Improvements in Machines for Applying Loops of String or Twine to Books, Pamphlets, and the like.
Year: 1897

page_text: Date of Application, 9th Nov., 1897-Accepted, 9th Apr., 1898
COMPLETE SPECIFICATION.
[Communicated from abroad by JOSEPH ABRAM WARD, Publisher, of No. 91, Main
Street, and JOHN MCLEAN, Manufacturer, of No. 72, Lock Street, both in
the City of Lockport, in the County of Niagara, in the State of New
York, United States of America.]
Improvements in Machines for Applying Loops of String or Twine
to Books, Pamphlets, and the like.
I, HENRY HARRIS LAKE, of the Firm of Haseltine, Lake & Co., Patent Agents,
45, Southampton Buildings, in the County of Middlesex, 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 a machine for attaching hangers or loops of string or
twine to books, pamphlets or other blanks and has the object to produce an
automatic machine for this purpose whereby the blanks are fed successively from
a pile or stack and are perforated, threaded and knotted and then gathered in a
pile or stack in a reliable and expeditious manner.
In the looping machine which forms the subject of this application the pam-
phlets or other blanks are placed side by by side, with one corner downward, in an
angular feed trough and are then separated successively at the front end of the
pile or stack and fed against the side of a vertical drum which rotates intermittently
about a vertical axis and which is provided on its cylindrical face with jaws by
which the blanks are clamped to the drum. The latter presents the pamphlets,
during its rotation, successively to mechanisms whereby each blank is perforated
and whereby the twine is drawn through the perforation, looped, tied and cut off.
The looped blanks are discharged one after the other from the drum and stacked
in a receiving trough from which they are removed from time to time.
In the accompanying drawings consisting of ten sheets ;-
Figure 1 is a front elevation of my improved pamphlet looping machine, partly
in section,
Figure 2 is a transverse section thereof, on line 2--2 Figure 1.
Figure 3 is a fragmentary longitudinal sectional elevation, on an enlarged scale,
on line 3-3, Figure 6.
Figure 4 is a fragmentary longitudinal sectional elevation, on an enlarged scale,
on line 44 Figure 16.
Figure 5 is a horizontal section on line 5-5, Figure 4.
Figure 6 is a top plan view of the machine, partly in section.
Figure 7 is a horizontal section on line 7-7, Figure 8.
Figure 8 is a rear elevation of the machine.
Figure 9 is a fragmentary sectional view, on an enlarged scale, showing the
operation of the packer and detent on the blanks.
Figure 10 is a fragmentary longitudinal section, on an enlarged scale, showing
the means for driving the blank supporting shafts on one side of the feed trough
and one of the rear wrapping screws.
Figure 11 is an elevation of the front end of the machine.

page_text: Figure 12 is an elevation of the rear end of the machine, partly in section.
Figures 13, 14 and 15, are transverse sections on lines 13-13, 14-14 and 15-15,
Figure 1, respectively.
Figures 16, 17 18, 19 and 20, are transverse sections on lines 16-16, 17-17,
18-18, 19-19 and 20-20, Figure 6 respectively.
Figure 21 is a fragmentary longitudinal section, on an enlarged scale, on
line 21-21, Figure 1.
Figure 22 is a vertical longitudinal sectional elevation, on an enlarged scale,
of the blank conveyor and connecting parts, on line 22-22, Figure 6.
Figures 23, 24 and 25 are fragmentary rear elevations of the conveyor screw
and adjacent parts, showing different positions of the parts.
Figures 26, 27, 28, and 29, are vertical cross sections on lines 26-26, 27-27,
28-28 and 29-29, Figures 22, 23, 24, and 25, respectively.
Figure 30 is a fragmentary horizontal section, on an enlarged scale, on
line 30-30, Figure 24.
Figure 31 is a vertical section, on an enlarged scale, on line 31-31, Figure 22.
Figure 32 is a longitudinal section, on an enlarged scale, on line 32-32,
Figure 1.
Figure 33 is a perspective view showing the manner in which the rotary blades
separate the blanks from the pile.
Figure 34 is a transverse section, on an enlarged scale, on line 34-34, Figure 6.
Figures 35, 36, 37 and 38, are horizontal sections on lines 35-35, 36-36,
37-37, and 38-38, Figure 34, respectively.
Figure 39 is a top plan view, on an enlarged scale, of the carrier drum and
adjacent parts.
Figure 40 is a fragmentary vertical section, on an enlarged scale, on line 40-40,
Figure 1.
Figure 41 is a fragmentary front view, on an enlarged scale, of the threading
device.
Figure 42 is a fragmentary horizontal section on
line 42 42, Figure 34.
an enlarged scale, on
Figure 43 is a similar view showing the parts in a different position.
Figures 44, 45 and 46 are fragmentary vertical sections in lines 44 44, 45-45,
and 46-46, Figure 42, respectively.
Figure 47 is a fragmentary vertical section, in line 47-47, Figure 44.
Figure 48 is an inside elevation of the twine feeding device on the same scale
as Figure 44.
Figure 49 is a detached view of one of the twine clearing hooks or fingers.
Figure 50 is a horizontal section, in line 50-50, Figure 45.
Figures 51 and 52 are fragmentary sectional views, on an enlarged scale, show-
ing two different longitudinal positions of the threading hook and needle.
Figures 53 and 54 are end views of the threading hook or needle showing the
same in different rotary positions.
Figure 55 is a fragmentary cross section, on an enlarged seale, on line 55-55
Figure 42.
Figure 56 is a fragmentary vertical section on line 56-56, Figure 55.
Figures 57 and 58 are horizontal sections, on an enlarged scale, on lines 57-57
and 58-58, Figure 55, respectively.
Figures 59, 60, 61-62-63-64-65 and 66 are fragmentary views showing
different positions of the knotter in the operation of tying a knot in the loop or
hanger.
Figure 67 is a fragmentary vertical section, on an enlarged scale, on line 67-67,
Figures 36 and 37, showing the mechanism for operating the blank holding clamp
of the carrier drum.
Figure 68 is a fragmentary transverse section, on
line 68-68, Figure 6, showing the blank transferring mechanism from the inner
an enlarged scale, on
side.

page_text: Figures J
Figure 68, respectively.
Figure 71 is a top view of the blank transferring mechanism.
Figure 72 is a transverse section in line 72-72, Figure 68.
Like letters of reference refer to like parts in the several figures.
The main frame of the machine consists essentially of an open bed A pro-
vided with legs a, and three main standards A¹ A2 A3, secured, respectively to the
front, intermediate and rear portions of the bed.
b, 61, 62, 63, 64, 65, 66, (Figures 1, 6, 8, 10, 12, 13, 14, 16, 17, 18, and 33) repre-
sent longitudinal supporting shafts or rods which are arranged in two downwardly
converging sets to form a V-shaped feed trough or receptacle. The pamphlets,
which I will call blanks for the sake of brevity, are placed upside down and side
by side in the trough with their backs or folded ends against the set of
shafts b, 6, 63 63, which form the oblique front side of the feed trough, and with
their upper ends against the set of shafts bº, 6º, 6º which form the oblique rear
side of the feed trough. These shafts are journalled in bearings formed in the
upper V-shaped portions of the standards A A2 A3 and are rotated and form roll-
ing supporting surfaces for the blanks which enable the latter to be readily moved
lengthwise through the trough. B, Figures 1, 6, 8, 17, and 21, represents a follower
which bears against the back of the pile or stack of blanks in the feed trough
and which is provided on opposite sides with lugs 67 which project outwardly
between the adjacent trough shafts. 68 are horizontal follower bars bearing with
their front ends against the lugs of the follower and secured with their rear ends
to a cross head composed of a V-shaped body which slides in the trough and
an end board 10 secured to the rear end of the body. These bars are arranged
between the feed trough shafts and below or outside of the supporting surfaces
thereof, (Figures 17 and 21), so that these bars will not interfere with the blanks
in the trough. The cross head, follower bars, follower and blanks are constantly
pressed forward by any suitable means, preferably by a weight 611 connected
with the cross head by a cord 612 passing around a roller b¹³ mounted on the front
standard A', as shown in Figure 8. When the pile of blanks requires replenish-
ing an additional lot of blanks is placed in the trough against the back of the
follower which is in use and another follower of the same construction is placed
behind the new lot of blanks after which the follower bars together with the cross
head are drawn rearwardly and engaged with the lugs of the rear follower. The
front follower is then removed. This follower mechanism permits of easily and
readily renewing the supply of blanks without stopping the machine or disarrang-
ing any of the blanks which have previously been placed in the feed trough.
c, c¹, c², c³, c4, 5, 6 (Figures 1, 6, 8, 17, 18 and 33) represent two sets of
rotary separating and supporting wings or blades which are secured to the front
ends of the feed trough shafts and which serve as an abutment against which the
front of the pile of blanks rests and also as separators whereby the foremost blanks
of the pile are separated from the remainder. The blades c, c¹, c², c³ forming one
set are secured, respectively, to the front ends of the trough shafts b, 61, 62, 63, and
form an abutment for the backs of the blanks. The blades c c5 and co forming
the other set are secured, respectively, to the front ends of the trough shafts 64, 65
and 66 and serve as an abutment for the upper inverted ends of the blanks. The
blades of both sets are arranged in the same transverse vertical plane, Figure 6,
and each blade has substantially the form of a semicircular wedge, the front or
advancing edge thereof being sharp while its rear or trailing end is comparatively
thick and ends abruptly, as represented in Figure 32. These separating blades
rotate with their inner portions upwardly, as indicated by the arrows, Figure 18,
and the relative arrangement of the blades on the shafts is such that the blades
of each set operate upon each blank successively, and the blades of both sets
operate upon each blank alternately. The lowermost blade c of the front set first
enters between the lower portions of two blanks and passes upwardly between the
same, whereby the lower portions of the foremost blank of the two is moved for-

page_text: wardly and away from the next following blank by the wedge action of the gradu-
ally thickening body of the blade. Before the rear end of the lowermost blade c
has cleared these blanks, the sharp front end of the lowermost blade of the rear
set; following behind the thick rear end of the lowermost blade of the front set;
enters the gap which has been formed between these blanks: and, in moving
upwardly, separates the same further. When this blade has nearly cleared the
rear side of these blanks the next higher blade c¹ of the front set enters the gap
in like manner and extends the separation of the blanks upwardly. The remain-
ing blades 5, c2, c and c³ of the two sets then follow each other alternately in
the order named. Each of said blades enters the gap between the
blanks as the next lower blade is about to leave the blanks and then
effects a further upward separation of the blanks.
When the upper-
most blade has passed between the two blanks the separation between the same
is completed from the lower ends to the upper ends of the same. The relative
timing of the separating blades is such that while the upper blades are passing
between the first and second blank of the pile, the intermediate separating blades
are passing between the second and third blanks, and the lowermost blades are
separating the third, and fourth blanks so that when the machine is in full opera-
tion three blanks are being separated simultaneously from the pile in different
stages of completeness. When all of the separating blades have made one rotation
the combined effect is equal to separating one blank completely from the pile after
which the movement of the blades is arrested until the foremost blank has been
carried away by mechanism hereafter described. This intermittent rotary move-
ment of the separating blades is preferably effected as follows;
€3
d, Figures 6, 8, and 10 represents horizontal spindles which are journalled
in the rear standard A³ and which are provided with gear pinions d' meshing with
gear pinions on the adjacent rear feed trough shafts 64 65 and 66.
Figures 6, 8, 10 and 12 is a crank arranged on the rear end of one of the
spindles and d are similar cranks arranged on the rear ends of the front feed
trough shafts b b1, b2 b³. d5 is an intermittently rotating crank shaft which is
journalled in the rear main standard A³ and a short standard A+ arranged on the
bed and which is provided on its rear end with a crank de of the same length as
the cranks d³ d. d is a bifurcated yoke or rod which connects the actuating
crank do with the two sets of driven cranks of the shafts and whereby these parts
are caused to rotate intermittently in unison.
D, Figures 1, 2, 5, 8, 13 and 14 is the continuously rotating main driving shaft
which is journalled lengthwise underneath the feed trough in bearings arranged
on the standards and D₁ is a counter shaft journalled in bearings on the rear
standard A3 and the short standard A. The counter shaft is driven from the main
shaft at the same speed as the latter by gear wheels do secured respectively to
these shafts. An intermittent rotary movement is transmitted from the counter
shaft to the crank shaft d by a driving gear wheel 10 Figure 1 secured to the
counter shaft and provided on its periphery with a segmental row of gear teeth ",
Figures 14 and 15, and a convex face da adapted to engage respectively with the
teeth d¹³ and concave face d¹ of an intermediate mutilitated gear pinion 15 secured
to the crank shaft №5. The pinion is held at rest while the convex face of the
driving wheel is in engagement with the concave face of the pinion but when the
teeth of the latter are engaged by the tooth of the driving wheel the pinion is
turned in the direction of the arrow, Figures 14 and 15, the number of teeth on
the wheel and pinion being so proportioned that the pinion makes one rotation
during each rotation of the driving wheel. The teeth of the driving wheel are
compelled to engage gradually at the proper time with the teeth of the pinion by
a shoulder de formed on the driving gear wheel and engaging with an arm dir
on the pinion.
In order to enable the lowermost separating blade c to pass positively and
reliably between the lower portions of two contiguous blanks and for the purpose

page_text: of aiding the blades in feeding off the blanks, a preliminary separating and feed-
ing device is provided which is constructed as follows:-
E, Figures 1, 6, 8, 17, 18, 22 to 30, represents a main feeding screw or con-
veyor whereby the lower portions of the partially separated blanks in the feed
trough are carried forwardly from the unseparated portion of the pile to the
mechanism which carries the blanks to the perforating, threading and tying
mechanisms. This conveyor is arranged lengthwise below the delivery end of the
feed trough and is mounted on the front end of a longitudinal shaft e which is
journalled in bearings in the adjacent stationary parts of the machine so as to be
capable of both a rotary and a longitudinally reciprocating movement. The
feed conveyor consists preferably of two convolutions so as to present three clamp-
ing jaws or faces e¹ e²e which are arranged in a longitudinal row, along the
upper side of the conveyor and are formed, respectively, by the rear side of the
first convolution of the conveyor, the front side of the first convolution and the front
side of the second convolution, as shown in Figures 22, 23, 24, 25, and 30.
The rear end of the conveyor is preferably made of the same form as the inter-
mediate separator blades and is arranged parallel therewith so that the rear jaw e¹
is arranged at right angles to the axis of the conveyor while the intermediate and
front jaws are arranged at an angle thereto.
F represents a separating and clamping finger whereby the foremost blank is
separated at its lower corner from the pile and pressed against the rear jaw e¹ of
the conveyor, Figures 22-30. This finger is arranged below the front portion
of the pile and has its end curved to form a bent jaw or hook f. This finger is
secured to the front portion of a shaft f¹ which is journalled lengthwise under the
feed trough in bearings on the adjacent stationary parts of the machine so as to
be capable of both a rocking and a longitudinal reciprocating movement. f f³
Figure 30 represent two clamping jaws which are arranged to face the front sides
of the first and second convolutions of the conveyor screw and whereby the blanks
are successively held against the jaws e e3 of the conveyor screw.
These clamp-
ing jaws are moved toward and from the conveyor jaws by a sliding rod f which is
arranged in the tubular front portion of the conveyor shaft. The clamping
jaws project laterally through a longitudinal slot f5 in the tubular shaft.
The clamping jaws f f are arranged at the same angle as the convolutions of
the conveyor against which they press the blanks and are preferably formed by
cutting them out of the conveyor, as represented in Figures 22, 27 and 30.
Preparatory to separating the lower corner of a blank from the pile the conveyor
shaft is moved rearwardly to its fullest extent whereby the rear jaw e¹ of the con-
veyor is pressed against the foremost blank of the pile and the latter is compacted at
the lower corner.
The finger shaft has been shifted to its most rearward position in
which the separating finger stands with its hook opposite the lower portion of the
foremost blank, as represented in Figures 22 and 26. While the lower corner of
the pile is held in this compressed condition by the rear jaw e¹ of the screw conveyor
the separating finger is turned so as to enter between the leaves of the foremost
blank near the back thereof and is then moved forward toward the rear jaw of the
conveyor whereby the part of the blank at the lower corner thereof is clamped
between the rear jaw of the screw conveyor and the finger, as represented in
Figure 23. By thus pressing the rear jaw of the screw conveyor against the
lower corner of the pile the location of the first blank is always the same and
the place where the finger engages between the leaves of the blank is definitely
determined, regardless of the thickness of the blanks, whereby the missing of a
blank is positively avoided. After the blank has been clamped between the con-
veyor and the finger, the shafts carrying these parts are moved forwardly together
to the end of their forward stroke, whereby the lower corner of the foremost blank
is separated from the succeeding blank and a gap is formed between the same.
As soon as this gap has been formed the lowermost separating blade c enters the
same and starts the upward separation of these blanks at the lower corner of the
same which operation is continued upwardly as hereinbefore described. When

page_text: the separating blades have finished separating the lower portion of the foremost
blank from the second blank the separating finger is withdrawn from the first blank.
The conveyor shaft and screw now move backward and after the initial portion of
this longitudinal movement the screw makes one complete turn in the direction
of the arrow, Figures 26-29, whereby the rear end of the conveyor passes behind
the first blank after which the conveyor stops turning and is pressed against the
front side of the lower corner of the second blank at the end of its backward move-
ment, preparatory to engaging the same by the separating finger, which latter has
in the meantime also been moved backwardly to the place where it is inserted into
the blanks. While the separating finger is holding the second blank against the
rear jaw of the conveyor during the next forward movement of the finger shaft,
the first blank is clamped against the intermediate jaw e² of the conveyor by the
jaw whereby the first and second blanks are carried forward simultaneously.
When the second blank has been separated at its lower end from the third blank
of the pile by the separating blades, the first and second blanks are released from
the intermediate and rear clamps, and the conveyor, in the course of its backward
movement, again makes one turn, whereby the first blank is carried in front of the
front jaw of the conveyor, the second blank is carried in front of the intermediate
jaw of the conveyor, and at the end of the backward movement of the conveyor
its rear jaw bears against the front side of the third blank. During the next longi-
tudinal forward movement of the conveyor the first blank is clamped between
the front jaw e3 of the conveyor and the front sliding jaw f³ and presented to the
mechanism which carries the blanks to the looping mechanism, the second blank
is held by the intermediate pair of clamping jaws, and the third blank is held
between the rear jaw of the conveyor and the finger which constitute the rear clamp.
When the third blank has been separated with its lower portion from the fourth
blank by the lower separating blades, the three blanks held by the conveyor are
released by the opening of the clamps, the first blank is carried away to the looping
mechanism, and the conveyor, while turning during its subsequent backward move-
ment, advances the second blank to the front clamp, the third blank to the inter-
mediate clamp and then bears against the fourth blank. When the machine is in
full operation there are always three blanks operated upon by the preliminary
separating, clamping and conveying device, the separation of each blank operated
upon being one step in advance of the next following and one blank being com-
pletely separated from the pile during each revolution of the conveyor screw.
The several parts of the preliminary separating and feeding device are preferably
driven as follows:-
G, Figures 1, 3, 8, 14 and 15, is a mutilated gear pinion mounted loosely on the
conveyor shaft between the standards A2 and A said shaft being free to slide
lengthwise in the hub of the pinion but compelled to turn therewith by means of
a ping on the shaft engaging with slots g' in the supporting hub or sleeve of the
gear pinion, as represented in Figure 3. This pinion engages with the upper
portion of the driving wheel do diametrically opposite the lower mutilated gear
pinion and is of the same size and construction. During each rotation of the
driving wheel do its shoulder d¹ engages with the arm d" of the lower gear
pinion d5 and throws the same into gear and after the teeth of the driving wheel
have cleared the lower pinion the shoulder of the driving wheel engages with the
arm 3 of the upper pinion and throws the latter into gear with the driving
wheel. This operation is repeated during each rotation of the latter and produces
alternate rotation of the separating blades and the conveyor screw. g³ is a longi-
tudinal reciprocating cross head which slides with one end on the counter shaft
and is secured with its opposite end to a sleeve which slides on the conveyor
shaft. The backward movement of the cross head is produced by springs g³,
Figures 1, 6, and 8, and is limited by the sleeve g engaging with a collar go on
the conveyor shaft, which collar in turn engages with the standard A. "The
forward movement of the cross head is produced by a rock lever 9' pivotally con-
necting said sleeve with the standard A* and a cam 98 mounted on the counter

page_text: shaft and engaging with a roller on said rock arm, Figures 1, 3, 8, and 13. The
rear end of the finger shaft is journalled in a bearing on the cross head and pro-
vided on opposite sides of this bearing with collars or shoulders 9 whereby the
finger shaft is permitted to turn in this bearing but compelled to move lengthwise
with the cross head. 910 is a collar or shoulder arranged on the conveyor shaft and
separated by an intervening or dead space from the front end of the sleeve of the
cross head when the latter is in its rearmost position, thereby producing a slack
connection between the cross head and conveyor shaft, whereby the finger shaft
is moved forwardly independent of the conveyor until the separating finger has
been pressed against the rear jaw of the conveyor after which the cross head sleeve
strikes the shoulder 10 of the conveyor shaft and moves the conveyor forward
together with the separating finger. The forward rotary movement of the separat-
ing finger for engaging the same between the leaves of a blank is produced by a
cam gl arranged on the counter shaft and engaging with a roller on the end of
a rock arm g2 secured to the finger shaft, the face of said cam being of sufficient
width to permit of the necessary longitudinal movement of the rock arm with the
finger shaft. The backward turning movement of the finger shaft is produced by
a spring g secured with its ends to an arm g¹ on the finger shaft and a stationary
part of the machine, as shown in Figures 1 and 18.
H, Figures 1, 8, 18, 22 and 31, is an elbow lever whereby the sliding clamping
rod in the front end of the conveyor shaft is operated and which is pivoted on the
adjacent portion of the frame. This lever is provided in the end of its upwardly
projecting arms with slots h¹ which receive pins ha projecting from opposite sides
of a swivel collar ³, Figure 31. The latter is mounted loosely on the front end
of the clamping rod and confined by a shoulder h and screw nut h5 arranged on
the rod and bearing respectively against opposite sides of the collar, whereby the
clamping rod is compelled to move back and forth with the elbow lever but is free
to turn independent thereof. The elbow lever is turned for moving the clamping
rod backwardly for clamping the blanks by a spring h6 which is connected at one
end to the frame and with its opposite end to a pull rod h7 connected with the lower
horizontal arm 8 of the elbow lever, Figures 18 and 22. The position of the elbow
lever for opening the front and intermediate clamps is controlled by a cam h³
mounted on the main shaft and engaging with a roller or projection h¹ on the pull
rod h. While the blank conveyor is in its rearmost position, with its rear jaw
pressing against the foremost blank of the solid pile, the clamping rod and its
When the blank
jaws are held in their foremost position by the cam hº.
conveyor begins its forward movement the cam h releases the elbow lever and
permits the same to be turned by the spring h6 for moving the jaws of the clamping
rod backwardly against the front and intermediate jaws of the conveyor after
which the jaws of the clamping rod are moved forwardly again to the end of the
forward movement against the pull of the spring 16 by the conveyor, whereby the
blanks are firmly held by the front and intermediate clamps. Before the conveyor
begins its backward movement the salient part of the cam 9 engages with the
roller 10 of the pull rod and holds the clamping rod f* and its jaws against back-
ward movement while the conveyor effects its entire backward movement, thereby
releasing the blanks from the front and intermediate clamps.
After each blank in the feed trough has been completely separated from the
pile the blank is delivered to a carrier which rotates intermittently about a ver-
tical axis and which presents the lowermost corner of the blank to the devices
which attach a hanger or loop to the same. This carrier is constructed as
follows: :-
I, Figures 6, 8, 34, represents a supplemental frame mounted on the front por-
tion of the main frame in front of the delivery end of the feed trough and con-
sisting of a lower supporting ring i, a lower supporting plate i arranged above
said ring, an intermediate supporting plate arranged above the lower supporting
plate, an upper supporting plate 23 arranged above the intermediate supporting
plate and vertical posts or members 24 connecting the supporting ring and plates

page_text: with each other and with the main frame. J, Figures 34, 35, 36, and 44 repre
sents a carrier wheel or drum to which is imparted an intermittent horizonta
rotary motion in the direction of the outer arrow, Figures 36 and 42. This drun
is arranged between the lower and intermediate supporting plates of the supple
mental frame with its axis vertical and with its receiving portion opposite the
delivery end of the feed trough. During the forward movement of the blank
conveyor the lower portion of the foremost blank is carried against the drum and
also wrapped around the same by a front wrapping screw j, which wraps the
advancing portion of the blank around the drum, and two rear wrapping
screws which wrap the trailing portion of the blank around the druni, as
shown in Figure 39. The front wrapping screw is mounted on the front end of
the trough shaft 62 so as to turn in a vertical plane therewith and has preferably
the form of a concave conoid, the curved side of which is substantially concentric
with the carrier drum, as represented in Figures 6 and 39. The front end j
Figure 6 of this concoidal screw enters the gap between the first and second
blank in the feed trough and in turning with the separating blades gradually
wraps the advancing end of the blank around the drum. The lower rear wrapping
screw jis mounted on the rear end of the feed trough shaft 65 and engages with
the rear portion of the blank adjacent to its lower corner and wraps the same
around the drum. The upper rear wrapping screw engages with the central rear
portion of the blank and wraps the same around the drum. In order to avoid
kinking the rear middle portion of the blank while it is being wrapped around
the drum the upper rear wrapping screw is turned in a direction opposite to that
of the lower rear wrapping screw. This is accomplished by a reversely rotating
shaft which carries the upper rear wrapping screw at its front end and is pro-
vided at its rear end with a crank which is connected with the bifurcated con-
necting rod or yoke d whereby the feed trough shafts are operated. The upper
rear screw shaft it is preferably journalled in the feed trough shaft 66 which
latter is made hollow for this purpose, as shown in Figure 10. This manner of
driving the wrapping screws causes the latter to turn and rest at the same time as
the separating blades. J' is a curved guide which is secured to the upper sup-
porting plate and which bears against the inner side of the blanks opposite the
front wrapping screw j.
The carrier drum is journalled on a hollow arbor or bushing 76, Figure 34 con-
necting the central portions of the lower and intermediate supporting plates and
is provided on its periphery with a suitable number of clamps, eight being shown,
whereby the blanks are successively seized and held on the carrier drum. Each
of these clamps consists of a stationary outer jaw and a movable inner jaw 8
having a radial movement toward and from the stationary jaw. Each of the
outer jaws is curved substantially concentric with the drum and is arranged at
a sufficient distance from the latter to permit a blank to pass into the space
between the outer jaw and the drum. The front end of the outer jaw is free while
its rear end is secured to the drum. When the blank conveyor has carried the
foremost blank in the feed trough against the drum, the latter rotates one eighth
of a turn and carries one of its outer clamping jaws behind or around the lower
portion of the foremost blank and then stops after which the blank conveyor E
moves backwardly and disengages itself from the foremost blank. Before the
drum begins its next forward movement its inner clamping jaw opposite the feed
trough is pushed out and clamps the foremost blank against the opposing outer
jaw, so that during the subsequent forward movement of the drum this blank is
carried laterally and forwardly away from the pile to the extent of one eighth of
a turn of the drum. In the meantime the blank conveyor E has carried the next
following blank forwardly so that the next following outer clamping jaw passes
behind the following blank, preparatory to clamping the same. The lower edge
of each outer jaw is horizontal while its upper edge rises from the front end to
the rear end of the jaw which gives the jaw a tapering or pointed form, whereby

page_text: the same is able to enter more freely into the gap behind the first blank. The
inclined upper edge also aids in separating the first blank from the second and
carrying the same against the drum. Each of the blanks is carried intermittently
with its back or folded side foremost from the receiving side of the drum, one half
way around the drum to the delivery side thereof, where the clamp is opened and
the blank is discharged. During this half rotation of the drum the blank is suc-
cessively presented to the perforating, threading and knotting mechanisms.
This intermittent rotary movement of the drum and the closing and opening
of its clamps is effected by the following means:-
K, (Figures 6, 34, 35, and 36,) is a vertical driving shaft which is
journalled with its central portion in the hollow arbor and with its
upper end in a bearing formed in the upper horizontal supporting plate 23.
The vertical driving shaft is driven from the main shaft and at the same speed
as the latter by a pair of bevel gear wheels k¹ secured, respectively, to the front
end of the main shaft and the lower end of the vertical shaft. ³, Figures 34
and 35, is a vertical counter shaft which is journalled with its upper and lower
ends in bearings arranged, respectively, on the upper and intermediate supporting
plates. The lower end of the vertical counter shaft is provided with a gear
pinion which meshes with a gear wheel secured to the upper end of the hub
of the carrier drum, the relative size of the pinion and gear wheel being such that
one complete turn of the pinion produces one eighth of a rotation of the carrier
drum. An intermittent rotary motion is imparted to the carrier drum by a hori-
zontal driving wheel, 6, Figures 6, 7, 8, 19, and 34, secured to the upper portion
of the vertical driving shaft and provided on its periphery with a segmental row
of teeth and a plain convex portion which are adapted to engage successively
with the teeth and the concave portion 10 of a mutilated gear pinion All secured
to the upper portion of the vertical counter shaft. The driving wheel is provided
with a shoulder 12, Figure 6, which is adapted to engage with an arm on the
gear pinion and start the same gradually and in correct register with the teeth
of the driving wheel in the same manner in which the gear pinions d¹³ and G of
the crank shaft and conveyor shaft e are geared with the driving wheel d¹ on
the horizontal counter shaft D¹.
The timing of the stop gearing connecting the vertical driving shaft with the
vertical counter shaft is such that during each rotation of the vertical driving
shaft the counter shaft makes one rotation, which, however, is produced while the
driving shaft makes one quarter of a rotation, the counter shaft then remaining
at rest during the remaining three quarters of the rotation of the driving shaft,
whereby the carrying drum is turned intermittently one eighth of a rotation
during each complete turn of the main shaft.
Each of the inner movable jaws of the drum is mounted on the outer end of a
radially movable carriage 1, Figures 34, 36, 44, and 47, which projects through an
opening in the rim of the carrier drum and is guided in a way on the underside
of the web of the drum. The carriage is preferably bifurcated and is yieldingly
held in its retracted or inner position by a spring 12 mounted on the carriage and
bearing against the inner side of the rim of the drum. L is a rotary cam whereby
the inner jaws are moved outwardly for clamping the blanks and which is journalled
on the lower portion of the hub of the drum, as represented in Figures 34, 44,
and 67. The face of this cam disc engages with rollers on the jaw carriages and
is provided with a short outwardly throwing cam portion 14 adjacent to the
receiving portion of the drum, a salient concentric portion 1 following the out-
wardly throwing cam portion and extending around the front half of the cam
disc, an inwardly throwing cam portion following the salient concentric portion
and arranged adjacent to the delivery portion of the drum and a depressed or
receding concentric portion 17 following the inwardly throwing cam portion and
extending half way around the rear side of the cam disc, as represented in
Figure 36.
Each of the clamp carriages, during one rotation of the drum, engages its

page_text: roller with the outwardly throwing cam portion 14 of the cam disc and is lifted
upon the salient concentric portion 15 thereof, whereby the foremost blank in the
feed trough is clamped and held while the drum makes the front half of its rotation,
after which the roller of the clamp carriage rides down the inwardly throwing
cam portion 16 onto the depressed concentric portion 17 whereby the clamp is opened,
the blank is released and the clamp is held open while moving around the rear
half of the drum. Before the drum begins each intermittent movement the cam
disc is turned backwardly in the direction of the inner arrow, Figure 36, sufficiently
to close the receiving clamp upon the foremost blank in the feed trough and
after the drum has turned forward sufficiently to bring the roller of the clamp
carriage beyond the reach of the outwardly throwing portion the cam disc is
again turned forwardly. By clamping the blank before the drum begins its for-
ward movement displacement of the blank on the drum is prevented. While a
new blank is being clamped on the drum by the backward movement of the cam
disc, the clamp on the diametrically opposite side of the drum is opened and releases
its blank, but the clamps on the front side of the drum remain unaffected because
their rollers remain on the salient concentric portion of the cam disc. 18 is a
vertical rock shaft whereby the cam disc is oscillated for closing and opening the
drum clamps and which is journalled with its upper end in a bearing in the lower
supporting plate and with its lower end in a bearing formed in a hanger 19 depend-
ing from said plate, as represented in Figures 36, 37 and 67. This rock shaft is
provided above the lower supporting plate with a rock arm. 10 having a pin which
engages with a radial slot 11 in the cam disc. 12 is a rock arm secured to the
vertical rock shaft 18 below the lower supporting plate and provided with a roller
which engages with a cam 7¹³ secured to the vertical driving shaft K. The back-
ward movement of the cam disc L is produced by the salient portion of the cam 713
engaging with the lower rock arm of the rock shaft 18 and the forward movement of
the cam disc is arrested by the roller on the lower rock arm 13 engaging with the
receding portion of the cam 113.
While the blanks are clamped on the drum the lowermost corners of
the blanks project downwardly below the drum and its jaws, and each
blank stands obliquely and laps over the preceding blank, as shown in
Figures 1 and 39, so that they are compactly arranged around the drum while
each lower corner is sufficiently exposed for performing the operations of perforat-
ing and threading the blank. This overlapping arrangement results from trans-
ferring the blanks in an oblique position from the feed trough to the drum. After
leaving the front wrapping screw the blanks are guided toward the delivery side
of the drum by a curved guide 114, Figures 1, 6, 11 and 39, arranged in front of
the central portion of the blanks and supported at one end on the shaft 62 and at
its opposite end on the supplementary frame.
After the foremost blank in the feed trough has been clamped against the drum
the latter moves forwardly one eighth of a turn and then stops with the lower
corner of said blank arranged in line with the punch which perforates the lower.
corner of the blank and which is constructed as follows:
M, Figures 1, 42, and 45, represents a perforating die arranged outside of the
path of blanks and adjacent to the place where the lower corner of the blank stops
to be perforated. This die is separated a sufficient distance from the drum to
permit the blank to pass between the die and the drum and is supported at its
lower end by a bracket m which is secured to the lower supporting plate and
extends outwardly below the path of the blanks. m³ represents a radially movable
punch which is normally arranged inside of the path of the blanks and which is
adapted to move outwardly against the die and perforate the blank which is in
place at this time between the punch and dic. The front end of the punch is
guided in an opening in the bracket m and is secured with its rear or inner end to
a radially movable slide or holder m³ which is guided in a way m³ in the lower
supporting plate. m² is a vertical rock shaft whereby the punch is operated and
which is journalled in a bearing in the lower supporting plate. This rock shaft

page_text: is provided above the lower supporting plate with a gear segment M¹ which
meshes with a gear rack m5 on one side of the punch slide. The rock shaft is
provided below the lower supporting plate with a rock arm m6 having a roller at
its end which bears against a cam m on the vertical driving shaft. When the
salient portion of this cam engages with the rock arm me the rock shaft and
segment are turned so as to project the punch and perforate a blank. The punch
is retracted by means of a spring m8 mounted on the lower supporting plate and
connected with the rock arm m6. The movement of the punch is so timed that
it is projected and retracted while the blank in front of the same remains at rest.
After the lower corner of the blank has been perforated the drum is turned
another one eighth of a rotation and stands still with the lower corner of the blank
arranged in line with the threading mechanism which draws the twine or cord
through the perforation of the blank and which is constructed as follows:-
N, N, Figures 1, 34, 40, 41, 42, 44, and 48, represent two twine feeding discs
which are arranged horizontally one above the other outside of the path of the
blanks and adjacent to the place where the perforated corner of the blank stops
temporarily. The upper disc is secured to the upper end of a vertical spindle n
and is provided on the underside of its marginal portion with an annular gripping
face n'. The spindle is journalled in a bearing formed in a standard n² which is
mounted on the front portion of the supporting ring i and the spindle is rotated
constantly in the direction of the arrow, Figure 34, by a train of gear
wheels n n n n6 mounted respectively on the vertical driving shaft, the lower
portion of the standard n³ and the lower portion of the feed spindle n. The lower
feeding disc N¹ is provided on the upper side of its marginal portion with an
annular gripping face n which stands opposite the marginal gripping face of the
upper disc. The lower feed disc is journalled on a bushing or arbor ne formed
on the standard around the upper portion of the feed spindle and has its axis
arranged slightly at an angle to the axis of the upper feed disc, so that one portion
of the lower disc is higher than the remaining portion of the disc and bears only
with a portion of its gripping face against the gripping face of the upper disc,
thereby causing the receiving side of the gripping discs to converge toward the
gripping point and the discharge side of the discs to diverge from the gripping
point, as represented in Figures 34, 44, and 48. The inclination of the lower
feed disc is such that the contact between the gripping faces of the discs takes
place on the inner portion of the disc, as represented in Figures 34, 40 and 44. The
feed spindle is pressed downwardly for holding the inner portions of the gripping
faces of the feed discs yieldingly in engagement with each other by a spring n³
which surrounds the spindle and bears with its ends against. the bottom of a recess
in the standard n on the upper side of the gear wheel no, as represented in
Figure 34. The lower feed disc is driven from the upper feed disc by vertical
pins no arranged on the underside of the upper feed disc and engaging loosely
with recesses n¹ in the upper side of the lower feed disc, as represented in
Figures 42, 44 and 51. n¹ is an annular flange which is formed on the underside
of the upper feed disc within its gripping face and engaging with an annular groove
formed in the upper side of the lower feed disc within the gripping face thereof and
which serves as a guard, whereby the twine is held in place between the gripping
faces of the discs.
The twine unwinds from a horizontal spool n¹s, Figures 1, and 11, mounted on
the front portion of the main frame below the drum and passes thence upwardly
through a twine guide n¹ arranged on the main frame in front of the feed discs
and thence around the receiving side of the guard flange and between the gripping
faces of the discs to the inner portions thereof, where the end of the twine is
clamped between the abutting portions of the gripping faces. Upon turning the
spindle this movement is transmitted by the pins from the upper to the lower feed
disc, whereby all portions of the gripping face of the lower disc are rolled suc-
cessively into engagement with the gripping face of the upper disc and the twine is
fed forward by the feed discs which roll in engagement with the opposite sides of

page_text: the twine. The slot in the twine guide through which the twine passes is preferably
so narrow that a knot or enlargement in the twine cannot pass through the same,
thereby arresting the forward feed of the twine and preventing imperfect work and
possible injury to the delicate parts of the machine. 15, Figures 42, 48 and 51, is
a notch or recess formed partly in the edge of the upper feed disc and partly in the
edge of the lower feed disc. This notch stands opposite the perforations of the
blank when the latter comes to a stand still before the threading device and forms a
clear space around the twine at the point where the twine is removed from the feed
discs and drawn through the perforations of the blank by the radially movable
threading needle o, which is provided at its outer end with a hook o'. This needle
stands with its hook on the inner side of the path of the blank, while the latter
is carried forward by the drum and is in line with the perforation thereof when
the blank stands still before the needle. The latter is guided with its outer portion
or free end in an opening formed in a guide and clamping block o2 which is secured
to the outer side of the lower supporting plate and is secured with its inner end to
a cylindrical holder o3 which is guided in a cylindrical way of in the lower support-
ing plate, as represented in Figures 34, 42, 44 and 47. After the blank has been
shifted so that its perforation stands opposite the needle the latter is moved out-
wardly with its hook uppermost through the perforation of the blank and into the
recess of the feeding discs. During the last portion of the outward movement of
the needle the inclined front side of its hook engages with the underside of the twine
which crosses the recess of the feeding discs, as represented in Figure 51, and
deflects the same upwardly and after the hook has passed the twine the latter drops
down into its normal position in front of the hook, as represented in Figure 52.
When the hook of the needle is in the recess of the feeding discs a considerable
portion of twine has previously been fed off by the feed discs and hangs loosely on
the delivery side of the feed discs, as represented in Figure 42. The twine is
grasped by those portions of the gripping faces on the discs which are on
opposite sides of its recess, the grip of the portions of the faces on the rear side of
the recess being stronger than the portions of the gripping faces on the front side
of the recess.
During the subsequent backward or inward movement of the needle its hook
engages with the twine which crosses the feed disc recess and disengages the loose
front portion of the twine from engagement with those portions of the gripping
faces on the front side of the recess and then pulls the loose front portion of the
twine through the perforation of the blank. After the needle is withdrawn from
the perforation of the blank it continues its backward movement until its hook
has receded into the opening of the clamping block o², as represented in Figure 43,
in which position the end of the twine is clamped lightly between the needle hook
and the adjacent portion of the clamping block. After the needle has receded
to its innermost position and clamped the end of the twine, the blank is moved
forward another one-eighth of a rotation and the twine is drawn into the form
of a loop or bight, as represented in Figure 43, the twine for this purpose being
sunnlied by the feed dises which pay the twine out continuously. When the
hook engages with the twine while 'the latter is held by the feed discs the portions
of twine on opposite sides of the hook are horizontally in line, as represented in
full lines Figure 53, and if the twine were held in this position by the hook while
the blank is moving forward and forming a loop in the twine, the front end of the
twine would be liable to creep over the top of the hook, as represented in dotted
lines, Figure 53, and disengage itself from the same. In order to obviate this
difficulty the needle, after its hook has disengaged the twine from the feed discs,
is turned one quarter so that its hook faces rearwardly, as represented in Figures 43
and 54, whereby the dangling free end of the twine is carried upwardly and the
main portion of the twine is carried downwardly, in which position the twine
cannot creep over the hook and disengage itself.
05, Figures 40, 41 and 42 is a horizontally reciprocating carriage whereby the
threading needle is moved back and forth and which is guided on the upper portion

page_text: of the standard n³ below the lower supporting plate. The inner portion of this
slide is provided with a bearing of which projects upwardly through an opening
in the bottom of the lower supporting plate and in which the front end of the
needle holder is journalled so as to be capable of turning independently of the
carriage but compelled to move lengthwise with the carriage. 07, Figures 40
and 41, is an elbow lever whereby the needle shifting carriage is operated and
which is pivotted on the front side of the standard n so as to turn in a vertical
plane. The upper arm of this lever engages with a notch or recess of in the outer
end of the needle carriage while its lower arm is provided with a roller engaging
with a horizontally rotating cam o. When the receding portion of the needle
cam engages with the elbow lever the latter is permitted to be turned in the
direction of the arrow, Figure 40 by a spring 010 whereby the needle is moved
outwardly through the perforation of the blank and into engagement with the
twine in the twine feeding discs. When the salient portion of this cam engages
with the elbow lever of the needle, together with its holder and carriage is moved
inwardly, so as to carry the twine through the perforation of the blank and clamp
its end against the clamping block. The spring which moves the needle outwardly
is preferably mounted on the pivot of the elbow lever o7 and connected with its
ends to said lever and the adjacent standard. The needle cam 09 is secured to the
upper end of a hollow spindle o" which is journalled in the standard n² and which
is rotated continuously at the same speed as the main shaft by the gear wheel no
mounted on the lower portion of the spindle, as represented in Figure 34 and
forming one of the train of gear wheels whereby the twine feed shaft is operated.
The oscillating movement of the needle is produced by a stationary pin o¹ arranged
in the bore of the cylindrical guide of the needle holder and engaging with a
cam or spiral slot o¹3 in the side of the needle holder, as represented in Figures 44
and 47. During the outward movement of the needle one side of the inclined or
spiral slot in its holder engages with the stationary pin whereby the needle is
turned so that its hook is on the upper side of the needle during the last portion
of the forward movement of the needle and engages properly with the twine in
the feed discs. During the backward movement of the needle the other side of the
inclined slot in its holder engages with the stationary pin and the needle is
turned one quarter after its hook has engaged with the twine. If a non-perforated
blank should be presented to the needle owing to the punch failing to perform its
function the needle will only be pressed against the inner side of the blank by
the spring, which latter is made of such strength that the needle will not be
forced through the blank, whereby the needle is prevented from being caught
in the lank and injured by the subsequent forward movement of the blank,
which injury would be liable to happen if the needle were moved forward positively
by a cam and retracted by a spring.
While the blank is moving forward one-eighth of a turn after leaving the
threading device the blank passes between a pair of co-operating twine cutters
or blades P P which are arranged, respectively, on the inner and outer sides of
the path of the blank and each of which is provided with a V-shaped cutting edge,
as represented in Figures 42, 43 and 46. The inner stationary cutter P is secured
'to a bracket p which is mounted on the adjacent portion of the lower supporting
plate and the outer movable cutter P¹ is mounted on a rock arm pl having a
horizontally swinging movement. After the blank has passed beyond the cutters
the outer cutter moves past the inner cutter whereby the overlapping V-shaped
cutters together form an eye or guide 22, as shewn in Figures 42 and 46 through
which both strands of the loop are drawn by the blank until the latter reaches
the end of the respective eighth of a turn, at which time the cutters have closed
upon the strands of the loop sufficient to produce a light tension on the twine
but not sufficient to cut the same and then stand still, thereby holding the twine
loop comparatively taut between the cutters and the blank. As the blank moves
forward from the threading device and forms the loop in the twine the blank
takes up
the slack which has been formed in the twine by the constant feeding

page_text: of the discs. The slack is fully taken up by the blank after the latter passes the
twine cutters, owing to the movement of the blank being faster than that of the
feed discs, and during the continued forward movement of the blank a tension is
produced on the loop which causes the front strand of the loop to be pulled out
of engagement with the needle hook owing to the grip of the feed discs on the
rear strand being greater than the grip of the needle hook on the front strand.
As the blank continues its forward movement after having passed the twine
cutters, the loose front strand of the loop is carried forward but still remains with
a considerable portion of its length in rear of the cutters when the blank comes to
a stand-still and the cutters close upon the strands for producing a tension on the
loop. When the blank comes to a stand still after having passed the twine cutters,
the knotting mechanism grasps both strands of the loop between the blank and
twine cutter and during the first portion of the tying operation draws a sufficient
portion of both strands through the cutters to form the knot. After the knotting
mechanism obtains control of both strands of the loop the outer cutter completes
its inward movement and cuts the 'twine, whereby a remnant of the front strand of
the loop is left behind the cutters and the rear strand of the loop is severed from
the main or supply portion of the twine, which main portion is now loose and free
to be pulled by the threading needle through the perforation of the next blank.
The movable twine cutter is mounted on the upper end of a vertical rock shaft på
which journalled in bearings on the supporting ring i and the standard n² and
passes through the hollow spindle o". For moving the outer twine cutter toward
the inner cutter the rock shaft is turned by a cam pt, Figures 34 and 38, arranged
on the lower end of the feed spindle m and engaging with a rock arm 25 on the
lower end of the cutter rock shaft and the latter is turned in the opposite direction
for separating the twine cutters by a spring 26 surrounding the lower portion of
the cutter shaft and secured with one end to the latter while its opposite end bears
against the lower end of the feed disc shaft or a stationary part of the machine.
The mechanism whereby the strands of the twine loop are tied together into
a knot is constructed as follows:
QQ, Figures 55-56, represent inner and outer knotter tubes arranged one
within the other and provided, respectively, at their upper ends with hook shaped
jaws gg. These tubes are arranged vertically in rear of the stationary twine
cutter and on the inner side of the path of the blanks, and the outer jaw is
journalled in the bracket p but is held against vertical movement by a gear
pinion q secured to the lower portion of the outer tube Q¹ and bearing with its
upper side against the underside of the bracket 2 and with its underside against
an arm ³ secured to the bracket p, Figures 55 and 56. The inner knotter tube
is capable of sliding vertically in the outer tube but is compelled to turn therewith
by means of keys or lugs 9 formed on the outer side of the inner tube and engag-
ing with longitudinal slots q5 in the outer tube, as represented in Figures 55, 56
and 58. Q2, Figure 55, is a vertically sliding pusher rod arranged within the
inner knotter tube and provided at its upper end with a notch or recess of forming
a fork which is adapted to engage with the twine and push the same against the
hooks of the knotter tubes.
Preparatory to tying a knot in a loop the pusher rod is depressed so that its
fork is arranged below the path of the twine and the knotter tubes are shifted so
that their jaws are arranged side by side and together form practically one hook
whose jaws are arranged on the inner side of the path of the twine and overhang
the same.
While the blank is moving from the threading to the knotting
mechanism the strands of its loop are carried against the outer side of the knotter
jaws and underneath the overhanging portion thereof, as represented in Figure 59.
After the blank comes to a stand still in advance of the knotter jaws the pusher
rod is moved upwardly so that its fork engages with the strands of the loop, forces
them against the underside of the knotter jaws and elevates the front or advancing
portion of the loop above the rear or trailing portion of the loop, as represented
in Figure 60. While the pusher rod is in this elevated position the knotter tubes are

page_text: turned in the direction of the arrow, Figure 61, and its jaws in a closed position
are carried underneath the raised front portion of the loop, as represented in this
figure. The pusher rod is now lowered, while the knotter tubes and jaws continue
to turn in the same direction and carry the rear portion of the loop underneath
the front portion thereof and form a complete sling or turn in the loop, as repre-
sented in Figure 62. As the jaws approach the rear portion of the strands the
inner jaw is lowered by depressing the inner tube and in continuing their
forward rotary movement the outer knotter jaw is carried over the rear portion of
the strands and the inner jaw is carried below the rear portion of the strands, as
represented in Figure 63. The inner knotter tube is now raised and its jaw is
moved toward the outer jaw, whereby the rear portions of the strands are clamped
between the two knotter jaws, as represented in Figure 64, and shortly thereafter
the twine cutters close entirely thereby severing the loop from the body of the
twine and from the remnant. The knotter tubes are now moved backwardly
with the ends of the strands clamped between the jaws until the jaws point
forwardly in the direction of the blank, as represented in Figure 65. The jaws
remain momentarily at rest in this position during the first portion of the next
forward movement of the blank, whereby the turn in the loop is stripped from
the jaws and the ends of the strands are pulled through the turn in the loop,
thereby forming a knot, as represented in Figure 66. The jaws retain hold of
the ends of the strands so that during the continued forward movement of the
blank the knot will be drawn tight and when the pull upon the loop becomes
sufficient to overcome the grip of the knotter jaws the ends of the loop are dis-
engaged from the knotter jaws, after which the knotter tubes and jaws are
returned to the normal position shown in Figure 59.
The oscillating movement of the knotter jaws is produced by a gear segment q
meshing with the pinion of the outer knotter tube and mounted on a rock arm 98
which is pivotted to the underside of the lower supporting plate. 9, Figure 37,
is a cam whereby the rock arm q8 is turned for moving the knotter jaws forwardly
and which is mounted on the vertical driving shaft and engages with a roller
on the rock arm 98. The backward movement of the knotter jaws is produced
by a spring 10 secured with its ends to the rock arm 98 and the lower supporting
plate. q is a horizontal connecting bar which is pivotally connected at its outer
end with the lower end of the pusher rod Q and which is hung by links q12 from
a horizontal rock lever q¹³, whereby the pusher rod is actuated. This rock lever
is pivotted with its inner end to the lower portion of the hanger 19, Figures 55
and 67, and is raised and lowered by a cam q14 which is secured to the vertical
driving shaft and which engages with a roller on the horizontal rock lever q¹³.
The inner knotter tube extends below the outer knotter tube, and is provided on
its lower portion with a stop collar q140 which is adapted to bear with its upper
side against
the lower end of the outer tube and thereby limit the
upward movement of the inner tube. q5 is a lifting lever which is
connected with the lower portion of the inner knotter tube and q16 is a spring
whereby this lever is pressed upwardly for holding the inner knotter tube yield-
ingly in its elevated position. The lifting lever is pivoted at its inner end to
one of the links q2 and is adjustably connected with the inner knotter tube by
passing the lower, exter, "ly screw threaded portion of the inner tube through
the lever and applying stop screws q7q18 to the inner tube above and below the
lifting lever, as shewn in Figure 55. q is a vertical rod which bears with its
upper end against the underside of the outer portion of the lifting lever and is
guided with its lower end in an arm 20 secured to the supporting ring i. The
spring 16 surrounds this rod and bears with its lower end against the arm 720
and with its upper end against a collar q21 on the guide rod. q is a collar which
slides on the inner knotter tube between the stop collar q140 and the upper stop
nut q and which is pivotally connected with the outer end of the rock lever glo
by pins q3 arranged on opposite sides of the sliding collar and engaging with

page_text: slots in the bifurcated outer end of the rock lever q¹³, as represented in
Figure 57.
During the first portion of the rotary movement of the cam q¹ it raises the rock
lever q3 from the normal position shewn in Figure 55 and the pusher rod con-
nected therewith, just after the loop of the blank has been carried against the
knotter jaws or hooks, whereby the pusher rod forms the upward bend in the
front portion of the loop to permit the jaws which now begin to turn forwardly,
to carry the rear portion of the loop under the front portion thereof. During
the last portion of the forward rotary movement of the knotter jaws the cam q¹4
depresses the rock lever below its normal position, whereby the pusher rod is
lowered into an inoperative position and the knotter jaws are separated by reason
of the sliding collar q22 on the lever engaging with the upper screw nut q" and
depressing the inner knotter tube, thereby permitting the knotter jaws to straddle
the loop. The cam now raises the rock lever to its normal position, whereby
the spring is permitted to raise the inner knotter tube and close the knotter jaws
on the loop in which position the parts are held while the knot is being completed
during the subsequent backward rotary movement of the jaws and until the loop
of the next blank has been carried across the knotter jaws. If the blank carrying
drum misses a blank or does not receive one so that a pair of drum jaws passes
by the looping mechanism without presenting a blank to the same the constant
feed of twine by the feeding discs is liable to clog the machine and obstruct the
parts in their subsequent operations. In order to prevent this occurrence each
pair of drum jaws is provided with a finger around which the loop is formed
when no blank is presented and which carries the loop away from the looping
mechanism. q, Figures 42, 44 and 49, are these clearing fingers which are hook
shaped and one of which is secured to each of the inner clamp jaws of the
drum. Each finger is arranged with its hook inside of the place where the blank
stands and back of the perforation in the same. If no blank is present the thread-
ing needle carries the twine across the clearing hook and the latter, during its
forward movement forms a loop in the twine and holds the same while its strands are a
being tied and takes the place of a blank.
3
After the knot has been tied on the loop of the blank and the latter is released
on the delivery side of the drum, the blank is carried obliquely downward and
rearward by a delivery or transfer mechanism into an inclined chute which latter
delivers the blanks into a V-shaped delivery or discharge trough. This chute
consists of a bottom board R, Figures 19, 68, 69 and 70, upon which the blanks
slide with their lower edges, a front board r extending upwardly from the bottom
board on the front side of the path of the blanks, and a bar arranged on the
inner side of the path of the blanks and secured by bolts 2 to the upper ends of
posts which are mounted on the bottom of the chute. The discharge trough 4
is arranged lengthwise in the rear of the chute, drum and feed trough and below
the same and is composed of a number of longitudinal bars which are connected
by V-shaped brackets 6 to the rear portion of the frame, Figures 6, 8, 11, 12, 16,
19 and 20.
4
The mechanism whereby the blanks are discharged is constructed as follows:-
55, $151, 52, 52, 53 53, Figures 1, 6, 8, 11, 68, 69, 70, 71 and 72, represent an
upper and a lower set of discharge rollers which are arranged adjacent to the
delivery portion of the drum and whereby the blanks are carried from the drum to
the discharge trough. The outer rollers s s of the upper set are arranged on the
outer side of the path of the blanks and mounted on a shaft and the inner
rollers of this set are arranged on the inner side of the path of the blanks
facing the rollers s s and mounted on a shafts. The outer rollers s² 2 of the
lower set are arranged on the outerside of the path of the blanks below the upper
outer rollers and mounted on a shaft s6 and the inner rollers of the lower set
are arranged on the inner side of the path of the blanks, below the upper inner 55
rollers and mounted on a shaft s. These shafts are arranged parallel with the

page_text: front and back ends of the blanks as the latter are discharged in an oblique position
by the drum whereby the blanks are propelled by the rollers in a line parallel
with the top and bottom edges of the blanks. The shaft s5 supporting the upper
inner rollers is journalled in fixed bearings arranged on the adjacent portion
of the stationary frame and the shaft supporting the upper outer rollers is
journalled in movable bearings, whereby the upper outer rollers are carried
toward and from the upper inner rollers. As the blank leaves the drum the upper
outer rollers stand away from the opposing inner rollers, so as to form a clear space
into which the blank can enter freely. After the blanks have entered between
the upper rollers the outer rollers are moved inwardly and the blank is pressed
between the rollers, whereby the latter obtain a firm grip upon the blank and feed
the same forward. The movable bearings of the upper outer roller shaft s are
formed on the upper portion of the rocking frame so which latter is pivotted at
its lower end on the main frame by pivots s¹l arranged parallel with the upper
outer roller shaft. The upper outer rollers are moved outwardly by an outer
spring secured at one end to the stationary frame and bearing with its other
end against the outer side of a downwardly projecting arm 13 on the upper rocking
frame 10, as represented in Figures 1, 6, 11, 70 and 71. 14 is an inner spring
bearing with its free end against the inner side of the arm 13 of the rocking frame
and secured to the stationary frame and s15 is a connecting rod which connects the
inner spring 14 with the rock arm (12 on the lower end of the rock shaft, 18, as
represented in Figures 37 68 and 70. When the salient portion of the cam [13
turns this arm 118 for the purpose of turning the cam L and releasing the blank
from the clamp on the delivery side of the drum, the inner spring s¹ is moved out-
wardly and thus turns the rocking frame $10 so that the outer upper rollers grip
the blank, and when the rock arm 12 engages with the receding portion of the
cam 13 the inner spring s moves inwardly so as to permit the outer spring $12
to separate the upper rollers.
By interposing the inner spring $14 between the connecting rod $15 and the rock-
ing frame 10 a yielding connection is formed between these parts which enables
the upper outer rollers to adjust themselves to the thickness of the blanks, thereby
avoiding binding and injury to the parts, which otherwise would be liable to happen
if the movable rollers were shifted by positive actuating mechanism.
The shaft suppering the upper outer rollers s extends forwardly beyond the
inner upper shaft $5 and is journalled at its front end in a fixed bearing 516 arranged
on the front portion of the frame, that portion of the outer shafts between its
fixed and movable bearings being sufficiently flexible to permit of the necessary
movement of the rocking frame. The upper rear end of the outer upper shaft is
provided with a gear pinion 17 which meshes with a similar gear pinion 518 on the
upper rear end of the upper inner shaft, whereby these shafts are rotated in unison,
the teeth of these gear pinions being sufficiently long so that they will remain in
gear in the different positions of the rocking frame. The shaft supporting the outer
lower discharge rollers 2 is journalled in fixed bearings 19 on the frame and the
shaft supporting the inner lower rollers 3 is mounted in movable bearings 520
which are arranged on a lower rocking frame 21 having a movement toward and
from the outer lower rollers. This lower frame 21 is pivotted on the post ³ and
is vieldingly moved towards the outer lower rollers by a spring, engaging its
ends with the post 3 and the lower rocking frame. The movement of the lower
inner rollers toward the lower outer rollers is limited by a stop 23 on the main
frame against which an arm 24 on the lower rocking frame engages, Figures 8,
and 68, and whereby the lower inner rollers are prevented from coming in contact
The lower
with the outer lower rollers when there is no blank between the same.
inner shaft is driven from the lower outer shaft by similar intermeshing gear
pinions 2526 secured, respectively, to these shafts below the path of the blanks,
and provided with teeth of such length that they remain in gear while the lower
rollers are moved toward and from each other. Motion is transmitted to the dis-
charge rollers for turning them in the direction of the arrows, Figure 69 by a belt $27

page_text: passing around a main driving pullev 28 arranged on the main horizontal shaft
in rear of the drum, guide rollers 29 29 arranged on the front portion of the main
frame, pulleys 30 31 secured, respectively to the lower front ends of the upper and
lower outer shafts, and a tension roller 2 mounted on the frame between the
rollers 3031, as shown in Figures 1, 6, and 68.
away from
and back-
T, Figures 6, 8, 11, 16, and 19 represents a vertical packer board which recipro-
cates lengthwise in the discharge trough and whereby each blank after being dis-
charged by the chute into the discharge trough, is moved rearwardly, so as to clear
the space in the trough below the chute and to pack the blanks into a pile or bundle.
While the blank is being delivered by the chute into the discharge trough the
packer board stands on the outer side of the path of th blank. After
the latter has dropped into the trough the board moves forwardly,
carrying the blank
the outlet of the chute
wardly in the discharge trough, after which the board returns 10
its normal position outside of the outlet of the chute. The packer board is
mounted on the front end of a bar which is guided in the bottom of the dis-
charge trough and connected with its rear end to a rock lever t¹, Figures 6, 8
and 16. This lever is pivotted on the main frame and is turned in the proper
direction for moving the packer board against the blank in the trough by a cam f
which is mounted on the main driving shaft and which engages with a roller on
the rock lever. The backward movement of the packer board is effected by a
spring connected with its ends to the rock lever &¹ and the discharge trough, as
represented in Figure 8.
, Figures 6, 8, 9, 19 and 68, is an inclined detent finger whereby the blanks,
after they have been carried away from the outlet of the chute by the packer board,
are prevented from moving backwardly again with the packer and obstructing
the chute outlet. This finger is arranged on the inner side of the discharge trough
and projects slightly into the path of the blank. As the latter is moved rear-
wardly by the packer board the inner edge of the blank passes along the inclined
under side of the detent finger and is deflected thereby and after the blank has
passed the detent finger the deflected portion of the blank straightens out and the
abrupt rear side of the finger engages against the blank when the packer is
retracted, thereby preventing the blank from moving back with the packer. The
detent finger is preferably formed on the lower end of the chute bar and is made
adjustable for different sizes of blanks by the fastening bolts 2 which pass through
a slot 5 in the bar 1, Figure 9.
U, Figures 6, 8 and 20, represents a vertical abutment board which is removably
arranged in the discharge trough on the inner side of the chute and against which
the blanks are packed after they have been delivered by the chute into the dis-
charge trough. This abutment board is provided with lugs u which project out-
wardly between the bars of the discharge trough, u represents a number of
abutment bars which are arranged lengthwise between the longitudinal bars of the
discharge trough and which bear loosely with their front ends against the lugs of the
abutment board while their rear ends are connected by a cross head u². A back
pressure is applied to the abutment board and the blanks behind the same by a
weight connected with the cross head 2 by a cord at which latter passes around a
roller mounted on the lower portions of the discharge trough, as shewn in
Figure 8.
If a blank becomes caught in the chute or in the mechanism which carries the
blanks from the drum to the discharge trough the operation of the machine is 5
automatically arrested by a stop mechanism which is constructed as follows:-
-
V is a main driving pulley which is so mounted on the rear end of the main
driving shaft as to be capable of a longitudinal and a rotary movement thereon.
This pulley is provided on the inner side of its hub with a clutch collar which is
adapted to be engaged with or disengaged from a clutch collar on the main 5
shaft by moving the pulley lengthwise on the shaft. is an intermediate coupling
lever which is arranged lengthwise in the main frame and pivoted between the rear

page_text: portions of the same to a bracket V1, Figures 1 and 12. This lever is provided on
its rear arm with a fork which engages with an annular groove in the clutch collar
of the pulley, Figures 1 and 12. is a main coupling lever which forms a forward
extension of the intermediate lever and is pivoted at to the main frame and loosely
connected at its rear end with the front end of the intermediate lever. is a
spring which connects the front end of the main lever with the main frame,
Figure 1, and exerts a downward pressure on the lever for uncoupling the driving
pulley from the driving shaft. W, Figures 1, 4 and 5, is a vertical catch whereby
the coupling levers are held in a coupled position. This catch is pivoted with its
lower end to the front arm of the intermediate coupling lever and passes with its
upper end through an opening which is formed in a bracket w mounted on the
main frame. The opening in the bracket is ☐ shaped one branch
being arranged transversely while the other branch w² is arranged
longitudinally and extends from the front end of the transverse branch toward the
rear end of the machine, as shown in Figure 5. The upper end of the catch is
provided with a shoulder w³ which is adapted to engage with a shoulder w formed
on the underside of the bracket adjacent to the rear side of the transverse branch
of the opening in the bracket, as represented in Figures 4 and 5. The catch is
yieldingly held in engagement with the shoulder of the bracket by a spring 105
connecting the same with the main frame and can be disengaged by hand from
the bracket shoulder by a handle w pivoted on the front arm of the main coupling
lever and connected by a rod w with the catch, Figure 1.
W8 is a vertical trip arm which is adapted to disengage the catch from the
shoulder on the bracket and uncouple the driving clutch. This arm is arranged
with its lower end in the rear of the upper end of the catch and is so mounted that
it is capable of a transverse and a longitudinal oscillating movement. This is
preferably accomplished by pivotting the upper end of the trip arm by a trans-
verse pin to a longitudinal horizontal shaft w10 which shaft is journalled with its
ends in bearings well on the main frame. Upon swinging the trip arm lengthwise
of the machine the catch is not disturbed but when the trip arm is swung trans-
versely forward it strikes the catch and disengages the same from the bracket,
thereby permitting the spring 6 to shift the parts for uncoupling the driving clutch.
W, Figures 4, 5 and 16, is a rotary trip disc mounted on the main shaft and pro-
vided with a pin 12 which is adapted to engage with the rear side of the trip arm
and swing the same forwardly so as to disengage the catch from the bracket
shoulder. 3 is a spring which connects the trip arm with the main frame and
which yieldingly holds the trip arm in the path of the pin on the trip disc. w repre-
sents an intermediate rock lever which is pivoted on the rear portion of the frame
The rear
and which is connected with its front arm by a rod wls to the trip arm.
arm of the intermediate rock lever is connected by a rod w with a main rock
lever X which is pivoted on the front portion of the main frame. The main rock
lever X is turned in the direction of the arrow, Figure 6, for permitting the
spring 3 to pull the trip arm into the path of the trip disc pin by means of a
cam, Figures 1, 8, and 18, mounted on the main shaft and engaging with a
roller on the main rock lever X and the latter is turned in a reverse direction for
shifting the trip arm out of the path of the trip disc pin w12 by a spring ¹,
Figures 6 and 8, which connects the main rock lever X with the main frame.
y, Figures 6, 8, 68, and 69, represents a number of feeling fingers which move
horizontally back and forth across the path of the blanks as they are carried by the
chute and delivery mechanism from the drum to the discharge trough and which
are adapted to detect any blanks that may be caught in the blank delivery devices.
These fingers are guided in openings formed in a stationary supporting bar y¹ which
is secured to the post or a part of the frame on the inner side of the chute, as
shown in Figures 68 and 69. y² is a reciprocating carrying bar to which the
inner ends of the feeling fingers are secured and which is connected with the free
end of the main rock lever X by rods y³. The movement of the feeling fingers is
so timed that they are moved forwardly across the path of the blanks, after a blank

page_text: is supposed to have been transferred from the drum to the discharge trough. If
the blank has been properly transferred the feeling fingers are moved forwardly
across the path of the blanks by the main rock lever X and the latter pulls the
trip arm rearwardly as shown in dotted lines, Figure 4, so that the pin of the
trip disc cannot strike the trip arm, thereby preventing uncoupling of the driving
mechanism. If a blank becomes caught in the transferring mechanism the feeling
fingers strike the same and are prevented from moving forwardly across the path
of the blanks, thereby preventing the rock lever X from pulling the trip arm w
out of the path of the trip disc pin w12 so that the latter during its rotary move-
ment strikes the trip arm and this arm in turn strikes the catch W and disengages
the same from the bracket, whereby the coupling levers are liberated and permitted
to uncouple the driving mechanism.
The blanks in moving through the machine are engaged only on their lower
portions while their upper portions are perfectly free, which enables this machine
to operate on blanks of various widths and lengths without necessitating a change
in the adjustment of its parts.
Having now particularly described and ascertained the nature of my said
invention and in what manner the same is to be performed, as communicated to
me by my foreign correspondents, I declare that what I claim is :-
1. A looping machine containing, in combination, perforating and looping
mechanism, and a rotating drum provided on its periphery with blank holding
jaws.
2. A looping machine containing, in combination, an upright rotating drum
provided on its periphery with blank holding jaws, a feed trough opening against the
drum and provided with means whereby the blanks are fed successively against the
drum, and perforating and looping mechanism arranged below said drum, sub-
stantially as set forth.
3. A feed trough composed of longitudinal rotating shafts arranged to deliver
the blanks to the carrier by which they are presented to the looping mechanism.
4. The herein-described mechanism whereby the two sets of shafts composing
the feed trough are rotated in opposite directions, such mechanism consisting of a
driving shaft provided with a crank, a yoke connected with said crank, cranks
secured to one set of said shafts and connected with said yoke, a counter shaft
provided with a crank which is connected with said yoke, and gear wheels con-
necting the counter shaft with the other set of shafts.
5. The open feed trough in which the blanks are arranged provided with a
follower which projects beyond the sides of the trough, and longitudinal actuating
bars detachably connected with the follower.
6. The separating finger which has a rotary motion across the feed trough, so
that the finger enters edgewise between the blanks, and which has a subsequent
motion lengthwise of the feed trough whereby the blank in front of the finger is
moved forward in the feed trough.
7. The conveyor screw against which the blanks are moved by the separating
finger which enters between the blanks in the feed trough and moves one of the
same forward and against said screw.
8. The combination of the feed trough, the conveyor screw, clamping jaws, and a
telescopic actuating shaft upon which the screw and jaws are mounted.
9. The combination of the feed trough, the separating finger whereby one of the
blanks is moved forwardly, the conveyor screw whereby the forward movement
of the blank is continued, and rotary separating blades which complete the separa-
tion of the blanks.
10. The separating blades mounted on the shafts which form the feed trough.
11. The blank carrying drum, in combination with a wrapping device whereby
the projecting portions of the blanks are laid against the peripheral face of the
drum.

page_text: 12. The combination of the blank carrying drum, a feeder whereby the blanks
are fed obliquely against the peripheral face of the drum, and a perforator so
arranged below the drum as to perforate the exposed corner of the blank.
13. The combination of the blank carrying drum, a feeder whereby the blanks
are fed obliquely against the peripheral face of the drum, a perforator so arranged
below the drum as to perforate the exposed corner of the blank, and a threading
mechanism so arranged below the drum as to draw the twine through the perfora-
tion in the blank.
14. The rotating twine feeding discs arranged at an angle to each other so as to
grasp the twine only on one side of the discs.
15. The rotating twine feeding discs arranged at an angle to each other and pro-
vided with a gap into which the needle enters and across which the twine extends.
16. The threading needle combined with mechanism whereby a reciprocating
movement is imparted to the needle and with mechanism whereby the needle is
given a partial turn backwardly after it has seized the twine.
17. The combination of a moving blank carrier, a threading needle which draws
the twine through the perforation of the blank, a knotting hook arranged in rear
of the blank carrier and past which the twine drawn through the perforation of the
blank, is carried by the movement of the blank carrier, and gripping and cutting
iaws which are arranged between the needle and hook and which impinge upon the
twine while the hook is tying the knot and afterwards cut the twine.
18. The combination of the knotter hook and a pusher whereby the twine is
pushed into the bight of the hook.
L
e Naamber 1907
HASELTINE, LAKE & Co.,
45, Southampton Buildings, London, W.C., Agents for the Applicant.