full lines in
Fig. 16 to the position shown in dotted lines in Fig. 13, which partially rotates the
fulcrum-pin and shifts the trunnions 58 and 58¹ from their lower to their higher
positions, as will be understood by comparison of Figs. 13, 14, and 16.
The feed-lever actuator, (see Figs. 12 and 13 and 16 to 24, inclusive,) preferably
comprises the eccentric-actuating shaft D2, which has been herein before described
as the intermediate shaft; a wedge-like eccentric carrying and shifting member R,
carried upon the shaft or eccentric-actuator D2, and shiftable longitudinally of the
axis of said shaft; a variable eccentric 54, carried upon the wedge-like eccentric-
shifting member and adapted to be shifted transversely of the axis of the shaft D
upon a movement of the eccentric-shifting member longitudinally of said shaft, and
having a peripheral eccentric-strap-receiving groove or guideway 54" which is
obliquely disposed relatively to the plane of movement of the eccentric; and a
two-part annular eccentric-strap 54', carried on the obliquely-disposed guideway,
and having a universal connection with the feed-lever 51.
The eccentric carrying and shifting member is shown as a wedge-like sleeve R,
which is mounted for longitudinal adjustment upon the shaft D³, and has at the
lower end thereof an obliquely-disposed wedge portion 66, which is circumferentially
eccentric to the axis of said shaft. This obliquely-disposed portion extends into a
complementary bore formed through the eccentric 54 with its axis oblique to the
axis of rotation of said eccentric, as will be readily understood by a comparison of
Figs. 17 to 24, inclusive, of the drawings.
For the purpose of changing the eccentricity of the eccentric relatively to said
shaft, an adjusting device R¹ is provided in connection with said wedge, which
adjusting device is adapted for moving the wedge or eccentric-shifting member
longitudinally of the shaft D' and also for holding said wedge in its shifted or
adjusted position.
To secure the eccentric 54 against longitudinal movement relatively to the
shaft D2; said eccentric is shown in Figs. 2 and 4, supported between the bevel-
gear d² which is shown fixed to the lower end of the shaft D2-and a journal-

page_text: bearing 67 in which the eccentric-shifting member R is journaled, which bearing
constitutes a portion of the framework of the machine.
#
In practice, the eccentric 54 will usually have, at the outer side thereof, a
slide 68 which fits a slideway 581 in the upper face of the gear d'; and the
eccentric-adjusting member R will usually be loosely mounted upon the shaft D³,
as shown in Figs. 17 and 18, it being held against rotation relatively to the
shaft D' by reason of the oblique disposition of the wedge portion 66 of the
eccentric-shifting member with respect to the eccentric 54, which eccentric is held
against rotative movement relatively to the gear d² by reason of its sliding engage-
ment with said gear; thus it will be evident that-owing to the oblique disposition
of the wedge relatively to the axis of rotation of the eccentric 54 and shaft D-
the shaft D cannot rotate without carrying the eccentric and the eccentric-shifting
member with it.
The wedge-adjusting device R', which is adapted for shifting the wedge longi-
tudinally of the shaft D2 and for holding the same in adjusted position, preferably.
consists of a stud 70, journaled for rotative movement in a bearing 70¹ on the
framework F; an eccentrically-disposed crank-pin 71 upon the inner end of the
stud; a collar 72, fixed to the upper end of the eccentric-shifting member R and
having a peripheral groove 731 in which is seated the crank-pin 71; said collar
being fixed to the eccentric-shifting member preferably by a set-screw, as shown
in Fig. 17. The stud 70 of the wedge-adjusting device will usually be removably
secured in the bearing by means of a sliding bolt or pin 73, which is shiftably
carried in a transverse opening in the stud 70 and normally projects beyond the
outer face of said stud and enters an annular groove formed in the face of the
bearing 70¹.
This sliding bolt or pin 73 is normally held in engagement with the walls of the
annular groove 75 by means of a bolt-shifting member 76, which is herein shown
as a screw having a conically-tapered shank, which screw has a screw-threade
bearing in an opening which is formed in the outer end of the stud 70, and which
intersects the recess in which the sliding bolt is seated. The bolt-shifting screw
has a bearing at its inner tapered end against the inner end of the sliding bolt, and
is adapted when moved longitudinally in one direction, for moving the sliding bolt
outward to force the same into engagement with the walls of the annular groove,
and when moved in the opposite direction for releasing the sliding bolt from engage-
ment with the walls of said groove to facilitate the removal of the adjusting-stud 70.
This screw will usually have a knurled head to facilitate the turning of the screw
to effect the requisite adjustment thereof.
It will be obvious that any suitable bolt-shifting member may be employed to
actuate the sliding bolt of the wedge-adjusting device to lock the same in its
adjusted position.
By the construction and organization of wedge-adjusting means (herein described
and shown most clearly in Figs. 17 and 18,) the wedge-shifting stud may be quickly
assembled and disassembled relatively to the eccentric-shifting member or wedge R
and may be readily adjusted and locked in its adjusted position.
The eccentric-strap 54', which is carried on and surrounds the guideway of the
eccentric 54 and which is shown made in two parts secured together in any suitable
manner, has a perimetrical extension 77, in the side face of which is formed a ball-
receiving socket 77, adapted for receiving a ball 80 upon the inner end of the
feed-lever 51.
The socket 77' in which the ball 80 is seated is open and conically flared at that
side of the extension 77 contiguous to the feed-lever, as shown in Figs. 12 and 19;
and one side wall of said socket is transversely bored and screw-threaded to
receive a screw 81, the inner end of which screw is concaved, as shown in dotted
lines in said figures, to fit the adjacent curvilinear face of the ball 80 on the feed-
lever 51; said concaved end of the screw. 81, forming a bearing for one side of,
and holding the ball in place in, the socket 77, thus facilitating the take-up of
wear.

page_text: By this construction and organization of ball-and-socket connection between the
feed-lever and feed-lever actuator, the feed-lever may be quickly disconnected
from the eccentric-strap 54' of said actuator by simply releasing the screw 81 from
engagement with the ball 80, and partially rotating the eccentric-strap to draw the
same away from the end of the feed-lever.
A comparison of Figs. 12, 13, 16, 17, 18, 19, 23, and 24 will show that the
eccentric-strap has, during the rotation of the eccentric, a continuous circuitous
movement in an elliptical path at its point of connection with the feed-lever, which
will cause the inner and outer ends of the feed-lever-owing to the peculiar pivotal
support of said feed-lever at the middle portion thereof to describe an ellipse, the
major and minor axes of which may be varied in length by adjusting the
eccentric 54 transversely of the shaft D² to increase or decrease the effective throw
or eccentricity thereof. This change in the eccentricity of the eccentric may, as
hereinbefore stated, be quickly effected by shifting the eccentric-adjusting wedge
or member R longitudinally of the shaft D2 through the medium of the wedge
adjusting device R¹.
1
The feed-lever, has a universal connection-to wit, a ball-and-socket connection-
with the eccentric-strap at one side only of and remote from the axis of movement
of said eccentric; and by reason of this "one-side" connection, and by reason of
the peculiar circuitous movement of the eccentric-strap--due to the peculiar
organization of the strap and eccentric, as before described-a truly elliptical
movement is imparted to the outer end of the feed-lever, without imparting rotative
movements to said feed-lever about its longitudinal axis, and, consequently, a
corresponding elliptical movement is secured to the feed-dog at the "feed" end of
said lever.
"
A practical operation of the feed mechanism herein described in connection with
a sewing-machine has demonstrated the fact that a feed-lever having a uniform;
continuous feed movement in an unbroken, elliptical path, has material advantages
over the ordinary "four-way" feed mechanism, in that the feed-bar carried by the
feed-lever engages the fabric with a gradually-increasing pressure during the first
stages of the advancing movement thereof, and this pressure is gradually released
during the latter stages of said advancing movement, which effects a uniform feed
movement of the fabric, without-as, in some cases-so tightly impinging the
fabric between the presser-foot and feed-bar, on the inauguration of the feed
movement thereof, as to cause the fabric to buckle or feed unevenly.
Furthermore, by the use of a feed-lever actuator, embodying an eccentric and an
eccentric-strap, organized and connected relatively to the feed-lever in the manner
shown and described, not only a different movement is secured to the feed-lever
than is secured to the feed-lèver of any ordinary four-way feed mechanisni
employing a two-way cam or cams for effecting the feed movement of the
feed-lever, but also a smooth, unabrupt, and practically noiseless movement is
secured to the feed-lever in contradistinction to the abrupt, noisy movements of the
feed-lever of any ordinary feed mechanism.
By the term "non-rotative elliptical movement," as employed in certain of the
claims to define the peculiar movement of the feed end of the feed-lever, is meant
the elliptical, circuitous movement imparted to the feed ends of the feed-lever,
without rotation of said feed-lever upon its longitudinal axis..
:
The reversing-driving device, as shown most clearly in Figs. 2, 4, and 31,
preferably comprises the two rectangularly-disposed shafts D1 and D2, which may
be termed the "driven " and "driving" shafts, respectively; a relatively-small
driving-gear d², carried on the lower end of the driving-shaft D'; two oppositely
rotative and alternately effective driven-gears d³ and d, carried upon the
driven-shaft D, and meshing with opposite sides of the driving-gear d², and adapted.
for respectively rotating the driven-shaft in opposite directions; a clutch C,
shiftably carried on the driven-shaft D', and adapted for effecting fixed
operative relation between the driven-shaft D and one or the other of the

page_text: driven-gears d³ or d'; and a locking device c', adapted for automatically engaging
and locking the clutch C in its adjusted or shifted positions.
The two driven gears d³ and d, which are of relatively-large diameter as
compared with the diameter of the driving-gear d, are preferably equal and
interchangeable, and are revoluhly mounted directly upon the driven-shaft D¹ with
the inner adjacent faces of their hubs 82 and 82¹ in bearing contact, as shown in
Fig. 31. Said gears a³ and d are held against movement longitudinally of the
shaft D¹ between suitable abutments upon said shaft, one of which abutments is in
the nature of a collar 83 which is fixed to the shaft by a set-screw and abuts
against the outer end of the hub of one of said gears, and the other of which
abutments is shown as the shaft-bearing 83¹ which abuts against the opposite end
of the hub of the other driven-gear.
The inner adjacent ends of the hubs 82 and 82¹ of the gears d³ and d' are shown
notched or cut away at one side thereof to form clutch-pin sockets 84 and 841,
respectively, which are adapted for registering, one with the other, at certain
points in the rotation of the gears d³ and d', and are adapted for receiving,
reciprocally, a clutch-pin 85 on the shiftable clutch-member 86 of the clutch
device C, which is carried by and rotates with the driven-shaft D¹.
The clutch C, which is in the nature of a pin-clutch and which is shiftably
carried by the driven-shaft D', comprises the angular member 86, seated in a
corresponding keyway or channel 87, formed longitudinally in the periphery of the
shaft D'. This member 86 is provided at one end thereof with a clutch-pin 85,
which normally engages in one or the other socket 84 or 84¹ of one or the other
gear dor d', as will be understood by a comparison of Figs. 2, 4, and 31 of the
drawings.
An actuator or pull is provided in connection with said clutch for moving said
clutch longitudinally of the shaft D¹, which actuator is shown in the nature of a
peripherally-knurled collar 88, mounted for shifting on the shaft D', and secured
to the clutch-member 86 by means of a screw 89. This actuator is shown provided
with a locking device C', which is preferably in the nature of a spring-actuated
detent carried by the actuator 88 in position and adapted for reciprocally engaging
in locking notches 90 and 90', formed in the periphery of the driven-shaft D'
These lock-notches 90 and 90¹ are shown in horizontal alignment with one another.
and set a distance apart corresponding to the extreme distance traversed by the
clutch-member 86 in engaging the clutch-pin 85 with one or the other of the
driven gears d³or d', as will be readily understood by reference to Fig. 31 of
the drawings.
The locking device C¹ preferably consists of a conically-pointed lock-pin 91,
seated in a socket formed through the collar 88. A spiral-spring 92 in bearing
engagement at its inner end with said lock-pin and an adjusting-screw 92¹ screws
into the outer end of said socket with its head in bearing engagement with the
spiral-spring.
It will be understood that the specified construction of the locking device may
be changed without departure from this invention; and that the organization and
arrangement of said locking device, relatively to the clutch-member 86, may also
be modified within the scope of this invention.
In Figs. 2, 4, and 31, the reversing mechanism is shown operative for rotating
the shuttle in the direction designated by the arrow in Fig. 2 as required
for forming a lock-stitch; the clutch C being shown in engagement with the
driven-geard, the driven-gear d running free upon the shuttle-actuating
shaft D¹.
When it is desired to rotate the loop-taker in the opposite direction to form a
chain stitch, it is simply necessary to shift the clutch C, by means of the actuator,
to the position shown in dotted lines in Fig. 31, which carries the clutch-pin of
the clutch-member into engagement with the driven-gear d³. The clutch-pin
engages one driven-gear and locks the same to the shuttle-actuating shaft D¹ before
..

page_text: releasing the other driven-gear from locked engagement with said shaft, which is
a matter of considerable importance, as it maintains a proper co-operative
relation between the needle-actuating mechanism and loop-taker actuating
mechanism during the operation of changing the direction of movement of the
loop-taker.
As a means for securing the proper tension to the upper and lower threads W
and W, respectively, there are provided two tension devices T and T³, respectively.
The tension device T is supported preferably upon the sewing-machine arm 5 in
close proximity to the spool-carrier V, and is adapted for regulating the tension of
the upper thread; whereas the tension device T³ is carried by the cap or thread-
guiding member 8 of the loop-taker as shown in Fig. 32, and is adapted for
regulating the tension of the lower thread W¹.
A retracting device or take-up T¹ is provided at the upper end of the needle-bar
which engages the needle-thread at a point intermediate to the tension device T and
the needle N' which acts during the latter stages of the upward stroke of the needle-
bar to draw the loop-end of the needle-thread upward and above the path of
movement of the loop-engaging hook of the loop-taker.
For preventing the accidental retraction or the premature taking up of the
needle-thread W-after the loop L has been formed, and prior to its engagement
by one of the loop-engaging hooks of the loop-taker, and during the early part of
the upward stroke of the needle-bar-there is provided a resistance device T²,
which is shown carried by the needle-bar in close proximity to the lower end
thereof.
This resistance device T2 will be of a construction and organization adapted for
exerting a resistance upon the upper thread at a point just above the needle
sufficient to prevent a retractive movement or backward slipping of the loop-end
of the needle-thread during the earlier part of the upward stroke of the needle-bar,
which backward slipping might accrue from the inherent elasticity of the needle-
thread, due to the tautness of that portion of the needle-thread above the
resistance device.
:
Briefly stated, the tension device T preferably consists of the axially-recessed
carrying-member 93, secured to and extending through the upper wall of the
frame-arm 5 with its axis in vertical alignment with the rocker-arm 46 on the
presser-bar-lifting shaft 40; tension-plates carried on said member near the upper
end thereof; a lifting-pin 94, seated in the recess of the carrying-member and
extending below the lower end thereof; a thrust-plate 94', supported upon the upper
end of the lifting-pin 94, and normally held in bearing engagement with the upper
tension-plate by means of a spiral-spring 95, located between the thrust-plate and
an adjusting-nut 95', screwed upon the upper end of the carrying-member 93. The
upper end of the carrying-member is shown bifurcated, and the thrust-plate is
recessed so as to fit around and between the bifurcated ends of said carrying-
member that is to say, the thrust-plate 941 will have two concentric substantially-
semicircular recesses formed therethrough, which recesses are separated by a
bridge-like portion, which, when the parts of the tension device T are assembled,
as shown in Figs. 26 and 27, rests upon the upper end of the lifting-pin 94.
The lifting-pin 94 has a head at the upper end thereof, and the axial recess
through the carrying-member 93 is enlarged at the upper end thereof to form a
shoulder for limiting the downward movement of the lifting-pin, the head of said
lifting-pin resting upon said shoulder when the pin is in its depressed position.
The lower end of the lifting-pin 94 normally rests upon the cani-face 46' of the
rocker-arm 46.
As will be understood by reference to Figs. 26 and 27, the tension device T is
controlled, in so far as its effective or ineffective operation in concerned, by the
operation of the presser-bar-lifting shaft 40. When the presser-bar is in its lowest
position, the lifting-pin of the tension device is depressed and the tension-plates exert
a tension upon the upper thread; and when the presser-bar of the machine is
elevated, as shown in Fig. 27, the lifting-pin 94 will be lifted by the arm 46 upon

page_text: the presser-bar-lifting shaft, which will carry the thrust-plate 94¹ upward and
away from the upper tension-plate 931, thus releasing the tension upon the thread.
This construction and organization of the tension device, whereby this is
controlled by the operation of the presser-bar, is of considerable importance, as it
enables the operator to withdraw the work, after lifting the presser-bar, without
regard to the tension of the thread, and without drawing off a considerable length W
from the spool by hand as is customary with sewing-machines of ordinary con-
struction, to prevent the breaking of the thread as the work is withdrawn from below
the presser-foot.
The tension device Ts for the lower thread W₁ is shown in the nature of a disk
notched at the periphery thereof (see Fig. 32,) to form two oppositely-disposed
thread-impinging arms 96 and 96¹.. This tension device is secured to the outer face
of the cap 8 of the loop-taker, near the periphery thereof, by a pin or other
suitable device; and the two arms 96 and 96' thereof extend partially over the
notched portion 8" of said cap. The lower thread W₁ of the cop or bobbin (not
shown,) which is carried on the hub of the member 8 of the shuttle, is threaded
through a transverse opening 97 or 97' in said member, and is carried over and
under one of the resilient. arms of the tension device T3 in the manner shown in.
said Fig. 32.
The resistance device T2, which is secured to the lower end of the needle-bar, as
described, and which is adapted for holding the needle-thread against premature
retractive movement, is shown consisting of two spring-pressed tension-plates 98
and 98, carried at the outer end of an arm 99, secured to the lower end of the
needle-bar by a set-screw 99'. The plates 98 and 98' are carried upon the shank
of a screw 100, which has an adjustable bearing at its inner end in a screw-
threaded opening at the outer end of the outer arm 99, and which is surrounded*
by a spiral-spring 100', seated between the head of said screw and the outer
tension-plate 98¹.
The retracting device T¹-which, as before stated, is adapted for taking up the
increment of the loop-end of the needle-thread immediately preceding the final
drawing up of the same to complete the stitch, and is adapted for drawing said
loop-end out of the path of movement of, and to prevent its re-engagement by, the
hook of the loop-taker-is preferably in the nature of a projecting arm having a
thread-guiding eye at the outer end thereof, and is carried at the upper end of the
needle-bar. This retracting device T¹ is so disposed relatively to the tension
device T that the thread-engaging end of said device will be located somewhat
below the horizontal plane of the tension-plates of the tension device T-when the
needle-bar is in its depressed position; and in consequence thereof, said device T
will, during the first part of the upward stroke of the needle-bar, have no
retractive effect upon the needle-thread, and will only be effective for this purpose,
during the latter part of its upper stroke; at which part of the separate stroke,
it will owing to the increased distance of the thread-engaging eye upon the
tension device T-act to draw up the needle-thread, and consequently reduce the
size of the loop released from the book of the shuttle and draw the same into close
proximity with the fabric and out of the path of movement of the hooks of said
shuttle. This peculiar taking-up or "in-drawing" of the loop-end of the needle-
thread is accomplished with great rapidity, owing to the peculiar connection of the
crank of the needle-bar-actuating shaft with the needle-bar at one side the axis
thereof, as before stated, which connection secures to the needle-bar downward and '
upward strokes of relatively-varying velocities; the movement of the needle-bar
being retarded through the latter stages of the downward stroke thereof and
being relatively accelerated through the earlier stages of the ascending,
movement thereof, as will be understood by reference to the graphical diagrams,"
Figs. 34 and 35.
Referring again to the loop-taker reversing-driving device hereinbefore described,
it will be noticed that said device has practically two functions, it being 'adapted

page_text: for reversing the movement of the loop-taker and also for locking said loop-
taker against movement until the proper hook thereof comes to a precise position
relatively to, and in co-operative relation with, the needle.
For this reason,
a change in the direction of the movement of the loop-taker cannot be effected---the
clutch of the reversing device being normally locked against shifting movement―
until a co-operative relation is established between each set of hooks and the
needle, or until the needle arrives at a neutral position relatively to two opposing
hooks of the loop-taker-as shown, for instance, in Fig. 37, of the drawings. By.
this movement the needle is positively maintained, during the reversing operation,
in such relation with two sets of hooks as to properly co-operate without further
adjustment with the proper set of hooks, irrespective of the direction of rotation of
the loop-taker.
As a preamble to the description of the operation of the machine, it is desired to
state that with the organization of loop-taker and needle actuating mechanism herein.
shown and described, the loop-taker and needle have, as before stated, a two-to-three.
ratio of movement; the loop-taker making two complete rotations to three complete
reciprocations of the needle-bar.
Thus it will be seen that each complete upward and downward stroke of the
needle-bar, the peripheral travel of the loop-taker, is substantially equal to
one third of the length of said periphery; and in consequence of the equidistant
peripheral disposition of the three-hook formative, recesses relatively to each other
and their peculiar operative arrangement with respect to the reciprocation of the
needle, the needle will, at the end of each downstroke, come in proper position
between two opposing hocks, or two adjacent hook-formative recesses, to insure the
engagement of the loop of the needle-thread by the proper hook and slightly in
advance of this book, irrespective of the direction of rotation of the loop-taker
and it will be further observed that at each complete reciprocation of the needle,:
one of the hooks will be carried to and past the loop-engaging position without
engaging the loop; and that the successive loops will be successively engaged by
the alternating hooks of the loop-taker.
Referring to the diagram Fig. 34, the relatively-small dotted circle Q represents
the circuit or path of movement of the needle-bar-actuating crank; the parallel
vertical lines Q' and Q' represent, respectively, the paths of movements of the
nicedle and the connections between the needle and crank; and the relatively-large
dotted circle Q³ represents the circuit or path of movement of the loop-engaging
hook of the loop-taker. The dotted circle Q, which represents the circuit of
the crank-pin, is shown divided by dots h, i, j, k, l, m, n, o, p, q, r, s, t, u, v, and w,.
respectively, into sixteen aliquot parts, which represent sixteen successive.
positions of the crank during one complete rotation thereof; and upon the vertical
lines Qand Q2 is a series of indicating-marks which coincide in number with the
dots of the circle Q, which marks are designated by h', i, j, k, l, m³, n¹, o¹, p¹, q¹,
, s, t, u, v, and w', respectively, and represent sixteen successive positions of
the needle corresponding to the aforesaid sixteen successive positions of the crank;
and the large circle Q3, which represents the peripheral path of movement of the
loop-taker, is divided by radial lines ², i, j, k², 12, m², n², o², p², q², r², s², t², u²,
v2, 2, and 3, 1³, j³, k³, 1³, m³, n³, and o³, respectively, into twenty-four aliquot parts,
representing twenty-four successive positions of a loop-engaging hook during one
and one-half reciprocations of the needle; the sum of the spaces between the lines
designated by 2 to w², inclusive and alphabetically, expressing a distance traversed
by one of the loop-engaging hooks of the loop-taker at each complete reciprocation
of the needle; and the sum of the spaces between the lines designated by 3 to 0³,
alphabetically and inclusive, expressing the distance traversed by said book during
one-half of the reciprocation of the needle.
Referring to the graphical diagram Fig. 35, the full horizontal line O and the
full curvilinear line O₁ represent the ordinates or the respective paths of movement
of the loop-taker and needle; said diagram representing relative positions of the
loop-taker and needle during one complete reciprocation of the latter. The
I

page_text: vertical dotted division lines (designated by 03 of said figure) represents sixteen
successive positions of the loop-taker and needle corresponding with the sixteen
successive positions thereof represented in Fig. 34. The points of intersection of
the vertical division lines O2 with the curvilinear lines O are designatel by,,
j, k, l, m, n, o¹, p¹, q', r¹, s¹, t', u', u', and w', respectively; and the distances of
these points of intersection above and below the horizontal dotted line Os represent
the successive positions of the eye of the needle above and below the throat-plate
of the machine, and correspond to the successive positions of the needle shown in
and designated by the same characters in Fig. 34.
By comparison of these two diagrams Eigs. 34 and 35, the relative movements
of the loop-taker and needle will be readily understood; the difference in the
velocity of the upward and downward strokes of the needle is defined by the
dotted curvilinear line 0
In describing the operation of inaugurating and completing a stitch, it is desired
to state that while Figs. 38 to 54, inclusive, of the drawings illustrate, by three
practically independent groups, three complete cycle of movements of a portion of
the stitch-forming mechanism, in making a lock-stitch, a chain-stitch, and a lock-
chain stitch, respectively, this present description of the operation. will only be
made in connection with the group comprised in Figs. 38 to 43, inclusive, which
illustrates the cycle of movements of the needle and shuttle in inaugurating and
completing a lock-stitch and it will be understood that this description applies to
the two groups comprised in Figs. 44 to 49 and 50 to 54, inclusive, with the exception
that in one of said groups the lower thread is dispensed with, and in both of said
groups the loop-taker is rotated in a direction opposite to that illustrated in
Figs. 38 to 43, inclusive.
For the purpose of designating without confusion the relative positions assumed
by the needle and loop-taker, at each step in the operation of forming a stitch, as
illustrated in Figs. 38 to 43, inclusive, these positions are represented in the
successive orders shown in Figs. 38 to 43, inclusive, by vertical lines marked "1st,"
"2d,"
," "3d," "4th," "5th," and "6th," on the graphical diagram Fig. 35, which
may be read in connection with Figs. 38 to 43, inclusive.
In the first position of the needle and loop-taker (shown in Fig. 38,) the needle
is in its lower dead-center position, and the hooks e, f, and g of the operative set of
hooks are in the positions designated by the radial lines ³, t, and h³, respectively,
in the diagram Fig. 34. In this position of the parts, the new loop L', which has
been formed by the descent of the needle, is located in position to be engaged by
the hook e, as the loop-taker is advanced in the direction of the arrow from the
position shown in Fig. 38 to that shown in Fig. 39; and the preceding loop has,
up to this point in the operation of the parts, been carried two-thirds way around
the loop-taker. This practically constitutes the first effective step in the
inauguration of the new stitch.
After the loop has been formed, as illustrated in Fig. 38, by the descent of the
needle, the resistance device T at the lower end of the needle-bar, as shown in
Figs. 5 and 7, becomes effective for holding the loop end of the needle-thread
against accidental drawing-up relatively to the needle, during the first stages of the
ascending movement of the needle-bar..
A continued movement of the needle and loop-taker brings said parts to
the 2d position (shown in Fig. 39) with the eye of the needle slightly below the
throat-plate and hook e of the loop-taker in its "loop-taking" position. After
the loop L' has been engaged by the hook e of the loop-taker, which occurs
immediately after the needle-bar has reached its lower dead-center position and is
on the ascendency, the velocity of the needle-owing to the peculiar disposition, of
the crank and link connector of the needle-bar-is greatly increased during the
lower part of the ascending movement of the needle, as compared with the decrease
in the velocity of the needle during the corresponding lower part of the descending
movement of said needle. This results in a comparatively sudden tightening of
the loop on the hook of the loop-taker, thereby holding the loop against accidental

page_text: .
displacement relatively to, and after the same has been engaged by, the hook of
the loop-taker, and also quickly carries the needle-bar past its lower dead-center
.position.
The needle and loop-taker are next carried by a continued movement thereof to
the 3d position (shown in Fig. 40;) the loop L' having at this time been carried
approximately one-third way around the loop-taker, and the needle-bar having
been carried to and slightly past its upward dead-center position, and the pre-
ceding loop L having been drawn off from the hook 9 and in close proximity to
the fabric.
In the next or 4th position of the needle and loop-taker, the loop L' is shown as
having been carried to its fully-drawn out position, and the preceding loop Lis
shown as having been completely taken up; the needle-bar in this position of the
parts being on the descent.
In the next or 5th position of the needle and loop-taker, as shown in Fig. 42,
the loop L is in its greatest slack position, and the crank and link connector
between the needle-bar and its actuating-shaft is in position to inaugurate the
retardation of the needle-bar; the velocity of which needle-bar is materially
decreased from this point in the cycle of movement thereof and until it has reached
its lower dead-center position shown in Fig. 38.
In the next, or 6th position of the needle and loop-taker, the loop L is shown
carried past its greatest slack position, and the needle is shown with its eye just
below the throat-plate and as having partially formed a new loop to be engaged
by the hook f, which is approaching its loop-engaging position, after which the
parts are further advanced to the 1st position described in connection with
Fig. 38.
When the parts are in positions intermediary to the positions shown in Figs. 39
and 41, the reciprocative device T¹ is effected-owing to the accelerated upward
stroke of the needle-bar-for drawing the loop L' taut, and through this loop
taking up the increment of the loop L, to thereby draw the loop L off the hook
carrying the same, and out of the path of movement of the succeeding hook of the
loop-taker.
Owing to the relatively-rapid velocity imparted to the needle, during the earlier
part of the ascending movement thereof, which effects a relatively-rapid and proper
drawing-up of the preceding loop, the needle is carried to and past its upper dead-
center position at a comparatively-early period in the operation of drawing out the
next succeeding loop; and therefore, the needle will begin its downward movement
before the said succeeding loop is fully drawn out, which will materially prolong
the latter portion of the stitch-forming operation and will draw up the preceding
loop with a reduced speed. This avoids a sudden tension of the thread while said
loop is being entirely drawn out, and, owing to this slow action, subjects the thread
to less strain than would otherwise accruc.
The combined needle-bar, and loop-taker actuating instrumentalities including
the connection between the needle bar actuating shaft, are so organized and timed
as to impart such comparative and relatively differential movements to the needle-
bar and. loop-taker as will effect a certain ratio of retardation in the velocity of
the needle-bar during the lower stages of its descending movement and just
preceding the arrival of the hook of the loop-taker in position to take the loop;
and will effect a relatively-great acceleration in the ascending movement of the
needle-bar, as compared with the retardation thereof, immediately succeeding the
engagement of the loop by the hook of the loop-taker.
The needle-bar has a retarded velocity during the lower stages of its descending
movement and a relatively-accelerated velocity during the corresponding lower
stages of its ascending movement; and the hook of the loop-taker arrives in
position to take the loop, iu point of time, practically between the retarded descending
and accelerated ascending movement of the needle-bar.
The means for imparting the comparative and relatively differential movements
described to the needle-bar; the tension device for preventing a retractive
>

page_text: movement under limited stress of the needle-thread, after the formation of the loop
and preparatory to the engagement of said loop by the hook of the loop-taker; and
the retractive device carried by the needle-bar, and adapted for retracting the
needle-thread after the release of the loop by the hook of the loop-taker, so as to
quickly draw the same out of the path of movement of the hooks of the loop-taker,
are important factors in the operation of the machine, and, in connection with the
tension device T, constitute an operative combination of elements whose coaction
materially contribute to the successful operation of said machine.
The particular organizations of the several elements comprising the sewing-
machine and the successive positions of the stitch-forming devices being so fully
illustrated in the several figures of the drawings, it is deemed unnecessary to a
clear understanding of the operation of forming a stitch to enter into a detailed
description of the operation of the minor parts of the machine, as this will be
readily understood by those conversant with that branch of the art to which this
invention appertains.
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 sewing-machine, the combination, with fabric holding and feeding devices,
of stitch-forming mechanism comprising a vertically-reciprocating needle-bar; a
revoluble three-hook loop-taker; a horizontally-disposed needle-bar-actuating
shaft; a crank carried by said needle-bar-actuating shaft; a link pivotally
connected at one end with said crank, and pivotally connected at its opposite end
with the needle-bar, in the rear of the path of movement of said needle-bar; a
horizontally-disposed loop-taker-actuating shaft; a driver carried by said loop-
taker-actuating shaft and in operative connection with the loop-taker; a vertically-
disposed feed-actuating shaft; a one-to-one train of gears operatively connecting
the needle-bar-actuating shaft and feed-actuating shaft; a two-to-three train of
gears operatively connecting the loop-taker-actuating, shaft and feed-actuating
shaft; a driver in connection with one of said shafts; and suitable tension devices
for the thread, all constructed and organized, whereby the loop-taker and needle-
bar will have a two-to-three ratio of movement, and whereby the needle will have
a relatively slight retardation during the lower part of its downward stroke,
and a relatively great acceleration during the corresponding lower part of its
upward stroke.
a
2. In a sewing-machine, the combination, of a reciprocatory needle-bar;
revoluble three-hook loop-taker; a feed-lever; a loop-taker-actuating shaft in
operative connection with the loop-taker; a needle-bar-actuating shaft in operative
connection with the needle-bar; a feed-lever-actuating shaft, having lever-
actuating means thereon, located intermediate the loop-taker and needle-bar-
actuating shaft; a two-to-three train of gears operatively connecting the loop-
taker-actuating shaft and intermediate shaft; a one-to-one train of gears
operatively connecting the intermediate shaft and needle-bar-actuating shaft; and
means for actuating one of said shafts, whereby a two-to-three ratio of movement
is effected between the loop-taker and needle-bar.
3. In a sewing-machine, the combination, with fabric-holding and fabric-feeding
devices; of stitch-forming mechanism comprising a revoluble loop-taker having
three equidistantly-disposed peripheral loop-engaging hooks; a reciprocatory
needle-bar carrying a needle; a loop-taker-actuating shaft; a needle-bar-actuating
shaft; an actuating-connector between and connecting said loop-taker-actuating
shaft and needle-bar-actuating shaft, and embodying a shaft and a one-to-one and a
two-to-three train of gears for effecting a two-to-three ratio of movement between
the loop-taker and needle-bar; and a connector between the needle-bar-actuating
shaft and needle-bar, for effecting a retardation in the velocity of the needle-bar
at that point in the descending movement thereof which correspouds with the loop-
taking position of the loop-taker, and for effecting an acceleration in the velocity

page_text: "
.
of the needle-bar at that point in the ascending movement which corresponds with
the initial loop-drawing position of the loop-taker.
4. In a sewing-machine of the class specified, the combination, with the frame
of the machine and with the vertically-reciprocating needle-bar and its actuating-
shaft of a revoluble loop-taker peripherally supported at an inclination to the
path of movement of and below the needle-bar, and having three relatively
equidistant peripherally-disposed loop-engaging hooks, and having three pairs of
relatively equidistantly-disposed driving-sockets in one side thereof, located, one
pair between each two adjacent hooks; a loop-taker-actuating shaft; a driver
carried by said shaft with its axis at an inclination to the axis of the loop-taker,
and having equidistantly-disposed driving-pins in position and adapted for
successively entering the successive pairs of driving-sockets in and for rotating the
loop-taker, and also adapted for holding said loop-taker against movement
relatively to said driving-pins; mechanism operatively connecting the needle-bar-
actuating shaft and loop-taker-actuating shaft, for reducing the speed of the latter;
and means for actuating one of said shafts.
5. In a sewing-machine, the combination, with the sewing-machine head and
with suitable fabric-feeding devices, of a longitudinally-recessed presser-bar
supported for vertical movement in, and locked as against rotary movement
relatively to, said head; a presser-bar actuator in operative connection with said
presser-bar; a needle-bar supported for reciprocatory movement in said presser-
bar; a needle-bar-actuating shaft; an actuating-connector extending through the
longitudinal recess in the presser-bar, and operatively connecting the needle-har
and needle-bar-actuating shaft, and providing means for holding the needle-bar
against rotation relatively to the presser-bar; and complemental stitch-forming
mechanism.
i
6. In a sewing-machine, the combination, with a reciprocatory needle and a
revoluble three-hook loop-taker, of needle-bar and loop-taker-actuating mechanism
organized and timed to impart relatively slow and fast downward and upward
strokes, respectively, to the needle-bar, and retard the lower part of the slow,
downward stroke, and accelerate the corresponding lower part of the fast, upward
stroke of said needle-bar at predetermined points in the rotation of the loop-taker,
substantially as, described, and comprising a needle-bar-actuating shaft having its
• axis in the plane of, and at right angles to, the axis of the needle-bar; a crank
· carried at the eud of said shaft and having a link connection with the needle-bar;
a loop-taker-actuating shaft located in the plane of, and parallel to, the needle-bat-
actuating shaft; and an actuating-connector between and connecting the needle-
bar and loop-taker-actuating shafts, and embodying a one-to-one and a two-to-three
train of gears, for effecting a two-to-three ratio of movement between the loop-
taker and needle-bar actuating shafts.
7. In a sewing-machine, the combination, with fabric holding and feeding
devices, of stitch-forming mechanism comprising a reciprocating needle-bar; a
revoluble three-hook loop-taker'; a needle-bar-actuating shaft; a crank carried by
said shaft; a link pivotally connected with said crank and needle-bar; a loop-
taker-actuating shaft; a driver carried by said loop-taker-actuating shaft and in
operative connection with the loop-taker; a feed-actuating shaft; a one-to-one
train of gears connecting the needle-bar-actuating shaft and feed-actuating shaft;
a two-to-three train of gears connecting the loop-taker-actuating shaft and feed-
actuating shaft; and a driver in connection with one of said shafts, the parts being
so organized that the loop-taker and needle-bar will have a two-to-three ratio of
movement, and the needle will have a relatively slight retardation during the lower
part of its downward stroke and a relatively great acceleration during the
corresponding lower part of its upward stroke.
8. The combination, with a sewing-machine head, of combined presser-bar and
needle-bar mechanism comprising a tubular, longitudinally-recessed presser-bar
non-rotatively supported for vertical movement in said head; a needle-bar sup-
ported for reciprocatory movenient within and concentric to the presser-bar; a

page_text: needle-bar-actuating shaft carrying a crank adjacent to the needle-bar; a strap
carried by the needle-bar and extending through the recess in the presser-bar, and
holding the needle-bar against rotation relatively to the presser-bar; a link pivotally
connected at one end to the strap and at the opposite end thereof to the crank on
the needle-bar-actuating shaft; a presser-regulating device in adjustable connection
with the presser-bar; means for actuating the presser-bar independently of the
needle-bar; and complementary stitch-forming mechanism.
9. The combination, with the sewing-machine. head and with the tubular,
longitudinally-recessed presser-bar non-rotatively supported for vertical movement
in the said head; of a needle-bar supported for reciprocatory movement within and
concentric to the presser-bar; a rotating needle-bar-actuating shaft carrying a
crank adjacent to the needle-bar; a strap carried by the needle-bar and extending
through the recess in the presser-bar and adapted for holding the needle-bar against
rotation relatively to the presser-bar; and a link pivotally connected at one end to
said strap and at the opposite end to the crank of the needle-bar-actuating shaft.
10. The combination, with the sewing-machine head, of a presser-bar supported
for vertical movement in said head; a laterally-projecting arm fixed to said presser-
bar and having cam-faces on the outer end thereof; a rock-shaft supported for
rocking movement in bearings in the sewing-machine head; and a crank carried at
the outer end of said rock-shaft, and having a pin extended between the cam-faces
of the laterally-projecting arm of the presser-bar; and means for actuating the
rock-shaft to raise and lower the presser-bar.
11. The combination, with the sewing-machine head, of a presser-bar supported
for vertical movement in bearings in said head; a pressure device in adjustable
engagement with the upper end of said presser-bar; a laterally-projecting arm
secured to said presser-bar and having oppositely-disposed cam-faces at the outer
end thereof; a rock-shaft supported in bearings in said head; a crank carried at
the outer end of said rock-shaft and having a crank-pin in movable engagement
with and between the cam-faces of the laterally-projecting arm; and means for
actuating the rock-shaft to raise and lower the presser-bar.
12. The combination, with the sewing-machine head, of a presser-bar supported
for vertical movement in said head, and having a laterally-projecting slotted arm;
a crank engaging in the slot in said arm and having stop-faces in bearing engage-
ment with the opposite sides of said arm, and holding the same against lateral
movement; and a rock-shaft in connection with, and having means adapted for
rocking, said crank to raise and lower the presser-bar.
13. In a sewing-machine, a vertically-reciprocating needle-bar; a revoluble
three-hook loop-taker peripherally supported below the needle-bar; a horizontally-
disposed needle-bar-actuating shaft having means in connection with, and adapted
for effecting a relatively slow downward movement and a relatively rapid upward
movement of, the needle-bar at every two-thirds of a revolution of the loop-taker;
a loop-taker-actuating shaft in vertical alignment and in horizontal parallelism with
the needle-bar-actuating shaft; a vertical shaft intermediate to the two horizontal
shafts; a one-to-one train of gears operatively connecting the needle-bar-actuating
and vertical shafts; a two-to-three train of gears connecting the loop-taker-
actuating and vertical shafts, whereby a two-to-three ratio of movement is main-
tained between the loop-taker-actuating shaft and needle-bar-actuating shaft ; and
feed mechanism in direct operative connection with, and actuated by, the
vertical shaft.
14. In a sewing-machine, co-operative stitch-forming fabric-feeding mechanism
comprising a reciprocating needle-bar; a revoluble three-hook loop-taker; a
universally oscillatory feed-lever carrying, a feed-dog; and combined needle-bar,
loop-taker, and feed-actuating mechanism constructed, organized, and timed to
actuate the loop-taker and needle-bar with a two-to-three ratio of movement, and
effect a slow downward and a relatively rapid upward movement of the needle-bar
at every two-thirds of a rotation of the loop-taker, and also to impart a feed
movement to the feed-lever subsequently to each downward stroke of the needle-

page_text: bar, and comprising a loop-taker-actuating shaft and needle-bar-actuating shaft
located in the plane of the axis of the needle-bar and at right angles thereto; a
feed-lever-actuating shaft; a one-to-one and a two-to-three train of gears
operatively connecting the feed-lever-actuating shaft with the needle-bar and loop-
taker actuating shafts, respectively; and means for actuating one of said shafts.
15. In a sewing-machine of the class specified having a suitable frame, a
vertically-reciprocatory needle-bar, a revoluble multi-hook loop-taker, and a feed-
dog supported for reciprocatory movement intermediate to the needle-bar and
loop-taker; in combination, with a horizontally-disposed needle-bar-actuating shaft
in operative connection with the needle-bar; a horizontally-disposed loop-taker-
actuating shaft operatively connected with the loop-taker; a vertical shaft having
means in operative connection with the feed-dog and adapted for directly controlling
the movements of said feed-dog; a one-to-one train of gears directly connecting
the needle-bar-actuating shaft and vertical shaft; and a two-to-three train of gears
directly connecting the vertical shaft and the loop-taker-actuating shaft.
. 16. In a sewing-machine, the combination, with two horizontally-disposed shafts
and a vertically-disposed shaft, of actuating mechanism for synchronously rotating
the two horizontal shafts with a two-to-three ratio of movement; a reciprocatory
needle-bar in operative connection with one of said horizontal shafts; a revoluble
three-hook loop-taker operated by the other horizontal shaft; a feed mechanism in
operative connection with the vertical shaft between the two horizontal shafts, and
actuated by said vertical shaft; means in direct connection with, and adapted for
. rotating, one of said shafts, to effect a simultaneous movement of all of said shafts';
and means in position and adapted for effecting a relatively slow downward and a
relatively rapid upward movement of the needle-bar at every two-thirds of a
revolution of the loop-taker.
17. In a sewing-machine, a reciprocatory needle-bar, a revoluble multi-hook
loop-taker; a feed-dog supported for reciprocatory movement intermediate to said
needle-bar and loop-taker; and a feed-lever supported for oscillatory movements
and carrying said feed-dog; in combination, with a horizontally-disposed needle-
bar-actuating shaft in operative connection with the needle-bar; a horizontally-
disposed loop-taker-actuating shaft in operative connection with the loop-taker;
a vertically-disposed feed-lever-actuating shaft; a feed-lever-actuating eccentric
adjustably carried by said shaft in operative connection with 'the feed-lever;
a one-to-one train of gears directly connecting the feed-lever-actuating shaft and
needle-bar-actuating shaft; a two-to-three train of gears directly connecting the
feed-lever-actuating shaft and loop-taker-actuating shaft; means for directly
actuating one of said horizontally-disposed shafts to rotate both of said shafts at
comparative speeds of relatively-varying velocities; and means for maintaining
the feed-dog in parallelism with the line of its longitudinal movement.
18. In a sewing-machine having a suitable frame and a revoluble loop-taker, the
combination therewith, of a combined cloth-clamp and needle-carrier comprising
two axially coincident members locked as against rotation and supported for
longitudinal movement relatively to each other, and the outer member of which
has an outwardly-extended cam-faced arm; and actuating mechanism for said
members which consist of two horizontally-disposed shafts, one of which is
supported for rotation and has a crank operatively connected by means of a link
with the inner member at one side of and remote from the axis of said inner
member, and is adapted for imparting a relatively slow advancing and a relatively
rapid retracting movement to said inuer member, and the other shaft of which
carries a crank in operative connection with the cam-faced arm, and is adapted to
be operated to lift the outer member independently of the inner member; means
for continuously rotating that shaft which is operatively connected with the inner
member, to effect a continuous reciprocation of said inner member; and means for
operating that shaft which is in operative connection with the outer member, to
raise and lower said outer member relatively to the inner member.
נ'
19. In a sewing-machine, the combination, with a feed-lever and with a feed-dog

page_text: pivotally mounted on said feed-lever; of an actuator for imparting movements to
said feed-lever; and vibratory means for holding the feed-dog in parallelism with
the plane of the longitudinal movement of said dog.
20. In a sewing-machine, the combination, with a feed-lever and with a feed-dog
pivotally mounted on said lever; of rotative mechanism constructed and arranged
to impart an elliptical movement to the feed end of said lever; and a vibratory
device for holding the feed-dog in parallelism with the plane of the longitudinal
movement of said dog.
21. In a sewing-machine, a feed mechanism of the class specified, comprising a
suitably-supported lever; a feed-dog carried by said lever; a rotative actuating-
eccentric universally connected with one end of said lever, and adapted to impart
an elliptical movement to both ends thereof; and vibratory means for holding the
feed-dog in parallelism with the plane of the longitudinal motion of said dog.
22. The combination, with a sewing-machine feed-lever and means for imparting
thereto elliptical movements; of a feed-dog directly carried by said lever; and
means having a movement conforming to the motion of the lever, for maintaining
the feed-dog in substantial parallelism with the line of its longitudinal movement.
23. The combination, with a sewing-machine feed-lever and means for imparting
thereto elliptical movements; of a feed-dog pivoted to said lever,, and directly
carried thereby; and a link having a movement conforming to the motion of the
lever, for maintaining the feed-dog in substantial parallelism with the line of its
longitudinal motion.
24. The combination, with a sewing-machine feed-lever and means for actuating
the same; of a feed-dog pivotally mounted on the free end of said lever, and
provided with an opening back of its pivotal-point; a device passing through said
opening, and permitting a slight play of the dog thereon; and means for maintaining
the feed-dog in substantial parallelism with the line of its longitudinal motion.
25. The combination, with a sewing-machine feed-lever; of an eccentric
universally connected to said lever, and serving to impart to the same elliptical
movements; a feed-dog pivotally mounted on the free end of the lever; and a link
connecting said dog with the feed-lever carrier, and serving to maintain said dog
in substantial parallelism with the line of its longitudinal movement.
26. The herein-described feed mechanism for sewing-machines it consisting of a
feed-lever supported approximately midway of its length, for vertical and horizontal
oscillations; a feed-actuating shaft; an eccentric carried by said shaft, and adapted
for adjustment, transversely of said shaft; an eccentric-strap revolubly carried by
said eccentric, in a plane oblique to the axis thereof; a universal connection
between said eccentric-strap and feed-lever; an eccentric-shifting member shiftably
carried upon the feed-actuating shaft, and in operative connection with the
eccentric, and adapted for shifting said eccentric, transversely of said shaft; and an
adjusting device in operative connection with said eccentric-shifting member, and
adapted for shifting said member longitudinally of the shaft, to effect a change, in
the effective throw of the eccentric, substantially as described, and for the purpose
set forth.
27. In a sewing-machine feed mechanism, a feed-lever supported near its middle
portion for elliptical movement at the feed end thereof, and held as against rotative
movement about its longitudinal axis; combined with a rotative actuator comprising
a shiftable eccentric having an obliquely-disposed eccentric-strap surrounding the
periphery thereof, and so connected with one end of the feed-lever as to impart,
during the rotation of the eccentric, an elliptical movement to the feed end of said
feed-lever, without rotating said feed-lever upon its longitudinal axis; a driver for
rotating said eccentric; and an adjusting device in operative connection with, and
adapted for shifting, said eccentric transversely of the driver, to increase or
decrease the eccentricity thereof, and effect a change in the range of elliptical
movement of the feed end of the feed-lever.
28. The herein-described feed mechanism for sewing-machines, it comprising a
feed-lever pivotally supported near its middle portion for elliptical movement at

page_text: the feed end thereof, and held against rotative movement about its longitudinal
axis; a variable eccentric; an annular eccentric-strap movably carried on the
periphery of said eccentric in a plane oblique to the plane of rotation of the
eccentric; a universal connection between the feed-lever and eccentric-strap
located at one side only of the axis of movement of said eccentric, and adapted for
transmitting an elliptical movement to the end of the feed-lever; and adjusting
means for effecting a change in the effective throw of said eccentric.
29. In a sewing-machine feed mechanism, a feed-lever supported midway of its
length for elliptical movement at the ends thereof, and held as against rotative
movement about its longitudinal axis; combined with continuous rotary-motion
feed-lever-actuating mechanism, for imparting an elliptical movement to the ends
of the feed-lever, and comprising an actuating-shaft; an eccentric rotative with,
and shiftable transversely of, said shaft; an eccentric-adjusting wedge interposed
between the eccentric and actuating-shaft; an eccentric-strap peripherally carried
by, and at an inclination to the path of movement of, said eccentric; a ball-and-
socket connection between the eccentric-strap and feed-lever; and means for
adjusting the eccentric-adjusting wedge longitudinally of the actuating-shaft, to
effect a change in the effective throw of the eccentric, whereby a change in the
range of elliptical movement of the ends of the feed-lever is attained.
30. The combination, with a feed-lever carrier pivotally supported in a bearing,
of a feed-lever pivotally supported for oscillation remote from the outer end of
Eaid carrier; a feed-dog pivotally carried for oscillatory reciprocation at one end
of said feed-lever; a link in parallel disposition relatively to the feed-lever, and
connecting the feed-dog and feed-lever carrier, and adapted for holding the feed-
dog in parallelism with the line of its longitudinal movement; and an actuator in
operative connection with the opposite end of said feed-lever, and adapted for
imparting vertical and horizontal oscillations to said feed-lever.
31. The combination, with a feed-lever pivotally supported for oscillation by a
carrier pivotally carried for oscillations in a bearing, of a feed-dog pivotally carried
at one end of the feed-lever; a link in parallelism with the feed-lever and pivotally
connected at one end thereof to the carrier and at its opposite end to the feed-dog,
and adapted for maintaining the feed-dog in parallelism with the line of its
longitudinal movement; actuating means for imparting vertical and horizontal
oscillations to the feed-lever and connected link; and a regulating device for
changing the effective throw of said feed-lever.
32. In a sewing-machine, the combination, with a reciprocatory needle-bar and
its horizontally-disposed actuating-shaft and with a revoluble loop-taker and. its
horizontally-disposed actuating-shaft, of a feed mechanism comprising a vertically-
disposed shaft in operative connection with the two aforesaid horizontally-disposed
shafts a feed-lever-actuating device carried by the vertical shaft; a feed-lever
fulcrumed near the middle portion thereof for vertical and horizontal oscillations,
and having one end thereof in operative engagement with the said device; a feed-
dog pivotally carried at the opposite end of said feed-lever; and a link pivotally
supported at one end in alignment with the fulcrum of the feed-lever and pivotally
connected at the opposite end thereof with the feed-dog and adapted for main-
taining the feed-dog in parallelism with the line of its longitudinal movement.
•
33. In a sewing-machine, the combination, with a suitable frame having a bed-
plate, of a feed-lever carrier pivotally carried in a horizontal bearing below, and in
connection with, the bed of the machine; a feed-lever pivotally supported for
horizontal oscillation remote from the extreme outer end of said carrier; n feed-dog
pivotally carried for borizontal oscillation at one end of said feed-lever and
operatively connected with the extreme outer end of said carrier by means of a link
in parallel disposition relatively to the feed-lever; a feed-lever-actuating device
in operative connection with the opposite end of the feed-lever and adapted for
imparting horizontal and vertical oscillations to said feed-lever; and means in
connection with and adapted for actuating said device...
34. In a sewing-machine, the combination, with a suitable frame having a bed-

page_text: plate, of a feed-lever carrier pivotally mounted in a horizontal bearing below, and
in connection with the bed of the machine; a feed-lever pivotally supported for
horizontal oscillation remote from the extreme outer end of said carrier; a feed-dog
pivotally carried at one end of said feed-lever and operatively connected with the
extreme outer end of said carrier by means of a link in parallel disposition relatively
to the feed-lever; a feed-lever actuating device shiftably carried by a driving-shaft
and in operative connection with the opposite end of the feed-lever and adapted
for imparting vertical and horizontal oscillations to said feed-lever; a driving-
shaft in operative connection with said device; and means for regulating the
effective movement of said lever, to increase or decrease the throw of the lever.
35. In a sewing-machine, the combination, with the framework thereof, of a feed-
lever supported for vertical and horizontal oscillations; a feed-dog pivotally carried
by said feed-lever; an actuating-shaft; a feed-lever-actuating device carried by,
and shiftable transversely of, said shaft; a sliding wedge in engagement with said
feed-lever-actuating device and adapted for shifting the same transversely of said
shaft, to change the throw thereof; and a regulating device comprising a stu
journaled for rotation in the frame and having an eccentrically-disposed pin at one.
end thereof in engagement with the sliding wedge; and a bolt carried by the stud
in movable engagement with an annular groove formed in the bearing in which the
stud is seated.
36. In a sewing-machine having a vertically-reciprocating needle-bar, the
combination therewith, of a revoluble loop-taker having two sets of peripheral
loor-engaging hooks, the hooks of one set being oppositely disposed relatively to
the hooks of the other set; driving mechanism in operative connection with, and
adapted for simultaneously operating, said needle-bar and loop-taker at comparative
velocities of a predetermined ratio; and loop-taker locking and reversing mechanism
in operative connection with, and adapted for changing the direction of movement
of, said loop-taker, and also adapted for maintaining an operative relation between
the needle-bar and one or the other of the two sets of hooks of the loop-taker, .
substantially as described and for the purpose set forth.
37. In a sewing-machine, an annular-recessed loop-taker having two sets or two
series of peripheral loop-engaging hooks, the hooks of one set of which are
oppositely disposed relatively to, and alternate with, the hooks of the other set; in
combination with reversing driving mechanism in operative connection with, and
adapted for rotating, the loop-taker in one or the other direction, substantially as
described.
38. In a sewing machine of the class specified, the combination, with a reversibly-
revoluble loop-taker; of a reversing driving mechanism for said loop-taker,
consisting of a loop-taker-actuating shaft; two gears revolubly mounted on said
shaft; means in position and adapted for locking and releasing said gears, recipro-
cally, relatively to the shaft, and for locking one of said gears to the shaft and to
the other gear before releasing said other gear from locked engagement with the
shaft, and vice versa; and means for rotating said gears in opposite directions,
substantially as described.
39. In a sewing-machine of the class specified, the combination, with a reversibly-
revoluble loop-taker; of a loop-taker-actuating shaft; two oppositely-disposed
driven gears revolubly mounted on said shaft, and having notched hubs in bearing
contact; a clutch member carried by the shaft, and having a clutch-pin seated in
the notch in one or the other of the driven-gear hubs, and adapted for locking and
releasing said gears, reciprocally, relatively to the loop-taker-actuating shaft, and
for locking one gear to the shaft and to the other gear before the release of said
other gear from locked engagement with the shaft, and vice versa; and means for
rotating said driven gear in relatively-opposite directions, substantially as described,
aud for the purpose set forth.
40. In a sewing-machine, the combination, with the reciprocating needle and
needle-actuating mechanism; and with the revolubly-reversible loop-taker and its
actuator; of loop-taker-reversing mechanism in direct operative connection with

page_text: "the loop-taker actuator, and consisting of two driven gears revoluble mounted on
said actuator; a clutch carried by said actuator in position and adapted for locking
and releasing said gears, reciprocally, relatively to said actuator, and for locking
one gear to the actuator and to the other gear before the unlocking of said other
gear from the actuator, and vice versa; a driving-gear in mesh with, and adapted
for rotating said driven gears in opposite directions; and means for rotating said
driving-gear, substantially as described and for the purpose set forth.
41. In a sewing-machine, the combination, with the reversibly-revoluble loop-
taker having two sets of peripheral loop-engaging hooks, the hooks of one set being
oppositely disposed relatively to, and alternating with, the hooks of the other set,
and with the vertically-reciprocating needle-bar and its actuating-shaft; of a loop-
taker-actuating shaft carrying a driver in position and adapted for rotating the
loop-taker; an intermediate shaft operatively connected with the needle-bar-
actuating shaft, and carrying a driving-gear adjacent to the loop-taker-actuating
shaft; two reversing driven gears revolubly mounted on the loop-taker-actuating
shaft and meshing with the driving-gear of the intermediate shaft; and a clutch
device carried by the loop-taker shaft in position and adapted for locking and
releasing the driven gears, reciprocally, relatively to said shaft, and for locking one
of said gears to the shaft and to the other gear before unlocking said other gear
from the shaft, and vice versa; and also adapted for maintaining an operative
relation between the needle-bar and the two sets of hooks of the loop-taker,
irrespective of the direction of movement of the loop-taker, substantially as
described.
42. In a sewing-machine, the combination, with a reversibly-revoluble loop-taker,
and with a longitudinally-recessed loop-taker-actuating shaft; of two bevel driven
gears revolubly mounted on said shaft; a clutch member supported for sliding
movement transversely of the driven gears in the longitudinal recess of the loop-
taker-actuating shaft, and carrying a clutch-pin between the adjacent ends of the
hubs of, and adapted for engaging said gears, reciprocally, and adapted for locking
one gear to the loop-taker-actuating shaft and to. the other gear before unlocking
said other gear from said shaft, and vice versa; a bevel driving-gear in mesh with
said driven gears, and adapted for continuously rotating said driven gears in
opposite directions, respectively; and means for supporting, and means for
rotating said driving-gears, substantially as described, and for the purpose set
-forth.
43. The combination, with a loop-taker having opposing loop-engaging hooks,
of a reciprocatory needle-bar; and reversing driving mechanism in operative
connection with and adapted for rotating the loop-taker in opposite directions, said
mechanism comprising locking means for preventing a change in direction of
rotation of the loop-taker. until the needle-bar has arrived at a neutral position
with respect to the opposing hooks of said loop-taker.
Dated this 9th day of December 1902
FRANCIS HENRY RICHARDS.¨
Haseltine, Lake & Co.,
45 Southampton Buildings, W.C., Agents for the Applicant.