Improvements in and connected with the Justification of Type, Type Dies, or Type Matrices.
Year: 1897

page_text: Date of Application, 25th May, 1897
Complete Specification Left. 25th Feb., 1898-Accepted, 25th May, 1898
Date of Application, 25th May, 1897
Complete Specification Left. 25th Feb., 1898-Accepted, 25th May, 1898
[Communicated from abroad by THE THORNE TYPE-SETTING MACHINE COMPANY, of
No. 34 Park Row, New York, a Corporation duly organised under the laws of
the State of New Jersey, United States of America.]
Improvements in and connected with the Justification of Type, Type
Dies, or Type Matrices.
I, WILLIAM HENRY LOCK, of No. 188, Fleet Street, in the City of London,
Manager and Secretary of the Linotype Company, Limited, do hereby declare the
nature of this invention to be as follows:-
This invention relates to improved mechanism for justifying type or type
matrices into lines of uniform length, so as to adapt them to be made up into
columns of the desired width.
The machine herein described is our most approved embodiment of this inven-
tion in its application to the justifying of separate type, and it is herein shown
and described as being adapted more particularly for use in connection with that
class of type-setting machines which set the type in a single continuous
line. In the operation of composing this continuous line, it is necessary
as a preliminary to our present method of justification, that the type-
setting machine shall contain in its channels, two different kinds of special
separators, one of which is to be inserted between the words which are to form a
line, and the other of which is to be inserted at each point where the continuous
line is to be separated for the purpose of arranging the short lines thus obtained
into column form. These special separators may be arranged, each kind in its
own particular channel, and may be released therefrom and assembled in proper
relation to the character type by means of special keys to be touched at the
proper time by the operator, the key for the word separator being touched at the end
of each word, excepting only those words which are to come at the end of the
column lines. After each of these final words, one of the line separators may
be inserted, the operator being governed in the determination of the location of
these final words of the intended line, by means of any suitable indicator or scale.
Various forms of these separators may be employed for thus temporarily pre-
serving the separations between the words until they are replaced by the final
justifying spacers; and for indicating the points in the continuous line where it
is to be separated to form column lines.
The special separators herein employed, differ from each other in the particular
that the line separator is slightly longer than the word separator, and both are
slightly longer than the character type with which they are employed
It is considered desirable to preface the description of the accompanying figures,
and the detailed description of the machine, by a brief explanation of the method
or system upon which the devices operate.
The continuous line of type is fed into the machine of the present invention,

page_text: 33
through a type channel which retains the type in line, allowing the two kinds of
separators to project from the edges thereof, the ends of the line separators pro-
jecting slightly beyond the ends of the word separators. What is termed the
line grab," lifts the leading line from the advancing continuous line by means of
the projecting ends of the line separator, which underlies the line to be separated.
That line is carried by the line grab up into what is termed the "measuring zone,"
passing, on the way, between two star wheels, the teeth of which are so disposed
as to be engaged by the projecting ends of the separators as the line is moved
past. Those separators thus operate as a rack to turn the star wheels to an
extent determined by the number of separators in the line. Arriving in the
'measuring zone," the leading end of the line is carried against the proper step
of the stepped jaw of the measuring device. The line is thus held against this
stepped jaw while a pawl attached to the measuring lever is brought against the
opposite or lower end thereof. That lever is suspended upon a fulcrum which is
capable of being moved so as to vary the effect of its measurement of the line in
accordance with the number of spaces contained therein. That end of the lever
which is on the other side of the fulcrum from its measuring pawl end is connected
by means of a secondary lever to the spacer selecting devices.
66
The justifying spacers are of four different sizes and are contained in four
channels arranged adjacent to the spacer selecting devices above mentioned, which,
governed by the amount of movement communicated to them from the measuring
lever, operate to select from the justifying spacer channels the proper sizes and
combinations of spacers required to justify the line being operated upon. The
spacer or combination of spacers required to justify one of the spaces of the line
are ejected from their channels into a raceway, and are assembled at a point
therein called the injecting plane, located immediately above the measuring zone.
After the line is released from engagement with the measuring devices, each word
is carried forward by means of a word grab which engages with its underlying
word separator. The word grab lifts each word separator high enough to carry
the character type composing the word lying above that separator into the galley,
where the character type are retained, the word separator itself being allowed to
drop back with the returning motion of the word grab as far as the plane in which
its corresponding justifying spacer or combination of spacers is located. This
plane is called the injecting plane because of the fact that justifying spacers are
here injected into the line at one side thereof, the corresponding word separator
being ejected therefrom into its proper channel on the other side of the line.
The word grab, the spacer selecting and assembling devices, and the word spacer
ejector repeat their operation for each one of the spaces in the line to be filled, the
number of times these operations have to be repeated being predetermined by
governor devices operated upon by the star wheels above described as having
been actuated by the projecting ends of the separators in the line as it is moved up
to the measuring zone by means of the line grab. The movement thus imparted to
these star wheels also operates through the one of them to determine the point
to which the movable fulcrum of the measuring lever is to be moved, and operates
through the other star wheel to determine which step of the stepped jaw shall be
employed for that particular line, it being, of course, understood that the position
of the fulcrum and the height of the jaw to be used is related to and dependent
upon the number of spaces contained in the line to be measured at that particular
setting.
Having thus briefly outlined the general method upon which the machine
operates, a description will now be given of the drawings.
Figure 1, Sheet 1, represents a general front elevation of the right hand end
of the machine, which is therein shown to be in the position occupied by it after a
line has been carried by the line grab into the measuring zone.
Figure 2, Sheet 2, is also a front elevation showing that portion of the machine
which lies at the left of the portion shown in Figure 1, it being deemed advisable

page_text: )
to thus extend this view over two sheets in order to draw it on a scale large enough
to be readable. The line on which these views should be joined is indicated on
each of these figures by the letters z―z.
Figure 3, Sheet 3, is a general end elevation of the machine, looking from the
right hand side of Figure 1.
Figure 4, Sheet 4, is also a general end elevation, looking from the left hand
side of Figure 2, some of the wheels being partially broken away to enable the
mechanism behind them to appear more clearly.
Figure 5, Sheet 5, is a plan view in section taken on the line 5-5 of Figure 1.
Figure 6, Sheet 6, is a plan view'in section taken on the line 6-6 of Figure 2,
that line being an extension of the line 5-5 of Figure 1.
Figure 7, Sheet 2, is a plan view of that portion of the mechanism shown in
Figure 2, to which it is immediately adjacent, and from which its lines are
projected.
Figure 8, Sheet 7, is a front elevation partly in section in places where the
mechanism therein contained may thus more clearly be shown. This view corre-
sponds to what is shown at the right hand side of Figure 1, excepting as regards
the sectional parts, as above noted, and is drawn to a scale twice the size of that
employed in Figure 1.
Figure 9, Sheet 8, is an end view partly in section taken on the line 9-9 of
Figure 8.
1
Figure 10, Sheet 9, is a plan view in section taken on the line 10-10 of
Figures 8 and 22.
Figure 11, Sheet 9, is a plan view in section taken on the line 11-11 of
Figure 8, which is herein referred to as the datum line of the measuring zone.
The word grab is shown in this view, being supposed to be at the bottom of its
stroke, although its proper position in Figure 8 is about half way of its stroke.
Figure 12, Sheet 9, is a plan view in secțion taken on the line 12-12 of
Figure 8.
Figure 13,. Sheet 9, is an end elevation projected from Figure 11, of the
parts shown in the latter figure.
Figure 14, Sheet 10, is a front elevation, and
Figure 15 a plan view, drawn to enlarged scale, of the devices for determining
the position of the moveable fulcrum, and for moving the latter to that position,
these devices being herein shown at the end of their stroke, opposite to that at
which they are shown in Figures 1 and 2.
Figure 16, Sheet 11, is a side view of what is shown in Figure 14, looking from
the left hand side of the latter figure.
Figure 17, Sheet 11, is a similar view, excepting that it is taken in section
on the line 17-17 of Figure 14.
Figure 18, Sheet 12, is a front view, and
Figure 19 is an end view looking from the left hand side of Figure 18, of
that part of the machine which is most intimately concerned in the selection of
the proper justifying spacers.
Figure 20, Sheet 13, is a rear view partly in section taken on the line 20--20
of Figure 21; and
Figure 21 is an end view in section taken on the line 21-21 of Figures 18, 20
and 22.
Figure 22, Sheet 14, is a plan view of the mechanism shown in the four preced-
ing figures portions of the frame work being broken away as shown in section,
to enable the more important mechanism to be clearly seen.
Figure 23, Sheet 15, is an elevation taken from the rearward side of the
machine, of portions of the mechanism employed in the selecting, ejecting and
assembling of the basic justifying spacers A.
Figures 24, 25, 26 and 27 of Sheet 16 show some of the details in enlarged scale
of devices connected with the justifying spacer selecting mechanism, and more

page_text: especially that particular part thereof which is hereinafter referred to as the
correcting device.
Figures 28, 29, 30 and 31 of Sheet 17 are front views of the devices for ejecting
and assembling what are hereinafter termed the basic spacers of this system,
the parts being shown in these views in four different positions during their
operation.
Figure 32, Sheet 18, is a diagram representing a flat development of the
circumference of what are herein after designated as the fulcrum setting quills.
The open or extended position of the quills, in which they are shown in Figure 1,
is herein represented by full lines, while the closed position, in which they are
shown in Figures 14 and 15, is represented by dotted lines.
Figure 33, Sheet 18, is a longitudinal section taken through the centre of the
quills, showing their relation to each other and to the shaft, on which they are
adapted to slide.
Figure 34, Sheet 19, is an end elevation, partly in section taken on the
line 34 34 of Figures 2 and 6, looking toward the left, showing the governor
mechanism for controlling the number of times the word mechanism must repeat
its operation in order to justify all of the spaces in a given line.
Figure 35, Sheet 19, is a front view of some of the details of the governor
mechanism in section taken on the line 35-35 of Figure 34.
Figure 36, Sheet 19, is a similar view of other of those details in section
taken on the line 36-36 of Figure 34.
Figure 36, Sheet 19, is an end projection from Figure 36.
Figure 37, Sheet 20, is a front view in section taken on the line 37-37 of
Figure 6.
Figure 38, Sheet 20, is a plan view in section taken on the line 38-38 of
Figure 37.
Figure 39, Sheet 20, is an edge view in vertical section taken through the
centre of the governor shaft in Figure 40, looking toward the right in that
figure, and
Figure 40, Sheet 20, is a front view of details of the governor mechanism in
section taken on the line 40-40 of Figure 6.
Figure 41, Sheet 20, is a plan view of other details of the governor mechanism.
Figure 42, Sheet 20, is a vertical section taken through the centres of
Figure 40, looking toward the left in that figure.
Figure 43, Sheet 19, is a table representing the system of spacer combinations,
the first vertical column thereof being a representation of the progressive com-
binations of type; the second vertical column being descriptive of the combination
in terms of the four lettered sizes of spacers, while the third column expresses
the size of each space combination in fractional parts of the em of the font
employed.
Figures 44, 45 and 46, Sheet 21, are diagrammatic front elevations representing
the devices employed in the measurement of the lines under three different con-
ditions. In Figure 44 the parts are shown in their inoperative position. In
Figure 45 they are shown in engagement with a line of type having but a single
space to be justified, and in Figure 46 the parts are shown in the position occupied
by them while measuring a line having ten spaces to be justified.
Figure 47, Sheet 18, is an end elevation in section taken on the line 47-47 of
Figure 6, looking toward the right hand in that figure.
Figures 48, 49 and 50, Sheet 22, are views representing devices for pushing
the justifying line into the receiving galley, Figures 48 and 49 being plan views
of those devices shown in their two extreme positions respectively, while Figure 50
is a front elevation of the same parts on the extreme opposite position to that in
which they are represented in Figure 1.
Figure 51, Sheet 18, is a rear view of what is shown in Figure 47, showing the
position and relation of the steps of the governor cam.

page_text: Figure 52, Sheet 2, is a fragmentary plan view showing in detail the
construction and arrangement of the clutch X³.
Figure 53, Sheet 3, is a fragmentary rear view projected from Figure 3, and
showing in detail the arrangement of portions of the mechanism of that figure.
Figure 54, Sheet 9, is an isometric view of a fragmentary portion of the
type channel, showing a word separator and a line separator in connection with
some character type.
In the organization of this machine the inter-relation of the parts is such that
it is difficult to give a strictly consecutive description thereof in the order in
which the several operations are performed, for in the description of one group of
the mechanism it often happens that reference must be made to other groups not
then yet described, in which case the reader is referred to the paragraph descriptive
of that group. The division and subdivision herein assumed of this machine into
separate groups or sections is to a large extent arbitrary, since many of the
combinations set forth and claimed are comprised in more than one group of
mechanism, as these groups are herein divided.
The machine will therefore be herein considered under three general divisions,
the first of which for convenience we will term the line mechanism, it being
understood to comprise all of those parts which are principally concerned in the
manipulation of the lines, as such, and most or all of which, perform their com-
plete function once for each line justified. The second general division of the
machine is designated as the word mechanism, comprising those devices principally
concerned in the manipulation of the words, and the spacers which are to go
between those words. Most or all of these devices perform their complete function
or cycle of movement once for each space between the words contained in the line
justified. The third general division of the machine comprises the governing and
actuating mechanism, most of which is located below the lines 5-5 and 6-6 of
Figures 1 and 2.
The first two of these general divisions are herein considered as being further
sub-divided into sections or combinations of mechanism, the grouping being
made with reference to the particular function or functions performed by
cach, and the name herein given to each group or section being, as far as possible,
suggestive of its function. It will of course be understood that each of these
sections, in addition to performing its own particular function, also performs
its share of other functions common to two or more sections. The following
description will take up these sections as far as possible in their natural and
logical sequence, each under its own heading.
The general division designated as the line mechanism is divided into the
following sections:-
Line grab mechanism,
Measuring mechanism,
Fulcrum adjusting mechanism,
Stepped jaw adjusting mechanism,
Galley mechanism.
That division of the machine comprehended under the general designation of
word mechanism is sub-divided into the following named sections:
-
.
Word grab mechanism,
Spacer selecting and ejecting mechanism,
Selector correcting mechanism,
Spacer assembling mechanism

page_text: "
is to be employed. In connection with the above mentioned division of the
devices of this machine into three general sections, it may here be noted that
those devices contained in the line mechanism are nearly, if not quite, all con-
nected with, and receive their motion from, the shaft X, which is therefore
designated by us the line shaft, while those devices included in the general
division called the word mechanism receive their motion from the word shaft Y.
Following the above order, we will first describe the line grab mechanism.
This is shown in Figures 1, 3, 5, 8, 9 and 12. Its function is to detach
the leading line of type from the oncoming continuous line advancing from the
type composing machine, and carry it forward into what is termed by us the
measuring zone of the machine, which is that portion located above the datum
line 11-11 of Figure 8, and between the stepped and the movable jaws of the
measuring devices. The line grab consists of two principal combinations of parts,
the line separating device and the carrier. The separating device consists of a
slide E, which is loosely fitted upon the rods e, e, attached at their ends to the
frame work W of the machine. This separator slide has pivoted upon it at E'
and E2 respectively, the stop arms E3 and E. Upon the same pivots are also
loosely mounted the fingers E5 and E6. These arms and fingers are arranged in
pairs upon the opposite edges of the type channel V, the extreme upper ends of
each pair being located adjacent to each other, and just within the paths traversed
by the respective ends of the special line separators T; lying, however, outside of
the paths of travel of the word separators U. The normal positions of these pairs
of stop arms and fingers with relation to the type channel V is best delineated
in Figure 9, wherein they are shown to be in engagement with the ends of one
of the special line separators T. The extent of oscillatory movement of the stop
arms E and E is regulated by means of pins which extend therefrom into the
grooves E7 and Es, best seen in Figure 9, the fingers E³ and E being therein
shown in their innermost position, toward which they are urged by their respective
springs E and E10 respectively. These separating devices attached to the slide E
are moved upward by means of the advancing line of type until disengaged there-
from on arriving at the upper end of their permitted movement, at which point
the grooves E and E8 curve outward, and open the arms E3 and E. At the
same time the cranked outer ends of the stop fingers E and E6 are brought in
contact with the pins E and E12, by means of which those fingers are also moved
outside of the path of the line separators, and at the same time are moved out
of engagement with the carrier, which will next be described.
The carrier slide F is loosely fitted upon the rods ff, and is connected by
means of the link F¹, arm F2, shaft 13, and connecting rod F, to the crank F³,
by means of which the carrier slide F is caused to reciprocate vertically upon the
rods ff from its extreme upward position, shown in Figure 3, to the lower end
of those rods as they appear in that figure. Upon the slide F is pivotted the
lifting pawl F7, which is bifurcated to enable it to pass by the measuring pawl G³.
That lifting pawl is urged by the spring F8 against a stop, to the position shown
in Figure 8, so as to enable its engaging end to pass under the line separator T,
when that separator is lifted from the rest of the continuous line by means of the
separating devices E. The inclined projections F9 and F10 of the slide F are
adapted to engage with the projections E3, E14 of the stop fingers E5 and E,
as shown in Figures 8 and 9, the engaging surfaces of the projections F and F10
describing an arc struck from the centres of the pivots of their respective stop
fingers E, E when in the position shown in Figure 9, or those surfaces may be
made normal to those pivots, the object being to enable the projections F9 and F10
to engage with the projections E13, E14, of the fingers E, E respectively, and
thereby lift up the line separating devices, which, in turn, engaging with the
ends of the line separator T, lifts that separator so as to allow the carrier pawl F7
to engage beneath it. Having thus obtained positive engagement with the
separated line of type, the carrier slide F is moved upward by means of its crank,
being freed from the separating device when the latter reaches the upper limit of

page_text: its stroke, as set forth in the above description of that device. Thus released from
the separated line which is being moved up by the carrier, the separating device
drops by gravity, aided, if necessary, by a light spring, until the engaging ends
of the stop arms, E³, E' collide with the ends of the next advancing line separator T,
by means of which the separating device is again moved upward until upon the
returning stroke of the line carrier, it is again engaged thereby. As before stated,
the function of the line carrier or grab is to carry the line of type thus separated
from the advancing continuous line up into the "measuring zone" to a point
where the underside of the line may be engaged by the measuring pawl G³, as
shown in Figure 8.
The Measuring Mechanism:-A comprehension of the general principles upon
which this mechanism operates may best be gained by reference to the diagrams
shown in Figures 44, 45 and 46. The details of its construction are more clearly
shown in Figures 1, 2, 8, 11, 12, 14, 16 and 17. The principal member thereof
is the measuring beam G, which is attached by means of the pivot G¹ to the
slide G³, fitted to slide vertically on the rods gg, which are attached at their ends
to the frame work W of the machine, and the slide is provided with an extension
adjacent to the type channel upon which is pivoted the measuring pawl G³, best
seen in Figure 8. That pawl is normally pressed by the spring G toward the
position shown in that figure, so as to cause the pawl to enter beneath the line of
type when the latter has been lifted up to its position by the line grab.
Into the lower end of the slide G2 is fitted the telescoping yoke G5, which by
means of the spring G6 is normally pressed outward to the fullest extent against
a stop pin, as shown in Figure 8. This yoke G5 is also guided by means of
projections thereof engaging the rod G', and it is provided with a cam pin G³,
adapted to engage with the cam Go, fixed upon the line shaft X. The cam G³
is so formed as to move the yoke G5 upward to an extent equal to the greatest
deficiency that can occur in any of the lines of type to be measured, and the
yoke is therefore necessarily moved upward to that extent for every line at each
of the intermittent rotations of the shaft X. The clastic nature of the connection
between the slide G2 and its yoke is for the purpose of permitting the cam G⁹
to complete its stroke after the upward movement of the measuring slide has been
stopped by the line of type being measured, the mechanism being thus adapted
to accommodate itself to the variations which occur in the lines.
The measuring beam G, which is connected by means of the pivot pin G¹,
to the slide G2, is an extended member, of the form shown in cross section in
Figure 17, having a T-slot extending along and opening out of its front surface.
A corresponding T-shaped block Go is fitted in the slot and is capable of being
moved the entire length thereof. The block G10 is also provided with a cylindrical
extension which has a bearing in the fulcrum block G, being secured thereto
by means of a nut and washer, as shown in Figures 16 and 17, forming a closely
fitting pivotal connection between that block and the measuring beam G. The
fulcrum block G is fitted to slide in ways of the frame W of the machine, so
as to enable the pivot of the measuring beam to be moved to its several required
positions by means of the fulcrum adjusting mechanism to be hereinafter
described.
The extreme left hand end of the beam G, as seen in Figures 14 and 15, is
bifurcated in order to receive a T-shaped block G¹, similar to that of G13, except-
ing that it is faced in the opposite direction, and has its cylindrical portion
journalled in the rectangular part of the rod G¹³, which is fitted at its ends to slide
in the frame W. Beyond the guide rod G¹³ the cylindrical portion of the block G
is provided with a roller G, held in place by means of a washer and split pin,
as shown in Figure 16. Upon the frame work W at G, is pivotted the secondary
beam or lever G16, the shorter end of which is adapted to engage with the roller G4,
by means of which the movements of the beam G are communicated to the
secondary lever. That lever is connected at its longer end to the selector setting

page_text: racks G and G18, the arrangement and function of which will be described in
connection with the spacer selecting mechanism, it being understood that the
upward movements of the right hand end of the measuring beam during the
measuring operation from the position shown in Figure 44 to those shown in
Figures 45 and 46, produce a related upward movement of the selector setting
racks G17 and G18.
The relation of the movement of the racks to that of the measuring pawl end
of the beam G, as that relation is varied by the position of the fulcrum block G",
will best be seen by the diagrammatic views comprised in Figures 44, 45, and 46,
and in this connection it is deemed desirable to give a more extended explanation
of the system of measurement herein employed by us, that explanation being an
almost necessary preface to the descriptions of the fulcrum adjusting mechanism
and the stepped jaw adjusting mechanism, which are logically next in order.
For the purpose of determining the size of the spacer or combination of spacers
to be inserted in the spaces which occur between the words of a line, it is necessary
first to ascertain the net deficiency of the line to be justified, or in other words, to
ascertain what aggregate thickness of spacer type must be added to the character type
contained in that line to fill it out to the desired width, and secondly to divide
that aggregate thickness into the number of spaces which occur in the line, in
order that the spacers representing the size determined by this division shall,
when all are inserted in their respective spaces, exactly fill out or justify the line.
The first requirement is to eliminate from the problem the measurement of
the special separators U and T which, as above described, have been inserted
in the line in the operation of composing for the purpose of locating the divisions
between the words and the lines respectively. As a means of effecting this
elimination, one of the jaws of the measuring device is formed with a series of
steps on its type-engaging face, the height of each of these steps being exactly
equal to the thickness of one of the special separators employed. In the diagrams
represented in the last named figures of the drawings, the lines i indicate that
step of the jaw I which should be employed if there were no separators to be
eliminated from the measurement. In Figure 45 the devices are shown in engage-
ment with a line of two words, containing, therefore, a single word separator U,
and at the bottom the inevitable line separator T, therefore requiring for the
correct elimination of the thickness represented by those separators, the employ-
ment of the second step of the jaw I above that step indicated by the line ii.
This diagram illustrates the minimum requirement of the machine, inasmuch as
it is always necessary to have at least one space between the words for the purpose
of justification, and when a single word occurs in the line, as, for instance, at
the end of a paragraph, it is necessary to fill out the line with slugs, between which
it is advisable to insert a number of word separators so as to allow greater range
in the subsequent operation of justifying. An illustration of the opposite or
maximum capacity of the machine, as herein organized, is represented in
Figure 46, wherein the devices are shown in engagement with a line containing
ten words, and having therefore nine word separators at the bottom, and the usual
line separator. In order to eliminate the measurement of these ten separators
from the line, the jaw I is drawn toward the left so as to allow the line of type
to engage with the tenth step above the plane ii, thus eliminating from the
measurement of that line the space represented by the thickness of the ten
separators contained therein, and allowing of a movement of the measuring beam G
exactly equal to that which it would have in measuring a line composed only of the
character type contained in the line.
The mechanism by means of which the jaw I is moved to its correct position
for each line to be measured will be described under the heading of the stepped
jaw adjusting mechanism.
Having thus provided for the elimination from the measured line of all except-
ing the character type therein contained, it is necessary to divide the net deficiency

page_text: thus determined into the number represented by the space between the words.
The normal position of the measuring beam G is horizontal, as shown in Figure 44,
and in that position the engaging surface of its measuring pawl G3 stands
coincident with the datum line 11-11 at a distance from the plane ii of the
stepped jaw I equal to the full column width, or in other words, to the desired
length of the justified line. It will, therefore, be seen that the extent of upward
movement of the measuring end of the beam from the horizontal or datum line
position shown in Figure 44, will be exactly equal to the deficiency of the line,
representing, therefore, the aggregate set-wise measurement of the spacers required
to fully justify the line.
For greater convenience and definiteness we have herein shown the limit of
justifying capacity of this machine to be equal to a printer's em at each space
between words, as shown in Figure 43. There is, however, nothing in the nature
of the machine to limit it to this capacity, it being capable of extension to any
amount required in practice. In Figures 45 and 46 this assumed maximum of
one-em deficiency is supposed to exist in each of the spaces between words therein
occurring. Therefore, it will be observed that the secondary lever G16 occupies
the same position in both figures, although the upward movement of the pawl G³
is ten times as great in Figure 46 as in Figure 45. This difference in the relative
movements of the beam and of the secondary lever is determined by the location
of the fulcrum block G, which, in Figure 45 occupies such a position as to
cause the movement due to a deficiency of one em-to impart to the secondary
lever and to its selector setting racks an amount of movement equal
to that imparted to them by the movement due to a deficiency of ten
ems in Figure 46, it being obviously necessary that the selector setting
racks, which determine merely the size of the spacer or spacers to be selected, shall
be set to the amount called for by each space, without regard to the number of
those spaces.
Having thus described the effect of the changes in position of the fulcrum, a
brief description will next be given of the operation of the measuring mechanism.
The line having been carried up by the line grab so that its line separator T rests
on the pawl G³, the cam G, acting through the yoke G³, carries the pawl G³
upward until the latter is stopped by the closing up of the line against the proper
step of the jaw I, thus determining the movement of the beam. The cam G
completes its rotation, bringing the beam back to its horizontal position shown in
Figure 8.
Fulcrum Adjusting Mechanism: This comprises means for moving the fulcrum
block G of the measuring beam G to the proper point thercon for the purpose
indicated above. A comparison of Figures 45 and 46 will show the extreme move-
ment required of the fulcrum, it being understood that the position. occupied by
it is governed by the number of spaces in a line to be measured, and that the
fulcrum may therefore require to be moved to any one of ten positions, sometimes
one, sometimes five or ten spaces or intervals to the right, or to the left, as the
case may be, from its previous position.
A pin G, best shown in Figure 15, extends from the fulcrum block G" into
the path of movement of the adjusting quills H and H¹. These quills consist of
mutilated cylinders, which are capable of endwise movement to and from cach
other upon the shaft H2, to which they are splined. When brought together their
mutilated portions overlap and match one another, as shown in Figures 14
and 15, leaving circular openings along the line of their matching surfaces
arranged upon a spiral line increasing from left to right, as seen in Figures 14
and 15, being equally spaced circumferentially around the completed cylinder thus
formed by the two quills, but spaced at varying distances longitudinally thereof,
corresponding in this respect with the different required positions of the fulcrum.
A flat development of the circumferential surfaces of these quills is shown in
Figure 32, the full lines thereof representing their open position, while the dotted

page_text: lines represent their closed position. Each of these quills is provided with a loose
collar H³, which collars are engaged by suitable forks on the racks H4, those racks
being connected by means of the pinion H³ so as to impart to the racks and quills
opposite, simultaneous, and equal movement toward and from each other to the
extent indicated in Figure 32, and shown also by a comparison of Figures 1
and 14. One of the racks H4 is connected by means of an arm H6 to the cam H
on the line shaft X, and that cam is so formed as to communicate to the quills
suitable longitudinal movements at the proper times.
The quills H and H¹ are adjusted circularly to their proper position for each
line by means of the pinion or star wheel H³, fixed on the shaft H³. As previously
explained, this pinion is located adjacent to the type channel V, as shown in
Figure 9, with its teeth lying in engaging relation to the special separators, which
operate as they are carried past the star wheel to turn the latter one tooth for
each of the separators in the line. The shaft H2 is journalled at its right hand
end in a bracket H attached to the frame W of the machine, and at its left hand
end it is journalled in the upper end of the governor bracket h, as shown in
Figure 2. The shaft is also provided with a spring H10, which is preferably in
the form of a coiled clock spring, as shown in Figures 2 and 4, and is so attached
to the shaft and to its casing as to tend to turn the shaft in the direction opposite
to that in which it is turned by the separators. A. ratchet H", shown in
Figures 2, 14 and 15, is fixed to one of the quills, and is engaged by means
of a detent H¹ pivoted upon the rack H4 adjacent thereto. The function of this-
ratchet and detent is to retain the quills, so far as rotary motion is concerned, in
the position to which they are moved by the separators acting upon the star wheel
or pinion H³.
The operation of these fulcrum adjusting devices is as follows:-
While a line is being carried up by the line grab, the quills are in their
separated position, shown in Figure 1, clear of the fulcrum adjusting pin G.
The quills are thus left free, and are turned one step for each of the separators U
and T contained in the line. When that line has been carried past the star
wheel, the quills remain in the position to which they have been turned by the
star wheel so that when pushed together to the position shown in Figures 14
and 15, the pin G¹ is engaged by the proper notch, and is moved thereby to
its correct position with relation to the beam, being carried from the previous
position to its new place by the right hand or by the left hand quill, according
as it may require to be moved to the left or to the right respectively. The quills
remain in this position holding the fulcrum in its proper place while the measur-
ing operation is performed, when they are again separated to the position shown in
Figures 1 and 2, bringing the lower end of the detent H13 against a suitable pin in
the frame W, which operates to release the ratchet and allow the shaft H³, and
its quills, to be rotated back to the zero position, by means of the spring H
Stepped Jaw Adjusting Mechanism: This is best shown in Figures 1, 8, 9, 10
and 16. The stepped jaw I consists of a piece with parallel flat sides, and is of a
generally rectangular form, excepting as to its front or right hand edge, which, as
shown in Figures 1, 8 and 9, is formed in steps, each of a height corresponding
to the thickness of the special separators employed in the line of type, as herein-
before explained. This jaw is fitted to slide horizontally in the frame W toward
and from the main type channel V, and substantially central thereof, as shown in
Figures 3 and 9, the members which compose the type channel being slotted so
as to allow the jaw to pass transversely across the path of the type. The jaw is
connected by means of the link I to the arm I³, which is pivotted at 13 to a
bracket on the main frame W, and is provided with a cam pin adapted to engage
with the cam I' on the shaft X. That cam is not provided with a groove, but
is adapted to bear against one side only of the cam pin of the arm I, and is
adapted to move the stepped jaw toward the left, as seen in 'Figure 1, being

page_text: normally held toward the right and against the cam projection by means of the
spring I.
Therefore, these devices, if unobstructed, would carry the stepped jaw reciprocally
from right to left to the extent shown by a comparison of Figures 45 and 46.
But it is necessary to arrest the movement of the stepped jaw for. each line to be
measured, at the point adapted to the number of separators contained in that
line, as herein before described. This is accomplished by means of devices best
shown in Figures 8, 9 and 17, consisting of a stop I, which is fitted to slide
vertically in the frame work W, having on its upper end an L-shaped portion
projecting into the path of traverse of the jaw I on the stepped end thereof,
the other end being provided with rack-teeth which engage with a pinion I' on the
shaft Is that shaft being journalled in a bracket attached to or integral with the
main frame W. Upon the shaft Is is fixed also the star wheel or pinion Iº, best
shown in Figure 9, arranged opposite to the star wheel H8 with its teeth lying in
the path of travel of the separators, so that those separators in passing between the
star wheels H8 and 19 operate to turn each of them equally; that is to say, to
the extent of one tooth for each separator carried past, the resistance offered by the
two pinions thus being adapted to counteract each other to avoid tilting the type.
The movement thus communicated to the star wheel I' is transmitted to the stepped
jaw stop I raising it one step for each of the separators carried through; therefore,
when the entire line has been carried past the star wheels, the upper end of the
stop I stands in such a relation to the steps of the jaw I as to arrest its move-
ment at the proper step thereof for the correct measurement of that particular line.
The cam I is so timed as to allow the stepped jaw to be moved toward the right,
as shown in Figure 8, just after the stop has been set to its proper position, as
just described, operating therefore to arrest the movement of the stepped jaw at
the proper step thereof. The pressure of the jaw I against the stop 16 serves to
hold the latter in the position to which it has been elevated by its star wheel Iº.
After the completion of the measuring operation the jaw I is moved back toward
the left by its cams clear of the type channel V, so as to enable the words to be
carried up into the galley, while the stop I, relased from the jaw I, drops to its
normal position ready for the next line.
Galley Mechanism: This is best shown in Figures 8, 9, 48, 49 and 50. It
comprises mechanism adapted to hold a suitable column galley in position, to
receive the justified lines of type from the word grab mechanism, and for pushing
each line when completed along the column galley so as to make room for a new
line to enter.
The column receiving galley J, which may be so attached to the frame Was
to be easily removable therefrom, rests upon its side, and is provided with a
plunger J¹, fitted to slide into the right hand end thereof to the extent shown by a
comparison of Figures 8 and 50. In the former figure the plunger is shown in its
open position, which permits of the character type being pushed up into the galley
between the face of the plunger and the rule J. Upon the plunger is pivoted
a pawl J, having a T-shaped bell cranked extension best shown in Figures S
and 9, adapted to be engaged by the spiral springs J, by means of which the
pawl is pressed downward to the position shown in Figure 8. In that position
the front face of the pawl is vertical and coincides with the front or left hand vertical
face of the plunger J', the lower portion of which is bevelled backward from the
general plane of its surface to an extent shown in Figure 8, so as to allow the type
to enter past the corner J. The lower end of the pawl J3 is bevelled at an angle
of about forty-five degrees, and the separators U and T have a corresponding
nick in their corners centrally of their length. The character type forming a
word, when carried upward by means of their underlying separator, operate to
crowd back the pawl J3 against the pressure of its springs, thereby allowing the
character type to pass into the galley until the lower edge of the last character
type has passed above the corner J5 of the bottom wall of the galley. The nick in

page_text: the word separator then permits the pawl to return to its normal position, trans-
ferring the line of character type slightly to the left, from the support of the
separator to that of the corner J. The separator is then allowed to drop to its
position shown in Figure 8, resting on the pair of detents Jo, the tops of which are
pressed together by means of their springs, as shown in Figures 8 and 50. These
detents are pivoted in suitable recesses in the frame W, and are forced apart by
the type passing through, closing behind the separator in order to form a support
for the latter while it is being extracted, and also to form a support for the
justifying spacers which are substituted for the separators. The spacers thus
injected are carried up into the galley on the top of the next word, this operation
being repeated until all the spaces of a line have been justified and the type carried
into the galley.
The galley plunger J¹ is provided at its right hand end with a stem which is
fitted to slide in a hub of the frame W, for the purpose of guiding the plunger
in its longitudinal movement. That movement is imparted to it by means of the
cam J' on the line shaft X, which operates through the cranked arm Js, connecting
rod J and cranked arm J, to impart a suitable reciprocating motion to the
slide J, which is splined on the stem of the galley plunger so as to prevent rotary
motion thereon, leaving it free to move longitudinally. That slide is provided with a
bevelled projection J18 adapted to fit against the correspondingly bevelled cranked
end of the pawl J³, when the slide is moved to the left as shown in Figure 50,
thus locking that pawl in the position shown in that figure so as to present a planc
unyielding surface against the line of type, for the purpose of pushing it further
into the galley. Before the line can thus be pushed into the galley it is evident
that the rule J2 must be withdrawn from between the line last formed and those
which precede it. That rule is made a little longer than the width of the column,
and is fitted to slide in grooves made in the top and bottom walls thereof. It
is pivotted at its front edge to a preferably bifurcated arm J12, which is pivotted
at J3 to an extension of the frame W. That arm is provided with a bell
cranked extension J, which is adapted to engage with the pawl J15, as shown
in Figures 48 and 49. That pawl is pivotted upon the slide J, and is normally
held in the position shown by means of a spring J. It will be observed that the
slide J is required to move some distance on its supporting plunger before
abutting against those surfaces thereof, by means of which it moves that plunger
forward. This preliminary movement of the slide J" is utilised to carry the
rule J out of the way of the plunger, by means of the pawl J¹s engaging with
the cranked end J of the arm J, thus moving it from the position shown in
Figure 49 to its fully withdrawn position shown in Figure 48. The parts are so
adapted that the slide J" is brought against the abutting surface of the plunger,
as shown in Figure 50, so as to move the new line forward to the left just at the
time when the rule is fully withdrawn, as shown in Figure 48, at which time the
engaging pawl J15 has passed beyond the sweep of the cranked arm J, allowing
the latter to be returned by its spring, thus bringing the rule behind the new
line of type so as to permit of the return of the plunger. The slide J" is then
moved, by means of its cam, toward the right against the pin J, thereby moving
the plunger back to its open position, shown in Figures 8 and 49. The spring Ji
allows its pawl J15 to be depressed out of the way as it passes by the cranked arm J14
on the return stroke.
Having thus completed a description of the devices comprising the line
mechanism, a description will now be given of the devices comprehended under the
general designation of the word mechanism, beginning with the
Word Grab Mechanism :-This is best shown in Figures 1, 3, 8, 11, 12 and 13.
In its general construction and mode of operation it resembles the devices compos-
ing the line grab mechanism, differing from those devices chiefly in the respect
that the devices for separating and for carrying the words are embodied in one
organization, instead of being composed of two separable organizations. The

page_text: slide K is loosely mounted upon the rods ff, and is provided with the bifurcated
stop finger K¹ pivoted thereon at K². The bifurcations of this stop finger are
upon opposite sides of the slide K, and their upper extremities extend on either
side of the type channel V into the paths of the respective ends of the word
separators U. One of the bifurcations of the stop finger is provided with a pin K³,
which is fitted in a slot in the guide K4, the latter being attached to the main
frame W. The extent of oscillatory motion of the finger K¹ is controlled by
the form of the groove in the guide K+, best seen in Figure 8, the stop finger
being held in the position shown in that figure from the lowest point of its vertical
motion up to within a short distance of the upward extremity thereof, at which
point the groove is curved so as to move the stop finger to the right out of the
path of the separators. Upon the slide K is also mounted the oppositely disposed
pair of pawls Kº, K. These pawls are pivotted at K and K13 respectively to the
slide K and their upper ends extend on either side of the type channel immediately
below the corresponding members of the bifurcated finger K¹, and at a distance
therefrom substantially equal to the thickness of one of the word separators, as
best shown in Figure 8. The lower ends of the pawls K, and K, on the
opposite side of their respective pivots, are provided with the spring Ki³, which
operates to press the separator engaging ends of the pawls toward each other, and
toward the type channel.
An
The slide Kis caused to reciprocate vertically upon the rods ff by means of the
arm K, pivoted at the back of the main frame, as shown in, Figure 3, and that
arm is connected by means of the rod K and the rod R2 to the crank pin K'
fixed in the side of the cam M³, on the line shaft Y, as shown in Figure 53.
elastic connection between the arm K5 and the rod R2 is formed by the spiral
spring K8 coiled on the rod K. The movement communicated to the slide K by
its crank-pin K' is sufficient to carry the upper or separator engaging portions of
the word pawls K and K from the lower end of the line of type shown in
Figure 8 to, and a little above, the upper surface of the detents J6 of the galley
mechanism.
While the line is being measured, and while the spacer selecting mechanism is
being set, the word grab rests by means of its bifurcated stop finger K¹ upon the
uppermost of the word separators U'contained in the line to be measured, as shown
in Figure 8. As soon as the preliminary operations of measuring, and of setting
the spacer selecting mechanism have been completed, the word shaft Y is put in
operation, as hereinafter explained in connection with the governor mechanism,
and the rotary motion thus communicated to the crank pin K7 operates to carry
the word grab to its uppermost position, the pawls K and K10 carrying forward
the separator, beneath the ends of which they have been resting, up between
and past the detents J6. As the slide approaches the upper end of its stroke, the
pin K³, guided by its slot in the guide K4, is oscillated backward so that its engag-
ing points are outside of the path of travel of the type separators, which are thus
enabled to pass by the finger. At the beginning of the downward stroke the finger
returns to within the path of the separators, and is stopped by the next occuring
separator, the pawls K and K10 dropping into engagement beneath the ends of
the separator as before, ready to elevate it with the character type lying above it.
into the galley, as before explained. The yielding connection formed by the
spring K8, between the crank K' and the slide K, allows that crank to make its
full downward stroke, and to pick up the slide when it reaches it on the return
stroke. Meanwhile the separator which has just been left resting upon the
detents Jo, has been extracted therefrom as described in connection with the
separator extracting mechanism, and the proper justifying spacers have been
substituted therefor, as explained in connection with the spacer injecting
mechanism. Those spacers are carried up into the galley on the next word, and
thus by the repeated movements of the word grab each word is elevated from the
measuring plane into the galley.
In Figures 4, 18, 19, 20, 21, 22, 23, 28, 29 and 31 is shown the devices comprising

page_text: the spacer selecting and ejecting mechanism, the selector correcting mechanism,
and the assembling and injecting mechanisms. These different mechanisms are
so involved and interdependent that their separation into groups is more difficult
and arbitrary than in the case of any of the other sections of the machine. It is
thought advisable to preface the detailed description of these mechanisms by an
explanation of the system upon which the spacers are arranged and combined.
The justifying spacers employed in this system are four in number, herein
designated as A, B, C, and 1). (See the table, Figure 43.) The setwise thickness
of the spacer A is herein assumed to be equal to one-fourth of the em of the type
which is being justified, or in printers' parlance, it is a "4-to-em space." The
other sizes B, C, D are equal respectively to 5/16 3/8 and 16 of an em.
The method
of combining these spacers so as to satisfy the-varying widths required is shown
in the table, Figure 43 above referred to, to the extent of one em, it being how-
ever, obvious that the combinations can be continued on the same system to any
desired extent. The difference in size between the spacers A, B, C, D is
uniformly 16 of an em, and this difference exists also between the successive
combinations formed by those spacers. These combinations are arranged in
series of four, the first series employing the spacers A, B, C, D in the order given,
each of the succeeding series differing from the one preceding only by the use of
an additional A spacer. Thus it will be seen that the spacers B, C, D are never
combined with each other, and that no more than one of either of them is ever
employed in a combination. On the other hand, the spacer A is repeated to any
extent required to fill out the thickness called for. By reason of the fact that
the A spacer is the smallest employed, and also because it is thus repeated in the
different combinations, we designate it as the basic spacer. On account of the
frequent repetition of this spacer in the combinations, we employ devices for its
selection differing considerably from those employed in the selection and ejection
of the B, C and D) spacers, as will be hereinafter described.
On account of their intimate relationship to the spacer combination system it
is desirable at this point to complete the description of the setting racks G17 and
G18, which was begun in connection with the description of the measuring
mechanism, and carried only so far as it pertained to that mechanism. These two
racks are fitted to slide in suitable guides formed by extensions of the main frame,
as shown in Figures 19 and 22, and are provided on their front surfaces with
ratchet teeth, as shown in Figures 18 and 19. The teeth on the rack G17 are
located at a distance apart equal to that by which the racks are elevated by the
measuring mechanism for each deficiency of 16 of an em in each of the spaces of
that line. The teeth on the rack G18 are much closer together, there being six
of them in the distance which separates two of the teeth of the rack G, and the
pitch of these fine teeth is therefore equal to one-sixth of that of the rack G17.
and is also equal to the distance the racks are elevated by the measuring mechanism
for each deficiency of ½ of an en. Upon the frame W at No is the setting rack
detent N', the point of which extends across both of the racks G17 and G18, as
shown in Figure 18, being pressed into engagement with those racks by means
of the spring N8, the function of this detent being to engage the setting racks and
retain them in substantially the highest position to which they are carried by the
operation of the measuring mechanism, through the medium of the secondary
lever G. The rack G is connected to that lever by means of a swivelling and
sliding pivot, as shown in Figures 1, 44, 45, the rack G¹18 resting in engagement
with a suitable foot or projection of the rack G, as shown in the last mentioned
figures, being capable of vertical movement away from that foot with relation to
the rack G to an extent represented by five of the small notches upon its front
surface. When the racks are carried up by the operation of the measuring
device, the detent N7 drops into each of the notches and as the measuring beam
moves back to its horizontal position, it leaves the setting racks and the secondary
lever G, connected therewith, suspended upon the detent at approximately the
highest point of the measurement. As it would seldom happen that a tooth of the

page_text: rack G" would be exactly in position to be engaged by the detent N7, it follows
that that rack would drop down with the returning movement of the measuring
mechanism until its next tooth came in contact with the detent N'. Thus it
might happen that the rack G7 might return to an extent represented by one,
two, three, four or five of the notches of the rack G18. The position in which the
rack G is thus suspended as the result of each measuring operation is utilized as
hereinafter described in connection with the selecting mechanism, to determine
which spacer or combination of spacers are to be inserted, and the difference in the
relative vertical positions of the two racks when suspended from the detent N',
after the completion of the measuring operation, is also utilised in the manner
hereinafter to be described in connection with the selector correcting mechanism.
It is desirable, however, to explain in this connection that the backs of these racks
are each provided with steps N³, N4, N5, best shown in Figure 19, which are located
at a distance apart equal to four times the pitch of the rack G. The correspond-
ing steps of the two racks exactly coincide when the rack G18 rests on the foot
of the rack G, and they are carried out of coincidence to the extent of the
relative displacement of the two racks as a result of the measuring operation.
The spacer selecting mechanism will now be described, beginning with that
portion thereof which attends to the A or basic spacers.
In the plan view, Figure 22, may best be seen the relative location of the spacer
containing channels. The channel L, containing the A spacers is alongside the
main type channel V, while the channels Mas, M29 and M30, containing the
spacers B, C, D respectively, are arranged side by side adjacent to a raceway into
which the required spacers are ejected.
The selecting mechanism for the A spacers is shown in Figures 9, 23, 28, 29, 30
and 31. Beneath the channel L, containing the A spacers is an elevating race-
way or table L, upon which those spacers rest. That table serves. also as an
elevating raceway, and is provided with the guide rods L2 and L³, which are fitted
to slide in projections from the side of the channel L. Pivotted upon the table L'
is the stop L, best seen in Figures 9 and 23. The lower end of this stop is pro-
vided with three steps, of a height above one another corresponding to the thick-
ness of the basic or A spacer. These steps of the stop L' are adapted to rest upon
the shoe L5, fitted to slide vertically in the frame, and that shoe is provided with
a slot through which is transversely passed the end of the table clevator L, which
is also fitted to slide in the frame W, and is urged toward the left, as seen in
Figure 23, by means of the spring L. The opposite or right hand end of the
elevator passes beyond and in front of the selector setting rack G17. That rack
is provided with a longitudinal cam-like surface along one edge thereof, as shown
in Figures 1 and 23, having four planes L³, L, L10 and L", those planes being
arranged in equal steps from the rack G and connected by short inclines, the
elevator L6 having at its end a projection adapted to be engaged by these stepped
and inclined surfaces of the rack G17. From this description and reference to the
figures it will be seen that the vertical position of the raceway table L', so far
as it is governed by the position of the elevator L, is at its highest position when
the clevator rests against the plane L8, the table being then close against the
bottom of the channel L, so that none of the spacers are exposed to the action of
the extractor, the operation of which will be hereinafter described, but as the
rack G is pushed upward by the operation of the measuring mechanism the
elevator L is carried successively upon the planes L, L1 and L", thus permitting
the basic table L₁ to drop away from the bottom of the channel L to an extent
equal to the thickness of one, two and three spacers respectively, to satisfy the
requirement thus expressed by the measuring devices.
It will be understood that the rack G7 remains in the position in which it is
left by the measurement of the given line throughout the operation of justifying
all of the spaces contained in that line, so that the position of the elevator L
remains constant during the justification of an entire line. But for reasons which
appear on reference to the table in Figure 43, and for other reasons hereinafter

page_text: explained in connection with the selector correcting mechanism, it is occasionally
necessary to provide for the insertion of an additional basic or A spacer, and the
means for obtaining this occasional or accidental" A spacer consists principally
in the basic stop L, which, as represented in Figure 23, rests during the usual
operation of the machine upon the highest of its stepped faces. As these steps 5
differ in height by an amount equal to the thickness of one of the basic spacers,
it will be seen that it is only necessary to move the stop L from the position
shown in Figure 23 to the second or third step in order to obtain one or two basic
spaces respectively in addition to those which may have been obtained by virtue
of the position of the elevator Lº.
1
The stop L is pivotally connected to the frame L", which extends along the
back of the selecting devices, and is supported at its opposite end by means of an
extension L2 extending through a boss in the frame W, upon the outside of which
it is provided with a collar L³, adapted to serve as a stop for the frame L¹, and
that frame is pressed toward the left, as shown in Figure 23, by means of the 1
spring L, thus tending to hold the basic stop L in the position shown in the
latter figure, with its highest step resting upon the shoe L5. The lower member
of the frame is provided with the spur 115, and the upper member is pro-
vided with a similar spur L, those spurs being located adjacent to the path of
travel of the selecting fingers M and M respectively, upon the carriage M, best 2
shown in Figure 22. By reference to Figure 23 it will be seen that the vertical
or engaging face of the spur L15 is located farther from the basic stop L' than the
corresponding surface of the upper spur L16, to an extent equal to the difference in
horizontal position of the steps in the lower end of the stop L', the purpose of
this difference being to cause the frame to be moved to the second or middle step:
when the spur L₁ is engaged by its selecting finger M5, and to cause it to be
moved to the forward or shortest step when the spur L₁ is engaged by its selecting
finger Mº.
The carriage M is loosely mounted upon the rods mm fixed to the main
frame W, and is adapted to slide horizontally thereon to an extent indicated by
the difference between the full and the dot and dash lines thereof, shown in
Figure 23, being moved to this extent by means of the lever M¹ pivoted at M² to
the main frame W, and driven by the cam M³, fixed to the word shaft Y. Upon
the vertical pivot shaft M are pivoted the selecting fingers M5, M6, M7, Ms and M,
best shown in Figures 20, 21 and 22. By reference to the latter figure it will be
seen that these figures somewhat resemble the letter L in plan view, the extended
base members M10 of the shape of the fingers serving as a stop against a suitable
extension of the carriage, against which they are urged by means of the springs M".
located in the vertical member M, thus operating to normally hold the fingers
in the position shown in Figure 22. The vertical distance between the centres
of the adjacent fingers is equal to the distance between the notches on the
front face of the rack G, for reasons hereinafter made apparent. The fingers M³.
and M are provided with spurs M¹³ and M¹ respectively, adapted to engage with
the spurs L and L16 of the frame L", as above described, when the carriage
at the backward end of its stroke, as represented by the dot and dash lines in
Figure 23, while the fingers M, M and Ms are provided with similar but shorter
spurs, M5, M6 and M17 respectively, which are adapted to engage with the
ends M18, M1 and M20 respectively of the ejecting levers, M1, M2 and M23. Those
levers are fitted to oscillate upon the stud M2, fixed in the frame W, to an extent
represented by the dot and dash position of the lever M, shown in Figure 22.
Those levers are attached to the ejecting slides M25, M26 and M27 respectively,
adapted to slide through the bottom of the type channels M28, M29 and M30, which
contain the justifying spacers B, C, D respectively, best shown in Figure 22, and
those ejecting slides are adapted to eject singly from their respective channels the
lowest spacers contained therein, in the manner usual in type-setting machinery.
The motion of the parts is so timed that the spacers B, C, D are thus ejected from
their respective channels into the adjacent raceway when the plunger Ŏ, which is

page_text: adapted to reciprocate therein, is in the rearward position, shown in dot and dash
outline in Figure 22.
From the above description and the drawings it will be understood that when-
ever one of the fingers M or M is oscillated upon its pivot as its carriage reaches
the backward end of its stroke, as represented by dot and dash lines in Figure 22,
it operates to move the frame L, and the stop L' so as to release one or two
respectively of the basic spacers A, but whenever one of the fingers M6, M7 and Ms
are similarly moved it operates to engage with its corresponding. ejecting lever
and cause the ejection of one of the spacers B, C, D. The means whereby the
required fingers are thus turned upon their pivot M at the proper time of the stroke
of their carriage, are appurtenant to the crosshead N, which is fitted to slide
vertically upon the rods nn fixed to bosses on the main frame W. The extent to
which the crosshead may be reciprocated vertically upon the rods nn is sub-
stantially equal to the vertical space occupied by the selecting fingers M5, M6, M7
and Ms, which is also equal to the distance between each of the steps N³, N*
and N5 on the rack G, the crosshead being represented in its uppermost position
in Figures 18, 19, 20 and 21.
Upon the crosshead at N¹ is pivoted the latch N2, shown in Figures 19, 21,
and 22. The lower end of that latch is adapted to engage with the steps N³, N4, N,
shown in Figure 19 on the rearward side of the selector setting rack G, and
operates to support the crosshead at its desired keight by means of whichever
one of those steps may happen to be brought by the setting of the rack G within
the range or zone of vertical movement of the latch N2.
The selector N15 is a projection preferably integral with the selector slide N16,
that slide being fitted at its ends to the crosshead N. That slide normally rests
in its lowest position as shown in Figures 18, 19 and 20, upon suitable shoulders
which rest upon the lower lateral member of the crosshead, but it is capable of
upward movement therefrom with relation to the crosshead for purposes herein-
after described in connection with the selector correcting mechanism. For the
purpose of the description of this section it may be considered as remaining in
its lowest position shown in the last mentioned figures. The selector N15, best
shown in Figures 19, 20 and 22, is located in the general vertical plane of the
selecting fingers M³ to M inclusive, and moves with the vertical motion of the
crosshead along that plane so as to be brought opposite to one or the other of those
fingers as may be determined by the position in which the crosshead rests after
the conclusion of the measuring operation. In the last mentioned figures the
crosshead being shown in its uppermost position, the selector N15 rests in a position
to engage the selecting finger M8 when the latter is carried with the movement of
its carriage M, and therefore operates to move that finger to the dot and dash
position shown in Figure 22, thereby engaging with its corresponding ejecting
lever M23 and causing the ejection of the spacer D) into the raceway. It will be
seen by reference to Figure 20 that those portions of the selecting fingers which
move across the vertical pathway of the selector N15 are separated by a space
substantially equal to the vertical width of the selector, and the notches on the
rack G are so located that the selector N15 is never permitted to engage with
more than one at a time of the selecting fingers. It will be observed that those
notches are of the same patch as the fingers, and that the selector may therefore
be brought into the same relation to each of the fingers as that in which it is
herein shown to the finger M³.
!
The means whereby the crosshead N is carried into and out of operative rela-
tion to the setting racks, will now be described.
Upon the crosshead is mounted the correcting slide P being capable of vertical
movement thereon to an extent equal to five of the small notches of the setting
rack G18. Upon this slide is pivoted the correcting slide latch P¹, having its
point adapted to engage with the steps N³, N, N5 of the rack G18. This latch,
therefore, lies alongside of, and is substantially co-extensive with, the latch N³, to
which it is connected by means of a pin in one of the latches engaging in a slot

page_text: in the other latch, as shown in Figures 19 and 21, in which views the latch P¹ is
shown pushed above the latch N2 to the extreme limit of its movement with rela-
tion thereto, corresponding to the five notches in the rack G18, as above described.
The latches N and P¹ are pressed toward their respective racks by means of the
spring No, seated in a recess in the crosshead. The latch P¹ is provided with a
cranked extension to which is pivoted at N10 the connecting rod N", and that
connecting rod extends downward and is connected with the arm N, which is
pivoted upon the bracket Q and is provided with a cam pin which rests in
contact with the cam N13 upon the line shaft X, as best shown in Figure 5. That
cam N13 operates through the connecting rod N" to move the correcting slide P
upward to its extreme position with relation to the cross-head, and then, continuing
its upward motion, moves the crosshead to its upper position, shown in Figures 18
and 21. The action of the rod N¹ against the weight of the crosshead N operates
by reason of the nature of its connection with the two latches to compress the
spring No and swing the engaging points of those latches laterally away from
the path of movement of the steps N3, N4, N5, of the setting racks G and G18.
The cam N13 is so timed as to hold the latches and the crosshead in the position
shown in Figure 19, during the operation of the measuring mechanism, so as to
permit of the setting racks G7 and G18 being pushed up thereby to their required
position, bringing some one of the steps N, N4 or N of those racks within the
zone of movement of the latches, that zone being, as heretofore stated, equal to
the distance between those steps. Therefore, as soon as one of the steps, as, for
example N³, of the setting rack is carried out of the upper boundary of the zone
of operation of its latch, the next step N4 passes into the lower boundary of that
zone, so that one, and only one, of the steps N³, N and N5 can at any time rest
within that zone.
The operation of the Selecting and Ejecting Mechanism is therefore as follows:-
The crosshead N being held in its uppermost position, shown in Figures 18
to 21 inclusive, and the fatches being consequently held out of engagement with
the setting racks, the latter are moved upward by the operation of the measuring
devices to an extent determined by the deficiency existing in the line, divided
by the number of spaces into which the justifying spacers, which are to supply
that deficiency, are to be inserted.
At the conclusion of the measuring operation those teeth of the measuring racks
which are next above the point of the detent N7 settle into engagement with that
detent, and remain suspended therefrom while the cam N13 allows the latches N2
and P to be again forced into contact with the rearward or stepped surfaces of those
racks by the operation of the spring N, and also allows the crosshead to settle
down until the engaging points of the latches rest upon those steps of the setting
racks which are within the zone of their operation, as above described. These
latches and their crosshead N remain in this position throughout the justification
of the line then being operated upon, determining by their position and by the
resultant position of the selector, which one of the selecting fingers M5, M6, M7, Ms
and M³ shall be moved into engaging relation to its corresponding space ejector.
The crosshead therefore rests in this position supported by the step of the rack G",
holding the selector N15 in the path of some one of the selecting fingers M5, M6, M7
or M8, the selecting finger M being never acted upon excepting when called into
use by the operation of the correcting devices, as will be hereinafter described.
As the carriage is caused to reciprocate, that one of the selecting fingers which lics
in the horizontal plane of the selector N15 is moved by that selector to the position
shown in dot and dash line in Figure 22, causing the ejection of its corresponding
spacer into the raceway. If the selecting finger M5 lies in the plane of the
selector N15, it is brought into contact with the spur L5 of the frame L", thereby
moving the stop L so that the middle step thereof rests upon the shoe L5, thus
permitting the column of A spacers to fall far enough so that an additional one of
them is carried forward by the operation of the assembling mechanism, as herein-
after described. After the return of the carriage M to its full line position, shown

page_text: in Figure 23, that finger which has been operated upon by its forward movement
returns to its normal position, even though the conditions require that it shall
immediately thereafter repeat the same operation. These lateral reciprocations
of the carriage are continued to the extent predetermined by the setting of the
governor mechanism, at the conclusion of which the crosshead N is again carried
to its uppermost position by means of the cam N13, there to remain until the next
line has been measured. The cam N¹³ is so formed as to first move the crosshead
slightly above the normal upper position shown in the above mentioned figures,
and this slight additional movement enables the crosshead by means of its pro-
jection N to engage with a cranked projection of the detent N, as best shown
in Figure 21, thus momentarily carrying that detent out of contact with the teeth
of the setting racks G and G18, and permitting the latter to fall to their lowest
or zero position in order that they may again be raised from that position by the
subsequent operation of the measuring mechanism upon the next line.
Selector Correcting Mechanism:-From the above description of the spacer
selecting mechanism it will be seen that that mechanism is in itself insufficient to
effect the justification of the lines of type within the necessary limits of accuracy,
inasmuch as it would seldom happen that any of these spacers or combination of
these spacers would, if repeated without change, in all of the spaces existing in a
given line, justify that line with sufficient accuracy. The arrangement and
operation of the above described devices is such that if the measurement of the
spacer required, as indicated by the position of the measuring racks, does not
quite equal one of the spacers or combination of spacers, the selection will fall
upon the next size below. In other words, if the racks G and G18, when at the
highest position to which they are carried by the measurement of a given line, do
not stand at a position at which one of the notches in the rack G is exactly
engaged by the detent N', that rack will drop back until its next notch engages
with the detent, thus causing the selection of a spacer or combination of spacers
smaller than the size indicated by the measurement. Thus it will be seen that the
effect of a certain amount of the measurement is lost, or in other words, that the
extent to which the rack G17 drops back from its measurement indicating posi-
tion to the position wherein it rests by the engagement of one of its notches
with the detent N7, represents relatively the extent to which the spacer or combi-
nation of spacers thus selected is less than the space to be filled. The purpose of
the devices at present under consideration is to compensate for these deficiencies,
keeping account of them, as it were, until they have amounted to the difference
between the size of the spacer selected and the size of the next larger spacer, opera-
ting then to move the selector up to a position in which it shall select and eject a
spacer or combination of spacers of that next larger size. Having supplied the
deficiency the selector must return to its first position, until the increments of
deficiency again require the insertion of the larger spacer.
The mechanism comprising this correcting auxiliary to the spacer selecting
mechanism is shown in the same figures in which that selecting mechanism
appears.
Reference has already been made to the correcting slide P, and to its latch Pl,
which is adapted to be engaged by the measuring rack G18. That slide is carried
upon the crosshead N and is capable of a vertical motion with relation thereto to
the extent of five of the small notches of the rack G18, as shown in Figures 19
and 21, as it might sometimes happen that the detent N, at the conclusion of a
measurement might engage the fifth tooth of the rack G18, below one of those
teeth which normally are in line with the notches of the rack G, holding the
former rack in that position while the rack G7 falls to the extent represented by
the five notches, before engaging with the detent N7. Upon the slide P is
pivotally attached an end of the lever P², the other end of which is pivotally
attached to the hub P³ of the crosshead N. At a point midway of the length of
this lever is pivoted the lever P, which is normally held in a position coincident
with that of the lever P2, by means of the spring. 15, attached to the crosshead N,
.

page_text: as shown in Figure 18. One end of the lever P is provided with a projecting
pin P, best shown in Figures 22 and 24, located in the plane of and adapted to
engage with the inclined ends of the cam-like pieces P', which are attached to or
integral with the carriage M. Whenever the spaces existing in a given line may
be exactly filled by a certain number of similar spacers or spacer combinations,
the position of the measuring rack incident upon the measurement of that line
is such that the latch engaging steps N³, N, N³, thereof are coincident upon the
two racks, and in that case when the crosshead and its latches are let down into
contact with those steps, the correcting slide P rests in such a position that the
pin P6 of the lever P* will pass between the cam pieces Pi of the carriage M as the
latter is caused to reciprocate in the operation of assembling the spacers. But
when the result of the measurement is such that the steps of the rack G18 are held
above those of the rack G17, the resultant position of the correcting slide P and its
levers P2, P is such as to bring the pin P under the operation of the bevelled
face of that one of the cam projections P7 to which it is opposite. That operation
causes a vertical oscillation of the lever P upon its pivotal connection with the
lever P2, at each backward stroke of the carriage M, the extent of that oscillation
being in direct proportion to the amount of relative displacement of the racks G17
and G18.
The
Upon the left hand end of the lever P, as best seen in Figure 24, is pivotally
mounted the pawl P8. The point of that pawl is adapted to engage with teeth 19,
made in the right hand edge of the selector slide N16, being capable of an oscilla-
tory movement into and out of those teeth, and being limited in its forward move-
ment away from the teeth by means of the pin Po fixed in the crosshead.
pawl is further provided with a connecting rod P, pivotted thereto, the opposite
end of that rod passing through a clamping swivel P on the carriage M, that
hub being split and provided with a clamping screw, which is adjusted so as to
engage the rod P" with sufficient friction to carry the pawl P8 into contact with
the teeth P upon the left hand or backward movement of the carriage, and to
carry that pawl away from the teeth against the stop 110 upon the forward move-
ment thereof.
From the foregoing description it will be seen that any upward movement
imparted to the pawl Ps while it is in contact with the teeth P would operate to
raise the selector slide N16 a corresponding extent, and that extent is controlled
by the amount which the racks G and GIS are displaced in relation to each other,
as the result of a measurement of a line operating through the levers P2 and P
to hold the pin P6 to a corresponding extent above the adjacent slot between the
cam pieces P7. In Figure 23 that pin is shown to be in the position to which it
is carried by a displacement of five of the small notches of the rack G18, the
carriage being here shown in its forward position, while in Figure 24 the cams P7
are shown in their backward position, the progress toward which has caused the
pin P to be forced down by the inclined face of the adjacent cam piece P³, until
it can enter the slot below that cam piece, thus imparting to the selector slide N16
an upward movement equal to five of the notches P³, which is also the equivalent
of the extent to which the rack G18 has been displaced.
The selector slide N16 is retained in the raised position to which it is moved by
the pawl P8, by means of the detent P12, which is pressed into engagement with the
teeth P13 corresponding to the teeth I, located on the opposite or left hand edge
of the slide N16 By reference to Figure 24 it will be seen that there are six of
these teeth P. After the fifth tooth occurs an interval as though the sixth and
seventh teeth were removed, the sixth tooth being therefore where the eighth tooth-
would be located if the teeth were continuous, and we will hereinafter refer to this
isolated tooth as being the eighth on that side, regarding the sixth and seventh
as being removed, for reasons hereinafter set forth.
It will be understood that the object of the mechanism at present under con- 5
sideration is to raise the selector N15 from its lowest or normal position with respect
to the crosshead so as to cause it to engage with and select the next larger size of

page_text: spacer, or combination of spacers, whenever the deficiency between the size of
spacer called for by the measurement, and the size of spacer supplied by the select-
ing mechanism shall have amounted to the additional thickness represented by a
larger size. Having supplied this deficiency by the insertion of one or more
spacers or combinations of the larger size, it is necessary that the selector shall be
allowed to drop back to its former position until the deficiency resulting from
the repeated selection of the spacer too small for the space to be filled shall again
require the selection of the larger space. The mechanism by means of which the
selector slide is thus released and allowed to drop back to its normal position will
now be described, reference being made to Figures 24 to 27 inclusive.
The detent P2 is provided with an approximately lozenge shaped projection P¹4
upon its face. That projection is adapted to engage with similar shaped projec-
tions P1, P16 upon the escapement pawl P, which is pivoted upon the selector
slide N. Upon that slide is also revolubly mounted the escapement wheel P18,
which is, urged in the direction of the arrow against the stop 19 by means of a
coiled spring P20. The escapement pawl P1 is provided with a point which is
pressed into engagement with the wheel P18 by means of the spring P21. A rod P22
is fixed in a lateral member of the crosshead N, and extends downward partially
across the face of the escapement wheel in line with a pin P2 located upon that
wheel, for the purposes hereinafter explained.
By again referring to the table shown in Figure 43 it will be seen that the size
of the smallest space is equal to one-fourth of an em, and that the spacers B, C, D
progress in size above the A by one-sixteenth of an em. It therefore follows that
where the measurement shows the spaces to be 796 of an em in width, the insertion
of an A spacer, which equals 6/96 or 16 of an em, leaves a deficiency of 196 in each
space. At the insertion of the sixth spacer this deficiency would, therefore,
amount to % or 16 of an em, which is equal to the difference in size between
the A and the B spacers, and that deficiency would therefore be made up if a B
spacer were to be put into the sixth space instead of an
spacer. Therefore, this
mechanism is adapted to make this substitution, resuming, however, the insertion
of A spacers in the succeeding spaces until the amount of deficiency again requires
the insertion of the larger size.
The mode of operation of this correcting mechanism differs with each of the five
different amounts of corrections that may be required, and a description is there-
fore now given of its operation under each of these five possible conditions. The
difference between these conditions, and the difficulty in satisfying them, are due
chiefly to the circumstance that the selector must be allowed to return to its lower
or normal position upon the completion of that stroke of the carriage at which the
amount of correction then applied equals the amount of deficiency then accumu-
lated. In correcting for a deficiency of 19 of an em the slide must return at the
conclusion of the sixth stroke, because at that stroke the devices will have applied
a correction of % or 16 of an em, equalling the accumulation of six deficiencies
of 6 of an em. Therefore, in correcting for deficiencies of 2/96 3/96 4/96 and 5/96
the selector must be returned to its lower or normal position at each first, second,
third and sixth stroke respectively of the carriage.
When
From the description already given it will be understood that the "deficiency,"
occurring in each space is added up or tallied," so to speak, upon the notches P
of the selector slide N16, one notch for every deficiency of 196 of an em.
that deficiency occurs in each space of a line the selector will be raised one notch
at each stroke of the carriage M by the operation of one of its cam pieces P7, the
slide being retained in its raised position by means of the detent Piz Therefore
upon the sixth stroke of the carriage the selector slide will be raised six notches,
causing the selector N15 to engage the next selecting finger above that employed in
the previous five strokes of the carriage. The escapement pawl P17, carried up by
the elevation of the slide N16 reaches at this point such a relation to the detent Piz
that the lower point of the lozenge shaped projection P16 of the pawl engages with
the upper point of the similar projection P¹ of the detent, exactly as the projec-

page_text: tion P15 is shown in engagement therewith in Figure 24. Upon the forward
stroke of the carriage M the pawl Ps is withdrawn from the teeth P9, thus allow-
ing the weight of the slide to operate through the lozenge shaped point P15 of
the pawl P, to cam the detent away from the teeth P. The slide, being thus
left unsupported falls to its first position shown in Figure 18, carrying the
selector N back to its former and normal position, when it resumes the selection
of the smaller spacer until again elevated by the correcting device.
The operation of the mechanism in the correction for deficiencies of 2/96 and 3/96
of an em differs from that just described only in the respect that the selector
slide reaches its releasing point at the third and second strokes respectively;
inasmuch as the numbers 2 and 3 are also even divisors of 6. But 4 and 5 are
not even divisors of 6 and therefore the operations of the devices for the correc-
tion of deficiencies of 96 and 5/96 of an em become more complex.
96'
Describing first the correction for a deficiency of G. In this case the first stroke
of the carriage will elevate the slide N16 four notches, which will be detained by
the detent P. The next stroke will elevate the slide four more notches, bringing
the eighth of the notches P13 above the detent P12, where it remains until the
third stroke of the carriage, when the pawl PS engaging the fifth of the notches P
raises the slide as shown in Figure 24, so that the lozenge projection P¼ of the
detent Prides over the projection P¹s of the pawl P, as shown in Figure 24,
allowing the slide to drop as before. It will be observed that the selector was in
position to select the larger space at both the second and third strokes of the
carriage, and therefore the "correction" amounted to 12/96 of an em, just equalling
the deficiency of % occurring in each of the three spaces justified by the three
strokes of the carriage.
In the case of a deficiency of 5/6 of an em, the first stroke of the carriage raises
the slide N16 five notches, where it is held by the detent engaging the fifth of the
notches P13. At the second stroke of the carriage the pawl Ps engages with the
fifth of the notches P' and, raising the slide higher than on any of the other
corrections, brings the pin P2 of the escapement wheel P17 against the rod P2,
re-acting upon the wheel to turn it to the position shown in Figure 26, so as to
engage with and hold the pawl P17 out of engagement with the detent P¹². That
detent therefore remains against the slide N16, supporting it in its raised position
by means of the eighth one of the notches P13. The partial revolution of the
wheel P18 caused by its contact with the rod P22 serves to carry the first of the
tecth P into the path of the pawl Ps, which upon its third stroke engages with
that tooth, as shown in Figure 26, and advances it another notch. The fourth
and fifth strokes of the carriage each operate thus to turn the wheel an additional
notch, without releasing the slide from the detent P12. But the sixth stroke of
the carriage brings beneath the pawl P17 a portion of the wheel P18 which is deeply
recessed, thereby allowing that pawl to drop against its stop pin P30 to the position
shown in Figure 27, thereby disengaging the detent P and allowing the slide N16
to drop to its normal position. As it approaches the bottom of its stroke the
cranked spring arm of the pawl P17 collides with the pin P2 attached to the cross-
head N, which serves to move the pawl to the position shown in Figure 18, thus
releasing the wheel, P18 and allowing it to be returned by its spring P20 to its
normal position as shown also in the latter figure.
If either of these correcting operations should while yet unfinished, be inter-
rupted by the completion of the justification of the line, thus leaving the selector
raised above its normal position on the crosshead, it will be released therefrom by
means of the rod P, attached to the frame W, against which the cranked end of
the pawl P¹² is carried, as shown in Figure 24, when the crosshead is moved to its
highest position by its cam N13. The movement of the pawl P12 due to this engage-
ment with the rod P28 serves to release the slide N and allow it to fall to its normal
position. If the completion of the line finds the escapement wheel P18 in an
incomplete stage of its operation, for example, as in Figure 26, the movement of
the pawl P7 due to its engagement with the rod P2 will serve also to disengage

page_text: that pawl from the teeth of the wheel, allowing the latter to be rotated to its normal
position by means of its spring P2. This releasing of the respective devices at
the completion of each line is necessary in order that they may be at their normal
or starting point at the commencement of each new line."
Spacer Assembling Mechanism: The construction and relation of the devices
which comprise this mechanism is best shown in Figures 22, 28, 29, 30 and 31.
The plunger O is attached to the carriage M, and is carried by the lateral recipro-
cations of that carriage along the raceway 0%, best shown in Figure 22, which lies
immediately in front of the channels M28, M2, and M30, containing the B, C, D
spacers respectively. Those spacers are ejected one at a time, as previously
described, into that raceway, at the end of the movement of the carriage toward
the left, and while the plunger O is therefore in the position shown in dot and dash
lines in Figure 23. On the return or forward movement of the carriage toward
the right, the spacer that has been ejected is moved forward into line with the type
containing channel into which it is to be injected by the injector plunger R. In
this position it is alongside of the channel L containing the A spacers, as shown
in Figure 22, and in Figures 28 to 30 inclusive.
The devices by means of which the A spacers withdrawn from the channel L
are assembled in combination with the spacer ejected from either of the
channels M8, M29 and M30, consists of a bifurcated plunger O¹, which is fitted
to slide in a boss w on the main frame. W, and is connected by means of the
lever 03, also pivoted on the boss w, and best shown in Figure 22. The opposite
end of that lever is provided with a slot, by means of which the lever engages with
a pin 03 on the carriage M. This arrangement of the lever operates to impart to
the plunger O¹ a movement contemporaneous with, but in the opposite direction
to, that of the carriage M, and the plunger O. The bifurcated ends of the
plunger O pass through corresponding slots in the basic table L', as best seen in
Figure 22, the ends of the plunger being turned upward to form hooks, which, as
the plunger is moved toward the left, operate to move along upon the basic table
or raceway L' all of those A spacers which have been allowed to escape from below
the level of the channel L by the lowering of the table, whether by the operation
of the elevator L6, or of the stop L, as previously described. The upper surfaces
of these hooks of the plunger O¹ are fitted against the lower surface of the chan-
nel L so as to form a support for the column of spacers which remain in the
channel, as shown in Figure 30, the basic raceway-table L' remaining in its lowered
position until the A spacers have been carried to the position shown in Figure 30,
and until the B, C or 1 spacer has been brought forward and pushed upon the top
of the A spacers, as shown in the last mentioned figure. The basic table L is then
elevated to the position shown in Figure 31, thus raising the combination of
assembled spacers up to the level of the top of the detents J, to which it is at that
time lying immediately adjacent. This raising of the basic table is accomplished
by means of the lifter O'. That lifter rests upon the ends of the plunger 01, and
is provided with a bevelled end which engages with a correspondingly bevelled
and hooked projection or extension 05 of the basic table L', shown also in side
view in Figure 9. The opposite end of that lifter is supported by and slides in
the bracket O' attached to the frame W, and receives its motion from the spacer
injecting devices, as best shown in plan view in Figure 22.
The consecutive order of operation of the assembling devices will best be seen
by reference to Figures 28 to 31 inclusive, Figure 28 showing the basic table in
its elevated position, the spacers assembled by its previous operation having been
removed therefrom by means of the injecting mechanism. In Figure 29 the basic
table is shown in a lowered position, this time by the operation of the stop L
in being moved to its second or lowest step, thus lowering the column of A spacers
far enough to permit of the two lower ones to be drawn away by the movement of
the plunger 01, as shown in Figure 30, where they rest ready for the spacer which
is therein shown as being advanced by the plunger O. After that spacer has been
pushed by the completion of the movement of the plunger O upon the two A

page_text: spacers, all three are raised by the elevating movement of the basic table to the
position shown in Figure 31, whence they are injected into the line by the inject-
ing mechanism. The parts are now again in the position shown in Figure 28,
and repeat the above operation for each of the spaces to be justified, under the
control of the governing mechanism.
Separator Extracting Mechanism:-This is shown in Figures 3, 4, 5, 9, 10
and 22. As previously described, the separators are extracted from the line while
resting upon the top surface of the detents Jo, which is coincident with the inject-
ing plane, and with the surface of the raceway.
The form of the word separators U and the line separators T is best shown in
plan view in Figures 10, 12 and 22, differing from each other only in the respect
that the ends of the line separators T are made slightly longer than the ends of
the word separators U. Both kinds of these separators are provided with shoulders
corresponding to the length of the type, by means of which they are retained in
the type channel, their reduced ends passing through slots in the edges of the
channel which are narrower than the thickness of the type, and thus extending a
short distance on either side of the channel so as to enable them to be engaged by
the fingers of their respective grabs. Both kinds of these separators are provided
with similar extracting notches, which are similarly located on the opposite ends
of the separators so as to enable them to be extracted, even when reversed by
accident, or otherwise. The separators are withdrawn from the line by means of
the extractor hook Q, which is adapted to reciprocate toward and from the channel
upon the level of the injecting plane thereof, normally lying at rest adjacent to
the location in which the separators rest upon the detents Jo when in position to
be extracted. The hook is held out of the path of the type while in its inoperative
position, as shown in Figure 22, by means of its bevelled end which is pressed
against a correspondingly bevelled portion of the side of the channel V, the hook
being sufficiently elastic to allow it to spring away from the type to the position
shown in that figure. At this portion of the channel V the shoulders thereof,
by means of which the type and the separators are retained in their lengthwise
position, are cut away so as to allow the separators to be extracted in one direction,
and to allow the justifying spacers to be inserted from the opposite direction.
The opposite end of the extractor hook Q is pivotally mounted upon the block Q¹,
as shown in Figure 9, that block being fitted to slide upon the rods
99, which
are fitted at their ends in the frame W. The slotted end of the arm Q2 is con-
nected by means of a pin to the block Q¹, and is fixed upon one end of the shaft Q³,
and that shaft is pivotally mounted in the bracket Q4, having fixed upon its
opposite end the cam arm Q5. That cam arm is provided at different portions of
its length with the cam pins Q and Q7, adapted to engage with the cams Q and Qº
upon the shafts X and Y respectively, as best shown in Figure 5, being pressed into
engagement with the cams by means of the spring Q. The arm Q5 is thus con-
nected with these two cams in order that two independent movements of differing
amplitude may be imparted to that arm, and consequently to the extractor hook Q,
for the purpose of distributing the word separators U and the line separators T
into their respective channels Q10 and Q¹¹. Those channels are supported by
extensions from the main frame W in the relative positions shown in Figures 9
and 22, the channel Q10 for the word separators U being located nearer to the type
channel than is the line separator channel Qu
The mode of operation of this mechanism is as follows.
During the operation of the devices comprising the line mechanism, this extract-
ing mechanism, along with the other devices comprising the word mechanism,
remains at rest, the hook Q resting in the position shown in Figure 22, out of the
path of travel of the type. After the commencement of the operation of the word
imechanism, the first word having been carried up into the galley by the word
grab, and the first of the U separators being then at rest upon the detents J6, the
extractor hook Q is moved by means of the cam Q2 toward the left from its position
shown in Figure 22, catching into the nick of the separator U, and carrying it

page_text: toward the left to a position immediately over the channel Q10, into which it drops
by its gravity. The hook Q then returns to its previous position adjacent to the
type channel, repeating the extracting operation for each of the U separators in
the line, the number of its operations being controlled by the governing mechanism,
as hereinafter described. The last separator in each line is invariably one of the
line separators T, and after the final word has been carried into the galley, this
separator T remains lying upon the detents J until the line shaft X is put in
operation for the purpose of measuring the next line, thereby bringing the cam Q8
into engagement with the arm Q, the form of the cam being adapted to impart
to the arm Q2 a movement of sufficient extent to carry the T separator which is then
engaged by the extractor hook Q, to a position above the channel Q₁, into which it
also falls by gravity. This separator being longer than the word separators is
thereby enabled to pass across the top of the channel Q10 without falling therein.
It will be observed that the relative location of the cams Q8 and Q' to the arm Q³ is
such as to favor the imparting of a greater amplitude of movement to that arm
when moved by the cam Q8 than when moved by the cam Q.
Spacer Injecting Mechanism:-This is shown in Figures 3, 5 and 22, and
operates in connection with the word grab and spacer assembling mechanisms.
The injector R is a plunger, the spacer engaging end of which rests upon that
extension of the frame W which forms the bottom of the channels M28, M29 and
M30, and of the raceway this general level constituting what is herein termed the
injecting plane. The opposite end of the plunger R is supported by its connection
with the lifter 0%, and is connected by means of a pin to, a slotted bell cranked
arm R', which is pivoted upon an extension of the frame W, as shown in Figures 3
and 53. The opposite end of that arm is connected by means of the rod R2 to the
crank pin K7, located in the side of the cam M³, that crank serving thus to com.
municate movement to the word grab, the basic table, the lifter 0 and the spacer
injecting devices, inasmuch as these devices, require to be operated contempor-
aneously. The forward movement of the injector R begins at the conclusion of
the space assembling movement, when the spacers assembled by that movement
have been lifted to the level of the injecting plane by the basic table, and that
injecting movement follows close upon the extraction of the word separators U
described in the last section. No movement, however, of the injector, accompanies
the extraction of the line separator T, inasmuch as the extracting of that separator
is accomplished by the operation of the line shaft mechanism.
Having thus completed a description of the devices comprehended under the
general designation of word mechanism, a description will be given of the third
general division of the machine herein designated as the
Governor and Actuating Mechanism:-This is shown in Figures 1, 2, 6, and
from 34 to 42 inclusive. The general line of shafting which has upon it the cams
and other devices for operating the devices composing the line mechanism, and.
which is herein referred to under the general designation of the line shaft X, is
composed of three sections, herein distinguished by the designations X1, X2, and X³,
while the line of shafting herein referred to as the word shaft Y, is composed of
two sections, distinguished by the designations Y' and Y2 respectively. The
section Y2 is provitled with the pulley Y³, and also has fixed upon it the pinion Y4,
by means of which motion is communicated to the gear X on the shaft X¹. All
of these shafts are journalled in suitable brackets attached to the main frame W
of the machine, and the sections X', Y' are driven continuously in opposite direc-
tions, as indicated by their respective arrows in Figure 4, the line shaft being
rotated at a considerably reduced rate of speed as compared with that of the word
shaft Y.
The arrangement and connection of these shafts are best shown in the plan
views, Figures 5 and 6. The shaft X¹ has splined thereon the sliding clutch X5,
which is adapted to engage with and be disengaged from a fixed clutch X, on the
shaft X2, and that shaft is provided with the crank F5 for operating the line grab.
Beyond that crank the shaft X² is provided with the sliding clutch X', which is

page_text: adapted to be moved into and out of engagement with a corresponding fixed
clutch X8, on the shaft X³. The end of the shaft X is herein shown to extend
into the adjacent end of the third section X³, but this is merely for the purpose
of forming a supporting bearing for that end of the shaft X³. Referring now to
Figure 5, the governor cam S" is shown fixed upon the shaft X3 adjacent to the
clutch X8, after which come the cams H, I, Q, N13, J7 and G in the order named.
The shaft Y is provided with a fixed clutch Y5, and the adjacent end of the
shaft Y is provided with a sliding clutch Y adapted to engage with and be dis-
engaged from the clutch Y³. Toward the right hand end of the shaft Y2 are fixed
the cams Q and M³, to the latter of which is fixed the crank pin K7.
These cams and cranks are thus located upon detachable sections of the shafts X
and Y in order that their respective groups of mechanism may be thrown into or
out of operation by means of their clutches under the control of the governing
mechanism, which will now be described.
The shaft is provided with a worm 17, which is adapted to engage with the
worm wheel S, fixed on the governor shaft S¹. That shaft is journalled at its ends
in suitable bearings in the frame W of the machine, and has fixed upon it the
ratchet wheel S2, best shown in Figures 40 and 41, the relation of the worm, worm
wheel and ratchet being such that the latter is rotated continuously in the direction
of the arrow shown upon the ratchet in Figure 40, to an angular extent equal to
that to which the notches are separated, at each revolution of the shaft Y¹. Upon
the shaft S, adjacent to the ratchet wheel S2, is loosely mounted a controller S³,
having integral therewith three flanges S*, S³ and S. The flange S has pivoted
upon the side thereof the pawl S7, in engaging relation to the ratchet wheel S².
Loosely supported upon the shaft S' on the opposite side of the ratchet, is the pawl
releasing cam S8, having in its face adjacent to the ratchet, a groove, best shown in
Figures 39, 40 and 42, into which extends a projection S9 of the pawl S. A
similar projection S1, on the opposite end of the pawl extends over the periphery
of the cam Ss, as shown in Figures 39 and 41. The pawl releasing cam S8 is pro-
vided with a secondary flange S", which is squared, as shown in Figure 37, and
engages with a corresponding mortice in the arm S2 of the releasing rod S22, so as
to prevent the cam from rotating, the flange S" being provided with pins S12,
adapted to engage with the inclined slots S25 of the arm S2, as best shown in
Figures 37 and 38, the purpose of this arrangement being to move the pawl releas-
ing cam S8 endwise upon its shaft S₁ at the desired time, so as to release the
projection $10 of the pawl S7 and allow the latter to engage with the teeth of the
ratchet S², that pawl being urged toward its ratchet by means of its spring S³,
attached to a pin located in the side of the pawl flange St. That endwise move-
ment of the cam S8 is never, however, sufficient to release the projection S⁹ of the
pawl from its groove in the side of that cam. It will, therefore, be seen that the
pawl S7 cannot engage with its ratchet S2 unless partially rotated to some other
position with relation to the groove of the cam S8 than that in which it is shown in
Figure 40, and when so moved to a position which allows of such engagement, it
is disengaged therefrom upon arrival at the position shown in that figure by the
operation of the groove of the cam S8 upon the projection S9, which not only serves
to disengage the pawl from the ratchet wheel, but also serves to prevent any
further motion of the pawl and its attached controller in the direction of rotation
of the ratchet wheel.
The flange S6 of the controller S³, is stepped in the manner shown in Figure 2,
the steps being arranged in the form of a spiral. Adjacent to this stepped flange
is the detent S13, fixed to the detent shaft S, which is journalled in bearings in
the adjacent bracket, and is provided with the arm S15, as best shown in Figures 2,
6, and 35. The detent can engage only with the last or highest step of the
flange S, as shown in the latter figure, thus serving to hold the flanges S4, S5
and S6 in the positions in which they are shown in Figures 40, 36 and 35 res-
pectively, during the operation of the measuring mechanism. The controller S³
is provided with a spring or weight, as shown in Figures 2, 34 and 36, adapted to

page_text: normally urge the sleeve and its appurtenant flanges in the direction indicated by
the arrow in Figure 36, which is the opposite direction to that in which the
ratchet S rotates.
The stop S16 is located above and in the plane of the stepped flange S6, and is
connected with the rack S7 by means of a telescopic connection, as shown in
Figure 34. That rack is fitted in engagement with the pinion S18 fixed on the
shaft H, which, as it is turned by the separators T and U, as described in connec-
tion with the fulcrum adjusting mechanism, operates to lift the stop S16 to an
extent equal to the height of one of the steps of the flange So for each of the .
separators in the line. Therefore, after the line to be measured has passed into
the measuring zone, the stop S16 stands in engaging relation to that step of the
flange S corresponding in number to the number of spaces or U separators in the
line to be justified. The single additional movement of the stop due to the line
separator is compensated for by the position of the steps on the flange.
From the foregoing description it will be understood that the controller S³, if
released from its detent S13 will make a partial rotation in the direction of the
arrow shown in Figure 36 by the operation of its weight or spring, until one of the
steps of the flange collides with the stop S16, carrying with it the flanges S
and S5, and thereby moving the pawl $7 to a position relative to the releasing
cam S8, which permits of its engagement with the ratchet S2 so far as the groove
of that cam is concerned, being, however, still held out of engagement with the
ratchet because of its projection S10 resting upon the periphery of that cam. If
at this point, however, the cam were to be drawn endwise upon the shaft S¹, the
pawl would be released and would be carried into engagement with the ratchet S³,
and would be released therefrom upon arriving at the position shown in Figure 40.
The telescoping connection of the stop S16 with its rack S7 is for the purpose of
enabling the rack to be returned to its lowest position by the releasing of the
detent H before the stepped flange S is returned to the position which allows
the stop S16 to drop with the rack, a condition which may occur in the justification
of a line having a large number of spaces.
The means whereby the releasing of the controller S3 and of the pawl is accom-
plished will now be described.
The governor releasing cam S¹19 is fixed upon the shaft X3, and is best shown
in Figures 2, 6, 47 and 51. Its flanged left hand edge is provided with two
steps S2 and S21, and is adapted to engage with the releasing rod S, which rests
in suitable guiding supports, and is pressed into contact with its cam by means of
a spring S As shown in Figure 6, the rod is bifurcated toward its left hand
end, the pawl releasing arm S24 being adapted to engage with the squared flange Su
of the releasing cam S³, the arm S2 being provided with inclined slots S25 adapted
to engage with the pins S1, as best seen in Figures 37 and 38. The detent releas-
ing arm S26 of the rod S22 is connected by means of the link S with the arm $15,
and the lower side of the arm $26 is provided with a spur S28, best shown in
Figure 35, that spur being in the path of movement of the pin S29 on the flange St.
The releasing rod S2 is adapted to engage with the clutch fork $30 which is fitted
to slide in suitable supports of the frame W, by means of the shoulders S31 and S
as best shown in Figure 35, so as to move the fork to an extent sufficient to engage
and disengage its clutch Y from the clutch Y5 of the shaft Y¹.
The step S20 of the cam S19 is made high enough to move the rod S22 and its
arms S and S26 toward the left from the position in which it is shown in Figures 6,
35, 37 and 38 a sufficient extent to release the detent S¹³ from engagement with the
stepped flange S6, and sufficient also to move the shoulder S31 into contact with the
clutch fork $30. This movement, however, is not sufficient to carry the releasing
cam S8 away from the ratchet so as to release its pawl, the slots S25 being straight
as shown in Figure 34, for a distance equal to the movement imparted to the
arm S by the step $20 of the governor cam S¹. The parts remain in this position
while the stepped flange S is rotated by means of its weight until the proper step
from which its return motion is to begin is brought against its stop $16. Mean-

page_text: while the cam S¹ continues to revolve and brings its step S21 in contact with the
rod S2, thus moving the clutch Y6 into engagement with the clutch Y³ by means
of the shoulder S³ of the releasing rod S2. This additional movement of the
latter rod operates also by means of the inclined portion of its slots S25 to move
the releasing cam S8 away from the ratchet wheel S2 so as to allow its pawl $7 to
engage therewith, it being remembered that the pawl has been carried back with
ihe stepped flange S6. As the pawl drops into engagement with one of the teeth of
the constantly revolving ratchet wheels, the controller S³, with its flanges St, S
and S6, is carried with the movement of that wheel until the pawl again arrives at
the position shown in Figure 40, when it is disengaged from the ratchet by means
of the cam S8 acting upon the projection S. The last part of the return movement
of the controller S operates through the pin S2, the flange $5, and the spur S28,
to move the releasing rod S toward the right, that rod being at this time opposite
to the lowest portion of the flange of the cam S. This movement of the releasing
rod S operates through the inclined grooves S25 to move the releasing cam S8
toward the ratchet wheel so as to again support the projection S10 of the pawl S7
and hold it out of engagement with the ratchet wheel during its subsequent reset-
ting operation. That movement of the releasing rod S toward the right also
operates by reason of the engagement of its shoulder S with the clutch fork $30
to move the clutch Y out of engagement with the driving clutch Y thus permit-
ting the word shaft Y2 to stand still until again re-clutched by the operation of
the step S2 in the next recurring revolution of the governor cam $19.
The sliding clutch X³, upon the shaft X', is normally pressed toward the left
or engaging position by means of its clutch fork X. urged by the spring X10 Thát
clutch is provided with a spur X", best shown in Figures 6 and 52, which is urged
by the action of the spring X against the end of the flange of the adjacent bearing.
That flange is provided with a recess, as shown in Figure 52, into which the spur X¹¹
is forced by the action of its spring at each revolution of the shaft X', thereby dis-
engaging it from the clutch Xº. As the rotation of the shaft X¹ is continuous, the
clutch X5 will, after passing by its engaging point with the clutch X6, be again
forced out by means of the inclined leading surfaces of the spur X", so as to be in
position to re-engage its clutch at its next revolution if the conditions so require.
The left hand end of the clutch fork X is located in the path of movement of the
pin X fixed in the flange $5, as shown in Figure 36, and that pin is so located in
the flange with relation to the pawl S7 as to hold the clutch fork X' and its
clutch X into engagement with the clutch X6, as shown in Figure 6, when the
pawl is in its position of rest, as shown in Figure 40, so that the clutch will not be
disengaged from its mate X while thus supported by the pin X12, even when its
spur X is passing by the recess shown in Figure 52, at which point it would
otherwise disconnect, as shown in the latter figure. The effect of thus holding
the clutch X in its engaging position operates to continue the rotation of the
shaft X, and thus causes the repetition of the movement of the line grab mechanism
by means of the crank F5.
The clutch X is splined to and fitted to slide upon the shaft X2, and is operated
by means of the fork X¹³. That fork is pivoted at X" upon the main frame W, its
opposite end being connected by means of the link X15 with the bell crank arm X16,
pivoted upon the frame W, as best shown in Figure 5. That bell crank is located
adjacent to the indicator arm X17, which is pivoted upon the main frame W, as
shown in Figure 3. One edge of that arm is located in the plane of movement of
the line grab separator slide E, so that the latter when moved up from its lowest
position by an advancing line operates to engage with the indicator arm X" and
hold it in its vertical position shown in Figures 3 and 5, thus operating through
the bell crank X16, link X5 and fork X¹³ to hold the clutch X7 into engagement
with the clutch X8. That part of the indicator arm X" which is adjacent to the
separator slide E, when the latter is in its lowest position, is cut away so as to
allow the indicator arm to swing toward the right from the position shown in
Figure 3, allowing the clutch X7 to be disengaged from the clutch X8 by the action

page_text: of the spring X 18. Thus the clutches are held in engagement whenever the
separator slide is raised above its lowest position by an advancing line, and are
allowed to disengage only when the slide is in its lowest position, or in other words,
when no line is brought within the range of operation of the machine. By a com-
parison of this description with that of the operation of the line grab it will be
understood that whenever a line has been brought within the range of operation
of the separators, it will be engaged by the line grab and carried up into the
measuring plane, and that the measuring devices being actuated by the cam upon the
shaft X3, will also be put in operation because of the engagement of the clutches X7
and X8.
The clutch X8 is provided with a flange in which is located a slot or recess X20,
shown in Figure 47, that slot being large enough to allow of the entrance therein
of the stop arm X1. The remaining unnotched portion of the flange of the
clutch X operates through the arm X to hold the clutches in engagement until
the clutch, and hence the shaft X³, has completed its rotation, even though the
indicator arm X1 should fail to so hold them by reason of the absence of a line,
as previously described. In such a case, the spring X18 will press the arm X19
against the periphery of the flange of the clutch X8 until the latter reaches that
part of its rotation shown in Figure 47, bringing the notch X 20 opposite to the
arm X, which therefore enters the notch and allows the clutch to be released,
and also serves to hold the shaft X3 and its mechanism in a certain definite position,
it being desirable that all of the devices actuated by the cams upon this shaft
should occupy the same definite position when at rest.
A brief description will now be given of the complete operation of the entire
machine under normal conditions in which there is no interruption in the con-
tinuity of the advancing line of type, so that by the time the apparatus has com-
pleted that line, the succeeding line is in position to be carried up by the line
grab. Under these circumstances the indicator arm X" is constantly held in the
position shown in Figures 3 and 5, thus operating through the bell crank X16 and
the clutch fork X13 to hold the clutch X' into engagement with the clutch X³, and
keeping the shafts X2 and X³ clutched together. While waiting for a line the
governor is released and resting in the position shown in Figures 35 and 40, the
measured beam being in its horizontal position shown in Figure 1, so that
the setting racks rest in their lowest position.
The position at which the line grab rests with its new line while waiting for
the completion of the justification of the previous line is preferably just below
the measuring zone, so that the leading end of the new line carried by it shall
rest just below the star wheels H8 and 1°. The first movement, therefore, of the
line grab upon the completion of the previous line is to carry the new line into
the measuring zone, moving the star wheels as the separators pass by, so that their
respective mechanisms are moved to the proper position corresponding to the
number of separators contained in the line. The line is raised by the line grab
high enough to enable the measuring pawl G³ to engage beneath and support the
line. The stepped jaw I, having been set in the manner already described by
means of its star wheel I', now rests with its proper step in position to be engaged
by the upper end of the line, while the fulcrum having been moved to its proper
point by the joint operation of its star wheel H8, and its cam H7, stands in proper
relation to the beam. At the same time the selector crosshead N is raised to its
uppermost position by means of its cam N13 so as to hold the latches N2 and P1
out of the path of movement of their racks, as shown in Figures 19 and 21.
The measuring operation now commences. The line engaging end of the beam
is moved upward by means of its cam G9 until its upward movement is arrested by
the closing up of the line between the pawl G3 and the proper step of the jaw I,
the cam G being enabled to complete its full stroke by the yielding of the
spring G6, as previously described. The upward movement of the beam, multi-
plied to its proper ratio by the position of the fulcrum, operates to lift the setting
racks to their required position, where they are retained by their detent N'. At

page_text: this time the selector crosshead is allowed by its cam N13 to be lowered so that its
latch N rests against whichever one of the steps N3, N4 or No of the setting rack G17
may have been brought within its zone of action by the measuring operation. At
the same time the correcting slide P descends to a point where its latch P₁ is sup-
ported by one of the corresponding steps of the setting rack G18, and the spacer
selecting mechanism being thus set to the position required by the measurement
of the line, is ready to co-operate with the other mechanism to eject, assemble and
inject the proper spacers or spacer combinations, and to extract the word separators.
The line separator of each line is extracted by the operation of the cam Q, during
the operation of the measuring devices upon the succeeding line.
During this time also the stop S16 has been raised to its proper height by the
operation of the star wheel H³ so as to engage the proper step of the governor
flange S6, corresponding to the number of spaces in the line to be justified, and
that step of the flange has been brought against the stop by the action of its
weight upon being released from the detent S13 by means of the step S20 of the
governor cam $19.
At the conclusion of the measuring operation the selector cross-
head and the correcting slide having come to their proper positions, the clutch Y,
on the shaft Y2, is brought into engagement with the clutch Y5 by the operation
of the step SI, thus serving to set in motion the word shaft mechanism. The same
movement of the rod S which starts the shaft Y also serves to release the
pawl S7 which drops into engagement with the ratchet S3 simultaneously with the
starting of the word shaft Y2, and the word mechanism being thus set in motion
operates to eject, assemble and inject the spacers or spacer combinations determined
by the position and operation of the selecting and correcting devices, repeating
its operation for each of the spaces in the line, under the control of the governor
devices, which hold the clutch Y in engagement until it has made the proper
number of revolutions sufficient to bring the controller S³ to the position shown
in Figure 40, at which time the pin S29 in the flange St will have come in contact
with the spur S28, and moved the clutch Y6 out of engagement by means of the
clutch fork S30 so as to allow the word shaft Y2 and the word mechanism actuated
thereby to come to rest. At the same time the pin X1, fixed in the flange $5, will
have been brought against the fork X9 so as to keep the clutch X³ in engagement
with the clutch X6, and thereby continue the rotary motion of the sections X³
and X3 of the line shaft, thereby bringing up and measuring another line, repeat-
ing the operation as long as there is a line within the range of action of the indi-
cator arm X17.
If no line has been brought within the range of action of the indicator arm X",
that arm being unsupported, will oscillate toward the right from the position
shown in Figure 3, thereby allowing the clutch X to be disengaged from its
mate X8 when the latter has reached that point in its rotation represented in
Figure 47, at which the notch X20 in the flange of the clutch is brought opposite
to the arm X, which then enters the notch, serving then to hold the clutch, and
hence the mechanism carried by the shaft X³, in a fixed position until again
released by the operation of another line upon the indicator arm X".
At the conclusion of the justification of each line the selecting and correcting
devices remain in the position at which they stood at the time of justifying the
last space in the completed line, and these devices remain in that position until
the commencement of the measuring operation upon the next line, during the
first part of which, as above described, the selecting crosshead N is raised to its
uppermost position by the operation of the cam №13, whereupon the correcting
mechanism is released and allowed to return to its original or starting position,
as explained in the description of the selector correcting mechanism.
The selecting devices herein shown can be operated independently of the cor-
recting devices, which are in the nature of an auxiliary device thereto.
The measuring beam is herein shown as being a compound structure consisting
of the two principal members G and G16, but this is a constructive feature merely,
devised to secure compactness. It is evident that the lever G, if made long enough

page_text: at its left hand end to secure the required multiplication of its movement, would
give precisely the same results, the desired object being to multiply the deficiency
existing in the measured line to such an extent as to enable the sub-divisions
thereof to be utilized in selecting the proper spacers, inasmuch as the indications
of those deficiencies, if not enlarged, would be too fine to enable mechanism to act
upon them with certainty in the practical operation of the machine.
Although the beam and the secondary lever both turn upon pivots, and their
ends therefore would seem to describe circular arcs from those pivots, yet it will
be observed that all of the measurements communicated through, and multiplied
or otherwise varied by, the measurements of the beam, invariably bear a constant
relation to each other. This is due to the fact that the movements are communi-
cated to, and transmitted from, the beam, upon straight lines which are tangential
to arcs struck from the respective pivots.. In this way the measured deficiency
of the line, and the resultant movement of the racks are to each other as the
altitudes of similar right angled triangles. Inasmuch as the lever G is pivoted
to the measuring slide G2, it follows that that lever G must move toward the right
with relation to its fulcrum block G in moving from the position shown in
Figure 44 to those of Figures 45 and 46, to an extent equalling that by which the
secant exceeds the radius of the arc of its movement.
Many of the features of this invention, and particularly this one of the measur-
ing beam, are capable of a more extended application than is or can be herein
shown. They may be employed, for example, in type writing, type casting,
matrix making and linotype machines, and we desire for those features a pro-
tection commensurate with their novelty and usefulness in this as well as in other
branches of the art to which they may be applicable.
Various mechanical equivalents may obviously be substituted for many of the
devices herein shown and described, and different forms or various applications
of springs may be substituted for those shown without essentially altering the
nature of the function or the practical operation of these parts in their relation
to the general scheme of the machine. For example, the beam may be bell-
cranked in form so as to transmit the measurement of the shortage of the line in
a direction at right angles or at any other angle to its present direction. The
stepped jaw, which is herein shown as being incapable of movement in the direc-
tion of the length of the line, may be incorporated with, or substituted for the
pawl G3, upon the measuring beam. In like manner many of the parts may be
transposed as to position, or direction, or sequence of operation, and many similar
modifications may be made in the various elements, or equivalent elements may
be substituted therefor without departing from the general scope and intent of
this invention.
The operation of the measuring beam may be varied by first moving its type-
engaging end against the line of type to be measured, and then moving the
fulcrum to its desired position, which would, of course, operate to move the selector
setting devices to the same position that would be occupied by them if operated in
the sequence described herein. This transposition of the relative times of move-
ment of the parts may be obtained by suitably changing the form and adjustment
of the cams G and H7, the adjusting quills being rotated to their desired position
in the same manner and at the same time as herein described.
The elevating raceway or table L is utilized in a threefold capacity. It serves
as a support for the basic or A spacers by means of which the desired number of
those spacers are lowered into the position which permits of their being removed
from the channel by the assembling plunger 01; serving them in its second
capacity as a raceway upon which those spacers are moved along to the position
adjacent to the raceway 06, as shown in Figure 30. As the level of the raceway 06
is coincident with that of the lower end of the channel L, it follows that the top
surface of the A spacers thus removed from the channel will also be coincident
with the surface of that raceway, as shown in the latter figure, thus enabling the
spacers B, C or D to slide from their raceway directly upon the A or basic spacers,

page_text: 33
as shown in Figure 31. Immediately following this point in its operation, the
table raceway L¹ serves in its third capacity by the operation of its lifter 0* to
raise the assembled combination of spaces to the level of the injecting plane.
The terms "
space," "separator." and "spacer are herein used advisedly in
order to avoid the confusion of terms and of ideas which otherwise might occur in
referring to the three particular features to which we have applied these designa-
tions. As herein used, the word " space refers to the actual space occurring
between adjacent words, regardless of the object which occupies the space, or
whether it is occupied at all. By the word "separator" we mean the pieces U
and T, which are temporarily placed between the words and the lines respectively
in order to temporarily maintain the separation between them, and by the term
spacer we refer to the final type body which is inserted in each of the spaces
66
"
of a line.
37
By the terms "shortage" or "deficiency" of the line, as herein employed, we
refer to the amount by which the measured line falls short of the required length,
the "shortage" being therefore equal to the aggregate length of the justifying
spacers required to exactly fill out that line, as above explained.
For,convenience and clearness of reference, that part of the governing mechanism
which is herein shown as an integral part, consisting of the flanges S4, S5 and S6,
is herein referred to as the controller.
The governing devices herein shown are capable of application to other machines of
this class, which are either wholly or partly automatic. In the latter case the
releasing devices of the governor may be so connected to the key board of the com-
posing machine as to permit of being released by the operator at the conclusion
of the measurement of each line.
Many of the parts which are herein preferably arranged in pairs for practical
reasons may by suitable modification, and in some instances without any modifica-
tion, be used singly. Among the parts herein shown which may be thus used,
may be enumerated the word and line grab pawls, stop fingers and arms. One of
the detents J might be omitted, the type engaging lip of the other detent being
adapted to extend across the channel far enough to support the separators, but
such a pawl located on one side of the channel, and therefore coming in contact
with one side only of the uppermost piece of type which is being pushed past it,
might be liable occasionally to turn that leading piece upon its side. For safety
and certainty we therefore prefer the double pawls, which react equally upon the
two sides of the type, and do not therefore tend to turn it. This remark would
also apply to the star wheels H8 and I, which are arranged on opposite sides of
the channel so as to simultaneously engage with the opposite ends of the same
separator, and thereby prevent its being tilted. Were it not for this consideration,
the devices which are herein shown to be operated by those two star wheels might
be operated by one of them alone.
Some of the cams of this machine are herein shown with grooves, in which is
located the engaging pin of the connection or part to be operated, the two sides of
the grooves serving therefore to positively control the operation of the connected
part in both of its movable directions. Other cams are shown without such a
closed groove, the engaging pin being held against the surface of the cam by
means of a spring or weight. These two well-known forms of cams are considered
by us to be equivalent constructions, the spring or the weight used in connection
with the so-called open cam serving as the equivalent of one of the sides of the
grooves of the closed cam. Both kinds of cams are shown herein in accordance
with our preferences under the conditions controlling each cam operated device.
-The fulcrum setting device herein shown may be modified by dispensing with
one of the quills, a spring or weight being employed to bring the fulcrum back
against the step of the slide which has been previously moved to determine the
position of the fulcrum, but we prefer to employ the two quills, as herein shown,
inasmuch as we thereby provide a more positive means of operating the devices.
We therefore do not desire to be limited in our claims to the employment of this

page_text: double form of stepped quill, excepting so far as that construction is specifically
claimed herein.
PHILLIPS & LEIGH,
Agents for the Applicants.
Improvements in and connected with the Justification of Type, Type
Dies, or Type Matrices.
I, WILLIAM HENRY LOCK, of No. 188, Fleet Street, in the City of London,
Manager and Secretary of the Linotype Company, Limited, do hereby declare the
nature of this invention (a communication to me from The Thorne Type-setting
Machine Company, of No. 34, Park Row, New York, a corporation duly organised
under the laws of the State of New Jersey, United States of America), and in
what manner the same is to be performed, to be particularly described and ascer-
tained in and by the following statement:-
This invention relates to improved mechanism for justifying type, type dies,
or type matrices into lines of uniform length, so as to adapt them to be made up
into columns of the desired width.
The machine herein described is the most approved embodiment of this inven-
tion in its application to the justifying of separate type, and it is herein shown
and described as being adapted more particularly for use in connection with that
class of type-setting machines which set the type in a single continuous line.
In the operation of composing this continuous line, it is necessary as a pre-
liminary to the present method of justification, that the type-setting machine
shall contain in its channels, two different kinds of special separators, one of which
is to be inserted between the words which are to form a line, and the other to be
inserted at each point where the continuous line is to be separated. into short
lines proper for being arranged in column form. These special separators may
be arranged, each kind in its own particular channel, and may be released there-
form and assembled in proper relation to the character type, by means of special
keys to be touched at the proper time by the operator; the key for the word
separator being touched at the end of each word, excepting only as to those words
which are to come at the end of the short or column lines. After each of these
final words, one of the line separators may be inserted, the operator being governed
in the determination of the location of these final words of the intended line, by
means of any suitable indicator or scale.
Various forms of these separators may be employed for thus temporarily pre-
serving the separations between the words until they are replaced by the final
justifying spacers; and for indicating the points in the continuous line where it
is to be separated to form column lines.
The special separators herein employed, differ from each other in the par-
ticular that the line separator is slightly longer than the word separator, and
both are slightly longer than the character type with which they are employed.
It is considered desirable to preface the detailed description of the machine,
by a brief explanation of the method or system upon which the devices operate.
The continuous line of type is fed into the machine of the present invention,
through a type channel which retains the type in line, allowing the two kinds
of separators to project from the edges thereof, the ends of the line separators
projecting slightly beyond the ends of the word separators. What

page_text: 66
is termed the "line grab," lifts the leading line from the advancing continuous
line by means of the projecting ends of the line separators, which underlies the
line to be separated. That line is carried by the line grab up into what is
termed the " measuring zone," passing, on the way, between two star wheels,
the teeth of which are so disposed as to be engaged by the projecting ends of the
separators as the line is moved past. Those separators thus operate as a rack
to turn the star wheels to an extent determined by the number of separators in
the line. Arriving in the measuring zone," the leading end of the line is
carried, against the proper step of the stepped jaw of the measuring device. The
line is thus held against this stepped jaw while a pawl attached to the measuring
lever is brought against the opposite or lower end thereof. That lever is sus-
pended upon a fulcrum which is capable of being moved so as to vary the effect
of its measurement of the line in accordance with the number of spaces contained
therein. That end of the lever which is on the other side of the fulcrum from
its measuring pawl end, is connected by means of a secondary lever to the spacer
selecting devices.
The justifying spacers are of four different sizes and are contained in four
channels arranged adjacent to the spacer selecting devices above mentioned,
which, governed by the amount of movement communicated to them from the
measuring lever, operate to select from the justifying spacer channels, the proper
sizes and combinations of spacers required to justify the line being operated upon.
The spacer or combination of spacers required to justify one of the spaces of the
line, are ejected from their channels into a raceway; and are assembled at a point
therein called the injecting plane which is located immediately above the
measuring zone. After the line is released from engagement with the measuring
devices, each word is carried forward by means of a word grab which engages with
its underlying word separator. The word grab lifts each word separator high
enough to carry the character type composing the word lying above that separator
into the galley, where the character type are retained, the word separator itself
being allowed to drop back with the returning motion of the word grab as far as
the plane in which its corresponding justifying spacer or combination of spacers
is located. This plane is called the injecting plane because of the fact that
justifying spacers are here injected into the line at one side thereof, the corres-
ponding word separator being ejected therefrom into its proper channel on the
other side of the line.
The word grab, the spacer selecting and assembling devices, and the word
spacer ejector, repeat their operation for each one of the spaces in the line to be
filled, the number of times these operations have to be repeated being predeter-
mined by governor devices operated upon by the star wheels above described as
having been actuated by the projecting ends of the separators in the line as it
is moved up to the measuring zone by means of the line grab. The movement
thus imparted to these star wheels also operates through one of them to determine
the point to which the moveable fulcrum of the measuring lever is to be moved.
and through the other star wheel to determine which step of the stepped jaw shall
be employed for that particular line, it being, of course, understood that the
position of the fulcrum and the height of the jaw to be used, is related to and
dependent upon the number of spaces contained in the line to be measured at
that particular setting.
The 22 sheets of drawings filed with the Provisional Specification and the 4
further sheets filed herewith are to be taken as part of this specification and read
therewith. Of them,
Figure 1, Sheet 1, represents a general front elevation of the right hand portion
of the machine, which is therein shown to be in the position occupied by it after
a line has been carried by the line grab into the measuring zone.
Figure 2, Sheet 2, is also a front elevation showing that portion of the machine
which lies at the left of the portion shown in Figure 1, it being deemed advisable
to thus extend this view over two sheets in order to draw it on a scale large

page_text: enough to be readable. The line on which these views should be joined is indi-
cated on each of these figures by the letters -—2.
Figure 3, Sheet 3, is a general end elevation of the machine, looking from the
right hand side of Figure 1.
Figure A, Sheet 4, is also a general end elevation, looking from the left hand
side of Figure 2, some of the wheels being partially broken away to enable the
mechanism behind them to appear more clearly.
Figure 5, Sheet 5, is a plan view in section taken on the line 5-5 of Figure 1.
Figure 6, Sheet 6, is a plan view in section taken on the line 6-6 of Figure 2,
that line being an extension of the line 5-5 of Figure 1.
Figure 7, Sheet 2, is a plan view of that portion of the mechanism shown in
Figure 2, to which it is immediately adjacent, and from which its lines are pro-
jected.
Figure 8, Sheet 7, is a front elevation partly in section in places where the
mechanism therein contained may thus more clearly be shown. This view corres-
ponds to what is shown at the right hand side of Figure 1, excepting as regards
the sectional parts, as above noted, and is drawn to a scale twice the size of that
employed in Figure 1.
Figure 8, Sheet 23, is a side elevation of the slide G³ and portions of its guide
rods g.
Figure 8, Sheet 24, is a front elevation, and Figure 8°, a side elevation, both
on an enlarged scale of the same slide.
Figure 9, Sheet 8, is an end view partly in section taken on the line 9-9 of
Figure 8.
Figure 10, Sheet 9, is a plan view in section taken on the line 10-10 of
Figures 8 and 22.
Figure 11, Sheet' 9, is a plan view in section taken on the line 11-11 of
Figure 8, and which line is herein referred to as the datum line of the measuring
zone. The word grab is shown in this view, being supposed to be at the bottom
of its stroke, although its proper position in Figure 8 is about half way of its
stroke.
Figure 12, Sheet 9, is a plan view in section taken on the line 12-12 of
Figure 8.
Figure 12, Sheet 23, is a perspective view of the lifting pawl F³.
Figure 12, Sheet 24, is an oblique front elevation, and Figure 12º, a side eleva-
tion corresponding therewith, of the same pawl, only slightly varied in form.
Figure 13, Sheet 9, is an end elevation projected from Figure 11, of the parts
shown in the latter figure.
Figure 14, Sheet 10, is a front elevation, and Figure 15 a plan view, drawn to an
enlarged scale, of the devices for determining the position of the movable fulcrum,
and for moving the latter to that position, these devices being herein shown at the
end of their stroke, opposite to that at which they are shown in Figures 1 and 2.
Figure 16, Sheet 11, is a side view of what is shown in Figure 14, looking from
the left hand side of the latter figure.
Figure 17, Sheet 11, is a similar view, excepting that it is taken in section on
the line 17-17 of Figure 14.
Figure 18, Sheet 12, is a front view, and Figure 19 is an end view looking from
the left hand side of Figure 18, of that part of the machine which is most inti-
mately concerned in the selection of the proper justifying spacers.
Figure 19, Sheet 25, is a rear elevation on an enlarged scale, taken on the
line 20-20 of Figure 21, and shewing the carriage M at the end of its stroke
opposite to that in which it is shewn in Figure 20.
Figure 19, Sheet 25, is an end view projected from Figure 19* and shewing
the selector N15 in engaging relation to the uppermost ejecting levers.
Figure 20, Sheet 13, is a rear view partly in section, taken on the line 20-20
of Figure 21.

page_text: Figure 21 is an end view in section taken on the line 21-21 of Figures 18, 20
and 22.
Figure 22, Sheet 14, is a plan view of the mechanism shown in the four pre-
ceding figures, portions of the frame work having been broken away as shown in
section, to enable the more important mechanism to be clearly seen.
Figure 22, Sheet 26, is a plan view shewing the crosshead N, the selector N15,
the finger M8, the carriage M, the ejecting lever M23 and the space D in the position
which they occupy before displacement by the carriage M.
Figure 22, Sheet 26, is a plan view shewing the parts of Figure 22 in the
position which they occupy after displacement by the carriage M, with the result-
ant ejection of the spacer D.
Figure 23, Sheet 15, is an elevation taken from the rearward side of the
machine, of portions of the mechanism employed in the selecting, ejecting and
assembling of the basic justifying spacers A.
?.
Figures 24, 25, 26 and 27 of Sheet 16 show some of the details on an enlarged
scale of devices connected with the justifying spacer selecting mechanism, and
more especially that particular part thereof which is hereinafter referred to as
the correcting device.
Figure 24, Sheet 24, is a rear elevation supplementary to Figure 20. In it,
the crosshead N is in its highest position and the slide N16 has not been raised by
the pawl P8; when it is so raised by the action of the carriage M, the selector Nis
will still be in position to engage the finger M8.
Figure 24, Sheet 24, is a plan of the crosshead N, the selector N15, the finger MB
and adjacent parts, before displacement by the carriage M.
Figure 24, Sheet 24, is a side elevation as Figure 59, but omitting certain
parts to illustrate the action of the correcting lever 1 and correcting lever hub P³
of the selector correcting mechanism.
Figure 24º, Sheet 24, is a plan similar to Figure 60, illustrating the position
of the same parts after their displacement by the carriage M.
Figure 27, Sheet 23, is a front view, on an enlarged scale, of the parts shewn
in Figure 24, shewing them in a position in which the selector slide is released
from the engagement of the pawl P8 and the detent P2, and has fallen nearly to
its lowest position.
Figure 27, Sheet 24, is a front elevation of the selector slide N16, shewing the
stop P⁹ on the escapement wheel P18.
Figures 28, 29, 30 and 31 of Sheet 17 are front views of the devices for ejecting
and assembling what are hereinafter termed the basic spacers of this system, the
parts being shown in these views in four different positions during their operation.
Figure 32, Sheet 18, is a diagram representing a flat development of the cir-
cumference of what are hereinafter designated as the fulcrum setting quills.
The open or extended position of the quills, in which they are shown in Figure 1,
is herein represented by full lines, while the closed position, in which they are
shown in Figures 14 and 15, is represented by dotted lines.
Figure 33, Sheet 18, is a longitudinal section taken through the centre of the
quills, showing their relation to each other and to the shaft, on which they are
adapted to slide.
Figure 34, Sheet 19, is an end elevation, partly in section taken on the
line 34 34 of Figures 2 and 6, looking toward the left, showing the governor
mechanism for controlling the number of times the word mechanism must repeat
its operation in order to justify all of the spaces in a given line.
Figure 34, Sheet 23 is a side elevation, and Figure 34%, Sheet 24, a front
elevation, of the ratchet S².
Figure 34°, Sheet 23, is a side elevation of the stop S16.
Figure 34, Sheet 24, is a side elevation of the stop S16 and stepped disc So with
parts of the clutch controller S3 and the shaft S¹.
Figure 35, Sheet 19, is a front view of some of the details of the governor
mechanism in section taken on the line 35-35 of Figure 34.

page_text: Figure 36, Sheet 19, is a similar view of other of those details in section taken
on the line 36-36 of Figure 34.
Figure 36, Sheet 19, is an end projection from Figure 36.
Figure 37, Sheet 20, is a front view in section taken on the line 37-37 of
Figure 6.
Figure 38, Sheet 20, is a plan view in section taken on the line 38-38 of
Figure 37.
Figure 39, Sheet 20, is an edge view in vertical section taken through the centre
of the governor shaft in Figure 40, looking toward the right in that figure, and
Figure 40, Sheet 20, is a front view of details of the governor mechanism in
section taken on the line 40-40 of Figure 6.
Figure 41, Sheet 20, is a plan view of other details of the governor mechanism.
Figure 42, Sheet 20, is a vertical section taken through the centres of Figure 40,
looking toward the left in that figure.
Figure 43, Sheet 19, is a table representing the system of spacer combinations,
the first vertical column thereof being a representation of the progressive com-
binations of type; the second vertical column being descriptive of the combination
in terms of the four lettered sizes of spacers, while the third column expresses
the size of each space combination in fractional parts of the em of the font
employed.
Figures 44, 45 and 46, Sheet 21, are diagrammatic front elevations represent-
ing the devices employed in the measurement of the lines under three different
conditions. In Figure 44 the parts are shown in their inoperative position. In
Figure 45 they are shown in engagement with a line of type having but a single
space to be justified, and in Figure 46 the parts are shown in the position occupied
by them while measuring a line having ten spaces to be justified.
Figure 47, Sheet 18, is an end elevation in section taken on the line 47-47 of
Figure 6, looking toward the right hand in that figure.
Figures 48, 49, and 50; Sheet 22, are views representing devices for pushing
the justifying line into the receiving galley, Figures 48 and 49 being plan views
of those devices shown in their two extreme positions respectively, while Figure 50
is a front elevation of the same parts on the extreme opposite position to that in
which they are represented in Figure 1.
Figure 51, Sheet 18, is a rear view of what is shown in Figure 47, showing the
position and relation of the steps of the governor cam.
Figure 52, Sheet 2, is a fragmentary plan view showing in detail the con-
struction and arrangement of the clutch X5.
Figure 53, Sheet 3, is a fragmentary rear view projected from Figure 3, and
showing in detail the arrangement of portions of the mechanism of that figure.
Figure 54, Sheet 9, is an isometric view of a fragmentary portion of the type
channel, showing a word separator and a line separator in connection with some
character type.
The interrelation of the parts of the machine is such that it is difficult to give
a strictly consecutive description of them in the order in which the several opera-
tions are performed, for in the description of one section of the mechanism, it
often happens that reference must be made to other sections still undescribed
up to that point; in which case the reader is referred to the paragraph descriptive
of that section. The herein assumed division of the machine into the four main
divisions and the subdivision of the latter into sections, is to a large extent
arbitrary, since many of the combinations set forth and claimed are comprised
in more than one section.
The machine will therefore be herein considered under three general divisions,
the first of which for convenience I will term the line mechanism. This com-
prises all those parts which are principally concerned in the manipulation of the
lines, as such; and most or all of which, perform their complete function once
for each line justified. The second general division of the machine is designated
as the word mechanism. It comprises those devices which are principally con-
F

page_text: cerned in the manipulation of the words, and the spacers which are to go between
those words.. Most or all of these devices perform their complete function or
cycle of movement once for each space between the words contained in the line
justified. The third general division of the machine comprises the governing
and actuating mechanism, most of which is located below the lines 5-5 and 6-6
of Figures and 2.
The first two general divisions are herein considered as being further sub-
divided into sections, such subdivision being made with reference to the particular
function or functions performed by each, and the name herein given to each
section being, as far as possible, suggestive of its function. It will of course be
understood that each of these sections, in addition to performing its own particular
function, also performs its share of other functions common to two or more
sections. The following description will take up these sections as far as possible
in their natural and logical sequence; each under its own heading.
The line mechanism division is subdivided into the following sections:--
Line grab mechanism,
Measuring mechanism,
Fulcrum adjusting mechanism,
Stepped jaw adjusting mechanism, and
Galley mechanism.
The word mechanism division is subdivided into the following sections:-
Word grab mechanism,
Spacer selecting and ejecting mechanism,
Selector correcting mechanism,
Spacer assembling mechanism.
Separator extracting mechanism, and
Spacer injecting mechanism.
Only that portion of the frame W of the machine, which is most intimately
connected with the devices of this invention is herein shown, it being understood
that that frame is intended to be supported on, or incorporated with, the general
frame of the particular form of type composing machine with which it is to be
employed. In connection with the above mentioned division of the devices of
the machine into three general divisions, it may here be noted that those devices
contained in the line mechanism are nearly, if not quite, all connected with, and
receive their motion from, the shaft X, which is therefore designated by me
the line shaft, while those devices included in the word mechanism, receive their
motion from the word shaft Y.
Line Grab Mechanism:-This is shown in Figures 1, 3, 5, 8, 8, 8, 8, 9, 12,
12, 12, and 12°. Its function is to detach the leading line of type from the
oncoming continuous line from the type composing machine, and to carry it for-
ward into what is termed by me the "measuring zone "of the justifying machine,
which is that portion located above the datum line 11-11 of Figure 8, and between
the stepped and the movable jaws of the measuring devices. The line grab con-
sists of two principal combinations of parts, the line separator and the carrier.
The line separator consists of a slide E fitting loosely upon rods e, e, which are
fixed by their ends to the frame W; stop arms E³, E+, pivotted upon the said slide E
at E1, E2, respectively; and fingers E5, E6, also loosely mounted upon the same
pivots respectively. These arms and fingers are arranged in pairs upon the
opposite edges of the type channel V, the extreme upper ends of each pair being
located adjacent to each other, and just within the paths traversed by the
respective ends of the special line separators T; lying, however, outside of the
paths of travel of the special word separators U. The normal positions of these
pairs of stop arms and fingers with relation to the type channel V is best delineated
in Figure 9, wherein they are shown to be in engagement with the ends of one
of the special line separators T. The arms E³, E and the fingers E5, E6, are
moved upward by means of the advancing line of type until disengaged therefrom
on arriving at the upper end of their permitted movement, at which point the

page_text: grooves E and Es curve outward, and open the arms E³ and E. At the same
time the cranked outer ends of the stop fingers E and E are brought in contact
with the pins E1 and E2, by means of which those fingers are also moved out-
side of the path of the line separators T, and at the same time are moved out of
engagement with the carrier, which will next be described. The extent of oscil-
latory movement of the stop arms E3 and E is regulated by means of pins which
extend therefrom into the grooves E7 and E8, best seen in Figure 9, the fingers E5
and E6 being therein shown in their innermost position, toward which they are
urged by their respective springs E9 and E, respectively.
Fis the slide of the above mentioned carrier F. It is loosely fitted upon the
rods f, f, and is connected by means of the link F', arm F, shaft F³, and con-
necting rod, to the crank F5, by means of which it is caused to reciprocate
vertically upon the rods f, f, from its extreme upward position, shown in Figure 3,
to the lower end of those rods as they appear in that figure. Upon the slide F
there is pivotted the lifting pawl F, which is bifurcated to enable it to pass by
the measuring pawl G described further on. That lifting pawl is urged by the
spring F8 against a stop, into the position shown in Figure 8, so as to enable its
engaging end to pass under the line separator T, when that separator is lifted
from the rest of the continuous line by means of the line separator just described.
The inclined projections F and F of the slide F, are adapted to engage with the
projections E, E¼ of the stop fingers E and E6, as shown in Figures 8 and 9,
the engaging surfaces of the projections F and F10 describing an arc struck from
the centres of the pivots of the respective stop fingers E5, E6, when in the position
shown in Figure 9; or those surfaces may be made normal to those pivots, the
object being to enable the projections F and F10 to engage with the projec-
tions E13, E, of the fingers E5, E6, respectively, and to thereby lift up the line
separator, which, in turn, engaging with the ends of the line separator T, lifts
that separator so as to allow the carrier pawl F7 to engage beneath it. Having
thus obtained positive engagement with the separated line of type the carrier
slide F is moved upward by means of its crank F5, being freed from the line
separator when the latter reaches the upper limit of its stroke, as set forth in the
above description thereof. Thus released from the separated line which is being
moved up by the line carrier, the line separator drops by gravity, aided, if
necessary, by a light spring, until the engaging ends of the stop arms E3, E,
collide with the ends of the next advancing line separator T, by means of which
the separator is again moved upward until upon the return stroke of the line
carrier, it is again engaged thereby. The function of the line carrier is to carry
the line of type thus separated from the advancing continuous line up into the
measuring zone," to a point where the underside of the line may be engaged
by the measuring pawl G³, as shown in Figure 8.
Measuring Mechanism: A comprehension of the general principles upon which
this mechanism operates may best be gained by reference to, the diagrams shown
in Figures 44, 45 and 46. The details of its construction are more clearly shown
in Figures 1, 2, 8, 11, 12 to 12°, 14, 16 and 17. The principal member thereof is
the measuring lever G, which is attached by means of the pivot G to the slide G²,
fitted to slide vertically on the rods g, g, which are attached at their ends to the
frame W of the machine. The slide G2 is provided with an extension adjacent
to the type channel upon which is pivotted the measuring pawl G³, best seen in
Figure 8. That pawl is normally pressed by the spring G4 toward the position
shown in that figure, so as to cause it to enter beneath the line of type when the
latter has been lifted up to its position by the line grab.
Into the lower end of the slide G2, is fitted the telescoping yoke G³, which, by
means of the spring. G", is normally pressed outward to the fullest extent against
a stop pin, as shown in Figure 8. This yoke G5 is also guided by means of pro-
jections thereon engaging the rod G7, and it is provided with a cam pin Gs,
adapted to engage with the cam G, fixed upon the line shaft X. The cam Gº is
so formed as to move the yoke G³ upward to an extent equal to the greatest

page_text: deficiency that can occur in any of the lines of type to be measured, and the yoke
is therefore necessarily moved upward to that extent for every line at each of
the intermittent rotations of the shaft X. The elastic nature of the connection
between the slide G2 and its yoke, is for the purpose of permitting the cam Go to
complete its stroke after the upward movement of the measuring slide has been
stopped by the line of type being measured, the mechanism being thus adapted
to accommodate itself to the variations which occur in the lines.
The measuring lever G, which is connected by means of the pivot pin G', to
the slide G2, is an extended member, of the form shown in cross section in
Figure 17, having a T-slot extending along and opening out of its front surface.
A corresponding T-shaped block G-Figure 16-is fitted in the slot and is
capable of being moved the entire length thereof. The block G10 is also pro-
vided with a cylindrical extension which has a bearing in the fulcrum block G",
being secured thereto by means of a nut and washer, as shown in Figures 16
and 17, forming a closely fitting pivotal connection between that block and the
measuring lever G. The fulcrum block G" is fitted to slide in ways in the frame W
of the machine, so as to enable the pivot of the measuring lever to be moved to
its several required positions by means of the fulcrum adjusting mechanism to
be hereinafter described.
The extreme left hand end of the lever G, as seen in Figures 14 and 15, is
bifurcated in order to receive a T-shaped block G2, similar to Go, excepting
that it is faced in the opposite direction, and has its cylindrical portion journalled
in the rectangular part of the rod G3, which is fitted at its ends to slide in the
frame W. Beyond the guide rod G13, the cylindrical portion of the block G2 is
provided with a roller G, held in place by means of a washer and split pin, as
shown in Figure 16. Upon the frame W at G15, is pivotted the secondary lever G16,
the shorter end of which is adapted to engage with the roller G, by means of
which the movements of the lever G are communicated to the said secondary
lever. That lever is connected at its longer end to the selector setting racks Giz
and G8 Figure 1-the arrangement and function of which will be described
in connection with the spacer selecting mechanism, it being understood that
the upward movements of the right hand end of the measuring lever G during
the measuring operation from the position shown in Figure 44 to those shown in
Figures 45 and 46, produce a co-related upward movement of the selector setting
racks G17 and G18.
The relation of the movement of the racks to that of the measuring pawl end
of the lever G, as that relation is varied by the position of the fulcrum block G",
will best be seen by the diagrammatic views comprised in Figures 44, 45 and 46,
and in this connection it is deemed desirable to give a more extended explanation
of the system of measurement herein employed by me, that explanation being
an almost necessary preface to the descriptions of the fulcrum adjusting mechan-
ism and the stepped jaw adjusting mechanism, which are logically next in order.
For the purpose of determining the size of the spacer or combination of spacers
to be inserted in the spaces which occur between the words of a line, it is neces-
sary first to ascertain the net deficiency of the line to be justified, or in other
words, to ascertain what aggregate thickness of spacer type must be added to
the character type contained in that line to fill it out to the desired length, and
secondly, to divide that aggregate thickness into the number of spaces which
occur in the line, in order that the spacers representing the size determined by
this division shall, when all are inserted in their respective spaces, exactly fill
out or justify the line.
The first requirement is to eliminate from the problem, the measurement of
the special separators U and T which, as above described, have been inserted in
the line in the operation of composing for the purpose of locating the divisions
between the words and the lines respectively. As a means of effecting this
elimination, one of the jaws of the measuring device is formed with a series of
steps on its type-engaging face, the height of each of these steps being exactly

page_text: equal to the thickness of one of the special separators employed: In the diagrams
represented in the last named figures, the lines ii, indicate that step of the
jaw I which should be employed if there were no separators to be eliminated
from the measurement. In Figure 45, the devices are shown in engagement
with a line of two words, there being, therefore, a single word separator U, and
at the bottom the inevitable line separator T, The presence of these two separators
requires for the correct elimination of the thickness represented by them, the
employment of the second step of the jaw I above the step indicated by the line i―i.
Figure 45 illustrates the minimum requirement of the machine, inasmuch as it
is always necessary to have at least one space between the words for the purpose
of justification, and when a single word occurs in the line, as, for instance, at the
end of a paragraph, it is necessary to fill out the line with quads, between which
it is advisable to insert a number of word separators so as to allow greater range
in the subsequent operation of justifying. An illustration of the opposite or
maximum capacity of the machine, as herein organized, is represented in Figure 46,
wherein the devices are shown in engagement with a line containing
eleven words, and having therefore ten word separators, and the usual
line separator at the bottom. In order to eliminate the measurement
of these eleven separators from the line, the jaw I is drawn toward
the left so as to allow the line of type to engage with the eleventh step above
the plane, thus eliminating from the measurement of that line the space
represented by the thickness of the eleven.separators contained therein, and allow-
ing of a movement of the measuring lever G exactly equal to that which it would
have in measuring a line composed only of the character type contained in the line.
The mechanism by means of which the jaw I is moved to its correct position for
each line to be measured will be described under the heading of the stepped jaw
adjusting mechanism.
Having thus provided for the elimination from the measured line, of all except-
ing the character type therein contained, it is necessary to divide the net deficiency
thus determined into the number represented by the spaces between the words.
The normal position of the measuring lever G is horizontal, as shown in Figure 44,
and in that position, the engaging surface of its measuring pawl G3 stands coin-
cident with the datum line 11-11 at a distance from the plane ii of the stepped
jaw I equal to the full column width, or in other words, to the desired length
of the justified line. It will, therefore, be seen that the extent of upward move-
ment of the measuring end of the beam from the horizontal or datum line position
shown in Figure 44, will be exactly equal to the deficiency of the line, represent-
ing, therefore, the aggregate set-wise measurement of the spacers required to
fully justify the line.
For greater convenience and definiteness, I have herein shown the limit of
justifying capacity of this machine to be equal to a printer's em at each space
between words, as shown in Figure 43. There is, however, nothing in the nature
of the machine to limit it to this capacity, it being capable of extension to any
amount required in practice. In Figures 45 and 46, this assumed maximum
of one em deficiency is supposed to exist in each of the spaces between words
therein occurring. Therefore, it will be observed that the secondary lever G16
occupies the same position in both figures, although the upward movement of
the pawl G3 is eleven times as great in Figure 46 as in Figure 45. This differ-.
ence in the relative movements of the lever G and of the secondary lever G16 is
determined by the location of the fulcrum block G", which, in Figure 45 occupies
such a position as to cause the movement due to a deficiency of one em, to impart
to the secondary lever G16 and to its selector setting racks, an amount of move-
ment equal to that imparted to them by the movement due to a deficiency of
eleven ems in Figure 46, it being obviously necessary that the selector setting
racks, which determine merely the size of the spacer or spacers to be selected,
shall be set to the amount called for by each space, without regard to the number
of those spaces.
'

page_text: Having thus described the effect of the changes in position of the fulcrum, a
brief description will next be given of the operation of the measuring mechanism.
The line having been carried up by the line grab so that its line separator T
rests on the pawl G³; the cam G-Figure 8-acting through the yoke G5, carries
the pawl G³ upward until the latter is stopped by the closing up of the line against
the proper step of the jaw I, thus determining the movement of the lever G.
The cam G completes its rotation, bringing the lever back to the horizontal
position shown in Figure 8.
Fulcrum Adjusting Mechanism:-This comprises means for moving the ful-
crum block G of the measuring lever G to the proper point thereon for the pur-
pose indicated above. A comparison of Figures 45 and 46, will show the extreme
movement required of the fulcrum, it being understood that the position occupied
by it, is governed by the number of spaces in a line to be measured, and that
the fulcrum may therefore require to be moved to any one of ten positions, some-
times one, sometimes five or ten spaces or intervals to the right, or to the left,
as the case may be, from its previous position.
A pin G, best shown in Figure 15, extends from the fulcrum block G" into
the path of the adjusting quills H and H¹. These quills consist of mutilated
cylinders capable of endwise movement to and from each other upon the shaft H³,
to which they are splined. When brought together, their mutilated portions
overlap and match, one another, as shown in Figures 14 and 15, leaving circular
openings along the line of their matching surfaces arranged upon a spiral line
increasing from left to right, as seen in the said figures, being equally spaced
circumferentially around the completed cylinder thus formed by the two quills,
but spaced at varying distances longitudinally thereof, corresponding in this
respect with the different required positions of the fulcrum. A flat development
of the circumferential surfaces of these quills is shown in Figure 32, the full
lines thereof representing their open position, while the dotted lines represent
their closed position. Each of these quills is provided with a loose collar H³,
which collars are engaged by suitable forks on the racks H4, those racks being
connected by means of the pinion H³ so as to impart to the racks and quills
opposite, simultaneous, and equal movement toward and from each other to the
extent indicated in Figure 32, and shown also by a comparison of Figures 1 and 14.
One of the racks H is connected by means of an arm He to the cam H7 on the
line shaft X, and that cam is so formed as to communicate to the quills, suitable
longitudinal movements at the proper times.
The quills H and H are adjusted circularly to their proper position for each
line, by means of the star wheel H8, fixed on the shaft H2-Figures 9, 14 and 15.
This pinion is located adjacent to the type channel V, as shown in Figure 9, with
its teeth lying in engaging relation to the separators T and U, which operate as
they are carried past the star wheel to turn the latter one tooth for each of such
separators in the line. The shaft H2 is journalled at its right hand end in a
bracket H attached to the frame W of the machine-Figure 1; and
at its left hand end, in the upper end of the governor bracket_h,
as shown in Figure 2. The shaft is also provided with a spring H¹º,
which is preferably in the form of a coiled clock spring, as shown
in Figures 2 and 4. This is so attached to the shaft and to its casing
as to tend to turn the shaft in the direction opposite to that in which it
it turned by the separators T. A ratchet H", shown in Figures 2, 14 and 15,
is fixed to one of the quills, and is engaged by means of a detent H¹² pivotted
upon the rack H adjacent thereto. The function of this ratchet and detent is to
retain the quills, so far as rotary motion is concerned, in the position into which
they are moved by the separators acting upon the star wheel H8.
The operation of these fulcrum adjusting devices is as follows:-
While a line is being carried up by the line grab, the quills are in their
separated position, shown in Figure 1, clear of the fulcrum adjusting pin G9.
The quills are thus left free, and are turned one step for each of the separators U

page_text: and T contained in the line. When that line has been carried past the star
wheel H8, the quills remain in the position to which they have been turned by
the said star wheel, so that when pushed together to the position shown in
Figures 14 and 15, the pin G19 is engaged by the proper notch, and is moved
thereby to its correct position with relation to the lever G, being carried from
the previous position to its new place by the right hand or by the left hand quill,
according as it may require to be moved to the left or to the right respectively.
The quills remain in this position holding the fulcrum block G" in its proper
place while the measuring operation is being performed, when they are again
separated to the position shown in Figures 1 and 2, bringing the lower end of
the detent H2 against a suitable pin in the frame W, which operates to release
the ratchet and allow the shaft H2 and its quills, to be rotated back to their zero
position, by means of the spring H10.
Stepped Jaw Adjusting Mechanism: This is best shown in Figures 1, 8, 9, 10
and 16. The stepped jaw I consists of a piece with parallel flat sides, and is of
a generally rectangular form, excepting as to its front or right hand edge, which,
as shown in Figures 1, 8, 9, and 44 to 46, is formed in steps, each of a height
corresponding to the thickness of the special separators employed in the line of
type, as hereinbefore explained. This jaw is fitted to slide horizontally in the
frame W toward and from the main type channel V, and substantially central
thereof, as shown in Figures 3 and 9, the members which compose the type
channel being slotted so as to allow the jaw to pass transversely across the path
of the type. The jaw is connected by means of the link I¹ to the arm I, which
is pivotted at I³ to a bracket on the frame W, and is provided with a cam pin
adapted to engage with the left side of the cam I on the shaft X-Figure 1.
That cam is not provided with a groove, but is adapted to bear against one side
only of the cam pin of the arm 12, and to move the stepped jaw toward the left
The said jaw is pulled to the right normally, against the action of the cam, by
the spring I. Therefore, would these devices, if unobstructed, carry the stepped
jaw reciprocally from right to left to the extent shown by a comparison of
Figures 45 and 46. But it is necessary to arrest the movement of the stepped
jaw for each line to be measured, at the point adapted to the number of separators
contained in that line, as hereinbefore described. This is accomplished by means
of devices best shown in Figures 8, 9 and 17, consisting of a stop 16, which is
fitted to slide vertically in the frame W, having on its upper end an L-shaped
portion projecting into the path of the jaw I on the stepped end thereof, the other
end being provided with rack teeth which engage with a pinion 17 on the shaft Is,
that shaft being journalled in a bracket attached to or integral with the frame W.
Upon the shaft I, is fixed also the star wheel Iº, best shown in Figure 9, arranged
opposite to the star wheel H8, with its teeth lying in the path of the separators,
so that those separators in passing between the star wheels H8 and 1º, operate
to turn each of them equally; that is to say, to the extent of one tooth for each
separator carried past, the resistance offered by the two wheels being thus adapted
to counteract each other to avoid tilting the type. The movement thus com-
municated to the star wheel I is transmitted to the stepped jaw stop I raising
it one step for each of the separators carried through; therefore, when the entire
line has been carried past the star wheels H8, 19, the upper end of the stop I° stands
in such a relation to the steps of the jaw I as to arrest its movement at the proper
step thereof for the correct measurement of that particular line. The cam I
is so timed as to allow the stepped jaw to be moved toward the right, as shown
in Figure 8, just after the stop 16 has been set to its proper position, as just
described, the said stop operating therefore to arrest the movement of the stepped
jaw at the proper step thereof. The pressure of the jaw I against the stop IG
serves to hold the latter in the position to which it has been elevated by its star
wheel I. After the completion of the measuring operation, the jaw I is moved
back toward the left by its cam I' clear of the type channel V, so as to enable

page_text: the words to be carried up into the galley, while the stop I6, released from the
jaw I, drops to its normal position ready for the next line.
Galley Mechanism:-This is best shown in Figures 8, 9, 48, 49 and 50. It
comprises mechanism adapted to hold a suitable column galley in position, to
receive the justified lines of type from the word grab mechanism, and for push-
ing each line when complete along the column galley so as make room for a new
line to enter.
The column receiving galley J, which may be so attached to the frame W as
to be easily removable therefrom, rests upon its side, and is provided with a
plunger J, fitted to slide into the right hand end thereof to the extent shown
by a comparison of Figures 8 and 50. In the former figure, the plunger is
shown in its open position, which permits of the character type being pushed up
into the galley between the face of the plunger and the rule J2. Upon the
plunger is pivotted a pawl J³, having a T-shaped bell cranked extension best shown
in Figures 8 and 9, adapted to be engaged by the spiral springs J*, by means of
which the pawl is pressed downward to the position shown in Figure 8. In that
position the front face of the pawl is vertical and coincides with the front or left
hand vertical face of the plunger J¹, the lower portion of which is bevelled back-
ward from the general plane of its surface to an extent shown in Figure 8, so
as to allow the type to enter past the corner J. The lower end of the pawl J³
is bevelled at an angle of about forty-five degrees, and the separators U and T
have a corresponding nick in their corners centrally of their length. The
character type forming a word, when carried upwards by means of their underly-.
ing separator, operate to crowd back, the pawl J³ against the pressure of its
springs J, thereby allowing the character type to pass into the galley J until the.
lower edge of the last character type has passed above the corner J5 of the bottom
wall of the galley. The nick in the word separator then permits the pawl to return.
to its normal position, transferring the line of character type slightly to the left,
from the support of the separator to that of the corner J³. The separator is then
allowed to drop to its position shewn in Figure 8, resting on the pair of detents Jo,
the tops of which are pressed together by their springs, as shown in Figures 8
and 50. These detents are pivotted in suitable recesses in the frame W, and are
forced apart by the type passing through, closing behind the separator in order
to form a support for the latter while it is being extracted, and also to form a
support for the justifying spacers which are substituted for the separators. The
spacers thus injected are carried up into the galley on the top of the next word,
this operation being repeated until all the spaces of a line have been justified
and the type carried into the galley.
The galley plunger J¹ is provided at its right hand end with a stem which is
fitted to slide in a hub of the frame W, for the purpose of guiding the plunger in
its longitudinal movement. That movement is imparted to it by means of the
cam J' on the line shaft X, which operates through the cranked arm JB, connecting
rod J⁹ and cranked arm J, to impart a suitable reciprocating motion to the
slide J¹¹, which is splined on the stem of the galley plunger so as to prevent rotary
motion thereon, leaving it free to move longitudinally. That slide is provided
with a bevelled projection J18 adapted to fit against the correspondingly bevelled
end of the pawl J³, when the slide is moved to the left as shown in Figure 50,
thus locking that pawl in the position shown in that figure so as to present a plane
unyielding surface against the line of type, for the purpose of pushing it further
into the galley. Before the line can thus be pushed into the galley, it is evident
that the rule J2 must be withdrawn from between the line last formed and those
which precede it. That rule is made a little longer than the width of the column,
and is fitted to slide in grooves made in the top and bottom walls thereof. It is
pivotted at its front edge to a preferably bifurcated arm J12, which is pivotted
at J13 to an extension of the frame W. That arm is provided with a bell cranked
extension J¹, which is adapted to engage with the pawl J15, as shown in Figures 48
and 49. That pawl is pivotted upon the slide J¹¹, and is normally held in the

page_text: position shown by means of a spring J16. It will be observed that the slide Ju
is required to move some distance on its supporting stem before abutting against
those surfaces thereof, by means of which it moves that plunger forward. This
preliminary movement of the slide J" is utilised to carry the rule J2 out of the way
of the plunger, by means of the pawl J15 engaging with the cranked end J of
the arm J, thus moving it from the position shown in Figure 49 to its fully with-
drawn position shown in Figure 48. The parts are so adapted to each other, that
the slide J is brought against the abutting surface of the plunger J¹, as shown in
Figure 50, so as to move the new line forward to the left just at the time when the
rule is fully withdrawn, as shown in Figure 48, at which time the engaging
pawl J has passed beyond the sweep of the cranked arm J14, allowing the latter
to be returned by its spring, thus bringing the rule behind the new line of type
so as to permit of the return of the plunger. The slide J" is then moved, by means
of its cam,
toward the right against the pin J", thereby moving the plunger back
to its open position, shown in Figures 8 and 49. The spring J16 allows the arm J¹4
to rock the pawl J15 out of its way, as it passes it on the return stroke.
Having thus completed a description of the devices comprising the line mech-
anism, a description will now be given of the devices comprehended under the
general designation of the word mechanism, beginning with the
Word Grab Mechanism : This is best shown in Figures 1, 3, 8,
11, 12, 12, 12", 12°, and 13. In its general construction and mode
of operation, it resembles the devices composing the line grab mech-
anism, differing from those devices chiefly in the respect that the devices
for separating and for carrying the words are embodied in one organization,
instead of being composed of two separable organizations. The slide K is loosely
mounted upon the rods f, f, and is provided with the bifurcated stop finger K¹
pivotted thereon at K2-Figure 8. The bifurcations of this stop finger are upon
opposite sides of the slide K, and their upper extremities extend on either side of
the type channel V into the paths of the respective ends of the word separators U.
One of the bifurcations of the stop finger is provided with a pin K³, which is fitted
in a slot in the guide K, the latter being attached to the frame W. The extent of
oscillatory motion of the finger K₁ is controlled by the form of the groove in the
guide K4, best seen in Figure 8, the stop finger being held in the position shown
in that figure from the lowest point of its vertical motion up to within a short dis-
tance of the upward extremity thereof, at which point the groove is curved so as
to move the stop finger to the right out of the path of the separators. Upon the
slide K, is also mounted the oppositely disposed pair of pawls K, K10. These pawls
are pivotted at K and K respectively, to the slide K; and their upper ends
extend on either side of the type channel V immediately below the corresponding
members of the bifurcated finger K', and at a distance therefrom substantially
equal to the thickness of one of the word separators, as best shown in Figure 8.
The lower ends of the pawls K and K, on the opposite side of their respective
pivots, are provided with the spring K, which operates to press the separator
engaging ends of the pawls toward each other, and toward the type channel.
The slide K is caused to reciprocate vertically upon the rods f, f, by means of
the arm Ko, pivotted at the back of the frame W, as shown in Figure 3, and that
arm is connected by means of the rod K and the rod R2 to the crank pin K' fixed
in the side of the cam M³, on the line shaft Y, as shown in Figure 53, Sheet 3. An
elastic connection between the arm K³ and the rod R2 is formed by the spiral
spring K8 coiled on the rod K. The movement communicated to the slide K by
its crank-pin K' is sufficient to carry the upper or separator engaging portions of
the word pawls K9 and K10 from the lower end of the line of type shown in Figure 8
to, and a little above, the upper surface of the detents Je of the galley mechanism.
While the line is being measured, and while the spacer selecting mechanism is
being set, the word grab rests by means of its bifurcated stop finger K¹ upon the
uppermost of the word separators U contained in the line to be measured, as shown
in Figure 8. As soon as the preliminary operations of measuring, and of setting

page_text: the spacer selecting mechanism have been completed, the word shaft Y-Figure 4
―is put in operation, as hereinafter explained in connection with the governor
mechanism, and the rotary motion thus communicated to the crank pin K7 operates
to carry the word grab to its uppermost position, the pawls K and K carrying
forward the separator, beneath the ends of which they have been resting, up
between and past the detents J. As the slide approaches the upper end of its
stroke, the pin K³, guided by its slot in the guide K4, is moved backward so that its
engaging points are outside of the path of the type separators, which are thus
enabled to pass by the finger. At the beginning of the downward stroke, the finger
returns to within the path of the separators, and is stopped by the next occurring
separator, the pawls K and K dropping into engagement beneath the ends of the
separator as before, ready to elevate it with the character type lying above it into
the galley, as before explained. The yielding connection formed by the spring K8,
between the crank K' and the slide K, allows that crank to make its full downward
stroke, and to pick up the slide when it reaches it on the return stroke. Mean-
while, the separator which has just been left resting upon the detents Jo, has been
extracted therefrom as described further on in connection with the separator
extracting mechanism, and the proper justifying spacers have been substituted
therefor, as explained further on in connection with the spacer injecting mech-
anism. Those spacers are carried up into the galley on the next word, and thus
by the repeated movements of the word grab, each word is elevated from the
measuring plane into the galley.
In Figures 4, 18, 19, 19, 19, 20, 21, 22, 22, 22" 23, 28, 29 and 31, is shown
the devices comprising the Spacer Selecting and Ejecting Mechanism, the Selector
Correcting Mechanism, and the Spacer Assembling and Injecting Mechanisms.
These different mechanisms are so involved and interdependent that their separa-
tion into groups is more difficult and arbitrary than in the case of any of the other
sections of the machine. It is thought advisable to preface the detailed descrip-
tion of these mechanisms by an explanation of the system upon which the spacers
are arranged and combined.
The justifying spacers employed according to the present invention, are four in
number, herein designated as A, B, C and D. (See the table, Figure 43, Sheet 19).
The setwise thickness of the spacer A. is herein assumed to be equal to one-fourth
of the em of the type which is being justified, or in printers' parlance, it is a "4-to-
em space." The other sizes B, C, D are equal respectively to 5/16ths, 3/8ths
andths of an em. The method of combining these spacers so as to satisfy the
varying widths required, is shown in the table, Figure 43 above referred to, to the
extent of one em, it being however, obvious that the combinations can be continued
on the same system to any desired extent. The difference in size between the
spacers A, B, C, 1) is uniformly 16th of an em, and this difference exists also
between the successive combinations formed by those spacers. These combinations
are arranged is series of four, the first series employing the spacers A, B, C, D in
the order given, each of the succeeding series differing from the one preceding
only by the use of an additional A spacer. Thus it will be seen that the
spacers B, C, D) are never combined with each other, and that no more than one
of either of them is ever employed in a combination. On the other hand, the
spacer A is repeated to any extent required to fill out the thickness called for. By
reason of the fact that the A spacer is the smallest employed, and also because it
is thus repeated in the different combinations, I designate it as the basic spacer.
On account of the frequent repetition of this spacer in the combinations, I employ
devices for its selection differing considerably from those employed in the selection
and ejection of the B, C and D spacers, as will be hereinafter described.
On account of their intimate relationship to the spacer combination system, it
is desirable at this point to complete the description of the setting racks G17
and G18, which was begun in connection with the description of the measuring
mechanism, and carried only so far as it pertained to that mechanism. These two
racks are fitted to slide in suitable guides formed by extensions of the frame W,

page_text: as shown in Figures 19 and 22, and are provided on their front surfaces with
ratchet teeth, as shown in Figures 18 and 19. The teeth on the rack Gare
located at a distance apart equal to that by which the racks are elevated by the
measuring mechanism for each deficiency of 16th of an em in each of the spaces
of that line. The teeth on the rack G¹s are much closer together, there being six
of them in the distance which separates two of the teeth of the rack G7, and the
pitch of these fine teeth is therefore equal to one-sixth of that of the rack G17 and
is also equal to the distance the racks are elevated by the measuring mechanism
for each deficiency of th of an em. Upon the frame W at No is the setting
rack detent N7, the nose of which extends across both of the racks G17 and G18, as
shown in Figure 18, being pressed into engagement with those racks by means of
the spring N8, the function of this detent being to engage the setting racks and
retain them in substantially the highest position to which they are carried by the
operation of the measuring mechanism, through the medium of the secondary
lever G¹. The rack G₁ is connected to that lever by means of a swivelling and
sliding pivot, as shown in Figures 1, 44 and 45, the rack G18 resting in engagement
with a suitable lateral foot or projection of the rack G, as shown in the last men-
tioned figures, being capable of vertical movement away from that foot with
relation to the rack G17 to an extent represented by five of its teeth. When the
racks are carried up by the operation of the measuring device, the detent N7 drops
into each of the notches and as the measuring lever G moves back to its horizontal
position, it leaves the setting racks and the secondary lever G16, connected there-
with, suspended upon the detent N7 at approximately the highest point of the
measurement. As it would seldom happen that a tooth of the rack G7 would be
exactly in position to be engaged by the detent N7, it follows that that rack would
drop down with the returning movement of the measuring mechanism until its next
tooth came in contact with the detent N. Thus it might happen that the rack G17,
might return to an extent represented by one, two, three, four or five of the notches
of the rack G18 The position in which the rack G7 is thus suspended as the result
of each measuring operation, is utilized as hereinafter described in connection with
the selecting mechanism, to determine which spacer, or combination of spacers,
is to be inserted; and the difference in the relative vertical positions of the two
racks when suspended from the detent N, after the completion of the measuring
operation, is also utilized in the manner hereinafter to be described in connection
with the selector correcting mechanism. It is desirable, however, to explain in
this connection that the backs of these racks each provided with
steps N³, N4, N5, best shown in Figure 19, which are located at a distance apart
equal to four times the pitch of the rack G. The corresponding steps of the two
racks exactly coincide when the rack G18 rests on the foot of the rack G, and they
are carried out of coincidence to the extent of the relative displacement of the two
racks as a result of the measuring operation.
are
Spacer Selecting Mechanism: This will now be described, beginning with that
portion thereof which attends to the A or basic spacers.
Figure 22 illustrates the relative location of the spacer containing channels.
The channel L, containing the A spacers, is alongside the main type channel V,
while the channels M2s, M and M30, containing the spacers B, C, D, respectively,
are arranged side by side adjacent to a raceway into which the required spacers
are ejected.
.
The selecting mechanism for the A spacers is shown in Figures 9, 23, 28, 29, 30
and 31. Beneath the channel L, containing the A spacers, is an elevating raceway
or table L', upon which those spacers rest. That table serves also as an elevating
raceway, and is provided with the guide rods L2 and L³, which are fitted to slide
in projections from the side of the channel L. Pivotted upon the table L' is the
stop LA, best seen in Figures 9 and 23. The lower end of this stop is provided
with three steps, of a height above one another corresponding to the thickness of
the basic or A spacer. These steps of the stop L are adapted to rest upon the
shoe L5, fitted to slide vertically in the frame W, and that shoe is provided with a

page_text: slot through which is transversely passed the end of the table elevator Lº, which is
also fitted to slide in the frame W, and is urged toward the left, as seen in
Figure 23, by means of the spring L'. The opposite or right hand end of the
elevator L passes beyond and in front of the selector setting rack G. That rack
is provided with a longitudinal cam-like surface along one edge thereof, as shown
in Figures 1, 18 and 23, having four planes L³, L, L and L, those planes being
arranged in equal steps from the rack G and connected by short inclines, the
elevator L having at its end, a projection-Figure 23-adapted to be engaged by
these stepped and inclined surfaces of the rack G. From this description and
reference to the figures, it will be seen that the vertical position of the race-way
table L', so far as it is governed by the position of the elevator L, is at its highest
position when the elevator rests against the plane L8, the table being then close
against the bottom of the channel L, so that none of the spacers are exposed to
the action of the extractor, the operation of which will be hereinafter described;
but as the rack G is pushed upward by the operation of the measuring mechanism,
the elevator L is carried successively upon the planes L³, L1 and L", thus per-
mitting the basic spacer table L' to drop away from the bottom of the channel L
to an extent equal to the thickness of one, two and three spacers, respectively, to.
satisfy the requirement thus expressed by the measuring devices.
It will be understood that the rack G17 remains in the position in which it is
left by the measurement of the given line, throughout the operation of justifying
all of the spacers contained in that line, so that the position of the elevator L
remains constant during the justification of an entire line. But for reasons which
appear on reference to the table in Figure 43, and for other reasons hereinafter
explained in connection with the selector correcting mechanism, it is occasionally
necessary to provide for the insertion of an additional basic or A spacer, and the
means for obtaining this occasional or "accidental" A spacer, consists principally
in the basic stop LA, which, as represented in Figure 23, rests during the usual
operation of the machine upon the highest of its stepped faces. As these steps
differ in height by an amount equal to the thickness of one of the basic spacers,
it will be seen that it is only necessary to move the stop L from the position shown
in Figure 23 to the second or third step, in order to obtain one or two basic spacers
respectively in addition to those which may have been obtained by virtue of the
position of the elevator Lº.
The stop L is pivotally connected to the frame L" which extends along the
back of the selecting devices, and is supported at its opposite end by means of an
extension L3 passed through a boss on the frame W, upon the outside of which
boss, it is provided with a collar L13, adapted to serve as a stop for the frame L17,
and that frame is pressed toward the left, as shown in Figure 23, by means of the
spring L, thus tending to hold the basic stop L' in the position shown in the
latter figure, i.e., with its highest step resting upon the shoe L³. The lower mem-
ber of the frame L is provided with the spur L15, and the upper member is pro-
vided with a similar spur L16, those spurs being located adjacent to the path of the
selecting fingers M5 and M respectively, upon the carriage M, best shown in
Figures 22. By reference to Figure 23, it will be seen that the vertical or engaging
face of the spur L15 is located farther from the basic stop L than the corresponding
surface of the upper spur L16, to an extent equal to the difference in horizontal
position of the steps in the lower end of the stop LA, the purpose of this difference
being to cause the frame to be moved to the second or middle step when the
spur L15 is engaged by its selecting finger M³, and to cause it to be moved to the
forward or shortest step when the spur L16 is engaged by its selecting finger M.
The carriage M is loosely mounted upon the rods m, m, fixed to the frame W,
and is adapted to slide horizontally thereon to an extent indicated by the difference
between the full and the dot and dash lines thereof, shown in Figure 23, being
moved to this extent by means of the lever M¹ pivotted at M² to the frame W, and
driven by the cam M³ fixed on the word shaft Y. Upon the vertical pivot shaft M4,
are pivotted the selecting fingers M5, M6, M7, Ms and M, best shown in Figures 20,

page_text: 21 and 22 to 22. By reference to the latter figure it will be seen that these fingers
somewhat resemble the letter L in plan view; the extended base members. M¹º
of the shape of the fingers, serving as a stop against a suitable extension of the
carriage M, against which they are urged by means of the springs M" located in
the vertical member M2, thus operating to normally hold the fingers in the posi-
tion shown in Figure 22. The vertical distance between the centres of the adja-
cent fingers, is equal to the distance between the teeth on the front face of the
rack G, for reasons hereinafter made apparent. The fingers M5 and M are pro-
vided with spurs M1 and M14, respectively adapted to engage with the spurs L15
and L16 of the frame L", as above described, when the carriage M is at the back-
ward end of its stroke, as represented by the dot and dash lines in Figure 23; while
the fingers M, M7, and M³, are respectively provided with similar but shorter
spurs, M5, M6, and M, respectively adapted to engage with the ends M18, M19,
and M20, of the ejecting levers, M21, M22 and M23. Those levers are fitted to oscil-
late upon the stud M24 fixed in the frame W, to an extent represented by the dot
and dash position of the lever M2, shown in Figure 22. Those levers are attached
to the ejecting slides M25, M2 and M27 respectively, adapted to slide through the
bottom of the type channels M28, M29 and M, which contain the justifying
spacers B, C, D respectively, best shown in Figures 22 to 22; and those ejecting
slides are adapted to eject singly from their respective channels the lowest spacers
contained therein, in the manner usual in type-setting machinery. The motion of
the parts is so timed that the spacers B, C, D, are thus ejected from their respective
channels into the adjacent raceway, when the plunger O, which is adapted: to
reciprocate therein, is in the rearward position shown in dot and dash outline in
Figure 22:
:
From the above description and the drawings, it will be understood that when-
ever one of the fingers M or M is oscillated upon its pivot as its carriage reaches
the backward end of its stroke, as represented by dot and dash lines in Figure 22,
it operates to move the frame L17 and the stop L' so as to release one or two
respectively of the basic spacers A; but whenever one of the fingers M, M or M³,
is similarly moved, it operates to engage with its corresponding ejecting lever and
cause the ejection of one of the spacers B, C, D. The means whereby the required
fingers are thus turned upon their pivot M4 at the proper time of the stroke of
their carriage, are appurtenant to the crosshead N, which is fitted to slide ver-
tically upon the rods n, n, fixed to bosses on the frame W. The extent to which
the said crosshead may be reciprocated vertically upon the rods n, n, is substantially
equal to the vertical space occupied by the selecting fingers M5, M6, M7 and M³,
which is also equal to the distance between each of the steps N³, N and N5 on the
rack G7, the crosshead being represented in its uppermost position in Figures 18,
19, 20 and 21.
Upon the said crosshead at N₁, is pivotted the latch N2, shown in Fig-
ures 22, 22. The lower end of that latch is adapted to engage with the
steps N3, N4, N5, shown in Figure 19 on the rearward side of the selector setting
rack G7; and operates to support the crosshead at its desired height by means of
whichever one of those steps may happen to be brought by the setting of the
rack G17 within the range of the vertical movement of the latch N2.
The selector N15 is a projection preferably integral with the selector slide N16,
that slide being fitted at its ends to the crosshead N. The said slide normally
rests in its lowest position as shown in Figures 18, 19 and 20, upon suitable
shoulders which rest upon the lower lateral member of the crosshead, but it is
capable of upward movement therefrom with relation to the crosshead for purposes
hereinafter described in connection with the selector correcting mechanism. For
the purpose of the description of this section, it may be considered as remaining
in its lowest position shown in the last mentioned figures. The selector N15, best
shown in Figures 19, 20 and 22 to 22³, is located in the general vertical plane of
the selecting fingers M to M inclusive, and moves with the vertical motion of the
crosshead along that plane so as to be brought opposite to one or the other of
J

page_text: those fingers, as may be determined by the position in which the crosshead rests
after the conclusion of the measuring operation. In the last mentioned figures,
the crosshead being shown in its uppermost position, the selector N15 rests in a
position to engage the selecting finger M8 when the latter is carried with the move-
ment of its carriage M, and therefore operates to move that finger to the dot and
dash position shown in Figure 22, thereby engaging with its corresponding ejecting
lever M23 and causing the ejection of the spacer D into the raceway. It will be
seen by reference to Figure 20 that those portions of the selecting fingers which
move across the vertical pathway of the selector N15 are separated by a space sub-
stantially equal to the vertical width of the selector, and the notches on the
rack G7 are so located that the selector N15 is never permitted to engage with more
than one at a time of the selecting fingers. It will be observed that those notches
are of the same pitch as the fingers, and that the selector may therefore be brought
into the same relation to each of the fingers as that in which it is herein shown
to the finger Ms.
The means whereby the crosshead N is carried into and out of operative relation
to the setting racks, will now be described.
Upon the crosshead is mounted the correcting slide P being capable of vertical
movement thereon to an extent equal to five of the small notches of the setting
rack G18. Upon this slide is pivotted the correcting slide latch P¹, having its point
adapted to engage with the steps N3, N4, No, of the rack G18. This latch, there-
fore, lies alongside of, and is substantially co-extensive with, the latch No, to which
it is connected by means of a pin in one of the latches engaging in a slot in the
other latch, as shown in Figures 19 and 21, in which views the latch P¹ is shown
pushed above the latch N2 to the extreme limit of its movement with relation
thereto, corresponding to the five notches in the rack G18, as above described. The
latches N and P₁ are pressed toward their respective racks by means of the
spring No, seated in a recess in the crosshead. The latch P¹ is provided with a
cranked extension to which is pivotted at N10 the connecting rod N, and that con-
'necting rod extends downward and is connected with the arm N12-Figure 5-,
and which is pivotted upon the bracket Q4 and is provided with a cam pin which
rests in contact with the cam N13 upon the line shaft X, as shown in Figure 5.
That cam N13 operates through the connecting rod N¹ to move the correcting
slide P upward to its extreme position with relation to the crosshead N, and then,
continuing its upward motion, moves the crosshead to its upper position, shown in
Figures 18 and 21. The action of the rod N" against the weight of the cross-
head N operates by reason of the nature of its connection with the two latches,
to compress the spring N° and swing the engaging points of those latches laterally
away from the path of the steps N3, N4, No, of the setting racks G and G18. The
cam N¹ is so timed as to hold the latches and the crosshead in the position shown
in Figure 19, during the operation of the measuring mechanism, so as to permit
of the setting racks G17 and G18 being pushed up thereby to their required position,
bringing some one of the steps N³, N or N of those racks within the zone of
movement of the latches, that zone being, as heretofore stated, equal to the dis-
tance between those steps. Therefore, as soon as one of the steps, as, for exam-
ple N3, of the setting rack is carried out of the upper boundary of the zone of
operation of its latch, the next step N4 passes into the lower boundary of that zone,
so that one, and only one, of the steps N³, N or N5, can at any time rest within
that zone.
The operation of the selecting and ejecting mechanism is therefore as follows:
The crosshead N being held in its uppermost position, shown in Figures 18
to 21 inclusive, and the latches being consequently held out of engagement with
the setting racks, the latter are moved upward by the operation of the measuring
devices to an extent determined by the deficiency existing in the line, divided by
the number of spaces into which the justifying spacers, which are to supply that
deficiency, are to be inserted.
At the conclusion of the measuring operation, those teeth of the measuring racks

page_text: which are next above the point of the detent N7 settle into engagement with that
detent, and remain suspended therefrom while the cam N13 allows the latches N2
and P to be again forced into contact with the rearward or stepped surfaces of
those racks by the operation of the spring No, and also allows the crosshead to
settle down until the engaging points of the latches rest upon those steps of the
setting racks which are within the zone of their operation, as above described.
These latches and their crosshead N remain in this position throughout the justi-
fication of the line then being operated upon, determining by their position and
by the resultant position of the selector, which one of the selecting fingers M5, M6,
M7, MS and M shall be moved into engaging relation to its corresponding space
ejector. The crosshead therefore rests in this position supported by the step of the
rack G, holding the selector N15 in the path of some one of the selecting fin-
gers M5, M6, M7 or Ms, the selecting finger M being never acted upon excepting
when called into use by the operation of the correcting devices, as will be herein-
after described. As the carriage is caused to reciprocate, that one of the selecting
fingers which lies in the horizontal plane of the selector N15 is moved by that
selector to the position shown in dot and dash line in Figure 22, causing the ejec-
tion of its corresponding spacer into the raceway. If the selecting finger M5 lies
in the plane of the selector N15, it is brought into contact with the spur L15 of the
frame L, thereby moving the stop L' so that the middle step. thereof rests upon
the shoe L³, so permitting the column of A spacers to fall far enough for an addi-
tional one of them to be carried forward by the operation of the assembling
mechanism, as hereinafter described. After the return of the carriage M to its
full line position, shown in Figure 23, that finger which has been operated upon
by its forward movement returns to its normal position, even though the conditions
require that it shall immediately thereafter repeat the same operation. These
lateral reciprocations of the carriage are continued to the extent predetermined
by the setting of the governor mechanism, at the conclusion of which the cross-
head N is again carried to its uppermost position by means of the cam N¹³, there to
remain until the next line has been measured. The cam N13 is so formed as to
first move the crosshead slightly above the normal upper position shown in the
above mentioned figures, and this slight additional movement enables the crosshead
by means of its projection N14 to engage with a cranked projection of the detent N,
as best shown in Figure 21, thus momentarily carrying that detent out of contact
with the teeth of the setting racks G and G18, and permitting the latter to fall
to their lowest or zero position in order that they may again be raised from that
position by the subsequent operation of the measuring mechanism upon the next
line.
Selector Correcting Mechanism: -From the above description of the spacer
selecting mechanism it will be seen that that mechanism is in itself insufficient to
effect the justification of the lines of type within the necessary limits of accuracy,
inasmuch as it would seldom happen that any of these spacers or combination of
them would, if repeated without change, in all of the spaces existing in a given
line, justify that line with sufficient accuracy. The arrangement and operation of
the above described devices, is such that if the measurement of the spacer required,
as indicated by the position of the measuring racks, does not quite equal one of the
spacers or combination of spacers, the selection will fall upon the next size below.
In other words, if the racks G17 and G18, when at the highest position to which
they are carried by the measurement of a given line, do not stand at a position
at which one of the notches in the rack G7 is exactly engaged by the detent N',
that rack will drop back until its next notch engages with the detent, thus causing
the selection of a spacer or combination of spacers smaller than the size indicated
by the measurement. Thus it will be seen that the effect of a certain amount of
the measurement is lost, or in other words, that the extent to which the rack G
drops back from its measurement indicating position to the position wherein it
rests by the engagement of one of its notches with the detent N', represents rela-
tively the extent to which the spacer or combination of spacers thus selected, is

page_text: less than the space to be filled. The purpose of the devices at present under con-
sideration is to compensate for these deficiencies, keeping account of them, as it
were, until they have amounted to the difference between the size of the spacer
selected and the size of the next larger spacer, operating then to move the selector
up to a position in which it shall select and eject a spacer or combination of spacers
of that next larger size. Having supplied the deficiency, the selector must return
to its first position, until the increments of deficiency again require the insertion
of the larger spacer.
The mechanism comprising this correcting auxiliary to the spacer selecting
mechanism is shown in the same figures in which that selecting mechanism
appears.
Reference has already been made to the correcting sli-le P, and to its latch P¹,
which is adapted to be engaged by the measuring rack G¹8. That slide is carried
upon the crosshead N and is capable of a vertical motion with relation thereto,
to the extent of five of the small notches of the rack G18, as it might sometimes
happen that the detent N7, at the conclusion of a measurement, might engage the
fifth tooth of the rack G18 below one of those teeth which normally are in line with
the notches of the rack G, holding the former rack in that position while the
rack G falls to the extent represented by the five notches, before engaging with
the detent N. Upon the slide P is pivotally attached an end of the lever P² the
other end of which is pivotally attached to the hub P³ of the crosshead N. At a
point midway of the length of this lever, is pivotted the lever P4, which is normally
held in a position coincident with that of the lever 12, by means of the spring 1
attached to the crosshead N, as shown in Figure 18. One end of the lever P
is provided with a projecting pin P, best shown in Figures 22, 23, 24, 24", and 24°,
and located in the plane of, and adapted to engage with, the inclined ends of the
cam-like pieces P7, which are attached to or integral with the carriage M. When-
ever the spaces existing in a given line may be exactly filled by a certain number
of similar spacers or spacer combinations, the position of the measuring rack inci-
dent upon the measurement of that line is such that the latch engaging
steps N³, N, N5, thereof, are coincident upon the two racks, and in that case when
the crosshead and its latches are let down into contact with those steps, the cor-
recting slide P rests in such a position that the pin P6 of the lever P4, will pass
between the cam pieces P7 of the carriage M as the latter is caused to reciprocate
in the operation of assembling the spacers. But when the result of the measure-
ment is such that the steps of the rack G18 are held above those of the rack G.
the resultant position of the correcting slide P and its levers P2, P, is such as to
bring the pin 16 under the operation of the bevelled face of that one of the cam
pieces P' to which it is opposite. That operation causes a vertical oscillation of
the lever P upon its pivotal connection with the lever P2, at each backward stroke
of the carriage M, the extent of that oscillation being in direct proportion to the
amount of relative displacement of the racks G17 and G18.
Upon the left hand end of the lever P4, as best seen in Figures 24, 24, and 24°,
is pivotally mounted the pawl P8. The point of that pawl is adapted to engage
with teeth P' in the right hand edge of the selector slide N1, being capable of an
oscillatory movement into and out of those teeth, and being limited in its forward
movement away from the teeth by means of the pin P10 fixed in the crosshead.
The pawl is further provided with a connecting rod P11, pivotted thereto, the oppo-
site end of that rod passing through a clamping swivel P2 on the carriage M,
that swivel being split and provided with a clamping screw which is adjusted so
as to engage the rod P with sufficient friction to carry the pawl P8 into contact
with the teeth P upon the left hand or backward movement of the carriage,. and
to carry that pawl away from the teeth against the stop Po upon the forward move-
ment thereof.
From the foregoing description it will be seen that any upward movement im-
parted to the pawl P8 while it is in contact with the teeth P9, would operate to
raise the selector slide N to a corresponding extent, and that extent is con-

page_text: trolled by the amount which the racks G17 and G18 are displaced in relation to
each other, as the result of a measurement of a line, operating through the levers P³
and P to hold the pin P6 to a corresponding extent above the adjacent slot between
the cam pieces P7 In Figure 23, that pin P is shown to be in the position to
which it is carried by a displacement of five of the small notches of the rack G18,
the carriage M being here shown in its forward position, while in Figure 24, the
cams P are shown in their backward position, the progress toward which has
caused the pin P to be forced down by the inclined face of the adjacent cam
piece P7, until it can enter the slot below that cam piece, thus imparting to the
selector slide N16 an upward movement equal to five of the notches P, which is
also the equivalent of the extent to which the rack G18 has been displaced.
The selector slide N¹ is retained in the raised position to which it is moved by
the pawl Ps, by means of the detent P₁, which is pressed into engagement with
the teeth P3 corresponding to the teeth P³, located on the opposite or left hand
edge of the slide N16. By reference to Figure 24, it will be seen that there are
six of these teeth P. After the fifth tooth, occurs an interval as though the sixth
and seventh teeth were removed, the sixth tooth being therefore where the eighth
tooth would be located if the teeth were continuous, and we will hereinafter refer
to this isolated tooth as being the eighth on that side, regarding the sixth and
seventh as being removed, for reasons hereinafter set forth.
It will be understood that the object of the mechanism at present under con-
sideration, is to raise the selector N15 from its lowest or normal position with
respect to the cross-head, so as to cause it to engage with and select the next larger
size of spacer, or combination of spacers, whenever the deficiency between the
size of spacer called for by the measurement, and the size of spacer supplied by
the selecting mechanism, shall have amounted to the additional thickness repre-
sented by a larger size. Having supplied this deficiency by the insertion of one or
more spacers or combinations of the larger size, it is necessary that the selector
shall be allowed to drop back to its former position until the deficiency resulting
from the repeated selection of the spacer too small for the space to be filled shall
again require the selection of the larger space. The mechanism by means of
which the selector slide is thus released and allowed to drop back to its normal
position will now be described, reference being made to Figures 24 to 27" inclusive.
The detent P2 is provided with an approximately lozenge shaped projection P¹4
upon its face. That projection is adapted to engage with similar shaped projec-
tions P1, P16, upon the escapement pawl P, which is pivotted upon the selector
slide N16. Upon that slide is also revolubly mounted the escapement wheel P18,
which is urged in the direction of the arrow against the stop P¹ by means of a
coiled spring P20. The escapement pawl P7 is provided with a point which is
pressed into engagement with the wheel P18 by the spring P21. A rod P22 is fixed
in a lateral member of the crosshead N, and extends downward partially across
the face of the escapement wheel in line with a pin P2 located upon that wheel,
for the purposes hereinafter explained.
"
By again referring to the table shown in Figure 43, it will be seen that the size
of the smallest space is equal to one-fourth of an em, and that the spacers B, C, D,
progress in size above the A by one-sixteenth of an em. It therefore follows that
where the measurement shows the spaces to be 7ths of an em in width, the inser-
tion of an A spacer, which equals 6ths or 16th of an em, leaves a deficiency of
1/6th in each space. At the insertion of the sixth spacer this deficiency would,
therefore, amount to ths or 1/16th of an em, which is equal to the difference in
size between the A and the B spacers, and that deficiency would therefore be made
up if a B spacer were to be put into the sixth space instead of an A spacer. There-
fore, this mechanism is adapted to make this substitution, resuming, however, the
insertion of A spacers in the succeeding spaces until the amount of the deficiency
again requires the insertion of the larger size.
The mode of operation of this correcting mechanism differs with each of the five
different amounts of corrections that may be required, and a description is there-

page_text: fore now given of its operation under each of these five possible conditions. The
difference between these conditions, and the difficulty in satisfying them, are due
chiefly to the circumstance that the selector must be allowed to return to its lower
or normal position upon the completion of that stroke of the carriage at which the
amount of correction then applied equals the amount of deficiency then accumu-
lated. In correcting for a deficiency of th of an em, the slide must return at the
conclusion of the sixth stroke, because at that stroke the devices will have applied
a correction of 6ths or 1/16th of an em, equaling the accumulation of six deficiencies
of th of an em. Therefore, in correcting for deficiencies of 26ths 3/ths, /ths
and 5ths the selector must be returned to its lower or normal position at each
first, second, third and six stroke respectively of the carriage.
$6
From the description already given, it will be understood that the "deficiency,"
occurring in each space is added up or tallied," so to speak, upon the notches P
When
of the selector slide N16, one notch for every deficiency of th of an em.
that deficiency occurs in each space of a line, the selector will be raised one notch
at each stroke of the carriage M by the operation of one of its cam pieces P7, the
slide being retained in its raised position by means of the detent P. Therefore
upon the sixth stroke of the carriage, the selector slide will be raised six notches,
causing the selector N15 to engage the next selecting finger above that employed in
the previous five strokes of the carriage. The escapement pawl P17, carried up by
the elevation of the slide N16 reaches at this point, such a relation to the detent Piz
that the lower point of the lozenge shaped projection P16 of the pawl engages with
the upper point of the similar projection P¼ of the detent, exactly as the projec-
tion P is shown in engagement therewith in Figure 24. Upon the forward stroko
of the carriage M, the pawl Ps is withdrawn from the teeth P9, thus allowing the
weight of the slide N to operate through the lozenge shaped point P15 of the
pawl P, to cam the detent away from the teeth P13 The slide, being thus left
unsupported falls to its first position shown in Figure 18, carrying the selector N15
back to its former and normal position, when it resumes the selection of the smaller
spacer until again elevated by the correcting device.
The operation of the mechanism in the correction for deficiencies of ths and
3/ths of an em, differs from that just described only in the respect that the
selector slide N16 reaches its releasing point at the third and second strokes res-
pectively, inasmuch as the numbers 2 and 3 are also even divisors of 6. But 4
and 5 are not even divisors of 6 and therefore the operations of the devices for the
correction of deficiencies of ths and 5ths of an em, become more complex.
I will describe first the correction for a deficiency of ths. In this case the
first stroke of the carriage will elevate the slide N four notches, and it will be
detained by the detent P12. The next stroke will elevate the slide four more
notches, bringing the eighth of the notches P13 above the detent P12, where it
remains until the third stroke of the carriage, when the pawl P8 engaging the
fifth of the notches P, raises the slide as shown in Figure 24, so that the lozenge
projection P14 of the detent P12 rides over the projection P15 of the pawl P17, as
shown in Figure 24, allowing the slide N16 to drop as before. It will be observed
that the selector was in position to select the larger spacer at both the second and
amounted to 12ths
third strokes of the carriage, and therefore the "correction
of an em, just equalling the deficiency of ths occurring in each of the three
spacers justified by the three strokes of the carriage.
,,
In the case of a deficiency of 5/ths of an em, the first stroke of the carriage
raises the slide N16 five notches, where it is held by the detent engaging the fifth
of the notches P13. At the second stroke of the carriage, the pawl P8 engages with
the fifth of the notches P9 and, raising the slide higher than on any of the other
corrections, brings the pin P2 of the escapement wheel P" against the rod P2
reacting upon the wheel to turn it to the position shown in Figure 26, so as to
engage with and hold the pawl P17 out of engagement with the detent P13. That
detent therefore remains against the slide N16, supporting it in its raised position by
means of the eighth one of the notches P¹³. The partial revolution of the wheel pis

page_text: caused by its contact with the rod P23 serves to carry the first of the teeth P25 into
the path of the pawl P8, which upon its third stroke engages with that tooth, as
shown in Figure 26, and advances it another notch. The fourth and fifth strokes
of the carriage each operate thus to turn the wheel an additional notch, without
releasing the slide from the detent P. But the sixth stroke of the carriage,
brings beneath the pawl P, a portion of the wheel P18 which is deeply recessed,
thereby allowing that pawl to drop against its stop pin P30 to the position shown in
Figure 27, thereby disengaging the detent P2 and allowing the slide N16 to drop
to its normal position. As it approaches the bottom of its stroke, the cranked
spring arm of the pawl P7 collides with the pin P27 attached to the crosshead N,
which serves to move the pawl to the position shown in Figure 18, thus releasing
the wheel P18 and allowing it to be returned by its spring P20 to its normal position
as also shown in the latter figure.
If either of these correcting operations should, while yet unfinished, be inter-
rupted by the completion of the justification of the line, thus leaving the selector
raised above its normal position on the crosshead, it will be released therefrom
by means of the rod P2, attached to the frame W, against which the cranked end
of the pawl P2 is carried, as shown in Figure 24, when the crosshead is moved to
its highest position by its cam N13. The movement of the pawl P12 due to this
engagement with the rod P28 serves to release the slide N16 whereupon it falls to
its normal position. If the completion of the line finds the escapement wheel P18
in an incomplete stage of its operation, for example, as in Figure 26, the move-
ment of the pawl P due to its engagement with the rod P2, will serve also to
disengage that pawl from the teeth of the wheel, allowing the latter to be rotated
to its normal position by means of its spring P20. This releasing of the respective
devices at the completion of each line is necessary in order that they may be at
their normal or starting point at the commencement of each new line.
Spacer Assembling Mechanism: -The construction and relation of the devices
which comprise this mechanism are best shown in Figures 22 to 22", 28, 29, 30 and
31. The plunger 0 is attached to the carriage M, and is carried by the lateral
reciprocations of that carriage along the raceway 06, best shown in Figures 22
to 22, which lies immediately in front of the channels M, M29, and №30, con-
taining the B, C, D spacers, respectively. Those spacers are ejected one at a time,
as previously described, into that raceway, at the end of the movement of the
carriage M toward the left, and while the plunger O is therefore in the position
shown in dot and dash lines in Figure 23. On the return or forward movement of
the carriage toward the right, the spacer that has been ejected is moved forward
into line with the type containing channel into which it is to be injected by the
injector plunger R. In this position it is alongside of the channel L containing the A
spacers, as shown in Figure 22, and in Figures 28 to 30 inclusive.
The devices by means of which the A spacers withdrawn from the channel L,
are assembled in combination with the spacer ejected from either of the
channels M2, M29 or M30, consist of a bifurcated plunger O', which is fitted to slide
in a boss w on the main frame W, and is connected by means of the lever 02 also
pivotted on the boss w, and best shown in Figure 22. The opposite end of that
lever is provided with a slot, by means of which the lever engages with a pin 0³ on
the carriage M. This arrangement of the lever operates to impart to the plunger O
a movement contemporaneous with, but in the opposite direction to, that of the
carriage M, and the plunger O. The bifurcated ends of the plunger O¹ pass
through corresponding slots in the basic table L', as best seen in Figure 22, the
ends of the plunger being turned upward to form hooks, which, as the plunger is
moved toward the left, operate to move along upon the basic table or raceway L',
all of those A spacers which have been allowed to escape from below the level of
the channel L by the lowering of the table, whether by the operation of the
elevator L, or of the stop L, as previously described. The upper surfaces of these
hooks of the plunger O₁ are fitted against the lower surface of the channel L so
as to form a support for the column of spacers which remain on the channel, as

page_text: shown in Figure 30, the basic raceway table L' remaining in its lowered position
until the A spacers have been carried to the position shown in Figure 30, and
until the B, C, or D spacer has been brought forward and pushed upon the top
of the A spacers, as shown in the last mentioned figure. The basic table L' is then
elevated to the position shown in Figure 31, thus raising the combination of
assembled spacers up to the level of the top of the detents J6, to which it is at that
time lying immediately adjacent. This raising of the basic table is accomplished
by means of the lifter 04 That lifter rests upon the ends of the plunger 01.
and is provided with a bevelled end which engages with a correspondingly bevelled
and hooked projection or extension 05 of the basic table L', shown also in side view
in Figure 9. The opposite end of that lifter is supported by and slides in the
bracket 07 attached to the frame W, and receives its motion from the spacer inject-
ing devices, as best shown in plan view in Figure 22.
The consecutive order of operation of the assembling devices will be best seen by
reference to Figures 28 to 31 inclusive, Figure 28 showing the basic table in its
elevated position, the spacers assembled by its previous operation having been
removed therefrom by means of the injecting mechanism. In Figure 29, the basic
table is shown in a lowered position, this time by the operation of the stop L' in
being moved to its second or lowest step, thus lowering the column of A .spacers
far enough to permit the two lower ones to be drawn away by the movement of
the plunger 0, as shown in Figure 30, where they rest ready for the spacer which
is therein shown as being advanced by the plunger O. After that spacer has been
pushed by the completion of the movement of the plunger O upon the two A
spacers, all three are raised by the elevating movement of the basic table to the
position shown in Figure 31, whence they are injected into the line by the inject-
ing mechanism. The parts are now again in the position shown in Figure 28,
and repeat the above operation for each of the spaces to be justified, under the
control of the governing mechanism..
'
Separator Extracting Mechanism:-This is shown in Figures 3, 4, 5, 9, 10, 22,
22 and 22. As previously described, the separators are extracted from the line
while resting upon the top surface of the detents J6, which is coincident with the
injecting plane, and with the surface of the raceway.
The form of the word separators U and the line separators T is best shown in plan
view in Figures 10, 12, 124, 12", 12°, 22 and 54 (Sheet 9), differing from each other
only in the respect that the ends of the line separators T are made slightly longer
than the ends of the word separators U. Both kinds of these separators are pro-
vided with shoulders corresponding to the length of the type, by means of which
they are retained in the type channel, their reduced ends passing through slots in
the edges of the channel, which slots are narrower than the thickness of the type,
and thus extend for a short distance on either side of the channel-Figure 54,
Sheet 9 so as to enable them to be engaged by the fingers of their respective grabs.
Both kinds of these separators are provided with similar extracting notches, which
are similarly located on the opposite ends of the separators, so as to enable them to
be extracted, even when reversed by accident, or otherwise. The separators are
withdrawn from the line by means of the extractor hook Q-Figures 22 to 22-
which is adapted to reciprocate to and from the channel upon the level of the
injecting plane thereof, normally lying at rest adjacent to the location in which the
separators rest upon the detents Jo when in position to be extracted. The hook
is held out of the path of the type while in its inoperative position---Figures 22
to 22 by means of its bevelled end which is pressed against a correspondingly
bevelled portion of the side of the channel V, the hook being sufficiently elastic to
allow it to spring away from the type to the position shown in that figure. At
this portion of the channel V, the shoulders thereof, by means of which the type
and the separators are retained in their lengthwise position, are cut away so as to
allow the separators to be extracted in one direction, and to allow the justifying
spacers to be inserted from the opposite direction.
The opposite end of the extractor hook Q is pivotally mounted upon the block Q

page_text: as shown in Figure 9, that block being fitted to slide upon the rods q, q, which are
fitted at their ends in the frame W. The slotted end of the arm Q2 is connected by
means of a pin to the block Q', and is fixed upon one end of the shaft Q³, and that
shaft is pivotally mounted in the bracket Q, having fixed upon its opposite end the
cam arm Q. That cam arm is provided at different portions of its length with the
cam pins Q and Q7, adapted to engage with the cams Q and Q upon the shafts X
and Y respectively, as best shown in Figure 5, being pressed into engagement with
the cams by means of the spring Q. The arm Q5 is thus connected with these two
cams in order that two independent movements of differing amplitude may be
imparted to that arm, and consequently to the extractor hook Q, for the purpose of
distributing the word separators U and the line separators T into their respective
channels Q and Q. Those channels are supported by extensions from the main
frame Win the relative positions shown in Figures 9 and 22, the channel Q for
the word separators U being located nearer to the type channel than is the line
separator channel Qu
The mode of operation of this mechanism is as follows:-
During the operation of the devices comprising the line mechanism, this extract-
ing mechanism, along with the other devices comprising the word mechanism,
remains at rest, the hook Q resting in the position shown in Figures 22 to 22", out
of the path of travel of the type. After the commencement of the operation of the
word mechanism, the first word having been carried up into the galley by the word
grab, and the first of the U separators being then at rest upon the detents Jo, the
extractor hook Q is moved by means of the cam Q toward the left from its last
described position, catching into the nick of the separator U, and carrying it
toward the left-Figure 9-to a position immediately over the channel Q10, into
which it drops by its gravity. The hook Q then returns to its previous position
adjacent to the type channel, repeating the extracting operation for each of the U
separators in the line, the number of its operations being controlled by the govern-
ing mechanism, as hereinafter described. The last separator in each line is
invariably one of the line separators T, and after the final word has been carried
into the galley, this separator T remains lying upon the detents Jo until the line
shaft X is put in operation for the purpose of measuring the next line, thereby
bringing the cam Q8 into engagement with the arm Q, the form of the cam being
adapted to impart to the arm Q2 a movement of sufficient extent to carry the
T separator which is then engaged by the extractor hook Q, to a position above the
channel Qu, into which it also falls by gravity. This separator being longer than
the word separators is thereby enabled to pass across the top of the channel Q10
without falling therein. It will be observed that the relative location of the
cams Q and Q to the arm Q5 is such as to favour the imparting of a greater
amplitude of movement to that arm when moved by the cam Q8 than when moved
by the cam Q.
Spacer Injecting Mechanism:-This is shown in Figures 3, 5, and 22 to 22" and
operates in connection with the word grab and spacer assembling mechanisms. The
injector R is a plunger, the spacer engaging end of which rests upon that extension
of the frame W which forms the bottom of the channels M28, M29 and M30, and of
the raceway, this general level constituting what is herein termed the injecting
plane. The opposite end of the plunger R is supported by its connection with the
lifter 0, and is connected by means of a pin, to a slotted bell crank lever arm R
which is pivotted upon an extension of the frame W, as shown in Figures 3 and 53
(Sheet 3.) The opposite end of that lever is connected by means of the rod R² to
the crank pin K' located in the side of the cam M³, that crank serving thus to
communicate movement to the word grab, the basic table L', the lifter 0 and the
spacer injecting devices, inasmuch as these devices require to be operated con-
temporaneously. The forward movement of the injector R begins at the conclusion
of the space assembling movement, when the spacers assembled by that movement
have been lifted to the level of the injecting plane by the basic table, and that inject-
ing movement follows close upon the extraction of the word separators U described

page_text: in the last section. No movement, however, of the injector R, accompanies the
extraction of the line separator T, inasmuch as the extracting of that separator is
accomplished by the operation of the line shaft mechanism.
Having thus completed a description of the devices comprehended under the
general designation of word mechanism, a description will be given of the third
general division of the machine herein designated as the
Governor and Actuating Mechanism: This is shown in Figures 1, 2, 6, and
from 34 to 42 inclusive. The general line of shafting which has upon it the camis
and other devices for operating the devices composing the line mechanism, and
which is herein referred to under the general designation of the line shaft X, is
composed of three sections, herein distinguished by the designations X, X²,
and X³, while the line of shafting herein referred to as the word shaft Y, is com-
posed of two sections, distinguished by the designations Y¹ and Y2, respectively.
The section Y¹ is provided with the pulley Y3 and also has fixed upon it the
pinion Y, by means of which motion is communicated to the gear X on the
shaft X. All of these shafts are journalled in suitable brackets attached to
the frame W, and the sections X', and Y¹, are driven continuously in opposite
directions, the line shaft X being rotated at a considerably reduced rate of speed
as compared with that of the word shaft Y.
The arrangement and connection of these shafts are best shown in the plan views,
Figures 5 and 6. The shaft X¹ has splined thereon the sliding clutch X5, which
is adapted to engage with, and to be disengaged from, a fixed clutch X6, on the
shaft X³, and that shaft is provided with the crank F5 for operating the line grab.
Beyond that crank the shaft X2 is provided with the sliding clutch X', which is
adapted to be moved into and out of engagement with a corresponding clutch X8
fast on the shaft X³. The end of the shaft X2 is herein shown to extend into the
adjacent end of the third section X3, but this is merely for the purpose of forming
a supporting bearing for it. Referring now to Figure 5, the governor cam §19 is
shown fixed upon the shaft X3 adjacent to the clutch X8, after which come the
cams H7, 14, Q³, N13, J7 and G2 in the order named.
The shaft Y is provided with a fixed clutch Y5, and the adjacent end of the
shaft Y2 is provided with a sliding clutch Y adapted to engage with and be
disengaged from the clutch Y5. Toward the right hand end of the shaft Y2 are
fixed the cams Q and M³, to the latter of which is fixed the crank pin K7.
These cams and cranks are thus located upon detachable sections of the shafts X
and Y, in order that their respective groups of mechanism may be thrown into or
out of operation by means of their clutches under the control of the governing
mechanism, which will now be described.
.
The shaft Y is provided with a worm Y' which is adapted to engage with the
worm wheel S, fixed on the governor shaft S-Figures 34 and 37. That shaft is
journalled at its ends in suitable bearings in the frame W, and has fixed upon it,
the ratchet wheel S2, best shown in Figures 34, 34, 40, 41 and 42, the relation of
the worm, worm wheel and ratchet being such that the latter is rotated continuously
in the direction of the arrow shown upon the ratchet in Figure 40, to an angular
extent equal to that to which the notches are separated, at each revolution of the
shaft Y. Upon the shaft S¹, adjacent to the ratchet wheel S2, is loosely mounted
a controller S³, having integral therewith three discs $4, $5 and $6-Figures 34
and 34°. The disc S+ has pivotted upon the side thereof the pawl S7 engaging with
the ratchet wheel S. Loosely supported upon the shaft S¹ on the opposite side
of the ratchet, is the pawl releasing cam S8, having in its face adjacent to the
ratchet, a groove, best shown in Figures 39, 40 and 42, into which extends a
projection S⁹ of the pawl S7. A similar projection S1, on the opposite end of the
pawl extends over the periphery of the cam S8, as shown in Figures 39 and 41. The
pawl releasing cam S8 is provided with a boss S", which is squared, as shown in
Figure 37, and engages with a corresponding mortice in the arm S2 of the releasing
rod S, so as to prevent the cam from rotating, the boss S being provided with
pins $12 adapted to engage with the inclined slots S25 of the arm S2, as best shown

page_text: in Figures 37 and 38; the purpose of this arrangement being to move the pawl
releasing cam S8 endwise upon its shaft S¹ at the desired time, so as to release the
projection S10 of the pawl S7 and allow the latter to engage with the teeth of the
ratchet S2, that pawl being urged toward its ratchet by means of its spring S³,
attached to a pin located in the side of the pawl disc S. That endwise movement
of the cam S8 is never, however, sufficient to release the projection S9 of the pawl
from its groove in the side of that cam. It will, therefore, be seen that the pawl $7
cannot engage with its ratchet S2 unless partially rotated to some other position
with relation to the groove of the cam 8 than that in which it is shown in
Figure 40, and when so moved to a position which allows of such engagement, it
is disengaged therefrom upon arrival at the position shown in that figure, by the
operation of the groove in the cam S8 upon the projection $9, which not only serves
to disengage the pawl from the ratchet wheel, but also serves to prevent any
further motion of the pawl and its attached controller in the direction of rotation
of the ratchet wheel.
The disc S6 of the controller S³, is stepped in the manner shown in Figures 2,
34 and 35, the steps being arranged in the form of a spiral. Adjacent to this
stepped disc is the detent S3 fixed to the detent shaft S4 which is journalled in
bearings in the adjacent bracket, and is provided with the arm S15, as best shown
in Figures 2, 6 and 35. The detent can engage only with the last or highest step
of the disc So, as shown in the latter figure, thus serving to hold the three discs, S4,
S, S6, in the positions in which they are shown in Figures 40, 36, and 35, respec-
tively, during the operation of the measuring mechanism. The controller $3 is
provided, with a spring or weight, as shown in Figures 34, 35 and 36, adapted to
normally urge the sleeve and its appurtenant discs in the direction indicated by
the arrow in Figure 36, which is the opposite direction to that in which the
ratchet Sa rotates.
S16 is a stop-Figures 2, 34 and 34",-located above and in the plane of the
stepped disc S, and is connected with the rack S" by means of a telescopic con-
nection, as shown in Figure 34. That rack engages with the pinion S18 fixed on the
shaft H³, which, as it is turned by the separators T and U, as described in con-
nection with the fulcrum adjusting mechanism, operates to lift the stop S16 to an
extent equal to the height of one of the steps of the disc Se for each of the separa;
tors in the line. Therefore, after the line to be measured has passed into the
measuring zone, the stop S16 stands in engaging relation to that step of the disc So
corresponding in number to the number of spaces or U separators in the line to
be justified. The single additional movement of the stop due to the line separa-
tor T, is compensated for by the position of the steps on the flange.
From the foregoing description it will be understood that the controller S³, if
released from its detent S3, will make a partial rotation in the direction of the
arrow shown in Figure 36, by the operation of its weight or spring, until one of the
steps of the disc S engages with the stop S16, carrying with it the discs S and S5,
and thereby moving the pawl $7 to a position relative to the releasing cam S8,
which permits of its engagement with the ratchet S so far as the groove of that
cam is concerned, being, however, still held out of engagement with the ratchet
because of its projection S10 resting upon the periphery of that cam. If at this
point, however, the cam were to be drawn endwise. upon the shaft S¹, the pawl
would be released and would be carried into engagement with the ratchet S2, and
would be released therefrom upon arriving at the position shown in Figure 40. .
The telescopic connection of the stop S16 with its rack S7 is for the purpose of
enabling the rack to be returned to its lowest position by the releasing of the
detent H¹ before the stepped disc S is returned to the position which allows the
stop S to drop with the rack, a condition which may occur in the justification of
a line having a large number of spaces.
The means whereby the releasing of the controller S³ and of the pawl is
accomplished will now be described....
The governor releasing cam S is fixed upon the shaft X³, and is best shown in

page_text: 0
Figures 2, 6, 47 (Sheet 18) and 51 (Sheet 18). Its flanged left hand edge is
provided with two steps S20 and S21, and is adapted to engage with the releasing
rod S22, which rests in suitable guiding supports, and is pressed into contact with
its cam by means of a spring $23. As shown in Figure 6, the rod is bifurcated
toward its left hand end, the pawl releasing arm S24 being adapted to engage with
the squared flange S" of the releasing cam S8, the arm S2 being provided with
inclined slots $25 adapted to engage with the pins S12, as best seen in Figures 37
and 38. The detent releasing arm S26 of the rod S2 is connected by means of the
link S27 with the arm S15, and the lower side of the arm S26 is provided with a
spur S2, best shown in Figure 35, that spur being in the path of the pin S29 on the
disc S. The releasing rod S is adapted to engage with the clutch fork S30 which
is fitted to slide in suitable supports of the frame W, by means of the shoulders S31
and S2, as best shown in Figure 35, so as to move the fork to an extent sufficient to
engage and disengage its clutch Y from the clutch Y5 of the shaft Y¹.
The step S20 of the cam S19 is made high enough to move the rod S2 and its
arms S24 and S26 toward the left from the position in which it is shown in Figures 6,
35, 37 and 38 for a sufficient distance to release the detent S¹³ from engagement
with the stepped disc S6, and sufficient also to move the shoulder S31 into contact
with the clutch fork $30 This movement, however, is not sufficient to carry the
releasing cam S8 away from the ratchet so as to release its pawl, the slots $25 being
straight, as shown in Figure 38, for a distance equal to the movement imparted
to the arm S2 by the step S20 of the governor cam S. The parts remain in this
position while the stepped disc S6 is rotated by means of its weight until the proper
step from which its return motion is to begin is brought against its stop S16. Mean-
while the cam S19 continues to revolve and brings its step S2 in contact with the
rod S2, thus moving the clutch Ye into engagement with the clutch Y5 by means
of the shoulder S1 of the said rod S2. This additional movement of the rod,
operates also by means of the inclined portion of its slots S25, to move the releasing
cam S8 away from the ratchet wheel S so as to allow its pawl S7 to engage there-
with, it being remembered that the pawl has been carried back with the stepped
disc S. As the pawl drops into engagement with one of the teeth of the constantly
revolving ratchet wheel, the controller S³, with its discs S4, S5, S6, is carried with
the movement of that wheel until the pawl again arrives at the position shown
in Figure 40, when it is disengaged from the ratchet by means of the cam S8 acting
upon the projection S. The last part of the return movement of the controller S
operates through the pin S2, the disc S³, and the spur S28, to move the releasing
rod S toward the right, that rod being at this time opposite to the lowest portion
of the flange of the cam S. This movement of the releasing rod S23 operates
through the inclined grooves $25, to move the releasing cam S8 toward the ratchet
wheel so as to again support the projection S10 of the pawl S7 and hold it out of
engagement with the ratchet wheel during its subsequent resetting operation.
That movement of the releasing rod $2 toward the right also operates by reason
of the engagement of its shoulder S with the clutch fork $30, to move the
clutch Y out of engagement with the driving clutch Y, thus permitting the word
shaft Y³ to stand still until again re-clutched by the operation of the step S21 in
the next recurring revolution of the governor cam S¹º.
The sliding clutch X5 upon the shaft X-Figure 6-is normally pressed toward
the left or engaging position, by means of its clutch fork X urged by the spring X.
That clutch is provided with a spur X-Figures 6 and 52-which is urged by the
action of the spring X against the adjacent bearing. The latter is provided with
a recess, as shown in Figure 52, into which the spur X" is forced by the action of
its spring at each revolution of the shaft X', thereby disengaging it from the
clutch X. As the rotation of the shaft X' is continuous, the clutch X will, after
passing by its engaging point with the clutch X, be again forced out by means of
the inclined leading surfaces of the spur X", so as to be in position to re-engage
its clutch at its next revolution if the conditions so require. The left hand end
of the clutch fork X is located in the path of the pin X fixed in the disc S5, as

page_text: shown in Figure 36, and that pin is so located in the disc with relation to the
pawl S7, as to hold the clutch fork X and its clutch X5 in engagement with the
clutch X, as shown in Figure 6, when the pawl is in the position of rest shown
in Figure 40, so that the clutch X5 will not be disengaged from its mate X6 while
thus supported by the pin X, even when its spur X is passing by the recess
shown in Figure 52, at which point it would otherwise disconnect, as shown in the
latter figure. The effect of thus holding the clutch X5 in its engaging position,
operates to continue the rotation of the shaft X2, and thus causes the repetition of
the movement of the line grab mechanism by means of the crank F5.
The clutch X is splined to, and fitted to slide upon, the shaft X2-Figure 5-,
and is operated by means of the fork X13. That fork is pivotted at X upon the
frame W, its opposite end being connected by means of the link X 15
with the bell crank lever arm X16, pivotted upon the frame W.
That bell crank lever is located adjacent to the indicator arm X 17
which is pivotted upon the frame W, as shown in Figure 3. One edge of that arm
is located in the plane of movement of the line grab separator slide E, so that the
latter when moved up from its lowest position by an advancing line, operates to
engage with the indicator arm X" and to hold it in its vertical position shown in
Figures 3 and 5, thus operating through the bell crank X1, link X15, and fork X13,
to hold the clutch X in engagement with the clutch X8 which is fast on the
shaft X. That part of the indicator arm X" which is adjacent to the separator
slide E, when the latter is in its lowest position, is cut away so as to allow the
indicator arm to swing toward the right from the position shown in Figure 3,
allowing the clutch X7 to be disengaged from the clutch X8 by the action of the
spring 18 Figure 8. Thus the clutches are held in engagement whenever the
separator slide is raised above its lowest position by an advancing line, and are
allowed to disengage only when the slide E is in its lowest position, or in other
words, when no line is brought within the range of operation of the machine.
By a comparison of this description with that of the operation of the line grab,
it will be understood that whenever a line has been brought within the range of
operation of the separators, it will be engaged by the line grab and carried up into
the measuring plane, and that the measuring devices being actuated by the cam
upon the shaft X³, will also be put in operation because of the engagement of the
clutches X and X8.
The clutch X8 is provided with a flange in which is located a slot or recess X 20,
shown in Figure 47 (Sheet 18), that slot being large enough to allow of the
entrance therein of the stop arm X19. The remaining unnotched portion of the
flange of the clutch XS operates through the arm X to hold the clutches X, X8, in
engagement until the clutch, and with it the shaft X³, has completed its rotation,
even though the indicator arm X17 should fail to so hold them by reason of the
absence of a line, as previously described. In such a case, the spring X18 will
press the arm X 19 against the periphery of the flange of the clutch X8 until the
latter reaches that part of its rotation shown in Figure 47, bringing the notch X20
opposite to the arm X1, which therefore enters the said notch and allows the
clutch X' to be released, and also serves to hold the shaft X3 and its mechanism
in a certain definite position, it being desirable that all of the devices actuated by
the cams upon this shaft should occupy the same definite position when at rest.
A brief description will now be given of the complete operation of the entire
machine under normal conditions in which there is no interruption in the continuity
of the advancing line of type, so that by the time the apparatus has completed that
line, the succeeding line is in position to be carried up by the line grab. Under
these circumstances, the indicator arm X17 is constantly held in the position shown
in Figures 3 and 5, thus operating through the bell crank X16 and the clutch fork X 13
to hold the clutch X7 in engagement with the clutch X8 so keeping the shafts X2
5 and X3 clutched together. While waiting for a line, the governor is released and
rests in the position shown in Figures 35 and 40, the measuring lever G being in
its horizontal position shown in Figure 1, so that the setting racks rest in their
lowest position.

page_text: ⋅
The position at which the line grab rests with its new line while waiting for
the completion of the justification of the previous line is preferably just below the
measuring zone, so that the leading end of the new line carried by it shall rest just
below the star wheels H8 and 19-Figures 8 and 9. The first movement, there-
fore, of the line grab upon the completion of the previous line is to carry the new
line into the measuring zone, moving the star wheels as the separators pass by, so
that their respective mechanisms are moved to the proper position corresponding
to the number of separators contained in the line. The line is raised by the line
grab high enough to enable the measuring pawl G3 to engage beneath and support
the line. The stepped jaw I, having been set in the manner already described by
means of its star wheel Iº, now rests with its proper step in position to be engaged
by the upper end of the line, while the fulcrum having been moved to its proper
point by the joint operation of its star wheel H8, and its cam H7, stands in proper
relation to the measuring lever. At the same time, the selector crosshead N is
raised to its uppermost position by means of its cam N13 so as to hold tho
latches N and P out of the path of their racks, as shown in Figures 19 and 21.
The measuring operation now commences. The line engaging end G³ of the
measuring lever is moved upward by means of its cam G-Figure 8-until its
upward movement is arrested by the closing up of the line between the pawl G³
and the proper step of the jaw I, the cam G being enabled to complete its full
stroke by the yielding of the spring G6, as previously described. The upward,
movement of the measuring lever, multiplied to its proper ratio by the position of
the fulcrum, operates to lift the setting racks G, G18, to their required position,
where they are retained by their detent N7. At this time the selector crosshead
is allowed by its cami N13 to be lowered so that its latch N2-Figure 19-rests
against whichever one of the steps N³, N, or N5 of the setting rack G" may have
been brought within its zone of action by the measuring operation. At the same
time the correcting slide P descends to a point where its latch 1" is supported by
one of the corresponding steps of the setting rack G18, and the spacer selecting
mechanism being thus set to the position required by the measurement of the line,
is ready to co-operate with the other mechanism to eject, assemble, and inject, the
proper spacers or spacer combinations, and to extract the word separators. The
line separator of each line is extracted by the operation of the cam Q during
the operation of the measuring devices upon the succeeding line.
During this time also, the stop S16 has been raised to its proper height by the
operation of the star wheel H8-Figure 34--so as to engage the proper step of the
governor disc S6, corresponding to the number of spaces in the line to be justified,
and that step of the disc has been brought against the stop S16 by the action of its
weight upon being released from the detent S13 by means of the step $20 of the
governor cam S1. At the conclusion of the measuring operation, the selector
crosshead N and the correcting slide P having come to their proper positions, the
clutch Y on the shaft Y Figure 6, is brought into engagement with the
clutch Y by the operation of the step S1, thus serving to set in motion the word
- shaft mechanism. The same movement of the rod S which starts the shaft Ye
also serves to release the pawl S7, which drops into engagement with the ratchet Sa
simultaneously with the starting of the word shaft Y2, and the word mechanism
being thus set in motion operates to eject, assemble, and inject the spacers or
spacer combinations determined by the position and operation of the selecting
and correcting devices, repeating its operation for each of the spaces in the line,
under the control of the governor devices, which hold the clutch Y6 in engagement
until it has made the proper number of revolutions sufficient to bring the con-
troller S3 to the position shown in Figure 40, at which time the pin S2 in the
disc S will have come in contact with the spur S28 and moved the clutch Yo out of
engagement by means of the clutch fork $30, so as to allow the word shaft Y2 and
the word mechanism actuated thereby, to come to rest. At the same time, the
pin X, fixed on the disc $5, will have been brought against the fork X so
as to keep the clutch X in engagement with the clutch X6, and thereby continue
the rotary motion of the sections X2 and X3 of the line shaft, thereby bringing

page_text: up and measuring another line, repeating the operation as long as there is a line
within the range of action of the indicator arm X".
If
line
no
has been brought within the range of action of
the indicator arm X", that arm, being unsupported, will oscillate toward
the right from the position shown in Figure 3, thereby allowing the clutch X'
to be disengaged from its mate X when the latter has reached that point in its
rotation represented in Figure 47, at which the notch X20 in the flange of the
clutch is brought opposite to the arm X, which then enters the notch, serving then
to hold the clutch, and hence the mechanism carried by the shaft X3, in a fixed
position until again released by the operation of another line upon the indicator
arm X17
At the conclusion of the justification of each line, the selecting and correcting
devices remain in the position at which they stood at the time of justifying the
last space in the completed line, and these devices remain in that position until the
commencement of the measuring operation upon the next line, during the first
part of which, as above described, the selecting crosshead N is raised to its upper-
most position by the operation of the cam N13, whereupon the correcting mechanism
is released and allowed to return to its original or starting position, as explained
in the description of the selector correcting mechanism.
The selecting devices herein shown can be operated independently of the correct-
ing devices, which are in the nature of an auxiliary device thereto.
The measuring lever is herein shown as being a compound structure consisting
of the two principal members G and G6, but this is a constructive feature merely,
devised to secure compactness. It is evident that the lever G, if made long
enough at its left hand end to secure the required multiplication of its movement,
would give precisely the same results, the desired object being to multiply the
deficiency existing in the measured line to such an extent as, to enable the sub-
divisions thereof to be utilized in selecting the proper spacers, inasmuch as the
indications of those deficiencies, if not enlarged, would be too fine to enable
mechanism to act upon them with certainty in the practical operation of the
imachine.
Although the measuring lever G and the secondary lever G16 both turn upon
pivots, and their ends therefore would seem to describe circular arcs from those
pivots, yet it will be observed that all of the measurements communicated througli,
and multiplied or otherwise varied by, the measurements of the lever G, invariably
bear a constant relation to each other. This is due to the fact that the movements
are communicated to, and transmitted from, the lever G, upon straight lines
which are tangential to arcs struck from the respective pivots. In this way the
measured deficiency of the line, and the resultant movement of the racks, are to
each other as the altitudes of similar right angled triangles. Inasmuch as the
lever. G is pivotted to the measuring slide G2, it follows that that lever G must
move toward the right with relation to its fulcrum block G" in moving from the
position shown in Figure 44 to those of Figures 45 and 46, to an extent equalling
that by which the secant exceeds the radius of the arc of its movement.
Many of the features of this invention, and particularly this one of the measur-
ing lever, are capable of a more extended application than is or can be herein
shown. They may be employed, for example, in type writing, type casting, matrix
making and linotype machines, and I claim for those features, a protection com-
mensurate with their joint novelty and usefulness in this as well as in other
branches of the art to which they may be applicable.
Various mechanical, equivalents may obviously be substituted for many of the
devices herein shown and described, and different forms or various applications of
springs may be substituted for those shown without essentially altering the nature
of the function or the practical operation of these parts in their relation to the
general scheme of the machine. For example, the measuring lever may be bell-
cranked in form so as to transmit the measurement of the shortage of the line in a
direction at right angles or at any other angle to its present direction. The

page_text: stepped jaw, which is herein shown as being incapable of movement in the direction
of the length of the line, may be incorporated with, or substituted for the pawl G³,
upon the measuring lever. In like manner many of the parts may be transposed
as to position, or direction, or sequence of operation, and many similar modifica-
tions may be made in the various elements, or equivalent elements may be
substituted therefor, without departing from the general scope and intent of this
invention.
The operation of the measuring lever may be varied by first moving its type-
engaging end against the line of type to be measured, and then moving the fulcrum
to its desired position, which would, of course, operate to move the selector setting
devices to the same position that would be occupied by them if operated in the
sequence described herein. This transposition of the relative times of movement
of the parts may be obtained by suitably changing the form and adjustment of
the cams G and H7, the adjusting quills being rotated to their desired position in
the same manner and at the same time as herein described.
The elevating raceway or table L¹ is utilized in a three-fold capacity. It serves
as a support for the basic or A. spacers by means of which the desired number of
those spacers is lowered into the position which permits of their being removed
from the channel by the assembling plunger 01; serving them in its second
capacity as a raceway upon which those spacers are moved along to the position
adjacent to the raceway 06, as shown in Figure 30. As the level of the raceway 06
is coincident with that of the lower end of the channel L, it follows that the top
surface of the A spacers thus removed from the channel will also be coincident with
the surface of that raceway, as shown in the latter figure, thus enabling the spacers
B, C, or D, to slide from their raceway directly upon the A or basic spacers, as
shown in Figure 31. Immediately following this point in its operation, the table
raceway L¹ serves in its third capacity, by the operation of its lifter O*, to raise the
assembled combination of spacers to the level of the injecting plane.
«
" 66
The terms space,' separator" and "spacer" are herein used advisedly in
order to avoid the confusion of terms and of ideas which otherwise might occur
in referring to the three particular features to which we have applied these
designations. As herein used, the word " space" refers to the actual space
occurring between adjacent words, regardless of the object which occupies the space,
or whether it is occupied at all. By the word "separator" we mean the pieces U
and T, which are temporarily placed between the words and the lines respectively in
order to temporarily maintain the separation between them, and by the term
spacer" we refer to the final type body which is inserted in each of the spaces
of a line.
<
By the terms "shortage" or "deficiency” of the line, as herein employed, we
refer to the amount by which the measured line falls short of the required length,
the "shortage" being therefore equal to the aggregate length of the justifying
spacers required to exactly fill out that line, as above explained.
For convenience and clearness of reference, that part of the governing mechanism
which is herein shown as an integral part, consisting of the discs S4, S5 and S6, is
herein referred to as the controller.
The governing devices herein shown are capable of application to other machines
of this class, which are either wholly or partly automatic. In the latter case, the
releasing devices of the governor may be so connected to the key board of the
composing machine, as to permit of being released by the operator at the con-
clusion of the measurement of each line.
Many of the parts which are herein preferably arranged in pairs for practical
reasons, may by suitable modification, and in some instances without any modifica-
tion, be used singly. Among the parts herein shown which may be thus used, may
be enumerated the word and line grab pawls, stop fingers and arms. One of the
detents J6 might be omitted, the type engaging lip of the other detent being
adapted to extend across the channel far enough to support the separators, but
such a pawl located on one side of the channel, and therefore coming in contact

page_text: with one side only of the uppermost piece of type which is being pushed past it,
might be liable occasionally to turn that leading piece upon its side. For safety
and certainty, I therefore prefer the double pawls, which react equally upon the
two sides of the type, and do not therefore tend to turn it. This remark would also
apply to the star wheels H8 and I, which are arranged on opposite sides of the
channel so as to simultaneously engage with the opposite ends of the same
separator, and thereby prevent its being tilted. Were it not for this consideration,
the devices which are herein shown to be operated by those two star wheels, might
be operated by one of them alone.
Some of the cams of this machine are herein shown with grooves in which is
located the engaging pin of the connection or part to be operated, the two sides of
the grooves serving therefore to positively control the operation of the connected
part in both of its moveable directions. Other cams are shown. without such a
closed groove, the engaging pin being held against the surface of the cam by means
of a spring or weight. These two well-known forms of cams are considered by me
to be equivalent constructions, the spring or the weight used in connection with
the so-called open cam, serving as the equivalent of one of the sides of the grooves
of the closed cam. Both kinds of cams are shown herein in accordance with my
preferences under the conditions controlling each cam-operated device.
The fulcrum setting device herein shown may be modified by dispensing with one
of the quills, a spring or weight being employed to bring the fulcrum back against
the step of the slide which has been previously moved to determine the position of
the fulcrum, but I prefer to employ the two quills, as herein shown, inasmuch as
I thereby provide a more positive means of operating the devices. I therefore do
not desire to be limited in my claims to the employment of this double form of
stepped quill, excepting so far as that construction is specifically claimed herein.
Having now particularly described and ascertained the nature of my said inven-
tion and in what manner the same is to be performed, I declare that what I
claim is:-
1. The combination with a type containing channel provided with shoulders
adjacent to the ends of the type, whereby the character type are preserved in
alignment, of a separator having a body corresponding substantially to the bodies
of the character type, and having shouldered ends agreeing with the length of
the character type, whereby it is retained in alignment therewith by. the channel,
and having thinner ends adapted to project through and beyond the end walls of
the type channel for the purposes specified; substantially as described.
2. The combination with a type containing channel, provided with shoulders
adjacent to the ends of the type, whereby the character type are preserved in
alignment, of word and line separators having bodies corresponding substantially,
to the bodies of the character type, and having shouldered ends agreeing with the
length of the type, whereby they are retained in alignment by the channel, and
having thinner ends adapted to project through and beyond the end walls of the
type channel, the ends of the line separators projecting beyond the ends of the
word separators for the purposes specified; substantially as described.
3. Means for separating the line of type at predetermined points therein indicated
by separators which extend beyond the character type, consisting of a carriage or
slide having pivotted thereto one or more stop arms adapted to rest upon the project-
ing ends of the separators, and one or more stop fingers adapted to engage beneath
the projecting ends of the separators, with means for holding the stop arms and
fingers in engagement with the separators, whereby their carriage or slide is moved
with and by the type, the said means being adapted to disengage those arms and
fingers at the desired point in the movement of the carriage; substantially as
described.
4. Means for separating a line of type at predetermined points therein indicated
by separators which extend beyond the character type, in combination with the
type channel adapted to align and guide the type and their inserted separators; a

page_text: carriage or slide adapted to be moved parallel with the type channel, and having
a stop arm and a stop finger pivotally mounted thereon with their working ends
adapted to engage the separators between them; and means for holding the arm and
the finger in engaging relation with the end of the separator during a portion of
the stroke of the carriage, and for removing it therefrom at the end of that stroke
for the purpose specified; substantially as described.
5. The herein described means of separating a line of type at predetermined
points therein indicated by separators, the ends of which extend beyond the ends
of the type bodies, consisting of a type channel adapted to receive and guide a line
of type; a carriage or slide adapted to slide upon ways parallel with the type
channel a carriage having pivotted thereon on opposite edges of the channel, a pair
of oppositely disposed stop arms, and a pair of oppositely disposed stop fingers, each
located adjacent to its corresponding stop arm, with which it is adapted to co-operate
in engaging the adjacent projecting end of one of the separators; means for
holding the stop arms within the path of the ends of the separators during a
portion of the movement of the carriage, and for moving them out of that path
at the conclusion of the carriage stroke; with springs adapted to hold the stop
fingers in engaging relation to the separators during the carriage stroke; and means
for removing them therefrom toward the conclusion of the stroke; substantially
as described.
6. The combination with a type channel adapted to receive and guide a line of
type having separators projecting beyond the bodies of the character type, of means
for separating the lines at the points indicated by the separators, consisting of a
separating carriage or slide, provided with stop arms and fingers adapted to engage
with the projecting ends of the separators, whereby the carriage is carried along
by the movement of the line; and a reciprocating line grab or carrier adapted to
engage with the separating carriage mechanism, and to carry it with its engaged
line away from the rest of the line, the line carrier being provided with a pawl and
with a spring adapted to move the pawl into the space formed by the separation of
the line, whereby the separated line is transferred to the carrier."
7. The combination with a type channel adapted to receive and guide a line of
type having separators projecting beyond the bodies of the character type, of means
for separating the lines at the points indicated by the separators, consisting of a
separating carriage or slide, provided with stop arms and fingers adapted to engage
with the projecting ends of the separators, whereby the carriage is carried along
by the movement of the line; a reciprocating line grab or carrier adapted to engage
with the separating carriage mechanism, and to carry it with its engaged line away
from the rest of the line, the line carrier being provided with a pawl and with
a spring adapted to move the pawl into the space formed by the separation of the
line, whereby the separated line is positively engaged by the carrier; and means
for moving the stop arms and fingers out of engagement with the carrier to release
the carriage from the line when thus transferred therefrom to the carrier; substan-
tially as described.
8. In a type justifying machine, the combination with a measuring lever pro-
vided at one end with type engaging means moveable to an extent represented by
the aggregate shortage or required spacing of the line, and provided with an
adjustable fulcrum, of means for moving the fulcrum to a suitable position relative
to the said lever in accordance with the number of spaces occurring in the line,
whereby the aggregate shortage of the line is converted into a suitably related
movement of the opposite end of the lever; substantially as described.
9. In a type justifying machine, and in combination with the spacer selecting
devices thereof; the herein described measuring lever provided at one end with type
engaging means arranged to move to an extent representing the aggregate shortage
or deficiency of the line, a moveable fulcrum, with means for moving the fulcrum to
a position on the said lever suitably related to the number of spaces in the line,
the other end of that lever being connected with the selecting devices whereby they

page_text: are set to the proper positions for the selection of the required size of spacer or
spacers; substantially as described.
10. In a type justifying machine, a measuring lever provided with a fulcrum,
and operatively connected at its ends with a slide adapted to move in tangential
relation to the movement of the lever upon its fulcrum, the slide being located
adjacent to and, adapted to engage with the line of type to be measured; substan-
tially as described.
11. In a type justifying machine, a measuring lever provided with a fulcrum,
and operatively connected at one end with the measuring devices, and at the other
end with the spacer selecting devices, the connections of the lever with those devices
being such that the latter are enabled to move in tangential relation to the move-
ment of the said lever upon its fulcrum; substantially as described.
12. In a type justifying machine; the combination of a measuring lever; a
fulcrum on which the lever is pivotally mounted, adapted to be moved to different
positions with relation to the said lever; a measuring slide pivotally connected
with one end of the lever; and a measuring pawl mounted upon the slide and
adapted to engage with the line of type; substantially as described.
13. In a type justifying machine, the combination of a measuring lever; a
fulcrum adapted to pivotally support it and to be moved to different positions
with relation thereto; a measuring slide and pawl pivotally connected at one end
of the said lever and mounted to move in tangential relation thereto; and a
secondary lever pivotally mounted adjacent to that lever; and operatively connected
therewith by means of a tangentially moving slide; substantially as described.
14. In a type justifying machine and in combination with the selector setting
devices thereof; a measuring lever; a fulcrum adapted to pivotally support it and
to be moved to different positions with relation thereto; a line measuring slide and
pawl pivotally connected at one end of the said lever and mounted to move in
tangential relation thereto; and a secondary lever pivotally mounted adjacent to
that lever and to the setting devices, and tangentially connected with each of
them, whereby the measured deficiency of the line and the resultant movement of
the setting devices are to each other as the altitudes of similar right-angled
triangles; substantially as described.
15. A device for moving a slide or other object in irregular sequence from point
to point, consisting of a quill adapted to move longitudinally, having steps arranged
longitudinally on it in accordance with the desired positions of the slide, means
for rotating the quill so as to bring the desired step into the path of the object to
be moved, and means for moving the quills longitudinally to the extent desired;
substantially as described.
10. In combination with a measuring lever having a movable fulcrum; means
for moving that fulcrum to desired points consisting of two oppositely stepped
quills, the steps being located longitudinally thereof in accordance with the desired
positions of the fulcrum; means for rotating the quills to bring the desired step
into operative relation to the fulcrum; and means for moving the two quills
toward and from each other, for the purpose specified.
17. In a type justifying machine, and in combination with the measuring lever
thereof having an adjustable fulcrum, means for adjusting that fulcrum irregularly
to desired points, consisting of a pair of quills arranged adjacent to, and parallel
with, the path of the fulcrum; means whereby the quills are rotated to a proper
position with relation to the number of spaces in the line, the quills being provided
with correspondingly located steps adapted to be brought into engagement with the
fulcrum; and means for moving the quills longitudinally towards and from each
other; substantially as described.
18. In a line measuring device, a pair of jaws for engaging the opposite ends
of the line, one of the jaws being movable laterally of the line, and provided with
stepped engaging surfaces, for the purpose specified.
19. In a line measuring device; the combination of a movable jaw provided
with steps adapted to compensate for and eliminate from the resultant measure-

page_text: ment, the extraneous matter contained in the line; and means operable by the
extraneous matter, adapted to move the proper step of the jaw into engaging
position; substantially as described.
20. In a type justifying machine and in the line measuring devices thereof; a
movable jaw provided with steps each corresponding in height to the thickness
of the special separators contained in the line, whereby the measurement of the
said separators is eliminated from the resultant measurement; substantially as
described.
21. In a type justifying machine and in the line measuring devices thereof; the
combination of a movable jaw provided with steps corresponding in height to
the thickness of special separators contained in the line; and means operable by the
said separators, adapted to move the proper step of the jaw into engaging relation
to the line, whereby the measurement of the said separators is eliminated from the
resultant measurement; substantially as described.
22. In a type justifying machine and in the measuring devices thereof; the
combination with temporary separators inserted at desired intervals in the line to
be measured, of a jaw arranged and adapted to be moved transversely to the line,
provided with steps each corresponding in height to the thickness of the temporary
separators of the line; a stop; and means operable by the separators adapted to
move that stop to a suitable position relative to the stepped jaw, whereby the latter
is held with its proper step in engaging relation to the line; substantially as
described.
23. The herein described galley plunger, provided with a pawl which is adapted
to yield under the tension of a spring when the plunger is in its open or type-
receiving position and with means for locking the pawl so as to form a fixed part of
the face of the plunger when the latter is operated for the purpose of pushing a line
into the galley.
24. In combination with a galley adapted to receive lines of type, the combination
of a plunger having its type receiving end bevelled to allow of the entrance of the
type; a pawl pivoted upon the plunger, with its working edge in line with the
general line of the face of the plunger; and a spring or its equivalent adapted
when the plunger is in its type-receiving position to press the pawl toward the
position in which it aligns with the plunger, whereby the pawl is enabled to yield
to allow the type to be pushed into the galley; substantially as described.
25. In combination with a type-receiving galley having its end wall located in
line with the side of the type channel and provided with a shoulder J5 adapted to
support the type; a plunger located with the general line of its front face adjacent
to the end wall of the galley, and at a distance therefrom substantially less than the
thickness of the type, the type-receiving end of the plunger being bevelled to allow
of the entrance of the type, and a spring-pressed pawl pivotted upon the plunger
with its type-engaging face completing the general line of the face of the plunger,
arranged to yield sufficiently to allow the type to enter, and operating to push the
type upon the shoulder J5, as it is raised above that shoulder; substantially as
described.
26. In combination with a type-receiving galley, having its end wall located in
line with the side of the type channel, and provided with a shoulder J5 adapted to
support the type; a plunger located with the general line of its front face adjacent
to the end wall of the galley and at a distance therefrom substantially less than
the thickness of the type, the type-receiving end of the plunger being bevelled to
allow of the entrance of the type; a spring-pressed pawl pivotted upon the plunger
with its type-engaging face completing the general line of the face of the plunger,
arranged to yield sufficiently to allow the type to enter, and operating to push the
type upon the shoulder J5, as it is raised to the height of that shoulder; an
auxiliary slide; and actuating means therefor adapted to lock the pawl before
moving the plunger, whereby the line of type is held in a straight line while being
pushed laterally into the galley.
27. In a machine of the class specified and in combination with the type receiving

page_text: galley thereof; a line carrying plunger having a portion of its face bevelled to
allow of the entrance of the type; a pawl pivotally mounted thereon, with its front
face normally held coincident with the true or unbevelled portion of the face of
the plunger, and adapted to yield to the extent of the bevelled portions thereof;
and an auxiliary slide adapted to first engage with and lock the pawl in its normal
position and then to move the plunger with its locked pawl; for the purpose
specified.
28. In a machine of the class specified and in combination with the galley
mechanism thereof; a rule and a plunger between which the forming line is
received; an auxiliary slide; and devices appurtenant thereto, adapted to with-
draw the rule, to move the completed line behind the plane of the rule, to release
the rule and to withdraw the plunger, whereby they resume their original or type-
receiving positions; substantially as described.
29. In a machine of the class specified, employing separators between the words,
and in combination with the extractor therefor, a detent located adjacent to the
type containing channel, and adapted to support the separator until extracted;
substantially as described.
30. In a machine of the class specified, employing separators between the words,
and in combination with a grab or lifter for the words; a detent located adjacent
to the type containing channel and adapted to receive the separators from the word
grab; substantially as described.
31. In a machine of the class specified, employing separators between the words,
and in combination with the receiving galley, and with the word grab or lifter,
adapted to engage with the separator, and to carry its word into the galley; a
detent located adjacent to the type channel and to the galley, adapted to receive
the unloaded separator and to support it until extracted; substantially as described.
32. The herein described word grab consisting of a carriage or slide adapted to
reciprocate in a direction substantially parallel with the line, provided with a stop
finger, adapted to be held in engaging relation to the line during a portion of
its reciprocatory movement, and means for moving the stop finger out of engaging
relation to the line at one end of that movement; substantially as described.
33. A word grab consisting of a carriage or slide having a stop finger pivotally
mounted thereon, with means adapted to hold the stop finger in engaging relation
to the line during a portion of its stroke, and to release it therefrom
at the end of the stroke, and means for reciprocating the carriage or slide,
adapted to move it positively toward the upper or releasing end of its
stroke, provided with a connecting spring or its equivalent adapted to enable the
word grab to remain where stopped by the leading word of the line while its
operating means makes its full stroke; substantially as described.
34. In a type justifying machine and in combination with the measuring and
spacer selecting devices thereof, a selector setting rack operatively connected with
the measuring devices, provided with teeth spaced in coincident relation to the
location of the spacer selecting fingers, and with a detent adapted to engage with.
the teeth and support the rack in substantially the highest position to which it
is moved by the measuring devices; substantially as described.
35. In a type justifying machine and in combination with the measuring and
spacer selecting devices thereof; a rack operatively connected with the measuring
devices, and provided with teeth corresponding in pitch to the separation of the
selector fingers, and provided with steps adapted to engage with and support the
spacer selecting devices in positions suitably related to the movements of
the measuring devices; substantially as described.
36. In a type justifying machine and in combination with the spacer selecting
fingers thereof; a rack adapted to be moved by the measuring devices, provided
with teeth corresponding in pitch to the separation of the selecting fingers, and
provided also with steps, and a selector adapted to be supported by the steps of
the rack in engaging relation to the required selecting finger; substantially as
described.
37. In a type justifying machine and in combination with a series of selecting

page_text: fingers adapted to communicate with the channels of the justifying spacers; a
selector capable of being moved into engaging relation with each of the series of
selecting fingers, provided with a pawl adapted to engage with that step of the
setting rack which has been brought within its zone of movement by the operation
of the measuring devices, whereby the selector is held in engaging relation to the
selecting finger of the spacer required by the measurement; substantially as
described.
38. In a type justifying machine; a selector provided with a pawl adapted to
engage with the steps of a setting rack, and with means operatively connected with
the pawl adapted to raise the selector to the top of its zone of movement, and to
hold its pawl out of engagement with the setting rack while the latter is being
moved to its place by the measuring mechanism, and adapted at the conclusion of
the measuring operation to allow the selector pawl to move into engagement with,
and be supported by that step of the setting rack which has been brought within
its zone of movement.
39. In a type justifying machine and in combination with a series of spacer
selecting fingers connected respectively with a series of justifying spacer channels;
a selector having a zone of movement extending across the path of the series of
selecting fingers; a setting rack provided with steps located at a distance apart
equal to the zone of movement of the selector, and provided also with teeth of a
pitch corresponding to that of the selecting fingers; and a détent adapted to
engage with the latter teeth and to support the rack in the position to which it
is moved by the measuring devices; the selector being provided with means
adapted to engage with that step of the rack which is within the zone of movement
of the selector; all arranged and operating to support the selector in engaging
relation to that one of the selecting fingers representing the spacer required by the
measurement of the line; substantially as described.
40. In a type justifying machine and in combination with the measuring devices,
and with the spacer selecting mechanism thereof; a selector setting rack provided
with a progressively stepped cam surface along one edge thereof, and with means
operatively connected with the described basic spacer channel, whereby an
additional basic spacer is brought into extracting relation at each progressive step
of the cam surface of the setting rack.
41. In a type justifying machine and in combination with the measuring devices
and with the described basic table or elevating raceway thereof, adapted to support
a column of the described basic spacers; a setting rack operatively connected with
the measuring devices, and provided with a progressively stepped cam surface, and
an elevator adapted to engage with the cam surface of the rack, and with the basic
table, whereby the latter is lowered to an extent allowing of the extraction of an
additional spacer at each suitably related extent of movement of the measuring
devices; substantially as described.
42. In a machine of the class specified and in combination with a spacer-con-
taining channel, and a supporting table therefor; a stop connected with the table
and provided with steps agreeing in height with the thickness of the spacers
contained in the channel; means for moving the stop to different positions wherein
the table is supported by the desired step; and a lifter adapted to raise the support-
ing table to its uppermost position at each operation of the devices, whereby the
stop is left free to be reset to its desired position for the succeeding operation;
substantially as described.
43. In a machine of the class specified and in combination with the measuring
devices and the spacer selecting devices thereof; a spacer containing channel;
supporting table therefor; means operatively connected with the measuring
devices adapted to lower the table to an extent suitably related to the movement
of those devices and means operatively connected with the selecting devices,
adapted to vary the height of the table in accordance with the requirements thereof;
subtantially as described.
44. In a type justifying machine and in combination with the measuring devices

page_text: and with the spacer selecting devices thereof; a spacer containing channel; a
supporting table therefor; an elevator adapted to govern the height of the table
in suitable relation to the movement of those devices; and a stop operatively con-
nected with the selecting devices, whereby the general position of the table, as
determined by the measuring devices, is modified by the requirements of the select-
ing devices; substantially as described.
45. In a machine of the class specified and in combination with the spacer con-
taining channel; an elevator raceway adjacent to the channel and adapted to serve
as a supporting table for the spacers contained therein; means for lowering the
raceway table to a suitable extent; assemblers for withdrawing the spacers thus
exposed to its action; and a lifter adapted to raise the raceway-table to its original
position; for the purposes specified.
46. The combination of a spacer containing channel; an elevating table or race-
way adapted to support the spacers contained therein; a stop provided with steps
adapted to engage with a suitable support and to hold the table at the different
heights represented by the steps; with means operatively connected with the spacer
selecting devices, adapted to engage with and move the stop so that its proper
stepped face shall engage with its support, whereby one or more of the spacers are
lowered into extracting position; substantially as described.
47. In a machine of the class specified and in combination with the described
basic spacer channel and with a table adapted to support the spacers contained in
the channel; a supporting stop for the table provided with steps corresponding
to the thickness of the spacers contained therein, and with means operatively con-
nected with the spacer selecting devices, whereby the stop may be moved to its
different stepped positions for the purpose specified; substantially as described.
48. In a machine of the class specified and in combination with a spacer con-
taining channel and supporting table therefor; a stop connected with the table and
provided with steps agreeing in height with the thickness of the spacers contained
in the channel; means for moving the stop to different positions, whereby it is
supported by the desired step, consisting of a frame provided with spurs arranged
in suitable relation to the steps of the stop; and selecting fingers adapted to engage
with one or the other of the spurs, substantially as described.
49. In a machine of the class specified and in combination with the basic table
and with the spacer selecting mechanism thereof; a stop connected with the table
and provided with steps agreeing in height with the thickness of the basic spacers;
means operatively connected with the stop, provided with spurs or engaging
shoulders; and selecting fingers adapted to be moved into engagement with one
or the other of the spurs, whereby the stop may be changed to either one of its
stepped faces, for the purpose specified.
50. In a machine of the class specified and in combination with a spacer con-
taining channel and with the spacer selecting mechanism thereof; a table adapted
to support the spacers contained in the channel; a stop connected therewith, and
provided with stepped supporting faces differing in height to an extent equal to
the thickness of the spacers contained in the channel; and a frame or its equiva-
lent connected with the stop and provided with spurs located thereon corresponding
in number and relative position to the stepped surfaces of the stop; a series of
selecting fingers corresponding in number to the spurs and stepped faces, adapted
to reciprocate adjacent to their respective spurs, and each adapted to be moved by
the spacer selecting devices into engaging relation with its spur, whereby the stop
is moved to a distance which allows the basic table to rest upon the desired step
of stop; substantially as described.
51. In combination with ejecting devices of a type channel and with a con-
trollable selector therefor; a selecting finger adapted to reciprocate in the plane
of the ejecting device and adapted to be raised into engaging relation thereto by
the selector; substantially as described.
52. In combination with the ejecting device for a type channel and with a con-
trollable selector therefor; a selecting finger normally held out of engaging

page_text: relation with the ejecting device and adapted to be moved into engagement there-
with by the selector; substantially as described.
53. In combination with a series of spacer channels provided with a correspond-
ing series of ejecting devices and with a controllable selector therefor;
a corresponding series of selecting fingers each adapted to be moved by the selector
into engaging relation with the ejecting devices; substantially as described.
54. The combination of a series of spacer ejecting levers; a corresponding
series of selecting fingers adapted to reciprocate in engagable relation to the spacer
ejecting levers; and a selector adapted to move across the paths of the selecting
fingers, whereby any one of them may be moved into engaging relation with its
ejecting lever; substantially as described.
55. In a type justifying machine; the combination of a series of spacer channels
and of a series of ejecting devices therefor; a corresponding series of selecting
fingers adapted to reciprocate in engageable relation to the ejecting levers; and a
controllable selector moveable transversely in the paths of the reciprocating
selecting fingers, and adapted to engage with one of those fingers whereby it is
moved into engaging relation with its corresponding spacer ejecting device;
substantially as described.
56. In a type justifying machine and in combination with a spacer channel and
with an ejecting device therefor; a selecting finger; a reciprocating carriage upon
which that finger is pivotally mounted in engagable relation to the ejecting device;
and a spring or its equivalent, adapted to yieldingly hold the finger out of engaging
relation to its spacer ejecting device during the reciprocation of the carriage;
substantially as described.
57. In a type justifying machine and in combination with a series of spacer
channels and with ejecting devices therefor; a corresponding series of selecting
fingers; and a reciprocating carriage on which those fingers are pivotally mounted
in engagable relation to their respective ejecting devices, each finger being provided
with a spring or its equivalent adapted to yieldingly hold the finger out of engaging
relation to its ejecting device; substantially as described.
58. In a machine of the class specified and in combination with the selector
setting rack thereof; a correcting rack provided with a series of teeth relatively
finer than those of the selector setting rack; and a detent adapted to engage those
teeth, whereby the correcting rack may be detained in a displaced position with
relation to the selector setting rack; for the purpose specified.
59. In a machine of the class specified and in combination with the measuring
devices and with the spacer selecting devices thereof; a setting rack provided with
teeth of a pitch corresponding with the location of the selecting fingers for the
different sizes of spacers; a correcting rack provided with teeth finer than those
of the setting rack, and arranged serially in relation to each of the teeth thereof;
and a detent adapted to engage with and support the racks in the relatively
displaced position to which they may be moved by the operation of the measuring
device.
60. In a type justifying machine; a spacer selector provided with teeth suitably
related to the amount of the desired correction; a pawl adapted to engage with the
teeth and to actuate the selector; and a detent adapted to detain the selector in
its intermediate positions and to release the selector when the desired amount of
correction is obtained.
61. In a machine of the class specified and in combination with the spacer
selecting fingers and with a selector therefor; means for moving the selector from
one finger to another for the purpose specified, the selector being provided with
teeth suitably related to the desired amount of movement; a pawl adapted to move
the selector to the extent determined by the measuring operation; and a detent
adapted to retain the selector in its intermediate positions and to release it when
the desired correction is secured.
62. In a type justifying machine and in combination with the measuring devices
thereof; a correcting rack operatively connected with the said devices, adapted to

page_text: be detained in the extreme position to which it is moved by them and provided
with a series of supporting steps; and a correcting slide provided with a pawl
adapted to engage with the supporting steps of the correcting rack, whereby the
correcting slide is supported in a position suitably related to the movement of the
measuring device; substantially as described.
63. In a type justifying machine and in combination with the measuring
devices, and with the spacer selecting devices thereof; means operatively connected
with the measuring devices, adapted, when the indicated measurement of the line
does not exactly require one of the regular spacers, to hold the selector in engaging
relation to the next smaller spacer; a correcting slide; and means substantially
as described for holding that correcting slide above the selector to an extent
suitably related to the correction required.
64. In a type justifying machine and in combination with the measuring
devices and with the spacer selecting devices thereof; a pair of setting racks pro-
vided with similarly stepped supporting surfaces; means adapted, when the spaces
in the measured line will not be exactly justified by either size of justifying spacers,
to support one rack above the other to an extent suitably related to the indicated
discrepancy; a pawl or its equivalent attached to the selector, and adapted to rest
upon the steps of its rack; and a correcting slide provided with a similar pawl
adapted to engage with the correcting rack, whereby the correcting slide is elevated
above the selector to an extent corresponding to the relative displacement of the
setting racks; substantially as described.
65. In a machine of the class specified and in combination with the selector
cross head and the correcting slide; a pair of setting racks controlled by the
measuring devices of the machine and provided with a series of steps adapted to
support the cross-head and the correcting slide in suitable relation to each other
according to the desired amount of correction, substantially as described.
66. The combination of a pivotally mounted correcting lever; a pawl lever
pivotally mounted thereon; a cam adapted to engage with the pawl lever; and
means operatively connected with the movable end of the correcting lever, adapted
to carry the pivot of the pawl lever to a suitable position relative to the cam; for
the purpose specified.
67. In a machine of the class specified and in combination with the selector
thereof provided with, suitable engaging teeth; a pivotally mounted correcting lever;
a pawl lever pivotally mounted thereon, the latter being provided with a pawl
adapted to engage with the teeth of the selector; a cam adapted to engage with
the pawl lever; and means adapted to support the correcting lever in suitable,
relation to the cam, whereby the desired amount of motion may be communicated
to the selector by means of a cam.
68. In a machine of the class specified and in combination with the selector and.
with the cross-head on which the selector is mounted; a correcting lever pivotally.
mounted upon the cross-head; a pawl lever pivotally mounted thereon and pro-
vided with a pawl adapted to engage with the teeth of the selector; a reciprocating
cam adapted to engage with the pawl lever; and a correcting slide adapted to
support the pivot of the pawl lever in a position with respect to the cam suitably
related to the desired amount of movement of the pawl; substantially as described.
69. In a machine of the class specified and in combination with the selector
cross-head adapted to be set to different positions; a correcting lever mounted upon
the cross-head; a pawl lever pivotally mounted upon the correcting lever and
provided with a pawl adapted to engage with suitable teeth on the selector; a
series of reciprocating cams arranged in coincidence with the several positions of
the cross-head; and means substantially as described adapted to support the pivot
of the pawl lever in a relation to the actuating face of the adjacent cam suitably
adapted to the amount of correcting movement required of the pawl.
70. In a machine of the class specified and in combination with the selector
cross-head; the correcting slide and the setting rack therefor controlled by the
measuring devices of the machine; a correcting lever having its ends pivotally
T

page_text: mounted upon the cross-head and the correcting slide respectively; a pawl lever
pivotally mounted upon the correcting lever, provided at one end with a pawl
adapted to engage with suitable teeth on the selector; and a reciprocating cam
adapted to engage with and operate the pawl lever, substantially as described.
71. In a machine of the class specified and in combination with a series of spacer
selecting fingers; a selector and its cross-head adapted to be moved into coincident
relation to either of the fingers; correcting devices mounted upon the cross-head;
and a series of cam pieces arranged in corresponding relation to the fingers, and
adapted to actuate the correcting devices, all arranged and operated to advance the
selector to the next selecting finger; substantially as described.
72. In a machine of the class specified and in combination with a series of
selecting fingers, and a corresponding series of cam pieces; a reciprocating carriage
on which the fingers and the cam pieces are mounted; a selector and its cross-
head adapted to be moved into operative relation to each of the fingers; and a
correcting device mounted in the cross-head and adapted to engage with the
adjacent cam of the series, whereby the selector is advanced into engaging relation
with the next higher finger of the series in accordance with the required correction;
substantially as described.
73. In a machine of the class specified and in combination with the spacer
selector thereof provided with suitable engaging teeth; a pawl pivotally mounted
adjacent to and adapted to engage with the teeth of the selector; a reciprocating
carriage provided with a cam adapted to move the pawl to the desired extent, the
carriage being operatively connected with the pawl, whereby it holds the latter
into operative engagement with the teeth of the selector during the operation of
the cam; substantially as described.
74. In a machine of the class specified and in combination with the spacer
selector thereof provided with suitable engaging teeth; an actuating pawl mounted
adjacent to and adapted to engage with the teeth; and a reciprocating carriage
provided with a cam; all arranged and operating during the stroke of the carriage
in one direction to hold the pawl into engagement with its teeth and to actuate it
to the desired extent, and operating to withdraw the pawl from the teeth during
the return movement of the carriage; substantially as described.
75. In combination with the selector provided with suitable engaging teeth, and
with an actuating pawl therefor; a detent adapted to engage with the teeth of the
selector; and an escapement pawl pivotally mounted upon the selector, and adapted
to release the detent from the teeth of the pawl at predetermined points thereof;
substantially as described.
76. In combination with the selector provided with suitable teeth and with an
actuating pawl therefor; a detent adapted to engage with and support the teeth of
the selector; and an escapement pawl pivotally mounted upon the selector; the
detent and the escapement being provided with inter-engaging portions adapted
to release the detent from the teeth of the selector at suitable predetermined
positions of the latter; substantially as described.
77. The combination of a selector; a detent therefor; and an escapement pawl
for the detent, pivotally mounted upon the selector; an escapement wheel rotatably
mounted on the selector and provided with teeth adapted to engage with and
support the escapement pawl in a non-engaging relation to the detent; and actuat-
ing means adapted to rotate the escapement wheel to a position which permits the
escapement pawl to come into releasing engagement with the detent.
78. In combination with a type containing channel; means for extracting
matter therefrom and distributing it in two or more different locations, consisting
of an extractor adapted to engage with the matter to be extracted and arranged in
operative connection with two or more cams or their equivalents, adapted respec-
tively to move the extractor to the desired locations; substantially as described.
79. In combination with a type containing channel and with the type separators
thereof; means for extracting the separators therefrom and distributing them in
different channels, consisting of an extractor adapted to engage with the separators,

page_text: arranged in operative connection with two independent cams, or their equivalents
adapted respectively to move the separators into distributing relation to their
respective receiving channels; substantially as described.
80. In a machine of the class specified and in combination with separators
adapted to indicate the separations between the words and between the lines
respectively; an extractor adapted to engage with the separators; two cams or
their respective equivalents, arranged in operative connection with the extractor
and adapted to move that extractor so as to carry the two kinds of separators to
their respective receiving channels; substantially as described.
81. In an assembling device for type matter; the combination of a fixed and a
movable raceway located side by side, with means adapted to depress the movable
raceway relative to the fixed raceway to an extent corresponding to the amount of
type matter on the movable raceway; for the purpose specified.
82. In an assembling device for type matter; the combination of a fixed raceway
and of a movable raceway adjacent thereto; means for moving the type matter
along those raceways toward their meeting edges; and means for depressing the
movable raceway to an extent corresponding to the amount of type matter thereon;
whereby the surface of that type matter is substantially coincident with the plane
of the fixed raceway, for the purpose specified.
83. In an assembling device for type matter; the combination of a fixed race-
way; a channel for the type matter having its lower open end located in the plane
of the fixed raceway; a movable raceway located adjacent to the fixed raceway,
and having a portion of its surface underlying the open end of the channel, and
adapted to support the type matter contained therein; means for depressing the
movable raceway so as to permit the withdrawal of the desired amount of matter
from the channel; and an assembling plunger adapted to move the type matter
thus withdrawn from beneath the channel toward the fixed raceway; substantially
as described.
84. An assembling device for type matter, consisting of a fixed raceway; a
channel for the type matter having an open end located in the plane of the fixed
raceway; a moveable raceway located adjacent to the fixed raceway and having a
portion of its surface underlying the channel and adapted to support the type
matter contained therein; means for depressing the moveable raceway so as to
permit the withdrawal therefrom of the desired amount of type matter; am
assembling plunger adapted to move the type matter thus withdrawn from the
channel toward the fixed raceway; and an assembler adapted to move type matter
along the fixed raceway, and upon the matter contained on the movable raceway.
85. In a machine of the class specified and in combination with a fixed raceway
and with spacer containing channels adjacent thereto; a basic spacer channel having
its lower open end located in the plane of the fixed raceway; a moveable raceway
located adjacent to the fixed raceway and having a portion of its surface adapted
to serve as a supporting table for the spacers contained in the basic spacer channel;
means adapted to select and eject the desired spacer upon the fixed raceway, and
adapted to depress the moveable raceway so as to allow of the withdrawal of the
desired number of basic spacers from the channel; and means adapted to assemble
the two kinds of spacers along their respective raceways into a single pile; sub-
stantially as described.
86. A controller for the purpose specified, operatively connected with the line
and word shaft clutches of the machine and actuating means for moving the con-
troller to predetermined starting positions; substantially as described.
87. A controller for the purpose specified, operatively connected with the line
and word shaft clutches of the machine, provided with a stepped disc for regulating
the backward setting of the controller, and with actuating means for setting the
controller backward to the predetermined step of the stepped flange; substantially
as described.
°
88. The combination of controller for the purpose specified, adapted to engage
with the clutch operating devices and provided with a stepped disc, or its equiva-

page_text: lent, adapted to regulate the backward setting of the controller; and stop adapted
to be moved into engaging relation with the different steps of the said disc;
substantially as described.
89. The combination of a controller for the purpose specified, adapted to engage
with the clutch operating devices and provided with a stepped disc or its equiva-
lent adapted to regulate the backward setting of the controller; a stop adapted to
be moved into engaging relation with the different steps of the said disc, and means
for setting the controller back to the extent predetermined by the stop; sub-
stantially as described.
90. The combination of a controller for the purpose specified, adapted to engage
with the clutch operating devices, and provided with a pawl located thereon in
engaging relation to an actuating ratchet; a stepped disc, or its equivalent,
adapted to regulate the backward setting of the controller; and a stop located in
the path of the stepped disc and adapted to be moved into engaging relation with
the step of the controller corresponding to the number of spaces in the line; sub-
stantially as described.
91. In a machine of the class specified and in combination with the controller
and with the separators thereof, the controller being provided with a stepped disc
or its equivalent; a stop located in the plane of the said disc, and adapted to be
moved across the path of the steps thereof, and means substantially as described
adapted to be actuated by the separators whereby the stop is moved into engaging
relation with that step of the flange which corresponds with the number of
separators in the line; substantially as described.
92. In a machine of the class specified and in combination with the controller
and with the separators thereof, the controller being provided with a stepped disc
or its equivalent; a stop located in the plane of the said disc and capable of move-
ment across the path of the series of steps thereof; and a star wheel or its
equivalent located in engaging relation to the separators and operatively con-
nected with the stop, whereby the latter is moved into engaging relation with the
successive steps of the disc, as the said star wheel is intermittently rotated by the
successive separators; substantially as described.
93. The combination of a controller for the purpose specified, adapted to engage
with the clutch operating devices, provided with a pawl; a rotating ratchet
located in engaging relation to the pawl; and means substantially as described for
moving the pawl into and out of engagement with the ratchet.
94. The combination of a controller for the purpose specified, adapted to engage
with the clutch operating devices; a pawl pivotally mounted thereon; a rotating
ratchet located in engaging relation to the pawl; and a cam or its equivalent
adapted to disengage the pawl from the ratchet when the controller has operated
its clutches; substantially as described.
95. In combination with a controller for the purpose specified; a pawl pivotally
mounted thereon; a rotating ratchet located in engaging relation to the pawl;
a spring or its equivalent adapted to press the pawl toward engaging relation with
the ratchet; and a cam, or its equivalent, adapted to disengage the pawl at the
desired position of the controller, and adapted to hold the pawl out of engagement
while the controller is being reset.
96. In a controller for the purpose specified and in combination with means for
moving the controller backward through the desired distance, and with means for
moving it forward to its clutch operating position; a pawl; a cam adapted to
engage with the pawl; and means for actuating the cam whereby the pawl is
moved into and out of engaging relation with the ratchet; substantially as
described.
97. In a machine of the class specified and in combination with the controller
and with the measuring mechanism thereof, provided with a stepped disc or its
equivalent; a detent adapted to engage with and hold the controller in its forward
position, and operatively connected with the measuring mechanism, whereby the

page_text: controller is released from the detent at a suitable stage in the operation of the
measuring mechanism; substantially as described.
98. In a machine of the class specified and in combination with the controller
and with the measuring mechanisin thereof, the controller being provided with a
pawl located thereon in engaging relation to an actuating ratchet; a cam or its
equivalent located in engaging relation to the pawl and operatively connected
with the measuring mechanism, whereby the controller is put in operation at the
desired point in the operation of the measuring mechanism; substantially as
described.
99. In a machine of the class specified and in combination with the measuring
mechanism and with the word mechanism thereof, the latter being provided with a
clutch adapted to be moved into and out of engagement with the actuating mechanism
therefor; means operatively connected with the measuring mechanism and adapted
to move the word mechanism clutch into engagement with its actuating devices at
a suitable time in the operation of the measuring mechanism; substantially as
described.
100. In a machine of the class specified and in combination with the measuring
mechanism and with the word mechanism thereof, the latter being provided with a
clutch adapted to be moved into and out of engaging relation with its actuating
means a controller provided with a pawl located thereon in engaging relation to
an actuating ratchet, and a cam, or its equivalent located in engaging relation to
the pawl with means substantially as described operatively connected with the
cam, and with the word mechanism clutch, and located in engaging relation to the
measuring mechanism, whereby the controller and the word mechanism are put in
operation simultaneously at the desired point in the operation of the measuring
mechanism; substantially as described.
101. In a type justifying machine and in combination with the spacer inserting
mechanism thereof, provided with a clutch located in operative relation to a
moving actuating shaft; the herein described controller, or its equivalent, adapted
to disconnect the clutch of the spacer inserting mechanism at a given position, with
means for setting the controller back from its clutch operating position to an
extent suitably related to the number of spaces in the line to be justified; sub-
stantially as described.
102. In a type justifying-machine and in combination with the spacer inserting
mechanism thereof, provided with a clutch located in operative relation to a moving
actuating shaft; the herein described controller, or its equivalent, adapted to
disconnect the clutch of the spacer inserting mechanism at a given position, with
means for setting the controller back from its clutch operating position to an extent
suitably related to the number of spaces in the line to be justified, and means for
simultaneously engaging the controller and the spacer inserting mechanism with
their respective actuating shafts; substantially as described.
103. In a type justifying machine and in combination with the actuating
mechanism and with the measuring devices thereof; means adapted to be operated
by the type matter to be justified, and adapted to cause the measuring devices to
be engaged by the actuating mechanism; substantially as described.
104. In a type justifying machine, and in combination with the actuating
mechanism thereof; a line measuring device; a latch; and means disposed in
the pathway of the type matter adapted to hold the measuring devices in engage-
ment with the actuating mechanism while the type matter is present; substantially
as described.
105. In a machine of the class specified and in combination with the measuring
mechanism and with the actuating means therefor; provided with a clutch adapted
to engage and disengage the measuring mechanism therefrom; an indicator arm
located in engaging relation to the type containing channel, and operatively con-
nected with the clutch, whereby the clutch of the measuring mechanism is held
in engaging relation therewith at all times while type matter is contained in the
channel; substantially as described.

page_text: 106. In a machine of the class specified and in combination with the line grab
mechanism and with the measuring mechanism thereof, provided with a clutch
adapted to engage the two mechanisms together; an indicator arm located in
engaging relation to the type matter contained in the channel, together with
operative connection between the indicator arm end and the clutch, whereby the
word and the line mechanisms remain clutched together during the presence of
matter in the type channel; substantially as described.
Dated the th
1000
PHILLIPS & LEIGH,
No. 22, Southampton Buildings, Chancery Lane, London, W.C.,
Agents for the Applicant.