Improvements in or applicable to Sheaf-binding Harvesters.
Year: 1891

page_text: Date of Application, 19th May, 1891-Accepted, 5th Sept. 1891
COMPLETE SPECIFICATION.
Improvements in or applicable to Sheaf-binding Harvesters.
A communication from JAMES RALPH SEVERANCE, residing at Poughkeepsie,
County of Duchess, State of New York, United States of America, Inventor.
I, ALFRED JULIUS BOULT of 323 High Holborn in the County of Middlesex.
M.I.M.E., 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 sheaf-binding harvesters of that type in which the
grain is bound into sheaves between the platform-conveyor and the driving wheel,
and it consists in improvements in the construction and arrangement of the feeding
mechanism, the binding mechanism, and the mechanism for discharging the bound
sheaves, and also in certain other improvements in the apparatus and in the details
of construction, all as hereinafter described and specified.
In the accompanying drawings representing the improvements in sheaf-binding-
harvesters;
Fig. 1 is a plan view, the platform being partially omitted.
Fig. 2 is a section on the line 2-2 Fig. 1, showing some of the parts in front
of said line, the platform and driving wheel being omitted, and the binding arm
and other devices connected therewith being represented in the position they
Occupy when at rest.
Fig. 3 is a similar section, showing the parts in the position which they occupy
when the point of the binder-arm is about to cross the throat, and representing
also the position of the binder-arm at the end of its movement by dotted lines.
Fig. 4 is a partial front elevation, representing the swinging binder post, the
mechanism for operating the same, and the binder-arm.
Fig. 5 is a longitudinal section of the feeding mechanism on the line 5-5
Fig. 1.
Fig. 6 is a front elevation of the binder driving gear, showing part of the starting
and stopping mechanism.
Fig. 7 is a horizontal section on line 7-7 Fig. 6.
Fig. 8 is a section on line 8-8 Fig. 7, looking forward.
Fig. 9 is a similar section on line 9-9 Fig. 7.
Fig. 10 is a horizontal section of the clutch similar to Fig. 7, showing the
tripper disc withdrawn.
Fig. 11 is a section similar to Fig. 9 on the line 11-11 Fig. 10.
Fig. 12 is a diagram representing the knot in open or loose formation..
Fig. 13 is a plan view of the knotting-mechanism.
Fig. 14 is a plan view of the same,-the protecting casing being removed.
Fig. 15 is a transverse section on the line 15-15 Fig. 14, showing the knotter-
spirals, their driving cam, and the cord-holder in elevation.
Fig. 16 is a section through the stationary cord-guide, on the line 16-16,
Fig. 17, showing the cord-holder in side-elevation.
Fig. 17 is an elevation of the cord-holder and the stationary cord-guide.
Fig. 18 is a transverse section through the cord-holder, on the line 18-18,
Fig. 16, showing the parts to the right hand of said line.
Figs. 19 to 24 inclusive are diagrams representing the successive steps in the
formation of the knot.
Fig. 25 is a plan view representing the cam-shell, the knotter-spirals, and the
divided nut or guide for the latter.
Fig. 26 is a side elevation of the knotter-spirals detached.

page_text: Fig. 27 is a section on the line 27-27, Fig. 25 showing the parts to
hand of said line.
Fig. 28 is a section on the line 28-28, Fig. 25.
the ICLG
Figs. 29 and 30 show the inner surfaces of the washers used to adjust the
cam-shell.
Fig. 31 is a rear elevation of the knotting mechanism.
Fig. 32 is a side elevation of the discharger-mechanism, taken from the left-hand
side in Fig. 1, showing also a part of the binding mechanism.
Fig. 33 is a plan showing the parts of the discharger mechanism below the
line 33-33, Fig. 32.
Fig. 34 is a front elevation of the parts of the discharger in the position they
occupy when the discharger-arm is vertical.
Fig. 35 represents the same when the discharger-arm is horizontal.
Fig. 36 is a side elevation, partially in section, of the feeding mechanism.
Fig. 37 is an interior view of one of the wooden staves of the feeding
mechanism.
Fig. 38 is a transverse section of the feeding mechanism, showing one of the.
fecders in elevation.
In the accompanying drawings, AA represents the longitudinal sills of the frame
of the machine, B the transverse sills, Ċ the main driving wheel, D the cutting
apparatus, E the conveyor-belt, F the grain feeder, G the binding arm, H the
swinging binder-post, I the knotter, and the bundle discharger arm.
The main driving wheel C transmits motion to the operating parts of the machine
by means of the gear a, pinion and shaft c provided with a bevel wheel which,
through a corresponding pinion, operates the main driving shaft d. The knives of
the cutter bar D are operated by a crank on the forward end of the shaft d, or in
any suitable manner.
The shaft is supported in suitable journals depending from the harvester-frame,
and transmits motion to the shaft which drives the binding and knotting
mechanism, through suitable gearing 2 m², Fig. 1. The platform is provided at
the end next the uncut grain with a roller for the conveyor belt, a wheel and a
divider, as usual. The machine is provided with suitable draft appliances, and
may be arranged to be raised or lowered, or tilted, in any suitable way.
In the operation of the machine, the cut grain falling on the platform, is
conveyed towards the binder mechanism, by the conveyor belt E, and elevated
through the throat K into the receptacle L, where it is seized by the movement of
the binder arm and carried across the throat to a position over the binding table,
where the cord is tied about the gavel by the operation of the knotter, after which
the bound bundle is discharged by the teeth or prongs ff on the bundle discharger
arm J, the bound bundle being delivered in the rear of the machine. The bundle
bound at one operation of the binding mechanism remains on the binding table with
the fork of the discharger engaged under it, until at the next operation it is
discharged by the movement of the discharger arm, which returns to engage with
the bundle which is being bound. The binder arm G is sustained by the overhung
swinging binder-post H, which is operated from the crank e on the forward end
of the binder driving shaft by means of the link hi, which also operates the
binder arm through the connection and crank. The shaft g is driven from the
main driving shaft d by suitable gearing.
The binding frame consists of suitable transverse bars m m, connected together
by the longitudinal rods or bars n which are arranged to be adjusted backward and
forward on the main frame of the machine on suitable ways or guides. Provision
is made for adjusting the binding mechanism so as to adapt the machine to binding
grain of different lengths centrally by means of the lever N, Fig. 1, connected to
the binder frame by a suitable link, and provided with a notched segment and catch
by which the binding mechanism is fixed in any desired position relative to the
cutter-bar, the shaft, Figs. 1 and 2, being arranged to slide lengthways through
the gear which drives it. The binder frame may be provided with a suitable

page_text: platform to prevent the grain from falling into the machinery beneath it,―the said.
platform being omitted in the drawings for the sake of greater clearness of
illustration.
Proceeding now to a description of the mechanism by which the binder arm is
operated, it will be observed from Fig. 4, that the lower end of the overhung
binder-post II, is pivoted at o on the front corner of the binder frame and that it
is provided with a projection or arm carrying a stud on which the link / is
pivoted. The other end of the link is pivoted to the crank pin on the crank e,
which by its revolution imparts a reciprocating motion to the binding post, as.
indicated by the full and dotted lines, HH, in Fig. 3. At its upper end the over-
hung swinging binder-post H carries the shaft, to the rear end of which the
binder arm G is secured. In order to impart the requisite vibrating motion to the
binder arm, the link is extended beyond the pivot 9 by an arm i, Fig. 4, carrying
the pins at its extremity, on which the lower end of the connection is pivoted, -
its upper end being pivoted at u on a stud on the crank fastened to the forward
end of the binder-arm-shaft t. The crank e makes one revolution in the direction
indicated by the arrow in Fig. 4, for each bundle bound, and the result of the
arrangement is that every time the crank e revolves, the binder swings forward and
back over the binding table carrying the binder arm with it, while at the same time
the binder arm makes a vibration, its point swinging downward and outward,
sweeping the grain across the opening of throat K, from the gavel receptacle L to
a position over the knotter I where the band is secured. The lower end of the
connection is threaded into a sleeve v, provided with a jam nut, so that the length
of the connection can be adjusted to vary the path traversed by the binder arm
during its vibration. During its return movement, the point of the binder arm
swings upward so that it clears any grain in the receptacle. The position occupied
by the binder arm when at rest is represented by full lines in Fig. 2, and its position
at the extremity of its vibration while compressing the bundle, is indicated by the
dotted lines in Fig. 3. The links are connected together by the brace, so as
to secure stiffness in the lever with the least weight. The swinging binder-post H
may be pivoted to the forward end o of the rod à of the binder frame. The arm w
is also attached to the forward end of the rod n, by a set screw or pin, thus serving
to hold the binder post in place on the rod. The arm w connects the feeding
mechanism or a portion thereof, with the binding mechanism, so as to cause it to
move backward and forward simultaneously with the binder frame, when the
latter is adjusted to bind short or long grain centrally of its length. The guides or
ways on which the binder frame slides are represented at a, in Fig. 4.
A clutch is provided by which the binding mechanism is automatically thrown
into operation by the accumulation of sufficient grain to form a bundle in the gavel
receptacle L, raising the sizing lever y, Figs. 1 and 2. This clutch, which is repre-
sented in detail in Figs. 6 to 11 inclusive, serves to connect the main driving
shaft 3, which runs continuously, with the binder shaft g, at the proper time, so
that the shaft g makes one revolution and then remains at rest until the next bundle
is ready to be bound.
The conveyor E is of any usual or preferred construction. As represented in
the drawings, it consists of an ordinary canvas belt provided with transverse slats
and running over rollers at each end. The roller z Fig. 2 at the end of the
conveyor next the binding mechanism is driven from the shaft d by a chain belt and
sprocket wheels, as indicated at p q², Fig. 1, or other suitable devices.
Across the end of the conveyor belt and parallel therewith, is placed the
clearance roller V, which is driven from the shaft d in any convenient manner, as
for instance by the chain p' and a suitable sprocket-wheel,-the direction of its
rotation being indicated by the arrow in Fig. 3. At suitable distances along its
length, the clearance roller is provided with grooves in which the lower ends of the
spring guides a' are located, these guides being connected with the frame by the
arms . The lower ends of the spring guides'a are provided with the projecting
fingers c¹ which receive the grain from the delivery end of the conveyor and prevent

page_text: its falling onto the ground. The spring fingers a¹ extend upward, being given a
suitable curved form, and constitute practically the outer side of the throat K,
through which the grain is carried to the gavel receptacle by the revolving feeding
mechanism F.
The feeding mechanism, by which the grain is carried through the throat into
the receptacle, consists of a series of rims or collars d' provided with the projecting
teeth e, to which motion is imparted by the gears fg at the forward end of the
machine, as represented in Figs. 1 and 4. The pinion is secured on the forward
end of the shaft of the clearance roller V and meshes with the gear g', which causes
the feeders to revolve. Provision may also be made for driving the reel from the
gear by means of the bevel gears and the upright shaft j'. The toothed wheels
constituting the feeders are preferably cast in pairs, adapted to be attached together,
the line of division being indicated at yl, Fig. 5. The lower ends of the points of
the clearer bars Z extend into circumferential grooves, m', Fig. 5, between the
rings d', so that the grain cannot become entangled under the points of the clearer
bars. As indicated in Figs. 2 and 3, the clearer bars are given a suitable curved
form, extending upward and inward towards the grain side of the machine,, and are
bent over or recurved at their upper ends so as to hold the grain and constitute the
lower and grain sides of the gavel receptacle. The clearer bars are supported by
the angle-bar & extending lengthways of the machine, and which is itself sustained
by suitable arms at its ends.
At the front end of the grain-receptacle is placed the end board M', Figs. 1,
4 and 5. Immediately behind the end-board is placed the revolving butt-disc I",
which revolves with the feeders, and assists in feeding the butts of the grain
upward through the throat. The butt-disc is made of a size to correspond with
the throat so that the front end of the throat is closed by a moving surface, or
travelling end board, which travels at the same speed as the feeders. This device
avoids the retarding effect of the friction of the butts of the grain against a
stationary end-board, and with the front row of feeder teeth forms an effective
means of forcing forward the butts into the receptacle, when the grain comes to the
feeder with the heads in advance. The feeders at the forward and rear ends of the
feeding mechanism are stationary or non-adjustable lengthways, while the feeder
next to the binder-arm is made adjustable lengthways of the grain with the binding
mechanism, and the corresponding clearer bar Z is also made adjustable,-being
attached to the rod W which slides through the bosses in the other clearer
bars. The clearer bars Z Z are provided with the feet' by which they are
secured to the angle-bar . The adjustable feeder, F', Fig. 5, is fastened to the
rear end of the rod, ', and at its forward end the rod is attached to the binding
mechanism by the arm we, so that when the binder is shifted lengthways of the grain,
the feeder F, opposite the knotter, is shifted correspondingly.
is
By this construction the feeding of the grain into the receptacle and the passage
of the point of the binder-arm through the grain are facilitated. The rod
secured to the feeder F¹ at its rear end, as indicated at 2, Fig. 5, and at its
forward end it revolves in an eye in the end of the arm wr, being retained longi-
tudinally by the collars S¹ which are fastened to the rod on each side of the eye.
The feeder F may however, if preferred, turn on the rod. The gear g'is
supported in a suitable standard W1, Fig. 5 at the forward end of the machine,
by a sleeve revolving in the standard, rod sliding freely through an opening
in the sleeve. The sleeve may be formed integral with the bevel, and its inner
end threaded into the boss on the gear g. The gear g' also preferably forms the
forward head of the drum or cylinder Y,-the rear end of which is preferably
formed by the rear feeder F, provided with a central spindle Q', which
turns in a journal fastened on the bracket R', which is curved outward to afford
room for the passage of long grain, Fig. 5. The drum Y may be made of sheet-
metal in one length or in sections of suitable length, or, as represented in the
accompanying drawings, of wooden staves. As shown the drum is constructed.
of. four wooden staves, Y, Y, but any other preferred number may be used:

page_text: The tie-rods 2, connect the heads together, being provided at one or both
ends with nuts by which the heads are drawn up firmly against the ends of the
staves. The heads are provided with inwardly projecting circular flanges, of an
internal diameter equal to the external diameter of the drum, and forming
recesses into which the ends of the staves are inserted. The edges of the staves
are dressed on radial lines so that they bear against and support each other in
place. Suitable means are provided to compel the staves to revolve with the
heads; as for instance lugs or wedges es, e³ Fig. 36, fastened to the heads and
projecting inward between the ends of the staves at one or more of the joints
between the staves. These wedges are conveniently cast with the heads.
In order to locate the stationary feeders F and the front half of the rear
feeder F on the drum, and cause them to revolve with the drum, notches e¹,
Fig. 37 are cut in the edges of two of the staves, and the feeders are provided
with lugs of, Figs. 5 and 38 projecting radially into the notches. Between the
front feeder and the revolving butt-dise PI an enlarged drum Y³ is placed,
which, while it is not essential to the operation of the disc, is useful in preventing
any accumulation of straw, grass or weeds at the forward end of the feeders.
This drum and butt-disc arc conveniently made of sheet iron, and are conveniently
mounted as shown in the drawings by extending the drum between the front
feeder and the head, and attaching the disc to the exterior surface of the drum.
In this case an opening is made through the end-board M' sufficient to admit
the drum, Y. The adjustable feeder is provided with one or more radial
arms Fig. 36 which extend inward from the rim or rims of the feeder, and
constitute the means of connection with the rod. These radial arms & pass
through slots t made in the staves by cutting away one edge of two of the staves
along the joint. The diameter of the adjustable feeder is preferably made some-
what greater than that of the drum, so that it may move easily thereon.
The parts constituting this feeder drum are readily assembled by placing the
feeders in position on the notched staves, and then sliding the sinooth staves
lengthways into place, after which the heads are secured to the staves by the
rods, . It will be observed from an inspection of Figs. 2 and 3, that while
the acting edges of the feeder teeth e e² are inclined backwards from the radial
line, the edges of the teeth ele are still more inclined. The object of this
arrangement is to facilitate the operation of the binder arm in carrying the grain
from the receptacle to the binding-table,-the movements of the binder-arm and
the feeder being so timed that the point of the binder-arm always crosses the
throat K when one of the teeth e¹ is travelling upward in the upper part of the
throat. The feeder revolves at one half of the speed of the shaft gan the clutch
by which the binder-arm is driven has four teeth or points of engagement, so that
the parts can be adjusted so that the point of the binder-arm will always cross the
throat at the time one of the teeth e arrives at the upper part of the throat, sub-
stantially as indicated in Fig. 3. The teeth e, in consequence of their being more
nearly radial, are stronger feeders than the other set of teeth e' e'. The teeth of
all the feeders are constructed like those on the adjustable feeder. The lower part
of the adjustable clearer-bar Z¹ is provided with an arm 1, Fig. 3, which fits the
groove in the rim d', so as to prevent the clearer bar from being accidentally swung
towards the binding-table.
The construction and operation of the clutch by which the binding mechanism is
actuated, will next be described.
A', Fig. 6 represents a pinion mounted upon a shaft 13 which is rotated from the
main shaft d by suitable intermediate connecting gears, as shown at m² n² in Fig. 1.
The shaft is made square for most of its length so as to slide through a square
hole in the hub of the gear m² when the binding mechanism is shifted on the main
frame. B' represents a gear engaging with the pinion A', which is mounted upon
the binder driving shaft 9. As indicated in Fig. 1, the pinion and gear are placed
immediately in front of the knotter casing.
The gear B' is recessed on its rear side and is provided with a pawl C¹ secured

page_text: thereto on a pivot o¹, Fig. 8. D¹ represents a disc secured to the shaft g, Fig. 7,
and provided with an annular rim Fig. 8, having four ratchet teeth. The
pawl C¹ is arranged adjacent to the inner side of the rib E' and is held out of
engagement with the ratchet teeth, by means of an auxiliary pawl F which bears
against the tails of the pawl C, which is thrown into engagement with the ratchet
teeth by means of the spring f Fig. 8. The auxiliary pawl F3 is provided with
a forwardly extending finger which projects through a slot formed in the
gear Band rests against the periphery of the tripper disc H. The latter is
mounted loosely on a collar I', secured to the shaft g by a pin , Fig. 10. The
disc H is provided with an arm J', secured on a guide rod K, and L' is a rod,
which through suitable mechanism connects the arm J of the tripper disc H' with
the sizing lever y, over the gavel-receptacle, so that when the sizing lever is raised
by the accumulation of a bundle of grain in the receptacle, the disc H¹ is shifted
lengthways of the shaft g, from the position near the gear B represented in Fig. 7
to the position indicated in Fig. 10.
which fits into a
The disc H' slides
and 10.
The collar is provided with a laterally projecting lug
correspondingly shaped slot m³ formed in the tripper disc H.
forward and backward on the collar I', as represented in Figs. 7
The rear side of the tripper disc H' is provided with four Figs. 9, 10
and 11, which force the finger g' outward to the periphery of the tripper disc H
whenever the latter is moved up to the gear B.
cams,
During the time that the revolving feeding teeth feed the grain into the gavel-
receptacle, the disc D¹ remains stationary, and the gear B₁, carrying the pawl C',
disengaged from the ratchet rim E, is revolved by the pinion A', as indicated in
Figs. 2, 3 and 6.
When a sufficient quantity of grain has been fed into the gaveling or measuring
receptacle, the gavel operates the sizing lever y, which is connected with an
elbow lever Figs. 1 and 4, attached to the end of the rod L', and draws
the tripper disc H forward, releasing the finger q' of the auxiliary pawl F³, from
its bearing on the edge of the disc H', thereby allowing the spring to force the
pawl Cinto engagement with some one of the ratchet teeth on the rim E', which
causes the disc D' to revolve in unison with the gear B¹.
The disc D', being secured to the shaft g, the latter, by the connecting mechanism,
operates to move the oscillating post carrying the binder arm forward and backward
and also operates the knotter.
When the disc H is drawn forward away from the gear B', it releases the lug
from the recess m³, and by the revolution of the shaft g, the lug 2 is carried around
opposite to the plane surface of the disc H and prevents the disc from being
returned towards the gear B' by the action of the spring, until the binder has
completed one revolution and the lug has returned opposite to the slot m³.
When the disc H is withdrawn from its position near the gear B', the auxiliary
pawl swings inwardly which causes the finger 91 of the latter to stand directly
opposite the series of cams ³ formed on the rear side of the disc H', as shown in
Fig. 11, and when the disc H', is forced rearwardly again after the shaft makes one
revolution, one of the cams ³ next adjacent to the finger engages with it and
forces the latter gradually outward, until it again bears on the periphery of the
disc H' around which it continues to travel, until again released by the withdrawal
of the disc H'.
When the finger of the auxiliary pawl bears on the periphery of the disc H', it
has withdrawn the pawl C from the ratchet rim E', and the motion of the disc D' and
the shaft is discontinued. It is necessary to make the slot m³ somewhat elongated,
thereby permitting the lug to enter the slot, and continue to move with the shaft g
a sufficient distance to enable the cams ³ to move the pawl finger F³ outward, and
consequently throw off the pawl C from the ratchet E¹.
If the pawl C happens to drop in behind a ratchet tooth, there may be nearly a
quarter revolution of inactive movement, and the swinging post of the binder arm
remains stationary, until the pawl C₁ strikes the next ratchet tooth. This

page_text: arrangement enables me to properly time the movement of the binder-arm and the
inclined feeding teeth, e', as already described.
The guide-rod K' slides in suitable ways on the binder-frame.
The movement of the tripping or sizing lever is transmitted to the disc H in the
following manner; the sizing lever y is attached to a rock-shaft a³, Figs. 1 and 4,
supported in suitable journals on the binder-arm-post H, and the rock-shaft a has
fastened to it at its front end an arm 6 to which the rod is connected, the lower
end of which is pivoted to the elbow-lever w', which in its turn is pivoted to the
rod L' which is fastened to the arm J' carrying the disc H. The elbow lever w
is pivoted to the side of the binder-arm-post. The rod c is provided with an
adjusting nut, and a spring, Fig. 4, bearing against a collar on the rod, by
which the sizing lever y may be set so as to make any desired size of bundle.
12, Figs. 1 and 10 is a spring on the rod K', which forces the disc H' towards the
gear B
The binding cord is carried in a suitable box N1, Fig. 1, from which it passes
through a suitable tension device, and the guide-eye o³, to the point of the needle-
arm and thence to the knotter I, the construction and operation of which are
hereinafter described. The knotter is enclosed within a suitable casing, which is
supported on the binder-frame,-being provided with a slot in which the point of the
binder-arm works. The casing has one or more upwardly projecting horns or
detents, O, or P¹ Figs. 13 and 32 against which the grain is carried by the binder-
arm, and which assists in the formation of the bundle during the compressing
operation. An upper or top compressor is provided which travels with the gavel
during its progress from the receptacle or measuring-chamber to the binding-
chamber, retaining the gavel in proper shape, and forming a cover for each
chamber alternately.
The construction of the bundle-compressor is represented in Figs. 1, 2, and 3.
An arm or bracket, 2, Figs. 2 and 3, on the rear end of the binder-arm post, is
provided with a studs, on which the compressor-carrying-arm U₁ is pivoted,
provision being made for limiting the vibration of the arm U' on the stud by
means of the stop t² and the lugs ²². The arm U' extends towards the grain side
of the machine, -being provided with an extension XI, which projects upwards at a
suitable angle. The compressor V is pivoted to the arm U₁ at w² and in the
position shown in Fig. 2, extends over the gavel-receptacle, being held down
against the grain therein by a spring a, and provision being made for limiting its
movement on the point w³, by the stop on the arm U₁ and the lugs a³ Fig. 2.
The spring is coiled one or more times around the studs, and one of its ends
bears against a lug or projection on the arm U₁ and the other against a notch or
recess in the compressor V₁. When the binding mechanism is in its initial position,
as shown in Fig. 2, the arm U rests against a shoulder on the clearer-bar Z, and
the compressor is held in suitable position over the grain receptacle to assist in
retaining the grain and guide it against the tripping lever y. As the rocking
binder post, H, swings over toward the binding-chamber the arm U' is carried
away from the shoulder or stop 13, and by reason of its being loosely pivoted at s
the whole compressor, VI, U¹, is free to adjust itself to the direction of pressure of
the gavel and act as a cover for the bundle while it is carried across by the
binder-arm into the binding chamber.
The dotted lines in Fig. 3, show the position of the binder-arm and top-com-
pressor, when the compression of the bundle is finally completed in a binding
chamber formed by the knotter casing, the horn or detent O' or P on the knotter
casing, the binder arm, the top-compressor and a side compressor Y¹ hereinafter
described. During the return movement of the binder arm post the compressor, V',
is carried off from the bound bundle. It is thus made to act in harmony with the
discharger mechanism, affording opportunity for the bundle to be lifted out of the
binding chamber as hereinafter described.
Near the end of the return, movement of the post, the long extension X' of the

page_text: compressor-carrying-arm U¹, rides against the offset or shoulder, j³, on the clearer
bar, Z, thereby causing the compressor again to take its proper position over the
grain receptacle.
A gate or side compressor, Y¹, Fig. 2, is arranged to stand between the receptacle
and binding-chamber during the operation of the knotting mechanism, and to assist
in separating the bundle which is being bound from the grain which is being fed
into the receptacle.
The side compressor consists of an arm Y¹, pivoted below the knotter casing,
and projecting above the casing as shown in Fig. 2. The portion of the arm
above the casing is made wide and is preferably constructed, as shown, in
skeleton form. To permit the passage of the bundle from the receptacle to
the binding-chamber the compressor-gate, Y', is arranged to rock on its pivot, 63,
to the position shown by full lines, in Fig. 3. In this position the end of the side-
compressor lies near to or between the teeth of the adjustable feeder, F1, so that,
as the teeth travel upward, they carry the grain above the end of the compressor,
and at the time when the binder-arm is carrying the gavel across the throat, K,
the side-compressor Y', and the more sloping feeder teeth, e¹, act together to
partially separate the grain in the receptacle or gaveling-chamber from that in
the throat, and facilitate the passage of the point of the binder-arm. It will be
observed that the gate or side-compressor occupies a position below the path of the
gavel, while the latter is being carried across the throat by the binding-arm, so
that the gate assists in supporting the gavel during the passage across the throat,
and that it then rises, behind the bundle, to the position shown by dotted lines in
Fig. 3, and assists in the compression of the bundle. The side compressor is
pivoted at 63 on the frame-bar X, Fig. 15, and is operated by a cam groove c³, on
the side of the disc D', the return motion being secured by a pin or roller, g, striking
against the lug, d³, so as to give the side-compressor a quick movement downward.
The side-compressor is shown in the different positions it occupies at the ends of its
vibration, by the dotted and full lines in Fig. 3. It remains in the position indicated
by the dotted lines, during the return movement of the binder-arm, and retains the
bundle in position on the binding-table until it is lifted by the discharger-fork
as hereinafter described.
A butt-hook, 2, Fig. 1, is keyed on the binder-shaft t, so as to oscillate with the
binder-arm. It is made of the same general form as the needle arm, but is some-
what shorter, and serves the purpose of pulling the butts of the grain over into the
binding-chamber. The binder-arm-post is recessed to permit the attachment of the
butt-hook to the shaft t. A spring pawl, t³, Fig. 2, prevents a backward movement
of the binding mechanism.
Any suitable knotting mechanism may be used in connection with my improved
sheaf-binding harvester, but it is preferred to employ a knotter of the form
represented in Figs. 13 to 31 inclusive.
Fig. 12 is a diagram representing the kind of knot formed by my improved
knotter, the knot being shown open or with the cords separated from each other.
In the accompanying drawings, n n, Figs. 13, 14, 15 and 31, represent the parallel
rods of the binder frame, y the knotter driving shaft, O and 13, Figs. 25 and 26,
the knotter spirals, Q the cord-holder, and R the stationary cord-guide.
S, Figs. 15 and 19, represents the point of the binder-arm, which carries the cord
around the gavel, and presents it to the knotting mechanism. The shaft g is con-
nected with the operative mechanism of the harvester, so that it receives therefrom
a rotary movement of one revolution for cach sheaf bound. The knotter-spirals
and the cord-holder are actuated from the shaft g by the cam T and the segmental
gear U, Figs. 15 and 31.
The shaft g also actuates the binder-arm, as previously described. The rods n, n,
are connected together at their ends by suitable cross-bars, and immediately under
the knotter, by the cross-bar or frame X, Fig. 15, which carries an arm or arms, 9³,
which support a journal for the binder-driving-shaft 13. The cross-bar X also

page_text: The
carries the pivot on which the reciprocating gate or side-compressor Y¹ swings,
as already described. The side-compressor travels in the slot B², Fig. 13.
binder or needle-arm travels in the slot C2, Fig. 13.
The grain is brought to the knotter by the binding-arm from the left-hand as
represented in Fig. 15, the knotter-frame or casing being provided with a pro-
jecting detent or horn which prevents the grain from being forced beyond the
knotter, and which also assists in the compression of the gavel. At the time when
the binder arm is entering the slot in the knotter casing, the cord passes from the
cord-holder around the bundle to the eye of the binder-arm (as indicated in
Fig. 15).
The construction and operation of the knotter-spirals will be understood from the
following description. The knotter-spirals are mounted on an axis or stem R²,
which is fastened in a boss Q on the outer end of the cross-bar or frame of the
knotter, P, which extends across between the rods n n, and affords support for the
various operative parts of the knotter mechanism. As indicated in Fig. 15,
the knotter spirals are preferably inclined downwards towards the incoming grain.
The cord-holder Q is supported on the stud S2 inserted in the cross-bar P, which
is bent or curved upwards so as to sustain the parts in the proper relative positions.
V2 is a bent arm on the cross-bar P2 which carries the boss Q2. The stem R²
extends all the way through the knotter spirals, terminating at its inner end in a
guide of, which assists in the formation of the knot.
The cam-shell U2 is caused to revolve on the stem R³, first in one direction and
then in the other, by the cam T, the vibrating toothed segment d² and the bevel
pinion. The toothed segment is supported on an arm pivoted at, Figs. 14
and 15, to the cross-bar . The arm is provided with a stud or roller, k³,
Fig. 15, which engages with the cam-groove in the cam T, and, as the latter revolves
with the shaft y, it causes the segment d to vibrate and to impart a reciprocating
rotary movement to the pinion and the cam-shell U2. The back of the curved
toothed segment & bears against a shoulder n³, Fig. 14, on the arm V², by which
it is held in mesh with the pinion f³ and is prevented from springing away
therefrom.
An offset extension o³, Figs. 14 and 15, on the arm carries the roller ³. The
segment vibrates on a pivot at formed by the stud p³ passing through a boss³,
on the cross-bar P2. The stud is provided with a washer and split-pin on its outer
end. When the segment is elevated it passes within a curved channel, s
Figs. 15 and 31, on the horn O', which protects it from becoming entangled with
the straw.
The pinion revolves on the stem R². At its inner end it is provided with an
enlarged hub V3, Figs. 25 and 28, (preferably made hollow) to which the cam-
shell U is adjustably secured by means of the screws and me and the
washers and o³. Openings are made through the cam-shell, of sufficient
dimensions to permit the adjustment of the cam-shell U2 on the hub V³, both
lengthways, and by turning it about its axis,-the screws and m passing
through these openings into threaded holes in the hub. The outer surface of
the cam-shell, immediately around the openings is roughened or corrugated,
as represented at p and ', Fig. 25,-the ribs or corrugations extending lengthways
of the cam-shell and the ribs q* circumferentially as shown. The inner surfaces
of the washers and of are provided with similar corrugations, so that as the
washers fit the screws closely, whenever it is desired to adjust the cam-shell on the
hub V3, this may be accomplished by slacking the screws until the washers are free
of the corrugations, in which condition the cam-shell can be moved lengthways or
turned axially, and then firmly secured in the altered position by tightening the
screws, and causing the corrugations on the washers to engage with those on the
cam-shell. The adjustment of the cam-shell enables me to vary the movements of
the knotter-spirals, as hereinafter described.
The knotter spirals 0 P³ are substantially two screw threads mounted on
tubular cores or shanks,-one within the other, the operating part of the spirals

page_text: extending beyond the shanks and lying side by side as seen in Fig. 26. The front
of the spiral P³ is made in hook form, u, Figs. 19 and 26, and in the end or jaw t
of the spiral O is a corresponding groove. The spiral O is attached to the exterior
sleeve or shank X³ and is extended along its surface as a screw thread. The
spiral P³ is attached to the end of the interior shank 73, which extends entirely
through the sleeve-shank X3 and projects beyond for the reception of the spring a,
and collar d, which is fastened rigidly to the shank, and, for the purpose of
retaining the two spirals in their position side by side, the heel of the spiral P³ is
fitted into a notch Fig. 20 in the exterior shank, so that slight movements of the
spirals in relation to each other must be in the direction of the thread of the screw,
and tend to either open or close the jaws. The spring a tends to close the
jaws. Upon the rear end of the knotter shanks are fastened studs carrying friction
rollers adapted to work in the longitudinal slots or tracks w³w in the cam-
shell U, see Figs. 14, 15, 25 and 31.
The spirals are retained in their position on the stem or spindle R², by the
divided nuts, which is made of a form adapted to fit the thread and sustain the
shank of the spiral O, being attached to the cross-bar or knotter-frame P² by
screw, and connected at the opposite ends by the bolt or screw . By the
above described arrangement, the reciprocating rotary motion of the cam-shell U²,
transmitted to the cam-shell by the rack d², gives to the knotter spirals a recipro-
cating screw motion forward and backward through the divided nut 4, s, causing
the jaws at the ends of the spirals to advance and retreat in a path such as would
be occupied by the screw threads, which form the spirals, prolonged. Near the
extremity of the forward movement of the cam-shell the jaws t, u, at the free ends
of the spirals, are opened to receive the cord, by the roller or stud coming in
contact with a suitable stop a on the knotter-frame or on the divided nut, so that
the spiral O is arrested in its movement, while the other spiral, P³, is carried
forward for a short distance, so as to separate the jaws at the extremity of the
spirals. The stud travels entirely out of the slot, w³, in the cam-shell, when it
comes in contact with the stop 21.
As the cam-shell begins its reverse motion and releases the stud, 3, from pressure,
the jaws are closed by the action of the spring, a. During the backward screw
motion of the knotter shanks through the nut, 4, 4, the friction rollers or
studs ³,, travel backward along the tracks,, in the cam-shell. The
knotter jaws are opened to release the cord at the proper time by a slight rotation
of the knotter shanks in relation to each other, caused by the passage of the
roller over the inclined in the track, Fig. 31, while the roller travels
along the straight track w³.
The cord-holder is represented in Figs. 14 15, 16, 17 18 and 24. The cord-
holder is supported on the cross-bar P by the stud S, which is clamped in place
on the bar by the cap 1, Figs. 13 and 14, secured to the bar by bolts or screws.
The stud S is prevented from turning in its support by a pin c, Fig. 16, inserted
in the bar and entering a hole in the stud. X2 is a segmental pinion, which
meshes with the teeth U, Fig. 15 on the cam-dise T, so that the cord-holder makes
a single revolution for each bundle bound. The segmental pinion is provided
with the delay-surface W2, Fig. 17 which bears against the smooth portion of the
periphery of the cam-disc T.
The pinion X is provided with a starting-tooth D2, Fig. 17, which is moved by
the tooth Fig. 15, on the side of the cam-disc. A tooth y at the opposite end
of the teeth U, may be employed to prevent disarrangement in case the binder
should be accidentally turned backwards. The segmental pinion X2 has attached
to it the hub Y, which carries the clamping-plate Z, horn T', and the knife A².
The stud S2 passes through the hub Y, and supports at its inner end the trans-
verse bar E, Figs. 16 and 17 which carries the segmental curved flanges G
and H³ constituting the cord-clamping-jaw and clearer respectively. The clamping-
plate revolves around the clamping-jaw G and the clearer H³. The pinion X
has a curved flange 1 cast on it, and the body J2 of the clamping plate Z2 is
.

page_text: secured to this flange by the screw 4 and spring e, Fig. 18. This spring is
arranged across the hollow or concave inner surface of the flange 1', bearing on its
edges, and the screw, d enters a threaded hole in the spring as indicated in Fig. 18.
Fig. 16 is a screw inserted in the curved plate 12 through a smooth hole in the
body of the clamping-plate, to secure it in proper position without preventing its
yielding outward to grip the cord. Provision is thus made for allowing the
clamping-plate to yield away from the clamping-jaw, when the cord is gripped
between them. The position of the cord between the clamping-plate and the jaw,
is indicated by the dotted lines, ", Fig. 16,—the portion of the cord which extends
to the binder-arm being shown by the full lines m³. The spring bends outwards
slightly, as indicated by the dotted lines in Fig. 18, when the cord is gripped
between the clamping-plate and the jaw. The amount of pressure on the cord is
regulated by the screw . The edge of the clamp-plate is bent over the edge of
the clamping-jaw, forming a flange as represented at f, Fig. 17. The knife A
is mounted on an arm provided with a stem j fitting a hole in the centre of the
stud S. The knife projects into a notch in the flange f in the clamping-plate and
is thus made to revolve with the clamping-plate and severs the cord against the
edge of the clamping-jaw. During their revolution the clamping-plate and knife
pass one on each side of the clearer H³, and the clearer serves to remove any bits
of cord or other refuse from between the clamping-plate and the knife.
At the commencement of the operation of making the knot, the cord, Fig. 19,
is brought in towards the spirals by the binder-arm, as indicated at S.
At the same time the portion of the cord, which is held by the cord-holder at m
is carried along the lower edge K of the stationary cord-guide R, by the grain
passing over the knotter, until the cord occupies the position represented by the
full lines 118 in Fig. 19. The cord at 1, Fig. 19 has now been placed by the
binding arm where the free ends of the spirals will pass under it as they move
forward. The lower side of the end of the stem R³ is recessed as indicated by
the dotted lines n³, Fig. 19, and the cord is received in this recess, the projecting
lip o serving to guide it to the proper position. As the spirals travel forward,
the binder-arm moves backward, so that the next position of the parts is
represented in Fig. 20 where the free ends of the spirals have passed over the end
of the stem R2, and between the cords 15 and 18. The motion of the spirals is now
arrested, while the roller ³ is passing through the concentric portion 7, Fig. 15,
of the cam T, so that at this time no movement is imparted to the vibrating
segment d' While the spirals remain stationary in this position the binding arm
continues its backward movement, and the cord slips along the curved surface p,
Fig. 20, of the rear side of the spiral P³, so that this portion of the cord moves
towards the cord-holder, and, as the binder arm continues to travel backward, the
cord comes behind the stationary cord-guide R, or between it and the cord-holder.
This operation will be understood more clearly from an examination of Fig. 21,
from which it will be seen that the strain on the cord maintained by the backward
movement of the binder-arm, causes the cord to slide along the inclined surface p³
of the spirals, thus virtually changing its direction and bringing it nearer the
cord-holder.
The further backward movement of the binder-arm slides the cord up along the
inside of the cord-guide and brings it successively into the positions represented
in Figs. 21 and 22, in which the cord comes above the stationary clamping-jaw G,
and in position to be engaged by the horn T', and to be acted on by the clamping
plate and the knife. It will be understood that that portion of the cord next the
eye of the binding arm, as it comes into the knotter, passes in front of the cord-
guide R or on the side of it away from the cord-holder, while, as the binder-arm
moves backwards, this portion of the cord passes inside the cord-guide R or
between it and the cord-holder. And this difference, or change in the direction
of the cord, is produced by the sliding of the cord along the inclined surface p³ of
the spiral, under the strain maintained on it as the binder arm moves backward.
The cord-guide R is provided on the side next the knotter with a rib L², Fig. 16,

page_text: '
which rib has a projection at 7, which prevents the cord from being drawn above
it. The cord is thus guided and held within the path of the point T¹ of the
clamping-plate. It will be understood that, in order to accomplish this result of
placing the cord behind the cord-guide, as the binder-arm withdraws, it is not
necessary that the forward movement of the spirals should be arrested, but it is
preferable to do so, as the shifting movement of the cord is thereby better tim.ed
relatively to the other operations. The result could also be effected by slowing
the movement of the spirals.
After the spirals have been arrested in the position approximately represented
by Fig. 20, while the cord is placed behind the cord-guide, they then move
forward into the position represented by Fig. 21, the jaws t u are opened, and
the cord near the holder is carried into the jaws by the motion of the holder, which
now commences to revolve. The jaws now close on the cord, the cord-holder
releases the end of the cord, the spirals begin to retract, pulling the end through
the loop, as represented in Fig. 22, in which the point T of the clamping-plate is
shown as just passing over the cord extending to the binder-arm, and m³ Fig. 22
shows the cut end of the cord, and 15 18 the cord extending around the bundle.
Fig. 23, the formed knot is shown, as stripped from the ends of the knotter
spirals, the end having been just severed by the knife A2, which has completed
its revolution and returned to its position of rest. The cord now extends away
In
to the binder-arm, its end being held at me between the stationary clamping jaw
and the clamping plate, as indicated in Fig. 16, ready for the repetition of the
operations of forming the knot, when another gavel has accumulated in the
receptacle.
The cord-guide R projects downward from any suitable part of the knotter-
casing, in the proper relation with the cord-holder, the knotter spirals and the path
of the binder-arm. In the accompanying drawings, it is shown as attached to or
forming part of a curved guard R³, Figs. 13, 14 and 31, which is attached at one
end to the frame P2 by the lug and screw S3, and at the other end by a lug
through which passes the screw y, Fig. 13, which may also serve to secure the
divided nut. The edge of the casing R³ next the path of the birding arm is
straight, as seen from above, except as the cord-guide R preferably projects
short distance. T2, Fig. 13, is a removable cover, which may be hinged to a lug
at 1, so that it may be readily turned up to afford access to the cord-holder and
knotter.
The horn O', and guard ³, are carried by a plate 2, which is secured at one end
by a bolt, to the lug on the boss Q2, and at the other end is provided with
a tongue to which fits a recess in the end of the plate R³.
On the side of the plane of the path of the binder arm opposite the horn O¹, is
placed a corresponding horn P, Fig. 13, which is carried by the knotter
casing U³, secured at one end to the lug by the bolt, and at the other to the
rod by a clamp and screw »¹. This portion of the casing is given a suitable
form adapted to protect the parts underneath it. The bar which extends along
the path of the binder arm forms a part of the casing Us,-being elevated to
the same level as the plate R³.
A supplementary casing, V³, Fig. 13, covers the driving gear B' and the
starting and stopping mechanism.
A lug, a', Fig. 13, on the bar, we, limits the inward movement of the side-
compressor. A notch, c, Fig. 13, in the plate R³, serves to guide the cord.
The bundle, after being bound, rests on the platform and the casing which
protects the knotter, and is discharged in rear of the machine by the vibrating
discharger J, Fig. 32, which oscillates on the pivot B3, as indicated by the full
and dotted lines in said figure. The discharger-arm is provided with the prongs
or horns which engage under the bundle and lift it from the platform,
delivering it, as the arm vibrates, on the stubble immediately behind the machine,
butt-end down.
The discharger-arm is operated from the binder-shaft g by means of the

page_text: crank E³ and cam F₁, and the connecting mechanism hereinafter described. It
will be observed that, in addition to the vibrating movement in the vertical plane
about the pivot B3, it is necessary to impart to the discharger-arm, an oscillating
movement about its longitudinal axis, in order to enable the prongs or fingers f
to engage under the bundle as it lies on the platform. The vibration in the
vertical plane is imparted to the discharger-arm by the crank E³ on the shaft,
while the oscillation about the axis is produced by the cam F. As represented in
the accompanying drawings, the crank and cam are conveniently formed in one
piece.
The shaft g receives a single complete revolution for each bundle bound and
discharged. The bundle bound at one operation of the binding-mechanism remains
on the knotter casing, until at the commencement of the next binding-operation, it
is discharged by the discharger.
The
On the rear cross-bar, m, of the binder-frame is placed one or more upright posts
which support the pivot 13 of the vibrating discharger-arm. The post is preferably
cast in one piece with the cross-bar, as indicated in the elevation, Fig. 35. At its
upper end it is provided with a suitable journal, in which the pivot B³ turns.
discharger-arm J is sustained by the vibrating support J³, pivoted on the post or
upright I, by the pivot B³, and provided with a rearward extension a', Figs. 32
and 33 to which the connecting-rod K³ is attached by the universal joint ^. The
discharger-arm is journaled in the support J³, so that it can turn about its
longitudinal axis under the influence of the cam F', lever L³, rod M², and crank
arm N. Suitable collars, or other devices, secure the discharger-arm from end-
play. The support J³ may be given any desired shape adapted to the purposes for
which it is designed. The pivot B³ may be either keyed or pinned in the support;
or the support may be arranged to turn on the pivot.
9
On the rear end of the shaft is secured the crank E³, provided with the crank-
pin, on which the collar is secured by any suitable device.
The collar is provided with a perforated lug 6, Fig. 34, to which the lower
end of the connecting-rod K³ is jointed by the pivot This arrangement
constitutes in effect a universal joint between the crank E³ and the connecting-
rod K, which permits the swinging of the connecting-rod as the support J³
vibrates. The other end of the connecting-rod is attached to the arm on the
support J by a joint, which permits movement in planes at right angles with each
other, which joint is formed by the universal connection, having holes in it
arranged at right angles with each other, into one of which a stud or pin on the
connection is fitted, while in the other a pin on the arm as of the support .J³ is
inserted. A universal joint is thus formed between the end of the connecting-
rod K³ and the arm as on the vibrating support of the bundle-discharger, which in
connection with the universal joint at the lower end of the connection, permits the
requisite movements of the parts while the bundle-discharger-arm support J³
oscillates about an axis at right angles with the axis of revolution of the crank E³.
As the crank E³ revolves, the arm J, carrying the fingers, will vibrate about
the pivotal axis B³, as indicated by the full and dotted lines in Fig. 32, so as to
effect the discharge of the bundle. The range of the movement is also indicated in
this figure, as it is only necessary to cause the discharger-arm to swing behind the
vertical plane in which the axis B³ is located to a sufficient degree to insure the
delivery of the bundle in rear of the machine.
Any other preferred form of universal joint may be employed at either end of
the connecting-rod K³.
In order to secure the oscillating movement of the discharger-arm J about its
longitudinal axis, the crank-arm N2, which receives motion from the lever L³ by
means of the connecting-rod M², is applied to it. The lever L3 is pivoted to the
cross-bar m or the standard 13, as shown at O2, Fig. 35, and its lower end is
provided with a stud or roller p, which engages with the cam-groove of the
cam F. The cam F is formed in such position relatively to the crank E and the
cam-groove g is made of such a shape as to impart the requisite rolling movement

page_text: to the discharger arm J, so that the prongs ff will engage under the bundle.
While the arm is raising the bundle from the platform, it rests on the concave sides
of the fingers ff, little or no rolling movement being imparted to the arm J at this
time, as the roller is then in the circular portion of the cam-groove 7. During
the return movement of the arm, however, the cam operates the lever so as to
turn the arm about its longitudinal axis, so as to cause the fingers to engage
under the bundle on the platform. The cam first swings the upper end of the
lever L³ inward, causing the arm to roll on its longitudinal axis by means of the
jointed connection M2 and crank-arm N2, so that the points of the fingers are
directed downward toward the outer edge of the platform and outside of the bundle
thereon. As the arm J continues to descend, a rolling motion in the opposite
direction is imparted to it, so that the fingers pass inward under the bundle in
position, as indicated at ff Fig. 1, to lift the bundle from the platform when the
arm rises. The cam-groove 76 is given a suitable shape adapted to produce the
rolling motion in one direction and then in the other, as represented in Fig. 34.
The connections between the upper end of the lever L³ and the discharger J are
built with universal joints, so as to permit the relative movements of the parts.
The universal-joint connections between the lever L³ and the discharger-arm are
conveniently formed as represented in the accompanying drawings. Thus on the
upper end of the lever L is formed a ball, 7%, on which the connecting rod M² is
jointed by a spherical socket formed partially in the ends of the connection itself,
and partially in the piece attached to the connection by a suitable bolt. At its
other end, the connection M2 is provided with a ball, u, Fig. 34, which fits a
correspondingly shaped socket in the lever N, which is conveniently formed of two
parts, Fig. 34, secured together by the bolt 2, and both being keyed or
otherwise secured on the discharger-arm.
A single key will serve to fasten both parts of the crank-arm to the discharger-
arm. It will be observed that by this construction the connection M2 is provided
with universal joints at each of its ends, thus securing the requisite rolling
movement of the discharger-arm, while permitting the vibration thereof in the
vertical plane to discharge the bundle.
It is obvious that either the mechanism for vibrating the discharger or that for
rolling it may be used independently of the other, or that other mechanism for
effecting either purpose may be substituted, while that herein shown for the other
purpose is retained.
The discharger-arm J is bent or offset, as indicated at P, Fig. 1, so that when
down, as indicated by the dotted lines J Fig. 32, it may clear the knotter-casing
or any projecting part thereon, as 01. The extremity of the upward vibration of
the discharger-arm is represented at J, Fig. 32,-movement to about this position
being sufficient to secure the discharge of the bundle clear of the machine.
Jo, Fig. 32, represents the discharger during its return movement, with the prongs
of the fork directed downward in position to pass outside the bundle so as to be
inserted under it by the turning of the discharger on its axis.
The crank E³ and cam F' are preferably made in one piece, and are fastened to
the shaft in such relation to the crank arm e, which operates the binder-arm
that the discharger operates to lift the bundle from the binding table at the time
when the rocking binder post is near to that end of its motion indicated in Fig. 2,
and the top compressor V has been carried off from above the bound bundle.
Having now particularly described and ascertained the nature of the said inven-
tion, as communicated to me by my foreign correspondent, and in what manner the
same is to be performed, I declare that what I claim is :-
:-
1. The combination of the grain-platform, a throat or passage way leading there-
from, a gaveling chamber located at one side of the terminus of said throat, and a
binding chamber located at the other side, a binder-arm which embraces the grain
in the gaveling chamber, and carries it across the throat and into the binding
chamber, a pivoted positively actuated gate which during the passage of the gavel

page_text: across the throat occupies a position below the path of the gavel, and suitable
mechanism arranged to operate the gate at the proper time relative to the motion
of the binder-arm, substantially as described.
2. The combination of the grain-platform, a throat or passage way leading there-
from, the packing device located at one side of the throat at the end of the platform
and having a fixed relation thereto, the gaveling chamber, located above the packing
device and constructed to permit the movement of the binder-arm in different planes,
and the endwise adjustable binding table and mechanism, located on the side of the
throat opposite the gaveling chamber, and provided with a pivoted positively
actuated gate which during the passage of the binder arm occupies a position below
the path of the gavel, substantially as described.
3. In a low-down grain binder, the combination of the main frame, with the main
driving wheel located at its outer end, the grain platform, a throat or passage way
leading therefrom, the packing device located at the delivery end of the platform,
the gaveling chamber located above the packing device and constructed to permit
the movement of the binder-arm in different planes, the binding table and mechanism
located outside the throat and adjustable lengthways of the grain, a positively
actuated swinging gate which during the movement of the binder-arm occupies a
position below the path of the gavel, and a rear-discharge bundle ejector, consisting
of a vertically vibrating arm pivoted to the rear of the binder frame and adjustable
therewith, substantially as described.
4. The combination of a throat or passage way with gaveling and binding
chambers located on opposite sides of its terminus, a binder-arm which carries the
grain from the gaveling to the binding chamber across the throat, an arm or gate
pivoted below the binding receptacle and operated by suitable mechanism driven
by the binder-shaft in such manner that the gate assists in supporting the gavel as
it crosses the throat, and then rises towards the binding receptacle and with the
binder-arm acts as a compressor, substantially as described.
5. The combination of a throat or passage way with gaveling and binding
chambers located on opposite sides of its terminus, a binder-arm which carries the
grain from the gaveling to the binding chamber, across the throat, a pivoted arm
or gate operated by suitable mechanism driven by the binder shaft, in such manner
that the gate is withdrawn from before the gavel during its passage across the
throat, and then is forced against the gavel on the same side with the binder arm,
and a rear-discharge bundle ejector consisting of a vertically vibrating fork-
carrying-arm pivoted to the rear of the binder frame, substantially as described.
6. The combination with the grain-conveying and binding mechanism of a grain-
binder, of suitable rotary feeding mechanism, provided at the forward end with the
revolving circular plate or disc Parranged to revolve about a horizontal axis, and
opposed to the butts of the grain, substantially as described.
7. The combination of the conveyor belt of a sheaf-binding harvester, and the
throat or passage way at one end thereof, extending inward and upward, open at its
rear end and closed or partially closed at its forward end by the rotating butt-disc
and located between the rotary feeders having projecting feeder teeth and the
spring guards opposite the feeder teeth, the clearance roller at the end of the
conveyor belt and the clearer bars Z Z, substantially as described.
8. The combination, with the grain-conveying and binding mechanism of a grain-
binder of the continuously revolving feeder provided with projecting feeder teeth,
the clearer-bars extending across the path of the teeth, and the revolving plate or
disc arranged to revolve on a horizontal axis and opposed to the butts of the grain,
substantially as described.
9. The combination with the grain-conveying and binding mechanism of a grain-
binder, of the continuously revolving feeders provided with projecting feeder
teeth, the spring guards placed opposite the feeders, and the rotating disc, opposed
to the butts of the grain, substantially as described.
10. The combination, with the grain-conveying and binding mechanism of a
grain-binder, of the continuously revolving feeders, provided with projecting

page_text: feeding teeth, the clearer bars extending outwards and upwards across the path of
the teeth, the spring guards placed opposite the feeders and bars, and the revolving
dise, opposed to the butts of the grain, substantially as described.
11. The combination with the grain-conveying and binding mechanism of a
grain-binder, of the continuously revolving feeders, the rotating disc, opposed to
the butts of the grain, and the cylindrical drum, of smaller diameter than the
disc, and extending from the disc to the next adjacent feeder, substantially as
described.
12. The combination, with the grain-conveying and binding mechanism of a
grain-binder, of the continuously revolving feeders, the board constituting the
forward end of the gaveling chamber and the revolving butt-disc opposed to the
butts of the grain, and arranged. to revolve in a plane parallel with the plane of
the end board, substantially as described.
13. The combination with the grain-conveying and binding mechanism of a
grain-binder, of the continuously revolving feeders, the spring guards placed
opposite the feeders, the grooved clearance roller and the rotating butt disc,
opposed to the butts of the grain, substantially as described.
14. The combination, with the grain conveying and binding mechanism of a
grain-binder, of the continuously revolving feeders, provided with feeding teeth,
the clearer bars extending across the path of the teeth, the rotating disc opposed
to the butts of the grain and the rearwardly curved bracket arranged to support
the rear end of the feeding mechanism, substantially as described.
15. The combination, in the feeding mechanism of a grain-binder, with the front
row of feeder teeth of a rotary feeder, of the grain guide or guard opposite the
first row of feeder teeth operating to keep the straw in contact with the teeth, and
the disc revolving with the feeder teeth and forming revolving end-plate for the
feeder mechanism, adapted to carry forward the butts of the grain, substantially
as described.
a
16. The combination, with the travelling and vibrating binder arm, of the
compressor which forms the top of the binding chamber, a suitable binding table
which forms the bottom of the binding chamber, the horn which forms one side of
the binding chamber, and a vibrating gate which forms the other side of the
binding chamber, substantially as described.
17. The combination, of the binder-post rocked by suitable mechanism, the
compressor pivoted on the post so as to rock on its pivot within fixed limits, and
adapted to operate as a cover for the measuring receptacle when the post is at onc
extreme of its oscillation and as the cover of the binding chamber when the post is
at the opposite extreme of its oscillation, substantially as described.
18. In a grain-binder of that type in which the gavel is bound between the
grain platform and the master wheel, the combination of the rocking binder-post,
a compressor pivoted on the post so as to rock on its pivot within fixed limits; and
adapted to operate as a cover for the binding chamber when the post is at onc
extreme and to slide off the bundle when the post is rocked towards the other
extreme of its oscillation, a rear-discharge bundle ejector adapted to lift the bundle
upward out of the binding chamber when the cover is removed, and suitable
connecting and driving mechanism whereby the post and the discharger are operated
in proper time relatively to each other, substantially as described.
19. In the binding chamber of a grain-binder, the combination of the knotter
casing forming the bottom of the chamber, the compressor gate forming the side of
the chamber next the binder arm, the horn formning the opposite side, and the
compressor cover carried on the rocking post and arranged to slide off the bundle
to allow of its being lifted by the discharger, substantially as described..
20. The combination, with the grain-conveyor of a grain-binder of the adjustable
revolving feeder F' located at the delivery end of the conveyor, and operating to
feed the grain upward through a throat or passageway, the grain receptacle on the
inner side of the throat and the binding chamber on the outer side, adjustable
binding mechanism provided with the vibrating and travelling binding-arm adapted

page_text: to carry the grain across the throat from the grain receptacle to the binding
chamber, and suitable connecting mechanism whereby the simultaneous adjustment
of the feeder and the binding mechanism is secured, substantially as described.
21. The combination, with the grain-conveyor of a grain-binder of a compound
revolving grain feeding mechanism, consisting of an adjustable feeder F' and a
non-adjustable feeder F, located at the delivery end of the conveyor, and operating
to feed the grain upward through throat or passageway, the grain-receptacle on
the inner side of the throat and the binding chamber on the outer side, adjustable
binding mechanism provided with a binding arm adapted to carry the grain across
the throat from the grain-receptacle to the binding chainber, and suitable connecting
mechanism, whereby the simultaneous adjustment of the adjustable feeder and the
binding mechanist is secured, substantially as described.
22. The combination, with the grain-conveyor of a grain-binder, of the
adjustable revolving feeder F', located at the delivery end of the conveyor and
operating to feed the grain upward through a throat or passageway, the grain
receptacle on the inner side of the throat and the binding chamber on the other
side, adjustable binding mechanism provided with a binding-arm adapted to carry
the grain across the throat from the grain receptacle to the binding chamber, the
connecting arm w, and rod ', substantially as described.
23. The combination, with the grain-delivery-throat of a grain-binder of the
continuously revolving feeder F, provided with feeding teeth e e e e projecting
into the throat, having acting edges inclined backwards at different inclinations,
substantially as described.
24 The combination, with the grain-delivery throat, of a continuously revolving
feeding mechanism, provided with feeding teeth having acting edges inclined
backwards, and a binding-arm arranged to pass through the stream of grain at the
time it is being advanced by a feeding tooth of the greatest inclination, substantially
as described.
25. The combination, with the grain-delivery-throat of a grain binder, of a
continuously revolving grain feeding mechanism consisting of a series of two or
more feeders FF, provided with feeding teeth of different inclination, one of the
said feeders being adjustable while the other is non-adjustable, substantially as.
described.
26. The combination, with the grain-delivery-throat of a grain binder, of an
adjustable binding mechanism adapted to receive the grain from the throat, and a
continuously revolving grain feeding mechanism, consisting of a series of two or
more feeders provided with feeding teeth of different inclination, one of said feeders
being adjustable lengthways simultaneously with the binding mechanism, while the
other is non-adjustable, substantially as described.
27. The combination, with the grain-delivery throat of a grain-binder, of suitable
adjustable binding mechanism and continuously revolving grain-feeding mechanism,
consisting of a series of two or more feeders F¹, mounted on the same axis, one
of which is adjustable lengthways of the axis simultaneously with the binding
mechanism, while the other or others are non-adjustable, and the adjustable clearer-
bar 7, substantially as described.
28. The combination, with the grain-delivery throat of a grain-binder, of
suitable adjustable binding mechanism, and a continuously revolving grain-feeding
mechanism, consisting of a series of two or more feeders F F', one of which is
adjustable lengthways of the axis simultaneously with the binding mechanism, while
the other or others are non-adjustable, and the spring finger or fingers a' located on
the opposite side of the throat and opposite the non-adjustable feeder, or feeders,
substantially as described.
29. The combination, with the grain-delivery throat of a grain-binder, of suitable
adjustable binding mechanism, the grain receptacle L, the continuously revolving
feeding mechanism consisting of a series of two or more feeders F F, mounted on
the same axis, one of which is adjustable lengthways of the axis simultaneously

page_text: with the binding mechanism, while the other or others are non-adjustable, and the
clearer bar or bars Z, substantially as described.
30. The combination, with the non-adjustable revolving grain-feeder F, of the
adjustable revolving feeder F, and drum Y, substantially as described.
31. The combination, with the non-adjustable revolving grain feeder I, of the
adjustable revolving feeder F¹, drum Y and tie rods = 2, substantially as
described.
32. The combination, of the revolving adjustable grain-feeder F, the non-
adjustable feeder or feeders F, the drum Y and revolving butt disc ", substantially
as described.
33. The combination; in the rotary feeding mechanism of a grain-binder, of the
revolving slotted drum constructed of the staves and the heads at the end of the
drum, the toothed ring secured to the drum, the adjustable feeder, arranged to
slide thereon and provided with one or radial arms passing through the slot or
slots in the drum, and the central rod for adjusting the feeder, substantially as
described.
34. The combination, in the rotary feeding mechanism of a grain-binder, of the
revolving slotted drum, constructed of the notched staves and the heads at the ends
of the drum, the toothed rings provided with internal lugs fitting the notches in the
staves, the adjustable feeder having one or more radial arms passing through the
slot or slots in the drum, and the central rod for adjusting the feeder, substantially
as described.
35. The combination, in a rotary feeding mechanism of a grain-binder, of the
staves and heads forming the drum, the toothed rings secured to the drum, and the
adjustable feeder arranged to slide thereon, substantially as described.
36. The combination, with the overhung swinging binder post H, of the binder-
arm G, shaft t, crank-arm 7, connection k, link-lever hi, and revolving crank e,
substantially as described.
37. The combination, with the adjustable binding mechanism provided with the
travelling and vibrating binder-arm G, arranged to carry the grain from the grain-
receptacle to the binding-chamber, of the vibrating side compressor Y, and the
adjustable feeder F, substantially as described.
38. The combination, with the adjustable binding mechanism, provided with the
travelling and vibrating binder-arm G, arranged to carry the grain from the grain-
receptacle to the binding-chamber, of the vibrating side-compressor Y, the upper
compressor V, and the adjustable feeder F, substantially as described.
39. The combination, with the adjustable binder frame mn, supporting a binding
mechanism comprising the overhung swinging binder-arm-post H carrying the
binder-arm G, adapted to carry the grain from the grain receptacle to the binding
chamber, of a continuously revolving grain-feeding mechanism containing one or
more non-adjustable feeders and an adjustable feeder connected with the binding
mechanism by the axially arranged rod and arın.w, substantially as described.
Dated this Fifth day of December 1890.
JAMES RALPH SEVERANCE,
W. P. Thompson & Boult.